WO2016067907A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

Info

Publication number
WO2016067907A1
WO2016067907A1 PCT/JP2015/078907 JP2015078907W WO2016067907A1 WO 2016067907 A1 WO2016067907 A1 WO 2016067907A1 JP 2015078907 W JP2015078907 W JP 2015078907W WO 2016067907 A1 WO2016067907 A1 WO 2016067907A1
Authority
WO
WIPO (PCT)
Prior art keywords
fin
tube
heat transfer
heat exchanger
here
Prior art date
Application number
PCT/JP2015/078907
Other languages
English (en)
Japanese (ja)
Inventor
正憲 神藤
筒井　正浩
好男 織谷
潤一 濱舘
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 CN201580056296.1A priority Critical patent/CN107076525B/zh
Publication of WO2016067907A1 publication Critical patent/WO2016067907A1/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
    • F24F1/06—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
    • F28F1/10—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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

Definitions

  • the present invention relates to a heat exchanger, in particular, a heat exchanger provided with a plurality of flat tubes and a plurality of insertion fins.
  • Patent Document 1 Japanese Patent Laid-Open No. 2012-163320
  • the flat tubes are arranged along a predetermined tube step direction with the flat surfaces facing each other.
  • the insertion fin is formed with a plurality of notches for inserting a flat tube extending along the tube insertion direction intersecting the tube step direction and the longitudinal direction of the flat tube, and is arranged along the longitudinal direction of the flat tube.
  • the insertion fin is formed with a plurality of waffles forming a mountain-shaped inclined surface along the tube insertion direction.
  • the insertion fin when a flat tube is inserted into a notch portion of the insertion fin, the insertion fin may buckle in a valley portion between adjacent waffles in the tube insertion direction. That is, when the flat tube is inserted into the notch portion of the insertion fin, the valley portion between the waffles becomes a V-shaped fold, and the insertion fin may be bent.
  • An object of the present invention is to suppress the occurrence of buckling of an insertion fin when a flat tube is inserted into a notch in a heat exchanger provided with a plurality of flat tubes and a plurality of insertion fins.
  • the heat exchanger is a heat exchanger including a plurality of flat tubes and a plurality of insertion fins.
  • the flat tubes are arranged along a predetermined tube step direction with the flat surfaces facing each other.
  • the insertion fin is formed with a plurality of notches for inserting a flat tube extending along the tube insertion direction intersecting the tube step direction and the longitudinal direction of the flat tube, and is arranged along the longitudinal direction of the flat tube. ing.
  • the portion of the cutout portion that contacts the flat tube while the flat tube is inserted is a tube insertion portion.
  • the base part which makes a flat surface is formed in the some fin intermediate part pinched
  • a pedestal portion that forms a flat surface is formed in the fin intermediate portion, unlike the case where a waffle is formed in the insertion fin as in Patent Document 1, a flat tube is provided in the notch portion of the insertion fin.
  • the part which becomes a V-shaped crease like the trough part between waffles is lost.
  • the fin strength in the direction intersecting the tube insertion direction can be improved, and the occurrence of buckling of the insertion fin when the flat tube is inserted into the notch can be suppressed.
  • the heat exchanger according to the second aspect is the heat exchanger according to the first aspect, wherein the entire flat surface is disposed at a position protruding to one side in the longitudinal direction of the flat tube from the base surface of the insertion fin.
  • the base surface of the insertion fin means the fin surface of the insertion fin in a state before the formation of the pedestal portion and other portions.
  • a heat exchanger according to a third aspect is the heat exchanger according to the first or second aspect, wherein the flat surfaces have first and second sides that are parallel to each other and extend along the tube insertion direction, and the first side.
  • a third side connecting the end portions of the side and the second side in the tube insertion direction, and a fourth side connecting the end portions of the first side and the second side on the back side in the tube insertion direction. is doing.
  • the flat surface formed by the pedestal has a substantially square shape.
  • the fin strength in the direction intersecting the tube insertion direction can be improved by the first side and the second side which are a part of four sides having a substantially rectangular shape.
  • a heat exchanger according to a fourth aspect is the heat exchanger according to the third aspect, wherein the rib portion extending along the tube insertion direction has insertion fins on the front side and the back side of the base portion in the tube insertion direction.
  • the rib portion is formed continuously with the third side and the fourth side.
  • the rib part is integrated with the base part so that the third side and the fourth side of the base part do not fold. be able to. For this reason, the fin intensity
  • the heat exchanger according to the fifth aspect is the heat exchanger according to the fourth aspect, wherein the insertion fins are connected to the front side in the tube insertion direction from the end on the near side in the tube insertion direction of the plurality of fin intermediate portions.
  • a fin front portion extending toward each other, and a plurality of fin intermediate portions from the back end in the tube insertion direction toward the back in the tube insertion direction, and a plurality of fin intermediate portions at the back end in the tube insertion direction.
  • a fin back portion extending continuously is formed.
  • the rib part is disposed across the boundary part between the fin intermediate part and the fin front part and the boundary part between the fin intermediate part and the fin back part.
  • the rib part is arranged so as to straddle the boundary part between the fin intermediate part and the fin front part and the boundary part between the fin intermediate part and the fin back part, the boundary part between the fin intermediate part and the fin front part And the fin intensity
  • the heat exchanger according to the sixth aspect is formed by a louver raising an insertion fin in a pedestal portion in any of the first to fifth heat exchangers.
  • the portion where the louver is formed on the fin intermediate portion is also in the tube insertion direction.
  • the fin strength in the intersecting direction can be improved, and a louver having a large size (particularly a large size in the tube step direction) can be provided as compared with the case where the louver is formed in the waffle. For this reason, the heat transfer performance can be improved while suppressing buckling of the insertion fin when the flat tube is inserted into the notch of the insertion fin.
  • FIG. 1 It is a schematic block diagram of the air conditioning apparatus which has an outdoor heat exchanger as a heat exchanger concerning one Embodiment of this invention. It is a perspective view which shows the external appearance of an outdoor unit. It is a top view which shows the state which removed the top plate of the outdoor unit. It is a perspective view which shows the state which removed the top plate, the front plate, and the side plate of the outdoor unit. It is a schematic perspective view of an outdoor heat exchanger. It is the elements on larger scale of the heat exchange part of FIG. It is the elements on larger scale which show the state which looked at the heat exchange part of FIG. 6 from the direction along the longitudinal direction of a heat exchanger tube. It is a figure which shows the principal part of a heat-transfer fin.
  • FIG. 9 is a cross-sectional view taken along the line II-II, a cross-sectional view taken along the line III-III, and a cross-sectional view taken along the line IV-IV in FIG. It is the figure which looked at FIG. 8 from the near side of the pipe insertion direction, and the figure which looked at the back side of the pipe insertion direction.
  • FIG. 10 is a sectional view taken along the line VV in FIG. 8. It is a figure which shows the heat exchanger concerning a modification, Comprising: It is a figure corresponding to FIG. It is a figure which shows the heat exchanger concerning a modification, Comprising: It is a figure corresponding to FIG.
