Classifications

• • 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
  • 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
  • F25B2309/00—Gas cycle refrigeration machines
  • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
  • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
• • 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
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
  • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
• • 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
  • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
  • F25B2341/06—Details of flow restrictors or expansion valves
  • F25B2341/063—Feed forward expansion valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2600/00—Control issues
  • F25B2600/17—Control issues by controlling the pressure of the condenser
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2600/00—Control issues
  • F25B2600/25—Control of valves
  • F25B2600/2513—Expansion valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
  • F25B2700/19—Pressures
  • F25B2700/193—Pressures of the compressor
  • F25B2700/1931—Discharge pressures
• • 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
  • F25B2700/2102—Temperatures at the outlet of the gas cooler
• • 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
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
• • 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
  • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
  • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Definitions

• the present invention relates to a refrigeration apparatus, and more particularly to a refrigeration apparatus in which a refrigerant enters a supercritical state during a refrigeration cycle.
• Patent Document 1 JP-A-10-115470 (Page 4, Column 5, Line 12, Page 5, Column 7, Line 39, Fig. 3)
• An object of the present invention is to enable stable liquid level control of a liquid receiver in the refrigerant device as described above.
• a refrigeration apparatus includes a compression mechanism, a radiator, a first expansion mechanism, a liquid receiver, a second expansion mechanism, an evaporator, a temperature detection unit, a first pressure storage unit, and a second pressure determination unit.
• the compression mechanism compresses the refrigerant.
• the radiator is connected to the refrigerant discharge side of the compression mechanism.
• the first expansion mechanism is connected to the outlet side of the radiator.
• the liquid receiver is connected to the refrigerant outflow side of the first expansion mechanism.
• the second expansion mechanism is connected to the outlet side of the liquid receiver.
• the evaporator is connected to the refrigerant outflow side of the second expansion mechanism and to the refrigerant suction side of the compression mechanism.
• the temperature detector is provided between the outlet side of the radiator and the refrigerant inflow side of the first expansion mechanism.
• the first pressure storage unit stores an upper limit value and a lower limit value of the first pressure.
• the “first pressure” is the pressure of the refrigerant flowing from the refrigerant outflow side of the first expansion mechanism to the refrigerant inflow side of the second expansion mechanism.
• the second pressure determining unit determines the upper and lower limit values of the second pressure from the upper and lower limit values of the first pressure and the temperature detected by the temperature detecting unit.
• the “second pressure” here is the pressure of the refrigerant flowing from the refrigerant discharge side of the compression mechanism to the refrigerant inflow side of the first expansion mechanism.
• the pressure detector is provided between the refrigerant discharge side of the compression mechanism and the refrigerant inflow side of the first expansion mechanism.
• the control unit is configured to control the first expansion mechanism so that the pressure detected by the pressure detection unit is not more than the upper limit value of the second pressure and not less than the lower limit value, and the first pressure is not more than the upper limit value of the first pressure and not less than the lower limit value. And controls the second expansion mechanism.
• the second pressure determination unit determines the upper limit value and the lower limit value of the second pressure from the upper limit value and lower limit value of the first pressure and the temperature detected by the temperature detection unit.
• the control unit is configured so that the pressure detected by the pressure detection unit is not more than the upper limit value of the second pressure and not less than the lower limit value, and the first pressure is not more than the upper limit value of the first pressure and not less than the lower limit value. Controls the first expansion mechanism and the second expansion mechanism. For this reason, in this refrigeration apparatus, both the first pressure and the second pressure can be maintained at appropriate values.
• the upper limit value and the lower limit value of the first pressure are set so that the refrigerant flowing out of the first expansion mechanism is in the state near the saturation line but not in the vicinity of the critical point. This makes it possible to control the liquid level of the receiver liquid stably.
• a supercooling heat exchanger (which may be an internal heat exchanger) is installed between the receiver and the second expansion mechanism, it is possible to ensure a temperature difference between the high and low pressures of the supercooling heat exchanger. In consideration of this, it is necessary to set the upper and lower limits of the first pressure. In this way, an increase in the size of the supercooling heat exchanger can be avoided.
