EP3276289A1 - Wärmetauscher und klimaanlage - Google Patents

Wärmetauscher und klimaanlage Download PDF

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Publication number
EP3276289A1
EP3276289A1 EP16786110.3A EP16786110A EP3276289A1 EP 3276289 A1 EP3276289 A1 EP 3276289A1 EP 16786110 A EP16786110 A EP 16786110A EP 3276289 A1 EP3276289 A1 EP 3276289A1
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EP
European Patent Office
Prior art keywords
refrigerant
flat tubes
heat exchanger
heat exchange
leeward
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.)
Granted
Application number
EP16786110.3A
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English (en)
French (fr)
Other versions
EP3276289A4 (de
EP3276289B1 (de
Inventor
Masanori Jindou
Yoshio Oritani
Shun Yoshioka
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
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Daikin Industries Ltd
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Filing date
Publication date
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Publication of EP3276289A1 publication Critical patent/EP3276289A1/de
Publication of EP3276289A4 publication Critical patent/EP3276289A4/de
Application granted granted Critical
Publication of EP3276289B1 publication Critical patent/EP3276289B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F1/24—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
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to a heat exchanger and an air conditioner.
  • this heat exchanger functions as an evaporator, for example, a refrigerant in a saturated liquid state flows through the lower heat exchange region to evaporate through absorption of heat from the air. This refrigerant further evaporates by flowing through the upper heat exchange region to be a superheated refrigerant, which then flows out of the heat exchanger.
  • Patent Document 1 Japanese Unexamined Patent Publication No. 2012-163328
  • the flat tubes may have their length extended so as to increase the channel length of refrigerant channels formed in the flat tubes.
  • the increase in the total length of the refrigerant channels may result in an increase in the pressure loss of the refrigerant passing through the refrigerant channels.
  • each of the refrigerant channels has a relatively small channel area.
  • the flow velocity of the refrigerant may easily increase in each of the refrigerant channels.
  • the pressure loss of the refrigerant flowing through each of the refrigerant channels may further increase.
  • a first aspect of the present invention is directed to a heat exchanger including: a plurality of flat tubes (31, 41) arranged parallel to each other, in each of which a plurality of refrigerant channels (C) are formed; and fins (32, 42) joined to the flat tubes (31, 41), the heat exchanger allowing a refrigerant flowing through each of the refrigerant channels (C) to exchange heat with air.
  • a plurality of banks (30, 40) each of which includes two or more of the flat tubes (31, 41), are arranged in an air flow direction. The refrigerants in the plurality of banks (30, 40) flow in parallel with each other.
  • Each of the flat tubes (31, 41) in the plurality of banks (30, 40) has one or more bent portions (33a, 33b, 33c) which are bent in a width direction of the flat tubes (31, 41) such that the flat tubes (31, 41) of a pair of the banks (30, 40) adjacent to each other in the air flow direction extend along with each other.
  • each of the banks (30, 40) includes the principal heat exchange region (35, 45) and the auxiliary heat exchange region (37, 47).
  • the refrigerants in the flat tubes (31, 41) in the principal heat exchange regions (35, 45) of the banks (30, 40) flow in parallel with each other, and the refrigerants in the flat tubes (31, 41) in the auxiliary heat exchange regions (37, 47) of the banks (30, 40) also flow in parallel with each other. This reduces the pressure loss of the refrigerants flowing through the principal heat exchange regions (35, 45) and the auxiliary heat exchange regions (37, 47).
  • the refrigerant in the flat tubes (31, 41) in the principal heat exchange region (35, 45) and the refrigerant in the flat tubes (31, 41) in the auxiliary heat exchange region (37, 47) in an adjacent pair of the banks (30, 40) flow in the same direction.
  • Each of the banks (30, 40) is connected to a communicating pipe (68, 88), a branched liquid pipe (28), and a branched gas pipe (29).
  • the branched liquid pipe (28) and the branched gas pipe (29) are provided for an end of each of the flat tubes (31, 41), and the communicating pipe (68, 88) is provided for the other end of each of the flat tubes (31, 41). This reduces space for the branched gas pipe (29) and the branched liquid pipe (28) in the heat exchanger.
