EP2667134A1 - Wärmetauscher und klimaanlage - Google Patents

Wärmetauscher und klimaanlage Download PDF

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Publication number
EP2667134A1
EP2667134A1 EP12736601.1A EP12736601A EP2667134A1 EP 2667134 A1 EP2667134 A1 EP 2667134A1 EP 12736601 A EP12736601 A EP 12736601A EP 2667134 A1 EP2667134 A1 EP 2667134A1
Authority
EP
European Patent Office
Prior art keywords
heat exchange
exchange part
heat exchanger
flat tube
flat tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12736601.1A
Other languages
English (en)
French (fr)
Other versions
EP2667134A4 (de
Inventor
Masanori Jindou
Yoshio Oritani
Hirokazu Fujino
Toshimitsu Kamada
Yoshimasa Kikuchi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP2667134A1 publication Critical patent/EP2667134A1/de
Publication of EP2667134A4 publication Critical patent/EP2667134A4/de
Withdrawn legal-status Critical Current

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    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28D1/05308—Assemblies of conduits connected side by side or with individual headers, e.g. section 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F28F1/30—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 being attachable to the element
    • 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
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0444—Condensers with an integrated receiver where the flow of refrigerant through the condenser receiver is split into two or more flows, each flow following a different path through the condenser receiver
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • 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
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present disclosure relates to a heat exchanger including flat tubes and fins and configured to exchange heat between fluid flowing through the flat tube and air, and to an air conditioner.
  • Patent Document 1 discloses an air conditioner including the refrigerating apparatus of this type.
  • an outdoor heat exchanger functions as a condenser
  • an indoor heat exchanger functions as an evaporator.
  • the indoor heat exchanger functions as the condenser
  • the outdoor heat exchanger functions as the evaporator.
  • Patent Document 2 also discloses an air conditioner configured to perform a refrigeration cycle.
  • an outdoor heat exchanger configured to exchange heat between refrigerant and outdoor air is provided.
  • the outdoor heat exchanger is a heat exchanger including two headers each formed in a cylindrical shape, and a plurality of flat heat transfer pipes provided between the headers.
  • Patent Document 3 also discloses a heat exchanger including headers and flat heat transfer pipes.
  • the heat exchanger disclosed in Patent Document 3 functions as a condenser.
  • a main heat exchange part for condensation and an auxiliary heat exchange part for sub-cooling are formed. While passing through the main heat exchange part, refrigerant flowing into the heat exchanger is condensed into a substantially liquid single-phase state. Then, the refrigerant flows into the auxiliary heat exchange part, and is further cooled.
  • the auxiliary heat exchange part typically has flow paths fewer than those of the main heat exchange part.
  • a flow velocity in the auxiliary heat exchange part increases, and therefore a pressure loss in the auxiliary heat exchange part increases.
  • the present disclosure has been made in view of the foregoing, and it is an objective of the present disclosure to reduce, in a heat exchanger in which headers and flat tubes are provided and a main heat exchange part(s) for condensation and an auxiliary heat exchange part(s) for sub-cooling are formed, a pressure loss in the auxiliary heat exchange part.
  • a first aspect of the invention is intended for a heat exchanger including a plurality of flat tubes (53, 58) arranged in the vertical direction such that side surfaces thereof face each other and each formed with a plurality of flow paths (49) of fluid, and a plurality of fins (54, 59) configured to divide part between adjacent ones of the flat tubes (53, 58) into a plurality of air passages through each of which air flows.
  • the heat exchanger includes a first header collecting pipe (51, 56); and a second header collecting pipe (52, 57).
  • Each flat tube (53, 58) is, at one end thereof, connected to the first header collecting pipe (51, 56), and is, at the other end thereof, connected to the second header collecting pipe (52, 57).
  • Some of the flat tubes (53) form a main heat exchange part (50), and the other flat tubes (58) form an auxiliary heat exchange part (55).
  • the flat tubes (58) forming the auxiliary heat exchange part (55) are fewer than the flat tubes (53) forming the main heat exchange part (50).
  • the total cross-sectional area of flow paths (49) per flat tube (58) in the auxiliary heat exchange part (55) is greater than the total cross-sectional area of flow paths (49) per flat tube (53) in the main heat exchange part (50). If the heat exchanger serves as a condenser, refrigerant is condensed in the main heat exchange part (50), and the refrigerant is sub-cooled in the auxiliary heat exchange part (55).
  • the number of flat tubes (58) forming the auxiliary heat exchange part (55) is less than the number of flat tubes (53) forming the main heat exchange part (50).
  • the total cross-sectional area of flow paths (49) per flat tube (58) in the auxiliary heat exchange part (55) is greater than the total cross-sectional area of flow paths (49) per flat tube (53) in the main heat exchange part (50).
  • a second aspect of the invention is intended for the heat exchanger of the first aspect of the invention, in which the width (W2) of each flat tube (58) of the auxiliary heat exchange part (55) is greater than the width (W1) of each flat tube (53) of the main heat exchange part (50), and the flow paths per flat tube (58) in the auxiliary heat exchange part (55) is more than the flow paths per flat tube (53) in the main heat exchange part (50).
  • the number of flow paths per flat tube (53, 58) and the width (W1, W2) of the flat tube (53, 58) are adjusted to set the total cross-sectional area of flow paths (49) per flat tube (53, 58).
  • a third aspect of the invention is intended for the heat exchanger of the first or second aspect of the invention, in which each flow path (49) is formed with a plurality of grooves in a corresponding one of the flat tubes (53) of the main heat exchange part (50), and each flat tube (58) of the auxiliary heat exchange part (55) is a bare pipe.
  • a fourth aspect of the invention is intended for the heat exchanger of any one of the first to third aspects of the invention, in which each fin (236) is formed in such a plate shape that a plurality of cut parts (245) into each of which a corresponding one of the flat tubes (53, 58) is inserted are provided, the fins (236) are arranged at predetermined intervals in an extension direction of the flat tubes (53, 58), each flat tube (53, 58) is sandwiched between peripheral edge parts of a corresponding one of the cut parts (245) of the fins (236), and, in each fin (236), part between adjacent ones of the cut parts (245) arranged in the vertical direction forms a heat transfer part (237).
  • the plurality of fins (236) each formed in a plate shape are arranged at the predetermined intervals in the extension direction of the flat tubes (53, 58).
  • the plurality of cut parts (245) into each of which a corresponding one of the flat tubes (53, 58) is inserted are formed.
  • the flat tube (53, 58) is sandwiched between the peripheral edge parts of a corresponding one of the cut parts (245) of the fin (236).
  • the part between adjacent ones of the cut parts (245) arranged in the vertical direction forms the heat transfer part (237).
  • a fifth aspect of the invention is intended for the heat exchanger of the fourth aspect of the invention, in which an end of each flat tube (53, 58) in a width direction thereof is aligned with an end of a corresponding one of the cut parts (245) on an open side thereof.
  • the end of the flat tube (53, 58) in the width direction thereof is aligned with the end of the cut part (245) on the inlet side thereof.
  • a sixth aspect of the invention is intended for an air conditioner including a refrigerant circuit (20) provided with the heat exchanger (40) of any one of claims 1-5. Refrigerant circulates to perform a refrigeration cycle in the refrigerant circuit (20).
  • the heat exchanger is connected to the refrigerant circuit (20).
  • refrigerant circulating through the refrigerant circuit (20) flows through the flow paths (49) of the flat tubes (53, 58) to exchange heat with air flowing through air passages.
  • the flow velocity of refrigerant in the auxiliary heat exchange part (55) can be lowered, and therefore a pressure loss in the auxiliary heat exchange part (55) can be reduced.
