WO2014038028A1 - Dispositif de réfrigération - Google Patents

Dispositif de réfrigération Download PDF

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Publication number
WO2014038028A1
WO2014038028A1 PCT/JP2012/072673 JP2012072673W WO2014038028A1 WO 2014038028 A1 WO2014038028 A1 WO 2014038028A1 JP 2012072673 W JP2012072673 W JP 2012072673W WO 2014038028 A1 WO2014038028 A1 WO 2014038028A1
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Prior art keywords
temperature side
refrigerant
low temperature
low
condenser
Prior art date
Application number
PCT/JP2012/072673
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English (en)
Japanese (ja)
Inventor
杉本　猛
野本　宗
智隆 石川
池田　隆
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2014534094A priority Critical patent/JP5759076B2/ja
Priority to PCT/JP2012/072673 priority patent/WO2014038028A1/fr
Publication of WO2014038028A1 publication Critical patent/WO2014038028A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle

Definitions

  • the present invention relates to a refrigeration apparatus, and more particularly to a refrigeration apparatus having a liquid receiver that stores liquid refrigerant.
  • a conventional refrigeration system has a dual refrigeration cycle in which a low temperature side circulation circuit and a high temperature side circulation circuit are connected by a cascade heat exchanger, and a CO 2 refrigerant is adopted in the low temperature side circulation circuit.
  • a CO 2 refrigerant is used as the refrigerant
  • the refrigerant pressure becomes high, and the design pressure of the refrigeration apparatus needs to be increased accordingly. That is, for example, it is necessary to increase the thickness of the hairpin (copper tube) of the evaporator or the thickness of the pipe connected to the evaporator so as to withstand the refrigerant pressure.
  • Patent Document 1 operates the compressor of the high-temperature side circulation circuit at the time of defrosting the evaporator of the low-temperature side circulation circuit.
  • the cascade heat exchanger of the high-temperature side circulation circuit cools the cascade heat exchanger of the low-temperature side circulation circuit, suppresses the pressure rise in the low-temperature side circulation circuit, and realizes a lower design pressure of the refrigeration system Trying to.
  • JP 2004-190917 A (see, for example, page 14 and FIG. 1)
  • Patent Document 1 operates the compressor of the high-temperature side circulation circuit at the time of defrosting the evaporator of the low-temperature side circulation circuit, and reduces the design pressure of the refrigeration apparatus. However, it takes about 30 to 40 minutes to operate the compressor in the high-temperature side circulation circuit during defrosting (defrosting is performed about 4 to 5 times a day). There was a problem that would be damaged.
  • the present invention has been made to solve the above-described problems, and suppresses the deterioration of convenience while reducing the design pressure, and suppresses the reduction of the pull-down speed while reducing the design pressure.
  • An object of the present invention is to provide a refrigeration apparatus that achieves this.
  • a refrigeration apparatus includes a high temperature side compressor, a high temperature side condenser, a high temperature side expansion device, and a high temperature side refrigeration cycle configured by connecting the evaporation side of a cascade condenser with a refrigerant pipe, a low temperature side compressor, and a cascade.
  • a refrigeration system having a condenser side, a receiver, a low temperature side throttle device, and a low temperature side refrigeration cycle configured by connecting a low temperature side evaporator with a refrigerant pipe
  • the receiver is filled in the low temperature side refrigeration cycle
  • a container having a volume of 5 to 7 times the volume when the total refrigerant is liquid refrigerant is provided.
  • the volume of the liquid receiver is 5 to 7 times the converted volume of the liquid refrigerant. Therefore, it is possible to suppress the deterioration of convenience and to suppress the reduction of the pull-down speed while reducing the design pressure.
  • Embodiment 1 FIG.
  • the refrigeration apparatus 100 suppresses the deterioration of convenience while reducing the design pressure, and suppresses the reduction of the pull-down speed while reducing the design pressure.
  • the liquid receiver 9 provided in the circuit is improved.
  • FIG. 1 is an example of a refrigerant circuit diagram of the refrigeration apparatus 100 according to the first embodiment.
  • FIG. 2 is a schematic diagram illustrating a configuration example of the liquid receiver 9 illustrated in FIG. 1.
