WO2015140874A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2015140874A1 WO2015140874A1 PCT/JP2014/057032 JP2014057032W WO2015140874A1 WO 2015140874 A1 WO2015140874 A1 WO 2015140874A1 JP 2014057032 W JP2014057032 W JP 2014057032W WO 2015140874 A1 WO2015140874 A1 WO 2015140874A1
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- refrigerant
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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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- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
- C09K5/02—Materials undergoing a change of physical state when used
- C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
- C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
- C09K5/044—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds
- C09K5/045—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds containing only fluorine as halogen
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B45/00—Arrangements for charging or discharging refrigerant
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- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
- C09K2205/10—Components
- C09K2205/12—Hydrocarbons
- C09K2205/126—Unsaturated fluorinated hydrocarbons
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/12—Inflammable refrigerants
- F25B2400/121—Inflammable refrigerants using R1234
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
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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
- F25B2500/19—Calculation of parameters
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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
- F25B2600/021—Inverters therefor
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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
- F25B2600/02—Compressor control
- F25B2600/027—Compressor control by controlling pressure
- F25B2600/0271—Compressor control by controlling pressure the discharge pressure
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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
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
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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
- F25B2600/2501—Bypass 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2519—On-off 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
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction 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
- F25B2700/2115—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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P20/00—Technologies relating to chemical industry
- Y02P20/10—Process efficiency
Definitions
- the present invention relates to an air conditioner including a refrigerant circuit in which a compressor, a heat source side heat exchanger, an expansion valve, and a use side heat exchanger are connected by piping and the refrigerant circulates.
- Patent Document 1 describes a thermal cycle system using a thermal cycle working medium containing 1,1,2-trifluoroethylene (HFO1123).
- the HFO1123 refrigerant or the mixed refrigerant containing HFO1123 When the HFO1123 refrigerant or the mixed refrigerant containing HFO1123 is applied as the refrigerant to be filled in the refrigerant circuit as in the technique described in Patent Document 1, the HFO1123 generates a disproportionation reaction (self-decomposition reaction) under high pressure and high temperature conditions. However, a rapid increase in pressure occurs due to the chain reaction. For this reason, it is desired to operate in the range of an appropriate pressure and temperature so that the disproportionation reaction does not occur.
- the present invention has been made against the background of the above problems, and in the case of applying HFO1123 refrigerant or a mixed refrigerant containing HFO1123, air conditioning that can suppress the occurrence of disproportionation reaction (self-decomposition reaction).
- the object is to obtain a device.
- An air conditioner is an air conditioner including a refrigerant circuit in which a compressor, a heat source side heat exchanger, an expansion valve, and a use side heat exchanger are connected by piping, and the refrigerant circulates, wherein the refrigerant Is an HFO1123 refrigerant, or a mixed refrigerant containing HFO1123, so that the temperature and pressure of the refrigerant discharged from the compressor do not exceed a threshold, the operating frequency of the compressor, the opening of the expansion valve, And the control apparatus which controls at least 1 of the air volume of the air blower ventilated to the said heat source side heat exchanger is provided.
- the present invention can suppress the occurrence of disproportionation reaction (self-decomposition reaction) in the case of applying HFO1123 refrigerant or a mixed refrigerant containing HFO1123.
- FIG. 2 is a refrigerant circuit diagram of the air-conditioning apparatus 100 according to Embodiment 1.
- FIG. It is a figure which shows the relationship between the disproportionation reaction of HFO1123 refrigerant
- 3 is a flowchart showing the operation of the control device 40 of the air-conditioning apparatus 100 according to Embodiment 1.
- 6 is a flowchart showing the operation of the control device 40 of the air-conditioning apparatus 100 according to Embodiment 2.
- FIG. 1 is a refrigerant circuit diagram of an air-conditioning apparatus 100 according to Embodiment 1.
