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WO2019150852A1 - 熱交換器又は熱交換器を有する冷凍装置 - Google Patents

熱交換器又は熱交換器を有する冷凍装置 Download PDF

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Publication number
WO2019150852A1
WO2019150852A1 PCT/JP2018/047589 JP2018047589W WO2019150852A1 WO 2019150852 A1 WO2019150852 A1 WO 2019150852A1 JP 2018047589 W JP2018047589 W JP 2018047589W WO 2019150852 A1 WO2019150852 A1 WO 2019150852A1
Authority
WO
WIPO (PCT)
Prior art keywords
pipe
space
header
refrigerant
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/047589
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
佐藤　健
正憲 神藤
好男 織谷
甲樹 山田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to ES18903461T priority Critical patent/ES2896693T3/es
Priority to US16/966,767 priority patent/US20230106747A1/en
Priority to CN201880088246.5A priority patent/CN111656125A/zh
Priority to EP18903461.4A priority patent/EP3748275B1/en
Publication of WO2019150852A1 publication Critical patent/WO2019150852A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/20—Casings or covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present disclosure relates to a heat exchanger or a refrigeration apparatus having a heat exchanger.
  • Patent Document 1 International Publication WO2013 / 160952
  • a heat exchange unit in which a plurality of flat tubes are arranged, a flow divider disposed at a liquid side end, a heat exchange unit, and a branch flow Heat exchangers having a header tube disposed between the vessels are known.
  • a plurality of spaces are formed in the header pipe so as to be aligned along the direction in which the flat tubes are stacked, and the corresponding flat tubes communicate with each space.
  • each space in the header pipe and the shunt are connected by a thin pipe.
  • a plurality of paths are formed in the heat exchanger configured as described above.
  • the flat tubes are often arranged so as to be aligned along the vertical direction.
  • the liquid refrigerant tends to stay in a flat tube (pass) arranged near the lowermost stage in relation to the head difference caused by the installation height of the flow divider.
  • a heat exchanger that suppresses retention of liquid refrigerant.
  • the heat exchanger includes a heat exchange part, a first diversion part, and a plurality of second diversion parts.
  • the heat exchange part includes a plurality of flat tubes.
  • the plurality of flat tubes are arranged along the vertical direction in the installed state.
  • the first diversion part includes a first pipe, a plurality of second pipes, and a main body part.
  • the first pipe is a pipe through which the refrigerant enters and exits.
  • the second pipe forms a refrigerant flow path closer to the heat exchange part than the first pipe.
  • the main body is formed in the first space.
  • the first space communicates with one end of the first tube and one end of each second tube. The first space allows the refrigerant flowing out from one of the first pipe and the second pipe to flow into the other.
  • the second diversion unit forms a refrigerant flow path between the heat exchange unit and the first diversion unit.
  • the second branch part is formed with the second space inside.
  • the second space communicates with one end of the corresponding flat tube.
  • the second space communicates with the other end of the corresponding second pipe.
  • the second space allows the refrigerant flowing out from one of the corresponding flat tube and second tube to flow into the other.
  • Three or more second spaces are arranged along the vertical direction in the installed state.
  • the number of flat tubes communicating with the lower second space is smaller than the number of flat tubes communicating with the central second space.
  • the center second space is the center second space in the installed state.
  • the lower second space is a second space located below the central second space in the installed state.
  • three or more second spaces are arranged along the vertical direction, and are lower than the number of flat tubes communicating with the central second space (second space located in the center).
  • the number of flat tubes communicating with the second side space is smaller. This facilitates the reduction of the liquid refrigerant head in the first space when used as a condenser.
  • the liquid refrigerant is suppressed from staying when used as a condenser.
  • the “center second space” is arranged between the uppermost second space and the lowermost second space among the plurality of second spaces arranged in the vertical direction in the installed state.
  • Second space includes a space located at a height of at least one third from the lower end of the height dimension of the entire heat exchanger and at most one third from the upper end in the installed state.
  • the number of “center second spaces” is appropriately selected according to the number of second spaces.
  • the “lower second space” here is the central second space including the second space arranged at the lowest stage among the plurality of second spaces arranged in the vertical direction in the installed state. It is the 2nd space arranged below.
  • the number of “center second spaces” is appropriately selected according to the number of second spaces.
  • the heat exchanger according to the second aspect is the heat exchanger according to the first aspect, and further includes a third pipe and at least one third branch part.
  • the third pipe is a refrigerant outlet pipe when the first pipe is a refrigerant inlet pipe.
  • the third pipe is a refrigerant inlet pipe when the first pipe is a refrigerant outlet pipe.
  • the third branch part forms a refrigerant flow path between the second branch part and the third pipe.
  • the third branch part is formed with the third space inside.
  • the third space communicates with the other end of the corresponding flat tube.
  • the third space communicates with the third tube, or communicates with one end of the second flat tube disposed on the same stage as the flat tube.
  • the third space is a space for allowing the refrigerant flowing out from the other end of the flat tube to flow into the third tube or the second flat tube when the first tube is the refrigerant inlet tube.
  • the third space is a space through which the refrigerant flowing out from one end of the third tube or the second flat tube flows into the flat tube when the first tube is an outlet tube for the refrigerant.
  • the heat exchanger according to the third aspect is the heat exchanger according to the first aspect or the second aspect, and the heat exchange unit exchanges heat between the refrigerant in the flat tube and the air flow.
  • the air flow passing through the periphery of the flat tube communicating with the second space above the lower second space is higher than the wind speed of the air flow passing through the periphery of the flat tube communicating with the lower second space.
  • the wind speed is larger.
  • the heat exchanger according to the fourth aspect is the heat exchanger according to any one of the first to third aspects, and the lower second space is one third of the overall height of the heat exchange part in the installed state. It is arranged at the following height position.
  • the heat exchanger according to the fifth aspect is the heat exchanger according to any one of the first to fourth aspects, and the flat tube located at the lowest stage in the installed state communicates with the second space on the lower stage side.
  • the heat exchanger according to the sixth aspect is the heat exchanger according to any one of the first to fifth aspects, and in the installed state, a plurality of lower second spaces are arranged along the vertical direction.
  • the heat exchanger according to the seventh aspect is any one of the heat exchangers according to the first to sixth aspects, and the plurality of central second spaces are arranged along the vertical direction in the installed state.
  • a heat exchanger according to an eighth aspect is the heat exchanger according to any one of the first to seventh aspects, wherein the first pipe extends in a downward direction from the first space in the installed state. One end is connected to. One end of the second tube is connected to the main body so as to extend upward from the first space in the installed state.
  • a heat exchanger according to a ninth aspect is the heat exchanger according to any one of the first to seventh aspects, and the first pipe extends in the upward direction from the first space in the installed state. One end is connected to. One end of the second tube is connected to the main body so as to extend downward from the first space in the installed state.
  • a refrigeration apparatus includes a compressor and any one of the heat exchangers according to the first to ninth aspects.
  • the compressor compresses the refrigerant.
  • the schematic block diagram of an air conditioning system The perspective view of an outdoor unit.
  • tube shown by FIG. The enlarged view which showed a part of 2nd partition member to which the partition plate and the baffle plate were attached.
  • tube The perspective view of a shunt body.
  • the outdoor heat exchanger 15 heat exchanger
  • the air conditioning system 1 refrigeration apparatus
  • the following embodiment is a specific example, does not limit the technical scope, and can be changed as appropriate without departing from the scope of the invention.
  • the “horizontal direction” means the direction shown in each figure unless otherwise specified, and indicates the direction in the installed state (note that the right and left and / or front and rear in the following embodiments are appropriately reversed. May be).
  • the outdoor heat exchanger 15 according to an embodiment of the present disclosure is applied to the outdoor unit 10 that is a heat source unit of the air conditioning system 1.
  • FIG. 1 is a schematic configuration diagram of an air conditioning system 1.
  • the air conditioning system 1 is a system that performs air conditioning such as cooling or heating of a target space (a space to be conditioned such as a living space or a storage space) by a vapor compression refrigeration cycle.
  • the air conditioning system 1 mainly includes an outdoor unit 10, a plurality (two in this case) of indoor units 20, and a liquid side communication pipe LP and a gas side communication pipe GP.
  • the outdoor unit 10 and each indoor unit 20 are connected via the liquid side communication pipe LP and the gas side communication pipe GP, whereby the refrigerant circuit RC is configured.
  • a refrigeration cycle is performed in which the refrigerant is compressed, cooled or condensed, decompressed, heated or evaporated, and then compressed again in the refrigerant circuit RC.
  • Outdoor unit 10 The outdoor unit 10 is installed in an outdoor space.
  • the outdoor space is a space outside the target space where air conditioning is performed, and is, for example, the outdoors on the rooftop of a building, an underground space, or the like.
  • the outdoor unit 10 is connected to each indoor unit 20 via the liquid side communication pipe LP and the gas side communication pipe GP, and constitutes a part of the refrigerant circuit RC (outdoor circuit RC1).
  • the outdoor unit 10 mainly includes a plurality of refrigerant pipes (first pipe P1 to ninth pipe P9), an accumulator 11, a compressor 12, an oil separator 13, and a four-way switching valve 14 as devices constituting the outdoor circuit RC1.
  • the outdoor heat exchanger 15 and the outdoor expansion valve 16 are included. These devices (11-16) are connected by refrigerant piping.
  • the first pipe P1 connects the gas side communication pipe GP and the first port of the four-way switching valve 14.
  • the second pipe P2 connects the inlet port of the accumulator 11 and the second port of the four-way switching valve 14.
  • the third pipe P ⁇ b> 3 connects the outlet port of the accumulator 11 and the suction port of the compressor 12.
  • the fourth pipe P4 connects the discharge port of the compressor 12 and the inlet of the oil separator 13.
  • the fifth pipe P5 connects the outlet of the oil separator 13 and the third port of the four-way switching valve 14.
  • the sixth pipe P6 connects the oil return port of the oil separator 13 and the portion between both ends of the third pipe P3.
  • the seventh pipe P7 connects the fourth port of the four-way switching valve 14 and the gas side inlet / outlet of the outdoor heat exchanger 15.
  • the eighth pipe P8 connects the liquid side inlet / outlet of the outdoor heat exchanger 15 and one end of the outdoor expansion valve 16.
  • the ninth pipe P9 connects the other end of the outdoor expansion valve 16 and the liquid side connection pipe LP.
  • these refrigerant pipes (P1-P9) may actually be constituted by a single pipe, or may be constituted by connecting a plurality of pipes via joints or the like.
  • the accumulator 11 is a container that stores the refrigerant and separates the gas and liquid in order to prevent the liquid refrigerant from being excessively sucked into the compressor 12.
  • the compressor 12 is a device that compresses a low-pressure refrigerant in the refrigeration cycle until it reaches a high pressure.
  • the compressor 12 has a hermetic structure in which a displacement type compression element such as a rotary type or a scroll type is rotationally driven by a compressor motor (not shown).
  • the operation frequency of the compressor motor can be controlled by an inverter, whereby the capacity of the compressor 12 can be controlled.
  • the start / stop and operating capacity of the compressor 12 are controlled by the outdoor unit controller 19.
  • the oil separator 13 is a container that separates refrigeration oil compatible with the refrigerant discharged from the compressor 12 and returns it to the compressor 12.
  • the four-way switching valve 14 is a flow path switching valve for switching the refrigerant flow in the refrigerant circuit RC.
