US20140326019A1 - Double-pipe heat exchanger and air conditioner using same - Google Patents

Double-pipe heat exchanger and air conditioner using same Download PDF

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Publication number
US20140326019A1
US20140326019A1 US14/358,527 US201214358527A US2014326019A1 US 20140326019 A1 US20140326019 A1 US 20140326019A1 US 201214358527 A US201214358527 A US 201214358527A US 2014326019 A1 US2014326019 A1 US 2014326019A1
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United States
Prior art keywords
pipe
heat exchanger
refrigerant
double
liquid
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Abandoned
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US14/358,527
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English (en)
Inventor
Mikio Kagawa
Tadashi Sao
Yuusuke Nakagawa
Katsutoshi Sakurai
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication date
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Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAGAWA, MIKIO, SAKURAI, KATSUTOSHI, NAKAGAWA, YUUSUKE, SAO, TADASHI
Publication of US20140326019A1 publication Critical patent/US20140326019A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
    • 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
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/14—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically both tubes being bent
    • 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Definitions

  • the present invention relates to a double-pipe heat exchanger and an air conditioner using same.
  • Patent Literature 1 discloses a double-pipe heat exchanger of a vertical pipe shape arranged in the up and down direction, and a double-pipe heat exchanger of an inverted U shape.
  • Patent Literature 1 Japanese Unexamined Patent Publication No. 2003-75026
  • the double-pipe heat exchanger of the inverted U shape can be arranged compactly in the up and down direction, and both ends are arranged on the same side (lower side).
  • a task of connecting a refrigerant pipe is easily performed.
  • a gas-liquid two-phase refrigerant flowing in from one end (inlet side end) of an inner pipe flows upward and then flows downward through a U shape curved portion, and flows out from the other end (outlet side end).
  • the present invention is achieved in consideration with the situation described above, and an object thereof is to provide a double-pipe heat exchanger and an air conditioner capable of achieving a compact configuration, and suppressing a liquid refrigerant contained in a gas-liquid two-phase refrigerant from flowing out from an inner pipe so as to prevent generation of a liquid-back phenomenon.
  • the present invention is a double-pipe heat exchanger including an outer pipe through which a high pressure liquid refrigerant flows, and an inner pipe having an inlet side end into which a low pressure gas-liquid two-phase refrigerant obtained by reducing pressure of the high pressure liquid refrigerant flows, and an outlet side end connected to a suction side part of a compressor, wherein the double-pipe heat exchanger includes a plurality of vertical pipes arranged in the up and down direction, and a curve pipe connecting ends of the plurality of vertical pipes, the outlet side end of the inner pipe is provided in an upper end of one vertical pipe, and the inlet side end of the inner pipe is provided in an upper end of the other vertical pipe.
  • the gas-liquid two-phase refrigerant flowing in from the inlet side end of the inner pipe performs heat exchange with the high pressure liquid refrigerant flowing through the outer pipe, and is evaporated to become a gas refrigerant, and then flows out from the outlet side end of the inner pipe.
  • the outlet side end of the inner pipe is provided in the upper end of the one vertical pipe.
  • Both the inlet side end and the outlet side end of the inner pipe are provided in the upper ends of the vertical pipes.
  • the refrigerant pipe can be connected, so that a pipe connecting task can be easily performed.
  • the two vertical pipes are provided, and lower ends of the vertical pipes are connected by the curve pipe.
  • the double-pipe heat exchanger can achieve a simple configuration, and by reducing a curve pipe part, a pressure loss of the refrigerant can be decreased.
  • An air conditioner of the present invention includes a compressor, a condenser for condensing a high pressure gas refrigerant compressed by the compressor, a pressure reduction mechanism for reducing pressure of the condensed high pressure liquid refrigerant, an evaporator for evaporating the low pressure refrigerant after pressure reduction, and the double-pipe heat exchanger according to (1) or (2) described above, the double-pipe heat exchanger for supercooling the high pressure liquid refrigerant condensed by the condenser before reducing the pressure of the refrigerant by the pressure reduction mechanism.