  • the refrigerants in the flat tubes (31, 41) of the adjacent banks (30, 40) flow in opposite directions.
  • the superheated regions of the flat tubes (31, 41) of the banks (30, 40) are located distant from each other. This substantially prevents the drift of the air.
  • the refrigerants in the flat tubes (31, 41) of the adjacent banks (30, 40) among the plurality of banks (30, 40) flow in opposite directions.
  • the superheated refrigerant regions of the flat tubes (31, 41) of the banks (30, 40) do not overlap with each other. If the superheated refrigerant regions (S1, S2) of the banks (30, 40) overlapped with each other in the air flow direction, the air would flow only toward the overlapping regions. According to the present invention, however, the superheated refrigerant regions (S1, S2) do not overlap with each other. Thus, the drift of the air can be effectively prevented.
  • the refrigerants in the flat tubes (31, 41) of the banks (30, 40) are allowed to flow in parallel with each other.
  • the pressure loss of the refrigerants flowing through the refrigerant channels (C) of the flat tubes (31, 41) can be drastically reduced. Consequently, with an increase in power caused by the increase in pressure loss reduced, a desired heat exchange efficiency can be achieved.
  • the flat tubes (31, 41) of each bank (30, 40) may be bent to fabricate a four-surface heat exchanger. This allows for downsizing of the heat exchanger. Reducing the width of the flat tubes (31, 41) allows the ventilation resistance between the flat tubes (31, 41) of each bank (30, 40) to be reduced, thus curbing a decline in thermal transmittance. Further, the decrease in the width of the flat tubes (31, 41) also precludes the possibility of condensed water stagnating on the flat tubes (31, 41). This substantially prevents the surfaces of the flat tubes (31, 41) from being frosted.
  • the pressure loss of the refrigerants can be cut down in both of the principal heat exchange region (35, 45) and the auxiliary heat exchange region (37, 47).
  • the outdoor heat exchanger (23) allows outdoor air and a refrigerant to exchange heat.
  • the outdoor heat exchanger (23) will be described in detail later.
  • the indoor heat exchanger (25) allows indoor air and the refrigerant to exchange heat.
  • the indoor heat exchanger (25) is configured as a so-called "cross-fin, fin-and-tube heat exchanger" including circular heat transfer tubes.
  • the refrigerant circuit (20) performs a refrigeration cycle with the four-way switching valve (22) set to the first state.
  • the refrigerant circulates through the outdoor heat exchanger (23), the expansion valve (24), and the indoor heat exchanger (25) in this order, the outdoor heat exchanger (23) functions as a condenser, and the indoor heat exchanger (25) functions as an evaporator.
  • the outdoor heat exchanger (23) a gas refrigerant coming from the compressor (21) is condensed through dissipation of heat to the outdoor air. Then, the condensed refrigerant flows toward the expansion valve (24).
  • the refrigerant circuit (20) performs a refrigeration cycle with the four-way switching valve (22) set to the second state.
  • the refrigerant circulates through the indoor heat exchanger (25), the expansion valve (24), and the outdoor heat exchanger (23) in this order, the indoor heat exchanger (25) functions as a condenser, and the outdoor heat exchanger (23) functions as an evaporator.
  • the refrigerant which has expanded while passing through the expansion valve (24) and turned into a two-phase gas-liquid refrigerant, flows into the outdoor heat exchanger (23).
  • the refrigerant that has flowed into the outdoor heat exchanger (23) evaporates through absorption of heat from the outdoor air, and then flows toward the compressor (21).
  • the outdoor heat exchanger (23) is a four-surface air heat exchanger having four side surfaces (23a, 23b, 23c, 23d).
  • the outdoor heat exchanger (23) includes a first side surface (23a), a second side surface (23b), a third side surface (23c), and a fourth side surface (23d), which are arranged continuously.
  • the first side surface (23a) is a lower left surface
  • the second side surface (23b) is an upper left surface
  • the third side surface (23c) is an upper right surface
  • the fourth side surface (23d) is a lower right surface.
  • the side surfaces (23a, 23b, 23c, 23d) have approximately the same height.
  • the first and fourth side surfaces (23a) and (23d) have a smaller width than the second and third side surfaces (23b) and (23c).
