[go: up one dir, main page]

WO2018154972A1 - Unité d'échange de chaleur - Google Patents

Unité d'échange de chaleur Download PDF

Info

Publication number
WO2018154972A1
WO2018154972A1 PCT/JP2017/047238 JP2017047238W WO2018154972A1 WO 2018154972 A1 WO2018154972 A1 WO 2018154972A1 JP 2017047238 W JP2017047238 W JP 2017047238W WO 2018154972 A1 WO2018154972 A1 WO 2018154972A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
heat exchanger
flat tubes
heat
refrigerant
Prior art date
Application number
PCT/JP2017/047238
Other languages
English (en)
Japanese (ja)
Inventor
佐藤　健
正憲 神藤
好男 織谷
甲樹 山田
智嗣 井上
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to US16/487,865 priority Critical patent/US20200232709A1/en
Priority to CN201780086714.0A priority patent/CN110300876A/zh
Priority to EP17897780.7A priority patent/EP3587979A1/fr
Publication of WO2018154972A1 publication Critical patent/WO2018154972A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F28D1/024—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels with an air driving element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to a heat exchange unit, in particular, a casing in which a suction port is formed on a side surface and a blower outlet on a top surface, a blower disposed facing the blower port, and a heat exchange disposed on a lower side of the blower. And a heat exchanging unit.
  • a heat exchanger having a plurality of flat tubes arranged vertically may be employed as an outdoor heat exchanger accommodated in an outdoor unit of an air conditioner.
  • a heat exchanger having a plurality of flat tubes arranged vertically
  • a plurality of sub heat exchange units arranged together below the plurality of main heat exchange units, and the main heat exchange unit and the sub heat exchange unit are connected via a communication pipe
  • a plurality of heat exchange portions are formed.
  • a casing having a suction port on the side and a blower outlet on the top surface, a blower arranged facing the blower outlet, and heat exchange arranged on the lower side of the blower
  • a heat exchanging unit top-blow-type heat exchanging unit
  • the heat exchanger is located below the blower, so the air velocity through the heat exchanger is higher in the upper part of the heat exchanger than in the lower part of the heat exchanger. Tend to be faster.
  • the heat exchanger shown in Patent Document 1 when functioning as a refrigerant evaporator, the refrigerant flowing through the flat tube located at the top of the heat exchanger is: Since heat exchange is easier to proceed than the refrigerant flowing through the flat tubes located at the bottom of the heat exchanger, the degree of heat exchange varies between the flat tubes, and as a result, heat exchange between the heat exchange units also occurs. The bias will occur to the extent.
  • An object of the present invention is to provide a casing having a suction port on the side and a blower outlet on the top surface, a blower disposed facing the blower outlet, and a heat exchanger disposed on the lower side of the blower.
  • An object of the present invention is to improve the diversion performance when the heat exchanger functions as a refrigerant evaporator.
  • the heat exchange unit has a casing, a blower, and a heat exchanger.
  • the casing is formed with a suction port on the side surface and an air outlet on the top surface.
  • the blower is disposed in the casing so as to face the air outlet, and takes air into the casing from the air inlet and discharges it from the air outlet.
  • the heat exchanger is disposed below the blower in the casing and performs heat exchange between the refrigerant and the air.
  • the heat exchanger has a plurality of header collecting pipes standing upright, a plurality of flat pipes each having one end connected to the header collecting pipe, and a plurality of ventilation paths through which air flows between adjacent flat pipes. And fins.
  • the flat tubes are arranged vertically and have a refrigerant passage formed therein.
  • the plurality of flat tubes are divided into a plurality of heat exchanging portions arranged vertically.
  • the header collecting pipe is partitioned into upper and lower interiors to form folded communication spaces corresponding to the respective heat exchange portions.
  • Each heat exchanging part has a main heat exchanging part and a sub heat exchanging part connected in series through the folded communication space below the main heat exchanging part. And here, according to the wind speed distribution of the air in the heat exchanger, the number of flat tubes constituting the heat exchange part located at the upper part of the heat exchanger constitutes the heat exchange part located at the lower part of the heat exchanger It is set to be smaller than the number of flat tubes.
  • the heat exchanger constituting the top-blow-type heat exchange unit
  • the sub heat connected in series through the folded communication space of the header collecting pipe below the main heat exchange part and the main heat exchange part.
  • a configuration is adopted in which the heat exchanging section composed of the exchanging section is arranged vertically.
  • the arrangement of the heat exchanging portions is along the wind speed distribution in the heat exchanger, and the communication pipe connecting the main heat exchanging portion and the sub heat exchanging portion. Can also be eliminated.
  • the number of flat tubes constituting the heat exchanging part located in the upper part is set to be smaller than the number of flat tubes constituting the heat exchanging part located in the lower part of the heat exchanger. For this reason, the heat transfer area of the heat exchange part located in the upper part of the heat exchanger is smaller than the heat transfer area of the heat exchange part located in the lower part of the heat exchanger, and the heat exchange part located in the upper part of the heat exchanger. And the degree of heat exchange between the heat exchanger and the heat exchanger located below the heat exchanger can be eliminated.
  • the refrigerant can be appropriately diverted to the respective heat exchanging portions, and the diversion when the heat exchanger functions as the refrigerant evaporator. Performance can be improved.
