WO2021124499A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2021124499A1 WO2021124499A1 PCT/JP2019/049722 JP2019049722W WO2021124499A1 WO 2021124499 A1 WO2021124499 A1 WO 2021124499A1 JP 2019049722 W JP2019049722 W JP 2019049722W WO 2021124499 A1 WO2021124499 A1 WO 2021124499A1
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- heat exchanger
- refrigerant
- flow path
- compressor
- switching device
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
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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
- F24F11/70—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
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
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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
- F24F2140/00—Control inputs relating to system states
- F24F2140/20—Heat-exchange fluid temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/31—Low ambient temperatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2507—Flow-diverting valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
Definitions
- the present invention relates to an air conditioner having a plurality of heat exchangers.
- the condenser of the outdoor unit In the cooling operation when the outside air temperature of the outdoor unit is not high, the condenser of the outdoor unit does not require heat exchange capacity. In such a case, the condenser of the outdoor unit is controlled so that the heat exchange capacity is reduced in order to maintain the operating range of the high pressure and the low pressure of the compressor.
- the volume of the entire outdoor unit as a condenser can be reduced.
- the heat exchange capacity is controlled to be lowered (see, for example, Patent Document 1).
- the former condenser In a condenser in which the flow path of the refrigerant is blocked (hereinafter referred to as "former condenser"), the former condenser is connected to the low pressure side in order to recover the refrigerant remaining in the former condenser.
- the saturation pressure of the refrigerant in the original condenser may be lower than the pressure on the suction side of the compressor. Therefore, there is a problem that the refrigerant remaining in the condenser is not recovered by the compressor and remains in the original condenser.
- the present invention has been made in view of the above circumstances, and is a cooling operation in which the outside air temperature of an outdoor unit having a plurality of heat exchangers is below the freezing point, and is condensed by blocking the flow path of the refrigerant. It is an object of the present invention to provide an air conditioner capable of releasing the refrigerant remaining in the heat exchanger that is not functioning as a condenser to the refrigerant circuit when there is a heat exchanger that is not functioning as a container.
- a compressor that compresses the refrigerant, a high-pressure side pipe through which the refrigerant discharged from the compressor flows, and a first heat exchange that is connected to the high-pressure side pipe and functions as a condenser.
- a second heat exchanger connected to the high-pressure side pipe and the first heat exchanger and connected in parallel to the first heat exchanger to function as a condenser, the high-pressure side pipe and the first heat exchanger. 2
- the first flow path or the first flow path which is connected to the heat exchanger and supplies the refrigerant discharged from the compressor to the first heat exchanger via the high pressure side pipe and does not supply to the second heat exchanger.
- a flow path switching device that switches to a second flow path that supplies the first heat exchanger and the second heat exchanger via the high-pressure side pipe, and a flow rate adjustment connected to the outlet of the refrigerant of the second heat exchanger. Controls the valve, the outlet of the refrigerant of the first heat exchanger, the refrigerant circuit piping connected to the flow rate adjusting valve, the outside air temperature sensor for measuring the outside air temperature, the flow path switching device, and the flow rate adjusting valve.
- the refrigerant circuit piping includes a control device, and the refrigerant is the compressor, the flow path switching device, the first heat exchanger, the second heat exchanger, the flow rate adjusting valve, the expansion valve, and the indoor unit.
- the control device uses the flow path switching device as the first.
- Predetermined conditions in which the outside air temperature measured by the outside air temperature sensor is equal to or less than the first temperature below the freezing point and the discharge superheat degree of the compressor is equal to or higher than the first discharge superheat degree in the state of switching to one flow path.
- the flow path switching device is switched to the second flow path, the flow rate adjusting valve is opened, and the second flow path is opened.
- the refrigerant remaining in the heat exchanger is allowed to flow through the refrigerant circuit piping.
- the control device is a second when a predetermined condition is satisfied when the flow path switching device is switched to the first flow path and the flow rate adjusting valve corresponding to the second heat exchanger is closed. It is determined that the refrigerant remains in the heat exchanger. In that case, by switching the flow path switching device to the second flow path, opening the flow rate adjusting valve, and connecting the second heat exchanger to the high-pressure side piping, the refrigerant remaining in the second heat exchanger can be removed from the refrigerant circuit. Flow through the constituent pipes. As a result, the refrigerant remaining in the second heat exchanger can be released to the refrigerant circuit.
