WO2022211077A1 - Refrigeration cycle device - Google Patents
Refrigeration cycle device Download PDFInfo
- Publication number
- WO2022211077A1 WO2022211077A1 PCT/JP2022/016797 JP2022016797W WO2022211077A1 WO 2022211077 A1 WO2022211077 A1 WO 2022211077A1 JP 2022016797 W JP2022016797 W JP 2022016797W WO 2022211077 A1 WO2022211077 A1 WO 2022211077A1
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- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat
- heat exchanger
- utilization
- refrigeration cycle
- Prior art date
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 168
- 239000003507 refrigerant Substances 0.000 claims abstract description 618
- 238000010438 heat treatment Methods 0.000 claims abstract description 89
- 238000001816 cooling Methods 0.000 claims abstract description 81
- 230000009977 dual effect Effects 0.000 claims abstract description 22
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 60
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 30
- 239000001569 carbon dioxide Substances 0.000 claims description 30
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 51
- 230000006870 function Effects 0.000 description 38
- 238000010586 diagram Methods 0.000 description 28
- 239000007788 liquid Substances 0.000 description 26
- 238000001704 evaporation Methods 0.000 description 19
- 238000000034 method Methods 0.000 description 18
- 238000010792 warming Methods 0.000 description 8
- 239000002826 coolant Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000006866 deterioration Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 230000002528 anti-freeze Effects 0.000 description 3
- 239000012267 brine Substances 0.000 description 3
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 3
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 239000003570 air Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
Images
Classifications
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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
- 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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
-
- 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
-
- 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
- F25B2313/004—Outdoor unit with water as a heat sink or heat source
-
- 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
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-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
- 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
- F25B2400/12—Inflammable refrigerants
- F25B2400/121—Inflammable refrigerants using R1234
Definitions
- Patent Document 1 Japanese Patent Application Laid-Open No. 2015-197254
- the refrigerant circuit is filled with a working fluid whose GWP is equal to or less than a predetermined value.
- low-pressure refrigerants that are used at relatively low refrigerant pressures.
- Such a low-pressure refrigerant has a low heat transfer ability and cannot secure a sufficient circulation amount of the refrigerant during heating operation, which makes heating operation difficult or COP (Coefficient Of Performance) during heating operation. tends to be low.
- a dual refrigeration cycle is used to ensure the capacity during heating operation. can be considered.
- the critical pressure of the carbon dioxide refrigerant on the heat source side is exceeded during cooling operation, and the COP during cooling operation becomes low.
- a refrigeration cycle device that can efficiently perform cooling operation and heating operation when using high-pressure refrigerant and low-pressure refrigerant is desired.
- a refrigeration cycle apparatus performs a heating operation by performing a dual refrigeration cycle including a user-side refrigeration cycle using a first refrigerant and a heat source-side refrigeration cycle using a second refrigerant.
- the first refrigerant is 1 MPa or less at 30°C.
- the second refrigerant is 1.5 MPa or more at 30°C.
- the refrigeration cycle device performs cooling operation by performing a unit refrigeration cycle using the first refrigerant.
- a user-side refrigeration cycle using a first refrigerant that is a low-pressure refrigerant of 1 MPa or less at 30° C. and a second refrigerant that is a high-pressure refrigerant of 1.5 MPa or more at 30° C. are used. Since the dual refrigerating cycle including the refrigerating cycle on the heat source side is performed, it is easy to secure the heating capacity while improving the COP.
- this refrigerating cycle since a unit refrigerating cycle using the first refrigerant, which is a low-pressure refrigerant of 1 MPa or less at 30° C., is performed during cooling operation, a dual refrigerating cycle using the second refrigerant in the refrigerating cycle on the heat source side. , it is possible to avoid a decrease in COP due to the second refrigerant exceeding the critical pressure. As a result, it is possible to efficiently perform the cooling operation and the heating operation when using the high-pressure refrigerant and the low-pressure refrigerant.
- the refrigerating cycle device includes the cascade heat exchanger in the refrigerating cycle device according to the first aspect.
- the cascade heat exchanger has a first cascade flow path and a second cascade flow path.
- the first cascade channel is a channel through which the first refrigerant flows during heating operation.
- the second cascade flow path is a flow path independent of the first cascade flow path, and is a flow path for flowing the second refrigerant during heating operation.
- a cascade heat exchanger allows heat exchange between the first refrigerant and the second refrigerant.
- the refrigeration cycle device is the refrigeration cycle device according to the second aspect, and includes a utilization heat exchanger.
- the utilization heat exchanger the first refrigerant releases heat during heating operation.
- the first refrigerant evaporates when passing through the first cascade flow path, and heat is released when the second refrigerant passes through the second cascade flow path.
- the first refrigerant may be condensed in the utilization heat exchanger during heating operation.
- the utilization heat exchanger is preferably a heat exchanger that processes a heat load, and the refrigerant flowing through the utilization heat exchanger may exchange heat with air, or may exchange heat with a fluid such as brine or water. may be
- a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the first to third aspects, and includes a utilization heat exchanger and a first outdoor heat exchanger.
- the utilization heat exchanger the first refrigerant evaporates during cooling operation.
- the first outdoor heat exchanger the first refrigerant releases heat during cooling operation.
- first refrigerant may be condensed in the first outdoor heat exchanger during cooling operation.
- the first outdoor heat exchanger is not particularly limited, for example, the refrigerant flowing through the first outdoor heat exchanger may be heat-exchanged with air.
- a refrigeration cycle device is the refrigeration cycle device according to any one of the first to fourth aspects, and includes a second outdoor heat exchanger. In the second outdoor heat exchanger, the second refrigerant evaporates during heating operation.
- the second outdoor heat exchanger is not particularly limited, for example, the refrigerant flowing through the second outdoor heat exchanger may be heat-exchanged with the air.
- a refrigeration cycle device performs a heating operation by performing a dual refrigeration cycle including a user-side refrigeration cycle using a first refrigerant and a heat source-side refrigeration cycle using a second refrigerant.
- the first refrigerant is 1 MPa or less at 30°C.
- the second refrigerant is 1.5 MPa or more at 30°C.
- the refrigeration cycle device performs cooling operation by performing a dual refrigeration cycle including a user-side refrigeration cycle using the second refrigerant and a heat source-side refrigeration cycle using the first refrigerant.
- a user-side refrigeration cycle using a first refrigerant that is a low-pressure refrigerant of 1 MPa or less at 30° C. and a second refrigerant that is a high-pressure refrigerant of 1.5 MPa or more at 30° C. are used. Since the dual refrigerating cycle including the refrigerating cycle on the heat source side is performed, it is easy to secure the heating capacity while improving the COP.
- COP due to the second refrigerant exceeding the critical pressure when the second refrigerant is the binary refrigeration cycle used in the refrigeration cycle on the heat source side can be avoided. As a result, it is possible to efficiently perform the cooling operation and the heating operation when using the high-pressure refrigerant and the low-pressure refrigerant.
- the refrigeration cycle device is the refrigeration cycle device according to the sixth aspect, including a cascade heat exchanger.
- the cascade heat exchanger has a first cascade flow path and a second cascade flow path independent of the first cascade flow path.
- the first cascade channel is a channel for flowing the first coolant.
- the second cascade channel is a channel for flowing the second coolant.
- a cascade heat exchanger allows heat exchange between the first refrigerant and the second refrigerant.
- the refrigerating cycle device is the refrigerating cycle device according to the seventh aspect, including a utilization heat exchanger.
- the utilization heat exchanger has a first utilization channel and a second utilization channel independent of the first utilization channel.
- the first use channel is a channel for flowing the first coolant.
- the second use channel is a channel for flowing the second coolant.
- the utilization heat exchanger is preferably a heat exchanger that processes a heat load, and the refrigerant flowing through the utilization heat exchanger may exchange heat with air, or may exchange heat with a fluid such as brine or water. may be
- a refrigerating cycle device is the refrigerating cycle device according to the eighth aspect, wherein during heating operation, the first refrigerant evaporates when passing through the first cascade flow path, and the second refrigerant evaporates in the second cascade flow path. and heat is released when the first coolant passes through the first use channel.
- first refrigerant may be condensed when passing through the first usage flow path during heating operation.
- a refrigerating cycle device is the refrigerating cycle device according to the eighth or ninth aspect, wherein during cooling operation, the first refrigerant evaporates when passing through the first cascade flow path, and the second refrigerant evaporates. Heat is released when passing through the two cascade channels, and the second refrigerant evaporates when passing through the second utilization channel.
- a refrigeration cycle device is the refrigeration cycle device according to any one of the eighth aspect to the tenth aspect.
- the refrigerant evaporates as it passes through the second utilization channel.
- a refrigerating cycle device is the refrigerating cycle device according to any one of the eighth aspect to the eleventh aspect, wherein during heating operation, the first refrigerant radiates heat when passing through the first use channel, Heat is radiated when the refrigerant passes through the second utilization channel.
- first refrigerant may be condensed when passing through the first usage flow path during heating operation.
- a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the sixth to twelfth aspects, including a first outdoor heat exchanger.
- the first refrigerant releases heat during cooling operation.
- first refrigerant may be condensed in the first outdoor heat exchanger during cooling operation.
- the first outdoor heat exchanger is not particularly limited, for example, the refrigerant flowing through the first outdoor heat exchanger may be heat-exchanged with air.
- a refrigeration cycle apparatus is the refrigeration cycle apparatus according to any one of the sixth to thirteenth aspects, and includes a second outdoor heat exchanger. In the second outdoor heat exchanger, the second refrigerant evaporates during heating operation.
- the second outdoor heat exchanger is not particularly limited, for example, the refrigerant flowing through the second outdoor heat exchanger may be heat-exchanged with the air.
- a refrigeration cycle device is the refrigeration cycle device according to any one of the first to fourteenth aspects, wherein the first refrigerant contains at least one of R1234yf and R1234ze.
- the first refrigerant may consist of only R1234yf, or may consist of only R1234ze.
- This refrigeration cycle device can be operated using a refrigerant with a sufficiently low global warming potential (GWP).
- GWP global warming potential
- a refrigeration cycle device is the refrigeration cycle device according to any one of the first to fifteenth aspects, wherein the second refrigerant contains carbon dioxide.
- the second refrigerant may be composed only of carbon dioxide.
- This refrigeration cycle device can be operated using a refrigerant with sufficiently low ozone depletion potential (ODP) and global warming potential (GWP).
- ODP ozone depletion potential
- GWP global warming potential
- FIG. 1 is an overall configuration diagram of a refrigeration cycle apparatus according to a first embodiment;
- FIG. 1 is a functional block configuration diagram of a refrigeration cycle device according to a first embodiment;
- FIG. 4 is a diagram showing how a refrigerant flows during cooling operation in the first embodiment;
- FIG. 4 is a diagram showing how a refrigerant flows during heating operation in the first embodiment;
- It is a whole block diagram of the refrigerating-cycle apparatus which concerns on 2nd Embodiment.
- It is a functional block configuration diagram of a refrigeration cycle apparatus according to a second embodiment.
- FIG. 10 is a diagram showing how a refrigerant flows during cooling operation of the second embodiment;
- FIG. 10 is a diagram showing how a refrigerant flows during cooling operation of the second embodiment;
- FIG. 10 is a diagram showing how a refrigerant flows during heating operation in the second embodiment; It is a whole block diagram of the refrigerating-cycle apparatus which concerns on 3rd Embodiment. It is a functional block configuration diagram of a refrigeration cycle apparatus according to a third embodiment.
- FIG. 11 is a diagram showing how a refrigerant flows during cooling operation in the third embodiment;
- FIG. 11 is a diagram showing how a refrigerant flows during heating operation in the third embodiment;
- It is a whole block diagram of the refrigerating-cycle apparatus which concerns on 4th Embodiment.
- FIG. 11 is a diagram showing how a refrigerant flows during a first cooling operation in the fourth embodiment;
- FIG. 11 is a diagram showing how a refrigerant flows during a second cooling operation of the fourth embodiment;
- FIG. 11 is a diagram showing how a refrigerant flows during a third cooling operation in the fourth embodiment;
- FIG. 11 is a diagram showing how a refrigerant flows during a first heating operation in the fourth embodiment;
- FIG. 11 is a diagram showing how a refrigerant flows during a second heating operation in the fourth embodiment;
- FIG. 11 is a diagram showing how a refrigerant flows during a third heating operation in the fourth embodiment;
- FIG. 1 the schematic block diagram of the refrigerating-cycle apparatus 1 which concerns on 1st Embodiment is shown.
- FIG. 2 shows a functional block configuration diagram of the refrigeration cycle device 1 according to the first embodiment.
