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WO2024252470A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2024252470A1
WO2024252470A1 PCT/JP2023/020816 JP2023020816W WO2024252470A1 WO 2024252470 A1 WO2024252470 A1 WO 2024252470A1 JP 2023020816 W JP2023020816 W JP 2023020816W WO 2024252470 A1 WO2024252470 A1 WO 2024252470A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
heat source
bypass
load
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/JP2023/020816
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English (en)
Japanese (ja)
Inventor
皓亮 宮脇
宗史 池田
幸二 古谷
宏亮 浅沼
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2025525446A priority Critical patent/JPWO2024252470A1/ja
Priority to PCT/JP2023/020816 priority patent/WO2024252470A1/fr
Publication of WO2024252470A1 publication Critical patent/WO2024252470A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • 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
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat

Definitions

  • This disclosure relates to a refrigeration cycle device.
  • Patent Document 1 As social demands for ZEB (Zero Energy Based) and carbon neutrality grow, air conditioners that use unused heat such as geothermal heat or solar heat in addition to conventional air heat sources have been proposed (for example, Patent Document 1).
  • This disclosure has been made to solve the problems described above, and aims to provide a refrigeration cycle device that suppresses the decline in energy-saving performance.
  • the refrigeration cycle device includes a heat source unit, an auxiliary heat source unit, and a load device, and the heat source unit, auxiliary heat source unit, and load device are connected by multiple pipes through which a refrigerant flows.
  • the heat source unit includes a compressor that compresses the refrigerant, and a heat source side heat exchanger that exchanges heat between the refrigerant and a first fluid.
  • the auxiliary heat source unit includes an auxiliary heat exchanger that exchanges heat between the refrigerant and a second fluid that is thermally independent of the first fluid and that is a fluid that has heat or waste heat derived from renewable energy.
  • the load device includes a load side heat exchanger that exchanges heat between the refrigerant and a third fluid that is an object to be heated or cooled.
  • the refrigeration cycle device includes a bypass pipe that bypasses one of the auxiliary heat exchanger or the load side heat exchanger that acts as an evaporator, a bypass side throttle device that is provided in the bypass pipe and that reduces the pressure of the refrigerant, and a control device that controls the bypass side throttle device.
  • the control device opens the bypass side throttle device so that a portion of the refrigerant flowing toward the auxiliary heat exchanger or the load side heat exchanger that acts as an evaporator passes through the bypass pipe.
  • a throttling device provided in the bypass piping is opened so that a portion of the refrigerant flowing toward the auxiliary heat exchanger or the load side heat exchanger acting as an evaporator passes through the bypass piping.
  • the excess refrigerant generated due to the volume difference between the heat source side heat exchanger and the auxiliary heat exchanger flows to the heat source unit without passing through the evaporator. Therefore, the ratio of gas phase refrigerant, which has a lower density than liquid phase refrigerant and gas-liquid two-phase refrigerant, can be reduced in the piping between the auxiliary heat source unit or the load device and the heat source unit. Therefore, the refrigeration cycle device can suppress a decrease in energy saving performance.
  • FIG. 2 is a refrigerant circuit diagram showing a flow of refrigerant during cooling operation of the refrigeration cycle device according to the first embodiment.
  • FIG. FIG. 2 is a hardware configuration diagram showing a control device according to the first embodiment.
  • FIG. 2 is a hardware configuration diagram showing a control device according to the first embodiment.
  • 1 is a functional block diagram of a refrigeration cycle device according to a first embodiment.
  • FIG. 4 is a flowchart showing the operation of the control device according to the first embodiment.
  • 2 is a refrigerant circuit diagram showing a flow of a refrigerant during heating operation of the refrigeration cycle device according to the first embodiment.
  • FIG. FIG. 11 is a refrigerant circuit diagram showing a flow of refrigerant during cooling operation of a refrigeration cycle device according to a second embodiment.
  • FIG. 11 is a functional block diagram of a refrigeration cycle device according to a second embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing a flow of a refrigerant during heating operation of a refrigeration cycle device according to a second embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing a flow of refrigerant during cooling operation of a refrigeration cycle device according to a third embodiment.
  • FIG. 11 is a functional block diagram of a refrigeration cycle device according to a third embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing a flow of a refrigerant during heating operation of a refrigeration cycle device according to a third embodiment.
  • FIG. 11 is a functional block diagram of a refrigeration cycle device according to a second embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing a flow of a refrigerant during heating operation of a refrigeration cycle device according to a third embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of a refrigeration cycle device according to a fourth embodiment.
  • FIG. 11 is a functional block diagram of a refrigeration cycle device according to a fourth embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing a flow of a refrigerant during heating operation of a refrigeration cycle device according to a fourth embodiment.
  • FIG. 13 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of a refrigeration cycle device according to a fifth embodiment.
  • FIG. 13 is a refrigerant circuit diagram showing a refrigeration cycle device according to a sixth embodiment.
  • FIG. 13 is a functional block diagram of a refrigeration cycle device according to a sixth embodiment.
  • FIG. 11 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of a refrigeration cycle device according to a fourth embodiment.
  • FIG. 13 is a functional block diagram of a refrigeration cycle device according to a sixth embodiment.
  • FIG. 13 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of a refrigeration cycle device according to a seventh embodiment.
  • FIG. 13 is a functional block diagram of a refrigeration cycle device according to a seventh embodiment.
  • FIG. 13 is a refrigerant circuit diagram showing the flow of refrigerant during heating operation of a refrigeration cycle device according to a seventh embodiment.
  • FIG. 13 is a refrigerant circuit diagram showing a refrigeration cycle device according to an eighth embodiment.
  • FIG. 13 is a functional block diagram of a refrigeration cycle device according to an eighth embodiment.
  • FIG. 23 is a refrigerant circuit diagram showing a refrigeration cycle device according to a modified example of the eighth embodiment.
  • FIG. 13 is a refrigerant circuit diagram showing a refrigeration cycle device according to a ninth embodiment.
  • FIG. 13 is a functional block diagram of a refrigeration cycle device according to a ninth embodiment.
  • FIG. 1 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of the refrigeration cycle device according to the first embodiment.
  • the refrigeration cycle device 1 of the first embodiment is an air conditioning device that conditions an air-conditioned space such as a room.
  • the refrigeration cycle device 1 is an air conditioning device that can perform at least cooling operation and heating operation as operation modes, but the refrigeration cycle device 1 may be a refrigerator, a freezer, or a vending machine that cools stored items.
  • the refrigeration cycle device 1 may also be a refrigeration device provided in a showcase or the like.
  • the refrigeration cycle device 1 may be a water heater that supplies hot water, or a chiller that supplies cold water. As shown in FIG.
  • the refrigeration cycle device 1 has a heat source device 2, a load device 3, a relay device 4, and an auxiliary heat source device 7.
  • the heat source device 2 and the relay device 4 are connected by connection pipes 801 and 802.
  • the load device 3 and the relay device 4 are connected by connection pipes 803 and 804.
  • the auxiliary heat source device 7 and the relay device 4 are connected by connection pipes 805 and 806.
  • a refrigerant circulates through the heat source unit 2, the load unit 3, the relay unit 4, and the auxiliary heat source unit 7, as well as through the connection pipes 801 to 806.
  • the refrigeration cycle device 1 may be capable of performing an operation mode other than the cooling operation and the heating operation, such as a dehumidification operation.
  • the heat source unit 2 is, for example, an outdoor unit installed outdoors.
  • the heat source unit 2 is a device that supplies hot or cold heat to the load device 3.
  • the heat source unit 2 has a heat source side pipe 201.
  • the heat source unit 2 also has a compressor 21, a flow path switching device 22, a heat source side heat exchanger 23, and a heat source side blower 24.
  • the heat source side piping 201 is a piping provided inside the housing (not shown) of the heat source unit 2, with one end connected to the connection piping 801 and the other end connected to the connection piping 802.
  • the heat source side piping 201 connects the compressor 21, the flow path switching device 22, and the heat source side heat exchanger 23.
  • a refrigerant flows inside the heat source side piping 201.
  • the compressor 21 draws in a refrigerant in a low-temperature, low-pressure state, compresses the refrigerant with the internal compressor 21 mechanism, and discharges the refrigerant in a high-temperature, high-pressure state.
  • the refrigerant compressed by the compressor 21 is discharged and sent to the flow path switching device 22.
  • a rotary compressor, a scroll compressor, a screw compressor, or a reciprocating compressor is used as the compressor 21, for example, a rotary compressor, a scroll compressor, a screw compressor, or a reciprocating compressor is used.
  • the flow path switching device 22 switches the flow direction of the refrigerant in the refrigerant circuit, and is, for example, a four-way valve.
  • the flow path switching device 22 connects the discharge side of the compressor 21 to the heat source side heat exchanger 23.
  • the flow path switching device 22 connects the suction side of the compressor 21 to the heat source side heat exchanger 23. Note that when the refrigeration cycle device 1 is a device that performs only either cooling operation or heating operation, the flow path switching device 22 may be omitted.
  • the heat source side heat exchanger 23 exchanges heat between the refrigerant flowing into it and the outdoor air OA.
  • the heat source side heat exchanger 23 acts as a condenser during cooling operation, exchanging heat between the refrigerant and the outdoor air OA to condense and liquefy the refrigerant.
  • the heat source side heat exchanger 23 acts as an evaporator during heating operation, exchanging heat between the refrigerant and the outdoor air OA to evaporate and vaporize the refrigerant.
  • a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double-tube heat exchanger, or a plate heat exchanger is used as the heat source side heat exchanger 23, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double-tube heat exchanger, or a plate heat exchanger is used.
  • the outdoor air OA is an energy source having renewable energy.
  • Renewable energy means energy that is replenished by nature at a rate greater than the rate at which it is used.
  • the heat source side heat exchanger 23 may also exchange heat between the refrigerant and another fluid, such as water, instead of the outdoor air OA.
  • the fluid that exchanges heat with the refrigerant corresponds to the "first fluid" in this disclosure.
  • the heat source side blower 24 is a device that sends outdoor air OA to the heat source side heat exchanger 23.
  • the heat source side blower 24 is disposed adjacent to the heat source side heat exchanger 23.
  • a propeller fan, a line flow fan (registered trademark), or a multi-blade centrifugal fan is used as the heat source side blower 24, a propeller fan, a line flow fan (registered trademark), or a multi-blade centrifugal fan is used.
  • the type and specifications of the heat source side blower 24 are determined from the operating conditions such as the type, flow rate, and static pressure of the fluid that performs the heat exchange. Note that if the heat source side heat exchanger 23 exchanges heat between a fluid such as water and a refrigerant, a pump that circulates water or the like may be used instead of the heat source side blower 24.
  • the load device 3 is, for example, an indoor unit installed in a room.
  • the load device 3 receives cold or hot heat via refrigerant from the heat source unit 2 and the auxiliary heat source unit 7, and performs air conditioning in the room.
  • the load device 3 has a load-side piping 301.
  • the load device 3 also has a load-side heat exchanger 31, a load-side throttling device 32, and a load-side blower 33.
  • the load side pipe 301 is a pipe provided inside the housing (not shown) of the load device 3, and one end is connected to the connection pipe 803 and the other end is connected to the connection pipe 804.
  • the load side pipe 301 connects the load side heat exchanger 31 and the load side throttle device 32.
  • a refrigerant flows inside the load side pipe 301.
  • the load side heat exchanger 31 exchanges heat between the refrigerant flowing into it and the indoor air.
  • the load side heat exchanger 31 acts as an evaporator during cooling operation, exchanging heat between the refrigerant and the indoor air to evaporate the refrigerant and vaporize it.
  • the load side heat exchanger 31 also acts as a condenser during heating operation, exchanging heat between the refrigerant and the indoor air to condense the refrigerant and liquefy it.