- FIG. 1 It is a figure which shows the refrigerant circuit structure of the air conditioner which concerns on Embodiment 1.
- FIG. It is a figure which shows the case where the flow path switching device of the air conditioner which concerns on Embodiment 1 is switched to a 2nd flow path.
- It is a block diagram which shows the function of the control device of the air conditioner which concerns on Embodiment 1.
- FIG. It is a flowchart for demonstrating operation of the outdoor unit of the air conditioner which concerns on Embodiment 1.
- FIG. It is a figure for demonstrating the refrigerant recovery time of the air conditioner which concerns on Embodiment 2.
- FIG. It is a flowchart for demonstrating operation of the outdoor unit of the air conditioner which concerns on Embodiment 3.
- FIG. 1 is a diagram showing a refrigerant circuit configuration of the air conditioner 100 according to the first embodiment. Further, FIG. 1 shows a flow path configuration when the outside air temperature of the outdoor unit 101 of the air conditioner 100 is, for example, ⁇ 15 ° C.
- the circuit configuration of the air conditioner 100 will be described with reference to FIG.
- the air conditioner 100 performs a cooling operation by utilizing a refrigerating cycle (heat pump cycle) for circulating a refrigerant. Further, in the following drawings including FIG. 1, the relationship between the sizes of the constituent members may differ from the actual one.
- the air conditioner 100 includes an outdoor unit 101 and an indoor unit 102.
- the outdoor unit 101 includes a compressor 1, a compressor discharge temperature sensor 2, an oil separator 3, an oil return bypass capillary 4, an electromagnetic valve for return oil bypass 5, an accumulator 6, a high pressure pressure sensor 7, a flow path switching device 8, and a first.
- the compressor 1 has an inverter circuit, and the compressor rotation speed is controlled by power frequency conversion by the inverter circuit, and the capacity is controlled.
- the compressor 1 compresses the sucked refrigerant into a high temperature and high pressure state.
- the compressor 1 is connected to the oil separator 3 via the high pressure side pipe 21.
- the compressor discharge temperature sensor 2 is provided on the high-pressure side pipe 21 and measures the discharge temperature of the refrigerant discharged from the compressor 1.
- the oil separator 3 is provided on the discharge side of the compressor 1 and has a function of separating the refrigerating machine oil component from the refrigerant gas discharged from the compressor 1 and mixed with the refrigerating machine oil.
- a pipe 22 is connected to the outlet of the refrigerating machine oil separated by the oil separator 3.
- the pipe 22 is connected in the middle of the pipe 23.
- the pipe 23 connects the suction port of the compressor 1 and the accumulator 6.
- the pipe 22 is provided with an oil return bypass capillary 4 and an oil return bypass solenoid valve 5.
- the oil return bypass capillary 4 is provided so as to connect the upstream side and the downstream side of the oil return bypass solenoid valve 5 and bypass the oil return bypass solenoid valve 5.
- the oil return bypass capillary 4 adjusts the flow rate of refrigerating machine oil through the pipe 22.
- the return oil bypass solenoid valve 5 is controlled to open and close, so that the flow rate of the refrigerating machine oil is adjusted together with the return oil bypass capillary 4.
- the accumulator 6 is provided on the suction side of the compressor 1 and stores excess refrigerant that circulates in the refrigerant circuit of the air conditioner 100.
- the high pressure pressure sensor 7 is provided in the high pressure side pipe 24.
- the high-pressure side pipe 24 connects the outlet of the oil separator 3 of the refrigerant gas separated by the oil separator 3, the flow path switching device 8, and the inlet of the refrigerant of the first heat exchanger 9a.
- the high-pressure pressure sensor 7 measures the pressure (high pressure) of the refrigerant discharged from the compressor 1 and flowing in the high-pressure side pipe 24 toward the flow path switching device 8 and the first heat exchanger 9a.
