EP2787314B1 - Échangeur de chaleur à tuyau double et climatiseur l'utilisant - Google Patents

Échangeur de chaleur à tuyau double et climatiseur l'utilisant Download PDF

Info

Publication number
EP2787314B1
EP2787314B1 EP12852894.0A EP12852894A EP2787314B1 EP 2787314 B1 EP2787314 B1 EP 2787314B1 EP 12852894 A EP12852894 A EP 12852894A EP 2787314 B1 EP2787314 B1 EP 2787314B1
Authority
EP
European Patent Office
Prior art keywords
pipe
heat exchanger
refrigerant
liquid
double
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.)
Active
Application number
EP12852894.0A
Other languages
German (de)
English (en)
Other versions
EP2787314A1 (fr
EP2787314A4 (fr
Inventor
Mikio Kagawa
Tadashi Sao
Yuusuke Nakagawa
Katsutoshi Sakurai
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 EP2787314A1 publication Critical patent/EP2787314A1/fr
Publication of EP2787314A4 publication Critical patent/EP2787314A4/fr
Application granted granted Critical
Publication of EP2787314B1 publication Critical patent/EP2787314B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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.
  • EP 0 517 578 A1 discloses a heat exchanger of the type comprising a means of heating producing hot gases for the purpose of heating a fluid, such as water, intended more specifically for heating rooms and/or sanitary water, characterized in that it comprises: a tubular circuit having the general shape of a U passed through by the hot gases and positioned in an enclosure in which the fluid to be heated circulates; a bank of fins fixed on said tubular circuit in order to improve the heat exchanges between the hot gases circulating in said tubular circuit and the fluid circulating in said enclosure, and a pipe, in which the sanitary water to be heated circulates and which is coiled in a spiral inside said enclosure and kept in heat-exchange contact with said bank of fins.
  • JP 2003 075026 A discloses a refrigeration unit wherein a supercooling heat exchanger is constituted of a double-pipe heat exchanger having a vertical high-pressure side channel and a low-pressure side channel, and performs supercooling by exchanging heat between the high-pressure liquid medium X 1 at the upstream of a depressurizing mechanism and the low pressure medium X 2 obtained by depressurizing the high-pressure liquid medium X 1 .
  • the low pressure medium X 2 which makes a gas-liquid two-phase flow in the initial stage of inflow is allowed to readily turn into an annular flow, whereby performance of the supercooling heat exchanger can be improved.
  • DE 2 044 207 A discloses a heat exchanger comprising a shell having closure flange and an inner tube disposed within said shell in spaced relation thereto, means for connecting said inner tube to said shell in fluidtight relation and for longitudinal movement relative thereto; said connecting means comprising means on said inner tube providing an outer peripheral sealing surface, said shell having an internal all with a beveled sealing surface adjacent said peripheral sealing surface, an annular compression member carried by said shell flange; and a seal ring encircling said inner tube and interposed between said peripheral sealing surface, said beveled sealing surface, and said annular member, whereby an axial force exerted on said annular member compresses said seal ring into pressure sealing engagement with said peripheral sealing surface and said beveled sealing surface.
  • 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 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.
  • An air conditioner according to the present invention is defined by the combination of features of claim 1.
  • 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 double-pipe heat exchanger can be stably supported.
  • 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 may include 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 any one of the embodiments 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 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.
  • 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, 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, 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 17a, and the outdoor expansion valve 14 and the indoor expansion valve 15 are connected by a liquid side refrigerant communication pipe 17b.
  • 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, and the liquid side stop valve 19 is arranged on the side of the outdoor expansion valve 14.
  • the gas side refrigerant communication pipe 17a is connected to the gas side stop valve 18, and the liquid side refrigerant communication pipe 17b 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 17b.
  • 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 17a, 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 17b.
  • 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 be 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.
  • 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) 33A connected to the diverting pipe 27, and the other end (outlet side end) 33B connected to the joining pipe 28.
  • the supercooling heat exchanger 31 is formed in a U curved structure. Specifically, the supercooling heat exchanger 31 includes two vertical pipes 34A and 34B, and a curve pipe 35 connecting ends of the two vertical pipes 34A and 34B.
  • the curve pipe 35 connects lower ends of the two vertical pipes 34A and 34B. Therefore, inlet side ends 32A and 33A and outlet side ends 32B and 33B of the refrigerant are provided in upper ends of the two vertical pipes 34A and 34B.
  • 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 33A, 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 33B.
  • 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 33B, 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 33B of the inner pipe 33 is provided in the upper end of the vertical pipe 34B.
  • the liquid component of the gas-liquid two-phase refrigerant does not easily go up toward the outlet side end 33B of the inner pipe 33, and does not easily flow out from the end 33B. 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 33B.
  • Both the inlet side end 32A and the outlet side end 32B of the outer pipe 32, and the inlet side end 33A and the outlet side end 33B 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 34A to 34D, and three curve pipes 35A to 35C. Ends of the adjacent vertical pipes 34A to 34D are respectively connected by the curve pipes 35A to 35C, so as to be formed in a substantially W form as a whole. Inlet side ends 32A and 33A and outlet side ends 32B and 33B of an outer pipe 32 and an inner pipe 33 are provided in upper ends of the vertical pipes 34A and 34D.
  • the curve pipes 35A and 35C 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 35A to 35C 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 34A to 34D and curve pipes 35A to 35C 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).