  • a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double-tube heat exchanger, or a plate heat exchanger is used as the load side heat exchanger 31, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double-tube heat exchanger, or a plate heat exchanger is used.
  • the load side heat exchanger 31 may exchange heat between the refrigerant and water to supply cold water.
  • the refrigeration cycle device 1 is, for example, a water heater
  • the load side heat exchanger 31 may exchange heat between the refrigerant and water to supply hot water.
  • the fluid that exchanges heat with the refrigerant corresponds to the "third fluid" of this disclosure.
  • the refrigeration cycle device 1, which is an air conditioning device performs cooling operation
  • the air in the air-conditioned space in which the load device 3 is installed is the "cooling target” of this disclosure
  • the refrigeration cycle device 1, which is a chiller supplies cold water
  • the water flowing through the load side heat exchanger 31 is the "cooling target” of this disclosure.
  • the refrigeration cycle device 1, which is an air conditioning device performs heating operation
  • the air in the air-conditioned space in which the load device 3 is installed is the "heating target” of this disclosure
  • the refrigeration cycle device 1, which is a water heater supplies hot water
  • the water flowing through the load side heat exchanger 31 is the "heating target” of this disclosure.
  • the load side blower 33 is a device that sends indoor air to the load side heat exchanger 31.
  • the load side blower 33 is disposed adjacent to the load side heat exchanger 31. By sending indoor air from the load side blower 33, the efficiency of heat exchange between the refrigerant and the indoor air is improved.
  • a propeller fan, a line flow fan (registered trademark), or a multi-blade centrifugal fan is used as the load side blower 33.
  • the type and specifications of the load side blower 33 are determined based on the operating conditions such as the type, flow rate, and static pressure of the fluid that performs the heat exchange. Note that if the load side heat exchanger 31 exchanges heat between a fluid such as water and a refrigerant, a pump that circulates water or the like may be used instead of the load side blower 33.
  • the load side throttle device 32 reduces the pressure of the refrigerant flowing through the load side piping 301 to expand it, and is, for example, an electric expansion valve that can adjust the flow rate of the refrigerant by changing the opening degree.
  • the load side throttle device 32 is not limited to an electric expansion valve, and may be a mechanical expansion valve that uses a diaphragm in the pressure receiving section.
  • the load side throttle device 32 may also be configured with a capillary tube, etc.
  • the relay unit 4 is a device that relays the flow of refrigerant between the heat source unit 2, the load unit 3, and the auxiliary heat source unit 7.
  • the relay unit 4 has relay pipes 401 to 403, as well as a first bypass pipe 501 and a second bypass pipe 502.
  • the relay unit 4 also has a first bypass side throttle device 51, a second bypass side throttle device 52, and an on-off valve 40 and an on-off valve 41.
  • Relay pipe 401 is a pipe provided inside the housing of relay unit 4 (not shown), with one end connected to connection pipe 801 and the other end connected to connection pipe 803.
  • Relay pipe 402 is a pipe provided inside the housing of relay unit 4, with one end connected to connection pipe 804 and the other end connected to connection pipe 805.
  • Relay pipe 403 is a pipe provided inside the housing of relay unit 4, with one end connected to connection pipe 806 and the other end connected to connection pipe 802.
  • the first bypass pipe 501 is a pipe provided inside the housing of the relay unit 4, and one end is connected to the relay pipe 401 and the other end is connected to the relay pipe 402.
  • the part where the first bypass pipe 501 connects to the relay pipe 401 is referred to as the branch section 601.
  • the part where the first bypass pipe 501 connects to the relay pipe 402 is referred to as the branch section 602.
  • a part of the refrigerant flowing through the relay pipe 402 does not flow through the load side heat exchanger 31 acting as an evaporator, but flows through the first bypass pipe 501 via the branch section 602.
  • a part of the refrigerant flowing toward the load side heat exchanger 31 acting as an evaporator bypasses the load side heat exchanger 31.
  • the second bypass pipe 502 is a pipe provided inside the housing of the relay unit 4, with one end connected to the relay pipe 402 and the other end connected to the relay pipe 403.
  • the portion where the second bypass pipe 502 connects to the relay pipe 402 is referred to as the branch section 603.
  • the portion where the second bypass pipe 502 connects to the relay pipe 403 is referred to as the branch section 604.
  • a portion of the refrigerant flowing through the relay pipe 402 does not flow through the auxiliary heat exchanger 72 acting as an evaporator, but flows through the second bypass pipe 502 via the branch section 603.
  • a portion of the refrigerant flowing toward the auxiliary heat exchanger 72 acting as an evaporator bypasses the auxiliary heat exchanger 72.
  • the first bypass side throttle device 51 is provided in the first bypass pipe 501 and reduces the pressure of the refrigerant flowing through the first bypass pipe 501 to expand it. For example, it is an electric expansion valve that can adjust the flow rate of the refrigerant by changing the opening degree.
  • the second bypass side throttle device 52 is provided in the second bypass pipe 502 and reduces the pressure of the refrigerant flowing through the second bypass pipe 502 to expand it. For example, it is an electric expansion valve that can adjust the flow rate of the refrigerant by changing the opening degree.
  • the first bypass side throttle device 51 and the second bypass side throttle device 52 are not limited to electric expansion valves, and may be mechanical expansion valves that use a diaphragm in the pressure receiving part.
  • the first bypass side throttle device 51 and the second bypass side throttle device 52 may be configured with a capillary tube or the like.
  • the first bypass pipe 501 connects the relay pipe 402 through which the refrigerant flows from the auxiliary heat exchanger 72 to the load side heat exchanger 31, and the relay pipe 401 through which the refrigerant flows from the load side heat exchanger 31 to the heat source side heat exchanger 23. Therefore, during cooling operation, the first bypass pipe 501 and the first bypass side throttle device 51 correspond to the "bypass pipe” and "bypass side throttle device” of this disclosure.
  • the second bypass pipe 502 connects the relay pipe 402 through which the refrigerant flows from the load side heat exchanger 31 to the auxiliary heat exchanger 72, and the relay pipe 403 through which the refrigerant flows from the auxiliary heat exchanger 72 to the heat source side heat exchanger 23. Therefore, during heating operation, the second bypass pipe 502 and the second bypass side throttle device 52 correspond to the "bypass pipe” and "bypass side throttle device” of this disclosure.
  • the on-off valve 40 is a valve provided in the relay pipe 402.
  • the on-off valve 40 switches between an open state that allows the flow of refrigerant through the relay pipe 402 and a closed state that blocks the flow of refrigerant through the relay pipe 402.
  • the on-off valve 41 is a valve provided in the relay pipe 403.
  • the on-off valve 41 switches between an open state that allows the flow of refrigerant through the relay pipe 403 and a closed state that blocks the flow of refrigerant through the relay pipe 403.
  • the auxiliary heat source unit 7 is a device that supplies hot or cold heat to the load device 3. As will be described in detail later, the auxiliary heat source unit 7 uses renewable energy or so-called unused heat such as waste heat as a heat source, and has an auxiliary function to the heat source unit 2.
  • the auxiliary heat source unit 7 has auxiliary heat source side piping 701.
  • the auxiliary heat source unit 7 also has an auxiliary side throttle device 71 and an auxiliary heat exchanger 72.
  • the auxiliary heat source side piping 701 is a piping provided inside the housing (not shown) of the auxiliary heat source unit 7, with one end connected to the connection piping 805 and the other end connected to the connection piping 806.
  • the auxiliary heat exchanger 72 exchanges heat between the refrigerant and the heat medium.
  • the auxiliary heat exchanger 72 has a refrigerant flow path 721 through which the refrigerant flows, and a heat medium flow path 722 through which the heat medium flows.
  • the refrigerant flow path 721 is a flow path through which the refrigerant flows through the auxiliary heat source side piping 701.
  • the compressor 21, flow path switching device 22, and heat source side heat exchanger 23 of the heat source unit 2, the load side heat exchanger 31 and load side throttle device 32 of the load device 3, and the refrigerant flow path 721 and auxiliary side throttle device 71 of the auxiliary heat exchanger 72 of the auxiliary heat source unit 7 are connected by the connection pipes 801-806, the heat source side pipe 201, the load side pipe 301, the relay pipes 401-403, and the auxiliary heat source side pipe 701 to form a refrigerant circuit.
  • the refrigerant used is a fluid that undergoes latent heat change, and examples of such refrigerants include a single refrigerant such as R1234yf, R1234ze, R32, or R290, or a mixed refrigerant made by mixing two or more of these.
  • a mixed refrigerant made by mixing any of the single refrigerants with another refrigerant, a mixed refrigerant containing R1132(E), or a mixed refrigerant containing R1123 may also be used.
  • a mixed refrigerant containing R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, R459A, R474A, or R479A may also be used.
  • the heat medium flow path 722 is connected to a tank 92 in which the heat medium is stored by a heat medium pipe 901.
  • the heat medium is supplied to the heat medium flow path 722 from the tank 92 via the heat medium pipe 901.
  • a water circuit is formed by connecting the tank 92 and the heat medium flow path 722 of the auxiliary heat exchanger 72 by the heat medium pipe 901.
  • the auxiliary heat exchanger 72 is provided with a water pump 91 that circulates the heat medium in the water circuit.
  • the auxiliary heat exchanger 72 acts as a condenser during cooling operation, and exchanges heat between the refrigerant flowing through the refrigerant flow path 721 and the heat medium flowing through the heat medium flow path 722, condensing and liquefying the refrigerant.
  • the auxiliary heat exchanger 72 acts as an evaporator during heating operation, and exchanges heat between the refrigerant that has flowed inside and the heat medium, evaporating and vaporizing the refrigerant.
  • the auxiliary heat exchanger 72 is, for example, a plate-type heat exchanger, etc.
  • the heat medium stored in the tank 92 is, for example, well water.
  • Well water contains geothermal heat, which is renewable energy contained in the earth S.
  • well water is a fluid that has heat derived from geothermal heat
  • the auxiliary heat exchanger 72 uses the geothermal heat contained in the well water as its heat source.
  • Solar heat may also be used as the heat source.
  • solar heat is used as the heat source for the auxiliary heat exchanger 72, the heat medium that has been warmed via solar panels or the like is stored in the tank 92.
  • heat mediums that can be used in this case include calcium chloride aqueous solution, sodium chloride aqueous solution, magnesium chloride aqueous solution, brine containing ethylene glycol, antifreeze, or fluids that undergo latent heat change, such as water. In this way, renewable energy is used as the heat source for the auxiliary heat exchanger 72.
  • a heat exchanger that exchanges heat between the well water and a heat medium such as a calcium chloride solution, a sodium chloride solution, a magnesium chloride solution, a brine containing ethylene glycol, an antifreeze solution, or water may be provided in the tank 92, and the heat-exchanged heat medium may be circulated through the water circuit.
  • a heat medium such as a calcium chloride solution, a sodium chloride solution, a magnesium chloride solution, a brine containing ethylene glycol, an antifreeze solution, or water
  • a heat medium having waste heat may be used other than renewable energy, so long as it is continuously supplied.
  • wastewater from the facility in which the refrigeration cycle device 1 is installed may be stored in a tank 92, and a heat exchanger may be provided in the tank 92 to exchange heat between the heat medium flowing through the auxiliary heat exchanger 72 and the wastewater stored in the tank 92, and the heat medium that has been heat exchanged may be circulated to the water circuit.
  • the auxiliary heat exchanger 72 may be disposed in a heat exhaust duct of the facility in which the refrigeration cycle device 1 is disposed, and heat may be exchanged between the air in the heat exhaust duct and the heat medium.
  • the heat source utilized by the auxiliary heat source unit 7 is limited to one that is not thermally affected by the fluid that exchanges heat with the refrigerant in the heat source unit 2. For this reason, the space in which the heat source unit 2 is disposed and the space in which the auxiliary heat source unit 7 is disposed must be, for example, sufficiently distant from each other, or must be partitioned by a structure.
