[go: up one dir, main page]

WO2010064427A1 - Dispositif de réfrigération - Google Patents

Dispositif de réfrigération Download PDF

Info

Publication number
WO2010064427A1
WO2010064427A1 PCT/JP2009/006561 JP2009006561W WO2010064427A1 WO 2010064427 A1 WO2010064427 A1 WO 2010064427A1 JP 2009006561 W JP2009006561 W JP 2009006561W WO 2010064427 A1 WO2010064427 A1 WO 2010064427A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
compression mechanism
intermediate pressure
compression
pressure
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2009/006561
Other languages
English (en)
Japanese (ja)
Inventor
古井秀治
古庄和宏
森脇道雄
岩田育弘
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to KR1020117012681A priority Critical patent/KR101254433B1/ko
Priority to AU2009323588A priority patent/AU2009323588B2/en
Priority to US13/132,836 priority patent/US20110232325A1/en
Priority to EP09830197.1A priority patent/EP2357427A4/fr
Priority to CN200980148808.1A priority patent/CN102227599B/zh
Publication of WO2010064427A1 publication Critical patent/WO2010064427A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • 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
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way 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
    • 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
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators

Definitions

  • the present invention relates to a refrigeration apparatus that performs gas injection for supplying an intermediate-pressure gas refrigerant to a compressor.
  • a refrigeration apparatus that performs a vapor compression refrigeration cycle and performs so-called gas injection is known.
  • an intermediate-pressure gas refrigerant is introduced into a compression chamber in the middle of compression in a compressor.
  • Patent Document 1 discloses an air conditioner configured by a refrigeration apparatus that performs gas injection.
  • an intermediate cooler is provided in the refrigerant circuit (see FIG. 1).
  • the high-pressure liquid refrigerant flowing from the condenser (the indoor heat exchanger during heating operation) exchanges heat with the intermediate-pressure refrigerant generated by branching and expanding a part of the high-pressure liquid refrigerant.
  • coolant cooled in the intermediate cooler is supplied to an evaporator (outdoor heat exchanger at the time of heating operation).
  • the intermediate pressure refrigerant (intermediate pressure gas refrigerant) evaporated in the intermediate cooler is supplied to a compression chamber in the middle of compression in the compressor.
  • Patent Document 2 also discloses an air conditioner configured by a refrigeration apparatus that performs gas injection.
  • a gas-liquid separator is provided between two expansion valves.
  • the flowing intermediate pressure refrigerant is separated into a gas refrigerant and a liquid refrigerant.
  • the intermediate-pressure liquid refrigerant in the gas-liquid separator expands when passing through the expansion valve on the downstream side of the gas-liquid separator, and is then sent to the evaporator.
  • the intermediate-pressure gas refrigerant in the gas-liquid separator is supplied to a compression chamber in the middle of compression in the compressor.
  • Patent Document 3 discloses a refrigeration apparatus that performs a multistage compression refrigeration cycle.
  • a plurality of compressors are arranged in series, and the high-stage compressor sucks and further compresses the refrigerant discharged from the low-stage compressor.
  • the intermediate-pressure gas refrigerant is supplied to the pipe connecting the low-stage compressor and the high-stage compressor. Is done.
  • FIG. 2 of Patent Document 3 discloses a refrigerant circuit that performs a four-stage compression refrigeration cycle. In this refrigerant circuit, three types of intermediate-pressure gas refrigerants having different pressures are supplied to the pipes connecting the compressors of the respective stages.
  • the compressor compresses the low-pressure refrigerant sucked from the evaporator and the intermediate-pressure gas refrigerant introduced into the compression chamber in the middle of compression, and directs the compressed refrigerant to the condenser To discharge. Therefore, in this refrigerant circuit, the mass flow rate of the refrigerant in the condenser is larger than the mass flow rate of the refrigerant in the evaporator.
  • the mass flow rate of the refrigerant in the condenser increases, the amount of heat released by the refrigerant in the condenser (that is, the amount of heat released from the refrigerant) increases.
  • the mass flow rate of the intermediate-pressure gas refrigerant supplied to the compressor is increased, the mass flow rate of the refrigerant in the condenser can be increased without increasing the mass flow rate of the low-pressure refrigerant sucked from the evaporator by the compressor.
  • the pressure of the intermediate pressure gas refrigerant may be increased by increasing the pressure of the intermediate pressure gas refrigerant and flowing into the compression chamber.
  • the present invention has been made in view of the above points, and an object of the present invention is to secure both the amount of heat released from the refrigerant in the condenser and the amount of heat absorbed from the refrigerant in the evaporator in a refrigeration apparatus that performs gas injection. There is to make it.
  • the first invention includes a refrigerant circuit (5) having a radiator and an evaporator for performing a refrigeration cycle, a first compression mechanism (71) and a second compression mechanism (85, 95) formed in each of the refrigerant circuit (5).
  • a refrigeration system including a compression mechanism (72), wherein each of the first compression mechanism (71) and the second compression mechanism (72) sucks low-pressure refrigerant into the compression chamber (85, 95) and compresses it to a high pressure. Intended for equipment.
  • the refrigerant circuit (5) generates the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having a pressure lower than that of the first intermediate pressure gas refrigerant, so that the radiator to the evaporator.
  • a second injection passage (45) for supplying is provided.
  • Each of the second and third inventions includes a refrigerant circuit (5) having a radiator and an evaporator and performing a refrigeration cycle, and a first compression mechanism (71) in which a compression chamber (85, 95) is formed. ) And a second compression mechanism (72), the first compression mechanism (71) sucks and compresses the low-pressure refrigerant into the compression chamber (85), and the second compression mechanism (72)
  • a refrigeration system that sucks and compresses the refrigerant discharged from the first compression mechanism (71) into the compression chamber (95) is an object.
  • the refrigerant circuit (5) generates the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having a pressure lower than that of the first intermediate pressure gas refrigerant.
  • the enthalpy reducing means (20) for reducing the enthalpy of the refrigerant flowing from the evaporator toward the evaporator, and the first intermediate pressure gas refrigerant generated in the enthalpy reducing means (20) are supplied to the first compression mechanism (71).
  • the first injection passage (35) for supplying to the compression chamber (85) in the middle of compression and the second intermediate pressure gas refrigerant generated in the enthalpy reduction means (20) are compressed by the second compression mechanism (72).
  • a compression chamber (95) in the middle or a second injection passage (45) for supplying the compression chamber (95) to the suction side of the second compression mechanism (72) is provided.
  • the refrigerant circuit (5) generates the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having a pressure lower than that of the first intermediate pressure gas refrigerant.
  • the enthalpy reducing means (20) for reducing the enthalpy of the refrigerant flowing from the evaporator toward the evaporator, and the first intermediate pressure gas refrigerant generated in the enthalpy reducing means (20) are supplied to the second compression mechanism (72).
  • the first injection passage (35) for supplying to the suction side and the second intermediate pressure gas refrigerant generated in the enthalpy reducing means (20) are compressed in the compression chamber (95) during the compression of the second compression mechanism (72). ) Is provided with a second injection passage (45).
  • a single-stage compression refrigeration cycle is performed by circulating the refrigerant.
  • the refrigerant discharged from each compression mechanism (71, 72) dissipates heat in the radiator, then absorbs heat in the evaporator and evaporates, and then to each compression mechanism (71, 72). Inhaled.
  • a two-stage compression refrigeration cycle is performed by circulating the refrigerant.
  • the refrigerant discharged from the second compression mechanism (72) dissipates heat in the radiator, then absorbs heat in the evaporator and evaporates, and then is sucked into the first compression mechanism (71).
  • the refrigerant radiated by the radiator is supplied to the evaporator after the enthalpy is lowered by the enthalpy reducing means (20).
  • a first intermediate pressure gas refrigerant and a second intermediate pressure gas refrigerant having different pressures are generated.
  • This enthalpy reducing means (20) lowers the enthalpy of the refrigerant flowing from the radiator to the evaporator in the process of generating two types of intermediate pressure gas refrigerant.
