WO2016059696A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
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- WO2016059696A1 WO2016059696A1 PCT/JP2014/077520 JP2014077520W WO2016059696A1 WO 2016059696 A1 WO2016059696 A1 WO 2016059696A1 JP 2014077520 W JP2014077520 W JP 2014077520W WO 2016059696 A1 WO2016059696 A1 WO 2016059696A1
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- refrigerant
- refrigeration cycle
- hfo
- cycle apparatus
- heat exchanger
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
-
- 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
-
- 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
-
- 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
- F25B40/04—Desuperheaters
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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
- F25B49/027—Condenser control arrangements
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
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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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- 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
- C09K2205/22—All components of a mixture being fluoro compounds
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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
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
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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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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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
Definitions
- the present invention relates to a refrigeration cycle apparatus including a refrigerant circuit.
- R410A ozone layer depletion coefficient
- ODP ozone layer depletion coefficient
- GWP global warming potential
- HFC refrigerant As a candidate for a low GWP refrigerant, there is an HFC refrigerant that does not have a carbon double bond in its composition.
- HFC refrigerants include, for example, R32 (CH 2 F 2 ; difluoromethane) having a lower GWP than R410A.
- a halogenated hydrocarbon having a carbon double bond in the composition, which is a kind of HFC refrigerant like R32.
- halogenated hydrocarbons for example, HFO-1234yf (CF 3 CF ⁇ CH 2 ; tetrafluoropropene), HFO-1234ze (CF 3 —CH ⁇ CHF) and the like are known.
- HFC refrigerant having a carbon double bond in order to distinguish the HFC refrigerant having a carbon double bond from the HFC refrigerant having no carbon double bond in the composition such as R32, an olefin (unsaturated carbon having a carbon double bond) is used.
- olefin unsaturated carbon having a carbon double bond
- HFO refrigerant “HFO refrigerant”.
- HFO-1123 (CF 2 ⁇ CHF; 1, 1, 2 trifluoroethene (ethylene)
- HFO-1234yf 1, 1, 2 trifluoroethene (ethylene)
- HFO-1123 which is a low GWP refrigerant, may cause self-decomposition. Therefore, in order to suppress self-decomposition, there is a case where an HFC refrigerant is mixed with HFO-1123 and used (for example, see Patent Document 1).
- the content of HFO-1123 is preferably 60% or more, more preferably 70% or more in the working fluid (100 mass percent (%)). 80% is more preferable, and 100% is particularly preferable.
- Patent Document 1 since the technology shown in Patent Document 1 has a content of HFO-1123 of 60% or more, the risk of self-decomposition of HFO-1123 under high temperature and high pressure when used in an air conditioner Can not be removed. This can leave problems in performance and quality.
- the present invention has been made to solve the above problems, and provides a refrigeration cycle apparatus in which the refrigerant composition in the refrigerant circuit does not change even when a refrigerant having the property of causing self-decomposition is used. For the purpose.
- a refrigeration cycle apparatus includes a compressor that compresses and discharges a sucked refrigerant, a condenser that radiates heat to the refrigerant and condenses the refrigerant, a decompression device that depressurizes the condensed refrigerant, and causes the refrigerant to absorb heat.
- a refrigerant circuit is configured by connecting an evaporator for evaporating the refrigerant to form a refrigerant circuit.
- the refrigerant is a mixed refrigerant obtained by mixing R32 and HFO-1123, and the mixed refrigerant has a mass percentage of R32> the mass of HFO-1123. Percent.
- the mass% ratio of R32 and HFO-1123 satisfies R32> HFO-1123, thereby preventing self-decomposition of HFO-1123 and changing the refrigerant composition in the refrigerant circuit. Therefore, sufficient performance and quality can be secured.
- FIG. 1 is a schematic configuration diagram showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100A) according to Embodiment 1 of the present invention.
- refrigeration cycle apparatus 100A a refrigeration cycle apparatus
- the refrigeration cycle apparatus 100A has an outdoor unit 1 and an indoor unit 2. And the outdoor unit 1 and the indoor unit 2 are connected via the liquid pipe 7 and the gas pipe 9, and the refrigerant
- coolant comprises the refrigerant circuit.