  • the heat medium that exchanges heat with the refrigerant in the auxiliary heat exchanger 72 corresponds to the "second fluid" of this disclosure.
  • the "second fluid” is a fluid that has heat or waste heat derived from renewable energy, and is thermally independent from the first fluid.
  • a fluid that has so-called unused heat may also be used. Unused heat is a general term for thermal energy that has not been utilized in the past.
  • the refrigeration cycle device 1 has a control device 100.
  • the control device 100 controls each device of the refrigeration cycle device 1 for each operation mode.
  • the operation modes are cooling operation and heating operation.
  • FIG. 2 is a hardware configuration diagram showing the control device 100 according to the first embodiment.
  • the control device 100 is dedicated hardware composed of a processing circuit 101 such as an ASIC (Application Specific Integrated Circuit) or an FPGA (Field-Programmable Gate Array).
  • FIG. 3 is a hardware configuration diagram showing the control device 100 according to the first embodiment.
  • the control device 100 may be composed of a processor 102 such as a CPU and a memory 103 as shown in FIG. 3.
  • FIG. 3 is a hardware configuration diagram showing the control device 100 according to the first embodiment.
  • the processor 102 and the memory 103 are connected to each other so as to be able to communicate with each other via a bus 104.
  • the functions of the control device 100 are realized by the processor 102 reading and executing a program stored in the memory 103.
  • the memory 103 may be a non-volatile or volatile semiconductor memory, or a removable recording medium.
  • FIG. 4 is a functional block diagram showing the control device 100 according to the first embodiment.
  • the control device 100 is connected to the compressor 21, the flow path switching device 22, the heat source side blower 24, the load side throttle device 32, the load side blower 33, the on-off valves 40 and 41, the first bypass side throttle device 51, the second bypass side throttle device 52, the auxiliary side throttle device 71, and the water pump 91 so as to be able to communicate wirelessly or by wire.
  • the control device 100 controls the connection direction of the flow path switching device 22 to switch the operation mode.
  • the control device 100 controls the rotation speed (discharge amount of refrigerant) of the compressor 21, the rotation speed of the heat source side blower 24, the opening degree of the load side throttle device 32, the rotation speed of the load side blower 33, the opening degree of the auxiliary side throttle device 71, and the rotation speed of the water pump 91 so that the temperature of the room becomes the temperature set by the user.
  • the control device 100 opens the first bypass side throttle device 51 and closes the second bypass side throttle device 52 during cooling operation.
  • the opening degree of the first bypass side throttle device 51 in the first embodiment is fixed (for example, 50%).
  • the second bypass side throttle device 52 may be opened during cooling operation.
  • the control device 100 closes the first bypass side throttle device 51 and opens the second bypass side throttle device 52 during heating operation.
  • the opening degree of the second bypass side throttle device 52 in the first embodiment is fixed (for example, 50%).
  • the first bypass side throttle device 51 may be opened during heating operation to ensure a differential pressure between the front and rear of the valve downstream of the branching section 602.
  • the control device 100 controls the opening and closing valves 40 and 41 to the open state when blocking the flow of refrigerant to the auxiliary heat source unit 7, regardless of the operation mode.
  • the control device 100 performs the cooling operation by switching the flow path switching device 22 so that the discharge side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state (single phase) refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows into the heat source side heat exchanger 23 acting as a condenser.
  • the refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air sent by the heat source side blower 24, condenses, and becomes a high-temperature, high-pressure gas-liquid two-phase state.
  • the high-temperature, high-pressure gas-liquid two-phase refrigerant flows into the auxiliary heat exchanger 72 acting as a condenser.
  • the refrigerant that has flowed into the auxiliary heat exchanger 72 exchanges heat with the heat medium and is condensed to become a high-pressure liquid.
  • the high-pressure liquid refrigerant is branched at the branching section 602, with a portion flowing toward the load device 3 and the remaining portion flowing through the first bypass pipe 501.
  • the two-phase gas-liquid refrigerant flows into the load-side heat exchanger 31, which acts as an evaporator.
  • the refrigerant that flows into the load-side heat exchanger 31 exchanges heat with the indoor air sent by the load-side blower 33, causing the liquid phase to evaporate and become gaseous (single phase). At that time, the indoor air is cooled, and cooling is performed in the room.
  • the high-pressure liquid refrigerant that is branched off at the branching section 602 flows into the first bypass side throttle device 51, where it is decompressed and expanded to become a low-temperature, low-pressure, gas-liquid two-phase refrigerant.
  • the gas-dominated two-phase gas-liquid refrigerant passes through the flow path switching device 22 and flows back into the compressor 21, where it is compressed and discharged in a high-temperature, high-pressure gas state. This cycle is repeated during cooling operation of the refrigeration cycle device 1.
  • FIG. 5 is a refrigerant circuit diagram showing the flow of the refrigerant during the heating operation of the refrigeration cycle device 1 according to the first embodiment.
  • the control device 100 performs the heating operation by switching the flow path switching device 22 so that the suction side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows into the load side heat exchanger 31 acting as a condenser.
  • the refrigerant that flows into the load side heat exchanger 31 exchanges heat with the indoor air sent by the load side blower 33, condenses, and becomes a low-temperature liquid state. At that time, the indoor air is warmed, and heating is performed in the room.
  • the low-temperature, high-pressure liquid state refrigerant is divided at the branching portion 603, a part of it flows toward the auxiliary heat source unit 7, and the remaining part flows through the second bypass piping 502.
  • the low-temperature, high-pressure liquid refrigerant that flows toward the auxiliary heat exchanger 72 after being diverted at the branching section 603 is decompressed by the auxiliary side throttle device 71 and becomes a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant flows into the auxiliary heat exchanger 72, which acts as an evaporator.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium, evaporating the liquid phase and becoming a gas (single phase).
  • the low-temperature, high-pressure liquid refrigerant that is branched off at the branching section 603 flows into the second bypass side throttle device 52, where it is decompressed and expanded to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air supplied by the heat source side blower 24, evaporating the liquid phase, and becoming a low-pressure gas refrigerant (single phase).
  • the low-pressure gas refrigerant that flows out of the heat source side heat exchanger 23 passes through the flow path switching device 22 and flows back into the compressor 21, where it is compressed and discharged in a high-temperature, high-pressure gas state. This cycle is repeated during the heating operation of the refrigeration cycle device 1.
  • FIG. 6 is a flowchart showing an example of the operation of the control device 100 according to the first embodiment.
  • the control device 100 determines whether the operation mode of the refrigeration cycle device 1 is cooling operation (step S1). If the operation mode is cooling operation (step S1: YES), the control device 100 opens the first bypass side throttle device 51 (step S2). If the operation mode is not cooling operation, i.e., heating operation (step S2), the control device 100 opens the second bypass side throttle device 52 (step S3).
  • the refrigeration cycle device 1 can perform two operation modes, cooling operation and heating operation, as an example, the refrigeration cycle device 1 may also be capable of performing, for example, a dehumidification operation.
  • a means for processing the excess refrigerant generated from the volume difference between the heat source side heat exchanger 23 and the auxiliary heat exchanger 72 a means such as making the refrigerant two-phase gas-liquid at the outlet of the load side heat exchanger 31 is considered.
  • the control target of the load side throttle device 32 is not determined and controllability is reduced.
  • the refrigeration cycle device 1 has multiple load devices 3, it becomes impossible to provide the required air conditioning capacity for each load device 3.
  • a throttling device provided in the bypass piping is opened so that a portion of the refrigerant flowing toward the auxiliary heat exchanger 72 or the load side heat exchanger 31 acting as an evaporator bypasses the auxiliary heat exchanger 72 or the load side heat exchanger 31.
  • the excess refrigerant generated from the volumetric difference between the heat source side heat exchanger 23 and the auxiliary heat exchanger 72 flows to the heat source unit 2 without passing through the evaporator. Therefore, in the piping between the auxiliary heat source unit 7 or the load device 3 and the heat source unit 2, the ratio of gas phase refrigerant, which has a lower density than liquid phase refrigerant and gas-liquid two-phase refrigerant, can be reduced. Therefore, the refrigeration cycle device 1 can suppress a decrease in energy saving performance.
  • the liquid phase ratio of the refrigerant from the branching part 601 inside the relay unit 4 to the compressor 21 inside the heat source unit 2 is improved compared to when the first bypass piping 501 is not provided.
  • the condensation saturation temperature in the heat source unit 2 and the auxiliary heat source unit 7 is lowered, and the deterioration of energy saving performance is suppressed.
  • the ratio of two-phase gas-liquid refrigerant from the branching point 604 inside the relay unit 4 to the heat source side heat exchanger 23 inside the heat source unit 2 is improved compared to when the second bypass piping 502 is not provided.
  • the volumetric flow rate is reduced, so the pressure loss of the refrigerant from the branching point 604 to the heat source side heat exchanger 23 is reduced, and the deterioration of energy saving performance is suppressed.
  • the pressure loss can be reduced without increasing the piping diameter, the deterioration of space efficiency is also suppressed.
  • Fig. 7 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of the refrigeration cycle apparatus 1A according to embodiment 2.
  • the refrigeration cycle apparatus 1A according to embodiment 3 differs from the refrigeration cycle apparatus 1 according to embodiment 1 in the piping configuration of the relay unit 4A.
  • the differences from the refrigeration cycle apparatus 1 according to embodiment 1 will be mainly described, and the commonalities will be omitted. Note that in the following figures, the water pump 91 and the tank 92 may be omitted.
  • the heat source unit 2 has a heat source side pipe 202 and a heat source side pipe 203.
  • the heat source unit 2 also has an accumulator 25 and check valves 26 to 29.
  • the heat source side pipe 202 is a pipe provided inside the housing of the heat source unit 2, with one end connected between the check valve 26 in the heat source side pipe 201 and the connection position of the connection pipe 801, and the other end connected between the check valve 29 in the heat source side pipe 201 and the heat source side heat exchanger 23.
  • the heat source side pipe 203 is a pipe provided inside the housing of the heat source unit 2, with one end connected between the check valve 26 in the heat source side pipe 201 and the flow path switching device 22, and the other end connected between the check valve 29 in the heat source side pipe 201 and the connection position of the connection pipe 802.
  • the accumulator 25 is provided on the suction side of the compressor 21 and is a container for storing excess refrigerant circulating through the refrigerant circuit.
  • Check valve 26 is provided in heat source side piping 201 between the connection position of flow path switching device 22 and connection piping 801, and allows refrigerant to flow from flow path switching device 22 to relay unit 4A and blocks the reverse flow.
  • Check valve 27 is provided in heat source side piping 203, allows refrigerant to flow from relay unit 4A to flow path switching device 22 and blocks the reverse flow.
  • Check valve 28 is provided in heat source side piping 202, and allows refrigerant to flow from heat source side heat exchanger 23 to relay unit 4A, and blocks the reverse flow.
  • Check valve 29 is provided in heat source side piping 201 between the heat source side heat exchanger 23 and the connection position of connection piping 802, and allows refrigerant to flow from relay unit 4A to heat source side heat exchanger 23, and blocks the reverse flow.
  • the relay unit 4A has relay pipes 404-410 and a third bypass pipe 503.
  • the relay unit 4A also has a third bypass side throttle device 53 and on-off valves 42-47.
  • the relay pipe 404 is a pipe provided inside the housing of the relay unit 4A, with one end connected to the connection pipe 803 and the other end connected to the relay pipe 405 and the relay pipe 406.
  • the relay pipe 405 is a pipe provided inside the housing of the relay unit 4A, with one end connected to the relay pipe 404 and the other end connected to the connection pipe 801.