  • the heat exchange unit according to the second aspect is the heat exchange unit according to the first aspect, wherein the number of flat tubes constituting the main heat exchange part of the heat exchange part located above the heat exchanger is the heat exchanger.
  • the number of flat tubes constituting the main heat exchanging part of the heat exchanging part located in the lower part of the tube is smaller.
  • the degree of heat exchange in each heat exchange unit is greatly influenced by the size of the heat transfer area of the main heat exchange unit through which a large amount of gaseous refrigerant flows when functioning as a refrigerant evaporator.
  • the flat tube constituting the heat exchange portion located at the top of the heat exchanger is changed.
  • the number is set so as to be smaller than the number of flat tubes constituting the heat exchanging part located in the lower part of the heat exchanger.
  • the heat exchange unit according to the third aspect is the heat exchange unit according to the first or second aspect, wherein the number of flat tubes constituting the heat exchange unit located at the top of the heat exchanger is the heat exchanger. It is 0.6 to 0.9 times the value obtained by dividing the total number of the flat tubes constituting by the number of heat exchange parts.
  • the heat transfer area of the heat exchange part located at the top of the heat exchanger is The average heat transfer area of the part is preferably about 0.6 to 0.9 times.
  • the number of flat tubes constituting the uppermost heat exchanging portion is determined by the average number of flat tubes constituting each heat exchanging portion (that is, the total number of flat tubes constituting the heat exchanger). Is divided by the number of heat exchanging parts) to 0.6 to 0.9 times.
  • the heat exchanger is used as a refrigerant evaporator by setting the number of flat tubes constituting the uppermost heat exchange section to an appropriate number in consideration of the air velocity distribution in the heat exchanger.
  • the shunt performance when functioning can be improved.
  • a heat exchange unit according to a fourth aspect is the heat exchange unit according to any one of the first to third aspects, wherein the main heat exchange unit for the number of flat tubes constituting the sub heat exchange unit in each heat exchange unit is provided.
  • the ratio of the number of the flat tubes constituting is 1.5 to 4.5.
  • the heat exchanger functions as a refrigerant evaporator
  • the refrigerant that has flowed back from the sub heat exchanging part into the communicating space is divided and sent to the flat tubes constituting the main heat exchanging part.
  • the number of flat tubes constituting the main heat exchange section is sub-heat exchange from the viewpoint of reducing pressure loss and securing a heat transfer area.
  • the number is preferably larger than the number of flat tubes constituting the portion.
  • the ratio of the number of flat tubes constituting the main heat exchange portion to the number of flat tubes constituting the sub heat exchange portion is within a certain range.
  • the ratio of the number of flat tubes constituting the main heat exchange unit to the number of flat tubes constituting the sub heat exchange unit in each heat exchange unit is 1.5 to 4.5. Within the range.
  • the ratio of the number of flat tubes constituting the main heat exchange portion to the number of flat tubes constituting the sub heat exchange portion in each heat exchange portion is calculated from the flat communication space constituting the main heat exchange portion from the folded communication space.
  • a heat exchange unit is the heat exchange unit according to any one of the first to fourth aspects, wherein a position corresponding to a boundary part between the main heat exchange part and the sub heat exchange part among the plurality of fins. Further, a fin cutting portion that suppresses heat conduction in the vertical direction at the boundary portion is formed.
  • heat exchanger when adopting a configuration in which the heat exchange part composed of the sub heat exchange part connected in series through the folded communication space of the header collecting pipe below the main heat exchange part and the main heat exchange part is arranged vertically, Heat conduction through the fins occurs between the main heat exchange unit and the adjacent sub heat exchange unit.
  • the heat exchanger functions as a refrigerant evaporator
  • the main heat exchanging part is cooled by the adjacent sub heat exchanging part, and the refrigerant flowing through the main heat exchanging part is heated. May become insufficient, and the evaporation performance of the heat exchanger may be reduced.
  • the heat exchanger functions as a refrigerant radiator
  • the sub heat exchange part is heated by the adjacent main heat exchange part, and cooling of the refrigerant flowing through the sub heat exchange part becomes insufficient. As a result, the heat dissipation performance of the heat exchanger may be reduced.
  • a fin cutting portion that suppresses heat conduction in the vertical direction at the boundary portion is formed at a position corresponding to the boundary portion between the main heat exchange portion and the sub heat exchange portion among the plurality of fins. Like to do.
  • the fin cutting part can suppress heat conduction through the fins generated between the main heat exchanging part and the adjacent sub heat exchanging part, and the heat exchanger evaporating performance and heat dissipation performance are reduced. Can be suppressed.
  • FIG. 1 is a schematic configuration diagram of an air conditioner 1 that employs an outdoor unit 2 as a heat exchange unit according to an embodiment of the present invention.
  • the air conditioner 1 is a device that can cool and heat a room such as a building by performing a vapor compression refrigeration cycle.
  • the air conditioner 1 mainly includes an outdoor unit 2, indoor units 3a and 3b, a liquid refrigerant communication tube 4 and a gas refrigerant communication tube 5 that connect the outdoor unit 2 and the indoor units 3a and 3b, an outdoor unit 2 and And a control unit 23 that controls the constituent devices of the indoor units 3a and 3b.
  • the vapor compression refrigerant circuit 6 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the indoor units 3 a and 3 b via the refrigerant communication tubes 4 and 5.