- the refrigerant flowing through the refrigerant circuit in the refrigeration cycle apparatus 100A is assumed to use a refrigerant having a property of causing self-decomposition as a main component.
- one outdoor unit 1 and one indoor unit 2 are connected to each other by pipes to form a refrigerant circuit.
- the number of units is not limited to one, and any one or a plurality of each may be connected.
- the outdoor unit (heat source unit) 1 conveys heat (hot or cold) to the indoor unit 2.
- the outdoor unit 1 includes a compressor 3, a four-way valve 4, an outdoor heat exchanger (first heat exchanger) 5, an outdoor fan 5a, and an electronic expansion valve 6.
- the indoor unit (use side unit) 2 supplies heat to a supply target, for example, and heats or cools the supply target.
- the indoor unit 2 has an indoor heat exchanger (second heat exchanger) 8 and an indoor blower 8a.
- Compressor 3 compresses and discharges the refrigerant.
- the compressor 3 for example, a positive displacement compressor in which the number of revolutions is controlled by an inverter circuit and the capacity is controlled may be used.
- the positive displacement compressor include a rotary compressor, a scroll compressor, a screw compressor, and a reciprocating compressor.
- the compressor 3 has an electric motor.
- the four-way valve 4 that is a refrigerant circuit switching device switches the refrigerant flow path in accordance with a cold supply mode (for example, cooling operation mode) and a warm supply mode (for example, heating operation mode).
- a cold supply mode for example, cooling operation mode
- a warm supply mode for example, heating operation mode
- the four-way valve 4 is described as an example of the refrigerant circuit switching device.
- the configuration is not limited to the four-way valve 4 as long as it can be configured by a device that can selectively switch the refrigerant flow path.
- the refrigerant circuit switching device can be configured by combining two two-way valves or three-way valves.
- the refrigeration cycle apparatus 100A of the present embodiment has the refrigerant circuit switching device. However, when the refrigerant flow path need not be switched, the refrigeration cycle apparatus 100A may not be provided with the refrigerant circuit switching device. .
- the outdoor heat exchanger 5 that is the first heat exchanger functions as a condenser or an evaporator.
- the outdoor heat exchanger 5 can be composed of, for example, a cross fin type fin-and-tube heat exchanger having a heat transfer tube and a large number of fins.
- the outdoor heat exchanger 5 is demonstrated as what heat-exchanges the refrigerant
- the outdoor heat exchanger 5 may not be a fin-and-tube heat exchanger depending on the heat medium to be heat-exchanged.
- a microchannel heat exchanger for example, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double tube heat exchanger, a plate heat exchanger, or the like may be used.
- the 1st heat exchanger is the outdoor heat exchanger 5 which exists in the outdoor
- the installation position of a 1st heat exchanger is not limited to outdoor.
- the first heat exchanger may be a heat exchanger on the heat source side.
- the outdoor blower 5a supplies air to the outdoor heat exchanger 5.
- the outdoor blower 5a can change the flow rate of the air supplied to the outdoor heat exchanger 5.
- a centrifugal fan driven by a motor such as a DC fan motor, a multiblade fan, or the like can be used.
- the outdoor heat exchanger 5 performs heat exchange between the refrigerant and a heat medium other than air
- the heat medium is supplied to the outdoor heat exchanger 5 by a transfer device such as a pump instead of the outdoor fan 5a. It may be.
- the electronic expansion valve 6 that is a flow rate adjusting device is a device that adjusts the throttle opening based on an instruction from the control device 20 to adjust the refrigerant flow rate, depressurize the refrigerant, and the like.
- the electronic expansion valve 6 having a structure capable of adjusting the throttle opening is described as an example, but the present invention is not limited to this.
- a mechanical expansion valve using a diaphragm for the pressure receiving portion, a capillary tube, or the like may be used as the flow rate adjusting device.
- the indoor heat exchanger 8 functions as an evaporator or a condenser.
