WO2019239990A1 - Échangeur de chaleur intérieur et dispositif de climatisation - Google Patents

Échangeur de chaleur intérieur et dispositif de climatisation Download PDF

Info

Publication number
WO2019239990A1
WO2019239990A1 PCT/JP2019/022415 JP2019022415W WO2019239990A1 WO 2019239990 A1 WO2019239990 A1 WO 2019239990A1 JP 2019022415 W JP2019022415 W JP 2019022415W WO 2019239990 A1 WO2019239990 A1 WO 2019239990A1
Authority
WO
WIPO (PCT)
Prior art keywords
indoor
heat exchanger
flat tube
outdoor
indoor heat
Prior art date
Application number
PCT/JP2019/022415
Other languages
English (en)
Japanese (ja)
Inventor
俊 吉岡
祥志 松本
智歩 藤井
好男 織谷
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
Publication of WO2019239990A1 publication Critical patent/WO2019239990A1/fr

Links

Images

Classifications

    • 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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • 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
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/032—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers
    • F24F1/0325—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • 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
    • F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
    • 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
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular

Definitions

  • the indoor heat exchanger is an indoor heat exchanger used for an indoor unit of an air conditioner.
  • the indoor heat exchanger includes a plurality of flat tubes and a plurality of heat transfer fins.
  • the flat tube has a flow path through which the refrigerant passes.
  • the heat transfer fin has a communication portion extending in the first direction.
  • the heat transfer fins are joined to a plurality of flat tubes arranged in the first direction.
  • the plurality of flat tubes are arranged side by side in the longitudinal direction of the flat tubes and the second direction intersecting the first direction.
  • the flat tube satisfies the relationship of WT ⁇ 12 mm.
  • WT is a dimension in the longitudinal direction in a cross-sectional view of the flat tube.
  • the indoor heat exchanger according to the third aspect is an indoor heat exchanger according to the second aspect, and the flat tube further satisfies the relationship of WT ⁇ 12 mm.
  • WT is a dimension in the longitudinal direction in a cross-sectional view of the flat tube.
  • This indoor heat exchanger can suppress the scattering of condensed water while ensuring heat transfer performance.
  • the indoor heat exchanger according to the sixth aspect is an indoor heat exchanger according to any of the second to fifth aspects, and the flat tube further satisfies a relationship of HT / WT ⁇ 0.2.
  • HT is a dimension in the short direction in a cross-sectional view of the flat tube.
  • WT is a dimension in the longitudinal direction in a cross-sectional view of the flat tube.
  • the indoor heat exchanger according to the seventh aspect is an indoor heat exchanger according to any one of the second to sixth aspects, and the flat tube further satisfies a relationship of HT / WT ⁇ 0.3.
  • HT is a dimension in the short direction in a cross-sectional view of the flat tube.
  • WT is a dimension in the longitudinal direction in a cross-sectional view of the flat tube.
  • This indoor heat exchanger can suppress the scattering of condensed water while ensuring heat transfer performance.
  • the air conditioner according to the ninth aspect is the air conditioner according to the eighth aspect, further comprising an outdoor heat exchanger.
  • the outdoor heat exchanger has a plurality of flat tubes and heat transfer fins.
  • the flat tube has a flow path through which the refrigerant passes.
  • the heat transfer fins are joined to a plurality of flat tubes arranged in the third direction.
  • the air conditioner according to the tenth aspect is the air conditioner according to the ninth aspect, and satisfies a relationship of HT / WT ⁇ HTo / WTo.
  • HT is a dimension in the short direction in a cross-sectional view of the flat tube of the indoor heat exchanger.
  • WT is a dimension in the longitudinal direction in a cross-sectional view of the flat tube of the indoor heat exchanger.
  • HTo is a dimension in the short direction in a cross-sectional view of the flat tube of the outdoor heat exchanger.
  • WTo is a dimension in the longitudinal direction in a cross-sectional view of the flat tube of the outdoor heat exchanger.
  • An air conditioner according to a thirteenth aspect is the air conditioner according to any of the ninth to twelfth aspects, wherein the heat transfer fin of the outdoor heat exchanger has a communication portion extending in the third direction. .
  • the communication portion is downstream of the flat tube in the flow direction of the gas passing through the indoor heat exchanger.
  • the communication portion is upstream of the flat tube in the flow direction of the gas passing through the outdoor heat exchanger.
  • FIG. 8 is a schematic side view of the indoor unit in the AA cross section of FIG. 7. It is a schematic external perspective view of an indoor heat exchanger. It is a partial expansion outline appearance perspective view of an indoor heat exchanger. It is explanatory drawing which shows the positional relationship of an indoor fin and an indoor flat tube.
  • FIG. 1 is a schematic configuration diagram of the air conditioner 1.
  • the air conditioner 1 is a device capable of cooling and heating a room such as a building by performing a vapor compression refrigeration cycle.
  • the air conditioner 1 mainly includes an outdoor unit 2, an indoor unit 3, a liquid refrigerant communication tube 4, and a gas refrigerant communication tube 5.
  • the liquid refrigerant communication tube 4 and the gas refrigerant communication tube 5 are refrigerant paths that connect the outdoor unit 2 and the indoor unit 3.
  • the vapor compression refrigerant circuit 6 of the air conditioner 1 is configured by connecting an outdoor unit 2 and an indoor unit 3 via a liquid refrigerant communication tube 4 and a gas refrigerant communication tube 5.
  • the liquid refrigerant communication pipe 4 and the gas refrigerant communication pipe 5 are refrigerant pipes that are constructed on site when the air conditioner 1 is installed in a predetermined place such as a building.
  • the refrigerant circuit 6 is filled with R32 as a working refrigerant.
  • FIG. 2 is a schematic external perspective view of the outdoor unit 2.
  • FIG. 3 is a schematic configuration diagram of the outdoor unit 2 in plan view.
  • the outdoor unit 2 constitutes a part of the refrigerant circuit 6 and is installed outdoors.
  • the outdoor refers to the rooftop of the building, the vicinity of the wall surface of the building, and the like.
  • 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, a liquid side closing valve 13, and a gas side closing valve 14.
  • the outdoor fan 15 and the casing 40 are provided.
  • the accumulator 7 is a container for supplying a gas refrigerant to the compressor 8.
  • the accumulator 7 is provided on the suction side of the compressor 8.
  • Compressor 8 sucks and compresses low-pressure gas refrigerant and discharges high-pressure gas refrigerant.
  • the outdoor heat exchanger 11 functions as a radiator for the refrigerant discharged from the compressor 8 during the cooling operation.
  • the outdoor heat exchanger 11 functions as an evaporator for the refrigerant sent from the indoor heat exchanger 51 during the heating operation.
  • An outdoor expansion valve 12 is connected to the liquid side of the outdoor heat exchanger 11.
  • a four-way switching valve 10 is connected to the gas side of the outdoor heat exchanger 11.
  • the outdoor expansion valve 12 is an electric expansion valve that functions as an expansion mechanism of the refrigerant circuit 6.
  • the outdoor expansion valve 12 decompresses the refrigerant radiated in the outdoor heat exchanger 11 during the cooling operation before sending it to the indoor heat exchanger 51.
  • the outdoor expansion valve 12 decompresses the refrigerant radiated in the indoor heat exchanger 51 during the heating operation before sending it to the outdoor heat exchanger 11.
