WO2015140873A1 - 冷凍装置、及び、冷凍装置の制御方法 - Google Patents
冷凍装置、及び、冷凍装置の制御方法 Download PDFInfo
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- WO2015140873A1 WO2015140873A1 PCT/JP2014/057031 JP2014057031W WO2015140873A1 WO 2015140873 A1 WO2015140873 A1 WO 2015140873A1 JP 2014057031 W JP2014057031 W JP 2014057031W WO 2015140873 A1 WO2015140873 A1 WO 2015140873A1
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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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
- 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
- F25B49/022—Compressor 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
- 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
- F25B2400/16—Receivers
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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
- F25B2700/19—Pressures
- F25B2700/195—Pressures of 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction 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
- 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
Definitions
- the present invention relates to a refrigeration apparatus having a multi-component refrigeration cycle and a control method for a refrigeration apparatus having a multi-component refrigeration cycle.
- a low-source side compressor, a low-source side condenser, a low-source-side decompressor, and a low-source-side evaporator, and a low-source-side refrigeration cycle for circulating the low-source-side refrigerant A high-side refrigeration cycle that has a main-side compressor, a high-side condenser, a high-side decompressor, and a high-side evaporator and circulates the high-side refrigerant, and a low-side condenser low Some of them include a cascade capacitor that exchanges heat between the side refrigerant and the high-side refrigerant of the high-side evaporator, and a control device. In such a refrigeration apparatus, a CO 2 refrigerant is used as the low-source refrigerant (see Patent Document 1).
- the pressure range of the low-source side refrigeration cycle may be controlled to 7.4 MPa or less, which is the critical pressure of the CO 2 refrigerant.
- HFO-1123 refrigerant (1,1,2 trifluoroethylene refrigerant), which can lower the pressure range as compared with CO 2 refrigerant, is used as the low-source refrigerant.
- the safety performance of the refrigeration apparatus can be improved, and the pressure resistance performance of each device constituting the low-source side refrigeration cycle can be reduced to reduce the cost of the refrigeration apparatus.
- the COP (coefficient of performance) in the theoretical cycle is 5.70 for CO 2 refrigerant and HFC (hydrofluorocarbon) -32 refrigerant when the evaporation temperature is 10 ° C., the condensation temperature is 45 ° C., the degree of supercooling is 0K, and the degree of superheat is 0K.
- HFC-410A refrigerant 2.13 for HFC-410A refrigerant and 1.99 for HFC-410A refrigerant (quoted from “Advanced Refrigeration Examination Text by SI” (7th revised edition, published by the Japan Society of Refrigerating and Air Conditioning Engineers)). That is, when the low-side refrigerant is a CO 2 refrigerant, the COP (coefficient of performance) in the theoretical cycle may be inferior compared to the case where the low-side refrigerant is an HFC refrigerant.
- the refrigeration apparatus may be reduced to global warming. In some cases, the influence can be reduced.
- GWP global warming potential
- the HFO-1123 refrigerant or the like is a refrigerant that causes a disproportionation reaction, and a technology for operating a refrigeration apparatus using such a refrigerant as a low-side refrigerant has not yet been established.
- a refrigerant as a refrigerant for example, improving the safety performance of the refrigeration apparatus, reducing the cost of the refrigeration apparatus, improving the operating efficiency of the refrigeration apparatus, the impact of the refrigeration apparatus on global warming There has been a problem that the feasibility is low, such as reducing the above.
- the present invention has been made against the background of the above problems, and established a technique for operating a refrigeration apparatus using a refrigerant that causes a disproportionation reaction in a low-source side refrigerant.
- the purpose is to obtain a refrigeration apparatus with improved feasibility, such as improvement, cost reduction, operation efficiency improvement, and reduction of impact on global warming. Moreover, it aims at obtaining the control method of such a freezing apparatus.
- the refrigeration apparatus includes a low-source side compressor, a low-side condenser, a low-side decompression device, and a low-side evaporator, and a low-side refrigeration cycle for circulating the low-side refrigerant.
- a high-end side compressor, a high-end side condenser, a high-end side decompressor, and a high-end side evaporator, and a high-end side refrigeration cycle for circulating the high-end side refrigerant, and the low-end side condenser A cascade condenser that exchanges heat between the low-side refrigerant of the high-side evaporator and the high-side refrigerant of the high-side evaporator, and a control device, and the low-side refrigerant causes a disproportionation reaction It is a refrigerant
- the pressure of the low-side refrigerant is maintained at a lower pressure than the pressure at which the low-side refrigerant causes a disproportionation reaction. Therefore, it is possible to operate the refrigeration apparatus as in the case where the low-side refrigerant is a refrigerant that causes a disproportionation reaction even though the low-side refrigerant is a refrigerant that causes a disproportionation reaction. For example, improving the safety performance of the refrigeration device, reducing the cost of the refrigeration device, improving the energy saving performance of the refrigeration device, reducing the impact of the refrigeration device on global warming, etc. Feasibility is improved.
- FIG. 6 is a diagram for explaining the characteristics of the refrigeration apparatus according to Embodiment 1 when the low-source side refrigerant is an HFO-1123 refrigerant.
- FIG. 5 is a diagram for explaining characteristics of the refrigeration apparatus according to Embodiment 1 when the low-source side refrigerant is a mixed refrigerant of HFO-1123 refrigerant and HFO-1234yf refrigerant. It is a figure for demonstrating the structure of the freezing apparatus which concerns on Embodiment 2.