- the indoor heat exchanger 8 can be constituted by, for example, a cross fin type fin-and-tube heat exchanger having a heat transfer tube and a large number of fins.
- the indoor heat exchanger 8 is demonstrated as what heat-exchanges the refrigerant
- the indoor heat exchanger 8 may not be a fin-and-tube heat exchanger depending on the heat medium to be heat-exchanged.
- a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double tube heat exchanger, a plate heat exchanger, or the like may be used.
- the installation position of a 2nd heat exchanger is not limited indoors.
- the 2nd heat exchanger should just be a heat exchanger in use side, such as a space for air conditioning.
- the indoor blower 8a supplies air to the indoor heat exchanger 8.
- the indoor blower 8a can change the flow rate of the air supplied to the indoor heat exchanger 8.
- a centrifugal fan or a multiblade fan driven by a motor such as a DC fan motor can be used as the indoor blower 8a.
- the heat medium may be supplied to the indoor heat exchanger 8 by a transfer device such as a pump instead of the indoor fan 8a.
- the refrigeration cycle apparatus 100A includes a control device 20 that performs overall control of the operation of the refrigeration cycle apparatus 100A and the like with a focus on equipment included in the outdoor unit 1.
- the control device 20 includes various actuators (compressor 3, four-way valve) of the refrigeration cycle apparatus 100A based on values (detection values) related to detection by various detectors (sensors) (not shown) attached to the refrigerant circuit or the like. 4.
- the control device 20 is composed of, for example, a microcomputer, a digital signal processor, and the like. For example, it has a control processing unit such as a CPU (Central Processing Unit).
- CPU Central Processing Unit
- control device 20 has a memory
- the control device 20 is installed in the outdoor unit 1, but the installation location is not limited as long as the device can be controlled.
- the inside of the four-way valve 4 is a flow path indicated by a solid line.
- the heat supply mode for example, heating operation
- the four-way valve 4 has a flow path indicated by a dotted line. Accordingly, in the cold supply mode, the refrigerant circulates in the order of the compressor 3, the four-way valve 4, the outdoor heat exchanger 5, the electronic expansion valve 6, the indoor heat exchanger 8, and the compressor 3. Further, in the heat supply mode, the refrigerant circulates in the order of the compressor 3, the four-way valve 4, the indoor heat exchanger 8, the electronic expansion valve 6, the outdoor heat exchanger 5, and the compressor 3.
- the outdoor heat exchanger 5 functions as a condenser
- the indoor heat exchanger 8 functions as an evaporator.
- the outdoor heat exchanger 5 functions as an evaporator
- the indoor heat exchanger 8 functions as a condenser.
- refrigerant used for the refrigeration cycle apparatus 100A in the present embodiment will be described.
- refrigerants used in the refrigeration cycle apparatus 100A 1,2 trifluoroethylene (HFO-1123) having low GWP and high operating pressure among HFO refrigerants, and low GWP and operating pressure among HFC refrigerants.
- R32 CH 2 F 2 ; difluoromethane is used.
- HFO-1123 When HFO-1123 is used as a refrigerant in a refrigeration cycle apparatus, HFO-1123 tends to undergo a self-decomposition reaction under high temperature and high pressure conditions. Therefore, in the present embodiment, by circulating a mixed refrigerant in which HFO-1123 and R32 are mixed, the stability of HFO-1123 is increased and self-decomposition can be suppressed.
- FIG. 2 is a diagram showing the relationship between the mixed refrigerant of R32 and HFO-1123, temperature, and pressure according to Embodiment 1 of the present invention.
- FIG. 2 it can be seen that the temperature and pressure at which HFO-1123 undergoes self-decomposition differs in the refrigerant circuit depending on the mixing ratio of R32 and HFO-1123. From this, the performance of the refrigeration cycle apparatus 100A is obtained by mixing R32 and HFO-1123 so that the HFO-1123 does not self-decompose at a temperature and pressure that are equal to or higher than the compressor operating point of the refrigeration cycle apparatus 100A. You can drive without sacrificing.
