US20220316767A1 - Refrigerant cycle system - Google Patents

Refrigerant cycle system Download PDF

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Publication number
US20220316767A1
US20220316767A1 US17/618,075 US202017618075A US2022316767A1 US 20220316767 A1 US20220316767 A1 US 20220316767A1 US 202017618075 A US202017618075 A US 202017618075A US 2022316767 A1 US2022316767 A1 US 2022316767A1
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United States
Prior art keywords
refrigerant
connection pipe
cycle
pipe
pipe diameter
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Pending
Application number
US17/618,075
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English (en)
Inventor
Takuro Yamada
Eiji Kumakura
Atsushi Yoshimi
Ikuhiro Iwata
Tomoatsu Minamida
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Daikin Industries Ltd
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Daikin Industries Ltd
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Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MINAMIDA, TOMOATSU, YOSHIMI, ATSUSHI, IWATA, IKUHIRO, KUMAKURA, EIJI, YAMADA, TAKURO
Publication of US20220316767A1 publication Critical patent/US20220316767A1/en
Pending legal-status Critical Current

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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
    • 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
    • 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
    • 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

  • the present disclosure relates to a refrigerant cycle system including a cascade heat exchanger.
  • a refrigerant cycle system including a cascade heat exchanger.
  • a refrigerant cycle system constitutes a dual refrigerant cycle that includes a primary-side cycle including a heat-source heat exchanger and a secondary-side cycle including a usage heat exchanger.
  • a refrigerant cycle system includes a vapor compression primary-side cycle that circulates a first refrigerant, a vapor compression secondary-side cycle that circulates a second refrigerant, and a cascade heat exchanger that exchanges heat between the first refrigerant and the second refrigerant.
  • the primary-side cycle includes a heat-source heat exchanger for giving cold or heat to the first refrigerant, and a primary-side connection pipe that connects the cascade heat exchanger and the heat-source heat exchanger.
  • the secondary-side cycle includes a usage heat exchanger for using the cold or the heat obtained by the second refrigerant from the cascade heat exchanger, and a secondary-side connection pipe that connects the cascade heat exchanger and the usage heat exchanger.
  • the primary-side connection pipe includes a primary-side gas connection pipe and a primary-side liquid connection pipe.
  • the secondary-side connection pipe includes a secondary-side gas connection pipe and a secondary-side liquid connection pipe.
  • the pipe diameter of the secondary-side gas connection pipe is smaller than the pipe diameter of the primary-side gas connection pipe, or the pipe diameter of the secondary-side liquid connection pipe is smaller than the pipe diameter of the primary-side liquid connection pipe.
  • the pipe diameter of the connection pipe in the secondary-side cycle is smaller than the pipe diameter of the connection pipe in the primary-side cycle. Consequently, it is possible to increase the flow speed of refrigerant in the secondary-side cycle. Therefore, a refrigerating-machine oil that has flowed out from the compressor easily returns to the compressor.
  • the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary-side cycle is 4.5 kW or more and 5.6 kW or less.
  • the pipe diameter of the secondary-side gas connection pipe is 7.9 mm ( 5/16 inches).
  • the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary-side cycle is 7.1 kW or more and 9.0 kW or less.
  • the pipe diameter of the secondary-side gas connection pipe is 9.5 mm (3 ⁇ 8 inches).
  • the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary-side cycle is 16 kW or more and 22.4 kW or less.
  • the pipe diameter of the secondary-side gas connection pipe is 12.7 mm (1 ⁇ 2 inches).
  • the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary-side cycle is 5.6 kW or more and 8.0 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 4.8 mm ( 3/16 inches).
  • the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary-side cycle is 11.2 kW or more and 16 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 6.4 mm (1 ⁇ 4 inches).
  • the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary-side cycle is 16 kW or more and 28 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 7.9 mm ( 5/16 inches).
  • the second refrigerant is carbon dioxide.
  • the refrigerating capacity of the secondary-side cycle is 33.5 kW or more and 45 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 9.5 mm (3 ⁇ 8 inches).
  • the second refrigerant is R32.
  • the refrigerating capacity of the secondary-side cycle is 16 kW or more and 22.4 kW or less.
  • the pipe diameter of the secondary-side gas connection pipe is 15.9 mm (5 ⁇ 8 inches).
  • the second refrigerant is R32.