- the flow path switching device 8 is connected to the high-pressure side pipe 24 between the oil separator 3 and the first heat exchanger 9a and the second heat exchanger 9b. Specifically, the port P of the flow path switching device 8 is connected to the high-pressure side pipe 24, and the port Q is sealed. The port R of the flow path switching device 8 is connected to the inlet of the refrigerant of the second heat exchanger 9b, and the port S is connected to the pipe 27. The pipe 27 connects the port S of the flow path switching device 8 and the accumulator 6. The flow path switching device 8 switches the flow path of the refrigerant flowing in the high-pressure side pipe 24 to the first flow path or the second flow path based on the control from the control device 30.
- the first flow path is a flow path in which the refrigerant discharged from the compressor 1 is supplied to the first heat exchanger 9a and is not supplied to the second heat exchanger 9b.
- the flow path switching device 8 connects the port P and the port Q of the flow path switching device 8 based on the control from the control device 30, and the port R and the port S. And connect.
- the second flow path is a flow path in which the refrigerant discharged from the compressor 1 is supplied to the first heat exchanger 9a and the second heat exchanger 9b.
- FIG. 2 is a diagram showing a case where the flow path switching device 8 of the air conditioner 100 according to the first embodiment is switched to the second flow path. Specifically, as shown in FIG. 2, the flow path switching device 8 connects the port P and the port R of the flow path switching device 8 based on the control from the control device 30, and the port Q and the port S And connect.
- the first heat exchanger 9a and the second heat exchanger 9b are connected in parallel and are heat exchangers as condensers.
- the first heat exchanger 9a and the second heat exchanger 9b exchange heat between the compressed refrigerant flowing through the first heat exchanger 9a and the second heat exchanger 9b and the outside air.
- the refrigerant (high pressure) flowing in the high-pressure side pipe 24 is supplied to the first heat exchanger 9a and not to the second heat exchanger 9b when the flow path switching device 8 is switched to the first flow path. .. That is, when switched to the first flow path, the second heat exchanger 9b does not function as a condenser.
- the case where the first heat exchanger 9a and the second heat exchanger 9b are connected in parallel is shown, but three or more heat exchangers as condensers are connected in parallel. You may have.
- the flow path switching device 8 is connected to the inlet and the flow rate adjusting valve 12 is connected to the outlet, similarly to the second heat exchanger 9b.
- the refrigerant flowing in the high-pressure side pipe 24 is supplied to the first heat exchanger 9a and the second heat exchanger 9b when the flow path switching device 8 is switched to the second flow path.
- the refrigerant circuit pipe 26 is connected to the refrigerant outlet (high pressure) of the first heat exchanger 9a.
- the refrigerant circuit pipe 26 connects the outlet of the first heat exchanger 9a to the pipe 27 via the high / low voltage heat exchanger 13, the expansion valve 15 of the indoor unit 102, and the indoor heat exchanger 16.
- the outlet of the refrigerant of the second heat exchanger 9b is connected to the refrigerant circuit pipe 25.
- the refrigerant circuit pipe 25 is provided with a flow rate adjusting valve 12.
- the refrigerant circuit pipe 25 is connected to the refrigerant circuit pipe 26 on the upstream side of the high / low pressure heat exchanger 13 connected to the outlet of the first heat exchanger 9a.
- the first heat exchanger fan 10a supplies outdoor air to the first heat exchanger 9a based on the control of the control device 30 to adjust the amount of heat exchange.
- the second heat exchanger fan 10b supplies outdoor air to the second heat exchanger 9b to adjust the amount of heat exchange based on the instruction of the control device 30.
- the outside air temperature sensor 11 measures the outside air temperature around the outdoor unit 101.
- the flow rate adjusting valve 12 prevents the refrigerant from flowing from the outlet (high pressure) of the second heat exchanger 9b to the refrigerant circuit pipe 25 based on the control of the control device 30. Specifically, when the flow control valve 12 is open, the refrigerant flowing in the second heat exchanger 9b flows through the refrigerant circuit pipe 25, and joins the refrigerant flowing in the first heat exchanger 9a at the refrigerant circuit pipe 26. To do. When the flow rate adjusting valve 12 is closed, the refrigerant in the second heat exchanger 9b does not flow into the refrigerant circuit pipe 25.
- a bypass pipe 28 is connected to the pipe 27 on the upstream side of the accumulator 6.
- the bypass pipe 28 is provided with a high / low pressure heat exchanger 13 and a bypass flow rate adjusting valve 14.