  • the outdoor heat exchanger 15 is a heat exchanger that functions as a refrigerant condenser (or radiator) or an evaporator. Details of the outdoor heat exchanger 15 will be described later.
  • the outdoor expansion valve 16 is an electric expansion valve whose opening degree can be controlled, and depressurizes or adjusts the flow rate of the refrigerant flowing in accordance with the opening degree.
  • the outdoor unit 10 has an outdoor fan 18 that generates an outdoor air flow AF (see FIGS. 4 and 5).
  • the outdoor air flow AF (corresponding to “air flow” described in claims) is a flow of air that flows from the outdoor unit 10 into the outdoor unit 10 and passes through the outdoor heat exchanger 15.
  • the outdoor air flow AF is a cooling source or a heating source for the refrigerant flowing through the outdoor heat exchanger 15, and exchanges heat with the refrigerant in the outdoor heat exchanger 15 when passing through the outdoor heat exchanger 15.
  • the outdoor fan 18 includes an outdoor fan motor (not shown) and is driven in conjunction with the outdoor fan motor. The start and stop of the outdoor fan 18 is appropriately controlled by the outdoor unit controller 19.
  • the outdoor unit 10 is provided with a plurality of outdoor sensors (not shown) for detecting the state (mainly pressure or temperature) of the refrigerant in the refrigerant circuit RC.
  • the outdoor sensor is a pressure sensor, a temperature sensor such as a thermistor or a thermocouple.
  • Examples of the outdoor sensor include a suction pressure sensor that detects a suction pressure that is a refrigerant pressure on the suction side of the compressor 12, a discharge pressure sensor that detects a discharge pressure that is a refrigerant pressure on the discharge side of the compressor 12, And the temperature sensor etc. which detect the temperature of the refrigerant
  • the outdoor unit 10 also has an outdoor unit control unit 19 that controls the operation / state of each device included in the outdoor unit 10.
  • the outdoor unit control unit 19 includes a microcomputer having a CPU, a memory, and the like, and various electric components.
  • the outdoor unit control unit 19 is electrically connected to each device (12, 14, 16, 18, etc.) and outdoor sensors included in the outdoor unit 10, and inputs / outputs signals to / from each other.
  • the outdoor unit controller 19 transmits and receives control signals and the like to and from the indoor unit controller 25 of each indoor unit 20 and a remote controller (not shown).
  • the outdoor unit controller 19 is housed in an electrical component box 39 (see FIGS. 3 and 4) described later.
  • the indoor unit 20 is installed in a room (such as a living room or a ceiling space) and constitutes a part of the refrigerant circuit RC (the indoor circuit RC2).
  • the indoor unit 20 mainly includes an indoor expansion valve 21 and an indoor heat exchanger 22 as devices constituting the indoor circuit RC2.
  • the indoor expansion valve 21 is an electric expansion valve capable of opening degree control, and depressurizes or adjusts the flow rate of the refrigerant flowing in accordance with the opening degree.
  • the indoor heat exchanger 22 is a heat exchanger that functions as a refrigerant evaporator or condenser (or radiator).
  • the indoor unit 20 has an indoor fan 23 for sucking air in the target space, passing through the indoor heat exchanger 22 and exchanging heat with the refrigerant, and then sending it again to the target space.
  • the indoor fan 23 includes an indoor fan motor that is a drive source.
  • the indoor fan 23 generates an indoor air flow when driven.
  • the indoor air flow is a flow of air that flows into the indoor unit 20 from the target space, passes through the indoor heat exchanger 22, and is blown into the target space.
  • the indoor air flow is a heating source or a cooling source for the refrigerant flowing through the indoor heat exchanger 22, and exchanges heat with the refrigerant in the indoor heat exchanger 22 when passing through the indoor heat exchanger 22.
  • the indoor unit 20 has an indoor unit control unit 25 that controls the operation / state of the devices (21, 23, etc.) included in the indoor unit 20.
  • the indoor unit control unit 25 includes a microcomputer including a CPU and a memory, and various electrical components.
  • the liquid side communication pipe LP and the gas side communication pipe GP are refrigerant communication pipes that connect the outdoor unit 10 and the indoor units 20 and are constructed on site.
  • the pipe lengths and pipe diameters of the liquid side connection pipe LP and the gas side connection pipe GP are appropriately selected according to the design specifications and the installation environment.
  • the liquid side connection pipe LP and the gas side connection pipe GP may actually be configured by a single pipe, or may be configured by connecting a plurality of pipes via joints or the like. .
  • the gas refrigerant that has flowed into the outdoor heat exchanger 15 performs heat exchange with the outdoor air flow AF sent by the outdoor fan 18 in the outdoor heat exchanger 15 to dissipate heat and condense.
  • the refrigerant that has flowed out of the outdoor heat exchanger 15 flows into the indoor circuit RC2 of the indoor unit 20 in operation through the liquid side connection pipe LP.
  • the refrigerant that has flowed into the indoor side circuit RC2 of the indoor unit 20 during operation flows into the indoor expansion valve 21 and is decompressed to a low pressure in the refrigeration cycle in accordance with the opening of the indoor expansion valve 21, and then is subjected to indoor heat exchange. Flows into the vessel 22.
  • the refrigerant flowing into the indoor heat exchanger 22 evaporates by exchanging heat with the indoor air flow sent by the indoor fan 23, becomes a gas refrigerant, and flows out of the indoor heat exchanger 22.
  • the gas refrigerant that has flowed out of the indoor heat exchanger 22 flows out of the indoor circuit RC2.
  • the refrigerant that has flowed out of the indoor circuit RC2 flows into the outdoor circuit RC1 through the gas side connection pipe GP.
  • the refrigerant that has flowed into the outdoor circuit RC1 flows into the accumulator 11.
  • the refrigerant flowing into the accumulator 11 is temporarily stored and then sucked into the compressor 12 again.
  • the refrigerant that has flowed into the indoor circuit RC2 flows into the indoor heat exchanger 22 and condenses by exchanging heat with the indoor airflow sent by the indoor fan 23.
  • the refrigerant that has flowed out of the indoor heat exchanger 22 flows into the indoor expansion valve 21, is decompressed or adjusted in flow rate according to the opening of the indoor expansion valve 21, and then flows out of the indoor circuit RC2.
  • the refrigerant that has flowed out of the indoor circuit RC2 flows into the outdoor circuit RC1 through the liquid side connection pipe LP.
  • the refrigerant that has flowed into the outdoor circuit RC1 flows into the outdoor expansion valve 16 and is depressurized to a low pressure in the refrigeration cycle according to the degree of opening of the outdoor expansion valve 16, and then enters the liquid side inlet / outlet of the outdoor heat exchanger 15. Inflow.
  • the refrigerant flowing into the outdoor heat exchanger 15 evaporates by exchanging heat with the outdoor air flow AF sent by the outdoor fan 18 in the outdoor heat exchanger 15.
  • the refrigerant flowing out from the gas side inlet / outlet of the outdoor heat exchanger 15 flows into the accumulator 11.
  • the refrigerant flowing into the accumulator 11 is temporarily stored and then sucked into the compressor 12 again.
  • FIG. 2 is a perspective view of the outdoor unit 10.
  • FIG. 3 is a schematic exploded view of the outdoor unit 10.
  • Outdoor unit casing 30 The outdoor unit 10 includes an outdoor unit casing 30 that constitutes an outer shell and accommodates each device (11-16 and the like).
  • the outdoor unit casing 30 is formed in a substantially rectangular parallelepiped shape by assembling a plurality of sheet metal members. Most of the left side surface, the right side surface, and the back surface of the outdoor unit casing 30 are openings, and the openings function as an intake port 301 for sucking the outdoor airflow AF.
  • the outdoor unit casing 30 mainly includes a pair of installation legs 31, a bottom frame 33, a plurality of (four in this case) support columns 35, a front panel 37, and a fan module 38.
  • the installation leg 31 is a sheet metal member that extends in the left-right direction and supports the bottom frame 33 from below. In the outdoor unit casing 30, installation legs 31 are disposed in the vicinity of the front end and the vicinity of the rear end.
  • the bottom frame 33 is a sheet metal member that constitutes a bottom surface portion of the outdoor unit casing 30.
  • the bottom frame 33 is disposed on the pair of installation legs 31.
  • the bottom frame 33 has a substantially rectangular shape in plan view.
  • FIG. 2-3 shows a state in which the support column 35 extends in the vertical direction from each of the four corner portions of the bottom frame 33.
  • the front panel 37 is a sheet metal member that constitutes a front portion of the outdoor unit casing 30.
  • the fan module 38 is attached in the vicinity of the upper end of each column 35.
  • the fan module 38 constitutes a part of the outdoor unit casing 30 that is above the front, back, left side, and right side columns 35 and the top surface of the outdoor unit casing 30.
  • the fan module 38 includes the outdoor fan 18 and the bell mouth 381. More specifically, the fan module 38 is an assembly in which the outdoor fan 18 and the bell mouth 381 are accommodated in a substantially rectangular parallelepiped box having an upper surface and a lower surface opened.
  • the outdoor fan 18 is arranged in such a posture that the rotation axis extends in the vertical direction.
  • the upper surface portion of the fan module 38 is open and functions as a blowout port 302 that blows out the outdoor airflow AF from the outdoor unit casing 30.
  • the blower outlet 302 is provided with a grid-like grill 382.
  • the outdoor unit 10 may have a plurality of fan modules 38.
  • two fan modules 38 may be arranged side by side.
  • the outdoor unit 10 may include an outdoor unit casing 30 having a size larger than that of the outdoor unit 10 including one fan module 38, and may include one front panel 37 on each side.
  • the size of the outdoor heat exchanger 15 may be configured to be large according to the size of the outdoor unit casing 30.
  • FIG. 4 is a diagram schematically showing the arrangement mode of the equipment arranged on the bottom frame 33 and the flow direction of the outdoor air flow AF. As shown in FIG. 4, various devices including an accumulator 11, a compressor 12, an oil separator 13, and an outdoor heat exchanger 15 are arranged at predetermined positions on the bottom frame 33. An electrical component box 39 that houses the outdoor unit control unit 19 is disposed on the bottom frame 33.
  • the outdoor heat exchanger 15 includes a heat exchanging unit 40 arranged along the left side surface, the right side surface, and the back surface of the outdoor unit casing 30 (see FIG. 4).
  • the heat exchanging unit 40 has substantially the same height as the intake port 301.
  • Most of the back surface, the left side surface, and the right side surface of the outdoor unit casing 30 are the intake ports 301, and the heat exchange unit 40 of the outdoor heat exchanger 15 is exposed from the intake ports 301.
  • the back surface, the left side surface, and the right side surface of the outdoor unit casing 30 are substantially formed by the heat exchange unit 40 of the outdoor heat exchanger 15.
  • the outdoor heat exchanger 15 has three heat exchange portions 40, and has a curved portion on the left and right in plan view in relation to this (see B1, B2, and B3 shown in FIG. 8). It has a substantially U-shape that opens in the front direction.
  • FIG. 5 is a diagram schematically showing the flow of the outdoor air flow AF in the outdoor unit casing 30.
  • the outdoor air flow AF flows into the outdoor unit casing 30 from the intake ports 301 formed on the left side surface, the right side surface, and the back surface of the outdoor unit casing 30, and the outdoor heat exchanger 15 After passing through (the heat exchanging unit 40), it flows mainly from the lower side to the upper side, and flows out from the air outlet 302. That is, the outdoor air flow AF flows along the horizontal direction into the outdoor unit casing 30 via the intake port 301, passes through the outdoor heat exchanger 15, and then turns upward to move toward the outlet 302.