  • FIG. 1 is a schematic configuration diagram of an air conditioner 1 having an outdoor heat exchanger 23 as a heat exchanger 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 is mainly configured by connecting an outdoor unit 2 and an indoor unit 4.
  • the outdoor unit 2 and the indoor unit 4 are connected via a liquid refrigerant communication tube 5 and a gas refrigerant communication tube 6.
  • the vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the indoor unit 4 via the refrigerant communication pipes 5 and 6.
  • the indoor unit 4 is installed indoors and constitutes a part of the refrigerant circuit 10.
  • the indoor unit 4 mainly has an indoor heat exchanger 41.
  • the indoor heat exchanger 41 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool room air, and functions as a refrigerant radiator during heating operation to heat indoor air.
  • the liquid side of the indoor heat exchanger 41 is connected to the liquid refrigerant communication tube 5, and the gas side of the indoor heat exchanger 41 is connected to the gas refrigerant communication tube 6.
  • the indoor unit 4 has an indoor fan 42 for sucking indoor air into the indoor unit 4 and exchanging heat with the refrigerant in the indoor heat exchanger 41 and supplying the indoor air as supply air. That is, the indoor unit 4 has an indoor fan 42 as a fan that supplies indoor air as a heating source or cooling source of the refrigerant flowing through the indoor heat exchanger 41 to the indoor heat exchanger 41.
  • the indoor fan 42 a centrifugal fan or a multiblade fan driven by an indoor fan motor 42a is used as the indoor fan 42.
  • the outdoor unit 2 is installed outside and constitutes a part of the refrigerant circuit 10.
  • the outdoor unit 2 mainly has a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, a liquid side closing valve 25, and a gas side closing valve 26.
  • the compressor 21 is a device that compresses the low-pressure refrigerant in the refrigeration cycle until it reaches a high pressure.
  • the compressor 21 has a hermetically sealed structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a.
  • the compressor 21 has a suction pipe 31 connected to the suction side and a discharge pipe 32 connected to the discharge side.
  • the suction pipe 31 is a refrigerant pipe that connects the suction side of the compressor 21 and the four-way switching valve 22.
  • the discharge pipe 32 is a refrigerant pipe that connects the discharge side of the compressor 21 and the four-way switching valve 22.
  • the four-way switching valve 22 is a switching valve for switching the direction of refrigerant flow in the refrigerant circuit 10.
  • the four-way switching valve 22 causes the outdoor heat exchanger 23 to function as a radiator for the refrigerant compressed in the compressor 21 and the indoor heat exchanger 41 for the refrigerant that has radiated heat in the outdoor heat exchanger 23.
  • the suction side (here, the suction pipe 31) of the compressor 21 and the gas refrigerant communication pipe 6 side (here, the second gas refrigerant pipe 34) are connected (solid line of the four-way switching valve 22 in FIG. 1). See).
  • the four-way switching valve 22 causes the outdoor heat exchanger 23 to function as an evaporator of the refrigerant that has radiated heat in the indoor heat exchanger 41 during the heating operation, and the indoor heat exchanger 41 is compressed in the compressor 21. Switching to a heating cycle state that functions as a refrigerant radiator.
  • the four-way switching valve 22 is connected to the discharge side (here, the discharge pipe 32) of the compressor 21 and the gas refrigerant communication pipe 6 side (here, the second gas refrigerant pipe 34). (Refer to the broken line of the four-way switching valve 22 in FIG. 1).
  • the suction side of the compressor 21 here, the suction pipe 31
  • the gas side of the outdoor heat exchanger 23 here, the first gas refrigerant pipe 33
  • the first gas refrigerant pipe 33 is a refrigerant pipe connecting the four-way switching valve 22 and the gas side of the outdoor heat exchanger 23.
  • the second gas refrigerant pipe 34 is a refrigerant pipe that connects the four-way switching valve 22 and the gas-side closing valve 26.
  • the outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant radiator that uses outdoor air as a cooling source during cooling operation, and that functions as a refrigerant evaporator that uses outdoor air as a heating source during heating operation.
  • the outdoor heat exchanger 23 has a liquid side connected to the liquid refrigerant pipe 35 and a gas side connected to the first gas refrigerant pipe 33.
  • the liquid refrigerant pipe 35 is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the liquid refrigerant communication pipe 5 side.
  • the expansion valve 24 is a valve that depressurizes the high-pressure refrigerant of the refrigeration cycle radiated in the outdoor heat exchanger 23 to the low pressure of the refrigeration cycle during the cooling operation.
  • the expansion valve 24 is a valve that reduces the high-pressure refrigerant of the refrigeration cycle radiated in the indoor heat exchanger 41 to the low pressure of the refrigeration cycle during heating operation.
  • the expansion valve 24 is provided in a portion of the liquid refrigerant pipe 35 near the liquid side closing valve 25.
  • an electric expansion valve is used as the expansion valve 24.
  • the liquid side shutoff valve 25 and the gas side shutoff valve 26 are valves provided at connection ports with external devices and pipes (specifically, the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6).
  • the liquid side closing valve 25 is provided at the end of the liquid refrigerant pipe 35.
  • the gas side closing valve 26 is provided at the end of the second gas refrigerant pipe 34.
  • the outdoor unit 2 has an outdoor fan 36 for sucking outdoor air into the outdoor unit 2, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging the air to the outside. That is, the outdoor unit 2 includes an outdoor fan 36 as a fan that supplies outdoor air as a cooling source or a heating source of the refrigerant flowing through the outdoor heat exchanger 23 to the outdoor heat exchanger 23.
  • the outdoor fan 36 a propeller fan or the like driven by an outdoor fan motor 36a is used as the outdoor fan 36.
  • Refrigerant communication pipes 5 and 6 are refrigerant pipes constructed on site when the air conditioner 1 is installed at an installation location such as a building.
  • the refrigerant communication tubes 5 and 6 include a combination of the installation location and the outdoor unit 2 and the indoor unit 4. Depending on the installation conditions, those having various lengths and pipe diameters are used.
  • the air conditioner 1 can perform a cooling operation and a heating operation as basic operations.
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and is compressed until it reaches a high pressure in the refrigeration cycle, and then discharged.
  • the high-pressure gas refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 through the four-way switching valve 22.
  • the high-pressure gas refrigerant sent to the outdoor heat exchanger 23 radiates heat by exchanging heat with outdoor air supplied as a cooling source by the outdoor fan 36 in the outdoor heat exchanger 23 that functions as a refrigerant radiator. Become a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant radiated in the outdoor heat exchanger 23 is sent to the expansion valve 24.
  • the high-pressure liquid refrigerant sent to the expansion valve 24 is decompressed to the low pressure of the refrigeration cycle by the expansion valve 24 to become a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve 24 is sent to the indoor heat exchanger 41 through the liquid-side closing valve 25 and the liquid refrigerant communication pipe 5.
  • the low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchanger 41 evaporates in the indoor heat exchanger 41 by exchanging heat with indoor air supplied as a heating source by the indoor fan 42. 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 exchanger 41 is again sucked into the compressor 21 through the gas refrigerant communication pipe 6, the gas side closing valve 26 and the four-way switching valve 22.
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and is compressed until it reaches a high pressure in the refrigeration cycle, and then discharged.
  • the high-pressure gas refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 through the four-way switching valve 22, the gas side closing valve 26 and the gas refrigerant communication pipe 6.