  • the curve pipe connected to lower ends of the plurality of vertical pipes in the double-pipe heat exchanger is supported on a bottom frame of a casing in the air conditioner via a support member.
  • the double-pipe heat exchanger can be stably supported.
  • the double-pipe heat exchanger can achieve a compact configuration
  • the liquid refrigerant contained in the gas-liquid two-phase refrigerant can be suppressed from flowing out from the inner pipe so as to prevent generation of the liquid-back phenomenon.
  • FIG. 1 is a pattern diagram showing a refrigerant circuit of an air conditioner according to a first embodiment of the present invention.
  • FIG. 2 is a schematic view of a double-pipe heat exchanger provided in the refrigerant circuit of the air conditioner shown in FIG. 1 .
  • FIG. 3 is a schematic view showing a modified example of a double-pipe heat exchanger according to a second embodiment of the present invention.
  • FIG. 4 is a pattern diagram showing a modified example of the refrigerant circuit of the air conditioner.
  • FIG. 1 is a pattern diagram showing a refrigerant circuit of an air conditioner according to a first embodiment of the present invention.
  • An air conditioner 1 is for example a multiple type air conditioner for a building in which a refrigerant circuit 10 is formed in such a manner that a plurality of indoor units 3 is connected in parallel to one or a plurality of outdoor unit 2 so as to circulate a refrigerant.
  • compressors 11 In the outdoor unit 2 , compressors 11 , a four way valve 12 , an outdoor heat exchanger 13 , an outdoor expansion valve 14 , a supercooling heat exchanger 31 , and the like are provided. These parts are connected by a refrigerant pipe so as to form the refrigerant circuit.
  • a fan 23 is provided in the outdoor unit 2 .
  • an indoor expansion valve 15 In the indoor unit 3 , an indoor expansion valve 15 , an indoor heat exchanger 16 , and the like are provided in the indoor unit 3 .
  • the four way valve 12 and the indoor heat exchanger 16 are connected by a gas side refrigerant communication pipe 17 a, and the outdoor expansion valve 14 and the indoor expansion valve 15 are connected by a liquid side refrigerant communication pipe 17 b.
  • a gas side stop valve 18 and a liquid side stop valve 19 are provided in terminal portions of the inside refrigerant circuit of the outdoor unit 2 .
  • the gas side stop valve 18 is arranged on the side of the four way valve 12
  • the liquid side stop valve 19 is arranged on the side of the outdoor expansion valve 14 .
  • the gas side refrigerant communication pipe 17 a is connected to the gas side stop valve 18
  • the liquid side refrigerant communication pipe 17 b is connected to the liquid side stop valve 19 .
  • the four way valve 12 is retained in a state shown by solid lines in FIG. 1 .
  • a high temperature and high pressure gas refrigerant discharged from the compressors 11 flows into the outdoor heat exchanger (condenser) 13 via the four way valve 12 , and performs heat exchange with the outdoor air by actuation of the fan 23 so as to be condensed and liquefied.
  • the liquefied refrigerant passes through the outdoor expansion valve 14 in a fully open state, and flows into the indoor units 3 through the liquid side refrigerant communication pipe 17 b.
  • pressure of the refrigerant is reduced to predetermined low pressure by the indoor expansion valve (pressure reduction mechanism) 15 , and further, the refrigerant performs the heat exchange with the indoor air in the indoor heat exchanger (evaporator) 16 so as to be evaporated.
  • the indoor air cooled by evaporation of the refrigerant is blown out to an interior by an indoor fan (not shown) so as to cool the interior.
  • the refrigerant evaporated in the indoor heat exchanger 16 is returned to the outdoor unit 2 through the gas side refrigerant communication pipe 17 a, and suctioned into the compressors 11 via the four way valve 12 .
  • the four way valve 12 is retained in a state shown by broken lines in FIG. 1 .
  • a high temperature and high pressure gas refrigerant discharged from the compressors 11 flows into the indoor heat exchanger (condenser) 16 of the indoor unit 3 via the four way valve 12 , and performs the heat exchange with the indoor air so as to be condensed and liquefied.
  • the indoor air heated by condensation of the refrigerant is blown out to the interior by the indoor fan so as to heat the interior.
  • the refrigerant liquefied in the indoor heat exchanger 16 is returned to the outdoor unit 2 from the indoor expansion valve 15 in a fully open state through the liquid side refrigerant communication pipe 17 b.
  • the pressure of the refrigerant returned to the outdoor unit 2 is reduced to predetermined low pressure by the outdoor expansion valve (pressure reduction mechanism) 14 , and further, the refrigerant performs the heat exchange with the outdoor air in the outdoor heat exchanger (evaporator) 13 so as to he evaporated.
