WO2024252473A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2024252473A1
WO2024252473A1 PCT/JP2023/020819 JP2023020819W WO2024252473A1 WO 2024252473 A1 WO2024252473 A1 WO 2024252473A1 JP 2023020819 W JP2023020819 W JP 2023020819W WO 2024252473 A1 WO2024252473 A1 WO 2024252473A1
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WIPO (PCT)
Prior art keywords
heat
heat source
refrigerant
heat exchanger
heat medium
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.)
Ceased
Application number
PCT/JP2023/020819
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English (en)
Japanese (ja)
Inventor
宏亮 浅沼
亮宗 石村
宗史 池田
幸二 古谷
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Priority to PCT/JP2023/020819 priority Critical patent/WO2024252473A1/fr
Priority to JP2025525449A priority patent/JPWO2024252473A1/ja
Publication of WO2024252473A1 publication Critical patent/WO2024252473A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/87—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling absorption or discharge of heat in outdoor units
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • 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 capable of multiple operations such as cooling, heating, and hot water supply, and in particular to a refrigeration cycle device that can reduce the load on the heat source side heat exchanger by using unused heat as a heat source.
  • the refrigeration cycle device disclosed in Patent Document 1 includes a heat source unit, a relay unit connected to the heat source unit by a high-pressure side connection pipe and a low-pressure side connection pipe, and a user side unit including an indoor unit and a hot water heat source circuit.
  • the relay unit has a first distribution section and a second distribution section that are configured so that two connection pipes extending from each user side unit can be selectively connected to the high-pressure side connection pipe or the low-pressure side connection pipe.
  • the first distribution section switches the connection between one connection pipe of each user side unit and the high-pressure side connection pipe or the low-pressure side connection pipe, so that each user side unit can individually perform heating operation, cooling operation, or hot water supply operation.
  • the refrigeration cycle device of Patent Document 1 balances the cooling load, heating load, and hot water load of multiple user units, improving the efficiency of the entire system.
  • Patent Document 2 air conditioning systems that use melted snow water or well water are known from the past (see, for example, Patent Document 2).
  • the snow and ice air conditioning system disclosed in Patent Document 2 comprises an indirect outdoor air cooling machine, a compression refrigeration cooling machine, and a snow and ice air conditioning machine.
  • the snow and ice air conditioning machine uses the cold energy of the snowy mountains to cool a refrigerant, which then cools the outdoor air supplied to the heat exchangers on the heat source side of the indirect outdoor air cooling machine and the compression refrigeration cooling machine.
  • the snow and ice air conditioning system of Patent Document 2 makes effective use of the cold energy of the snowy mountains, enabling energy-saving operation.
  • the refrigeration cycle device disclosed in Patent Document 1 can improve the COP by balancing the cooling load, heating load, and hot water load of the user unit, but the heating and cooling capacity required for the load in the corresponding usage situation of the user unit is borne by the heat source unit. Therefore, no further energy saving effect beyond the improvement of the COP of the refrigeration cycle device can be expected.
  • the snow and ice air conditioning system disclosed in Patent Document 2 can use the cold energy of snowy mountains to reduce the load on the indirect outdoor air cooler and the compression refrigeration cooler, but the refrigerant circuits of the indirect outdoor air cooler, the compression refrigeration cooler, and the snow and ice cooler are independent.
  • the snow and ice cooler supplies cooled outdoor air to the sensible heat exchanger of the indirect outdoor air cooler and the condenser of the compression refrigeration cooler, and the refrigerant circuits of the indirect outdoor air cooler and the compression refrigeration cooler are also independent, making it difficult to improve the efficiency of the entire system by balancing the load on the two coolers.
  • This disclosure has been made to solve the problems described above, and provides a refrigeration cycle device that improves COP by balancing the load between each user unit, and enables energy-saving operation of the entire system by utilizing an external heat source.
  • the refrigeration cycle device includes a heat source machine having a compressor for compressing a refrigerant, a heat source side heat exchanger, and a first flow path switching device for switching the flow path of the refrigerant, a high-pressure side pipe through which the refrigerant flows out of the heat source machine, a low-pressure side pipe through which the refrigerant flows into the heat source machine, a utilization side unit connected to the high-pressure side pipe and the low-pressure side pipe and having a utilization side heat exchanger and a first flow control device for controlling the flow rate of the refrigerant flowing to the utilization side heat exchanger, and a utilization side unit connected to the high-pressure side pipe and the low-pressure side pipe.
  • a heat medium relay unit having an intermediate heat exchanger for exchanging heat between the refrigerant and a heat medium carrying heat from an external heat source and a second flow control device for controlling a flow rate of the refrigerant flowing through the intermediate heat exchanger; a first branch unit for branching the high-pressure side piping and the low-pressure side piping to the user side unit and the heat medium relay unit, respectively, and connected to a first connection piping extending from the user side unit and the heat medium relay unit; and a second branch unit for branching the high-pressure side piping and the low-pressure side piping to the user side unit and the heat medium relay unit, respectively, and connected to a second connection piping extending from the user side unit and the heat medium relay unit.
  • the first flow switching device is configured to connect the refrigerant so that it flows from the discharge side of the compressor through the heat source side heat exchanger to the high-pressure side pipe and from the low-pressure side pipe to the suction side of the compressor when the heat source side heat exchanger functions as a condenser, and to connect the refrigerant so that it flows from the discharge side of the compressor to the high-pressure side pipe and from the low-pressure side pipe to the suction side of the compressor through the heat source side heat exchanger when the heat source side heat exchanger functions as an evaporator
  • the first branching section is configured to switch the connection between the first connection pipe and the high-pressure side pipe or the low-pressure side pipe
  • the second flow switching device is configured so that the heat medium heat exchanger can function as an auxiliary condenser when the heat source side heat exchanger functions as a condenser, and the heat medium heat exchanger can function as an auxiliary evaporator when the heat source side heat exchanger functions as an evaporator.