- the air conditioner 100 includes an outdoor unit 1 and an indoor unit 2, and the outdoor unit 1 and the indoor unit 2 are connected by a liquid pipe 8 and a gas pipe 5.
- the outdoor unit 1 includes the compressor 3, the four-way valve 4, the heat source side heat exchanger 9, the expansion valve 7, the heat source side blower 91 that blows air to the heat source side heat exchanger 9, and the operation of each part constituting the air conditioner 100.
- the control apparatus 40 which controls is provided.
- the indoor unit 2 includes a use side heat exchanger 6 and a use side blower 61 that blows air to the use side heat exchanger 6.
- the compressor 3, the four-way valve 4, the heat source side heat exchanger 9, the expansion valve 7, and the use side heat exchanger 6 are sequentially connected by a pipe to form a refrigerant circuit in which the refrigerant circulates.
- the outdoor unit 1 further includes a bypass circuit 20 that branches a pipe between the expansion valve 7 and the first on-off valve 11 and connects to a pipe on the suction side of the compressor 3.
- the bypass circuit 20 is provided with a first bypass opening / closing valve 21, a second bypass opening / closing valve 22, and a container 30 for storing refrigerant.
- the compressor 3 is a type in which the number of revolutions is controlled by an inverter, for example, and the capacity is controlled.
- the expansion valve 7 is an electronic expansion valve whose opening degree is variably controlled, for example.
- the heat source side heat exchanger 9 exchanges heat with the outside air blown by the heat source side blower 91.
- the use side heat exchanger 6 exchanges heat with room air blown by the use side blower 61.
- the first bypass on-off valve 21 is provided on the refrigerant inflow side of the bypass circuit 20 (the pipe side between the expansion valve 7 and the first on-off valve 11).
- the second bypass on-off valve 22 is provided on the refrigerant outflow side of the bypass circuit 20 (the piping side on the suction side of the compressor 3).
- the first bypass on-off valve 21 and the second bypass on-off valve 22 are on-off valves that open and close the refrigerant flow path of the bypass circuit 20.
- the container 30 is a container that stores a refrigerant.
- the gas pipe 5 and the liquid pipe 8 are connection pipes that connect the outdoor unit 1 and the indoor unit 2.
- the first on-off valve 11 and the second on-off valve 12 are connected to the liquid pipe 8 and the gas pipe 5, respectively.
- the liquid pipe 8 connects between the use side heat exchanger 6 of the indoor unit 2 and the first on-off valve 11 of the outdoor unit 1.
- the gas pipe 5 connects between the use side heat exchanger 6 of the indoor unit 2 and the second on-off valve 12 of the outdoor unit 1.
- the first on-off valve 11, the second on-off valve 12, the first bypass on-off valve 21, and the second bypass on-off valve 22 may be manual valves that are manually opened and closed, and the open / close state is controlled by the control device 40. It may be a solenoid valve.
- the outdoor unit 1 further includes a discharge temperature sensor 41, a discharge pressure sensor 51, and a suction pressure sensor 52.
- the discharge temperature sensor 41 detects the temperature of the refrigerant discharged from the compressor 3.
- the discharge pressure sensor 51 detects the pressure of the refrigerant discharged from the compressor 3.
- the suction pressure sensor 52 detects the pressure of the refrigerant sucked into the compressor 3. Note that the pressure of the refrigerant circulating in the refrigerant circuit is lowest on the suction side of the compressor 3 and highest on the discharge side of the compressor 3. Therefore, in the following description, the pressure on the suction side of the compressor 3 is referred to as a low pressure, and the pressure on the discharge side of the compressor 3 is referred to as a high pressure.
- a substance causing a disproportionation reaction such as 1,1,2-trifluoroethylene (HFO1123) or a nature causing a disproportionation reaction.
- a mixed refrigerant in which another substance is mixed with this substance is used.
- a substance mixed with a substance having a disproportionation reaction includes, for example, tetrafluoropropene (HFO1234yf, which is 2,3,3,3-tetrafluoropropene, 1,3,3).