  • the pressure of the second intermediate pressure gas refrigerant is lower than the pressure of the first intermediate pressure gas refrigerant, and therefore the temperature thereof is also lower than the temperature of the first intermediate pressure gas refrigerant. For this reason, the enthalpy of the refrigerant sent from the enthalpy reducing means (20) to the evaporator is lower than when only the first intermediate pressure gas refrigerant is generated in the enthalpy reducing means (20).
  • the compression mechanisms (71, 72) suck in the low-pressure refrigerant.
  • the first intermediate pressure gas refrigerant is introduced into the compression chamber (85) in the middle of compression of the first compression mechanism (71) through the first injection passage (35).
  • the first compression mechanism (71) compresses the low-pressure refrigerant and the first intermediate-pressure gas refrigerant flowing into the compression chamber (85), and discharges the compressed high-pressure refrigerant from the compression chamber (85).
  • the second intermediate pressure gas refrigerant is introduced into the compression chamber (95) in the middle of compression of the second compression mechanism (72) through the second injection passage (45).
  • the second compression mechanism (72) compresses the low-pressure refrigerant and the second intermediate-pressure gas refrigerant that have flowed into the compression chamber (95), and discharges the compressed high-pressure refrigerant from the compression chamber (95).
  • the refrigerant is further compressed in the second compression mechanism (72) after being compressed in the first compression mechanism (71).
  • the first intermediate pressure gas refrigerant is introduced into the compression chamber (85) in the middle of compression of the first compression mechanism (71) through the first injection passage (35).
  • the first compression mechanism (71) compresses the low-pressure refrigerant and the first intermediate-pressure gas refrigerant that have flowed into the compression chamber (85), and discharges the compressed refrigerant from the compression chamber (85).
  • the second compression mechanism (72) When the second intermediate pressure gas refrigerant is introduced from the second injection passage (45) into the compression chamber (95) in the middle of compression of the second compression mechanism (72), the second compression mechanism (72) The refrigerant discharged from the compression mechanism (71) and sucked into the compression chamber (95) and the second intermediate pressure gas refrigerant introduced into the compression chamber (95) from the second injection passage (45) are compressed and compressed. The subsequent high-pressure refrigerant is discharged from the compression chamber (95).
  • the second compression mechanism (72) is connected to the first compression mechanism (71 ) And the second intermediate pressure gas refrigerant supplied from the second injection passage (45) are sucked into the compression chamber (95) and compressed, and the compressed high-pressure refrigerant is compressed into the compression chamber (95). Discharge from.
  • the refrigerant is further compressed in the second compression mechanism (72) after being compressed in the first compression mechanism (71).
  • the first compression mechanism (71) compresses the low-pressure refrigerant flowing into the compression chamber (85), and discharges the compressed refrigerant from the compression chamber (85).
  • the second compression mechanism (72) sucks the refrigerant discharged from the first compression mechanism (71) and the first intermediate pressure gas refrigerant supplied from the first injection passage (35) into the compression chamber (95). .
  • the second intermediate pressure gas refrigerant is introduced into the compression chamber (95) in the middle of compression of the second compression mechanism (72) through the second injection passage (45).
  • the second compression mechanism (72) compresses the refrigerant sucked into the compression chamber (95) and the second intermediate pressure gas refrigerant introduced into the compression chamber (95) from the second injection passage (45), and after compression High pressure refrigerant is discharged from the compression chamber (95).
  • a portion of the refrigerant circuit (5) in the refrigerant circuit (5), a portion of the refrigerant circuit (5) from an outlet of the radiator to an inlet of the evaporator. Constitutes a main passage portion (7), while the enthalpy reduction means (20) is connected to the main passage portion (7) and a branch passage into which a part of the refrigerant flowing through the main passage portion (7) flows (21) and an expansion mechanism (22 for generating a first intermediate pressure refrigerant and a second intermediate pressure refrigerant having a pressure lower than that of the first intermediate pressure refrigerant by expanding the refrigerant flowing into the branch passage (21).
  • the refrigerant flowing through the main passage portion (7) connected to the downstream of the radiator in the main passage portion (7) and the first intermediate pressure refrigerant to exchange heat, the main passage portion (7)
  • the first intermediate A first heat exchanger (30) that generates a pressurized gas refrigerant, and is connected between the first heat exchanger (30) and the evaporator in the main passage portion (7) and flows through the main passage portion (7).
  • the second intermediate pressure gas refrigerant is generated by exchanging heat between the refrigerant and the second intermediate pressure refrigerant, cooling the refrigerant flowing through the main passage portion (7) and evaporating the second intermediate pressure refrigerant. 2 heat exchangers (40).
  • the branch passage (21), the expansion mechanism (22), the first heat exchanger (30), and the second heat exchanger (40) are provided in the enthalpy reducing means (20). .
  • the high-pressure refrigerant that has flowed into the branch passage (21) is expanded by the expansion mechanism (22), part of which becomes the first intermediate-pressure refrigerant and the rest becomes the second intermediate-pressure refrigerant.
  • the pressure and temperature of the second intermediate pressure refrigerant is lower than that of the first intermediate pressure refrigerant.
  • the first intermediate-pressure refrigerant and the high-pressure refrigerant flowing out of the radiator exchange heat.
  • the high-pressure refrigerant is cooled by the first intermediate-pressure refrigerant and its enthalpy is reduced.
  • the first intermediate-pressure refrigerant absorbs heat from the high-pressure refrigerant and evaporates.
  • a pressurized gas refrigerant is generated.
  • the first intermediate pressure gas refrigerant generated in the first heat exchanger (30) flows into the first injection passage (35).
  • the second intermediate pressure refrigerant and the high-pressure refrigerant flowing out of the first heat exchanger (30) exchange heat.
  • the high-pressure refrigerant is cooled by the second intermediate-pressure refrigerant and its enthalpy is reduced, while the second intermediate-pressure refrigerant absorbs heat from the high-pressure refrigerant and evaporates to cause the second intermediate pressure.
  • a pressurized gas refrigerant is generated.
  • the second intermediate pressure gas refrigerant generated in the second heat exchanger (40) flows into the second injection passage (45).
  • the branch passage (21) of the enthalpy reduction means (20) is provided between the radiator and the first heat exchanger (30) in the main passage portion (7).
  • a first branch pipe (33) connected to supply refrigerant flowing from the main passage portion (7) to the first heat exchanger (30), and a first heat exchanger (30 in the main passage portion (7)) )
  • the second heat exchanger (40) and a second branch pipe (43) for supplying the refrigerant flowing from the main passage portion (7) to the second heat exchanger (40).
  • the expansion mechanism (22) of the enthalpy reducing means (20) is provided with a first expansion valve (30) that generates the first intermediate pressure refrigerant by expanding the refrigerant that is provided in the first branch pipe (33) and flows in. 34) and the second intermediate pressure refrigerant by expanding the refrigerant flowing in the second branch pipe (43).
  • a first expansion valve (30) that generates the first intermediate pressure refrigerant by expanding the refrigerant that is provided in the first branch pipe (33) and flows in. 34) and the second intermediate pressure refrigerant by expanding the refrigerant flowing in the second branch pipe (43).
  • the branch passage (21) is constituted by the first branch pipe (33) and the second branch pipe (43), and the expansion mechanism (22) is the first expansion valve (34) and the second expansion valve.
  • the high-pressure refrigerant that has flowed into the first branch pipe (33) expands into the first intermediate-pressure refrigerant when passing through the first expansion valve (34), and is then supplied to the first heat exchanger (30). .
  • the supplied first intermediate pressure refrigerant evaporates to become a first intermediate pressure gas refrigerant.
  • the high-pressure refrigerant (that is, the first heat exchanger) flows through the main passage portion (7) from the first heat exchanger (30) toward the second heat exchanger (40). Part of the high-pressure refrigerant cooled in (30) flows in.
  • the high-pressure refrigerant that has flowed into the second branch pipe (43) expands into the second intermediate-pressure refrigerant when passing through the second expansion valve (44), and is then supplied to the second heat exchanger (40). .
  • the supplied second intermediate pressure refrigerant evaporates to become a second intermediate pressure gas refrigerant.
  • the branch passage (21) of the enthalpy reduction means (20) is provided between the radiator and the first heat exchanger (30) in the main passage portion (7).