  • the outdoor air flow AF flowing into the outdoor unit casing 30 the wind speed is higher in the space near the outdoor fan 18 than in the lower space far from the outdoor fan 18.
  • the outdoor air flow AF that passes through the heat exchange unit 40 of the outdoor heat exchanger 15 is an upper part (especially above the center) above the air that passes through the lower part (particularly the path below the center). The air speed passing through (pass) is higher.
  • FIG. 6 is a perspective view of the outdoor heat exchanger 15.
  • FIG. 7 is a perspective view of the outdoor heat exchanger 15 viewed from a direction different from that in FIG.
  • FIG. 8 is a schematic diagram of the outdoor heat exchanger 15 in plan view.
  • the outdoor heat exchanger 15 mainly includes a heat exchange unit 40, a first header pipe 50, a gas side collecting pipe 60, a second header pipe 70, a folded header 80, and a flow divider 90. Yes.
  • the heat exchange unit 40, the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70, the folded header 80, and the flow divider 90 are all made of aluminum or an aluminum alloy.
  • the outdoor heat exchanger 15 includes a heat exchange unit 40, a first header pipe 50, a gas side collecting pipe 60, a second header pipe 70, a folded header 80, and a flow divider 90 in a temporarily assembled state. It is assembled by brazing with materials.
  • FIG. 9 is a schematic diagram of the heat exchange unit 40.
  • FIG. 10 is a partially enlarged view of a cross section taken along line XX in FIG.
  • the heat exchange unit 40 is a part where the outdoor air flow AF and the refrigerant in the outdoor heat exchanger 15 (a heat transfer tube 41 described later) exchange heat. Specifically, the heat exchanging unit 40 is a portion that extends in a direction intersecting the traveling direction of the outdoor air flow AF in the central portion of the outdoor heat exchanger 15, and occupies most of the outdoor heat exchanger 15.
  • the heat exchange part 40 mainly has three heat exchange surfaces, and has a substantially U shape or a substantially C shape in plan view (see FIG. 8).
  • the outdoor heat exchanger 15 has a plurality of (here, two) heat exchange units 40.
  • the outdoor heat exchanger 15 includes a windward side heat exchange unit 40 a and a leeward side heat exchange unit 40 b as the heat exchange unit 40.
  • the windward side heat exchanging part 40a and the leeward side heat exchanging part 40b are arranged adjacent to each other along the flow direction of the outdoor air flow AF.
  • the windward side heat exchanging part 40a is the heat exchanging part 40 located on the windward side (outside here).
  • the leeward side heat exchanging part 40b is the heat exchanging part 40 located on the leeward side (inner side here).
  • Each heat exchanging unit 40 mainly includes a plurality of heat transfer tubes 41 (corresponding to “flat tubes” described in claims) through which a refrigerant flows and a plurality of heat transfer fins 42.
  • the heat transfer tube 41 is a flat multi-hole tube having a plurality of refrigerant channels 411 formed therein.
  • the heat transfer tube 41 is made of aluminum or aluminum alloy.
  • 97 heat transfer tubes 41 are arranged in the vertical direction (vertical direction) in the heat exchange unit 40 in the installed state.
  • the heat transfer tube 41 extends along the horizontal direction, and extends along the shape of the heat exchange part 40 in plan view.
  • the heat transfer tube 41 included in the windward heat exchange unit 40a is referred to as a windward heat transfer tube 41a
  • the heat transfer tube 41 included in the leeward heat exchange unit 40b is referred to as a leeward heat transfer tube 41b.
  • windward side heat transfer tube 41 a is connected to the second header tube 70, and the other end is connected to the folded header 80.
  • the leeward heat transfer tube 41 b has one end connected to the first header tube 50 and the other end connected to the folded header 80.
  • the heat transfer fins 42 are flat members that increase the heat transfer area between the heat transfer tubes 41 and the outdoor air flow.
  • the heat transfer fins 42 are made of aluminum or aluminum alloy.
  • the heat transfer fins 42 extend in the vertical direction so as to intersect the heat transfer tubes 41 in the heat exchanging unit 40.
  • a plurality of notches are formed in the heat transfer fin 42 in the vertical direction, and the heat transfer tubes 41 are inserted into the notches.
  • the alternate long and two short dashes arrow indicates the flow direction of the refrigerant flowing through the heat exchange section.
  • the reason why the two-dot chain line arrow points in both directions is that the flow of refrigerant is reversed between the heating operation and the cooling operation.
  • the refrigerant flows from the second header pipe 70 into the windward heat exchange section 40a (windward heat transfer pipe 41a) and then flows back, and then turns back at the turnup header 80 and from the turnup header 80 to the leeward heat exchange section. It flows into 40 b (leeward side heat transfer tube 41 b) and reaches the first header tube 50.
  • the refrigerant flows from the first header pipe 50 into the leeward side heat exchange section 40b (the leeward side heat transfer pipe 41b), and then flows back at the folding header 80. It flows into 40a (windward side heat transfer tube 41a) and reaches the second header tube 70.
  • FIG. 11 is an exploded view of the first header pipe 50 and the gas side collecting pipe 60.
  • the first header pipe 50 is an elongated hollow cylindrical part extending in the vertical direction with its upper end and lower end closed.
  • tube 50 is arrange
  • the first header tube 50 includes a leeward heat transfer tube side member 51, a first header partition member 52, a collecting tube side member 53, a plurality of first partition plates 54, and a second partition plate 55.
  • the leeward heat transfer tube side member 51, the first header partition member 52 and the collecting pipe side member 53 are respectively in a state where the first header partitioning member 52 is sandwiched between the leeward heat transfer tube side member 51 and the collecting tube side member 53. Are combined and integrated so that their longitudinal directions coincide.
  • the upper end and the lower end are closed by two first partition plates 54.
  • the second partition plate 55 is disposed near the lower end, and the inside of the first header pipe 50 is divided into the first header main space S1 and the first header subspace S2. (See FIG. 32). As shown in FIG.
  • the first header main space S1 communicates with one end of 96 leeward heat transfer tubes 41b, and the first header subspace S2 is one leeward side located at the lowermost position. It communicates with one end of the heat transfer tube 41b.
  • the leeward heat transfer tube side member 51, the first header partition member 52, the collecting tube side member 53, the first partition plate 54, and the second partition plate 55 are joined together by brazing with a brazing material in a furnace. It becomes.
  • the leeward heat transfer tube side member 51 is a member having an arcuate cross section cut along a plane perpendicular to the vertical direction.
  • the leeward heat transfer tube side member 51 is formed with a leeward heat transfer tube connection opening 511 into which an end of the heat transfer tube 41 (leeward side heat transfer tube 41b) is inserted.
  • the number of leeward heat transfer tube connection openings 511 is the same as the number of stages of the heat transfer tubes 41.
  • the first header partition member 52 has a plurality of openings (not shown) for allowing the coolant to flow from the leeward heat transfer tube side member 51 toward the collecting tube side member 53.
  • the collecting pipe side member 53 has an arcuate cross section cut along a plane perpendicular to the vertical direction.
  • a plurality of openings 531 into which one end of the connection pipe 61 is inserted are formed in the collecting pipe side member 53.
  • the connection pipe 61 is a pipe connected to the first header pipe 50 and the gas side collecting pipe 60.
  • the number of the openings 531 is the same as the number of the plurality of connecting pipes 61 arranged in the vertical direction.
  • the opening 531 communicates with the first header main space S1.
  • the collecting pipe side member 53 is formed with a second thin tube connection opening 532 for connecting a second thin tube 94 (described later) of the flow divider 90.
  • the second capillary connection opening 532 communicates with the first header subspace S2.
  • the gas side collecting pipe 60 (corresponding to “third pipe” in the claims) is a cylindrical straight pipe having a bottom.
  • the gas side collecting pipe 60 forms a gas side inlet / outlet in the outdoor heat exchanger 15.
  • the gas-side collecting pipe 60 is a refrigerant inlet pipe during normal cycle operation (when an inlet / outlet pipe 91 of a flow divider 90 described later is an outlet pipe of the refrigerant).
  • the gas side collecting pipe 60 is an outlet pipe for the refrigerant during reverse cycle operation (when an inlet / outlet pipe 91 described later is an inlet pipe for the refrigerant).
  • the gas side collecting pipe 60 is disposed adjacent to the first header pipe 50.
  • the first header pipe 50 and the gas side collecting pipe 60 are bound by a binding band 62.
  • the gas side collecting pipe 60 is located between the first header pipe 50 and the seventh pipe P7 in the refrigerant circuit RC. One end of a seventh pipe P7 is connected to the gas side collecting pipe 60.
  • the gas side collecting pipe 60 has a plurality of openings (not shown) connected to the other end of the connecting pipe 61 (extending to the first header pipe 50) (not shown).
  • the outdoor heat exchanger 15 communicates from the heat transfer pipe 41 (leeward heat transfer pipe 41b) to the seventh pipe P7 through the first header pipe 50, the plurality of connection pipes 61, and the gas side collecting pipe 60.
  • FIG. 12 is an exploded view of the second header pipe 70.
  • FIG. 13 is an enlarged view showing a part of the second header pipe 70 shown in FIG.
  • FIG. 14 is an enlarged view of a part of the second header partition member 72 to which the partition plate 74 and the rectifying plate 75 are attached.
  • FIG. 15 is a view of the second header pipe 70 as viewed from above.
  • FIG. 16 is an enlarged schematic view of a part of the second header pipe 70.
  • the second header pipe 70 is an elongated hollow cylindrical part extending in the vertical direction with its upper and lower ends closed.
  • tube 70 is arrange
  • the second header tube 70 includes an upwind heat transfer tube side member 71, a second header partition member 72, a flow divider side member 73, a plurality of partition plates 74, and a plurality of rectifying plates 75.
  • the windward heat transfer tube side member 71, the second header partition member 72, and the flow divider side member 73 are in a state where the second header partition member 72 is sandwiched between the windward heat transfer tube side member 71 and the flow divider side member 73.
  • the upper and lower ends are closed by two partition plates 74.
  • the windward heat transfer tube side member 71, the second header partition member 72, the flow divider side member 73, the partition plate 74, and the rectifying plate 75 are joined and integrated together by brazing with a brazing material in a furnace, for example.
  • the windward heat transfer tube side member 71 has an arcuate cross section cut along a plane perpendicular to the vertical direction.
  • the windward heat transfer tube side member 71 is formed with a plurality of windward heat transfer tube connection openings 711 into which end portions of the corresponding heat transfer tubes 41 (windward heat transfer tubes 41a) are inserted.
  • the number of upwind heat transfer tube connection openings 711 is the same as the number of stages of the heat transfer tubes 41.
  • the plurality of upwind heat transfer tube connection openings 711 are arranged along the vertical direction.
  • the second header partition member 72 is a plate-like member extending along the vertical direction.
  • openings for flowing the refrigerant from the upwind heat transfer tube side member 71 toward the flow divider side member 73 are arranged along the vertical direction. A plurality are formed.
  • the shunt side member 73 has an arcuate cross section cut along a plane perpendicular to the vertical direction.
  • the shunt-side member 73 is formed with a plurality of first capillary connection openings 73a for connecting one end of the corresponding first capillary 93.
  • the number of first capillary connection openings 73a is the same as the number of first capillary tubes 93.