  • the configuration of the refrigeration apparatus 100 will be described with reference to FIGS. 1 and 2.
  • the refrigeration apparatus 100 includes a high temperature side compressor 1 and the like, a high temperature side circulation circuit A in which a first refrigerant circulates, and a low temperature side circulation circuit B in which a low temperature side compressor 5 and the like are provided and a second refrigerant circulates. have.
  • the high-temperature side circulation circuit A and the low-temperature side circulation circuit B are connected via a cascade capacitor 8 described later, and the first refrigerant and the second refrigerant exchange heat to heat the second refrigerant. It has come to be.
  • the high temperature side circulation circuit A includes a high temperature side compressor 1 that compresses and discharges the first refrigerant, a high temperature side condenser 2 that functions as a condenser (heat radiator), and a high temperature side expansion valve 3 that depressurizes the first refrigerant. And a high temperature side evaporator 4 (cascade capacitor 8) functioning as an evaporator is connected by a refrigerant pipe.
  • the low temperature side circulation circuit B includes a low temperature side compressor 5 that compresses and discharges the second refrigerant, an auxiliary capacitor 6 and a low temperature side condenser 7 that function as a condenser (heat radiator), and a liquid of the second refrigerant.
  • a liquid receiver 9 that stores the refrigerant, a low-temperature side electromagnetic valve 11 that opens and closes the flow path, a low-temperature side first expansion valve 10 that depressurizes the second refrigerant, and a low-temperature side evaporator 12 that functions as an evaporator. They are connected by refrigerant piping.
  • the low temperature side circulation circuit B includes a liquid pipe 15 that connects the liquid receiver 9 and the low temperature side solenoid valve 11, and a gas pipe 16 that connects the low temperature side evaporator 12 and the suction side of the low temperature side compressor 5.
  • a cooling unit 13 such as a showcase or a unit cooler.
  • the high temperature side circulation circuit A does not have the liquid piping 15 and the gas piping 16, and is a short closed circuit with a small amount of refrigerant.
  • coolant for example, R410A, R134a, R32, HFO refrigerant
  • GWP global warming potential
  • the high temperature side compressor 1 sucks the first refrigerant, compresses the first refrigerant, and discharges it in a high temperature / high pressure state.
  • the discharge side of the first refrigerant is connected to the high temperature side condenser 2, and the suction side is connected to the high temperature side evaporator 4.
  • the low temperature side compressor 5 also has the same function as the high temperature side compressor 1. That is, the low temperature side compressor 5 sucks the second refrigerant, compresses the second refrigerant, and discharges it in a high temperature / high pressure state.
  • the low temperature side compressor 5 has a second refrigerant discharge side connected to the auxiliary condenser 6 and a suction side connected to the low temperature side evaporator 12.
  • the case where the outputs of the high temperature side compressor 1 and the low temperature side compressor 5 are about 10 horsepower will be described as an example.
  • the high-temperature side condenser 2 performs heat exchange between air supplied by a fan (not shown) and a first refrigerant, and condenses and liquefies the first refrigerant.
  • One side of the high temperature side condenser 2 is connected to the discharge side of the high temperature side compressor 1, and the other side is connected to the high temperature side expansion valve 3.
  • the auxiliary capacitor 6 and the low temperature side condenser 7 also have the same functions as the high temperature side condenser 2.
  • condenser 6 heat-exchanges between the air supplied with the fan by which the illustration was abbreviate
  • the low temperature side condenser 7 condenses and liquefies the second refrigerant by using the cold heat from the first refrigerant flowing through the high temperature side evaporator 4.
  • One of the auxiliary capacitors 6 is connected to the discharge side of the low temperature side compressor 5, and the other is connected to the low temperature side condenser 7.
  • One of the low temperature side condensers 7 is connected to the auxiliary capacitor 6 and the other is connected to the liquid receiver 9.
  • the high temperature side expansion valve 3 is for depressurizing and expanding the first refrigerant.
  • One side of the high temperature side expansion valve 3 is connected to the high temperature side condenser 2, and the other side is connected to the high temperature side evaporator 4.