- the refrigerant flowing through the refrigerant circuit pipe 26 branches and flows to the bypass pipe 28.
- the refrigerant flowing in the bypass pipe 28 passes through the bypass flow rate adjusting valve 14 and flows to the high / low voltage heat exchanger 13.
- the high / low pressure heat exchanger 13 exchanges heat between the refrigerant flowing through the refrigerant circuit pipe 26 and the refrigerant flowing through the bypass pipe 28 toward the accumulator 6.
- the bypass flow rate adjusting valve 14 functions as a pressure reducing valve or an expansion valve to reduce the pressure of the refrigerant and expand it.
- the bypass flow rate adjusting valve 14 can be configured by a valve whose opening degree can be variably controlled, for example, an electronic expansion valve or the like.
- the indoor unit 102 has an expansion valve 15 and an indoor heat exchanger 16.
- the expansion valve 15 is connected to the refrigerant circuit pipe 26 and functions as an expansion valve for the refrigerant flowing in the refrigerant circuit pipe 26.
- the indoor heat exchanger 16 is connected to the refrigerant circuit pipe 26 downstream of the expansion valve 15 and exchanges heat with the refrigerant flowing through the refrigerant circuit pipe 26 and the indoor air.
- the refrigerant circuit pipe 26 is connected to the pipe 27.
- the refrigerant flowing in the heat-exchanged refrigerant circuit pipe 26 flows in the pipe 27 and is stored in the accumulator 6.
- the expansion valve 15, the indoor heat exchanger 16 and the accumulator 6 are connected in this order so that the refrigerant flows.
- the refrigerant branched from the refrigerant flowing through the refrigerant circuit pipe 26 to the bypass pipe 28 is connected so that the refrigerant flows in the order of the bypass flow rate adjusting valve 14, the high / low pressure heat exchanger 13, and the accumulator 6.
- the control device 30 controls the entire air conditioner 100. Further, the control device 30 is a compressor measured by the outside air temperature measured by the outside air temperature sensor 11, the discharge temperature of the refrigerant discharged from the compressor 1 measured by the compressor discharge temperature sensor 2, and the high pressure pressure sensor 7. Flow path switching device 8, first heat exchanger fan 10a, second heat exchanger fan 10b, flow rate adjusting valve 12, bypass flow rate adjusting valve based on the pressure of the refrigerant discharged from 1 and flowing to the flow path switching device 8. 14 and the expansion valve 15 are controlled.
- FIG. 3 is a block diagram showing the function of the control device 30 of the air conditioner 100 according to the first embodiment.
- control device 30 includes an outside air temperature determination unit 31, a predetermined condition determination unit 32, a discharge superheat degree calculation determination unit 33, and a flow path control unit 34.
- the outside air temperature determination unit 31 determines whether or not the outside air temperature measured by the outside air temperature sensor 11 is a predetermined temperature. For example, the outside air temperature determination unit 31 determines whether or not the temperature is the first temperature (for example, ⁇ 5 ° C.).
- the predetermined condition determination unit 32 determines whether or not the predetermined condition is satisfied based on the outside air temperature measured by the outside air temperature sensor 11 and the pressure measured by the compressor discharge temperature sensor 2.
- the "predetermined condition” means that the outside air measured by the outside air temperature sensor 11 after continuously detecting that the discharge superheat degree of the compressor 1 is equal to or higher than the set discharge superheat degree (for example, 30 ° C.) for 5 minutes. This is the case where the temperature is equal to or lower than the first temperature (for example, ⁇ 5 ° C.).
- the discharge superheat degree calculation determination unit 33 is based on the discharge temperature of the compressor 1 measured by the compressor discharge temperature sensor 2 and the saturation temperature of the refrigerant calculated using the pressure measured by the high pressure pressure sensor 7. , The discharge superheat degree of the compressor 1 is obtained. Further, the discharge superheat degree calculation determination unit 33 detects that the obtained discharge superheat degree is continuously detected for 5 minutes to be equal to or higher than a predetermined discharge superheat degree (for example, 30 ° C.).
- a predetermined discharge superheat degree for example, 30 ° C.
