WO2021006336A1 - Heat exchanger and heat exchange unit - Google Patents

Heat exchanger and heat exchange unit Download PDF

Info

Publication number
WO2021006336A1
WO2021006336A1 PCT/JP2020/027038 JP2020027038W WO2021006336A1 WO 2021006336 A1 WO2021006336 A1 WO 2021006336A1 JP 2020027038 W JP2020027038 W JP 2020027038W WO 2021006336 A1 WO2021006336 A1 WO 2021006336A1
Authority
WO
WIPO (PCT)
Prior art keywords
opening
heat exchange
heat exchanger
heat
exchange section
Prior art date
Application number
PCT/JP2020/027038
Other languages
French (fr)
Japanese (ja)
Inventor
祥志 松本
透 安東
智己 廣川
秀之 日下
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 CN202090000706.7U priority Critical patent/CN217635915U/en
Priority to EP20836392.9A priority patent/EP3992564B1/en
Publication of WO2021006336A1 publication Critical patent/WO2021006336A1/en

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • 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
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/0273—Cores having special shape, e.g. curved, annular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0064—Vaporizers, e.g. evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • F28F2270/02—Thermal insulation; Thermal decoupling by using blind conduits

Definitions

  • This disclosure relates to heat exchangers and heat exchange units.
  • Patent Document 1 discloses a heat exchanger. This heat exchanger is provided in the indoor unit of the air conditioner and exchanges heat with the refrigerant for the air sucked into the indoor unit. During the cooling operation in which the heat exchanger functions as an evaporator, the moisture in the air condenses on the surface of the fins of the heat exchanger, and the generated condensed water flows down along the fins.
  • the heat transfer tube arranged at the lowermost part of the heat exchanger becomes wet for a long time and is more easily corroded than other heat transfer tubes. If the heat transfer tube is corroded, the refrigerant may leak from the heat transfer tube, and the reliability of the heat exchanger is impaired.
  • the purpose of this disclosure is to improve the reliability of heat exchangers and heat exchange units.
  • the first aspect of the present disclosure is a plurality of plate shapes in which a plurality of heat transfer tubes (40) arranged parallel to each other and a plurality of tube openings (46) for inserting the heat transfer tubes (40) are formed.
  • the target is a heat exchanger equipped with fins (45).
  • the fins (45) are arranged so that the longitudinal direction is in the vertical direction, and the opening rows are composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45).
  • the pipe opening (46) having only one (50) and being located at the lowermost position in the opening row (50) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted. It is a feature.
  • the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46).
  • the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to this aspect, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
  • a second aspect of the present disclosure is a plurality of plate shapes in which a plurality of heat transfer tubes (40) arranged in parallel with each other and a plurality of tube openings (46) for inserting the heat transfer tubes (40) are formed.
  • the target is a heat exchanger equipped with fins (45).
  • the fins (45) are arranged so that the longitudinal direction is in the vertical direction, and the opening rows are composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45).
  • the tube opening (46) having a plurality of (51a, 52a, 51b, 52b) and located at the lowermost position in each of the plurality of opening rows (51a, 52a, 51b, 52b) is the heat transfer tube (40). Is a non-insertion opening (47) through which is not inserted.
  • each fin (45) is provided with a plurality of opening rows (51a, 52a, 51b, 52b).
  • the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46).
  • the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to this aspect, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
  • the third aspect of the present disclosure is characterized in that, in the first or second aspect, the material of the heat transfer tube (40) is an aluminum alloy.
  • a heat transfer tube (40) made of an aluminum alloy is provided in the heat exchanger (30).
  • Aluminum has a higher ionization tendency than copper and is generally more susceptible to corrosion than copper. According to this aspect, the corrosion of the heat transfer tube (40) can be suppressed in the heat exchanger (30) provided with the heat transfer tube (40) made of an aluminum alloy, which is more easily corroded than the heat transfer tube made of copper.
  • a fourth aspect of the present disclosure is characterized in that, in the third aspect, the heat transfer tube (40) has a flat shape having a width longer than a thickness.
  • the heat exchanger is provided with a flat-shaped heat transfer tube having a width longer than the thickness.
  • a heat transfer tube (40) having such a flat shape is more likely to retain condensed water on its surface than a circular tubular heat transfer tube. According to this aspect, corrosion of the heat transfer tube (40) can be suppressed in the heat exchanger (30) provided with the flat-shaped heat transfer tube (40) in which condensed water tends to stay as compared with the circular tubular heat transfer tube. ..
  • a fifth aspect of the present disclosure is, in any one of the first to fourth aspects, the tubular shape extending along the longitudinal direction of the fin (45) and connected to the heat transfer tube (40).
  • the header member (61,62) whose internal space communicates with the heat transfer tube (40) is provided, and the bottom wall surface (63) of the internal space of the header member (61,62) is the above-mentioned opening row (50). It is characterized in that it is located above the non-insertion opening (47).
  • the interior space through which the refrigerant flows in the header members (61,62) has its bottom wall surface (63) positioned above the non-insertion opening (47) of the opening row (50) of the fins (45). To do. Therefore, when the heat exchanger (30) functions as an evaporator, the temperature at the lower end of the heat exchanger (30) becomes higher than the temperature of other parts, and the lower end of the heat exchanger (30) becomes higher. The retention of condensed water in the water is suppressed.
  • a sixth aspect of the present disclosure is, in any one of the first to fifth aspects, the fin (45) and the heat transfer tube inserted through the tube opening (46) of the fin (45).
  • Each has a first heat exchange unit (31) and a second heat exchange unit (32) having (40), and the second heat exchange unit (32) is above the first heat exchange unit (31).
  • the longitudinal direction of the fin (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fin (45) of the first heat exchange section (31).
  • the pipe opening (46) located at is the non-insertion opening (47).
  • a seventh aspect of the present disclosure is, in any one of the first to fifth aspects, the fin and the heat transfer tube (40) inserted into the tube opening (46) of the fin, respectively.
  • the first heat exchange unit (31) and the second heat exchange unit (32) are provided, and the second heat exchange unit (32) is arranged above the first heat exchange unit (31). 2
  • the longitudinal direction of the fin (45) of the heat exchange section (32) is inclined with respect to the longitudinal direction of the fin (45) of the first heat exchange section (31), so that the first heat exchange section (31) In the opening row (50a) of the fins (45) of In the opening row (50b) of 45), a non-circulation pipe (41) through which fluid does not flow is inserted into the pipe opening (46) located at the lowermost position.
  • the second heat exchange section (32) arranged above the first heat exchange section (31) is inclined with respect to the first heat exchange section (31). Therefore, condensed water may stay near the lower end of the second heat exchange section (32).
  • the lowermost pipe opening (46) is the non-insertion opening (47). Therefore, the heat transfer tube (40) does not exist near the lower end of the second heat exchange section (32), and therefore, the possibility that the heat transfer tube (40) of the second heat exchange section (32) is corroded can be reduced.
  • the non-circulation pipe (41) is inserted through the pipe opening (46) located at the lowermost position. .. Even if the non-circulation pipe (41) is corroded, fluid such as a refrigerant does not leak from the non-circulation pipe (41). Therefore, according to this aspect, the reliability of the heat exchanger (30) can be improved.
  • An eighth aspect of the present disclosure is a heat exchanger (30) according to any one of the first to seventh aspects, a fan (24) for sending air to the heat exchanger (30), and the heat exchange.
  • the target is a heat exchange unit provided below the container (30) and equipped with a drain pan (13,25,26) for receiving the condensed water generated by the heat exchanger (30). Then, in the heat exchanger (30), the non-insertion opening (47) of the opening row (50) of the fin (45) is the upper edge (13a, 25a, 26a) of the drain pan (13,25,26). ) Is located below.
  • the lower end of the heat exchanger (30) is located below the upper edge of the drain pan (13,25,26) and the lower end of the heat exchanger (30) is long for condensed water. May be soaked over time.
  • the pipe opening (46) formed in the portion of the fins (45) of the heat exchanger (30) located below the upper edge of the drain pan (13,25,26) is not inserted. It becomes an opening (47). Therefore, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30), and therefore the possibility that the heat transfer tube (40) of the heat exchanger (30) is corroded can be reduced.
  • FIG. 1 is a perspective view of the outdoor unit of the first embodiment.
  • FIG. 2 is a schematic perspective view of the heat exchanger of the first embodiment.
  • FIG. 3 is a partial cross-sectional view of the heat exchanger of the first embodiment.
  • FIG. 4 is a cross-sectional view showing an IV-IV cross section in FIG.
  • FIG. 5 is a schematic cross-sectional view of the indoor unit of the second embodiment.
  • FIG. 6 is a schematic front view of the upwind row portion and the leeward row portion constituting the first and third heat exchange portions of the heat exchanger of the second embodiment.
  • FIG. 7 is a schematic front view of the upwind row portion and the leeward row portion constituting the second heat exchange portion of the heat exchanger of the second embodiment.
  • FIG. 8 is a schematic cross-sectional view of the indoor unit of the modified example of the second embodiment.
  • FIG. 9 is a schematic cross-sectional view of the indoor unit of the third embodiment.
  • Embodiment 1 The first embodiment will be described.
  • the present embodiment is an outdoor unit (10) of an air conditioner.
  • This outdoor unit (10) is a heat exchange unit provided with a heat exchanger (30).
  • the outdoor unit (10) includes a flat rectangular parallelepiped casing (11).
  • An air outlet (12) is formed on the front surface of the casing (11).
  • suction ports are formed on the back surface and one side surface of the casing (11).
  • the heat exchanger (30) of the present embodiment is housed in the casing (11) of the outdoor unit (10) together with constituent devices such as a compressor and a fan.
  • the heat exchanger (30) is a fin-and-tube type heat exchanger.
  • the heat exchanger (30) exchanges heat with the air supplied by the fan.
  • the heat exchanger (30) includes a plurality of fins (45), a plurality of heat transfer tubes (40), and a pair of header members (61,62).
  • the heat exchanger (30) is formed in an L shape in a plan view.
  • the heat exchanger (30) is arranged along the suction port (specifically, the back surface and one side surface of the casing (11)) of the casing (11).
  • the fins (45) are formed in a substantially rectangular plate shape, and are arranged so that their long sides are in the vertical direction.
  • the material of the fin (45) is an aluminum alloy.
  • a plurality of pipe openings (46) are formed in the fin (45).
  • the pipe opening (46) is a notch extending from one long side of the fin (45) toward the other long side (from the long side on the left side to the long side on the right side in FIG. 4).
  • the shape of the pipe opening (46) is an elongated shape along the short side of the fin (45).
  • the plurality of tube openings (46) are arranged in a row at regular intervals from each other in the longitudinal direction of the fins (45).
  • each fin (45) all the pipe openings (46) formed in the fin (45) form an opening row (50). Further, in each fin (45), the pipe opening (46) located at the lowermost position of the opening row (50) is the non-insertion opening (47).
  • the plurality of fins (45) are arranged at regular intervals in a posture facing each other.
  • the heat transfer tube (40) is formed in a flat shape having a width longer than the thickness.
  • the material of the heat transfer tube (40) is an aluminum alloy.
  • the plurality of heat transfer tubes (40) are arranged so as to intersect the fins (45) in a posture in which their longitudinal directions are substantially horizontal. Further, the plurality of heat transfer tubes (40) are arranged at regular intervals in the vertical direction.
  • one heat transfer tube (40) is inserted into each tube opening (46) of the fin (45) and is joined to the fin (45) by brazing or the like.
  • the heat transfer tube (40) is not inserted into the non-insertion opening (47) of each fin (45).
  • a heat transfer tube (40) is inserted into a tube opening (46) other than the non-insertion opening (47) located at the lowermost position thereof.
  • each header member (61,62) is a tubular member with both ends closed.
  • the material of the header member (61,62) is an aluminum alloy.
  • Each header member (61,62) is arranged in a posture in which its axial direction is in the vertical direction.
  • header members (61,62) are connected one by one to one end and the other end of the heat transfer tube (40).
  • each header member (61,62) communicates with the heat transfer tube (40) connected to the header member (61,62).
  • the bottom wall surface (63) of its interior space is located above the non-insertion opening (47) of the fin (45).
  • the drain pan (13) is a recess formed in the bottom plate of the casing (11) of the outdoor unit (10).
  • the drain pan (13) receives the condensed water generated in the heat exchanger (30), which functions as an evaporator.
  • the upper edge (13a) of the drain pan (13) is located above the non-insertion opening (47) of the fin (45).
  • the heat exchanger (30) heat exchanges the refrigerant with air.
  • the heat exchanger (30) provided in the outdoor unit (10) functions as an evaporator.
  • the refrigerant that has flowed into one of the header members (61) is separated into a plurality of heat transfer tubes (40) and flows in from the air that passes between the fins (45). It absorbs heat and evaporates.
  • the refrigerant that has passed through each heat transfer tube (40) flows into the other header member (62), merges, and then flows out from the heat exchanger (30).
  • the heat exchanger (30) of the present embodiment includes a plurality of heat transfer tubes (40) arranged in parallel with each other and a plurality of plate-shaped fins (45).
  • the fin (45) is formed with a plurality of tube openings (46) for inserting the heat transfer tube (40).
  • the fins (45) are arranged so that the longitudinal direction is the vertical direction.
  • the fins (45) have only one opening row (50).
  • the opening row (50) is composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45).
  • the tube opening (46) located at the lowermost position in the opening row (50) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted.
  • the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46).
  • the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to the present embodiment, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
  • the material of the heat transfer tube (40) is an aluminum alloy.
  • Aluminum has a higher ionization tendency than copper and is generally more susceptible to corrosion than copper.
  • the corrosion of the heat transfer tube (40) can be suppressed in the heat exchanger (30) provided with the heat transfer tube (40) made of an aluminum alloy, which is more easily corroded than the heat transfer tube made of copper.
  • the heat transfer tube (40) has a flat shape having a width longer than a thickness.
  • the heat exchanger (30) of the present embodiment is provided with a flat heat transfer tube having a width longer than the thickness.
  • a heat transfer tube (40) having such a flat shape is more likely to retain condensed water on its surface than a circular tubular heat transfer tube.
  • corrosion of the heat transfer tube (40) is suppressed. it can.
  • the heat exchanger (30) of this embodiment includes header members (61,62).
  • the header members (61,62) are formed in a tubular shape extending along the longitudinal direction of the fins (45), and are connected to the heat transfer tube (40) so that the internal space communicates with the heat transfer tube (40).
  • the bottom wall surface (63) of the internal space of the header member (61,62) is located above the non-insertion opening (47) of the opening row (50).
  • the internal space through which the refrigerant flows in the header members (61,62) has a non-insertion opening (47) in which the bottom wall surface (63) is a fin (45) opening row (50). ) Is located above. Therefore, when the heat exchanger (30) functions as an evaporator, the temperature at the lower end of the heat exchanger (30) becomes higher than the temperature of other parts, and the lower end of the heat exchanger (30) becomes higher. The retention of condensed water in the water is suppressed.
  • the outdoor unit (10) of the present embodiment includes a heat exchanger (30), a fan that sends air to the heat exchanger (30), and a drain pan (13).
  • the drain pan (13) is provided below the heat exchanger (30) and receives the condensed water generated by the heat exchanger (30).
  • the non-insertion opening (47) of the opening row (50) of the fins (45) is located below the upper edge (13a) of the drain pan (13).
  • the lower end of the heat exchanger (30) is located below the upper edge (13a) of the drain pan (13), and the lower end of the heat exchanger (30) is located. It may be immersed in condensed water for a long time.
  • the pipe opening (46) formed in the portion of the fin (45) located below the upper edge (13a) of the drain pan (13) is not inserted. It becomes an opening (47). Therefore, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30), and therefore the possibility that the heat transfer tube (40) of the heat exchanger (30) is corroded can be reduced.
  • Embodiment 2 The second embodiment will be described.
  • the present embodiment is an indoor unit (20) of an air conditioner.
  • This indoor unit (20) is a heat exchange unit provided with a heat exchanger (30).
  • the indoor unit (20) includes a box-shaped casing (21).
  • the casing (21) is formed in a horizontally long rectangular parallelepiped shape.
  • a suction port (22) is formed on the upper surface of the casing (21).
  • An air outlet (23) is formed on the lower surface of the casing (21).
  • a heat exchanger (30) and a fan (24) are housed inside the casing (21).
  • the fan (24) is a so-called cross-flow fan, and its rotation axis is arranged in a posture along the longitudinal direction (direction perpendicular to the paper surface of FIG. 5) of the casing (21).
  • the casing (21) has a front drain pan (25) located in front of the fan (24) (left in FIG. 5) and a rear drain pan (26) located behind the fan (24) (right in FIG. 5). ) And are formed.
  • the heat exchanger (30) is arranged from the front to the top of the fan (24).
  • the heat exchanger (30) includes a first heat exchange unit (31), a second heat exchange unit (32), and a third heat exchange unit (33).
  • Each of the first heat exchange section (31), the second heat exchange section (32), and the third heat exchange section (33) has a two-row structure.
  • the first heat exchange unit (31) is arranged in front of the fan (24) (left side in FIG. 5).
  • the portion near the lower end of the first heat exchange portion (31) enters the front drain pan (25).
  • the first heat exchange portion (31) is inclined so that the upper portion thereof is closer to the front surface (to the left side in FIG. 5) of the casing (21) than the lower portion.
  • the first heat exchange section (31) has a first windward row section (31a) and a first leeward row section (31b).
  • the first leeward row portion (31a) and the first leeward row portion (31b) are arranged so as to overlap each other.
  • the first leeward row portion (31b) is arranged closer to the fan (24) than the first leeward row portion (31a).