- 3-tetrafluoro-1-propene such as HFO1234ze), difluoromethane (HFC32), etc., but is not limited thereto, HC290 (propane), etc.
- HC290 propane
- Any material may be used as long as it is a substance having thermal performance that can be used as the refrigerant of (), and any mixing ratio may be used.
- the air conditioner 100 configured in this manner can be cooled or heated by switching the four-way valve 4.
- the air conditioner 100 can perform a pump-down operation for collecting the refrigerant in the indoor unit 2 in the outdoor unit 1.
- the solid line indicates the flow during cooling
- the dotted line indicates the flow during heating
- the low-pressure two-phase refrigerant that has flowed out of the expansion valve 7 passes through the liquid pipe 8 and flows into the indoor unit 2, evaporates by exchanging heat with indoor air in the use-side heat exchanger 6, and flows out as low-pressure gas refrigerant. To do.
- the low-pressure gas refrigerant that has flowed out of the use-side heat exchanger 6 passes through the gas pipe 5, flows into the outdoor unit 1, and returns to the compressor 3 through the four-way valve 4.
- the first bypass opening / closing valve 21 is in a closed state, so that no refrigerant flows into the bypass circuit 20.
- the liquid sealing of the container 30 can be prevented by opening the second bypass on-off valve 22.
- the heating operation in the normal operation will be described.
- the four-way valve 4 is switched to the heating side (state indicated by a dotted line).
- the 1st on-off valve 11, the 2nd on-off valve 12, and the 2nd bypass on-off valve 22 are an open state.
- the first bypass on-off valve 21 is in a closed state.
- the high-pressure and high-temperature gas refrigerant flows into the use side heat exchanger 6 of the indoor unit 2 through the four-way valve 4 and the gas pipe 5. Dissipates heat by exchanging heat with room air and flows out as high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant that has flowed out of the use-side heat exchanger 6 passes through the liquid pipe 8 and flows into the expansion valve 7 to become a low-pressure two-phase refrigerant.
- the low-pressure two-phase refrigerant that has flowed out of the expansion valve 7 flows into the heat source side heat exchanger 9 and evaporates by heat exchange with outdoor air, and flows out as low-pressure gas refrigerant.
- the low-pressure gas refrigerant that has flowed out of the heat source side heat exchanger 9 returns to the compressor 3 via the four-way valve 4.
- the first bypass opening / closing valve 21 is in the closed state, so that no refrigerant flows into the bypass circuit 20.
- the liquid sealing of the container 30 can be prevented by opening the second bypass on-off valve 22.
- the low-pressure gas refrigerant is compressed by the compressor 3 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-pressure and high-temperature gas refrigerant discharged from the compressor 3 flows into the heat source side heat exchanger 9 through the four-way valve 4 and radiates heat by exchanging heat with outdoor air, and flows out as high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 9 passes through the expansion valve 7 and flows into the bypass circuit 20.
- the high-pressure liquid refrigerant flowing into the bypass circuit 20 passes through the first bypass opening / closing valve 21 and flows into the container 30.
- the second bypass opening / closing valve 22 Since the second bypass opening / closing valve 22 is in the closed state, the high-pressure liquid refrigerant that has flowed into the bypass circuit 20 is stored in the container 30.
- the refrigerant in the use side heat exchanger 6, the liquid pipe 8, and the gas pipe 5 is sucked by the operation of the compressor 3, discharged from the compressor 3, and then stored in the container 30 by the above operation.
- the refrigerant in the indoor unit 2 is recovered to the outdoor unit 1 side.
- the second on-off valve 12 is closed and, for example, the indoor unit 2 is removed.
- the air conditioner 100 uses an HFO1123 refrigerant alone or a mixed refrigerant obtained by mixing HFO1123 and another refrigerant (for example, R32, HFO1234yf, etc.) as the refrigerant used in the refrigeration cycle (refrigerant circuit).
