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WO2017221401A1 - Distributeur de dérivation de réfrigérant, échangeur de chaleur le comprenant et dispositif à cycle de réfrigération - Google Patents

Distributeur de dérivation de réfrigérant, échangeur de chaleur le comprenant et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2017221401A1
WO2017221401A1 PCT/JP2016/068811 JP2016068811W WO2017221401A1 WO 2017221401 A1 WO2017221401 A1 WO 2017221401A1 JP 2016068811 W JP2016068811 W JP 2016068811W WO 2017221401 A1 WO2017221401 A1 WO 2017221401A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
flow path
pipe
heat exchanger
branch
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.)
Ceased
Application number
PCT/JP2016/068811
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English (en)
Japanese (ja)
Inventor
良太 赤岩
真哉 東井上
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2018523251A priority Critical patent/JP6668469B2/ja
Priority to GB1816567.0A priority patent/GB2566165B/en
Priority to PCT/JP2016/068811 priority patent/WO2017221401A1/fr
Priority to US16/089,651 priority patent/US20190113244A1/en
Publication of WO2017221401A1 publication Critical patent/WO2017221401A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • 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
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • 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
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to a refrigerant branching distributor, a heat exchanger including the refrigerant, and a refrigeration cycle apparatus, and more particularly, a refrigerant branching distributor capable of branching a two-phase refrigerant of a liquid refrigerant and a gas refrigerant into refrigerants having different liquid ratios. And a heat exchanger including the refrigerant branching distributor and a refrigeration cycle apparatus including the heat exchanger.
  • the heat exchanger when a heat exchanger is used to lower the temperature of the air, the heat exchanger functions as an evaporator (evaporator).
  • the refrigerant flows into the heat exchanger as the evaporator in a gas-liquid two-phase flow state in which a gas refrigerant and a liquid refrigerant are mixed.
  • the density of the gas refrigerant and the liquid refrigerant differ by several tens of times.
  • the liquid refrigerant mainly absorbs the heat of the air and evaporates to become a gas refrigerant.
  • a gas refrigerant single phase
  • the air passing through the heat exchanger becomes cold due to the loss of latent heat (heat of evaporation) when the liquid refrigerant undergoes a phase change.
  • heat exchangers there are parts where the air volume flowing through the heat exchanger is large and small. Corresponding heat exchange is performed between the portion of the heat exchanger with a large air volume and the portion of the heat exchanger with a small air volume, and the heat exchanger portion with a larger air volume performs heat exchange more efficiently.
  • the present invention has been made as part of such development, and one object is to provide a refrigerant branch distributor that efficiently exchanges heat between two-phase refrigerants, and another object is to It is providing the heat exchanger provided with such a refrigerant
  • the refrigerant distributor according to the present invention includes a first flow path, a second flow path, a third flow path, and a branch portion.
  • the branch portion is connected to the first flow path, is connected to the second flow path and the third flow path, and the refrigerant including the liquid refrigerant and the gas refrigerant flowing in from the first flow path is supplied to the second flow path.
  • the third flow path is defined as the liquid ratio.
  • the first liquid ratio of the first refrigerant branched into the second flow path is higher than the second liquid ratio of the second refrigerant branched into the third flow path.
  • a heat exchanger is a heat exchanger provided with the refrigerant branching distributor, and includes a first heat exchanger and a second heat exchanger.
  • first heat exchanger heat is exchanged between the refrigerant and the first fluid.
  • second heat exchanger heat exchange is performed between the refrigerant and the second fluid.
  • the amount of the first fluid is greater than the amount of the second fluid.
  • the second flow path is connected to the first heat exchanger.
  • the third flow path is connected to the second heat exchanger.
  • the refrigeration cycle apparatus is a refrigeration cycle apparatus provided with the heat exchanger.
  • the first refrigerant having a high liquid ratio is positively sent to the second flow path, and the second refrigerant third flow path having a low liquid ratio is positively sent to efficiently. Heat exchange can be performed.
  • the second flow path of the refrigerant branching distributor is connected to the first heat exchanger, and the third flow path is connected to the second heat exchanger.
  • heat exchange is performed between the 2nd refrigerant
  • heat exchange is performed between the first refrigerant having a high liquid ratio and the first fluid larger than the amount of the second fluid.
  • the second refrigerant having a high liquid ratio can be efficiently heat-exchanged.
  • the heat exchange of the refrigerant can be efficiently performed by including the heat exchanger.
  • FIG. 1 it is a perspective view which shows an outdoor unit.
  • FIG. 1 it is a perspective view which shows an outdoor unit.
  • FIG. 1 it is a perspective view which shows an example of the relationship between the air volume sent into an outdoor heat exchanger, and a heat exchanger.
  • FIG. 7 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line VII-VII shown in FIG. 6 in the same embodiment.
  • FIG. 10 is a partial view showing a refrigerant distributor including a branch distribution unit arranged in an outdoor unit according to the second embodiment.