  • the refrigerating capacity of the secondary-side cycle is 2.8 kW or more and 3.6 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 4.8 mm ( 3/16 inches).
  • the second refrigerant is R32.
  • the refrigerating capacity of the secondary-side cycle is 14 kW or more and 16 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 7.9 mm ( 5/16 inches).
  • the second refrigerant is R32.
  • the refrigerating capacity of the secondary-side cycle is 28 kW or more and 33.5 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 9.5 mm (3 ⁇ 8 inches).
  • the second refrigerant is R454B.
  • the refrigerating capacity of the secondary-side cycle is 9.0 kW or more and 11.2 kW or less.
  • the pipe diameter of the secondary-side gas connection pipe is 15.9 mm (5 ⁇ 8 inches).
  • the second refrigerant is R454B.
  • the refrigerating capacity of the secondary-side cycle is 16.0 kW or more and 22.4 kW or less.
  • the pipe diameter of the secondary-side gas connection pipe is 19.1 mm (3 ⁇ 4 inches).
  • the second refrigerant is R454B.
  • the refrigerating capacity of the secondary-side cycle is 16 kW or more and 22.4 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 9.5 mm (3 ⁇ 8 inches).
  • the second refrigerant is R454B.
  • the refrigerating capacity of the secondary-side cycle is 45 kW or more and 56 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 12.7 mm (1 ⁇ 2 inches).
  • the second refrigerant is R454B.
  • the refrigerating capacity of the secondary-side cycle is 85 kW or more and 109 kW or less.
  • the pipe diameter of the secondary-side liquid connection pipe is 15.9 mm (5 ⁇ 8 inches).
  • the pipe diameter of the secondary-side gas connection pipe is less than or equal to 90% of the pipe diameter of the primary-side gas connection pipe, or the pipe diameter of the secondary-side liquid connection pipe is less than or equal to 90% of the pipe diameter of the primary-side liquid connection pipe.
  • a compression ratio of the secondary-side cycle is smaller than a compression ratio of the primary-side cycle.
  • FIG. 1 is a view illustrating a refrigerant cycle system 100 according to a first embodiment.
  • FIG. 1 illustrates a refrigerant cycle system 100 .
  • the refrigerant cycle system 100 is configured to acquire cold or heat from a heat source and supply the cold or the heat to a user.
  • the “acquire cold from a heat source” means releasing heat to the heat source.
  • the “acquire heat from a heat source” means absorbing heat from the heat source.
  • the “supply the cold to a user” means absorbing heat from an environment in which the user is present.
  • the “supply heat to a user” means releasing heat into an environment in which the user is present.
  • the refrigerant cycle system 100 includes one heat source unit 10 , one cascade unit 30 , and one usage unit 50 .
  • the heat source unit 10 and the cascade unit 30 are connected to each other to configure a primary-side cycle 20 .
  • the primary-side cycle 20 is a vapor compression circuit that circulates a first refrigerant.
  • the cascade unit 30 and the usage unit 50 are connected to each other to configure a secondary-side cycle 40 .
  • the secondary-side cycle 40 is a vapor compression circuit that circulates a second refrigerant.
  • the first refrigerant and the second refrigerant may be the same refrigerant and may be different refrigerants.
  • the heat source unit 10 acquires cold or heat from outside air that 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 subcooling expansion valve 15 , a subcooling heat exchanger 16 , a liquid shutoff valve 18 , and a gas shutoff valve 19 .
  • the compressor 11 sucks and compresses low-pressure gas refrigerant that is the first refrigerant and discharges high-pressure gas refrigerant.
  • the four-way switching valve 12 makes connection indicated by the solid lines in FIG. 1 during cooling operation and makes connection indicated by the broken lines in FIG. 1 during heating operation.
  • the heat-source heat exchanger 13 exchanges heat between the first refrigerant and outside air.
  • the heat-source heat exchanger 13 functions as a condenser during cooling operation and functions as an evaporator during heating operation.
  • the heat-source expansion valve 14 adjusts the flow rate of the first refrigerant.
  • the heat-source expansion valve 14 also functions as a decompression device that decompresses the first refrigerant.
  • the subcooling expansion valve 15 produces cooling gas by decompressing the first refrigerant that circulates.
  • the subcooling heat exchanger 16 exchanges heat between the first refrigerant that circulates and the cooling gas, thereby giving a degree of subcooling to the first refrigerant.