- HFO1123 refrigerant a disproportionation reaction (self-decomposition reaction) occurs under high pressure and high temperature conditions, and a rapid pressure increase or the like occurs due to a chain reaction. That is, in order to prevent the occurrence of the disproportionation reaction, it is necessary to operate so that the temperature of the refrigerant falls within an appropriate pressure and temperature range.
- FIG. 2 is a diagram showing the relationship between the disproportionation reaction of HFO1123 refrigerant, pressure and temperature.
- the refrigerant having the highest temperature and pressure is the refrigerant discharged from the compressor 3.
- the amount of refrigerant circulating in the refrigerant circuit is reduced, and thus the temperature and pressure of the refrigerant discharged from the compressor 3 are likely to increase. Therefore, as shown in FIG. 2, the temperature of the refrigerant discharged from the compressor 3 is prevented from exceeding the temperature threshold value Tdmax, and the pressure of the refrigerant discharged from the compressor 3 is not exceeded the pressure threshold value Pdmax.
- FIG. 3 is a flowchart showing the operation of the control device 40 of the air-conditioning apparatus 100 according to Embodiment 1. Hereinafter, based on each step of FIG. 3, the control operation for preventing the occurrence of the disproportionation reaction will be described.
- the control device 40 stores in advance information on a temperature threshold Tdmax and a pressure threshold Pdmax that are lower than the temperature and pressure in the disproportionation reaction region.
- the control device 40 acquires the detection results of the discharge temperature sensor 41 and the discharge pressure sensor 51, determines whether or not the temperature of the refrigerant discharged from the compressor 3 (hereinafter referred to as discharge temperature Td) exceeds a temperature threshold Tdmax, and Then, it is determined whether or not the pressure of the refrigerant discharged from the compressor 3 (hereinafter, discharge pressure Pd) exceeds the pressure threshold value Pdmax. If the discharge temperature Td exceeds the temperature threshold Tdmax and the discharge pressure Pd exceeds the pressure threshold Pdmax, the process proceeds to step S11.
- step S11 when the discharge temperature Td does not exceed the temperature threshold value Tdmax or the discharge pressure Pd does not exceed the pressure threshold value Pdmax, the operation of step S11 is not performed, and the current control state is maintained and the process proceeds to step S10. Return.
- the control device 40 decelerates (decreases) the operating frequency of the compressor 3. This deceleration amount may be set according to the discharge temperature Td and the discharge pressure Pd, or may be a preset value. After step S11, the control device 40 returns to step S10 and repeats the above operation. That is, the above operation is repeated until the discharge temperature Td and the discharge pressure Pd are lower than the temperature threshold value Tdmax and the pressure threshold value Pdmax.
- the control in step S11 is not limited to the deceleration of the operating frequency of the compressor 3, and the opening degree of the expansion valve 7 may be increased. Moreover, you may increase the air volume of the air blower sent to the heat source side heat exchanger 9. That is, the control device 40 controls the operation frequency of the compressor 3, the opening degree of the expansion valve 7, and the heat source side heat exchanger 9 so that the discharge temperature Td and the discharge pressure Pd do not exceed the temperature threshold value Tdmax and the pressure threshold value Pdmax. What is necessary is just to control at least one of the air volume of the air blower which ventilates.
- control operation for preventing the above-described disproportionation reaction may be performed in any of the cooling operation, the heating operation, and the pump-down operation.
- the control device 40 performs control so that the discharge temperature Td and the discharge pressure Pd do not exceed the temperature threshold Tdmax and the pressure threshold Pdmax. For this reason, when applying the HFO1123 refrigerant
- Embodiment 2 the difference from the first embodiment will be mainly described, and the same components as those in the first embodiment will be denoted by the same reference numerals and the description thereof will be omitted.
- the discharge temperature sensor 41 is used to detect the discharge temperature Td discharged from the compressor 3. However, since there is a response delay in temperature detection by the discharge temperature sensor 41, there may be a difference between the actual temperature and the detected temperature.