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (3)

  1. Climatiseur comprenant:
    un boîtier ayant un cadre inférieur (43) ;
    un échangeur de chaleur à tuyau double (31) comprenant un tuyau extérieur (32) à travers lequel circule un réfrigérant liquide haute pression ; et un tuyau intérieur (33) ayant une extrémité côté entrée (33A) dans laquelle circule un réfrigérant biphasé gaz-liquide basse pression obtenu en réduisant la pression du réfrigérant liquide haute pression, et une extrémité côté sortie (33B) raccordée à une partie côté aspiration d'un compresseur; et
    un élément de support (49), dans lequel
    l'échangeur de chaleur à tuyau double comporte une pluralité de tuyaux verticaux (34A, 34B, 34C, 34D) agencés dans les directions vers le haut et le bas, et un tuyau courbe (35, 35A, 35B, 35C) raccordant les extrémités de la pluralité de tuyaux verticaux (34A, 34B, 34C, 34D),
    l'extrémité côté sortie (33B) du tuyau intérieur (33) est située à une extrémité supérieure d'un tuyau vertical (34B, 34D),
    l'extrémité côté entrée (33A) du tuyau intérieur (33) est située à une extrémité supérieure de l'autre tuyau vertical (34A), et
    le tuyau courbe (35) raccordé aux extrémités inférieures de la pluralité de tuyaux verticaux (34A, 34B, 34C, 34D) dans l'échangeur de chaleur à tuyau double (31) est supporté sur le cadre inférieur (43) du boîtier dans le climatiseur par le biais de l'élément de support (40).
  2. Climatiseur selon la revendication 1, dans lequel
    l'élément de support (40) est en caoutchouc ou résine synthétique, et
    une partie évidée de fixation (41) pour fixer le tuyau courbe (35) est formée sur une surface supérieure de l'élément de support (40).
  3. Climatiseur selon la revendication 1 ou 2, dans lequel
    l'échangeur de chaleur à tuyau double (31) comporte deux tuyaux verticaux (34A, 34B), et
    les extrémités inférieures des tuyaux verticaux (34A, 34B) sont raccordées par le tuyau courbe (35).
EP12852894.0A 2011-11-30 2012-11-06 Échangeur de chaleur à tuyau double et climatiseur l'utilisant Active EP2787314B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011262525A JP5403039B2 (ja) 2011-11-30 2011-11-30 空気調和装置
PCT/JP2012/078678 WO2013080754A1 (fr) 2011-11-30 2012-11-06 Echangeur de chaleur à tuyau double et climatiseur l'utilisant

Publications (3)

Publication Number Publication Date
EP2787314A1 EP2787314A1 (fr) 2014-10-08
EP2787314A4 EP2787314A4 (fr) 2015-08-05
EP2787314B1 true EP2787314B1 (fr) 2018-06-13

Family

ID=48535221

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12852894.0A Active EP2787314B1 (fr) 2011-11-30 2012-11-06 Échangeur de chaleur à tuyau double et climatiseur l'utilisant

Country Status (9)

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6657613B2 (ja) * 2015-06-18 2020-03-04 ダイキン工業株式会社 空気調和装置
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
DE102020001338A1 (de) * 2020-02-29 2021-09-02 REGASCOLD GmbH Wärmeübertrager für die Rückgewinnung von Kälteleistung aus der Regasifizierung tiefkalter verflüssigter Gase
CN113184937B (zh) * 2021-04-25 2023-09-26 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
GB2614358B (en) * 2022-07-20 2024-01-10 Peak Scient Instruments Limited Improvements in or relating to gas apparatus

