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WO2024261859A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2024261859A1
WO2024261859A1 PCT/JP2023/022759 JP2023022759W WO2024261859A1 WO 2024261859 A1 WO2024261859 A1 WO 2024261859A1 JP 2023022759 W JP2023022759 W JP 2023022759W WO 2024261859 A1 WO2024261859 A1 WO 2024261859A1
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WIPO (PCT)
Prior art keywords
heat exchanger
flow
partial heat
refrigerant
bypass
Prior art date
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Pending
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PCT/JP2023/022759
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English (en)
Japanese (ja)
Inventor
淳平 濱口
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Priority to PCT/JP2023/022759 priority Critical patent/WO2024261859A1/fr
Publication of WO2024261859A1 publication Critical patent/WO2024261859A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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    • 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
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles

Definitions

  • This disclosure relates to an air conditioner with a defrost function that removes frost that adheres to an outdoor heat exchanger.
  • Heat pump air conditioners that use air as a heat source in cold regions, replacing boiler-type heating appliances that heat by burning fossil fuels.
  • Heat pump air conditioners can heat efficiently by providing heat from the air in addition to the electrical input to the compressor.
  • an air conditioner in which the outdoor heat exchanger is divided into multiple outdoor heat exchangers and which operates in a heating/defrosting operation mode (see, for example, Patent Document 1).
  • the air conditioner of Patent Document 1 has a heating/defrosting operation mode in which one outdoor heat exchanger is defrosted by flowing a portion of the refrigerant discharged from the compressor into the other outdoor heat exchanger while the other outdoor heat exchanger acts as an evaporator.
  • this heating/defrosting operation mode each outdoor heat exchanger is defrosted alternately, so that the room can be heated continuously without making the flow of the refrigeration cycle the same as in cooling operation.
  • This disclosure has been made to solve the problems described above, and aims to provide an air conditioner that has improved heating capacity in heating/defrost operation mode compared to conventional air conditioners.
  • the air conditioning apparatus comprises a compressor, two flow path switching devices, one or more indoor heat exchangers and a pressure reducing device, an outdoor heat exchanger having two flow paths each composed of a plurality of branch flow paths, and two flow control devices for adjusting the flow of each of the two flow paths of the outdoor heat exchanger, all of which are connected by piping; a main circuit through which a refrigerant circulates, and bypass piping that connects between the discharge side of the compressor and one of the two flow path switching devices, between a first partial heat exchanger having one of the two flow paths of the outdoor heat exchanger and one of the two flow control devices, between the discharge side of the compressor and one of the two flow path switching devices, and between a second partial heat exchanger having the other of the two flow paths of the outdoor heat exchanger and the other of the two flow control devices, and through which a portion of the refrigerant discharged from the compressor branches off and flows; , a bypass circuit having a bypass flow rate control device provided in the bypass piping and controlling the flow
  • the control device has an operation mode including a normal heating operation mode in which the first partial heat exchanger and the second partial heat exchanger are operated as evaporators, and a heating/defrost operation mode in which one of the first partial heat exchanger and the second partial heat exchanger is set as a defrost target and the other is operated as an evaporator.
  • a normal heating operation mode in which the first partial heat exchanger and the second partial heat exchanger are operated as evaporators
  • a heating/defrost operation mode in which one of the first partial heat exchanger and the second partial heat exchanger is set as a defrost target and the other is operated as an evaporator.
  • the multiple branch flow paths of the flow path of the first partial heat exchanger and the multiple branch flow paths of the flow path of the second partial heat exchanger are arranged alternately in the vertical direction.
  • the multiple branch flow paths of the flow path of the first partial heat exchanger and the multiple branch flow paths of the flow path of the second partial heat exchanger are arranged alternately in the vertical direction, so that during the heating/defrost operation mode, when water generated by melting frost is discharged by gravity onto the surface of the heat exchanger on the defrost operation side of the first partial heat exchanger or the second partial heat exchanger, the water passes through the surface of the heat exchanger acting as an evaporator.