- the flow path control unit 34 has a flow path switching device 8, a flow rate adjusting valve 12, a first heat exchanger fan 10a, and a second heat according to a judgment result by the outside air temperature judgment unit 31 and a judgment result by the predetermined condition judgment unit 32. Controls the exchanger fan 10b.
- the control device 30 is composed of dedicated hardware or a CPU (also referred to as a central processing unit, a processing unit, a computing device, a microprocessor, a microprocessor, or a processor) that executes a program stored in a memory. ..
- a CPU also referred to as a central processing unit, a processing unit, a computing device, a microprocessor, a microprocessor, or a processor
- control device 30 When the control device 30 is dedicated hardware, the control device 30 corresponds to, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field ProgrammableGate Array), or a combination thereof.
- ASIC Application Specific Integrated Circuit
- FPGA Field ProgrammableGate Array
- Each of the functional units realized by the control device 30 may be realized by individual hardware, or each functional unit may be realized by one hardware.
- each function executed by the control device 30 is realized by software, firmware, or a combination of software and firmware.
- Software and firmware are written as programs and stored in memory.
- the CPU realizes each function of the control device 30 by reading and executing a program stored in the memory.
- the memory is a non-volatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.
- control device 30 may be realized by dedicated hardware, and some may be realized by software or firmware.
- FIG. 4 is a flowchart for explaining the operation of the outdoor unit 101 of the air conditioner 100 according to the first embodiment.
- the operation of the compressor 1 starts with the start of the cooling operation (S1).
- the control device 30 controls the flow path switching device 8 to switch to the second flow path and controls the flow rate adjusting valve 12 to open.
- the refrigerant discharged from the compressor 1 circulates through the oil separator 3, the first heat exchanger 9a and the second heat exchanger 9b, the high and low pressure heat exchanger 13, the expansion valve 15, the indoor heat exchanger 16 and the accumulator 6.
- the refrigerant discharged from the compressor 1 passes through the oil separator 3, the flow path switching device 8, the second heat exchanger 9b, the flow rate adjusting valve 12, and the refrigerant circuit pipe 25, and flows through the refrigerant circuit pipe 26. It merges with the refrigerant that has passed through the heat exchanger 9a.
- the control device 30 uses only the first heat exchanger 9a to perform the heat exchanger 1/2 operation without using the second heat exchanger 9b (S2).
- the control device 30 controls the flow path switching device 8 to switch to the first flow path and controls the flow rate adjusting valve 12 to be closed.
- the refrigerant discharged from the compressor 1 circulates in the oil separator 3, the first heat exchanger 9a, the high / low pressure heat exchanger 13, the expansion valve 15, the indoor heat exchanger 16 and the accumulator 6 and returns to the compressor 1.
- the refrigerant discharged from the compressor 1 is not supplied to the second heat exchanger 9b because the flow path switching device 8 is switched to the first flow path. Further, since the flow rate adjusting valve 12 is controlled to be closed, the refrigerant does not flow out from the second heat exchanger 9b.
- the flow rate adjusting valve 12 blocks the flow path of the refrigerant of the second heat exchanger 9b.
- the refrigerant remains in the second heat exchanger 9b, which is not functioning as a condenser.
- the circulation amount of the refrigerant is reduced, and the discharge superheat degree of the compressor 1 is lowered.
- the control device 300 operates the first heat exchanger fan 10a, and does not operate the second heat exchanger fan 10b.
- the control device 30 determines whether or not 30 minutes have passed since the compressor 1 was operated while the second heat exchanger 9b is not being used and the heat exchanger 1/2 operation is being performed. (S3). If it is determined in step S3 that 30 minutes have not passed (NO in S3), the control device 30 continues the determination in step S3. On the other hand, if it is determined in step S3 that 30 minutes have passed (YES in S3), the control device 30 moves to the process of step S4. Here, 30 minutes was used as the criterion for determination. In the outdoor unit 101 of the air conditioner 100 of the first embodiment, the refrigerant remained in the second heat exchanger 9b and the amount of refrigerant circulation increased in 30 minutes. This is because the cycle is reduced.
- step S4 may be frequently performed, and each time, the heat exchange amount of the second heat exchanger 9b is increased and the pressure is decreased, so that the compressor is used. This is because it is easy to deviate from the operating range of 1.