  • the plurality of first capillary connection openings 73a are arranged along the vertical direction.
  • the inside of the second header pipe 70 is partitioned by a plurality of partition plates 74 and divided into a plurality of spaces (ten second header internal spaces SP1 and one second header subspace SPa) (see FIG. 31).
  • a plurality of corresponding heat transfer pipes 41 (upwind transmission pipes) are provided in the second header internal space SP1 formed between the two partition plates 74 in the second header pipe 70.
  • the end of the heat pipe 41a) communicates.
  • the end portion of the corresponding first narrow tube 93 communicates with the second header internal space SP1.
  • the rectifying plate 75 is disposed near the upper portion of the corresponding first thin tube 93.
  • the second header subspace SPa is formed near the lower end of the second header pipe 70 and is located below each second header internal space SP1 (see FIG. 31).
  • the second header subspace SPa communicates with end portions of a plurality of (in this case, two) corresponding heat transfer tubes 41 (upstream heat transfer tubes 41a).
  • the second header partition member 72 has a first communication opening 72a formed near the lower side of the upper partition plate 74, and a second communication opening 72b formed near the upper side of the rectifying plate 75. Has been.
  • the rectifying plate 75 is formed with a third communication opening 75a.
  • Each second header internal space SP1 allows the refrigerant flowing out from one of the corresponding heat transfer tube 41 and the first thin tube 93 to flow into the other.
  • the refrigerant that has flowed into the second header internal space SP1 from the first thin tube 93 flows upward via the small third communication opening 75a.
  • the refrigerant that has flowed upward flows into the flow paths 411 of the plurality of heat transfer tubes 41 (41 a) between the rectifying plate 75 and the upper partition plate 74.
  • a part of the refrigerant that has flowed upward forms a loop-like flow (see the broken-line arrow Ar in FIG. 16) that passes through the second communication opening 72b after the first communication opening 72a.
  • Such a refrigerant eventually flows into the flow path 411 of the plurality of heat transfer tubes 41 separately from the loop-shaped flow. Further, during the normal cycle operation, the refrigerant flowing into the second header internal space SP1 from the corresponding heat transfer tube 41 passes through the third communication opening 75a and the like and flows into the first thin tube 93.
  • each second header internal space SP1 in the second header pipe 70, is formed along the vertical direction.
  • each second header internal space SP1 includes a part of the windward heat transfer pipe side member 71, a part of the second header partition member 72, a part of the flow divider side member 73, and It is formed by being surrounded by a pair of partition plates 74.
  • a part of the upwind heat transfer tube side member 71, the second header partition member 72, a part of the flow divider side member 73, and the pair of partition plates 74 forming one second header internal space SP1 are combined. It can also be interpreted as the second header internal space forming member 78 (corresponding to “second diversion portion” in the claims).
  • the second header pipe 70 is also possible to interpret the second header pipe 70 as a member configured by a plurality of second header internal space forming members 78 forming the second header internal space SP1.
  • a plurality of second header internal space forming members 78 are arranged along the vertical direction in the installed state (see FIG. 31).
  • each second header internal space forming member 78 is made of aluminum or an aluminum alloy. Each second header internal space forming member 78 has a second header internal space SP1 formed therein. Each second header internal space forming member 78 forms a refrigerant flow path between the windward heat exchange unit 40 a and the flow divider 90. Each second header internal space forming member 78 is formed with a first capillary connection opening 73a for connecting one end of the corresponding first capillary 93. Each second header internal space forming member 78 is formed with an upwind heat transfer tube connection opening 711 for connecting one end of the corresponding heat transfer tube 41. As shown in FIG.
  • the height position of the first thin tube connection opening 73a in the installed state is the upwind heat transfer tube connection opening 711 (wind flow) It is arrange
  • the second header internal space SP1 located above the second header pipe 70 is referred to as “upper second header internal space SA”, and the second header internal space located at the center of the second header pipe 70.
  • SP1 is referred to as “middle second header internal space SB”
  • the second header internal space SP1 located below the second header pipe 70 is referred to as “lower second header internal space SC” (see FIG. 31).
  • the upper second header internal space SA in the installed state is the second header internal space located above the middle second header internal space SB among the plurality of second header internal spaces SP1 arranged in the vertical direction. It is a space SP1 and includes the second header internal space SP1 at the uppermost stage. Specifically, in the present embodiment, the first to fourth second header internal spaces SP1 counted from the top (that is, each second header internal space SP1 positioned above the two-dot chain line L4 in FIG. 31). Corresponds to the upper second header internal space SA.
  • the middle second header internal space SB here (corresponding to the “center second space” described in the claims) is, among the plurality of second header internal spaces SP1 arranged in the vertical direction in the installed state.
  • This is a second header internal space SP1 arranged between the upper second header internal space SP1 and the lowermost second header internal space SP1.
  • the middle second header internal space SB is located at a height of at least one third from the lower end of the overall height dimension of the outdoor heat exchanger 15 and one third or less from the upper end.
  • the second header internal spaces SP1 from the fifth to the eighth from the top that is, the second headers located between the two-dot chain line L4 and the two-dot chain line L8 in FIG. 31).
  • the internal space SP1) corresponds to the middle second header internal space SB.
  • the lower second header internal space SC (corresponding to the “lower second side space” described in the claims) is a plurality of second header internal spaces SP1 arranged along the vertical direction in the installed state. This is a second header internal space SP1 positioned below the middle second header internal space SB, and includes the lowermost second header internal space SP1.
  • the ninth to thirteenth second header internal spaces SP1 (that is, the second header internal spaces SP1 positioned below the two-dot chain line L8 in FIG. 31) counted from the top are the lower second. This corresponds to the header internal space SC.
  • FIG. 17 is a perspective view of the folded header 80.
  • FIG. 18 is a cross-sectional view of the folded header 80 cut along the horizontal direction.
  • FIG. 19 is an enlarged cross-sectional view of a part of the folded header 80 cut along the vertical direction.
  • the folded header 80 is an elongated hollow cylindrical member extending in the vertical direction with the upper end and lower end closed.
  • the folding header 80 is disposed on the other end side of the windward side heat exchanging part 40a and the leeward side heat exchanging part 40b.
  • a plurality of windward openings 81 (the same number as the windward heat transfer tubes 41a) into which the other ends of the windward heat transfer tubes 41a are inserted are formed in the folding header 80.
  • a plurality of leeward openings 82 (the same number as the leeward heat transfer tubes 41b) into which the other end of the leeward heat transfer tube 41b is inserted are formed in the folded header 80.
  • the windward side opening 81 and the leeward side opening 82 are adjacent to each other along the direction in which the windward side heat exchange unit 40a and the leeward side heat exchange unit 40b are adjacent to each other.
  • a plurality of windward side openings 81 and a plurality of leeward side openings 82 are arranged so as to be aligned in the vertical direction.
  • a plurality of turn-back spaces SP2 are formed in which the refrigerant flowing out from one of the adjacent windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b flows into the other.
  • the folding space SP2 (corresponding to the “third space” in the claims) is a space for the refrigerant that has passed through one of the windward side heat transfer tube 41a and the leeward side heat transfer tube 41b to be folded back to the other side (in FIG. 18). (See dashed arrow Ar).
  • the turn-back space SP2 flows the refrigerant flowing out from the end of the leeward heat transfer tube 41b into the leeward heat transfer tube 41a during the normal cycle operation (when the gas side collecting tube 60 is the refrigerant inlet tube). It is a space to make.
  • the turn-back space SP2 is a space for allowing the refrigerant flowing out from the end of the windward side heat transfer tube 41a to flow into the leeward side heat transfer tube 41b during reverse cycle operation (when the gas side collecting pipe 60 is a refrigerant outlet pipe). is there.
  • a pair of windward side openings 81 and a leeward side opening 82 are arranged in each folding space SP2. That is, in the turn-back space SP2, any one of the windward side heat transfer tubes 41a communicates with the corresponding leeward side heat transfer tube 41b.
  • a pair of the windward side heat transfer tubes 41a and the leeward side heat transfer tubes 41b arranged in the same stage communicate with each other in the turn-back space SP2.
  • the number of folding spaces SP2 formed in the folding header 80 is the same as the number of pairs of the windward side opening 81 and the leeward side opening 82.
  • the plurality of folding spaces SP2 are configured by providing a plurality of top portions 85, bottom portions 86, and side portions 87 in the folding header 80 (see FIG. 19). That is, the top portion 85, the bottom portion 86, and the side portion 87 that form one folding space SP2 can be interpreted together as the folding space forming member 88. According to such an interpretation, it is also possible to interpret the folded header 80 as a member configured by a plurality of folded space forming members 88 forming the folded space SP2. In particular, it is also possible to interpret that the plurality of folded space forming members 88 are arranged along the vertical direction (in the installed state).
  • each folded space forming member 88 (corresponding to “third shunt” described in claims) has a folded space SP2 formed therein.
  • Each folding space forming member 88 includes a refrigerant gas side inlet / outlet (in this embodiment, a gas side collecting pipe 60) and each second header internal space SP1 (each second header internal space forming member). 78).
  • FIG. 20 is a perspective view of the flow divider 90.
  • FIG. 21 is an enlarged view of a portion A surrounded by a two-dot chain line in FIG.
  • the flow divider 90 is a member disposed in the liquid side inlet / outlet (that is, between the second header pipe 70 and the eighth pipe P8) in the outdoor heat exchanger 15.
  • the flow divider 90 allows the refrigerant flowing out from one of the second header pipe 70 and the eighth pipe P8 to flow into the other.
  • the flow divider 90 is a mechanism that diverts the refrigerant flowing out from the eighth pipe P8 and sends it to the plurality of second header internal spaces SP1 during the reverse cycle operation.
  • the flow divider 90 is also a mechanism that collects the refrigerant sent from each second header internal space SP1 and sends it to the eighth pipe P8 during the normal cycle operation.
  • the shunt 90 is mainly located between the second header pipe 70 and the eighth pipe P8 in the refrigerant circuit RC.
  • the flow divider 90 mainly includes an inlet / outlet pipe 91, a plurality of (here, 13) first thin tubes 93 extending to the second header tube 70, a second thin tube 94 extending to the first header tube 50, and a flow divider body 95. And have.
  • the inlet / outlet pipe 91, the first thin tube 93, the second thin tube 94, and the flow divider main body 95 are made of aluminum or an aluminum alloy.
  • the flow divider 90 is configured by brazing and joining the inlet / outlet pipe 91, the first thin tubes 93, the second thin tubes 94, and the flow divider main body 95 in a temporarily assembled state in the furnace with a brazing material.
  • FIG. 22 is an enlarged view schematically showing a cross section of the shunt main body 95 cut in the vertical direction.
  • FIG. 23 is a perspective view of the flow distributor main body 95 and the inlet / outlet pipe 91.
  • the entrance / exit pipe 91 (corresponding to the “first pipe” recited in the claims) is a cylindrical pipe with one end and the other end opened. One end of the inlet / outlet pipe 91 is connected to the flow divider main body 95, and the other end is connected to the eighth pipe P8.
  • the inlet / outlet pipe 91 is a pipe through which the refrigerant passing through the outdoor heat exchanger 15 enters and exits, and is a pipe that forms the liquid side inlet / outlet of the outdoor heat exchanger 15.
  • the inlet / outlet pipe 91 forms a flow path for allowing the refrigerant flowing out from one of the flow divider main body 95 and the eighth pipe P8 to flow into the other.