  • the outdoor heat exchanger (23) is a double-bank heat exchanger including two banks (30, 40), each having flat tubes (31, 41) and fins (32, 42).
  • the outdoor heat exchanger (23) may include three or more banks.
  • one of the two banks on the windward side in an air flow direction is configured as a windward bank (30)
  • the other bank on the leeward side is configured as a leeward bank (40).
  • FIGS. 3 and 4 schematically show the windward and leeward banks (30) and (40) respectively developed in separate plan views.
  • the outdoor heat exchanger (23) includes a first header collecting pipe (50), a second header collecting pipe (60), a third header collecting pipe (70), a fourth header collecting pipe (80), a first divergence unit (91), and a second divergence unit (92).
  • the first header collecting pipe (50) is arranged to stand upright near one end of the windward bank (30) adjacent to the first side surface (23a).
  • the second header collecting pipe (60) is arranged to stand upright near the other end of the windward bank (30) adjacent to the fourth side surface (23d).
  • the third header collecting pipe (70) is arranged to stand upright near one end of the leeward bank (40) adjacent to the first side surface (23a).
  • the fourth header collecting pipe (80) is arranged to stand upright near the other end of the leeward bank (40) adjacent to the fourth side surface (23d).
  • the first divergence unit (91) is arranged to stand upright near the first header collecting pipe (50).
  • the second divergence unit (92) is arranged to stand upright near the third header collecting pipe (70).
  • the flat tubes (31, 41), the fins (32, 42), the first to fourth header collecting pipes (50, 60, 70, 80), and the first and second divergence units (91, 92) are all members made of an aluminum alloy, and are joined to one another by brazing.
  • the windward bank (30) includes multiple flat tubes (31) and multiple fins (32).
  • Each of the flat tubes (31) is a heat transfer tube having a flat, substantially oval cross section when viewed in a section cut along a plane perpendicular to its axis (see FIG. 7 ).
  • the plurality of flat tubes (31) are arranged such that upper and lower flat surfaces of each of the flat tubes face those of adjacent flat tubes. That is, the plurality of flat tubes (31) are vertically arranged at regular intervals, with their axes extending substantially parallel to each other.
  • each of the flat tubes (31) includes a first windward tube portion (31a) extending along the first side surface (23a), a second windward tube portion (31b) extending along the second side surface (23b), a third windward tube portion (31c) extending along the third side surface (23c), and a fourth windward tube portion (31d) extending along the fourth side surface (23d). Further, as shown in FIG. 2 , each of the flat tubes (31) includes a first windward tube portion (31a) extending along the first side surface (23a), a second windward tube portion (31b) extending along the second side surface (23b), a third windward tube portion (31c) extending along the third side surface (23c), and a fourth windward tube portion (31d) extending along the fourth side surface (23d). Further, as shown in FIG.
  • An end of the first windward tube portion (31a) of each of the flat tubes (31) is inserted in the first header collecting pipe (50) (see FIG. 5 ), and an end of the fourth windward tube portion (31d) of each of the flat tubes (31) is inserted in the second header collecting pipe (60) (see FIG. 6 ).
  • a plurality of refrigerant channels (C) are formed in each of the flat tubes (31).
  • the plurality of refrigerant channels (C) extend in the axial direction of the flat tubes (31), and are aligned in the width direction of the flat tubes (31) (an air flow direction).
  • Each of the refrigerant channels (C) opens at both end faces of an associated one of the flat tubes (31).
  • a refrigerant supplied to the windward bank (30) exchanges heat with air while flowing through the refrigerant channels (C) in the flat tubes (31).
  • the plurality of refrigerant channels (C) in each of the flat tubes (31) of the windward bank (30) constitute a set of windward refrigerant channels (C1).
  • Each of the fins (32) is a vertically elongated plate fin formed by pressing a metal plate as shown in FIG. 7 .
  • the plurality of fins (32) are arranged at regular intervals in the axial direction of the flat tubes (31).
  • Each of the fins (32) has a plurality of long narrow notches (32a) extending in the width direction of the fin (32) from an outer edge (i.e., a windward edge) of the fin (32).
  • the plurality of notches (32a) are formed in the fin (32) at regular intervals in the longitudinal direction of the fins (32) (the vertical direction).