- the refrigeration cycle device 1 is a device used to process a heat load by performing vapor compression refrigeration cycle operation.
- the refrigeration cycle device 1 has a heat load circuit 90 , a first refrigerant circuit 10 , a second refrigerant circuit 20 , an outdoor fan 9 and a controller 7 .
- the heat load processed by the refrigeration cycle device 1 is not particularly limited, and heat exchange may be performed with fluids such as air, water, and brine.
- Water flowing through the heat load circuit 90 is supplied to the heat load heat exchanger 91 to process the heat load in the heat load heat exchanger 91 .
- the heat load circuit 90 is a circuit in which water as a heat medium circulates, and includes a heat load heat exchanger 91, a pump 92, and a utilization heat exchanger 13 shared with the first refrigerant circuit 10. is doing.
- the pump 92 circulates water in the heat load circuit 90 by being driven and controlled by the controller 7 to be described later.
- the utilization heat exchanger 13 has a first utilization passage 13a through which the first refrigerant flowing through the first refrigerant circuit 10 passes, as will be described later.
- the water flowing through the heat load channel 13c of the heat utilization exchanger 13 is cooled during the cooling operation and warmed during the heating operation by exchanging heat with the first refrigerant flowing through the first utilization channel 13a.
- the first refrigerant circuit 10 includes a first compressor 11, a first switching mechanism 12, a utilization heat exchanger 13 shared with the heat load circuit 90, a first utilization expansion valve 15, and a second utilization expansion valve 16. , a heat source heat exchanger 17 shared with the second refrigerant circuit 20 , and a first outdoor heat exchanger 18 .
- the first refrigerant circuit 10 is filled with a first refrigerant, which is a low-pressure refrigerant, as a refrigerant.
- the first refrigerant is a refrigerant of 1 MPa or less at 30 ° C., for example, a refrigerant containing at least one of R1234yf and R1234ze. good.
- the first compressor 11 is a positive displacement compressor driven by a compressor motor.
- the compressor motor is driven by being supplied with power through an inverter device.
- the operating capacity of the first compressor 11 can be changed by varying the drive frequency, which is the number of revolutions of the compressor motor.
- a discharge side of the first compressor 11 is connected to a first switching mechanism 12 .
- the suction side of the first compressor 11 is connected to the gas refrigerant side outlet of the first heat source flow path 17 a of the heat source heat exchanger 17 .
- the first switching mechanism 12 has a switching valve 12a and a switching valve 12b.
- the switching valve 12 a and the switching valve 12 b are connected in parallel with each other on the discharge side of the first compressor 11 .
- the switching valve 12 a connects the discharge side of the first compressor 11 and the first utilization passage 13 a of the heat utilization heat exchanger 13 , and the suction side of the first compressor 11 and the first utilization flow path 13 a of the heat utilization heat exchanger 13 . It is a three-way valve that switches between a state in which it is connected to the use channel 13a and a state in which it is connected.
- the switching valve 12b connects the discharge side of the first compressor 11 and the first outdoor heat exchanger 18, and connects the suction side of the first compressor 11 and the first outdoor heat exchanger 18. It is a three-way valve that switches between .
- the gas refrigerant side of the first utilization flow path 13a through which the first refrigerant flowing through the first refrigerant circuit 10 passes in the utilization heat exchanger 13 is connected to the switching valve 12a. Further, the liquid refrigerant side of the first use channel 13 a is connected to the first branch point A of the first refrigerant circuit 10 .
- the first refrigerant can cool the water flowing through the heat load circuit 90 by evaporating while flowing through the first use flow path 13 a of the heat utilization exchanger 13 , and can cool the water flowing through the first use flow path 13 a of the heat utilization heat exchanger 13 . Water flowing through thermal load circuit 90 can be warmed by condensing as it flows through path 13a.
- a flow path extending from the liquid refrigerant side of the first utilization flow path 13a, a flow path extending on the side opposite to the heat source heat exchanger 17 side of the first utilization expansion valve 15, and a second utilization flow path 13a and a channel extending from the expansion valve 16 to the side opposite to the first outdoor heat exchanger 18 side are connected.
- the first utilization expansion valve 15 is composed of an electronic expansion valve whose opening degree can be adjusted.
- the first utilization expansion valve 15 is provided in the first refrigerant circuit 10 between the first branch point A and the liquid refrigerant side inlet of the first heat source flow path 17 a of the heat source heat exchanger 17 . .
- the second utilization expansion valve 16 is composed of an electronic expansion valve whose opening degree can be adjusted.
- the second utilization expansion valve 16 is provided in the first refrigerant circuit 10 between the first branch point A and the liquid refrigerant side outlet of the first outdoor heat exchanger 18 .
- the heat source heat exchanger 17 includes a first heat source flow path 17a through which the first refrigerant flowing through the first refrigerant circuit 10 passes, and a second heat source flow path 17b through which the second refrigerant flowing through the second refrigerant circuit 20 passes. and a cascade heat exchanger for heat exchange between the first refrigerant and the second refrigerant.
- the first heat source passage 17a and the second heat source passage 17b are independent of each other, and the first refrigerant and the second refrigerant do not mix.
- the outlet, which is the gas refrigerant side, of the first heat source flow path 17 a of the heat source heat exchanger 17 is connected to the suction side of the first compressor 11 .
- the inlet, which is the liquid refrigerant side, of the first heat source flow path 17 a of the heat source heat exchanger 17 is connected to the first utilization expansion valve 15 .
- the first outdoor heat exchanger 18 is configured with a plurality of heat transfer tubes and a plurality of fins joined to the plurality of heat transfer tubes.
- the first outdoor heat exchanger 18 is arranged outdoors.
- the first refrigerant flowing through the first outdoor heat exchanger 18 exchanges heat with the air sent to the first outdoor heat exchanger 18, thereby functioning as a condenser for the first refrigerant.
- the outdoor fan 9 generates an air flow of outdoor air that passes through both the first outdoor heat exchanger 18 and the second outdoor heat exchanger 23.
- the second refrigerant circuit 20 has a second compressor 21, a heat source heat exchanger 17 shared with the first refrigerant circuit 10, a first heat source expansion valve 26, and a second outdoor heat exchanger 23. ing.
- the second refrigerant circuit 20 is filled with a second refrigerant, which is a high-pressure refrigerant, as a refrigerant.
- the second refrigerant is a refrigerant having a pressure of 1.5 MPa or more at 30° C., and may contain, for example, carbon dioxide, or may be composed of only carbon dioxide.
- the second compressor 21 is a positive displacement compressor driven by a compressor motor.
- the compressor motor is driven by being supplied with power through an inverter device.
- the operating capacity of the second compressor 21 can be changed by varying the drive frequency, which is the number of revolutions of the compressor motor.
- the discharge side of the second compressor 21 is connected to the inlet, which is the gas refrigerant side, of the second heat source flow path 17 b of the heat source heat exchanger 17 .
- a suction side of the second compressor 21 is connected to a second outdoor heat exchanger 23 .
- the inlet of the second heat source flow path 17 b of the heat source heat exchanger 17 on the gas refrigerant side is connected to the discharge side of the second compressor 21 .
- the outlet of the second heat source flow path 17 b of the heat source heat exchanger 17 on the liquid refrigerant side is connected to the first heat source expansion valve 26 .
- the first heat source expansion valve 26 is provided in a channel between the liquid refrigerant side of the second heat source channel 17 b of the heat source heat exchanger 17 and the liquid refrigerant side of the second outdoor heat exchanger 23 .
- the second outdoor heat exchanger 23 is configured with a plurality of heat transfer tubes and a plurality of fins joined to the plurality of heat transfer tubes.
- the second outdoor heat exchanger 23 is arranged outdoors alongside the first outdoor heat exchanger 18 .
- the second refrigerant flowing through the second outdoor heat exchanger 23 exchanges heat with the air sent to the second outdoor heat exchanger 23, thereby functioning as an evaporator for the second refrigerant.
- the controller 7 controls the operation of each device that constitutes the heat load circuit 90 , the first refrigerant circuit 10 and the second refrigerant circuit 20 .
- the controller 7 has a processor as a CPU provided for control, a memory, and the like.
- the controller 7 controls each device to execute the refrigeration cycle, thereby performing a cooling operation for processing the cooling load in the thermal load heat exchanger 91 and a heating load in the thermal load heat exchanger 91.
- a heating operation is performed to process the
- Cooling operation During cooling operation, as shown in FIG. A unit refrigerating cycle is performed so as to function as a condenser for the first refrigerant, and the refrigerating cycle is not performed in the second refrigerant circuit 20 .
- the switching valves 12a and 12b of the first switching mechanism 12 are switched to the connected state indicated by solid lines in FIG. is fully closed, and the degree of opening of the second utilization expansion valve 16 is controlled so that the degree of superheat of the first refrigerant sucked into the first compressor 11 satisfies a predetermined condition.
- the first refrigerant discharged from the first compressor 11 is sent to the first outdoor heat exchanger 18 via the switching valve 12b of the first switching mechanism 12.
- the first refrigerant sent to the first outdoor heat exchanger 18 is condensed by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant that has passed through the first outdoor heat exchanger 18 is decompressed in the second utilization expansion valve 16, passes through the first branch point A, and is sent to the first utilization flow path 13a of the utilization heat exchanger 13. .
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 exchanges heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90, thereby evaporating.
- the water cooled by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to process the cooling load.
- the first refrigerant evaporated in the first utilization passage 13 a of the utilization heat exchanger 13 is sucked into the first compressor 11 via the switching valve 12 a of the first switching mechanism 12 .
- FIG. 1 A refrigeration cycle is performed so as to function as an evaporator of the refrigerant, and in the second refrigerant circuit 20, the heat source heat exchanger 17 functions as a radiator for the second refrigerant, and the second outdoor heat exchanger 23 evaporates the second refrigerant.
- a refrigeration cycle is performed so that it functions as a container.
- a dual refrigeration cycle is performed by the second refrigerant circuit 20 and the first refrigerant circuit 10 during the heating operation.
- the switching valves 12a and 12b of the first switching mechanism 12 are switched to the connection state indicated by the broken lines in FIG.
- the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven,
- the second utilization expansion valve 16 is fully closed, the valve opening degree of the first utilization expansion valve 15 is controlled so that the degree of superheat of the first refrigerant sucked by the first compressor 11 satisfies a predetermined condition, and the first heat source is controlled.
- the degree of opening of the expansion valve 26 is controlled so that the degree of superheat of the second refrigerant sucked into the second compressor 21 satisfies a predetermined condition.
- the second refrigerant discharged from the second compressor 21 is sent to the heat source heat exchanger 17, and when flowing through the second heat source flow path 17b, the first refrigerant flowing through the first heat source flow path 17a and the heat Dissipate heat by exchanging.
- the second refrigerant that has released heat in the heat source heat exchanger 17 is decompressed in the first heat source expansion valve 26, and then heat-exchanged with the outdoor air supplied by the outdoor fan 9 in the second outdoor heat exchanger 23 to evaporate. , is sucked into the second compressor 21 .
- the first refrigerant discharged from the first compressor 11 is sent to the first utilization passage 13a of the utilization heat exchanger 13 via the switching valve 12a of the first switching mechanism 12 .
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 is condensed by exchanging heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90 .
- the water warmed by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to treat the heating load.
- the first refrigerant condensed in the first utilization flow path 13 a of the utilization heat exchanger 13 is decompressed in the first utilization expansion valve 15 .
- the refrigerant decompressed by the first utilization expansion valve 15 evaporates by exchanging heat with the second refrigerant flowing through the second heat source passage 17b when passing through the first heat source passage 17a of the heat source heat exchanger 17. .
- the first refrigerant evaporated in the first heat source flow path 17 a of the heat source heat exchanger 17 is sucked into the first compressor 11 .
- the first refrigerant circuit 10 uses a first refrigerant having a sufficiently low global warming potential (GWP).
- the second refrigerant circuit 20 uses a second refrigerant having a sufficiently low ozone depletion potential (ODP) and a sufficiently low global warming potential (GWP). Therefore, deterioration of the global environment can be suppressed.
- GWP global warming potential
- the second refrigerant circuit 20 is used as the heat source side cycle for heating operation, and the first refrigerant circuit A dual refrigeration cycle is performed with 10 as the utilization side cycle.
- GWP global warming potential
- the refrigeration cycle is not performed in the second refrigerant circuit 20, but the unit refrigeration cycle is performed by the first refrigerant circuit 10 during cooling operation.
- the pressure of the carbon dioxide refrigerant becomes the critical pressure as in the case of performing a single refrigeration cycle using carbon dioxide refrigerant, which is a high-pressure refrigerant, or when performing a dual refrigeration cycle using carbon dioxide, which is a high-pressure refrigerant, in the heat source side cycle.