  • the energy added to the water generated by melting frost during defrost operation is recovered by the heat exchanger acting as an evaporator more than the energy added to melting frost during defrost operation, so energy loss is suppressed and heating capacity can be improved compared to conventional methods.
  • FIG. 1 is a diagram showing a configuration of an air conditioning apparatus according to an embodiment.
  • 2 is an enlarged schematic view of an outdoor heat exchanger of the air conditioning apparatus according to the embodiment.
  • FIG. 4 is a diagram showing a flow of refrigerant during cooling operation of the air conditioning apparatus according to the embodiment.
  • FIG. FIG. 4 is a diagram showing a flow of refrigerant during heating operation of the air conditioner according to the embodiment.
  • 5 is a diagram showing a flow of refrigerant when defrosting a first partial heat exchanger during heating/defrosting operation of the air conditioning apparatus according to the embodiment.
  • FIG. 11 is a diagram showing a flow of refrigerant when defrosting a second partial heat exchanger during heating/defrosting operation of the air conditioner according to the embodiment.
  • FIG. 1 is a diagram showing the configuration of an air conditioning device 100 according to an embodiment.
  • FIG. 2 is an enlarged schematic diagram of an outdoor heat exchanger 13 of the air conditioning device 100 according to an embodiment.
  • the air conditioning device 100 according to the embodiment is a device that adjusts the air in an indoor space to be air-conditioned. As shown in FIG. 1, the air conditioning device 100 includes an outdoor unit 10, an indoor unit 20, and a control device 50.
  • the outdoor unit 10 includes a compressor 11, a plurality of flow path switching devices 12 (first flow path switching device 12a, second flow path switching device 12b), an outdoor heat exchanger 13, an outdoor blower 14, a plurality of flow control devices 15 (first flow control device 15a, second flow control device 15b), and a plurality of bypass circuits 42 (first bypass circuit 42a, second bypass circuit 42b).
  • the indoor unit 20 includes an indoor heat exchanger 21, an indoor blower 22, and a pressure reducing device 23.
  • the outdoor unit 10 and the indoor unit 20 are connected by a first extension pipe 31 and a second extension pipe 32.
  • an air conditioning apparatus 100 having one outdoor unit 10 and one indoor unit 20 is exemplified, but the air conditioning apparatus 100 may have two or more outdoor units 10 and indoor units 20.
  • the compressor 11, multiple flow switching devices 12, outdoor heat exchanger 13, multiple flow control devices 15, pressure reducing device 23, and indoor heat exchanger 21 are connected by piping including a first extension piping 31 and a second extension piping 32 to form a main circuit 41 through which the refrigerant circulates.
  • the refrigerant circuit of the air conditioning device 100 is composed of this main circuit 41 and a bypass circuit 42 described below.
  • the compressor 11 draws in low-temperature, low-pressure refrigerant, compresses it, and discharges it as high-temperature, high-pressure refrigerant.
  • the flow path switching device 12 switches the direction in which the refrigerant flows in the refrigerant circuit, and is, for example, a four-way valve.
  • the discharge side of the compressor 11 and the flow path switching device 12 are connected by discharge piping 35 (first discharge piping 35a, second discharge piping 35b).
  • the suction side of the compressor 11 and the flow path switching device 12 are connected by suction piping 36.
  • the outdoor heat exchanger 13 for example, exchanges heat between the outdoor air, i.e., the air outside the room, and the refrigerant, and acts as a condenser during cooling operation and as an evaporator during heating operation.
  • the outdoor heat exchanger 13 has two systems (Sa, Sb) of flow paths, and each system has multiple branch flow paths, with the branch flow paths of each system arranged alternately in the vertical direction.
  • the outdoor heat exchanger 13 is composed of a first partial heat exchanger 13a having a flow path of one system, Sa, and a second partial heat exchanger 13b having a flow path of the other system, Sb. That is, as shown in FIG.