- FIG. 2 it can be seen that the temperature and pressure at which HFO-1123 undergoes self-decomposition differs in the refrigerant circuit depending on the mixing ratio of R32 and HFO-1123. From this, the performance of the refrigeration cycle apparatus 100A is obtained by mixing R32 and HFO-1123 so that the HFO-1123 does not self-decompose at
- FIG. 3 is a diagram showing the relationship between the mixing ratio of HFO-1234yf and the GWP in the mixed refrigerant according to Embodiment 1 of the present invention. As shown in FIG. 3, by adding HFO-1234yf, which is a low GWP refrigerant, to R32 and HFO-1123, the GWP can be lowered without causing HFO-1123 to self-decompose.
- HFO-1234yf which is a low GWP refrigerant
- FIG. 4 is a diagram showing the relationship between the mixing ratio of HFO-1234yf in the mixed refrigerant according to Embodiment 1 of the present invention and the performance of the refrigeration cycle in the refrigeration cycle apparatus 100A.
- HFO-1234yf is a low-pressure refrigerant.
- the mixing ratio of R32, HFO-1234yf and HFO1234yf is preferably R32> HFO-1123> HFO-1234yf in mass%.
- FIG. FIG. 5 is a schematic configuration diagram showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100B) according to Embodiment 2 of the present invention.
- refrigeration cycle apparatus 100B of the second embodiment devices that perform the same operation as the refrigeration cycle apparatus 100A described in the first embodiment are denoted by the same reference numerals.
- the basic configuration of the refrigeration cycle apparatus 100B is the same as that of the refrigeration cycle apparatus 100A according to Embodiment 1.
- the gas-liquid separator 10 is provided on the downstream side of the electronic expansion valve 6 with respect to the refrigerant flow in the cold supply mode in which the outdoor heat exchanger 5 functions as a condenser. Yes.
- the gas-liquid separator 10 is connected to a pipe for flowing the refrigerant to the indoor heat exchanger 8 and a pipe (bypass pipe) for bypassing the indoor heat exchanger 8 and flowing the refrigerant to the compressor 3.
- a liquid-phase refrigerant (liquid refrigerant) mainly flows through the piping flowing through the indoor heat exchanger 8.
- a gas phase refrigerant (gas refrigerant) mainly flows through the bypass pipe.
- the bypass pipe has a bypass electronic expansion valve 11 serving as a bypass flow rate adjusting device.
- the refrigerant used for refrigeration cycle apparatus 100B is the same mixed refrigerant as the refrigerant used in refrigeration cycle apparatus 100A according to Embodiment 1.
- the gas-liquid separator 10 shown in FIG. 5 is a device that separates a gas refrigerant and a liquid refrigerant. This is particularly effective during cooling operation.
- the liquid refrigerant flows to the indoor heat exchanger 8, and the gas refrigerant bypasses the indoor heat exchanger 8 and flows to the compressor 3.
- the refrigerant pressure loss in the indoor heat exchanger 8 can be reduced. For this reason, the performance of the refrigeration cycle apparatus 100B can be improved.
- the bypass electronic expansion valve 11 can adjust the amount of gas refrigerant that bypasses the indoor heat exchanger 8. It is a device that adjusts the throttle opening based on an instruction from the control device 20, adjusts the refrigerant flow rate, depressurizes the refrigerant, and the like.
- the bypass electronic expansion valve 11 having a structure capable of adjusting the throttle opening is described as an example, but the present invention is not limited to this.
- a mechanical expansion valve, a capillary tube, or the like that employs a diaphragm for the pressure receiving unit may be used as the bypass flow rate adjusting device.
- FIG. 6 is a diagram showing the relationship between the mixing ratio of HFO-1234yf in the refrigerant mixture according to Embodiment 2 of the present invention and the performance of the refrigeration cycle in the refrigeration cycle apparatus 100B.
- the HFO-1123 is self-decomposed while maintaining the performance of the refrigeration cycle. Since the mixing ratio of HFO-1234yf that does not cause the increase can be increased, the GWP of the refrigerant can be lowered.
- FIG. 7 is a schematic configuration diagram showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100C) according to Embodiment 3 of the present invention.