  • the refrigerant evaporated in the outdoor heat exchanger 13 is suctioned into the compressors 11 via the four way valve 12 .
  • the supercooling heat exchanger 31 of the present embodiment is used for supercooling the high pressure liquid refrigerant flowing out from the outdoor heat exchanger 13 before reducing the pressure by the indoor expansion valve 15 at the time of the cooling operation as described above.
  • the supercooling heat exchanger 31 is provided in a part of the refrigerant pipe (called as a main refrigerant pipe 25 ) between the outdoor expansion valve 14 and the liquid side stop valve 19 .
  • the refrigerant circuit has a bypass refrigerant circuit 26 in which a part of the refrigerant condensed in the outdoor heat exchanger 13 (high pressure liquid refrigerant) is diverted from the main refrigerant pipe 25 , the cooling refrigerant serving as a cooling source is supplied to the supercooling heat exchanger 31 , and then the cooling refrigerant is returned to a suction side part of the compressors 11 .
  • the bypass refrigerant circuit 26 has a diverting pipe 27 by which the refrigerant is diverted from a part of the main refrigerant pipe 25 between the outdoor expansion valve 14 and the supercooling heat exchanger 31 , the diverting pipe 27 being connected to an inlet of the cooling refrigerant in the supercooling heat exchanger 31 , and a joining pipe 28 extending from an outlet of the cooling refrigerant in the supercooling heat exchanger 31 and joining a pipe of the suction side part of the compressors 11 .
  • a bypass expansion valve 29 for reducing the pressure of the refrigerant is provided in the diverting pipe 27 .
  • the bypass expansion valve 29 is formed by an electric valve or the like for reducing the pressure of the high pressure liquid refrigerant flowing through the diverting pipe 27 so as to make the refrigerant a low pressure gas-liquid two-phase refrigerant.
  • the high pressure liquid refrigerant flowing from the outdoor heat exchanger 13 toward the indoor expansion valve 15 is supercooled by the low pressure gas-liquid two-phase refrigerant in the supercooling heat exchanger 31 .
  • a liquid component (liquid refrigerant) contained in the gas-liquid two-phase refrigerant is evaporated by the heat exchange with the high pressure liquid refrigerant to become a gas refrigerant, and suctioned by the compressors 11 .
  • FIG. 2 is a schematic view of the supercooling heat exchanger (double-pipe heat exchanger) provided in the refrigerant circuit of the air conditioner shown in FIG. 1 .
  • the supercooling heat exchanger 31 of the present embodiment is a double-pipe heat exchanger. That is, as shown in FIGS. 1 and 2 , the supercooling heat exchanger 31 is formed by double pipes including an outer pipe 32 connected to the main refrigerant pipe 25 of the refrigerant circuit, the outer pipe 32 through which the high temperature and high pressure liquid refrigerant flowing out from the outdoor heat exchanger 13 flows, and an inner pipe 33 connected to the bypass refrigerant circuit 26 , the inner pipe 33 through which the cooling refrigerant after pressure reduction by the bypass expansion valve 29 flows.
  • the inner pipe 33 has one end (inlet side end) 33 A connected to the diverting pipe 27 , and the other end (outlet side end) 33 B connected to the joining pipe 28 .
  • the high pressure liquid refrigerant flowing through the outer pipe 32 and the gas-liquid two-phase refrigerant flowing through the inner pipe 33 the high pressure liquid refrigerant is supercooled, and the gas-liquid two-phase refrigerant becomes the gas refrigerant by evaporation of the liquid component.
  • the supercooling heat exchanger 31 is formed in a U curved structure. Specifically, the supercooling heat exchanger 31 includes two vertical pipes 34 A and 34 B, and a curve pipe 35 connecting ends of the two vertical pipes 34 A and 34 B.
  • the curve pipe 35 connects lower ends of the two vertical pipes 34 A and 34 B. Therefore, inlet side ends 32 A and 33 A and outlet side ends 32 B and 33 B of the refrigerant are provided in upper ends of the two vertical pipes 34 A and 34 B.
  • the gas-liquid two-phase cooling refrigerant after the pressure reduction by the bypass expansion valve 29 flows into the inner pipe 33 of the supercooling heat exchanger 31 from the inlet side end 33 A, performs the heat exchange with the high pressure liquid refrigerant flowing through the outer pipe 32 while flowing through the inner pipe 33 to become the gas refrigerant, and flows out from the outlet side end 33 B.
  • the liquid component of the gas-liquid two-phase refrigerant is not completely evaporated by the heat exchange with the high pressure liquid refrigerant, and when the liquid component flows out from the outlet side end 33 B, the liquid component is suctioned by the compressors 11 and a liquid-back phenomenon is generated, so as to cause a decrease in a performance of the compressors 11 .