  • the four-way switching valve 10 is a valve for switching between a cooling operation connection state and a heating operation connection state.
  • the discharge side of the compressor 8 is connected to the outdoor heat exchanger 11 side, and the suction side of the compressor 8 is connected to the gas side shut-off valve 14 side.
  • the discharge side of the compressor 8 is connected to the gas side shut-off valve 14 side, and the suction side of the compressor 8 is connected to the outdoor heat exchanger 11 side.
  • the connection state of the cooling operation is represented by a solid line of the four-way switching valve 10 in FIG.
  • the connection state of the heating operation is represented by a broken line of the four-way switching valve 10 in FIG.
  • the casing 40 mainly includes a bottom frame 40a, a top plate 40b, a left front plate 40c, a right front plate 40d, and a right side plate 40e.
  • the bottom frame 40 a is a horizontally long and substantially rectangular plate-like member that constitutes the bottom surface portion of the casing 40.
  • the bottom frame 40a is installed on the installation surface by a fixed leg 41 fixed to the lower surface thereof.
  • the top plate 40 b is a horizontally long and substantially rectangular plate-like member that constitutes the top surface portion of the casing 40.
  • the left front plate 40c is a plate-like member that mainly constitutes a left front portion and a left side portion of the casing 40.
  • the left front plate 40c is formed with two air outlets arranged vertically. These outlets are openings for blowing outdoor air taken into the casing 40 from the back side and the left side by the outdoor fan 15 to the front side.
  • a fan grill 42 is provided at each outlet.
  • the air outlet may be an opening that is formed in the top plate 40b and blows out outdoor air taken into the casing 40 upward.
  • the right front plate 40d is a plate-like member that mainly forms the right front portion of the casing 40 and the front portion of the right side surface.
  • the right side plate 40e is a plate-like member that mainly constitutes the right rear surface portion of the casing 40 and the rear portion of the right side surface.
  • a partition plate 43 is provided in the casing 40.
  • the partition plate 43 partitions the internal space of the casing 40 into a blower chamber in which the outdoor fan 15 and the like are disposed, and a machine chamber in which the compressor 8 and the like are disposed.
  • FIG. 4 is a schematic external perspective view of the outdoor heat exchanger 11.
  • the outdoor heat exchanger 11 mainly includes a gas-side flow divider 23, a liquid-side flow divider 24, a plurality of inflow-side folded members 25, a plurality of anti-inflow-side folded members 26, a plurality of outdoor flat tubes 90, It has a plurality of outdoor fins 91.
  • These components constituting the outdoor heat exchanger 11 are made of aluminum or an aluminum alloy, and are joined to each other by brazing or the like.
  • the plurality of outdoor flat tubes 90 are arranged side by side in the vertical direction (vertical direction).
  • the plurality of outdoor fins 91 are arranged side by side along the direction in which the outdoor flat tube 90 extends.
  • the plate thickness direction of the outdoor fins 91 is the same as the direction in which the outdoor fins 91 are arranged.
  • the liquid side flow divider 24 is connected to the plurality of outdoor flat tubes 90 disposed below the plurality of outdoor flat tubes 90 and is connected to the refrigerant tube 20.
  • the outdoor heat exchanger 11 functions as a refrigerant radiator
  • the refrigerant that has flowed through each of the plurality of outdoor flat tubes 90 connected to the liquid side flow divider 24 is merged by the liquid side flow divider 24, and the refrigerant It flows out of the outdoor heat exchanger 11 through the pipe 20.
  • the plurality of inflow side folding members 25 are disposed between the gas side flow divider 23 and the liquid side flow divider 24.
  • the inflow side folding member 25 is a tube that connects the ends of the outdoor flat tubes 90 provided at different height positions.
  • the plurality of anti-inflow side folding members 26 are ends of the outdoor heat exchanger 11, and the side on which the gas side flow divider 23, the liquid side flow divider 24, and the plurality of inflow side folding members 25 are provided. It is provided at the opposite end.
  • the anti-inflow side folding member 26 is a tube that connects the ends of the outdoor flat tubes 90 provided at different height positions.
  • the outdoor flat tube 90 has an upper flat surface 90a, a lower flat surface 90b, and a plurality of flow paths 90c.
  • the upper flat surface 90a is the surface of the outdoor flat tube 90 and is the upper surface facing upward in the vertical direction.
  • the lower flat surface 90b is a surface of the outdoor flat tube 90 and is a lower surface facing downward in the vertical direction.
  • the flow path 90c is a space through which the refrigerant flows.
  • the plurality of flow paths 90c are provided side by side in the outdoor air flow direction.
  • the outdoor air flow direction is a direction in which outdoor air passing through the outdoor heat exchanger 11 flows.
  • the outdoor air flow direction is a longitudinal direction in a cross-sectional view of the outdoor flat tube 90, and is a direction indicated by an arrow in FIG.
  • “windward” means the upstream side in the outdoor air flow direction
  • “leeward side” means the downstream side in the outdoor air flow direction.
  • the cross-sectional dimensions of the plurality of outdoor flat tubes 90 are all the same. Specifically, the cross-sectional dimensions are the width WTo of the outdoor flat tube 90 and the height HTo of the outdoor flat tube 90.
  • the width WTo of the outdoor flat tube 90 is a dimension in the longitudinal direction (the direction in which the plurality of flow paths 90c are arranged) in a cross-sectional view of the outdoor flat tube 90.
  • the height HTo of the outdoor flat tube 90 is a dimension in the short direction (vertical direction) in the cross-sectional view of the outdoor flat tube 90.
  • the height HTo of the outdoor flat tube 90 corresponds to the distance between the upper flat surface 90a and the lower flat surface 90b of the outdoor flat tube 90.
  • the plurality of outdoor flat tubes 90 are arranged at a predetermined step pitch DPo in the vertical direction.
  • the step pitch DPo corresponds to the distance between the upper flat surfaces 90a of the two outdoor flat tubes 90 adjacent in the vertical direction.
  • the leeward side end portion of the outdoor flat tube 90 is located further on the leeward side than the leeward side end portion of the outdoor fin 91. Thereby, damage and breakage of the leeward side end portion of the outdoor fin 91 at the time of manufacturing or transporting the outdoor heat exchanger 11 are suppressed.
  • the outdoor fins 91 are plate-like members that spread in the outdoor air flow direction and the vertical direction.
  • a plurality of the outdoor fins 91 are arranged at predetermined intervals along the thickness direction.
  • a plurality of outdoor flat tubes 90 are fixed to each outdoor fin 91.
  • the dimension of the flat portion of the outdoor fin 91 in the plate thickness direction is, for example, 0.05 mm or more and 0.15 mm or less.
  • the outdoor fin 91 mainly includes a plurality of insertion portions 92, an outdoor communication portion 97a, a plurality of leeward portions 97b, a waffle portion 93, an upwind fin tab 94a, a leeward fin tab 94b, an outdoor slit 95, It has the upper side rib 96a and the leeward side rib 96b.
  • the insertion portion 92 is formed so as to be cut along the outdoor air flow direction (horizontal direction) from the leeward edge of the outdoor fin 91 to the vicinity of the windward edge of the outdoor fin 91. Part.
  • the plurality of insertion portions 92 are provided so as to be arranged in the vertical direction.
  • the insertion portion 92 constitutes a fin collar formed by burring or the like.