  • the high-pressure gas refrigerant sent to the indoor heat exchanger 41 radiates heat by exchanging heat with indoor air supplied as a cooling source by the indoor fan 42 in the indoor heat exchanger 41 to become 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 exchanger 41 is sent to the expansion valve 24 through the liquid refrigerant communication pipe 5 and the liquid-side closing valve 25.
  • the high-pressure liquid refrigerant sent to the expansion valve 24 is decompressed to the low pressure of the refrigeration cycle by the expansion valve 24 to become a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve 24 is sent to the outdoor heat exchanger 23.
  • the low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 23 exchanges heat with the outdoor air supplied as a heating source by the outdoor fan 36 in the outdoor heat exchanger 23 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 23 is again sucked into the compressor 21 through the four-way switching valve 22.
  • FIG. 2 is a perspective view showing an appearance of the outdoor unit 2.
  • FIG. 3 is a plan view showing a state in which the top plate 57 of the outdoor unit 2 is removed.
  • FIG. 4 is a perspective view showing a state in which the top plate 57, the front plates 55 and 56, and the side plates 53 and 54 of the outdoor unit 2 are removed.
  • the wording means a direction and a surface when the surface on the fan blowing grill 55b side is a front surface unless otherwise specified.
  • the outdoor unit 2 has a structure (so-called trunk type structure) in which the inside of the unit casing 51 is partitioned into a blower chamber S1 and a machine chamber S2 by a partition plate 58 extending in the vertical direction.
  • the outdoor unit 2 is configured to discharge air from the front surface of the unit casing 51 after sucking outdoor air into the inside from a part of the back surface and side surface of the unit casing 51.
  • the outdoor unit 2 mainly includes a unit casing 51, a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, closing valves 25 and 26, and refrigerant pipes 31 to 35 connecting these devices.
  • the blower chamber S1 is formed near the left side surface of the unit casing 51 and the machine chamber S2 is formed near the right side surface of the unit casing 51 will be described, but the left and right sides may be reversed.
  • the unit casing 51 is formed in a substantially rectangular parallelepiped shape.
  • the unit casing 51 mainly includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, closing valves 25 and 26, and a refrigerant pipe connecting these devices.
  • the apparatus and piping which comprise the refrigerant circuit 10 containing 31-35, the outdoor fan 36, and the outdoor fan motor 36a are accommodated.
  • the unit casing 51 includes a bottom plate 52 on which the devices and piping 21 to 26, 31 to 35, the outdoor fan 36, and the like constituting the refrigerant circuit 10 are placed, a blower chamber side plate 53, a machine chamber side plate 54, It has a blower room side front plate 55, a machine room side front plate 56, a top plate 57, and two installation legs 59.
  • the bottom plate 52 is a plate-like member that constitutes the bottom surface portion of the unit casing 51.
  • the blower chamber side plate 53 is a plate-like member constituting the side surface portion (here, the left side surface portion) of the unit casing 51 near the fan chamber S1.
  • the lower part of the blower chamber side plate 53 is fixed to the bottom plate 52, and here, the front end portion thereof is an integral member with the left end portion of the blower chamber side front plate 55.
  • the blower chamber side plate 53 is formed with a side fan inlet 53 a for sucking outdoor air into the unit casing 51 from the side surface side of the unit casing 51 by the outdoor fan 36.
  • the blower chamber side plate 53 may be a separate member from the blower chamber side front plate 55.
  • the machine room side plate 54 is a plate-like member that constitutes a part of the side surface portion (here, the right side surface portion) of the unit casing 51 near the machine room S2 and the back surface portion of the unit casing 51 near the machine room S2. is there.
  • the lower part of the machine room side plate 54 is fixed to the bottom plate 52.
  • Outdoor air is passed into the unit casing 51 from the back side of the unit casing 51 by the outdoor fan 36 between the rear side end of the blower room side plate 53 and the end of the machine room side plate 54 on the blower chamber S1 side.
  • a rear fan inlet 53b for inhalation is formed.
  • the blower chamber side front plate 55 is a plate-like member that constitutes the front portion of the blower chamber S1 of the unit casing 51.
  • the lower portion of the blower chamber side front plate 55 is fixed to the bottom plate 52, and here, the left side end portion is an integral member with the front end portion of the blower chamber side plate 53.
  • the blower chamber side front plate 55 is provided with a fan outlet 55a for blowing the outdoor air sucked into the unit casing 51 by the outdoor fan 36 to the outside.
  • a fan blow grill 55b that covers the fan blow outlet 55a is provided on the front side of the blower chamber side front plate 55.
  • the blower chamber side front plate 55 may be a separate member from the blower chamber side plate 53.
  • the machine room side front plate 56 is a plate-like member that constitutes a part of the front part of the machine room S2 of the unit casing 51 and a part of the side part of the machine room S2 of the unit casing 51.
  • the machine room side front plate 56 has an end portion on the fan chamber S1 side fixed to an end portion on the machine room S2 side of the blower chamber side front plate 55, and an end portion on the back side on the front side of the machine room side plate 54. It is fixed to the end of the.
  • the top plate 57 is a plate-like member that constitutes the top surface portion of the unit casing 51.
  • the top plate 57 is fixed to the blower chamber side plate 53, the machine room side plate 54, and the blower chamber side front plate 55.
  • the partition plate 58 is a plate-like member that is arranged on the bottom plate 52 and extends in the vertical direction.
  • the partition plate 58 divides the inside of the unit casing 51 into left and right to form a blower chamber S1 near the left side and a machine chamber S2 near the right side.
  • the lower portion of the partition plate 58 is fixed to the bottom plate 52, the front end portion thereof is fixed to the blower chamber side front plate 55, and the rear end portion thereof is the side closer to the machine room S ⁇ b> 2 of the outdoor heat exchanger 23. It extends to the end.
  • the installation leg 59 is a plate-like member extending in the front-rear direction of the unit casing 51.
  • the installation leg 59 is a member fixed to the installation surface of the outdoor unit 2.
  • the outdoor unit 2 has two installation legs 59, one is arranged near the blower room S1, and the other is arranged near the machine room S2.
  • the outdoor fan 36 is a propeller fan having a plurality of blades, and faces the front surface of the unit casing 51 (here, the fan air outlet 55a) at a position on the front surface side of the outdoor heat exchanger 23 in the blower chamber S1.
  • the outdoor fan motor 36a is disposed between the outdoor fan 36 and the outdoor heat exchanger 23 in the front-rear direction in the blower chamber S1.
  • the outdoor fan motor 36 a is supported by a motor support base 36 b placed on the bottom plate 52.
  • the outdoor fan 36 is pivotally supported by an outdoor fan motor 36a.
  • the outdoor heat exchanger 23 is a heat exchanger panel having a substantially L shape in plan view, and is mounted on the bottom plate 52 along the side surface (here, the left side surface) and the back surface of the unit casing 51 in the blower chamber S1. Is placed.
  • the compressor 21 is a vertical cylindrical hermetic compressor, and is placed on the bottom plate 52 in the machine room S2.
  • FIG. 5 is a schematic perspective view of the outdoor heat exchanger 23.
  • FIG. 6 is a partially enlarged view of the heat exchange unit 60 of FIG.
  • the terms indicating directions and surfaces mean directions and surfaces based on the state in which the outdoor heat exchanger 23 is placed on the outdoor unit 2 unless otherwise specified.