• a refrigeration apparatus is the refrigeration apparatus according to the first invention, further comprising a heat exchanger for cooling the refrigerant.
• the refrigerant cooling heat exchanger is disposed between the outlet side of the radiator and the refrigerant inflow side of the first expansion mechanism.
• the temperature detector is provided between the outlet side of the refrigerant cooling heat exchanger and the refrigerant inflow side of the first expansion mechanism.
• the temperature detection unit is provided between the outlet side of the refrigerant cooling heat exchanger and the refrigerant inflow side of the first expansion mechanism. For this reason, in this refrigeration apparatus, the control according to the present invention can be performed even when a refrigerant cooling heat exchanger is provided. The invention's effect
• both the first pressure and the second pressure can be maintained at appropriate values. Therefore, in this refrigeration system, if the upper limit value and lower limit value of the first pressure are set so that the refrigerant flowing out of the first expansion mechanism is in the vicinity of the saturation line but not in the vicinity of the critical point, the refrigeration apparatus is stable. The liquid level control of the received liquid receiver becomes possible. If a supercooling heat exchanger (which may be an internal heat exchanger) is installed between the receiver and the second expansion mechanism, it is also possible to ensure a temperature difference between the high and low pressures of the supercooling heat exchanger. In consideration of this, it is necessary to set the upper and lower limits of the first pressure. In this way, the force S can avoid the increase in size of the supercooling heat exchanger.
• a supercooling heat exchanger which may be an internal heat exchanger
• control according to the present invention can be performed even when a refrigerant cooling heat exchanger is provided.
• FIG. 1 is a refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention.
• FIG. 2 is a functional block diagram of a control device provided in the air-conditioning apparatus according to the embodiment of the present invention.
• FIG. 3 is a diagram for explaining liquid receiver liquid level control by the control device for the air-conditioning apparatus according to the embodiment of the present invention.
• FIG. 4 is a refrigerant circuit diagram of an air conditioner according to Modification (A).
• FIG. 5 is a diagram for explaining receiver liquid level control by the control device of the air-conditioning apparatus according to Modification (B).
• FIG. 1 shows a schematic refrigerant circuit 2 of an air conditioner 1 according to an embodiment of the present invention.
• the air conditioner 1 is an air conditioner that can perform cooling and heating operations using carbon dioxide as a refrigerant.
• the air conditioner 1 mainly includes a refrigerant circuit 2, blower fans 26 and 32, a control device 23, a high-pressure sensor 21, and a temperature. It consists of sensor 22 etc.
• the refrigerant circuit 2 mainly includes a compressor 11, a four-way selector valve 12, an outdoor heat exchanger 13, a first electric expansion valve 15, a liquid receiver 16, a second electric expansion valve 17, and an indoor heat exchanger 31. As shown in FIG. 1, each device is connected via a refrigerant pipe.
• the air conditioner 1 is a separation type air conditioner, and includes an indoor unit 30 mainly including an indoor heat exchanger 31 and an indoor fan 32, a compressor 11, and a four-way switching valve. 12, outdoor heat exchanger 13, first electric expansion valve 15, liquid receiver 16, second electric expansion valve 17, high pressure sensor 21, temperature sensor 22, and control unit 23
• the first connecting pipe 41 that connects the refrigerant gas piping of the indoor unit 30 and the refrigerant gas piping of the outdoor unit 10 It can be said that it consists of 2 connecting pipes 42.
• the refrigerant liquid piping of the outdoor unit 10 and the first connection pipe 41 are connected to the outdoor unit 10 refrigerant gas piping and the second communication pipe 42 via the first closing valve 18 of the outdoor unit 10.
• 10 second shutoff valves 19 are connected to each other.
• the indoor unit 30 mainly includes an indoor heat exchanger 31, an indoor fan 32, and the like.
• the indoor heat exchanger 31 is a heat exchanger for exchanging heat between indoor air that is air in the air-conditioned room and the refrigerant.