  • the outdoor unit 2 is installed outside the building (on the roof of the building, near the wall of the building, etc.) and constitutes a part of the refrigerant circuit 6.
  • the outdoor unit 2 mainly includes an accumulator 7, a compressor 8, a four-way switching valve 10, an outdoor heat exchanger 11, an outdoor expansion valve 12 as an expansion mechanism, a liquid side shut-off valve 13, and a gas side shut-off valve. 14 and an outdoor fan 15.
  • Each device and the valve are connected by refrigerant pipes 16 to 22.
  • the indoor units 3 a and 3 b are installed in a room (such as a living room or a ceiling space) and constitute a part of the refrigerant circuit 6.
  • the indoor unit 3a mainly has an indoor expansion valve 31a, an indoor heat exchanger 32a, and an indoor fan 33a.
  • the indoor unit 3b mainly includes an indoor expansion valve 31b as an expansion mechanism, an indoor heat exchanger 32b, and an indoor fan 33b.
  • the refrigerant communication pipes 4 and 5 are refrigerant pipes that are constructed on site when the air conditioner 1 is installed at a place such as a building.
  • One end of the liquid refrigerant communication tube 4 is connected to the liquid side closing valve 13 of the indoor unit 2, and the other end of the liquid refrigerant communication tube 4 is connected to the liquid side ends of the indoor expansion valves 31a and 31b of the indoor units 3a and 3b.
  • One end of the gas refrigerant communication pipe 5 is connected to the gas side shut-off valve 14 of the indoor unit 2, and the other end of the gas refrigerant communication pipe 5 is connected to the gas side ends of the indoor heat exchangers 32a and 32b of the indoor units 3a and 3b. It is connected.
  • the control unit 23 is configured by communication connection of control boards or the like (not shown) provided in the outdoor unit 2 and the indoor units 3a and 3b. In FIG. 1, for the sake of convenience, the outdoor unit 2 and the indoor units 3a and 3b are illustrated at positions away from each other.
  • the control unit 23 controls the components 8, 10, 12, 15, 31a, 31b, 33a, 33b of the air conditioner 1 (here, the outdoor unit 2 and the indoor units 3a, 3b), that is, the air conditioner 1 The whole operation control is performed.
  • the four-way switching valve 10 is switched to the outdoor heat radiation state (the state indicated by the solid line in FIG. 1).
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 8 and is compressed until it reaches the high pressure in the refrigeration cycle, and then discharged.
  • the high-pressure gas refrigerant discharged from the compressor 8 is sent to the outdoor heat exchanger 11 through the four-way switching valve 10.
  • the high-pressure gas refrigerant sent to the outdoor heat exchanger 11 dissipates heat by exchanging heat with outdoor air supplied as a cooling source by the outdoor fan 15 in the outdoor heat exchanger 11 that functions as a refrigerant radiator. Become a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant radiated in the outdoor heat exchanger 11 is sent to the indoor expansion valves 31 a and 31 b through the outdoor expansion valve 12, the liquid-side closing valve 13, and the liquid refrigerant communication pipe 4.
  • the refrigerant sent to the indoor expansion valves 31a and 31b is decompressed to the low pressure of the refrigeration cycle by the indoor expansion valves 31a and 31b, and becomes a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant decompressed by the indoor expansion valves 31a and 31b is sent to the indoor heat exchangers 32a and 32b.
  • the low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchangers 32a and 32b exchanges heat with indoor air supplied as a heating source by the indoor fans 33a and 33b in the indoor heat exchangers 32a and 32b. Evaporate. As a result, the room air is cooled and then supplied to the room to cool the room.
  • the low-pressure gas refrigerant evaporated in the indoor heat exchangers 32 a and 32 b is again sucked into the compressor 8 through the gas refrigerant communication pipe 5, the gas side closing valve 14, the four-way switching valve 10, and the accumulator 7.
  • the four-way selector valve 10 is switched to the outdoor evaporation state (the state indicated by the broken line in FIG. 1).
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 8 and is compressed until it reaches the high pressure in the refrigeration cycle, and then discharged.
  • the high-pressure gas refrigerant discharged from the compressor 8 is sent to the indoor heat exchangers 32 a and 32 b through the four-way switching valve 10, the gas side closing valve 14, and the gas refrigerant communication pipe 5.
  • the high-pressure gas refrigerant sent to the indoor heat exchangers 32a and 32b dissipates heat by exchanging heat with indoor air supplied as a cooling source by the indoor fans 33a and 33b in the indoor heat exchangers 32a and 32b. Becomes a high-pressure liquid refrigerant. Thereby, indoor air is heated, and indoor heating is performed by being supplied indoors after that.
  • the high-pressure liquid refrigerant radiated by the indoor heat exchangers 32 a and 32 b is sent to the outdoor expansion valve 12 through the indoor expansion valves 31 a and 31 b, the liquid refrigerant communication tube 4 and the liquid-side closing valve 13.
  • the refrigerant sent to the outdoor expansion valve 12 is decompressed to the low pressure of the refrigeration cycle by the outdoor expansion valve 12, and becomes a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant decompressed by the outdoor expansion valve 12 is sent to the outdoor heat exchanger 11.
  • the low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 11 exchanges heat with outdoor air supplied as a heating source by the outdoor fan 15 in the outdoor heat exchanger 11 that functions as a refrigerant evaporator. Go and evaporate into a low-pressure gas refrigerant.
  • the low-pressure refrigerant evaporated in the outdoor heat exchanger 11 is again sucked into the compressor 8 through the four-way switching valve 10 and the accumulator 7.
  • FIG. 2 is an external perspective view of the outdoor unit 2.
  • FIG. 3 is a front view of the outdoor unit 2 (illustrated excluding refrigerant circuit components other than the outdoor heat exchanger 11).