  • the outdoor heat exchanger 23 mainly includes a heat exchanging unit 60 that exchanges heat between outdoor air and refrigerant, a refrigerant flow divider 70 provided on one end side (here, the right end side) of the heat exchanging unit 60, and an inlet / outlet header. 71 and an intermediate header 72, and a connection header 74 provided on the other end side (here, the left front end side) of the heat exchanging unit 60.
  • the outdoor heat exchanger 23 is an all-aluminum heat exchanger in which all of the refrigerant flow distributor 70, the inlet / outlet header 71, the intermediate header 72, the connection header 74, and the heat exchange unit 60 are made of aluminum or aluminum alloy. Is performed by brazing such as brazing in a furnace.
  • the heat exchanging unit 60 includes an upwind heat exchanging unit 61 that constitutes an upwind portion of the outdoor heat exchanger 23 and an upwind heat exchanging unit 62 that constitutes a downwind portion of the outdoor heat exchanger 23.
  • the heat exchangers 61 and 62 are arranged in two rows in the direction in which the outdoor air passes through the unit casing 51 generated by driving the outdoor fan 36.
  • the windward side heat exchange unit 61 is disposed closer to the side surface (here, the left side surface) and the back side of the unit casing 51 than the leeward side heat exchange unit 62.
  • the portion of the heat exchanging unit 60 that is located on the windward side near the fan suction ports 53 a and 53 b with respect to the direction in which the outdoor air passes is the windward heat exchanging unit 61.
  • the windward heat exchange part 61 has the windward main heat exchange part 61a which comprises the upper part of the outdoor heat exchanger 23, and the windward sub heat exchange part 61b which comprises the lower part of the outdoor heat exchanger 23. ing.
  • the leeward side heat exchanging unit 62 includes a leeward side main heat exchanging unit 62 a constituting the upper part of the outdoor heat exchanger 23 and a leeward side sub heat exchanging unit 62 b constituting the lower part of the outdoor heat exchanger 23. ing.
  • the heat exchanging unit 60 is an insertion fin type heat exchanging unit constituted by a large number of heat transfer tubes 63 made of flat tubes and a large number of heat transfer fins 66 made of insertion fins.
  • the heat transfer tube 63 is made of aluminum or aluminum alloy, and is a flat multi-hole tube having a flat surface 64 serving as a heat transfer surface and a large number of small internal flow paths 65 through which a refrigerant flows.
  • a large number of heat transfer tubes 63 are arranged in a plurality of stages at intervals along a predetermined tube step direction with the flat surfaces 64 facing each other, and one end in the longitudinal direction (here, the right end) is the inlet / outlet header 71 or the intermediate header.
  • the connection header 74 the connection header 74. That is, the large number of heat transfer tubes 63 are disposed between the inlet / outlet header 71 and the intermediate header 72 and the connection header 74.
  • the tube step direction means the vertical direction
  • the heat transfer tube 63 is arranged along the side surface (here, the left side surface) and the back surface of the unit casing 51. Therefore, the longitudinal direction of the heat transfer tube 63 means the horizontal direction along the side surface (here, the left side surface) and the back surface of the unit casing 51.
  • the heat transfer fins 66 are made of aluminum or an aluminum alloy, and a plurality of heat transfer fins 66 are arranged along the longitudinal direction of the heat transfer tube 63 at intervals.
  • the heat transfer fins 66 are formed with a number of notches 67 for inserting the heat transfer tubes 63 extending along the tube insertion direction that intersects the tube step direction and the longitudinal direction of the heat transfer tubes 63.
  • the tube step direction is the vertical direction
  • the longitudinal direction of the heat transfer tube 63 is the horizontal direction along the side surface (here, the left side surface) and the back surface of the unit casing 51
  • the tube insertion direction is the heat transfer tube 63.
  • the large number of heat transfer tubes 63 include a heat transfer tube group constituting the windward main heat exchange unit 61a, a heat transfer tube group constituting the windward sub heat exchange unit 61b, and a leeward main heat exchange unit 62a.
  • the heat transfer tube group is divided into a heat transfer tube group and a heat transfer tube group constituting the leeward side sub heat exchange unit 62b.
  • the large number of heat transfer fins 66 include a group of fins that form a common windward row for the windward main heat exchange unit 61a and the windward sub heat exchange unit 61b, and the leeward main heat exchange unit 62a and the leeward side sub.
  • the heat exchange section 62b is divided into fin groups that form a common leeward row.
  • the refrigerant distributor 70 is connected between the liquid refrigerant pipe 35 and the lower part of the inlet / outlet header 71.
  • the refrigerant flow divider 70 is a member made of aluminum or aluminum alloy and extending in the vertical direction.
  • the refrigerant distributor 70 divides the refrigerant flowing in through the liquid refrigerant pipe 35 and guides it to the lower part of the inlet / outlet header 71, or joins the refrigerant flowing in through the lower part of the inlet / outlet header 71 and guides it to the liquid refrigerant pipe 35.
  • the entrance / exit header 71 is provided on one end side (here, the right end side) of the windward heat exchange unit 61 in the heat exchange unit 60.
  • the inlet / outlet header 71 is connected to one end (here, the right end) of the heat transfer pipe 63 that constitutes the upwind heat exchange unit 61.
  • the entrance / exit header 71 is a member made of aluminum or aluminum alloy and extending in the vertical direction.
  • the internal space of the entrance / exit header 71 is vertically partitioned by a baffle (not shown), and the upper space communicates with one end (here, the right end) of the heat transfer pipe 63 constituting the upwind main heat exchange section 61a.
  • the lower space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the windward side sub heat exchanging portion 61b.
  • the upper part of the entrance / exit header 71 is connected to the 1st gas refrigerant pipe 33, and exchanges a refrigerant
  • the lower part of the inlet / outlet header 71 is connected to the refrigerant distributor 70 so that the refrigerant is exchanged with the refrigerant distributor 70.
  • the intermediate header 72 is provided on one end side (here, the right end side) of the leeward heat exchange unit 62 in the heat exchange unit 60.
  • the intermediate header 72 is connected to one end (here, the right end) of the heat transfer tube 63 that constitutes the leeward heat exchange unit 62.
  • the intermediate header 72 is a member that is formed of aluminum or an aluminum alloy and extends in the vertical direction.
  • the internal space of the intermediate header 72 is vertically partitioned by a baffle (not shown), and the upper space communicates with one end (here, the right end) of the heat transfer pipe 63 that constitutes the leeward main heat exchange section 62a.
  • the lower space communicates with one end (here, the right end) of the heat transfer tube 63 constituting the leeward side sub heat exchanging portion 62b.
  • the upper space and the lower space of the intermediate header 72 are partitioned into a plurality of spaces by baffles (not shown) according to the number of passes of the heat exchanging unit 60, and the upper space and the lower space through the intermediate connecting pipe 73 and the like. It communicates with the space.
  • the intermediate header 72 exchanges refrigerant between the leeward main heat exchange unit 62a and the leeward sub heat exchange unit 62b.
  • connection header 74 is provided on the other end side (here, the left front end side) of the heat exchange unit 60.
  • the connection header 74 is connected to the other end (here, the left front end) of the heat transfer tube 63 constituting the heat exchanging unit 60.
  • the connection header 74 is a member made of aluminum or aluminum alloy and extending in the vertical direction.
  • the connection header 74 includes the other end (here, the left front end) of the heat transfer tube 63 constituting the windward heat exchange unit 61 and the other end (here, the left front end) of the heat transfer tube 63 constituting the leeward side heat exchange unit 62. ) Are connected to each other.
  • the connection header 74 exchanges a refrigerant
  • the outdoor heat exchanger 23 having such a configuration functions as a refrigerant evaporator