• the indoor fan 32 takes air in the air-conditioned room into the unit 30 and sends out conditioned air, which is air after heat exchange with the refrigerant via the indoor heat exchanger 31, to the air-conditioned room again.
• the outdoor unit 10 mainly includes a compressor 11, a four-way switching valve 12, an outdoor heat exchanger 13, a first electric expansion valve 15, a receiver 16, a second electric expansion valve 17, an outdoor fan 26, and a control device 23. , High pressure sensor 21, temperature sensor 22 and the like.
• the compressor 11 is a device for sucking low-pressure gas refrigerant flowing through the suction pipe, compressing it into a supercritical state, and discharging it to the discharge pipe.
• the four-way switching valve 12 is a valve for switching the flow direction of the refrigerant corresponding to each operation.
• the discharge side of the compressor 11 and the high temperature side of the outdoor heat exchanger 13 are connected.
• the suction side of the compressor 11 and the gas side of the indoor heat exchanger 31 are connected.
• the discharge side of the compressor 11 and the second shut-off valve 19 are connected, and the suction side of the compressor 11 and the outdoor heat exchange are connected.
• the gas side of the vessel 13 can be connected.
• the outdoor heat exchanger 13 can cool the high-pressure supercritical refrigerant discharged from the compressor 11 during the cooling operation using air outside the air-conditioning room as a heat source, and during the heating operation, the indoor heat exchanger 31 It is possible to evaporate the liquid refrigerant returning from.
• the first electric expansion valve 15 is used to depressurize the supercritical refrigerant (cooling operation) flowing out from the low temperature side of the outdoor heat exchanger 13 or the liquid refrigerant flowing through the receiver 16 (heating operation). It is.
• the liquid receiver 16 is for storing a surplus refrigerant according to the operation mode and the air conditioning load.
• the second electric expansion valve 17 is a liquid refrigerant flowing through the liquid receiver 16 (during cooling operation) or Is for depressurizing the supercritical refrigerant (during heating operation) flowing out from the low temperature side of the indoor heat exchanger 31.
• the outdoor fan 26 is a fan for exhausting air after taking outdoor air into the unit 10 and exchanging heat with the refrigerant via the outdoor heat exchanger 13.
• the high pressure sensor 21 is provided on the discharge side of the compressor 11.
• the temperature sensor 22 is provided near the inlet of the first electric expansion valve 15! /.
• the control device 23 is communicatively connected to the high pressure sensor 21, temperature sensor 22, first electric expansion valve 15, second electric expansion valve 17, etc., and temperature information and high pressure pressure sent from the temperature sensor 22 are connected. Based on the high pressure information sent from the sensor 21, the opening degree of the first electric expansion valve 15 and the second electric expansion valve 17 is controlled.
• the control device 23 mainly includes a storage unit 23a, a calculation unit 23b, and a control unit 23c.
• the storage unit 23a stores an upper limit value U of the pressure of the refrigerant (hereinafter referred to as intermediate pressure refrigerant) flowing between the refrigerant outflow side of the first electric expansion valve 15 and the refrigerant inflow side of the second electric expansion valve 17 during the cooling operation.
• the calculation unit 23b is configured to calculate the compressor from the information on the upper limit value UL1 and the lower limit value LL1 of the pressure of the intermediate pressure refrigerant sent from the storage unit 23a, and the temperature information transmitted from the temperature sensor 22.
• An upper limit value UL2 and a lower limit value LL2 of the pressure of the refrigerant flowing between the refrigerant discharge side of 11 and the refrigerant inflow side of the first electric expansion valve 15 (hereinafter referred to as high-pressure side refrigerant) are calculated.
• the upper limit UL2 and lower limit LL2 of the pressure of the high-pressure refrigerant are the upper limit UL1 and lower limit LL1 of the intermediate-pressure refrigerant, respectively, as shown in Fig. 3.
• control unit 23c holds the value indicated by the high pressure sensor 21 between the upper limit value UL2 and the lower limit value LL2 of the pressure of the high pressure refrigerant obtained above, and the pressure of the intermediate pressure refrigerant is the pressure of the intermediate pressure refrigerant.
