US20190113244A1 - Heat Exchanger Including Refrigerant Branch Distribution Device, and Refrigeration Cycle Apparatus - Google Patents

Heat Exchanger Including Refrigerant Branch Distribution Device, and Refrigeration Cycle Apparatus Download PDF

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Publication number
US20190113244A1
US20190113244A1 US16/089,651 US201616089651A US2019113244A1 US 20190113244 A1 US20190113244 A1 US 20190113244A1 US 201616089651 A US201616089651 A US 201616089651A US 2019113244 A1 US2019113244 A1 US 2019113244A1
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Prior art keywords
refrigerant
flow path
pipe
heat exchanger
branch
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US16/089,651
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English (en)
Inventor
Ryota AKAIWA
Shinya Higashiiue
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AKAIWA, Ryota, HIGASHIIUE, SHINYA
Publication of US20190113244A1 publication Critical patent/US20190113244A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/003—
    • 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 branch distribution device and a heat exchanger including the same, and a refrigeration cycle apparatus.
  • the present invention relates to a refrigerant branch distribution device configured to divide refrigerant in a two-phase state of liquid refrigerant and gas refrigerant into refrigerants having different liquid ratios, a heat exchanger including the refrigerant branch distribution device, and a refrigeration cycle apparatus including the heat exchanger.
  • the heat exchanger when a heat exchanger is used to decrease the temperature of the air, the heat exchanger functions as an evaporator.
  • Refrigerant flows into the heat exchanger functioning as an evaporator, in a state of a gas-liquid two-phase flow in which gas refrigerant and liquid refrigerant are mixed.
  • the gas refrigerant and the liquid refrigerant differ in density by approximately several tens of times.
  • the heat exchanger includes a portion through which a large volume of air flows and a portion through which a small volume of air flows. Corresponding heat exchange is performed in each of the portion of the heat exchanger having a large volume of air and the portion of the heat exchanger having a small volume of air, and heat exchange is performed more efficiently in the portion of the heat exchanger having a large volume of air.
  • PTL 1 makes a suggestion about a path of a heat exchanger.
  • PTL 2 makes a suggestion about a refrigerant distribution device configured to divide refrigerant.
  • the present invention has been made as a part of development, and one object is to provide a refrigerant branch distribution device that achieves efficient heat exchange of refrigerant in a two-phase state, another object is to provide a heat exchanger including the refrigerant branch distribution device, and still another object is to provide a refrigeration cycle apparatus including the heat exchanger.
  • a refrigerant branch distribution device includes: a first flow path, a second flow path and a third flow path; and a branch portion.
  • the branch portion is connected to the first flow path and is connected to the second flow path and the third flow path, and the branch portion is configured to divide refrigerant so as to flow into the second flow path and the third flow path, the refrigerant including liquid refrigerant and gas refrigerant and flowing from the first flow path.
  • a ratio of the liquid refrigerant in a weight ratio between the liquid refrigerant and the gas refrigerant is defined as a liquid ratio.
  • a first liquid ratio of first refrigerant flowing into the second flow path is higher than a second liquid ratio of second refrigerant flowing into the third flow path.
  • a refrigeration cycle apparatus is a refrigeration cycle apparatus including the above-described heat exchanger.
  • the first refrigerant having a high liquid ratio is positively discharged to the second flow path and the second refrigerant having a low liquid ratio is positively discharged to the third flow path, and thus, heat exchange can be performed efficiently.
  • the second flow path of the refrigerant branch distribution device 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 second refrigerant having a low liquid ratio and the second fluid.
  • heat exchange is performed between the first refrigerant having a high liquid ratio and the first fluid that is larger in amount than the second fluid.
  • the second refrigerant having a high liquid ratio can be subjected to efficient heat exchange.
  • the refrigeration cycle apparatus includes the heat exchanger, and thus, the refrigerant can be subjected to efficient heat exchange.
  • FIG. 1 shows a configuration of a refrigeration cycle apparatus including an outdoor unit provided with a refrigerant distribution device according to a first embodiment.