  • the refrigerant flowing from the liquid refrigerant pipe 35 is transferred to the refrigerant flow divider 70 as indicated by the arrows indicating the flow of the refrigerant in FIG. And through the lower part of the inlet / outlet header 71, it is guided to the windward side sub heat exchange part 61b.
  • coolant which passed the windward sub heat exchange part 61b is guide
  • coolant which passed the leeward side sub heat exchange part 62b is guide
  • coolant which passed the leeward side main heat exchange part 62a is guide
  • the refrigerant that has passed through the windward main heat exchanging portion 61 a flows out to the first gas refrigerant pipe 33 through the upper part of the inlet / outlet header 71. In the course of such a refrigerant flow, the refrigerant evaporates by heat exchange with outdoor air.
  • the refrigerant flowing from the first gas refrigerant pipe 33 passes through the upper part of the inlet / outlet header 71 as shown by the arrows indicating the refrigerant flow in FIG. Then, it is guided to the windward main heat exchanging part 61a.
  • coolant which passed the windward main heat exchange part 61a is guide
  • coolant which passed the leeward side main heat exchange part 62a is guide
  • coolant which passed the leeward side sub heat exchange part 62b is guide
  • the refrigerant that has passed through the windward side sub heat exchanging portion 61 b flows out to the liquid refrigerant pipe 35 through the lower portion of the inlet / outlet header 71 and the refrigerant distributor 70.
  • the refrigerant radiates heat by heat exchange with the outdoor air.
  • FIG. 7 is a partially enlarged view showing a state in which the heat exchanging unit 60 in FIG. 6 is viewed from the direction along the longitudinal direction of the heat transfer tube 63.
  • FIG. 8 is a view showing a main part of the heat transfer fin 66.
  • 9 is a cross-sectional view taken along the line II of FIG. 10 is a cross-sectional view taken along the line II-II, a cross-sectional view taken along the line III-III, and a cross-sectional view taken along the line IV-IV in FIG.
  • FIG. 11 is a view of FIG. 8 viewed from the front side in the tube insertion direction and a view viewed from the back side in the tube insertion direction.
  • 12 is a cross-sectional view taken along the line VV of FIG.
  • the heat transfer fin 66 is a plate-like fin that is long in one direction (here, vertically long) formed by pressing a plate material made of aluminum or aluminum alloy.
  • a large number of notches 67 of the heat transfer fins 66 are formed at predetermined intervals in the tube step direction of the heat transfer fins 66.
  • a portion of the cutout portion 67 that contacts the heat transfer tube 63 in a state where the heat transfer tube 63 is inserted constitutes a tube insertion portion 80.
  • the tube insertion portion 80 has a vertical width substantially equal to the width between the flat surfaces 64 of the heat transfer tubes 63, and a horizontal width substantially equal to the width in the direction intersecting the flat surfaces 64 of the flat tubes 63. It has become.
  • the peripheral edge portion of the tube insertion portion 80 protrudes from the base surface 66a of the heat transfer fin 66 toward one side in the longitudinal direction of the heat transfer tube 63 (here, the front side in FIG.
  • the base surface 66a of the heat transfer fin 66 means the fin surface of the heat transfer fin 66 fin in a state before the formation of each part including the tube insertion portion 80.
  • the heat transfer tube 63 is inserted into the notch 67 and guided to the tube insertion portion 80 which is a part of the notch 67, and is joined to the peripheral edge of the tube insertion portion 80 by brazing.
  • the heat transfer fins 66 are formed with a plurality of fin intermediate portions 81 sandwiched between the tube insertion portions 80 adjacent in the tube step direction.
  • the heat transfer fin 66 has a plurality of fin intermediate portions 81 from the front side in the tube insertion direction (here, the windward side with respect to the passage direction of outdoor air) toward the front side in the tube insertion direction. Fin front portions 82 extending respectively are formed. Further, the heat transfer fin 66 has a plurality of fin intermediate portions 81 extending from the end on the back side in the tube insertion direction (here, the leeward side with respect to the passage direction of outdoor air) toward the back side in the tube insertion direction. A fin back portion 83 extending continuously from the back end of the plurality of fin intermediate portions 81 in the tube insertion direction is formed.
  • heat transfer fin 66 for example, it is conceivable to form a plurality of waffles having a mountain-shaped inclined surface along the tube insertion direction.
  • the heat transfer fins 66 buckle at the valleys between the waffles adjacent in the tube insertion direction. May occur. That is, when the heat transfer tube 63 is inserted into the cutout portion 67 of the heat transfer fin 66, the valley portion between the waffles becomes a V-shaped fold, and the heat transfer fin 66 may be bent. For this reason, it is necessary to be able to suppress the occurrence of buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67.
  • the portion of the notch 67 sandwiching the fin front portion 82 guides the heat transfer tube 63 to the tube insertion portion 80 when the heat transfer tube 63 is inserted into the heat transfer fin 66.
  • the heat transfer tubes 63 are in contact with the fin intermediate portion 81 but are not in contact with the fin front portion 82.
  • the heat transfer fins 66 may be buckled at the boundary between the fin intermediate portion 81 and the fin front portion 82.
  • a boundary portion between the fin intermediate portion 81 and the fin front portion 82 is a starting point.
  • the heat transfer fins 66 may be bent.
  • the heat transfer fin 66 is devised as follows.
  • a pedestal portion 84 that forms a flat surface 85 is formed in a plurality of fin intermediate portions 81 by causing the heat transfer fins 66 to bulge.
  • the pedestal portion 84 is disposed near the center of the fin intermediate portion 81 in the tube insertion direction.
  • the entire flat surface 85 is arranged at a position protruding from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). ing.
  • the pedestal portion 84 forming the flat surface 85 is formed in the fin intermediate portion 81, unlike the case where the waffle is formed in the heat transfer fin 66, the notch portion 67 of the heat transfer fin 66 is formed.
  • the heat transfer tube 63 is inserted, there is no V-shaped crease such as a valley between the waffles. For this reason, it becomes possible to improve the fin strength in the direction intersecting the tube insertion direction, and to suppress the occurrence of buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67. .
  • the protruding height of the pedestal portion 84 from the base surface 66a of the heat transfer fin 66 is set to be higher than the protruding height of the tube insertion portion 80. For this reason, the effect which improves fin intensity
  • the flat surface 85 connects the first side 85a and the second side 85b that are parallel to each other extending in the tube insertion direction, and the end portions of the first side 85a and the second side 85b on the near side in the tube insertion direction. It has a third side 85c and a fourth side 85d that connects the ends of the first side 85a and the second side 85b on the back side in the tube insertion direction.
  • the first side 85a is along one side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the upper side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged.
  • the second side 85b is arranged along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8).
  • the flat surface 85 formed by the pedestal portion 84 has a substantially square shape.
  • the fin strength in the direction intersecting the tube insertion direction can be improved by the first side 85a and the second side 85b, which are a part of four sides having a substantially rectangular shape.
  • the ends of the sides 85a to 85d are connected so as to form sharp corners. However, even if the corners are chamfered or the corners are rounded to make the corners smooth, the ends may be smooth. Good.
  • first side 85a and the second side 85b have the same length in the tube insertion direction and are arranged at the same position in the tube insertion direction, so the third side 85c and the fourth side 85d are also The lengths in the direction intersecting the tube insertion direction (tube step direction) are the same, and are arranged at positions in the direction intersecting the same tube insertion direction.