  • the first partial heat exchanger 13a has an odd-numbered branch flow path BF among the multiple branch flow paths BF divided and arranged in the vertical direction (arrow X direction in FIG. 2)
  • the second partial heat exchanger 13b has an even-numbered branch flow path BF
  • the first partial heat exchanger 13a has an even-numbered branch flow path BF among the multiple branch flow paths BF divided and arranged in the vertical direction
  • the second partial heat exchanger 13b has an odd-numbered branch flow path BF.
  • the outdoor heat exchanger 13 has two flow paths (Sa, Sb) and the branch flow paths BF of each system are alternately arranged in the vertical direction, but the present invention is not limited to this, and may have three or more flow paths and the branch flow paths BF of each system are alternately arranged in the vertical direction.
  • the first partial heat exchanger 13a and the second partial heat exchanger 13b are assumed to have the same area and heat exchange rate related to heat exchange and have the same capacity.
  • the outdoor blower 14 is provided near the outdoor heat exchanger 13 and sends outdoor air to the outdoor heat exchanger 13.
  • the flow rate control device 15 is provided in each of the multiple branch pipes 37 (first branch pipe 37a, second branch pipe 37b) and adjusts the amount of refrigerant flowing through the branch pipes 37.
  • the first flow rate control device 15a is provided in the first branch pipe 37a and adjusts the amount of refrigerant flowing through the first branch pipe 37a.
  • the second flow rate control device 15b is provided in the second branch pipe 37b and adjusts the amount of refrigerant flowing through the second branch pipe 37b.
  • the flow rate control device 15 may be any device that is at least capable of opening and closing the flow path, and may be, for example, a solenoid valve or a two-way valve.
  • the bypass circuit 42 includes a bypass pipe 16 (first bypass pipe 16a, second bypass pipe 16b) and a bypass flow control device 17 (first bypass flow control device 17a, second bypass flow control device 17b).
  • the bypass circuit 42 is a circuit that allows a portion of the refrigerant discharged from the compressor 11 to flow from the discharge pipe 35 between the compressor 11 and the multiple flow path switching devices 12 to the branch pipe 37 between the outdoor heat exchanger 13 and the flow control device 15.
  • the bypass pipe 16 is a pipe that bypasses the discharge side of the compressor 11 to the branch pipe 37.
  • the first bypass pipe 16a is a pipe that bypasses from the first discharge pipe 35a between the compressor 11 and the first flow path switching device 12a to the first branch pipe 37a between the first partial heat exchanger 13a and the first flow control device 15a.
  • the second bypass pipe 16b is a pipe that bypasses the second discharge pipe 35b between the compressor 11 and the second flow switching device 12b to the second branch pipe 37b between the second partial heat exchanger 13b and the second flow control device 15b.
  • the bypass flow rate control device 17 is provided in the bypass pipe 16 and adjusts the amount of refrigerant flowing through the bypass pipe 16.
  • the first bypass flow rate control device 17a is provided in the first bypass pipe 16a and adjusts the amount of refrigerant flowing through the first bypass pipe 16a.
  • the second bypass flow rate control device 17b is provided in the second bypass pipe 16b and adjusts the amount of refrigerant flowing through the second bypass pipe 16b.
  • the bypass flow rate control device 17 may be any device that is at least capable of opening and closing the flow path, and may be, for example, a solenoid valve or a two-way valve.
  • the indoor heat exchanger 21 exchanges heat between the indoor air that is the space to be air-conditioned and the refrigerant, and acts as an evaporator during cooling operation and as a condenser during heating operation.
  • the indoor blower 22 is provided near the indoor heat exchanger 21 and sends indoor air to the indoor heat exchanger 21.
  • the pressure reducing device 23 reduces the pressure of the refrigerant to expand it, and is, for example, an electronic expansion valve whose opening can be adjusted.
  • a fluorocarbon refrigerant for example, a fluorocarbon refrigerant, an HFO refrigerant, etc.
  • a fluorocarbon refrigerant for example, there are HFC refrigerants such as R32 refrigerant, R125, and R134a.
  • HFC refrigerant mixed refrigerants such as R410A, R407c, and R404A.
  • HFO refrigerant for example, there are HFO-1234yf, HFO-1234ze(E), and HFO-1234ze(Z).