  • FIG. 2 is a perspective view showing the outdoor unit in the first embodiment.
  • FIG. 3 is a perspective view showing one example of the relation between a volume of air introduced into an outdoor heat exchanger and the heat exchanger in the first embodiment.
  • FIG. 4 shows one example of a routing structure of heat transfer tubes in a part of the outdoor heat exchanger, and one example of the connection relation between a part of the outdoor heat exchanger and a branch distribution portion in the first embodiment.
  • FIG. 5 shows one example of the connection relation between the outdoor heat exchanger and the branch distribution portion in the first embodiment.
  • FIG. 6 is a partial view showing the branch distribution portion arranged in the outdoor unit in the first embodiment.
  • FIG. 7 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line VII-VII shown in FIG. 6 in the first embodiment.
  • FIG. 8 is a partial view showing a refrigerant distribution device including a branch distribution portion arranged in an outdoor unit according to a second embodiment.
  • FIG. 9 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line IX-IX shown in FIG. 8 in the second embodiment.
  • FIG. 10 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line X-X shown in FIG. 8 in the second embodiment.
  • FIG. 11 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XI-XI shown in FIG. 8 in the second embodiment.
  • FIG. 12 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XII-XII shown in FIG. 8 in the second embodiment.
  • FIG. 13 is a partial view showing a branch distribution portion arranged in an outdoor unit according to a modification of the second embodiment.
  • FIG. 15 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XV-XV shown in FIG. 13 in the second embodiment.
  • FIG. 16 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XVI-XVI shown in FIG. 13 in the second embodiment.
  • FIG. 17 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XVII-XVII shown in FIG. 13 in the second embodiment.
  • FIG. 18 is a partial view showing a branch distribution portion arranged in an outdoor unit according to a third embodiment.
  • FIG. 19 is a cross-sectional view of an orifice according to a first example used in the branch distribution portion, along a cross-sectional line XIX-XIX shown in FIG. 18 in the third embodiment.
  • FIG. 20 is a cross-sectional view of an orifice according to a second example used in the branch distribution portion, along the cross-sectional line XIX-XIX shown in FIG. 18 in the third embodiment.
  • FIG. 21 is a cross-sectional view of an orifice according to a third example used in the branch distribution portion, along the cross-sectional line XIX-XIX shown in FIG. 18 in the third embodiment.
  • FIG. 22 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXII-XXII shown in FIG. 18 in the third embodiment.
  • FIG. 23 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXIII-XXIII shown in FIG. 18 in the third embodiment.
  • FIG. 24 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XXIV-XXIV shown in FIG. 18 in the third embodiment.
  • FIG. 25 is a partial view showing a refrigerant distribution device including a branch distribution portion arranged in an outdoor unit according to a fourth embodiment.
  • FIG. 26 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXVI-XXVI shown in FIG. 25 in the fourth embodiment.
  • FIG. 27 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXVII-XXVII shown in FIG. 25 in the fourth embodiment.
  • FIG. 28 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXVIII-XXVIII shown in FIG. 25 in the fourth embodiment.
  • FIG. 29 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXIX-XXIX shown in FIG. 25 in the fourth embodiment.
  • FIG. 30 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXX-XXX shown in FIG. 25 in the fourth embodiment.
  • FIG. 31 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XXXI-XXXI shown in FIG. 25 in the fourth embodiment.
  • FIG. 32 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XXXII-XXXII shown in FIG. 25 in the fourth embodiment.
  • FIG. 33 is a partial view showing a branch distribution portion arranged in an outdoor unit according to a modification of the fourth embodiment.
  • FIG. 34 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXXIV-XXXIV shown in FIG. 33 in the fourth embodiment.
  • FIG. 35 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXXV-XXXV shown in FIG. 33 in the fourth embodiment.
  • FIG. 36 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXXVI-XXXVI shown in FIG. 33 in the fourth embodiment.
  • FIG. 37 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXXVII-XXXVII shown in FIG. 33 in the fourth embodiment.