  • the low temperature side first expansion valve 10 also has the same function as the high temperature side expansion valve 3. That is, the low temperature side first expansion valve 10 is for depressurizing and expanding the second refrigerant.
  • One of the low temperature side first expansion valves 10 is connected to the low temperature side solenoid valve 11, and the other is connected to the low temperature side evaporator 12.
  • the low temperature side first expansion valve 10 is mounted on the cooling unit 13.
  • the high temperature side expansion valve 3 and the low temperature side first expansion valve 10 may be constituted by, for example, a temperature type automatic expansion valve or an electronic type expansion valve whose opening degree is variable.
  • the high temperature side evaporator 4 evaporates the first refrigerant using the heat of the second refrigerant flowing through the low temperature side condenser 7.
  • One side of the high temperature side evaporator 4 is connected to the high temperature side expansion valve 3, and the other side is connected to the suction side of the high temperature side compressor 1. Further, the high temperature side evaporator 4 constitutes a part of the cascade capacitor 8.
  • the low temperature side evaporator 12 heat-exchanges between the air supplied with the fan with illustration not shown, and the 2nd refrigerant
  • the low temperature side evaporator 12 is connected to the low temperature side first expansion valve 10, and the other end is connected to the suction side of the low temperature side compressor 5 via the gas pipe 16.
  • the low temperature side evaporator 12 is mounted on the cooling unit 13.
  • the low-temperature side evaporator 12, the high-temperature side condenser 2, and the auxiliary condenser 6 may be constituted by, for example, a plate fin tube heat exchanger that can exchange heat between the air passing through the fins and the refrigerant. .
  • the liquid receiver 9 stores a part of the liquid refrigerant condensed by the low-temperature side condenser 7 circulating in the low-temperature side circulation circuit B so that it can be stably supplied to the low-temperature side evaporator 12.
  • the liquid receiver 9 can separate the gas refrigerant and the liquid refrigerant and supply the separated liquid refrigerant to the downstream side.
  • the liquid receiver 9 includes a container 9A for storing a gas refrigerant and a liquid refrigerant, and a refrigerant inflow pipe 9B1 and a refrigerant outflow pipe 9B2 connected to the container 9A so as to communicate with the container 9A. Have.
  • the container 9A is a container for storing liquid refrigerant and gas refrigerant supplied from the low-temperature side condenser 7 side.
  • a refrigerant inflow pipe 9B1 and a refrigerant outflow pipe 9B2 are connected to the container 9A. For this reason, the refrigerant is supplied into the container 9A from the refrigerant inflow pipe 9B1, and the liquid refrigerant stored in the container 9A flows out from the refrigerant outflow pipe 9B2 to the low temperature side evaporator 12 side.
  • One of the refrigerant inflow pipes 9B1 is connected to a pipe on the low-temperature side condenser 7 side, and the other end is provided inside the container 9A.
  • One end of the refrigerant outflow pipe 9B2 is provided inside the container 9A, and the other end is connected to the liquid pipe 15.
  • the volume of the container 9A of the refrigeration apparatus 100 according to Embodiment 1 is set so as to reduce the pressure of the second refrigerant (CO 2 refrigerant) circulating in the low-temperature side circulation circuit B.
  • the volume of the container 9A will be described in detail later with reference to FIG.
  • the case where the liquid receiver 9 has the container 9A, the refrigerant inflow pipe 9B1, and the refrigerant outflow pipe 9B2 has been described as an example.
  • the present invention is not limited thereto.
  • a desiccant or the like that removes impurities such as dust and moisture contained in the second refrigerant circulating in the low-temperature side circulation circuit B may be provided.
  • the cascade condenser 8 includes the high temperature side evaporator 4 and the low temperature side condenser 7, and transmits the cold heat of the first refrigerant flowing through the high temperature side evaporator 4 to the second refrigerant flowing through the low temperature side condenser 7. Can be done.
  • the cascade capacitor 8 may be constituted by, for example, a plate heat exchanger.
  • the low temperature side solenoid valve 11 opens and closes the refrigerant flow path.