- the cooling operation can be performed while avoiding the COP from exceeding and becoming low.
- FIG. 5 shows a schematic block diagram of the refrigerating-cycle apparatus 1a which concerns on 2nd Embodiment.
- FIG. 6 shows a functional block configuration diagram of a refrigeration cycle device 1a according to the second embodiment.
- the refrigeration cycle device 1a is a device used to process a heat load by performing vapor compression refrigeration cycle operation.
- the refrigerating cycle device 1 a has a heat load circuit 90 , a first refrigerant circuit 10 , a second refrigerant circuit 20 , an outdoor fan 9 and a controller 7 .
- the heat load processed by the refrigeration cycle device 1a and the heat load circuit 90 are the same as in the first embodiment.
- the utilization heat exchanger 13 includes a heat load flow path 13c through which water flowing through the heat load circuit 90 passes, a first utilization flow path 13a through which the first refrigerant flowing through the first refrigerant circuit 10 passes, a second refrigerant and a second utilization channel 13b through which the second refrigerant flowing through the circuit 20 passes.
- Water flowing through the heat load flow path 13c of the heat utilization heat exchanger 13 is cooled during cooling operation by exchanging heat with the first refrigerant flowing through the first utilization flow path 13a or the second refrigerant flowing through the second utilization flow path 13b. and warmed during heating operation.
- the first refrigerant circuit 10 includes a first compressor 11, a first switching mechanism 12x, a utilization heat exchanger 13 shared by the thermal load circuit 90 and the second refrigerant circuit 20, a second utilization expansion valve 16, It has a third utilization expansion valve 14 , a heat source heat exchanger 17 shared with the second refrigerant circuit 20 , and a first outdoor heat exchanger 18 .
- the first refrigerant circuit 10 is filled with a first refrigerant, which is a low-pressure refrigerant, as a refrigerant.
- the first refrigerant is a refrigerant of 1 MPa or less at 30 ° C., for example, a refrigerant containing at least one of R1234yf and R1234ze. good.
- the specific configuration of the first compressor 11 itself is the same as that of the first embodiment.
- the discharge side of the first compressor 11 is connected to the first switching mechanism 12x.
- the suction side of the first compressor 11 is connected to the gas refrigerant side outlet of the first heat source flow path 17 a of the heat source heat exchanger 17 .
- the first switching mechanism 12x connects the discharge side of the first compressor 11 and the first utilization flow path 13a of the heat utilization heat exchanger 13 while connecting the suction side of the first compressor 11 and the first outdoor heat exchanger 18. and connecting the discharge side of the first compressor 11 and the first outdoor heat exchanger 18 while connecting the suction side of the first compressor 11 and the first utilization flow path 13a of the utilization heat exchanger 13. It is a four-way switching valve that switches between the state of
- the gas refrigerant side of the first use flow path 13a through which the first refrigerant flowing through the first refrigerant circuit 10 passes in the use heat exchanger 13 is connected to the first switching mechanism 12x.
- a channel extending from the third use expansion valve 14 is connected to the liquid refrigerant side of the first use channel 13a.
- the first refrigerant is condensed while flowing through the first utilization channel 13 a of the heat utilization exchanger 13 , thereby warming the water flowing through the heat load circuit 90 .
- the third utilization expansion valve 14 is composed of an electronic expansion valve whose opening degree can be adjusted.
- the third utilization expansion valve 14 is provided between the utilization heat exchanger 13 and the first branch point A in the first refrigerant circuit 10 .
- a flow path extending from the third utilization expansion valve 14, a flow path extending from the liquid refrigerant side of the first heat source flow path 17a in the heat source heat exchanger 17, and a flow path extending from the second utilization expansion valve 16 to the first and a channel extending in the opposite direction to the outdoor heat exchanger 18 side are connected.
- the second utilization expansion valve 16 is the same as that of the first embodiment.
- the heat source heat exchanger 17 is the same as that of the first embodiment.
- the outlet, which is the gas refrigerant side, of the first heat source flow path 17 a of the heat source heat exchanger 17 is connected to the suction side of the first compressor 11 .
- the inlet, which is the liquid refrigerant side, of the first heat source flow path 17a of the heat source heat exchanger 17 is connected to the first branch point A. As shown in FIG.
- the first outdoor heat exchanger 18 is the same as that of the first embodiment.
- the outdoor fan 9 generates an air flow of outdoor air that passes through both the first outdoor heat exchanger 18 and the second outdoor heat exchanger 23.
- the second refrigerant circuit 20 includes a second compressor 21, a utilization heat exchanger 13 shared with the heat load circuit 90 and the second refrigerant circuit 20, and a heat source heat exchanger 17 shared with the first refrigerant circuit 10. , a first heat source expansion valve 26 , a second heat source expansion valve 24 , and a second outdoor heat exchanger 23 .
- the second refrigerant circuit 20 is filled with a second refrigerant, which is a high-pressure refrigerant, as a refrigerant.
- the second refrigerant is a refrigerant having a pressure of 1.5 MPa or more at 30° C., and may contain, for example, carbon dioxide, or may be composed of only carbon dioxide.
- the specific configuration of the second compressor 21 itself is the same as that of the first embodiment.
- the discharge side of the second compressor 21 is connected to the inlet, which is the gas refrigerant side, of the second heat source flow path 17 b of the heat source heat exchanger 17 .
- a suction side of the second compressor 21 is connected to a flow path extending from the third branch point C in the second refrigerant circuit 20 .
- the flow path extending from the suction side of the second compressor 21, the flow path extending from the outlet on the gas refrigerant side of the second outdoor heat exchanger 23, and the second utilization heat exchanger 13 and the flow path extending from the outlet on the gas refrigerant side of the flow path 13b are connected.
- the inlet of the second heat source flow path 17 b of the heat source heat exchanger 17 on the gas refrigerant side is connected to the discharge side of the second compressor 21 .
- An outlet on the liquid refrigerant side of the second heat source flow path 17 b of the heat source heat exchanger 17 is connected to a flow path extending from the second branch point B in the second refrigerant circuit 20 .
- the second refrigerant radiates heat when flowing through the second heat source passage 17b of the heat source heat exchanger 17, thereby evaporating the first refrigerant flowing through the first heat source passage 17a.
- the first heat source expansion valve 26 is provided in the flow path between the second branch point B and the liquid refrigerant side inlet of the second outdoor heat exchanger 23 .
- the second outdoor heat exchanger 23 is the same as that of the first embodiment.
- the second heat source expansion valve 24 is provided in the flow path between the second branch point B and the liquid refrigerant side inlet of the second utilization flow path 13 b of the heat utilization exchanger 13 .
- the second use flow path 13b through which the second refrigerant flowing through the second refrigerant circuit 20 passes in the use heat exchanger 13 is provided in the flow path between the second heat source expansion valve 24 and the third branch point C. there is The second refrigerant can cool the water flowing through the heat load circuit 90 by evaporating while flowing through the second utilization channel 13 b of the heat utilization exchanger 13 .
- the controller 7 controls the operation of each device that constitutes the heat load circuit 90 , the first refrigerant circuit 10 and the second refrigerant circuit 20 .
- the controller 7 has a processor as a CPU provided for control, a memory, and the like.
- the controller 7 controls each device to execute the refrigeration cycle, thereby performing a cooling operation for processing the cooling load in the thermal load heat exchanger 91 and a heating load in the thermal load heat exchanger 91.
- a heating operation is performed to process the
- (2-1) Cooling operation During cooling operation, as shown in FIG. 7, in the first refrigerant circuit 10, the first outdoor heat exchanger 18 functions as a condenser for the first refrigerant, and the heat source heat exchanger 17 While performing the refrigeration cycle so as to function as an evaporator for the first refrigerant, in the second refrigerant circuit 20, the heat source heat exchanger 17 functions as a radiator for the second refrigerant, and the utilization heat exchanger 13 functions as a radiator for the second refrigerant.
- a dual refrigeration cycle is performed by performing a refrigeration cycle so as to function as an evaporator. Specifically, the first switching mechanism 12x is switched to the connected state indicated by solid lines in FIG. is fully closed, and the first heat source expansion valve 26 is fully closed. The opening degree of the second heat source expansion valve 24 is controlled so that the degree of superheat of the second refrigerant sucked into the second compressor 21 satisfies a predetermined condition.
- the first refrigerant discharged from the first compressor 11 is sent to the first outdoor heat exchanger 18 via the first switching mechanism 12x.
- the first refrigerant sent to the first outdoor heat exchanger 18 is condensed by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant that has passed through the first outdoor heat exchanger 18 is decompressed in the second utilization expansion valve 16, passes through the first branch point A, and is sent to the first heat source flow path 17a of the heat source heat exchanger 17. .
- the first refrigerant flowing through the first heat source flow path 17a of the heat source heat exchanger 17 evaporates by exchanging heat with the second refrigerant flowing through the second heat source flow path 17b of the heat source heat exchanger 17 .
- the first refrigerant evaporated in the first heat source flow path 17 a of the heat source heat exchanger 17 is sucked into the first compressor 11 .
- the second refrigerant discharged from the second compressor 21 is sent to the second heat source flow path 17b of the heat source heat exchanger 17.
- the second refrigerant flowing through the second heat source passage 17b of the heat source heat exchanger 17 exchanges heat with the first refrigerant flowing through the first heat source passage 17a of the heat source heat exchanger 17 to radiate heat.
- the second refrigerant that has passed through the second heat source flow path 17 b of the heat source heat exchanger 17 passes through the second branch point B, is depressurized in the second heat source expansion valve 24 , and flows into the heat utilization heat exchanger 13 .
- the second refrigerant flowing through the second utilization channel 13b of the heat utilization exchanger 13 exchanges heat with water flowing through the heat load flow channel 13c of the utilization heat exchanger 13 of the heat load circuit 90, thereby evaporating.
- the water cooled by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to process the cooling load.
- the second refrigerant that has passed through the second utilization channel 13b of the utilization heat exchanger 13 is sucked into the second compressor 21 .
- FIG. 2 Heating operation During heating operation, as shown in FIG. A refrigeration cycle is performed so as to function as an evaporator of the refrigerant, and in the second refrigerant circuit 20, the heat source heat exchanger 17 functions as a radiator for the second refrigerant, and the second outdoor heat exchanger 23 evaporates the second refrigerant. A refrigeration cycle is performed so that it functions as a container. As a result, a dual refrigeration cycle is performed by the second refrigerant circuit 20 and the first refrigerant circuit 10 during the heating operation. Specifically, the first switching mechanism 12x is switched to the connected state indicated by the dashed line in FIG.
- the second heat source expansion valve 24 is fully closed, and the degree of opening of the third utilization expansion valve 14 is adjusted so that the degree of superheat of the first refrigerant sucked into the first compressor 11 satisfies a predetermined condition.
- the opening degree of the first heat source expansion valve 26 is controlled so that the degree of superheat of the second refrigerant sucked into the second compressor 21 satisfies a predetermined condition.
- the second refrigerant discharged from the second compressor 21 is sent to the heat source heat exchanger 17, and when flowing through the second heat source flow path 17b, the first refrigerant flowing through the first heat source flow path 17a and the heat Dissipate heat by exchanging.
- the second refrigerant that has released heat in the heat source heat exchanger 17 passes through the second branch point B, is decompressed in the first heat source expansion valve 26, and is supplied in the second outdoor heat exchanger 23 by the outdoor fan 9. It evaporates by exchanging heat with outdoor air and is sucked into the second compressor 21 .
- the first refrigerant discharged from the first compressor 11 is sent to the first utilization channel 13a of the utilization heat exchanger 13 via the first switching mechanism 12x.
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 is condensed by exchanging heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90 .
- the water warmed by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to treat the heating load.
- the first refrigerant condensed in the first utilization flow path 13 a of the heat utilization exchanger 13 is decompressed in the third utilization expansion valve 14 .
- the first refrigerant decompressed in the third utilization expansion valve 14 passes through the second heat source flow path 17b when passing through the first heat source flow path 17a of the heat source heat exchanger 17. It evaporates by exchanging heat with the flowing second refrigerant.
- the first refrigerant evaporated in the first heat source flow path 17 a of the heat source heat exchanger 17 is sucked into the first compressor 11 .