  • refrigerants used in vapor compression heat pump circuits such as CO2 refrigerant, HC refrigerant, ammonia refrigerant, and a mixed refrigerant of R32 and HFO-1234yf, etc.
  • CO2 refrigerant for example, propane, isobutane refrigerant, etc.
  • HC refrigerant for example, propane, isobutane refrigerant, etc.
  • the air conditioning device 100 has three operation modes: a cooling operation mode, a normal heating operation mode, and a heating/defrost operation mode.
  • the outdoor heat exchanger 13 acts as a condenser, and the indoor unit 20 cools the room.
  • the outdoor heat exchanger 13 acts as an evaporator, and the indoor unit 20 heats the room.
  • the heating/defrost operation mode a part of the outdoor heat exchanger 13 becomes the defrost target, that is, one of the first partial heat exchanger 13a and the second partial heat exchanger 13b becomes the defrost target, the other acts as an evaporator, and the indoor unit 20 heats the room.
  • the heating/defrost operation mode is an operation mode in which the heating operation is maintained while defrosting, by the other of the first partial heat exchanger 13a and the second partial heat exchanger 13b acting as an evaporator.
  • the first partial heat exchanger 13a and the second partial heat exchanger 13b are alternately defrosted.
  • one of the first partial heat exchanger 13a and the second partial heat exchanger 13b acts as an evaporator to perform heating operation while the other is defrosted.
  • the heating/defrosting operation mode when the defrosting of the other is completed, the other acts as an evaporator to perform heating operation and one is defrosted.
  • the heating/defrosting operation mode is performed when the first partial heat exchanger 13a and the second partial heat exchanger 13b are frosted during normal heating operation.
  • the heating/defrosting mode may also be switched to when the drive frequency of the compressor 11 becomes lower than the frequency threshold value.
  • the control device 50 controls the cooling and heating operations of the indoor unit 20, changes to the set room temperature, the flow rate regulator 15, the bypass flow rate regulator 17, and the pressure reducing device 23.
  • the control device 50 according to the embodiment is composed of a microcomputer having a control arithmetic processing device such as a CPU (Central Processing Unit).
  • the control device 50 also has a memory device (not shown) and has data in the form of a program that contains processing procedures related to control, etc. Then, the control arithmetic processing device executes processing based on the program data to realize control.
  • FIG. 3 is a diagram showing the flow of refrigerant during cooling operation of the air conditioner 100 according to the embodiment.
  • the first flow switching device 12a and the second flow switching device 12b are switched as shown by solid lines in FIG. 3, the discharge side of the compressor 11 is connected to the first partial heat exchanger 13a and the second partial heat exchanger 13b, and the suction side of the compressor 11 is connected to the indoor heat exchanger 21.
  • the first flow control device 15a and the second flow control device 15b are opened, and the first bypass flow control device 17a and the second bypass flow control device 17b are closed.
  • the flow of refrigerant is indicated by white arrows
  • the closed flow control devices are indicated by black arrows.
  • the compressor 11 compresses the refrigerant drawn in and discharges the refrigerant in a high-temperature, high-pressure gaseous state.
  • the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 11 branches, passes through the first flow path switching device 12a and the second flow path switching device 12b, and flows into the first partial heat exchanger 13a and the second partial heat exchanger 13b acting as condensers.
  • the refrigerant exchanges heat with the outdoor air sent by the outdoor blower 14, condenses, and liquefies, becoming a medium-temperature, high-pressure liquid refrigerant.
  • the condensed medium-temperature, high-pressure liquid refrigerant passes through the first flow control device 15a and the second flow control device 15b, respectively, merges, and then flows into the pressure reducing device 23.
  • the medium-temperature, high-pressure liquid refrigerant that flows into the pressure reducing device 23 is expanded and reduced in pressure reducing device 23 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant flows into the indoor heat exchanger 21, which acts as an evaporator, and is evaporated and gasified by heat exchange with the indoor air sent by the indoor blower 22. At this time, the indoor air is cooled, and cooling is performed in the room.
