WO2020250952A1 - Conditionneur d'air - Google Patents

Conditionneur d'air Download PDF

Info

Publication number
WO2020250952A1
WO2020250952A1 PCT/JP2020/022922 JP2020022922W WO2020250952A1 WO 2020250952 A1 WO2020250952 A1 WO 2020250952A1 JP 2020022922 W JP2020022922 W JP 2020022922W WO 2020250952 A1 WO2020250952 A1 WO 2020250952A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
connecting pipe
cycle
diameter
secondary side
Prior art date
Application number
PCT/JP2020/022922
Other languages
English (en)
Japanese (ja)
Inventor
山田　拓郎
熊倉　英二
吉見　敦史
岩田　育弘
知厚 南田
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to EP20822547.4A priority Critical patent/EP3978831B1/fr
Priority to CN202080042764.0A priority patent/CN113950602B/zh
Priority to US17/618,075 priority patent/US20220316767A1/en
Priority to PL20822547.4T priority patent/PL3978831T3/pl
Priority to ES20822547T priority patent/ES2961904T3/es
Publication of WO2020250952A1 publication Critical patent/WO2020250952A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • 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
    • F25B2500/16—Lubrication

Definitions

  • Patent Document 1 Japanese Unexamined Patent Publication No. 2014-74508 discloses a refrigerant cycle system having a cascade heat exchanger. By introducing a cascade heat exchanger, the refrigerant cycle system constitutes a dual refrigerant cycle having a primary side cycle including a heat source heat exchanger and a secondary side cycle including a utilization heat exchanger.
  • the flow velocity of the refrigerant tends to be slower in the secondary side cycle of the dual refrigerant cycle. In this case, it becomes difficult for the refrigerating machine oil that has flowed out of the compressor to return to the compressor again.
  • the refrigerant cycle system includes a vapor compression type primary side cycle for circulating the first refrigerant, a vapor compression type secondary side cycle for circulating the second refrigerant, and a first refrigerant and a second refrigerant. It is equipped with a cascade heat exchanger that allows heat exchange between them.
  • the primary side cycle has a heat source heat exchanger for applying cold or hot heat to the first refrigerant, and a primary side connecting pipe for connecting the cascade heat exchanger and the heat source heat exchanger.
  • the secondary side cycle includes a utilization heat exchanger for utilizing the cold or hot heat obtained from the cascade heat exchanger by the second refrigerant and a secondary side connecting pipe for connecting the cascade heat exchanger and the utilization heat exchanger.
  • the primary side connecting pipe has a primary side gas connecting pipe and a primary side liquid connecting pipe.
  • the secondary side connecting pipe has a secondary side gas connecting pipe and a secondary side liquid connecting pipe.
  • the diameter of the secondary gas connecting pipe is smaller than the diameter of the primary gas connecting pipe, or the diameter of the secondary liquid connecting pipe is smaller than the diameter of the primary liquid connecting pipe. ..
  • the diameter of the connecting pipe in the secondary cycle is smaller than the diameter of the connecting pipe in the primary side cycle. Therefore, since the flow velocity of the refrigerant can be increased in the secondary side cycle, the refrigerating machine oil flowing out of the compressor can easily return to the compressor.
  • the refrigerant cycle system according to the second aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary cycle is 4.5 kW or more and 5.6 kW or less.
  • the diameter of the secondary gas connecting pipe is 7.9 mm (5/16 inch).
  • the refrigerant cycle system according to the third aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary cycle is 7.1 kW or more and 9.0 kW or less.
  • the diameter of the secondary gas connecting pipe is 9.5 mm (3/8 inch).
  • the refrigerant cycle system according to the fourth aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary cycle is 16 kW or more and 22.4 kW or less.
  • the diameter of the secondary gas connecting pipe is 12.7 mm (1/2 inch).
  • the refrigerant cycle system according to the fifth aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary cycle is 5.6 kW or more and 8.0 kW or less.
  • the diameter of the secondary side liquid communication pipe is 4.8 mm (3/16 inch).
  • the refrigerant cycle system according to the sixth aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary cycle is 11.2 kW or more and 16 kW or less.
  • the diameter of the secondary side liquid communication pipe is 6.4 mm (1/4 inch).
  • the refrigerant cycle system according to the seventh aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary cycle is 16 kW or more and 28 kW or less.
  • the diameter of the secondary side liquid connecting pipe is 7.9 mm (5/16 inch).
  • the refrigerant cycle system according to the eighth aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary cycle is 33.5 kW or more and 45 kW or less.
  • the diameter of the secondary side liquid connecting pipe is 9.5 mm (3/8 inch).
  • the refrigerant cycle system according to the ninth aspect is the refrigerant cycle system according to the first aspect, and the second refrigerant is R32.
  • the refrigerating capacity of the secondary cycle is 16 kW or more and 22.4 kW or less.
  • the diameter of the secondary gas connecting pipe is 15.9 mm (5/8 inch).