  • the liquid shutoff valve 18 and the gas shutoff valve 19 shut off a flow path in which the first refrigerant circulates, for example, during work of installation of the heat source unit 10 .
  • the cascade unit 30 is configured to exchange 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 shutoff valve 38 , and a gas shutoff valve 39 .
  • the primary-side expansion valve 31 adjusts the amount of the first refrigerant that circulates in the primary-side cycle 20 .
  • the primary-side expansion valve 31 also decompresses the first refrigerant.
  • the secondary-side expansion valve 32 adjusts the amount of the second refrigerant that circulates in the secondary-side cycle 40 .
  • the secondary-side expansion valve 32 also decompresses the second refrigerant.
  • the compressor 33 sucks and compresses low-pressure gas refrigerant that is the second refrigerant and discharges high-pressure gas refrigerant.
  • the four-way switching valve 34 functions as a switching device and makes connection indicated by the solid lines in FIG. 1 during cooling operation and connection indicated by the broken lines in FIG. 1 during 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 includes a first refrigerant passage 351 and a second refrigerant passage 352 .
  • the first refrigerant passage 351 allows the first refrigerant to pass therethrough.
  • the second refrigerant passage 352 allows the second refrigerant to pass therethrough.
  • the cascade heat exchanger 35 functions as an evaporator for the first refrigerant and a condenser for the second refrigerant during cooling operation and functions as an evaporator for the first refrigerant and a condenser for the second refrigerant during heating operation.
  • the liquid shutoff valve 38 and the gas shutoff valve 39 shut off a flow path in which the second refrigerant circulates, for example, during work of installation of the cascade unit 30 .
  • the usage unit 50 is configured to supply cold or heat to a user.
  • the usage unit 50 includes a usage heat exchanger 51 and a usage expansion valve 52 .
  • the usage heat exchanger 51 is configured to cause cold or heat to be used by a user.
  • the usage heat exchanger 51 is a microchannel heat exchanger and includes a flat multi-hole pipe.
  • the usage expansion valve 52 adjusts the amount of the second refrigerant that circulates in the secondary-side cycle 40 .
  • the usage expansion valve 52 also functions as a decompression device that decompresses the second refrigerant.
  • a primary-side connection pipe includes a primary-side liquid connection pipe 21 and a primary-side gas connection pipe 22 .
  • the primary-side liquid connection pipe 21 connects the liquid shutoff valve 18 of the heat source unit 10 and the cascade unit 30 .
  • the primary-side gas connection pipe 22 connects the gas shutoff valve 19 of the heat source unit 10 and the cascade unit 30 .
  • a secondary-side connection pipe includes a secondary-side liquid connection pipe 41 and a secondary-side gas connection pipe 42 .
  • the secondary-side liquid connection pipe 41 connects the liquid shutoff valve 38 of the cascade unit 30 and the usage unit 50 .
  • the secondary-side gas connection pipe 42 connects the gas shutoff valve 39 of the cascade unit 30 and the usage unit 50 .
  • the compressor 11 sucks low-pressure gas refrigerant that is the first refrigerant and discharges high-pressure gas refrigerant.
  • the high-pressure gas refrigerant reaches the heat-source heat exchanger 13 via the four-way switching valve 12 .
  • the heat-source heat exchanger 13 condenses the high-pressure gas refrigerant and thereby produces high-pressure liquid refrigerant.
  • the refrigerant that is the first refrigerant releases heat into outside air.
  • the high-pressure liquid refrigerant passes through the heat-source expansion valve 14 that is full opened, passes through the subcooling heat exchanger 16 , and reaches the primary-side expansion valve 31 via the liquid shutoff valve 18 and the primary-side liquid connection pipe 21 .
  • the primary-side expansion valve 31 whose opening degree is appropriately set decompresses the high-pressure liquid refrigerant and thereby produces 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 and thereby produces 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 connection pipe 22 and the gas shutoff valve 19 , and is sucked by the compressor 11 via the four-way switching valve 12 .
  • a portion of the high-pressure liquid refrigerant that has exited the heat-source expansion valve 14 is decompressed by the subcooling expansion valve 15 whose opening degree is appropriately set, and becomes gas-liquid two-phase cooling gas.
  • the cooling gas passes through the subcooling heat exchanger 16 . At this time, the cooling gas cools the high-pressure liquid refrigerant and thereby gives a degree of subcooling.