  • the inlet / outlet pipe 91 is located between the flow distributor main body 95 and the eighth pipe P8 in the refrigerant circuit RC.
  • the entrance / exit pipe 91 is curved from one end to the other end, and has a substantially J-shape or a substantially U-shape (see FIG. 23).
  • the first thin tube 93 (corresponding to the “second tube” in the claims) is a cylindrical pipe with one end and the other end opened.
  • the first narrow tube 93 has a smaller diameter than the entrance / exit tube 91.
  • One end of the first thin tube 93 is connected to the shunt main body 95.
  • the first thin tubes 93 have a one-to-one correspondence with any of the second header internal spaces SP1 (second header internal space forming member 78), and are arranged in the corresponding second header internal space SP1.
  • the other end is connected to the connection opening 73a.
  • the 1st thin tube 93 forms the flow path for making the refrigerant
  • the first thin tube 93 is located between the flow divider body 95 and the corresponding second header internal space SP1. That is, the first narrow tube 93 forms a refrigerant flow path on the windward side heat exchange unit 40a side than the inlet / outlet tube 91.
  • the second thin tube 94 is a cylindrical pipe whose one end and the other end are open.
  • the second thin tube 94 is smaller in diameter than the entrance / exit tube 91.
  • One end of the second thin tube 94 is connected to the shunt main body 95.
  • the other end of the second capillary 94 is connected to the second capillary connection opening 532 disposed in the first header subspace S2.
  • the 2nd thin tube 94 forms the flow path for making the refrigerant
  • the second thin tube 94 is located between the flow divider main body 95 and the first header subspace S2 in the refrigerant circuit RC.
  • FIG. 24 is a perspective view of the shunt main body 95.
  • FIG. 25 is a view of the shunt main body 95 as viewed from the top surface side.
  • FIG. 26 is a view of the shunt main body 95 as seen from the bottom surface side.
  • the shunt main body 95 (corresponding to the “main body” described in the claims) is a substantially cylindrical member having a main body internal space SP3 formed therein.
  • the main body internal space SP3 communicates with the inlet / outlet pipes 91 and one ends of the first thin tubes 93, and is a space through which the refrigerant flowing out of the inlet / outlet tubes 91 flows (divides) into the first thin tubes 93.
  • the main body internal space SP3 is also a space for collecting the refrigerant flowing out from each first thin tube 93 and flowing it into the inlet / outlet pipe 91.
  • the shunt main body 95 has a top surface 951 facing upward and a bottom surface 952 facing downward in the installed state.
  • the shunt main body 95 has a first opening 95 a for inserting the inlet / outlet pipe 91 on the top surface 951.
  • the first opening 95a is disposed at the central portion of the top surface 951.
  • the shunt main body 95 has a plurality of (here 14) second openings 95b for inserting the first narrow tubes 93 or the second thin tubes 94 on the bottom surface 952.
  • Each second opening 95b has a one-to-one correspondence with either the first capillary tube 93 or the second capillary tube 94, and the corresponding capillary tube is inserted.
  • the plurality of second openings 95b are annularly arranged at intervals on the bottom surface 952.
  • the first opening 95a and each second opening 95b individually communicate with the main body internal space SP3 (see FIG. 22).
  • FIG. 27 is an enlarged view showing the periphery of the shunt main body 95 viewed from the horizontal direction.
  • FIG. 28 is an enlarged view showing the state of FIG. 27 viewed from different directions.
  • the inlet / outlet pipe 91 extends upward from the top surface of the flow distributor main body 95 (see FIG. 27).
  • the inlet / outlet pipe 91 is connected to the flow divider main body 95 so as to extend upward from the main body internal space SP3 in the installed state (see FIG. 22).
  • each first thin tube 93 extends once downward from the bottom surface of the flow distributor main body 95 (see FIGS. 27 and 28).
  • each first thin tube 93 is connected to the flow divider main body 95 so as to extend downward from the main body internal space SP3 in the installed state.
  • each first thin tube 93 extends from the main body internal space SP3 along the downward direction, then curves, and extends along the upward direction toward the corresponding second header internal space SP1. More specifically, in the present embodiment, more than half (here, nine) first tubules 93 of the first tubules 93 extend downward from the main body internal space SP3 and then swell downward. It is an upper curved pipe 93a (see FIGS.
  • the upper bending tube 93a has at least two curved portions (a curved portion that folds upward from below and a curved portion that extends upward and curves toward the second header internal space SP1).
  • the upper curved pipes 93a are curved toward the center of the flow distributor main body 95 and extend along the upward direction while being adjacent to the inlet / outlet pipe 91 with a space therebetween (see FIG. 27, see FIG. 28). That is, the upper bending tube 93a further includes one bending portion (a bending portion that curves toward the center of the flow distributor main body 95).
  • the upper bending pipe 93a is arranged at intervals in the circumferential direction of the flow divider main body 95 and the inlet / outlet pipe 91 in a plan view in the installed state.
  • the flow divider main body 95 and the inlet / outlet pipe 91 extending upward from the top surface side are connected to the bottom surface side and curved to extend upward (the upper curved pipe 93a).
  • the flow divider main body 95 has an outer surface portion that is not surrounded by the first thin tube 93, and the outer surface portion is contacted with a jig used when moving into the furnace when the flow divider 90 is assembled. It functions as a contact portion 953 that comes into contact. That is, the flow divider main body 95 is moved into the furnace while being supported by a jig 100 as shown in FIG. 29, for example, with the inlet / outlet pipe 91, the plurality of first thin tubes 93, and the second thin tubes 94 inserted.
  • a part of the shunt main body 95 (that is, a part corresponding to the contact part 953) is not adjacent to the first thin tube 93. That is, the flow distributor main body 95 has a contact portion 953 that contacts the jig.
  • the refrigerant flowing out from each second header internal space SP1 flows into the corresponding first thin tube 93, passes through the first thin tube 93, and flows into the flow divider main body 95 (main body internal space SP3. ).
  • the refrigerant flowing into the main body internal space SP3 flows through the inlet / outlet pipe 91 and flows out to the eighth pipe P8.
  • the refrigerant flowing out from the eighth pipe P8 passes through the inlet / outlet pipe 91 and flows into the flow divider main body 95 (main body internal space SP3).
  • the refrigerant that has flowed into the main body internal space SP3 is divided, flows through the plurality of first thin tubes 93, and flows into any of the second header internal spaces SP1.
  • FIG. 30 is a schematic diagram showing the positional relationship of the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70, and the flow divider 90 in plan view. It is.
  • the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70 and the flow divider 90 are densely arranged near one end of the outdoor heat exchanger 15 as shown in FIG. 30.
  • the second header pipe 70 (second header internal space forming member 78) and the flow divider 90 are arranged close to each other in the vicinity of one end of the windward heat exchange unit 40a.
  • the straight line distance D1 in plan view of the second header pipe 70 (second header internal space forming member 78) and the flow divider 90 is appropriately set according to the design specifications and installation environment. From the viewpoint, it is set to 100 mm or less.
  • the outdoor heat exchanger 15 is configured by brazing and joining each part with a brazing material in a furnace.
  • the outdoor heat exchanger 15 is greatly curved at three locations in plan view, and bent portions B1, B2, and B3 are formed (see FIG. 8).
  • the brazing in the furnace is performed in a flat state before the bent portions B1, B2, and B3 are formed for the heat exchange unit 40.
  • the bending portions B1, B2, and B3 are configured using a predetermined roll jig and a pressing jig after brazing in the furnace.
  • Path configuration in the outdoor heat exchanger 15 In the outdoor heat exchanger 15 configured as described above, a plurality of paths are configured.
  • the “path” includes the first thin tube 93 of the flow divider 90, the second header internal space SP1 (second header internal space forming member 78), and the corresponding one or more heat transfer tubes 41 (41a and 41b).
  • the refrigerant passage is constituted by the folded space SP2.
  • FIG. 31 is a schematic diagram schematically showing each path of the outdoor heat exchanger 15 as viewed from the windward side.
  • FIG. 32 is a schematic diagram schematically showing each path of the outdoor heat exchanger 15 as viewed from the leeward side.
  • the outdoor heat exchanger 15 includes a first path RP1 to a thirteenth path RP13.
  • the first path RP1 is a path located at the top in the installed state. 31 and 32, the first path RP1 is a path located above the two-dot chain line L1.
  • the first path RP1 includes three windward side heat transfer tubes 41a and a leeward side heat transfer tube 41b.
  • the first path RP1 is a path including the second header internal space SP1 (ie, the uppermost upper second header internal space SA) located above the two-dot chain line L1.
  • the second path RP2 is the second path from the top in the installed state. 31 and 32, the second path RP2 is a path located between the two-dot chain line L1 and the two-dot chain line L2.
  • the second path RP2 includes four windward side heat transfer tubes 41a and a leeward side heat transfer tube 41b.
  • the second path RP2 is a path including a second header internal space SP1 (that is, the second upper header internal space SA that is second from the top) located between the two-dot chain line L1 and the two-dot chain line L2.
  • the third path RP3 is the third path from the top in the installed state. 31 and 32, the third path RP3 is a path located between the two-dot chain line L2 and the two-dot chain line L3.
  • the third path RP3 includes eight windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b.
  • the third path RP3 is a path including the second header internal space SP1 (that is, the third upper stage second header internal space SA from the top) located between the two-dot chain line L2 and the two-dot chain line L3.
  • the fourth path RP4 is the fourth path from the top in the installed state. 31 and 32, the fourth path RP4 is a path located between the two-dot chain line L3 and the two-dot chain line L4.
  • the fourth path RP4 includes nine upwind heat transfer tubes 41a and downwind heat transfer tubes 41b.
  • the fourth path RP4 is a path including the second header internal space SP1 (that is, the fourth upper second header internal space SA from the top) located between the two-dot chain line L3 and the two-dot chain line L4.
  • the fifth path RP5 is the fifth position from the top in the installed state. 31 and 32, the fifth path RP5 is a path located between the two-dot chain line L4 and the two-dot chain line L5.
  • the fifth path RP5 includes ten upwind heat transfer tubes 41a and downwind heat transfer tubes 41b.
  • the fifth path RP5 is a path including the second header internal space SP1 (that is, the uppermost middle second header internal space SB) located between the two-dot chain line L4 and the two-dot chain line L5.
  • the sixth path RP6 is the sixth path from the top in the installed state. 31 and 32, the sixth path RP6 is a path located between the two-dot chain line L5 and the two-dot chain line L6.
  • the sixth path RP6 includes eleven windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b.
  • the sixth path RP6 is a path including the second header internal space SP1 (that is, the second middle second header internal space SB from the top) located between the two-dot chain line L5 and the two-dot chain line L6.
  • the seventh path RP7 is the seventh path from the top in the installed state. 31 and 32, the seventh path RP7 is a path located between the two-dot chain line L6 and the two-dot chain line L7.
  • the seventh path RP7 includes twelve windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b.
  • the seventh path RP7 is a path including the second header internal space SP1 (that is, the third middle second header internal space SB from the top) located between the two-dot chain line L6 and the two-dot chain line L7.
  • the eighth path RP8 is the eighth path from the top in the installed state. 31 and 32, the eighth path RP8 is a path located between the two-dot chain line L7 and the two-dot chain line L8.
  • the eighth path RP8 includes twelve windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b.
  • the eighth path RP8 is a path including the second header internal space SP1 (that is, the fourth middle second header internal space SB from the top) located between the two-dot chain line L7 and the two-dot chain line L8.