- refrigeration cycle apparatus 100C according to the third embodiment, devices that perform the same operations as those of the refrigeration cycle apparatus 100A or the refrigeration cycle apparatus 100B described in the first embodiment or the second embodiment are denoted by the same reference numerals.
- the basic configuration of the refrigeration cycle apparatus 100C is the same as that of the refrigeration cycle apparatus 100A or the refrigeration cycle apparatus 100B according to the first embodiment or the second embodiment.
- the refrigeration cycle apparatus 100B of the second embodiment includes the gas-liquid separator 10 on the downstream side of the refrigerant of the electronic expansion valve 6 in the cold supply mode.
- the rectifier circuit is provided so that the gas-liquid separator 10 is located on the downstream side of the refrigerant of the electronic expansion valve 6 even in the warm heat supply mode in which the indoor heat exchanger 8 functions as a condenser.
- the refrigerant used for refrigeration cycle apparatus 100C is the same mixed refrigerant as the refrigerant used in refrigeration cycle apparatus 100A and refrigeration cycle apparatus 100B according to Embodiment 1 and Embodiment 2.
- FIG. 8 is an enlarged configuration diagram of the rectifier circuit portion in the refrigeration cycle apparatus 100C according to Embodiment 3 of the present invention.
- the check valves 12A to 12D are valves that make the flow of refrigerant in one direction.
- the check valve 12A to the check valve 12D constitute a rectifier.
- the refrigerant flow in the rectifier circuit will be described.
- the refrigerant flowing out of the outdoor heat exchanger 5 flows into the rectifier circuit from the point a, passes through the check valve 12A, and flows into the electronic expansion valve 6 from the point b.
- the refrigerant that has passed through the electronic expansion valve 6 flows into the gas-liquid separator 10.
- the liquid refrigerant flowing out of the gas-liquid separator 10 passes through the point c and the check valve 12D.
- the refrigerant flowing out from the check valve 12D passes through the point d and flows out to the indoor heat exchanger 8.
- the gas refrigerant flowing out from the gas-liquid separator 10 passes through the point e and flows out to the bypass pipe.
- the refrigerant flowing out of the indoor heat exchanger 8 flows into the rectifier circuit from the point d, passes through the check valve 12C, and flows into the electronic expansion valve 6 from the point b.
- the refrigerant that has passed through the electronic expansion valve 6 flows into the gas-liquid separator 10.
- the liquid refrigerant flowing out from the gas-liquid separator 10 passes through the point c and the check valve 12B.
- the refrigerant flowing out from the check valve 12B passes through the point a and flows out to the outdoor heat exchanger 5.
- the gas refrigerant flowing out from the gas-liquid separator 10 passes through the point e and flows out to the bypass pipe.
- the refrigeration cycle apparatus 100C switches the circulation path and cools the load in the cold supply mode using the indoor heat exchanger 8 as an evaporator and the room heat for heating the load.
- the gas-liquid separator 10 can be made to function in either operation state of the heat supply mode in which the exchanger 8 is a condenser. For this reason, the performance of the refrigeration cycle apparatus 100C can be improved.
- FIG. 9 is a diagram showing the relationship between the mixing ratio of HFO-1234yf in the mixed refrigerant according to Embodiment 3 of the present invention and the performance of the refrigeration cycle in the refrigeration cycle apparatus 100C.
- the gas-liquid separator 10 can be operated regardless of the mode, while maintaining the performance of the refrigeration cycle. Since the mixing ratio of HFO-1234yf in which HFO-1123 does not cause self-decomposition can be increased, the GWP of the refrigerant can be lowered.
- FIG. 10 is a schematic configuration diagram showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100D) according to Embodiment 4 of the present invention.
- refrigeration cycle apparatus 100D equipment that performs the same operation as the refrigeration cycle apparatus 100A, the refrigeration cycle apparatus 100B, or the refrigeration cycle apparatus 100C described in the first, second, or third embodiment. are given the same reference numerals.