  • the heat medium converter can function to supplement the capacity of the heat source side heat exchanger. Since the heat medium converter is configured to exchange heat with the refrigerant of the refrigeration cycle device using an external heat source such as well water or geothermal heat, and part or all of the capacity of the heat source side heat exchanger can be supplemented by the external heat source, the refrigeration cycle device can be operated in a more energy-efficient manner than before.
  • FIG. 1 is a schematic diagram of a configuration of a refrigeration cycle device 100 according to a first embodiment.
  • 1 is an example of a circuit diagram showing a refrigeration cycle device 100 according to a first embodiment.
  • 3 is an explanatory diagram of a flow of a refrigerant when the refrigeration cycle apparatus 100 according to the first embodiment is performing a cooling operation.
  • FIG. FIG. 4 is a diagram showing usage states of heat medium relay units D1, D2 based on temperatures T, t1, and t2 of various parts of the refrigeration cycle apparatus 100 according to the first embodiment.
  • 3 is an explanatory diagram of a flow of a refrigerant when the refrigeration cycle apparatus 100 according to the first embodiment is performing a cooling-dominant operation.
  • FIG. 3 is an explanatory diagram of a flow of a refrigerant when the refrigeration cycle apparatus 100 according to the first embodiment is performing a heating operation.
  • FIG. 3 is an explanatory diagram of a flow of a refrigerant when the refrigeration cycle apparatus 100 according to the first embodiment is performing a heating-dominant operation.
  • FIG. 4 is a flowchart showing an operation of the refrigeration cycle apparatus 100 according to the first embodiment.
  • FIG. 2 is a Mollier diagram of the refrigeration cycle apparatus 100 according to the first embodiment during cooling operation.
  • FIG. 2 is a Mollier diagram of the refrigeration cycle apparatus 100 according to the first embodiment during cooling operation.
  • FIG. 2 is a Mollier diagram of the refrigeration cycle apparatus 100 according to the first embodiment during cooling-dominant operation.
  • FIG. 1 is an explanatory diagram of a flow of a refrigerant when the refrigeration cycle apparatus 100 according to the first embodiment is performing a heating-dominant operation.
  • FIG. 4 is a flowchart showing an operation of the refrigeration cycle apparatus 100
  • FIG. 11 is an example of a circuit diagram showing a refrigeration cycle device 200 according to a second embodiment.
  • FIG. FIG. 11 is a Mollier diagram during heating operation of the refrigeration cycle apparatus 200 according to the second embodiment.
  • 11 is an example of a circuit diagram showing a refrigeration cycle device 200 according to a second embodiment.
  • FIG. 11 is a Mollier diagram of the refrigeration cycle apparatus 200 according to the second embodiment during heating-dominated operation.
  • the user side unit C is, for example, an indoor air conditioner or water heater, and is supplied with refrigerant from the repeater B to perform indoor air conditioning or water heating through a refrigeration cycle.
  • Each user side unit C is connected in series to the repeater B and in parallel with each other. In FIG. 1, three user side units C are connected to the repeater B, but this number is not limited, and two or more user side units C may be installed, or there may be only one.
  • the user side unit C can be an indoor unit of an air conditioner, a water heater, a refrigerator, etc., and there is no limit to the equipment that can be connected.
  • the heat medium converter D is further connected to the relay unit B.
  • the heat medium converter D is connected to the relay unit B and is connected in a circuit configuration similar to that of the user unit C.
  • the heat medium converter D also receives refrigerant from the relay unit B, like the user unit C.
  • the heat medium converter D is further connected to an external heat source E.
  • the external heat source E and the heat medium converter D are connected by a circuit in which a heat medium different from the refrigerant flowing from the relay unit B circulates.
  • the external heat source E connected to the heat medium converter D has heat or cold, such as well water, geothermal heat, or sunlight.
  • the heat medium converter D is a device that transfers the heat or cold of the external heat source E to a refrigerant via a heat medium.
  • the external heat source E is well water
  • the well water is pumped up and circulated as a heat medium through the heat medium circulation circuit 34 (see FIG. 2).
  • geothermal heat is used as the external heat source E
  • a heat medium such as water heated by geothermal heat circulates through the heat medium circulation circuit 34.
  • sunlight is used as the external heat source E
  • a heat medium such as water heated by sunlight circulates through the heat medium circulation circuit 34.
  • Other examples of the external heat source E include ice and snow, melted snow, etc.
  • the external heat source E can also be unused heat such as heat from river water, exhaust gas from equipment, wastewater, and waste heat generated by equipment.
  • the heat medium, such as water, circulating through the heat medium circulation circuit 34 is heat exchanged with the refrigerant circulating through the heat source unit A, etc., in the heat medium heat exchanger 30 (see FIG. 2).
  • FIG. 1 multiple heat transfer devices D and external heat sources E are installed, but a single one may be used. In addition, multiple types of heat sources may be used as the external heat source E.
  • Whether the heat medium converter D is used as an evaporator or a condenser is determined based on whether the temperature of the external heat source E is high or low, based on the evaporation temperature and condensation temperature of the refrigerant in the refrigeration cycle that circulates through the heat source unit A, relay unit B, user unit C, and heat medium converter D.