- Embodiment 1 FIG. The refrigeration apparatus according to Embodiment 1 will be described. ⁇ Configuration of refrigeration equipment> The configuration of the refrigeration apparatus according to Embodiment 1 will be described below. 1 and 2 are diagrams for explaining the configuration of the refrigeration apparatus according to Embodiment 1.
- FIG. 1 and FIG. 2 the refrigeration apparatus 1 includes a binary refrigerant cycle of a low-source side refrigeration cycle 10 and a high-source side refrigeration cycle 30.
- the refrigeration apparatus 1 may include three or more refrigeration cycles.
- the low source side refrigeration cycle 10 includes a low source side compressor 11, a low source side condenser 12, a low source side expansion valve 13 that is a low source side decompression device, and a low source side evaporator 14. , Circulating the low-source refrigerant.
- the low-side condenser 12 and the low-side expansion valve 13 The low-source side liquid receiver 15 may be disposed in a pipe that communicates between the two.
- the low-side expansion valve 13 may be another decompression device such as a capillary tube.
- the low source side evaporator 14 is used as a cold heat source.
- the low-source-side refrigerant is a refrigerant that causes a disproportionation reaction, such as HFO-1123 refrigerant.
- the high-side refrigeration cycle 30 includes a high-side compressor 31, a high-side condenser 32, a high-side expansion valve 33 that is a high-side decompression device, and a high-side evaporator 34. , Circulate the high-side refrigerant.
- the high-end compressor 31 is a variable capacity type.
- the high-side expansion valve 33 may be another decompression device such as a capillary tube.
- the low-side condenser 12 and the high-side evaporator 34 are built in the cascade condenser 40.
- the cascade condenser 40 the low source side refrigerant of the low source side condenser 12 and the high source side refrigerant of the high source side evaporator 34 perform heat exchange.
- the high-source side refrigerant is an HFC refrigerant having a high GWP (global warming potential).
- GWP global warming potential
- a structure in which the high-side refrigerant is difficult to leak such as the high-side evaporator 34 built in the cascade condenser 40, is adopted. , Environmental impact is small.
- the HFC refrigerant has a higher COP (coefficient of performance) than other refrigerants, the operation efficiency of the high-side refrigeration cycle 30 is improved.
- the high-side refrigerant another refrigerant having a higher GWP (global warming potential) than the HFC refrigerant, for example, HFO-1234yf refrigerant (2,3,3,3-tetrafluoropropene refrigerant), HC A system refrigerant, a CO 2 refrigerant, water, or the like may be used. That is, the high-source-side refrigerant is a refrigerant that increases the operating efficiency of the refrigeration cycle as compared with the case where the low-source-side refrigerant is used in the same refrigeration cycle.
- GWP global warming potential
- the high-source side refrigerant has a high critical point, such as an HFC-based refrigerant
- a high-source side liquid receiver is disposed on the high-pressure side of the high-source side refrigeration cycle 30, and surplus The refrigerant may be processed.
- the high-side refrigerant has a low critical point, such as a CO 2 refrigerant
- a high-side accumulator is disposed on the low-pressure side of the high-side refrigeration cycle 30; Excess refrigerant may be processed.
- the low-source-side refrigeration cycle 10 detects a low-source-side high-pressure sensor 21 that is a low-source-side high-pressure detector that detects the high-pressure of the low-source-side refrigeration cycle 10, and detects the low-pressure of the low-source-side refrigeration cycle
- the low-source-side low-pressure pressure sensor 22 is a low-source-side low-pressure pressure sensor 22
- the low-source-side discharge temperature detector is a low-source-side discharge temperature detector that detects the temperature of the low-source-side refrigerant discharged from the low-source compressor 11.
- a former-side discharge temperature sensor 23 is disposed in a pipe that communicates between the low-source side condenser 12 and the low-source side expansion valve 13.
- the low-source side low-pressure sensor 22 is disposed in a pipe that communicates between the low-side evaporator 14 and the low-side compressor 11.
- the low-source side discharge temperature sensor 23 is disposed in a pipe that communicates between the low-side compressor 11 and the low-side condenser 12.
- movement mentioned later does not need to be arrange
- the low original side high pressure sensor 21 and the low original side low pressure sensor 22 may detect the pressure of the low original refrigerant itself, or may detect other physical quantities that can be converted into the low original refrigerant pressure.
- the “low source side high pressure detection means” and “low source side low pressure detection means” in the present invention may be any means that substantially detects pressure.
- the low-source-side discharge temperature sensor 23 may detect the discharge temperature of the low-source-side refrigerant itself, or may detect other physical quantities that can be converted into the discharge temperature of the low-source-side refrigerant.
- the detection signal of the low source side high pressure sensor 21, the detection signal of the low source side low pressure sensor 22, and the detection signal of the low source side discharge temperature sensor 23 are input to the control device 50.
- the control device 50 governs the overall operation of the refrigeration apparatus 1. All or each part constituting the control device 50 may be constituted by, for example, a microcomputer, a microprocessor unit, etc., or may be constituted by a firmware or the like that can be updated, or by a command from the CPU or the like. It may be a program module to be executed.
- the high-side refrigerant compressed and discharged by the high-side compressor 31 is radiated and condensed by the high-side condenser 32 that is an air heat exchanger,
- the pressure is reduced by the high-side expansion valve 33.