  • the total cross-sectional area of flow paths (49) in the flat tube (53) for the main heat exchange part (50) and the total cross-sectional area of flow paths (49) in the flat tube (58) for the auxiliary heat exchange part (55) can be easily set.
  • the flat tube (53) for the main heat exchange part (50) and the flat tube (58) for the auxiliary heat exchange part (55) are different from each other in width (W1, W2), and therefore both pipes (53, 58) can be easily identified with eyes.
  • a heat exchange efficiency in the main heat exchange part (50) can be improved.
  • a pressure loss due to a pipe shape can be further reduced.
  • the brazing material for joining the fin (236) and the flat tube (53, 58) together can be easily set, and therefore it can be further ensured that the fin (236) and the flat tube (53, 58) can be joined together.
  • the end of the flat tube (53, 58) is aligned with the end of the cut part (245) on the open side thereof.
  • the depth of the cut part (245) may be set corresponding to the flat tube (58) having a greater width. That is, even if plural types of flat tubes (53, 58) having different widths are used, the common fin (236) can be used.
  • the present embodiment is intended for an air conditioner including a refrigerating apparatus.
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner (10) of the first embodiment of the present disclosure, and illustrates a state in an air-cooling operation.
  • FIG. 2 is a refrigerant circuit diagram of the air conditioner (10) of the first embodiment, and illustrates a state in an air-heating operation.
  • the air conditioner (10) of the present embodiment includes a single indoor unit (12) which is a utilization-side unit, and a single outdoor unit (11) which is a heat-source-side unit.
  • the outdoor unit (11) and the indoor unit (12) are connected together by pipes to form a refrigerant circuit (20).
  • indoor units (12) and outdoor units (11) has been set forth merely for the purpose of an example. That is, in the air conditioner (10) of the present embodiment, a plurality of indoor units (12) may be connected to a single outdoor unit (11) to form a refrigerant circuit (20). Alternatively, a plurality of outdoor units (11) and a plurality of indoor units (12) may be connected together to form a refrigerant circuit (20).
  • the compressor (31), the outdoor heat exchanger (40), the expansion valve (33), and the four-way valve (34) are accommodated in the outdoor unit (11).
  • the indoor heat exchanger (32) is accommodated in the indoor unit (12).
  • an outdoor fan configured to supply outdoor air to the outdoor heat exchanger (40) is provided in the outdoor unit (11), and an indoor fan configured to supply indoor air to the indoor heat exchanger (32) is provided in the indoor unit (12).
  • the compressor (31) is a hermetic rotary compressor or a hermetic scroll compressor.
  • an outlet pipe of the compressor (31) is connected to a first port of the four-way valve (34) through a pipe, and an inlet pipe of the compressor (31) is connected to a second port of the four-way valve (34) through a pipe.
  • the outdoor heat exchanger (40) includes first and second header members (46, 47) standing upright, and a plurality of heat transfer pipes (hereinafter also referred to as "flat tubes") (53, 58).
  • the outdoor heat exchanger (40) is configured to exchange heat between refrigerant and outdoor air.
  • the structure of the outdoor heat exchanger (40) will be described in detail later.
  • the indoor heat exchanger (32) is a so-called “cross-fin type fin- and-tube heat exchanger,” and is configured to exchange heat between refrigerant and indoor air.
  • the expansion valve (33) is a so-called “electronic expansion valve (33).”
  • the four-way valve (34) includes four ports, and switches between a first state (state illustrated in FIG. 1 ) in which the first port communicates with a third port and the second port communicates with a fourth port and a second state (state illustrated in FIG. 2 ) in which the first port communicates with the fourth port and the second port communicates with the third port.
  • a first gas pipe (21), a second gas pipe (22), and a liquid pipe (23) are provided in the refrigerant circuit (20.
  • the first gas pipe (21) is, at one end thereof, connected to the third port of the four-way valve (34), and is, at the other end thereof, connected to an upper end part of the first header member (46) of the outdoor heat exchanger (40).
  • the second gas pipe (22) is, at one end thereof, connected to the fourth port of the four-way valve (34), and is, at the other end thereof, connected to a gas end of the indoor heat exchanger (32).
  • the liquid pipe (23) is, at one end thereof, connected to a lower end part of a first header collecting pipe (56) which will be described later, and is, at the other end thereof, connected to a liquid end of the indoor heat exchanger (32).
  • the expansion valve (33) is provided in the middle of the liquid pipe (23).
  • FIG. 3 is a schematic perspective view of a heat exchanger unit forming the outdoor heat exchanger of the first embodiment.
  • FIG. 4 is a schematic front view of the heat exchanger unit forming the outdoor heat exchanger of the first embodiment.
  • FIG. 5 is an enlarged perspective view of a main part of the heat exchanger unit of the first embodiment in the state in which part of the main part is not shown.
  • the outdoor heat exchanger (40) of the present embodiment includes a single heat exchanger unit (45).
  • the heat exchanger unit (45) forming the outdoor heat exchanger (40) includes the single first header member (46), the single second header member (47), the plurality of heat transfer pipes (53, 58), and a plurality of fins (54, 59).
  • the first header member (46), the second header member (47), the flat tubes (53, 58), and the fins (54, 59) are members made of an aluminum alloy, and are joined together by brazing.
  • the fin (54, 59) divides part between adjacent ones of the flat tubes (53, 58) into a plurality of air passages through each of which air flows.
  • the first header member (46) and the second header member (47) are each formed in an elongated hollow cylindrical shape closed at both ends thereof.
  • the first header member (46) stands upright at the left of the heat exchanger unit (45)
  • the second header member (47) stands upright at the right of the heat exchanger unit (45). That is, the first header member (46) and the second header member (47) are mounted in such an attitude that the axial directions thereof are along the vertical direction.
  • FIG. 6 is a schematic view illustrating an example of a cross-sectional shape of the flat tube (53, 58).
  • the width (W2) of the flat tube (58) is, referring to FIG. 6 , greater than the width (W1) of the flat tube (53).
  • the number of flow paths per flat tube (58) is greater than the number of flow paths per flat tube (53).
  • FIG. 7A is a view illustrating an example of a cross-sectional shape of the refrigerant flow path (49) in the flat tube (53) for a main heat exchange part (50) which will be described later
  • FIG. 7B is a view illustrating an example of a cross-sectional shape of the refrigerant flow path (49) in the flat tube (58) for an auxiliary heat exchange part (55) which will be described later.
  • a plurality of grooves (49a) are formed in each of the refrigerant flow paths (49) of the flat tube (53), whereas the flat tube (58) is a so-called “bare pipe (smooth inner pipe)" having a circular cross section.
  • each of the refrigerant flow paths (49) of the flat tube (58) has a diameter of about 0.5 mm.
  • cross-sectional shapes of the refrigerant flow path (49) are set forth merely for the purpose of examples, and other shapes (e.g., a rectangular cross section illustrated in FIG. 6 ) may be employed.
  • the flat tubes (53, 58) are arranged at predetermined intervals in the axial direction of the first and second header members (46, 47) in such an attitude that the axial direction of the flat tube (53, 58) is along the horizontal direction and side surfaces of the flat tubes (53, 58) face each other. That is, in the heat exchanger unit (45), the flat tubes (53, 58) are arranged parallel to each other between the first header member (46) and the second header member (47). One end part of the flat tube (53, 58) is inserted into the first header member (46), and the other end part of the flat tube (53, 58) is inserted into the second header member (47).
  • Each of the refrigerant flow paths (49) in the flat tube (53, 58) communicates, at one end thereof, with an internal space of the first header member (46), and communicates, at the other end thereof, with an internal space of the second header member (47).
  • the fin (54, 59) is provided between adjacent ones of the flat tubes (53, 58).