  • FIG. 9 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line IX-IX shown in FIG. 8 in the same embodiment.
  • FIG. 9 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XX shown in FIG. 8 in the embodiment.
  • FIG. 9 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XI-XI shown in FIG. 8 in the embodiment.
  • FIG. 9 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XII-XII shown in FIG. 8 in the same embodiment.
  • it is a fragmentary figure which shows the branch distribution part arrange
  • FIG. 14 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe taken along a cross-sectional line XIV-XIV shown in FIG. 13 in the embodiment.
  • FIG. 14 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XV-XV shown in FIG. 13 in the embodiment.
  • FIG. 14 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XVI-XVI shown in FIG. 13 in the embodiment.
  • FIG. 14 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XVII-XVII shown in FIG.
  • FIG. 19 is a cross-sectional view taken along a cross-sectional line XIX-XIX shown in FIG. 18 of the orifice according to the first example used for the branch distribution unit in the same embodiment.
  • FIG. 19 is a cross-sectional view taken along a cross-sectional line XIX-XIX shown in FIG. 18 of an orifice according to a second example used for the branch distribution unit in the same embodiment.
  • FIG. 19 is a cross-sectional view taken along a cross-sectional line XIX-XIX shown in FIG.
  • FIG. 19 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXII-XXII shown in FIG. 18 in the same embodiment.
  • FIG. 19 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXIII-XXIII shown in FIG. 18 in the same embodiment.
  • FIG. 19 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe, taken along a cross-sectional line XXIV-XXIV shown in FIG. 18 in the embodiment.
  • FIG. 19 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe, taken along a cross-sectional line XXIV-XXIV shown in FIG. 18 in the embodiment.
  • FIG. 10 is a partial view showing a refrigerant distributor including a branch distribution unit arranged in an outdoor unit according to a fourth embodiment.
  • FIG. 26 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXVI-XXVI shown in FIG. 25 in the embodiment.
  • FIG. 26 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXVII-XXVII shown in FIG. 25 in the embodiment.
  • FIG. 26 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXVIII-XXVIII shown in FIG. 25 in the embodiment.
  • FIG. 26 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXIX-XXIX shown in FIG. 25 in the embodiment.
  • FIG. 26 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XXX-XXX shown in FIG. 25 in the same embodiment.
  • FIG. 26 is a cross-sectional view showing an example of a distribution of refrigerant in a pipe taken along a cross-sectional line XXXI-XXXI shown in FIG. 25 in the embodiment.
  • FIG. 26 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXII-XXXII shown in FIG. 25 in the same embodiment.
  • FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXIV-XXXIV shown in FIG. 33 in the embodiment.
  • FIG. 34 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XXXV-XXXV shown in FIG. 33 in the embodiment.
  • FIG. 34 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XXXVI-XXXVI shown in FIG. 33 in the embodiment.
  • FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXVII-XXXVII shown in FIG. 33 in the embodiment.
  • FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXVIII-XXXVIII shown in FIG. 33 in the embodiment.
  • FIG. 34 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XXXIX-XXXIX shown in FIG. 33 in the embodiment.
  • FIG. 34 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XL-XL shown in FIG. 33 in the embodiment. It is a fragmentary figure which shows the branch distribution part arrange
  • FIG. FIG. 42 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe, taken along a cross-sectional line XLII-XLII shown in FIG. 41 in the embodiment.
  • FIG. 42 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XLIII-XLIII shown in FIG. 41 in the embodiment.
  • FIG. 42 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe taken along a cross-sectional line XLIV-XLIV shown in FIG. 41 in the embodiment.
  • FIG. 42 is a cross-sectional view showing an example of a distribution of refrigerant in the pipe taken along a cross-sectional line XLV-XLV shown in FIG. 41 in the embodiment.
  • FIG. 42 is a cross-sectional view showing an example of the distribution of refrigerant in the pipe taken along a cross-sectional line XLVI-XLVI shown in FIG. 41 in the embodiment.
  • FIG. 42 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe along the cross-sectional line XLVII-XLVII shown in FIG. 41 in the embodiment.
  • FIG. 42 is a cross-sectional view showing an example of the distribution of the refrigerant in the pipe taken along a cross-sectional line XLVIII-XLVIII shown in FIG. 41 in the embodiment.
  • Embodiment 1 FIG. A refrigeration cycle apparatus including the refrigerant distributor according to Embodiment 1 will be described. First, the configuration of the refrigeration cycle apparatus will be described. Here, a building multi-air conditioner is taken as an example of the refrigeration cycle apparatus.
  • the refrigeration cycle apparatus 1 includes a compressor 3, four-way valves 5a and 5b, indoor fans 19a, 19b, 19c and 19d, expansion valves 13a, 13b and 13c, 13d, expansion valves 9a and 9b, refrigerant distributors 21a and 21b, an outdoor fan 17 and an accumulator 23.
  • a branch distribution unit 11 is provided between the refrigerant distributors 21 a and 21 b and the expansion valve 13.