- the dual refrigeration cycle is also performed during the cooling operation, but instead of dissipating heat from the carbon dioxide refrigerant, which is the second refrigerant, in the second outdoor heat exchanger 23, the carbon dioxide refrigerant, which is the second refrigerant, is Instead of evaporating the refrigerant and condensing the first refrigerant, the heat source heat exchanger 17 evaporates the first refrigerant by radiating heat from the carbon dioxide refrigerant, which is the second refrigerant. Evaporation at 13 handles the cooling load. Therefore, the pressure of the carbon dioxide refrigerant exceeds the critical pressure and the COP is lowered by performing the cooling operation using the carbon dioxide refrigerant in the cycle on the heat source side of the binary refrigeration cycle. It can be carried out. In addition, it is possible to lower the standard of pressure resistance strength required for element parts of the second refrigerant circuit 20 in which carbon dioxide, which is a high-pressure refrigerant, is used.
- FIG. 9 the schematic block diagram of the refrigerating-cycle apparatus 1b which concerns on 3rd Embodiment is shown.
- FIG. 10 shows a functional block configuration diagram of a refrigeration cycle device 1b according to the third embodiment.
- the refrigeration cycle device 1b is a device used to process a heat load by performing vapor compression refrigeration cycle operation.
- the refrigeration cycle device 1 b has a heat load circuit 90 , a first refrigerant circuit 10 , a second refrigerant circuit 20 , an outdoor fan 9 and a controller 7 .
- the heat load processed by the refrigeration cycle device 1b and the heat load circuit 90 are the same as in the first embodiment.
- the utilization heat exchanger 13 includes a heat load flow path 13c through which water flowing through the heat load circuit 90 passes, a first utilization flow path 13a through which the first refrigerant flowing through the first refrigerant circuit 10 passes, a second refrigerant and a second utilization channel 13b through which the second refrigerant flowing through the circuit 20 passes.
- Water flowing through the heat load flow path 13c of the heat utilization heat exchanger 13 is cooled during cooling operation by exchanging heat with the first refrigerant flowing through the first utilization flow path 13a or the second refrigerant flowing through the second utilization flow path 13b. and warmed during heating operation.
- the first refrigerant circuit 10 includes a first compressor 11, a first switching mechanism 12, a utilization heat exchanger 13 shared by the thermal load circuit 90 and the second refrigerant circuit 20, a first utilization expansion valve 15, It has a second use expansion valve 16 , a third use expansion valve 14 , a heat source heat exchanger 17 shared with the second refrigerant circuit 20 , and a first outdoor heat exchanger 18 .
- the first refrigerant circuit 10 is filled with a first refrigerant, which is a low-pressure refrigerant, as a refrigerant.
- the first refrigerant is a refrigerant of 1 MPa or less at 30 ° C., for example, a refrigerant containing at least one of R1234yf and R1234ze. good.
- the specific configuration of the first compressor 11 itself is the same as that of the first embodiment.
- a discharge side of the first compressor 11 is connected to a first switching mechanism 12 .
- the suction side of the first compressor 11 is connected to the gas refrigerant side outlet of the first heat source flow path 17 a of the heat source heat exchanger 17 .
- the first switching mechanism 12 has a switching valve 12a and a switching valve 12b.
- the switching valve 12 a and the switching valve 12 b are connected in parallel with each other on the discharge side of the first compressor 11 .
- the switching valve 12 a connects the discharge side of the first compressor 11 and the first utilization passage 13 a of the heat utilization heat exchanger 13 , and the suction side of the first compressor 11 and the first utilization flow path 13 a of the heat utilization heat exchanger 13 . It is a three-way valve that switches between a state in which it is connected to the utilization channel 13a and a state in which it is connected.
- the switching valve 12b connects the discharge side of the first compressor 11 and the first outdoor heat exchanger 18, and connects the suction side of the first compressor 11 and the first outdoor heat exchanger 18. It is a three-way valve that switches between .
- the gas refrigerant side of the first use flow path 13 a through which the first refrigerant flowing through the first refrigerant circuit 10 passes in the use heat exchanger 13 is connected to the switching valve 12 a of the first switching mechanism 12 .
- a channel extending from the third use expansion valve 14 is connected to the liquid refrigerant side of the first use channel 13a.
- the first refrigerant is condensed while flowing through the first utilization channel 13 a of the heat utilization exchanger 13 , thereby warming the water flowing through the heat load circuit 90 .
- the third utilization expansion valve 14 is composed of an electronic expansion valve whose opening degree can be adjusted.
- the third utilization expansion valve 14 is provided between the utilization heat exchanger 13 and the first branch point A in the first refrigerant circuit 10 .
- the flow path extending from the third utilization expansion valve 14, the flow path extending from the first utilization expansion valve 15, and the side opposite to the first outdoor heat exchanger 18 side from the second utilization expansion valve 16 is connected to the flow path extending to the
- the first utilization expansion valve 15 is the same as that of the first embodiment.
- the second utilization expansion valve 16 is the same as that of the first embodiment.
- the heat source heat exchanger 17 is the same as that of the first embodiment.
- the outlet, which is the gas refrigerant side, of the first heat source flow path 17 a of the heat source heat exchanger 17 is connected to the suction side of the first compressor 11 .
- the inlet, which is the liquid refrigerant side, of the first heat source flow path 17 a of the heat source heat exchanger 17 is connected to the flow path extending from the first utilization expansion valve 15 .
- the first outdoor heat exchanger 18 is the same as that of the first embodiment.
- the outdoor fan 9 generates an air flow of outdoor air that passes through both the first outdoor heat exchanger 18 and the second outdoor heat exchanger 23.
- the second refrigerant circuit 20 includes a second compressor 21, a utilization heat exchanger 13 shared with the heat load circuit 90 and the second refrigerant circuit 20, and a heat source heat exchanger 17 shared with the first refrigerant circuit 10. , a first heat source expansion valve 26 , a second heat source expansion valve 24 , and a second outdoor heat exchanger 23 .
- the second refrigerant circuit 20 is filled with a second refrigerant, which is a high-pressure refrigerant, as a refrigerant.
- the second refrigerant is a refrigerant having a pressure of 1.5 MPa or more at 30° C., and may contain, for example, carbon dioxide, or may be composed of only carbon dioxide.
- the specific configuration of the second compressor 21 itself is the same as that of the first embodiment.
- the discharge side of the second compressor 21 is connected to the inlet, which is the gas refrigerant side, of the second heat source flow path 17 b of the heat source heat exchanger 17 .
- a suction side of the second compressor 21 is connected to a flow path extending from the third branch point C in the second refrigerant circuit 20 .
- the flow path extending from the suction side of the second compressor 21, the flow path extending from the outlet on the gas refrigerant side of the second outdoor heat exchanger 23, and the second utilization heat exchanger 13 and the flow path extending from the outlet on the gas refrigerant side of the flow path 13b are connected.
- the inlet of the second heat source flow path 17 b of the heat source heat exchanger 17 on the gas refrigerant side is connected to the discharge side of the second compressor 21 .
- An outlet on the liquid refrigerant side of the second heat source flow path 17 b of the heat source heat exchanger 17 is connected to a flow path extending from the second branch point B in the second refrigerant circuit 20 .
- the second refrigerant radiates heat when flowing through the second heat source passage 17b of the heat source heat exchanger 17, thereby evaporating the first refrigerant flowing through the first heat source passage 17a.
- the first heat source expansion valve 26 is provided in the flow path between the second branch point B and the liquid refrigerant side inlet of the second outdoor heat exchanger 23 .
- the second outdoor heat exchanger 23 is the same as that of the first embodiment.
- the second heat source expansion valve 24 is provided in the flow path between the second branch point B and the liquid refrigerant side inlet of the second utilization flow path 13 b of the heat utilization exchanger 13 .
- the second use flow path 13b through which the second refrigerant flowing through the second refrigerant circuit 20 passes in the use heat exchanger 13 is provided in the flow path between the second heat source expansion valve 24 and the third branch point C. there is The second refrigerant can cool the water flowing through the heat load circuit 90 by evaporating while flowing through the second utilization channel 13 b of the heat utilization exchanger 13 .
- the controller 7 controls the operation of each device that constitutes the heat load circuit 90 , the first refrigerant circuit 10 and the second refrigerant circuit 20 .
- the controller 7 has a processor as a CPU provided for control, a memory, and the like.
- the controller 7 controls each device to execute the refrigeration cycle, thereby performing a cooling operation for processing the cooling load in the thermal load heat exchanger 91 and a heating load in the thermal load heat exchanger 91.
- a heating operation is performed to process the
- the first outdoor heat exchanger 18 functions as a condenser for the first refrigerant
- the heat source heat exchanger 17 While performing the refrigeration cycle so as to function as an evaporator for the first refrigerant
- the heat source heat exchanger 17 functions as a radiator for the second refrigerant
- the utilization heat exchanger 13 functions as a radiator for the second refrigerant.
- a dual refrigeration cycle is performed by performing a refrigeration cycle so as to function as an evaporator. Specifically, the switching valves 12a and 12b of the first switching mechanism 12 are switched to the connected state indicated by solid lines in FIG.
- the third utilization expansion valve 14 is fully closed, the first heat source expansion valve 26 is fully closed, and one of the first utilization expansion valve 15 and the second utilization expansion valve 16 is fully opened while the other valve is opened.
- the degree of superheat of the first refrigerant sucked into the first compressor 11 satisfies a predetermined condition
- the valve opening degree of the second heat source expansion valve 24 is controlled to superheat the second refrigerant sucked into the second compressor 21. The degree is controlled so that it satisfies a predetermined condition.
- the first refrigerant discharged from the first compressor 11 is sent to the first outdoor heat exchanger 18 via the switching valve 12b of the first switching mechanism 12.
- the first refrigerant sent to the first outdoor heat exchanger 18 is condensed by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant that has passed through the first outdoor heat exchanger 18 is decompressed in the second use expansion valve 16 and passes through the first branch point A, or after passing through the first branch point A, the first use expansion valve 15 , and sent to the first heat source flow path 17 a of the heat source heat exchanger 17 .
- the first refrigerant flowing through the first heat source flow path 17a of the heat source heat exchanger 17 evaporates by exchanging heat with the second refrigerant flowing through the second heat source flow path 17b of the heat source heat exchanger 17 .
- the first refrigerant evaporated in the first heat source flow path 17 a of the heat source heat exchanger 17 is sucked into the first compressor 11 .
- the second refrigerant discharged from the second compressor 21 is sent to the second heat source flow path 17b of the heat source heat exchanger 17.
- the second refrigerant flowing through the second heat source passage 17b of the heat source heat exchanger 17 exchanges heat with the first refrigerant flowing through the first heat source passage 17a of the heat source heat exchanger 17 to radiate heat.
- the second refrigerant that has passed through the second heat source flow path 17 b of the heat source heat exchanger 17 passes through the second branch point B, is depressurized in the second heat source expansion valve 24 , and flows into the heat utilization heat exchanger 13 .
- the second refrigerant flowing through the second utilization channel 13b of the heat utilization exchanger 13 exchanges heat with water flowing through the heat load flow channel 13c of the utilization heat exchanger 13 of the heat load circuit 90, thereby evaporating.
- the water cooled by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to process the cooling load.
- the second refrigerant that has passed through the second utilization channel 13b of the utilization heat exchanger 13 is sucked into the second compressor 21 .
- (3-2) Heating operation During heating operation, as shown in FIG. A refrigeration cycle is performed so as to function as an evaporator of the refrigerant, and in the second refrigerant circuit 20, the heat source heat exchanger 17 functions as a radiator for the second refrigerant, and the second outdoor heat exchanger 23 evaporates the second refrigerant.
- a refrigeration cycle is performed so that it functions as a container.
- a dual refrigeration cycle is performed by the second refrigerant circuit 20 and the first refrigerant circuit 10 during the heating operation. Specifically, the switching valves 12a and 12b of the first switching mechanism 12 are switched to the connection state indicated by the dashed lines in FIG.
- the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven,
- the second utilization expansion valve 16 is fully closed,
- the second heat source expansion valve 24 is fully closed, and the valve opening degree of the third utilization expansion valve 14 or the first utilization expansion valve 15 is sucked into the first compressor 11.
- the degree of superheat of the first refrigerant is controlled so as to satisfy a predetermined condition, and the degree of opening of the first heat source expansion valve 26 is controlled so that the degree of superheat of the second refrigerant sucked into the second compressor 21 satisfies the predetermined condition. .
- the second refrigerant discharged from the second compressor 21 is sent to the heat source heat exchanger 17, and when flowing through the second heat source flow path 17b, the first refrigerant flowing through the first heat source flow path 17a and the heat Dissipate heat by exchanging.
- the second refrigerant that has released heat in the heat source heat exchanger 17 passes through the second branch point B, is decompressed in the first heat source expansion valve 26, and is supplied in the second outdoor heat exchanger 23 by the outdoor fan 9. It evaporates by exchanging heat with outdoor air and is sucked into the second compressor 21 .