  • the relay pipe 406 is a pipe provided inside the housing of the relay unit 4A, with one end connected to the relay pipe 404 and the other end connected to the connection pipe 802.
  • Relay pipe 407 is a pipe provided inside the housing of relay unit 4A, with one end connected to connection pipe 806 and the other end connected to relay pipe 408 and relay pipe 409.
  • Relay pipe 408 is a pipe provided inside the housing of relay unit 4A, with one end connected to relay pipe 407 and the other end connected to relay pipe 405.
  • Relay pipe 409 is a pipe provided inside the housing of relay unit 4A, with one end connected to relay pipe 407 and the other end connected to relay pipe 406.
  • the relay pipe 410 is a pipe provided inside the housing of the relay unit 4A, with one end connected to the connection pipe 804 and the other end connected to the connection pipe 805.
  • the third bypass pipe 503 is a pipe provided inside the housing of the relay unit 4A, and one end is connected to the relay pipe 406 and the other end is connected to the relay pipe 410.
  • the part where the third bypass pipe 503 connects to the relay pipe 406 is called the branch section 605.
  • the part where the third bypass pipe 503 connects to the relay pipe 410 is called the branch section 606.
  • a part of the refrigerant flowing toward the load side heat exchanger 31 acting as an evaporator bypasses the load side heat exchanger 31.
  • a part of the refrigerant flowing through the relay pipe 410 does not flow through the auxiliary heat exchanger 72 acting as an evaporator, but flows through the third bypass pipe 503 via the branch section 606. That is, some of the refrigerant flowing toward the auxiliary heat exchanger 72, which acts as an evaporator, bypasses the auxiliary heat exchanger 72.
  • the third bypass side throttle device 53 is provided in the third bypass pipe 503 and reduces the pressure of the refrigerant flowing through the third bypass pipe 503 to expand it.
  • it is an electric expansion valve that can adjust the flow rate of the refrigerant by changing the opening degree.
  • the third bypass side throttle device 53 is not limited to an electric expansion valve, and may be a mechanical expansion valve that uses a diaphragm in the pressure receiving part.
  • the load side throttle device 32 may be configured with a capillary tube or the like.
  • the third bypass piping 503 connects the relay piping 410 through which the refrigerant flows from the auxiliary heat exchanger 72 to the load side heat exchanger 31, and the relay piping 406 through which the refrigerant flows from the load side heat exchanger 31 to the heat source side heat exchanger 23.
  • the third bypass piping 503 connects the relay piping 410 through which the refrigerant flows from the load side heat exchanger 31 to the auxiliary heat exchanger 72, and the relay piping 406 through which the refrigerant flows from the auxiliary heat exchanger 72 to the heat source side heat exchanger 23. Therefore, during both cooling operation and heating operation, the third bypass piping 503 and the third bypass side throttle device 53 correspond to the "bypass piping" and the "bypass side throttle device" of this disclosure.
  • the on-off valve 42 is a valve provided in the relay pipe 405.
  • the on-off valve 42 switches between an open state that allows the flow of refrigerant through the relay pipe 405, and a closed state that blocks the flow of refrigerant through the relay pipe 405.
  • the on-off valve 42 is closed during cooling operation and opened during heating operation.
  • the on-off valve 43 is a valve provided in the relay pipe 406.
  • the on-off valve 43 switches between an open state that allows the flow of refrigerant through the relay pipe 406, and a closed state that blocks the flow of refrigerant through the relay pipe 406.
  • the on-off valve 43 is opened during cooling operation and closed during heating operation.
  • the on-off valve 44 is a valve provided in the relay pipe 408.
  • the on-off valve 44 switches between an open state that allows the flow of refrigerant through the relay pipe 408 and a closed state that blocks the flow of refrigerant through the relay pipe 408.
  • the on-off valve 44 is opened during cooling operation and closed during heating operation.
  • the on-off valve 45 is a valve provided in the relay pipe 409.
  • the on-off valve 45 switches between an open state that allows the flow of refrigerant through the relay pipe 409 and a closed state that blocks the flow of refrigerant through the relay pipe 409.
  • the on-off valve 45 is closed during cooling operation and open during heating operation.
  • the on-off valve 46 is a valve provided between the connection position of the connection pipe 804 in the relay pipe 410 and the connection position of the third bypass pipe 503.
  • the on-off valve 46 switches between an open state that allows the flow of refrigerant flowing through the relay pipe 410 and a closed state that blocks the flow of refrigerant flowing through the relay pipe 405.
  • the on-off valve 47 is a valve provided between the connection position of the connection pipe 805 in the relay pipe 410 and the connection position of the third bypass pipe 503.
  • the on-off valve 47 switches between an open state that allows the flow of refrigerant flowing through the relay pipe 405 and a closed state that blocks the flow of refrigerant flowing through the relay pipe 405.
  • FIG. 8 is a functional block diagram of the refrigeration cycle apparatus 1A according to the second embodiment.
  • the control device 100 is connected to the compressor 21, the flow path switching device 22, the heat source side blower 24, the load side throttle device 32, the load side blower 33, the on-off valves 42-47, the third bypass side throttle device 53, the auxiliary side throttle device 71, and the water pump 91 so as to be able to communicate wirelessly or by wire.
  • the control device 100 only the parts that differ from the first embodiment will be described.
  • the control device 100 opens the third bypass throttle device 53 during cooling operation and heating operation. Note that the opening degree of the third bypass throttle device 53 in the second embodiment is fixed (e.g., 50%).
  • control device 100 opens the on-off valves 43, 44, 46, and 47, and closes the on-off valves 42 and 45.
  • control device 100 opens the on-off valves 42, 45, 46, and 47, and closes the on-off valves 43 and 44.
  • the control device 100 performs the cooling operation by switching the flow path switching device 22 so that the discharge side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the control device 100 opens the on-off valves 43, 44, 46, and 47, and closes the on-off valves 42 and 45.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state (single phase) refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows into the heat source side heat exchanger 23 acting as a condenser.
  • the refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air sent by the heat source side blower 24, condenses, and becomes a high-temperature, high-pressure gas-liquid two-phase state.
  • the high-temperature, high-pressure refrigerant in a gas-liquid two-phase state passes through relay pipes 405, 408, and 407 of the relay unit 4A and flows into the auxiliary heat exchanger 72, which acts as a condenser.
  • the refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium and condenses to become a high-pressure liquid state.
  • the high-pressure liquid refrigerant passes through the relay pipe 410 of the relay unit 4A and is branched at the branching section 606, with a portion flowing toward the load device 3 and the remaining portion flowing through the third bypass pipe 503.
  • the two-phase gas-liquid refrigerant flows into the load-side heat exchanger 31, which acts as an evaporator.
  • the refrigerant that flows into the load-side heat exchanger 31 exchanges heat with the indoor air sent by the load-side blower 33, causing the liquid phase to evaporate and become gaseous (single phase). At that time, the indoor air is cooled, and cooling is performed in the room.
  • the high-pressure liquid refrigerant that is branched off at the branching section 606 flows into the third bypass side throttle device 53, where it is decompressed and expanded to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure gaseous refrigerant flowing out of the load-side heat exchanger 31 passes through the relay pipes 404 and 406 of the relay unit 4A, and merges with the two-phase gas-liquid refrigerant that has flowed through the third bypass pipe 503 at the branch point 605.
  • the refrigerant flowing through the relay pipe 406 becomes a gas-dominated two-phase gas-liquid refrigerant.
  • the gas-dominated two-phase gas-liquid refrigerant passes through the flow path switching device 22 and the accumulator 25, flows back into the compressor 21, is compressed, and is discharged in a high-temperature, high-pressure gaseous state. This cycle is repeated during cooling operation of the refrigeration cycle device 1A.
  • FIG. 9 is a refrigerant circuit diagram showing the flow of the refrigerant during the heating operation of the refrigeration cycle apparatus 1A according to the second embodiment.
  • the control device 100 performs the heating operation by switching the flow path switching device 22 so that the suction side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the control device 100 opens the on-off valves 42, 45, 46, and 47, and closes the on-off valves 43 and 44.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state refrigerant discharged from the compressor 21 passes through the flow path switching device 22, passes through the relay pipes 405 and 404 of the relay device 4A, and flows into the load side heat exchanger 31 acting as a condenser.
  • the refrigerant that flows into the load side heat exchanger 31 exchanges heat with the indoor air sent by the load side blower 33, condenses, and becomes a low-temperature liquid state. At that time, the indoor air is heated, and heating is performed in the room.
  • the low-temperature, high-pressure liquid refrigerant passes through the relay pipe 410 of the relay unit 4A and is branched at the branching section 606, with a part of it flowing toward the auxiliary heat source unit 7 and the remaining part flowing through the third bypass pipe 503.
  • the low-temperature, high-pressure liquid refrigerant that flows toward the auxiliary heat exchanger 72 after being diverted at the branching section 606 flows into the auxiliary throttle device 71, where it is decompressed and becomes a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant flows into the auxiliary heat exchanger 72, which acts as an evaporator.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium, evaporating the liquid phase and becoming a gas (single phase).
  • the low-temperature, high-pressure liquid refrigerant that is branched off at the branching section 606 flows into the third bypass side throttle device 53, where it is decompressed and expanded to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure gas-state refrigerant that flows out of the auxiliary heat exchanger 72 passes through the relay pipes 407, 409, and 406 of the relay unit 4A, and merges with the gas-liquid two-phase refrigerant that flows through the third bypass pipe 503 at the branching point 605. As a result, the refrigerant flowing through the relay pipe 406 becomes a gas-based two-phase refrigerant.
  • the low-temperature, low-pressure gas-based two-phase refrigerant flows into the heat source side heat exchanger 23, which acts as an evaporator.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air supplied by the heat source side blower 24, evaporating the liquid phase, and becoming a low-pressure gas refrigerant (single phase).
  • the low-pressure gas refrigerant that flows out of the heat source side heat exchanger 23 passes through the flow switching device 22 and the accumulator 25, flows back into the compressor 21, is compressed, and is discharged in a high-temperature, high-pressure gas state. This cycle is repeated during heating operation of the refrigeration cycle device 1A.
  • a throttling device provided in the bypass piping is opened so that a portion of the refrigerant flowing toward the auxiliary heat exchanger 72 acting as an evaporator or the load side heat exchanger 31 bypasses the auxiliary heat exchanger 72 or the load side heat exchanger 31. Therefore, the refrigeration cycle apparatus 1A can suppress a decrease in the energy saving performance.
  • Fig. 10 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of the refrigeration cycle apparatus 1B according to embodiment 3.
  • the refrigeration cycle apparatus 1B of embodiment 3 differs from the refrigeration cycle apparatus 1A of embodiment 2 in the piping configuration of the relay unit 4B.
  • the following mainly describes the differences with the refrigeration cycle apparatus 1B of embodiment 2, and omits a description of the commonalities.
  • the relay unit 4B has relay pipes 404-409 and 411-417, and a fourth bypass pipe 504.
  • the relay unit 4B also has a fourth bypass side throttle device 54 and on-off valves 42-45.
  • the relay unit 4B also has check valves 61-64.
  • the relay pipes 404-409 and on-off valves 42-45 have the same configuration as in the second embodiment.
  • the relay pipe 411 is a pipe provided inside the housing of the relay unit 4B, and one end is connected to the connection pipe 804, and the other end is connected to the relay pipe 412 and the relay pipe 413.
  • the connection portion between the relay pipe 411 and the relay pipe 412 and the relay pipe 413 is called the branch section 607.
  • the relay pipe 412 is a pipe provided inside the housing of the relay unit 4B, and one end is connected to the relay pipe 411, and the other end is connected to the relay pipes 415 and 417, and the fourth bypass pipe 504.
  • the connection portion between the relay pipe 411 and the relay pipes 415 and 417, and the fourth bypass pipe 504 is called the branch section 608.