  • the branch distribution unit 11 will be described later.
  • the expansion valves 9a and 9b provided between the branch distribution unit 11 and the refrigerant distributors 21a and 21b are not essential, and are provided as necessary.
  • the heating operation will be described as the operation of the building multi air conditioner.
  • high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 3.
  • the discharged high-temperature and high-pressure gas refrigerant passes through the four-way valves 5a and 5b and flows into each of the plurality of indoor heat exchangers 15a, 15b, 15c and 15d.
  • Air is sent into each of the indoor heat exchangers 15a to 15d by indoor fans 19a, 19b, 19c, and 19d.
  • each of the indoor heat exchangers 15a to 15d heat exchange is performed between the fed air and the flowing gas refrigerant, and the high-temperature and high-pressure gas refrigerant is condensed and converted into a high-pressure liquid refrigerant (single phase). Become.
  • each of the rooms where the indoor heat exchangers 15a to 15d are arranged is heated.
  • the high-pressure liquid refrigerant sent out from the indoor heat exchangers 15a to 15d passes through the expansion valves 13a, 13b, 13c, and 13d, thereby becoming a two-phase refrigerant consisting of a low-pressure gas refrigerant and a liquid refrigerant. Become.
  • the refrigerant in the two-phase state flows into the outdoor unit 25.
  • the refrigerant in the two-phase state that has flowed into the outdoor unit 25 is branched into two in the branch distribution unit 11.
  • one refrigerant (refrigerant A) flows through the piping 47 through the expansion valve 9a and the refrigerant distributor 21a and into the outdoor heat exchanger 7a.
  • the other refrigerant (refrigerant B) flows through the expansion valve 9b and the refrigerant distributor 21b through the pipe 48 and into the outdoor heat exchanger 7b.
  • the outdoor heat exchangers 7a and 7b heat exchange is performed between the air sent by the outdoor fan 17 and the flowing refrigerant (refrigerant A and refrigerant B), and the liquid refrigerant of the two-phase refrigerant is Evaporates into a low-pressure gas refrigerant (single phase).
  • the low-pressure gas refrigerant sent out from the outdoor unit 25 flows into the compressor 3 through the four-way valves 5a and 5b and the accumulator 23.
  • the low-pressure gas refrigerant that has flowed into the compressor 3 is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 3 again. Thereafter, this cycle is repeated.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor 3 passes through the four-way valves 5a and 5b and flows into the outdoor heat exchangers 7a and 7b.
  • the outdoor heat exchangers 7a and 7b heat exchange is performed between the air sent by the outdoor fan 17 and the gas refrigerant flowing in, and the high-temperature and high-pressure gas refrigerant is condensed to a low-temperature and high-pressure liquid refrigerant (simple Phase).
  • the low-temperature and high-pressure liquid refrigerant becomes a low-temperature and low-pressure liquid refrigerant by passing through the expansion valves 13a to 13d.
  • the low-temperature and low-pressure liquid refrigerant flows into each of the plurality of indoor heat exchangers 15a to 15d.
  • the indoor heat exchangers 15a to 15d heat exchange is performed between the air sent by the indoor fans 19a to 19d and the flowing liquid refrigerant, and the low-temperature and low-pressure liquid refrigerant is evaporated to a low-pressure gas refrigerant ( Single phase).
  • a low-pressure gas refrigerant Single phase
  • the low-pressure gas refrigerant sent out from the indoor heat exchangers 15a to 15d flows into the compressor 3 through the four-way valves 5a and 5b and the accumulator 23.
  • the low-pressure gas refrigerant flowing into the compressor is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor again. Thereafter, this cycle is repeated.
  • the outdoor heat exchanger 7 of the outdoor unit 25 functions as an evaporator in the heating operation and functions as a condenser in the cooling operation.
  • an outdoor unit of a building multi air conditioner there is an outdoor unit having a top flow type fan. As shown in FIG. 2, in the top-flow type outdoor unit 25, the outdoor fan 17 is attached to the upper surface portion of the housing 26.
  • the outdoor heat exchanger 7 is disposed in the casing 26.
  • the outdoor heat exchanger 7 is disposed so as to face three air intake ports (side surfaces of the housing).
  • a branching / distributing unit 11, a compressor (not shown), and the like are arranged in the casing 26 in the casing 26 in the casing 26 in the casing 26, a branching / distributing unit 11, a compressor (not shown), and the like.
  • the outdoor fan 17 is attached to the upper surface portion of the casing 26. Therefore, in the outdoor heat exchanger 7, the air pressure loss decreases as the distance from the outdoor fan 17 decreases, and the air pressure loss increases as the distance from the outdoor fan 17 increases. That is, the pressure loss gradually increases from the upper part to the lower part of the outdoor heat exchanger 7, the air volume passing through the outdoor heat exchanger 7a is relatively large, and the air volume passing through the outdoor heat exchanger 7b. Is relatively small (see arrows in FIG. 3).