  • the heat medium converter D is used as an evaporator
  • the heat medium converter D is used as a condenser.
  • the heat medium converter D when a relatively high-temperature external heat source E such as geothermal energy or sunlight is used, the heat medium converter D should be used as an evaporator, and when a relatively low-temperature external heat source E such as well water, snow and ice, or melted snow is used, the heat medium converter D should be used as a condenser.
  • a relatively high-temperature external heat source E such as geothermal energy or sunlight
  • a relatively low-temperature external heat source E such as well water, snow and ice, or melted snow
  • the heat medium converter D switches between using the first connection pipe 40 as an evaporator by directly connecting it to the low-pressure side pipe 6, and using the first connection pipe 40 as a condenser by directly connecting it to the high-pressure side pipe 7. Switching of operation using the heat medium converter D is performed by the second flow path switching device 10c (see Figure 2) provided in the relay unit B.
  • Figure 1 shows, as an example, a case where the topmost user side unit C1 is in heating operation, the second user side unit C2 from the top is in cooling operation, and the third user side unit from the top is in water boiling operation.
  • circuit configuration of refrigeration cycle device 100 is an example of a circuit diagram showing the refrigeration cycle apparatus 100 according to the first embodiment.
  • the heat source unit A and the relay unit B are connected by a low-pressure side pipe 6 and a high-pressure side pipe 7.
  • the high-pressure side pipe 7 is a pipe through which the high-pressure refrigerant compressed by the compressor 1 flows out, either directly or via the heat source side heat exchanger 3.
  • the low-pressure side pipe 6 is a pipe through which the low-pressure refrigerant that has passed through the user side unit C or the heat medium converter D flows in, and is a pipe for returning the refrigerant from the relay unit B to the heat source unit A.
  • the refrigerant in the high-pressure side pipe 7 flows into the high-pressure side branch 10a of the first branch 10 of the relay unit B.
  • the refrigerant in the high-pressure side branch 10a flows into the user unit C or the heat medium converter D by opening the high-pressure side solenoid valves 9c1, 9c2, 9d1, and 9d2 provided in the first branch 10.
  • the high-pressure side solenoid valves 9c1, 9c2, 9d1, and 9d2 may be collectively referred to as the high-pressure side solenoid valves 9.
  • the low-pressure side pipe 6 is connected to the low-pressure side branch 10b of the first branch 10 of the relay unit B.
  • the refrigerant from the user side unit C or the heat medium converter D flows into the low-pressure side branch 10b by opening the low-pressure side solenoid valves 8c1, 8c2, 8d1, and 8d2.
  • the low-pressure side solenoid valves 8c1, 8c2, 8d1, and 8d2 may be collectively referred to as the low-pressure side solenoid valves 8.
  • the low-pressure side solenoid valve 8 and the high-pressure side solenoid valve 9 are connected to first connection pipes 40c1, 40c2, 40d1, and 40d2, which are one of the pipes extending from the utilization side unit C and the heat medium converter D, respectively.
  • the first connection pipes 40c1, 40c2, 40d1, and 40d2 may be collectively referred to as the first connection pipes 40.
  • the other pipes extending from the user unit C and the heat medium converter D are called second connection pipes 41c1, 41c2, 41d1, and 41d2.
  • the second connection pipes 41c1, 41c2, 41d1, and 41d2 are connected to the second branch 11 of the relay unit.
  • the second connection pipes 41c1, 41c2, 41d1, and 41d2 may be collectively called second connection pipes 41.
  • the refrigerant flows from the second branch section 11 to the user side unit C and the heat medium converter D, respectively, or flows from the user side unit C and the heat medium converter D to the second branch section 11.
  • the refrigerant flows from the high pressure side branch 10a connected to the high pressure side pipe 7 through the high pressure side solenoid valve 9 into the user side unit C or the heat medium converter D, and the refrigerant that has passed through the user side unit C or the heat medium converter D flows into the second branch 11.
  • refrigerant that has passed through another user unit C, another heat medium converter D, or refrigerant that has been separated from the high-pressure side piping 7 by the gas-liquid separator 12 and passed through the first heat exchanger 17 and the second heat exchanger 16 flows from the second branch 11 into the user unit C or the heat medium converter D.
  • the refrigerant that has passed through the user unit C or the heat medium converter D passes through the low-pressure side solenoid valve 8 and flows from the low-pressure side branch 10b into the low-pressure side piping 6.
  • the first heat exchanger 17 and the second heat exchanger 16 are sometimes referred to as internal heat exchangers.
  • the relay unit B switches the connection state of the utilization side unit C or the heat medium converter D by switching the opening and closing of the low pressure side solenoid valve 8 and the high pressure side solenoid valve 9 of the first branch section 10. This switching allows the utilization side heat exchanger 5 of the utilization side unit C and the heat medium converter 30 of the heat medium converter D to switch between functioning as an evaporator or a condenser, respectively.
  • the first branching section 10 branches the high-pressure side pipe 7 and the low-pressure side pipe 6 for each of the user side units C and the heat medium converters D, and connects them to the first connection pipe 40, which is one of the pipes extending from each of the user side units C and the heat medium converters D.
  • the first branching section 10 controls whether the first connection pipe 40 of the user side units C and the heat medium converters D is connected to the high-pressure side pipe 7 or the low-pressure side pipe 6 by controlling the high-pressure side solenoid valve 9 and the low-pressure side solenoid valve 8 to close one and open the other.
  • the low-pressure side solenoid valve 8 and the high-pressure side solenoid valve 9 of the first branching section 10 may be collectively referred to as the second flow path switching device 10c.