  • One of the low temperature side solenoid valves 11 is connected to the liquid receiver 9 via the liquid pipe 15, and the other is connected to the low temperature side first expansion valve 10.
  • the low temperature side solenoid valve 11 includes a coil that is controlled by the control device 18 to be energized and a valve element that operates to open and close the refrigerant flow path when the coil is energized.
  • Liquid pipe 15 and gas pipe 16 One of the liquid pipes 15 is connected to the liquid receiver 9 and the other is connected to the low temperature side solenoid valve 11.
  • the liquid refrigerant separated in the liquid receiver 9 flows through the liquid pipe 15.
  • One of the gas pipes 16 is connected to the low temperature side evaporator 12 and the other is connected to the suction side of the low temperature side compressor 5.
  • the gas pipe 16 exchanges heat with the air supplied to the low temperature side evaporator 12, and the gasified second refrigerant flows.
  • the lengths of the liquid pipe 15 and the gas pipe 16 are about 70 m will be described as an example.
  • Control device 18 The control device 18 determines the frequency (including operation / stop) of the high temperature side compressor 1 and the low temperature side compressor 5 based on the detection result of a temperature sensor or the like (not shown), and the rotational speed of the fan attached to these compressors. (Including operation / stopping), the opening degree of the high temperature side expansion valve 3 and the low temperature side first expansion valve 10, the opening and closing of the low temperature side solenoid valve 11, and the like.
  • the installation position of the control device 18 is not particularly limited, but is installed in, for example, the cooling unit 13 as shown in FIG.
  • the control apparatus 18 is comprised by a microcomputer etc., for example.
  • the cooling unit 13 includes a low temperature side evaporator 12, a low temperature side first expansion valve 10, and a low temperature side electromagnetic valve 11, and corresponds to, for example, a showcase or a unit cooler.
  • the first embodiment will be described as a showcase. In the example of the first embodiment, six showcases of the cooling unit 13 and six of six showcases are connected, and the total inner volume of the showcase is about 72 liters. It shall be.
  • the state transition of the first refrigerant flowing through the high temperature side circulation circuit A shown in FIG. 1 will be described with reference to FIG.
  • the gaseous first refrigerant compressed and discharged by the high temperature side compressor 1 flows into the high temperature side condenser 2.
  • the gaseous first refrigerant flowing into the high temperature side condenser 2 is condensed by exchanging heat with the outside air supplied from the fan, and flows out from the high temperature side condenser 2.
  • the first refrigerant flowing out of the high temperature side condenser 2 flows into the high temperature side expansion valve 3 and is decompressed by the high temperature side expansion valve 3.
  • the decompressed first refrigerant flows into the high temperature side evaporator 4, vaporizes by exchanging heat with the second refrigerant flowing through the low temperature side condenser 7, and flows out from the high temperature side evaporator 4.
  • the gaseous first refrigerant flowing out of the high temperature side evaporator 4 is sucked into the high temperature side compressor 1.
  • the gaseous second refrigerant compressed and discharged by the high temperature side compressor 1 flows into the low temperature side condenser 7 via the auxiliary capacitor 6 that functions as a condenser.
  • the second refrigerant is condensed by exchanging heat with the outside air supplied from the fan, and flows out from the low-temperature side condenser 7.
  • the second refrigerant that has flowed out of the low-temperature side condenser 7 flows into the liquid receiver 9 and is separated into liquid refrigerant and gas refrigerant.
  • the liquid refrigerant in the liquid receiver 9 flows into the low temperature side first expansion valve 10 through the liquid pipe 15 and the low temperature side solenoid valve 11.
  • the second refrigerant flowing into the low temperature side first expansion valve 10 is decompressed.
  • the decompressed second refrigerant flows into the low temperature side evaporator 12, performs heat exchange with the air supplied from the fan, evaporates, and flows out from the low temperature side evaporator 12.
  • the gaseous second refrigerant flowing out from the low temperature side evaporator 12 is sucked into the low temperature side compressor 5 through the gas pipe 16.
  • FIG. 3 shows the relationship between the volume in the low temperature side circulation circuit B and the pressure in the low temperature side circulation circuit B of the refrigeration apparatus 100 according to the first embodiment.