  • FIG. 4 An example of the connection relationship between the outdoor heat exchanger 7a and the piping is shown in FIG.
  • the outdoor heat exchanger 7a is composed of, for example, three rows of outdoor heat exchangers 7aa, 7ab, and 7ac.
  • a heat transfer tube (not shown) is attached to each of the three rows of outdoor heat exchangers 7aa, 7ab, 7ac.
  • the plurality of pipes 47 branched from the refrigerant distributor 21a are connected to the corresponding heat transfer tubes of the outdoor heat exchanger 7a in the first row.
  • One refrigerant path passes from the heat transfer tube of the outdoor heat exchanger 7aa in the first row to the heat transfer tube of the outdoor heat exchanger 7ab in the second row and the heat transfer tube of the outdoor heat exchanger 7ac in the third row. It is connected to. As shown in FIGS. 1 and 3, a plurality of pipes 48 branched from the refrigerant distributor 21b are also connected to the outdoor heat exchanger 7b disposed below the outdoor heat exchanger 7a (see FIG. 5). ).
  • the outdoor heat exchanger 7 When the outdoor heat exchanger 7 is caused to function as an evaporator, in order to efficiently evaporate the liquid refrigerant out of the two-phase refrigerant into a gas refrigerant, the outdoor heat exchanger 7a having a larger air volume is sent to the outdoor heat exchanger 7a. It is required to flow. Therefore, as shown in FIG. 5, the branch distribution unit 11 is provided in the outdoor unit 25.
  • the two-phase refrigerant flowing from the indoor heat exchanger 15 is branched into two refrigerants (refrigerant A and refrigerant B) during the heating operation.
  • the ratio of the liquid refrigerant is the liquid ratio.
  • the refrigerant A is a refrigerant with a high liquid ratio.
  • the refrigerant B is a refrigerant with a low liquid ratio.
  • the refrigerant is distributed macroscopically into the refrigerant A having a high liquid ratio and the refrigerant B having a low liquid ratio.
  • the refrigerant A is further microscopically distributed by the refrigerant distributor 21a and sent to the outdoor heat exchanger 7a having a large air volume.
  • the refrigerant B is further microscopically distributed by the refrigerant distributor 21b and sent to the outdoor heat exchanger 7b having a small air volume.
  • the branch distributor 11 includes a pipe 41 (first flow path) including a bent pipe 33, a branch pipe 31 (branch section), a pipe 43 (second flow path), and a pipe 44 (third flow). Road).
  • the refrigerant in the two-phase state that has flowed through the pipe 41 flows through the bent pipe 33, thereby causing an uneven distribution of the liquid refrigerant. That is, the amount of liquid refrigerant flowing along the inner wall surface on the outer peripheral side of the bent pipe 33 is larger than the amount of liquid refrigerant flowing along the inner wall surface on the inner peripheral side due to the centrifugal force.
  • the refrigerant (refrigerant A) having a high liquid ratio flows in a region corresponding to the outer peripheral side of the bent pipe 33, and corresponds to the inner peripheral side of the bent pipe 33.
  • a refrigerant having a low liquid ratio (refrigerant B) flows in the region.
  • the refrigerant that has flowed through the pipe 41 in this state is distributed to the refrigerant A and the refrigerant B by the branch pipe 31.
  • the distributed refrigerant A flows through the pipe 43, the refrigerant distributor 21a and the pipe 47 and is sent to the outdoor heat exchanger 7a.
  • the refrigerant B flows through the pipe 45, the refrigerant distributor 21b, and the pipe 48 and is sent to the outdoor heat exchanger 7b.
  • the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume.
  • pressure loss is adjusted by changing the length of piping connected to the outdoor heat exchangers 7a and 7b, the inner diameter of the piping, or the like as a method of flowing a refrigerant having a high liquid ratio to the outdoor heat exchanger 7a having a larger air volume.
  • this method as the number of pipes increases, it becomes difficult to adjust the length of the pipes. Moreover, the area
  • a refrigerant having a high liquid ratio to the outdoor heat exchanger 7a having a simple structure and a larger air volume is formed by only the bent pipe 33 and the branch pipe 31. Can be sent in.
  • the length L of the straight portion from the bent pipe 33 to the branch pipe 31 is a length that flows into the branch pipe 31 with an uneven distribution (see FIG. 7) in which the liquid refrigerant in the pipe 41 is biased. It is necessary to set it.
  • the length L of the straight portion needs to satisfy the relationship L ⁇ 10 ⁇ D.
  • the liquid refrigerant returns to a state in which the liquid refrigerant is distributed almost uniformly and annularly on the inner wall of the pipe 41 from the uneven distribution of the liquid refrigerant. . For this reason, it becomes impossible to send more liquid refrigerant into the outdoor heat exchanger 7a.
  • expansion valves 9a and 9b may be provided between the refrigerant distributors 21a and 21b and the branch distributor 11 as shown in FIG. In particular, it is possible to prevent excessive liquid refrigerant from flowing into the pipe 43 by adjusting the opening degree of the expansion valve 9a.