- the discharge temperature Td is calculated from the detection values of the discharge pressure sensor 51 and the suction pressure sensor 52.
- FIG. 4 is a flowchart showing the operation of the control device 40 of the air-conditioning apparatus 100 according to Embodiment 2.
- differences from the first embodiment will be described based on the steps in FIG.
- the same operations as those in the first embodiment are denoted by the same step numbers, and description thereof is omitted.
- the control device 40 calculates the discharge temperature Td from the detection values of the discharge pressure sensor 51 and the suction pressure sensor 52.
- the discharge temperature Td [K] is the temperature of the refrigerant sucked into the compressor 3 (hereinafter referred to as the suction temperature Ts) [K]
- the discharge pressure Pd [MPa] Using the pressure of the refrigerant sucked into the compressor 3 (hereinafter referred to as the suction pressure Ps) [MPa] and the polytropic index k [ ⁇ ], the relationship of Expression (1) is established.
- the detection value of the discharge pressure sensor 51 is used as the discharge pressure Pd.
- a detection value of the suction pressure sensor 52 is used as the suction pressure Ps.
- the suction temperature Ts is calculated and obtained as the saturated gas temperature of the suction pressure Ps.
- the polytropic index k a fixed value determined from the characteristics of the compressor 3 is used.
- the control device 40 calculates the discharge temperature Td from the detection values of the discharge pressure sensor 51 and the suction pressure sensor 52. For this reason, in addition to the effect of the said Embodiment 1, there exist the following effects. That is, since the discharge temperature Td is calculated using the detection values of the discharge pressure sensor 51 and the suction pressure sensor 52 that do not cause a response delay due to the heat capacity as in the temperature sensor, an error between the actual discharge temperature Td and the detection value. Can be reduced. Therefore, the temperature rise of the discharge temperature Td can be detected more quickly. Therefore, generation of disproportionation reaction (self-decomposition reaction) can be suppressed with higher accuracy.