  • the result of FIG. 3 was calculated from the following conditions.
  • the curve in FIG. 3 employs CO 2 refrigerant in the low temperature side circulation circuit B, the nominal output of the low temperature side compressor 5 of the low temperature side circulation circuit B is about 10 horsepower, and is connected to the cooling unit 13.
  • the liquid pipe 15 and the gas pipe 16 are assumed to be 70 m.
  • the cooling unit 13 has six 8-sized showcases and two six-sized showcases, and the total internal volume of the showcase is about 72 liters.
  • the refrigerant amount in the low-temperature side circulation circuit B path when the liquid pipe 15 is filled with the liquid refrigerant is about 30 kg.
  • the weight of the gas refrigerant is ignored in calculating the refrigerant amount by weight. That is, the refrigerant in the gas pipe 16 is not taken into consideration.
  • FIG. 3 shows the relationship between the circuit internal volume in the low temperature side circulation circuit B and the pressure in the circuit (ambient temperature 46 ° C.).
  • the required circuit internal volume is about 400 (liters) (see the upper curve in FIG. 3).
  • the total internal volume of the vessel 12 (eight showcases and about 72 liters) is about 160 (liters).
  • the container 9A of the liquid receiver 9 has a volume approximately seven times (40 liters + 240 liters) that is usually about 40 (liters).
  • the volume is usually limited to about seven times (40 liters + 240 liters) of the liquid receiver of about 40 (liters). It is not a thing.
  • the volume of the container 9A of the liquid receiver 9 is preferably in the range of about 5 to 7 times that of a normal 40 (liter) liquid receiver.
  • the design pressure of the low-temperature side circulation circuit B is increased to, for example, about 8.5 (Mpa)
  • the low-temperature side evaporator 12 is a plate fin tube heat exchanger
  • the copper passing through the inside The specification of the pipe (hairpin) is, for example, about ⁇ 9.52 mm (wall thickness 0.8 mm).
  • the design pressure of the low-temperature side circulation circuit B can be suppressed to about 4.15 (Mpa), which is equivalent to R410A
  • the specification of the hairpin of the low-temperature side evaporator 12 is about ⁇ 9.52 mm (thickness 0.35 mm). Therefore, the material cost alone can be reduced to about half.
  • the refrigerant pressure in the low temperature side circulation circuit B can be reduced, for example, when the low temperature side evaporator 12 in the low temperature side circulation circuit B is defrosted, the high temperature side compressor 1 in the high temperature side circulation circuit A is operated.
  • the necessity to implement control for reducing the refrigerant pressure can also be reduced, and convenience can be prevented from being impaired.
  • the refrigerant pressure in the low-temperature side circulation circuit B can be reduced, when the refrigerant pressure in the low-temperature side circulation circuit B rises, for example, the CO 2 refrigerant is discharged by a safety valve and then the CO 2 refrigerant is replenished.
  • the refrigeration apparatus 100 can reduce the refrigerant pressure of the low-temperature side circulation circuit B, it is possible to prevent the convenience from being impaired while reducing the design pressure.
  • the refrigeration apparatus 100 when a load is generated and restarted when the low temperature side circulation circuit B is stopped (when the thermostat is off), the refrigerant pressure discharged from the low temperature side compressor 5 is transient. Even if it rises, the following effects can be obtained. Since the refrigerant pressure in the low-temperature side circulation circuit B can be reduced, the value of the refrigerant pressure that has risen transiently can be kept below a preset value. In order to suppress the transient increase in the refrigerant pressure in this way, the low temperature side compressor 5 of the low temperature side circulation circuit B after several tens of seconds to several minutes from the start of the high temperature side compressor 1 of the high temperature side circulation circuit A. The necessity to implement control (see Patent Document 2) for starting up is reduced. That is, the refrigeration apparatus 100 according to the present embodiment can suppress the reduction of the pull-down speed, and can suppress the loss of convenience while reducing the design pressure.
  • the thickness of the hairpin (copper pipe) of the low temperature side evaporator 12 is the same as that of the HFC refrigerant.