  • FIG. 38 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XXXVIII-XXXVIII shown in FIG. 33 in the fourth embodiment.
  • FIG. 40 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XL-XL shown in FIG. 33 in the fourth embodiment.
  • FIG. 42 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XLII-XLII shown in FIG. 41 in the fifth embodiment.
  • FIG. 44 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XLIV-XLIV shown in FIG. 41 in the fifth embodiment.
  • FIG. 45 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XLV-XLV shown in FIG. 41 in the fifth embodiment.
  • FIG. 46 is a cross-sectional view showing one example of distribution of refrigerant in a pipe along a cross-sectional line XLVI-XLVI shown in FIG. 41 in the fifth embodiment.
  • FIG. 47 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XLVII-XLVII shown in FIG. 41 in the fifth embodiment.
  • FIG. 48 is a cross-sectional view showing one example of distribution of refrigerant in pipes along a cross-sectional line XLVIII-XLVIII shown in FIG. 41 in the fifth embodiment.
  • a refrigeration cycle apparatus including a refrigerant distribution device will be described. First, a configuration of the refrigeration cycle apparatus will be described. A multi air conditioner for buildings will be described as an example of the refrigeration cycle apparatus.
  • a branch distribution portion 11 is provided between refrigerant distribution devices 21 a and 21 b and expansion valve 13 .
  • Branch distribution portion 11 will be described below.
  • Expansion valves 9 a and 9 b provided between branch distribution portion 11 and refrigerant distribution devices 21 a and 21 b are not essential and are provided as needed.
  • Air is introduced into indoor heat exchangers 15 a to 15 d by indoor fans 19 a , 19 b, 19 c, and 19 d, respectively.
  • indoor heat exchangers 15 a to 15 d heat exchange is performed between the introduced air and the gas refrigerant flowing into each of indoor heat exchangers 15 a to 15 d, and the high-temperature and high-pressure gas refrigerant condenses to high-pressure liquid refrigerant (single phase).
  • each of the rooms where indoor heat exchangers 15 a to 15 d are arranged is heated.
  • the high-pressure liquid refrigerant discharged from indoor heat exchangers 15 a to 15 d passes through expansion valves 13 a, 13 b, 13 c, and 13 d, to thereby become refrigerant in a two-phase state of low-pressure gas refrigerant and liquid refrigerant.
  • the refrigerant in a two-phase state flows into an outdoor unit 25 .
  • the refrigerant in a two-phase state flowing into outdoor unit 25 is divided into two in branch distribution portion 11 .
  • One refrigerant (refrigerant A), of the refrigerant divided into two flows through expansion valve 9 a, refrigerant distribution device 21 a and pipes 47 into outdoor heat exchanger 7 a.
  • the other refrigerant (refrigerant B), of the refrigerant divided into two flows through expansion valve 9 b, refrigerant distribution device 21 b and pipes 48 into outdoor heat exchanger 7 b.
  • outdoor heat exchangers 7 a and 7 b heat exchange is performed between air introduced by outdoor fan 17 and the refrigerant (refrigerant A and refrigerant B) flowing into outdoor heat exchangers 7 a and 7 b, and the liquid refrigerant of the refrigerant in a two-phase state evaporates to low-pressure gas refrigerant (single phase).
  • the low-pressure gas refrigerant discharged from outdoor unit 25 flows through four-way valves 5 a and 5 b and accumulator 23 into compressor 3 .
  • the low-pressure gas refrigerant flowing into compressor 3 is compressed to high-temperature and high-pressure gas refrigerant, which is again discharged from compressor 3 . Thereafter, this cycle is repeated.
  • the high-temperature and high-pressure gas refrigerant compressed by compressor 3 flows through four-way valves 5 a and 5 b into outdoor heat exchangers 7 a and 7 b.
  • outdoor heat exchangers 7 a and 7 b heat exchange is performed between the air introduced by outdoor fan 17 and the gas refrigerant flowing into outdoor heat exchangers 7 a and 7 b, and the high-temperature and high-pressure gas refrigerant condenses to low-temperature and high-pressure liquid refrigerant (single phase).