  • the refrigerant cycle system according to the tenth viewpoint is the refrigerant cycle system according to the first viewpoint, and the second refrigerant is R32.
  • the refrigerating capacity of the secondary cycle is 2.8 kW or more and 3.6 kW or less.
  • the diameter of the secondary side liquid communication pipe is 4.8 mm (3/16 inch).
  • the refrigerant cycle system according to the eleventh viewpoint is the refrigerant cycle system according to the first viewpoint, and the second refrigerant is R32.
  • the refrigerating capacity of the secondary cycle is 14 kW or more and 16 kW or less.
  • the diameter of the secondary side liquid connecting pipe is 7.9 mm (5/16 inch).
  • the refrigerant cycle system according to the twelfth viewpoint is the refrigerant cycle system according to the first viewpoint, and the second refrigerant is R32.
  • the refrigerating capacity of the secondary cycle is 28 kW or more and 33.5 kW or less.
  • the diameter of the secondary side liquid connecting pipe is 9.5 mm (3/8 inch).
  • the refrigerant cycle system according to the thirteenth viewpoint is the refrigerant cycle system according to the first viewpoint, and the second refrigerant is R454B.
  • the refrigerating capacity of the secondary cycle is 9.0 kW or more and 11.2 kW or less.
  • the diameter of the secondary gas connecting pipe is 15.9 mm (5/8 inch).
  • the refrigerant cycle system according to the 14th viewpoint is the refrigerant cycle system according to the 1st viewpoint, and the second refrigerant is R454B.
  • the refrigerating capacity of the secondary cycle is 16.0 kW or more and 22.4 kW or less.
  • the diameter of the secondary gas connecting pipe is 19.1 mm (3/4 inch).
  • the refrigerant cycle system according to the fifteenth viewpoint is the refrigerant cycle system according to the first viewpoint, and the second refrigerant is R454B.
  • the refrigerating capacity of the secondary cycle is 16 kW or more and 22.4 kW or less.
  • the diameter of the secondary side liquid connecting pipe is 9.5 mm (3/8 inch).
  • the refrigerant cycle system according to the 16th viewpoint is the refrigerant cycle system according to the 1st viewpoint, and the second refrigerant is R454B.
  • the refrigerating capacity of the secondary cycle is 45 kW or more and 56 kW or less.
  • the diameter of the secondary side liquid connecting pipe is 12.7 mm (1/2 inch).
  • the refrigerant cycle system according to the 17th viewpoint is the refrigerant cycle system according to the 1st viewpoint, and the second refrigerant is R454B.
  • the refrigerating capacity of the secondary cycle is 85 kW or more and 109 kW or less.
  • the diameter of the secondary side liquid connecting pipe is 15.9 mm (5/8 inch).
  • the refrigerant cycle system according to the 18th viewpoint is the refrigerant cycle system according to any one of the 1st to 17th viewpoints, and the pipe diameter of the secondary gas connecting pipe is 90 of the pipe diameter of the primary gas connecting pipe. % Or less, or the pipe diameter of the secondary side liquid connecting pipe is 90% or less of the pipe diameter of the primary side liquid connecting pipe.
  • the compression ratio of the secondary side cycle is smaller than the compression ratio of the primary side cycle in the refrigerant cycle system according to any one of the 1st to 18th viewpoints.
  • FIG. 1 shows a refrigerant cycle system 100.
  • the refrigerant cycle system 100 is for acquiring cold or hot from a heat source and providing cold or hot to the user.
  • acquiring cold heat from a heat source means dissipating heat to the heat source.
  • Getting heat from a heat source means endothermic from a heat source.
  • Providing cold heat to the user means endothermic from the environment in which the user is.
  • providing heat to the user means dissipating heat to the environment in which the user is present.
  • the refrigerant cycle system 100 has one heat source unit 10, one cascade unit 30, and one utilization unit 50.
  • the primary side cycle 20 is configured by connecting the heat source unit 10 and the cascade unit 30.
  • the primary side cycle 20 is a vapor compression type circuit that circulates the first refrigerant.
  • the secondary side cycle 40 is configured by connecting the cascade unit 30 and the utilization unit 50.
  • the secondary side cycle 40 is a vapor compression type circuit that circulates the second refrigerant.
  • the first refrigerant and the second refrigerant may be the same refrigerant or may be different refrigerants.
  • the heat source unit 10 acquires cold heat or heat from the outside air which is a heat source.
  • the heat source unit 10 includes a compressor 11, a four-way switching valve 12, a heat source heat exchanger 13, a heat source expansion valve 14, a supercooling expansion valve 15, a supercooling heat exchanger 16, a liquid closing valve 18, and a gas closing valve 19. ..
  • the compressor 11 sucks in the low-pressure gas refrigerant which is the first refrigerant, compresses it, and discharges the high-pressure gas refrigerant.
  • the four-way switching valve 12 makes the connection shown by the solid line in FIG. 1 in the case of cooling operation, and makes the connection shown by the broken line in FIG. 1 in the case of heating operation.
  • the heat source heat exchanger 13 exchanges heat between the first refrigerant and the outside air.