  • the fin (54, 59) is formed in a corrugated plate shape meandering up and down, and is mounted in such an attitude that a ridge line of such a wave shape is along the front-back direction (direction perpendicular to the plane of paper of FIG. 4 ) of the heat exchanger unit (45). In the heat exchanger unit (45), air passes in the direction perpendicular to the plane of paper of FIG. 4 .
  • a discoid partition plate (48) is provided in the first header member (46).
  • the internal space of the first header member (46) is horizontally divided by the partition plate (48).
  • the internal space of the second header member (47) is a single undivided space.
  • the upper part relative to the partition plate (48) forms the main heat exchange part (50), and the lower part relative to the partition plate (48) forms the auxiliary heat exchange part (55).
  • the upper part relative to the partition plate (48) forms a first header collecting pipe (51) of the main heat exchange part (50), and the lower part relative to the partition plate (48) forms the first header collecting pipe (56) of the auxiliary heat exchange part (55).
  • the flat tubes (53, 58) provided in the heat exchanger unit (45) the flat tubes (53) connected to the first header collecting pipe (51) of the main heat exchange part (50) are for the main heat exchange part (50), and the flat tubes (58) connected to the first header collecting pipe (56) of the auxiliary heat exchange part (55) are for the auxiliary heat exchange part (55).
  • the fins (54) each provided between adjacent ones of the flat tubes (53) of the main heat exchange part (50) are for the main heat exchange part (50)
  • the fins (59) each provided between adjacent ones of the flat tubes (58) of the auxiliary heat exchange part (55) are for the auxiliary heat exchange part (55).
  • part of the second header member (47) to which the flat tubes (53) of the main heat exchange part (50) are inserted forms a second header collecting pipe (52) of the main heat exchange part (50)
  • part of the second header member (47) to which the flat tubes (58) of the auxiliary heat exchange part (55) are inserted forms a second header collecting pipe (57) of the auxiliary heat exchange part (55).
  • the width (W1) of the flat tube (53) of the main heat exchange part (50), the number of refrigerant flow paths (49), the cross-sectional area of the refrigerant flow path (49), the number of flat tubes (53), etc. are determined based on requirements of a heat exchange capacity required for air-cooing and air-heating.
  • the number of flat tubes (53, 58) which can be provided in the outdoor heat exchanger (40) is limited.
  • the number of flat tubes (58) is the number obtained by subtracting the number of flat tubes (53) from the maximum possible number.
  • the width (W2) of the flat tube (58), the number of refrigerant flow paths (49), and the cross-sectional area of the refrigerant flow path (49) are set depending on the capacity required for the auxiliary heat exchange part (55).
  • the number of flat tubes (58) of the auxiliary heat exchange part (55) is less than the number of flat tubes (53) of the main heat exchange part (50).
  • the total cross-sectional area of refrigerant flow paths (49) per flat tube (58) provided in the auxiliary heat exchange part (55) is greater than the total cross-sectional area of refrigerant flow paths (49) per flat tube (53) provided in the main heat exchange part (50).
  • sixty flat tubes (53, 58) are provided in the outdoor heat exchanger (40).
  • the number of flat tubes (58) of the auxiliary heat exchange part (55) is ten, and the number of flat tubes (53) of the main heat exchange part (50) is fifty. That is, the number of flat tubes (58) of the auxiliary heat exchange part (55) is one-fifth of the number of flat tubes (53) of the main heat exchange part (50).
  • the number of flat tubes (53, 58) illustrated in FIGS. 3 and 4 is different from the actual number of flat tubes (53, 58) provided in the outdoor heat exchanger (40).
  • the first gas pipe (21) is connected to the upper end part of the first header member (46), and the liquid pipe (23) is connected to a lower end part of the first header member (46) (see FIG. 1 ). That is, in the outdoor heat exchanger (40), the first gas pipe (21) is connected to the first header collecting pipe (51) of the main heat exchange part (50), and the liquid pipe (23) is connected to the first header collecting pipe (56) of the auxiliary heat exchange part (55).
  • the operations of the air conditioner (10) will be described.
  • the air conditioner (10) performs the air-cooling operation which is a cooling process and the air-heating operation which is a heating process.
  • the four-way valve (34) is set at the first state. Moreover, the degree of opening of the expansion valve (33) is adjusted such that the degree of superheat of refrigerant flowing out from the gas end of the indoor heat exchanger (32) reaches a predetermined target value (e.g., 5°C). Further, in the air-cooling operation, outdoor air is supplied to the outdoor heat exchanger (40) by the outdoor fan, and indoor air is supplied to the indoor heat exchanger (32) by the indoor fan.
  • a predetermined target value e.g., 5°C
  • refrigerant discharged from the compressor (31) passes through the four-way valve (34) and the first gas pipe (21) in this order, and then flows into the first header collecting pipe (51) of the main heat exchange part (50).
  • the refrigerant flowing into the first header collecting pipe (51) flows into the flat tubes (53) of the main heat exchange part (50).
  • the refrigerant While passing through each of the refrigerant flow paths (49) of the flat tubes (53), the refrigerant is condensed by dissipating heat to outdoor air.
  • the refrigerant flows into the second header collecting pipe (52) of the main heat exchange part (50), and then flows down to the second header collecting pipe (57) of the auxiliary heat exchange part (55).
  • the refrigerant flowing into the second header collecting pipe (57) flows into the flat tubes (58) of the auxiliary heat exchange part (55). While passing through each of the refrigerant flow paths (49) of the flat tubes (58), the refrigerant enters a sub-cooling state by dissipating heat to outdoor air. After passing through the flat tubes (58), the refrigerant flows into the first header collecting pipe (56) of the auxiliary heat exchange part (55).
  • the refrigerant flowing into the liquid pipe (23) from the first header collecting pipe (56) of the auxiliary heat exchange part (55) is expanded (i.e., the pressure of refrigerant is reduced) upon passage of the expansion valve (33), and then flows into the liquid end of the indoor heat exchanger (32).
  • the refrigerant flowing into the indoor heat exchanger (32) is evaporated by absorbing heat from indoor air.
  • the indoor unit (12) supplies taken indoor air to the indoor heat exchanger (32), and sends indoor air cooled by the indoor heat exchanger (32) back to a room.
  • the refrigerant evaporated in the indoor heat exchanger (32) flows into the second gas pipe (22) from the gas end of the indoor heat exchanger (32). Subsequently, the refrigerant is sucked into the compressor (31) through the four-way valve (34). The compressor (31) compresses the taken refrigerant and then discharge the compressed refrigerant.
  • the four-way valve (34) is set at the second state. Moreover, the degree of opening of the expansion valve (33) is adjusted such that the degree of superheat of refrigerant flowing out from the outdoor heat exchanger (40) reaches a predetermined target value (e.g., 5°C). Further, in the air-heating operation, outdoor air is supplied to the outdoor heat exchanger (40) by the outdoor fan, and indoor air is supplied to the indoor heat exchanger (32) by the indoor fan.
  • a predetermined target value e.g., 5°C
  • refrigerant discharged from the compressor (31) passes through the four-way valve (34) and the second gas pipe (22) in this order, and then flows into the gas end of the indoor heat exchanger (32).
  • the refrigerant flowing into the indoor heat exchanger (32) is condensed by dissipating heat to indoor air.
  • the indoor unit (12) supplies taken indoor air to the indoor heat exchanger (32), and sends indoor air heated by the indoor heat exchanger (32) back to a room.
  • the refrigerant flowing into the liquid pipe (23) from the liquid end of the indoor heat exchanger (32) is expanded (i.e., the pressure of refrigerant is reduced) upon passage of the expansion valve (33), and then flows into the first header collecting pipe (56) of the auxiliary heat exchange part (55).