  • FIG. 4 is a schematic perspective view of the outdoor heat exchanger 11.
  • FIG. 5 is a partially enlarged view of the heat exchange parts 60A to 60K in FIG.
  • FIG. 6 is a schematic configuration diagram of the outdoor heat exchanger 11.
  • the outdoor unit 2 is a top blow type heat exchange unit that sucks air from the side surface of the casing 40 and blows air from the top surface of the casing 40.
  • the outdoor unit 2 mainly includes a substantially rectangular parallelepiped box-shaped casing 40, an outdoor fan 15 as a blower, devices 7, 8, 11 such as a compressor and an outdoor heat exchanger, a four-way switching valve, an outdoor expansion valve, and the like.
  • refrigerant circuit components that constitute a part of the refrigerant circuit 6 including the valves 10, 12 to 14, the refrigerant pipes 16 to 22, and the like.
  • “top”, “bottom”, “left”, “right”, “front”, “back”, “front”, and “back” are shown in FIG. 2 unless otherwise specified.
  • the direction when the outdoor unit 2 to be viewed is viewed from the front (left oblique front side of the drawing) is meant.
  • the casing 40 mainly includes a bottom frame 42 that spans a pair of installation legs 41 that extend in the left-right direction, a column 43 that extends vertically from a corner of the bottom frame 42, and a fan module 44 that is attached to the upper end of the column 43. And a front panel 45, and air inlets 40a, 40b, 40c are formed on the side surfaces (here, the rear surface and the left and right side surfaces), and an air outlet 40d is formed on the top surface.
  • the bottom frame 42 forms the bottom surface of the casing 40, and the outdoor heat exchanger 11 is provided on the bottom frame 42.
  • the outdoor heat exchanger 11 is a substantially U-shaped heat exchanger in plan view facing the back surface and both left and right side surfaces of the casing 40, and substantially forms the back surface and both left and right side surfaces of the casing 40. .
  • a fan module 44 is provided on the upper side of the outdoor heat exchanger 11, and forms a portion above the front and rear surfaces of the casing 40 and the right and left both-side support columns 43 and the top surface of the casing 40.
  • the fan module 44 is an assembly in which the outdoor fan 15 is accommodated in a substantially rectangular parallelepiped box having an upper surface and a lower surface opened.
  • the opening on the top surface of the fan module 44 is an air outlet 40d, and an air outlet grill 46 is provided at the air outlet 40d.
  • the outdoor fan 15 is disposed in the casing 40 so as to face the air outlet 40d, and is a blower that takes air into the casing 40 from the suction ports 40a, 40b, and 40c and discharges it from the air outlet 40d.
  • the front panel 45 is spanned between the support columns 43 on the front side, and forms the front surface of the casing 40.
  • refrigerant circuit components other than the outdoor fan 15 and the outdoor heat exchanger 11 are also housed.
  • the compressor 8 and the accumulator 7 are provided on the bottom frame 42.
  • the outdoor unit 2 includes the casing 40 in which the air suction ports 40a, 40b, and 40c are formed on the side surfaces (here, the rear surface and the left and right side surfaces), and the air outlet 40d is formed on the top surface. It has the outdoor fan 15 arrange
  • the outdoor heat exchanger 11 is a heat exchanger that performs heat exchange between the refrigerant and the outdoor air, and mainly includes a first header collecting pipe 80, a second header collecting pipe 90, a plurality of flat tubes 63, and a plurality of flat tubes 63. And fins 64.
  • all of the first header collecting pipe 80, the second header collecting pipe 90, the flat pipe 63, and the fins 64 are formed of aluminum or an aluminum alloy, and are joined to each other by brazing or the like.
  • the first header collecting pipe 80 and the second header collecting pipe 90 are both vertically long hollow cylindrical members.
  • the first header collecting pipe 80 is erected on one end side of the outdoor heat exchanger 11 (here, the left front end side in FIG. 4 or the left end side in FIG. 6), and the second header collecting pipe 90 is It is erected on the other end side of the outdoor heat exchanger 11 (here, the right front end side in FIG. 4 or the right end side in FIG. 6).
  • the flat tube 63 is a flat multi-hole tube having a flat surface portion 63a facing the vertical direction as a heat transfer surface and a large number of small passages 63b through which the refrigerant flows.
  • a plurality of flat tubes 63 are arranged vertically, and both ends thereof are connected to the first header collecting tube 80 and the second header collecting tube 90.
  • the fins 64 are partitioned into a plurality of ventilation paths through which air flows between adjacent flat tubes 63, and a plurality of cutouts 64a extending horizontally are formed so that the plurality of flat tubes 63 can be inserted. .
  • the shape of the notch 64 a of the fin 64 substantially matches the outer shape of the cross section of the flat tube 63.
  • the outdoor heat exchanger 11 is divided into a plurality of (here, 11) heat exchange sections 60A to 60K in which a plurality of flat tubes 63 are lined up and down. Specifically, the first heat exchange unit 60A, the second heat exchange unit 60B,... The tenth heat exchange unit 60J, and the eleventh heat exchange unit 60K are formed in this order from top to bottom. .
  • Each of the first to fourth heat exchange units 60A to 60D has seven flat tubes 63.
  • Each of the fifth to eighth heat exchange units 60E to 60H has eight flat tubes 63.
  • Each of the ninth to eleventh heat exchange units 60I to 60K has nine flat tubes 63.
  • the first header collecting pipe 80 is partitioned into upper and lower portions by partition plates 81, thereby forming inlet / outlet communication spaces 82A to 82K corresponding to the heat exchange portions 60A to 60K.
  • Each of the inlet / outlet communication spaces 82A to 82K is further partitioned vertically by a partition plate 83 to form upper gas side inlet / outlet communication spaces 84A to 84K and lower liquid side inlet / outlet communication spaces 85A to 85K.
  • the liquid side inlet / outlet communication spaces 85A to 85K communicate with the two flat tubes 63 from the bottom among the flat tubes 63 constituting the corresponding heat exchange sections 60A to 60K, and the gas side inlet / outlet communication spaces 84A to 84K.