  • the relay pipe 413 is a pipe provided inside the housing of the relay unit 4B, and one end is connected to the relay pipe 411, and the other end is connected to the relay pipes 416 and 417.
  • the connection between relay pipe 411 and relay pipes 416 and 417 is called branch section 609.
  • the relay pipe 414 is a pipe provided inside the housing of the relay unit 4B, and one end is connected to the connection pipe 805, and the other end is connected to the relay pipe 415 and the relay pipe 416.
  • the connection part between the relay pipe 414 and the relay pipes 415 and 416 is called the branch section 610.
  • the relay pipe 415 is a pipe provided inside the housing of the relay unit 4B, and one end is connected to the relay pipe 414 at the branch section 610, and the other end is connected to the relay pipes 412 and 417 and the fourth bypass pipe 504 at the branch section 608.
  • the relay pipe 416 is a pipe provided inside the housing of the relay unit 4B, and one end is connected to the relay pipe 414 at the branch section 610, and the other end is connected to the relay pipe 413 and the relay pipe 417 at the branch section 609.
  • the relay pipe 417 is a pipe provided inside the housing of the relay unit 4B, and one end of the pipe is connected to the relay pipes 412 and 415 and the fourth bypass pipe 504 at the branching point 608, and the other end of the pipe is connected to the relay pipes 413 and 416 at the branching point 609.
  • the fourth bypass pipe 504 is a pipe provided inside the housing of the relay unit 4B, and one end is connected to the relay pipe 406, and the other end is connected to the relay pipe 411 at the branching section 608.
  • the part where the fourth bypass pipe 504 connects to the relay pipe 406 is called the branching section 611.
  • a part of the refrigerant flowing through the relay pipe 415 does not flow through the load side heat exchanger 31 acting as an evaporator, but flows through the fourth bypass pipe 504 via the branching section 608.
  • a part of the refrigerant flowing toward the load side heat exchanger 31 acting as an evaporator bypasses the load side heat exchanger 31.
  • a part of the refrigerant flowing through the relay pipe 412 does not flow through the auxiliary heat exchanger 72 acting as an evaporator, but flows through the fourth bypass pipe 504 via the branching section 608. That is, some of the refrigerant flowing toward the auxiliary heat exchanger 72, which acts as an evaporator, bypasses the auxiliary heat exchanger 72.
  • the fourth bypass side throttle device 54 is provided in the fourth bypass pipe 504 and reduces the pressure of the refrigerant flowing through the fourth bypass pipe 504 to expand it.
  • it is an electric expansion valve that can adjust the flow rate of the refrigerant by changing the opening degree.
  • the fourth bypass side throttle device 54 is not limited to an electric expansion valve, and may be a mechanical expansion valve that uses a diaphragm in the pressure receiving part.
  • the load side throttle device 32 may be configured with a capillary tube or the like.
  • the fourth bypass pipe 504 connects the relay pipes 415 and 417 through which the refrigerant flows from the auxiliary heat exchanger 72 to the load side heat exchanger 31, and the relay pipe 406 through which the refrigerant flows from the load side heat exchanger 31 to the heat source side heat exchanger 23.
  • the fourth bypass pipe 504 connects the relay pipes 412 and 417 through which the refrigerant flows from the load side heat exchanger 31 to the auxiliary heat exchanger 72, and the relay pipe 406 through which the refrigerant flows from the auxiliary heat exchanger 72 to the heat source side heat exchanger 23. Therefore, during both cooling operation and heating operation, the fourth bypass pipe 504 and the fourth bypass side throttle device 54 correspond to the "bypass pipe” and the "bypass side throttle device" of this disclosure.
  • Check valve 61 is provided in relay pipe 412, and allows refrigerant to flow from branch 607 to branch 608, while blocking the reverse flow.
  • Check valve 62 is provided in relay pipe 413, and allows refrigerant to flow from branch 609 to branch 607, while blocking the reverse flow.
  • Check valve 63 is provided in relay pipe 415, and allows refrigerant to flow from branch 610 to branch 608, while blocking the reverse flow.
  • Check valve 64 is provided in relay pipe 416, and allows refrigerant to flow from branch 609 to branch 610, while blocking the reverse flow.
  • FIG. 11 is a functional block diagram of the refrigeration cycle apparatus 1B according to the third embodiment.
  • the control device 100 is connected to the compressor 21, the flow path switching device 22, the heat source side blower 24, the load side throttle device 32, the load side blower 33, the on-off valves 42-44, the fourth bypass side throttle device 54, the auxiliary side throttle device 71, and the water pump 91 so as to be able to communicate wirelessly or by wire.
  • the control device 100 only the parts that differ from the second embodiment will be described.
  • the control device 100 opens the fourth bypass throttle device 54 during cooling operation and heating operation.
  • the opening degree of the fourth bypass throttle device 54 in embodiment 3 is fixed (e.g., 50%).
  • the control device 100 performs the cooling operation by switching the flow path switching device 22 so that the discharge side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the control device 100 opens the on-off valves 43 and 44 and closes the on-off valves 42 and 45.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state (single phase) refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows into the heat source side heat exchanger 23 acting as a condenser.
  • the refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air sent by the heat source side blower 24, condenses, and becomes a high-temperature, high-pressure gas-liquid two-phase state.
  • the high-temperature, high-pressure refrigerant in a gas-liquid two-phase state passes through relay pipes 405, 408, and 407 of the relay unit 4B and flows into the auxiliary heat exchanger 72, which acts as a condenser.
  • the refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium and condenses to become a high-pressure liquid state.
  • the high-pressure liquid refrigerant passes through relay pipes 414 and 415 of the relay unit 4B and is branched at a branching point 608, with a portion flowing toward the load device 3 and the remainder flowing through the third bypass pipe 503.
  • the high-pressure liquid refrigerant that is diverted at the branch point 608 and flows toward the load device 3 passes through the relay pipes 417, 413, and 411 of the relay unit 4B and flows into the load-side throttle device 32, where it is decompressed and expanded to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the load-side heat exchanger 31, which acts as an evaporator.
  • the refrigerant that flows into the load-side heat exchanger 31 exchanges heat with the indoor air sent by the load-side blower 33, causing the liquid phase to evaporate and become gaseous (single phase). At that time, the indoor air is cooled and cooling is performed in the room.
  • the high-pressure liquid refrigerant that is diverted at the branching section 608 flows into the fourth bypass side throttle device 54, where it is decompressed and expanded to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure gaseous refrigerant flowing out of the load-side heat exchanger 31 passes through the relay pipes 404 and 406 of the relay unit 4B, and merges with the two-phase gas-liquid refrigerant that has flowed through the third bypass pipe 503 at the branch point 611.
  • the refrigerant flowing through the relay pipe 406 becomes a gas-dominated two-phase gas-liquid refrigerant.
  • the gas-dominated two-phase gas-liquid refrigerant passes through the flow path switching device 22 and the accumulator 25, flows back into the compressor 21, is compressed, and is discharged in a high-temperature, high-pressure gaseous state. This cycle is repeated during cooling operation of the refrigeration cycle device 1B.
  • FIG. 12 is a refrigerant circuit diagram showing the flow of the refrigerant during the heating operation of the refrigeration cycle device 1B according to the third embodiment.
  • the control device 100 performs the heating operation by switching the flow path switching device 22 so that the suction side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the control device 100 opens the on-off valves 42 and 45 and closes the on-off valves 43 and 44.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows through the relay pipes 405 and 404 of the relay device 4B into the load side heat exchanger 31 acting as a condenser.
  • the refrigerant that flows into the load side heat exchanger 31 exchanges heat with the indoor air sent by the load side blower 33, condenses, and becomes a low-temperature liquid state. At that time, the indoor air is heated, and heating is performed in the room.
  • the low-temperature, high-pressure liquid refrigerant passes through the relay pipes 411 and 412 of the relay unit 4B, and is branched at the branching point 608, with a part of it flowing toward the auxiliary heat source unit 7 and the remaining part flowing through the fourth bypass pipe 504.
  • the low-temperature, high-pressure liquid refrigerant flowing toward the auxiliary heat exchanger 72 flows through the relay pipes 417, 416, and 414 of the relay unit 4B, and enters the auxiliary side throttle device 71, where it is decompressed and becomes a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant flows into the auxiliary heat exchanger 72, which acts as an evaporator.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium, evaporating the liquid phase and becoming a gas (single phase).
  • the low-temperature, high-pressure liquid refrigerant that is branched off at the branching section 608 flows into the fourth bypass side throttle device 54, where it is decompressed and expanded to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure gas-state refrigerant that flows out of the auxiliary heat exchanger 72 passes through the relay pipes 407, 409, and 406 of the relay unit 4B, and merges with the gas-liquid two-phase refrigerant that flows through the fourth bypass pipe 504 at the branch point 611. As a result, the refrigerant flowing through the relay pipe 406 becomes a gas-based two-phase refrigerant.
  • the low-temperature, low-pressure gas-based two-phase refrigerant flows into the heat source side heat exchanger 23, which acts as an evaporator.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air supplied by the heat source side blower 24, evaporating the liquid phase, and becoming a low-pressure gas refrigerant (single phase).
  • the low-pressure gas refrigerant that flows out of the heat source side heat exchanger 23 passes through the flow switching device 22 and the accumulator 25, flows into the compressor 21 again, is compressed, and is discharged in a high-temperature, high-pressure gas state. This cycle is repeated during heating operation of the refrigeration cycle device 1B.
  • a throttling device provided in the bypass piping is opened so that a portion of the refrigerant flowing toward the auxiliary heat exchanger 72 acting as an evaporator or the load side heat exchanger 31 bypasses the auxiliary heat exchanger 72 or the load side heat exchanger 31. Therefore, the refrigeration cycle apparatus 1B can suppress a decrease in the energy saving performance.
  • Fig. 13 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of the refrigeration cycle apparatus 1C according to embodiment 4.
  • the refrigeration cycle apparatus 1C of embodiment 4 differs from the refrigeration cycle apparatus 1B of embodiment 3 in that a relay unit 4C has a refrigerant heat exchanger 65.
  • the following description will focus on the differences from the refrigeration cycle apparatus 1B of embodiment 3, and will omit a description of the commonalities.
  • the relay unit 4C has relay pipes 404-409 and 411-417, and a fifth bypass pipe 505.
  • the relay unit 4C also has a fifth bypass side throttle device 55, and on-off valves 42-45.
  • the relay unit 4C has check valves 61-64.
  • the relay unit 4C also has an inter-refrigerant heat exchanger 65 that exchanges heat between the refrigerant flowing through the relay pipe 417 and the refrigerant flowing through the fifth bypass pipe 505.
  • the relay pipes 404-409 and 411-417, the on-off valves 42-45, and the check valves 61-64 have the same configuration as in the third embodiment.
  • the refrigerant-to-refrigerant heat exchanger 65 exchanges heat between the refrigerant flowing upstream of the fifth bypass side throttling device 55 and the refrigerant flowing downstream of the fifth bypass side throttling device 55.
  • the refrigerant-to-refrigerant heat exchanger 65 has a first refrigerant flow path 651 to which the relay pipe 417 is connected and through which the refrigerant upstream of the fifth bypass side throttling device 55 flows, and a second refrigerant flow path 652 to which the fifth bypass pipe 505 is connected and through which the refrigerant downstream of the fifth bypass side throttling device 55 flows.
  • the fifth bypass pipe 505 is a pipe provided inside the housing of the relay unit 4C, and one end is connected to the relay pipe 406 and the other end is connected to the relay pipe 417.
  • the part where the fifth bypass pipe 505 connects to the relay pipe 406 is called the branch section 612.
  • the part where the fifth bypass pipe 505 connects to the relay pipe 417 is called the branch section 613.