- the high-side refrigerant decompressed by the high-side expansion valve 33 evaporates in the high-side evaporator 34 in the cascade condenser 40 while exchanging heat with the refrigerant in the low-side condenser 12. Reflux to 31.
- FIG. 3 is a diagram for explaining the characteristics of the refrigeration apparatus according to Embodiment 1 when the low-source side refrigerant is an HFO-1123 refrigerant.
- the low-side refrigerant is an HFO-1123 refrigerant
- FIG. 3 when the pressure increases, a disproportionation reaction occurs in the low-side refrigerant.
- the pressure at which the disproportionation reaction occurs decreases as the temperature increases. That is, even when there is no pressure fluctuation, a disproportionation reaction occurs in the low-side refrigerant when the temperature increases.
- the temperature is about 120 ° C.
- a disproportionation reaction occurs in the low-side refrigerant when the pressure exceeds 0.7 MPa
- the pressure is 0.7 MPa
- the temperature is about 120 ° C.
- Exceeding this causes a disproportionation reaction in the low-side refrigerant.
- the low-source refrigerant is HFO-1123 refrigerant
- the chemical formula before and after the disproportionation reaction is (1) below.
- FIG. 4 is a diagram for explaining the characteristics of the refrigeration apparatus according to Embodiment 1 when the low-source-side refrigerant is a mixed refrigerant of HFO-1123 refrigerant and HFO-1234yf refrigerant.
- the pressure at which the disproportionation reaction occurs can be increased as shown in FIG.
- the temperature at which the disproportionation reaction occurs can be increased. That is, it is possible to make the disproportionation reaction less likely to occur as compared with the case where the low-source-side refrigerant is an HFO-1123 refrigerant.
- the pressure at which the disproportionation reaction occurs increases.
- the low-source side refrigerant is a mixed refrigerant of HFO-1123 refrigerant and HFC-32 refrigerant
- the low-source side refrigerant is a mixed refrigerant of HFO-1123 refrigerant and HFO-1234yf refrigerant
- the pressure at which the disproportionation reaction occurs can be further increased.
- the temperature at which the disproportionation reaction occurs can be further increased.
- the low-source side refrigerant is compared with the HFO-1123 refrigerant.
- a mixed refrigerant of HFO-1123 refrigerant and HFO-1234yf refrigerant having a high pressure causing disproportionation reaction may be used.
- the low-source side refrigerant is a mixed refrigerant of the HFO-1123 refrigerant and the HFC-32 refrigerant, which has a higher pressure causing a disproportionation reaction than the mixed refrigerant of the HFO-1123 refrigerant and the HFO-1234yf refrigerant. And even better. However, even when the low-source-side refrigerant is a mixed refrigerant thereof, a disproportionation reaction occurs when the high-pressure pressure in the low-source-side refrigeration cycle 10 increases.
- the high pressure of the low-source-side refrigeration cycle 10 is maintained at a lower pressure than the pressure at which the low-source-side refrigerant causes a disproportionation reaction.
- the control device 50 operates the operating pressure (low pressure) of the high-side refrigeration cycle 30 when the cooling load of the low-side refrigeration cycle 10 increases.
- the operation pressure (low-pressure pressure) of the high-source side refrigeration cycle 30 is controlled to increase.
- the difference between the high-pressure pressure of the low-source side refrigeration cycle 10 and the low-pressure pressure of the high-source side refrigeration cycle 30 increases. The high pressure of 10 drops.
- the operating pressure (low pressure) of the high-source side refrigeration cycle 30 As the operating pressure (low pressure) of the high-source side refrigeration cycle 30 is increased, the difference between the high-pressure pressure of the low-source side refrigeration cycle 10 and the low-pressure pressure of the high-source side refrigeration cycle 30 is reduced. 10 high pressure increases.
- the operation state (the number of revolutions, etc.) of the high-source side compressor 31 By controlling the operation state (the number of revolutions, etc.) of the high-source side compressor 31 in this way, the amount of heat released from the low-side refrigerant to the high-side refrigerant is increased or decreased. Even when the cooling load varies, the high pressure of the low-source-side refrigeration cycle 10 can be maintained below the pressure at which the low-source-side refrigerant causes a disproportionation reaction.
- the control device 50 sets the operating state (the rotational speed, etc.) of the high-side compressor 31 so that the high-pressure detected by the low-side high-pressure sensor 21 is less than the pressure at which the low-side refrigerant causes a disproportionation reaction. Control to be maintained. By controlling the operation state (the number of revolutions, etc.) of the high-source side compressor 31 in this way, the amount of heat released from the low-side refrigerant to the high-side refrigerant is increased or decreased. Even when the cooling load varies, the high pressure of the low-source-side refrigeration cycle 10 can be maintained below the pressure at which the low-source-side refrigerant causes a disproportionation reaction.
- the control device 50 sets the operation state (the rotation speed, etc.) of the high-side compressor 31 so that the discharge temperature detected by the low-side discharge temperature sensor 23 is lower than the temperature at which the low-side refrigerant causes a disproportionation reaction. You may control so that it may be maintained.
- the low-source-side refrigeration cycle 10 has a pressure relief device that is opened when the pressure or temperature rises to a reference value, and the low-source-side refrigerant is disproportionated by the pressure relief device. Maintained below the pressure causing the reaction.