  • the branch distribution unit 11 includes a T-shaped branch pipe 35 a (35) (branch portion) similar to the shape of the alphabet “T”.
  • the T-shaped branch pipe 35a is provided with a part extending in one direction (pipe part A) and a part (pipe part B) branching from the pipe part A in a direction substantially perpendicular to the one direction. Yes.
  • the pipe 43 (second flow path) including the bent pipe 33 is connected to the pipe portion A.
  • the refrigerant distributor 21a is connected to the pipe 43, and a plurality of pipes 47 are connected to the refrigerant distributor 21a.
  • a pipe 44 (third flow path) is connected to the pipe part B.
  • the refrigerant distributor 21b is connected to the pipe 44, and a plurality of pipes 48 are connected to the refrigerant distributor 21b.
  • the plurality of pipes 47 are connected to the outdoor heat exchanger 7a, and the plurality of pipes 48 are connected to the outdoor heat exchanger 7b (see FIG. 3).
  • the refrigerant (refrigerant AA) having a high liquid ratio flows in the area corresponding to the outer peripheral side, and the area corresponding to the inner peripheral side.
  • a refrigerant having a low liquid ratio flows.
  • the refrigerant that has flowed is distributed to the plurality of pipes 47.
  • the refrigerant AA having a high liquid ratio flows into the pipes 47 arranged at positions corresponding to the outer peripheral side of the bent pipes.
  • the refrigerant AB having a low liquid ratio flows into the pipe 47 arranged at a position corresponding to the inner peripheral side of the bent pipe.
  • the distributed refrigerant AA and refrigerant AB flow through the pipe 47 and are sent to the outdoor heat exchanger 7a.
  • the refrigerant B flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.
  • the refrigerant AA having a high liquid ratio is caused to flow through an upper path having a relatively large air volume in the outdoor heat exchanger 7a, and the refrigerant AB having a low liquid ratio is supplied to the outdoor heat exchanger 7a.
  • the lower path having a relatively small air volume see FIG. 5.
  • T-shaped branch pipe 35b (branch part) according to the modification, two parts (pipe part B, pipe part C) are divided from a part extending in one direction (pipe part A). ) Is provided.
  • a pipe 45 (fourth flow path) is connected to the pipe portion C.
  • the refrigerant distributor 21c is connected to the pipe 45, and a plurality of pipes 49 are connected to the refrigerant distributor 21c.
  • a plurality of piping 49 is connected to outdoor heat exchanger 7b with piping 48, for example.
  • T-shaped branch piping 35b etc. it is the same as that of the structure shown in FIG. 8, and about the structure of an outdoor unit and the structure of a refrigeration cycle apparatus, the structure shown in FIG. 1 and FIG. It is the same. For this reason, the same code
  • the liquid refrigerant hardly flows through the pipe part B and the pipe part C branched from the pipe part A, and the refrigerant (refrigerant B) having a low liquid ratio flows.
  • the gas refrigerant easily flows into the pipe part C located on the upstream side of the refrigerant flow, and the refrigerant having a low liquid ratio flows into the pipe part C, and downstream of the refrigerant flow.
  • a refrigerant with a high liquid ratio flows into the piping part B located.
  • the refrigerant (refrigerant BB) having a low liquid ratio flows into the pipe 45 connected to the pipe part C.
  • the refrigerant (refrigerant BA) having a high liquid ratio flows into the pipe 44 (third flow path) connected to the pipe part B.
  • the refrigerant A flowing through the pipe 43 is distributed to the plurality of pipes 47 by the refrigerant distributor 21a.
  • the refrigerant (refrigerant AA) having a high liquid ratio flows in the area corresponding to the outer peripheral side, and the liquid corresponding to the area corresponding to the inner peripheral side.
  • a refrigerant with a low ratio flows.
  • the refrigerant AA having a high liquid ratio flows into the pipes 47 arranged at positions corresponding to the outer peripheral side of the bent pipes.
  • the refrigerant AB having a low liquid ratio flows into the pipe 47 arranged at a position corresponding to the inner peripheral side of the bent pipe.
  • the refrigerant AA and the refrigerant AB flow through the pipe 47 and are sent to the outdoor heat exchanger 7a.
  • the distributed refrigerant B (refrigerant BB, refrigerant BA) flows through the pipes 48 and 49 and is sent to the outdoor heat exchanger 7b.
  • the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio (refrigerant BB, refrigerant BA) is supplied to the outdoor heat exchanger 7b having a smaller air volume. ) Will flow.
  • the refrigerant BA having a high liquid ratio is caused to flow through the upper path having a relatively large air volume in the outdoor heat exchanger 7b, and the refrigerant BB having a low liquid ratio is supplied to the outdoor heat exchanger 7b.
  • the lower path having a relatively small air volume see FIG. 5.