  • a part of the refrigerant flowing toward the load side heat exchanger 31 acting as an evaporator bypasses the load side heat exchanger 31.
  • a part of the refrigerant flowing through the relay pipe 417 does not flow through the auxiliary heat exchanger 72 acting as an evaporator, but flows through the fifth bypass pipe 505 via the branch section 613. That is, some of the refrigerant flowing toward the auxiliary heat exchanger 72, which acts as an evaporator, bypasses the auxiliary heat exchanger 72.
  • the fifth bypass throttle device 55 is provided in the fifth bypass pipe 505 and reduces the pressure of the refrigerant flowing through the fifth bypass pipe 505 to expand it.
  • it is an electric expansion valve that can adjust the flow rate of the refrigerant by changing the opening degree.
  • the fifth bypass throttle device 55 is not limited to an electric expansion valve, and may be a mechanical expansion valve that uses a diaphragm in the pressure receiving part.
  • the load throttle device 32 may be configured with a capillary tube or the like.
  • the fifth bypass pipe 505 connects the relay pipe 417 through which the refrigerant flows from the auxiliary heat exchanger 72 to the load side heat exchanger 31, and the relay pipe 406 through which the refrigerant flows from the load side heat exchanger 31 to the heat source side heat exchanger 23.
  • the fifth bypass pipe 505 connects the relay pipe 417 through which the refrigerant flows from the load side heat exchanger 31 to the auxiliary heat exchanger 72, and the relay pipe 406 through which the refrigerant flows from the auxiliary heat exchanger 72 to the heat source side heat exchanger 23. Therefore, during both cooling operation and heating operation, the fifth bypass pipe 505 and the fifth bypass side throttle device 55 correspond to the "bypass pipe” and the "bypass side throttle device" of this disclosure.
  • FIG. 14 is a functional block diagram of the refrigeration cycle apparatus 1C according to the third embodiment.
  • the control device 100 is connected to the compressor 21, the flow path switching device 22, the heat source side blower 24, the load side throttle device 32, the load side blower 33, the on-off valves 42-45, the fifth bypass side throttle device 55, the auxiliary side throttle device 71, and the water pump 91 so as to be able to communicate wirelessly or by wire.
  • the control device 100 only the parts that differ from the third embodiment will be described.
  • the control device 100 opens the fifth bypass throttle device 55 during cooling operation and heating operation.
  • the opening degree of the fifth bypass throttle device 55 in the fourth embodiment is fixed (e.g., 50%).
  • the control device 100 performs the cooling operation by switching the flow path switching device 22 so that the discharge side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the control device 100 opens the on-off valves 43 and 44 and closes the on-off valves 42 and 45.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state (single phase) refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows into the heat source side heat exchanger 23 acting as a condenser.
  • the refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air sent by the heat source side blower 24, condenses, and becomes a high-temperature, high-pressure gas-liquid two-phase state.
  • the high-temperature and high-pressure refrigerant in a gas-liquid two-phase state flows through the relay pipes 405, 408, and 407 of the relay unit 4C into the auxiliary heat exchanger 72 acting as a condenser.
  • the refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium and condenses to become a high-pressure liquid state.
  • the high-pressure liquid refrigerant flows through the relay pipes 414, 415, and 417 of the relay unit 4C into the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65.
  • the high-pressure refrigerant flowing through the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65 exchanges heat with the low-pressure refrigerant flowing through the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65 and is cooled.
  • the refrigerant that flows out of the inter-refrigerant heat exchanger 65 is branched at the branching section 613, with a part of it flowing toward the load device 3 and the remaining part flowing through the fifth bypass pipe 505.
  • the high-pressure liquid refrigerant that is diverted at the branch point 613 and flows toward the load device 3 passes through the relay pipes 417, 413, and 411 of the relay unit 4C and flows into the load-side throttle device 32, where it is decompressed and expanded to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the load-side heat exchanger 31, which acts as an evaporator.
  • the refrigerant that flows into the load-side heat exchanger 31 exchanges heat with the indoor air sent by the load-side blower 33, causing the liquid phase to evaporate and become gaseous (single phase). At that time, the indoor air is cooled and cooling is performed in the room.
  • the high-pressure liquid refrigerant branched off at the branching section 613 flows into the fifth bypass throttle device 55, where it is decompressed and expanded to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant flows into the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65.
  • the high-pressure refrigerant flowing through the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65 exchanges heat with the high-pressure refrigerant flowing through the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65, and is heated.
  • the low-temperature, low-pressure gaseous refrigerant flowing out of the load-side heat exchanger 31 passes through the relay pipes 404 and 406 of the relay unit 4C, and merges with the two-phase gas-liquid refrigerant that has flowed through the fifth bypass pipe 505 at the branch point 612.
  • the refrigerant flowing through the relay pipe 406 becomes a gas-dominated two-phase gas-liquid refrigerant.
  • the gas-dominated two-phase gas-liquid refrigerant passes through the flow path switching device 22 and the accumulator 25, flows back into the compressor 21, is compressed, and is discharged in a high-temperature, high-pressure gaseous state. This cycle is repeated during cooling operation of the refrigeration cycle device 1C.
  • the refrigerant flowing out of the auxiliary heat source unit 7 is in a liquid state, but depending on the number of auxiliary heat source units 7 and load devices 3 in operation and their operating conditions, the refrigerant flowing out of the auxiliary heat source unit 7 may be in a two-phase gas-liquid state.
  • the two-phase gas-liquid refrigerant flows through the relay pipes 414, 415, and 417 of the relay unit 4C and flows into the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65, it exchanges heat with the refrigerant flowing in the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65 and becomes liquid. Therefore, by providing the inter-refrigerant heat exchanger 65, the refrigerant flowing through the branching section 613 is in a liquid state regardless of the phase state when it flows out of the auxiliary heat source unit 7.
  • FIG. 15 is a refrigerant circuit diagram showing the flow of the refrigerant during the heating operation of the refrigeration cycle apparatus 1C according to the first embodiment.
  • the control device 100 performs the heating operation by switching the flow path switching device 22 so that the suction side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the control device 100 opens the on-off valves 42 and 45 and closes the on-off valves 43 and 44.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows through the relay pipes 405 and 404 of the relay device 4C into the load side heat exchanger 31 acting as a condenser.
  • the refrigerant that flows into the load side heat exchanger 31 exchanges heat with the indoor air sent by the load side blower 33, condenses, and becomes a low-temperature liquid state. At that time, the indoor air is heated, and heating is performed in the room.
  • the low-temperature, high-pressure refrigerant in a liquid state passes through the relay pipes 411, 412, and 417 of the relay unit 4C and flows into the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65.
  • the high-pressure refrigerant flowing through the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65 exchanges heat with the low-pressure refrigerant flowing through the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65, and is cooled.
  • the refrigerant that flows out of the inter-refrigerant heat exchanger 65 is branched at the branching section 613, and a part of it flows toward the auxiliary heat source unit 7, and the remaining part flows through the fourth bypass pipe 504.
  • the low-temperature, high-pressure liquid refrigerant flowing toward the auxiliary heat exchanger 72 which is branched at the branching section 613, flows through the relay pipes 417, 416, and 414 of the relay unit 4C, and enters the auxiliary side throttle device 71, where it is decompressed and becomes a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant flows into the auxiliary heat exchanger 72, which acts as an evaporator.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium, evaporating the liquid phase and becoming a gas (single phase).
  • the low-temperature, high-pressure liquid refrigerant branched at the branching section 613 flows into the fifth bypass side throttle device 55, where it is decompressed and expanded to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant flows into the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65.
  • the low-pressure refrigerant flowing through the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65 exchanges heat with the high-pressure refrigerant flowing through the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65, and is heated.
  • the low-temperature, low-pressure gas-state refrigerant that flows out of the auxiliary heat exchanger 72 passes through the relay pipes 407, 409, and 406 of the relay unit 4C, and merges with the gas-liquid two-phase refrigerant that flows through the fifth bypass pipe 505 at the branch point 611. As a result, the refrigerant flowing through the relay pipe 406 becomes a gas-based two-phase refrigerant.
  • the low-temperature, low-pressure gas-based two-phase refrigerant flows into the heat source side heat exchanger 23, which acts as an evaporator.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air supplied by the heat source side blower 24, evaporating the liquid phase portion and becoming a low-pressure gas refrigerant (single phase).
  • the low-pressure gas refrigerant that flows out of the heat source side heat exchanger 23 passes through the flow switching device 22 and the accumulator 25, flows into the compressor 21 again, is compressed, and is discharged in a high-temperature, high-pressure gas state. This cycle is repeated during heating operation of the refrigeration cycle device 1C.
  • the refrigerant flowing out of the load device 3 may be in a two-phase gas-liquid state.
  • the refrigerant in the two-phase gas-liquid state flows through the relay pipes 411, 412, and 417 of the relay unit 4C and flows into the first refrigerant flow path 651 of the inter-refrigerant heat exchanger 65, it is heat exchanged with the refrigerant flowing in the second refrigerant flow path 652 of the inter-refrigerant heat exchanger 65 and becomes liquid. Therefore, by providing the inter-refrigerant heat exchanger 65, the refrigerant flowing through the branch section 613 is in a liquid state regardless of the phase state when it flows out of the auxiliary heat source unit 7.
  • a throttling device provided in the bypass piping is opened so that a portion of the refrigerant flowing toward the auxiliary heat exchanger 72 acting as an evaporator or the load side heat exchanger 31 bypasses the auxiliary heat exchanger 72 or the load side heat exchanger 31. Therefore, the refrigeration cycle apparatus 1C can suppress a decrease in the energy saving performance.
  • the refrigerant flowing through the branch 613 is in a gas-liquid two-phase state, it may be difficult to adjust the distribution of the refrigerant flow rate between the load device 3 or auxiliary heat source unit 7 acting as an evaporator and the fifth bypass pipe 505, and the refrigerant may not be distributed appropriately.
  • the refrigerant in either a gas or liquid state may be biased toward the evaporator side or the fifth bypass pipe 505 side. In this case, the energy-saving performance of the refrigeration cycle device 1C may be reduced.
  • the refrigerant flowing through the branch 613 is in a liquid state by providing the refrigerant-to-refrigerant heat exchanger 65.
  • the refrigeration cycle device 1C can suppress the deterioration of energy saving performance.
  • FIG. 16 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of a refrigeration cycle apparatus 1D according to embodiment 6.
  • the refrigeration cycle apparatus 1D of embodiment 6 differs from the refrigeration cycle apparatus 1 of embodiment 1 in that it has a gas-liquid separator 66.
  • the following description will focus on the differences from the refrigeration cycle apparatus 1D of embodiment 1, and will omit a description of the commonalities.
  • the relay unit 4D has a gas-liquid separator 66.
  • the gas-liquid separator 66 is provided in the relay pipe 403 between the part where the connection pipe 802 is connected and the on-off valve 41.
  • the second bypass pipe 502 is also connected to the gas-liquid separator 66.
  • the gas-liquid separator 66 separates the refrigerant that has flowed into the gas-liquid separator 66 into a gas phase and a liquid phase, and causes the refrigerant in the gas state to flow out to the relay pipe 403 and the refrigerant in the liquid state to flow out to the second bypass pipe 502.
  • the refrigeration cycle apparatus 1D has a gas-liquid separator 66. Therefore, during cooling operation, gaseous refrigerant can be selectively distributed to the auxiliary heat exchanger 72. This improves the condensation performance of the auxiliary heat exchanger 72. In addition, since the amount of liquid refrigerant circulating through the first bypass piping 501 can be increased, the liquid phase ratio of the refrigerant from the branching section 601 to the compressor 21 is improved. Therefore, the refrigeration cycle apparatus 1D can suppress a decrease in energy saving performance.