  • the flat tubes 63 communicating with the gas side inlet / outlet communication spaces 84A to 84K are referred to as main heat exchange portions 61A to 61K
  • the flat tubes 63 communicating with the liquid side inlet / outlet communication spaces 85A to 85K are sub heat exchange portions 62A to 62A. 62K. That is, in the first to fourth inlet / outlet communication spaces 82A to 82D, the first to fourth liquid side inlet / outlet communication spaces 85A to 85D are arranged from the bottom of the flat tubes 63 constituting the first to fourth heat exchange sections 60A to 60D.
  • the flat tubes 63 communicated with the two flat tubes 63 (sub heat exchange portions 62A to 62D), and the first to fourth gas side inlet / outlet communication spaces 84A to 84D constitute the first to fourth heat exchange portions 60A to 60D.
  • the main heat exchanging parts 61A to 61D The main heat exchanging parts 61A to 61D.
  • the fifth to eighth liquid side inlet / outlet communication spaces 85E to 85H are two from the bottom of the flat tubes 63 constituting the fifth to eighth heat exchange sections 60E to 60H.
  • the flat tube 63 (sub heat exchange portions 62E to 62H) and the fifth to eighth gas side inlet / outlet communication spaces 84E to 84H constitute the fifth to eighth heat exchange portions 60E to 60H. It communicates with six (main heat exchange parts 61E-61H).
  • the ninth to eleventh inlet / outlet communication spaces 82I to 82K the ninth to eleventh liquid side inlet / outlet communication spaces 85I to 85K are two from the bottom of the flat tubes 63 constituting the ninth to eleventh heat exchange sections 60I to 60K.
  • the ninth to eleventh gas side inlet / outlet communication spaces 84I to 84K constitute the ninth to eleventh heat exchange portions 60I to 60K. It communicates with seven (main heat exchanging parts 61I to 61K).
  • the first header collecting pipe 80 includes a liquid side diverting member 70 for diverting a refrigerant sent from the outdoor expansion valve 12 during heating operation to the liquid side inlet / outlet communication spaces 85A to 85K, and a compressor 8 during cooling operation.
  • a liquid side diverting member 70 for diverting a refrigerant sent from the outdoor expansion valve 12 during heating operation to the liquid side inlet / outlet communication spaces 85A to 85K, and a compressor 8 during cooling operation.
  • gas side branching members 75 that branch and send the refrigerant sent from each to the gas side inlet / outlet communication spaces 84A to 84K.
  • the liquid side diverting member 70 extends from the liquid side refrigerant diverter 71 connected to the refrigerant pipe 20 (see FIG. 1) and the liquid side refrigerant diverter 71, and is connected to the liquid side inlet / outlet communication spaces 85A to 85K. Liquid-side refrigerant distribution pipes 72A to 72K.
  • the gas side branch member 75 extends from the gas side refrigerant branch mother pipe 76 connected to the refrigerant pipe 19 (see FIG. 1), and is connected to the gas side inlet / outlet communication spaces 84A to 84K.
  • the inner space of the second header collecting pipe 90 is partitioned up and down by a partition plate 91, so that folded communication spaces 92A to 92K corresponding to the heat exchange portions 60A to 60K are formed.
  • the folded communication spaces 92A to 92K communicate with all of the flat tubes 63 that constitute the corresponding heat exchange sections 60A to 60K. That is, the first to fourth folded communication spaces 92A to 92D communicate with all the seven flat tubes 63 constituting the first to fourth heat exchange units 60A to 60D.
  • the fifth to eighth folded communication spaces 92E to 92H communicate with all of the eight flat tubes 63 constituting the fifth to eighth heat exchange portions 60E to 60H.
  • the ninth to eleventh folded communication spaces 92I to 92K communicate with all the nine flat tubes 63 constituting the ninth to eleventh heat exchange units 60I to 60K.
  • each of the heat exchange units 60A to 60K is connected to the main heat exchange units 61A to 61K and the sub heat exchange units 62A to 62K connected in series through the folded communication spaces 92A to 92K below the main heat exchange units 61A to 61K. And have. That is, the heat exchanging parts 60A to 60D are positioned directly below the flat tubes 63 constituting the main heat exchanging parts 61A to 61D communicating with the gas side inlet / outlet communicating spaces 84A to 84D and the main heat exchanging parts 61A to 61D.
  • the flat tubes 63 constituting the sub heat exchange portions 62A to 62D communicating with the liquid side inlet / outlet communication spaces 85A to 85D are connected in series through the folded communication spaces 92A to 92D.
  • the heat exchange units 60E to 60H are located directly below the flat tubes 63 constituting the main heat exchange units 61E to 61H communicating with the gas side inlet / outlet communication spaces 84E to 84H and the main heat exchange units 61E to 61H.
  • the flat tubes 63 constituting the sub heat exchange portions 62E to 62H communicating with the side inlet / outlet communication spaces 85E to 85H are connected in series through the folded communication spaces 92E to 92H.
  • the heat exchange units 60I to 60K are located directly below the flat tubes 63 constituting the main heat exchange units 61I to 61K communicating with the gas side inlet / outlet communication spaces 84I to 84K and the main heat exchange units 61I to 61K.
  • the flat tubes 63 constituting the sub heat exchange portions 62I to 62K communicating with the side inlet / outlet communication spaces 85I to 85K are connected in series through the folded communication spaces 92I to 92K.
  • the number (7) of flat tubes 63 constituting the first heat exchanging portion 60 ⁇ / b> A located at the top of the outdoor heat exchanger 11 is equal to the total number of flat tubes 63 constituting the outdoor heat exchanger 11 ( 87) is divided by the number (11) of the heat exchange sections 60A to 60K, which is 0.6 to 0.9 times.
  • the number of the heat exchange parts in the outdoor heat exchanger 11 may be 10 or less, may be 12 or more, and is set according to the height of the outdoor heat exchanger 11 or the like.