  • the shape of the insertion portion 92 substantially matches the outer shape of the cross section of the outdoor flat tube 90.
  • the insertion portion 92 is fixed by brazing with the outdoor flat tube 90 inserted.
  • the windward portion 97b is a portion sandwiched between two insertion portions 92 adjacent in the vertical direction.
  • a plurality of leeward portions 97b extend further from the leeward end of the outdoor communication portion 97a toward the leeward side at different height positions.
  • the waffle portion 93 is formed near the center of the outdoor fin 91 in the outdoor air flow direction.
  • the waffle portion 93 is composed of a raised portion and a non-raised portion.
  • the raised portion is a portion raised in the plate thickness direction of the outdoor fin 91.
  • the non-protruding portion is a flat portion that does not protrude in the plate thickness direction of the outdoor fin 91.
  • the windward fin tab 94a and the leeward fin tab 94b are respectively provided in the vicinity of the windward end portion and the windward end portion of the outdoor fin 91 in order to regulate the interval between the outdoor fins 91 adjacent in the plate thickness direction. Is provided.
  • FIG. 6 is an external perspective view of the indoor unit 3.
  • FIG. 7 is a schematic plan view showing a state in which the top plate of the indoor unit 3 is removed.
  • FIG. 8 is a schematic side cross-sectional view of the indoor unit 3 taken along the line AA in FIG.
  • the indoor heat exchanger 51 functions as an evaporator for the refrigerant sent from the indoor heat exchanger 51 during the cooling operation.
  • the indoor heat exchanger 51 functions as a radiator for the refrigerant discharged from the compressor 8 during heating operation.
  • the indoor side end of the liquid refrigerant communication tube 4 is connected to the liquid side of the indoor heat exchanger 51.
  • the indoor side end of the gas refrigerant communication pipe 5 is connected to the gas side of the indoor heat exchanger 51.
  • the indoor fan 52 is a centrifugal blower disposed inside the casing body 31 of the indoor unit 3.
  • the indoor fan 52 sucks room air into the casing 30 through the suction port 36 of the decorative panel 35, passes the indoor heat exchanger 51, and then casing the indoor air through the outlet 37 of the decorative panel 35.
  • the air flow which blows out 30 is formed. This air flow is indicated by arrows in FIG.
  • the temperature of the indoor air supplied by the indoor fan 52 is adjusted by exchanging heat with the refrigerant passing through the indoor heat exchanger 51.
  • the casing 30 mainly has a casing body 31 and a decorative panel 35.
  • the casing body 31 is installed so as to be inserted into an opening formed in a ceiling U of a room that is a space to be air-conditioned.
  • the casing body 31 is a box-shaped member having a substantially octagonal shape in which long sides and short sides are alternately connected in a plan view.
  • the casing body 31 has a top plate and a plurality of side plates extending downward from the peripheral edge of the top plate. The lower surface of the casing body 31 is open.
  • the decorative panel 35 is installed so as to be fitted into an opening formed in the ceiling U.
  • the decorative panel 35 extends outward from the top and side plates of the casing body 31 in a plan view.
  • the decorative panel 35 is attached below the casing body 31.
  • the decorative panel 35 has an inner frame 35a and an outer frame 35b.
  • a substantially rectangular suction port 36 that opens downward is formed inside the inner frame 35a.
  • a filter 34 for removing dust in the air sucked from the suction port 36 is provided above the suction port 36.
  • An air outlet 37 and a corner air outlet 38 that are opened downward or obliquely downward are formed inside the outer frame 35b and outside the inner frame 35a.
  • the blower outlet 37 is arrange
  • the corner blower outlets 38 are arranged at positions corresponding to the substantially square corners in the plan view of the decorative panel 35, the first corner blower outlets 38 a, the second corner blower outlets 38 b, and the third corners. It is comprised from the blower outlet 38c and the 4th corner
  • the flap 39 is a member for changing the direction of air flow passing through the air outlet 37.
  • the flap 39 includes a first flap 39a disposed at the first outlet 37a, a second flap 39b disposed at the second outlet 37b, a third flap 39c disposed at the third outlet 37c, It is comprised from the 4th flap 39d arrange
  • Each flap 39 is pivotally supported at a predetermined position of the casing 30 so as to be rotatable.
  • the drain pan 32 is disposed below the indoor heat exchanger 51.
  • the drain pan 32 receives drain water generated by condensation of moisture in the air in the indoor heat exchanger 51.
  • the drain pan 32 is attached to the lower part of the casing body 31.
  • the drain pan 32 is formed with a cylindrical space extending in the vertical direction inside the indoor heat exchanger 51 at the center portion in plan view.
  • a bell mouth 33 is disposed below the inside of the cylindrical space. The bell mouth 33 guides the air sucked from the suction port 36 to the indoor fan 52.
  • the fourth outlet channel 47d communicates with the fourth outlet 37d at the lower end thereof.
  • the corner blowing channels 48a to 48c are composed of a first corner blowing channel 48a, a second corner blowing channel 48b, and a third corner blowing channel 48c.
  • the first corner portion outlet flow passage 48a communicates with the first corner portion outlet 38a at the lower end thereof.
  • the second corner blowout channel 48b communicates with the second corner blowout port 38b at the lower end thereof.
  • the third corner portion outlet passage 48c communicates with the third corner portion outlet 38c at the lower end thereof.
  • FIG. 9 is a schematic external perspective view of the indoor heat exchanger 51.
  • FIG. 10 is a partially enlarged external perspective view of the plurality of indoor fins 60 of the indoor heat exchanger 51 on the windward side.
  • the indoor heat exchanger 51 is disposed inside the casing body 31 in a state of being bent so as to surround the periphery of the indoor fan 52 at the same height as the indoor fan 52.
  • the indoor heat exchanger 51 mainly includes a liquid side header 81, a gas side header 71, a folded header 59, a plurality of indoor flat tubes 55, and a plurality of indoor fins 60. These parts constituting the indoor heat exchanger 51 are made of aluminum or an aluminum alloy, and are joined to each other by brazing or the like.
  • the liquid side header 81 constitutes one end of the leeward heat exchange unit 80 in plan view.
  • the liquid side header 81 is a cylindrical member extending in the vertical direction.
  • the liquid-side header 81 is connected to the indoor side end of the liquid refrigerant communication tube 4.
  • the liquid side header 81 is connected with a plurality of indoor flat tubes 55 constituting the leeward heat exchange unit 80.
  • the gas side header 71 constitutes one end of the upwind heat exchanging unit 70 in plan view.
  • the gas side header 71 is a cylindrical member extending in the vertical direction.
  • the gas side header 71 is connected to an end portion on the indoor side of the gas refrigerant communication pipe 5.
  • the gas side header 71 is connected to a plurality of indoor flat tubes 55 constituting the upwind heat exchange unit 70.
  • the return header 59 enables the refrigerant that has flowed through the indoor flat tube 55 at each height position to be sent back to the indoor flat tube 55 on the upwind or leeward side at the same height position.
  • the folding header 59 folds the refrigerant upwind.
  • the turn-up header 59 turns the refrigerant back to the leeward side.
  • the plurality of indoor fins 60 constitutes the indoor fin 60 fixed to the indoor flat tube 55 constituting the windward heat exchange part 70 of the indoor heat exchanger 51 and the leeward heat exchange part 80 of the indoor heat exchanger 51. And an indoor fin 60 fixed to the indoor flat tube 55.