  • each of the first leeward row portion (31a) and the first leeward row portion (31b) has a plurality of rectangular plate-shaped fins (45) and a plurality of flat-shaped heat transfer tubes ( 40) and a pair of tubular header members (61,62) are provided, and are configured in the same manner as the heat exchanger (30) of the first embodiment.
  • one opening row (50a) is formed in each fin (45) of the first leeward row portion (31a) and the first leeward row portion (31b).
  • the pipe opening (46) located at the bottom of the opening row (50a) of each fin (45) is a non-insertion opening ( 47).
  • the bottom wall surface (63) of the internal space of each header member (61, 62) is formed from the non-insertion opening (47). Is also located above.
  • the fins (45), heat transfer tubes (40), and header members (61,62) are all made of aluminum alloy.
  • first leeward row portion (31a) and the first leeward row portion (31b) are L-shaped in a plan view in that the heat transfer tube (40) is formed in a flat shape extending linearly. It is different from the formed heat exchanger (30) of the first embodiment.
  • the number and size of fins (45), the number and length of heat transfer tubes (40), and the header members (61, respectively) of the first windward row portion (31a) and the first windward row portion (31b) are provided.
  • the shape of 62) is different from that of the heat exchanger (30) of the first embodiment.
  • the positions of the pipe openings (46) forming the opening row (50a) of the first leeward row portion (31a) and the pipe openings (46) forming the opening row (50a) of the first leeward row portion (31b). ) are deviated by 1/2 pitch from each other in the longitudinal direction of the fins (45).
  • the second heat exchange section (32) is arranged above the first heat exchange section (31).
  • the lower end of the second heat exchange section (32) is in contact with the upper end of the first heat exchange section (31).
  • the second heat exchange portion (32) is inclined so that the upper portion thereof is closer to the back surface (to the right side in FIG. 5) of the casing (21) than the lower portion.
  • the second heat exchange section (32) has a second upwind row section (32a) and a second leeward row section (32b).
  • the second leeward row (32a) and the second leeward row (32b) are arranged so as to overlap each other.
  • the second leeward row (32b) is located closer to the fan (24) than the second leeward row (32a).
  • each of the second leeward row (32a) and the second leeward row (32b) has a plurality of rectangular plate-shaped fins (45) and a plurality of flat heat transfer tubes ( 40) and a pair of tubular header members (61,62) are provided, and are configured in the same manner as the heat exchanger (30) of the first embodiment.
  • the fins (45), heat transfer tubes (40), and header members (61,62) are all made of aluminum alloy.
  • the longitudinal direction of the fins (45) constituting the second leeward row portion (32a) and the second leeward row portion (32b) constitutes the first leeward row portion (31a) and the first leeward row portion (31b). It is inclined toward the back surface side of the casing (21) with respect to the longitudinal direction of the fins (45).
  • each fin (45) of the second windward row portion (32a) and the second windward row portion (32b) has one opening row (50b). It is formed. However, in each of the second leeward row (32a) and the second leeward row (32b), the pipe opening (46) located at the lowermost position of the opening row (50b) formed in the fins (45) , Non-distribution pipe (41) is inserted. In each of the second leeward row (32a) and the second leeward row (32b), the bottom wall surface (63) of the internal space of each header member (61,62) is above the non-circulation pipe (41). Located in. Therefore, the non-circulation pipe (41) does not communicate with the internal space of each header member (61,62). Therefore, the refrigerant does not flow in the non-distribution pipe (41).
  • the second leeward row portion (32a) and the second leeward row portion (32b) are L-shaped in a plan view in that the heat transfer tube (40) is formed in a flat shape extending linearly. It is different from the formed heat exchanger (30) of the first embodiment.
  • the number and size of fins (45), the number and length of heat transfer tubes (40), and the header members (61, respectively) of the second windward row portion (32a) and the second windward row portion (32b) are provided.
  • the shape of 62) is different from that of the heat exchanger (30) of the first embodiment.
  • the positions of the pipe openings (46) forming the opening row (50b) of the second leeward row (32a) and the pipe openings (46) forming the opening row (50b) of the second leeward row (32b). ) are deviated by 1/2 pitch from each other in the longitudinal direction of the fins (45).
  • the third heat exchange unit (33) is arranged behind the second heat exchange unit (32) (on the right side in FIG. 5).
  • the upper end of the third heat exchange section (33) is in contact with the upper end of the second heat exchange section (32).
  • the portion near the lower end of the third heat exchange portion (33) enters the rear drain pan (26).
  • the third heat exchange portion (33) is inclined so that the upper portion thereof is closer to the front surface (to the left side in FIG. 5) of the casing (21) than the lower portion.
  • the third heat exchange section (33) has a third upwind row section (33a) and a third leeward row section (33b).
  • the third leeward row (33a) and the third leeward row (33b) are arranged so as to overlap each other.
  • the third leeward row (33b) is located closer to the fan (24) than the third leeward row (33a).
  • each of the third leeward row (33a) and the third leeward row (33b) has a plurality of rectangular plate-shaped fins (45) and a plurality of flat heat transfer tubes ( 40) and a pair of tubular header members (61,62) are provided, and are configured in the same manner as the heat exchanger (30) of the first embodiment.
  • one opening row (50c) is formed in each fin (45) of the third leeward row portion (33a) and the third leeward row portion (33b).
  • the pipe opening (46) located at the bottom of the opening row (50c) of each fin (45) is a non-insertion opening ( 47).
  • the bottom wall surface (63) of the internal space of each header member (61, 62) is formed from the non-insertion opening (47). Is also located above.
  • the fins (45), heat transfer tubes (40), and header members (61,62) are all made of aluminum alloy.
  • the third leeward row portion (33a) and the third leeward row portion (33b) are L-shaped in a plan view in that the heat transfer tube (40) is formed in a flat shape extending linearly. It is different from the formed heat exchanger (30) of the first embodiment.
  • the number and size of fins (45), the number and length of heat transfer tubes (40), and the header members (61, respectively) of the third windward row portion (33a) and the third windward row portion (33b) are provided.
  • the shape of 62) is different from that of the heat exchanger (30) of the first embodiment.
  • the positions of the pipe openings (46) forming the opening row (50c) of the third leeward row (33a) and the pipe openings (46) forming the opening row (50c) of the third leeward row (33b). ) are deviated by 1/2 pitch from each other in the longitudinal direction of the fins (45).
  • the heat exchanger (30) exchanges heat with the air for the refrigerant.
  • the heat exchanger (30) provided in the indoor unit (20) functions as an evaporator.
  • the refrigerant flowing through the heat transfer tube (40) absorbs heat from the air passing between the fins (45) and evaporates.
  • the water vapor contained in the air condenses to generate condensed water.
  • the generated condensed water flows down along the fin (45).
  • the condensed water generated in the first heat exchange section (31) flows down to the front drain pan (25) along the fins (45) of the first heat exchange section (31).
  • the condensed water generated in the second heat exchange section (32) flows down along the fins (45) of the second heat exchange section (32), and then travels down the fins (45) of the first heat exchange section (31). It flows down to the front drain pan (25).
  • the condensed water generated in the third heat exchange section (33) flows down to the rear drain pan (26) along the fins (45) of the third heat exchange section (33).
  • the indoor unit (20) of the present embodiment includes a heat exchanger (30), a fan (24) for sending air to the heat exchanger (30), and a drain pan (25, 26).
  • the drain pans (25,26) are provided below the heat exchanger (30) and receive the condensed water generated by the heat exchanger (30).
  • the non-insertion opening (47) of the opening row (50a) of the fins (45) of the first heat exchange section (31) has an upper edge (25a) of the front drain pan (25). ) Is located below.
  • the non-insertion opening (47) of the opening row (50b) of the fins (45) of the third heat exchange section (33) is the upper edge of the rear drain pan (26). It is located below (26a).
  • the lower end of the first heat exchange section (31) is located below the upper edge (25a) of the front drain pan (25), and the third heat exchange section (33) has a lower end portion.
  • the lower end is located below the upper edge (26a) of the rear drain pan (26). Therefore, the lower ends of the first heat exchange section (31) and the third heat exchange section (33) may be immersed in the condensed water for a long time.
  • the heat exchanger (30) of the present embodiment it is formed in a portion of the fins (45) of the first heat exchange section (31) located below the upper edge (25a) of the front drain pan (25).
  • the pipe opening (46) becomes the non-insertion opening (47).
  • a pipe opening formed in a portion of the fins (45) of the third heat exchanger (33) located below the upper edge (26a) of the rear drain pan (26). (46) becomes the non-insertion opening (47). Therefore, the heat transfer tube (40) is not provided at the lower ends of the first heat exchange section (31) and the third heat exchange section (33), and therefore the heat transfer tube (40) of the heat exchanger (30) is corroded. The possibility of doing so can be reduced.
  • the heat exchanger (30) of the present embodiment includes a first heat exchange unit (31) and a second heat exchange unit (32).
  • Each of the first heat exchange section (31) and the second heat exchange section (32) has a fin (45) and a heat transfer tube (40) inserted through a tube opening (46) of the fin (45). ..
  • the second heat exchange section (32) is arranged above the first heat exchange section (31).
  • the longitudinal direction of the fins (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fins (45) of the first heat exchange section (31).
  • the pipe opening (46) located at the lowermost position is the non-insertion opening (47).
  • a non-circulation pipe (41) through which fluid does not flow is inserted into the pipe opening (46) located at the lowermost position.
  • the non-circulation pipe (41) is inserted into the pipe opening (46) located at the lowermost position. ) Is inserted. Even if the non-circulation pipe (41) is corroded, the refrigerant does not leak from the non-circulation pipe (41). Therefore, according to this aspect, the possibility of leakage of the refrigerant due to the corrosion of the heat transfer tube (40) can be reduced, and the reliability of the heat exchanger (30) can be improved.
  • the non-circulation pipe (41) of the second heat exchange section (32) is omitted, the amount of air passing through the portion near the lower end of the second heat exchange section (32) without heat exchange with the refrigerant is increased. As the number increases, the heat exchange performance of the heat exchanger (30) may deteriorate.
  • the non-circulation pipe (41) is provided near the lower end of the second heat exchange section (32), and the flow rate of air passing near the lower end of the second heat exchange section (32) is measured. , The flow rate of air passing through the other part of the second heat exchange part (32) can be made similar. Therefore, according to the present embodiment, it is possible to avoid deterioration of the heat exchange performance of the heat exchanger (30).
  • the pipe opening (46) located at the lowermost position of the opening row (50) formed in the fins (45) may be a non-insertion opening (47).
  • a non-circulation pipe (41) is not provided in each of the second leeward row portion (32a) and the second leeward row portion (32b) of this modification.
  • the heat exchanger (30) of this modified example includes a first heat exchange unit (31) and a second heat exchange unit (32).
  • Each of the first heat exchange section (31) and the second heat exchange section (32) has a fin (45) and a heat transfer tube (40) inserted through a tube opening (46) of the fin (45). ..
  • the second heat exchange section (32) is arranged above the first heat exchange section (31).
  • the longitudinal direction of the fins (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fins (45) of the first heat exchange section (31).
  • the opening row (50a) of the fins (45) of the first heat exchange section (31) and the opening row (45) of the fins (45) of the second heat exchange section (32) In each of 50b), the lowermost pipe opening (46) is the non-insertion opening (47).
  • the second heat exchange section (32) arranged above the first heat exchange section (31) is inclined with respect to the first heat exchange section (31).
  • this heat exchanger (30) functions as an evaporator
  • the condensed water generated in the second heat exchange section (32) flows down to the first heat exchange section (31) located below the heat exchanger (30). Therefore, condensed water may stay near the lower end of the second heat exchange section (32).
  • the lowermost pipe opening (46) is not inserted in the opening row (50b) of the fins (45) of the second heat exchange section (32). It becomes an opening (47). Therefore, the heat transfer tube (40) does not exist near the lower end of the second heat exchange section (32), and therefore, the possibility that the heat transfer tube (40) of the second heat exchange section (32) is corroded can be reduced.
  • Embodiment 3 The third embodiment will be described.
  • the structure of the heat exchanger (30) is changed in the indoor unit (20) of the second embodiment.
  • the difference between the indoor unit (20) of the present embodiment and the indoor unit (20) of the second embodiment will be described.
  • the heat exchanger (30) of the present embodiment is a so-called cross-fin type fin-and-tube heat exchanger.
  • the heat exchanger (30) includes a plurality of plate-shaped fins (45) and a plurality of circular tubular heat transfer tubes (40).
  • the material of the fin (45) is an aluminum alloy.
  • the material of the heat transfer tube (40) is a copper alloy.
  • the heat exchanger (30) is arranged from the front to the top of the fan (24).
  • the heat exchanger (30) includes a front heat exchange unit (35) and a rear heat exchange unit (36).
  • Each of the front heat exchange section (35) and the rear heat exchange section (36) has a two-row structure.
  • the front heat exchange section (35) is curved toward the back side (right side in FIG. 5) of the casing (21).
  • the front heat exchange section (35) is arranged from the front (left side in FIG. 9) of the fan (24) to the upper side.
  • the portion near the lower end of the front heat exchange section (35) enters the front drain pan (25).
  • the front heat exchange section (35) is provided with a plurality of plate-shaped fins (45) and a plurality of circular tubular heat transfer tubes (40).
  • the fins (45) are formed in the shape of an elongated plate.
  • the pair of long sides along the longitudinal direction of the fins (45) are curved and substantially parallel to each other.
  • the front heat exchange section (35) is arranged so that the longitudinal direction of the fins (45) is in the vertical direction.
  • a plurality of pipe openings (46) are formed in the fin (45).
  • the pipe opening (46) is a circular hole that penetrates the fin (45) in the thickness direction.
  • the pipe openings (46) are arranged in a row along each of the pair of long sides along the longitudinal direction of the fins (45).
  • a plurality of pipe openings (46) along the outer long sides of the curved fins (45) form a first opening row (51a).
  • a plurality of pipe openings (46) along the inner long sides of the curved fins (45) form a second opening row (52a).
  • the plurality of pipe openings (46) are arranged in a row in the longitudinal direction of the fins (45).
  • the plurality of pipe openings (46) are arranged at predetermined intervals in the longitudinal direction of the fins (45).
  • the position of the pipe opening (46) forming the first opening row (51a) and the position of the pipe opening (46) forming the second opening row (52a) are 1/1 in the longitudinal direction of the fins (45). It is off by 2 pitches.
  • the pipe opening (46) located at the lowermost position thereof is a non-insertion opening (47).
  • One heat transfer tube (40) is inserted into each tube opening (46) of the fin (45). However, in the front heat exchange section (35), the heat transfer tube (40) is not inserted into the non-insertion opening (47) of each fin (45). In the first opening row (51a) and the second opening row (52a) of each fin (45), the heat transfer tube (40) is connected to the tube opening (46) other than the non-insertion opening (47) located at the lowermost position thereof. Is plugged in.
  • the rear heat exchange section (36) is formed in a flat shape.
  • the rear heat exchange section (36) is located above the fan (24).
  • the portion near the lower end of the rear heat exchange section (36) enters the rear drain pan (26).
  • the rear heat exchange portion (36) is inclined so that the upper portion thereof is closer to the front surface (to the left side in FIG. 9) of the casing (21) than the lower portion.
  • the rear heat exchange section (36) is provided with a plurality of plate-shaped fins (45) and a plurality of circular tubular heat transfer tubes (40).
  • the fins (45) are formed in the shape of an elongated rectangular plate.
  • the rear heat exchange section (36) is arranged so that the longitudinal direction of the fins (45) is in the vertical direction.
  • a plurality of pipe openings (46) are formed in the fin (45).
  • the pipe opening (46) is a circular hole that penetrates the fin (45) in the thickness direction.
  • the pipe openings (46) are arranged in a row along each of the pair of long sides along the longitudinal direction of the fins (45).
  • a plurality of pipe openings (46) along the upper long side of the inclined fins (45) constitute a first opening row (51b).
  • a plurality of pipe openings (46) along the lower long side of the sloping fins (45) form a second opening row (52b).
  • the plurality of pipe openings (46) are arranged in a row in the longitudinal direction of the fins (45).
  • the plurality of pipe openings (46) are arranged at regular intervals in the longitudinal direction of the fins (45).
  • the position of the pipe opening (46) forming the first opening row (51b) and the position of the pipe opening (46) forming the second opening row (52b) are 1/1 in the longitudinal direction of the fins (45). It is off by 2 pitches.
  • the pipe opening (46) located at the lowermost position thereof is a non-insertion opening (47).
  • One heat transfer tube (40) is inserted into each tube opening (46) of the fin (45). However, in the rear heat exchange section (36), the heat transfer tube (40) is not inserted into the non-insertion opening (47) of each fin (45). In the first opening row (51b) and the second opening row (52b) of each fin (45), the heat transfer tube (40) is connected to the tube opening (46) other than the non-insertion opening (47) located at the lowermost position. Is plugged in.
  • the heat exchanger (30) of the present embodiment includes a plurality of heat transfer tubes (40) arranged in parallel with each other and a plurality of plate-shaped fins (45).
  • the fin (45) is formed with a plurality of tube openings (46) for inserting the heat transfer tube (40).
  • the fins (45) are arranged so that the longitudinal direction is the vertical direction.
  • the fin (45) has a plurality of opening rows (51a, 52a, 51b, 52b).
  • Each opening row (51a, 52a, 51b, 52b) is composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45).
  • the tube opening (46) located at the lowermost position in each of the plurality of opening rows (51a, 52a, 51b, 52b) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted.
  • each fin (45) is provided with a plurality of opening rows (51a, 52a, 51b, 52b).
  • the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46).
  • the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to the present embodiment, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
  • the present disclosure is useful for heat exchangers and heat exchange units.