- the first refrigerant discharged from the first compressor 11 is sent to the first utilization passage 13a of the utilization heat exchanger 13 via the switching valve 12a of the first switching mechanism 12 .
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 is condensed by exchanging heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90 .
- the water warmed by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to treat the heating load.
- the first refrigerant condensed in the first utilization flow path 13a of the utilization heat exchanger 13 passes through the first branch point A after being decompressed in the third utilization expansion valve 14, or after passing through the first branch point A
- the pressure is reduced in the first utilization expansion valve 15 .
- the first refrigerant that has passed through the first branch point A evaporates by exchanging heat with the second refrigerant that flows through the second heat source flow path 17b when passing through the first heat source flow path 17a of the heat source heat exchanger 17. .
- the first refrigerant evaporated in the first heat source flow path 17 a of the heat source heat exchanger 17 is sucked into the first compressor 11 .
- the refrigerating cycle device 1b of the present embodiment can suppress the deterioration of the global environment, as with the refrigerating cycle device 1 of the first embodiment. easy to secure.
- the dual refrigeration cycle is also performed during the cooling operation, but instead of dissipating heat from the carbon dioxide refrigerant, which is the second refrigerant, in the second outdoor heat exchanger 23, the carbon dioxide refrigerant, which is the second refrigerant, is Instead of evaporating the refrigerant and condensing the first refrigerant, the heat source heat exchanger 17 evaporates the first refrigerant by radiating heat from the carbon dioxide refrigerant, which is the second refrigerant.
- Evaporation at 13 handles the cooling load. Therefore, the pressure of the carbon dioxide refrigerant exceeds the critical pressure and the COP is lowered by performing the cooling operation using the carbon dioxide refrigerant in the cycle on the heat source side of the binary refrigeration cycle. It can be carried out. In addition, it is possible to lower the standard of pressure resistance strength required for element parts of the second refrigerant circuit 20 in which carbon dioxide, which is a high-pressure refrigerant, is used.
- FIG. 13 shows a schematic configuration diagram of a refrigeration cycle apparatus 1c according to a fourth embodiment.
- FIG. 14 shows a functional block configuration diagram of a refrigeration cycle device 1c according to the fourth embodiment.
- the refrigeration cycle device 1c is a device used to process a heat load by performing vapor compression refrigeration cycle operation.
- the refrigeration cycle device 1 c has a heat load circuit 90 , a first refrigerant circuit 10 , a second refrigerant circuit 20 , an outdoor fan 9 and a controller 7 .
- the heat load processed by the refrigeration cycle device 1c and the heat load circuit 90 are the same as in the first embodiment.
- the utilization heat exchanger 13 includes a heat load flow path 13c through which water flowing through the heat load circuit 90 passes, a first utilization flow path 13a through which the first refrigerant flowing through the first refrigerant circuit 10 passes, a second refrigerant and a second utilization channel 13b through which the second refrigerant flowing through the circuit 20 passes.
- the water flowing through the heat load flow path 13c of the heat utilization exchanger 13 exchanges heat with the first refrigerant flowing through the first utilization flow path 13a and/or the second refrigerant flowing through the second utilization flow path 13b. It is sometimes cooled and warmed during heating operation.
- the first refrigerant circuit 10 includes a first compressor 11, a first switching mechanism 12, a utilization heat exchanger 13 shared by the thermal load circuit 90 and the second refrigerant circuit 20, a first utilization expansion valve 15, It has a second use expansion valve 16 , a third use expansion valve 14 , a heat source heat exchanger 17 shared with the second refrigerant circuit 20 , and a first outdoor heat exchanger 18 .
- the first refrigerant circuit 10 is filled with a first refrigerant, which is a low-pressure refrigerant, as a refrigerant.
- the first refrigerant is a refrigerant of 1 MPa or less at 30 ° C., for example, a refrigerant containing at least one of R1234yf and R1234ze. good.
- the specific configuration of the first compressor 11 itself is the same as that of the first embodiment.
- the discharge side and the suction side of the first compressor 11 are connected to different connection points of the first switching mechanism 12, respectively.
- the first switching mechanism 12 has a switching valve 12a, a switching valve 12b, and a switching valve 12c.
- the switching valve 12 a , the switching valve 12 b and the switching valve 12 c are connected in parallel with each other on the discharge side of the first compressor 11 .
- the switching valve 12 a connects the discharge side of the first compressor 11 and the first utilization passage 13 a of the heat utilization heat exchanger 13 , and the suction side of the first compressor 11 and the first utilization flow path 13 a of the heat utilization heat exchanger 13 . It is a three-way valve that switches between a state in which it is connected to the use channel 13a and a state in which it is connected.
- the switching valve 12b connects the discharge side of the first compressor 11 and the first outdoor heat exchanger 18, and connects the suction side of the first compressor 11 and the first outdoor heat exchanger 18. It is a three-way valve that switches between .
- the switching valve 12 c connects the discharge side of the first compressor 11 and the first heat source flow path 17 a of the heat source heat exchanger 17 , and the suction side of the first compressor 11 and the first heat source heat exchanger 17 . It is a three-way valve that switches between a state in which it is connected to the heat source channel 17a and a state in which it is connected.
- the gas refrigerant side of the first use flow path 13 a through which the first refrigerant flowing through the first refrigerant circuit 10 passes in the use heat exchanger 13 is connected to the switching valve 12 a of the first switching mechanism 12 .
- a channel extending from the third use expansion valve 14 is connected to the liquid refrigerant side of the first use channel 13a.
- the first refrigerant can cool the water flowing through the heat load circuit 90 by evaporating while flowing through the first use flow path 13 a of the heat utilization exchanger 13 , and can cool the water flowing through the first use flow path 13 a of the heat utilization heat exchanger 13 . Water flowing through thermal load circuit 90 can be warmed by condensing as it flows through path 13a.
- the third utilization expansion valve 14 is composed of an electronic expansion valve whose opening degree can be adjusted.
- the third utilization expansion valve 14 is provided between the utilization heat exchanger 13 and the first branch point A in the first refrigerant circuit 10 .
- the flow path extending from the third utilization expansion valve 14, the flow path extending from the first utilization expansion valve 15, and the side opposite to the first outdoor heat exchanger 18 side from the second utilization expansion valve 16 is connected to the flow path extending to the
- the first utilization expansion valve 15 is the same as that of the first embodiment.
- the second utilization expansion valve 16 is the same as that of the first embodiment.
- the heat source heat exchanger 17 is the same as that of the first embodiment.
- An outlet on the gas refrigerant side of the first heat source flow path 17 a of the heat source heat exchanger 17 is connected to the switching valve 12 c of the first switching mechanism 12 .
- the inlet, which is the liquid refrigerant side, of the first heat source flow path 17 a of the heat source heat exchanger 17 is connected to the flow path extending from the first utilization expansion valve 15 .
- the first outdoor heat exchanger 18 is the same as that of the first embodiment.
- the outdoor fan 9 generates an air flow of outdoor air that passes through both the first outdoor heat exchanger 18 and the second outdoor heat exchanger 23.
- the second refrigerant circuit 20 is shared with the second compressor 21 , the second switching mechanism 22 , the heat load circuit 90 and the heat utilization heat exchanger 13 shared with the second refrigerant circuit 20 , and the first refrigerant circuit 10 .
- the second refrigerant circuit 20 is filled with a second refrigerant, which is a high-pressure refrigerant, as a refrigerant.
- the second refrigerant is a refrigerant having a pressure of 1.5 MPa or more at 30° C., and may contain, for example, carbon dioxide, or may be composed of only carbon dioxide.
- the specific configuration of the second compressor 21 itself is the same as that of the first embodiment.
- the discharge side and the suction side of the second compressor 21 are connected to different connection points of the second switching mechanism 22, respectively.
- the second switching mechanism 22 has a switching valve 22a, a switching valve 22b, and a switching valve 22c.
- the switching valve 22 a , the switching valve 22 b and the switching valve 22 c are connected in parallel with each other on the discharge side of the second compressor 21 .
- the switching valve 22 a connects the discharge side of the second compressor 21 and the second utilization flow path 13 b of the heat utilization heat exchanger 13 , and the suction side of the second compressor 21 and the second utilization flow path 13 b of the heat utilization heat exchanger 13 . It is a three-way valve that switches between a state in which it is connected to the utilization channel 13b and a state in which it is connected.
- the switching valve 22b connects the discharge side of the second compressor 21 and the second outdoor heat exchanger 23, and connects the suction side of the second compressor 21 and the second outdoor heat exchanger 23. It is a three-way valve that switches between .
- the switching valve 22 c connects the discharge side of the second compressor 21 and the second heat source flow path 17 b of the heat source heat exchanger 17 , and the suction side of the second compressor 21 and the second heat source heat exchanger 17 . It is a three-way valve that switches between a state in which it is connected to the heat source channel 17b and a state in which it is connected.
- the inlet on the gas refrigerant side of the second heat source flow path 17 b of the heat source heat exchanger 17 is connected to the switching valve 22 c of the second switching mechanism 22 .
- An outlet on the liquid refrigerant side of the second heat source flow path 17 b of the heat source heat exchanger 17 is connected to a flow path extending from the third heat source expansion valve 25 .
- the second refrigerant radiates heat when flowing through the second heat source passage 17b of the heat source heat exchanger 17, thereby evaporating the first refrigerant flowing through the first heat source passage 17a.
- the flow path extending from the third heat source expansion valve 25 the flow path extending from the first heat source expansion valve 26, and the flow path extending from the second heat source expansion valve 24 are connected.
- the first heat source expansion valve 26 is provided in the flow path between the second branch point B and the liquid refrigerant side inlet of the second outdoor heat exchanger 23 .
- the second outdoor heat exchanger 23 is the same as that of the first embodiment.
- the second heat source expansion valve 24 is provided in the flow path between the second branch point B and the liquid refrigerant side inlet of the second utilization flow path 13 b of the heat utilization exchanger 13 .
- the second use flow path 13b through which the second refrigerant flowing through the second refrigerant circuit 20 passes in the use heat exchanger 13 is a flow path between the second heat source expansion valve 24 and the switching valve 22a of the second switching mechanism 22.
- the second refrigerant can cool the water flowing through the heat load circuit 90 by evaporating while flowing through the second use flow path 13 b of the heat utilization exchanger 13 , and can cool the water flowing through the second use flow path 13 b of the heat utilization heat exchanger 13 .
- the water flowing through the thermal load circuit 90 can be warmed by releasing heat while flowing through the path 13b.
- the controller 7 controls the operation of each device that constitutes the heat load circuit 90 , the first refrigerant circuit 10 and the second refrigerant circuit 20 .
- the controller 7 has a processor as a CPU provided for control, a memory, and the like.
- the controller 7 controls each device to execute the refrigeration cycle, thereby performing a cooling operation for processing the cooling load in the thermal load heat exchanger 91 and a heating load in the thermal load heat exchanger 91.
- a heating operation is performed to process the
- Cooling Operation During the cooling operation, a first cooling operation, a second cooling operation, and a third cooling operation are selectively performed.
- the first outdoor heat exchanger 18 functions as a condenser for the first refrigerant
- the utilization heat exchanger 13 functions as an evaporator for the first refrigerant.
- the unitary refrigerating cycle is performed by stopping the second compressor 21 in the second refrigerant circuit 20 .
- the switching valves 12a, 12b, and 12c of the first switching mechanism 12 are switched to the connected state indicated by solid lines in FIG.
- the valve 16 is fully opened, the first utilization expansion valve 15 is fully closed, and the degree of opening of the third utilization expansion valve 14 is controlled so that the degree of superheat of the first refrigerant sucked into the first compressor 11 satisfies a predetermined condition. control to fill.
- the first refrigerant discharged from the first compressor 11 is sent to the first outdoor heat exchanger 18 via the switching valve 12b of the first switching mechanism 12.
- the first refrigerant sent to the first outdoor heat exchanger 18 is condensed by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant that has passed through the first outdoor heat exchanger 18 passes through the second utilization expansion valve 16 and the first branch point A, is decompressed in the third utilization expansion valve 14, and then flows into the utilization heat exchanger 13. do.
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 exchanges heat with water flowing through the heat load flow channel 13c of the utilization heat exchanger 13 of the heat load circuit 90, thereby evaporating.
- the water cooled by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to process the cooling load.
- the first refrigerant evaporated in the first use channel 13 a is sucked into the first compressor 11 via the switching valve 12 a of the first switching mechanism 12 .
- the second cooling operation is performed when the required temperature of the heat medium flowing through the heat load circuit 90 falls below a predetermined value, increasing the cooling load and causing the unitary refrigeration cycle by the first refrigerant circuit 10 to run out of capacity. .