  • Embodiment 3 the 3rd example of the branch distribution part which comprises a refrigerant
  • the branch distribution unit 11 includes an orifice 39 in the pipe 41 (first flow path) before (upstream side) the T-shaped branch pipe 35 a (35) (branch part).
  • an opening through which the refrigerant flows is provided in a shielding part that blocks the flow of the refrigerant.
  • the area of the opening of the orifice 39 (channel cross-sectional area) is narrower than the channel cross-sectional area of the pipe 41.
  • FIG. 39 A first example of the orifice 39 is shown in FIG. In the orifice 39, a substantially circular opening 39b is concentrically formed in a shielding part 39a that blocks the flow of the refrigerant.
  • FIG. 39 A second example of the orifice 39 is shown in FIG. In the orifice 39, a substantially semicircular opening 39b is formed in a shielding part 39a that blocks the flow of the refrigerant.
  • the shielding part 39a is disposed at a circumferential position where the pipe 44 (third flow path) is connected to the T-shaped branch pipe 35a.
  • FIG. 39 A third example of the orifice 39 is shown in FIG.
  • a substantially circular opening 39b is formed in a shielding part 39a that blocks the flow of the refrigerant.
  • the substantially circular opening 39b is formed in the shielding part 39a so that the center of the opening 39b deviates from the center of the orifice 39.
  • the shielding part 39a is disposed at a circumferential position where the pipe 44 is connected to the T-shaped branch pipe 35a.
  • T-shaped branch pipe 35a and the like are the same as those shown in FIG. 8, and the configurations of the outdoor unit and the refrigeration cycle apparatus are the configurations shown in FIGS. It is the same. For this reason, the same code
  • the refrigerant in the two-phase state flowing through the pipe 41 is peeled off from the inner wall of the pipe 41 by the shielding part 39a of the orifice 39 before flowing into the T-shaped branch pipe 35a.
  • the flow rate of the refrigerant increases as the refrigerant passes through the opening 39b having a narrow channel cross-sectional area. This makes it easier for more liquid refrigerant to flow through the pipe portion A extending in one direction of the T-shaped branch pipe 35a.
  • the flow rate of the refrigerant in the two-phase state is small, the amount of liquid refrigerant flowing into the pipe portion A can be increased.
  • the liquid refrigerant is peeled off from the inner wall of the pipe 41 in front of the pipe part B branching from the pipe part A, so that the liquid refrigerant is less likely to flow as compared with the case where there is no orifice. Gas refrigerant can easily flow.
  • the refrigerant (refrigerant B) having a low liquid ratio flows into the pipe 44 connected to the pipe part B.
  • the shielding portion 39a of the orifice 39 shown in FIG. 20 or FIG. 21 at the circumferential position where the pipe 44 is connected to the T-shaped branch pipe 35a, the amount of liquid refrigerant flowing into the pipe 44 can be reduced.
  • the amount of liquid refrigerant flowing into the pipe 43 (second flow path) can be increased accordingly.
  • the refrigerant having a high liquid ratio that has flowed into the pipe 43 flows through the bent pipe 33, so that a refrigerant having a high liquid ratio (refrigerant AA) and a refrigerant having a low liquid ratio (refrigerant) as shown in FIG. AB).
  • the distributed refrigerant AA and refrigerant AB are further distributed by the refrigerant distributor 21a.
  • the distributed refrigerant AA and refrigerant AB flow through the pipe 47 and are sent to the outdoor heat exchanger 7a.
  • the refrigerant B flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.
  • the branch distribution unit 11 includes a Y-shaped branch pipe 37a (37) (branch unit) similar to the shape of the alphabet “Y”.
  • the Y-shaped branch pipe 37a one pipe is bifurcated.
  • a pipe 43 is connected to one branch pipe portion branched into two branches, and a pipe 44 is connected to the other branch pipe portion.
  • the Y-shaped branch pipe 37a is arranged so that the pipe 43 is located below and the pipe 44 is located above.
  • the pipes 43 and 44 include a bent pipe 33.
  • the two-phase refrigerant (see FIG. 26) that has flowed through the pipe 41 (first flow path) flows into the Y-shaped branch pipe 37a.
  • the refrigerant flowing into the Y-shaped branch pipe 37a is distributed to the pipe 43 (second flow path) and the pipe 44 (third flow path).
  • the liquid refrigerant easily flows into the pipe 43 disposed below due to gravity, and the refrigerant (refrigerant A) having a high liquid ratio flows.
  • the liquid refrigerant is difficult to flow into the pipe 44 disposed above, and the refrigerant (refrigerant B) having a low liquid ratio flows.
  • the refrigerant flowing through the pipe 43 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21a.
  • the distributed refrigerant flows through the pipe 47 and is sent to the outdoor heat exchanger 7a.
  • the refrigerant flowing through the pipe 44 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21b.
  • the distributed refrigerant flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.
  • the distribution of the refrigerant in the pipe 43 immediately after flowing through the bent pipe 33 of the pipe 43 is shown in FIG. 29, and the distribution of the refrigerant in the pipe 44 immediately after flowing through the bent pipe 33 of the pipe 44 is shown in FIG.