  • FIG. 17 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 1E according to embodiment 6. As shown in Fig. 17, the refrigeration cycle apparatus 1E of embodiment 6 differs from the refrigeration cycle apparatus 1 of embodiment 1 in that a heat medium temperature measuring device 93 is provided in a heat medium pipe 901. The following description will focus on the differences from the refrigeration cycle apparatus 1E of embodiment 1, and will omit a description of the commonalities.
  • the heat medium temperature measuring device 93 is provided in the heat medium pipe 901.
  • the heat medium temperature measuring device 93 measures the temperature of the heat medium flowing through the water circuit.
  • the heat medium temperature measuring device 93 transmits the measurement result to the control device 100.
  • FIG. 18 is a functional block diagram of a refrigeration cycle apparatus 1E according to embodiment 6.
  • the control device 100 controls the opening degrees of the first bypass side throttle device 51 and the second bypass side throttle device 52 based on the measurement results of the heat medium temperature measuring device 93. Specifically, the control device 100 determines the opening degrees of the first bypass side throttle device 51 and the second bypass side throttle device 52 in an integrated manner so that the heat recovery ratio and the heat dissipation ratio of the heat source unit 2 and the auxiliary heat source unit 7 fall within a predetermined range.
  • the amount of heat recovered by the auxiliary heat source unit 7 from the heat source can be estimated by measuring the temperature and pressure of the refrigerant undergoing latent heat change.
  • the correlation between the temperature and pressure information and the latent heat it possesses is low, making it difficult to estimate the amount of heat recovered.
  • the refrigeration cycle device 1E performs heat exchange between the refrigerant flowing through the refrigerant circuit and the heat medium flowing through the water circuit 8.
  • a heat medium temperature measuring device 93 is provided in the heat medium piping 901 to measure the temperature of the heat medium. Then, by adjusting the opening of the first bypass side throttle device 51 and the second bypass side throttle device 52 based on the measurement result of the heat medium temperature, the heat recovery ratio and heat dissipation ratio of the heat source unit 2 and the auxiliary heat source unit 7 can be controlled. This makes it possible to improve energy saving performance. Furthermore, by using a heat medium with small latent heat change, it is possible to more accurately control the heat recovery ratio and heat dissipation ratio of the heat source unit 2 and the auxiliary heat source unit 7 based on the measurement result of the heat medium temperature.
  • Fig. 19 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of the refrigeration cycle apparatus 1F according to embodiment 7.
  • the refrigeration cycle apparatus 1F according to embodiment 6 differs from the refrigeration cycle apparatus 1 according to embodiment 1 in that it has a plurality of load devices 3a and 3b.
  • the differences from the refrigeration cycle apparatus 1 according to embodiment 1 will be mainly described, and a description of the commonalities will be omitted.
  • the refrigeration cycle device 1F has load devices 3a and 3b.
  • the load device 3a and the relay unit 4E are connected by connection pipes 803a and 804a.
  • the load device 3b and the relay unit 4E are connected by connection pipes 803b and 804b.
  • the load device 3a has a load-side pipe 301a.
  • the load device 3 also has a load-side heat exchanger 31a, a load-side throttle device 32a, and a load-side blower 33a.
  • the load side pipe 301a is a pipe provided inside the housing (not shown) of the load device 3a, and one end is connected to the connection pipe 803a and the other end is connected to the connection pipe 804a.
  • the load side pipe 301a connects the load side heat exchanger 31a and the load side throttle device 32a. Refrigerant flows inside the load side pipe 301a.
  • the load side heat exchanger 31a, the load side throttling device 32a, and the load side blower 33a of the load device 3a of embodiment 7 have the same configuration as the load side heat exchanger 31, the load side throttling device 32, and the load side blower 33 of the load device 3 of embodiment 1. For this reason, detailed explanations of the load side heat exchanger 31a, the load side throttling device 32a, and the load side blower 33a of the load device 3a of embodiment 7 will be omitted.
  • the load device 3b has a load-side pipe 301b.
  • the load device 3 also has a load-side heat exchanger 31b, a load-side throttle device 32b, and a load-side blower 33b.
  • the load side pipe 301b is a pipe provided inside the housing (not shown) of the load device 3b, and one end is connected to the connection pipe 803b and the other end is connected to the connection pipe 804b.
  • the load side pipe 301b connects the load side heat exchanger 31b and the load side throttle device 32b.
  • a refrigerant flows inside the load side pipe 301b.
  • the load side heat exchanger 31b, the load side throttling device 32b, and the load side blower 33b of the load device 3b of embodiment 7 have the same configuration as the load side heat exchanger 31, the load side throttling device 32, and the load side blower 33 of the load device 3 of embodiment 1. For this reason, detailed explanations of the load side heat exchanger 31b, the load side throttling device 32b, and the load side blower 33b of the load device 3b of embodiment 7 will be omitted.
  • the relay unit 4E has relay pipes 401 to 403, a first bypass pipe 501, and a second bypass pipe 502.
  • the relay unit 4E also has a first bypass side throttle device 51, a second bypass side throttle device 52, and opening and closing valves 48a, 48b, 49a, and 49b.
  • relay pipe 401 One end of relay pipe 401 is connected to connection pipe 801, and the other end is connected to connection pipes 803a and 803b. In other words, relay pipe 401 branches out to correspond to load devices 3a and 3b.
  • One end of relay pipe 402 is connected to connection pipe 805, and the other end is connected to connection pipes 803b and 804b. In other words, relay pipe 402 branches out to correspond to load devices 3a and 3b.
  • the on-off valve 48a is a valve provided at a branch portion of the relay pipe 401 corresponding to the load device 3a side.
  • the on-off valve 48a switches between an open state that allows the flow of refrigerant through the relay pipe 401 and a closed state that blocks the flow of refrigerant through the relay pipe 401.
  • the on-off valve 48b is a valve provided at a branch portion of the relay pipe 401 corresponding to the load device 3b side.
  • the on-off valve 48b switches between an open state that allows the flow of refrigerant through the relay pipe 401 and a closed state that blocks the flow of refrigerant through the relay pipe 401.
  • the on-off valve 49a is a valve provided at a branch portion of the relay pipe 402 corresponding to the load device 3a side.
  • the on-off valve 49a switches between an open state that allows the flow of refrigerant through the relay pipe 402 and a closed state that blocks the flow of refrigerant through the relay pipe 402.
  • the on-off valve 49b is a valve provided at a branch portion of the relay pipe 402 corresponding to the load device 3b side.
  • the on-off valve 49b switches between an open state that allows the flow of refrigerant through the relay pipe 402 and a closed state that blocks the flow of refrigerant through the relay pipe 402.
  • FIG. 20 is a functional block diagram showing a control device 100 according to the seventh embodiment.
  • the control device 100 is connected to the compressor 21, the flow path switching device 22, the heat source side blower 24, the load side throttling device 32, the load side blower 33, the on-off valves 40 and 41, the first bypass side throttling device 51, the second bypass side throttling device 52, the auxiliary side throttling device 71, and the water pump 91 so as to be able to communicate wirelessly or by wire.
  • the control device 100 controls the on-off valves to the open state when blocking the flow of refrigerant to the load device 3.
  • the control device 100 performs the cooling operation by switching the flow path switching device 22 so that the discharge side of the compressor 21 and the heat source side heat exchanger 23 are connected. In the cooling operation, the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature and high-pressure gas state.
  • the high-temperature and high-pressure gas state (single phase) refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and flows into the heat source side heat exchanger 23 acting as a condenser.
  • the refrigerant that flows into the heat source side heat exchanger 23 is heat exchanged with the outdoor air sent by the heat source side blower 24, condenses, and becomes a high-temperature and high-pressure gas-liquid two-phase state.
  • the high-temperature, high-pressure refrigerant in a gas-liquid two-phase state flows into the auxiliary heat exchanger 72, which acts as a condenser.
  • the refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium and condenses to become a high-pressure liquid.
  • the high-pressure liquid refrigerant is branched at the branching section 602, with a portion flowing toward the load device 3 and the remainder flowing through the first bypass piping 501.
  • the high-pressure liquid refrigerant that flows toward the load device 3 after being diverted at the diverging portion 602 is further diverted at the diverging portion of the relay pipe 402 that diverges corresponding to the load devices 3a and 3b.
  • the refrigerant diverted to the load devices 3a and 3b then flows into the load side throttle devices 32a and 32b, where it is decompressed and expanded to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the load side heat exchangers 31a and 31b that act as evaporators.
  • the refrigerant that flows into the load side heat exchangers 31a and 31b exchanges heat with the indoor air sent by the load side fans 33a and 33b, evaporating the liquid phase and becoming a gaseous state (single phase). At this time, the indoor air is cooled to perform indoor cooling.
  • the high-pressure liquid refrigerant that is branched off at the branching section 602 flows into the first bypass side throttle device 51, where it is decompressed and expanded to become a low-temperature, low-pressure, gas-liquid two-phase refrigerant.
  • the low-temperature, low-pressure gaseous refrigerant flowing out of the load-side heat exchangers 31a and 31b of the load devices 3a and 3b merges with the relay pipe 401 at a branching point that branches off corresponding to the load devices 3a and 3b.
  • the refrigerant merged at this branching point further merges with the gas-liquid two-phase refrigerant that flowed through the first bypass pipe 501 at branching point 601.
  • the refrigerant flowing through the relay pipe 401 becomes a gas-based two-phase refrigerant.
  • the gas-based two-phase refrigerant passes through the flow path switching device 22 and flows back into the compressor 21, where it is compressed and discharged in a high-temperature, high-pressure gaseous state. This cycle is repeated during the cooling operation of the refrigeration cycle device 1F.
  • FIG. 21 is a refrigerant circuit diagram showing the flow of the refrigerant during the heating operation of the refrigeration cycle apparatus 1F according to the seventh embodiment.
  • the control device 100 performs the heating operation by switching the flow path switching device 22 so that the suction side of the compressor 21 and the heat source side heat exchanger 23 are connected.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature and high-pressure gas state.
  • the high-temperature and high-pressure gas state refrigerant discharged from the compressor 21 passes through the flow path switching device 22 and is diverted at the branching portion of the relay pipe 401 that branches corresponding to the load devices 3a and 3b. Then, the refrigerant diverted corresponding to the load devices 3a and 3b flows into the load side heat exchangers 31a and 31b that act as condensers.
  • the refrigerant that flows into the load side heat exchangers 31a and 31b is heat exchanged with the indoor air sent by the load side blowers 33a and 33b, condenses, and becomes a low-temperature liquid state. At that time, the indoor air is heated, and heating is performed in the room.
  • the low-temperature, high-pressure liquid refrigerant flowing out from the load-side heat exchangers 31a and 31b joins together at a branching portion of the relay pipe 402 that branches off corresponding to the load devices 3a and 3b.
  • the refrigerant joined at this branching portion is divided at a branching section 603, and a part of the refrigerant flows toward the auxiliary heat source unit 7 and the remaining part flows through the second bypass pipe 502.
  • the low-temperature, high-pressure liquid refrigerant that flows toward the auxiliary heat exchanger 72 after being diverted at the branching section 603 is decompressed by the auxiliary side throttle device 71 and becomes a low-temperature, low-pressure, two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant flows into the auxiliary heat exchanger 72, which acts as an evaporator.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows into the auxiliary heat exchanger 72 exchanges heat with the heat medium, evaporating the liquid phase and becoming a gas (single phase).
  • the low-temperature, high-pressure liquid refrigerant that is branched off at the branching section 603 flows into the second bypass side throttle device 52, where it is decompressed and expanded to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that flows into the heat source side heat exchanger 23 exchanges heat with the outdoor air supplied by the heat source side blower 24, evaporating the liquid phase, and becoming a low-pressure gas refrigerant (single phase).