  • the indoor fins 60 are arranged in the thickness direction of the indoor fins 60 along the longitudinal direction of the indoor flat tube 55.
  • FIG. 11 is a cross-sectional view of the indoor heat exchanger 51 and shows the positional relationship between the indoor fin 60 and the indoor flat tube 55.
  • FIG. 11 is a cross-sectional view taken along the direction in which the flow channel 55c extends in a state where the indoor flat tube 55 is cut perpendicular to the direction in which the flow channel 55c inside the indoor flat tube 55 extends. is there.
  • the indoor flat tube 55 has an upper flat surface 55a, a lower flat surface 55b, and a plurality of flow paths 55c.
  • the upper flat surface 55a is a surface of the indoor flat tube 55 and is an upper surface facing upward in the vertical direction.
  • the lower flat surface 55b is a surface of the indoor flat tube 55 and is a lower surface facing downward in the vertical direction.
  • the flow path 55c is a space through which the refrigerant flows.
  • the plurality of flow paths 55c are provided side by side in the indoor air flow direction.
  • the indoor air flow direction is a longitudinal direction in a cross-sectional view of the indoor flat tube 55, and is a direction indicated by an arrow in FIG.
  • the indoor flat tube 55 constituting the windward heat exchanging unit 70 and the indoor flat tube 55 constituting the leeward heat exchanging unit 80 are arranged at respective height positions when viewed along the indoor air flow direction. Are arranged so as to overlap each other.
  • the windward side end portions of the plurality of indoor flat tubes 55 and the windward side end portions of the indoor fins 60 are at substantially the same position in the indoor air flow direction. Is provided.
  • the cross-sectional dimensions of the plurality of indoor flat tubes 55 are all the same. Specifically, the cross-sectional dimensions are the width WT of the indoor flat tube 55 and the height HT of the indoor flat tube 55.
  • the width WT of the indoor flat tube 55 is a dimension in the longitudinal direction (the direction in which the plurality of flow paths 55c are arranged) in a cross-sectional view of the indoor flat tube 55.
  • the height HT of the indoor flat tube 55 is a dimension in the short side direction (vertical direction) in the cross-sectional view of the indoor flat tube 55.
  • the height HT of the indoor flat tube 55 corresponds to the distance between the upper flat surface 55a and the lower flat surface 55b of the indoor flat tube 55.
  • the plurality of indoor flat tubes 55 are arranged at a predetermined step pitch DP in the vertical direction.
  • the step pitch DP corresponds to the distance between the upper flat surfaces 55a of the two indoor flat tubes 55 adjacent in the vertical direction.
  • the width WT of the indoor flat tube 55 is 12 mm or less.
  • the width WT of the indoor flat tube 55 is preferably 10 mm or less.
  • the width WT of the indoor flat tube 55 is preferably 3 mm or more and 12 mm or less, and more preferably 3 mm or more and 10 mm or less.
  • the indoor flat tube 55 satisfies the relationship of HT / WT ⁇ 0.15.
  • the indoor flat tube 55 preferably further satisfies the relationship of HT / WT ⁇ 0.2.
  • the indoor flat tube 55 preferably satisfies the relationship of 0.15 ⁇ HT / WT ⁇ 0.3, and more preferably satisfies the relationship of 0.2 ⁇ HT / WT ⁇ 0.3. .
  • width WT of the indoor flat tube 55 is preferably smaller than the width WTo of the outdoor flat tube 90.
  • the height HT of the indoor flat tube 55 is preferably 1.2 mm or more and 2.5 mm or less.
  • the pitch in the plate thickness direction of the plurality of indoor fins 60 of the indoor heat exchanger 51 is preferably smaller than the pitch in the plate thickness direction of the plurality of outdoor fins 91 of the outdoor heat exchanger 11.
  • the pitch in the plate thickness direction is the interval between the surfaces on the same side of the indoor fins 60 adjacent in the plate thickness direction or the interval between the surfaces on the same side of the outdoor fins 91 adjacent in the plate thickness direction.
  • the indoor heat exchanger 51 satisfies the relationship of 4.0 ⁇ DP / HT ⁇ 10.0. It is preferable that the indoor heat exchanger 51 further satisfies the relationship of 4.6 ⁇ DP / HT ⁇ 8.0.
  • the DP / HT value of the indoor heat exchanger 51 is smaller than the DPo / HTo value of the outdoor heat exchanger 11.
  • the indoor fin 60 is a plate-like member that spreads in the indoor air flow direction and the vertical direction.
  • a plurality of indoor fins 60 are arranged at predetermined intervals along the thickness direction.
  • a plurality of indoor flat tubes 55 are fixed to each indoor fin 60.
  • the indoor fins 60 constituting the windward heat exchange unit 70 and the indoor fins 60 constituting the leeward heat exchange unit 80 are arranged so as to substantially overlap each other when viewed along the indoor air flow direction. Has been.
  • the leeward side end of the indoor fin 60 constituting the windward heat exchange unit 70 and the windward side end of the indoor fin 60 constituting the leeward heat exchange unit 80 are in contact with each other at least partially. ing.
  • the indoor fin 60 mainly includes a main surface 61, a plurality of fin collar portions 65a, an indoor communication unit 64, a plurality of upwind portions 65, A slit 62 and a communication position slit 63 are provided.
  • board thickness direction in the main surface 61 of the indoor fin 60 is 0.05 mm or more and 0.15 mm or less, for example. It is preferable that the pitch in the plate thickness direction of the plurality of indoor fins 60 (the distance between the surfaces on the same side of the adjacent indoor fins 60) is 1.0 mm or more and 1.6 mm or less.
  • the main surface 61 is a surface of the indoor fin 60 and corresponds to a flat portion where the fin collar portion 65a, the main slit 62, and the communication position slit 63 are not provided.
  • the fin collar portion 65 a is formed so as to extend along the indoor air flow direction (horizontal direction) from the leeward edge of the indoor fin 60 to the vicinity of the leeward edge of the indoor fin 60.
  • the plurality of fin collar portions 65a are arranged in the vertical direction.
  • the fin collar portion 65a is formed by burring or the like.
  • the contour shape of the fin collar portion 65 a substantially matches the outer shape of the cross section of the indoor flat tube 55.
  • the fin collar portion 65a is brazed and fixed in a state where the indoor flat tube 55 is inserted.
  • FIG. 12 is a cross-sectional view showing a joined state between the indoor fin 60 and the indoor flat tube 55.
  • FIG. 12 is a cross-sectional view of the indoor heat exchanger 51 cut along a plane including the direction in which the refrigerant passes through the flow path 55c of the indoor flat tube 55 and the vertical direction.
  • the fin collar portion 65 a is configured to be raised with respect to the main surface 61 on the side opposite to the cut and raised side of the main slit 62 in the thickness direction of the main surface 61.
  • the fin collar portion 65a is bent on the side opposite to the main surface 61 side so as to extend away from the upper flat surface 55a (or the lower flat surface 55b) of the indoor flat tube 55 fixed to the fin collar portion 65a.
  • a positioning portion 65x is provided.
  • the positioning portion 65x defines the pitch in the plate thickness direction of the plurality of indoor fins 60 by making surface contact with the main surface 61 of the adjacent indoor fins 60.
  • the fin collar portion 65a is flattened by brazing in a state where the brazing material 58 is interposed between the upper flat surface 55a (or the lower flat surface 55b) of the indoor flat tube 55. It is joined to the tube 55.
  • a location where the fin collar portion 65 a starts to rise with respect to the main surface 61, and a location where the main slit 62 begins to be raised and raised Is preferably 1 mm or less. Condensed water on the lower flat surface 55b of the indoor flat tube 55 is guided downward and drained through a location where the main slit 62 starts to be cut and raised. Therefore, by setting the distance DS to a short distance of 1 mm or less, it is possible to suppress the dew condensation water from being retained on the lower flat surface 55b of the indoor flat tube 55.