Abstract

A plurality of heat transfer tubes (40) and a plurality of fins (45) are provided in the heat exchanger (30). A plurality of tube openings (46) are formed in the fins (45). The plurality of tube openings (46) of the fins (45) constitute an opening row (50). The tube opening (46) at the lowermost position in the opening row (50) is a non-insertion opening (47) into which the heat transfer tube (40) is not inserted.

Description

熱交換器および熱交換ユニットHeat exchanger and heat exchange unit
　本開示は、熱交換器および熱交換ユニットに関するものである。 This disclosure relates to heat exchangers and heat exchange units.
　特許文献１には、熱交換器が開示されている。この熱交換器は、空調機の室内ユニットに設けられ、室内ユニットに吸い込まれた空気を冷媒と熱交換させる。熱交換器が蒸発器として機能する冷房運転中には、熱交換器のフィンの表面で空気中の水分が凝縮し、生成した凝縮水がフィンを伝って下方へ流れ落ちる。 Patent Document 1 discloses a heat exchanger. This heat exchanger is provided in the indoor unit of the air conditioner and exchanges heat with the refrigerant for the air sucked into the indoor unit. During the cooling operation in which the heat exchanger functions as an evaporator, the moisture in the air condenses on the surface of the fins of the heat exchanger, and the generated condensed water flows down along the fins.
特開２０１５－１２７６０７号公報JP-A-2015-127607
　上述したように、蒸発器として機能する熱交換器では、凝縮水がフィンを伝って流れ落ちる。そのため、熱交換器の最も下方に配置された伝熱管は、長時間に亘って濡れた状態になり、他の伝熱管に比べて腐食しやすい。伝熱管が腐食すると、伝熱管から冷媒が漏洩するおそれがあり、熱交換器の信頼性が損なわれる。 As mentioned above, in the heat exchanger that functions as an evaporator, condensed water flows down along the fins. Therefore, the heat transfer tube arranged at the lowermost part of the heat exchanger becomes wet for a long time and is more easily corroded than other heat transfer tubes. If the heat transfer tube is corroded, the refrigerant may leak from the heat transfer tube, and the reliability of the heat exchanger is impaired.
　本開示の目的は、熱交換器および熱交換ユニットの信頼性を高めることにある。 The purpose of this disclosure is to improve the reliability of heat exchangers and heat exchange units.
　本開示の第１の態様は、互いに平行に配置された複数の伝熱管（40）と、上記伝熱管（40）を挿し通すための複数の管用開口（46）が形成された複数の板状のフィン（45）とを備えた熱交換器を対象とする。そして、上記フィン（45）は、長手方向が上下方向となるように配置されると共に、上記フィン（45）の長手方向に一列に並んだ複数の上記管用開口（46）によって構成される開口列（50）を一つだけ有し、上記開口列（50）において最も下方に位置する上記管用開口（46）は、上記伝熱管（40）が挿し通されない非挿通開口（47）であることを特徴とする。 The first aspect of the present disclosure is a plurality of plate shapes in which a plurality of heat transfer tubes (40) arranged parallel to each other and a plurality of tube openings (46) for inserting the heat transfer tubes (40) are formed. The target is a heat exchanger equipped with fins (45). The fins (45) are arranged so that the longitudinal direction is in the vertical direction, and the opening rows are composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45). The pipe opening (46) having only one (50) and being located at the lowermost position in the opening row (50) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted. It is a feature.
　第１の態様では、各フィン（45）に開口列（50）が一つだけ設けられる。フィン（45）の開口列（50）において、最も下方に位置する管用開口（46）である非挿通開口（47）には、伝熱管（40）が挿し通されない。この態様では、凝縮水が滞留しやすい熱交換器（30）の下端部に、伝熱管（40）が設けられない。従って、この態様によれば、凝縮水によって伝熱管（40）が腐食する可能性を低減でき、熱交換器（30）の信頼性を向上させることができる。 In the first aspect, only one opening row (50) is provided for each fin (45). In the opening row (50) of the fins (45), the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46). In this embodiment, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to this aspect, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
　本開示の第２の態様は、互いに平行に配置された複数の伝熱管（40）と、上記伝熱管（40）を挿し通すための複数の管用開口（46）が形成された複数の板状のフィン（45）とを備えた熱交換器を対象とする。そして、上記フィン（45）は、長手方向が上下方向となるように配置されると共に、上記フィン（45）の長手方向に一列に並んだ複数の上記管用開口（46）によって構成される開口列（51a,52a,51b,52b）を複数有し、複数の上記開口列（51a,52a,51b,52b）のそれぞれにおいて最も下方に位置する上記管用開口（46）は、上記伝熱管（40）が挿し通されない非挿通開口（47）であることを特徴とする。 A second aspect of the present disclosure is a plurality of plate shapes in which a plurality of heat transfer tubes (40) arranged in parallel with each other and a plurality of tube openings (46) for inserting the heat transfer tubes (40) are formed. The target is a heat exchanger equipped with fins (45). The fins (45) are arranged so that the longitudinal direction is in the vertical direction, and the opening rows are composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45). The tube opening (46) having a plurality of (51a, 52a, 51b, 52b) and located at the lowermost position in each of the plurality of opening rows (51a, 52a, 51b, 52b) is the heat transfer tube (40). Is a non-insertion opening (47) through which is not inserted.
　第２の態様では、各フィン（45）に開口列（51a,52a,51b,52b）が複数ずつ設けられる。フィン（45）の各開口列（51a,52a,51b,52b）において、最も下方に位置する管用開口（46）である非挿通開口（47）には、伝熱管（40）が挿し通されない。この態様では、凝縮水が滞留しやすい熱交換器（30）の下端部に、伝熱管（40）が設けられない。従って、この態様によれば、凝縮水によって伝熱管（40）が腐食する可能性を低減でき、熱交換器（30）の信頼性を向上させることができる。 In the second aspect, each fin (45) is provided with a plurality of opening rows (51a, 52a, 51b, 52b). In each opening row (51a, 52a, 51b, 52b) of the fins (45), the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46). In this embodiment, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to this aspect, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
　本開示の第３の態様は、上記第１又は第２の態様において、上記伝熱管（40）の材質がアルミニウム合金であることを特徴とする。 The third aspect of the present disclosure is characterized in that, in the first or second aspect, the material of the heat transfer tube (40) is an aluminum alloy.
　第３の態様では、アルミニウム合金製の伝熱管（40）が、熱交換器（30）に設けられる。アルミニウムは、銅に比べてイオン化傾向が大きく、一般的に銅よりも腐食しやすい。この態様によれば、銅製の伝熱管に比べて腐食しやすいアルミニウム合金製の伝熱管（40）を備えた熱交換器（30）において、伝熱管（40）の腐食を抑制できる。 In the third aspect, a heat transfer tube (40) made of an aluminum alloy is provided in the heat exchanger (30). Aluminum has a higher ionization tendency than copper and is generally more susceptible to corrosion than copper. According to this aspect, the corrosion of the heat transfer tube (40) can be suppressed in the heat exchanger (30) provided with the heat transfer tube (40) made of an aluminum alloy, which is more easily corroded than the heat transfer tube made of copper.
　本開示の第４の態様は、上記第３の態様において、上記伝熱管（40）は、幅が厚さよりも長い扁平な形状であることを特徴とする。 A fourth aspect of the present disclosure is characterized in that, in the third aspect, the heat transfer tube (40) has a flat shape having a width longer than a thickness.
　第４の態様では、厚さよりも幅が長い扁平な形状の伝熱管が熱交換器に設けられる。このような扁平な形状の伝熱管（40）は、円管状の伝熱管に比べて、その表面に凝縮水が滞留しやすい。この態様によれば、円管状の伝熱管に比べて凝縮水が滞留しやすい扁平な形状の伝熱管（40）を備えた熱交換器（30）において、伝熱管（40）の腐食を抑制できる。 In the fourth aspect, the heat exchanger is provided with a flat-shaped heat transfer tube having a width longer than the thickness. A heat transfer tube (40) having such a flat shape is more likely to retain condensed water on its surface than a circular tubular heat transfer tube. According to this aspect, corrosion of the heat transfer tube (40) can be suppressed in the heat exchanger (30) provided with the flat-shaped heat transfer tube (40) in which condensed water tends to stay as compared with the circular tubular heat transfer tube. ..
　本開示の第５の態様は、上記第１乃至第４のいずれか一つの態様において、上記フィン（45）の長手方向に沿って延びる筒状に形成され、上記伝熱管（40）に接続して内部空間が上記伝熱管（40）に連通するヘッダ部材（61,62）を備え、上記ヘッダ部材（61,62）の内部空間の底壁面（63）が、上記開口列（50）の上記非挿通開口（47）よりも上方に位置することを特徴とする。 A fifth aspect of the present disclosure is, in any one of the first to fourth aspects, the tubular shape extending along the longitudinal direction of the fin (45) and connected to the heat transfer tube (40). The header member (61,62) whose internal space communicates with the heat transfer tube (40) is provided, and the bottom wall surface (63) of the internal space of the header member (61,62) is the above-mentioned opening row (50). It is characterized in that it is located above the non-insertion opening (47).
　第５の態様では、ヘッダ部材（61,62）において冷媒が流れる内部空間は、その底壁面（63）がフィン（45）の開口列（50）の非挿通開口（47）よりも上に位置する。このため、熱交換器（30）が蒸発器として機能するときに、熱交換器（30）の下端部の温度が他の部分の温度に比べて高くなり、熱交換器（30）の下端部における凝縮水の滞留が抑制される。 In a fifth aspect, the interior space through which the refrigerant flows in the header members (61,62) has its bottom wall surface (63) positioned above the non-insertion opening (47) of the opening row (50) of the fins (45). To do. Therefore, when the heat exchanger (30) functions as an evaporator, the temperature at the lower end of the heat exchanger (30) becomes higher than the temperature of other parts, and the lower end of the heat exchanger (30) becomes higher. The retention of condensed water in the water is suppressed.
　本開示の第６の態様は、上記第１乃至第５のいずれか一つの態様において、上記フィン（45）と、該フィン（45）の上記管用開口（46）に挿し通された上記伝熱管（40）とをそれぞれが有する第１熱交換部（31）及び第２熱交換部（32）を備え、上記第２熱交換部（32）は、上記第１熱交換部（31）の上方に配置され、上記第２熱交換部（32）の上記フィン（45）の長手方向が、上記第１熱交換部（31）の上記フィン（45）の長手方向に対して傾斜し、上記第１熱交換部（31）の上記フィン（45）の上記開口列（50a）と、上記第２熱交換部（32）の上記フィン（45）の上記開口列（50b）のそれぞれにおいて、最も下方に位置する上記管用開口（46）が上記非挿通開口（47）となることを特徴とする。 A sixth aspect of the present disclosure is, in any one of the first to fifth aspects, the fin (45) and the heat transfer tube inserted through the tube opening (46) of the fin (45). Each has a first heat exchange unit (31) and a second heat exchange unit (32) having (40), and the second heat exchange unit (32) is above the first heat exchange unit (31). The longitudinal direction of the fin (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fin (45) of the first heat exchange section (31). The lowest in each of the opening row (50a) of the fin (45) of the heat exchange section (31) and the opening row (50b) of the fin (45) of the second heat exchange section (32). The pipe opening (46) located at is the non-insertion opening (47).
　本開示の第７の態様は、上記第１乃至第５のいずれか一つの態様において、上記フィンと、該フィンの上記管用開口（46）に挿し通された上記伝熱管（40）とをそれぞれが有する第１熱交換部（31）及び第２熱交換部（32）を備え、上記第２熱交換部（32）は、上記第１熱交換部（31）の上方に配置され、上記第２熱交換部（32）の上記フィン（45）の長手方向が、上記第１熱交換部（31）の上記フィン（45）の長手方向に対して傾斜し、上記第１熱交換部（31）の上記フィン（45）の上記開口列（50a）において、最も下方に位置する上記管用開口（46）が上記非挿通開口（47）となり、上記第２熱交換部（32）の上記フィン（45）の上記開口列（50b）において、最も下方に位置する上記管用開口（46）には、内部を流体が流通しない非流通管（41）が挿し通されることを特徴とする。 A seventh aspect of the present disclosure is, in any one of the first to fifth aspects, the fin and the heat transfer tube (40) inserted into the tube opening (46) of the fin, respectively. The first heat exchange unit (31) and the second heat exchange unit (32) are provided, and the second heat exchange unit (32) is arranged above the first heat exchange unit (31). 2 The longitudinal direction of the fin (45) of the heat exchange section (32) is inclined with respect to the longitudinal direction of the fin (45) of the first heat exchange section (31), so that the first heat exchange section (31) In the opening row (50a) of the fins (45) of In the opening row (50b) of 45), a non-circulation pipe (41) through which fluid does not flow is inserted into the pipe opening (46) located at the lowermost position.
　第６及び第７の各態様では、第１熱交換部（31）の上方に配置された第２熱交換部（32）が、第１熱交換部（31）に対して傾斜する。このため、第２熱交換部（32）の下端付近に凝縮水が滞留するおそれがある。 In each of the sixth and seventh aspects, the second heat exchange section (32) arranged above the first heat exchange section (31) is inclined with respect to the first heat exchange section (31). Therefore, condensed water may stay near the lower end of the second heat exchange section (32).
　第６の態様では、第２熱交換部（32）のフィン（45）の開口列（50b）において、最も下方に位置する管用開口（46）が非挿通開口（47）となる。このため、第２熱交換部（32）の下端付近に伝熱管（40）が存在せず、従って、第２熱交換部（32）の伝熱管（40）が腐食する可能性を低減できる。 In the sixth aspect, in the opening row (50b) of the fins (45) of the second heat exchange section (32), the lowermost pipe opening (46) is the non-insertion opening (47). Therefore, the heat transfer tube (40) does not exist near the lower end of the second heat exchange section (32), and therefore, the possibility that the heat transfer tube (40) of the second heat exchange section (32) is corroded can be reduced.
　第７の態様では、第２熱交換部（32）のフィン（45）の開口列（50b）において、最も下方に位置する管用開口（46）に、非流通管（41）が挿し通される。仮に非流通管（41）が腐食しても、非流通管（41）から冷媒等の流体は漏洩しない。従って、この態様によれば、熱交換器（30）の信頼性を高めることができる。 In the seventh aspect, in the opening row (50b) of the fins (45) of the second heat exchange section (32), the non-circulation pipe (41) is inserted through the pipe opening (46) located at the lowermost position. .. Even if the non-circulation pipe (41) is corroded, fluid such as a refrigerant does not leak from the non-circulation pipe (41). Therefore, according to this aspect, the reliability of the heat exchanger (30) can be improved.
　本開示の第８の態様は、上記第１乃至第７のいずれか一つの態様の熱交換器（30）と、上記熱交換器（30）へ空気を送るファン（24）と、上記熱交換器（30）の下方に設けられて上記熱交換器（30）で生成した凝縮水を受けるドレンパン（13,25,26）とを備えた熱交換ユニットを対象とする。そして、上記熱交換器（30）は、上記フィン（45）の上記開口列（50）の上記非挿通開口（47）が上記ドレンパン（13,25,26）の上縁（13a,25a,26a）よりも下方に位置することを特徴とする。 An eighth aspect of the present disclosure is a heat exchanger (30) according to any one of the first to seventh aspects, a fan (24) for sending air to the heat exchanger (30), and the heat exchange. The target is a heat exchange unit provided below the container (30) and equipped with a drain pan (13,25,26) for receiving the condensed water generated by the heat exchanger (30). Then, in the heat exchanger (30), the non-insertion opening (47) of the opening row (50) of the fin (45) is the upper edge (13a, 25a, 26a) of the drain pan (13,25,26). ) Is located below.
　第８の態様では、熱交換器（30）の下端部がドレンパン（13,25,26）の上縁よりも下方に位置しており、熱交換器（30）の下端部が凝縮水に長時間に亘って浸かるおそれがある。一方、この態様では、熱交換器（30）のフィン（45）のうちドレンパン（13,25,26）の上縁よりも下方に位置する部分に形成された管用開口（46）が、非挿通開口（47）となる。このため、熱交換器（30）の下端部に伝熱管（40）は設けられず、従って、熱交換器（30）の伝熱管（40）が腐食する可能性を低減できる。 In the eighth aspect, the lower end of the heat exchanger (30) is located below the upper edge of the drain pan (13,25,26) and the lower end of the heat exchanger (30) is long for condensed water. May be soaked over time. On the other hand, in this embodiment, the pipe opening (46) formed in the portion of the fins (45) of the heat exchanger (30) located below the upper edge of the drain pan (13,25,26) is not inserted. It becomes an opening (47). Therefore, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30), and therefore the possibility that the heat transfer tube (40) of the heat exchanger (30) is corroded can be reduced.
図１は、実施形態１の室外ユニットの斜視図である。FIG. 1 is a perspective view of the outdoor unit of the first embodiment. 図２は、実施形態１の熱交換器の概略斜視図である。FIG. 2 is a schematic perspective view of the heat exchanger of the first embodiment. 図３は、実施形態１の熱交換器の一部断面図である。FIG. 3 is a partial cross-sectional view of the heat exchanger of the first embodiment. 図４は、図３におけるIV－IV断面を示す断面図である。FIG. 4 is a cross-sectional view showing an IV-IV cross section in FIG. 図５は、実施形態２の室内ユニットの概略断面図である。FIG. 5 is a schematic cross-sectional view of the indoor unit of the second embodiment. 図６は、実施形態２の熱交換器の第１および第３熱交換部を構成する風上列部および風下列部の概略正面図である。FIG. 6 is a schematic front view of the upwind row portion and the leeward row portion constituting the first and third heat exchange portions of the heat exchanger of the second embodiment. 図７は、実施形態２の熱交換器の第２熱交換部を構成する風上列部および風下列部の概略正面図である。FIG. 7 is a schematic front view of the upwind row portion and the leeward row portion constituting the second heat exchange portion of the heat exchanger of the second embodiment. 図８は、実施形態２の変形例の室内ユニットの概略断面図である。FIG. 8 is a schematic cross-sectional view of the indoor unit of the modified example of the second embodiment. 図９は、実施形態３の室内ユニットの概略断面図である。FIG. 9 is a schematic cross-sectional view of the indoor unit of the third embodiment.
　《実施形態１》
　実施形態１について説明する。本実施形態は、空気調和機の室外ユニット（10）である。この室外ユニット（10）は、熱交換器（30）を備えた熱交換ユニットである。 << Embodiment 1 >>
The first embodiment will be described. The present embodiment is an outdoor unit (10) of an air conditioner. This outdoor unit (10) is a heat exchange unit provided with a heat exchanger (30).
　図１に示すように、室外ユニット（10）は、扁平な直方体状のケーシング（11）を備える。ケーシング（11）の前面には、吹出口（12）が形成される。また、図１には現れないが、ケーシング（11）の背面と一方の側面には、吸込口が形成される。室外ユニット（10）のケーシング（11）には、本実施形態の熱交換器（30）が、圧縮機およびファン等の構成機器と共に収容される。 As shown in FIG. 1, the outdoor unit (10) includes a flat rectangular parallelepiped casing (11). An air outlet (12) is formed on the front surface of the casing (11). Further, although not shown in FIG. 1, suction ports are formed on the back surface and one side surface of the casing (11). The heat exchanger (30) of the present embodiment is housed in the casing (11) of the outdoor unit (10) together with constituent devices such as a compressor and a fan.
　　－熱交換器－
　図２に示すように、熱交換器（30）は、フィン・アンド・チューブ型の熱交換器である。熱交換器（30）は、冷媒をファンによって供給された空気と熱交換させる。熱交換器（30）は、複数のフィン（45）と、複数の伝熱管（40）と、一対のヘッダ部材（61,62）とを備える。熱交換器（30）は、平面視でＬ字状に形成される。熱交換器（30）は、ケーシング（11）の吸込口（具体的には、ケーシング（11）の背面と一方の側面）に沿って配置される。 -Heat exchanger-