  • the thickness of the refrigerant pipe (liquid pipe, gas pipe) connected to the low temperature side evaporator 12 can be made the same as that of the HFC refrigerant. Thereby, it can suppress that the manufacturing cost of the freezing apparatus 100 increases.
  • FIG. 4 is an example of a refrigerant circuit diagram of the refrigeration apparatus 200 according to Embodiment 2. The refrigeration apparatus 200 will be described with reference to FIG.
  • the low temperature side second expansion valve 14 is configured to depressurize the second refrigerant to an intermediate pressure and bring the second refrigerant into a gas-liquid two-phase state.
  • One of the low temperature side second expansion valves 14 is connected to the liquid receiver 9 and the other is connected to the liquid pipe 15.
  • the low temperature side second expansion valve 14 may be constituted by, for example, a temperature type automatic expansion valve or an electronic expansion valve whose opening degree is variable.
  • the second refrigerant that is the high-pressure liquid refrigerant that has flowed out of the low-temperature side condenser 7 flows into the liquid receiver 9 and is separated into liquid refrigerant and gas refrigerant.
  • the liquid refrigerant in the liquid receiver 9 flows out of the liquid receiver 9
  • the liquid refrigerant is decompressed by the low temperature side second expansion valve 14 and becomes a medium-pressure gas-liquid two-phase refrigerant.
  • This medium-pressure gas-liquid two-phase refrigerant flows into the low temperature side first expansion valve 10 through the liquid pipe 15 and the low temperature side solenoid valve 11.
  • the second refrigerant flowing into the low temperature side first expansion valve 10 is decompressed.
  • the decompressed second refrigerant flows into the low temperature side evaporator 12, performs heat exchange with the air supplied from the fan, evaporates, and flows out from the low temperature side evaporator 12.
  • the gaseous second refrigerant flowing out from the low temperature side evaporator 12 is sucked into the low temperature side compressor 5 through the gas pipe 16.
  • FIG. 5 is a pH diagram illustrating the operation of the refrigeration apparatus 200 according to Embodiment 2. That is, FIG. 5 shows the operation of the low-temperature side circulation circuit B on the pressure-enthalpy diagram.
  • a point is discharge of the low temperature side compressor 5
  • B point is the exit of a low temperature side condenser
  • C point is in the liquid piping 15
  • D point is the inlet of the low temperature side evaporator 12
  • E point is the low temperature side compressor 5 Shows the state of inhalation.
  • the liquid refrigerant and the gas refrigerant flow at a relative speed.
  • the ratio of the liquid phase and the gas phase in the section of the liquid pipe 15 may be about 0.5, respectively.
  • the average density in the liquid pipe 15 in which the second refrigerant in the gas-liquid two-phase state having a dryness of about 0.1 to 0.2 flows is about half of the complete liquid state.
  • the required amount of refrigerant in the liquid pipe 15 through which the gas-liquid two-phase refrigerant flows is about half of the liquid state.
  • the relationship between the circuit volume in the low-temperature circuit B and the pressure in the circuit corresponds to the lower curve in FIG. 3 described above.
  • the refrigerant amount in the low temperature side circulation circuit B is about 26 (kg).
  • the required circuit internal volume is about 300 (liters) (the lower curve in FIG. 3). reference).
  • 140 (liter) is the difference between 300 (liter) and 160 (liter). ) Volume is insufficient.
  • the container 9A of the liquid receiver 9 has a volume approximately 4.5 times (40 liters + 140 liters) of a liquid receiver of about 40 (liters).
  • the gas pipe diameter is about 31.75 (mm).
  • the pipe diameter may be further reduced.
  • the gas pipe 16 may be thinned to about ⁇ 19.05 (mm).
  • the pipe diameter of the gas pipe 16 is set to about ⁇ 31.75 (mm) which is the pipe diameter equivalent to that of the HFC refrigerant, the volume of the container 9A of the liquid receiver 9 can be reduced correspondingly.
  • the volume of the container 9A of the liquid receiver 9 is increased. It can be reduced accordingly. Since the length of the gas pipe 16 is about 70 (m), if the pipe diameter of the gas pipe 16 is about ⁇ 31.75 (mm), the internal volume increases by about 40 (liter), and the volume of the container 9A is increased. It can be reduced from 140 (liter) to 100 (liter).