  • the outlet side end 33 B of the inner pipe 33 is provided in the upper end of the vertical pipe 34 B.
  • the liquid component of the gas-liquid two-phase refrigerant remains unevaporated, the liquid component does not easily go up toward the outlet side end 33 B of the inner pipe 33 , and does not easily flow out from the end 33 B. Therefore, the liquid-back phenomenon to the compressors 11 can be suppressed.
  • the liquid component of the gas-liquid two-phase refrigerant performs the heat exchange with the high pressure liquid refrigerant in the outer pipe 32 while remaining in the curve pipe 35 to become the gas refrigerant, and then flows out from the outlet side end 33 B.
  • Both the inlet side end 32 A and the outlet side end 32 B of the outer pipe 32 , and the inlet side end 33 A and the outlet side end 33 B of the inner pipe 33 in the supercooling heat exchanger 31 are provided on the same side (upper side) in the up and down direction.
  • the refrigerant pipe can be connected to these parts without inverting the supercooling heat exchanger 31 upside down. Therefore, a task of connecting the refrigerant pipe to the supercooling heat exchanger 31 can be performed with favorable workability.
  • the supercooling heat exchanger 31 is attached onto a bottom frame 43 in a casing of the outdoor unit 2 via a support member 40 .
  • This support member 40 is made of rubber, synthetic resin, or the like, and fixed to the bottom frame 43 by fixing tools 42 including bolts, nuts, and the like.
  • a fitting recessed portion 41 recessed in a curved shape is formed on an upper surface of the support member 40 .
  • the supercooling heat exchanger 31 is supported by the support member 40 by fitting the curve pipe 35 into the fitting recessed portion 41 and fixing the support member 40 and the curve pipe 35 by a fastening band or the like.
  • the supercooling heat exchanger 31 has relatively high strength in a part of the curve pipe 35 . Thus, the supercooling heat exchanger 31 can be stably supported by the support member 40 .
  • FIG. 3 is a schematic view showing a supercooling heat exchanger (double-pipe heat exchanger) according to a second embodiment.
  • a supercooling heat exchanger 31 shown in FIG. 3 includes four vertical pipes 34 A to 34 D, and three curve pipes 35 A to 35 C. Ends of the adjacent vertical pipes 34 A to 34 D are respectively connected by the curve pipes 35 A to 35 C, so as to be formed in a substantially W form as a whole. Inlet side ends 32 A and 33 A and outlet side ends 32 B and 33 B of an outer pipe 32 and an inner pipe 33 are provided in upper ends of the vertical pipes 34 A and 34 D.
  • the curve pipes 35 A and 35 C arranged on the lower part side of the supercooling heat exchanger 31 are supported by a bottom frame 43 of a casing via a support member 40 .
  • the supercooling heat exchanger 31 of the present embodiment exerts the same operations and effects as the supercooling heat exchanger 31 shown in FIG. 2 . Further, in comparison to the supercooling heat exchanger 31 of the first embodiment, the supercooling heat exchanger 31 of the present embodiment can be formed more compactly in the up and down direction in a case where pipe length is the same. However, since the number of the curve pipes 35 A to 35 C is higher in the present embodiment, a pressure loss of the refrigerant is more easily generated. Thus, in this point, the first embodiment is more advantageous.
  • the supercooling heat exchanger (double-pipe heat exchanger) 31 of the present invention can also be applied to a refrigerant circuit shown in FIG. 4 .
  • the supercooling heat exchanger 31 performs the heat exchange between the high pressure liquid refrigerant flowing out from the outdoor heat exchanger 13 and the gas-liquid two-phase refrigerant after the pressure reduction by the indoor expansion valve 15 , a part of the gas-liquid two-phase refrigerant being evaporated in the indoor heat exchanger 16 .
  • the high pressure liquid refrigerant can be favorably supercooled by the supercooling heat exchanger 31 even at the time of the heating operation.
  • the pluralities of vertical pipes 34 A to 34 D and curve pipes 35 A to 35 C are arranged on one straight line in a plan view.
  • the pipes may be arranged in a square form or a substantially Z form in a plan view.
  • the supercooling heat exchanger 31 may include six or more vertical pipes (and five or more curve pipes).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
US14/358,527 2011-11-30 2012-11-06 Double-pipe heat exchanger and air conditioner using same Abandoned US20140326019A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2011262525A JP5403039B2 (ja) 2011-11-30 2011-11-30 空気調和装置
JP2011-262525 2011-11-30
PCT/JP2012/078678 WO2013080754A1 (ja) 2011-11-30 2012-11-06 二重管式熱交換器及びこれを備えた空気調和装置