  • the low-temperature and high-pressure liquid refrigerant passes through expansion valves 13 a to 13 d and the like, to thereby become low-temperature and low-pressure liquid refrigerant.
  • the low-temperature and low-pressure liquid refrigerant flows into each of the plurality of indoor heat exchangers 15 a to 15 d.
  • indoor heat exchangers 15 a to 15 d heat exchange is performed between the air introduced by indoor fans 19 a to 19 d and the liquid refrigerant flowing into indoor heat exchangers 15 a to 15 d, and the low-temperature and low-pressure liquid refrigerant evaporates to low-pressure gas refrigerant (single phase).
  • each of the rooms where indoor heat exchangers 15 a to 15 d are arranged is cooled.
  • the low-pressure gas refrigerant discharged from indoor heat exchangers 15 a to 15 d flows through four-way valves 5 a and 5 b and accumulator 23 into compressor 3 .
  • the low-pressure gas refrigerant flowing into the compressor is compressed to high-temperature and high-pressure gas refrigerant, which is again discharged from the compressor. Thereafter, this cycle is repeated.
  • outdoor heat exchanger 7 of outdoor unit 25 functions as an evaporator during heating operation, and functions as a condenser during cooling operation.
  • One example of the outdoor unit of the multi air conditioner for buildings is an outdoor unit including a top flow-type fan. As shown in FIG. 2 , in top flow-type outdoor unit 25 , outdoor fan 17 is attached to an upper surface portion of a housing 26 .
  • Air inlets 27 through which the air is taken in are provided in three side surface portions (three sides) of four side surface portions of the housing. As shown in FIG. 3 , outdoor heat exchanger 7 is arranged in housing 26 . Outdoor heat exchanger 7 is arranged so as to face the three air inlets (side surface portions of the housing). Branch distribution portion 11 , the compressor (not shown) and the like are also arranged in housing 26 .
  • outdoor fan 17 is attached to the upper surface portion of housing 26 . Therefore, in outdoor heat exchanger 7 , a pressure loss of the air becomes lower as a distance from outdoor fan 17 becomes shorter, and the pressure loss of the air becomes higher as the distance from outdoor fan 17 becomes longer. That is, the pressure loss becomes higher gradually from an upper part toward a lower part of outdoor heat exchanger 7 , and thus, a volume of air passing through outdoor heat exchanger 7 a is relatively large and a volume of air passing through outdoor heat exchanger 7 b is relatively small (see arrows in FIG. 3 ).
  • FIG. 4 shows one example of the connection relation between outdoor heat exchanger 7 a and the pipes.
  • outdoor heat exchanger 7 a is formed of, for example, three rows of outdoor heat exchangers 7 aa , 7 ab and 7 ac .
  • Heat transfer tubes (not shown) are attached to each of the three rows of outdoor heat exchangers 7 aa , 7 ab and 7 ac .
  • a plurality of pipes 47 branching off from refrigerant distribution device 21 a are connected to the corresponding heat transfer tubes of the first row of outdoor heat exchanger 7 a, respectively.
  • One refrigerant path extends from the heat transfer tube of the first row of outdoor heat exchanger 7 aa through the heat transfer tube of the second row of outdoor heat exchanger 7 ab and the heat transfer tube of the third row of outdoor heat exchanger 7 ac to a refrigerant distribution device 29 .
  • a plurality of pipes 48 branching off from refrigerant distribution device 21 b are connected (see FIG. 5 ).
  • outdoor heat exchanger 7 When outdoor heat exchanger 7 functions as an evaporator, it is required to allow the liquid refrigerant of the refrigerant in a two-phase state to flow into outdoor heat exchanger 7 a having a larger volume of air, such that the liquid refrigerant efficiently evaporates to gas refrigerant.
  • outdoor unit 25 is provided with branch distribution portion 11 as shown in FIG. 5 .