  • the heat source heat exchanger 13 functions as a condenser in the case of cooling operation and functions as an evaporator in the case of heating operation.
  • the heat source expansion valve 14 regulates the flow rate of the first refrigerant. Further, the heat source expansion valve 14 functions as a pressure reducing device for reducing the pressure of the first refrigerant.
  • the supercooling expansion valve 15 decompresses the circulating first refrigerant to produce a cooling gas.
  • the supercooling heat exchanger 16 imparts a degree of supercooling to the first refrigerant by exchanging heat between the circulating first refrigerant and the cooling gas.
  • the liquid shutoff valve 18 and the gas shutoff valve 19 shut off the flow path through which the first refrigerant circulates when the heat source unit 10 is installed.
  • (2-2) Cascade unit 30 The cascade unit 30 is for exchanging heat between the first refrigerant and the second refrigerant.
  • the cascade unit 30 includes a primary side expansion valve 31, a secondary side expansion valve 32, a compressor 33, a four-way switching valve 34, a cascade heat exchanger 35, a liquid closing valve 38, and a gas closing valve 39.
  • the primary side expansion valve 31 adjusts the amount of the first refrigerant circulating in the primary side cycle 20. Further, the primary expansion valve 31 depressurizes the first refrigerant.
  • the secondary side expansion valve 32 adjusts the amount of the second refrigerant circulating in the secondary side cycle 40. Further, the secondary expansion valve 32 depressurizes the second refrigerant.
  • the compressor 33 sucks in the low-pressure gas refrigerant which is the second refrigerant, compresses it, and discharges the high-pressure gas refrigerant.
  • the four-way switching valve 34 functions as a switching device, and makes the connection shown by the solid line in FIG. 1 in the case of cooling operation and the connection shown by the broken line in FIG. 1 in the case of heating operation.
  • the cascade heat exchanger 35 exchanges heat between the first refrigerant and the second refrigerant.
  • the cascade heat exchanger 35 is, for example, a plate heat exchanger.
  • the cascade heat exchanger 35 has a first refrigerant passage 351 and a second refrigerant passage 352.
  • the first refrigerant passage 351 passes the first refrigerant.
  • the second refrigerant passage 352 allows the second refrigerant to pass through.
  • the cascade heat exchanger 35 functions as an evaporator of the first refrigerant and a condenser of the second refrigerant in the case of cooling operation, and as an evaporator of the first refrigerant and a condenser of the second refrigerant in the case of heating operation. Function.
  • the liquid shutoff valve 38 and the gas shutoff valve 39 shut off the flow path through which the second refrigerant circulates when the cascade unit 30 is installed.
  • the utilization unit 50 is for providing cold or hot to the user.
  • the utilization unit 50 includes a utilization heat exchanger 51 and a utilization expansion valve 52.
  • the utilization heat exchanger 51 is for allowing the user to utilize cold heat or hot heat.
  • the utilization heat exchanger 51 is a microchannel heat exchanger and has a flat multi-hole tube.
  • the utilization expansion valve 52 adjusts the amount of the second refrigerant circulating in the secondary side cycle 40. Further, the utilization expansion valve 52 functions as a pressure reducing device for reducing the pressure of the second refrigerant.
  • the primary side connecting pipe includes a primary side liquid connecting pipe 21 and a primary side gas connecting pipe 22.
  • the primary side liquid connecting pipe 21 connects the liquid closing valve 18 of the heat source unit 10 and the cascade unit 30.
  • the primary side gas connecting pipe 22 connects the gas closing valve 19 of the heat source unit 10 and the cascade unit 30.
  • the secondary side connecting pipe includes a secondary side liquid connecting pipe 41 and a secondary side gas connecting pipe 42.
  • the secondary side liquid connecting pipe 41 connects the liquid closing valve 38 of the cascade unit 30 and the utilization unit 50.
  • the secondary side gas connecting pipe 42 connects the gas closing valve 39 of the cascade unit 30 and the utilization unit 50.
  • the high-pressure liquid refrigerant passes through the fully opened heat source expansion valve 14, the supercooling heat exchanger 16, and reaches the primary side expansion valve 31 via the liquid closing valve 18 and the primary side liquid communication pipe 21. To do.
  • the primary expansion valve 31 with an appropriate opening depressurizes the high-pressure liquid refrigerant, thereby producing a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant enters the first refrigerant passage 351 of the cascade heat exchanger 35.
  • the cascade heat exchanger 35 evaporates the low pressure gas-liquid two-phase refrigerant, thereby producing a low pressure gas refrigerant.
  • the first refrigerant absorbs heat from the second refrigerant.
  • the low-pressure gas refrigerant exits the first refrigerant passage 351, passes through the primary side gas connecting pipe 22 and the gas closing valve 19, and is sucked into the compressor 11 via the four-way switching valve 12.