  • the indoor communication portion 64 is a part of the indoor fin 60 and continuously extends in the vertical direction further on the leeward side than the end portion on the leeward side of the indoor flat tube 55.
  • WL is the length of the indoor communication portion 64 in the indoor air flow direction
  • WF is the length of the indoor fin 60 in the indoor air flow direction
  • the indoor fin 60 has a relationship of 0.2 ⁇ WL / WF ⁇ 0.5. It is preferable to satisfy.
  • the main slit 62 and the communication position slit 63 are cut and raised from the flat main surface 61 to the same side in the plate thickness direction, thereby forming openings on the windward side and the leeward side, respectively.
  • the outdoor heat exchanger 11 functions as a refrigerant radiator
  • the indoor heat exchanger 51 functions as a refrigerant evaporator.
  • the connection state of the four-way switching valve 10 is switched as shown by the solid line in FIG.
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 8 of the outdoor unit 2, compressed until reaching the high pressure in the refrigeration cycle, and then discharged.
  • the high-pressure gas refrigerant discharged from the compressor 8 passes through the four-way switching valve 10 and is sent to the outdoor heat exchanger 11.
  • the low-pressure gas-liquid two-phase refrigerant sent to the indoor unit 3 evaporates in the indoor heat exchanger 51 by exchanging heat with indoor air supplied as a heating source by the indoor fan 52. Thereby, the air which passes the indoor heat exchanger 51 is cooled, and indoor cooling is performed. At this time, moisture contained in the air passing through the indoor heat exchanger 51 is condensed, and condensed water is generated on the surface of the indoor heat exchanger 51.
  • the low-pressure gas refrigerant evaporated in the indoor heat exchanger 51 is sent to the outdoor unit 2 through the gas refrigerant communication pipe 5.
  • the low-pressure gas refrigerant sent to the outdoor unit 2 is again sucked into the compressor 8 through the gas-side closing valve 14, the four-way switching valve 10 and the accumulator 7.
  • the outdoor heat exchanger 11 functions as a refrigerant evaporator
  • the indoor heat exchanger 51 functions as a refrigerant radiator.
  • the connection state of the four-way selector valve 10 is switched as indicated by the broken line in FIG.
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 8 of the outdoor unit 2, compressed until reaching 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 unit 3 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 unit 3 performs heat exchange with the indoor air supplied as a cooling source by the indoor fan 52 in the indoor heat exchanger 51, and dissipates heat to become high-pressure liquid refrigerant. Thereby, the air which passes the indoor heat exchanger 51 is heated, and indoor heating is performed.
  • the high-pressure liquid refrigerant radiated by the indoor heat exchanger 51 is sent to the outdoor unit 2 through the liquid refrigerant communication tube 4.
  • the high-pressure liquid refrigerant sent to the outdoor unit 2 passes through the liquid-side closing valve 13 and is reduced in pressure to the low pressure of the refrigeration cycle in the outdoor expansion valve 12 to become a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant evaporates by exchanging heat with outdoor air supplied as a heating source by the outdoor fan 15 in the outdoor heat exchanger 11 to become a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant passes through the four-way switching valve 10 and the accumulator 7 and is sucked into the compressor 8 again.
  • the heat transfer coefficient of the indoor fins in the indoor heat exchanger can be increased as the width of the indoor flat tube is increased.
  • the width of the indoor flat tube is increased, it is difficult for condensed water that tends to stay on the surface (upper surface and lower surface) of the indoor flat tube to be discharged.
  • the discharge property of the dew condensation water of the indoor heat exchanger is lowered, and the dew condensation water is easily scattered in the room.
  • the dew condensation water is more likely to be scattered into the room if the wind speed of the indoor unit is increased.
  • FIG. 13 is a specific example of data obtained by changing the value of WT.
  • the horizontal axis represents the width WT of the indoor flat tube 55
  • the vertical axis represents the drainage time.
  • the drainage time means that the drainage of the indoor heat exchanger 51 is completed and the weight of the indoor heat exchanger 51 is constant from the time when the indoor heat exchanger 51 is pulled up from the water tank in which the indoor heat exchanger 51 is buried. This is the time until the point of time.
  • the height HT of the indoor flat tube 55 is 2 mm
  • the step pitch DP is 10 mm
  • the length WL of the indoor communication portion 64 in the indoor air flow direction is 3 mm.
  • the indoor heat exchanger 51 is provided with an upper limit on the width WT of the indoor flat tube 55, thereby making it easy to discharge condensed water that tends to stay on the surface of the indoor flat tube 55, and was used as a refrigerant evaporator. Suppresses the dew condensation that occurs in some cases. Further, by providing an upper limit on the width WT of the indoor flat tube 55, the size of the indoor fin 60 can be reduced, and the indoor unit 3 can be made compact.
  • the width WT of the indoor flat tube 55 is too small, the indoor air flow direction dimension of the indoor communication portion 64 of the indoor fin 60 increases. As a result, heat is less likely to be transferred to a region away from the indoor flat tube 55 in the region of the indoor fin 60, and the heat transfer performance of the indoor fin 60 may be reduced. Therefore, from the viewpoint of ensuring the heat transfer performance of the indoor fin 60, it is preferable to provide a lower limit for the width WT of the indoor flat tube 55. Specifically, the width WT of the indoor flat tube 55 may be 3 mm or more. preferable. Thereby, it becomes possible to suppress the fall of dew condensation water discharge
  • the heat transfer coefficient of the indoor fin in the indoor heat exchanger tends to increase the width of the indoor flat tube as the ratio of the height and width of the indoor flat tube is small. Will be easily scattered in the room.
  • the indoor heat exchanger 51 is configured when HT is the height of the indoor flat tube 55 and WT is the width of the indoor flat tube 55.
  • the indoor flat tube 55 preferably satisfies the relationship of HT / WT ⁇ 0.15.
  • an upper limit can be substantially provided for the width WT of the indoor flat tube 55.
  • the drainage time shown in FIG. 14 is the same as the drainage time shown in FIG. In FIG. 14, the step pitch DP is 10 mm, and the length WL of the indoor communication portion 64 in the indoor air flow direction is 3 mm.
  • the step pitch DP is 10 mm
  • the length WL of the indoor communication portion 64 in the indoor air flow direction is 3 mm.
  • the indoor heat exchanger 51 makes it easy to discharge the condensed water that tends to stay on the surface of the indoor flat tube 55, and suppresses the scattering of the condensed water that occurs when used as a refrigerant evaporator.
  • the width WT of the indoor flat tube 55 is preferably smaller than the width WTo of the outdoor flat tube 90.
  • the size of the outdoor fins 91 in the outdoor air flow direction is larger.
  • the width WTo of the outdoor flat tube 90 tends to increase. Therefore, by setting the width WT of the indoor flat tube 55 to be smaller than the width WTo of the outdoor flat tube 90, an upper limit can be substantially set on the width WT of the indoor flat tube 55. Thereby, it becomes possible to suppress a decrease in the drainage of condensed water that tends to stay on the surface of the indoor flat tube 55 while ensuring the frosting resistance of the outdoor fins 91.
  • HT is the height of the indoor flat tube 55