  • a normal (about 40 liter) receiver 9 and a 140 (liter) receiver 9 plus 100 (liter) are required.
  • the volume of the container 9A of the liquid receiver 9 is 3.5 times (40 liters + 100 liters) of a normal liquid receiver of about 40 (liters).
  • the volume of the liquid receiver 9 is usually about 40 (liters), it is recommended that the volume be about 3.5 times or 4.5 times that, but it is not limited to this. It may be in a range of about 3 to 5 times.
  • the refrigeration apparatus 200 according to the second embodiment has the low temperature side second expansion valve 14, and when the volume of the refrigerant filled in the low temperature side circulation circuit B is converted into the volume of the liquid refrigerant, the liquid receiver
  • the volume of the nine containers 9A is approximately 3 to 5 times the converted volume of the liquid refrigerant. Even in this configuration, the same effect as that of the refrigeration apparatus 100 according to Embodiment 1 can be obtained.

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Abstract

La présente invention concerne un dispositif de réfrigération qui comprend : un cycle de réfrigération côté haute température conçu de sorte qu'un compresseur côté haute température, un condensateur côté haute température, un étranglement côté haute température et le côté évaporation d'un condensateur en cascade soient raccordés au moyen d'une tuyauterie de réfrigérant ; et un cycle de réfrigération à basse température conçu de sorte qu'un compresseur côté basse température, le côté condensateur du condensateur en cascade, un réservoir de liquide, un étranglement côté basse température et un évaporateur côté basse température soient raccordés au moyen d'une tuyauterie de réfrigérant. Le réservoir de liquide comprend un récipient présentant une capacité 5 à 7 fois supérieure au volume du réfrigérant liquide remplissant le cycle de réfrigération à basse température lorsque la totalité du réfrigérant consiste en un réfrigérant liquide.
PCT/JP2012/072673 2012-09-06 2012-09-06 Dispositif de réfrigération WO2014038028A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2014534094A JP5759076B2 (ja) 2012-09-06 2012-09-06 冷凍装置
PCT/JP2012/072673 WO2014038028A1 (fr) 2012-09-06 2012-09-06 Dispositif de réfrigération

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GB2514530A (en) * 2013-02-20 2014-12-03 Arctic Circle Ltd Apparatus for providing refrigeration and utilising operation converter means
CN105091390A (zh) * 2015-09-11 2015-11-25 南通百源制冷设备有限公司 一种液态二氧化碳直冻设备
CN105980794A (zh) * 2014-03-17 2016-09-28 三菱电机株式会社 冷冻装置以及冷冻装置的控制方法
JP2020201011A (ja) * 2019-06-12 2020-12-17 ダイキン工業株式会社 空調機
WO2022195727A1 (fr) * 2021-03-16 2022-09-22 三菱電機株式会社 Machine de source de chaleur pour appareil de réfrigération et appareil de réfrigération équipé de celle-ci
WO2023176870A1 (fr) * 2022-03-17 2023-09-21 三菱電機株式会社 Unité extérieure pour dispositif de réfrigération et dispositif de réfrigération

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GB2514530A (en) * 2013-02-20 2014-12-03 Arctic Circle Ltd Apparatus for providing refrigeration and utilising operation converter means
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CN105091390A (zh) * 2015-09-11 2015-11-25 南通百源制冷设备有限公司 一种液态二氧化碳直冻设备
JP2020201011A (ja) * 2019-06-12 2020-12-17 ダイキン工業株式会社 空調機
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WO2022195727A1 (fr) * 2021-03-16 2022-09-22 三菱電機株式会社 Machine de source de chaleur pour appareil de réfrigération et appareil de réfrigération équipé de celle-ci
WO2023176870A1 (fr) * 2022-03-17 2023-09-21 三菱電機株式会社 Unité extérieure pour dispositif de réfrigération et dispositif de réfrigération
WO2023175821A1 (fr) * 2022-03-17 2023-09-21 三菱電機株式会社 Appareil de réfrigération et unité extérieure d'appareil de réfrigération

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