- the low-side liquid receiver 15 is provided with a soluble plug 15a that is a pressure relief device
- the pressure or temperature of the low-side refrigerant rises to a reference value
- the control device 50 increases the high pressure detected by the low-source-side high-pressure sensor 21 to the reference value, or when the discharge temperature detected by the low-source-side discharge temperature sensor 23 increases to the reference value.
- the low-side compressor 11 may be stopped.
- the control device 50 is configured such that the operating state (the rotational speed or the like) of the high-side compressor 31 is such that the high-pressure detected by the low-side high-pressure sensor 21 is the pressure at which the low-side refrigerant causes a disproportionation reaction, Control is performed so as to obtain a geometric mean value of the low pressure detected by the low-source-side low pressure sensor 22.
- the high-pressure of the low-side refrigeration cycle 10 is low, and the pressure at which the low-side refrigerant causes a disproportionation reaction is low. Since it is an intermediate pressure between the low pressure of the original refrigeration cycle 10 and the high pressure of the low original refrigeration cycle 10 is maintained below the pressure at which the low original refrigerant causes a disproportionation reaction, It becomes possible to suppress the discharge temperature of the machine 11.
- the refrigeration apparatus 1 since the high pressure of the low-source side refrigeration cycle 10 is reduced and the compression ratio of the high-source compressor 31 is increased, the operation efficiency is improved and the refrigeration apparatus 1 is energy-saving.
- the high-side refrigerant is an HFC refrigerant or the like
- the refrigeration apparatus 1 is further energy-saving.
- the high-side refrigerant is the HFC-410A refrigerant. The operating efficiency of 1 is almost maximized.
- the pressure of the low-source-side refrigerant is maintained at a lower pressure than the pressure at which the low-source-side refrigerant causes a disproportionation reaction. Therefore, even though the low-side refrigerant is a refrigerant that causes a disproportionation reaction such as HFO-1123 refrigerant, the low-side refrigerant is not a refrigerant that causes a disproportionation reaction.
- the refrigeration apparatus 1 can be operated, for example, improving the safety performance of the refrigeration apparatus 1, reducing the cost of the refrigeration apparatus 1, improving the energy saving performance of the refrigeration apparatus 1, and the refrigeration apparatus 1. Feasibility is improved, such as reducing the impact on global warming.
- the HFO-1123 refrigerant, the mixed refrigerant of the HFO-1123 refrigerant and the HFC-32 refrigerant, the mixed refrigerant of the HFO-1123 refrigerant and the HFO-1234yf refrigerant, etc. are refrigerants that cause a disproportionation reaction
- the pressure range of the side refrigeration cycle 10 can be lowered as compared with the CO 2 refrigerant. Therefore, it becomes possible to operate the refrigerating apparatus 1 as if those refrigerants are not the refrigerant that causes the disproportionation reaction, and the safety performance of the refrigerating apparatus 1 is improved.
- the pressure resistance performance of each device constituting the low-source side refrigeration cycle 10 can be reduced, and the cost of the refrigeration apparatus 1 can be reduced.
- the HFO-1123 refrigerant, the mixed refrigerant of the HFO-1123 refrigerant and the HFC-32 refrigerant, the mixed refrigerant of the HFO-1123 refrigerant and the HFO-1234yf refrigerant, etc. are refrigerants that cause a disproportionation reaction, but the theoretical cycle.
- COP coefficient of performance
- the HFO-1123 refrigerant, the mixed refrigerant of the HFO-1123 refrigerant and the HFC-32 refrigerant, the mixed refrigerant of the HFO-1123 refrigerant and the HFO-1234yf refrigerant, etc. are refrigerants that cause a disproportionation reaction.
- the global warming potential) can be reduced or comparable to the CO 2 refrigerant. Therefore, it becomes possible for these refrigerants to operate the refrigeration apparatus 1 as if the low-side refrigerant is not a refrigerant that causes a disproportionation reaction. In some cases, the influence can be reduced.
- the low-source side refrigerant is a mixed refrigerant of HFO-1123 refrigerant and HFC-32 refrigerant or a mixed refrigerant of HFO-1123 refrigerant and HFO-1234yf refrigerant.
- the low-side refrigerant can increase the pressure causing the disproportionation reaction, and the low-side refrigerant is not the refrigerant causing the disproportionation reaction. As in the case, the certainty of operating the refrigeration apparatus 1 is improved.
- the refrigeration apparatus 1 may be a refrigeration apparatus or a refrigeration apparatus such as a showcase, a commercial refrigerator-freezer, or a vending machine that is required to be non-fluorocarbon or reduce the use of CFC refrigerant or save energy. Needless to say.
- FIG. 5 is a diagram for explaining the configuration of the refrigeration apparatus according to Embodiment 2. As shown in FIG.
- the low-source-side refrigeration cycle 10 includes a low-source-side liquid receiver 15 disposed in a pipe that communicates between the low-source-side condenser 12 and the low-source-side expansion valve 13, Communicating between the check valve 16 disposed in the pipe for communicating between the low-side compressor 11 and the low-side condenser 12, and between the low-side liquid receiver 15 and the low-side expansion valve 13. And an electromagnetic valve 17 that is an on-off valve disposed in the pipe to be operated.
- the high-source side refrigeration cycle 30 includes a cooling unit 35 that is a cooling means for cooling the low-source-side refrigerant.
- the cooling unit 35 is, for example, a pipe that communicates between the high-side expansion valve 33 and the high-side evaporator 34 in the high-side refrigeration cycle 30.