  • an expansion mechanism (22) of the enthalpy reduction means (20) includes the second branch pipe (43) for supplying the refrigerant flowing in from the branch pipe (33) to the second heat exchanger (40).
  • a first expansion valve (34) that generates the first intermediate pressure refrigerant by expanding the refrigerant that has flowed into the first branch pipe (33) and the second branch pipe (43) flowed in.
  • the branch passage (21) is composed of the first branch pipe (33) and the second branch pipe (43), and the expansion mechanism (22) is the first expansion valve (34) and the second expansion valve.
  • Part of the high-pressure refrigerant that flows through the main passage portion (7) from the radiator toward the first heat exchanger (30) flows into the first branch pipe (33).
  • Part of the refrigerant flowing into the first branch pipe (33) is supplied to the first heat exchanger (30), and the rest flows into the second branch pipe (43) to enter the second heat exchanger (40). Supplied to.
  • the refrigerant supplied to the first heat exchanger (30) through the first branch pipe (33) expands to become the first intermediate pressure refrigerant when passing through the first expansion valve (34), and thereafter 1 is supplied to the heat exchanger (30).
  • the supplied first intermediate pressure refrigerant evaporates to become a first intermediate pressure gas refrigerant.
  • the refrigerant supplied to the second heat exchanger (40) through the second branch pipe (43) expands to become the second intermediate pressure refrigerant when passing through the second expansion valve (44), and thereafter To the second heat exchanger (40).
  • the supplied second intermediate pressure refrigerant evaporates to become a second intermediate pressure gas refrigerant.
  • the enthalpy reducing means (20) includes a first expansion valve (37) for expanding the high-pressure refrigerant flowing out from the radiator, A gas-liquid two-phase refrigerant flowing out from one expansion valve (37) is separated into a gas refrigerant and a liquid refrigerant, and the first refrigerant is supplied to the first injection passage (35) as the first intermediate pressure gas refrigerant.
  • the second gas-liquid separator (46) which separates the refrigerant in a state into a gas refrigerant and a liquid refrigerant, supplies the gas refrigerant as the second intermediate pressure gas refrigerant to the second injection passage (45), and supplies the liquid refrigerant to the evaporator. ).
  • the first expansion valve (37), the first gas-liquid separator (36), the second expansion valve (47), and the second gas-liquid separator (46) are enthalpy reducing means. (20) provided.
  • the first expansion valve (37), the first gas-liquid separator (36), the second expansion valve (47), and the second gas-liquid separator (46) are a radiator. Are arranged in order from the evaporator toward the evaporator.
  • the high-pressure refrigerant that has flowed out of the radiator expands into a gas-liquid two-phase state when passing through the first expansion valve (37), and then flows into the first gas-liquid separator (36). Then, it is separated into liquid refrigerant and gas refrigerant.
  • the gas refrigerant in the first gas-liquid separator (36) flows into the first injection passage (35) as the first intermediate pressure gas refrigerant.
  • the liquid refrigerant in the first gas-liquid separator (36) is in a saturated state, and its enthalpy is a gas-liquid two-phase sent from the first expansion valve (37) to the first gas-liquid separator (36). It is lower than the refrigerant in the state.
  • the liquid refrigerant in the first gas-liquid separator (36) expands into a gas-liquid two-phase state when passing through the second expansion valve (47), and then the second gas-liquid separation.
  • the gas refrigerant in the second gas-liquid separator (46) flows into the second injection passage (45) as the second intermediate pressure gas refrigerant.
  • the liquid refrigerant in the second gas-liquid separator (46) is in a saturated state, and its enthalpy is the gas-liquid two-phase sent from the second expansion valve (47) to the second gas-liquid separator (46). It is lower than the refrigerant in the state.
  • the liquid refrigerant in the second gas-liquid separator (46) is supplied to the evaporator.
  • the first compression mechanism (71) and the second compression mechanism (72) are provided in one compressor (50), and the compression is performed.
  • the machine (50) includes a single drive shaft (65) that engages with both the first compression mechanism (71) and the second compression mechanism (72).
  • both the first compression mechanism (71) and the second compression mechanism (72) are driven by a single drive shaft (65).
  • the first compression mechanism (71) is a first compressor (50a), and the second compression mechanism (72) is a second compression.
  • the first compressor (50a) is engaged with the first compression mechanism (71), and the second compression mechanism (72) is provided with the first compressor (50b).
  • the second drive shaft (65b) that engages with the two compression mechanism (72) is provided.
  • the first compression mechanism (71) is driven by the first drive shaft (65a), and the second compression mechanism (72) is driven by the second drive shaft (65b).
  • the first intermediate pressure gas refrigerant generated in the enthalpy reduction means (20) of the present invention has a higher pressure and density than the second intermediate pressure gas refrigerant.
  • the second intermediate pressure gas refrigerant is supplied to the second compression mechanism (72), while the first compression mechanism (71) is supplied more than the second intermediate pressure gas refrigerant.
  • a first intermediate-pressure gas refrigerant having a high pressure and density is supplied. Therefore, according to the present invention, the mass flow rate of the refrigerant discharged from the compressor (50) can be increased as compared with the case where only the second intermediate pressure gas refrigerant is supplied to each compression mechanism (71, 72). it can.
  • the 1st intermediate pressure gas refrigerant and the 2nd intermediate pressure gas refrigerant are introduce
  • the mass flow rate of the refrigerant does not increase, and only the mass flow rate of the refrigerant discharged from the compressor (50) toward the radiator increases. Therefore, according to the present invention, it is possible to increase the mass flow rate of the refrigerant discharged from the compressor (50) while suppressing an increase in energy required for driving the compressor (50).
  • the amount of heat released to the target object that is, the amount of heat released from the refrigerant) can be increased.
  • the enthalpy reducing means (20) generates not only the first intermediate pressure gas refrigerant but also the second intermediate pressure gas refrigerant having a lower pressure and temperature than the first intermediate pressure gas refrigerant. For this reason, according to the present invention, the enthalpy of the refrigerant sent from the enthalpy reducing means (20) to the evaporator is lowered as compared with the case where only the first intermediate pressure gas refrigerant is generated in the enthalpy reducing means (20). Can do. As a result, the amount of heat absorbed by the refrigerant from the object such as air (that is, the amount of heat absorbed by the refrigerant) in the evaporator can be increased.
  • the present invention it is possible to increase the heat dissipation amount of the refrigerant in the radiator by increasing the mass flow rate of the refrigerant in the radiator, and further reduce the enthalpy of the refrigerant flowing into the evaporator. As a result, the amount of heat absorbed by the refrigerant in the evaporator can be increased. Therefore, according to the present invention, it is possible to achieve both the securing of the heat radiation amount of the refrigerant in the radiator and the securing of the heat absorption amount of the refrigerant in the evaporator.
  • an intermediate-pressure gas refrigerant is supplied between the compressors of each stage. That is, for example, in a refrigerant circuit that performs a three-stage compression refrigeration cycle, an intermediate pressure gas is provided between the first-stage compressor and the second-stage compressor, and between the second-stage compressor and the third-stage compressor. The refrigerant will be supplied.
  • the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having different pressures are generated in the enthalpy reduction means (20).
  • a “three-stage compression refrigeration cycle is performed using three compression mechanisms, and the second intermediate-pressure gas refrigerant is passed between the first-stage compression mechanism and the second-stage compression mechanism. It is technically possible to employ a configuration in which the first intermediate-pressure gas refrigerant is supplied between the compression mechanism of the eye and the compression mechanism of the third stage.
  • the three-stage compression refrigeration cycle is performed when the difference between the low pressure and the high pressure of the refrigeration cycle is large and only a low COP (coefficient of performance) is obtained in the two-stage compression refrigeration cycle or the single-stage compression refrigeration cycle.
  • the present invention achieves the purpose of “to achieve both the securing of the heat radiation amount of the refrigerant in the radiator and the securing of the heat absorption amount of the refrigerant in the evaporator” in order to achieve “the enthalpy of the refrigerant flowing toward the evaporator”.
  • the enthalpy reduction means (20) for reducing the pressure of the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having different pressures is employed.
  • “the difference between the low pressure and the high pressure of the refrigeration cycle is not so large and a sufficiently high COP can be obtained even in a two-stage compression refrigeration cycle or a single-stage compression refrigeration cycle”.