  • the cooling gas exits the subcooling heat exchanger 16 , mixes with the low-pressure gas refrigerant that comes from the four-way switching valve 12 , and is sucked by the compressor 11 .
  • the compressor 33 sucks low-pressure gas refrigerant that is the second refrigerant and discharges 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 and thereby produces high-pressure liquid refrigerant.
  • the second refrigerant releases heat into the first refrigerant.
  • the high-pressure liquid refrigerant exits the second refrigerant passage 352 and reaches the secondary-side expansion valve 32 .
  • the secondary-side expansion valve 32 whose opening degree is appropriately set decompresses the high-pressure liquid refrigerant and thereby produces low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant passes through the liquid shutoff valve 38 and the secondary-side liquid connection pipe 41 and reaches the usage expansion valve 52 .
  • the usage expansion valve 52 whose opening degree is appropriately set further reduces the pressure of the low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant reaches the usage heat exchanger 51 .
  • the usage heat exchanger 51 evaporates the low-pressure gas-liquid two-phase refrigerant and thereby produces low-pressure gas refrigerant.
  • the refrigerant that is the second refrigerant absorbs heat from an environment in which a user is present.
  • the low-pressure gas refrigerant exits the usage heat exchanger 51 , passes through the secondary-side gas connection pipe 42 and the gas shutoff valve 39 , and is sucked by the compressor 33 via the four-way switching valve 12 .
  • the compressor 11 sucks low-pressure gas refrigerant that is the first refrigerant and discharges high-pressure gas refrigerant.
  • the high-pressure gas refrigerant passes through the gas shutoff valve 19 and the primary-side gas connection pipe 22 via the four-way switching valve 12 and enters the first refrigerant passage 351 of the cascade heat exchanger 35 .
  • the cascade heat exchanger 35 condenses the high-pressure gas refrigerant and thereby produces high-pressure liquid refrigerant. At this time, the first refrigerant releases heat into the second refrigerant.
  • the high-pressure liquid refrigerant passes through the primary-side expansion valve 31 that is full opened, then passes through the primary-side liquid connection pipe 21 , the liquid shutoff valve 18 , and the subcooling heat exchanger 16 , and reaches the heat-source expansion valve 14 .
  • the heat-source expansion valve 14 whose opening degree is appropriately set decompresses the high-pressure liquid refrigerant and thereby produces 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 and thereby produces low-pressure gas refrigerant.
  • the refrigerant that is the first refrigerant absorbs heat from outside air.
  • the low-pressure gas refrigerant passes through the four-way switching valve 12 and is sucked by the compressor 11 .
  • the compressor 33 sucks low-pressure gas refrigerant that is the second refrigerant and discharges high-pressure gas refrigerant.
  • the high-pressure gas refrigerant passes through the gas shutoff valve 39 and the secondary-side gas connection pipe 42 via the four-way switching valve 34 and reaches the usage heat exchanger 51 .
  • the usage heat exchanger 51 condenses the high-pressure gas refrigerant and thereby produces high-pressure liquid refrigerant.
  • the refrigerant that is the second refrigerant releases heat into an environment in which a user is present.
  • the high-pressure liquid refrigerant reaches the usage expansion valve 52 .
  • the usage expansion valve 52 whose opening degree is appropriately set decompresses the high-pressure liquid refrigerant and thereby produces low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant passes through the secondary-side liquid connection pipe 41 and the liquid shutoff valve 38 and reaches the secondary-side expansion valve 32 .
  • the secondary-side expansion valve 32 whose opening degree is appropriately set 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 and thereby produces low-pressure gas refrigerant. At this time, 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 by the compressor 33 .
  • Examples of the pipe diameter of the secondary-side connection pipe are presented in Table 1 to Table 6.
  • values of a capacity that should be achieved are indicated in different units.
  • pipe diameters of the gas connection pipe and the liquid connection pipe that are required to achieve the capacity indicated by “REFRIGERATING CAPACITY” in a single cycle are indicated.
  • pipe diameters of the secondary-side gas connection pipe 42 and the secondary-side liquid connection pipe 41 that are required to achieve the capacity indicated by “REFRIGERATING CAPACITY” in a dual cycle are indicated.
  • the pipe diameter of the primary-side gas connection pipe 22 and the primary-side liquid connection pipe 21 in the dual cycle are the same as those indicated in the field of the “SINGLE”.