  • the low-pressure gas refrigerant that flows out of the heat source side heat exchanger 23 passes through the flow switching device 22 and flows back into the compressor 21, where it is compressed and discharged in a high-temperature, high-pressure gas state. This cycle is repeated during the heating operation of the refrigeration cycle device 1F.
  • a throttling device provided in the bypass piping is opened so that a portion of the refrigerant flowing toward the auxiliary heat exchanger 72 acting as an evaporator or the load side heat exchanger 31 bypasses the auxiliary heat exchanger 72 or the load side heat exchanger 31. Therefore, the refrigeration cycle apparatus 1F can suppress a decrease in the energy saving performance.
  • Fig. 22 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 1G according to embodiment 8.
  • the refrigeration cycle apparatus 1G of embodiment 8 is different from the refrigeration cycle apparatus 1G of embodiment 1 in that, as shown in Fig. 22, the refrigeration cycle apparatus 1G of embodiment 8 includes a first refrigerant temperature measuring device 67 and a first refrigerant pressure measuring device 68, and performs control to vary the opening degrees of the first bypass side throttle device 51 and the second bypass side throttle device 52 during operation.
  • the following mainly describes the differences from the refrigeration cycle apparatus 1G of embodiment 1, and a description of the commonalities will be omitted.
  • the relay unit 4F has a first refrigerant temperature measuring device 67 and a first refrigerant pressure measuring device 68.
  • the first refrigerant temperature measuring device 67 is provided in the relay pipe 402 between the branching section 602 and the connection position of the connection pipe 804.
  • the first refrigerant temperature measuring device 67 measures the temperature of the refrigerant flowing through the relay pipe 402.
  • the first refrigerant temperature measuring device 67 transmits the measurement result to the control device 100.
  • the first refrigerant pressure measuring device 68 is provided in the relay pipe 402 between the branching section 602 and the connection position of the connection pipe 804.
  • the first refrigerant pressure measuring device 68 measures the pressure of the refrigerant flowing through the relay pipe 402.
  • the first refrigerant pressure measuring device 68 transmits the measurement result to the control device 100.
  • control device 100 is connected to the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68, the compressor 21, the flow path switching device 22, the heat source side blower 24, the load side throttling device 32, the load side blower 33, the on-off valves 40, 41, 48 and 49, the first bypass side throttling device 51, the second bypass side throttling device 52, the auxiliary side throttling device 71, and the water pump 91 so as to be able to communicate wirelessly or by wire.
  • the control device 100 changes the opening degree of the first bypass side throttling device 51 based on the measurement results of the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68. Specifically, the control device 100 calculates the degree of subcooling of the refrigerant from the measurement results of the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68. The control device 100 steadily controls the opening degree of the first bypass side throttle device 51 so that the calculated degree of subcooling is within a preset control range.
  • the control device 100 may control the opening degree of the first bypass side throttle device 51 to be larger when the calculated degree of subcooling exceeds the upper limit of the preset control range, and to be smaller when the calculated degree of subcooling exceeds the lower limit of the preset control range.
  • the control device 100 changes the opening degree of the second bypass side throttle device 52 based on the measurement results of the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68. Specifically, the control device 100 estimates the phase state of the refrigerant at the inlet of the auxiliary heat source unit 7 from the measurement results of the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68. Then, the control device 100 controls the opening degree of the second bypass side throttle device 52 so that the refrigerant is in a liquid state at the inlet of the auxiliary heat source unit 7.
  • the opening degree of the first bypass side throttle device 51 is adjusted so that the degree of subcooling of the refrigerant passing through the relay pipe 402 is within a preset control range. This prevents the liquid refrigerant from exceeding the condensation saturation temperature, improving energy saving performance.
  • the opening degree of the second bypass side throttle device 52 is adjusted so that the refrigerant is in a liquid state at the inlet of the auxiliary heat source unit 7 during heating operation. This reduces the volumetric flow rate of the refrigerant supplied to the auxiliary heat source unit 7 and suppresses excessive supply of refrigerant, thereby reducing the pressure loss from the auxiliary heat exchanger 72 to the branching section 604. Therefore, the energy saving performance can be improved.
  • FIG. 24 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 1H according to a modified example of embodiment 8.
  • the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68 are provided between the branching portion 602 and the branching portion 603 in the relay pipe 402.
  • only control during cooling operation or only control during heating operation may be performed based on the measurement results of the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68.
  • FIG. 25 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 1I according to embodiment 9.
  • the refrigeration cycle apparatus 1I of embodiment 9 differs from the refrigeration cycle apparatus 1I of embodiment 8 in that it has a second refrigerant temperature measuring device 73 and a second refrigerant pressure measuring device 74.
  • the following description will focus on the differences from the refrigeration cycle apparatus 1I of embodiment 8, and will omit a description of the commonalities.
  • the auxiliary heat source unit 7A has a second refrigerant temperature measuring device 73 and a second refrigerant pressure measuring device 74.
  • the second refrigerant temperature measuring device 73 is provided in the auxiliary heat source side piping 701 between the connection position of the auxiliary heat exchanger 72 and the connection piping 806.
  • the second refrigerant temperature measuring device 73 measures the temperature of the refrigerant flowing through the outlet side of the auxiliary heat exchanger 72 in the auxiliary heat source side piping 701.
  • the second refrigerant temperature measuring device 73 transmits the measurement result to the control device 100.
  • the second refrigerant pressure measuring device 74 is provided in the relay pipe 402 between the branching section 602 and the connection position of the connection pipe 804.
  • the second refrigerant pressure measuring device 74 is provided in the auxiliary heat source side pipe 701 between the connection position of the auxiliary heat exchanger 72 and the connection pipe 806.
  • the second refrigerant pressure measuring device 74 measures the pressure of the refrigerant flowing through the outlet side of the auxiliary heat exchanger 72 in the auxiliary heat source side pipe 701.
  • the second refrigerant pressure measuring device 74 transmits the measurement result to the control device 100.
  • 26 is a functional block diagram showing a control device 100 according to the ninth embodiment.
  • the control device 100 is connected to the first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68, the second refrigerant temperature measuring device 73 and the second refrigerant pressure measuring device 74, the compressor 21, the flow path switching device 22, the heat source side blower 24, the load side throttling device 32, the load side blower 33, the on-off valves 40, 41, 48 and 49, the first bypass side throttling device 51, the second bypass side throttling device 52, the auxiliary side throttling device 71, and the water pump 91 so as to be able to communicate wirelessly or by wire.
  • the control device 100 changes the opening degree of the auxiliary side throttling device 71 based on the measurement results of the second refrigerant temperature measuring device 73 and the second refrigerant pressure measuring device 74. Specifically, the control device 100 estimates the phase state of the refrigerant at the outlet of the auxiliary heat source unit 7 from the measurement results of the second refrigerant temperature measuring device 73 and the second refrigerant pressure measuring device 74. The control device 100 then controls the opening of the auxiliary throttle device 71 so that the refrigerant becomes a superheated gas at the inlet of the auxiliary heat source unit 7.
  • the opening degree of the auxiliary side throttle device 71 is adjusted so that the liquid refrigerant becomes a superheated gas in the auxiliary heat exchanger 72. Therefore, the heat exchange efficiency in the auxiliary heat exchanger 72 can be improved.
  • the opening degree of the second bypass side throttle device 52 is adjusted so that the refrigerant becomes a liquid state at the inlet of the auxiliary heat source unit 7 during heating operation. In other words, the liquid state refrigerant flows through the second bypass piping 502.
  • the refrigeration cycle device 1I can improve the energy saving performance.
  • the second refrigerant temperature measuring device 73 and the second refrigerant pressure measuring device 74 are not particularly limited as long as they are capable of measuring the temperature and pressure of the refrigerant flowing through the outlet side of the auxiliary heat exchanger 72.
  • they may be provided on any of the piping between the heat source side heat exchanger 23 of the heat source unit 2 and the auxiliary heat exchanger 72 of the auxiliary heat source unit 7.
  • the heat medium temperature measuring device 93 described in embodiment 6 may be provided in the refrigeration cycle device of another embodiment, and similar control may be performed.
  • multiple load devices 3 may be provided in embodiments 2 to 6, as described in embodiment 7, multiple load devices 3 may be provided.
  • multiple auxiliary heat source units 7 may be provided.
  • first refrigerant temperature measuring device 67 and the first refrigerant pressure measuring device 68, and the second refrigerant temperature measuring device 73 and the second refrigerant pressure measuring device 74 described in embodiments 8 and 9 may be provided in the refrigeration cycle device of another embodiment, and similar control may be performed.
  • the relay unit 4 may be omitted from the refrigeration cycle device 1 of embodiment 1. Even if the heat source unit 2, the load device 3, and the auxiliary heat source unit 7 are connected without the relay unit 4, the same effect as in embodiment 1 can be obtained by providing a bypass pipe and a bypass side throttle device, and opening the bypass side throttle device so that a portion of the refrigerant flowing toward the evaporator passes through the bypass pipe.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente invention concerne un dispositif à cycle de réfrigération qui comprend une machine de source de chaleur, une machine de source de chaleur auxiliaire et un dispositif de charge. La machine de source de chaleur, la machine de source de chaleur auxiliaire et le dispositif de charge sont reliés par une pluralité de tuyaux à travers lesquels s'écoule un fluide frigorigène. La machine de source de chaleur comprend un compresseur qui comprime le fluide frigorigène et un échangeur thermique côté source de chaleur qui échange de la chaleur entre le fluide frigorigène et un premier fluide. La machine de source de chaleur auxiliaire comprend un échangeur thermique auxiliaire qui échange de la chaleur entre le fluide frigorigène et un deuxième fluide qui a de la chaleur dérivée d'énergie renouvelable ou de chaleur perdue et qui est thermiquement indépendant du premier fluide. Le dispositif de charge comprend un échangeur thermique côté charge qui échange de la chaleur entre le fluide frigorigène et un troisième fluide qui doit être chauffé ou refroidi. Le dispositif à cycle de réfrigération comporte un tuyau de dérivation qui contourne l'échangeur thermique auxiliaire ou l'échangeur thermique côté charge qui agit comme un évaporateur, un dispositif d'étranglement côté dérivation qui est disposé dans le tuyau de dérivation et réduit la pression du fluide frigorigène, ainsi qu'un dispositif de commande qui commande le dispositif d'étranglement côté dérivation. Le dispositif de commande ouvre le dispositif d'étranglement côté dérivation de telle sorte qu'une partie du fluide frigorigène s'écoulant vers l'échangeur thermique auxiliaire ou l'échangeur thermique côté charge qui agit en tant qu'évaporateur passe à travers le tuyau de dérivation.
PCT/JP2023/020816 2023-06-05 2023-06-05 Dispositif à cycle de réfrigération Pending WO2024252470A1 (fr)

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JP2025525446A JPWO2024252470A1 (fr) 2023-06-05 2023-06-05
PCT/JP2023/020816 WO2024252470A1 (fr) 2023-06-05 2023-06-05 Dispositif à cycle de réfrigération

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PCT/JP2023/020816 WO2024252470A1 (fr) 2023-06-05 2023-06-05 Dispositif à cycle de réfrigération

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008275214A (ja) * 2007-04-26 2008-11-13 Osaka Gas Co Ltd 圧縮式ヒートポンプ装置
JP2015218939A (ja) * 2014-05-16 2015-12-07 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置
JP6958769B1 (ja) * 2021-02-02 2021-11-02 三菱電機株式会社 冷凍サイクル装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008275214A (ja) * 2007-04-26 2008-11-13 Osaka Gas Co Ltd 圧縮式ヒートポンプ装置
JP2015218939A (ja) * 2014-05-16 2015-12-07 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置
JP6958769B1 (ja) * 2021-02-02 2021-11-02 三菱電機株式会社 冷凍サイクル装置

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