  • the flat surface 85 has a rectangular shape including two sides 85a and 85b parallel to the tube insertion direction and two sides 85c and 85d parallel to the tube step direction. For this reason, not only the fin strength in the direction intersecting the tube insertion direction by the first side 85a and the second side 85b but also the fin strength in the tube insertion direction can be improved by the third side 85c and the fourth side 85d. .
  • the heat transfer fins 66 are formed by cutting up the heat transfer fins 66 with first fin tabs 90 for maintaining the distance between the heat transfer fins 66 adjacent in the longitudinal direction of the heat transfer tubes 63.
  • the first fin tab 90 is disposed across the boundary between the fin intermediate portion 81 and the fin front portion 82.
  • the first fin tab 90 is a substantially square-shaped piece that protrudes from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). is there.
  • the first fin tab 90 is in contact with the base surface 66a of the heat transfer fin 66 adjacent in the longitudinal direction of the heat transfer tube 63, so that the interval between the heat transfer fins 66 is maintained.
  • the first fin tab 90 is disposed in the vicinity of the center of the heat transfer fin 66 in the tube step direction and on the front side of the pedestal portion 84 in the tube insertion direction.
  • the heat transfer tubes 63 are inserted and joined to the heat transfer fins 66.
  • the occurrence of buckling of the heat transfer fins 66 at the boundary portion between the fin intermediate portion 81 and the fin front portion 82 can be suppressed. .
  • the heat transfer fin 66 of the heat transfer fin 66 at the boundary between the fin intermediate portion 81 and the fin front portion 82 is provided. Since the decrease in fin strength in the direction intersecting the tube insertion direction cannot be suppressed, the boundary between the fin intermediate portion 81 and the fin front portion 82 in the state where the heat transfer tube 63 is inserted and joined to the heat transfer fin 66. It is difficult to suppress the occurrence of buckling of the heat transfer fins 66 in the section. This also applies to the case where the fin tab is formed in the fin intermediate portion 81 and is not disposed at the boundary portion with the fin front portion 82.
  • the first fin tab 90 is disposed so as to form a wall portion along the tube insertion direction. For this reason, here, since the first fin tab 90 is arranged in a direction intersecting with the boundary between the fin intermediate portion 81 and the fin front portion 82, the first fin tab 90 intersects the tube insertion direction of the heat transfer fin 66. The effect which suppresses the fall of the fin strength of a direction can be heightened. And since the 1st fin tab 90 is arrange
  • the fin fin 83 has a second fin tab 91 for keeping the space between the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tube 63. Is formed.
  • the second fin tab 91 is a substantially square-shaped piece projecting from the base surface 66a of the heat transfer fin 66 to the one side in the longitudinal direction of the heat transfer tube 63 (here, the front side of the paper in FIGS. 7 and 8). is there.
  • the second fin tab 91 is in contact with the base surface 66a of the heat transfer fin 66 adjacent in the longitudinal direction of the heat transfer tube 63, so that the interval between the heat transfer fins 66 is maintained.
  • the second fin tab 91 is disposed in the vicinity of the center of the heat transfer fin 66 in the tube step direction and on the back side of the pedestal portion 84 in the tube insertion direction. Thereby, here, the place where the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tube 66 abut can be increased, and the retention performance of the fin interval can be improved.
  • the second fin tab 91 is arranged so as to form a wall portion along the tube insertion direction. For this reason, since the 2nd fin tab 91 will be arrange
  • first fin tab 90 and the second fin tab 91 are arranged so as not to overlap each other when the heat transfer fin 66 is viewed from the tube insertion direction.
  • the first fin tab 90 is cut and raised so that an opening 90a is formed on one side of the first fin tab 90 in the tube step direction (here, the upper side in FIG. 7 and FIG. 8). Is disposed at a position shifted from the center of the heat transfer fin 66 in the tube step direction to the other side in the tube step direction (here, the lower side of the drawing in FIGS. 7 and 8).
  • the second fin tab 91 is cut and raised so that an opening 91a is formed on the other side of the second fin tab 91 in the tube step direction (here, on the lower side of the paper in FIGS. 7 and 8).
  • the two fin tabs 91 are arranged at positions shifted from the center of the heat transfer fin 66 in the tube step direction to one side in the tube step direction (here, the upper side of the drawing in FIGS. 7 and 8).
  • the first fin tab 90 is disposed at a position shifted to the other side of the second fin tab 91 across the center of the heat transfer fin 66 in the tube step direction. It has been done.
  • the degree of parallelism between the heat transfer fins 66 adjacent to each other in the longitudinal direction of the heat transfer tubes 63 can be increased, and the fin gap holding performance can be further increased. Can be improved.
  • ribs 92 and 96 are formed on the heat transfer fins 66 by causing the heat transfer fins 66 to bulge on the front side and the back side of the base 85 in the tube insertion direction.
  • the near side rib portion 92 disposed on the near side in the tube insertion direction of the pedestal portion 85 intersects with the near side first rib portion 93 and the near side second rib 94 extending along the tube insertion direction in the tube insertion direction.
  • a near-side third rib 95 extending in the direction (tube step direction).
  • the back side rib part 96 arrange
  • the rib portions 92 and 96 bulge from the base surface 66a of the heat transfer fin 66 to one side in the longitudinal direction of the heat transfer tube 63 (here, the front side in FIG. 7 and FIG. 8).
  • the near-side first rib portion 93 is along one side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the upper side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged.
  • the front-side first rib portion 93 is formed in a mountain shape whose ridge line 93 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 93a of the near-side first rib portion 93 is disposed in parallel to the outdoor air passing direction.
  • the front-side second rib 94 is along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged.
  • the front side second rib portion 94 is formed in a mountain shape whose ridgeline 94 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 94a of the front-side second rib portion 94 is disposed in parallel to the outdoor air passing direction.
  • front side first rib portion 93 and the front side second rib portion 94 extend not only to the fin intermediate portion 81 but also to the fin front portion 82. That is, the near side first rib portion 93 and the near side second rib portion 94 are disposed across the boundary between the fin intermediate portion 81 and the fin near portion 82.
  • the near-side third rib 95 is arranged so as to connect ends of the near-side first rib portion 93 and the near-side second rib portion 94 on the pedestal portion 85 side in the tube insertion direction.
  • the front side third rib 95 is formed in a mountain shape parallel to the direction in which the ridge line 95 a intersects the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 95a of the front-side third rib 95 is disposed so as to intersect the outdoor air passage direction.
  • the ridgeline 93a of the near side first rib part 93, the ridgeline 95a of the near side third rib 95, and the ridgeline 94a of the near side second rib part 94 are connected in a U-shape.
  • the front side first rib portion 93, the front side third rib 95 and the front side second rib portion 94 as a whole are formed in a U-shaped mountain shape. Further, the edge 95 b on the pedestal portion 84 side of the front side third rib 95 coincides with the third side 85 c of the flat surface 85 of the pedestal portion 84. That is, the edge 95b on the pedestal portion 84 side of the front side third rib 95 is not located on the base surface 66a of the heat transfer fin 66 but is located on the flat surface 85 protruding from the base surface 66a.