- the basic configuration of the refrigeration cycle apparatus 100D is the same as that of the refrigeration cycle apparatus 100A, the refrigeration cycle apparatus 100B, or the refrigeration cycle apparatus 100C according to the first embodiment, the second embodiment, or the third embodiment.
- the refrigeration cycle apparatus 100 ⁇ / b> D of Embodiment 4 includes an internal heat exchanger (inter-refrigerant heat exchanger) 13.
- a pipe through which the refrigerant flowing into the electronic expansion valve 6 passes and a bypass pipe are connected to the internal heat exchanger 13.
- the refrigerant used for refrigeration cycle apparatus 100D is the same as the refrigerant used in refrigeration cycle apparatus 100A, refrigeration cycle apparatus 100B, and refrigeration cycle apparatus 100C according to Embodiment 1, Embodiment 2, and Embodiment 3. It is a mixed refrigerant.
- the internal heat exchanger 13 exchanges heat between the refrigerant before flowing into the electronic expansion valve 6 and the refrigerant flowing out of the gas-liquid separator 10 and passing through the bypass pipe.
- the refrigerant before flowing into the electronic expansion valve 6 is hotter than the refrigerant passing through the bypass pipe.
- the internal heat exchanger 13 performs heat exchange, the refrigerant before flowing into the electronic expansion valve 6 can be supercooled. By supercooling the refrigerant, the performance of the refrigeration cycle apparatus 100D can be improved.
- the internal heat exchanger 13 performs heat exchange, whereby the refrigerant passing through the bypass pipe can be heated and the degree of superheat can be ensured.
- the degree of superheat of the refrigerant By ensuring the degree of superheat of the refrigerant, the risk of liquid refrigerant flowing into the compressor 3 can be reduced. For this reason, the reliability of refrigeration cycle apparatus 100D can be improved.
- the liquid compression which arises when a liquid refrigerant flows in into the compressor 3 can be prevented, and the performance of refrigeration cycle apparatus 100D can be maintained.
- FIG. 11 is a diagram showing the relationship between the mixing ratio of HFO-1234yf in the mixed refrigerant according to Embodiment 4 of the present invention and the performance of the refrigeration cycle in the refrigeration cycle apparatus 100D.
- the internal heat exchanger 13 is provided, and the refrigerant before flowing into the electronic expansion valve 6 is supercooled. Therefore, the performance of the refrigeration cycle apparatus 100D can be improved.
- coolant which passes bypass piping is ensured, the reliability of refrigeration cycle apparatus 100D can be improved.
- liquid compression can be prevented and the performance of refrigeration cycle apparatus 100D can be improved.
- the mixing ratio of HFO-1234yf in which HFO-1123 does not cause self-decomposition can be increased while maintaining the performance of the refrigeration cycle, the GWP of the refrigerant can be lowered.
- FIG. FIG. 12 is a diagram showing a heat transfer tube 30 of the heat exchanger according to Embodiment 5 of the present invention.
- the heat transfer tube 30 used for at least one of the outdoor heat exchanger 5 and the indoor heat exchanger 8 is A circular heat transfer tube.
- the diameter r of the heat exchanger tube 30 shall be 7.0 mm or less.
- each refrigerant is slightly flammable. Is preferably smaller.
- the outdoor heat exchanger 5 Even if the diameter r of the heat transfer tube 30 is 7.0 mm or less, it is difficult to be affected by the pressure loss of the refrigerant piping. Further, the amount of refrigerant can be reduced, and a high-performance refrigeration cycle apparatus can be obtained.
- an inner surface groove can be formed on the inner surface side of the heat transfer tube 30 used for at least one of the outdoor heat exchanger 5 and the indoor heat exchanger 8.
- the inner surface groove By forming the inner surface groove, the surface area inside the heat transfer tube 30 can be increased, and the flow of the refrigerant can be turbulent, so that the heat transfer performance of the heat transfer tube 30 can be improved.
- FIG. 13 is a diagram showing a heat transfer tube 31 of a heat exchanger according to Embodiment 6 of the present invention.
- a heat transfer tube 31 used for at least one of the outdoor heat exchanger 5 and the indoor heat exchanger 8 is provided.