  • a windward portion of each notch (32a) serves as a tube receiving portion (32b).
  • the flat tube (31) is inserted in the tube receiving portion (32b), and is joined to a peripheral edge portion of the tube receiving portion (32b) by brazing. Further, the fin (32) is provided with louvers (32c) for promoting heat transfer.
  • the principal windward heat exchange sections (36) each include the same number of flat tubes (31), e.g., six flat tubes (31).
  • the number of the flat tubes (31) provided for each of the principal windward heat exchange sections (36) is merely an example, and may be two or more, or one.
  • the auxiliary windward heat exchange sections (38) each include the same number of flat tubes (31), e.g., two flat tubes (31).
  • the number of the flat tubes (31) provided for each of the auxiliary windward heat exchange sections (36) is merely an example, and may be two or more, or one.
  • a plurality of refrigerant channels (C) are formed in each of the flat tubes (41).
  • the plurality of refrigerant channels (C) extend in the axial direction of the flat tubes (41), and are aligned in the width direction of the flat tubes (41) (an air flow direction).
  • Each of the refrigerant channels (C) opens at both end faces of an associated one of the flat tubes (41).
  • a refrigerant supplied to the leeward bank (40) exchanges heat with air while flowing through the refrigerant channels (C) in the flat tubes (41).
  • the plurality of refrigerant channels (C) in each of the flat tubes (41) of the leeward bank (40) constitute a set of leeward refrigerant channels (C2).
  • the leeward bank (40) is divided into two heat exchange regions (45, 47) arranged one above the other.
  • the upper heat exchange region serves as a principal leeward heat exchange region (45)
  • the lower heat exchange region serves as an auxiliary leeward heat exchange region (47).
  • the number of the flat tubes (41) allocated to the auxiliary leeward heat exchange region (47) is smaller than that of the flat tubes (41) forming the principal leeward heat exchange region (45).
  • the principal leeward heat exchange region (45) is divided into six vertically arranged, principal leeward heat exchange sections (46).
  • the auxiliary leeward heat exchange region (47) is divided into six vertically arranged, auxiliary leeward heat exchange sections (48). That is, the principal and auxiliary leeward heat exchange regions (45) and (47) are each divided into the same number of heat exchange sections. Note that the number of the principal and auxiliary leeward heat exchange sections (46) and (48) is merely an example, and is suitably two or more.
  • the principal leeward heat exchange sections (46) each include the same number of flat tubes (41), e.g., six flat tubes (41).
  • the number of the flat tubes (41) provided for each of the principal leeward heat exchanger portions (46) is merely an example, and may be two or more, or one.
  • the third header collecting pipe (70) is a cylindrical member having closed top and bottom.
  • the third header collecting pipe (70) has a length (height) which is approximately the same as the heights of the windward and leeward banks (30) and (40).
  • the fourth header collecting pipe (80) is a cylindrical member with closed top and bottom.
  • the fourth header collecting pipe (80) has a length (height) which is approximately the same as the heights of the windward and leeward banks (30) and (40).
  • the fourth header collecting pipe (80) has substantially the same internal configuration as the second header collecting pipe (60) shown in FIG. 6 . Specifically, as shown in FIG. 4 , the internal space of the fourth header collecting pipe (80) is horizontally divided into two by a principal divider (81). The space above the principal divider (81) is an upper leeward space (82) corresponding to the principal leeward heat exchange region (45). The space below the principal divider (81) is a lower leeward space (83) corresponding to the auxiliary leeward heat exchange region (47).
  • the upper leeward space (82) is divided into six principal leeward communicating spaces (85) by five dividers (84) vertically arranged at regular intervals.
  • the six principal leeward communicating spaces (85) respectively correspond to the six principal leeward heat exchange sections (46).
  • the first leeward tube portions (41a) of the six flat tubes (41) for example, communicate with each of the principal leeward communicating spaces (85).
  • the lower leeward space (83) is divided into six auxiliary leeward communicating spaces (87) by five dividers (86) vertically arranged at regular intervals.
  • the six auxiliary leeward communicating spaces (87) respectively correspond to the six auxiliary leeward heat exchange sections (48).