  • the second flow path switching device 10c includes the high-pressure side solenoid valve 9 and the low-pressure side solenoid valve 8 provided for each of the user side units C and the heat medium converters D, but is not limited to this form and may be configured as a three-way valve to which the high-pressure side pipe 7, the low-pressure side pipe, and the first connection pipe 40 are connected, for example.
  • the heat source unit A is usually placed in a space such as a rooftop outside a building, and supplies cold or hot heat to the user units C1 and C2 via the relay unit B.
  • the heat source unit A is not limited to being placed outdoors, and may be placed in an enclosed space such as a machine room with a ventilation opening.
  • the heat source unit A may also be placed inside a building if the waste heat can be exhausted to the outside of the building through an exhaust duct.
  • the heat source unit A may be placed inside a building as a water-cooled outdoor unit.
  • the heat source unit A incorporates a compressor 1, a first flow path switching device 2 that switches the refrigerant flow direction of the heat source unit A, a heat source side heat exchanger 3, and an accumulator 29.
  • the compressor 1, the first flow path switching device 2, the heat source side heat exchanger 3, and the accumulator 29 are connected by a low pressure side pipe 6 and a high pressure side pipe 7.
  • the heat source side heat exchanger 3 is connected in series with the first flow control device 22.
  • a bypass pipe 25 having a second flow control device 26 is connected in parallel with the heat source side heat exchanger 3.
  • the second flow control device 26 can adjust the flow rate to adjust the amount of refrigerant that bypasses the heat source side heat exchanger 3.
  • an outdoor flow control device 3m is installed near the heat source side heat exchanger 3 to control the flow rate of a fluid such as outdoor air.
  • the outdoor air is sent to the heat source side heat exchanger 3 by the outdoor flow control device 3m, and heat exchange with the refrigerant is performed.
  • the outdoor flow control device 3m is, for example, a fan that sends outdoor air to the heat source side heat exchanger 3.
  • an air-cooled outdoor heat exchanger is used as an example of the heat source side heat exchanger 3
  • an outdoor fan is used as an example of the outdoor flow control device 3m.
  • the heat source side heat exchanger 3 may be a water-cooled outdoor heat exchanger or the like as long as the refrigerant exchanges heat with another fluid.
  • a pump is used as the outdoor flow control device 3m.
  • a heat medium such as outdoor air that exchanges heat with the refrigerant in the heat source side heat exchanger 3 may be referred to as a heat source heat medium. Note that, although the first embodiment illustrates a case in which there is one heat source side heat exchanger 3, multiple heat source side heat exchangers 3 may be provided.
  • the heat source unit A is also provided with a first connection pipe 60a, a second connection pipe 60b, a check valve 18, a check valve 19, a check valve 20, and a check valve 21.
  • the first connection pipe 60a, the second connection pipe 60b, the check valve 18, the check valve 19, the check valve 20, and the check valve 21 allow high-pressure refrigerant to flow out of the heat source unit A via the high-pressure side pipe 7.
  • the first connection pipe 60a, the second connection pipe 60b, the check valve 18, the check valve 19, the check valve 20, and the check valve 21 allow low-pressure refrigerant to flow into the heat source unit A via the low-pressure side pipe 6.
  • Compressor 1 draws in the refrigerant and compresses it to a high-temperature, high-pressure state, and is composed of, for example, an inverter compressor with a capacity controllable.
  • the first flow path switching device 2 switches between the flow of refrigerant during heating operation and the flow of refrigerant during cooling operation.
  • the first flow path switching device 2 switches between two connection states. In one connection state, the first pipe 27 and the bypass pipe 25 are connected to the discharge side of the compressor 1, and the low-pressure side pipe 6 is connected to an accumulator 29 provided on the suction side of the compressor 1.
  • the first pipe 27 is installed in parallel with the bypass pipe 25 and is a pipe leading to the heat source side heat exchanger 3.
  • the first pipe 27 and the bypass pipe 25 are connected to the accumulator 29 provided on the suction side of the compressor 1, and the discharge side of the compressor 1 is directly connected to the high-pressure side pipe 7.
  • the first flow path switching device 2 is exemplified as a four-way switching valve.
  • the heat source side heat exchanger 3 functions as an evaporator during heating operation and as a condenser or radiator during cooling operation.
  • the heat source side heat exchanger 3 exchanges heat between the refrigerant and the outdoor air, evaporating and gasifying the refrigerant or condensing and liquefying the refrigerant.
  • the outdoor flow control device 3m forms an air passage for the air flowing to the heat source side heat exchanger 3.
  • the accumulator 29 is provided on the suction side of the compressor 1, and stores surplus refrigerant due to differences between heating and cooling operations or surplus refrigerant due to transient changes in operation. Note that, although the first embodiment illustrates a case in which one heat source side heat exchanger 3 is provided, multiple heat source side heat exchangers 3 may be connected in parallel.
  • the check valve 18 is connected to the high-pressure side pipe 7 between the heat source side heat exchanger 3 and the relay unit B, and allows the refrigerant to flow only in the direction from the heat source unit A to the relay unit B.
  • the check valve 19 is provided in the low-pressure side pipe 6 between the relay unit B and the first flow path switching device 2, and allows the refrigerant to flow only in the direction from the relay unit B to the heat source unit A.
  • the check valve 20 is provided in the first connection pipe 60a, and allows the refrigerant discharged from the compressor 1 to flow to the relay unit B during heating operation.