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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の冷媒回路図である。
図1に示すように、空気調和装置100は、室外機1と室内機2とを備え、室外機1と室内機2とが液配管8及びガス配管5で接続されている。
室内機2は、利用側熱交換器6、及び利用側熱交換器6に空気を送風する利用側送風機61を備えている。
空気調和装置100は、圧縮機3、四方弁4、熱源側熱交換器9、膨張弁7、利用側熱交換器6が、順次配管で接続されて冷媒が循環する冷媒回路を形成する。
膨張弁7は、例えば開度が可変に制御される電子膨張弁である。
熱源側熱交換器9は、熱源側送風機91によって送風される外気と熱交換する。
利用側熱交換器6は、利用側送風機61によって送風される室内空気と熱交換する。
第2バイパス開閉弁22は、バイパス回路20の冷媒の流出側(圧縮機3の吸入側の配管側)に設けられている。
第1バイパス開閉弁21及び第2バイパス開閉弁22は、バイパス回路20の冷媒の流路を開閉する開閉弁である。
容器30は、冷媒を貯留する容器である。
吐出温度センサー41は、圧縮機3から吐出された冷媒の温度を検出する。
吐出圧力センサー51は、圧縮機3から吐出された冷媒の圧力を検出する。
吸入圧力センサー52は、圧縮機3へ吸入される冷媒の圧力を検出する。
なお、冷媒回路を循環する冷媒の圧力は、圧縮機3の吸入側が最も低く、圧縮機3の吐出側が最も高い。よって、以下の説明では、圧縮機3の吸入側の圧力を低圧、圧縮機3の吐出側の圧力を高圧と言う。
混合冷媒を生成させるために、不均化反応を起こす性質の物質に混合させる物質としては、例えば、テトラフルオロプロペン(2,3,3,3-テトラフルオロプロペンであるHFO1234yf、1,3,3,3-テトラフルオロ-1-プロペンであるHFO1234ze等)、ジフルオロメタン(HFC32)等が用いられるが、これらに限るものではなく、HC290(プロパン)等を混合させてもよく、冷凍サイクル(冷媒回路)の冷媒として使用できる熱性能を有する物質であれば、どのようなものを用いてもよく、どのような混合比としてもよい。
まず、通常運転における冷房運転について説明する。
冷房運転時において、四方弁4は冷房側(実線で示す状態)に切り換えられる。また、第1開閉弁11、第2開閉弁12、第2バイパス開閉弁22は、開状態である。第1バイパス開閉弁21は閉状態である。
この状態で圧縮機3から高圧高温のガス冷媒が吐出されると、その高圧高温のガス冷媒は、四方弁4を介して熱源側熱交換器9に流入し、室外空気との熱交換により放熱することで高圧液冷媒となり流出する。熱源側熱交換器9から流出した高圧液冷媒は、膨張弁7に流入し、低圧の二相冷媒となる。
なお、冷房運転時、第1バイパス開閉弁21は閉状態のため、バイパス回路20に冷媒が流入することはない。また、第2バイパス開閉弁22を開状態にすることで、容器30の液封を防止できる。
次に、通常運転における暖房運転について説明する。
暖房運転時において、四方弁4は暖房側(点線で示す状態)に切り換えられる。また、第1開閉弁11、第2開閉弁12、第2バイパス開閉弁22は、開状態である。第1バイパス開閉弁21は閉状態である。
この状態で圧縮機3から高圧高温のガス冷媒が吐出されると、その高圧高温のガス冷媒は、四方弁4及びガス配管5を介して室内機2の利用側熱交換器6に流入し、室内空気との熱交換により放熱することで高圧液冷媒となり流出する。利用側熱交換器6から流出した高圧液冷媒は、液配管8を通過して膨張弁7に流入し、低圧の二相冷媒となる。
なお、暖房運転時、第1バイパス開閉弁21は閉状態のため、バイパス回路20に冷媒が流入することはない。また、第2バイパス開閉弁22を開状態にすることで、容器30の液封を防止できる。
次に、ポンプダウン運転について説明する。
ポンプダウン運転時において、四方弁4は冷房側(実線で示す状態)に切り換えられる。また、第2開閉弁12、第1バイパス開閉弁21は開状態である。第1開閉弁11、第2バイパス開閉弁22は、閉状態である。更に、制御装置40は、膨張弁7の開度を全開にする。また、制御装置40は、熱源側送風機91及び利用側送風機61を運転させる。