- the control device 30 determines whether or not the outside air temperature measured by the outside air temperature sensor 11 is equal to or lower than the first temperature (for example, ⁇ 5 ° C.) (S4). When it is determined in step S4 that the outside air temperature measured by the outside air temperature sensor 11 is not equal to or lower than the first temperature (NO in S4), the control device 30 returns to the process of step S3. When it is determined in step S4 that the outside air temperature measured by the outside air temperature sensor 11 is equal to or lower than the first temperature (YES in S4), the control device 30 moves to the process of step S5.
- the second heat exchanger 9b is cooled to an outside air temperature of ⁇ 5 ° C. or lower.
- the pressure of the second heat exchanger 9b becomes lower than the operating pressure of the compressor 1. Therefore, the outside air temperature of ⁇ 5 ° C. or lower is set as a condition for the refrigerant to remain in the second heat exchanger 9b.
- step S5 the control device 30 is based on the discharge temperature of the compressor 1 measured by the compressor discharge temperature sensor 2 and the saturation temperature of the refrigerant calculated using the pressure measured by the high pressure pressure sensor 7. The discharge superheat degree of the compressor 1 is obtained. Then, the control device 30 determines whether or not it has been continuously detected for 5 minutes that the determined discharge superheat degree is equal to or higher than the predetermined discharge superheat degree (for example, 30 ° C.). In step S5, if it is not continuously detected for 5 minutes that the discharge superheat degree is equal to or higher than the predetermined discharge superheat degree (NO in S5), the control device 30 returns to the process of step S3.
- the predetermined discharge superheat degree for example, 30 ° C.
- step S5 when it is continuously detected for 5 minutes that the discharge superheat degree is equal to or higher than the predetermined discharge superheat degree (YES in S5), it is determined that the refrigerant remains in the second heat exchanger 9b. Then, the process proceeds to step S6.
- the condition that the detection is continuous for 5 minutes is to detect that the discharge superheat degree is transiently 30 ° C. to prevent erroneous detection.
- step S6 the control device 30 switches the flow path switching device 8 to the second flow path, and connects the second heat exchanger 9b to the high-pressure side pipe 24. Further, the control device 30 opens the flow rate adjusting valve 12. As a result, the refrigerant remaining in the second heat exchanger 9b is released to the refrigerant circuit pipe 26 via the refrigerant circuit pipe 25. Further, the control device 30 turns off the first heat exchanger fan 10a and the second heat exchanger fan 10b. As a result, the power consumption of the first heat exchanger fan 10a and the second heat exchanger fan 10b can be reduced.
- step S7 whether or not a predetermined time (for example, 30 seconds) has elapsed since the control device 30 controlled the flow path switching device 8 and the flow rate adjusting valve 12 to change the flow path in step S6. Judgment is made (S7). If it is determined in step S7 that 30 seconds have not elapsed (NO in S7), the control device 30 continues the determination in step S7. On the other hand, if it is determined in step S7 that 30 seconds have passed (YES in S7), the control device 30 moves to the process of step S8.
- 30 seconds was used as the criterion for determination when the second heat exchanger 9b was connected to the high pressure side for more than 30 seconds in the outdoor unit 101 of the air conditioner 100 of the first embodiment. This is because the amount of heat exchange as a condenser increases and the pressure on the high pressure side decreases.
- step S8 as shown in FIG. 1, the control device 30 switches the flow path switching device 8 to the first flow path and connects the second heat exchanger 9b to the low-voltage side pipe 27. Further, the control device 30 closes the flow rate adjusting valve 12. At this time, the first heat exchanger fan 10a and the second heat exchanger fan 10b are kept off. Further, the control device 30 resets the timer for measuring the time of 1/2 operation (S8), and returns to step S3.
- the control device 30 is the outside air temperature measured by the outside air temperature sensor 11, the pressure measured by the compressor discharge temperature sensor 2, and the high pressure pressure sensor 7. Based on the pressure measured by, it is determined whether or not the predetermined condition is satisfied. When the control device 30 determines that the predetermined conditions are satisfied, it determines that the refrigerant remains in the second heat exchanger 9b, switches the flow path switching device 8 to the second flow path, and adjusts the flow rate. Open the valve 12. As a result, the high-pressure side pipe 24 is connected to the second heat exchanger 9b, and the refrigerant remaining in the second heat exchanger 9b is released to the refrigerant circuit through the refrigerant circuit pipe 25.