• Upper limit value UL1 and lower limit value LL The opening degree of the first electric expansion valve 15 and the second electric expansion valve 17 is controlled so as to be within the range of 1.
• the pressure of the high-pressure side refrigerant is controlled exclusively by the first electric expansion valve 15.
• the pressure of the intermediate pressure refrigerant is controlled by the balance between the opening degree of the first electric expansion valve 15 and the opening degree of the second electric expansion valve 17.
• the opening degree of the second electric expansion valve 17 at this time is obtained by, for example, pre-functioning the opening degree of the second electric expansion valve 17 with the pressure of the intermediate pressure refrigerant and the opening degree of the first electric expansion valve 15 as variables. If you put it, you can easily decide.
• an average value of the upper limit value UL1 and the lower limit value LL1 may be used as the pressure value of the intermediate pressure refrigerant at this time.
• the operation of the air conditioner 1 will be described with reference to FIG.
• the air conditioner 1 can perform a cooling operation and a heating operation as described above.
• the four-way switching valve 12 is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor 11 is connected to the high temperature side of the outdoor heat exchanger 13 and the suction side of the compressor 11 is the second side. It is connected to the closing valve 19. At this time, the first closing valve 18 and the second closing valve 19 are opened.
• the cooled supercritical refrigerant is sent to the first electric expansion valve 15.
• the supercritical refrigerant sent to the first electric expansion valve 15 is depressurized and saturated, and then sent to the second electric expansion valve 17 via the liquid receiver 16.
• the saturated refrigerant sent to the second electric expansion valve 17 is reduced in pressure to become liquid refrigerant, and then supplied to the indoor heat exchanger 31 via the first closing valve 18 to cool the indoor air. It is evaporated to become a gas refrigerant.
• the four-way selector valve 12 is in the state indicated by the broken line in FIG.
• the discharge side of the compressor 11 is connected to the second closing valve 19, and the suction side of the compressor 11 is connected to the gas side of the outdoor heat exchanger 13.
• the first closing valve 18 and the second closing valve 19 are opened.
• the supercritical refrigerant is cooled while heating the indoor air in the indoor heat exchanger 31.
• the cooled supercritical refrigerant is sent to the second electric expansion valve 17 through the first closing valve.
• the supercritical refrigerant sent to the second electric expansion valve 17 is reduced in pressure and saturated, and then sent to the first electric expansion valve 15 via the liquid receiver 16.
• the saturated refrigerant sent to the first electric expansion valve 15 is reduced in pressure to become a liquid refrigerant, and then sent to the outdoor heat exchanger 13 via the internal heat exchanger 14, and in the outdoor heat exchanger 13. It is evaporated to become a gas refrigerant. Then, this gas refrigerant is sucked into the compressor 11 again via the four-way switching valve 12. In this way, the heating operation is performed.
• the information on the upper limit value UL1 and the information on the lower limit value LL1 are stored in the storage unit 23a so that the intermediate pressure refrigerant is in the vicinity of the saturation line but not in the vicinity of the critical point.
• the calculation unit 23b calculates the upper limit UL2 and the lower limit LL2 of the high-pressure side refrigerant pressure from the information on the upper limit UL1 and the information on the lower limit LL1, and the temperature information transmitted from the temperature sensor 22. To do.
• the control unit 23c keeps the value indicated by the high pressure sensor 21 between the upper limit value UL2 and the lower limit value LL2 of the pressure of the high pressure refrigerant obtained above, and the pressure of the intermediate pressure refrigerant is the pressure of the intermediate pressure refrigerant.
• the opening degree of the first electric expansion valve 15 and the second electric expansion valve 17 is controlled so as to be between the upper limit value UL1 and the lower limit value LL1. Therefore, in this air conditioner 1, both the pressure of the intermediate pressure refrigerant and the pressure of the high pressure side refrigerant can be maintained at appropriate values. Therefore, the air conditioner 1 can stably control the refrigerant liquid level of the liquid receiver 16.
• the present invention is applied to a separate air conditioner 1 in which one indoor unit 30 is provided for one outdoor unit 10.