  • a part of the high-pressure liquid refrigerant discharged from the heat source expansion valve 14 is decompressed by the supercooling expansion valve 15 having an appropriate opening degree, and becomes a gas-liquid two-phase cooling gas.
  • the cooling gas passes through the supercooling heat exchanger 16. At this time, the cooling gas gives a degree of supercooling by cooling the high-pressure liquid refrigerant.
  • the cooling gas exits the supercooling heat exchanger 16, mixes with the low-pressure gas refrigerant coming from the four-way switching valve 12, and is sucked into the compressor 11.
  • the compressor 33 sucks in the low-pressure gas refrigerant which is the second refrigerant and discharges the high-pressure gas refrigerant.
  • the high-pressure gas refrigerant enters the second refrigerant passage 352 of the cascade heat exchanger 35 via the four-way switching valve 34.
  • the cascade heat exchanger 35 condenses the high pressure gas refrigerant, thereby producing a high pressure liquid refrigerant.
  • the second refrigerant releases heat to the first refrigerant.
  • the high-pressure liquid refrigerant exits the second refrigerant passage 352 and reaches the secondary expansion valve 32.
  • the secondary expansion valve 32 which has an appropriate opening degree, depressurizes the high-pressure liquid refrigerant, thereby producing a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant passes through the liquid closing valve 38 and the secondary side liquid connecting pipe 41 and reaches the utilization expansion valve 52.
  • the utilization expansion valve 52 with an appropriate opening degree further reduces the pressure of the low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant reaches the utilization heat exchanger 51.
  • the utilization heat exchanger 51 evaporates the low-pressure gas-liquid two-phase refrigerant, thereby producing a low-pressure gas refrigerant.
  • the refrigerant which is the second refrigerant, absorbs heat from the environment in which the user is present.
  • the low-pressure gas refrigerant exits the utilization heat exchanger 51, passes through the secondary side gas connecting pipe 42 and the gas closing valve 39, and is sucked into the compressor 33 via the four-way switching valve 12.
  • the high-pressure liquid refrigerant passes through the fully opened primary side expansion valve 31, then passes through the primary side liquid communication pipe 21, the liquid closing valve 18, and the supercooling heat exchanger 16 and reaches the heat source expansion valve 14.
  • the heat source expansion valve 14 having an appropriate opening degree depressurizes the high-pressure liquid refrigerant, thereby producing a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant reaches the heat source heat exchanger 13.
  • the heat source heat exchanger 13 evaporates the low-pressure gas-liquid two-phase refrigerant, thereby producing a low-pressure gas refrigerant.
  • the refrigerant which is the first refrigerant, absorbs heat from the outside air.
  • the low-pressure gas refrigerant passes through the four-way switching valve 12 and is sucked into the compressor 11.
  • the compressor 33 sucks in the low-pressure gas refrigerant which is the second refrigerant and discharges the high-pressure gas refrigerant.
  • the high-pressure gas refrigerant passes through the gas closing valve 39 and the secondary side gas connecting pipe 42 via the four-way switching valve 34, and reaches the utilization heat exchanger 51.
  • the utilization heat exchanger 51 condenses the high-pressure gas refrigerant, thereby producing a high-pressure liquid refrigerant.
  • the refrigerant which is the second refrigerant, releases heat to the environment in which the user is present.
  • the high-pressure liquid refrigerant reaches the utilization expansion valve 52.
  • the utilization expansion valve 52 depressurizes the high-pressure liquid refrigerant, thereby producing a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant passes through the secondary side liquid connecting pipe 41 and the liquid closing valve 38, and reaches the secondary side expansion valve 32.
  • the secondary expansion valve 32 with an appropriate opening degree further reduces the pressure of the low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant enters the second refrigerant passage 352 of the cascade heat exchanger 35.
  • the cascade heat exchanger 35 evaporates the low pressure gas-liquid two-phase refrigerant, thereby producing a low pressure gas refrigerant.
  • the second refrigerant absorbs heat from the first refrigerant.
  • the low-pressure gas refrigerant exits the second refrigerant passage 352, passes through the four-way switching valve 34, and is sucked into the compressor 33.
  • the pipe diameters of the primary side gas connecting pipe 22 and the primary side liquid connecting pipe 21 in the dual cycle are the same as those shown in the "Unit" column.
  • the numerical values marked in millimeters in the table refer to pipes manufactured according to the standard based on inches. That is, 4.8 mm refers to 3/16 inch. 6.4 mm refers to 1/4 inch. 7.9 mm refers to 5/16 inch. 9.5 mm refers to 3/8 inch. 12.7 mm refers to 1/2 inch. 15.9 mm refers to 5/8 inch. 19.1 mm refers to 3/4 inch. 22.2 mm refers to 7/8 inch. 25.4 mm refers to 1 inch. 28.6 mm refers to 9/8 inch. 31.8 mm refers to 5/4 inch. 38.1 mm refers to 3/2 inch. 44.5 mm refers to 7/4 inch. 50.8 mm refers to 2 inches. 63.5 mm refers to 5/2 inches.