- the low-side refrigerant in the low-side liquid receiver 15 is cooled by arranging the pipe so as to pass through the low-side liquid receiver 15.
- the control device 50 circulates the low-source side refrigerant of the low-source side refrigeration cycle 10 and circulates the high-source side refrigerant of the high-source side refrigeration cycle 30 during the normal operation. And, for example, when the low-side compressor 11 is stopped in the case of intermittent operation of the low-side compressor 11 for temperature control or the like, the control device 50 includes the low-side compressor Before stopping 11, the electromagnetic valve 17 is closed and the low-side compressor 11 is operated for a predetermined time.
- the low-source-side refrigerant in the low-source-side refrigeration cycle 10 flows between the check valve 16 and the electromagnetic valve 17 of the low-source-side refrigeration cycle 10, particularly the low-source side receiver.
- the low-side compressor 11 is stopped in a state in which the high pressure is stored in the liquid container 15.
- the control device 50 operates the high-side compressor 31 while the low-side compressor 11 is stopped. Since the control device 50 operates in such a manner, the low-side refrigerant in the low-side condenser 12 is cooled by the high-side refrigerant in the high-side evaporator 34 in the cascade condenser 40. For example, even if the ambient temperature rises, the refrigerant density in the low-source-side refrigeration cycle 10 is kept high, and the pressure increase of the low-source-side refrigerant is suppressed.
- the inside of the low-source side liquid receiver 15 is cooled by the cooling unit 35. Since a large amount of the low-side refrigerant is stored in the low-side liquid receiver 15, the low-side refrigerant is efficiently cooled, and the pressure increase of the low-side refrigerant is further suppressed.
- FIG. 6 is a diagram for explaining the configuration of the refrigeration apparatus according to Embodiment 3. As shown in FIG.
- the low-source-side refrigeration cycle 10 includes a low-source-side liquid receiver 15 disposed in a pipe communicating between the low-source-side condenser 12 and the low-source-side expansion valve 13, Communicating between the check valve 16 disposed in the pipe for communicating between the low-side compressor 11 and the low-side condenser 12, and between the low-side liquid receiver 15 and the low-side expansion valve 13. And an electromagnetic valve 17 disposed in the piping to be made.
- the high-side refrigeration cycle 30 may or may not include the cooling unit 35.
- the low-source side liquid receiver 15 reverses all the low-side refrigerants as liquid refrigerants when the pressure in the low-side liquid receiver 15 is less than the pressure at which the low-side refrigerants cause a disproportionation reaction. It is a capacity that can be stored between the stop valve 16 and the electromagnetic valve 17.
- the maximum volume in the liquid state of the low-side refrigerant is determined from the total refrigerant amount of the low-side refrigerant sealed in the low-side refrigeration cycle 10 and the assumed maximum temperature of ambient air, Let the capacity
- the total capacity of the members that communicate between the check valve 16 and the electromagnetic valve 17 includes, for example, the capacity of the low-side condenser 15, the capacity of the low-side condenser 12, The capacity of the piping that communicates with the side condenser 12, the capacity of the piping that communicates between the low-side condenser 12 and the low-side receiver 15, the low-side receiver 15 and the solenoid valve 17, The capacity of piping that communicates between the two is added.
- the heat dissipation means of the low-side refrigeration cycle 10 disappears, but the low-side refrigerant is between the check valve 16 and the electromagnetic valve 17 of the low-side refrigeration cycle 10,
- the pressure of the low-source side refrigerant is kept low. Therefore, it is suppressed that the pressure of the low element side refrigerant
- the pressure of the low-source side refrigerant is suppressed from exceeding the pressure upper limit value, that is, the design pressure, the reliability of the refrigeration apparatus 1 is improved.
- the capacity that can be stored as a liquid refrigerant between the check valve 16 and the solenoid valve 17 is determined from the assumed maximum temperature of the ambient air. It is suppressed that the pressure of the former-side refrigerant rises due to a lack of the total capacity of members that communicate between the check valve 16 and the electromagnetic valve 17. Therefore, it is further suppressed that the pressure of the low element side refrigerant becomes higher than the pressure at which the low element side refrigerant causes the disproportionation reaction. Further, since the pressure of the low-source side refrigerant is further suppressed from exceeding the pressure upper limit value, that is, the design pressure, the reliability of the refrigeration apparatus 1 is further improved.
- the low-source-side refrigerant stored between the check valve 16 and the electromagnetic valve 17 of the low-source-side refrigeration cycle 10 is in a gas-liquid two-phase state that is close to the saturated liquid state, so the pressure of the low-source side refrigerant Can be determined from the temperature. Therefore, the pressure resistance performance between the check valve 16 and the solenoid valve 17 of the low-source side refrigeration cycle 10 can be determined using the pressure converted from the assumed maximum temperature of the ambient air.