  • the refrigerant flowing into the first header collecting pipe (56) of the auxiliary heat exchange part (55) flows into the flat tubes (58) of the auxiliary heat exchange part (55). While passing through the refrigerant flow paths (49), the refrigerant flowing into each of the flat tubes (58) absorbs heat from outdoor air, and part of the refrigerant is evaporated.
  • the refrigerant evaporated in the flat tubes (58) flows into the second header collecting pipe (52), and then flows into the flat tubes (53) of the main heat exchange part (50). While passing through the refrigerant flow paths (49), the refrigerant flowing into each of the flat tubes (53) is evaporated by absorbing heat from outdoor air.
  • the refrigerant After passing through the flat tubes (53) of the main heat exchange part (50), the refrigerant flows into the first header collecting pipe (51) of the main heat exchange part (50), and then flows into the first gas pipe (21). After passing through the four-way valve (34), the refrigerant flowing through the first gas pipe (21) is sucked into the compressor (31). The compressor (31) compresses the taken refrigerant and discharges the compressed refrigerant.
  • the number of flat tubes (58) forming the auxiliary heat exchange part (55) is less than the number of flat tubes (53) forming the main heat exchange part (50).
  • the total cross-sectional area of refrigerant flow paths (49) per flat tube (58) provided in the auxiliary heat exchange part (55) is greater than the total cross-sectional area of refrigerant flow paths (49) per flat tube (53) provided in the main heat exchange part (50).
  • the flow velocity of refrigerant in the auxiliary heat exchange part (55) can be lowered as compared to, e.g., a heat exchanger (hereinafter, for the sake of simplicity of description, referred to as a "conventional heat exchanger") in which a single type of flat tubes forms a main heat exchanger part and an auxiliary heat exchange part. Consequently, according to the present embodiment, a pressure loss in the auxiliary heat exchange part (55) can be reduced.
  • the number of flow paths per flat tube (53, 58) and the width (W1, W2) of the flat tube (53, 58) are adjusted so that the total cross-sectional area of refrigerant flow paths (49) per flat tube (53, 58) can be set.
  • the total cross-sectional area of refrigerant flow paths (49) in the flat tube (53) for the main heat exchange part (50) and the total cross-sectional area of refrigerant flow paths (49) in the flat tube (58) for the auxiliary heat exchange part (55) can be easily set.
  • the grooves (49a) are formed in each of the refrigerant flow paths (49) of the flat tube (53) in the main heat exchange part (50).
  • the surface area per refrigerant flow path (49) can be increased. That is, a heat exchange efficiency in the main heat exchange part (50) can be improved.
  • the refrigerant flow path (49) has, as described above, an extremely-small diameter.
  • the outdoor heat exchanger (40) is manufactured at a factory, if, e.g., flat tubes having the same width form a main heat exchange part and an auxiliary heat exchange part, it is difficult to identify, with eyes, the presence/absence of the grooves (49a) of the refrigerant flow path (49).
  • the flat tube (53) for the main heat exchange part (50) and the flat tube (58) for the auxiliary heat exchange part (55) have the different widths (W1, W2), the presence/absence of the grooves (49a) of the refrigerant flow path (49) can be easily identified.
  • FIG. 8 is a view illustrating part of a cross section of a heat exchanger (40) of a first variation of the first embodiment.
  • a fin (235) is a corrugated fin meandering up and down, and is arranged between adjacent ones of flat tubes (heat transfer pipes) (53, 58) which are respectively at the top and bottom of the fin (235).
  • a plurality of heat transfer parts (237) and a plurality of middle plate parts (241) are formed in the fin (235).
  • the middle plate parts (241) are joined to the flat tube (53, 58) by brazing.
  • FIG. 9 is a schematic perspective view of the fin (235) provided in the heat exchanger (40) of the first variation.
  • the fin (235) is the corrugated fin formed in such a manner that a metal plate having a uniform width is bent, and is in the shape meandering up and down.
  • the heat transfer parts (237) and the middle plate parts (241) are alternately formed along an extension direction of the flat tube (53, 58). That is, in the fin (235), the plurality of heat transfer parts (237) arranged in the extension direction of the flat tube (53, 58) are provided between the adjacent ones of the flat tubes (53, 58).
  • protruding plate parts (242) are formed. Note that louvers (250, 260, 270) and a water guide rib (271) which will be described later are not shown in FIG. 9 .
  • the heat transfer part (237) is a plate-shaped part extending from one of adjacent ones of the flat tubes (53, 58) to the other one of the adjacent ones of the flat tubes (53, 58).
  • an end part thereof on a windward side is a front edge (238).
  • the plurality of louvers (250, 260) are formed in the heat transfer part (237).
  • the middle plate part (241) is a plate-shaped part along flat side surfaces of the flat tubes (53, 58), and is continuous to upper ends of adjacent ones of the heat transfer parts (237) or lower ends of adjacent ones of the heat transfer parts (237).
  • the angle formed between the heat transfer part (237) and the middle plate part (241) is the substantially right angle.
  • the protruding plate part (242) is a plate-shaped part continuously formed with an end part of the heat transfer part (237) on a leeward side.
  • the protruding plate part (242) is formed in a vertically-elongated plate shape, and protrudes beyond the flat tube (53, 58) toward the leeward side.
  • An upper end of the protruding plate part (242) upwardly protrudes beyond the upper end of the heat transfer part (237), and a lower end of the protruding plate part (242) downwardly protrudes beyond the lower end of the heat transfer part (237).
  • the water guide rib (271) is formed in the protruding plate part (242) of the fin (235).
  • the water guide rib (271) is an elongated recessed groove vertically extending along an end part of the protruding plate part (242) on the leeward side.
  • FIGS. 10A and 10B are views illustrating the heat transfer part (237) provided in the fin (235) of the outdoor heat exchanger (40) of the first variation.
  • FIG. 10A is a front view of the heat exchange part
  • FIG. 10B is a cross-sectional view along a B-B line illustrated in FIG. 10A .
  • the plurality of louvers (250, 260, 270) are formed in the heat transfer part (237) and the protruding plate part (242) of the fin (235).
  • the louver (250, 260, 270) is formed in such a manner that part of the heat transfer part (237) or the protruding plate part (242) is cut and is folded up.
  • louvers (250, 260, 270) are formed in such a manner that a plurality of slit-shaped cut is formed in the heat transfer part (237) and the protruding plate part (242) and part between adjacent ones of the cuts is plastically deformed by twisting.
  • FIG. 11A is a partial cross-sectional view of a heat exchanger (40) of a second variation
  • FIG. 11B is a cross-sectional view of a fin along a V-V line illustrated in FIG. 11A
  • a plurality of waffle parts (251, 252, 253) are formed, instead of the louvers (250, 260, 270) described in the first variation.
  • the plurality of waffle parts (251, 252, 253) are formed in a heat transfer part (237) and a protruding plate part (242) of a fin (235).
  • the waffle part (251, 252, 253) is a protrusion protruding toward a side on which an air passage is formed and formed in a vertically elongated shape.
  • the waffle parts (251, 252, 253) are formed in such a manner that part of the heat transfer part (237) is plastically deformed by, e.g., pressing.
  • the waffle part (251, 252, 253) extends in a direction inclined relative to the vertical direction such that a lower end part of the waffle part (251, 252, 253) is positioned on the leeward side relative to an upper end part thereof.
  • the waffle part (251, 252, 253) has a pair of vertically-elongated trapezoidal surfaces (254) and a pair of flat upper and lower triangular surfaces (255).
  • the trapezoidal surfaces (254) are adjacent to each other in an air passage direction so as to form a ridge part (256) forming a ridge line.
  • the triangular surfaces (255) are formed respectively at the top and bottom of the ridge part (256).