  • the number (five) of the flat tubes 63 constituting the main heat exchanging parts 61A to 61D of the heat exchanging parts 60A to 60D located at the upper part of the outdoor heat exchanger 11 is equal to the lower part of the outdoor heat exchanger 11.
  • the number of the flat tubes 63 constituting the main heat exchanging parts 61I to 61K of the heat exchanging parts 60I to 60K located at (6) is smaller.
  • To 7) is 1.5 to 4.5.
  • the outdoor heat exchanger 11 functions as a radiator for the refrigerant discharged from the compressor 8.
  • the refrigerant discharged from the compressor 8 is sent to the gas-side branch member 75 through the refrigerant pipe 19 (see FIG. 1).
  • the refrigerant sent to the gas side diverting member 75 is diverted from the gas side refrigerant diverting mother pipe 76 to the gas side refrigerant diverting branch pipes 77A to 77K, and the gas side inlet / outlet communication spaces 84A to 84A of the first header collecting pipe 80 are separated. Sent to 84K.
  • the refrigerant sent to the gas side inlet / outlet communication spaces 84A to 84K is divided into the flat tubes 63 constituting the main heat exchanging portions 61A to 61K of the corresponding heat exchanging portions 60A to 60K.
  • the refrigerant sent to each flat tube 63 dissipates heat by exchanging heat with outdoor air while flowing through the passage 63b, and merges in the folded communication spaces 92A to 92K of the second header collecting tube 90. That is, the refrigerant passes through the main heat exchange parts 61A to 61K. At this time, the refrigerant dissipates heat from the superheated gas state until it becomes a liquid state close to a gas-liquid two-phase state or a saturated state.
  • the refrigerant that merges in each of the folded communication spaces 92A to 92K is divided into the flat tubes 63 that constitute the sub heat exchange units 62A to 62K of the corresponding heat exchange units 60A to 60K.
  • the refrigerant sent to each flat tube 63 is dissipated by heat exchange with outdoor air while flowing through the passage 63b, and merges in the liquid side inlet / outlet communication spaces 85A to 85K of the first header collecting pipe 80. That is, the refrigerant passes through the sub heat exchange units 62A to 62K. At this time, the refrigerant further dissipates heat until it becomes a supercooled liquid state from a liquid state close to a gas-liquid two-phase state or a saturated state.
  • the refrigerant sent to each of the liquid side inlet / outlet communication spaces 85A to 85K is sent to the liquid side refrigerant distribution pipes 72A to 72K of the liquid side refrigerant distribution member 70, and merges in the liquid side refrigerant distributor 71.
  • the refrigerant merged in the liquid side refrigerant divider 71 is sent to the outdoor expansion valve 12 (see FIG. 1) through the refrigerant pipe 20 (see FIG. 1).
  • the outdoor heat exchanger 11 functions as an evaporator of refrigerant decompressed by the outdoor expansion valve 12 (see FIG. 1).
  • the refrigerant decompressed in the outdoor expansion valve 12 is sent to the liquid side refrigerant distribution member 70 through the refrigerant pipe 20 (see FIG. 1).
  • the refrigerant sent to the liquid side refrigerant diverting member 70 is diverted from the liquid side refrigerant diverter 71 to the liquid side refrigerant diverting pipes 72A to 72K, and the liquid side inlet / outlet communication spaces 85A to 85K of the first header collecting pipe 80 are separated. Sent to.
  • the refrigerant sent to the liquid side inlet / outlet communication spaces 85A to 85K is divided into the flat tubes 63 constituting the sub heat exchange units 62A to 62K of the corresponding heat exchange units 60A to 60K.
  • the refrigerant sent to each flat tube 63 evaporates by heat exchange with the outdoor air while flowing through the passage 63b, and merges in the folded communication spaces 92A to 92K of the second header collecting tube 90. That is, the refrigerant passes through the sub heat exchange units 62A to 62K. At this time, the refrigerant evaporates from a gas-liquid two-phase state with a lot of liquid components to a gas state close to a saturated state with a gas-liquid two-phase state with many gas components.
  • the refrigerant that merges in each of the folded communication spaces 92A to 92K is divided into the flat tubes 63 that constitute the main heat exchange portions 61A to 61K of the corresponding heat exchange portions 60A to 60K.
  • the refrigerant sent to each flat tube 63 is evaporated (heated) by heat exchange with the outdoor air while flowing through the passage 63b, and the gas side inlet / outlet communication spaces 84A to 84K of the first header collecting pipe 80 are evaporated. Join in. That is, the refrigerant passes through the main heat exchange parts 61A to 61K. At this time, the refrigerant is further evaporated (heated) from a gas-liquid two-phase state with a lot of gas components or a gas state close to saturation to a superheated gas state.
  • the refrigerant sent to the gas side inlet / outlet communication spaces 84A to 84K is sent to the gas side refrigerant branch branches 77A to 77K of the gas side refrigerant branch member 75 and merges in the gas side refrigerant branch main pipe 76.
  • the refrigerant merged in the gas-side refrigerant branch mother pipe 76 is sent to the suction side of the compressor 8 (see FIG. 1) through the refrigerant pipe 19 (see FIG. 1).
  • the outdoor unit 2 of the present embodiment has the following features.
  • the outdoor heat exchanger 11 heat exchanger constituting the top-blowing outdoor unit 2 (heat exchange unit)
  • the main heat exchange units 61A to 61K and the main heat exchange units 61A to 61K are used as the outdoor heat exchanger 11 (heat exchanger) constituting the top-blowing outdoor unit 2 (heat exchange unit).
  • the heat exchanging units 60A to 60K including the sub heat exchanging units 62A to 62K connected in series through the folded communication spaces 92A to 92K of the header collecting pipe 90 are arranged vertically below. Therefore, unlike the configuration shown in Patent Document 1, the arrangement of the heat exchange units 60A to 60K is in line with the wind speed distribution in the heat exchanger, and the main heat exchange units 61A to 61K and the sub heat exchange unit