  • Table 1 shows the pipe diameters of the secondary side gas connecting pipe 42 and the secondary side liquid connecting pipe 41 in the refrigerant cycle system 100 using carbon dioxide as the refrigerant. ing.
  • the pipe diameter of the secondary side gas connecting pipe 42 is 7.9 mm. This pipe diameter is smaller than the pipe diameter of 9.5 mm of the gas connecting pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side gas connecting pipe 42 is 9.5 mm. This pipe diameter is smaller than the pipe diameter of 12.7 mm of the gas connecting pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side gas connecting pipe 42 is 12.7 mm. This pipe diameter is smaller than the pipe diameter of 15.9 mm of the gas connecting pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe 41 is 4.8 mm. This pipe diameter is smaller than the pipe diameter of 6.4 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe 41 is 6.4 mm. This pipe diameter is smaller than the pipe diameter of 7.9 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • the diameter of the secondary side liquid connecting pipe 41 is 7.9 mm. This pipe diameter is smaller than the pipe diameter of 9.5 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe 41 is 9.5 mm. This pipe diameter is smaller than the pipe diameter of 12.7 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • Table 2 shows the pipe diameters of the secondary side gas connecting pipe 42 and the secondary side liquid connecting pipe 41 in the refrigerant cycle system 100 using R32 as the refrigerant. ..
  • the pipe diameter of the secondary side gas connecting pipe 42 is 15.9 mm. This pipe diameter is smaller than the pipe diameter of 19.1 mm of the gas connecting pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe 41 is 4.8 mm. This pipe diameter is smaller than the pipe diameter of 6.4 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe is 7.9 mm. This pipe diameter is smaller than the pipe diameter of 9.5 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe is 9.5 mm. This pipe diameter is smaller than the pipe diameter of 12.7 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • Table 3 shows the pipe diameters of the secondary side gas connecting pipe 42 and the secondary side liquid connecting pipe 41 in the refrigerant cycle system 100 using R454B as the refrigerant. ..
  • the pipe diameter of the secondary side gas connecting pipe 42 is 15.9 mm. This pipe diameter is smaller than the pipe diameter of 19.1 mm of the gas connecting pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side gas connecting pipe 42 is 19.1 mm. This pipe diameter is smaller than the pipe diameter of 22.2 mm of the gas connecting pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe 41 is 9.5 mm. This pipe diameter is smaller than the pipe diameter of 12.7 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe 41 is 12.7 mm. This pipe diameter is smaller than the pipe diameter of 15.9 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • the pipe diameter of the secondary side liquid connecting pipe 41 is 15.9 mm. This pipe diameter is smaller than the pipe diameter of 19.1 mm of the liquid communication pipe in the unit cycle of the same capacity.
  • Table 4 shows the pipe diameters of the secondary side gas connecting pipe 42 and the secondary side liquid connecting pipe 41 in the refrigerant cycle system 100 using R1234yf as the refrigerant. ..
  • Table 5 shows the pipe diameters of the secondary side gas connecting pipe 42 and the secondary side liquid connecting pipe 41 in the refrigerant cycle system 100 using R1234ze as the refrigerant. ..
  • Refrigerant is a Mixed Refrigerant
  • Table 6 shows the secondary side gas communication pipe 42 and the secondary side liquid communication in the refrigerant cycle system 100 using the mixed refrigerant consisting of R32, R1234yf, and R1123 as the refrigerant.
  • the pipe diameter of the pipe 41 is shown.
  • the ratios of R32, R1234yf, and R1123 in the mixed refrigerant are 21.5%, 18.5%, and 60%, respectively.
  • the diameter of the connecting pipe in the secondary cycle 40 is smaller than the diameter of the connecting pipe in the primary side cycle 20. Therefore, since the flow velocity of the refrigerant can be increased in the secondary cycle, the refrigerating machine oil flowing out of the compressor can easily return to the compressor.
  • the pipe diameter of the secondary side gas connecting pipe 42 is 90% or less of the pipe diameter of the primary side gas connecting pipe 22, or the pipe diameter of the secondary side liquid connecting pipe 41 is the pipe diameter of the primary side liquid connecting pipe 21. It may be 90% or less of the pipe diameter.
  • the compression ratio of the secondary cycle 40 may be smaller than the compression ratio of the primary cycle 20.
  • the refrigerant cycle system 100 has one heat source unit 10, one cascade unit 30, and one utilization unit 50.
  • the refrigerant cycle system 100 may have one heat source unit 10, a plurality of cascade units 30, and a plurality of utilization units 50.
  • Heat source unit 13 Heat source heat exchanger 20: Primary side cycle 21: Primary side liquid communication pipe 22: Primary side gas communication pipe 30: Cascade unit 35: Cascade heat exchanger 40: Secondary side cycle 41: Secondary side Liquid communication pipe 42: Secondary gas communication pipe 50: Utilization unit 52: Utilization expansion valve 100: Refrigerator cycle system