  • the compression mechanism that compresses the refrigerant is usually composed of a plurality of members, mechanical loss such as friction loss between the members occurs in the compression mechanism. Therefore, the greater the number of compression mechanisms, the greater the total mechanical loss that occurs in each compression mechanism. Further, when the number of compression mechanisms provided in the refrigeration apparatus increases, the manufacturing cost of the refrigeration apparatus increases.
  • the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant generated in the enthalpy reduction means (20) are compressed by the compression mechanism (71 , 72).
  • the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant generated by the enthalpy reduction means (20) are compressed. Inhaled into mechanism (71, 72).
  • the first intermediate pressure gas refrigerant and the second intermediate pressure generated in the enthalpy reduction means (20) are also provided.
  • the pressurized gas refrigerant can be sucked into the compression mechanism (71, 72). Therefore, according to the present invention, the treatment of the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant generated in the enthalpy reduction means (20) despite the difference between the low pressure and the high pressure of the refrigeration cycle is not so large.
  • a three-stage compression refrigeration cycle is performed only for the purpose, and problems such as an increase in mechanical loss and an increase in manufacturing cost due to an increase in the compression mechanism can be solved.
  • the enthalpy reduction means (20) is provided with the first heat exchanger (30) and the second heat exchanger (40).
  • the first heat exchanger (30) the high-pressure refrigerant flowing out of the radiator is cooled by the first intermediate-pressure refrigerant, and in the second heat exchanger (40), it is cooled in the first heat exchanger (30).
  • the high pressure refrigerant is further cooled by the second intermediate pressure refrigerant. Therefore, according to the present invention, the enthalpy of the refrigerant sent from the radiator to the evaporator can be reliably lowered in the process of generating the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant.
  • the enthalpy reducing means (20) is provided with the first gas-liquid separator (36) and the second gas-liquid separator (46).
  • the first gas-liquid separator (36) is only a saturated liquid refrigerant having a lower enthalpy than the gas-liquid two-phase refrigerant supplied from the first expansion valve (37) to the first gas-liquid separator (36).
  • the second gas-liquid separator (46) is a saturated liquid refrigerant having a lower enthalpy than the refrigerant in the gas-liquid two-phase state supplied from the second expansion valve (47) to the second gas-liquid separator (46). Only to the evaporator. Therefore, according to the present invention, the enthalpy of the refrigerant sent from the radiator to the evaporator can be reliably lowered in the process of generating the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant.
  • FIG. 1 is a refrigerant circuit diagram illustrating the configuration of the air conditioner according to the first embodiment.
  • FIG. 2 is a longitudinal sectional view of the compressor according to the first embodiment.
  • 3A and 3B are cross-sectional views of a main part of the compressor according to the first embodiment, in which FIG. 3A shows a cross-section of the first compression mechanism, and FIG. 3B shows a cross-section of the second compression mechanism.
  • FIG. 4 is a Mollier diagram (pressure-enthalpy diagram) showing a refrigeration cycle performed in the refrigerant circuit of the first embodiment.
  • FIG. 5 is a refrigerant circuit diagram illustrating a configuration of the air conditioner of the second embodiment.
  • FIG. 6 is a Mollier diagram (pressure-enthalpy diagram) showing a refrigeration cycle performed in the refrigerant circuit of the second embodiment.
  • FIG. 7 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to Modification 1 of Embodiment 2.
  • FIG. 8 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a second modification of the second embodiment.
  • FIG. 9 is a Mollier diagram (pressure-enthalpy diagram) showing a refrigeration cycle performed in the refrigerant circuit of Modification 2 of Embodiment 2.
  • FIG. 10 is a refrigerant circuit diagram illustrating a configuration of the air conditioner of the third embodiment.
  • FIG. 11 is a Mollier diagram (pressure-enthalpy diagram) showing a refrigeration cycle performed in the refrigerant circuit of the third embodiment.
  • FIG. 12 is a schematic perspective view illustrating a configuration of a heat exchange member according to a first modification of the other embodiment.
  • FIG. 13 is a schematic side view which shows the structure of the member for heat exchange of the 1st modification of other embodiment.
  • FIG. 14 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a second modification of the other embodiment.
  • FIG. 15 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a third modification of the other embodiment.
  • FIG. 12 is a schematic perspective view illustrating a configuration of a heat exchange member according to a first modification of the other embodiment.
  • FIG. 13 is a schematic side view which shows the structure of the member for heat exchange of the 1st modification of other embodiment.
  • FIG. 14 is a refrigerant circuit diagram illustrating a configuration of an air
  • FIG. 16 is a Mollier diagram (pressure-enthalpy diagram) showing a refrigeration cycle performed in the refrigerant circuit of the third modified example of the other embodiment.
  • FIG. 17 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a fourth modification of the other embodiment.
  • FIG. 18 is a Mollier diagram (pressure-enthalpy diagram) showing a refrigeration cycle performed in the refrigerant circuit of the fourth modified example of the other embodiment.
  • FIG. 19 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a fourth modification of the other embodiment.
  • FIG. 20 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a fifth modification of the other embodiment.
  • FIG. 21 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a fifth modification of the other embodiment.
  • FIG. 22 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to a fifth modification of the other embodiment.
  • Embodiment 1 of the Invention A first embodiment of the present invention will be described.
  • the present embodiment is an air conditioner (1) configured by a refrigeration apparatus.
  • the air conditioner (1) of the present embodiment includes a refrigerant circuit (5).
  • the refrigerant circuit (5) is a closed circuit filled with a refrigerant, and performs a vapor compression refrigeration cycle by circulating the refrigerant.
  • This refrigerant circuit (5) is composed of 2,3,3,3-tetrafluoro-1-propene (HFO-1234yf), which is a high boiling point component, and HFC-32 (difluoromethane), which is a low boiling point component.
  • HFO-1234yf 2,3,3,3-tetrafluoro-1-propene
  • HFC-32 difluoromethane
  • the refrigerant circuit (5) includes a compressor (50), a four-way switching valve (11), an outdoor heat exchanger (12), a bridge circuit (15), and an indoor heat exchanger. (14) is provided.
  • the compressor (50) has its discharge pipe (52) connected to the first port of the four-way switching valve (11) and its suction pipe (53, 54) connected to the second port of the four-way switching valve (11). It is connected.
  • the outdoor heat exchanger (12) has a gas side end connected to the third port of the four-way switching valve (11) and a liquid side end connected to the bridge circuit (15).
  • the indoor heat exchanger (14) has a gas side end connected to the fourth port of the four-way switching valve (11) and a liquid side end connected to the bridge circuit (15).
  • Compressor (50) is a hermetic rotary compressor.
  • a drive shaft (65) connecting the part (70) and the electric motor (60) is accommodated in the casing (51). Details of the compressor (50) will be described later.
  • the four-way selector valve (11) includes a first state (state indicated by a solid line in FIG. 1) in which the first port communicates with the third port and the second port communicates with the fourth port; The state is switched to a second state (state indicated by a broken line in FIG. 1) in which the port communicates with the fourth port and the second port communicates with the third port.
  • the outdoor heat exchanger (12) exchanges heat between the outdoor air and the refrigerant.
  • the indoor heat exchanger (14) exchanges heat between the indoor air and the refrigerant.
  • the bridge circuit (15) has four check valves (16 to 19).
  • the outflow side of the first check valve (16) and the outflow side of the second check valve (17) are connected, and the inflow side of the second check valve (17) and the third check valve are connected.
  • the outflow side of the valve (18) is connected, the inflow side of the third check valve (18) and the inflow side of the fourth check valve (19) are connected, and the outflow side of the fourth check valve (19)
  • the inflow side of the check valve (16) is connected.
  • the liquid side end of the outdoor heat exchanger (12) is connected between the fourth check valve (19) and the first check valve (16), and the second check valve
  • the liquid side end of the indoor heat exchanger (14) is connected between (17) and the third check valve (18).
  • the refrigerant circuit (5) is provided with a one-way flow pipe (6).
  • the one-way flow pipe (6) has an inlet end connected between the first check valve (16) and the second check valve (17) of the bridge circuit (15), and an outlet end connected to the bridge circuit ( 15) connected between the third check valve (18) and the fourth check valve (19).