  • the distribution of the refrigerant in the pipe 47 is shown in FIG. 31, and the distribution of the refrigerant in the pipe 48 is shown in FIG.
  • the refrigerant flowing into the Y-shaped branch pipe 37a is distributed by the branch distributor 11 into a refrigerant with a high liquid ratio and a refrigerant with a low liquid ratio.
  • a refrigerant with a high liquid ratio flows into the outdoor heat exchanger 7a, and a refrigerant with a low liquid ratio flows into the outdoor heat exchanger 7b.
  • the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume.
  • heat exchange between the refrigerant and the air can be performed more efficiently.
  • the Y-shaped branch pipe 37b (37) (branch part) according to the modification has an aspect component (X direction component) with respect to the direction of refrigerant flow (for example, the X direction). And a portion (piping portion B) for branching the refrigerant in a mode having a direction component (-X direction component) opposite to the direction component (the piping portion A). (See vector shown in FIG. 33).
  • the Y-shaped branch pipe 37b has a part extending in one direction (pipe part A) into which the refrigerant flows and a part extending in another direction (pipe part B) intersecting with the one direction. ) And a portion (pipe portion C) extending in a direction opposite to the other direction.
  • the two-phase refrigerant (see FIG. 34) that has flowed through the pipe 41 (first flow path) flows into the Y-shaped branch pipe 37b.
  • the refrigerant flowing into the Y-shaped branch pipe 37b is distributed to the pipe 43 (second flow path) and the pipe 44 (third flow path).
  • the liquid refrigerant easily flows into the pipe 43 due to the inertial force, and the refrigerant (refrigerant A) having a high liquid ratio flows into the pipe 43.
  • the liquid refrigerant hardly flows and the refrigerant (refrigerant B) having a low liquid ratio flows into the pipe 44.
  • the refrigerant flowing through the pipe 43 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21a.
  • the distributed refrigerant flows through the pipe 47 and is sent to the outdoor heat exchanger 7a.
  • the refrigerant flowing through the pipe 44 flows through the bent pipe 33 and is further distributed by the refrigerant distributor 21b.
  • the distributed refrigerant flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.
  • the distribution of the refrigerant in the pipe 43 immediately after flowing through the bent pipe 33 of the pipe 43 is shown in FIG. 37, and the distribution of the refrigerant in the pipe 44 immediately after flowing through the bent pipe 33 of the pipe 44 is shown in FIG.
  • the distribution of the refrigerant in the pipe 47 is shown in FIG. 39, and the distribution of the refrigerant in the pipe 48 is shown in FIG.
  • the Y-shaped branch pipe 37b has a portion (pipe portion A) for branching the refrigerant in a manner having a direction component (X direction component) with respect to the direction (X direction) in which the refrigerant flows.
  • X direction component direction component
  • the liquid refrigerant can easily flow due to the inertial force, and the refrigerant having a high liquid ratio can be flowed from the pipe portion A to the pipe 43.
  • the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume. .
  • heat exchange between the refrigerant and the air can be performed more efficiently.
  • Embodiment 5 the 5th example of the branch distribution part which comprises a refrigerant
  • the branch distribution unit 11 includes a cylindrical body 36 (branch portion).
  • a pipe 41 first flow path
  • a pipe 43 second flow path
  • a pipe 44 third flow path
  • the pipes 43 and 44 include a bent pipe 33.
  • the two-phase refrigerant (see FIG. 42) that has flowed through the pipe 41 flows into the cylindrical body 36.
  • the high-density liquid refrigerant gathers in the lower part of the cylindrical body 36 due to gravity
  • the low-density gas refrigerant gathers in the upper part of the cylindrical body 36.
  • the refrigerant containing a large amount of liquid refrigerant collected at the lower part of the cylindrical body 36 flows through the pipe 43 including the bent pipe 33 and is further distributed by the refrigerant distributor 21a.
  • the distributed refrigerant flows through the pipe 47 and is sent to the outdoor heat exchanger 7a.
  • the refrigerant containing a large amount of gas refrigerant collected at the upper part of the cylindrical body 36 flows through the pipe 44 including the bent pipe 33 and is further distributed by the refrigerant distributor 21b.
  • the distributed refrigerant flows through the pipe 48 and is sent to the outdoor heat exchanger 7b.
  • the distribution of the refrigerant in the pipe 43 immediately after flowing out of the cylindrical body 36 is shown in FIG. 43, and the distribution of the refrigerant in the pipe 44 immediately after flowing out of the cylindrical body 36 is shown in FIG.
  • the distribution of the refrigerant in the pipe 43 immediately after flowing through the bent pipe 33 of the pipe 43 is shown in FIG. 45, and the distribution of the refrigerant in the pipe 44 immediately after flowing through the bent pipe 33 of the pipe 44 is shown in FIG.