  • Each of the leeward communicating pipes (88) connects associated ones of the ends of the flat tubes (41) in the principal leeward heat exchange region (45) of the leeward bank (40) to associated ones of the ends of the flat tubes (41) in the auxiliary leeward heat exchange region (47).
  • the outdoor heat exchanger (23) which functions as a condenser and an evaporator is configured to allow the refrigerant in the sets of windward refrigerant channels (C1) in the principal windward heat exchange region (35) to flow in the same direction as the refrigerant in the sets of leeward refrigerant channels (C2) in the principal leeward heat exchange region (45).
  • This refrigerant turns to a saturated, single-phase liquid refrigerant (saturated temperature: 50°C) while passing through the sets of windward refrigerant channels (C2) in the flat tubes (41) of the auxiliary windward heat exchange region (47), and further dissipates heat to become a supercooled refrigerant (at 47°C, for example).
  • the flows of the refrigerant that have passed through the leeward communicating pipes (88) are respectively supplied to the principal leeward communicating spaces (85) of the fourth header collecting pipe (80), and enter the principal leeward heat exchange sections (46).
  • the flows of the refrigerant passing through the sets of leeward refrigerant channels (C2) in the flat tubes (41) of each of the principal leeward heat exchange sections (46) evaporate through further absorption of heat from the air to be superheated (turn to a single gas phase).
  • the saturation temperature of the refrigerant further decreases (to 0°C, for example) due to the pressure loss of the refrigerant passing through the set of leeward refrigerant channels (C2).
  • This refrigerant turns to a single gas phase refrigerant while passing through the flat tubes (41) of the principal leeward heat exchange region (45), has its temperature raised to 1°C, and then flows out of the flat tubes (41) of the principal leeward heat exchange region (45).
  • the outdoor heat exchanger (23) functions as an evaporator
  • the temperature of the refrigerant becomes lower than the temperature of the air throughout the outdoor heat exchanger (23). This ensures a sufficient quantity of heat absorbed from the air to the refrigerant (a sufficient quantity of heat absorbed by the refrigerant).
  • the refrigerant in the sets of windward refrigerant channels (C1) and the refrigerant in the sets of leeward refrigerant channels (C2) flow in parallel with each other.
  • the pressure loss of the refrigerant channels (C) is proportional to the square of the velocity of a refrigerant flow, and to the total length of the refrigerant channels.
  • the refrigerant in the sets of refrigerant channels (C1) in the windward bank (30) and the refrigerant in the sets of refrigerant channels (C2) in the leeward bank (40) are allowed to flow in parallel with each other.
  • This configuration reduces the pressure loss of the refrigerant in the refrigerant channels (C) to 1/8 of that of the comparative example.
  • the first embodiment achieves the following advantages and effects.
  • the refrigerants in the flat tubes (31, 41) of the banks (30, 40) are allowed to flow in parallel with each other.
  • the pressure loss of the refrigerants flowing through the refrigerant channels (C) of the flat tubes (31, 41) can be drastically reduced. Consequently, with an increase in power caused by the increase in pressure loss reduced, a desired heat exchange efficiency can be achieved.
  • the branched liquid pipe (28) and the branched gas pipe (29) for providing parallel refrigerant flows in the banks (30, 40) may be collectively arranged. This configuration can reduce the space occupied by the pipes, or facilitate the installation of the pipes.
  • the width of the flat tubes (31, 41) allows the ventilation resistance between the flat tubes (31, 41) of each bank (30, 40) to be reduced, thus curbing a decline in thermal transmittance. Further, the decrease in the width of the flat tubes (31, 41) also precludes the possibility of condensed water stagnating on the flat tubes (31, 41). This substantially prevents the surfaces of the flat tubes (31, 41) from being frosted.
  • An air conditioner (10) according to a second embodiment includes an outdoor heat exchanger (23) configured differently from the counterpart of the first embodiment.
  • the outdoor heat exchanger (23) of the second embodiment has a windward bank (30) configured in the same manner as the counterpart of the first embodiment.
  • the third header collecting pipe (70) is arranged to stand upright near one end of the leeward bank (40) adjacent to the fourth side surface (23d).