  • the check valve 21 is provided in the second connection pipe 60b, and allows the refrigerant returning from the relay unit B to flow to the suction side of the compressor 1 via the heat source side heat exchanger 3 or the bypass pipe 25 during heating operation.
  • the first connection pipe 60a connects the low-pressure side pipe 6 between the first flow switching device 2 and the check valve 19 in the heat source unit A, and the high-pressure side pipe 7 between the check valve 18 and the relay unit B.
  • the second connection pipe 60b connects the low-pressure side pipe 6 between the check valve 19 and the relay unit B in the heat source unit A, and the high-pressure side pipe 7 between the heat source side heat exchanger 3 and the check valve 18.
  • the heat source unit A may also be provided with a discharge pressure gauge 51, a suction pressure gauge 52, a medium pressure pressure gauge 53, and a thermometer 54.
  • the discharge pressure gauge 51 is provided on the discharge side of the compressor 1 and measures the pressure of the refrigerant discharged from the compressor 1.
  • the suction pressure gauge 52 is provided on the suction side of the compressor 1 and measures the pressure of the refrigerant sucked into the compressor 1.
  • the medium pressure pressure gauge 53 is provided upstream of the check valve 18 and measures the medium pressure, which is the pressure of the refrigerant upstream of the check valve 18.
  • the thermometer 54 is provided on the discharge side of the compressor 1 and measures the temperature of the refrigerant discharged from the compressor 1.
  • the pressure information and temperature information detected by the discharge pressure gauge 51, the suction pressure gauge 52, the medium pressure pressure gauge 53, and the thermometer 54 are sent to the control device 50 that controls the operation of the refrigeration cycle device 100, and are used to control each actuator.
  • the bypass pipe 25 bypasses the heat source side heat exchanger 3.
  • the second flow control device 26 is provided midway through the bypass pipe 25 and is configured to be freely opened and closed, and controls the flow rate of the refrigerant flowing through the bypass pipe 25.
  • the second flow control device 26 adjusts the flow rate of the refrigerant flowing into the heat source side heat exchanger 3.
  • the second flow control device 26 is configured so that the flow path resistance changes continuously.
  • the relay unit B incorporates a first branching section 10, a second branching section 11, a gas-liquid separator 12, a first bypass pipe 14a, a second bypass pipe 14b, a third flow control device 13, a fourth flow control device 15, a first heat exchanger 17, a second heat exchanger 16, and a control device 50.
  • the control device 50 has the same configuration and function as the control device 50 of the heat source unit A.
  • the first branching section 10 branches the refrigerant flowing in the high-pressure side pipe 7 to the user side unit C and the heat medium converter D.
  • the first branching section 10 also merges the refrigerant flowing in the user side unit C and the heat medium converter D and allows it to flow into the low-pressure side pipe 6.
  • the first branching section 10 includes a low-pressure side solenoid valve 8 and a high-pressure side solenoid valve 9 installed in the first connection pipe 40 of the user side unit C and the heat medium converter D.
  • the first connection pipe 40 of the user side unit C and the heat medium converter D is branched at the first branching section 10, one of which is connected to the low-pressure side pipe 6 via the low-pressure side solenoid valve 8, and the other of which is connected to the high-pressure side pipe 7 via the high-pressure side solenoid valve 9.
  • the low-pressure side solenoid valve 8 and the high-pressure side solenoid valve 9 are controlled to open and close, so that the first connection pipe 40 of the user side unit C and the heat medium converter D can be switched to connect to either the low-pressure side pipe 6 or the high-pressure side pipe 7.
  • the low-pressure side solenoid valve 8 and the high-pressure side solenoid valve 9 provided in the relay unit B are collectively referred to as the second flow path switching device 10c.
  • the low-pressure side solenoid valve 8 and the high-pressure side solenoid valve 9 are installed in each pipe where the first connection pipe 40 is branched into two, but they may be configured using, for example, a three-way valve.
  • first connection pipe 40 of the user side unit C and the heat medium converter D is configured to connect to either the low-pressure side pipe 6 or the high-pressure side pipe 7.
  • the low-pressure side solenoid valve 8 and the high-pressure side solenoid valve 9 are preferably configured to be closed so that the refrigerant does not flow to any of the user side units C and the heat medium converters D.
  • the second branch section 11 branches the refrigerant flowing in the first bypass pipe 14a to the user unit C and the heat medium converter D.
  • the second branch section 11 also merges the refrigerant flowing in the user unit C and the heat medium converter D and causes it to flow into the second bypass pipe 14b.
  • the second branch section 11 has a junction between the first bypass pipe 14a and the second bypass pipe 14b.
  • the gas-liquid separator 12 is provided midway through the high-pressure side pipe 7, and separates the refrigerant that flows in through the high-pressure side pipe 7 into gas and liquid.
  • the gas phase portion separated by the gas-liquid separator 12 flows to the first branch section 10, and the liquid phase portion separated by the gas-liquid separator 12 flows to the second branch section 11.
  • the user side units C are installed at positions where they can supply conditioned air to a space to be air-conditioned, such as a room, and supply cooled air or heated air to the space to be air-conditioned by using cold or hot heat from the heat source unit A supplied via the relay unit B.
  • the user side units C1 and C2 each have a built-in user side heat exchanger 5c1, 5c2 and a first flow control device 4c1, 4c2.
  • Each of the utilization side heat exchangers 5c1 and 5c2 exchanges heat between the air supplied from the flow control device 5m and the refrigerant to generate heated air or cooled air to be supplied to the space to be air-conditioned.
  • the flow control device 5m forms an air path for the air flowing through the utilization side heat exchangers 5c1 and 5c2.