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Abstract
Description
なお、以下で説明する構成、動作等は、一例にすぎず、本発明に係る冷凍装置は、そのような構成、動作等である場合に限定されない。また、各図において、細かい構造については、適宜図示を簡略化又は省略している。また、重複又は類似する説明については、適宜簡略化又は省略している。
実施の形態1に係る冷凍装置について説明する。
<冷凍装置の構成>
以下に、実施の形態1に係る冷凍装置の構成について説明する。
図1及び図2は、実施の形態1に係る冷凍装置の、構成を説明するための図である。
図1及び図2に示されるように、冷凍装置1は、低元側冷凍サイクル10と高元側冷凍サイクル30との、二元冷媒サイクルを備える。冷凍装置1が、3つ以上の冷凍サイクルを備えていてもよい。
以下に、実施の形態1に係る冷凍装置の動作について説明する。
低元側冷凍サイクル10において、低元側圧縮機11で圧縮されて吐出された低元側冷媒は、カスケードコンデンサ40内の低元側凝縮器12で冷却された後、低元側膨張弁13で減圧される。低元側膨張弁13で減圧された低元側冷媒は、低元側蒸発器14で蒸発し、吸入管を介して低元側圧縮機11へ還流する。
低元側冷媒が、HFO-1123冷媒である場合には、図3に示されるように、圧力が高くなると、低元側冷媒に不均化反応が生じる。不均化反応が生じる圧力は、温度が高くなる程低くなる。つまり、圧力の変動がない場合でも、温度が高くなると、低元側冷媒に不均化反応が生じる。例えば、温度が120℃程度である場合には、圧力が0.7MPaを超えると、低元側冷媒に不均化反応が生じ、圧力が0.7MPaである場合には、温度が120℃程度を越えると、低元側冷媒に不均化反応が生じる。低元側冷媒が、HFO-1123冷媒である場合の、不均化反応前後の化学式は、以下(1)である。
CF2 = CHF → 1/2CF4 + 3/2C + HF ・・・(1)
一方、低元側冷媒が、HFO-1123冷媒とHFO-1234yf冷媒との混合冷媒である場合には、図4に示されるように、不均化反応が生じる圧力を高くすることができる。また、不均化反応が生じる温度を高くすることができる。つまり、低元側冷媒が、HFO-1123冷媒である場合と比較して、不均化反応を生じにくくすることができる。そして、HFO-1123冷媒のモル比が低くなる、つまり、HFO-1234yf冷媒の混合比率が高くなる程、不均化反応が生じる圧力が高くなる。
以下に、その実現の具体例を説明する。
なお、各具体例の全て又一部が、組み合わされてもよい。
制御装置50は、高元側圧縮機31の運転状態(回転数等)を、低元側冷凍サイクル10の冷却負荷が増加する場合には、高元側冷凍サイクル30の動作圧力(低圧圧力)が低下するように制御し、低元側冷凍サイクル10の冷却負荷が減少する場合には、高元側冷凍サイクル30の動作圧力(低圧圧力)が上昇するように制御する。高元側冷凍サイクル30の動作圧力(低圧圧力)が低下することで、低元側冷凍サイクル10の高圧圧力と高元側冷凍サイクル30の低圧圧力との差が大きくなり、低元側冷凍サイクル10の高圧圧力が低下する。高元側冷凍サイクル30の動作圧力(低圧圧力)が上昇することで、低元側冷凍サイクル10の高圧圧力と高元側冷凍サイクル30の低圧圧力との差が小さくなり、低元側冷凍サイクル10の高圧圧力が上昇する。高元側圧縮機31の運転状態(回転数等)がそのように制御されることで、低元側冷媒から高元側冷媒への放熱量が増減されることとなり、低元側冷凍サイクル10の冷却負荷が変動した場合でも、低元側冷凍サイクル10の高圧圧力を、低元側冷媒が不均化反応を生じる圧力未満に維持することが可能となる。
制御装置50は、高元側圧縮機31の運転状態(回転数等)を、低元側高圧圧力センサー21で検出される高圧圧力が、低元側冷媒が不均化反応を生じる圧力未満に維持されるように、制御する。高元側圧縮機31の運転状態(回転数等)がそのように制御されることで、低元側冷媒から高元側冷媒への放熱量が増減されることとなり、低元側冷凍サイクル10の冷却負荷が変動した場合でも、低元側冷凍サイクル10の高圧圧力を、低元側冷媒が不均化反応を生じる圧力未満に維持することが可能となる。制御装置50は、高元側圧縮機31の運転状態(回転数等)を、低元側吐出温度センサー23で検出される吐出温度が、低元側冷媒が不均化反応を生じる温度未満に維持されるように、制御してもよい。
低元側冷凍サイクル10が、圧力又は温度が基準値まで上昇すると開放される、圧力逃し装置を有し、低元側冷媒の圧力が、その圧力逃し装置によって、低元側冷媒が不均化反応を生じる圧力未満に維持される。例えば、図2に示されるように、低元側受液器15に、圧力逃し装置である可溶栓15aが設けられ、低元側冷媒の圧力又は温度が基準値まで上昇した際に、その可溶栓15aの融点が低い部分が溶けて穴が開くことで、低元側冷媒の圧力が、低元側冷媒が不均化反応を生じる圧力未満に維持される。制御装置50が、低元側高圧圧力センサー21で検出される高圧圧力が基準値まで上昇した際に、又は、低元側吐出温度センサー23で検出される吐出温度が基準値まで上昇した際に、低元側圧縮機11を停止してもよい。
制御装置50は、高元側圧縮機31の運転状態(回転数等)を、低元側高圧圧力センサー21で検出される高圧圧力が、低元側冷媒が不均化反応を生じる圧力と、低元側低圧圧力センサー22で検出される低圧圧力と、の相乗平均値となるように、制御する。
以下に、実施の形態1に係る冷凍装置の作用について説明する。