  • the fourth header collecting pipe (80) is arranged to stand upright near the other end of the leeward bank (40) adjacent to the first side surface (23a). That is to say, in the second embodiment, the positions where the third and fourth header collecting pipes (70) and (80) are arranged in the longitudinal direction of the flat tubes (31, 41) are interchanged, compared to the first embodiment.
  • the second divergence unit (92) is also arranged to stand upright near the third header collecting pipe (70).
  • the outdoor heat exchanger (23) functions as a condenser and an evaporator
  • the refrigerant in the flat tubes (31) of the windward bank (30) and the refrigerant in the flat tubes (41) of the leeward bank (40) flow in parallel with each other.
  • the outdoor heat exchanger (23) which functions as a condenser and an evaporator is configured to allow a refrigerant in the flat tubes (31) of the principal windward heat exchange region (35) of the windward bank (30) and a refrigerant in the flat tubes (41) of the principal leeward heat exchange region (45) of the leeward bank (40) to flow in parallel with each other, and also allow a refrigerant in the flat tubes (31) of the auxiliary windward heat exchange region (37) of the windward bank (30) and a refrigerant in the flat tubes (41) of the auxiliary leeward heat exchange region (47) of the leeward bank (40) to flow in parallel with each other.
  • the outdoor heat exchanger (23) which functions as a condenser and an evaporator is configured to allow the refrigerant in the sets of windward refrigerant channels (C1) in the principal windward heat exchange region (35) to flow in the opposite direction to the refrigerant in the sets of leeward refrigerant channels (C2) in the principal leeward heat exchange region (45).
  • the indoor heat exchanger (25) functions as an evaporator
  • the outdoor heat exchanger (23) functions as a condenser.
  • the refrigerant flows in the outdoor heat exchanger (23) during the cooling operation.
  • the gas refrigerant discharged from the compressor (21) is supplied to the outdoor heat exchanger (23) via the pipe (18).
  • This refrigerant in the pipe (18) diverges into the first and second principal gas pipes (52a) and (82a).
  • the refrigerant supplied to the first principal gas pipe (52a) flows into the upper windward space (52) of the first header collecting pipe (50), and is distributed to the principal windward heat exchange sections (36).
  • Flows of the refrigerant passing through the sets of windward refrigerant channels (C1) in the flat tubes (31) of each of the principal windward heat exchange sections (36) are condensed through dissipation of heat to the air.
  • the flows of the refrigerant are respectively supplied to the principal windward communicating spaces (65) of the second header collecting pipe (60), and enter the windward communicating pipes (68).
  • the flows of the supercooled liquid refrigerant are respectively supplied to the auxiliary windward spaces (55) of the first header collecting pipe (50), merge together in the first divergence unit (91), and are sent to the liquid interconnecting pipe (13) via the first principal liquid pipe (91c).
  • the refrigerant supplied from the pipe (18) to the second principal gas pipe (72a) flows into the upper leeward space (72) of the third header collecting pipe (70), and is distributed to the principal leeward heat exchange sections (46).
  • Flows of the refrigerant passing through the sets of leeward refrigerant channels (C2) in the flat tubes (41) of each of the principal leeward heat exchange sections (46) are condensed through dissipation of heat to the air.
  • the flows of the refrigerant are respectively supplied to the principal leeward communicating spaces (85) of the fourth header collecting pipe (80), and enter the leeward communicating pipes (88).
  • the flows of the refrigerant that have passed through the leeward communicating pipes (88) are respectively supplied to the auxiliary leeward communicating spaces (87) of the fourth header collecting pipe (80), and enter the auxiliary leeward heat exchange sections (48).
  • the flows of the refrigerant passing through the sets of leeward refrigerant channels (C2) in the flat tubes (41) of each of the auxiliary leeward heat exchange sections (48) are condensed through further dissipation of heat to the air, and supercooled (turn to a single liquid phase).
  • the flows of the supercooled liquid refrigerant are supplied to the auxiliary leeward spaces (75) of the third header collecting pipe (70), merge together in the second divergence unit (92), and then the merged refrigerant is sent to the liquid interconnecting pipe (13) together with the refrigerant flowing out of the first divergence unit (91).
  • the indoor heat exchanger (25) functions as a condenser
  • the outdoor heat exchanger (23) functions as an evaporator.