  • the plurality of waffle parts (251, 252, 253) are formed so as to be arranged from the windward side to the leeward side.
  • the waffle parts (251, 252, 253) are the single windward-side waffle part (251) formed on the windward side of the heat transfer part (237), the two leeward-side waffle parts (253) formed on the leeward side of the heat transfer part (237), and the single middle waffle part (252) formed between the windward-side waffle part (251) and the leeward-side waffle part (253).
  • the windward-side waffle part (251) is a windward-side protrusion formed on the most windward side.
  • the leeward-side waffle part (253) is a leeward-side protrusion formed on the most leeward side.
  • An upper end of the windward-side waffle part (251) is positioned lower than that of the leeward-side waffle part (253). Moreover, an upper end of the middle waffle part (252) and the upper end of the leeward-side waffle part (253) are at the substantially same height.
  • the upper end of the windward-side waffle part (251), the upper end of the middle waffle part (252), and the upper ends of the leeward-side waffle part (253) are substantially parallel to a flat surface of a flat tube (53, 58) provided on an upper side thereof.
  • a lower end of the windward-side waffle part (251) is positioned higher than that of the leeward-side waffle part (253).
  • the lower end of the windward-side waffle part (251) is inclined such that part of the lower end of the windward-side waffle part (251) on the leeward side is positioned lower than that on the windward side.
  • a lower end of the middle waffle part (252) is also inclined such that part of the lower end of the middle waffle part (252) on the leeward side is positioned lower than that on the windward side.
  • the lower end of the leeward-side waffle parts (253) are substantially parallel to the flat surface of the flat tube (53, 58).
  • FIG. 12 is a view illustrating part of a cross section of a heat exchanger (40) of a third variation of the first embodiment.
  • a fin (236) is an elongated plate-shaped fin formed in such a manner that a metal plate is pressed.
  • a plurality of elongated cut parts (245) each extending from a front edge (238) of the fin (236) in a width direction of the fin (236) are formed.
  • the cut parts (245) are formed at predetermined intervals in a longitudinal direction of the fin (236).
  • Part of the cut part (245) on the leeward side forms a pipe insertion part (246).
  • the pipe insertion part (246) has a vertical width substantially equal to the thickness of a flat tube (53, 58).
  • the length (depth) of the pipe insertion part (246) is substantially equal to the width of the flat tube (58) having a greater width. Since the depth of the pipe insertion part (246) corresponds, as described above, to the width of the flat tube (58) having a greater width, a single type of fins (236) can be used. That is, plural types of molds are not necessarily prepared for manufacturing of the fins (236), and reduction in manufacturing cost can be expected.
  • the flat tube (53, 58) is inserted into a corresponding one of the pipe insertion parts (246) of the fin (236), and is joined to a peripheral edge part of the pipe insertion part (246) by brazing.
  • an end of the flat tube (53, 58) in a width direction thereof is aligned with an end of the cut part (245) on an open side thereof. Since the length of the pipe insertion part (246) corresponds to the width (W2) of the flat tube (58), a clearance is formed on a closed side of the pipe insertion part (246) in the state in which the flat tube (53) is inserted into the pipe insertion part (246).
  • the fin (236) and the flat tube (53, 58) are brazed with each other as follows. First, a side of the fin (236) close to the cut part (245) (i.e., the left side as viewed in FIG. 12 ) faces up. Then, the end of the flat tube (53, 58) in the width direction thereof is set so as to be aligned with the end of the inlet side of the cut part (245) on the open side thereof, more specifically an end of the pipe insertion part (246) on an open side thereof (i.e., the left end as viewed in FIG. 12 ). A brazing material is applied in a linear shape at a position (A) illustrated in FIG. 12 .
  • the application position (A) is illustrated only for one of the flat tubes (53) in FIG. 12 , but the same applies to the other flat tubes (53, 58). If an attempt is made to cause the flat tube (53) to contact the deepest part of the pipe insertion part (246), the brazing material drops, upon brazing, into the pipe insertion part (246), and therefore it is difficult to set the brazing material. However, in the present embodiment, since the end of the flat tube (53, 58) in the width direction thereof is aligned with the end of the cut part (245) on the open side thereof as described above, the brazing material can be easily set.
  • the heat exchanger (40) is placed in a heating furnace (not shown in the figure), and the brazing material is melted. This allows the brazing material to flow along the flat tube (53, 58), and therefore the fin (236) and the flat tube (53, 58) are joined together.
  • part between adjacent ones of the cut parts (245) forms a heat transfer part (237)
  • part of the pipe insertion part (246) on the leeward side forms a leeward-side plate part (247). That is, in the fin (236), a plurality of heat transfer parts (237) adjacent to each other with the flat tube (53, 58) being interposed between adjacent ones of the heat transfer parts (237), and a single leeward-side plate part (247) continuously formed in end parts of the heat transfer parts (237) on the leeward side are provided.
  • each of the heat transfer parts (237) of the fin (236) is arranged between adjacent ones of the flat tubes (53, 58) arranged in the vertical direction, and the leeward-side plate part (247) protrudes beyond the flat tubes (53, 58) toward the leeward side.
  • FIGS. 13A and 13B are views illustrating a main part of the fin (236) of the heat exchanger (40) of the third variation.
  • FIG. 13A is a front view of the fin (236)
  • FIG. 13B is a cross-sectional view along a G-G line illustrated in FIG. 13A .
  • a plurality of louvers (250, 260) are formed in the heat transfer part (237) and the leeward-side plate part (247.
  • the louver (250, 260) is formed in such a manner that part of the heat transfer part (237) or the leeward-side plate part (247) is cut and is folded up.
  • FIG. 14A is a partial cross-sectional view of a heat exchanger (40) of a fourth variation
  • FIG. 14B is a cross-sectional view of a fin (236) along an X-X line illustrated in FIG. 14A
  • waffle parts (251, 252, 253) are, instead of the louvers (250, 260), formed in the plate-shaped fin described in the third variation.
  • the waffle parts (251, 252, 253) has a configuration similar to that described in the second variation.
  • FIG. 15 is a front view illustrating a schematic configuration of the outdoor heat exchanger (40) of the second embodiment.
  • FIG. 16 is a partial cross-sectional view illustrating a front side of the outdoor heat exchanger (40) of the second embodiment.
  • the outdoor heat exchanger (40) is divided into three heat exchange parts (350a-350c). Specifically, in the outdoor heat exchanger (40), the first exchange part (350a), the second exchange part (350b), and the third exchange part (350c) are formed in this order from the bottom to the top.
  • each of a first header collecting pipe (360) and a second header collecting pipe (370) three communication spaces (361a-361c, 371a-371c) are formed in such a manner that each of inner spaces of the first header collecting pipe (360) and the second header collecting pipe (370) is divided by partition plates (339).
  • the communication space (361a-361c) of the first header collecting pipe (360) is further horizontally divided by a partition plate (339).
  • the lower space is a lower space (362a-362c) which is a first space
  • the upper space is an upper space (363a-363c) which is a second space.
  • the exchange part (350a-350c) of the outdoor heat exchanger (40) is divided into a main heat exchange region (main heat exchange part) (351a-351c) and an auxiliary heat exchange region (auxiliary heat exchange part) (352a-352c).
  • eleven flat tubes (53) communicating with a corresponding one of the upper spaces (363a-363c) of the first header collecting pipe (360) form the main heat exchange part (351a-351c)
  • three flat tubes (58) communicating with a corresponding one of the lower spaces (362a-362c) of the first header collecting pipe (360) form the auxiliary heat exchange part (352a-352c).