  • the evaporated low-temperature, low-pressure gas refrigerant passes through the second flow switching device 12b and is sucked into the compressor 11.
  • FIG. 4 is a diagram showing the flow of refrigerant during heating operation of the air conditioner 100 according to the embodiment.
  • the first flow switching device 12a and the second flow switching device 12b are switched as shown by solid lines in FIG. 4, the discharge side of the compressor 11 is connected to the indoor heat exchanger 21, and the suction side of the compressor 11 is connected to the first partial heat exchanger 13a and the second partial heat exchanger 13b.
  • the first flow control device 15a and the second flow control device 15b are opened, and the first bypass flow control device 17a and the second bypass flow control device 17b are closed.
  • the flow of refrigerant is indicated by white arrows, and the closed flow control devices are indicated by black arrows.
  • the compressor 11 compresses the refrigerant it draws in and discharges it in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas state refrigerant discharged from the compressor 11 passes through the second flow switching device 12b and flows into the indoor heat exchanger 21, which acts as a condenser.
  • the indoor heat exchanger 21 the refrigerant exchanges heat with the indoor air sent by the indoor blower 22, condenses and liquefies, becoming a medium-temperature, high-pressure liquid state refrigerant.
  • the indoor air is warmed and heating is performed inside the room.
  • the condensed medium-temperature, high-pressure liquid state refrigerant flows into the pressure reducing device 23.
  • the medium-temperature, high-pressure refrigerant that flows into the pressure reducing device 23 expands and is reduced in pressure, becoming a medium-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant branches off and then passes through the first flow control device 15a and the second flow control device 15b, respectively, before flowing into the first partial heat exchanger 13a and the second partial heat exchanger 13b, which act as evaporators.
  • the refrigerant exchanges heat with the outdoor air sent by the outdoor blower 14, evaporating and gasifying.
  • the evaporated low-temperature, low-pressure gaseous refrigerant passes through the first flow switching device 12a and the second flow switching device 12b, respectively, where they merge, and are then drawn into the compressor 11.
  • ⁇ Heating defrost operation mode> 5 is a diagram showing the flow of refrigerant when the first partial heat exchanger 13a is defrosted during heating defrost operation of the air conditioning apparatus 100 according to the embodiment.
  • FIG. 6 is a diagram showing the flow of refrigerant when the second partial heat exchanger 13b is defrosted during heating defrost operation of the air conditioning apparatus 100 according to the embodiment.
  • the flow of refrigerant in the air conditioning apparatus 100 in the heating defrost operation mode will be described.
  • the first flow path switching device 12a and the second flow path switching device 12b are switched as shown by solid lines in FIG. 5 and FIG.
  • the discharge side of the compressor 11 is connected to the indoor heat exchanger 21, and the suction side of the compressor 11 is connected to the first partial heat exchanger 13a and the second partial heat exchanger 13b.
  • one of the first partial heat exchanger 13a and the second partial heat exchanger 13b is selected as a defrost target and defrosting is performed, while the other acts as an evaporator to continue the heating operation.
  • the opening and closing states of the first flow rate control device 15a and the second flow rate control device 15b, and the first bypass flow rate control device 17a and the second bypass flow rate control device 17b are alternately switched, and the defrost target is alternately switched between the first partial heat exchanger 13a and the second partial heat exchanger 13b.
  • the flow of the refrigerant is switched by switching between the first partial heat exchanger 13a or the second partial heat exchanger 13b as the defrost target and the first partial heat exchanger 13a or the second partial heat exchanger 13b acting as an evaporator.
  • the first partial heat exchanger 13a is selected as the defrost target, and the first partial heat exchanger 13a is defrosted while the second partial heat exchanger 13b acts as an evaporator to continue heating.
  • the second flow control device 15b and the first bypass flow control device 17a are open, and the first flow control device 15a and the second bypass flow control device 17b are closed.
  • the refrigerant flow related to defrosting is indicated by black arrows
  • the refrigerant flow related to heating is indicated by white arrows.
  • closed flow control devices are indicated by solid black arrows.