As shown in FIG. 2, the heat exchanger (30) is a fin-and-tube type heat exchanger. The heat exchanger (30) exchanges heat with the air supplied by the fan. The heat exchanger (30) includes a plurality of fins (45), a plurality of heat transfer tubes (40), and a pair of header members (61,62). The heat exchanger (30) is formed in an L shape in a plan view. The heat exchanger (30) is arranged along the suction port (specifically, the back surface and one side surface of the casing (11)) of the casing (11).
　　　〈フィン〉
　図４に示すように、フィン（45）は、概ね長方形板状に形成され、その長辺が上下方向となる姿勢で配置される。フィン（45）の材質は、アルミニウム合金である。 <fin>
As shown in FIG. 4, the fins (45) are formed in a substantially rectangular plate shape, and are arranged so that their long sides are in the vertical direction. The material of the fin (45) is an aluminum alloy.
　フィン（45）には、複数の管用開口（46）が形成される。管用開口（46）は、フィン（45）の一方の長辺から他方の長辺（図４における左側の長辺から右側の長辺）に向かって延びる切り込みである。管用開口（46）の形状は、フィン（45）の短辺に沿った細長い形状である。複数の管用開口（46）は、フィン（45）の長手方向に互いに一定の間隔をおいて一列に配置される。 A plurality of pipe openings (46) are formed in the fin (45). The pipe opening (46) is a notch extending from one long side of the fin (45) toward the other long side (from the long side on the left side to the long side on the right side in FIG. 4). The shape of the pipe opening (46) is an elongated shape along the short side of the fin (45). The plurality of tube openings (46) are arranged in a row at regular intervals from each other in the longitudinal direction of the fins (45).
　各フィン（45）では、そのフィン（45）に形成された全ての管用開口（46）が開口列（50）を構成する。また、各フィン（45）では、その開口列（50）の最も下方に位置する管用開口（46）が、非挿通開口（47）となる。 In each fin (45), all the pipe openings (46) formed in the fin (45) form an opening row (50). Further, in each fin (45), the pipe opening (46) located at the lowermost position of the opening row (50) is the non-insertion opening (47).
　図３に示すように、熱交換器（30）において、複数のフィン（45）は、互いに向かい合う姿勢で、一定の間隔をおいて配置される。 As shown in FIG. 3, in the heat exchanger (30), the plurality of fins (45) are arranged at regular intervals in a posture facing each other.
　　　〈伝熱管〉
　図３及び図４に示すように、伝熱管（40）は、幅が厚さよりも長い扁平な形状に形成される。伝熱管（40）の材質は、アルミニウム合金である。熱交換器（30）において、複数の伝熱管（40）は、それぞれの長手方向が概ね水平方向となる姿勢で、フィン（45）と交わるように配置される。また、複数の伝熱管（40）は、上下方向に互いに一定の間隔をおいて配置される。 <Heat transfer tube>
As shown in FIGS. 3 and 4, the heat transfer tube (40) is formed in a flat shape having a width longer than the thickness. The material of the heat transfer tube (40) is an aluminum alloy. In the heat exchanger (30), the plurality of heat transfer tubes (40) are arranged so as to intersect the fins (45) in a posture in which their longitudinal directions are substantially horizontal. Further, the plurality of heat transfer tubes (40) are arranged at regular intervals in the vertical direction.
　図４に示すように、伝熱管（40）は、フィン（45）の各管用開口（46）に一本ずつ差し込まれ、フィン（45）とロウ付け等によって接合される。ただし、本実施形態の熱交換器（30）では、各フィン（45）の非挿通開口（47）に伝熱管（40）が差し込まれない。各フィン（45）の開口列（50）では、その最も下方に位置する非挿通開口（47）以外の管用開口（46）に、伝熱管（40）が差し込まれる。 As shown in FIG. 4, one heat transfer tube (40) is inserted into each tube opening (46) of the fin (45) and is joined to the fin (45) by brazing or the like. However, in the heat exchanger (30) of the present embodiment, the heat transfer tube (40) is not inserted into the non-insertion opening (47) of each fin (45). In the opening row (50) of each fin (45), a heat transfer tube (40) is inserted into a tube opening (46) other than the non-insertion opening (47) located at the lowermost position thereof.
　　　〈ヘッダ部材〉
　図３に示すように、各ヘッダ部材（61,62）は、両端が閉塞された筒状の部材である。ヘッダ部材（61,62）の材質は、アルミニウム合金である。各ヘッダ部材（61,62）は、その軸方向が上下方向となる姿勢で配置される。熱交換器（30）では、伝熱管（40）の一端と他端に、ヘッダ部材（61,62）が一つずつ接続される。 <Header member>
As shown in FIG. 3, each header member (61,62) is a tubular member with both ends closed. The material of the header member (61,62) is an aluminum alloy. Each header member (61,62) is arranged in a posture in which its axial direction is in the vertical direction. In the heat exchanger (30), header members (61,62) are connected one by one to one end and the other end of the heat transfer tube (40).
　各ヘッダ部材（61,62）の内部空間は、そのヘッダ部材（61,62）に接続する伝熱管（40）と連通する。各ヘッダ部材（61,62）において、その内部空間の底壁面（63）は、フィン（45）の非挿通開口（47）よりも上方に位置する。 The internal space of each header member (61,62) communicates with the heat transfer tube (40) connected to the header member (61,62). In each header member (61,62), the bottom wall surface (63) of its interior space is located above the non-insertion opening (47) of the fin (45).
　　　〈熱交換器の配置〉
　図４に示すように、熱交換器（30）は、その下端付近の部分が、ドレンパン（13）に入り込んでいる。ドレンパン（13）は、室外ユニット（10）のケーシング（11）の底板に形成された凹部である。ドレンパン（13）は、蒸発器として機能する熱交換器（30）において生成した凝縮水を受ける。ドレンパン（13）の上縁（13a）は、フィン（45）の非挿通開口（47）よりも上方に位置する。 <Arrangement of heat exchangers>
As shown in FIG. 4, the portion of the heat exchanger (30) near the lower end is inserted into the drain pan (13). The drain pan (13) is a recess formed in the bottom plate of the casing (11) of the outdoor unit (10). The drain pan (13) receives the condensed water generated in the heat exchanger (30), which functions as an evaporator. The upper edge (13a) of the drain pan (13) is located above the non-insertion opening (47) of the fin (45).
　　　〈熱交換器の機能〉
　上述したように、熱交換器（30）は、冷媒を空気と熱交換させる。空気調和機の暖房運転において、室外ユニット（10）に設けられた熱交換器（30）は、蒸発器として機能する。蒸発器として機能する熱交換器（30）において、一方のヘッダ部材（61）へ流入した冷媒は、複数の伝熱管（40）に別れて流入し、フィン（45）の間を通過する空気から吸熱して蒸発する。各伝熱管（40）を通過した冷媒は、他方のヘッダ部材（62）へ流入して合流し、その後に熱交換器（30）から流出する。 <Function of heat exchanger>
As described above, the heat exchanger (30) heat exchanges the refrigerant with air. In the heating operation of the air conditioner, the heat exchanger (30) provided in the outdoor unit (10) functions as an evaporator. In the heat exchanger (30) that functions as an evaporator, the refrigerant that has flowed into one of the header members (61) is separated into a plurality of heat transfer tubes (40) and flows in from the air that passes between the fins (45). It absorbs heat and evaporates. The refrigerant that has passed through each heat transfer tube (40) flows into the other header member (62), merges, and then flows out from the heat exchanger (30).
　フィン（45）の表面では、空気に含まれる水蒸気が凝縮して凝縮水が生成する。生成した凝縮水は、フィン（45）を伝って下方へ流れ落ち、ドレンパン（13）を通ってケーシング（11）の外部へ排出される。 On the surface of the fin (45), water vapor contained in the air is condensed to generate condensed water. The generated condensed water flows down along the fin (45), passes through the drain pan (13), and is discharged to the outside of the casing (11).
　　－実施形態１の特徴（１）－
　本実施形態の熱交換器（30）は、互いに平行に配置された複数の伝熱管（40）と、複数の板状のフィン（45）とを備える。フィン（45）には、伝熱管（40）を挿し通すための複数の管用開口（46）が形成される。フィン（45）は、長手方向が上下方向となるように配置される。また、フィン（45）は、開口列（50）を一つだけ有する。開口列（50）は、フィン（45）の長手方向に一列に並んだ複数の管用開口（46）によって構成される。開口列（50）において最も下方に位置する管用開口（46）は、伝熱管（40）が挿し通されない非挿通開口（47）である。 -Features of Embodiment 1 (1)-
The heat exchanger (30) of the present embodiment includes a plurality of heat transfer tubes (40) arranged in parallel with each other and a plurality of plate-shaped fins (45). The fin (45) is formed with a plurality of tube openings (46) for inserting the heat transfer tube (40). The fins (45) are arranged so that the longitudinal direction is the vertical direction. Also, the fins (45) have only one opening row (50). The opening row (50) is composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45). The tube opening (46) located at the lowermost position in the opening row (50) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted.
　本実施形態の熱交換器（30）では、各フィン（45）に開口列（50）が一つだけ設けられる。フィン（45）の開口列（50）において、最も下方に位置する管用開口（46）である非挿通開口（47）には、伝熱管（40）が挿し通されない。本実施形態では、凝縮水が滞留しやすい熱交換器（30）の下端部に、伝熱管（40）が設けられない。従って、本実施形態によれば、凝縮水によって伝熱管（40）が腐食する可能性を低減でき、熱交換器（30）の信頼性を向上させることができる。 In the heat exchanger (30) of this embodiment, only one opening row (50) is provided for each fin (45). In the opening row (50) of the fins (45), the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46). In the present embodiment, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to the present embodiment, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
　　－実施形態１の特徴（２）－
　本実施形態の熱交換器（30）は、伝熱管（40）の材質がアルミニウム合金である。 -Features of Embodiment 1 (2)-
In the heat exchanger (30) of the present embodiment, the material of the heat transfer tube (40) is an aluminum alloy.
　アルミニウムは、銅に比べてイオン化傾向が大きく、一般的に銅よりも腐食しやすい。本実施形態では、銅製の伝熱管に比べて腐食しやすいアルミニウム合金製の伝熱管（40）を備えた熱交換器（30）において、伝熱管（40）の腐食を抑制できる。 Aluminum has a higher ionization tendency than copper and is generally more susceptible to corrosion than copper. In the present embodiment, the corrosion of the heat transfer tube (40) can be suppressed in the heat exchanger (30) provided with the heat transfer tube (40) made of an aluminum alloy, which is more easily corroded than the heat transfer tube made of copper.
　　－実施形態１の特徴（３）－
　本実施形態の熱交換器（30）において、伝熱管（40）は、幅が厚さよりも長い扁平な形状である。 -Features of Embodiment 1 (3)-
In the heat exchanger (30) of the present embodiment, the heat transfer tube (40) has a flat shape having a width longer than a thickness.
　本実施形態の熱交換器（30）には、厚さよりも幅が長い扁平な形状の伝熱管が設けられる。このような扁平な形状の伝熱管（40）は、円管状の伝熱管に比べて、その表面に凝縮水が滞留しやすい。本実施形態によれば、円管状の伝熱管に比べて凝縮水が滞留しやすい扁平な形状の伝熱管（40）を備えた熱交換器（30）において、伝熱管（40）の腐食を抑制できる。 The heat exchanger (30) of the present embodiment is provided with a flat heat transfer tube having a width longer than the thickness. A heat transfer tube (40) having such a flat shape is more likely to retain condensed water on its surface than a circular tubular heat transfer tube. According to the present embodiment, in a heat exchanger (30) provided with a flat-shaped heat transfer tube (40) in which condensed water tends to stay as compared with a circular tubular heat transfer tube, corrosion of the heat transfer tube (40) is suppressed. it can.
　　－実施形態１の特徴（４）－
　本実施形態の熱交換器（30）は、ヘッダ部材（61,62）を備える。ヘッダ部材（61,62）は、フィン（45）の長手方向に沿って延びる筒状に形成され、伝熱管（40）に接続して内部空間が伝熱管（40）に連通する。ヘッダ部材（61,62）の内部空間の底壁面（63）は、開口列（50）の非挿通開口（47）よりも上方に位置する。 -Features of Embodiment 1 (4)-
The heat exchanger (30) of this embodiment includes header members (61,62). The header members (61,62) are formed in a tubular shape extending along the longitudinal direction of the fins (45), and are connected to the heat transfer tube (40) so that the internal space communicates with the heat transfer tube (40). The bottom wall surface (63) of the internal space of the header member (61,62) is located above the non-insertion opening (47) of the opening row (50).
　本実施形態の熱交換器（30）では、ヘッダ部材（61,62）において冷媒が流れる内部空間は、その底壁面（63）がフィン（45）の開口列（50）の非挿通開口（47）よりも上に位置する。このため、熱交換器（30）が蒸発器として機能するときに、熱交換器（30）の下端部の温度が他の部分の温度に比べて高くなり、熱交換器（30）の下端部における凝縮水の滞留が抑制される。 In the heat exchanger (30) of the present embodiment, the internal space through which the refrigerant flows in the header members (61,62) has a non-insertion opening (47) in which the bottom wall surface (63) is a fin (45) opening row (50). ) Is located above. Therefore, when the heat exchanger (30) functions as an evaporator, the temperature at the lower end of the heat exchanger (30) becomes higher than the temperature of other parts, and the lower end of the heat exchanger (30) becomes higher. The retention of condensed water in the water is suppressed.
　　－実施形態１の特徴（５）－
　本実施形態の室外ユニット（10）は、熱交換器（30）と、熱交換器（30）へ空気を送るファンと、ドレンパン（13）とを備える。ドレンパン（13）は、熱交換器（30）の下方に設けられ、熱交換器（30）で生成した凝縮水を受ける。熱交換器（30）は、フィン（45）の開口列（50）の非挿通開口（47）が、ドレンパン（13）の上縁（13a）よりも下方に位置する。 -Features of Embodiment 1 (5)-
The outdoor unit (10) of the present embodiment includes a heat exchanger (30), a fan that sends air to the heat exchanger (30), and a drain pan (13). The drain pan (13) is provided below the heat exchanger (30) and receives the condensed water generated by the heat exchanger (30). In the heat exchanger (30), the non-insertion opening (47) of the opening row (50) of the fins (45) is located below the upper edge (13a) of the drain pan (13).
　本実施形態の室外ユニット（10）では、熱交換器（30）の下端部がドレンパン（13）の上縁（13a）よりも下方に位置しており、熱交換器（30）の下端部が凝縮水に長時間に亘って浸かるおそれがある。一方、本実施形態の熱交換器（30）では、フィン（45）のうちドレンパン（13）の上縁（13a）よりも下方に位置する部分に形成された管用開口（46）が、非挿通開口（47）となる。このため、熱交換器（30）の下端部に伝熱管（40）は設けられず、従って、熱交換器（30）の伝熱管（40）が腐食する可能性を低減できる。 In the outdoor unit (10) of the present embodiment, the lower end of the heat exchanger (30) is located below the upper edge (13a) of the drain pan (13), and the lower end of the heat exchanger (30) is located. It may be immersed in condensed water for a long time. On the other hand, in the heat exchanger (30) of the present embodiment, the pipe opening (46) formed in the portion of the fin (45) located below the upper edge (13a) of the drain pan (13) is not inserted. It becomes an opening (47). Therefore, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30), and therefore the possibility that the heat transfer tube (40) of the heat exchanger (30) is corroded can be reduced.
　《実施形態２》
　実施形態２について説明する。本実施形態は、空気調和機の室内ユニット（20）である。この室内ユニット（20）は、熱交換器（30）を備えた熱交換ユニットである。 << Embodiment 2 >>
The second embodiment will be described. The present embodiment is an indoor unit (20) of an air conditioner. This indoor unit (20) is a heat exchange unit provided with a heat exchanger (30).
　図５に示すように、室内ユニット（20）は、箱状のケーシング（21）を備える。ケーシング（21）は、横長の直方体状に形成される。ケーシング（21）の上面には、吸込口（22）が形成される。ケーシング（21）の下面には、吹出口（23）が形成される。ケーシング（21）の内部には、熱交換器（30）とファン（24）とが収容される。ファン（24）は、いわゆるクロスフローファンであって、その回転軸がケーシング（21）の長手方向（図５の紙面に垂直な方向）に沿う姿勢で配置される。ケーシング（21）には、ファン（24）の前方（図５における左方）に位置する前方ドレンパン（25）と、ファン（24）の後方（図５における右方）に位置する後方ドレンパン（26）とが形成される。 As shown in FIG. 5, the indoor unit (20) includes a box-shaped casing (21). The casing (21) is formed in a horizontally long rectangular parallelepiped shape. A suction port (22) is formed on the upper surface of the casing (21). An air outlet (23) is formed on the lower surface of the casing (21). A heat exchanger (30) and a fan (24) are housed inside the casing (21). The fan (24) is a so-called cross-flow fan, and its rotation axis is arranged in a posture along the longitudinal direction (direction perpendicular to the paper surface of FIG. 5) of the casing (21). The casing (21) has a front drain pan (25) located in front of the fan (24) (left in FIG. 5) and a rear drain pan (26) located behind the fan (24) (right in FIG. 5). ) And are formed.
　　－熱交換器－
　熱交換器（30）は、ファン（24）の前方から上方に亘って配置される。熱交換器（30）は、第１熱交換部（31）と、第２熱交換部（32）と、第３熱交換部（33）とを備える。第１熱交換部（31）と第２熱交換部（32）と第３熱交換部（33）のそれぞれは、二列構造である。 -Heat exchanger-
The heat exchanger (30) is arranged from the front to the top of the fan (24). The heat exchanger (30) includes a first heat exchange unit (31), a second heat exchange unit (32), and a third heat exchange unit (33). Each of the first heat exchange section (31), the second heat exchange section (32), and the third heat exchange section (33) has a two-row structure.
　　　〈第１熱交換部〉
　第１熱交換部（31）は、ファン（24）の前方（図５における左方）に配置される。第１熱交換部（31）の下端付近の部分は、前方ドレンパン（25）に入り込む。第１熱交換部（31）は、その上部が下部よりもケーシング（21）の前面寄り（図５の左寄り）となるように傾斜している。 <1st heat exchange section>
The first heat exchange unit (31) is arranged in front of the fan (24) (left side in FIG. 5). The portion near the lower end of the first heat exchange portion (31) enters the front drain pan (25). The first heat exchange portion (31) is inclined so that the upper portion thereof is closer to the front surface (to the left side in FIG. 5) of the casing (21) than the lower portion.
　第１熱交換部（31）は、第１風上列部（31a）と第１風下列部（31b）とを有する。第１風上列部（31a）と第１風下列部（31b）は、互いに重なり合うように配置される。第１風下列部（31b）は、第１風上列部（31a）よりもファン（24）寄りに配置される。 The first heat exchange section (31) has a first windward row section (31a) and a first leeward row section (31b). The first leeward row portion (31a) and the first leeward row portion (31b) are arranged so as to overlap each other. The first leeward row portion (31b) is arranged closer to the fan (24) than the first leeward row portion (31a).
　図６に示すように、第１風上列部（31a）と第１風下列部（31b）のそれぞれは、複数の長方形板状のフィン（45）と、複数の扁平な形状の伝熱管（40）と、一対の筒状のヘッダ部材（61,62）とを備え、実施形態１の熱交換器（30）と同様に構成される。 As shown in FIG. 6, each of the first leeward row portion (31a) and the first leeward row portion (31b) has a plurality of rectangular plate-shaped fins (45) and a plurality of flat-shaped heat transfer tubes ( 40) and a pair of tubular header members (61,62) are provided, and are configured in the same manner as the heat exchanger (30) of the first embodiment.
　具体的に、第１風上列部（31a）及び第１風下列部（31b）の各フィン（45）には、開口列（50a）が一つずつ形成される。第１風上列部（31a）と第１風下列部（31b）のそれぞれにおいて、各フィン（45）の開口列（50a）の最も下方に位置する管用開口（46）は、非挿通開口（47）となる。また、第１風上列部（31a）と第１風下列部（31b）のそれぞれにおいて、各ヘッダ部材（61,62）の内部空間の底壁面（63）は、非挿通開口（47）よりも上方に位置する。フィン（45）、伝熱管（40）、及びヘッダ部材（61,62）の材質は、何れもアルミニウム合金である。 Specifically, one opening row (50a) is formed in each fin (45) of the first leeward row portion (31a) and the first leeward row portion (31b). In each of the first leeward row (31a) and the first leeward row (31b), the pipe opening (46) located at the bottom of the opening row (50a) of each fin (45) is a non-insertion opening ( 47). Further, in each of the first leeward row portion (31a) and the first leeward row portion (31b), the bottom wall surface (63) of the internal space of each header member (61, 62) is formed from the non-insertion opening (47). Is also located above. The fins (45), heat transfer tubes (40), and header members (61,62) are all made of aluminum alloy.