  • the refrigerant In the one-way flow pipe (6), the refrigerant always flows from the inlet end toward the outlet end.
  • the bridge circuit (15) and the one-way flow pipe (6) constitute the main passage portion (7).
  • the one-way flow pipe (6) includes, in order from the inlet end to the outlet end, a first heat exchanger (30), a second heat exchanger (40), and a main expansion valve (13). It is connected.
  • the main expansion valve (13) is a so-called electronic expansion valve.
  • Each of the first heat exchanger (30) and the second heat exchanger (40) includes a high pressure side flow path (31, 41) and an intermediate pressure side flow path (32, 42), and a high pressure side flow path (31 , 41) and the refrigerant flowing through the intermediate pressure side flow path (32, 42) are configured to exchange heat.
  • pressure side flow path (31, 41) is connected to the one-way flow pipe (6).
  • the first branch pipe (33) and the first injection pipe (35) are connected to the intermediate pressure side flow path (32) of the first heat exchanger (30).
  • the first branch pipe (33) has one end connected to the upstream side of the first heat exchanger (30) in the one-way flow pipe (6) and the other end connected to the intermediate pressure side of the first heat exchanger (30).
  • the first branch pipe (33) is provided with a first expansion valve (34) made up of a so-called electronic expansion valve.
  • the first expansion valve (34) generates a first intermediate pressure refrigerant by expanding the high-pressure refrigerant that has flowed from the one-way flow pipe (6) into the first branch pipe (33).
  • One end of the first injection pipe (35) is connected to the outlet end of the intermediate pressure side flow path (32) of the first heat exchanger (30), and the other end is connected to the first compression mechanism (71 of the compressor (50)). )It is connected to the.
  • the second branch pipe (43) and the second injection pipe (45) are connected to the intermediate pressure side flow path (42) of the second heat exchanger (40).
  • One end of the second branch pipe (43) is connected between the first heat exchanger (30) and the second heat exchanger (40) in the one-way flow pipe (6), and the other end is the second heat. It is connected to the inlet end of the intermediate pressure side channel (42) of the exchanger (40).
  • the second branch pipe (43) is provided with a second expansion valve (44) made of a so-called electronic expansion valve.
  • the second expansion valve (44) generates a second intermediate pressure refrigerant by expanding the high-pressure refrigerant that has flowed from the one-way flow pipe (6) into the second branch pipe (43).
  • the second injection pipe (45) has one end connected to the outlet end of the intermediate pressure side flow path (42) of the second heat exchanger (40) and the other end connected to the second compression mechanism (72) of the compressor (50). )It is connected to the.
  • the first heat exchanger (30), the first branch pipe (33), the first expansion valve (34), the second heat exchanger (40), the second branch pipe ( 43) and the second expansion valve (44) constitute enthalpy reducing means (20) for reducing the enthalpy of the refrigerant flowing through the one-way flow pipe (6).
  • the first branch pipe (33) and the second branch pipe (43) constitute a branch passage (21), and the first expansion valve (34) and the second expansion valve (44). Constitutes an expansion mechanism (22).
  • the first injection pipe (35) constitutes a first injection passage
  • the second injection pipe (45) constitutes a second injection passage.
  • the compressor (50) includes a casing (51), a main body (70), an electric motor (60), and a drive shaft (65).
  • the casing (51) is formed in a vertically long hollow cylindrical shape whose both ends are closed.
  • the electric motor (60) is disposed above the main body (70).
  • the discharge pipe (52) is provided in the top part of the casing (51) so that a casing (51) may be penetrated.
  • the electric motor (60) includes a stator (61) and a rotor (62).
  • the stator (61) is fixed to the upper part of the body of the casing (51).
  • the rotor (62) is disposed inside the stator (61).
  • the drive shaft (65) includes a main shaft portion (68), a first eccentric portion (66), and a second eccentric portion (67).
  • the main shaft portion (68) is connected to the rotor (62) at a portion near its upper end.
  • the first eccentric part (66) and the second eccentric part (67) are formed near the lower end of the main shaft part (68).
  • the first eccentric portion (66) is disposed above the second eccentric portion (67).
  • Each of the first eccentric portion (66) and the second eccentric portion (67) has an outer diameter larger than the outer diameter of the main shaft portion (68), and each has an outer diameter relative to the axial center of the main shaft portion (68).
  • the first eccentric part (66) and the second eccentric part (67) have opposite eccentric directions with respect to the axis of the main shaft part (68).
  • the main shaft portion (68) has an oil supply passageway (69) extending upward from the lower end thereof.
  • the main body (70) includes a front head (73), a first cylinder (81), an intermediate plate (75), a second cylinder (91), and a rear head (74). It constitutes a rotary fluid machine.
  • the rear head (74), the second cylinder (91), the intermediate plate (75), the first cylinder (81), and the front head (73) are laminated in order from the bottom to the top. Are fastened to each other by bolts not shown.
  • the first piston (82) is accommodated in the first cylinder (81), and the second piston (92) is accommodated in the second cylinder (91).
  • Each piston (82, 92) is formed in a slightly thick cylindrical shape with a low height.
  • the first eccentric part (66) is inserted through the first piston (82), and the second eccentric part (67) is inserted through the second piston (92).
  • Each piston (82, 92) is integrally formed with a flat blade (83, 93) protruding from the outer peripheral surface thereof.
  • the blade (83) formed integrally with the first piston (82) is supported by the first cylinder (81) via a pair of bushes (84).
  • the blade (93) formed integrally with the second piston (92) is supported by the second cylinder (91) via a pair of bushes (94).
  • a first compression chamber (85) is formed between the inner peripheral surface and the outer peripheral surface of the first piston (82). Is done.
  • the first compression chamber (85) is partitioned into a low pressure side and a high pressure side by a blade (83).
  • a second compression chamber (95) is formed between the inner peripheral surface and the outer peripheral surface of the second piston (92).
  • the second compression chamber (95) is partitioned into a low pressure side and a high pressure side by a blade (93).
  • a first suction port (86) is formed in the first cylinder (81). Further, a second suction port (96) is formed in the second cylinder (91). In each cylinder (81, 91), the suction port (86, 96) penetrates the cylinder (81, 91) in the radial direction. Further, each suction port (86, 96) opens in the vicinity of the right side of the blade (83, 93) in FIG. 3 on the inner peripheral surface of the cylinder (81, 91). A first suction pipe (53) is inserted into the first suction port (86), and a second suction pipe (54) is inserted into the second suction port (96). Each suction pipe (53, 54) extends to the outside of the casing (51).
  • the first discharge port (87) is formed in the front head (73).
  • the first discharge port (87) passes through the front head (73).
  • the front head (73) is provided with a first discharge valve (88) for opening and closing the first discharge port (87).
  • the second discharge port (97) is formed in the rear head (74).
  • the second discharge port (97) passes through the rear head (74).
  • the rear head (74) is provided with a second discharge valve (98) for opening and closing the second discharge port (97).
  • the first injection port (89) is formed in the intermediate plate (75).
  • the first injection port (89) has one end opened on the upper surface of the intermediate plate (75) and the other end opened on the outer surface of the intermediate plate (75).
  • a first injection pipe (35) is inserted into the other end of the first injection port (89).
  • the second injection port (99) is formed in the rear head (74). One end of the second injection port (99) opens to the front surface (upper surface) of the rear head (74), and the other end opens to the outer surface of the rear head (74). On the front surface of the rear head (74), one end of the second injection port (99) opens to a portion facing the second compression chamber (95). A second injection pipe (45) is inserted into the other end of the second injection port (99).
  • the front head (73), the first cylinder (81), the intermediate plate (75), the first piston (82), and the blade (83) A first compression mechanism (71) forming the first compression chamber (85) is configured.
  • the rear head (74), the second cylinder (91), the intermediate plate (75), the second piston (92), and the blade (93) define the second compression chamber (95).
  • a second compression mechanism (72) is formed.
  • the air conditioner (1) of the present embodiment performs switching between cooling operation and heating operation.
  • the four-way switching valve (11) is set to the first state (the state indicated by the solid line in FIG. 1), and the first expansion valve (34), the second expansion valve (44), and the main expansion valve (13). The degree of opening is appropriately adjusted.