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3174301A (en) * 1963-10-07 1965-03-23 Gen Electric Heat exchanger structure
US3593782A (en) * 1969-09-08 1971-07-20 American Precision Ind Heat exchanger
US5095712A (en) * 1991-05-03 1992-03-17 Carrier Corporation Economizer control with variable capacity
FR2677113B1 (fr) * 1991-06-03 1993-11-26 Puzio Jean Claude Echangeur de chaleur tubulaire a ailettes pour rechauffer un fluide liquide par des gaz chauds.
US5839295A (en) * 1997-02-13 1998-11-24 Frontier Refrigeration And Air Conditioning Ltd. Refrigeration/heat pump module
JP2003075026A (ja) * 2001-08-31 2003-03-12 Daikin Ind Ltd 冷凍装置
US6681597B1 (en) * 2002-11-04 2004-01-27 Modine Manufacturing Company Integrated suction line heat exchanger and accumulator
US6698221B1 (en) * 2003-01-03 2004-03-02 Kyung Kon You Refrigerating system
JP2005098581A (ja) * 2003-09-24 2005-04-14 Hoshizaki Electric Co Ltd 冷凍回路及び冷凍回路を用いた冷却装置
JP4897298B2 (ja) * 2006-01-17 2012-03-14 サンデン株式会社 気液分離器モジュール
JP2008002771A (ja) * 2006-06-23 2008-01-10 Denso Corp 冷凍サイクル用部品
CN201003917Y (zh) * 2006-06-30 2008-01-09 舒增鳌 管排式套管换热器
CN200941019Y (zh) * 2006-07-20 2007-08-29 苏宇贵 空调用换热器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
KR20140106609A (ko) 2014-09-03
AU2012345060B2 (en) 2015-08-06
CN103930744A (zh) 2014-07-16
CN103930744B (zh) 2016-01-06
JP5403039B2 (ja) 2014-01-29
AU2012345060A1 (en) 2014-06-05
JP2013113559A (ja) 2013-06-10
US20140326019A1 (en) 2014-11-06
EP2787314A1 (fr) 2014-10-08
BR112014012826B8 (pt) 2022-07-19
BR112014012826B1 (pt) 2020-12-15
IN2014KN01172A (fr) 2015-10-16
EP2787314A4 (fr) 2015-08-05
WO2013080754A1 (fr) 2013-06-06
BR112014012826A2 (pt) 2017-06-13

Similar Documents

Publication Publication Date Title
EP2787314B1 (fr) Échangeur de chaleur à tuyau double et climatiseur l'utilisant
EP3098540B1 (fr) Appareil de pompe à chaleur
US10113776B2 (en) Packaged terminal air conditioner unit
JP5452367B2 (ja) 気液分離器および冷凍サイクル装置
WO2007034744A1 (fr) Conditionneur d'air
KR20180104416A (ko) 공기조화시스템
JP2006003022A (ja) 冷凍装置及び中間圧レシーバ
WO2013146415A1 (fr) Dispositif de chauffage du type pompe à chaleur
EP2771627B1 (fr) Appareil de climatisation à régénération
US11519645B2 (en) Air conditioning apparatus
KR102136883B1 (ko) 히트펌프 시스템
JP2012002418A (ja) 空気調和機および気液分離装置
JP2010139196A (ja) 熱交換器
JP2012107775A (ja) 熱交換器及びこの熱交換器を備えた空気調和装置
JP2010236707A (ja) 熱交換器
JP2007093167A (ja) 空気調和機用液ガス熱交換器
KR102226277B1 (ko) 다중관 형태를 갖는 다목적 열교환기 및 이를 갖는 정수 장치
JP2006029714A (ja) エジェクタサイクル
JP2008267731A (ja) 空気調和装置
KR102342956B1 (ko) 고효율 증발식 응축기
KR102136749B1 (ko) 공기 조화기
KR101489515B1 (ko) 차량용 듀얼 에어컨 시스템
CN109990515B (zh) 一种带经济器功能的热交换气液分离器
JP5686753B2 (ja) 空気調和装置
KR101323527B1 (ko) 공기 조화기

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20140522

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
RA4 Supplementary search report drawn up and despatched (corrected)

Effective date: 20150706

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 40/00 20060101ALI20150630BHEP

Ipc: F28D 7/06 20060101AFI20150630BHEP

Ipc: F28D 7/14 20060101ALI20150630BHEP

Ipc: F25B 13/00 20060101ALI20150630BHEP

Ipc: F25B 1/00 20060101ALI20150630BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20180130

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1008930

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180615

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602012047536

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180613

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180913

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180913

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180914

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1008930

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181013

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602012047536

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20190314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181106

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20181130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20121106

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180613

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230525

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20230928

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20230929

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230929

Year of fee payment: 12