バイパス回路20へ流入した高圧液冷媒は、第1バイパス開閉弁21を通過して、容器30へ流入する。第2バイパス開閉弁22は閉状態であるので、バイパス回路20に流入した高圧液冷媒は、容器30内に貯留される。
利用側熱交換器6、液配管8、及びガス配管5内の冷媒は、圧縮機3の運転によって吸引され、圧縮機3から吐出されたあと、上記動作によって、容器30内に貯留される。
HFO1123冷媒は、高圧高温条件では不均化反応(自己分解反応)が発生し、連鎖反応により、急激な圧力上昇等が発生する。
即ち、不均化反応の発生を防止するには、冷媒の温度が適正な圧力及び温度の範囲となるように運転する必要がある。
なお、不均化反応の化学式は、以下の通りである。
CF2=CHF(gas)→1/2CF4(gas)+3/2C(amorphous)+HF+44.7kcal/mol
空気調和装置100の冷媒回路において、冷媒の温度及び圧力が最も高くなるのは、圧縮機3から吐出された冷媒である。特に、ポンプダウン運転を行う場合には、冷媒回路を循環する冷媒量が減少するため、圧縮機3から吐出される冷媒の温度及び圧力が上昇しやすい事情がある。
このため、図2に示すように、圧縮機3から吐出された冷媒の温度が温度閾値Tdmaxを超えないようにし、且つ、圧縮機3から吐出された冷媒の圧力が圧力閾値Pdmax超えないように制御することで、冷媒の温度及び圧力が不均化反応領域とならず、不均化反応の発生を防止できる。
以下、図3の各ステップに基づき、不均化反応の発生を防止する制御動作を説明する。
制御装置40には、予め、不均化反応領域の温度及び圧力よりも低い、温度閾値Tdmax及び圧力閾値Pdmaxの情報が記憶されている。
制御装置40は、吐出温度センサー41及び吐出圧力センサー51の検出結果を取得し、圧縮機3から吐出された冷媒の温度(以下、吐出温度Td)が温度閾値Tdmaxを超えているか否か、及び、圧縮機3から吐出された冷媒の圧力(以下、吐出圧力Pd)が圧力閾値Pdmaxを超えているか否かを判断する。
吐出温度Tdが温度閾値Tdmaxを超え、且つ、吐出圧力Pdが圧力閾値Pdmaxを超えている場合、ステップS11へ進む。
一方、吐出温度Tdが温度閾値Tdmaxを超えていない、又は、吐出圧力Pdが圧力閾値Pdmaxを超えていない場合には、ステップS11の動作を行わず、現在の制御状態を維持してステップS10に戻る。
制御装置40は、圧縮機3の運転周波数を減速(低下)させる。この減速量は、吐出温度Tdと吐出圧力Pdとに応じて設定しても良いし、予め設定した値でも良い。
制御装置40は、ステップS11のあと、ステップS10へ戻り、上記の動作を繰り返す。つまり、吐出温度Td及び吐出圧力Pdが、温度閾値Tdmax及び圧力閾値Pdmaxを下回るまで上記の動作が繰り返される。
このため、HFO1123冷媒又はHFO1123を含む混合冷媒を適用する場合において、不均化反応(自己分解反応)の発生を抑制することができる。
本実施の形態2では実施の形態1との相違点を中心に説明し、実施の形態1と同一の構成には同一の符号を付して説明を省略する。
本実施の形態2においては、吐出温度Tdを、吐出圧力センサー51及び吸入圧力センサー52の検出値から算出して求める。
以下、図11の各ステップに基づき、上記実施の形態1との相違点について説明する。なお、上記実施の形態1と同じ動作には同じステップ番号を付し、説明は省略する。
制御装置40は、吐出温度Tdを、吐出圧力センサー51及び吸入圧力センサー52の検出値から算出する。
圧縮機3の圧縮過程がポリトロープ変化と考えると、吐出温度Td[K]は、圧縮機3への吸入される冷媒の温度(以下、吸入温度Ts)[K]、吐出圧力Pd[MPa]、圧縮機3への吸入される冷媒の圧力(以下、吸入圧力Ps)[MPa]、ポリトロープ指数k[-]を用いて、式(1)の関係となる。
吸入圧力Psは、吸入圧力センサー52の検出値を用いる。
吸入温度Tsは、吸入圧力Psの飽和ガス温度として算出して求める。
ポリトロープ指数kは、圧縮機3の特性から定まる固定値を用いる。
このため、上記実施の形態1の効果に加えて以下の効果がある。即ち、温度センサーのような熱容量による応答遅れが発生しない、吐出圧力センサー51及び吸入圧力センサー52の検出値を用いて、吐出温度Tdを算出するので、実際の吐出温度Tdと検出値との誤差を少なくすることができる。よって、より速く吐出温度Tdの温度上昇を検知できる。したがって、より精度良く、不均化反応(自己分解反応)の発生を抑制することができる。
Claims (2)
- 圧縮機、熱源側熱交換器、膨張弁、及び利用側熱交換器が配管で接続され、冷媒が循環する冷媒回路を備えた空気調和装置であって、
前記冷媒は、HFO1123冷媒、又はHFO1123を含む混合冷媒であり、
前記圧縮機から吐出された前記冷媒の温度及び圧力が、閾値を超えないように、