  • the refrigerant flows in the outdoor heat exchanger (23) during the heating operation.
  • a refrigerant that has expanded while passing through the expansion valve (24) and turned into a two-phase gas and liquid refrigerant is supplied to the outdoor heat exchanger (23) via the pipe (17).
  • This refrigerant diverges from the pipe (17) into the first and second divergence units (91) and (92).
  • the refrigerant supplied to the first divergence unit (91) diverges to the liquid connecting pipes (91b), and is distributed to the auxiliary windward heat exchange sections (38) via the auxiliary windward spaces (55) of the first header collecting pipe (50).
  • Flows of the refrigerant passing through the sets of windward refrigerant channels (C1) in the flat tubes (31) of each of the auxiliary windward heat exchange sections (38) evaporate through absorption of heat from the air.
  • the flows of the refrigerant are respectively supplied to the auxiliary windward communicating spaces (67) of the second header collecting pipe (60), and enter the windward communicating pipes (68).
  • the flows of the refrigerant that have passed through the windward communicating pipes (68) are respectively supplied to the principal windward communicating spaces (65) of the second header collecting pipe (60), and enter the principal windward heat exchange sections (36).
  • the flows of the refrigerant passing through the sets of windward refrigerant channels (C1) in the flat tubes (31) of each of the principal windward heat exchange sections (36) evaporate through further absorption of heat from the air to be superheated (turn to a single gas phase).
  • the flows of the superheated gas refrigerant merge together in the upper windward space (52) of the first header collecting pipe (50), and then the merged refrigerant is sent to the gas interconnecting pipe (14) via the first principal gas pipe (52a).
  • the refrigerant supplied to the second divergence unit (92) diverges to the liquid connecting pipes (92b), and enter the auxiliary leeward heat exchange sections (48) via the auxiliary leeward spaces (75) of the third header collecting pipe (70).
  • Flows of the refrigerant passing through the sets of leeward refrigerant channels (C2) in the flat tubes (41) of each of the auxiliary leeward heat exchange sections (48) evaporate through absorption of heat from the air.
  • the flows of the refrigerant are respectively supplied to the auxiliary leeward communicating spaces (87) of the fourth header collecting pipe (80), and enter the leeward communicating pipes (88).
  • the flows of the refrigerant that have passed through the leeward communicating pipes (88) are respectively supplied to the principal leeward communicating spaces (85) of the fourth header collecting pipe (80), and enter the principal leeward heat exchange sections (46).
  • the flows of the refrigerant passing through the sets of leeward refrigerant channels (C2) in the flat tubes (41) of each of the principal leeward heat exchange sections (46) evaporate through further absorption of heat from the air to be superheated (turn to a single gas phase).
  • the flows of the superheated gas refrigerant merge together in the upper leeward space (72) of the third header collecting pipe (70), and the merged refrigerant is sent to the gas interconnecting pipe (14) together with the refrigerant flowing out of the first principal gas pipe (52a).
  • each of the two banks (30, 40) is provided with the sets of refrigerant channels (C1, C2), and refrigerants in the sets of refrigerant channels (C1, C2) are allowed to flow in parallel with each other.
  • the two-phase gas and liquid refrigerant is used to cool the air.
  • moisture in the air may sometimes be condensed to frost the surfaces of the flat tubes (31, 41) and fins (32, 42).
  • superheated regions (S1, S2) of the banks (30, 40) are configured not to overlap with each other in the air flow direction so as to prevent the drift of the air.
  • the refrigerant in the sets of windward refrigerant channels (C1) and the refrigerant in the sets of leeward refrigerant channels (C2) flow in opposite directions as described above.
  • the superheated region (S1) of the windward bank (30) is formed near an end of each of the first windward tube portions (31a) of the flat tubes (31), while the superheated region (S2) of the leeward bank (40) is formed near an end of each of the fourth leeward tube portions (41d) of the flat tubes (41). That is, the superheated regions (S1) and (S2) are disposed most distant from each other in the longitudinal direction of the flat tubes (31, 41). This can effectively prevent the superheated regions (S1) and (S2) from overlapping with each other in the air flow direction, and also substantially eliminates the above-described drift of the air.