- This second cooling operation is performed when the temperature required in the heat load circuit 90 is low, particularly in a refrigeration cycle apparatus in which the heat medium flowing through the heat load circuit 90 is antifreeze.
- the first outdoor heat exchanger 18 functions as a condenser for the first refrigerant
- the heat source heat exchanger 17 functions as an evaporator for the first refrigerant.
- the heat source heat exchanger 17 is operated as a radiator for the second refrigerant, and the heat exchanger 13 is operated as an evaporator for the second refrigerant.
- a two-dimensional refrigeration cycle is performed by performing Specifically, the switching valves 12a, 12b, and 12c of the first switching mechanism 12 are switched to the connected state indicated by solid lines in FIG. 16, and the switching valves 22a, 22b, and 22c of the second switching mechanism 22 are indicated by solid lines in FIG. After switching to the connected state, the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven.
- the second use expansion valve 16 is controlled to be fully open, the third use expansion valve 14 is fully closed, and the valve opening degree of the first use expansion valve 15 is adjusted to superheat the first refrigerant sucked by the first compressor 11. The degree is controlled so that it satisfies a predetermined condition. Furthermore, the first heat source expansion valve 26 is controlled to a fully closed state, the third heat source expansion valve 25 is controlled to a fully open state, and the valve opening degree of the second heat source expansion valve 24 is set to the second Control is performed so that the degree of superheat of the refrigerant satisfies a predetermined condition.
- the first refrigerant discharged from the first compressor 11 is sent to the first outdoor heat exchanger 18 via the switching valve 12b of the first switching mechanism 12.
- the first refrigerant sent to the first outdoor heat exchanger 18 is condensed by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant passes through the second utilization expansion valve 16 , is decompressed in the first utilization expansion valve 15 , and then flows into the heat source heat exchanger 17 .
- the first refrigerant flowing through the first heat source passage 17a of the heat source heat exchanger 17 exchanges heat with the second refrigerant flowing through the second heat source passage 17b and evaporates.
- the first refrigerant evaporated in the heat source heat exchanger 17 is sucked into the first compressor 11 via the switching valve 12 c of the first switching mechanism 12 .
- the second refrigerant discharged from the second compressor 21 is sent to the heat source heat exchanger 17 via the switching valve 22 c of the second switching mechanism 22 .
- the second refrigerant flowing through the second heat source channel 17b of the heat source heat exchanger 17 releases heat by exchanging heat with the first refrigerant flowing through the first heat source channel 17a.
- the second refrigerant passes through the third heat source expansion valve 25 , is decompressed by the second heat source expansion valve 24 , and then flows into the utilization heat exchanger 13 .
- the second refrigerant flowing through the second utilization channel 13b of the utilization heat exchanger 13 exchanges heat with the antifreeze flowing through the heat load flow channel 13c of the utilization heat exchanger 13 of the heat load circuit 90, thereby evaporating.
- the antifreeze cooled by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to process the cooling load.
- the second refrigerant evaporated in the heat utilization exchanger 13 is sucked into the second compressor 21 via the switching valve 22 a of the second switching mechanism 22 .
- the third cooling operation is performed when the temperature of the heat medium flowing through the heat load circuit 90 is higher than a predetermined value and the cooling load is large, and when the performance is emphasized rather than the improvement of the operating efficiency. is driving.
- a parallel refrigerating cycle by the first refrigerant circuit 10 and the second refrigerating circuit 20 is performed in order to exhibit the ability rather than performing the original refrigerating cycle.
- the first outdoor heat exchanger 18 functions as a condenser for the first refrigerant
- the utilization heat exchanger 13 functions as an evaporator for the first refrigerant
- the second outdoor heat exchanger 23 functions as a radiator for the second refrigerant
- the utilization heat exchanger 13 functions as an evaporator for the second refrigerant.
- a parallel refrigerating cycle is performed by performing a refrigerating cycle. Specifically, the switching valves 12a, 12b, and 12c of the first switching mechanism 12 are switched to the connected state indicated by solid lines in FIG.
- the switching valves 22a, 22b, and 22c of the second switching mechanism 22 are indicated by solid lines in FIG.
- the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven.
- the second utilization expansion valve 16 is controlled to a fully open state
- the first utilization expansion valve 15 is controlled to a fully closed state
- the valve opening degree of the third utilization expansion valve 14 is set to the first degree of opening for the suction of the first compressor 11 . Control is performed so that the degree of superheat of the refrigerant satisfies a predetermined condition.
- the first heat source expansion valve 26 is controlled to a fully open state
- the third heat source expansion valve 25 is controlled to a fully closed state
- the valve opening degree of the second heat source expansion valve 24 is set to the second Control is performed so that the degree of superheat of the refrigerant satisfies a predetermined condition.
- the first refrigerant discharged from the first compressor 11 is sent to the first outdoor heat exchanger 18 via the switching valve 12b of the first switching mechanism 12.
- the first refrigerant sent to the first outdoor heat exchanger 18 is condensed by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant passes through the second utilization expansion valve 16 , is decompressed in the third utilization expansion valve 14 , and then flows into the utilization heat exchanger 13 .
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 exchanges heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90, thereby evaporating.
- the first refrigerant evaporated in the heat utilization exchanger 13 is sucked into the first compressor 11 via the switching valve 12 a of the first switching mechanism 12 .
- the second refrigerant discharged from the second compressor 21 is sent to the second outdoor heat exchanger 23 via the switching valve 22b of the second switching mechanism 22 .
- the second refrigerant sent to the second outdoor heat exchanger 23 exchanges heat with the outdoor air supplied by the outdoor fan 9 to radiate heat.
- the second refrigerant After passing through the second outdoor heat exchanger 23 , the second refrigerant passes through the first heat source expansion valve 26 , is decompressed in the second heat source expansion valve 24 , and then flows into the utilization heat exchanger 13 .
- the second refrigerant flowing through the second utilization channel 13b of the heat utilization exchanger 13 exchanges heat with water flowing through the heat load flow channel 13c of the utilization heat exchanger 13 of the heat load circuit 90, thereby evaporating.
- the water cooled by exchanging heat with the two refrigerants, the first refrigerant and the second refrigerant is sent to the heat load heat exchanger 91 in the heat load circuit 90 to process the cooling load.
- the second refrigerant evaporated in the heat utilization exchanger 13 is sucked into the second compressor 21 via the switching valve 22 a of the second switching mechanism 22 .
- the first heating operation is performed when the outside air temperature is equal to or higher than a predetermined value.
- the utilization heat exchanger 13 functions as a condenser for the first refrigerant
- the first outdoor heat exchanger 18 functions as an evaporator for the first refrigerant.
- the switching valves 12a and 12b of the first switching mechanism 12 are switched to the connected state indicated by the dashed lines in FIG. is fully opened, the first utilization expansion valve 15 is controlled to be fully closed, and the degree of opening of the second utilization expansion valve 16 is adjusted so that the degree of superheat of the first refrigerant sucked into the first compressor 11 satisfies a predetermined condition. to control.
- the first refrigerant discharged from the first compressor 11 is sent to the first utilization passage 13a of the utilization heat exchanger 13 via the switching valve 12a of the first switching mechanism 12.
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 is condensed by exchanging heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90 .
- the water heated by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to treat the heating load.
- the first refrigerant condensed in the first utilization flow path 13a of the utilization heat exchanger 13 passes through the third utilization expansion valve 14 and the first branch point A, is decompressed in the second utilization expansion valve 16, and then 1 flows into the outdoor heat exchanger 18 .
- the first refrigerant sent to the first outdoor heat exchanger 18 evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant evaporated in the first outdoor heat exchanger 18 is sucked into the first compressor 11 via the switching valve 12b of the first switching mechanism 12 .
- the second heating operation is an operation that is performed when the outside air temperature drops below a predetermined value and the unit refrigeration cycle using the first refrigerant in the first refrigerant circuit 10 cannot ensure the capacity.
- the utilization heat exchanger 13 functions as a condenser for the first refrigerant
- the heat source heat exchanger 17 functions as an evaporator for the first refrigerant.
- the heat source heat exchanger 17 functions as a radiator for the second refrigerant
- the second outdoor heat exchanger 23 functions as an evaporator for the second refrigerant.
- a two-dimensional refrigeration cycle is performed by performing Specifically, the switching valves 12a, 12b, and 12c of the first switching mechanism 12 are switched to the connected state indicated by broken lines in FIG. 19, and the switching valves 22a, 22b, and 22c of the second switching mechanism 22 are indicated by solid lines in FIG.
- the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven.
- the second use expansion valve 16 is controlled to a fully closed state
- the third use expansion valve 14 is controlled to a fully open state
- the valve opening degree of the first use expansion valve 15 is set to the first value for suction of the first compressor 11 . Control is performed so that the degree of superheat of the refrigerant satisfies a predetermined condition.
- the second heat source expansion valve 24 is controlled to a fully closed state
- the third heat source expansion valve 25 is controlled to a fully open state
- the valve opening degree of the first heat source expansion valve 26 is set to the second Control is performed so that the degree of superheat of the refrigerant satisfies a predetermined condition.
- the first refrigerant discharged from the first compressor 11 is sent to the utilization heat exchanger 13 via the switching valve 12 a of the first switching mechanism 12 .
- the first refrigerant flowing through the first utilization channel 13a of the heat utilization exchanger 13 is condensed by exchanging heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90 .
- the water heated by this heat exchange is sent to the heat load heat exchanger 91 in the heat load circuit 90 to treat the heating load.
- the first refrigerant passes through the third utilization expansion valve 14 , is decompressed in the first utilization expansion valve 15 , and then flows into the heat source heat exchanger 17 .
- the first refrigerant flowing through the first heat source passage 17a of the heat source heat exchanger 17 exchanges heat with the second refrigerant flowing through the second heat source passage 17b and evaporates.
- the first refrigerant evaporated in the heat source heat exchanger 17 is sucked into the first compressor 11 via the switching valve 12 c of the first switching mechanism 12 .
- the second refrigerant discharged from the second compressor 21 is sent to the heat source heat exchanger 17 via the switching valve 22 c of the second switching mechanism 22 .
- the second refrigerant flowing through the second heat source channel 17b of the heat source heat exchanger 17 exchanges heat with the first refrigerant flowing through the first heat source channel 17a, thereby releasing heat.
- the second refrigerant After passing through the heat source heat exchanger 17 , the second refrigerant passes through the third heat source expansion valve 25 and is decompressed in the first heat source expansion valve 26 before flowing into the second outdoor heat exchanger 23 .
- the second refrigerant sent to the second outdoor heat exchanger 23 evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the second refrigerant evaporated in the second outdoor heat exchanger 23 is sucked into the second compressor 21 via the switching valve 22b of the second switching mechanism 22 .
- the third heating operation is performed when the temperature of the heat medium flowing through the heat load circuit 90 is lower than a predetermined value and the heating load is large, and when the emphasis is placed on demonstrating the ability rather than improving the operating efficiency. is driving.
- the first refrigerant is used in the refrigeration cycle on the heat source side, which is on the high side
- the second refrigerant is used in the refrigeration cycle on the user side, which is on the low side, rather than the unitary refrigeration cycle using the first refrigerant.
- a parallel refrigerating cycle by the first refrigerant circuit 10 and the second refrigerating circuit 20 is performed in order to exhibit more capacity than the dual refrigerating cycle.
- the third heating operation as shown in FIG.
- the utilization heat exchanger 13 functions as a condenser for the first refrigerant, and the first outdoor heat exchanger 18 functions as an evaporator for the first refrigerant.
- the utilization heat exchanger 13 functions as a radiator for the second refrigerant, and the second outdoor heat exchanger 23 functions as an evaporator for the second refrigerant.
- a parallel refrigerating cycle is performed by performing a refrigerating cycle. Specifically, the switching valves 12a, 12b and 12c of the first switching mechanism 12 are switched to the connected state indicated by broken lines in FIG. 20, and the switching valves 22a and 22c of the second switching mechanism 22 are switched to the connected state indicated by broken lines in FIG.
- the switching valve 22b of the second switching mechanism 22 is switched to the connected state indicated by the solid line in FIG. Then, the third utilization expansion valve 14 is controlled to a fully open state, the first utilization expansion valve 15 is controlled to a fully closed state, and the valve opening degree of the second utilization expansion valve 16 is set to the first degree of opening for suction of the first compressor 11 . Control is performed so that the degree of superheat of the refrigerant satisfies a predetermined condition.
- the second heat source expansion valve 24 is controlled to a fully open state
- the third heat source expansion valve 25 is controlled to a fully closed state
- the valve opening degree of the first heat source expansion valve 26 is set to the second Control is performed so that the degree of superheat of the refrigerant satisfies a predetermined condition.