  • WT is the width of the indoor flat tube 55
  • HTo is the height of the outdoor flat tube 90
  • WTo is outdoor.
  • the width of the flat tube 90 it is preferable to satisfy the relationship of HT / WT ⁇ HTo / WTo.
  • the size of the outdoor fins 91 in the outdoor air flow direction is larger. As the dimension of the outdoor fin 91 in the outdoor air flow direction increases, the width WTo of the outdoor flat tube 90 tends to increase.
  • the HT / WT value of the indoor flat tube 55 is set to be larger than the HTo / WTo value of the outdoor flat tube 90, an upper limit can be substantially set on the width WT of the indoor flat tube 55. Thereby, it becomes possible to suppress a decrease in the drainage of condensed water that tends to stay on the surface of the indoor flat tube 55 while ensuring the frosting resistance of the outdoor fins 91.
  • the indoor heat exchanger 51 of the present embodiment includes an upwind heat exchange unit 70 and a downwind heat exchange unit 80. That is, the indoor heat exchanger 51 has a structure in which the indoor flat tubes 55 are arranged in two rows in the indoor air flow direction.
  • the row of indoor flat tubes 55 is a collection of a plurality of indoor flat tubes 55 arranged in the vertical direction. That is, the indoor heat exchanger 51 includes two rows including a row of the plurality of indoor flat tubes 55 constituting the upwind heat exchange unit 70 and a row of the plurality of indoor flat tubes 55 constituting the leeward heat exchange unit 80.
  • the indoor flat tube 55 is provided.
  • the indoor heat exchanger 51 Since the indoor heat exchanger 51 has two rows of indoor flat tubes 55, the dew condensation water generated in the upwind heat exchanging unit 70 out of the dew condensation water generated in the indoor heat exchanger 51 is upwind heat exchange. The water is drained downward in a portion between the unit 70 and the leeward heat exchange unit 80 or in the leeward heat exchange unit 80. Thus, more drainage paths for condensed water can be secured when there are a plurality of rows of indoor flat tubes 55 than when there is only one row of indoor flat tubes 55. Therefore, the indoor heat exchanger 51 can improve the drainage of condensed water by having a plurality of rows of the indoor flat tubes 55.
  • the leeward heat exchanging unit 80 is supplied with air that has increased in dryness by generating condensed water in the upwind heat exchanging unit 70 when passing through the upwind heat exchanging unit 70, the downwind heat exchanging unit 80 Condensed water generated in the portion 80 is reduced. As a result, scattering of condensed water from the leeward side end of the leeward heat exchange unit 80 is suppressed. Therefore, the indoor heat exchanger 51 can suppress scattering of condensed water by having a plurality of rows of the indoor flat tubes 55.
  • the outdoor heat exchanger 11 has only one row of outdoor flat tubes 90. That is, in the air conditioner 1, the number of the indoor flat tubes 55 is greater than the number of the outdoor flat tubes 90.
  • the lower limit of the row of the indoor flat tubes 55 can be set by setting the number of the rows of the indoor flat tubes 55 to be equal to or greater than the number of the rows of the outdoor flat tubes 90.
  • the number of rows of the indoor flat tubes 55 is set to be equal to or greater than the number of the rows of the outdoor flat tubes 90, thereby improving the drainage of condensed water.
  • the indoor fin 60 has an indoor communication portion 64 on the leeward side of the indoor flat tube 55. For this reason, the dew condensation water generated in the indoor flat tube 55 is easily discharged downward while passing through the indoor communication portion 64 located on the leeward side of the indoor flat tube 55. Therefore, by providing the indoor communication portion 64 on the leeward side of the indoor flat tube 55, the scattering of condensed water from the leeward end of the indoor fin 60 is suppressed.
  • the outdoor fins 91 of the outdoor heat exchanger 11 have an outdoor communication part 97 a on the windward side of the outdoor flat tube 90.
  • moisture contained in the air passing through the outdoor heat exchanger 11 is condensed and discharged.
  • the amount of water discharged from the outdoor heat exchanger 11 during the heating operation is smaller than the amount of condensed water discharged from the indoor heat exchanger 51 during the cooling operation. Therefore, in the outdoor heat exchanger 11, the scattering of condensed water is less likely to be a problem than the indoor heat exchanger 51.
  • the outdoor communication portion 97 a is preferably provided on the leeward side of the outdoor flat tube 90 on the leeward side. Therefore, by providing the outdoor communication portion 97a on the windward side of the outdoor flat tube 90, the frosting resistance of the outdoor fin 91 can be ensured.
  • the width of the indoor fin 60 is set to the outdoor fin. In addition to making it smaller than the width of 91, it is necessary to make the pitch of the indoor fins 60 smaller than the pitch of the outdoor fins 91.
  • the heat transfer coefficient of the indoor fin in the indoor heat exchanger increases as the interval between the indoor flat tubes decreases.
  • the interval between the indoor flat tubes is reduced, the flow velocity of the air passing between the indoor flat tubes is increased, and the condensed water is likely to be scattered.
  • the height of the indoor flat tube is increased, similarly, the flow velocity of the air passing between the indoor flat tubes is increased and the condensed water is likely to be scattered.
  • the interval between the indoor flat tubes is widened, the heat transfer coefficient of the indoor fins is lowered, so that the evaporation temperature of the refrigerant in the indoor heat exchanger has to be lowered, resulting in an environment in which condensed water is likely to be generated.
  • the indoor heat exchanger 51 is configured such that HT is the height of the indoor flat tube 55 and DP is the height direction of the plurality of indoor flat tubes 55.
  • HT is the height of the indoor flat tube 55
  • DP is the height direction of the plurality of indoor flat tubes 55.
  • the pitch it is preferable that the relationship of 4.0 ⁇ DP / HT ⁇ 10.0 is satisfied.
  • the value of WL / WF of the indoor fin 60 By setting the value of WL / WF of the indoor fin 60 to 0.2 or more, the width of the indoor communication portion 64 in the indoor air flow direction is sufficiently secured, and the dew condensation water generated in the indoor heat exchanger 51 is It becomes possible to facilitate the discharge through the communication portion 64. Further, by setting the WL / WF value of the indoor fin 60 to 0.5 or less, the area of the indoor fin 60 that is far from the indoor flat tube 55 and hardly contributes to improvement of heat transfer performance is suppressed. Thus, the material cost of the indoor fin 60 can be suppressed while maintaining the heat transfer performance of the indoor fin 60.
  • the value of WL / WF of the indoor fin 60 is 0.2 or more while the indoor communication portion 64 is positioned on the leeward side of the indoor flat tube 55, the drainage of the condensed water generated in the indoor flat tube 55 is discharged. Can be increased.
  • the indoor fin 60 has a main slit 62 and a communication position slit 63 that are cut and raised so that an opening is generated in the indoor air flow direction. For this reason, since the air supplied to the indoor heat exchanger 51 can be sufficiently brought into contact with the indoor fins 60, the air heat source can be fully utilized.
  • the upper ends of the main slit 62 and the communication position slit 63 are located near the lower end of the indoor flat tube 55 positioned above them. Therefore, the dew condensation water generated in the indoor flat tube 55 is easily captured by the main slit 62 and the communication position slit 63, and therefore the dew condensation water is easily discharged.
  • the distance DS shown in FIG. 12 is designed to be 1 mm or less, the retention of condensed water on the lower flat surface 55b side of the indoor flat tube 55 is more effectively suppressed. improves.