  • the compressor (50) is driven in this state, in the refrigerant circuit (5), the refrigerant circulates as shown by the solid line arrow in FIG. 1, and the vapor compression refrigeration cycle is performed.
  • the outdoor heat exchanger (12) operates as a condenser (that is, a radiator), and the indoor heat exchanger (14) operates as an evaporator.
  • the refrigerant discharged from the compressor (50) flows into the outdoor heat exchanger (12) through the four-way switching valve (11), dissipates heat to the outdoor air, and condenses. Thereafter, the refrigerant flows into the one-way flow pipe (6) through the first check valve (16) of the bridge circuit (15).
  • the first heat exchanger (30) the high-pressure refrigerant flowing through the high-pressure side flow path (31) is cooled, and the first intermediate-pressure refrigerant flowing through the intermediate pressure-side flow path (32) evaporates to form the first intermediate pressure gas refrigerant and become.
  • the first intermediate-pressure gas refrigerant is sent to the compressor (50) through the first injection pipe (35).
  • the high-pressure refrigerant that has flowed into the second branch pipe (43) expands to become the second intermediate-pressure refrigerant when passing through the second expansion valve (44), and then the intermediate-pressure side stream of the second heat exchanger (40). It flows into the road (32).
  • the high-pressure refrigerant flowing through the high-pressure side flow path (41) is cooled, and the second intermediate-pressure refrigerant flowing through the intermediate pressure-side flow path (42) is evaporated to form the second intermediate pressure gas refrigerant and Become.
  • the second intermediate-pressure gas refrigerant is sent to the compressor (50) through the second injection pipe (45).
  • the high-pressure refrigerant that has flowed out of the high-pressure channel (41) of the second heat exchanger (40) expands to become a low-pressure refrigerant when passing through the main expansion valve (13).
  • This low-pressure refrigerant flows into the indoor heat exchanger (14) through the third check valve (18) of the bridge circuit (15), absorbs heat from the indoor air, and evaporates. Thereafter, the refrigerant passes through the four-way switching valve (11) 1 and is sucked into the main body (70) of the compressor (50).
  • the indoor heat exchanger (14) the indoor air is cooled by heat exchange with the refrigerant, and the cooled indoor air is sent back into the room.
  • Air conditioner heating operation The operation of the air conditioner (1) during the heating operation will be described with reference to FIG.
  • the four-way switching valve (11) is set to the second state (the state indicated by the broken line in FIG. 1), and the first expansion valve (34), the second expansion valve (44), and the main expansion valve (13). The degree of opening is appropriately adjusted.
  • the compressor (50) is driven in this state, in the refrigerant circuit (5), the refrigerant circulates as shown by the dashed arrows in FIG. 1, and a vapor compression refrigeration cycle is performed.
  • the indoor heat exchanger (14) operates as a condenser (that is, a radiator), and the outdoor heat exchanger (12) operates as an evaporator.
  • the refrigerant discharged from the compressor (50) flows into the indoor heat exchanger (14) through the four-way switching valve (11), dissipates heat to the indoor air, and condenses. Thereafter, the refrigerant flows into the one-way flow pipe (6) through the second check valve (17) of the bridge circuit (15). In the indoor heat exchanger (14), the indoor air is heated by heat exchange with the refrigerant, and the heated indoor air is sent back into the room.
  • the first heat exchanger (30) the high-pressure refrigerant flowing through the high-pressure side flow path (31) is cooled, and the first intermediate-pressure refrigerant flowing through the intermediate pressure-side flow path (32) evaporates to form the first intermediate pressure gas refrigerant and become.
  • the first intermediate-pressure gas refrigerant is sent to the compressor (50) through the first injection pipe (35).
  • the high-pressure refrigerant that has flowed into the second branch pipe (43) expands to become the second intermediate-pressure refrigerant when passing through the second expansion valve (44), and then the intermediate-pressure side stream of the second heat exchanger (40). It flows into the road (32).
  • the high-pressure refrigerant flowing through the high-pressure side flow path (41) is cooled, and the second intermediate-pressure refrigerant flowing through the intermediate pressure-side flow path (42) is evaporated to form the second intermediate pressure gas refrigerant and Become.
  • the second intermediate-pressure gas refrigerant is sent to the compressor (50) through the second injection pipe (45).
  • the high-pressure refrigerant that has flowed out of the high-pressure channel (41) of the second heat exchanger (40) expands to become a low-pressure refrigerant when passing through the main expansion valve (13).
  • This low-pressure refrigerant flows into the outdoor heat exchanger (12) through the fourth check valve (19) of the bridge circuit (15), absorbs heat from the outdoor air, and evaporates. Thereafter, the refrigerant is sucked into the main body (70) of the compressor (50) through the four-way switching valve (11).
  • the low-pressure refrigerant is sucked into the first compression chamber (85) through the first suction port (86).
  • the closed first compression chamber (85) blocked from the first suction port (86) the refrigerant is compressed as the first piston (82) moves.
  • the first intermediate pressure gas refrigerant is introduced into the closed first compression chamber (85) through the first injection pipe (35) and the first injection port (89).
  • the first compression mechanism (71) compresses the refrigerant sucked into the first compression chamber (85), and discharges the compressed high-pressure refrigerant from the first discharge port (87) to the internal space of the casing (51). .
  • the low-pressure refrigerant is sucked into the second compression chamber (95) through the second suction port (96).
  • the refrigerant is compressed as the second piston (92) moves.
  • the second intermediate pressure gas refrigerant is introduced into the closed second compression chamber (95) through the second injection pipe (45) and the second injection port (99).
  • the second compression mechanism (72) compresses the refrigerant sucked into the second compression chamber (95), and discharges the compressed high-pressure refrigerant from the second discharge port (97) to the internal space of the casing (51). .
  • High-pressure refrigerant is discharged from the first compression mechanism (71) and the second compression mechanism (72) into the internal space of the casing (51).
  • the high-pressure refrigerant discharged from each compression mechanism (71, 72) flows upward in the internal space of the casing (51), and is sent out to the outside of the casing (51) through the discharge pipe (52).
  • refrigerating machine oil accumulates at the bottom.
  • This refrigerating machine oil flows into the oil supply passageway (69) opened at the lower end of the drive shaft (65), is supplied to the compression mechanisms (71, 72), and is used for lubricating the sliding portion.
  • evaporator refers to the outdoor heat exchanger (12) and the indoor heat exchanger (14) that operate as an evaporator (that is, indoor heat during cooling operation).
  • the exchanger (14) refers to the outdoor heat exchanger (12) during heating operation.
  • the “condenser” is the evaporator of the outdoor heat exchanger (12) and the indoor heat exchanger (14). The one that is operating (that is, the outdoor heat exchanger (12) during the cooling operation, and the indoor heat exchanger (14) during the heating operation).
  • m i1 be the mass flow rate of the high-pressure refrigerant flowing into the first branch pipe (33).
  • High-pressure refrigerant flowing into the first branch pipe (33), the pressure and expands while passing through the first expansion valve (34) is decreased from P H to P M1, the state of the point F (gas-liquid two-phase State) first intermediate pressure refrigerant.
  • the high-pressure refrigerant flowing through the high-pressure side flow path (31) is cooled, and the first intermediate-pressure refrigerant flowing through the intermediate pressure-side flow path (32) evaporates to form the first intermediate pressure gas refrigerant and Become.
  • coolant which the enthalpy fell and became the state of the point H flows out from the high voltage
  • the first intermediate pressure gas refrigerant in the state of point G flows out from the intermediate pressure side flow path (32) of the first heat exchanger (30).
  • the first intermediate-pressure gas refrigerant in the pressure P M1 is sent to the compressor (50) through the first injection pipe (35).
  • the mass flow rate of the first intermediate-pressure gas refrigerant supplied to the compressor (50) is m i1 .
  • the second intermediate pressure refrigerant in the state of point I is lower in pressure, specific enthalpy, and temperature than the first intermediate pressure refrigerant in the state of point F.
  • the second intermediate pressure refrigerant flows into the intermediate pressure side flow path (32) of the second heat exchanger (40).