  • the ninth path RP9 is the ninth path from the top in the installed state. 31 and 32, the ninth path RP9 is a path located between the two-dot chain line L8 and the two-dot chain line L9.
  • the ninth path RP9 includes seven upwind heat transfer tubes 41a and downwind heat transfer tubes 41b.
  • the ninth path RP9 is a path including the second header internal space SP1 (that is, the uppermost lower second header internal space SC) located between the two-dot chain line L8 and the two-dot chain line L9.
  • 10th path RP10 is the 10th path from the top in the installed state. 31 and 32, the tenth path RP10 is a path located between the two-dot chain line L9 and the two-dot chain line L10.
  • the tenth path RP10 includes six windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b.
  • the tenth path RP10 is a path including the second header internal space SP1 (that is, the second lower header internal space SC that is second from the top) located between the two-dot chain line L9 and the two-dot chain line L10.
  • the eleventh path RP11 is the eleventh path from the top in the installed state. 31 and 32, the eleventh path RP11 is a path located between the two-dot chain line L10 and the two-dot chain line L11.
  • the eleventh path RP11 includes six windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b.
  • the eleventh path RP11 is a path including the second header internal space SP1 (that is, the third lower header internal space SC third from the top) located between the two-dot chain line L10 and the two-dot chain line L11.
  • the 12th path RP12 is the 12th path from the top in the installed state. 31 and 32, the twelfth path RP12 is a path located between the two-dot chain line L11 and the two-dot chain line L12.
  • the twelfth path RP12 includes four upwind heat transfer tubes 41a and leeward heat transfer tubes 41b.
  • the twelfth path RP12 is a path including the second header internal space SP1 (that is, the fourth lower stage second header internal space SC from the top) located between the two-dot chain line L11 and the two-dot chain line L12.
  • the thirteenth path RP13 is the thirteenth (bottom) path from the top in the installed state. 31 and 32, the thirteenth path RP13 is a path located between the two-dot chain line L12 and the two-dot chain line L13.
  • the thirteenth path RP13 includes five windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b.
  • the thirteenth path RP13 is a path including the second header internal space SP1 (that is, the fifth and sixth lower second header internal spaces SC from the top) located between the two-dot chain line L12 and the one-dot chain line A1.
  • the thirteenth path RP13 is further divided into an upper thirteenth path RP13a and a lower thirteenth path RP13b.
  • the upper thirteenth path RP13a is located above the one-dot chain line A1 (FIGS. 31 and 32).
  • the upper thirteenth path RP13a is configured by a first narrow tube 93, a lowermost second header internal space SP1, three upwind heat transfer tubes 41a, a folding space SP2, and three leeward heat transfer tubes 41b.
  • the lower thirteenth path RP13b is located below the one-dot chain line A1 (FIGS. 31 and 32).
  • the lower thirteenth path RP13b includes the second narrow tube 94, the spaces (S1, S2) in the first header pipe 50, the two leeward heat transfer tubes 41b counted from the bottom, the folded space SP2, and the two counted from the bottom.
  • the windward side heat transfer tube 41a and the second header subspace SPa is located below the one-dot chain line A1 (FIGS. 31 and 32).
  • the thirteenth pass RP13 configured in this way has a longer flow path length than other passes.
  • Each path (RP1-RP13) configured in the above-described manner is branched in one of the first header main space S1 and the main body internal space SP3, and merged in the other.
  • each path is configured in parallel. That is, in principle, the refrigerant that has passed through one of the paths (RP1-RP13) flows out of the outdoor heat exchanger 15 without flowing into the other paths. From this point of view, the outdoor heat exchanger 15 is different from the heat exchanger in which the refrigerant that has passed through one of the paths returns to the other path.
  • the outdoor air flow AF passing through the heat exchanging unit 40 of the outdoor heat exchanger 15 is higher than the air passing through the lower part (especially the path below the center) (particularly from the center).
  • the wind speed is higher in the air passing through the upper path.
  • pass which passes through the lower part has the wind speed of the air flow which passes through it larger.
  • the wind speed of the stream is higher.
  • the air passing through the path (here, RP1-RP4) including the upper second header internal space SA is higher than the wind speed of the air flow passing through the path (here, RP5-RP8) including the middle second header internal space SB.
  • the wind speed of the stream is higher.
  • the refrigerant flows into the gas side collecting pipe 60 from the seventh pipe P7.
  • the refrigerant that has flowed into the gas side collecting pipe 60 flows into the first header main space S ⁇ b> 1 of the first header pipe 50 through the plurality of connecting pipes 61.
  • the refrigerant flowing into the first header main space S1 is divided and flows into the leeward heat transfer pipe 41b of each path (first path RP1 to thirteenth path RP13) and passes through the leeward heat exchange section 40b.
  • the refrigerant that has passed through the leeward heat exchange unit 40b reaches the turn-back header 80 (more specifically, the corresponding turn-back space SP2).
  • the refrigerant turns back in the turn-back space SP2 and flows into the corresponding upwind heat transfer tube 41a, and passes through the upwind heat exchange section 40a.
  • the refrigerant that has passed through the windward heat exchange unit 40a reaches the second header pipe 70 (more specifically, the corresponding second header internal space SP1).
  • the refrigerant flowing into the second header internal space SP1 flows into the flow divider 90 (main body internal space SP3) via the corresponding first narrow tube 93.
  • the refrigerant that has flowed into the main body internal space SP3 from the first thin tube 93 merges with the refrigerant that flows out from the other first thin tubes 93, passes through the inlet / outlet pipe 91, and flows out to the eighth pipe P8.
  • the leeward heat transfer pipe 41b (that is, the leeward side heat exchange) located at the lowest position of the first header main space S1.
  • the refrigerant that has flowed into the second leeward heat transfer tube 41b) from the bottom in the section 40b flows through the leeward heat exchange section 40b.
  • the refrigerant that has passed through the leeward heat exchange section 40b is folded back in the folding space SP2, flows into the second windward heat transfer pipe 41a from the bottom, and flows through the windward heat exchange section 40a.
  • the refrigerant that has passed through the windward heat exchange unit 40a is folded downward in the second header subspace SPa, flows into the lowermost windward heat transfer tube 41a, and flows through the windward heat exchange unit 40a again. Thereafter, the refrigerant that has passed through the windward side heat exchanging part 40a is folded back in the folding space SP2, flows into the lowermost leeward side heat transfer pipe 41b, and flows through the leeward side heat exchanging part 40b. Thereafter, the refrigerant that has passed through the leeward side heat exchange unit 40 b flows into the first header subspace S ⁇ b> 2 and then flows into the main body internal space SP ⁇ b> 3 of the flow divider main body 95 through the second thin tube 94.
  • the refrigerant flowing into the outdoor heat exchanger 15 during reverse cycle operation flows while exchanging heat with the outdoor air flow AF. Specifically, during reverse cycle operation, the refrigerant flows from the eighth pipe P8 into the inlet / outlet pipe 91. The refrigerant that has passed through the inlet / outlet pipe 91 reaches the flow divider 90 (main body internal space SP3), and is divided and flows into the plurality of first thin tubes 93 and the second thin tubes 94 (that is, flows into the respective paths).
  • the refrigerant that has flowed into the first thin tube 93 from the main body internal space SP3 reaches the second header tube 70 (more specifically, the corresponding second header internal space SP1).
  • the refrigerant that has flowed into the second header internal space SP1 flows into the corresponding upwind heat transfer tube 41a and passes through the upwind heat exchange section 40a.
  • the refrigerant that has passed through the windward heat exchange unit 40a reaches the turn-back header 80 (more specifically, the corresponding turn-back space SP2). Thereafter, the refrigerant turns back in the turn-back space SP2 and flows into the corresponding leeward heat transfer tube 41b and passes through the leeward heat exchange section 40b.
  • the refrigerant that has passed through the leeward heat exchange unit 40b reaches the first header pipe 50 (more specifically, the first header main space S1).
  • the refrigerant flowing into the first header main space S1 reaches the gas side collecting pipe 60 through the plurality of connecting pipes 61 and flows out of the outdoor heat exchanger 15.
  • the refrigerant flowing into the second thin tube 94 from the main body internal space SP3 (that is, the refrigerant flowing into the lower thirteenth path RP13b) reaches the first header subspace S2 of the first header pipe 50.
  • the refrigerant that has flowed into the first header subspace S2 flows into the lowermost leeward heat transfer tube 41b and passes through the leeward heat exchanger 40b.
  • the refrigerant that has passed through the leeward heat exchange unit 40b reaches the turn-back header 80 (more specifically, the corresponding turn-back space SP2). Thereafter, the refrigerant turns back in the turn-back space SP2, flows into the lowermost windward heat transfer tube 41a, and passes through the windward heat exchange section 40a.
  • the refrigerant that has passed through the windward heat exchange unit 40a is folded upward in the second header subspace SPa, flows into the second windward heat transfer pipe 41a from the bottom of the windward heat exchange unit 40a, and is again returned to the windward heat exchange unit 40a. Flowing. Thereafter, the refrigerant that has passed through the windward side heat exchanging part 40a is folded back in the folding space SP2, flows into the second leeward heat transfer pipe 41b from the bottom, and flows through the leeward side heat exchanging part 40b. Thereafter, the refrigerant that has passed through the leeward heat exchange section 40b flows into the first header main space S1, reaches the gas-side collecting pipe 60 through the connection pipe 61, and flows out of the outdoor heat exchanger 15.
  • Performance improvement promotion function (A) In the flow divider main body 95, the height (the height of the exit surface of the first thin tube 93) h2 (see FIG. 27) of the communication portion with the first thin tube 93 in the main body internal space SP3 is a reference of the head.
  • the head difference becomes larger than the pressure of the refrigerant flowing through the heat transfer tube 41, the refrigerant flow is hindered.
  • the circulation amount of the refrigerant is reduced due to the influence of the head, and the refrigerant tends to stay.
  • a flat tube is used as the heat transfer tube 41.
  • the outdoor heat exchanger 15 performs so-called header diversion in which the refrigerant is diverted to each path using the header (more specifically, the plurality of second header internal spaces SP1 in the second header pipe 70). It is configured.
  • a plurality of heat transfer tubes 41 are included in each path (RP1-RP10), and a flow is divided to each heat transfer tube 41 in the second header internal space SP1.
  • a loop-like refrigerant flow is formed in the second header internal space SP ⁇ b> 1 with respect to the diversion to each heat transfer tube 41.
  • drift may occur with respect to the refrigerant flowing into each heat transfer tube 41 in the second header internal space SP1 in relation to the head difference. That is, among the heat transfer tubes 41 connected to one second header internal space SP1, the liquid refrigerant is more likely to flow in the lower heat transfer tube 41, and the gas refrigerant is more likely to flow in the upper heat transfer tube 41. That is, a pressure loss difference is likely to occur with respect to the plurality of heat transfer tubes 41 positioned above and below in one path. In this connection, particularly during the cooling cycle defrost operation, the refrigerant is likely to stay in the lower heat transfer tube 41 that is susceptible to the influence of the liquid head in each pass, and hot melt is not supplied, so that undissolved components are likely to be generated.
  • the number of passes and the number of heat transfer tubes are in a one-to-one relationship, and when functioning as a condenser, the refrigerant that flows through the heat transfer tubes of the lowermost pass If the pressure difference over the liquid head of the flow divider is ensured, the refrigerant is suppressed from staying.