  • the compressor 11 compresses the refrigerant sucked in and discharges the refrigerant in a high-temperature, high-pressure gas state.
  • a portion of the high-temperature, high-pressure gas state refrigerant discharged from the compressor 11 passes through the second flow switching device 12b and flows into the indoor heat exchanger 21 acting as a condenser.
  • the indoor heat exchanger 21 the refrigerant exchanges heat with the indoor air sent by the indoor blower 22, condenses and liquefies, and becomes a medium-temperature, high-pressure liquid state refrigerant.
  • the condensed medium-temperature, high-pressure liquid state refrigerant flows into the pressure reducing device 23.
  • the medium-temperature, high-pressure refrigerant that flows into the pressure reducing device 23 is expanded and reduced in pressure to become a medium-pressure gas-liquid two-phase refrigerant.
  • the refrigerant in the gas-liquid two-phase state does not flow to the first partial heat exchanger 13a, which is the defrost target, but flows into the second partial heat exchanger 13b, which acts as an evaporator, where it exchanges heat with the outdoor air sent by the outdoor blower 14, evaporating and gasifying.
  • the evaporated low-temperature, low-pressure gaseous refrigerant passes through the second flow switching device 12b and is sucked into the compressor 11.
  • the refrigerant that flows into the first bypass pipe 16a passes through the first bypass flow control device 17a and flows into the first partial heat exchanger 13a that is the defrost target.
  • the refrigerant that flows into the first partial heat exchanger 13a is cooled by heat exchange with the frost that has adhered to the first partial heat exchanger 13a.
  • the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 11 flows into the first partial heat exchanger 13a, melting the frost that has adhered to the first partial heat exchanger 13a.
  • the first partial heat exchanger 13a is defrosted, and the refrigerant flowing out of the first partial heat exchanger 13a passes through the first flow path switching device 12a, merges with the low-temperature, low-pressure gas-state refrigerant that passed through the second flow path switching device 12b, and is then sucked into the compressor 11.
  • the second partial heat exchanger 13b is selected as the defrost target, and the second partial heat exchanger 13b is defrosted while the first partial heat exchanger 13a continues heating by acting as an evaporator.
  • the first flow control device 15a and the second bypass flow control device 17b are open, and the second flow control device 15b and the first bypass flow control device 17a are closed.
  • the refrigerant flow related to defrosting is indicated by black arrows
  • the refrigerant flow related to heating is indicated by white arrows.
  • closed flow control devices are indicated by solid black arrows.
  • the compressor 11 compresses the refrigerant sucked in and discharges the refrigerant in a high-temperature, high-pressure gas state.
  • a portion of the high-temperature, high-pressure gas state refrigerant discharged from the compressor 11 passes through the second flow switching device 12b and flows into the indoor heat exchanger 21 acting as a condenser.
  • the indoor heat exchanger 21 the refrigerant exchanges heat with the indoor air sent by the indoor blower 22, condenses and liquefies, and becomes a medium-temperature, high-pressure liquid state refrigerant.
  • the condensed medium-temperature, high-pressure liquid state refrigerant flows into the pressure reducing device 23.
  • the medium-temperature, high-pressure refrigerant that flows into the pressure reducing device 23 is expanded and reduced in pressure to become a medium-pressure gas-liquid two-phase refrigerant.
  • the refrigerant in the gas-liquid two-phase state does not flow to the second partial heat exchanger 13b, which is the defrost target, but flows into the first partial heat exchanger 13a, which acts as an evaporator, where it exchanges heat with the outdoor air sent by the outdoor blower 14, evaporating and gasifying.
  • the evaporated low-temperature, low-pressure gaseous refrigerant passes through the first flow switching device 12a and is sucked into the compressor 11.
  • the refrigerant that flows into the second bypass pipe 16b passes through the second bypass flow control device 17b and flows into the second partial heat exchanger 13b that is the defrost target.
  • the refrigerant that flows into the second partial heat exchanger 13b is cooled by heat exchange with the frost that has adhered to the second partial heat exchanger 13b.