  • the values indicated in millimeter unit in the tables indicate pipes that are manufactured according to a standard based on inch unit. That is, the value 4.8 mm indicates 3/16 inches. The value 6.4 mm indicates 1 ⁇ 4 inches. The value 7.9 mm indicates 5/16 inches. The value 9.5 mm indicates 3 ⁇ 8 inches. The value 12.7 mm indicates 1 ⁇ 2 inches. The value 15.9 mm indicates 5 ⁇ 8 inches. The value 19.1 mm indicates 3 ⁇ 4 inches. The value 22.2 mm indicates 7 ⁇ 8 inches. The value 25.4 mm indicates 1 inch. The value 28.6 mm indicates 9/8 inches. The value 31.8 mm indicates 5/4 inches. The value 38.1 mm indicates 3/2 inches. The value 44.5 mm indicates 7/4 inches. The value 50.8 mm indicates 2 inches. The value 63.5 mm indicates 5/2 inches.
  • the pipe diameter of the secondary-side gas connection pipe 42 is 7.9 mm. This pipe diameter is smaller than the pipe diameter 9.5 mm of a gas connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side gas connection pipe 42 is 9.5 mm. This pipe diameter is smaller than the pipe diameter 12.7 mm of a gas connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side gas connection pipe 42 is 12.7 mm. This pipe diameter is smaller than the pipe diameter 15.9 mm of a gas connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 4.8 mm. This pipe diameter is smaller than the pipe diameter 6.4 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 6.4 mm. This pipe diameter is smaller than the pipe diameter 7.9 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 7.9 mm. This pipe diameter is smaller than the pipe diameter 9.5 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 9.5 mm. This pipe diameter is smaller than the pipe diameter 12.7 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side gas connection pipe 42 is 15.9 mm. This pipe diameter is smaller than the pipe diameter 19.1 mm of a gas connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 4.8 mm. This pipe diameter is smaller than the pipe diameter 6.4 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe is 7.9 mm. This pipe diameter is smaller than the pipe diameter 9.5 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe is 9.5 mm. This pipe diameter is smaller than the pipe diameter 12.7 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side gas connection pipe 42 is 15.9 mm. This pipe diameter is smaller than the pipe diameter 19.1 mm of a gas connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side gas connection pipe 42 is 19.1 mm. This pipe diameter is smaller than the pipe diameter 22.2 mm of a gas connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 9.5 mm. This pipe diameter is smaller than the pipe diameter 12.7 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 12.7 mm. This pipe diameter is smaller than the pipe diameter 15.9 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the secondary-side liquid connection pipe 41 is 15.9 mm. This pipe diameter is smaller than the pipe diameter 19.1 mm of a liquid connection pipe in a single cycle having the same capacity.
  • the pipe diameter of the connection pipe in the secondary-side cycle 40 is smaller than the pipe diameter of the connection pipe in the primary-side cycle 20 . Consequently, it is possible to increase the flow speed of refrigerant in the secondary-side cycle. Therefore, a refrigerating-machine oil that has flowed out from the compressor easily returns to the compressor.
  • the pipe diameter of the secondary-side gas connection pipe 42 may be less than or equal to 90% of the pipe diameter of the primary-side gas connection pipe 22 , or the pipe diameter of the secondary-side liquid connection pipe 41 may be less than or equal to 90% of the pipe diameter of the primary-side liquid connection pipe 21 .
  • the compression ratio of the secondary-side cycle 40 may be smaller than the compression ratio of the primary-side cycle 20 .
  • the refrigerant cycle system 100 includes the one heat source unit 10 , the one cascade unit 30 , and the one usage unit 50 .
  • the refrigerant cycle system 100 may include the one heat source unit 10 , a plurality of the cascade units 30 , and a plurality of the usage units 50 .

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  • 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)
US17/618,075 2019-06-12 2020-06-10 Refrigerant cycle system Pending US20220316767A1 (en)

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JP2019109592A JP2020201011A (ja) 2019-06-12 2019-06-12 空調機
PCT/JP2020/022922 WO2020250952A1 (ja) 2019-06-12 2020-06-10 空調機

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EP3978831B1 (en) 2023-08-09
PL3978831T3 (pl) 2024-04-08
CN113950602B (zh) 2023-08-04
CN113950602A (zh) 2022-01-18
EP3978831A1 (en) 2022-04-06

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