  • the front side third rib 95 (that is, the front side rib portion 92 including the front side first rib portion 93 and the front side second rib portion 94) is connected to the third side 85c of the flat surface 85 of the pedestal portion 84. They are arranged continuously. Further, the front rib portion 92 is disposed so as to surround the first fin tab 90. Here, the three sides excluding the front side of the first fin tab 90 in the tube insertion direction are surrounded. The front side rib portion 92 is disposed at a position where the ridgelines 93 a, 94 a, and 95 a protrude from the flat surface 85 of the pedestal portion 84 than the base surface 66 a of the heat transfer fin 66.
  • the back side first rib portion 97 and the back side second rib 98 are formed on one side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the paper surface of each fin intermediate portion 81 in FIGS. 7 and 8). It is arranged along the upper tube insertion part 60).
  • the back side first rib portion 97 is formed in a mountain shape whose ridgeline 97 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 97a of the back side first rib portion 97 is arranged in parallel to the outdoor air passing direction.
  • the back side second rib 98 is along the other side of the pair of tube insertion portions 60 sandwiching the fin intermediate portion 81 (here, the tube insertion portion 60 on the lower side of the paper in each fin intermediate portion 81 in FIGS. 7 and 8). Are arranged.
  • the back side second rib portion 98 is formed in a mountain shape whose ridgeline 98 a is parallel to the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 98a of the back side second rib portion 98 is arranged in parallel to the outdoor air passage direction.
  • back side first rib portion 97 and the back side second rib portion 98 extend not only to the fin intermediate portion 81 but also to the fin back portion 83. That is, the back side first rib portion 97 and the back side second rib portion 98 are disposed across the boundary portion between the fin intermediate portion 81 and the fin back portion 83.
  • the back side third rib 99 is arranged so as to connect ends of the back side first rib part 97 and the back side second rib part 98 on the base part 85 side in the tube insertion direction.
  • the back side third rib 99 is formed in a mountain shape parallel to the direction in which the ridge line 99 a intersects the tube insertion direction of the heat transfer fins 66. That is, the ridgeline 99a of the back side third rib 99 is disposed so as to intersect the outdoor air passing direction.
  • the ridgeline 97a of the back side first rib portion 97, the ridgeline 99a of the backside third rib 99, and the ridgeline 98a of the backside second rib portion 98 are connected in a U-shape, thereby
  • the back side first rib part 97, the back side third rib 99, and the back side second rib part 98 as a whole (that is, the back side rib part 96) are formed in a U-shaped mountain shape.
  • the edge 99 b on the pedestal portion 84 side of the back side third rib 99 coincides with the fourth side 85 d of the flat surface 85 of the pedestal portion 84.
  • the edge 99b of the back side third rib 99 on the pedestal portion 84 side is not positioned on the base surface 66a of the heat transfer fin 66 but is positioned on the flat surface 85 protruding from the base surface 66a.
  • the back side third rib 99 (that is, the back side rib part 96 including the back side first rib part 97 and the back side second rib part 98) is connected to the fourth side 85d of the flat surface 85 of the pedestal part 84. They are arranged continuously.
  • the back rib portion 96 is disposed so as to surround the second fin tab 91.
  • the three sides excluding the near side of the second fin tab 91 in the tube insertion direction are surrounded.
  • the back side rib part 96 is arrange
  • the rib portions 92 and 96 (specifically, the first and second rib portions 93 and 94) extending along the tube insertion direction toward the front side and the back side of the base portion 84 in the tube insertion direction. , 97, 98) are arranged continuously with the third side 85c and the fourth side 85d of the flat surface 85.
  • the rib portions 92 and 96 can be integrated with the pedestal portion 84 so that the third side 85c and the fourth side 85d of the pedestal portion 84 do not fold.
  • inner side of the pipe insertion direction of the base part 84 and the base part 84 can be improved.
  • the rib portions 93 and 96 (specifically, the first and second rib portions 93, 94, 97, and 98) are connected to the boundary portion between the fin intermediate portion 81 and the fin front portion 82. And it arrange
  • the heat transfer fin 66 since the near-side rib portion 93 surrounding the first fin tab 90 is formed in the heat transfer fin 66, the heat transfer fin 66 at both ends where the first fin tab 90 is cut and raised is formed. A decrease in fin strength can be suppressed.
  • the pedestal portion 84 is formed on the heat transfer fin 66, but nothing is formed on the flat surface 85.
  • the present invention is not limited to this.
  • a louver is formed by cutting up the heat transfer fins 66 on the flat surface 85 of the pedestal portion 84 for the purpose of improving the heat transfer performance. 86 may be formed.
  • the louver 86 is formed on the pedestal portion 84, for example, a portion forming the louver of the fin intermediate portion 81 compared to a case where the louver is formed in a portion where the waffle of the fin intermediate portion 81 is not formed.
  • the fin strength in the direction intersecting the tube insertion direction can be improved.
  • the louver 86 having a large size can be provided as compared with the case where the louver is formed in the waffle. For this reason, the heat transfer performance can be improved while suppressing buckling of the heat transfer fins 66 when the heat transfer tubes 63 are inserted into the notches 67 of the heat transfer fins 66.
  • the first fin tabs 90 are formed of the plurality of fin front portions 82 and the corresponding plurality of fin intermediate portions 81 arranged along the tube step direction. I try to place them all.
  • the present invention is not limited to this.
  • the first fin tabs 90 are arranged in a plurality of stages of the plurality of fin front portions 82 and the corresponding plurality of fin intermediate portions 81. Also good.
  • the 1st fin tab 90 is arrange
  • the amount of condensed water retained by the fin tab 90 can be reduced, and the drainage performance of the heat transfer fin 66 can be ensured.
  • the second fin tabs 91 may be arranged in a plurality of stages as in the first fin tab 90.
  • the front side rib portion 92 surrounds the three sides except the front side in the tube insertion direction of the first fin tab 90, but is not limited thereto. It is not something.
  • the front rib portion 92 may surround four sides including the front side of the first fin tab 90 in the tube insertion direction.
  • the fin front portion 82 is disposed on the windward side with respect to the outdoor air passage direction, and the fin back portion 83 is disposed with respect to the outdoor air passage direction.
  • the present invention is not limited to this, and the fin front portion 82 is disposed on the leeward side with respect to the outdoor air passage direction, and the fin back portion 83 is disposed with respect to the outdoor air passage direction. May be arranged on the windward side.
  • the protruding height from the base surface 66a of the heat transfer fin 66 of the pedestal portion 84 is set to be higher than the protruding height of the tube insertion portion 80.
  • the present invention is not limited to this, and the protruding height of the pedestal portion 84 may be lower than the protruding height of the tube insertion portion 80.
  • the fin front portion 82 exists in the heat transfer fin 66, but is not limited thereto, and the fin front portion 82 exists. Instead, the front end of the fin intermediate portion 81 in the tube insertion direction may be the front end of the heat transfer fin 66 in the tube insertion direction.
  • a heat exchanger in which the heat transfer tubes 63 are arranged in two rows in the outdoor air passage direction is taken as an example, but the present invention is not limited thereto. It may be one row, or three or more rows.
  • the present invention is widely applicable to heat exchangers having a plurality of flat tubes and a plurality of insertion fins.