　ただし、第１風上列部（31a）と第１風下列部（31b）とは、伝熱管（40）が直線状に延びる平坦な形状に形成される点において、平面視でＬ字状に形成された実施形態１の熱交換器（30）と異なる。また、第１風上列部（31a）と第１風下列部（31b）のそれぞれは、フィン（45）の枚数および大きさと、伝熱管（40）の本数および長さと、ヘッダ部材（61,62）の形状とが、実施形態１の熱交換器（30）と異なる。また、第１風上列部（31a）の開口列（50a）を構成する管用開口（46）の位置と、第１風下列部（31b）の開口列（50a）を構成する管用開口（46）の位置とは、互いにフィン（45）の長手方向に１／２ピッチずれている。 However, the first leeward row portion (31a) and the first leeward row portion (31b) are L-shaped in a plan view in that the heat transfer tube (40) is formed in a flat shape extending linearly. It is different from the formed heat exchanger (30) of the first embodiment. In addition, the number and size of fins (45), the number and length of heat transfer tubes (40), and the header members (61, respectively) of the first windward row portion (31a) and the first windward row portion (31b) are provided. The shape of 62) is different from that of the heat exchanger (30) of the first embodiment. Further, the positions of the pipe openings (46) forming the opening row (50a) of the first leeward row portion (31a) and the pipe openings (46) forming the opening row (50a) of the first leeward row portion (31b). ) Are deviated by 1/2 pitch from each other in the longitudinal direction of the fins (45).
　　　〈第２熱交換部〉
　第２熱交換部（32）は、第１熱交換部（31）の上方に配置される。第２熱交換部（32）の下端部は、第１熱交換部（31）の上端部と接する。第２熱交換部（32）は、その上部が下部よりもケーシング（21）の背面寄り（図５の右寄り）となるように傾斜している。 <Second heat exchange section>
The second heat exchange section (32) is arranged above the first heat exchange section (31). The lower end of the second heat exchange section (32) is in contact with the upper end of the first heat exchange section (31). The second heat exchange portion (32) is inclined so that the upper portion thereof is closer to the back surface (to the right side in FIG. 5) of the casing (21) than the lower portion.
　第２熱交換部（32）は、第２風上列部（32a）と第２風下列部（32b）とを有する。第２風上列部（32a）と第２風下列部（32b）は、互いに重なり合うように配置される。第２風下列部（32b）は、第２風上列部（32a）よりもファン（24）寄りに配置される。 The second heat exchange section (32) has a second upwind row section (32a) and a second leeward row section (32b). The second leeward row (32a) and the second leeward row (32b) are arranged so as to overlap each other. The second leeward row (32b) is located closer to the fan (24) than the second leeward row (32a).
　図７に示すように、第２風上列部（32a）と第２風下列部（32b）のそれぞれは、複数の長方形板状のフィン（45）と、複数の扁平な形状の伝熱管（40）と、一対の筒状のヘッダ部材（61,62）とを備え、実施形態１の熱交換器（30）と同様に構成される。フィン（45）、伝熱管（40）、及びヘッダ部材（61,62）の材質は、何れもアルミニウム合金である。 As shown in FIG. 7, each of the second leeward row (32a) and the second leeward row (32b) has a plurality of rectangular plate-shaped fins (45) and a plurality of flat heat transfer tubes ( 40) and a pair of tubular header members (61,62) are provided, and are configured in the same manner as the heat exchanger (30) of the first embodiment. The fins (45), heat transfer tubes (40), and header members (61,62) are all made of aluminum alloy.
　第２風上列部（32a）及び第２風下列部（32b）を構成するフィン（45）の長手方向は、第１風上列部（31a）及び第１風下列部（31b）を構成するフィン（45）の長手方向に対して、ケーシング（21）の背面側に向かって傾斜している。 The longitudinal direction of the fins (45) constituting the second leeward row portion (32a) and the second leeward row portion (32b) constitutes the first leeward row portion (31a) and the first leeward row portion (31b). It is inclined toward the back surface side of the casing (21) with respect to the longitudinal direction of the fins (45).
　実施形態１の熱交換器（30）と同様に、第２風上列部（32a）及び第２風下列部（32b）の各フィン（45）には、開口列（50b）が一つずつ形成される。ただし、第２風上列部（32a）と第２風下列部（32b）のそれぞれにおいて、フィン（45）に形成された開口列（50b）の最も下方に位置する管用開口（46）には、非流通管（41）が差し込まれる。第２風上列部（32a）と第２風下列部（32b）のそれぞれにおいて、各ヘッダ部材（61,62）の内部空間の底壁面（63）は、非流通管（41）よりも上方に位置する。そのため、非流通管（41）は、各ヘッダ部材（61,62）の内部空間に連通しない。従って、非流通管（41）において冷媒は流通しない。 Similar to the heat exchanger (30) of the first embodiment, each fin (45) of the second windward row portion (32a) and the second windward row portion (32b) has one opening row (50b). It is formed. However, in each of the second leeward row (32a) and the second leeward row (32b), the pipe opening (46) located at the lowermost position of the opening row (50b) formed in the fins (45) , Non-distribution pipe (41) is inserted. In each of the second leeward row (32a) and the second leeward row (32b), the bottom wall surface (63) of the internal space of each header member (61,62) is above the non-circulation pipe (41). Located in. Therefore, the non-circulation pipe (41) does not communicate with the internal space of each header member (61,62). Therefore, the refrigerant does not flow in the non-distribution pipe (41).
　更に、第２風上列部（32a）と第２風下列部（32b）とは、伝熱管（40）が直線状に延びる平坦な形状に形成される点において、平面視でＬ字状に形成された実施形態１の熱交換器（30）と異なる。また、第２風上列部（32a）と第２風下列部（32b）のそれぞれは、フィン（45）の枚数および大きさと、伝熱管（40）の本数および長さと、ヘッダ部材（61,62）の形状とが、実施形態１の熱交換器（30）と異なる。また、第２風上列部（32a）の開口列（50b）を構成する管用開口（46）の位置と、第２風下列部（32b）の開口列（50b）を構成する管用開口（46）の位置とは、互いにフィン（45）の長手方向に１／２ピッチずれている。 Further, the second leeward row portion (32a) and the second leeward row portion (32b) are L-shaped in a plan view in that the heat transfer tube (40) is formed in a flat shape extending linearly. It is different from the formed heat exchanger (30) of the first embodiment. In addition, the number and size of fins (45), the number and length of heat transfer tubes (40), and the header members (61, respectively) of the second windward row portion (32a) and the second windward row portion (32b) are provided. The shape of 62) is different from that of the heat exchanger (30) of the first embodiment. Further, the positions of the pipe openings (46) forming the opening row (50b) of the second leeward row (32a) and the pipe openings (46) forming the opening row (50b) of the second leeward row (32b). ) Are deviated by 1/2 pitch from each other in the longitudinal direction of the fins (45).
　　　〈第３熱交換部〉
　第３熱交換部（33）は、第２熱交換部（32）の後方（図５における右方）に配置される。第３熱交換部（33）の上端部は、第２熱交換部（32）の上端部と接する。第３熱交換部（33）の下端付近の部分は、後方ドレンパン（26）に入り込む。第３熱交換部（33）は、その上部が下部よりもケーシング（21）の前面寄り（図５の左寄り）となるように傾斜している。 <Third heat exchange section>
The third heat exchange unit (33) is arranged behind the second heat exchange unit (32) (on the right side in FIG. 5). The upper end of the third heat exchange section (33) is in contact with the upper end of the second heat exchange section (32). The portion near the lower end of the third heat exchange portion (33) enters the rear drain pan (26). The third heat exchange portion (33) is inclined so that the upper portion thereof is closer to the front surface (to the left side in FIG. 5) of the casing (21) than the lower portion.
　第３熱交換部（33）は、第３風上列部（33a）と第３風下列部（33b）とを有する。第３風上列部（33a）と第３風下列部（33b）は、互いに重なり合うように配置される。第３風下列部（33b）は、第３風上列部（33a）よりもファン（24）寄りに配置される。 The third heat exchange section (33) has a third upwind row section (33a) and a third leeward row section (33b). The third leeward row (33a) and the third leeward row (33b) are arranged so as to overlap each other. The third leeward row (33b) is located closer to the fan (24) than the third leeward row (33a).
　図６に示すように、第３風上列部（33a）と第３風下列部（33b）のそれぞれは、複数の長方形板状のフィン（45）と、複数の扁平な形状の伝熱管（40）と、一対の筒状のヘッダ部材（61,62）とを備え、実施形態１の熱交換器（30）と同様に構成される。 As shown in FIG. 6, each of the third leeward row (33a) and the third leeward row (33b) has a plurality of rectangular plate-shaped fins (45) and a plurality of flat heat transfer tubes ( 40) and a pair of tubular header members (61,62) are provided, and are configured in the same manner as the heat exchanger (30) of the first embodiment.
　具体的に、第３風上列部（33a）及び第３風下列部（33b）の各フィン（45）には、開口列（50c）が一つずつ形成される。第３風上列部（33a）と第３風下列部（33b）のそれぞれにおいて、各フィン（45）の開口列（50c）の最も下方に位置する管用開口（46）は、非挿通開口（47）となる。また、第３風上列部（33a）と第３風下列部（33b）のそれぞれにおいて、各ヘッダ部材（61,62）の内部空間の底壁面（63）は、非挿通開口（47）よりも上方に位置する。フィン（45）、伝熱管（40）、及びヘッダ部材（61,62）の材質は、何れもアルミニウム合金である。 Specifically, one opening row (50c) is formed in each fin (45) of the third leeward row portion (33a) and the third leeward row portion (33b). In each of the third leeward row (33a) and the third leeward row (33b), the pipe opening (46) located at the bottom of the opening row (50c) of each fin (45) is a non-insertion opening ( 47). Further, in each of the third leeward row portion (33a) and the third leeward row portion (33b), the bottom wall surface (63) of the internal space of each header member (61, 62) is formed from the non-insertion opening (47). Is also located above. The fins (45), heat transfer tubes (40), and header members (61,62) are all made of aluminum alloy.
　ただし、第３風上列部（33a）と第３風下列部（33b）とは、伝熱管（40）が直線状に延びる平坦な形状に形成される点において、平面視でＬ字状に形成された実施形態１の熱交換器（30）と異なる。また、第３風上列部（33a）と第３風下列部（33b）のそれぞれは、フィン（45）の枚数および大きさと、伝熱管（40）の本数および長さと、ヘッダ部材（61,62）の形状とが、実施形態１の熱交換器（30）と異なる。また、第３風上列部（33a）の開口列（50c）を構成する管用開口（46）の位置と、第３風下列部（33b）の開口列（50c）を構成する管用開口（46）の位置とは、互いにフィン（45）の長手方向に１／２ピッチずれている。 However, the third leeward row portion (33a) and the third leeward row portion (33b) are L-shaped in a plan view in that the heat transfer tube (40) is formed in a flat shape extending linearly. It is different from the formed heat exchanger (30) of the first embodiment. In addition, the number and size of fins (45), the number and length of heat transfer tubes (40), and the header members (61, respectively) of the third windward row portion (33a) and the third windward row portion (33b) are provided. The shape of 62) is different from that of the heat exchanger (30) of the first embodiment. Further, the positions of the pipe openings (46) forming the opening row (50c) of the third leeward row (33a) and the pipe openings (46) forming the opening row (50c) of the third leeward row (33b). ) Are deviated by 1/2 pitch from each other in the longitudinal direction of the fins (45).
　　　〈熱交換器の機能〉
　熱交換器（30）は、冷媒を空気と熱交換させる。空気調和機の冷房運転において、室内ユニット（20）に設けられた熱交換器（30）は、蒸発器として機能する。蒸発器として機能する熱交換器（30）では、伝熱管（40）を流れる冷媒が、フィン（45）の間を通過する空気から吸熱して蒸発する。 <Function of heat exchanger>
The heat exchanger (30) exchanges heat with the air for the refrigerant. In the cooling operation of the air conditioner, the heat exchanger (30) provided in the indoor unit (20) functions as an evaporator. In the heat exchanger (30), which functions as an evaporator, the refrigerant flowing through the heat transfer tube (40) absorbs heat from the air passing between the fins (45) and evaporates.
　蒸発器として機能する熱交換器（30）のフィン（45）の表面では、空気に含まれる水蒸気が凝縮して凝縮水が生成する。生成した凝縮水は、フィン（45）を伝って下方へ流れ落ちる。第１熱交換部（31）において生成した凝縮水は、第１熱交換部（31）のフィン（45）を伝って前方ドレンパン（25）に流れ落ちる。第２熱交換部（32）において生成した凝縮水は、第２熱交換部（32）のフィン（45）を伝って流れ落ち、その後に第１熱交換部（31）のフィン（45）を伝って前方ドレンパン（25）に流れ落ちる。第３熱交換部（33）において生成した凝縮水は、第３熱交換部（33）のフィン（45）を伝って後方ドレンパン（26）に流れ落ちる。 On the surface of the fins (45) of the heat exchanger (30) that functions as an evaporator, the water vapor contained in the air condenses to generate condensed water. The generated condensed water flows down along the fin (45). The condensed water generated in the first heat exchange section (31) flows down to the front drain pan (25) along the fins (45) of the first heat exchange section (31). The condensed water generated in the second heat exchange section (32) flows down along the fins (45) of the second heat exchange section (32), and then travels down the fins (45) of the first heat exchange section (31). It flows down to the front drain pan (25). The condensed water generated in the third heat exchange section (33) flows down to the rear drain pan (26) along the fins (45) of the third heat exchange section (33).
　　－実施形態２の特徴（１）－
　本実施形態の室内ユニット（20）は、熱交換器（30）と、熱交換器（30）へ空気を送るファン（24）と、ドレンパン（25,26）とを備える。ドレンパン（25,26）は、熱交換器（30）の下方に設けられ、熱交換器（30）で生成した凝縮水を受ける。本実施形態の熱交換器（30）は、第１熱交換部（31）のフィン（45）の開口列（50a）の非挿通開口（47）が、前方ドレンパン（25）の上縁（25a）よりも下方に位置する。また、本実施形態の熱交換器（30）は、第３熱交換部（33）のフィン（45）の開口列（50b）の非挿通開口（47）が、後方ドレンパン（26）の上縁（26a）よりも下方に位置する。 -Features of Embodiment 2 (1)-
The indoor unit (20) of the present embodiment includes a heat exchanger (30), a fan (24) for sending air to the heat exchanger (30), and a drain pan (25, 26). The drain pans (25,26) are provided below the heat exchanger (30) and receive the condensed water generated by the heat exchanger (30). In the heat exchanger (30) of the present embodiment, the non-insertion opening (47) of the opening row (50a) of the fins (45) of the first heat exchange section (31) has an upper edge (25a) of the front drain pan (25). ) Is located below. Further, in the heat exchanger (30) of the present embodiment, the non-insertion opening (47) of the opening row (50b) of the fins (45) of the third heat exchange section (33) is the upper edge of the rear drain pan (26). It is located below (26a).
　本実施形態の室内ユニット（20）では、第１熱交換部（31）の下端部が前方ドレンパン（25）の上縁（25a）よりも下方に位置し、第３熱交換部（33）の下端部が後方ドレンパン（26）の上縁（26a）よりも下方に位置する。このため、第１熱交換部（31）及び第３熱交換部（33）の下端部が、凝縮水に長時間に亘って浸かるおそれがある。 In the indoor unit (20) of the present embodiment, the lower end of the first heat exchange section (31) is located below the upper edge (25a) of the front drain pan (25), and the third heat exchange section (33) has a lower end portion. The lower end is located below the upper edge (26a) of the rear drain pan (26). Therefore, the lower ends of the first heat exchange section (31) and the third heat exchange section (33) may be immersed in the condensed water for a long time.
　一方、本実施形態の熱交換器（30）では、第１熱交換部（31）のフィン（45）のうち前方ドレンパン（25）の上縁（25a）よりも下方に位置する部分に形成された管用開口（46）が、非挿通開口（47）となる。また、この熱交換器（30）では、第３熱交換部（33）のフィン（45）のうち後方ドレンパン（26）の上縁（26a）よりも下方に位置する部分に形成された管用開口（46）が、非挿通開口（47）となる。このため、第１熱交換部（31）及び第３熱交換部（33）の下端部に伝熱管（40）は設けられず、従って、熱交換器（30）の伝熱管（40）が腐食する可能性を低減できる。 On the other hand, in the heat exchanger (30) of the present embodiment, it is formed in a portion of the fins (45) of the first heat exchange section (31) located below the upper edge (25a) of the front drain pan (25). The pipe opening (46) becomes the non-insertion opening (47). Further, in this heat exchanger (30), a pipe opening formed in a portion of the fins (45) of the third heat exchanger (33) located below the upper edge (26a) of the rear drain pan (26). (46) becomes the non-insertion opening (47). Therefore, the heat transfer tube (40) is not provided at the lower ends of the first heat exchange section (31) and the third heat exchange section (33), and therefore the heat transfer tube (40) of the heat exchanger (30) is corroded. The possibility of doing so can be reduced.
　　－実施形態２の特徴（２）－
　本実施形態の熱交換器（30）は、第１熱交換部（31）及び第２熱交換部（32）を備える。第１熱交換部（31）と第２熱交換部（32）のそれぞれは、フィン（45）と、フィン（45）の管用開口（46）に挿し通された伝熱管（40）とを有する。第２熱交換部（32）は、第１熱交換部（31）の上方に配置される。第２熱交換部（32）のフィン（45）の長手方向は、第１熱交換部（31）のフィン（45）の長手方向に対して傾斜する。第１熱交換部（31）のフィン（45）の開口列（50a）において、最も下方に位置する管用開口（46）が非挿通開口（47）となる。第２熱交換部（32）のフィン（45）の開口列（50b）において、最も下方に位置する管用開口（46）には、内部を流体が流通しない非流通管（41）が挿し通される。 -Features of Embodiment 2 (2)-
The heat exchanger (30) of the present embodiment includes a first heat exchange unit (31) and a second heat exchange unit (32). Each of the first heat exchange section (31) and the second heat exchange section (32) has a fin (45) and a heat transfer tube (40) inserted through a tube opening (46) of the fin (45). .. The second heat exchange section (32) is arranged above the first heat exchange section (31). The longitudinal direction of the fins (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fins (45) of the first heat exchange section (31). In the opening row (50a) of the fins (45) of the first heat exchange section (31), the pipe opening (46) located at the lowermost position is the non-insertion opening (47). In the opening row (50b) of the fins (45) of the second heat exchange section (32), a non-circulation pipe (41) through which fluid does not flow is inserted into the pipe opening (46) located at the lowermost position. To.
　本実施形態の熱交換器（30）では、第２熱交換部（32）のフィン（45）の開口列（50b）において、最も下方に位置する管用開口（46）に、非流通管（41）が挿し通される。仮に非流通管（41）が腐食しても、非流通管（41）から冷媒は漏洩しない。従って、この態様によれば、伝熱管（40）の腐食に起因して冷媒が漏洩する可能性と低減でき、熱交換器（30）の信頼性を高めることができる。 In the heat exchanger (30) of the present embodiment, in the opening row (50b) of the fins (45) of the second heat exchange section (32), the non-circulation pipe (41) is inserted into the pipe opening (46) located at the lowermost position. ) Is inserted. Even if the non-circulation pipe (41) is corroded, the refrigerant does not leak from the non-circulation pipe (41). Therefore, according to this aspect, the possibility of leakage of the refrigerant due to the corrosion of the heat transfer tube (40) can be reduced, and the reliability of the heat exchanger (30) can be improved.