  • the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 11 flows into the second partial heat exchanger 13b, melting the frost that has adhered to the second partial heat exchanger 13b.
  • the second partial heat exchanger 13b is defrosted, and the refrigerant flowing out of the second partial heat exchanger 13b passes through the second flow path switching device 12b, merges with the low-temperature, low-pressure gas-state refrigerant that passed through the first flow path switching device 12a, and is then sucked into the compressor 11.
  • the outdoor heat exchanger 13 has two systems (Sa, Sb) of flow paths, each of which has a plurality of branch flow paths BF, and the branch flow paths BF of each system are arranged alternately in the vertical direction.
  • the outdoor heat exchanger 13 is also composed of a first partial heat exchanger 13a having a flow path of one system and a second partial heat exchanger 13b having a flow path of the other system.
  • the heating/defrosting operation mode when the water generated by melting frost is discharged by gravity onto the surface of the first partial heat exchanger 13a or the second partial heat exchanger 13b to be defrosted, the water passes through the surface of the first partial heat exchanger 13a or the second partial heat exchanger 13b acting as an evaporator.
  • the energy added to the water produced by melting the frost during defrost operation is recovered by the first partial heat exchanger 13a or the second partial heat exchanger 13b, which acts as an evaporator, rather than melting the frost, so energy loss is suppressed and heating capacity can be improved compared to conventional methods.
  • the air conditioning device 100 comprises a compressor 11, two flow path switching devices 12, one or more indoor heat exchangers 21 and a pressure reducing device 23, an outdoor heat exchanger 13 having two flow paths (Sa, Sb) each composed of a plurality of branch flow paths BF, and two flow control devices 15 that respectively adjust the flow of the flow paths of the two systems of the outdoor heat exchanger 13, all of which are connected by piping.
  • the main circuit 41 through which the refrigerant circulates is connected to the discharge side of the compressor 11 and the two flow path switching devices 12.
  • the outdoor heat exchanger 13 includes a bypass circuit 42 having a bypass piping 16 and a bypass flow rate control device 17 provided in the bypass piping 16 to adjust the flow rate of the refrigerant flowing through the bypass piping 16, and a control device 50 for controlling the two flow path switching devices 12, the pressure reducing device 23, the two flow rate control devices 15, and the two bypass flow rate control devices 17.
  • the control device 50 has a normal heating operation mode in which the first partial heat exchanger 13a and the second partial heat exchanger 13b act as evaporators, and a heating/defrost operation mode in which one of the first partial heat exchanger 13a and the second partial heat exchanger 13b is set as a defrost target and the other acts as an evaporator.
  • the multiple branch flow paths BF of the flow path of the first partial heat exchanger 13a and the multiple branch flow paths BF of the flow path of the second partial heat exchanger 13b are arranged alternately in the vertical direction.
  • the multiple branch flow paths BF of the flow path of the first partial heat exchanger 13a and the multiple branch flow paths BF of the flow path of the second partial heat exchanger 13b are arranged alternately in the vertical direction, so that during the heating/defrosting operation mode, when the water generated by melting frost is discharged by gravity onto the surface of the heat exchanger on the defrosting operation side of the first partial heat exchanger 13a or the second partial heat exchanger 13b, it passes through the surface of the heat exchanger acting as an evaporator.
  • the energy added to the water generated by melting frost during the defrosting operation is recovered by the heat exchanger acting as an evaporator more than the energy added to melting frost during the defrosting operation, so that energy loss is suppressed and the heating capacity can be improved compared to the conventional case.