冷凍装置1では、低元側冷媒の圧力が、低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持される。そのため、低元側冷媒が、HFO-1123冷媒等のような不均化反応を生じる冷媒であるにも関わらず、恰も、低元側冷媒が不均化反応を生じる冷媒でない場合のように、冷凍装置1を動作させることが可能となって、例えば、冷凍装置1の安全性能を向上すること、冷凍装置1を低コスト化すること、冷凍装置1の省エネ性能を向上すること、冷凍装置1の地球温暖化への影響を低減すること等の、実現性が向上される。
実施の形態2に係る冷凍装置について説明する。
なお、実施の形態1と重複又は類似する説明は、適宜簡略化又は省略している。
<冷凍装置の構成>
以下に、実施の形態2に係る冷凍装置の構成について説明する。
図5は、実施の形態2に係る冷凍装置の、構成を説明するための図である。
図5に示されるように、低元側冷凍サイクル10は、低元側凝縮器12と低元側膨張弁13との間を連通させる配管に配設された低元側受液器15と、低元側圧縮機11と低元側凝縮器12との間を連通させる配管に配設された逆止弁16と、低元側受液器15と低元側膨張弁13との間を連通させる配管に配設された、開閉弁である電磁弁17と、を有する。
以下に、実施の形態2に係る冷凍装置の動作について説明する。
制御装置50は、通常運転時には、実施の形態1と同様に、低元側冷凍サイクル10の低元側冷媒を循環させるとともに、高元側冷凍サイクル30の高元側冷媒を循環させる。そして、例えば、温度制御等のために、低元側圧縮機11を断続運転する等の場合において、低元側圧縮機11が停止される際には、制御装置50は、低元側圧縮機11を停止する前に、電磁弁17を閉状態にし、低元側圧縮機11を稼働することを所定時間継続する。制御装置50がそのように動作することで、低元側冷凍サイクル10内の低元側冷媒が、低元側冷凍サイクル10の逆止弁16と電磁弁17との間、特に低元側受液器15に、高圧となって貯留された状態で、低元側圧縮機11が停止されることとなる。
以下に、実施の形態2に係る冷凍装置の作用について説明する。
冷凍装置1では、低元側圧縮機11が停止する場合であっても、低元側冷媒の圧力が、低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持される。そのため、低元側冷媒が、HFO-1123冷媒等のような不均化反応を生じる冷媒であるにも関わらず、恰も、低元側冷媒が不均化反応を生じる冷媒でない場合のように、冷凍装置1を動作させることが可能となって、例えば、冷凍装置1の安全性能を向上すること、冷凍装置1を低コスト化すること、冷凍装置1の省エネ性能を向上すること、冷凍装置1の地球温暖化への影響を低減すること等の、実現性が向上される。
実施の形態3に係る冷凍装置について説明する。
なお、実施の形態1及び実施の形態2と重複又は類似する説明は、適宜簡略化又は省略している。
<冷凍装置の構成>
以下に、実施の形態3に係る冷凍装置の構成について説明する。
図6は、実施の形態3に係る冷凍装置の、構成を説明するための図である。
図6に示されるように、低元側冷凍サイクル10は、低元側凝縮器12と低元側膨張弁13との間を連通させる配管に配設された低元側受液器15と、低元側圧縮機11と低元側凝縮器12との間を連通させる配管に配設された逆止弁16と、低元側受液器15と低元側膨張弁13との間を連通させる配管に配設された電磁弁17と、を有する。なお、実施の形態2と同様に、高元側冷凍サイクル30が冷却部35を有していてもよく、また、有していなくてもよい。
以下に、実施の形態3に係る冷凍装置の動作について説明する。
例えば、高元側圧縮機31が故障する等の場合において、高元側圧縮機31が運転を停止する際には、制御装置50は、低元側圧縮機11を停止する前に、電磁弁17を閉状態にし、低元側圧縮機11を稼働することを所定時間継続する。制御装置50がそのように動作することで、低元側冷凍サイクル10内の低元側冷媒が、低元側冷凍サイクル10の逆止弁16と電磁弁17との間、特に低元側受液器15に、高圧となって貯留された状態で、低元側圧縮機11が停止されることとなる。
以下に、実施の形態3に係る冷凍装置の作用について説明する。
冷凍装置1では、高元側圧縮機31が停止する場合であっても、低元側冷媒の圧力が、低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持される。そのため、低元側冷媒が、HFO-1123冷媒等のような不均化反応を生じる冷媒であるにも関わらず、恰も、低元側冷媒が不均化反応を生じる冷媒でない場合のように、冷凍装置1を動作させることが可能となって、例えば、冷凍装置1の安全性能を向上すること、冷凍装置1を低コスト化すること、冷凍装置1の省エネ性能を向上すること、冷凍装置1の地球温暖化への影響を低減すること等の、実現性が向上される。
Claims (20)
- 低元側圧縮機、低元側凝縮器、低元側減圧装置、及び、低元側蒸発器を有し、低元側冷媒を循環させる低元側冷凍サイクルと、
高元側圧縮機、高元側凝縮器、高元側減圧装置、及び、高元側蒸発器を有し、高元側冷媒を循環させる高元側冷凍サイクルと、
前記低元側凝縮器の前記低元側冷媒と、前記高元側蒸発器の前記高元側冷媒と、を熱交換させるカスケードコンデンサと、
制御装置と、を備え、
前記低元側冷媒は、不均化反応を生じる冷媒であり、
前記低元側冷媒の圧力は、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持される、冷凍装置。 - 前記制御装置は、