　ここで、第２熱交換部（32）の非流通管（41）を省略すると、第２熱交換部（32）の下端付近の部分を、冷媒と熱交換せずに通過する空気の量が増加するため、熱交換器（30）の熱交換性能の低下を招くおそれがある。これに対し、本実施形態では、第２熱交換部（32）の下端付近に非流通管（41）を設けており、第２熱交換部（32）の下端付近を通過する空気の流量を、第２熱交換部（32）の他の部分を通過する空気の流量と同程度にすることができる。従って、本実施形態によれば、熱交換器（30）の熱交換性能の低下を回避できる。 Here, if the non-circulation pipe (41) of the second heat exchange section (32) is omitted, the amount of air passing through the portion near the lower end of the second heat exchange section (32) without heat exchange with the refrigerant is increased. As the number increases, the heat exchange performance of the heat exchanger (30) may deteriorate. On the other hand, in the present embodiment, the non-circulation pipe (41) is provided near the lower end of the second heat exchange section (32), and the flow rate of air passing near the lower end of the second heat exchange section (32) is measured. , The flow rate of air passing through the other part of the second heat exchange part (32) can be made similar. Therefore, according to the present embodiment, it is possible to avoid deterioration of the heat exchange performance of the heat exchanger (30).
　　－実施形態２の変形例－
　図８に示すように、本実施形態の熱交換器（30）では、第２熱交換部（32）を構成する第２風上列部（32a）と第２風下列部（32b）のそれぞれにおいて、フィン（45）に形成された開口列（50）の最も下方に位置する管用開口（46）が非挿通開口（47）となっていてもよい。本変形例の第２風上列部（32a）と第２風下列部（32b）のそれぞれに、非流通管（41）は設けられない。 -Modification of Embodiment 2-
As shown in FIG. 8, in the heat exchanger (30) of the present embodiment, each of the second upwind row portion (32a) and the second leeward row portion (32b) constituting the second heat exchange portion (32). The pipe opening (46) located at the lowermost position of the opening row (50) formed in the fins (45) may be a non-insertion opening (47). A non-circulation pipe (41) is not provided in each of the second leeward row portion (32a) and the second leeward row portion (32b) of this modification.
　　　〈変形例の特徴〉
　本変形例の熱交換器（30）は、第１熱交換部（31）及び第２熱交換部（32）を備える。第１熱交換部（31）と第２熱交換部（32）のそれぞれは、フィン（45）と、フィン（45）の管用開口（46）に挿し通された伝熱管（40）とを有する。第２熱交換部（32）は、第１熱交換部（31）の上方に配置される。第２熱交換部（32）のフィン（45）の長手方向は、第１熱交換部（31）のフィン（45）の長手方向に対して傾斜する。本変形例の熱交換器（30）では、第１熱交換部（31）のフィン（45）の開口列（50a）と、第２熱交換部（32）のフィン（45）の開口列（50b）のそれぞれにおいて、最も下方に位置する管用開口（46）が非挿通開口（47）となる。 <Characteristics of modified example>
The heat exchanger (30) of this modified example includes a first heat exchange unit (31) and a second heat exchange unit (32). Each of the first heat exchange section (31) and the second heat exchange section (32) has a fin (45) and a heat transfer tube (40) inserted through a tube opening (46) of the fin (45). .. The second heat exchange section (32) is arranged above the first heat exchange section (31). The longitudinal direction of the fins (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fins (45) of the first heat exchange section (31). In the heat exchanger (30) of this modification, the opening row (50a) of the fins (45) of the first heat exchange section (31) and the opening row (45) of the fins (45) of the second heat exchange section (32) ( In each of 50b), the lowermost pipe opening (46) is the non-insertion opening (47).
　本変形例の熱交換器（30）では、第１熱交換部（31）の上方に配置された第２熱交換部（32）が、第１熱交換部（31）に対して傾斜する。この熱交換器（30）が蒸発器として機能する場合、第２熱交換部（32）において生成した凝縮水は、その下方に位置する第１熱交換部（31）へと流れ落ちる。このため、第２熱交換部（32）の下端付近に凝縮水が滞留するおそれがある。 In the heat exchanger (30) of this modified example, the second heat exchange section (32) arranged above the first heat exchange section (31) is inclined with respect to the first heat exchange section (31). When this heat exchanger (30) functions as an evaporator, the condensed water generated in the second heat exchange section (32) flows down to the first heat exchange section (31) located below the heat exchanger (30). Therefore, condensed water may stay near the lower end of the second heat exchange section (32).
　これに対し、本変形例の熱交換器（30）では、第２熱交換部（32）のフィン（45）の開口列（50b）において、最も下方に位置する管用開口（46）が非挿通開口（47）となる。このため、第２熱交換部（32）の下端付近に伝熱管（40）が存在せず、従って、第２熱交換部（32）の伝熱管（40）が腐食する可能性を低減できる。 On the other hand, in the heat exchanger (30) of this modified example, the lowermost pipe opening (46) is not inserted in the opening row (50b) of the fins (45) of the second heat exchange section (32). It becomes an opening (47). Therefore, the heat transfer tube (40) does not exist near the lower end of the second heat exchange section (32), and therefore, the possibility that the heat transfer tube (40) of the second heat exchange section (32) is corroded can be reduced.
　《実施形態３》
　実施形態３について説明する。本実施形態は、実施形態２の室内ユニット（20）において、熱交換器（30）の構造を変更したものである。ここでは、本実施形態の室内ユニット（20）について、実施形態２の室内ユニット（20）と異なる点を説明する。 << Embodiment 3 >>
The third embodiment will be described. In this embodiment, the structure of the heat exchanger (30) is changed in the indoor unit (20) of the second embodiment. Here, the difference between the indoor unit (20) of the present embodiment and the indoor unit (20) of the second embodiment will be described.
　　－熱交換器－
　図９に示すように、本実施形態の熱交換器（30）は、いわゆるクロスフィン型のフィン・アンド・チューブ熱交換器である。この熱交換器（30）は、複数の板状のフィン（45）と、複数の円管状の伝熱管（40）とを備える。フィン（45）の材質は、アルミニウム合金である。伝熱管（40）の材質は、銅合金である。 -Heat exchanger-
As shown in FIG. 9, the heat exchanger (30) of the present embodiment is a so-called cross-fin type fin-and-tube heat exchanger. The heat exchanger (30) includes a plurality of plate-shaped fins (45) and a plurality of circular tubular heat transfer tubes (40). The material of the fin (45) is an aluminum alloy. The material of the heat transfer tube (40) is a copper alloy.
　熱交換器（30）は、ファン（24）の前方から上方に亘って配置される。熱交換器（30）は、前方熱交換部（35）と、後方熱交換部（36）とを備える。前方熱交換部（35）と後方熱交換部（36）のそれぞれは、二列構造である。 The heat exchanger (30) is arranged from the front to the top of the fan (24). The heat exchanger (30) includes a front heat exchange unit (35) and a rear heat exchange unit (36). Each of the front heat exchange section (35) and the rear heat exchange section (36) has a two-row structure.
　　　〈前方熱交換部〉
　前方熱交換部（35）は、ケーシング（21）の背面側（図５の右側）に湾曲している。前方熱交換部（35）は、ファン（24）の前方（図９における左方）から上方に亘って配置される。前方熱交換部（35）の下端付近の部分は、前方ドレンパン（25）に入り込む。 <Front heat exchange section>
The front heat exchange section (35) is curved toward the back side (right side in FIG. 5) of the casing (21). The front heat exchange section (35) is arranged from the front (left side in FIG. 9) of the fan (24) to the upper side. The portion near the lower end of the front heat exchange section (35) enters the front drain pan (25).
　前方熱交換部（35）は、複数の板状のフィン（45）と、複数の円管状の伝熱管（40）とを備える。フィン（45）は、細長い板状に形成される。フィン（45）の長手方向に沿った一対の長辺は、それぞれが湾曲しており、互いに実質的に平行である。前方熱交換部（35）は、フィン（45）の長手方向が上下方向となる姿勢で配置される。 The front heat exchange section (35) is provided with a plurality of plate-shaped fins (45) and a plurality of circular tubular heat transfer tubes (40). The fins (45) are formed in the shape of an elongated plate. The pair of long sides along the longitudinal direction of the fins (45) are curved and substantially parallel to each other. The front heat exchange section (35) is arranged so that the longitudinal direction of the fins (45) is in the vertical direction.
　フィン（45）には、複数の管用開口（46）が形成される。管用開口（46）は、フィン（45）を厚さ方向に貫通する円形の孔である。管用開口（46）は、フィン（45）の長手方向に沿った一対の長辺のそれぞれに沿って一列ずつ配置される。湾曲したフィン（45）の外側の長辺に沿った複数の管用開口（46）は、第１開口列（51a）を構成する。湾曲したフィン（45）の内側の長辺に沿った複数の管用開口（46）は、第２開口列（52a）を構成する。 A plurality of pipe openings (46) are formed in the fin (45). The pipe opening (46) is a circular hole that penetrates the fin (45) in the thickness direction. The pipe openings (46) are arranged in a row along each of the pair of long sides along the longitudinal direction of the fins (45). A plurality of pipe openings (46) along the outer long sides of the curved fins (45) form a first opening row (51a). A plurality of pipe openings (46) along the inner long sides of the curved fins (45) form a second opening row (52a).
　第１開口列（51a）と第２開口列（52a）のそれぞれにおいて、複数の管用開口（46）は、フィン（45）の長手方向に一列に配置される。第１開口列（51a）と第２開口列（52a）のそれぞれにおいて、複数の管用開口（46）は、フィン（45）の長手方向に互いに所定の間隔をおいて配置される。第１開口列（51a）を構成する管用開口（46）の位置と、第２開口列（52a）を構成する管用開口（46）の位置とは、互いにフィン（45）の長手方向に１／２ピッチずれている。第１開口列（51a）と第２開口列（52a）は、それぞれの最も下方に位置する管用開口（46）が、非挿通開口（47）となる。 In each of the first opening row (51a) and the second opening row (52a), the plurality of pipe openings (46) are arranged in a row in the longitudinal direction of the fins (45). In each of the first opening row (51a) and the second opening row (52a), the plurality of pipe openings (46) are arranged at predetermined intervals in the longitudinal direction of the fins (45). The position of the pipe opening (46) forming the first opening row (51a) and the position of the pipe opening (46) forming the second opening row (52a) are 1/1 in the longitudinal direction of the fins (45). It is off by 2 pitches. In the first opening row (51a) and the second opening row (52a), the pipe opening (46) located at the lowermost position thereof is a non-insertion opening (47).
　伝熱管（40）は、フィン（45）の各管用開口（46）に一本ずつ差し込まれる。ただし、前方熱交換部（35）では、各フィン（45）の非挿通開口（47）に伝熱管（40）が差し込まれない。各フィン（45）の第１開口列（51a）と第２開口列（52a）では、それぞれの最も下方に位置する非挿通開口（47）以外の管用開口（46）に、伝熱管（40）が差し込まれる。 One heat transfer tube (40) is inserted into each tube opening (46) of the fin (45). However, in the front heat exchange section (35), the heat transfer tube (40) is not inserted into the non-insertion opening (47) of each fin (45). In the first opening row (51a) and the second opening row (52a) of each fin (45), the heat transfer tube (40) is connected to the tube opening (46) other than the non-insertion opening (47) located at the lowermost position thereof. Is plugged in.
　　　〈後方熱交換部〉
　後方熱交換部（36）は、平坦な形状に形成される。後方熱交換部（36）は、ファン（24）の上方に配置される。後方熱交換部（36）の下端付近の部分は、後方ドレンパン（26）に入り込む。後方熱交換部（36）は、その上部が下部よりもケーシング（21）の前面寄り（図９の左寄り）となるように傾斜している。 <Rear heat exchange section>
The rear heat exchange section (36) is formed in a flat shape. The rear heat exchange section (36) is located above the fan (24). The portion near the lower end of the rear heat exchange section (36) enters the rear drain pan (26). The rear heat exchange portion (36) is inclined so that the upper portion thereof is closer to the front surface (to the left side in FIG. 9) of the casing (21) than the lower portion.
　後方熱交換部（36）は、複数の板状のフィン（45）と、複数の円管状の伝熱管（40）とを備える。フィン（45）は、細長い長方形板状に形成される。後方熱交換部（36）は、フィン（45）の長手方向が上下方向となる姿勢で配置される。 The rear heat exchange section (36) is provided with a plurality of plate-shaped fins (45) and a plurality of circular tubular heat transfer tubes (40). The fins (45) are formed in the shape of an elongated rectangular plate. The rear heat exchange section (36) is arranged so that the longitudinal direction of the fins (45) is in the vertical direction.
　フィン（45）には、複数の管用開口（46）が形成される。管用開口（46）は、フィン（45）を厚さ方向に貫通する円形の孔である。管用開口（46）は、フィン（45）の長手方向に沿った一対の長辺のそれぞれに沿って一列ずつ配置される。傾斜したフィン（45）の上側の長辺に沿った複数の管用開口（46）は、第１開口列（51b）を構成する。傾斜したフィン（45）の下側の長辺に沿った複数の管用開口（46）は、第２開口列（52b）を構成する。 A plurality of pipe openings (46) are formed in the fin (45). The pipe opening (46) is a circular hole that penetrates the fin (45) in the thickness direction. The pipe openings (46) are arranged in a row along each of the pair of long sides along the longitudinal direction of the fins (45). A plurality of pipe openings (46) along the upper long side of the inclined fins (45) constitute a first opening row (51b). A plurality of pipe openings (46) along the lower long side of the sloping fins (45) form a second opening row (52b).
　第１開口列（51b）と第２開口列（52b）のそれぞれにおいて、複数の管用開口（46）は、フィン（45）の長手方向に一列に配置される。第１開口列（51b）と第２開口列（52b）のそれぞれにおいて、複数の管用開口（46）は、フィン（45）の長手方向に互いに一定の間隔をおいて配置される。第１開口列（51b）を構成する管用開口（46）の位置と、第２開口列（52b）を構成する管用開口（46）の位置とは、互いにフィン（45）の長手方向に１／２ピッチずれている。第１開口列（51b）と第２開口列（52b）は、それぞれの最も下方に位置する管用開口（46）が、非挿通開口（47）となる。 In each of the first opening row (51b) and the second opening row (52b), the plurality of pipe openings (46) are arranged in a row in the longitudinal direction of the fins (45). In each of the first opening row (51b) and the second opening row (52b), the plurality of pipe openings (46) are arranged at regular intervals in the longitudinal direction of the fins (45). The position of the pipe opening (46) forming the first opening row (51b) and the position of the pipe opening (46) forming the second opening row (52b) are 1/1 in the longitudinal direction of the fins (45). It is off by 2 pitches. In the first opening row (51b) and the second opening row (52b), the pipe opening (46) located at the lowermost position thereof is a non-insertion opening (47).
　伝熱管（40）は、フィン（45）の各管用開口（46）に一本ずつ差し込まれる。ただし、後方熱交換部（36）では、各フィン（45）の非挿通開口（47）に伝熱管（40）が差し込まれない。各フィン（45）の第１開口列（51b）と第２開口列（52b）では、それぞれの最も下方に位置する非挿通開口（47）以外の管用開口（46）に、伝熱管（40）が差し込まれる。 One heat transfer tube (40) is inserted into each tube opening (46) of the fin (45). However, in the rear heat exchange section (36), the heat transfer tube (40) is not inserted into the non-insertion opening (47) of each fin (45). In the first opening row (51b) and the second opening row (52b) of each fin (45), the heat transfer tube (40) is connected to the tube opening (46) other than the non-insertion opening (47) located at the lowermost position. Is plugged in.
　　－実施形態３の特徴（１）－
　本実施形態の熱交換器（30）は、互いに平行に配置された複数の伝熱管（40）と、複数の板状のフィン（45）とを備える。フィン（45）には、伝熱管（40）を挿し通すための複数の管用開口（46）が形成される。フィン（45）は、長手方向が上下方向となるように配置される。また、フィン（45）は、複数の開口列（51a,52a,51b,52b）を有する。各開口列（51a,52a,51b,52b）は、フィン（45）の長手方向に一列に並んだ複数の管用開口（46）によって構成される。複数の開口列（51a,52a,51b,52b）のそれぞれにおいて最も下方に位置する管用開口（46）は、伝熱管（40）が挿し通されない非挿通開口（47）である。 -Features of Embodiment 3 (1)-
The heat exchanger (30) of the present embodiment includes a plurality of heat transfer tubes (40) arranged in parallel with each other and a plurality of plate-shaped fins (45). The fin (45) is formed with a plurality of tube openings (46) for inserting the heat transfer tube (40). The fins (45) are arranged so that the longitudinal direction is the vertical direction. Further, the fin (45) has a plurality of opening rows (51a, 52a, 51b, 52b). Each opening row (51a, 52a, 51b, 52b) is composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45). The tube opening (46) located at the lowermost position in each of the plurality of opening rows (51a, 52a, 51b, 52b) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted.
　本実施形態の熱交換器（30）では、各フィン（45）に開口列（51a,52a,51b,52b）が複数ずつ設けられる。フィン（45）の各開口列（51a,52a,51b,52b）において、最も下方に位置する管用開口（46）である非挿通開口（47）には、伝熱管（40）が挿し通されない。本実施形態では、凝縮水が滞留しやすい熱交換器（30）の下端部に、伝熱管（40）が設けられない。従って、本実施形態によれば、凝縮水によって伝熱管（40）が腐食する可能性を低減でき、熱交換器（30）の信頼性を向上させることができる。 In the heat exchanger (30) of the present embodiment, each fin (45) is provided with a plurality of opening rows (51a, 52a, 51b, 52b). In each opening row (51a, 52a, 51b, 52b) of the fins (45), the heat transfer tube (40) is not inserted into the non-insertion opening (47) which is the lowermost tube opening (46). In the present embodiment, the heat transfer tube (40) is not provided at the lower end of the heat exchanger (30) where the condensed water tends to stay. Therefore, according to the present embodiment, the possibility that the heat transfer tube (40) is corroded by the condensed water can be reduced, and the reliability of the heat exchanger (30) can be improved.
　以上、実施形態および変形例を説明したが、特許請求の範囲の趣旨および範囲から逸脱することなく、形態や詳細の多様な変更が可能なことが理解されるであろう。また、以上の実施形態および変形例は、本開示の対象の機能を損なわない限り、適宜組み合わせたり、置換したりしてもよい。 Although the embodiments and modifications have been described above, it will be understood that various modifications of the forms and details are possible without departing from the purpose and scope of the claims. In addition, the above embodiments and modifications may be appropriately combined or replaced as long as they do not impair the functions of the present disclosure.
　以上説明したように、本開示は、熱交換器および熱交換ユニットについて有用である。 As described above, the present disclosure is useful for heat exchangers and heat exchange units.
　10　　室外ユニット（熱交換ユニット）
　13　　ドレンパン
　13a 　上縁
　20　　室内ユニット（熱交換ユニット）
　24　　ファン
　25　　前方ドレンパン
　25a 　上縁
　26　　後方ドレンパン
　26a 　上縁
　30　　熱交換器
　31　　第１熱交換部
　32　　第２熱交換部
　40　　伝熱管
　41　　非流通管
　45　　フィン
　46　　管用開口
　47　　非挿通開口
　50,50a,50b　開口列
　51a,51b 　　第１開口列
　52a,52b 　　第２開口列
　61,62 　　　ヘッダ部材
　63　　底壁面 10 Outdoor unit (heat exchange unit)
13 Drain pan 13a Upper edge 20 Indoor unit (heat exchange unit)
24 Fan 25 Front drain pan 25a Upper edge 26 Rear drain pan 26a Upper edge 30 Heat exchanger 31 First heat exchange part 32 Second heat exchange part 40 Heat transfer tube 41 Non-circulation tube 45 Fin 46 Tube opening 47 Non-insertion opening 50,50a, 50b Opening row 51a, 51b First opening row 52a, 52b Second opening row 61,62 Header member 63 Bottom wall surface