  • the distribution of the refrigerant in the pipe 47 is shown in FIG. 47, and the distribution of the refrigerant in the pipe 48 is shown in FIG.
  • the refrigerant flowing through the pipe 41 is divided into a refrigerant with a high liquid ratio and a refrigerant with a low liquid ratio by the tubular body 36, the bent pipe 33, and the like.
  • a refrigerant with a high liquid ratio flows into the outdoor heat exchanger 7a, and a refrigerant with a low liquid ratio flows into the outdoor heat exchanger 7b.
  • the refrigerant A having a high liquid ratio flows into the outdoor heat exchanger 7a having a larger air volume, and the refrigerant B having a low liquid ratio flows into the outdoor heat exchanger 7b having a smaller air volume.
  • coolant and air can be performed more efficiently.
  • branching / distributing units described in the respective embodiments can be variously combined as necessary.
  • the orifice described in the third embodiment may be applied to the branch / distribution unit of another embodiment.
  • the building multi-air conditioner has been described as an example of the refrigeration cycle apparatus, it can be applied to a refrigeration cycle apparatus such as a heat pump apparatus or a car air conditioner.
  • the present invention is effectively used in a refrigeration cycle apparatus equipped with a heat exchanger.
  • Refrigeration cycle apparatus 3 compressor, 5a, 5b four-way valve, 7, 7a, 7b, 7aa, 7ab, 7ac outdoor heat exchanger, 9a, 9b expansion valve, 11 branch distributor, 13a, 13b, 13c, 13d expansion Valve, 15, 15a, 15b, 15c, 15d Indoor heat exchanger, 17 Outdoor fan, 19a, 19b Indoor fan, 21a, 21b Refrigerant distributor, 23 Accumulator, 25 Outdoor unit, 26 Housing, 27 Air intake, 31 Branch pipe, 33 bent pipe, 35, 35a, 35b, 35c T-shaped branch pipe, 36 cylindrical body, 37, 37a, 37b Y-shaped branch pipe, 39 orifice, 39a shielding part, 39b opening, 41, 43 44, 45, 47, 48, 49 piping, 51 liquid refrigerant, 53 gas refrigerant.

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  • General Engineering & Computer Science (AREA)
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Abstract

Un dispositif à cycle de réfrigération (1) est pourvu d'un distributeur de dérivation (11) qui dévie un réfrigérant d'états à deux phases liquide et gazeux vers des réfrigérants ayant des rapports liquides différents. Le distributeur de dérivation (11) comprend un tuyau (41) qui comprend un tuyau coudé (33), un tuyau de dérivation (31), un tuyau (43) et autre un tuyau (44). Le réfrigérant s'écoulant dans le tuyau (41) est divisé en réfrigérant ayant un rapport de liquide élevé et un réfrigérant ayant un faible rapport de liquide en s'écoulant à travers le tuyau coudé (33) et le tuyau de dérivation (31). Le réfrigérant ayant un rapport de liquide élevé s'écoule dans un tuyau (47) et est conduit à un échangeur de chaleur (7a) qui a un grand volume d'air. Le réfrigérant à faible rapport de liquide s'écoule dans un tuyau (48) et est conduit à un échangeur de chaleur (7b) qui possède un petit volume d'air.
PCT/JP2016/068811 2016-06-24 2016-06-24 Distributeur de dérivation de réfrigérant, échangeur de chaleur le comprenant et dispositif à cycle de réfrigération Ceased WO2017221401A1 (fr)

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JP2018523251A JP6668469B2 (ja) 2016-06-24 2016-06-24 冷媒分岐分配器を備えた熱交換器および冷凍サイクル装置
GB1816567.0A GB2566165B (en) 2016-06-24 2016-06-24 Heat exchanger including refrigerant branch distribution device, and refrigeration cycle apparatus
PCT/JP2016/068811 WO2017221401A1 (fr) 2016-06-24 2016-06-24 Distributeur de dérivation de réfrigérant, échangeur de chaleur le comprenant et dispositif à cycle de réfrigération
US16/089,651 US20190113244A1 (en) 2016-06-24 2016-06-24 Heat Exchanger Including Refrigerant Branch Distribution Device, and Refrigeration Cycle Apparatus

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JP2020115045A (ja) * 2019-01-17 2020-07-30 株式会社富士通ゼネラル 空気調和装置
CN112240654A (zh) * 2019-07-17 2021-01-19 日立江森自控空调有限公司 换热器、空调装置、室内机以及室外机
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CN108870633B (zh) * 2018-06-28 2019-10-25 珠海格力电器股份有限公司 空调系统的控制方法和装置
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JP2020115045A (ja) * 2019-01-17 2020-07-30 株式会社富士通ゼネラル 空気調和装置
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WO2025197923A1 (fr) * 2024-03-18 2025-09-25 三菱重工サーマルシステムズ株式会社 Tuyau de distribution de fluide frigorigène et climatiseur

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GB2566165B (en) 2020-11-11
US20190113244A1 (en) 2019-04-18

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