  • the width of the flat tube (58) provided in the auxiliary heat exchange part (352a-352c) is, as in the first embodiment, greater than that of the flat tube (53) provided in the main heat exchange part (351a-351c).
  • the number of flow paths per flat tube (58) provided in the auxiliary heat exchange part (352a-352c) is greater than the number of flow paths per flat tube (53) provided in the main heat exchange part (351a-351c).
  • fins (corrugated fins) (235) are employed as fins. Needless to say, the fins (54, 59) described in the first embodiment or the fins (236) described in the other variations may be employed.
  • a liquid connection member (380) and a gas header (385) are provided in the outdoor heat exchanger (40).
  • the liquid connection member (380) and the gas header (385) are attached to the first header collecting pipe (360).
  • the liquid connection member (380) includes a single distributor (381) and three thin pipes (382a-382c).
  • a pipe connecting between the outdoor heat exchanger (40) and an expansion valve (33) is connected to a lower end part of the distributor (381).
  • the thin pipe (382a-382c) is, at one end thereof, connected to an upper end part of the distributor (381).
  • the pipe connected to the lower end part thereof and the thin pipes (382a-382c) communicate with each other.
  • the thin pipe (382a-382c) is, at the other end, connected to the first header collecting pipe (360), and communicates with a corresponding one of the lower spaces (362a-362c).
  • the gas header (385) includes a single main pipe part (386) and three connection pipe parts (387a-387c).
  • the main pipe part (386) is formed in a pipe shape curving in an inverted U-shape at an upper part thereof and having a relatively-large diameter.
  • a pipe connecting between the outdoor heat exchanger (40) and a third port of a four-way valve (34) is connected to an upper end part of the main pipe part (386).
  • a lower end part of the main pipe part (386) is closed.
  • the connection pipe parts (387a-387c) laterally protrude from a straight part of the main pipe part (386).
  • refrigerant flows in a direction indicated by arrows illustrated in FIG. 15 in an air-cooling operation.
  • refrigerant flows in a direction opposite to the direction indicated by the arrows illustrated in FIG. 15 .
  • FIG. 17 is a front view illustrating a schematic configuration of the outdoor heat exchanger (40) of the third embodiment.
  • FIG. 18 is a partial cross-sectional view illustrating a front side of the outdoor heat exchanger (40) of the third embodiment.
  • the outdoor heat exchanger (40) includes a single first header collecting pipe (460), a single second header collecting pipe (470), a plurality of flat tubes (53, 58), and a plurality of fins (235).
  • the flat tubes (53, 58) of the outdoor heat exchanger (40) are divided for two upper and lower heat exchange regions (451, 452). That is, in the outdoor heat exchanger (40), the upper heat exchange region (451) and the lower heat exchange region (452) are formed.
  • the heat exchange region (451, 452) is horizontally divided into three heat exchange parts (451a-451c, 452a-452c). Specifically, in the upper heat exchange region (451), the first main heat exchange part (451a), the second main heat exchange part (451b), and the third main heat exchange part (451 c) are formed in this order from the bottom to the top.
  • the first auxiliary heat exchange part (452a), the second auxiliary heat exchange part (452b), and the third auxiliary heat exchange part (452c) are formed in this order from the bottom to the top.
  • the upper heat exchange region (451) and the lower heat exchange region (452) are each divided into the plurality of heat exchange parts (451a-451c, 452a-452c), the number of which is the same between the upper heat exchange region (451) and the lower heat exchange region (452).
  • the main heat exchange part (451a-451c) includes eleven flat tube (53), and the auxiliary heat exchange part (452a-452c) includes three flat tubes (58). Note that the number of heat exchange parts (451 a-451 c, 452a-452c) formed in the heat exchange region (451, 452) may be two or may be equal to or greater than four.
  • the width of the flat tube (58) provided in the auxiliary heat exchange part (452a-452c) is, as in the first embodiment, greater than that of the flat tube (53) provided in the main heat exchange part (451a-451c). Moreover, the number of flow paths per flat tube (58) provided in the auxiliary heat exchange part (452a-452c) is greater than the number of flow paths per flat tube (53) provided in the main heat exchange part (451a-451c).
  • the internal space of the first header collecting pipe (460) is divided into an upper space (461) corresponding to the upper heat exchange region (451) and a lower space (462) corresponding to the lower heat exchange region (452).
  • the upper space (461) is a single space corresponding to all of the main heat exchange parts (451a-451c). That is, the upper space (461) communicates with all of the flat tubes (53) of the main heat exchange parts (451a-455c).
  • the lower space (462) is, by the partition plates (439), further horizontally divided into communication spaces (462a-462c) corresponding to the auxiliary heat exchange parts (452a-452c) such that the number (i.e., three) of the communication spaces (462a-462c) is the same as that of the auxiliary heat exchange parts (452a-452c). That is, in the lower space (462), the first communication space (462a) communicating with the flat tubes (58) of the first auxiliary heat exchange part (452a), the second communication space (462b) communicating with the flat tubes (58) of the second auxiliary heat exchange part (452b), and the third communication space (462c) communicating with the flat tubes (58) of the third auxiliary heat exchange part (452c) are formed.
  • the internal space of the second header collecting pipe (470) is horizontally divided into five communication spaces (471a-471e). Specifically, the internal space of the second header collecting pipe (470) is divided into the four communication spaces (471 a, 471b, 471 d, 471e) corresponding to the main heat exchange parts (451b, 451c) and the auxiliary heat exchange parts (452a, 452b) other than the first main heat exchange part (451a) positioned lowermost in the upper heat exchange region (451) and the third auxiliary heat exchange part (452c) positioned uppermost in the lower heat exchange region (452), and into the single communication space (471c) corresponding to both of the first main heat exchange part (451a) and the third auxiliary heat exchange part (452c).
  • the fourth communication space (471d) and the fifth communication space (471e) are paired respectively with the first communication space (471a) and the second communication space (471b). Specifically, the first communication space (471a) and the fourth communication space (471d) are paired together, and the second communication space (471b) and the fifth communication space (471e) are paired together. Moreover, in the second header collecting pipe (470), a first communication pipe (472) connecting between the first communication space (471a) and the fourth communication space (471d) and a second communication pipe (473) connecting between the second communication space (471b) and the fifth communication space (471e) are provided.
  • the first main heat exchange part (451a) and the third auxiliary heat exchange part (452c) are paired together
  • the second main heat exchange part (451b) and the first auxiliary heat exchange part (452a) are paired together
  • the third main heat exchange part (451 c) and the second auxiliary heat exchange part (452b) are paired together.
  • the number of pairs of the heat exchange parts (451a-451c, 452a-452c) formed in the outdoor heat exchanger (40) is suitably set depending on the height of the outdoor heat exchanger (40) such that the total height of the main heat exchange part (451a-451c) and the auxiliary heat exchange part (452a-452c) which are to be paired together is equal to or lower than about 350 mm (preferably about 300-350 mm).
  • the communication spaces (471c, 471d, 471e) corresponding to the main heat exchange parts (451a-451c) of the upper heat exchange region (451) are formed such that the number thereof (e.g., three) is the same as that of the main heat exchange parts (451 a-451 c).
  • the communication spaces (471 a, 471b, 471c) corresponding to the auxiliary heat exchange parts (452a-452c) of the lower heat exchange region (452) are formed such that the number thereof (e.g., three) is the same as that of the auxiliary heat exchange parts (452a-452c).
  • the communication spaces (471 c, 471 d, 471e) corresponding to the upper heat exchange region (451) and the communication spaces (471a, 471b, 471c) corresponding to the lower heat exchange region (452) communicate with each other.
  • a liquid connection member (480) and a gas connection member (485) are provided in the outdoor heat exchanger (40).
  • the liquid connection member (480) and the gas connection member (485) are attached to the first header collecting pipe (460).