  • the refrigerant in a two-phase state flowing from indoor heat exchanger 15 is divided into two lines of refrigerant (refrigerant A and refrigerant B) during heating operation.
  • a ratio of the liquid refrigerant in a weight ratio between the liquid refrigerant and the gas refrigerant is defined as a liquid ratio.
  • Refrigerant A is refrigerant having a high liquid ratio.
  • Refrigerant B is refrigerant having a low liquid ratio.
  • the refrigerant is macroscopically divided into refrigerant A having a high liquid ratio and refrigerant B having a low liquid ratio.
  • Refrigerant A is further divided microscopically by refrigerant distribution device 21 a and fed to outdoor heat exchanger 7 a having a large volume of air.
  • Refrigerant B is further divided microscopically by refrigerant distribution device 21 b and fed to outdoor heat exchanger 7 b having a small volume of air.
  • branch distribution portion 11 includes a pipe 41 (first flow path) including a bent pipe 33 , a branch pipe 31 (branch portion), a pipe 43 (second flow path), and a pipe 44 (third flow path).
  • the refrigerant in a two-phase state flowing through pipe 41 flows through bent pipe 33 , which causes non-uniformity in distribution of the liquid refrigerant. That is, due to the centrifugal force, an amount of the liquid refrigerant flowing along an inner wall surface on the outer circumferential side of bent pipe 33 becomes larger than an amount of the liquid refrigerant flowing along an inner wall surface on the inner circumferential side of bent pipe 33 .
  • the refrigerant (refrigerant A) having a high liquid ratio flows through a region corresponding to the outer circumferential side of bent pipe 33
  • the refrigerant (refrigerant B) having a low liquid ratio flows through a region corresponding to the inner circumferential side of bent pipe 33 .
  • the refrigerant flowing through pipe 41 in this state is divided into refrigerant A and refrigerant B by branch pipe 31 .
  • Divided refrigerant A flows through pipe 43 , refrigerant distribution device 21 a and pipes 47 into outdoor heat exchanger 7 a.
  • refrigerant B flows through pipe 44 , refrigerant distribution device 21 b and pipes 48 into outdoor heat exchanger 7 b.
  • refrigerant A having a high liquid ratio flows into outdoor heat exchanger 7 a having a larger volume of air
  • refrigerant B having a low liquid ratio flows into outdoor heat exchanger 7 b having a smaller volume of air.
  • the above-described method using branch distribution portion 11 can allow the refrigerant having a high liquid ratio to flow into outdoor heat exchanger 7 a having a larger volume of air, with a simple structure of bent pipe 33 and branch pipe 31 .
  • a length L of a straight portion of pipe 41 extending from bent pipe 33 to branch pipe 31 needs to be set at such a length that the liquid refrigerant in pipe 41 flows into branch pipe 31 with non-uniform and uneven distribution (see FIG. 7 ).
  • Length L of the straight portion needs to satisfy the relation of L ⁇ 10 ⁇ D, where D represents an inner diameter ⁇ of the bent pipe.
  • expansion valves 9 a and 9 b may be provided between refrigerant distribution devices 21 a and 21 b and branch distribution portion 11 . Particularly by adjusting a degree of opening of expansion valve 9 a, it is possible to prevent the liquid refrigerant from flowing through pipe 43 excessively.
  • branch distribution portion 11 includes a T-shaped branch pipe 35 a ( 35 ) (branch portion) having a shape similar to the shape of alphabetical “T”.
  • T-shaped branch pipe 35 a includes a portion extending in one direction (pipe portion A), and a portion branching off from pipe portion A in a direction almost orthogonal to the one direction.
  • Pipe 43 (second flow path) including bent pipe 33 is connected to pipe portion A.
  • Refrigerant distribution device 21 a is connected to pipe 43 , and further, a plurality of pipes 47 are connected to refrigerant distribution device 21 a.
  • pipe 44 (third flow path) is connected to pipe portion B.
  • Refrigerant distribution device 21 b is connected to pipe 44 , and further, a plurality of pipes 48 are connected to refrigerant distribution device 21 b.