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  • Air Conditioning Control Device (AREA)

Abstract

Ce dispositif de climatisation comprend : un circuit principal dans lequel un compresseur, deux dispositifs de commutation de trajet d'écoulement, un ou plusieurs échangeurs de chaleur intérieurs, un dispositif de décompression, un échangeur de chaleur extérieur ayant deux systèmes de trajets d'écoulement qui sont chacun configurés à partir d'une pluralité de trajets d'écoulement de ramification, et deux dispositifs de réglage de débit qui règlent respectivement l'écoulement des deux systèmes de trajets d'écoulement de l'échangeur de chaleur extérieur sont raccordés par une tuyauterie, le circuit principal étant tel qu'un fluide frigorigène y circule ; un circuit de dérivation doté d'une tuyauterie de dérivation qui est raccordée entre le côté de refoulement du compresseur et l'un des deux dispositifs de commutation de trajet d'écoulement et entre un premier échangeur de chaleur partiel ayant l'un des deux systèmes de trajets d'écoulement de l'échangeur de chaleur extérieur et l'un des deux dispositifs de réglage de débit, ainsi qu'un raccordement entre le côté de refoulement du compresseur et l'un des deux dispositifs de commutation de trajet d'écoulement et entre un second échangeur de chaleur partiel ayant l'autre des deux systèmes de trajets d'écoulement de l'échangeur de chaleur extérieur et l'autre des deux dispositifs de réglage de débit, la tuyauterie de trajet d'écoulement étant telle qu'une partie du fluide frigorigène refoulé par le compresseur se ramifie et s'écoule dans la tuyauterie de dérivation, et le circuit de dérivation ayant également un dispositif de réglage de débit de dérivation qui est disposé sur la tuyauterie de dérivation et qui règle le débit du fluide frigorigène s'écoulant dans la tuyauterie de dérivation ; et un dispositif de commande qui commande les deux dispositifs de commutation de trajet d'écoulement, le dispositif de décompression, les deux dispositifs de réglage de débit et les deux dispositifs de réglage de débit de dérivation. Le dispositif de commande possédé, en tant que modes de fonctionnement, un mode de fonctionnement de chauffage normal dans lequel le premier échangeur de chaleur partiel et le second échangeur de chaleur partiel sont amenés à agir en tant qu'évaporateurs, et un mode de fonctionnement de dégivrage par chauffage dans lequel l'un ou l'autre du premier échangeur de chaleur partiel ou du second échangeur de chaleur partiel est défini en tant qu'objet à dégivrer et l'autre est amené à agir en tant qu'évaporateur. La pluralité de trajets d'écoulement de ramification des trajets d'écoulement disposés sur le premier échangeur de chaleur partiel et la pluralité de trajets d'écoulement de ramification des trajets d'écoulement disposés sur le second échangeur de chaleur partiel, parmi les deux systèmes de trajets d'écoulement de l'échangeur de chaleur extérieur, sont agencés en alternance dans la direction verticale.
PCT/JP2023/022759 2023-06-20 2023-06-20 Dispositif de climatisation Pending WO2024261859A1 (fr)

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PCT/JP2023/022759 WO2024261859A1 (fr) 2023-06-20 2023-06-20 Dispositif de climatisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2023/022759 WO2024261859A1 (fr) 2023-06-20 2023-06-20 Dispositif de climatisation

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WO2024261859A1 true WO2024261859A1 (fr) 2024-12-26

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010139097A (ja) * 2008-12-09 2010-06-24 Mitsubishi Electric Corp 空気調和機
KR101120371B1 (ko) * 2010-01-15 2012-02-27 엘지전자 주식회사 냉매시스템
WO2016113850A1 (fr) * 2015-01-13 2016-07-21 三菱電機株式会社 Dispositif de climatisation
WO2017138108A1 (fr) * 2016-02-10 2017-08-17 三菱電機株式会社 Dispositif de climatisation
US20210080140A1 (en) * 2018-11-29 2021-03-18 Lg Electronics Inc. Air conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010139097A (ja) * 2008-12-09 2010-06-24 Mitsubishi Electric Corp 空気調和機
KR101120371B1 (ko) * 2010-01-15 2012-02-27 엘지전자 주식회사 냉매시스템
WO2016113850A1 (fr) * 2015-01-13 2016-07-21 三菱電機株式会社 Dispositif de climatisation
WO2017138108A1 (fr) * 2016-02-10 2017-08-17 三菱電機株式会社 Dispositif de climatisation
US20210080140A1 (en) * 2018-11-29 2021-03-18 Lg Electronics Inc. Air conditioner

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