前記圧縮機の運転周波数、前記膨張弁の開度、及び前記熱源側熱交換器に送風する送風機の風量の少なくとも1つを制御する制御装置を、備えた
空気調和装置。 - 前記圧縮機から吐出された前記冷媒の圧力を検出する吐出圧力センサーと、
前記圧縮機へ吸入される前記冷媒の圧力を検出する吸入圧力センサーと、
を更に備え、
前記制御装置は、
前記圧縮機から吐出された前記冷媒の温度を、前記吐出圧力センサー及び前記吸入圧力センサーの検出値から算出する
請求項1に記載の空気調和装置。
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EP3421903A4 (en) * | 2016-02-22 | 2019-08-28 | Agc Inc. | EXCHANGER UNIT |
JPWO2018003096A1 (ja) * | 2016-06-30 | 2019-02-14 | 三菱電機株式会社 | 空気調和装置 |
JP2018059409A (ja) * | 2016-09-30 | 2018-04-12 | 株式会社富士通ゼネラル | 圧縮機および冷凍サイクル装置 |
JP2018169052A (ja) * | 2017-03-29 | 2018-11-01 | 株式会社富士通ゼネラル | 空気調和装置 |
EP3604971A4 (en) * | 2017-03-31 | 2020-12-02 | Daikin Industries, Ltd. | AIR CONDITIONING DEVICE |
WO2018181065A1 (ja) * | 2017-03-31 | 2018-10-04 | ダイキン工業株式会社 | 空気調和装置 |
JP2018173196A (ja) * | 2017-03-31 | 2018-11-08 | ダイキン工業株式会社 | 空気調和装置 |
US11112154B2 (en) | 2017-03-31 | 2021-09-07 | Daikin Industries, Ltd. | Air conditioner |
KR20190035057A (ko) * | 2017-09-26 | 2019-04-03 | 엘지전자 주식회사 | 공기조화기 및 그의 제어방법 |
KR102368987B1 (ko) * | 2017-09-26 | 2022-03-02 | 엘지전자 주식회사 | 공기조화기 및 그의 제어방법 |
JPWO2020003494A1 (ja) * | 2018-06-29 | 2021-04-01 | 三菱電機株式会社 | 冷凍サイクル装置 |
CN112292572A (zh) * | 2018-06-29 | 2021-01-29 | 三菱电机株式会社 | 制冷循环装置 |
JP2022009578A (ja) * | 2018-06-29 | 2022-01-14 | 三菱電機株式会社 | 冷凍サイクル装置 |
WO2020003494A1 (ja) * | 2018-06-29 | 2020-01-02 | 三菱電機株式会社 | 冷凍サイクル装置 |
JP7159313B2 (ja) | 2018-06-29 | 2022-10-24 | 三菱電機株式会社 | 冷凍サイクル装置 |
JP7258106B2 (ja) | 2018-06-29 | 2023-04-14 | 三菱電機株式会社 | 冷凍サイクル装置 |
JPWO2020039707A1 (ja) * | 2018-08-22 | 2020-08-27 | 日立ジョンソンコントロールズ空調株式会社 | 冷凍サイクル装置および冷凍サイクル装置の冷媒温度管理方法 |
WO2020039707A1 (ja) * | 2018-08-22 | 2020-02-27 | 日立ジョンソンコントロールズ空調株式会社 | 冷凍サイクル装置および冷凍サイクル装置の冷媒温度管理方法 |
Also Published As
Publication number | Publication date |
---|---|
EP3121533B1 (en) | 2021-09-01 |
US10001309B2 (en) | 2018-06-19 |
US20170003060A1 (en) | 2017-01-05 |
CN106164604B (zh) | 2019-01-22 |
CN106164604A (zh) | 2016-11-23 |
EP3121533A4 (en) | 2017-11-29 |
JPWO2015140874A1 (ja) | 2017-04-06 |
EP3121533A1 (en) | 2017-01-25 |
JP6266089B2 (ja) | 2018-01-24 |
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