前記高元側冷凍サイクルの低圧圧力を変化させることで、前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、請求項1に記載の冷凍装置。 - 前記制御装置は、
前記低元側冷凍サイクルの冷却負荷が増加する場合に、前記高元側冷凍サイクルの低圧圧力を低下させ、
前記低元側冷凍サイクルの冷却負荷が減少する場合に、前記高元側冷凍サイクルの低圧圧力を上昇させる、請求項2に記載の冷凍装置。 - 前記制御装置は、
前記高元側圧縮機を制御することで、前記高元側冷凍サイクルの低圧圧力を変化させる、請求項2又は3に記載の冷凍装置。 - 前記低元側冷凍サイクルは、
前記低元側冷凍サイクルの高圧圧力を検出する低元側高圧圧力検出手段と、
前記低元側冷凍サイクルの低圧圧力を検出する低元側低圧圧力検出手段と、を有し、
前記制御装置は、
前記低元側高圧圧力検出手段で検出される高圧圧力が、前記低元側冷媒が不均化反応を生じる圧力と、前記低元側低圧圧力検出手段で検出される低圧圧力と、の相乗平均値に、近づくように制御することで、前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、請求項1~4のいずれか一項に記載の冷凍装置。 - 前記制御装置は、
前記低元側圧縮機の停止中に前記高元側圧縮機を稼働することで、前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、請求項1~5のいずれか一項に記載の冷凍装置。 - 前記低元側冷凍サイクルは、
前記低元側凝縮器と前記低元側減圧装置との間を連通させる流路に配設された低元側受液器を有する、請求項1~6のいずれか一項に記載の冷凍装置。 - 前記低元側受液器の前記低元側冷媒は、前記低元側圧縮機の停止中に冷却される、請求項7に記載の冷凍装置。
- 前記低元側冷凍サイクルは、
前記低元側圧縮機と前記低元側凝縮器との間を連通させる流路に配設された逆止弁と、
前記低元側受液器と前記低元側減圧装置との間を連通させる流路に配設された開閉弁と、を有し、
前記制御装置は、
前記開閉弁を閉じつつ前記低元側圧縮機を稼働する状態を維持した後に、前記低元側圧縮機を停止して、前記逆止弁と前記開閉弁との間の前記低元側冷媒を冷却することで、前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、請求項7又は8に記載の冷凍装置。 - 前記低元側冷凍サイクルは、
前記低元側圧縮機と前記低元側凝縮器との間を連通させる流路に配設された逆止弁と、
前記低元側受液器と前記低元側減圧装置との間を連通させる流路に配設された開閉弁と、を有し、
前記制御装置は、
前記高元側圧縮機が停止する場合に、前記開閉弁を閉じつつ前記低元側圧縮機を稼働する状態を維持した後に、前記低元側圧縮機を停止して、前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、請求項7又は8に記載の冷凍装置。 - 前記制御装置は、
前記高元側圧縮機が停止する場合に、前記開閉弁を閉じつつ前記低元側圧縮機を稼働する状態を維持した後に、前記低元側圧縮機を停止して、前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、請求項9に記載の冷凍装置。 - 前記逆止弁と前記開閉弁との間を連通させる部材の総容量は、
前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力である場合の、前記低元側冷媒の液状態での最大体積と比較して、大きい、請求項10又は11に記載の冷凍装置。 - 前記低元側冷凍サイクルは、圧力逃し装置を有する、請求項1~12のいずれか一項に記載の冷凍装置。
- 前記制御装置は、
前記低元側冷媒の圧力及び温度のうちの少なくとも一方が基準値を超える場合に、前記低元側圧縮機を停止することで、前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、請求項1~13のいずれか一項に記載の冷凍装置。 - 前記高元側冷媒は、前記低元側冷媒が同一の冷凍サイクルに用いられる場合と比較して、該冷凍サイクルの運転効率を高くする冷媒である、請求項1~14のいずれか一項に記載の冷凍装置。
- 前記低元側冷媒は、HFO-1123冷媒を含む、請求項1~15のいずれか一項に記載の冷凍装置。
- 前記低元側冷媒は、HFO-1123冷媒にHFC系冷媒が混合された冷媒である、請求項16に記載の冷凍装置。
- 前記HFC系冷媒は、HFC-32冷媒である、請求項17に記載の冷凍装置。
- 前記低元側冷媒は、HFO-1123冷媒にHFO-1234yf冷媒が混合された冷媒である、請求項16に記載の冷凍装置。
- 低元側圧縮機、低元側凝縮器、低元側減圧装置、及び、低元側蒸発器を有し、低元側冷媒を循環させる低元側冷凍サイクルと、高元側圧縮機、高元側凝縮器、高元側減圧装置、及び、高元側蒸発器を有し、高元側冷媒を循環させる高元側冷凍サイクルと、前記低元側凝縮器の前記低元側冷媒と、前記高元側蒸発器の前記高元側冷媒と、を熱交換させるカスケードコンデンサと、を備えた冷凍装置の制御方法であって、
前記低元側冷媒は、不均化反応を生じる冷媒であり、
前記低元側冷媒の圧力を、前記低元側冷媒が不均化反応を生じる圧力と比較して低い圧力に維持する、冷凍装置の制御方法。
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