  • the end portion of the indoor fin 60 on the leeward side (downstream side in the indoor air flow direction) has a flat shape.
  • the shape of the leeward side end portion of the indoor fin 60 is not limited to a flat shape.
  • the indoor fin 60 may have water guide ribs 99 extending along the leeward side end.
  • FIG. 15 is an explanatory diagram showing the positional relationship between the indoor fin 60a and the indoor flat tube 55.
  • FIG. 16 is a cross-sectional view of the water guide rib 99 included in the indoor fin 60a, and is an explanatory view of a portion near the leeward side in the BB cross section of FIG.
  • the indoor heat exchanger 51 includes an upwind heat exchanging unit 70 and an upwind heat exchanging unit 80 as in the above embodiment.
  • the indoor fins 60 a of the windward heat exchange unit 70 and the leeward heat exchange unit 80 each have a water guide rib 99.
  • the water guiding rib 99 extends in the vertical direction along the leeward side end portion of the indoor communication portion 64 provided on the leeward side of the indoor fin 60a. As shown in FIG. 16, the water guiding rib 99 is configured to be recessed toward the plate thickness direction of the indoor fin 60 a with respect to the surrounding main surface 61. It is preferable that the water guide rib 99 is configured to be recessed more than the plate thickness of the indoor fin 60a.
  • the condensed water generated in the indoor heat exchanger 51 is captured by the water guiding rib 99, so that the condensed water is easily guided downward through the water guiding rib 99. . For this reason, it is suppressed that condensed water reaches
  • the water guide rib 99 is provided on the leeward side with respect to half the width of the indoor communication portion 64 in the indoor air flow direction. More preferably, the water guide rib 99 is provided at a position within 20% of the width of the indoor communication portion 64 in the indoor air flow direction from the leeward side end portion.
  • the width WL of the indoor communication portion 64 in the indoor air flow direction and the width WF of the indoor fin 60 in the indoor air flow direction have a relationship of 0.2 ⁇ WL / WF. It is preferable to satisfy.
  • the indoor heat exchanger 51 has the windward heat exchange part 70 and the leeward heat exchange part 80, and the indoor flat tube 55 is provided along with 2 rows in the indoor air flow direction.
  • the indoor flat tubes 55 provided in the indoor heat exchanger 51 are not limited to two rows, and may be three or more rows. By increasing the number of rows of the indoor flat tubes 55, it is possible to secure more drainage paths for the condensed water, and thus more effectively suppress the scattering of the condensed water from the leeward side end of the indoor heat exchanger 51. It becomes possible to do.
  • the plurality of indoor flat tubes 55 belonging to the windward heat exchange unit 70 and the plurality of indoor flat tubes 55 belonging to the leeward heat exchange unit 80 are along the indoor air flow direction. When viewed from above, they are generally arranged so as to overlap each other.
  • the arrangement of the indoor flat tubes 55 of the indoor heat exchanger 51 is not limited to this.
  • the plurality of indoor flat tubes 55 belonging to the windward heat exchange unit 70 and the plurality of indoor flat tubes 55 belonging to the leeward heat exchange unit 80 do not overlap each other when viewed along the indoor air flow direction. May be arranged.
  • the indoor air flow can be sufficiently applied to the indoor flat tube 55 located on the leeward side and the indoor flat tube 55 located on the leeward side, so that the heat transfer performance of the indoor heat exchanger 51 is achieved. Will improve.
  • the indoor fin 60 of the indoor heat exchanger 51 has the main slit 62 and the communication position slit 63.
  • the main slit 62 and the communication position slit 63 are configured to be cut and raised so that the entire slit is located on one side in the plate thickness direction with respect to the main surface 61 of the indoor fin 60.
  • the way to cut and raise the main slit 62 and the communication position slit 63 formed in the indoor fin 60 is not limited to this.
  • a structure called a louver may be adopted instead of the main slit 62 and the communication position slit 63.
  • a louver is a type of slit that is cut and raised.
  • the leeward end of the louver is located on one side of the main surface 61 of the indoor fin 60 in the plate thickness direction, and the leeward end of the louver is the other of the main surface 61 of the indoor fin 60 in the plate thickness direction. Located on the side.
  • the indoor heat exchanger 51 has two rows of indoor flat tubes 55.
  • an indoor heat exchanger 51 having only one row of indoor flat tubes 55 is used. May be.
  • the indoor flat tube 55 only needs to satisfy the relationship of HT / WT ⁇ 0.15 even if the width WT of the indoor flat tube 55 is not 12 mm or less.
  • the indoor flat tube 55 preferably further satisfies the relationship of HT / WT ⁇ 0.2.
  • the indoor flat tube 55 preferably satisfies the relationship of 0.15 ⁇ HT / WT ⁇ 0.3, and more preferably satisfies the relationship of 0.2 ⁇ HT / WT ⁇ 0.3. .
  • the indoor heat exchanger 51 is generated when it is used as a refrigerant evaporator by facilitating discharge of condensed water that tends to stay on the surface of the indoor flat tube 55. Suppresses dew condensation.
  • the width WT of the indoor flat tube 55 is preferably 12 mm or less. In this case, the width WT of the indoor flat tube 55 is more preferably 10 mm or less. In particular, the width WT of the indoor flat tube 55 is preferably 3 mm or more and 12 mm or less, and more preferably 3 mm or more and 10 mm or less.
  • the HT / WT value of the indoor flat tube 55 is preferably larger than the HTo / WTo value of the outdoor flat tube 90.
  • width WT of the indoor flat tube 55 is preferably smaller than the width WTo of the outdoor flat tube 90.
  • the height HT of the indoor flat tube 55 is preferably 1.2 mm or more and 2.5 mm or less.
  • the step pitch DP of the indoor heat exchanger 51 is preferably 8.0 mm or more and 15.0 mm or less.
  • the pitch in the plate thickness direction of the plurality of indoor fins 60 of the indoor heat exchanger 51 is preferably smaller than the pitch in the plate thickness direction of the plurality of outdoor fins 91 of the outdoor heat exchanger 11.
  • the indoor heat exchanger 51 satisfies the relationship of 4.0 ⁇ DP / HT ⁇ 10.0. It is preferable that the indoor heat exchanger 51 further satisfies the relationship of 4.6 ⁇ DP / HT ⁇ 8.0.
  • the indoor fin 60 satisfies 0.2 ⁇ WL / WF ⁇ 0.5. It is preferable to satisfy the relationship.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur intérieur et un dispositif de climatisation pouvant supprimer la diffusion d'eau condensée. L'échangeur de chaleur intérieur (51) est utilisé dans une unité intérieure (3) du dispositif de climatisation (1). L'échangeur de chaleur intérieur (51) comprend une pluralité de tubes plats intérieurs (55) et une pluralité d'ailettes intérieures (60). Les tubes plats intérieurs (55) comportent, à l'intérieur, un circuit d'écoulement apte à être traversé par un fluide frigorigène. Les ailettes intérieures (60) comportent une section de liaison intérieure (64) s'étendant dans une première direction. Les ailettes intérieures (60) sont reliées auxdits tubes plats intérieurs (55) agencés dans la première direction. Lesdits tubes plats intérieurs (55) sont agencés côte à côte dans la direction longitudinale des tubes plats intérieurs (55) et dans une seconde direction croisant la première direction. Les tubes plats intérieurs (55) satisfont à la relation WT ≤ 12 mm. WT représente une dimension dans la direction longitudinale, dans une vue en section transversale, du tube plat intérieur (55).
PCT/JP2019/022415 2018-06-12 2019-06-05 Échangeur de chaleur intérieur et dispositif de climatisation WO2019239990A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-111832 2018-06-12
JP2018111832A JP2019215117A (ja) 2018-06-12 2018-06-12 室内熱交換器及び空気調和装置