  • the high-pressure refrigerant flowing through the high-pressure side flow path (41) is cooled, and the second intermediate-pressure refrigerant flowing through the intermediate pressure-side flow path (42) is evaporated to form the second intermediate pressure gas refrigerant and Become.
  • coolant which the enthalpy fell and became the state of the point K flows out from the high voltage
  • the second intermediate pressure gas refrigerant in the state of point J flows out from the intermediate pressure side flow path (42) of the second heat exchanger (40).
  • the second intermediate-pressure gas refrigerant in the pressure P M2 is sent to the compressor (50) through the second injection pipe (45).
  • the mass flow rate of the second intermediate-pressure gas refrigerant supplied to the compressor (50) is m i2 .
  • This low-pressure refrigerant flows into the evaporator, absorbs heat from the air, evaporates and reaches the state of point A, and is then sucked into the compressor (50).
  • the compressor (50) the refrigerant at the point A is sucked into the first compression chamber (85) of the first compression mechanism (71) and the second compression chamber (95) of the second compression mechanism (72). It is.
  • the refrigerant sucked into the first compression chamber (85) is compressed, and the refrigerant in the first compression chamber (85) is changed from the state of point A to the point B. It changes toward the state.
  • the first intermediate pressure gas refrigerant in the state of point G is introduced from the first injection port (89) into the first compression chamber (85) in the middle of compression, which is in a closed state.
  • the refrigerant flowing into the first compression chamber (85) in the state of point A and being compressed, and the first state of the point G flowing in from the first injection port (89). 1 intermediate-pressure gas refrigerant is mixed, and the mixed refrigerant is compressed to a point D state.
  • the second compression mechanism (72) of the compressor (50) the refrigerant sucked into the second compression chamber (95) is compressed, and the refrigerant in the second compression chamber (95) It changes toward the state of point B ′.
  • the second intermediate pressure gas refrigerant in the state of point J is introduced from the second injection port (99) into the second compression chamber (95) in the middle of compression, which is in a closed state.
  • the intermediate-pressure gas refrigerant is mixed, and the mixed refrigerant is compressed to a point D state.
  • the main body portion of the compressor (50) (70) includes a low-pressure refrigerant sent from the evaporator (mass flow rate m e), the first intermediate-pressure gas refrigerant supplied through the first injection pipe (35) (Mass flow rate m i1 ) and second intermediate pressure gas refrigerant (mass flow rate m i2 ) supplied through the second injection pipe (45) are sucked and compressed.
  • the first intermediate pressure gas refrigerant is generated in the first heat exchanger (30), and the second intermediate pressure is generated in the second heat exchanger (40). Gas refrigerant is generated. Further, the first intermediate pressure gas refrigerant has a higher pressure and density than the first intermediate pressure gas refrigerant.
  • the second intermediate pressure gas refrigerant is supplied to the second compression mechanism (72) of the compressor (50), while the compressor (50 The first intermediate pressure gas refrigerant having higher pressure and density than the second intermediate pressure gas refrigerant is supplied to the first compression mechanism (71). Therefore, according to this embodiment, only the second intermediate-pressure gas refrigerant into the compression mechanisms (71, 72) as compared with the case of supplying, increasing the mass flow rate m c of refrigerant discharged from the compressor (50) Can be made.
  • the first intermediate pressure gas refrigerant is introduced into the compression chamber (85) in the middle of the compression of the first compression mechanism (71), and the compression of the second compression mechanism (72).
  • the second intermediate pressure gas refrigerant is introduced into the compression chamber (95) in the middle. Therefore, increase without increasing the mass flow rate m e of the low-pressure refrigerant sucked from the evaporator into the compressor (50), only the mass flow rate m c of refrigerant discharged toward the condenser from the compressor (50) Can be made.
  • the rotational speed of the compression mechanism (71, 72) provided in the compressor (50) (that is, the drive for driving the piston (82, 92) of each compression mechanism (71, 72).
  • the mass flow rate of the refrigerant discharged from the compressor (50) can be increased without increasing the rotational speed of the shaft (65).
  • the mass flow rate of the refrigerant discharged from the compressor (50) can be increased while suppressing the increase in power consumed by the electric motor (60) of the compressor (50), and the refrigerant is discharged into the air in the condenser.
  • the amount of heat ie, the amount of heat released from the refrigerant
  • the high-pressure refrigerant is cooled by exchanging heat with the first intermediate-pressure refrigerant in the first heat exchanger (30), and the first heat exchange is performed.
  • the high-pressure refrigerant cooled in the vessel (30) is further cooled by exchanging heat with the second intermediate-pressure refrigerant (that is, refrigerant having a lower pressure and temperature than the first intermediate-pressure refrigerant) in the second heat exchanger (40). Is done.
  • coolant which flows in into an evaporator can be made low compared with the case where the high pressure refrigerant
  • coolant As a result, the amount of heat absorbed by the refrigerant from the air in the evaporator (that is, the amount of heat absorbed by the refrigerant) can be increased.
  • the heat dissipation amount of the refrigerant in the condenser can be increased by increasing the mass flow rate of the refrigerant in the condenser, and further, the enthalpy of the refrigerant flowing into the evaporator is reduced. By doing so, the amount of heat absorbed by the refrigerant in the evaporator can be increased. That is, according to the present embodiment, it is possible to ensure both the heat radiation amount of the refrigerant in the condenser and the heat absorption amount of the refrigerant in the evaporator.
  • the heating capacity of the air conditioner (1) that is, the refrigerant in the indoor heat exchanger (14) operating as a condenser
  • the amount of heat released to the room air and the cooling capacity of the air conditioner (1) (that is, the refrigerant is absorbed from the room air in the indoor heat exchanger (14) operating as an evaporator).
  • the amount of heat generated can be increased.
  • the enthalpy of the refrigerant flowing into the evaporator can be lowered. For this reason, the mass flow rate of the refrigerant in the evaporator can be reduced while maintaining the heat absorption amount of the refrigerant in the evaporator.
  • the mass flow rate of the refrigerant in the evaporator decreases, the flow rate of the refrigerant in the evaporator decreases, and the pressure loss of the refrigerant while passing through the evaporator decreases.
  • the pressure loss of the refrigerant in the evaporator decreases, the pressure of the low-pressure refrigerant sucked into the compressor (50) increases by the reduction in the pressure loss in the evaporator and is consumed in the motor (60) of the compressor (50). Electric power decreases. Therefore, according to the present embodiment, the power consumption of the compressor (50) can be reduced while maintaining the heat radiation amount of the refrigerant in the evaporator, and the coefficient of performance (COP) during the cooling operation of the air conditioner (1) is improved. Can be made.
  • an intermediate-pressure gas refrigerant is supplied between the compressors of each stage. That is, for example, in a refrigerant circuit that performs a three-stage compression refrigeration cycle, an intermediate pressure gas is provided between the first-stage compressor and the second-stage compressor, and between the second-stage compressor and the third-stage compressor. The refrigerant will be supplied.
  • the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having different pressures are generated in the enthalpy reduction means (20). Therefore, in the refrigerant circuit of the present embodiment, “a three-stage compression refrigeration cycle is performed using three compression mechanisms, and the second intermediate-pressure gas refrigerant is supplied between the first-stage compression mechanism and the second-stage compression mechanism. It is technically possible to employ a configuration in which the first intermediate-pressure gas refrigerant is supplied between the stage compression mechanism and the third stage compression mechanism.
  • the three-stage compression refrigeration cycle is performed when the difference between the low pressure and the high pressure of the refrigeration cycle is large and only a low COP (coefficient of performance) is obtained in the two-stage compression refrigeration cycle or the single-stage compression refrigeration cycle.
  • the low pressure and high pressure of the refrigeration cycle performed in the refrigerant circuit of the air conditioner are values corresponding to the temperature inside the room where people are present and the temperature outside. Since it is unlikely that the temperature inside or outside the living room will be extremely high or low, the difference between the low pressure and high pressure of the refrigeration cycle performed in the refrigerant circuit of the air conditioner is usually extreme. It will never grow.