  • the first flow control devices 4c1 and 4c2 are provided between the second branching section 11 of the relay unit B and the utilization side heat exchanger 5c1 or 5c2, and are configured to be freely opened and closed.
  • the first flow control device 4c1 and the first flow control device 4c2 adjust the flow rate of the refrigerant flowing into the utilization side heat exchangers 5c1 and 5c2.
  • the heat medium relay unit D is for supplying heat or cold from an external heat source E to a refrigerant circulating in the refrigeration cycle apparatus 100.
  • the heat medium relay unit D incorporates an inter-heat medium heat exchanger 30 that exchanges heat between the refrigerant circulating in the heat source unit A, the relay unit B, and the user side unit C and a heat medium that carries heat from the external heat source E, and second flow control devices 4d1 and 4d2 that control the flow rate of the refrigerant circulating in the inter-heat medium heat exchanger 30.
  • the second flow control devices 4d1 and 4d2 are provided between the second branching section 11 of the relay unit B and the inter-heat medium heat exchanger 30d1 or 30d2, and are configured to be freely opened and closed.
  • the second flow control devices 4d1 and 4d2 adjust the flow rate of the refrigerant flowing into the inter-heat medium heat exchangers 30d1 and 30d2.
  • the heat medium is circulated through the heat medium circulation circuit 34 by the pump 31 and sent from the external heat source E to the heat medium-intermediate heat exchanger 30.
  • the heat medium-intermediate heat exchanger 30 is, for example, a plate-type heat exchanger, inside which the refrigerant and heat medium circulate, and the heat or cold of the heat medium is transferred to the refrigerant.
  • the heat medium converter D is equipped with external heat source temperature sensors 32 and 33.
  • the external heat source temperature sensor 32 detects the temperature of the heat medium flowing into the heat medium heat exchanger 30.
  • the external heat source temperature sensor 33 detects the temperature of the heat medium flowing out of the heat medium heat exchanger 30.
  • those connected to external heat sources E with different temperatures may be referred to as a first heat medium converter and a second heat medium converter, respectively.
  • the heat medium circulation circuit 34 may be configured to circulate an independent heat medium in the heat medium circulation circuit 34. As shown in FIG. 2, the heat medium circulation circuit 34 may be connected to an external heat exchanger F that exchanges heat between the external heat source E and the heat medium flowing through the heat medium circulation circuit 34. The external heat exchanger F exchanges heat between the heat medium and the external heat source E. The heat medium that has been heat exchanged in the external heat exchanger F is sent to the heat medium-to-heat medium heat exchanger 30 and is heat exchanged with the refrigerant circulating through the refrigerant circuit of the refrigeration cycle device 100.
  • the quality of the heat medium flowing through the heat medium circulation circuit 34 can be maintained, and the durability of the heat medium circulation circuit 34 and the heat medium converter D can be ensured, as opposed to pumping up well water as the heat medium, for example.
  • the configuration of the heat medium circulation circuit 34 may be changed as appropriate depending on what is used as the external heat source E.
  • the refrigeration cycle device 100 makes effective use of such an external heat source E to achieve energy savings.
  • the heat medium converters D1 and D2 can be installed in parallel on the relay unit B, so that multiple external heat sources E can be used for the refrigeration cycle device 100.
  • the heat source side heat exchanger 3 functions as a condenser
  • the heat medium converter D1 using the well water as the external heat source E1 also functions as a condenser, so that the capacity of the heat source side heat exchanger 3 during cooling operation or cooling-dominated operation can be supplemented by the heat medium converter D1.
  • the heat source side heat exchanger 3 functions as an evaporator
  • the heat medium converter D2 using sunlight as the external heat source E2 also functions as an evaporator, so that the capacity of the heat source side heat exchanger 3 during heating operation or heating-dominated operation can be supplemented by the heat medium converter D2.
  • the refrigeration cycle apparatus 100 can appropriately select the operating state of the multiple user side units C from cooling, heating, and water heating operation by switching the connection between the heat source unit A and the user side units C using the second flow path switching device 10c, thereby enabling simultaneous cooling and heating operation.
  • the refrigeration cycle apparatus 100 can appropriately switch the external heat source E to be used as an auxiliary for the heat source side heat exchanger 3 or as a substitute for the heat source side heat exchanger 3 by switching the connection state with the multiple heat medium converters D using the second flow path switching device 10c.
  • the refrigeration cycle apparatus 100 is provided with a control device 50.
  • the control device 50 controls actuators and the like based on refrigerant pressure information, refrigerant and heat medium temperature information, outdoor temperature information, indoor temperature information, and the like detected by each sensor provided in the refrigeration cycle apparatus 100.
  • the control device 50 controls driving of the compressor 1, switching between the first flow path switching device 2 and the second flow path switching device 10c, driving of the fan motor of the outdoor flow control device 3m, driving of the fan motor of the flow control device 5m, and the pump 31 that sends the heat medium to the heat source side heat exchanger 3.
  • the control device 50 controls the opening of the first flow control device 22, the second flow control device 26, the third flow control device 13, and the fourth flow control device 15.
  • the control device 50 includes a memory 50a in which information for determining each control value is stored.
  • the control device 50 may be configured with hardware such as a control circuit that realizes its functions.
  • the control device 50 may be configured with a software program stored in a storage unit such as a semiconductor memory, and a computing device such as a microcomputer or a CPU (central processing unit) that executes the software program.
  • the control device 50 is provided in the heat source unit A and the relay unit B, but the number of control devices 50 may be one or three or more.