  • various parameters such as the number and size of the flat tubes (31, 41), the number and size of the refrigerant channels (C), the amount of the refrigerant circulating, and the volume of the air, are set to prevent the superheated regions (S1) and (S2) from overlapping with each other in the air flow direction.
  • the pressure loss of the refrigerant can also be reduced as in the first embodiment.
  • the outdoor heat exchanger (23) functions as an evaporator
  • the superheated regions (S1, S2) where the superheated refrigerants flow can be substantially prevented from overlapping with each other.
  • the biased drift of the air only toward the superheated regions (S1, S2) can be prevented.
  • the air can still flow uniformly throughout the heat exchanger. This improves the heat exchange efficiency, and eventually the evaporation performance, of the heat exchanger.
  • each adjacent pair of the header collecting pipes (50, 70) and (60, 80) is comprised of two separate members.
  • at least one pair of these header collecting pipes may be configured as a single member, and the internal space thereof may be divided into two.
  • the superheated regions (S1, S2) of the sets of refrigerant channels (C1, C2) adjacent to each other in the two banks of the flat tubes (31, 41) do not overlap with each other.
  • each adjacent pair of the superheated regions among three or more sets of refrigerant channels (C1, C2), for example, may be configured not to overlap with each other.
  • auxiliary heat exchange regions (37, 47) of the outdoor heat exchanger (23) may be omitted.
  • the heat exchanger of the present disclosure is implemented as the outdoor heat exchanger (23).
  • the heat exchanger of the present disclosure may also be implemented as the indoor heat exchanger (25).
  • the indoor heat exchanger (25) is suitably a four-surface heat exchanger built in a ceiling-mounted, or -suspended indoor unit, for example.
  • the outdoor and indoor heat exchangers (23) and (25) do not necessarily have four surfaces, but may have three surfaces or less.
  • the heat exchanger of the present disclosure has, as shown in FIG. 7 , for example, the fins (32, 42) separately provided on the windward and leeward sides for the windward and leeward banks (30) and (40), respectively.
  • the flat tubes (31, 41) may form two banks arranged in the air flow direction, and the windward and leeward fins (32, 42) may be configured as a single fin covering both of the windward and leeward banks (30) and (40).
  • each of the fins (32, 42) of the heat exchanger of the present disclosure is provided with the tube receiving portions (32b, 42b) extending from a windward edge portion, and the flat tubes (31, 41) are inserted in the tube receiving portions (32b, 42b).
  • the heat exchanger may be configured such that the tube receiving portions are formed to extend from a leeward edge portion of the fin (32, 42), and the flat tubes (31, 41) may be inserted in the tube receiving portions.
  • each of the fins (32, 42) of the present disclosure is provided with the louvers (32c, 42c) as heat transfer accelerators.
  • bulges (projections) protruding from the fins (32, 42) in the thickness direction, slits, or any other suitable feature may be provided as the heat transfer accelerator.
  • the two banks (30, 40) of the above-described embodiments may have different configurations.
  • the flat tubes (31, 41) disposed in two banks may have different widths, may be arranged at different intervals in the thickness direction (the vertical direction), and may have the refrigerant channels (C) of different channel areas and in different numbers.
  • the fins (32, 42) disposed in two banks may have different widths (lengths measured in the air flow direction), may be arranged at different pitches (intervals) in the thickness direction of the fins (32, 42), or may have different shapes.
  • a refrigerant regulating valve may be provided for each of the plurality of banks (30, 40). Specifically, if the degrees of opening of the refrigerant regulating valves are controlled separately, the amounts of refrigerants flowing in parallel into the banks (30, 40) may be separately controlled.
  • the present invention is useful for a heat exchanger and an air conditioner.

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EP16786110.3A 2015-04-27 2016-04-08 Wärmetauscher und klimaanlage Active EP3276289B1 (de)

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EP3276289A4 (de) 2018-12-05
CN107429975B (zh) 2020-04-24
WO2016174830A1 (ja) 2016-11-03
US20180135900A1 (en) 2018-05-17
EP3276289B1 (de) 2024-03-06
JP6641721B2 (ja) 2020-02-05
JP2016205744A (ja) 2016-12-08

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