  • the liquid connection member (480) includes a single distributor (481) and three thin pipes (482a-482c).
  • a pipe connecting between the outdoor heat exchanger (40) and an expansion valve (33) is connected to a lower end part of the distributor (481).
  • the thin pipe (482a-482c) is, at one end thereof, connected to an upper end part of the distributor (481).
  • the pipe connected to the lower end part and the thin pipes (482a-482c) communicate with each other.
  • the thin pipe (482a-482c) is, at the other end thereof, connected to the lower space (462) of the first header collecting pipe (460), and communicates with a corresponding one of the communication spaces (462a-462c).
  • the thin pipe (482a-482c) opens at part of a corresponding one of the communication spaces (462a-462c) close to a lower end thereof. That is, the first thin pipe (482a) opens at part of the first communication space (462a) close to the lower end thereof, the second thin pipe (482b) opens at part of the second communication space (462b) close to the lower end thereof, and the third thin pipe (482c) opens at part of the third communication space (462c) close to the lower end thereof.
  • the length of the thin pipe (482a-482c) is independently set such that the difference in flow rate of refrigerant flowing into the auxiliary heat exchange parts (452a-452c) is reduced as much as possible.
  • the gas connection member (485) is formed of a single pipe having a relatively-large diameter.
  • the gas connection member (485) is, at one end thereof, connected to a pipe connecting between the outdoor heat exchanger (40) and a third port of a four-way valve (34).
  • the gas connection member (485) opens, at the other end thereof, part of the upper space (461) close to an upper end thereof in the first header collecting pipe (460).
  • refrigerant flows in a direction indicated by arrows illustrated in FIG. 17 in an air-cooling operation.
  • refrigerant flows in a direction opposite to the direction indicated by the arrows illustrated in FIG. 17 .
  • FIG. 19 is a front view illustrating a schematic configuration of the outdoor heat exchanger (40) of the fourth embodiment.
  • FIG. 20 is a partial cross-sectional view illustrating a front side of the outdoor heat exchanger (40) of the fourth embodiment.
  • flat tubes (53, 58) of the outdoor heat exchanger (40) are, as in the third embodiment, horizontally divided for an upper heat exchange region (451) and a lower heat exchange region (452).
  • the upper heat exchange region (451) is divided into three main heat exchange parts (451a-451c) arranged in the vertical direction, and the lower heat exchange region (452) is formed of a single auxiliary heat exchange part (452a). That is, in the upper heat exchange region (451), the first main heat exchange part (451a), the second main heat exchange part (451b), and the third main heat exchange part (451c) are formed in this order from the bottom to the top.
  • the main heat exchange part (451a-451c) includes eleven flat tubes (53), and the auxiliary heat exchange part (452a) includes nine flat tubes (58). Note that the number of main heat exchange parts (451a-451c) formed in the upper heat exchange region (451) may be two or may be equal to or greater than four.
  • the width of the flat tube (58) provided in the auxiliary heat exchange part (452a) is, as in the first embodiment, greater than that of the flat tube (53) provided in the main heat exchange part (451a-451c). Moreover, the number of flow paths per flat tube (58) provided in the auxiliary heat exchange part (452a) is greater than the number of flow paths per flat tube (53) provided in the main heat exchange part (451a-451c).
  • the internal space of the first header collecting pipe (460) is divided into an upper space (461) corresponding to the upper heat exchange region (451), and a lower space (462) (communication space (462a)) corresponding to the lower heat exchange region (452).
  • the upper space (461) is a single space corresponding to all of the main heat exchange parts (451a-451c). That is, the upper space (461) communicates with all of the flat tubes (53) of the main heat exchange parts (451a-451c).
  • the lower space (462) (communication space (462a)) is a single space corresponding to the single auxiliary heat exchange part (452a), and communicates with the flat tubes (58) of the auxiliary heat exchange part (452a).
  • the internal space of the second header collecting pipe (470) is horizontally divided into four communication spaces (471a-471d). Specifically, the internal space of the second header collecting pipe (470) is divided into three communication spaces (471b, 471 c, 471 d) corresponding respectively to the main heat exchange parts (451a-451c) of the upper heat exchange region (451), and a single communication space (471a) corresponding to the auxiliary heat exchange part (452a) of the lower heat exchange region (452).
  • the first communication space (471a) communicating with the flat tubes (58) of the auxiliary heat exchange part (452a), the second communication space (471b) communicating with the flat tubes (53) of the first main heat exchange part (451a), the third communication space (471c) communicating with the flat tubes (53) of the second main heat exchange part (451b), and the fourth communication space (471d) communicating with the flat tubes (53) of the third main heat exchange part (451c) are formed.
  • the communication member (475) includes a single distributor (476), a single main pipe (477), and three thin pipes (478a-478c).
  • the main pipe (477) is, at one end thereof, connected to a lower end part of the distributor (476), and is, at the other end thereof, connected to the first communication space (471a) of the second header collecting pipe (470).
  • the thin pipe (478a-478c) is, at one end thereof, connected to an upper end part of the distributor (476).
  • the main pipe (477) and the thin pipes (478a-478c) communicate with each other.
  • the thin pipe (478a-478c) communicates, at the other end thereof, with a corresponding one of the second to fourth communication spaces (471b-471d) of the second header collecting pipe (470).
  • the thin pipe (478a-478c) opens at part of a corresponding one of the second to fourth communication spaces (471b-471d) close to a lower end thereof. That is, the thin pipe (478a) opens at part of the second communication space (471b) close to the lower end thereof, the thin pipe (478b) opens at part of the third communication space (471c) close to the lower end thereof, and the thin pipe (478c) opens at part of the fourth communication space (471d) close to the lower end thereof.
  • the length of the thin pipe (478a-478c) is independently set such that the difference in flow rate of refrigerant flowing into the main heat exchange parts (451a-451c) is reduced as much as possible.
  • the communication member (475) of the second header collecting pipe (470) is connected so as to branch from the communication space (471a) into the second to fourth communication spaces (471b-471d) corresponding respectively to the main heat exchange parts (451a-451c). That is, in the second header collecting pipe (470), the communication space (471a) corresponding to the lower heat exchange region (452) and the communication space (471b-471d) corresponding to the upper heat exchange region (451) communicate with each other.
  • a liquid connection member (486) and a gas connection member (485) are provided in the outdoor heat exchanger (40).
  • the liquid connection member (486) and the gas connection member (485) are attached to the first header collecting pipe (460).
  • the liquid connection member (486) is formed of a single pipe having a relatively-large diameter.
  • a pipe connecting between the outdoor heat exchanger (40) and an expansion valve (33) is connected to one end of the liquid connection member (486).
  • the liquid connection member (486) opens, at the other end thereof, at part of the lower space (462) (communication space (462a)) close to a lower end thereof in the first header collecting pipe (460).
  • the gas connection member (485) is formed of a single pipe having a relatively-large diameter.
  • a pipe connecting between the outdoor heat exchanger (40) and a third port of a four-way valve (34) is connected to one end of the gas connection member (485).
  • the gas connection member (485) opens, at the other end thereof, at part of the upper space (461) close to an upper end thereof in the first header collecting pipe (460).
  • refrigerant flows in a direction indicated by arrows illustrated in FIG. 19 in an air-cooling operation.
  • refrigerant flows in a direction opposite to the direction indicated by the arrows illustrated in FIG. 19 .
  • a fifth embodiment of the present disclosure will be described.
  • the present embodiment is configured in such a manner that the configuration of the second header collecting pipe (470) of the outdoor heat exchanger (40) of the third embodiment is changed.
  • the other configuration is similar to that of the third embodiment.