  • the control device 50 may be provided in the user unit C or the heat medium converter D, or may be provided as a separate unit in a location other than the heat source unit A, the relay unit B, the user unit C, and the heat medium converter D.
  • the operation modes of the refrigeration cycle apparatus 100 include four modes: cooling operation, heating operation, cooling-dominated operation, and heating-dominated operation.
  • Cooling operation is an operation mode in which all user side units C are in cooling operation or stopped.
  • Heating operation is an operation mode in which all user side units C are in heating operation or stopped.
  • Cooling-dominated operation is an operation mode in which heating or cooling can be selected for each indoor unit, and the cooling load is greater than the heating load.
  • Cooling-dominated operation is an operation mode in which the heat source side heat exchanger 3 is connected to the discharge side of the compressor 1 and acts as a condenser.
  • Heating-dominated operation is an operation mode in which heating or cooling can be selected for each indoor unit, and the heating load is greater than the cooling load.
  • Heating-dominated operation is an operation mode in which the heat source side heat exchanger 3 is connected to the suction side of the compressor 1 and acts as an evaporator.
  • (Cooling operation) 3 is an explanatory diagram of the flow of refrigerant when the refrigeration cycle apparatus 100 according to the first embodiment is in cooling operation. A case of cooling operation in which all of the user side units C1 and C2 perform cooling will be described.
  • the control device 50 switches the first flow path switching device 2 so that the refrigerant discharged from the compressor 1 flows to the heat source side heat exchanger 3.
  • the low pressure side solenoid valves 8c1 and 8c2 connected to the user side units C1 and C2 are opened, and the high pressure side solenoid valves 9c1 and 9c2 are closed.
  • compressor 1 starts operating.
  • the low-temperature, low-pressure gaseous refrigerant is compressed by compressor 1 and discharged as high-temperature, high-pressure gaseous refrigerant.
  • the high-temperature, high-pressure gaseous refrigerant discharged from compressor 1 flows into heat source side heat exchanger 3 via first flow switching device 2.
  • the refrigerant is cooled while heating the outdoor air, becoming medium-temperature, high-pressure liquid refrigerant or gas-liquid two-phase refrigerant.
  • the medium-temperature, high-pressure refrigerant flowing out of heat source side heat exchanger 3 passes through high-pressure side piping 7 and is separated in gas-liquid separation device 12.
  • the liquid refrigerant separated by the gas-liquid separator 12 passes through the first bypass pipe 14a, exchanges heat with the refrigerant flowing through the second bypass pipe 14b in the first heat exchanger 17, passes through the third flow control device 13, exchanges heat with the refrigerant flowing through the second bypass pipe 14b in the second heat exchanger 16, is cooled, and flows into the second branch section 11.
  • a portion of the refrigerant that flows into the second branch 11 is bypassed to the second bypass piping 14b, and the remainder flows into the second connecting piping 41c1, 41c2 of the user side units C1, C2.
  • the high-pressure liquid or gas-liquid two-phase refrigerant branched at the second branch 11 flows through the second connecting piping 41c1, 41c2 and flows into the first flow control devices 4c1, 4c2 of the user side units C1, C2.
  • the high-pressure liquid refrigerant is then throttled and expanded by the first flow control devices 4c1, 4c2, reducing the pressure and becoming a low-temperature, low-pressure, two-phase gas-liquid state.
  • the change in the refrigerant at the first flow control devices 4c1, 4c2 is carried out under a constant enthalpy.
  • the low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows out of the first flow control devices 4c1, 4c2 flows into the user side heat exchangers 5c1, 5c2.
  • the refrigerant then heats up while cooling the indoor air, becoming a low-temperature, low-pressure gaseous refrigerant.
  • the low-temperature, low-pressure gaseous refrigerant flowing out of the user-side heat exchangers 5c1 and 5c2 passes through the low-pressure solenoid valves 8c1 and 8c2, respectively, and flows into the low-pressure branch 10b of the first branch 10.
  • the low-temperature, low-pressure gaseous refrigerant that joins in the low-pressure branch 10b also joins with the low-temperature, low-pressure gaseous refrigerant that has been heated in the first heat exchanger 17 and the second heat exchanger 16 of the second bypass piping 14b, passes through the low-pressure piping 6 and the first flow switching device 2, and flows into the compressor 1, where it is compressed.
  • the heat medium relays D1, D2 When the heat medium relays D1, D2 are connected to the refrigeration cycle device 100, it is determined whether or not to use the heat medium relays D1, D2 based on the magnitude relationship between the temperatures t1, t2 of the external heat sources E1, E2 and the temperature T flowing into the heat source side heat exchanger 3.
  • the external heat source temperature sensor 32 that measures the temperatures t1, t2 of the external heat sources E1, E2
  • the one installed in one of the heat medium relays D1 and D2 may be referred to as the first external heat source temperature sensor, and the other may be referred to as the second external heat source temperature sensor.
  • the temperature T is the temperature of the outside air sent to the heat source side heat exchanger 3
  • the temperature t1 is the temperature of the heat medium flowing into the heat medium heat exchanger 30d1 of the heat medium converter D1
  • the temperature t2 is the temperature of the heat medium flowing into the heat medium heat exchanger 30d2 of the heat medium converter D2.
  • the heat medium converters D1 and D2 are used when the heat medium temperatures t1 and t2 are lower than the temperature T of the outside air flowing into the heat source side heat exchanger 3.
  • the temperature T is measured by a temperature sensor 3t installed near the heat source side heat exchanger 3.
  • the temperature t1 is measured by an external heat source temperature sensor 32 installed upstream of the heat medium heat exchanger 30d1 of the heat medium circulation circuit 34 of the heat medium converter D1.