- a flat tube (flat tube) is used.
- the refrigeration cycle apparatus described in each embodiment constitutes a refrigerant circuit that uses the refrigeration cycle, such as an air conditioner (for example, a refrigeration apparatus, a room air conditioner, a packaged air conditioner, a multi air conditioner for buildings, etc.), a heat pump water heater, and the like. It can be applied to a device that performs.
- an air conditioner for example, a refrigeration apparatus, a room air conditioner, a packaged air conditioner, a multi air conditioner for buildings, etc.
- a heat pump water heater and the like. It can be applied to a device that performs.
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Abstract
Description
図1は、本発明の実施の形態1に係る冷凍サイクル装置(以下、冷凍サイクル装置100Aと称する)の冷媒回路構成の一例を示す概略構成図である。図1に基づいて、冷凍サイクル装置100Aについて説明する。
HFO-1123を冷媒として冷凍サイクル装置に使用する際、HFO-1123は、高温、高圧の条件では自己分解反応が起こりやすい。そのため、本実施の形態では、HFO-1123とR32とを混合した混合冷媒を循環させることで、HFO-1123の安定性が高まり、自己分解を抑制することができる。
図5は、本発明の実施の形態2に係る冷凍サイクル装置(以下、冷凍サイクル装置100Bと称する)の冷媒回路構成の一例を示す概略構成図である。実施の形態2の冷凍サイクル装置100Bにおいて、実施の形態1で説明した冷凍サイクル装置100Aと同様の動作を行う機器などについては同一符号を付している。
図6は、本発明の実施の形態2に係る混合冷媒におけるHFO-1234yfの混合比率と冷凍サイクル装置100Bにおける冷凍サイクルの性能との関係を示す図である。図6に示すように、本発明の実施の形態2に係る冷凍サイクル装置100Bによれば、気液分離器10を作動させることによって、冷凍サイクルの性能を維持しつつ、HFO-1123が自己分解を起こさないHFO-1234yfの混合比率を増加させることができるので、冷媒のGWPを低くすることができる。
図7は、本発明の実施の形態3に係る冷凍サイクル装置(以下、冷凍サイクル装置100Cと称する)の冷媒回路構成の一例を示す概略構成図である。実施の形態3の冷凍サイクル装置100Cにおいて、実施の形態1または実施の形態2で説明した冷凍サイクル装置100Aまたは冷凍サイクル装置100Bと同様の動作を行う機器などについては同一符号を付している。
図9は、本発明の実施の形態3に係る混合冷媒におけるHFO-1234yfの混合比率と冷凍サイクル装置100Cにおける冷凍サイクルの性能との関係を示す図である。図9に示すように、本発明の実施の形態3に係る冷凍サイクル装置100Cによれば、モードに関係なく気液分離器10を作動させることができることで、冷凍サイクルの性能を維持しつつ、HFO-1123が自己分解を起こさないHFO-1234yfの混合比率を増加させることができるので、冷媒のGWPを低くすることができる。
図10は、本発明の実施の形態4に係る冷凍サイクル装置(以下、冷凍サイクル装置100Dと称する)の冷媒回路構成の一例を示す概略構成図である。実施の形態4の冷凍サイクル装置100Dにおいて、実施の形態1、実施の形態2または実施の形態3で説明した冷凍サイクル装置100A、冷凍サイクル装置100Bまたは冷凍サイクル装置100Cと同様の動作を行う機器などについては同一符号を付している。