  • only a configuration of a second header collecting pipe (470) of an outdoor heat exchanger (40) will be described with reference to FIGS. 21 and 22 .
  • FIG. 21 is a front view illustrating the schematic configuration of the outdoor heat exchanger (40) of the fifth embodiment.
  • FIG. 22 is a partial cross-sectional view illustrating a front side of the outdoor heat exchanger (40) of the fifth embodiment.
  • an internal space of the second header collecting pipe (470) of the outdoor heat exchanger (40) is vertically divided into three communication spaces (471a-471c) by two partition plates (439). Specifically, in the internal space of the second header collecting pipe (470), the first communication space (471a), the second communication space (471b), and the third communication space (471c) are formed in this order from the right as viewed in FIG. 22 .
  • the first communication space (471a) communicates with flat tubes (53) of a third main heat exchange part (451c) and flat tubes (58) of a first auxiliary heat exchange part (452a).
  • the second communication space (471b) communicates with flat tubes (53) of a second main heat exchange part (451b) and flat tubes (58) of a second auxiliary heat exchange part (452b).
  • the third communication space (471c) communicates with flat tubes (53) of a first main heat exchange part (451a) and flat tubes (58) of a third auxiliary heat exchange part (452c).
  • the third main heat exchange part (451 c) and the first auxiliary heat exchange part (452a) are paired together
  • the second main heat exchange part (451b) and the second auxiliary heat exchange part (452b) are paired together
  • the first main heat exchange part (451a) and the third auxiliary heat exchange part (452c) are paired together.
  • the main heat exchange part (451 a-451 c) in an upper heat exchange region (451) is paired with a corresponding one of the auxiliary heat exchange parts (452a-452c) in a lower heat exchange region (452).
  • the communication space (471a-471c) for a corresponding one of the pairs of heat exchange parts (451a-451c, 452a-452c) is formed such that the number (e.g., three) of communication spaces (471a-471c) is the same as the number of pairs.
  • the flat tubes (53, 58) of the pair of main heat exchange part (451a-451c) and auxiliary heat exchange part (452a-452c) directly communicate with each other in the internal space of the second header collecting pipe (470).
  • the width of the flat tube (58) provided in the auxiliary heat exchange part (452a-452c) is, as in the first embodiment, greater than that of the flat tube (53) provided in the main heat exchange part (451 a-451 c). Moreover, the number of flow paths per flat tube (58) provided in the auxiliary heat exchange part (452a-452c) is greater than the number of flow paths per flat tube (53) provided in the main heat exchange part (451a-451c).
  • refrigerant flows in a direction indicated by arrows illustrated in FIG. 21 in an air-cooling operation.
  • refrigerant flows in a direction opposite to the direction indicated by the arrows illustrated in FIG. 21 .
  • a sixth embodiment of the present disclosure will be described.
  • the present embodiment is configured in such a manner that the configuration of the outdoor heat exchanger (40) of the third embodiment is changed. Differences in the outdoor heat exchanger (40) between the present embodiment and the third embodiment will be described with reference to FIGS. 23 and 24 .
  • An internal space of a second header collecting pipe (470) of the present embodiment is, as in the third embodiment, horizontally divided into five communication spaces (471a-471e).
  • the first communication space (471a) and the fifth communication space (471e) are paired together, and the second communication space (471b) and the fourth communication space (471d) are paired together.
  • a first communication pipe (472) connecting between the second communication space (471b) and the fourth communication space (471d) and a second communication pipe (473) connecting between the first communication space (471a) and the fifth communication space (471e) are provided.
  • a first main heat exchange part (451a) and a third auxiliary heat exchange part (452c) are paired together
  • a second main heat exchange part (451b) and a second auxiliary heat exchange part (452b) are paired together
  • a third main heat exchange part (451c) and a first auxiliary heat exchange part (452a) are paired together.
  • a connection position of a gas connection member (485) in a first header collecting pipe (460) is changed.
  • the gas connection member (485) opens at a middle part of an upper space (461) (i.e., at the middle of the upper space (461) in the vertical direction) in the first header collecting pipe (460).
  • the inner diameter B 1 of the first header collecting pipe (460) is greater than the inner diameter B2 of the second header collecting pipe (470).
  • the inner diameters of the header collecting pipes (460, 470) may be equal to each other, and the gas connection member (485) may open at part of the upper space (461) close to an upper end thereof in the first header collecting pipe (460).
  • FIG. 25 is a partial cross-sectional view of an outdoor heat exchanger (40) of a seventh embodiment.
  • the width of a flat tube (53) of a main heat exchange part (50) and the width of a flat tube (58) of an auxiliary heat exchange part (55) are equal to each other.
  • the number of flat tubes (58) of the auxiliary heat exchange part (55) is less than the number of flat tubes (53) of the main heat exchange part (50).
  • the total cross-sectional area of refrigerant flow paths (49) per flat tube (58) provided in the auxiliary heat exchange part (55) is greater than the total cross-sectional area of refrigerant flow paths (49) per flat tube (53) provided in the main heat exchange part (50).
  • the foregoing bare pipe is, in the present embodiment, employed as the flat tube (53) of the main heat exchange part (50), and each of the refrigerant flow paths (49) has a circular cross section.
  • the flat tube (58) of the auxiliary heat exchange part (55) a plurality of grooves are formed in each of the refrigerant flow paths (49) (see FIG. 7A ). In such a configuration, the flow velocity of refrigerant in the auxiliary heat exchange part (55) can be lowered.
  • a pressure loss in the auxiliary heat exchange part (55) can be also reduced.
  • the width of a flat tube (53) of a main heat exchange part (50) and the width of a flat tube (58) of an auxiliary heat exchange part (55) are equal to each other. Moreover, the number of flat tubes (58) of the auxiliary heat exchange part (55) is less than the number of flat tubes (53) of the main heat exchange part (50).
  • the total cross-sectional area of refrigerant flow paths (49) per flat tube (58) provided in the auxiliary heat exchange part (55) is greater than the total cross-sectional area of refrigerant flow paths (49) per flat tube (53) provided in the main heat exchange part (50).
  • the number of refrigerant flow paths (49) in the flat tube (53) of the main heat exchange part (50) is less than the number of refrigerant flow paths (49) in the flat tube (58) of the auxiliary heat exchange part (55).
  • the flow velocity of refrigerant in the auxiliary heat exchange part (55) can be lowered.
  • a pressure loss in the auxiliary heat exchange part (55) can be also reduced.
  • each of the refrigerant flow paths (49) of the heat transfer pipe (53, 58) in the main heat exchange part (50) or the auxiliary heat exchange part (55) may be provided with or without grooves (see FIGS. 7A and 7B ).
  • each of the outdoor heat exchangers (40) of the second to eighth embodiments various fins such as the fins (54, 59, 235, 236) described in the first embodiment and the variations thereof may be employed.
  • the present disclosure is useful as the heat exchanger including the flat tubes and the fins and configured to exchange heat between fluid flowing through the flat tube and air and as the air conditioner.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP12736601.1A 2011-01-21 2012-01-23 Wärmetauscher und klimaanlage Withdrawn EP2667134A4 (de)

Applications Claiming Priority (2)

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PCT/JP2012/000367 WO2012098912A1 (ja) 2011-01-21 2012-01-23 熱交換器および空気調和機

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EP2667134A4 (de) 2014-07-09
JPWO2012098912A1 (ja) 2014-06-09
KR101451057B1 (ko) 2014-10-15
AU2012208118A1 (en) 2013-08-15
US20130292098A1 (en) 2013-11-07
JP5617935B2 (ja) 2014-11-05
WO2012098912A1 (ja) 2012-07-26
KR20130129265A (ko) 2013-11-27
CN103339457A (zh) 2013-10-02

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