- Embodiment 2 In the first embodiment, the case of returning to the original heat exchanger 1/2 operation after 30 seconds have passed as the time for recovering the refrigerant remaining in the second heat exchanger 9b has been described. However, the amount of refrigerant remaining in the second heat exchanger 9b increases as the outside air temperature decreases.
- the refrigerant recovery time for recovering the refrigerant remaining in the second heat exchanger 9b is changed according to the outside air temperature when the control of the heat exchanger 1/2 operation is started.
- the refrigerant time is set to a time during which the refrigerant can be sufficiently recovered. If the recovery time of the residual refrigerant into the refrigerant circuit is too long, the condensing capacity of the first heat exchanger 9a and the second heat exchanger 9b increases, the pressure on the high pressure side of the compressor 1 decreases, and the compressor 1 It goes out of the operating range of.
- the refrigerant recovery time is determined in consideration of the above viewpoints.
- FIG. 5 is a diagram for explaining the refrigerant recovery time of the air conditioner 100 according to the second embodiment.
- the refrigerant recovery time is set in proportion to the outside air temperature.
- the refrigerant recovery time is set to 90 seconds.
- the refrigerant recovery time is set to 60 seconds, and when the outside air temperature is ⁇ 5 [° C.], the refrigerant recovery time is set to 30 seconds.
- the refrigerant remaining in the second heat exchanger 9b can be recovered more appropriately as compared with the first embodiment.
- Embodiment 3 In the second embodiment, the case where the refrigerant recovery time is set by the outside air temperature has been described.
- the control device 30, which will be described in the third embodiment, may determine the refrigerant recovery time based on the degree of superheat discharge of the compressor 1.
- FIG. 6 is a flowchart for explaining the operation of the outdoor unit 101 of the air conditioner 100 according to the third embodiment.
- steps S1 to S6 and step S8 are the same as the operations shown in FIG. 4, so the description thereof will be omitted, and only the operations of step S7A in different parts will be described here.
- step S7A the control device 30 controls the flow path switching device 8 and the flow rate adjusting valve 12 to change the flow path in step S6, and then the discharge superheat degree of the compressor 1 is a predetermined discharge superheat degree (for example). , 25 ° C) or less. If it is determined in step S7A that the discharge superheat degree is not 25 ° C. or lower (NO in S7A), the control device 30 continues the determination in step S7A. On the other hand, when it is determined in step S7A that the discharge superheat degree is 25 ° C. or lower (YES in S7A), the control device 30 moves to the process of step S8.
- a predetermined discharge superheat degree for example. , 25 ° C
- the control device 30 continues the determination in step S7A. On the other hand, when it is determined in step S7A that the discharge superheat degree is 25 ° C. or lower (YES in S7A), the control device 30 moves to the process of step S8.
- the embodiment is presented as an example and is not intended to limit the scope of the embodiment.
- the embodiment can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the gist of the embodiment. These embodiments and variations thereof are included in the scope and gist of the embodiments.