Claims (8)

  1. 　互いに平行に配置された複数の伝熱管（40）と、上記伝熱管（40）を挿し通すための複数の管用開口（46）が形成された複数の板状のフィン（45）とを備えた熱交換器であって、
    　上記フィン（45）は、
    　　長手方向が上下方向となるように配置されると共に、
    　　上記フィン（45）の長手方向に一列に並んだ複数の上記管用開口（46）によって構成される開口列（50）を一つだけ有し、
    　上記開口列（50）において最も下方に位置する上記管用開口（46）は、上記伝熱管（40）が挿し通されない非挿通開口（47）である
    ことを特徴とする熱交換器。     A plurality of heat transfer tubes (40) arranged parallel to each other and a plurality of plate-shaped fins (45) having a plurality of tube openings (46) for inserting the heat transfer tubes (40) are provided. It ’s a heat exchanger,
    The above fin (45)
    It is arranged so that the longitudinal direction is the vertical direction, and
    It has only one opening row (50) composed of a plurality of the pipe openings (46) arranged in a row in the longitudinal direction of the fins (45).
    The tube opening (46) located at the lowermost position in the opening row (50) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted.
  2. 　互いに平行に配置された複数の伝熱管（40）と、上記伝熱管（40）を挿し通すための複数の管用開口（46）が形成された複数の板状のフィン（45）とを備えた熱交換器であって、
    　上記フィン（45）は、
    　　長手方向が上下方向となるように配置されると共に、
    　　上記フィン（45）の長手方向に一列に並んだ複数の上記管用開口（46）によって構成される開口列（51a,52a,51b,52b）を複数有し、
    　複数の上記開口列（51a,52a,51b,52b）のそれぞれにおいて最も下方に位置する上記管用開口（46）は、上記伝熱管（40）が挿し通されない非挿通開口（47）である
    ことを特徴とする熱交換器。     A plurality of heat transfer tubes (40) arranged parallel to each other and a plurality of plate-shaped fins (45) having a plurality of tube openings (46) for inserting the heat transfer tubes (40) are provided. It ’s a heat exchanger,
    The above fin (45)
    It is arranged so that the longitudinal direction is the vertical direction, and
    It has a plurality of opening rows (51a, 52a, 51b, 52b) composed of a plurality of pipe openings (46) arranged in a row in the longitudinal direction of the fins (45).
    The tube opening (46) located at the lowermost position in each of the plurality of opening rows (51a, 52a, 51b, 52b) is a non-insertion opening (47) through which the heat transfer tube (40) is not inserted. Characterized heat exchanger.
  3. 　請求項１又は２において、
    　上記伝熱管（40）の材質がアルミニウム合金である
    ことを特徴とする熱交換器。     In claim 1 or 2,
    A heat exchanger characterized in that the material of the heat transfer tube (40) is an aluminum alloy.
  4. 　請求項３において、
    　上記伝熱管（40）は、幅が厚さよりも長い扁平な形状である
    ことを特徴とする熱交換器。     In claim 3,
    The heat transfer tube (40) is a heat exchanger characterized by having a flat shape having a width longer than a thickness.
  5. 　請求項１乃至４のいずれか一つにおいて、
    　上記フィン（45）の長手方向に沿って延びる筒状に形成され、上記伝熱管（40）に接続して内部空間が上記伝熱管（40）に連通するヘッダ部材（61,62）を備え、
    　上記ヘッダ部材（61,62）の内部空間の底壁面（63）が、上記開口列（50）の上記非挿通開口（47）よりも上方に位置する
    ことを特徴とする熱交換器。     In any one of claims 1 to 4,
    A header member (61,62) formed in a tubular shape extending along the longitudinal direction of the fin (45) and connected to the heat transfer tube (40) so that the internal space communicates with the heat transfer tube (40) is provided.
    A heat exchanger characterized in that the bottom wall surface (63) of the internal space of the header member (61, 62) is located above the non-insertion opening (47) of the opening row (50).
  6. 　請求項１乃至５のいずれか一つにおいて、
    　上記フィン（45）と、該フィン（45）の上記管用開口（46）に挿し通された上記伝熱管（40）とをそれぞれが有する第１熱交換部（31）及び第２熱交換部（32）を備え、
    　上記第２熱交換部（32）は、上記第１熱交換部（31）の上方に配置され、
    　上記第２熱交換部（32）の上記フィン（45）の長手方向が、上記第１熱交換部（31）の上記フィン（45）の長手方向に対して傾斜し、
    　上記第１熱交換部（31）の上記フィン（45）の上記開口列（50a）と、上記第２熱交換部（32）の上記フィン（45）の上記開口列（50b）のそれぞれにおいて、最も下方に位置する上記管用開口（46）が上記非挿通開口（47）となる
    ことを特徴とする熱交換器。     In any one of claims 1 to 5,
    The first heat exchange section (31) and the second heat exchange section (31) and the second heat exchange section (40) each having the fin (45) and the heat transfer tube (40) inserted into the tube opening (46) of the fin (45). 32) equipped
    The second heat exchange section (32) is arranged above the first heat exchange section (31).
    The longitudinal direction of the fin (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fin (45) of the first heat exchange section (31).
    In each of the opening row (50a) of the fin (45) of the first heat exchange section (31) and the opening row (50b) of the fin (45) of the second heat exchange section (32). A heat exchanger characterized in that the lowermost tube opening (46) becomes the non-insertion opening (47).
  7. 　請求項１乃至５のいずれか一つにおいて、
    　上記フィンと、該フィンの上記管用開口（46）に挿し通された上記伝熱管（40）とをそれぞれが有する第１熱交換部（31）及び第２熱交換部（32）を備え、
    　上記第２熱交換部（32）は、上記第１熱交換部（31）の上方に配置され、
    　上記第２熱交換部（32）の上記フィン（45）の長手方向が、上記第１熱交換部（31）の上記フィン（45）の長手方向に対して傾斜し、
    　上記第１熱交換部（31）の上記フィン（45）の上記開口列（50a）において、最も下方に位置する上記管用開口（46）が上記非挿通開口（47）となり、
    　上記第２熱交換部（32）の上記フィン（45）の上記開口列（50b）において、最も下方に位置する上記管用開口（46）には、内部を流体が流通しない非流通管（41）が挿し通されている
    ことを特徴とする熱交換器。     In any one of claims 1 to 5,
    A first heat exchange section (31) and a second heat exchange section (32) each having the fin and the heat transfer tube (40) inserted into the tube opening (46) of the fin are provided.
    The second heat exchange section (32) is arranged above the first heat exchange section (31).
    The longitudinal direction of the fin (45) of the second heat exchange section (32) is inclined with respect to the longitudinal direction of the fin (45) of the first heat exchange section (31).
    In the opening row (50a) of the fins (45) of the first heat exchange section (31), the pipe opening (46) located at the lowermost position becomes the non-insertion opening (47).
    In the opening row (50b) of the fins (45) of the second heat exchange section (32), the non-circulation pipe (41) in which no fluid flows through the pipe opening (46) located at the lowermost position. A heat exchanger characterized by being inserted through.
  8. 　請求項１乃至７のいずれか一つの熱交換器（30）と、
    　上記熱交換器（30）へ空気を送るファン（24）と、
    　上記熱交換器（30）の下方に設けられて上記熱交換器（30）で生成した凝縮水を受けるドレンパン（13,25,26）とを備えた熱交換ユニットであって、
    　上記熱交換器（30）は、上記フィン（45）の上記開口列（50）の上記非挿通開口（47）が上記ドレンパン（13,25,26）の上縁（13a,25a,26a）よりも下方に位置する
    ことを特徴とする熱交換ユニット。     With the heat exchanger (30) of any one of claims 1 to 7.
    A fan (24) that sends air to the heat exchanger (30) and
    A heat exchange unit provided below the heat exchanger (30) and provided with a drain pan (13,25,26) for receiving the condensed water generated by the heat exchanger (30).
    In the heat exchanger (30), the non-insertion opening (47) of the opening row (50) of the fin (45) is from the upper edge (13a, 25a, 26a) of the drain pan (13,25,26). A heat exchange unit characterized by being located below.
PCT/JP2020/027038 2019-07-10 2020-07-10 Heat exchanger and heat exchange unit WO2021006336A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202090000706.7U CN217635915U (en) 2019-07-10 2020-07-10 Heat exchanger and heat exchange unit
EP20836392.9A EP3992564B1 (en) 2019-07-10 2020-07-10 Heat exchanger and heat exchange unit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019128402A JP2021014929A (en) 2019-07-10 2019-07-10 Heat exchanger and heat exchange unit
JP2019-128402 2019-07-10