- the first refrigerant discharged from the first compressor 11 is sent to the utilization heat exchanger 13 via the switching valve 12a of the first switching mechanism 12, and is condensed by exchanging heat with water flowing through the heat load flow path 13c of the utilization heat exchanger 13 of the heat load circuit 90.
- the first refrigerant passes through the third utilization expansion valve 14 and is decompressed in the second utilization expansion valve 16 before flowing into the first outdoor heat exchanger 18 .
- the first refrigerant sent to the first outdoor heat exchanger 18 evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the first refrigerant evaporated in the first outdoor heat exchanger 18 is sucked into the first compressor 11 via the switching valve 12b of the first switching mechanism 12 .
- the second refrigerant discharged from the second compressor 21 is sent to the utilization heat exchanger 13 via the switching valve 22 a of the second switching mechanism 22 .
- the second refrigerant flowing through the second utilization channel 13b of the heat utilization exchanger 13 exchanges heat with water flowing through the heat load flow channel 13c of the heat utilization heat exchanger 13 of the heat load circuit 90, thereby releasing heat.
- the water thus heated by exchanging heat with the two refrigerants, the first refrigerant and the second refrigerant is sent to the heat load heat exchanger 91 in the heat load circuit 90 to process the heating load.
- the second refrigerant that has passed through the utilization heat exchanger 13 passes through the second heat source expansion valve 24 , is decompressed in the first heat source expansion valve 26 , and then flows into the second outdoor heat exchanger 23 .
- the second refrigerant sent to the second outdoor heat exchanger 23 evaporates by exchanging heat with the outdoor air supplied by the outdoor fan 9 .
- the second refrigerant evaporated in the second outdoor heat exchanger 23 is sucked into the second compressor 21 via the switching valve 22b of the second switching mechanism 22 .
- the refrigerating cycle device 1c of the present embodiment can suppress the deterioration of the global environment, as with the refrigerating cycle device 1 of the first embodiment. easy to secure.
- both cooling and heating not only the unitary refrigerating cycle and the dual refrigerating cycle, but also the parallel refrigerating cycle can be performed, so it is possible to secure the capacity according to the situation.
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Abstract
Description
図1に、第1実施形態に係る冷凍サイクル装置1の概略構成図を示す。図2に、第1実施形態に係る冷凍サイクル装置1の機能ブロック構成図を示す。 (1) 1st Embodiment In FIG. 1, the schematic block diagram of the refrigerating-
冷房運転時は、図3に示すように、第1冷媒回路10では、利用熱交換器13を第1冷媒の蒸発器として機能させ、第1室外熱交換器18を第1冷媒の凝縮器として機能させるように単元冷凍サイクルを行い、第2冷媒回路20では冷凍サイクルを行わせない。具体的には、第1切換機構12の切換弁12a、12bを図3に実線で示す接続状態に切り換え、ポンプ92、第1圧縮機11、室外ファン9を駆動させ、第1利用膨張弁15を全閉状態とし、第2利用膨張弁16の弁開度を第1圧縮機11の吸入する第1冷媒の過熱度が所定条件を満たすように制御する。 (1-1) Cooling operation During cooling operation, as shown in FIG. A unit refrigerating cycle is performed so as to function as a condenser for the first refrigerant, and the refrigerating cycle is not performed in the second
暖房運転時は、図4に示すように、第1冷媒回路10では、利用熱交換器13を第1冷媒の凝縮器として機能させ、熱源熱交換器17を第1冷媒の蒸発器として機能させるように冷凍サイクルを行い、第2冷媒回路20では、熱源熱交換器17を第2冷媒の放熱器として機能させ、第2室外熱交換器23を第2冷媒の蒸発器として機能させるように冷凍サイクルを行う。これにより、暖房運転時には、第2冷媒回路20と第1冷媒回路10とで二元冷凍サイクルが行われる。具体的には、第1切換機構12の切換弁12a、12bを図4に破線で示す接続状態に切り換え、ポンプ92、第1圧縮機11、第2圧縮機21、室外ファン9を駆動させ、第2利用膨張弁16を全閉状態とし、第1利用膨張弁15の弁開度を第1圧縮機11の吸入する第1冷媒の過熱度が所定条件を満たすように制御し、第1熱源膨張弁26の弁開度を第2圧縮機21の吸入する第2冷媒の過熱度が所定条件を満たすように制御する。 (1-2) Heating operation During heating operation, as shown in FIG. A refrigeration cycle is performed so as to function as an evaporator of the refrigerant, and in the second
第1実施形態の冷凍サイクル装置1では、第1冷媒回路10において地球温暖化係数(GWP)が十分に低い第1冷媒が用いられている。また、第2冷媒回路20においてオゾン層破壊係数(ODP)および地球温暖化係数(GWP)が十分に低い第2冷媒が用いられている。このため、地球環境の悪化を抑制することができる。 (1-3) Features of First Embodiment In the
図5に、第2実施形態に係る冷凍サイクル装置1aの概略構成図を示す。図6に、第2実施形態に係る冷凍サイクル装置1aの機能ブロック構成図を示す。 (2) 2nd Embodiment In FIG. 5, the schematic block diagram of the refrigerating-
冷房運転時は、図7に示すように、第1冷媒回路10では、第1室外熱交換器18を第1冷媒の凝縮器として機能させ、熱源熱交換器17を第1冷媒の蒸発器として機能させるように冷凍サイクルを行いつつ、第2冷媒回路20では、熱源熱交換器17を第2冷媒の放熱器として機能させ、利用熱交換器13を第2冷媒の蒸発器として機能させるように冷凍サイクルを行うことで二元冷凍サイクルを行う。具体的には、第1切換機構12xを図7に実線で示す接続状態に切り換え、ポンプ92、第1圧縮機11、第2圧縮機21、室外ファン9を駆動させ、第3利用膨張弁14を全閉状態とし、第1熱源膨張弁26を全閉状態とし、第2利用膨張弁16の弁開度を第1圧縮機11の吸入する第1冷媒の過熱度が所定条件を満たすように制御し、第2熱源膨張弁24の弁開度を第2圧縮機21の吸入する第2冷媒の過熱度が所定条件を満たすように制御する。 (2-1) Cooling operation During cooling operation, as shown in FIG. 7, in the first
暖房運転時は、図8に示すように、第1冷媒回路10では、利用熱交換器13を第1冷媒の凝縮器として機能させ、熱源熱交換器17を第1冷媒の蒸発器として機能させるように冷凍サイクルを行い、第2冷媒回路20では、熱源熱交換器17を第2冷媒の放熱器として機能させ、第2室外熱交換器23を第2冷媒の蒸発器として機能させるように冷凍サイクルを行う。これにより、暖房運転時には、第2冷媒回路20と第1冷媒回路10とで二元冷凍サイクルが行われる。具体的には、第1切換機構12xを図8に破線で示す接続状態に切り換え、ポンプ92、第1圧縮機11、第2圧縮機21、室外ファン9を駆動させ、第2利用膨張弁16を全閉状態とし、第2熱源膨張弁24を全閉状態とし、第3利用膨張弁14の弁開度を第1圧縮機11の吸入する第1冷媒の過熱度が所定条件を満たすように制御し、第1熱源膨張弁26の弁開度を第2圧縮機21の吸入する第2冷媒の過熱度が所定条件を満たすように制御する。 (2-2) Heating operation During heating operation, as shown in FIG. A refrigeration cycle is performed so as to function as an evaporator of the refrigerant, and in the second
本実施形態の冷凍サイクル装置1aでは、第1実施形態の冷凍サイクル装置1と同様に、地球環境の悪化を抑制することができ、暖房運転時に二元冷凍サイクルを行うことで能力を確保し易くなっている。また、冷房運転時にも二元冷凍サイクルを行うが、第2冷媒である二酸化炭素冷媒を第2室外熱交換器23において放熱させるのではなく、熱源熱交換器17において第2冷媒である二酸化炭素冷媒を蒸発させて第1冷媒を凝縮させるのでもなく、熱源熱交換器17では第2冷媒である二酸化炭素冷媒を放熱させて第1冷媒を蒸発させることで、第2冷媒を利用熱交換器13において蒸発させることにより冷房負荷を処理している。このため、二酸化炭素冷媒を二元冷凍サイクルの熱源側のサイクルで用いて冷房運転を行うことにより二酸化炭素冷媒の圧力が臨界圧力を超えてCOPが低くなってしまうことを避けて、冷房運転を行うことができる。また、高圧冷媒である二酸化炭素が用いられる第2冷媒回路20の要素部品として求められる耐圧強度の基準を低めのものとすることが可能になる。 (2-3) Features of Second Embodiment In the refrigerating
図9に、第3実施形態に係る冷凍サイクル装置1bの概略構成図を示す。図10に、第3実施形態に係る冷凍サイクル装置1bの機能ブロック構成図を示す。 (3) 3rd Embodiment In FIG. 9, the schematic block diagram of the refrigerating-
冷房運転時は、図11に示すように、第1冷媒回路10では、第1室外熱交換器18を第1冷媒の凝縮器として機能させ、熱源熱交換器17を第1冷媒の蒸発器として機能させるように冷凍サイクルを行いつつ、第2冷媒回路20では、熱源熱交換器17を第2冷媒の放熱器として機能させ、利用熱交換器13を第2冷媒の蒸発器として機能させるように冷凍サイクルを行うことで二元冷凍サイクルを行う。具体的には、第1切換機構12の切換弁12a、12bを図11に実線で示す接続状態に切り換え、ポンプ92、第1圧縮機11、第2圧縮機21、室外ファン9を駆動させ、第3利用膨張弁14を全閉状態とし、第1熱源膨張弁26を全閉状態とし、第1利用膨張弁15と第2利用膨張弁16について一方を全開状態に制御しつつ他方の弁開度を第1圧縮機11の吸入する第1冷媒の過熱度が所定条件を満たすように制御し、第2熱源膨張弁24の弁開度を第2圧縮機21の吸入する第2冷媒の過熱度が所定条件を満たすように制御する。 (3-1) Cooling operation During cooling operation, as shown in FIG. 11, in the first
暖房運転時は、図12に示すように、第1冷媒回路10では、利用熱交換器13を第1冷媒の凝縮器として機能させ、熱源熱交換器17を第1冷媒の蒸発器として機能させるように冷凍サイクルを行い、第2冷媒回路20では、熱源熱交換器17を第2冷媒の放熱器として機能させ、第2室外熱交換器23を第2冷媒の蒸発器として機能させるように冷凍サイクルを行う。これにより、暖房運転時には、第2冷媒回路20と第1冷媒回路10とで二元冷凍サイクルが行われる。具体的には、第1切換機構12の切換弁12a、12bを図12に破線で示す接続状態に切り換え、ポンプ92、第1圧縮機11、第2圧縮機21、室外ファン9を駆動させ、第2利用膨張弁16を全閉状態とし、第2熱源膨張弁24を全閉状態とし、第3利用膨張弁14または第1利用膨張弁15の弁開度を第1圧縮機11の吸入する第1冷媒の過熱度が所定条件を満たすように制御し、第1熱源膨張弁26の弁開度を第2圧縮機21の吸入する第2冷媒の過熱度が所定条件を満たすように制御する。 (3-2) Heating operation During heating operation, as shown in FIG. A refrigeration cycle is performed so as to function as an evaporator of the refrigerant, and in the second
本実施形態の冷凍サイクル装置1bは、第1実施形態の冷凍サイクル装置1と同様に、地球環境の悪化を抑制することができ、暖房運転時の能力を確保し易い。また、冷房運転時にも二元冷凍サイクルを行うが、第2冷媒である二酸化炭素冷媒を第2室外熱交換器23において放熱させるのではなく、熱源熱交換器17において第2冷媒である二酸化炭素冷媒を蒸発させて第1冷媒を凝縮させるのでもなく、熱源熱交換器17では第2冷媒である二酸化炭素冷媒を放熱させて第1冷媒を蒸発させることで、第2冷媒を利用熱交換器13において蒸発させることにより冷房負荷を処理している。このため、二酸化炭素冷媒を二元冷凍サイクルの熱源側のサイクルで用いて冷房運転を行うことにより二酸化炭素冷媒の圧力が臨界圧力を超えてCOPが低くなってしまうことを避けて、冷房運転を行うことができる。また、高圧冷媒である二酸化炭素が用いられる第2冷媒回路20の要素部品として求められる耐圧強度の基準を低めのものとすることが可能になる。 (3-3) Features of the Third Embodiment The refrigerating
図13に、第4実施形態に係る冷凍サイクル装置1cの概略構成図を示す。図14に、第4実施形態に係る冷凍サイクル装置1cの機能ブロック構成図を示す。 (4) Fourth Embodiment FIG. 13 shows a schematic configuration diagram of a
冷房運転時は、第1冷房運転と、第2冷房運転と、第3冷房運転と、が選択的に行われる。 (4-1) Cooling Operation During the cooling operation, a first cooling operation, a second cooling operation, and a third cooling operation are selectively performed.