  • the plurality of pipes 47 are connected to outdoor heat exchanger 7 a, and the plurality of pipes 48 are connected to outdoor heat exchanger 7 b (see FIG. 3 ).
  • non-uniformity occurs in the distribution of the liquid refrigerant included in refrigerant A. That is, as described above, due to the centrifugal force, an amount of the liquid refrigerant flowing along an inner wall surface on the outer circumferential side of bent pipe 33 becomes larger than an amount of the liquid refrigerant flowing along an inner wall surface on the inner circumferential side of bent pipe 33 .
  • the refrigerant (refrigerant AA) having a high liquid ratio flows through a region corresponding to the outer circumferential side
  • the refrigerant (refrigerant AB) having a low liquid ratio flows through a region corresponding to the inner circumferential side.
  • refrigerant (refrigerant AA and refrigerant AB) flowing through pipe 43 flows into refrigerant distribution device 21 a in this state.
  • refrigerant distribution device 21 a the refrigerant flowing into refrigerant distribution device 21 a is divided so as to flow into the plurality of pipes 47 .
  • refrigerant AA having a high liquid ratio flows into pipe 47 arranged at a position corresponding to the outer circumferential side of the bent pipe, of the plurality of pipes 47 .
  • refrigerant AB having a low liquid ratio flows into pipe 47 arranged at a position corresponding to the inner circumferential side of the bent pipe.
  • refrigerant AA having a high liquid ratio flows through an upper path of outdoor heat exchanger 7 a having a relatively large volume of air
  • refrigerant AB having a low liquid ratio flows through a lower path of outdoor heat exchanger 7 a having a relatively small volume of air (see FIG. 5 ).
  • heat exchange between the refrigerant and the air can be performed more efficiently.
  • T-shaped branch pipe 35 b (branch portion) according to the modification, two portions (pipe portion B and pipe portion C) branch off from a portion (pipe portion A) extending in one direction.
  • Pipe 45 (fourth flow path) is connected to pipe portion C.
  • a refrigerant distribution device 21 c is connected to pipe 45 , and further, a plurality of pipes 49 are connected to refrigerant distribution device 21 c.
  • the plurality of pipes 49 are connected to outdoor heat exchanger 7 b together with pipes 48 , for example.
  • T-shaped branch pipe 35 b and the like is similar to the configuration shown in FIG. 8 , and the remaining configuration of the outdoor unit and the remaining configuration of the refrigeration cycle apparatus are similar to the configurations shown in FIGS. 1 and 3 . Therefore, the same members are denoted by the same reference characters and description thereof will not be repeated except when necessary.
  • the liquid refrigerant is less likely to flow through pipe portion B and pipe portion C branching off from pipe portion A, and thus, the refrigerant (refrigerant B) having a low liquid ratio flows through pipe portion B and pipe portion C.
  • the gas refrigerant is likely to flow into pipe portion C located on the upstream side of the refrigerant flow, and thus, the refrigerant having a low liquid ratio flows into pipe portion C.
  • the refrigerant having a high liquid ratio flows into pipe portion B located on the downstream side of the refrigerant flow.
  • the refrigerant (refrigerant BB) having a low liquid ratio flows into pipe 45 connected to pipe portion C.
  • the refrigerant (refrigerant BA) having a high liquid ratio flows into pipe 44 (third flow path) connected to pipe portion B.
  • refrigerant distribution device 21 c the refrigerant flowing into refrigerant distribution device 21 c is divided so as to flow into the plurality of pipes 49 .
  • the refrigerant (refrigerant BA) flowing through pipe 44 flows into refrigerant distribution device 21 b.
  • refrigerant distribution device 21 b the refrigerant flowing into refrigerant distribution device 21 b is divided so as to flow into the plurality of pipes 48 .
  • refrigerant B (refrigerant BB and refrigerant BA) flows through pipes 48 and 49 into outdoor heat exchanger 7 b.