• the present invention is shown in FIG.
• the present invention may be applied to a multi-type air conditioner 101 in which a plurality of indoor units are provided for a single outdoor unit.
• FIG. 4 the same reference numerals are used for the same components as those of the air conditioner 1 according to the previous embodiment.
• FIG. 4 the same reference numerals are used for the same components as those of the air conditioner 1 according to the previous embodiment.
• reference numeral 102 denotes a refrigerant circuit
• reference numeral 110 denotes an outdoor unit
• reference numerals 130a and 130b denote indoor units
• reference numerals 31a and 31b denote indoor heat exchangers
• reference numerals 32a and 32b denote
• the reference numeral 33a, 33b indicates a second electric expansion valve
• the reference numerals 34a, 34b indicate an indoor control device
• the reference numerals 141, 142 indicate connecting pipes.
• the control device 23 controls the second electric expansion valves 33a and 33b via the indoor control devices 34a and 34b.
• the second electric expansion valves 33a and 33b are accommodated in the indoor units 130a and 130b.
• the second electric expansion valves 33a and 33b may be accommodated in the outdoor unit 110.
• the force which is not particularly mentioned, is a supercooling heat exchanger (internal heat exchanger) between the receiver 16 and the second electric expansion valve 17. May be provided).
• the upper limit value UL1 and the lower limit value LL1 of the pressure of the intermediate pressure refrigerant in consideration of ensuring the temperature difference between the high and low pressures of the supercooling heat exchanger. In this way, an increase in the size of the supercooling heat exchanger can be avoided.
• the refrigeration cycle is as shown in FIG.
• the first electric expansion valve 15, the force receiver 16 and the second electric expansion valve 17 are arranged in the outdoor unit 10, and the arrangement of these is particularly It is not limited.
• the second electric expansion valve 17 may be disposed in the indoor unit 30.
• the electric expansion valve is employed as the refrigerant pressure reducing means, but an expander or the like may be employed instead.
• the force that is not particularly mentioned may be connected to the suction pipe of the liquid receiver 16 and the compressor 11 to form a gas vent circuit.
• the force which is not particularly mentioned, is any one between the refrigerant outflow side of the first electric expansion valve 15 and the refrigerant inflow side of the second electric expansion valve 17.
• An intermediate pressure sensor may be provided at the position.
• the control unit 23c determines that the value indicated by the high pressure sensor 21 falls between the upper limit value UL2 and the lower limit value LL2 of the pressure of the high pressure refrigerant obtained above and the value indicated by the intermediate pressure sensor.
• the opening of the first electric expansion valve 15 and the second electric expansion valve 17 is controlled so as to be between the upper limit value UL1 and the lower limit value LL1 of the intermediate pressure refrigerant.
• the force or force that is not particularly mentioned is provided between the low-temperature side (or liquid side) of the outdoor heat exchanger 13 and the temperature sensor 22 (refrigerant cooling heat exchanger ( An internal heat exchanger may also be provided.
• the refrigerant flowing out from the first electric expansion valve 15 can be prevented from being in the vicinity of the critical point. Therefore, the air conditioner 1 can perform stable liquid level control of the liquid receiver.
• the refrigeration apparatus according to the present invention has! / When the liquid level control of the receiver liquid can be stably performed, and is particularly useful for a refrigeration apparatus that employs carbon dioxide or the like as a refrigerant. .

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Chemical Kinetics & Catalysis (AREA)
• Air Conditioning Control Device (AREA)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

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Citations (5)

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• 2006
  • 2006-09-11 JP JP2006246154A patent/JP4811204B2/ja not_active Expired - Fee Related
• 2007
  • 2007-08-30 EP EP07806338.5A patent/EP2068095A4/en not_active Withdrawn
  • 2007-08-30 US US12/439,977 patent/US8171747B2/en not_active Expired - Fee Related
  • 2007-08-30 CN CN2007800332999A patent/CN101512244B/zh not_active Expired - Fee Related
  • 2007-08-30 WO PCT/JP2007/066861 patent/WO2008032581A1/ja not_active Ceased

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