  • Temperature t2 is measured by an external heat source temperature sensor 32 installed upstream of the intermediate heat exchanger 30d2 in the heat medium circulation circuit 34 of the heat medium converter D2.
  • FIG. 3 shows the flow of the refrigerant in the case of No. 1 or No. 2 in FIG. 4.
  • the temperatures t1 and t2 of the heat medium are lower than the temperature T of the outside air flowing into the heat source side heat exchanger 3.
  • the refrigeration cycle device 100 uses both the heat medium converters D1 and D2 to assist the heat source side heat exchanger 3, which is a condenser.
  • FIG 20 is a Mollier diagram of the refrigeration cycle apparatus 200 according to embodiment 2 during heating operation.
  • the utilization side heat exchangers 5c1 and 5c2 are connected so that the refrigerant flowing out from the discharge side (high pressure side) of the compressor 1 flows in through the high pressure side branch 10a.
  • the utilization side heat exchangers 5c1 and 5c2 function as condensers, and the utilization side units C1 and C2 perform heating operation.
  • the refrigerant flowing out of the utilization side heat exchangers 5c1 and 5c2 is decompressed by the first flow control devices 4c1 and 4c2 and flows into the second branch 11.

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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)
  • Other Air-Conditioning Systems (AREA)

Abstract

Ce dispositif à cycle de réfrigération comprend : une machine de source de chaleur comprenant un compresseur qui comprime un fluide frigorigène, un échangeur de chaleur côté source de chaleur et un premier dispositif de commutation de trajet d'écoulement qui commute un trajet d'écoulement du fluide frigorigène ; un tuyau côté haute pression ; un tuyau côté basse pression ; une unité côté utilisation reliée au tuyau côté haute pression et au tuyau côté basse pression et comprenant un échangeur de chaleur côté utilisation et un premier dispositif de régulation de débit ; une unité de relais de milieu caloporteur reliée au tuyau côté haute pression et au tuyau côté basse pression et comprenant un second dispositif de régulation de débit et un échangeur de chaleur inter-milieu caloporteur qui échange de la chaleur entre le fluide frigorigène et un milieu caloporteur qui transporte de la chaleur provenant d'une source de chaleur externe ; une première partie ramification reliée à un premier tuyau de raccordement s'étendant à partir de l'unité côté utilisation et de l'unité de relais de milieu caloporteur ; et une seconde partie ramification reliée à un second tuyau de raccordement s'étendant à partir de l'unité côté utilisation et de l'unité de relais de milieu caloporteur. La présente invention est conçue pour former, lorsque l'échangeur de chaleur côté source de chaleur fonctionne comme un évaporateur, un raccordement tel que le fluide frigorigène s'écoule d'un côté évacuation du compresseur vers le tuyau côté haute pression et un raccordement tel que le fluide frigorigène s'écoule du tuyau côté basse pression vers un côté aspiration du compresseur à travers l'échangeur de chaleur côté source de chaleur. La première partie ramification est pourvue d'un second dispositif de commutation de trajet d'écoulement qui commute le raccordement entre le premier tuyau de raccordement et le tuyau côté haute pression ou le tuyau côté basse pression. Le second dispositif de commutation de trajet d'écoulement est conçu de telle sorte que l'échangeur de chaleur inter-milieu caloporteur peut fonctionner comme un condenseur auxiliaire lorsque l'échangeur de chaleur côté source de chaleur fonctionne comme un condenseur et que l'échangeur de chaleur inter-milieu caloporteur peut fonctionner comme un évaporateur auxiliaire lorsque l'échangeur de chaleur côté source de chaleur fonctionne comme un évaporateur.
PCT/JP2023/020819 2023-06-05 2023-06-05 Dispositif à cycle de réfrigération Ceased WO2024252473A1 (fr)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05306848A (ja) * 1992-04-30 1993-11-19 Matsushita Seiko Co Ltd 熱回収型マルチエアコン
WO2014049673A1 (fr) * 2012-09-25 2014-04-03 三菱電機株式会社 Système pour alimentation en eau chaude et pour conditionnement d'air combinés
WO2014091548A1 (fr) * 2012-12-11 2014-06-19 三菱電機株式会社 Système composite de climatisation et d'approvisionnement d'eau chaude
JP2017067318A (ja) * 2015-09-28 2017-04-06 パナソニックＩｐマネジメント株式会社 空気調和装置
WO2020208805A1 (fr) * 2019-04-12 2020-10-15 三菱電機株式会社 Dispositif de climatisation
WO2022239212A1 (fr) * 2021-05-14 2022-11-17 三菱電機株式会社 Climatiseur et système de climatisation

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05306848A (ja) * 1992-04-30 1993-11-19 Matsushita Seiko Co Ltd 熱回収型マルチエアコン
WO2014049673A1 (fr) * 2012-09-25 2014-04-03 三菱電機株式会社 Système pour alimentation en eau chaude et pour conditionnement d'air combinés
WO2014091548A1 (fr) * 2012-12-11 2014-06-19 三菱電機株式会社 Système composite de climatisation et d'approvisionnement d'eau chaude
JP2017067318A (ja) * 2015-09-28 2017-04-06 パナソニックＩｐマネジメント株式会社 空気調和装置
WO2020208805A1 (fr) * 2019-04-12 2020-10-15 三菱電機株式会社 Dispositif de climatisation
WO2022239212A1 (fr) * 2021-05-14 2022-11-17 三菱電機株式会社 Climatiseur et système de climatisation

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