  • refrigerant A having a high liquid ratio flows into outdoor heat exchanger 7 a having a larger volume of air
  • refrigerant B (refrigerant BB and refrigerant BA) having a low liquid ratio flows into outdoor heat exchanger 7 b having a smaller volume of air.
  • refrigerant BA having a high liquid ratio flows through an upper path of outdoor heat exchanger 7 b having a relatively large volume of air
  • refrigerant BB having a low liquid ratio flows through a lower path of outdoor heat exchanger 7 b having a relatively small volume of air (see FIG. 5 ).
  • heat exchange between the refrigerant and the air can be performed more efficiently.
  • branch distribution portion 11 includes an orifice 39 in pipe 41 (first flow path) before (on the upstream side of) T-shaped branch pipe 35 a ( 35 ) (branch portion).
  • Orifice 39 includes an opening through which the refrigerant flows, in a blocking portion configured to block the flow of the refrigerant.
  • An area (flow path cross-sectional area) of the opening of orifice 39 is smaller than a flow path cross-sectional area of pipe 41 .
  • FIG. 19 shows a first example of orifice 39 .
  • a substantially circular opening 39 b is concentrically formed in a blocking portion 39 a configured to block the flow of the refrigerant.
  • FIG. 20 shows a second example of orifice 39 .
  • substantially semicircular opening 39 b is formed in blocking portion 39 a configured to block the flow of the refrigerant.
  • blocking portion 39 a is arranged at a circumferential position at which pipe 44 (third flow path) is connected to T-shaped branch pipe 35 a.
  • FIG. 21 shows a third example of orifice 39 .
  • substantially circular opening 39 b is formed in blocking portion 39 a configured to block the flow of the refrigerant.
  • substantially circular opening 39 b is formed in blocking portion 39 a such that a center of opening 39 b deviates from a center of orifice 39 .
  • blocking portion 39 a is arranged at a circumferential position at which pipe 44 is connected to T-shaped branch pipe 35 a.
  • T-shaped branch pipe 35 a and the like is similar to the configuration shown in FIG. 8 , and the remaining configuration of the outdoor unit and the remaining configuration of the refrigeration cycle apparatus are similar to the configurations shown in FIGS. 1 and 3 . Therefore, the same members are denoted by the same reference characters and description thereof will not be repeated except when necessary.
  • the refrigerant flowing through pipe 43 flows through bent pipe 33 and is further divided by refrigerant distribution device 21 a.
  • the divided refrigerant flows through pipes 47 into outdoor heat exchanger 7 a.
  • the refrigerant flowing through pipe 44 flows through bent pipe 33 and is further divided by refrigerant distribution device 21 b.
  • the divided refrigerant flows through pipes 48 into outdoor heat exchanger 7 b.
  • FIG. 29 shows distribution of the refrigerant in pipe 43 immediately after the refrigerant flows through bent pipe 33 of pipe 43 .
  • FIG. 30 shows distribution of the refrigerant in pipe 44 immediately after the refrigerant flows through bent pipe 33 of pipe 44 .
  • FIG. 31 shows distribution of the refrigerant in pipes 47 .
  • FIG. 32 shows distribution of the refrigerant in pipes 48 .
  • refrigerant A having a high liquid ratio flows into outdoor heat exchanger 7 a having a larger volume of air
  • refrigerant B having a low liquid ratio flows into outdoor heat exchanger 7 b having a smaller volume of air.
  • a Y-shaped branch pipe 37 b ( 37 ) (branch portion) includes a portion (pipe portion A) configured to cause the refrigerant to branch so as to have a direction component (X direction component) of a direction (e.g., X direction) of the refrigerant flow, and a portion (pipe portion B) configured to cause the refrigerant to branch so as to have a direction component ( ⁇ X direction component) opposite to the direction component (see the vectors shown in FIG. 33 ).
  • FIG. 37 shows distribution of the refrigerant in pipe 43 immediately after the refrigerant flows through bent pipe 33 of pipe 43 .
  • FIG. 38 shows distribution of the refrigerant in pipe 44 immediately after the refrigerant flows through bent pipe 33 of pipe 44 .