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Abstract
Description
図1は、実施の形態1に係る空気調和装置100の冷媒回路構成を示す図である。また、図1は、空気調和装置100の室外機101の外気温度が例えば、-15℃の場合における流路構成を示す。
実施の形態1では、第2熱交換器9bに残留した冷媒を回収する時間として30秒を経過した後に元の熱交換器1/2運転に戻す場合について説明した。しかし、第2熱交換器9bに残留する冷媒量は、外気温度が低くなるにつれて多くなる。
実施の形態2においては、冷媒回収時間を外気温度により設定する場合について説明した。実施の形態3ではこれについて説明する、制御装置30は、圧縮機1の吐出過熱度によって冷媒回収時間を判断しても良い。
Claims (6)
- 冷媒を圧縮する圧縮機と、
前記圧縮機から吐出した冷媒が流れる高圧側配管と、
前記高圧側配管に接続され、凝縮器として機能する第1熱交換器と、
前記高圧側配管及び前記第1熱交換器に接続され、かつ前記第1熱交換器に並列に接続され、凝縮器として機能する第2熱交換器と、
前記高圧側配管と前記第2熱交換器とに接続され、前記圧縮機から吐出された冷媒を前記高圧側配管を介して前記第1熱交換器に供給し、前記第2熱交換器へ供給しない第1流路又は前記第1熱交換器及び前記第2熱交換器へ前記高圧側配管を介して供給する第2流路に切替える流路切替装置と、
前記第2熱交換器の冷媒の出口に接続された流量調整弁と、
前記第1熱交換器の冷媒の出口及び前記流量調整弁に接続された冷媒回路配管と、
外気温度を測定する外気温度センサと、
前記流路切替装置及び前記流量調整弁を制御する制御装置と
を具備し、
前記冷媒回路配管は、前記冷媒が前記圧縮機、前記流路切替装置、前記第1熱交換器、前記第2熱交換器、前記流量調整弁、膨張弁、室内機の蒸発器を循環する冷媒回路の前記第1熱交換器及び前記第2熱交換器と、前記膨張弁との間を接続する配管であり、
前記制御装置は、
前記流路切替装置を前記第1流路に切替えた状態において、前記外気温度センサにより測定された外気温度が氷点下以下の第1温度以下であり、かつ、前記圧縮機の吐出過熱度が第1吐出過熱度以上である所定条件が成立しているか否かを判断し、
前記所定条件が成立していると判断した場合に、前記流路切替装置を前記第2流路に切替え及び前記流量調整弁を開にし、前記第2熱交換器に残留した前記冷媒を前記冷媒回路配管に流す
空気調和装置。 - 前記圧縮機から吐出される冷媒の温度を測定する圧縮機吐出温度センサと、
前記圧縮機から吐出され、前記流路切替装置へ流れる冷媒の圧力を測定する高圧圧力センサと、
をさらに具備し、
前記圧縮機の吐出過熱度は、前記圧縮機吐出温度センサにより測定された吐出温度及び前記高圧圧力センサにより測定された圧力に基づいて得られる
請求項1に記載の空気調和装置。 - 前記制御装置は、
前記所定条件が成立し、前記流路切替装置を前記第2流路に切替え及び前記流量調整弁を開にした後、所定時間経過後、前記流路切替装置を前記第1流路に切替え及び前記流量調整弁を閉にする
請求項1又は2に記載の空気調和装置。 - 前記所定時間は、前記所定条件が成立した際の前記外気温度センサにより測定された外気温度に従って設定される
請求項3に記載の空気調和装置。 - 前記制御装置は、
前記所定条件が成立し、前記流路切替装置を前記第2流路に切替え及び前記流量調整弁を開にした後、前記圧縮機の吐出過熱度が第2吐出過熱度以下の場合に、前記流路切替装置を前記第1流路に切替え及び前記流量調整弁を閉にする
請求項1に記載の空気調和装置。 - 前記第1熱交換器に室外空気を供給して熱交換量を調整する第1熱交換器用ファンと、
前記第2熱交換器に室外空気を供給して熱交換量を調整する第2熱交換器用ファンと
をさらに具備し、
前記制御装置は、
前記流路切替装置を前記第1流路に切替えている場合、前記第1熱交換器用ファン及び前記第2熱交換器用ファンは停止する
請求項1~5のいずれか1項に記載の空気調和装置。
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JP2000193327A (ja) * | 1998-12-25 | 2000-07-14 | Mitsubishi Electric Corp | 空気調和機および空気調和機の制御方法 |
JP2014214951A (ja) * | 2013-04-25 | 2014-11-17 | 株式会社富士通ゼネラル | 空気調和装置 |
JP2018013287A (ja) * | 2016-07-20 | 2018-01-25 | 三菱重工サーマルシステムズ株式会社 | 空気調和機及び空気調和機の制御方法 |
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JP2000193327A (ja) * | 1998-12-25 | 2000-07-14 | Mitsubishi Electric Corp | 空気調和機および空気調和機の制御方法 |
JP2014214951A (ja) * | 2013-04-25 | 2014-11-17 | 株式会社富士通ゼネラル | 空気調和装置 |
JP2018013287A (ja) * | 2016-07-20 | 2018-01-25 | 三菱重工サーマルシステムズ株式会社 | 空気調和機及び空気調和機の制御方法 |
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