図11は、本発明の実施の形態4に係る混合冷媒におけるHFO-1234yfの混合比率と冷凍サイクル装置100Dにおける冷凍サイクルの性能との関係を示す図である。図11に示すように、本発明の実施の形態4に係る冷凍サイクル装置100Dによれば、内部熱交換器13を有し、電子膨張弁6に流入する前の冷媒を過冷却するようにしたので、冷凍サイクル装置100Dの性能を向上させることができる。また、バイパス配管を通過する冷媒の過熱度を確保するようにしたので、冷凍サイクル装置100Dの信頼性を高めることができる。また、液圧縮を防ぎ、冷凍サイクル装置100Dの性能を向上させることができる。以上より、冷凍サイクルの性能を維持しつつ、HFO-1123が自己分解を起こさないHFO-1234yfの混合比率を増加させることができるので、冷媒のGWPを低くすることができる。
図12は、本発明の実施の形態5に係る熱交換器の伝熱管30を示す図である。上述した実施の形態1~実施の形態4における冷凍サイクル装置100A~冷凍サイクル装置100Dに関し、図12に示すように、室外熱交換器5および室内熱交換器8の少なくとも一方に用いる伝熱管30は、円形状の伝熱管とする。そして、伝熱管30の径rを7.0mm以下とする。
図13は、本発明の実施の形態6に係る熱交換器の伝熱管31を示す図である。上述した実施の形態1~実施の形態4における冷凍サイクル装置100A~冷凍サイクル装置100Dに関し、図13に示すように、室外熱交換器5および室内熱交換器8の少なくとも一方に用いる伝熱管31を扁平形状の管(扁平管)とする。伝熱管31を扁平形状にすることで、配管容積を減らすことができ、冷媒の量を削減し、高性能な冷凍サイクル装置を得ることができる。
Claims (11)
- 吸入した冷媒を圧縮して吐出する圧縮機と、
前記冷媒に放熱させて前記冷媒を凝縮させる凝縮器と、
凝縮された前記冷媒を減圧させる減圧装置と、
前記冷媒に吸熱させて前記冷媒を蒸発させる蒸発器と
を配管接続して冷媒回路を構成し、
前記冷媒は、R32とHFO-1123とを混合した混合冷媒であり、該混合冷媒は、R32の質量パーセント>HFO-1123の質量パーセントである冷凍サイクル装置。 - 前記混合冷媒は、前記R32の質量パーセント:前記HFO-1123の質量パーセント=60:40である請求項1に記載の冷凍サイクル装置。
- さらにHFO-1234yfを混合した前記混合冷媒とする請求項1または請求項2に記載の冷凍サイクル装置。
- 前記混合冷媒において、R32の質量パーセント>HFO-1123の質量パーセント>HFO-1234yfの質量パーセントである請求項3に記載の冷凍サイクル装置。
- 前記R32の質量パーセント:前記HFO-1123の質量パーセント=60:40であり、さらに、前記HFO-1234yfの質量パーセントの比率が前記混合冷媒全体の26パーセント以上である請求項3に記載の冷凍サイクル装置。
- 前記減圧装置と前記蒸発器との間に設置され、気体状の冷媒と液体状の冷媒とを分離する気液分離器と、
該気液分離器と前記圧縮機の吸入側とを配管接続するバイパス配管と、
該バイパス配管を通過する冷媒量を調整する冷媒調整装置と
をさらに備える請求項1~請求項5のいずれか一項に記載の冷凍サイクル装置。 - 前記冷媒の循環経路を切り替える流路切替装置と、
前記冷媒の循環経路が前記減圧装置、前記気液分離器および前記蒸発器の順となるように調整する整流装置と
をさらに備える請求項6に記載の冷凍サイクル装置。 - 前記凝縮器から前記減圧装置に向けて流れる前記冷媒と前記バイパス配管を通過する前記冷媒とを熱交換する内部熱交換器をさらに備える請求項7に記載の冷凍サイクル装置。
- 前記R32の質量パーセント:前記HFO-1123の質量パーセント=60:40であり、前記冷媒の質量パーセント比を、R32>HFO-1123≧HFO-1234yfとする請求項6~請求項8のいずれか一項に記載の冷凍サイクル装置。
- 前記凝縮器および前記蒸発器の少なくとも一方は、円管状の伝熱管を有する熱交換器であり、前記伝熱管の径が7.0mmより小さい径である請求項1~請求項9のいずれか一項に記載の冷凍サイクル装置。
- 前記凝縮器および前記蒸発器の少なくとも一方は、扁平形状の伝熱管を有する熱交換器である請求項1~請求項9のいずれか一項に記載の冷凍サイクル装置。
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