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US20140326019A1 true US20140326019A1 (en) 2014-11-06

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US14/358,527 Abandoned US20140326019A1 (en) 2011-11-30 2012-11-06 Double-pipe heat exchanger and air conditioner using same

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US (1) US20140326019A1 (enExample)
EP (1) EP2787314B1 (enExample)
JP (1) JP5403039B2 (enExample)
KR (1) KR20140106609A (enExample)
CN (1) CN103930744B (enExample)
AU (1) AU2012345060B2 (enExample)
BR (1) BR112014012826B8 (enExample)
IN (1) IN2014KN01172A (enExample)
WO (1) WO2013080754A1 (enExample)

Cited By (3)

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CN113184937A (zh) * 2021-04-25 2021-07-30 清华大学 一种实现两套立式多层腔体不同层间独立连接的方法及其装置
WO2021170165A1 (de) * 2020-02-29 2021-09-02 REGASCOLD GmbH Wärmeübertrager für die rückgewinnung von kälteleistung aus der regasifizierung tiefkalter verflüssigter gase
US11199342B2 (en) 2015-06-18 2021-12-14 Daikin Industries, Ltd. Air conditioner

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DE102015215253A1 (de) * 2015-08-11 2017-02-16 Bayerische Motoren Werke Aktiengesellschaft Kühlvorrichtung für Energiespeicher
KR102125025B1 (ko) * 2018-05-08 2020-06-19 김봉석 냉동장치의 액열기
GB2614358B (en) * 2022-07-20 2024-01-10 Peak Scient Instruments Limited Improvements in or relating to gas apparatus

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US3174301A (en) * 1963-10-07 1965-03-23 Gen Electric Heat exchanger structure
US5095712A (en) * 1991-05-03 1992-03-17 Carrier Corporation Economizer control with variable capacity
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Cited By (3)

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Publication number Priority date Publication date Assignee Title
US11199342B2 (en) 2015-06-18 2021-12-14 Daikin Industries, Ltd. Air conditioner
WO2021170165A1 (de) * 2020-02-29 2021-09-02 REGASCOLD GmbH Wärmeübertrager für die rückgewinnung von kälteleistung aus der regasifizierung tiefkalter verflüssigter gase
CN113184937A (zh) * 2021-04-25 2021-07-30 清华大学 一种实现两套立式多层腔体不同层间独立连接的方法及其装置

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BR112014012826B8 (pt) 2022-07-19
IN2014KN01172A (enExample) 2015-10-16
CN103930744A (zh) 2014-07-16
EP2787314B1 (en) 2018-06-13
AU2012345060B2 (en) 2015-08-06
JP2013113559A (ja) 2013-06-10
KR20140106609A (ko) 2014-09-03
AU2012345060A1 (en) 2014-06-05
WO2013080754A1 (ja) 2013-06-06
BR112014012826B1 (pt) 2020-12-15
CN103930744B (zh) 2016-01-06
EP2787314A1 (en) 2014-10-08
JP5403039B2 (ja) 2014-01-29
BR112014012826A2 (pt) 2017-06-13
EP2787314A4 (en) 2015-08-05

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