Landscapes

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

Abstract

Selon l'invention, un tube aplati (63) est disposé suivant une direction épaulement de tube. Des ailettes d'insertion (66) sont telles qu'est formée une pluralité de parties encoche (67) se prolongeant dans une direction pénétration de tube croisant la direction épaulement de tube et la direction longitudinale du tube aplati (63), et sont disposées suivant la direction longitudinale du tube aplati (63). Une portion des parties encoche (67) venant en contact avec le tube aplati (63) dans un état d'insertion du tube aplati (63), constitue des parties pénétration de tube (80). Dans une pluralité de parties intermédiaires d'ailette (81) enserrée entre les parties pénétration de tube (80) adjacentes dans la direction épaulement de tube parmi les ailettes d'insertion (66), une partie base (84) formant une face plane (85), est formée par dilatation des ailettes d'insertion (66).
PCT/JP2015/078907 2014-10-27 2015-10-13 Échangeur de chaleur WO2016067907A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201580056296.1A CN107076525B (zh) 2014-10-27 2015-10-13 热交换器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-217916 2014-10-27
JP2014217916A JP6036788B2 (ja) 2014-10-27 2014-10-27 熱交換器

Publications (1)

Publication Number Publication Date
WO2016067907A1 true WO2016067907A1 (fr) 2016-05-06

Family

ID=55857248

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/078907 WO2016067907A1 (fr) 2014-10-27 2015-10-13 Échangeur de chaleur

Country Status (3)

Country Link
JP (1) JP6036788B2 (fr)
CN (1) CN107076525B (fr)
WO (1) WO2016067907A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3315876A4 (fr) * 2016-08-09 2018-11-21 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération pourvu d'un échangeur de chaleur
CN110612425A (zh) * 2017-07-03 2019-12-24 大金工业株式会社 热交换器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003161588A (ja) * 2001-11-27 2003-06-06 Hitachi Ltd 熱交換器及びこれを備えた空気調和機
WO2005010442A1 (fr) * 2003-07-28 2005-02-03 Matsushita Electric Industrial Co., Ltd. Climatiseur
JP2012163320A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
JP2012233680A (ja) * 2011-04-22 2012-11-29 Mitsubishi Electric Corp フィンチューブ型熱交換器及び冷凍サイクル装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL8100334A (nl) * 1980-01-28 1981-08-17 Lummus Co Buis met plaatvormige ribben en warmtewisselaar die met zulke ribben is uitgerust.
JP3864916B2 (ja) * 2002-08-29 2007-01-10 株式会社デンソー 熱交換器
JP2011202820A (ja) * 2010-03-24 2011-10-13 Mitsubishi Electric Corp 熱交換器用フィンおよび熱交換器
AU2012208126B2 (en) * 2011-01-21 2015-07-02 Daikin Industries, Ltd. Heat exchanger and air conditioner
JP5177307B2 (ja) * 2011-01-21 2013-04-03 ダイキン工業株式会社 熱交換器
JP2013245884A (ja) * 2012-05-28 2013-12-09 Panasonic Corp フィンチューブ熱交換器
WO2014091536A1 (fr) * 2012-12-10 2014-06-19 三菱電機株式会社 Dispositif d'échange de chaleur à tube plat

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003161588A (ja) * 2001-11-27 2003-06-06 Hitachi Ltd 熱交換器及びこれを備えた空気調和機
WO2005010442A1 (fr) * 2003-07-28 2005-02-03 Matsushita Electric Industrial Co., Ltd. Climatiseur
JP2012163320A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
JP2012233680A (ja) * 2011-04-22 2012-11-29 Mitsubishi Electric Corp フィンチューブ型熱交換器及び冷凍サイクル装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3315876A4 (fr) * 2016-08-09 2018-11-21 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération pourvu d'un échangeur de chaleur
CN110612425A (zh) * 2017-07-03 2019-12-24 大金工业株式会社 热交换器
CN110612425B (zh) * 2017-07-03 2021-03-09 大金工业株式会社 热交换器

Also Published As

Publication number Publication date
CN107076525B (zh) 2018-03-09
CN107076525A (zh) 2017-08-18
JP2016084975A (ja) 2016-05-19
JP6036788B2 (ja) 2016-11-30

Similar Documents

Publication Publication Date Title
JP5962734B2 (ja) 熱交換器
US9328973B2 (en) Heat exchanger and air conditioner
US9568221B2 (en) Indoor unit for air conditioning device
JP6897372B2 (ja) 熱交換器
JP5987889B2 (ja) 熱交換器
JP5447569B2 (ja) 空気調和装置の熱交換器及び空気調和装置
EP3078930A1 (fr) Échangeur de chaleur et climatiseur l'utilisant
US20210041115A1 (en) Indoor heat exchanger and air conditioning apparatus
WO2018056209A1 (fr) Échangeur de chaleur
WO2018235215A1 (fr) Échangeur de chaleur, dispositif à cycle frigorifique et climatiseur
WO2016076259A1 (fr) Échangeur de chaleur
JP6036788B2 (ja) 熱交換器
JP2017120134A (ja) 熱交換器
JP7190579B2 (ja) 熱交換器において使用されるフィン、該フィンを有する熱交換器、及び該熱交換器を有する冷凍サイクル装置
JP7137092B2 (ja) 熱交換器
JP7089187B2 (ja) 熱交換器及び空気調和装置
CN111247386B (zh) 热交换器和具有该热交换器的空调装置
JP6569525B2 (ja) 熱交換器
JP6340583B2 (ja) 熱交換器
JP2013113517A (ja) 熱交換器および空気調和装置の室外ユニット

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: 15855065

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: 15855065

Country of ref document: EP

Kind code of ref document: A1