  • the circulation amount is different for each path, and the circulation amount is most likely to be affected by the liquid head when functioning as a condenser. It is necessary to configure the refrigerant flowing through the lowermost heat transfer tube 41 so as to ensure a pressure difference over the liquid head.
  • the height position of the shunt main body 95 in the installed state is lower than the conventional one.
  • the height position of the flow divider main body 95 is suppressed so that the height h1 (see FIG. 27) of the bottom surface 952 from the top surface of the bottom frame 33 is 43 mm (within 100 mm).
  • the outdoor heat exchanger 15 it is possible to reduce the head difference caused by the installation height of the flow divider main body 95 when used as a condenser.
  • liquid refrigerant is prevented from staying and defrosting is promoted. For this reason, the unmelted frost is suppressed and excellent in reliability.
  • three heat transfer tubes 41 communicate with the upper second header internal space SA of the first path RP1.
  • Four heat transfer tubes 41 communicate with the upper second header internal space SA of the second path RP2.
  • Eight heat transfer tubes 41 communicate with the upper second header internal space SA of the third path RP3.
  • Nine heat transfer tubes 41 communicate with the upper second header internal space SA of the fourth path RP4.
  • ten heat transfer tubes 41 communicate with the middle second header internal space SB of the fifth path RP5. Eleven heat transfer tubes 41 communicate with the middle second header internal space SB of the sixth path RP6. Twelve heat transfer tubes 41 communicate with the middle second header internal space SB of the seventh path RP7. Twelve heat transfer tubes 41 communicate with the middle second header internal space SB of the eighth path RP8.
  • heat transfer tubes 41 communicate with the lower second header internal space SC of the ninth path RP9.
  • Six heat transfer tubes 41 communicate with the lower second header internal space SC of the tenth path RP10.
  • Six heat transfer tubes 41 communicate with the lower second header internal space SC of the eleventh path RP11.
  • Four heat transfer tubes 41 communicate with the lower second header internal space SC of the twelfth path RP12.
  • Three heat transfer tubes 41 communicate with the lower second header internal space SC of the thirteenth path RP13 (upper thirteenth path RP13a).
  • the number of heat transfer tubes 41 communicating with the lower second header internal space SC is seven or less.
  • the number of heat transfer tubes 41 communicating with one lower second space rather than the number of heat transfer tubes 41 communicating with one middle second header internal space SB. Is less.
  • reduction of the head of the liquid refrigerant in the flow divider main body 95 (main body internal space SP3) when used as a condenser is promoted.
  • the heat transfer pipe 41 communicating with the lower second header internal space SC in which liquid refrigerant tends to accumulate that is, the ninth path RP9 to the thirteenth path RP13 disposed in the lower part).
  • the refrigerant easily flows well, and the performance improvement is promoted.
  • liquid refrigerant is prevented from staying and defrosting is promoted. For this reason, the unmelted frost is suppressed and excellent in reliability.
  • the diverter main body 95 includes a large number (in this case, ten or more) of the inlet / outlet pipes 91 extending from the main body internal space SP3 along the upward direction.
  • the first thin tube 93 is installed so as to extend downward from the main body internal space SP3.
  • the soldering main body 95 and the first thin tube 93 are brazed and joined manually, the workability is remarkably lowered and the assemblability is improved. It is assumed that it is not excellent.
  • the flow divider main body 95 and the plurality of first thin tubes 93 are made of aluminum or an aluminum alloy, the flow divider 90 can be configured by joining them together by brazing in the furnace. It has become. In this connection, the improvement in assemblability is promoted.
  • each first capillary tube 93 extends from the main body internal space SP3 along the downward direction, then curves, and extends along the upward direction toward the corresponding second header internal space SP1. . More specifically, in the present embodiment, more than half (here, nine) first tubules 93 of the first tubules 93 extend downward from the main body internal space SP3 and then swell downward. It is an upper curved pipe 93a (see FIGS. 27 and 28) that curves and changes the extending direction upward, and extends along the upward direction while adjoining the flow distributor body 95 with a space therebetween.
  • Most of the upper curved pipes 93a are curved toward the center of the flow distributor main body 95 and extend along the upward direction while being adjacent to the inlet / outlet pipe 91 with a space therebetween (see FIG. 27, see FIG. 28). That is, more than half of the first thin tubes 93 are arranged in the circumferential direction of the flow distributor main body 95 and the inlet / outlet tube 91 in plan view in the installed state.
  • the flow divider main body 95 and the inlet / outlet pipe 91 extending upward from the top surface side are connected to the bottom surface side and curved to extend upward (the upper curved pipe 93a).
  • the flow divider 90 is configured in such a manner, the distance between the flow divider main body 95 and the first thin tube 93, the distance between the inlet / outlet tube 91 and each first thin tube 93, and / or the distance between each first thin tube 93 is reduced. It is possible to do. That is, it is possible to arrange the respective parts close to each other while ensuring the clearance. This promotes the compactness of the current divider 90 that is assumed to be arranged in a narrow space. As a result, downsizing of the outdoor heat exchanger 15 is promoted.
  • a heat exchange unit including a plurality of flat tubes in which flat tubes are arranged in the vertical direction in an installed state, a flow distributor disposed at a liquid side end, and a header disposed between the heat exchange unit and the flow distributor Heat exchangers having tubes are known.
  • a plurality of spaces are formed in the header pipe so as to be aligned along the direction in which the flat tubes are stacked, and the corresponding flat tubes communicate with each space.
  • Each space in the header and the flow divider are connected by a thin tube, and a plurality of paths (refrigerant flow paths) are formed.
  • liquid refrigerant tends to stay in a flat tube (pass) arranged near the lowermost stage in relation to the head difference caused by the installation height of the flow divider.
  • the outdoor heat exchanger 15 in the installed state, three or more second header internal spaces SP1 are arranged along the vertical direction, and the middle second header internal space SB (second header internal space located in the center) is arranged.
  • the number of heat transfer tubes 41 communicating with the lower second header internal space SC (second header internal space SP1 positioned below the middle second header internal space SB) is more than the number of heat transfer tubes 41 communicating with SP1). Few. Thereby, reduction of the head of the liquid refrigerant in the flow divider main body 95 (main body internal space SP3) when used as a condenser is promoted.
  • the heat transfer pipe 41 communicating with the lower second header internal space SC in which liquid refrigerant tends to accumulate that is, the ninth path RP9 to the thirteenth path RP13 disposed in the lower part.
  • the refrigerant easily flows well, and the performance improvement is promoted.
  • liquid refrigerant is prevented from staying and defrosting is promoted. For this reason, the unmelted frost is suppressed and excellent in reliability.
  • the folded space forming member 88 (third branching portion) forms a refrigerant flow path between the second header internal space forming member 78 and the gas side collecting pipe 60,
  • the folding space SP2 (third space) is formed inside.
  • the folded space SP2 communicates with the other end of the corresponding heat transfer tube (one of the windward side heat transfer tube 41a and the leeward side heat transfer tube 41b), and the second heat transfer tube (windward side) disposed on the same stage as the heat transfer tube 41.
  • the other end of the heat transfer tube 41a and the leeward side heat transfer tube 41b) communicates with one end.
  • each path (RP1-RP13) is configured in parallel. That is, in principle, the refrigerant that has passed through one of the paths (RP1-RP13) flows out of the outdoor heat exchanger 15 without flowing into the other paths.
  • the lower second header internal space SC is higher than the wind speed of the outdoor air flow AF that passes around the heat transfer pipe 41 communicating with the lower second header internal space SC.
  • the wind speed of the outdoor air flow AF passing through the periphery of the heat transfer tube 41 communicating with the second header internal space SP1 above is higher. That is, the performance improvement is promoted with respect to the outdoor heat exchanger 15 disposed in the outdoor unit 10 in which the outdoor air flow AF is sucked from the side and blown upward.
  • the lower second header internal space SC is disposed at a height position equal to or less than one-third of the overall height of the heat exchange unit 40 in the installed state.
  • the heat transfer tube 41 communicating with the second header internal space SC that is, the heat transfer tube 41 in which liquid refrigerant tends to accumulate particularly when used as a condenser
  • the refrigerant is likely to flow well, and the performance improvement is promoted. ing.
  • the heat transfer tube 41 located at the lowermost stage in the installed state communicates with the lower second header internal space SC, and is used when the heat transfer pipe 41 (that is, used as a condenser).
  • the heat transfer tube 41 in which the liquid refrigerant tends to accumulate, the refrigerant easily flows well, and the performance improvement is promoted.
  • one end of the inlet / outlet pipe 91 is connected to the flow divider main body 95 so as to extend upward from the main body internal space SP3 in the installed state.
  • One end of the first thin tube 93 is connected to the flow divider main body 95 so as to extend downward from the main body internal space SP3 in the installed state.
  • the height position of the current divider main body 95 of the current divider 90 in the installed state can be lowered.
  • the heat transfer tubes 41 are installed so as to be lined up in the vertical direction, it is possible to reduce the head difference caused by the installation height of the flow divider when used as a condenser. Therefore, when used as a condenser, it is particularly suppressed that the liquid refrigerant stays in the heat transfer tube 41 (pass) disposed near the lowermost stage where the liquid refrigerant easily stays. Therefore, the performance improvement is particularly promoted, and particularly a decrease in reliability during the normal cycle operation (cooling operation or cooling cycle defrosting operation) is particularly suppressed.
  • a plurality of second openings 95b to which one end of the first thin tube 93 is connected are formed on the bottom surface 952 facing downward in the installed state.
  • the flow divider 90 is preferably configured in such a manner.
  • the configuration of the flow divider 90 is not necessarily limited thereto, and may be appropriately selected as long as the first thin tube 93 is connected to the flow divider main body 95 so as to extend downward from the main body internal space SP3 in the installed state. It can be changed.
  • some or all of the plurality of second openings 95b may be formed on a side surface facing the side in the installed state.
  • the first opening 95a to which one end of the inlet / outlet pipe 91 is connected is formed on the top surface 951 facing upward in the installed state.
  • the flow divider 90 is preferably configured in this manner.
  • the configuration of the flow divider 90 is not necessarily limited to this, and can be changed as long as the inlet / outlet pipe 91 is connected to the flow divider main body 95 so as to extend upward from the main body internal space SP3 in the installed state. Is possible.
  • the first opening 95a may be formed on the side surface facing the side in the installed state.
  • a first opening 95a to which one end of the inlet / outlet pipe 91 is connected may be formed on the bottom surface 952 facing downward in the installed state.
  • a first opening 95a to which one end of the first thin tube 93 is connected may be formed on the top surface 951 facing upward in the installed state.
  • one end is connected to the flow divider main body 95 so that the inlet / outlet pipe 91 extends downward from the main body internal space SP3 in the installed state, and a plurality of first narrow tubes 93 are connected from the main body internal space SP3 in the installed state.
  • One end is connected to the shunt main body 95 so as to extend along the upward direction, but the effects described in “10-1” can be realized in the same manner as in the above embodiment.
  • each first capillary 93 may correspond to one of the second header internal spaces SP1 in one-to-many, many-to-one, or many-to-many.
  • the number of the first thin tubes 93 included in the flow divider 90 is not necessarily limited to that in the above-described embodiment, and can be appropriately changed according to the design specifications and the installation environment. That is, the flow divider 90 may have eleven or more first tubules 93 or may have less than ten first tubules 93.
  • the second header internal space forming member 78 includes the upwind heat transfer tube connection opening 711 connected to one end of the corresponding heat transfer tube 41 and the corresponding first thin tube 93.