暖房運転時は、第1暖房運転と、第2暖房運転と、第3暖房運転と、が選択的に行われる。 (4-2) Heating operation During the heating operation, the first heating operation, the second heating operation, and the third heating operation are selectively performed.
本実施形態の冷凍サイクル装置1cは、第1実施形態の冷凍サイクル装置1と同様に、地球環境の悪化を抑制することができ、暖房運転時の能力を確保し易い。また、冷房時と暖房時のいずれにおいても、単元冷凍サイクル、二元冷凍サイクルだけでなく、並列冷凍サイクルを行うことが可能であるため、状況に応じて能力を確保することが可能である。 (4-3) Features of the Fourth Embodiment The refrigerating
以上、本開示の実施形態を説明したが、特許請求の範囲に記載された本開示の趣旨及び範囲から逸脱することなく、形態や詳細の多様な変更が可能なことが理解されるであろう。 (Appendix)
Although embodiments of the present disclosure have been described above, it will be appreciated that various changes in form and detail may be made without departing from the spirit and scope of the present disclosure as set forth in the appended claims. .
12 :第1切換機構
12x :第1切換機構
13 :利用熱交換器
13a :第1利用流路
13b :第2利用流路
13c :熱負荷流路
14 :第3利用膨張弁
15 :第1利用膨張弁
16 :第2利用膨張弁
17 :熱源熱交換器(カスケード熱交換器)
17a :第1熱源流路(第1カスケード流路)
17b :第2熱源流路(第2カスケード流路)
18 :第1室外熱交換器
20 :第2冷媒回路
21 :第2圧縮機
23 :第2室外熱交換器
24 :第2熱源膨張弁
25 :第3熱源膨張弁
26 :第1熱源膨張弁
90 :熱負荷回路
91 :熱負荷熱交換器
92 :ポンプ 1, 1a, 1b, 1c: refrigeration cycle device 12: first switching
17a: first heat source channel (first cascade channel)
17b: Second heat source channel (second cascade channel)
18: first outdoor heat exchanger 20: second refrigerant circuit 21: second compressor 23: second outdoor heat exchanger 24: second heat source expansion valve 25: third heat source expansion valve 26: first heat source expansion valve 90 : Heat load circuit 91 : Heat load heat exchanger 92 : Pump
Claims (16)
- 30℃で1MPa以下の第1冷媒を用いた利用側の冷凍サイクルと、30℃で1.5MPa以上の第2冷媒を用いた熱源側の冷凍サイクルと、を含む二元冷凍サイクルを行うことで暖房運転を行い、
前記第1冷媒を用いた単元冷凍サイクルを行うことで冷房運転を行う、
冷凍サイクル装置(1)。 By performing a dual refrigeration cycle including a user side refrigeration cycle using a first refrigerant of 1 MPa or less at 30° C. and a heat source side refrigeration cycle using a second refrigerant of 1.5 MPa or more at 30° C. heating operation,
Cooling operation is performed by performing a unit refrigeration cycle using the first refrigerant,
A refrigeration cycle device (1). - 前記暖房運転時に前記第1冷媒を流すための第1カスケード流路(17a)と、前記第1カスケード流路とは独立しており、前記暖房運転時に前記第2冷媒を流すための第2カスケード流路(17b)と、を有し、前記第1冷媒と前記第2冷媒とを熱交換させるカスケード熱交換器(17)を備える、
請求項1に記載の冷凍サイクル装置。 A first cascade flow path (17a) for flowing the first refrigerant during the heating operation and a second cascade flow path for flowing the second refrigerant during the heating operation are independent of the first cascade flow path (17a). a cascade heat exchanger (17) having a flow path (17b) for exchanging heat between the first refrigerant and the second refrigerant;
The refrigeration cycle apparatus according to claim 1. - 前記暖房運転時に前記第1冷媒が放熱する利用熱交換器(13)を備え、
前記暖房運転時は、前記第1冷媒が前記第1カスケード流路(17a)を通過する時に蒸発し、前記第2冷媒が前記第2カスケード流路(17b)を通過する時に放熱する、
請求項2に記載の冷凍サイクル装置。 A utilization heat exchanger (13) in which the first refrigerant releases heat during the heating operation,
During the heating operation, the first refrigerant evaporates when passing through the first cascade flow path (17a), and heat is released when the second refrigerant passes through the second cascade flow path (17b).
The refrigeration cycle apparatus according to claim 2. - 前記冷房運転時に前記第1冷媒が蒸発する利用熱交換器(13)と、
前記冷房運転時に前記第1冷媒が放熱する第1室外熱交換器(18)と、
を備えた、
請求項1から3のいずれか1項に記載の冷凍サイクル装置。 a utilization heat exchanger (13) in which the first refrigerant evaporates during the cooling operation;
a first outdoor heat exchanger (18) in which the first refrigerant releases heat during the cooling operation;
with
The refrigeration cycle apparatus according to any one of claims 1 to 3. - 前記暖房運転時に前記第2冷媒が蒸発する第2室外熱交換器(23)を備えた、
請求項1から4のいずれか1項に記載の冷凍サイクル装置。 A second outdoor heat exchanger (23) in which the second refrigerant evaporates during the heating operation,
The refrigeration cycle apparatus according to any one of claims 1 to 4. - 30℃で1MPa以下の第1冷媒を用いた利用側の冷凍サイクルと、30℃で1.5MPa以上の第2冷媒を用いた熱源側の冷凍サイクルと、を含む二元冷凍サイクルを行うことで暖房運転を行い、
前記第2冷媒を用いた利用側の冷凍サイクルと、前記第1冷媒を用いた熱源側の冷凍サイクルと、を含む二元冷凍サイクルを行うことで冷房運転を行う、
冷凍サイクル装置(1a、1b、1c)。 By performing a dual refrigeration cycle including a user side refrigeration cycle using a first refrigerant of 1 MPa or less at 30° C. and a heat source side refrigeration cycle using a second refrigerant of 1.5 MPa or more at 30° C. heating operation,
Cooling operation is performed by performing a dual refrigeration cycle including a user-side refrigeration cycle using the second refrigerant and a heat source-side refrigeration cycle using the first refrigerant,
A refrigeration cycle device (1a, 1b, 1c). - 前記第1冷媒を流すための第1カスケード流路(17a)と、前記第1カスケード流路とは独立しており、前記第2冷媒を流すための第2カスケード流路(17b)と、を有し、前記第1冷媒と前記第2冷媒とを熱交換させるカスケード熱交換器(17)を備える、
請求項6に記載の冷凍サイクル装置。 a first cascade flow path (17a) for flowing the first refrigerant; and a second cascade flow path (17b) for flowing the second refrigerant, which is independent of the first cascade flow path. a cascade heat exchanger (17) for exchanging heat between the first refrigerant and the second refrigerant;
The refrigeration cycle apparatus according to claim 6. - 前記第1冷媒を流すための第1利用流路(13a)と、前記第1利用流路とは独立しており、前記第2冷媒を流すための第2利用流路(13b)と、を有する利用熱交換器(13)を備える、
請求項7に記載の冷凍サイクル装置。 a first use channel (13a) for flowing the first refrigerant; and a second use channel (13b) for flowing the second refrigerant, which is independent of the first use channel. a utilization heat exchanger (13) comprising
The refrigeration cycle apparatus according to claim 7. - 前記暖房運転時は、前記第1冷媒が前記第1カスケード流路(17a)を通過する時に蒸発し、前記第2冷媒が前記第2カスケード流路(17b)を通過する時に放熱し、前記第1冷媒が前記第1利用流路(13a)を通過する時に放熱する、
請求項8に記載の冷凍サイクル装置。 During the heating operation, the first refrigerant evaporates when passing through the first cascade flow path (17a), and the second refrigerant radiates heat when passing through the second cascade flow path (17b). 1. Heat is released when the refrigerant passes through the first use channel (13a),
The refrigeration cycle apparatus according to claim 8. - 前記冷房運転時は、前記第1冷媒が前記第1カスケード流路(17a)を通過する時に蒸発し、前記第2冷媒が前記第2カスケード流路(17b)を通過する時に放熱し、前記第2冷媒が前記第2利用流路(13b)を通過する時に蒸発する、
請求項8または9に記載の冷凍サイクル装置。 During the cooling operation, the first refrigerant evaporates when passing through the first cascade passage (17a), the second refrigerant radiates heat when passing through the second cascade passage (17b), and the second refrigerant evaporates when passing through the first cascade passage (17a). 2 refrigerant evaporates when passing through the second utilization channel (13b);
The refrigeration cycle apparatus according to claim 8 or 9. - 前記冷房運転時は、前記第1冷媒が前記第1利用流路(13a)を通過する時に蒸発し、前記第2冷媒が前記第2利用流路(13b)を通過する時に蒸発する、
請求項8から10のいずれか1項に記載の冷凍サイクル装置。 During the cooling operation, the first refrigerant evaporates when passing through the first use channel (13a), and the second refrigerant evaporates when passing through the second use channel (13b).
The refrigeration cycle apparatus according to any one of claims 8 to 10. - 前記暖房運転時は、前記第1冷媒が前記第1利用流路(13a)を通過する時に放熱し、前記第2冷媒が前記第2利用流路(13b)を通過する時に放熱する、
請求項8から11のいずれか1項に記載の冷凍サイクル装置。 During the heating operation, heat is released when the first refrigerant passes through the first use channel (13a), and heat is released when the second refrigerant passes through the second use channel (13b).
The refrigeration cycle apparatus according to any one of claims 8 to 11. - 前記冷房運転時に、前記第1冷媒が放熱する第1室外熱交換器(18)を備える、
請求項6から12のいずれか1項に記載の冷凍サイクル装置。 A first outdoor heat exchanger (18) in which the first refrigerant releases heat during the cooling operation,
The refrigeration cycle apparatus according to any one of claims 6 to 12. - 前記暖房運転時に、前記第2冷媒が蒸発する第2室外熱交換器(23)を備える、
請求項6から13のいずれか1項に記載の冷凍サイクル装置。 A second outdoor heat exchanger (23) in which the second refrigerant evaporates during the heating operation,
The refrigeration cycle apparatus according to any one of claims 6 to 13. - 前記第1冷媒は、R1234yfおよびR1234zeの少なくともいずれかを含む、
請求項1から14のいずれか1項に記載の冷凍サイクル装置。 The first refrigerant contains at least one of R1234yf and R1234ze,
The refrigeration cycle apparatus according to any one of claims 1 to 14. - 前記第2冷媒は、二酸化炭素を含む、
請求項1から15のいずれか1項に記載の冷凍サイクル装置。 The second refrigerant contains carbon dioxide,
The refrigeration cycle apparatus according to any one of claims 1 to 15.
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JP2000320914A (en) * | 1999-05-14 | 2000-11-24 | Daikin Ind Ltd | Refrigerating machine |
JP2015197254A (en) | 2014-04-01 | 2015-11-09 | 東芝キヤリア株式会社 | Refrigeration cycle device |
WO2017221382A1 (en) * | 2016-06-23 | 2017-12-28 | 三菱電機株式会社 | Binary refrigeration device |
JP2021011985A (en) * | 2019-07-08 | 2021-02-04 | 富士電機株式会社 | Two-stage refrigerator |
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CN109075591B (en) * | 2016-02-29 | 2022-09-06 | 维里蒂工作室股份公司 | System and method for charging, transporting and operating an aircraft |
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2022
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- 2022-03-31 JP JP2022058411A patent/JP7208577B2/en active Active
- 2022-03-31 CN CN202280026125.4A patent/CN117597558A/en active Pending
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Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000320914A (en) * | 1999-05-14 | 2000-11-24 | Daikin Ind Ltd | Refrigerating machine |
JP2015197254A (en) | 2014-04-01 | 2015-11-09 | 東芝キヤリア株式会社 | Refrigeration cycle device |
WO2017221382A1 (en) * | 2016-06-23 | 2017-12-28 | 三菱電機株式会社 | Binary refrigeration device |
JP2021011985A (en) * | 2019-07-08 | 2021-02-04 | 富士電機株式会社 | Two-stage refrigerator |
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JP2022159196A (en) | 2022-10-17 |
JP7208577B2 (en) | 2023-01-19 |
EP4317845A1 (en) | 2024-02-07 |
CN117597558A (en) | 2024-02-23 |
US20240019176A1 (en) | 2024-01-18 |
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