Landscapes

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

Abstract

Selon l'invention, un système de cycle de frigorigène (100) est équipé : d'un cycle côté primaire (20) dans lequel circule un premier frigorigène ; d'un cycle côté secondaire (40) dans lequel circule un second frigorigène ; et d'un échangeur de chaleur en cascade (35) effectuant un échange de chaleur entre le premier et le second frigorigène. Le cycle côté primaire (20) possède un tuyau de raccordement côté primaire. Le cycle côté secondaire (40) possède un tuyau de raccordement côté secondaire. Le tuyau de raccordement côté primaire possède un tuyau de raccordement de gaz côté primaire (22) et un tuyau de raccordement de liquide côté primaire (21). Le tuyau de raccordement côté secondaire possède un tuyau de raccordement de gaz côté secondaire (42) et un tuyau de raccordement de liquide côté secondaire (41). Soit, le diamètre du tuyau de raccordement de gaz côté secondaire (42) est inférieur à celui du tuyau de raccordement de gaz côté primaire (22), soit, le diamètre du tuyau de raccordement de liquide côté secondaire (41) est inférieur à celui du tuyau de raccordement de liquide côté primaire (21).
PCT/JP2020/022922 2019-06-12 2020-06-10 Conditionneur d'air WO2020250952A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP20822547.4A EP3978831B1 (fr) 2019-06-12 2020-06-10 Conditionneur d'air
CN202080042764.0A CN113950602B (zh) 2019-06-12 2020-06-10 空调机
US17/618,075 US20220316767A1 (en) 2019-06-12 2020-06-10 Refrigerant cycle system
PL20822547.4T PL3978831T3 (pl) 2019-06-12 2020-06-10 Układ cyklu czynnika chłodniczego
ES20822547T ES2961904T3 (es) 2019-06-12 2020-06-10 Acondicionador de aire