  • the first capillary connection opening 73a connected to the end is formed, and in the installed state, the height position of the first capillary connection opening 73a is the height of the windward heat transfer tube connection opening 711 located at the lowermost position. It was below the position.
  • the outdoor heat exchanger 15 is preferably configured in such a manner from the viewpoint of suppressing liquid refrigerant from staying in each pass when used as a condenser.
  • the height position of the first thin tube connection opening 73a is not necessarily equal to or lower than the height position of the windward heat transfer tube connection opening 711 located at the lowermost position.
  • the height h2 of the communication portion with the first thin tube 93 in the main body internal space SP3 is located at the lowest position with respect to the height position of the flow divider main body 95 in the installed state. You may set so that it may be located below the height position of the upper end of 2nd header internal space SP1. This further suppresses the liquid refrigerant from staying in each pass when used as a condenser.
  • the second header internal space forming member 78 (the “second shunt portion” described in the claims) that forms the second header internal space SP1 can be interpreted as a single unit.
  • the second header pipe 70 is disposed between the heat exchange unit 40 and the flow divider 90.
  • a member that forms a space corresponding to the second header internal space SP ⁇ b> 1 (that is, a member corresponding to the second header internal space forming member 78) is disposed other than the second header pipe 70. May be.
  • one or more members that form at least one space corresponding to the second header internal space SP1 between the heat exchanging unit 40 and the flow divider 90 / You may arrange
  • the member corresponds to a “second shunt” described in the claims.
  • a diversion mechanism for diverting the refrigerant to any / all of the plurality of paths (RP1-RP13) between the heat exchanging unit 40 and the diverter 90 is replaced with the second header pipe 70 / second header. It may be arranged with the tube 70.
  • (11-7) Modification 7 In the above embodiment, ten paths are formed in the outdoor heat exchanger 15. However, the number of paths formed in the outdoor heat exchanger 15 can be appropriately changed according to design specifications and installation environment. For example, in the outdoor heat exchanger 15, 11 or more paths may be formed, or less than 10 paths may be formed. Further, the number of second header internal spaces SP1 formed in the second header pipe 70 and the number of first thin tubes 93 may be appropriately changed according to the number of paths.
  • the path formation mode in the above embodiment can be appropriately changed.
  • the number of heat transfer tubes 41 included in each path can be appropriately changed as long as it does not contradict the idea described in (10-1) above.
  • the number of the upper second header internal space SA, the number of the middle second header internal space SB, and the number of the lower second header internal space SC formed in the outdoor heat exchanger 15 are appropriately changed. Is possible.
  • the number of the upper second header internal spaces SA in the outdoor heat exchanger 15 is not limited to 4, and may be 1 or more and 3 or less, or 5 or more.
  • the number of middle second header internal spaces SB in the outdoor heat exchanger 15 is not limited to 4, and may be 1 or more and 3 or less, or 5 or more.
  • the number of the lower second header internal spaces SC in the outdoor heat exchanger 15 is not limited to 5, and may be 1 or more and 4 or less, or 6 or more.
  • the thirteenth path RP13 is formed to include the upper thirteenth path RP13a and the lower thirteenth path RP13b.
  • the thirteenth path RP13 is not necessarily formed in this manner, and the lower thirteenth path RP13b in the thirteenth path RP13 may be omitted.
  • the first header subspace S2, the second header subspace SPa, the second capillary 94, and the like may be omitted.
  • the arrangement positions of the windward side heat exchange unit 40a and the leeward side heat exchange unit 40b may be switched. That is, the leeward heat exchange unit 40a may be arranged on the leeward side (or inside), and the leeward side heat exchange unit 40b may be arranged on the leeward side (or outside).
  • the gas side collecting pipe 60 in the above embodiment may be omitted as appropriate.
  • the seventh pipe P ⁇ b> 7 may be connected to the first header pipe 50.
  • the first header pipe 50 corresponds to a “third pipe” recited in the claims.
  • the outdoor heat exchanger 15 had the two heat exchange parts 40 (the windward side heat exchange part 40a and the leeward side heat exchange part 40b).
  • the configuration aspect of the outdoor heat exchanger 15 is not necessarily limited to such an aspect, and can be changed as appropriate.
  • the outdoor heat exchanger 15 may have three or more heat exchange units 40.
  • the heat exchange units 40 may be arranged along the flow direction of the outdoor air flow AF, or may be arranged in another manner.
  • the outdoor heat exchanger 15 may be configured to have only a single heat exchange unit 40.
  • the folded header 80 may be omitted, and the first header pipe 50 may be connected to the end of the windward heat transfer pipe 41a.
  • the space in the first header pipe 50 may be partitioned for each path (in this case, each partitioned space corresponds to a “third space” recited in the claims, and the first Each portion forming each space of the header pipe 50 corresponds to a “third branch portion”).
  • the outdoor heat exchanger 15 was comprised so that substantially U shape or substantially C shape might be exhibited in planar view. That is, the outdoor heat exchanger 15 is configured such that the heat exchanging unit 40 has three surfaces that intersect mainly the flow direction of the outdoor air flow AF.
  • the configuration aspect of the outdoor heat exchanger 15 is not necessarily limited to such an aspect, and can be changed as appropriate.
  • the outdoor heat exchanger 15 may be configured to have a substantially L shape or a substantially V shape in plan view. That is, the outdoor heat exchanger 15 may be configured such that the heat exchanging unit 40 has two surfaces that intersect the flow direction of the outdoor air flow AF.
  • the outdoor heat exchanger 15 may be configured to have a substantially I shape in plan view. That is, the outdoor heat exchanger 15 may be configured such that the heat exchange unit 40 has a single surface that intersects the flow direction of the outdoor air flow AF.
  • the outdoor heat exchanger 15 may be configured such that the heat exchanging unit 40 has four or more surfaces that intersect the flow direction of the outdoor air flow AF.
  • the heat transfer tube 41 is formed with a plurality of flow paths 411.
  • the present invention is not necessarily limited thereto, and a flat tube in which a single flow path 411 is formed may be used as the heat transfer tube 41.
  • the heat exchanging unit 40 includes 97 heat transfer tubes 41.
  • the number of the heat transfer tubes 41 included in the heat exchange unit 40 can be changed as appropriate, and may be 98 or more or less than 97.
  • the outdoor heat exchanger 15 is configured such that, in the installed state, the linear distance D1 in plan view between the flow divider 90 and the second header internal space forming member 78 is 100 mm or less. From the viewpoint of improving compactness, it is preferable to set D1 to a small value. However, the present invention is not necessarily limited to this, and the value of the linear distance D1 in plan view between the flow divider 90 and the second header internal space forming member 78 can be changed as appropriate.
  • the plurality of second openings 95b are annularly arranged at intervals.
  • the plurality of second openings 95b are preferably arranged in this manner.
  • the arrangement of the second openings 95b is not necessarily limited to this, and can be changed as appropriate.
  • the upper curved pipe 93a extends along the upward direction adjacent to the flow distributor body 95 in the installed state, and then curves again and extends toward the inlet / outlet pipe 91. Further, it is curved and extends along the upward direction adjacent to the inlet / outlet pipe 91.
  • the configuration of the upper bending tube 93a is not necessarily limited to that in the above-described embodiment, and can be appropriately changed according to design specifications and installation environment.
  • the plurality of upper curved tubes 93a are arranged at intervals in the circumferential direction of the inlet / outlet tube 91 in a plan view in the installed state. From the viewpoint of making the shunt 90 compact, it is preferable that the plurality of upper curved tubes 93a are arranged in such a manner.
  • the configuration of the upper bending tube 93a is not necessarily limited to that in the above embodiment, and can be appropriately changed according to the design specifications and the installation environment.
  • each part of the outdoor heat exchanger 15 in the above embodiment is not necessarily limited to the mode in the above embodiment, and the concept described in (10-1) above. As long as there is no contradiction, it can be appropriately changed according to the design specifications.
  • the outdoor heat exchanger 15 was applied in the outdoor unit 10 into which an airflow flows in from a side and flows out upwards.
  • the outdoor heat exchanger 15 may be applied to other units.
  • the outdoor heat exchanger 15 may be applied to the trunk-type outdoor unit 10 in which an air flow flows in from the side and flows out to the front side.
  • the outdoor heat exchanger 15 may be applied as the indoor heat exchanger 22 in the indoor unit 20.
  • the present disclosure can be used for a heat exchanger or an air-conditioning indoor unit having a heat exchanger.
  • Air conditioning system (refrigeration equipment) 10: Outdoor unit 12: Compressor 15: Outdoor heat exchanger (heat exchanger) 18: Outdoor fan 20: Indoor unit 30: Outdoor unit casing 40: Heat exchange section 40a: Upwind heat exchange section 40b: Downwind heat exchange section 41: Heat transfer tube (flat tube) 41a: windward side heat transfer tube 41b: leeward side heat transfer tube 42: heat transfer fin 50: first header tube 51: leeward heat transfer tube side member 52: first header partition member 53: collecting tube side member 54: first partition plate 55 : Second partition plate 60: Gas side collecting pipe (third pipe) 61: connecting pipe 62: binding band 70: second header pipe 71: upwind heat transfer pipe side member 72: second header partition member 72a: first communication opening 72b: second communication opening 73: flow divider side member 73a: first 1 narrow tube connection openings 74, 74a: partition plate 75: rectifying plate 75a: third communication opening 78: second header internal space forming member (second diversion portion) 80: Folding header 81

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
PCT/JP2018/047589 2018-01-31 2018-12-25 熱交換器又は熱交換器を有する冷凍装置 Ceased WO2019150852A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
ES18903461T ES2896693T3 (es) 2018-01-31 2018-12-25 Intercambiador de calor y dispositivo de refrigeración que tiene un intercambiador de calor
US16/966,767 US20230106747A1 (en) 2018-01-31 2018-12-25 Heat exchanger or refrigeration apparatus including heat exchanger
CN201880088246.5A CN111656125A (zh) 2018-01-31 2018-12-25 热交换器或具有热交换器的冷冻装置
EP18903461.4A EP3748275B1 (en) 2018-01-31 2018-12-25 Heat exchanger and refrigerant device having heat exchanger

Applications Claiming Priority (2)

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JP2018015306A JP6985603B2 (ja) 2018-01-31 2018-01-31 熱交換器又は熱交換器を有する冷凍装置
JP2018-015306 2018-01-31

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US (1) US20230106747A1 (zh)
EP (1) EP3748275B1 (zh)
JP (1) JP6985603B2 (zh)
CN (1) CN111656125A (zh)
ES (1) ES2896693T3 (zh)
WO (1) WO2019150852A1 (zh)

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JP2021188795A (ja) * 2020-05-27 2021-12-13 パナソニックＩｐマネジメント株式会社 熱交換器
JP7566155B2 (ja) 2021-07-09 2024-10-11 三菱電機株式会社 熱交換器及び空気調和装置
JP7185170B1 (ja) * 2021-09-30 2022-12-07 ダイキン工業株式会社 分流装置及び空気調和機

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JP2019132537A (ja) 2019-08-08
ES2896693T3 (es) 2022-02-25
US20230106747A1 (en) 2023-04-06
EP3748275B1 (en) 2021-09-15
EP3748275A4 (en) 2021-01-20
CN111656125A (zh) 2020-09-11
JP6985603B2 (ja) 2021-12-22
EP3748275A1 (en) 2020-12-09

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