  • the communication pipe connecting 62A to 62K can also be eliminated.
  • the air wind speed distribution in the outdoor heat exchanger 11 is changed as described above. Accordingly, the number of flat tubes 63 constituting the heat exchanging units 60A to 60D located at the upper part of the outdoor heat exchanger 11 corresponds to the flat tubes constituting the heat exchanging units 60I to 60K located at the lower part of the outdoor heat exchanger 11. The number is set to be smaller than 63.
  • the heat transfer area of the heat exchange units 60A to 60D located at the upper part of the outdoor heat exchanger 11 is smaller than the heat transfer area of the heat exchange parts 60I to 60K located at the lower part of the outdoor heat exchanger 11, and It is possible to eliminate a bias in the degree of heat exchange between the heat exchange units 60A to 60D located above the heat exchanger 11 and the heat exchange units 60I to 60K located below the outdoor heat exchanger 11.
  • the refrigerant can be appropriately diverted to each of the heat exchange units 60A to 60K, and the outdoor heat exchanger 11 is allowed to evaporate the refrigerant.
  • the shunt performance when functioning as a heater (here, during heating operation) can be improved.
  • the number of the flat tubes 63 constituting the main heat exchanging parts 61A to 61K constituting the heat exchanging parts 60A to 60K is changed to be positioned above the outdoor heat exchanger 11.
  • the number of flat tubes 63 constituting the heat exchanging parts 60A to 60D is set to be smaller than the number of flat tubes 63 constituting the heat exchanging parts 60I to 60K located at the lower part of the outdoor heat exchanger 11. .
  • the outdoor heat exchanger 11 is made to change the refrigerant by changing the number of the flat tubes 63 constituting the main heat exchanging parts 61A to 61K that greatly influence the degree of heat exchanging in each of the heat exchanging parts 60A to 60K.
  • the shunting performance when functioning as an evaporator can be improved.
  • the heat transfer area of the section 60A is preferably about 0.6 to 0.9 times the average heat transfer area of the heat exchange sections 60A to 60K.
  • the number of the flat tubes 63 constituting the uppermost heat exchanging portion 60A is set to the average number of the flat tubes 63 constituting the respective heat exchanging portions 60A to 60K (that is, the outdoor heat exchangers).
  • 11 is a value obtained by dividing the total number of flat tubes 63 constituting 11 by the number of heat exchange parts 60A to 60K).
  • the number of the flat tubes 63 constituting the uppermost heat exchange section 60A is set to an appropriate number in consideration of the air velocity distribution in the outdoor heat exchanger 11, so that the outdoor heat exchanger 11 It is possible to improve the shunting performance when functioning as a refrigerant evaporator.
  • the outdoor heat exchanger 11 functions as a refrigerant evaporator
  • the refrigerant that has flowed back from the sub heat exchange units 62A to 62K into the communicating spaces 92A to 92K is the main heat exchange unit 61A. It is divided and sent to a flat tube 63 that constitutes ⁇ 6K.
  • the flat tube 63 constituting the main heat exchanging parts 61A to 61K is used from the viewpoint of reducing pressure loss and securing a heat transfer area.
  • the number is preferably larger than the number of flat tubes 63 constituting the sub heat exchange sections 62A to 62K.
  • the ratio of the number of flat tubes 63 constituting the main heat exchange portions 61A to 61K to the number of flat tubes 63 constituting the sub heat exchange portions 62A to 62K in each of the heat exchange portions 60A to 60K is preferable to be within the range.
  • the ratio is set within the range of 1.5 to 4.5.
  • the ratio of the number of flat tubes 63 constituting the main heat exchange portions 61A to 61K to the number of flat tubes 63 constituting the sub heat exchange portions 62A to 62K in the respective heat exchange portions 60A to 60K is folded back.
  • the upper and lower portions of the plurality of fins 64 are located at positions corresponding to the boundary between the main heat exchange units 61A to 61K and the sub heat exchange units 62A to 62K.
  • the fin cutting part 64b which suppresses heat conduction in the direction is formed.
  • the fin cutting portion 64b is formed from one end to the other end in the refrigerant flow direction of the heat exchange portions 60A to 60K (that is, the longitudinal direction of the flat tube 63) (see FIG. 7).
  • the fin cutting portion 64b is horizontally arranged so as to cross between the flat tubes 63 constituting the main heat exchange portions 61A to 61K and the flat tubes 63 constituting the sub heat exchange portions 62A to 62K adjacent thereto. It is formed in a slit shape extending elongated. Note that the fin cutting portion 64b may not be formed from one end to the other end in the refrigerant flow direction of the heat exchange portions 60A to 60K, and the main heat exchange portions 61A to 61K and the sub heat exchange portions 62A to 62K.
  • the fin cutting portion 64b may be formed in a plurality of intermittent slit shapes (that is, perforated shapes) instead of a continuous slit shape.
  • the fin cutting part 64b can suppress the heat conduction through the fins 64 generated between the main heat exchange parts 61A to 61K and the adjacent sub heat exchange parts 62A to 62K, and the outdoor heat exchange. A decrease in the evaporation performance and heat dissipation performance of the container 11 can be suppressed.
  • the flat tubes 63 constituting each of the sub heat exchange units 61A to 61K have the same number (two), but the number of the flat tubes 63 may be different.
  • the present invention includes a casing having a suction port formed on a side surface and a blower outlet formed on a top surface, a blower disposed so as to face the blower port, and a heat exchanger disposed below the blower. Widely applicable to exchange units.
  • Outdoor unit heat exchange unit
  • Outdoor heat exchanger heat exchanger
  • Outdoor fan blower
  • Casing 40a, 40b, 40c Suction port 40d Air outlet 60A-60K Heat exchange part 61A-61K Main heat exchange part 62A-62K Sub heat exchange part 63 Flat pipe 64 Fin 64b Fin cutting part 90 Second header collecting pipe (header collecting pipe) tube)