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019-109592 2019-06-12
JP2019109592A JP2020201011A (ja) 2019-06-12 2019-06-12 空調機

Publications (1)

Publication Number Publication Date
WO2020250952A1 true WO2020250952A1 (fr) 2020-12-17

Family

ID=73744006

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/022922 WO2020250952A1 (fr) 2019-06-12 2020-06-10 Conditionneur d'air

Country Status (7)

Country Link
US (1) US20220316767A1 (fr)
EP (1) EP3978831B1 (fr)
JP (1) JP2020201011A (fr)
CN (1) CN113950602B (fr)
ES (1) ES2961904T3 (fr)
PL (1) PL3978831T3 (fr)
WO (1) WO2020250952A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4032194A1 (fr) * 2019-09-16 2022-07-27 Nokia Solutions and Networks Oy Sélection d'antenne pour signaux de liaison montante dans un système de communication sans fil

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6146859A (ja) * 1984-08-13 1986-03-07 株式会社日立製作所 二元冷凍装置
JP2006125762A (ja) * 2004-10-29 2006-05-18 Mitsubishi Heavy Ind Ltd 室内機およびこれを備えた空気調和装置ならびにその運転方法
JP2008209105A (ja) * 2007-02-02 2008-09-11 Daikin Ind Ltd 空気調和装置
JP2009126300A (ja) * 2007-11-21 2009-06-11 Denso Corp 冷凍サイクル装置及びそれを備えた車両用空調装置
JP2012087978A (ja) * 2010-10-19 2012-05-10 Mitsubishi Electric Corp 冷凍装置
WO2013146103A1 (fr) * 2012-03-26 2013-10-03 日立アプライアンス株式会社 Dispositif à cycle de réfrigération
WO2014038028A1 (fr) * 2012-09-06 2014-03-13 三菱電機株式会社 Dispositif de réfrigération
JP2014074508A (ja) 2012-10-02 2014-04-24 Samsung R&D Institute Japan Co Ltd カスケード熱交換器
WO2020004108A1 (fr) * 2018-06-25 2020-01-02 ダイキン工業株式会社 Système de climatisation