Publications (1)

Publication Number Publication Date
WO2019239990A1 true WO2019239990A1 (fr) 2019-12-19

Family

ID=68842255

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/022415 WO2019239990A1 (fr) 2018-06-12 2019-06-05 Échangeur de chaleur intérieur et dispositif de climatisation

Country Status (2)

Country Link
JP (1) JP2019215117A (fr)
WO (1) WO2019239990A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023190890A1 (fr) * 2022-03-31 2023-10-05 ダイキン工業株式会社 Climatiseur
WO2023190889A1 (fr) * 2022-03-31 2023-10-05 ダイキン工業株式会社 Climatiseur
JP2023152287A (ja) * 2022-03-31 2023-10-16 ダイキン工業株式会社 空気調和機

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022045667A1 (fr) 2020-08-31 2022-03-03 Samsung Electronics Co., Ltd. Échangeur de chaleur et climatiseur utilisant l'échangeur de chaleur

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003302183A (ja) * 2002-04-09 2003-10-24 Toyo Radiator Co Ltd 空調用熱交換器
JP2006336873A (ja) * 2002-10-02 2006-12-14 Showa Denko Kk 熱交換器用チューブ及び熱交換器
JP2009281693A (ja) * 2008-05-26 2009-12-03 Mitsubishi Electric Corp 熱交換器、その製造方法及びこの熱交換器を用いた空調冷凍装置
JP2014001882A (ja) * 2012-06-18 2014-01-09 Mitsubishi Electric Corp 熱交換器および空気調和機
WO2016194088A1 (fr) * 2015-05-29 2016-12-08 三菱電機株式会社 Échangeur de chaleur et appareil à cycle de réfrigération
JP2017187243A (ja) * 2016-04-07 2017-10-12 ダイキン工業株式会社 室内熱交換器
JP2018059704A (ja) * 2016-09-29 2018-04-12 ダイキン工業株式会社 熱交換器および空気調和装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003302183A (ja) * 2002-04-09 2003-10-24 Toyo Radiator Co Ltd 空調用熱交換器
JP2006336873A (ja) * 2002-10-02 2006-12-14 Showa Denko Kk 熱交換器用チューブ及び熱交換器
JP2009281693A (ja) * 2008-05-26 2009-12-03 Mitsubishi Electric Corp 熱交換器、その製造方法及びこの熱交換器を用いた空調冷凍装置
JP2014001882A (ja) * 2012-06-18 2014-01-09 Mitsubishi Electric Corp 熱交換器および空気調和機
WO2016194088A1 (fr) * 2015-05-29 2016-12-08 三菱電機株式会社 Échangeur de chaleur et appareil à cycle de réfrigération
JP2017187243A (ja) * 2016-04-07 2017-10-12 ダイキン工業株式会社 室内熱交換器
JP2018059704A (ja) * 2016-09-29 2018-04-12 ダイキン工業株式会社 熱交換器および空気調和装置

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023190890A1 (fr) * 2022-03-31 2023-10-05 ダイキン工業株式会社 Climatiseur
WO2023190889A1 (fr) * 2022-03-31 2023-10-05 ダイキン工業株式会社 Climatiseur
JP2023152287A (ja) * 2022-03-31 2023-10-16 ダイキン工業株式会社 空気調和機
JP2023151215A (ja) * 2022-03-31 2023-10-16 ダイキン工業株式会社 空気調和機
JP7401812B2 (ja) 2022-03-31 2023-12-20 ダイキン工業株式会社 空気調和機
JP7401803B2 (ja) 2022-03-31 2023-12-20 ダイキン工業株式会社 空気調和機

Also Published As

Publication number Publication date
JP2019215117A (ja) 2019-12-19

Similar Documents

Publication Publication Date Title
JP7092987B2 (ja) 室内熱交換器および空気調和装置
WO2019239990A1 (fr) Échangeur de chaleur intérieur et dispositif de climatisation
WO2015162689A1 (fr) Conditionneur d'air
CN110612425B (zh) 热交换器
US20090314020A1 (en) Indoor unit for air conditioner
JPWO2010146852A1 (ja) 天井設置型空気調和装置
JP7078840B2 (ja) 熱交換器および空気調和装置
JP6520353B2 (ja) 熱交換器及び空気調和機
WO2019004139A1 (fr) Échangeur de chaleur
JP6793831B2 (ja) 熱交換器、及び冷凍サイクル装置
WO2019240055A1 (fr) Échangeur de chaleur et climatiseur
JP6631608B2 (ja) 空気調和装置
JP7137092B2 (ja) 熱交換器
JP7089187B2 (ja) 熱交換器及び空気調和装置
WO2021095452A1 (fr) Échangeur de chaleur et climatiseur
JP2019132511A (ja) 冷凍装置
JPWO2019180764A1 (ja) 室内機及び空気調和機
JP2023148248A (ja) 空気調和機の室内機
JP5849697B2 (ja) 室外ユニット
JP2019132512A (ja) 冷凍装置

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: 19819233

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19819233

Country of ref document: EP

Kind code of ref document: A1