  • FIG. 39 shows distribution of the refrigerant in pipes 47 .
  • FIG. 40 shows distribution of the refrigerant in pipes 48 .
  • Y-shaped branch pipe 37 b has the portion (pipe portion A) configured to cause the refrigerant to branch so as to have the direction component (X direction component) of the direction (X direction) of the refrigerant flow. Therefore, even when a flow rate of the refrigerant is low, the liquid refrigerant is likely to flow by the inertial force, and thus, the refrigerant having a high liquid ratio can flow from pipe portion A to pipe 43 .
  • refrigerant A having a high liquid ratio flows into outdoor heat exchanger 7 a having a larger volume of air
  • refrigerant B having a low liquid ratio flows into outdoor heat exchanger 7 b having a smaller volume of air.
  • branch distribution portion 11 includes a tubular body 36 (branch portion).
  • Pipe 41 first flow path
  • Pipe 43 second flow path
  • Pipe 44 third flow path
  • Each of pipes 43 and 44 includes bent pipe 33 .
  • the refrigerant in a two-phase state (see FIG. 42 ) flowing through pipe 41 flows into tubular body 36 .
  • the liquid refrigerant having a high density accumulates in a lower part in tubular body 36 by gravity
  • the gas refrigerant having a low density accumulates in an upper part in tubular body 36 .
  • the refrigerant including a large amount of liquid refrigerant and accumulating in the lower part in tubular body 36 flows through pipe 43 including bent pipe 33 and is further divided by refrigerant distribution device 21 a.
  • the divided refrigerant flows through pipes 47 into outdoor heat exchanger 7 a.
  • the refrigerant including a large amount of gas refrigerant and accumulating in the upper part in tubular body 36 flows through pipe 44 including bent pipe 33 and is further divided by refrigerant distribution device 21 b.
  • the divided refrigerant flows through pipes 48 into outdoor heat exchanger 7 b.
  • FIG. 43 shows distribution of the refrigerant in pipe 43 immediately after the refrigerant flows out of tubular body 36 .
  • FIG. 44 shows distribution of the refrigerant in pipe 44 immediately after the refrigerant flows out of tubular body 36 .
  • FIG. 45 shows distribution of the refrigerant in pipe 43 immediately after the refrigerant flows through bent pipe 33 of pipe 43 .
  • FIG. 46 shows distribution of the refrigerant in pipe 44 immediately after the refrigerant flows through bent pipe 33 of pipe 44 .
  • FIG. 47 shows distribution of the refrigerant in pipes 47 .
  • FIG. 48 shows distribution of the refrigerant in pipes 48 .
  • the refrigerant flowing through pipe 41 is divided into the refrigerant having a high liquid ratio and the refrigerant having a low liquid ratio by tubular body 36 , bent pipe 33 and the like.
  • the refrigerant having a high liquid ratio flows into outdoor heat exchanger 7 a, and the refrigerant having a low liquid ratio flows into outdoor heat exchanger 7 b.
  • refrigerant A having a high liquid ratio flows into outdoor heat exchanger 7 a having a larger volume of air
  • refrigerant B having a low liquid ratio flows into outdoor heat exchanger 7 b having a smaller volume of air.
  • the branch distribution portions described in the embodiments can be variously combined as needed.
  • the orifice described in the third embodiment may be applied to the branch distribution portions in the other embodiments.
  • the multi air conditioner for buildings has been described as an example of the refrigeration cycle apparatus.
  • the present invention is also applicable to a refrigeration cycle apparatus such as, for example, a heat pump apparatus or a car air conditioner.
  • the present invention is effectively utilized in a refrigeration cycle apparatus including a heat exchanger.
US16/089,651 2016-06-24 2016-06-24 Heat Exchanger Including Refrigerant Branch Distribution Device, and Refrigeration Cycle Apparatus Abandoned US20190113244A1 (en)

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GB2566165A (en) 2019-03-06
GB201816567D0 (en) 2018-11-28

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