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5025634A (en) * 1989-04-25 1991-06-25 Dressler William E Heating and cooling apparatus
JP3327197B2 (ja) * 1997-08-19 2002-09-24 三菱電機株式会社 冷凍空調装置
JP2001248941A (ja) * 1999-12-28 2001-09-14 Daikin Ind Ltd 冷凍装置
BRPI0103786B1 (pt) * 2001-08-29 2015-06-16 Brasil Compressores Sa Sistema de controle de refrigeração de um ambiente refrigerado, método de controle de um sistema de refrigeração e refrigerador
US6557361B1 (en) * 2002-03-26 2003-05-06 Praxair Technology Inc. Method for operating a cascade refrigeration system
WO2005052467A1 (fr) * 2003-11-28 2005-06-09 Mitsubishi Denki Kabushiki Kaisha Congelateur et conditionneur d'air
JP4659521B2 (ja) * 2004-12-08 2011-03-30 三菱電機株式会社 冷凍空調装置、冷凍空調装置の運転方法、冷凍空調装置の製造方法、冷凍装置、冷凍装置の製造方法
JP2008032275A (ja) * 2006-07-27 2008-02-14 Daikin Ind Ltd 空気調和装置
KR100803144B1 (ko) * 2007-03-28 2008-02-14 엘지전자 주식회사 공기조화기
JP2012193908A (ja) * 2011-03-17 2012-10-11 Toshiba Carrier Corp 二元冷凍サイクル装置
US9429347B2 (en) * 2011-08-04 2016-08-30 Mitsubishi Electric Corporation Refrigeration apparatus
EP2910872B1 (fr) * 2012-10-22 2020-03-11 Mitsubishi Electric Corporation Dispositif de congélation
JP2015152240A (ja) * 2014-02-14 2015-08-24 パナソニックＩｐマネジメント株式会社 空気調和機
EP3121541B1 (fr) * 2014-03-17 2021-11-10 Mitsubishi Electric Corporation Dispositif de réfrigération et procédé de commande de dispositif de réfrigération
JP2018115831A (ja) * 2017-01-20 2018-07-26 ダイキン工業株式会社 室内ユニット
US20200378657A1 (en) * 2019-05-31 2020-12-03 Trane International Inc. Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6146859A (ja) * 1984-08-13 1986-03-07 株式会社日立製作所 二元冷凍装置
JP2006125762A (ja) * 2004-10-29 2006-05-18 Mitsubishi Heavy Ind Ltd 室内機およびこれを備えた空気調和装置ならびにその運転方法
JP2008209105A (ja) * 2007-02-02 2008-09-11 Daikin Ind Ltd 空気調和装置
JP2009126300A (ja) * 2007-11-21 2009-06-11 Denso Corp 冷凍サイクル装置及びそれを備えた車両用空調装置
JP2012087978A (ja) * 2010-10-19 2012-05-10 Mitsubishi Electric Corp 冷凍装置
WO2013146103A1 (fr) * 2012-03-26 2013-10-03 日立アプライアンス株式会社 Dispositif à cycle de réfrigération
WO2014038028A1 (fr) * 2012-09-06 2014-03-13 三菱電機株式会社 Dispositif de réfrigération
JP2014074508A (ja) 2012-10-02 2014-04-24 Samsung R&D Institute Japan Co Ltd カスケード熱交換器
WO2020004108A1 (fr) * 2018-06-25 2020-01-02 ダイキン工業株式会社 Système de climatisation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3978831A4

Also Published As

Publication number Publication date
EP3978831B1 (fr) 2023-08-09
EP3978831A4 (fr) 2022-08-03
PL3978831T3 (pl) 2024-04-08
JP2020201011A (ja) 2020-12-17
CN113950602A (zh) 2022-01-18
US20220316767A1 (en) 2022-10-06
ES2961904T3 (es) 2024-03-14
CN113950602B (zh) 2023-08-04
EP3978831A1 (fr) 2022-04-06

Similar Documents

Publication Publication Date Title
EP1944562B1 (fr) Conditionneur d'air
CN101946137B (zh) 制冷剂蒸汽压缩系统
CN107003048B (zh) 空调机
US20160238290A1 (en) Air conditioner
JP2007240025A (ja) 冷凍装置
US10174975B2 (en) Two-phase refrigeration system
US9970693B2 (en) Refrigeration cycle apparatus
US10168069B2 (en) Air-conditioning apparatus
JP2011242048A (ja) 冷凍サイクル装置
US11578898B2 (en) Air conditioning apparatus
JP2006003022A (ja) 冷凍装置及び中間圧レシーバ
JP2015108463A (ja) 熱交換器及び冷凍サイクル装置
WO2020250952A1 (fr) Conditionneur d'air
EP2578966A1 (fr) Dispositif de réfrigération et dispositif de refroidissement et de chauffage
US6422035B1 (en) Heat exchanged system efficiency enhancing device
US20220214082A1 (en) Refrigeration cycle apparatus
JP4468887B2 (ja) 過冷却装置及び過冷却装置を備える空気調和装置
JP2016053473A (ja) 熱交換器及び冷凍サイクル装置
WO2020250953A1 (fr) Conditionneur d'air
JP2007093167A (ja) 空気調和機用液ガス熱交換器
JP7469583B2 (ja) 空調機
US20200326092A1 (en) Air conditioning apparatus
JP2010112618A (ja) 空気調和装置
KR101685846B1 (ko) 공기 조화기
WO2015025414A1 (fr) Dispositif à cycle de réfrigération, et climatiseur et chauffe-eau utilisant le même dispositif à cycle de réfrigération

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20822547

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2020822547

Country of ref document: EP

Effective date: 20211229