Publications (1)

Publication Number Publication Date
WO2021006336A1 true WO2021006336A1 (en) 2021-01-14

Family

ID=74115262

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/027038 WO2021006336A1 (en) 2019-07-10 2020-07-10 Heat exchanger and heat exchange unit

Country Status (4)

Country Link
EP (1) EP3992564B1 (en)
JP (1) JP2021014929A (en)
CN (1) CN217635915U (en)
WO (1) WO2021006336A1 (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60128168U (en) * 1984-02-07 1985-08-28 ダイキン工業株式会社 Heat exchanger with fins
JP2012211735A (en) * 2011-03-31 2012-11-01 Daikin Industries Ltd Heat exchanger and air conditioner
WO2013160959A1 (en) * 2012-04-27 2013-10-31 三菱電機株式会社 Heat exchanger, method for producing same, and refrigeration cycle device
JP2013242104A (en) * 2012-05-22 2013-12-05 Mitsubishi Electric Corp Showcase
JP2015127607A (en) 2013-12-27 2015-07-09 ダイキン工業株式会社 Heat exchanger
JP2018035992A (en) * 2016-08-31 2018-03-08 株式会社富士通ゼネラル Heat exchanger

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2947331B1 (en) * 2009-06-29 2011-07-29 Valeo Systemes Thermiques HEAT EXCHANGER COMPRISING A BEAM OF TUBES WITH AT LEAST ONE INACTIVE TUBE
FR3049050B1 (en) * 2016-03-18 2018-04-27 Valeo Systemes Thermiques HEAT EXCHANGER, IN PARTICULAR FOR A MOTOR VEHICLE
US20170328637A1 (en) * 2016-05-13 2017-11-16 Denso Thermal Systems S.P.A. Heat exchanger with dummy tubes
JP2018054256A (en) * 2016-09-30 2018-04-05 ダイキン工業株式会社 Heat exchange unit

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60128168U (en) * 1984-02-07 1985-08-28 ダイキン工業株式会社 Heat exchanger with fins
JP2012211735A (en) * 2011-03-31 2012-11-01 Daikin Industries Ltd Heat exchanger and air conditioner
WO2013160959A1 (en) * 2012-04-27 2013-10-31 三菱電機株式会社 Heat exchanger, method for producing same, and refrigeration cycle device
JP2013242104A (en) * 2012-05-22 2013-12-05 Mitsubishi Electric Corp Showcase
JP2015127607A (en) 2013-12-27 2015-07-09 ダイキン工業株式会社 Heat exchanger
JP2018035992A (en) * 2016-08-31 2018-03-08 株式会社富士通ゼネラル Heat exchanger

Also Published As

Publication number Publication date
JP2021014929A (en) 2021-02-12
EP3992564A1 (en) 2022-05-04
EP3992564A4 (en) 2022-08-24
CN217635915U (en) 2022-10-21
EP3992564B1 (en) 2023-08-23

Similar Documents

Publication Publication Date Title
WO2012114719A1 (en) Heat exchanger for air conditioner
JP6749398B2 (en) Heat exchangers and air conditioning systems
JP2010164222A (en) Finned heat exchanger
JP6223596B2 (en) Air conditioner indoor unit
JP2010249343A (en) Fin tube type heat exchanger and air conditioner using the same
JP2009145009A (en) Air conditioner
JP6120978B2 (en) Heat exchanger and air conditioner using the same
JP2019128060A (en) Indoor heat exchanger and air conditioner
WO2016174802A1 (en) Heat exchanger and air conditioner
JP6765528B2 (en) Heat exchanger, refrigeration cycle device and air conditioner
JP2015218907A (en) Heat exchanger
KR20150119982A (en) Heat exchanger
JP2010216718A (en) Heat exchanger with fin
JP6260632B2 (en) Heat exchanger
WO2021006336A1 (en) Heat exchanger and heat exchange unit
GB2546202A (en) Indoor unit for air conditioning device
JP4995308B2 (en) Air conditioner indoor unit
JP6997722B2 (en) Heat exchanger and air conditioner
KR100893746B1 (en) Air conditioner
JP5940895B2 (en) Parallel flow type heat exchanger and air conditioner equipped with the same
WO2012098913A1 (en) Heat exchanger and air conditioner
JP7044991B2 (en) Heat exchanger and air conditioner
JP2017133814A (en) Heat exchanger
JP6771557B2 (en) Heat exchanger
JP2015227754A (en) Heat exchanger

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: 20836392

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020836392

Country of ref document: EP

Effective date: 20220127