Landscapes

  • 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)
  • Geometry (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur (11) constitué par une pluralité de tubes plats (63) divisés en une pluralité de sections d'échange de chaleur (60A - 60K) agencées verticalement. Chaque section d'échange de chaleur (60A - 60K) comporte une section d'échange de chaleur principale (61A - 61K) et une section d'échange de chaleur secondaire (62A - 62K) en dessous de la section d'échange de chaleur principale et reliée en série avec la section d'échange de chaleur principale par l'intermédiaire d'un espace de communication de retour (92A - 92K) d'un tuyau collecteur de distribution (90). Dans le cas présent, selon la distribution de la vitesse de l'air, le nombre de tubes plats (63) constituant les sections d'échange de chaleur (60A - 60D) dans la partie supérieure de l'échangeur de chaleur (11) est réglé pour être inférieur au nombre de tubes plats (63) constituant les sections d'échange de chaleur (60I - 60K) dans la partie inférieure.
PCT/JP2017/047238 2017-02-22 2017-12-28 Unité d'échange de chaleur WO2018154972A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US16/487,865 US20200232709A1 (en) 2017-02-22 2017-12-28 Heat exchange unit
CN201780086714.0A CN110300876A (zh) 2017-02-22 2017-12-28 热交换单元
EP17897780.7A EP3587979A1 (fr) 2017-02-22 2017-12-28 Unité d'échange de chaleur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017031453A JP2018136092A (ja) 2017-02-22 2017-02-22 熱交換ユニット
JP2017-031453 2017-02-22

Publications (1)

Publication Number Publication Date
WO2018154972A1 true WO2018154972A1 (fr) 2018-08-30

Family

ID=63252538

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/047238 WO2018154972A1 (fr) 2017-02-22 2017-12-28 Unité d'échange de chaleur

Country Status (5)

Country Link
US (1) US20200232709A1 (fr)
EP (1) EP3587979A1 (fr)
JP (1) JP2018136092A (fr)
CN (1) CN110300876A (fr)
WO (1) WO2018154972A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109405354A (zh) * 2018-11-19 2019-03-01 珠海格力电器股份有限公司 降膜式换热器及空调机组
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
US11725833B2 (en) 2020-06-09 2023-08-15 Goodman Global Group, Inc. Heat exchanger for a heating, ventilation, and air-conditioning system
DE102021128183A1 (de) 2021-10-28 2023-05-04 Güntner Gmbh & Co. Kg Verdampfer für einen Wärmepumpenkreislauf und Wärmepumpenkreislauf mit einem Verdampfer
CN116379649A (zh) * 2023-04-25 2023-07-04 安徽中科自动化股份有限公司 一种用于空气源热泵的u型蒸发器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012098912A1 (fr) * 2011-01-21 2012-07-26 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
JP2012163319A (ja) 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
JP2013083420A (ja) * 2011-09-30 2013-05-09 Daikin Industries Ltd 熱交換器および空気調和機
JP2014031944A (ja) * 2012-08-03 2014-02-20 Hitachi Appliances Inc 冷凍サイクル装置、並びに、この冷凍サイクル装置を備えた冷凍装置及び空調装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4599732B2 (ja) * 2000-03-16 2010-12-15 株式会社デンソー 複式熱交換器の製造方法
CN101292119B (zh) * 2005-11-01 2011-07-06 大金工业株式会社 空调装置的室外单元
JP2012163313A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
CN104272040B (zh) * 2012-04-26 2016-06-15 三菱电机株式会社 制冷剂分配器、具备此制冷剂分配器的热交换器、冷冻循环装置和空调机
JP6115111B2 (ja) * 2012-12-12 2017-04-19 ダイキン工業株式会社 熱交換器

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012098912A1 (fr) * 2011-01-21 2012-07-26 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
JP2012163319A (ja) 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
JP2013083420A (ja) * 2011-09-30 2013-05-09 Daikin Industries Ltd 熱交換器および空気調和機
JP2014031944A (ja) * 2012-08-03 2014-02-20 Hitachi Appliances Inc 冷凍サイクル装置、並びに、この冷凍サイクル装置を備えた冷凍装置及び空調装置

Also Published As

Publication number Publication date
EP3587979A1 (fr) 2020-01-01
JP2018136092A (ja) 2018-08-30
US20200232709A1 (en) 2020-07-23
CN110300876A (zh) 2019-10-01

Similar Documents

Publication Publication Date Title
JP6481793B1 (ja) 熱交換器
WO2018154972A1 (fr) Unité d'échange de chaleur
WO2018181338A1 (fr) Échangeur de chaleur et dispositif de climatisation
WO2019009162A1 (fr) Échangeur de chaleur et unité d'échange de chaleur comportant celui-ci
JP6693552B2 (ja) 熱交換器及びそれを備えた空気調和装置
JP6791196B2 (ja) 室外ユニット
JP2018138826A (ja) 空気調和装置
JP2019060513A (ja) 熱交換器及びそれを備えた空気調和装置
US20200200476A1 (en) Heat exchanger
JP6888686B2 (ja) 熱交換器及びそれを備えた空気調和装置
CN111065867B (zh) 热交换器及具备该热交换器的空调装置
JP6414167B2 (ja) 熱交換器及びそれを備えた室外ユニット
JP2022112775A (ja) 熱交換器
JP6863431B2 (ja) 熱交換器及びそれを備えた空気調和装置
JP2019035535A (ja) 熱交換器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17897780

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2017897780

Country of ref document: EP

Effective date: 20190923