  • the compression mechanism that compresses the refrigerant is composed of a plurality of members, mechanical loss such as friction loss between members occurs in the compression mechanism. Therefore, the greater the number of compression mechanisms, the greater the total mechanical loss that occurs in each compression mechanism. Further, when the number of compression mechanisms provided in the air conditioner increases, the manufacturing cost of the air conditioner increases. For this reason, even though “the difference between the low pressure and the high pressure in the refrigeration cycle is not so large and a sufficiently high COP can be obtained even in the single-stage compression refrigeration cycle”, “three-stage compression refrigeration using three compression mechanisms”. Adopting a “cycled configuration” increases the mechanical loss of the compression mechanism, leading to a decrease in the operating efficiency of the air conditioner, and increases the manufacturing cost of the air conditioner by increasing the number of compression mechanisms. Problems arise.
  • the first intermediate pressure gas refrigerant and the second intermediate pressure gas generated in the enthalpy reducing means (20) in the refrigerant circuit (5) performing the single-stage compression refrigeration cycle The refrigerant is sucked into the first compression mechanism (71) and the second compression mechanism (72), respectively. That is, according to the present embodiment, both the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having different pressures can be sucked into the compressor (50) that performs single-stage compression.
  • the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having different pressures can be processed while using only two compression mechanisms (71, 72), and the number of compression mechanisms can be increased. It is possible to eliminate problems such as an increase in mechanical loss of the compressor (50) and an increase in manufacturing cost of the air conditioner (1) due to the above.
  • Embodiment 2 of the Invention A second embodiment of the present invention will be described.
  • the configuration of the refrigerant circuit (5) is changed in the air conditioner (1) of the first embodiment.
  • a different point from the said Embodiment 1 is demonstrated.
  • the connection position of the second branch pipe (43) is different from that of the refrigerant circuit (5) of the first embodiment.
  • one end of the second branch pipe (43) is connected to the first expansion valve (34) and the first heat exchanger (30) in the first branch pipe (33). ) Is connected between.
  • the point that the other end of the 2nd branch piping (43) is connected to the 2nd heat exchanger (40) is the same as that of the refrigerant circuit (5) of the above-mentioned Embodiment 1.
  • evaporator refers to the outdoor heat exchanger (12) and the indoor heat exchanger (14) that operate as an evaporator
  • condenser refers to the outdoor One of the heat exchanger (12) and the indoor heat exchanger (14) operating as an evaporator.
  • the first branch pipe (33) and the second branch pipe (43) are connected.
  • the state change of the flowing refrigerant is different from the refrigeration cycle performed in the refrigerant circuit (5) of the first embodiment.
  • a part of the high-pressure refrigerant (refrigerant in the state of point D) flowing into the one-way flow pipe (6) through the bridge circuit (15) is the first. It flows into the branch pipe (33). High-pressure refrigerant flowing into the first branch pipe (33), the pressure and expands while passing through the first expansion valve (34) is decreased from P H to the P M1, the first intermediate state of point F It becomes a pressure refrigerant. A part of the first intermediate pressure refrigerant flows into the intermediate pressure side flow path (32) of the first heat exchanger (30), and the rest flows into the second branch pipe (43).
  • the first intermediate pressure refrigerant flowing into the intermediate pressure side flow path (32) of the first heat exchanger (30) absorbs heat from the high pressure refrigerant flowing through the high pressure side flow path (31) and evaporates, and the first intermediate pressure gas. It becomes a refrigerant and is supplied to the first compression mechanism (71) of the compressor (50).
  • the high pressure refrigerant flowing through the high pressure side flow path (31) of the first heat exchanger (30) is in the state of point H because its enthalpy is lowered.
  • the first intermediate pressure refrigerant that has flowed into the second branch pipe (43) expands when passing through the second expansion valve (44), and its pressure decreases from P M1 to P M2 . It becomes the 2nd intermediate pressure refrigerant of a state.
  • All of the second intermediate pressure refrigerant flows into the intermediate pressure side flow path (42) of the second heat exchanger (40).
  • the second intermediate pressure refrigerant that has flowed into the intermediate pressure side flow path (42) of the second heat exchanger (40) absorbs heat from the high pressure refrigerant flowing through the high pressure side flow path (41) and evaporates. It becomes a refrigerant and is supplied to the second compression mechanism (72) of the compressor (50).
  • the high pressure refrigerant flowing through the high pressure side flow path (41) of the second heat exchanger (40) is in the state of point K because its enthalpy is lowered.
  • the refrigeration cycle shown in the Mollier diagram of FIG. 6 is performed.
  • a part of the high-pressure refrigerant (refrigerant at the point E in FIG. 6) that has flowed from the one-way flow pipe (6) into the first branch pipe (33) is the first expansion valve. (34) and the remainder flows into the second branch pipe (43).
  • High-pressure refrigerant sent to the first expansion valve (34), the pressure and expands while passing through the first expansion valve (34) is decreased from P H to P M1, the state of point F in FIG. 6 It becomes a first intermediate pressure refrigerant and flows into the first heat exchanger (30).
  • a gas-liquid separator (23) is provided in the middle of the first branch pipe (33), and the gas-liquid separator (23) has a second One end of the branch pipe (43) may be connected.
  • the first branch pipe (33) is divided into an upstream part (33a) and a downstream part (33b).
  • One end of the upstream portion (33a) of the first branch pipe (33) is connected to the upstream side of the first heat exchanger (30) in the one-way flow pipe (6), and the other end is a gas-liquid separator. It is connected to the inlet of (23).
  • the first expansion valve (34) is provided in the upstream portion (33a) of the first branch pipe (33).
  • the downstream portion (33b) of the first branch pipe (33) has one end connected to the gas refrigerant outlet of the gas-liquid separator (23) and the other end of the first heat exchanger (30).
  • the second branch pipe (43) has one end connected to the liquid refrigerant outlet of the gas-liquid separator (23) and the other end connected to the intermediate pressure side flow path (42) of the second heat exchanger (40). It is connected to the.
  • the refrigeration cycle shown in the Mollier diagram of FIG. 9 is performed.
  • the high-pressure refrigerant (refrigerant in the state of point E) flowing from the one-way flow pipe (6) to the upstream portion (33a) of the first branch pipe (33) is the first expansion valve.
  • the pressure expands as it passes through the (34) is decreased from P H to P M1, flows becomes the first intermediate-pressure refrigerant in the state at the point F the gas-liquid separator (23).
  • the first intermediate pressure refrigerant that has flowed in is separated into a saturated liquid refrigerant in the state of point F ′ and a saturated gas refrigerant in the state of point F ′′.
  • the saturated gas refrigerant in the state of point F ′′ flows into the intermediate pressure side flow path (32) of the first heat exchanger (30) through the downstream portion (33b) of the first branch pipe (33), and Heat is absorbed from the high-pressure refrigerant flowing through the high-pressure side flow path (31) to become the first intermediate-pressure gas refrigerant in the state of point G.
  • the high-pressure refrigerant flowing through the high-pressure side flow path (31) of the first heat exchanger (30) is cooled by the refrigerant flowing through the intermediate-pressure side flow path (32) and becomes a point H state.
  • the saturated liquid refrigerant in the state of point F ′ flows into the second branch pipe (43).
  • the refrigerant having flowed into the second branch pipe (43), the pressure and expands while passing through the second expansion valve (44) is decreased from P M1 to P M2, the second intermediate-pressure refrigerant in the state at the point I And flows into the second heat exchanger (40).
  • the second intermediate-pressure refrigerant flowing through the intermediate-pressure side flow path (42) absorbs heat from the high-pressure refrigerant flowing through the high-pressure side flow path (41) and evaporates. 2 Intermediate pressure gas refrigerant.
  • the high-pressure refrigerant flowing through the high-pressure side flow path (41) of the second heat exchanger (40) is cooled by the refrigerant flowing through the intermediate pressure-side flow path (42) to be in the state of point K.
  • Embodiment 3 of the Invention >> Embodiment 3 of the present invention will be described.
  • the configuration of the refrigerant circuit (5) is changed in the air conditioner (1) of the first embodiment.
  • a different point from the said Embodiment 1 is demonstrated.
  • the heat exchanger (40) is omitted.
  • the first expansion valve (37), the first gas-liquid separator (36), and the second expansion valve (47) are provided in the one-way flow pipe (6).
  • a second gas-liquid separator (46) is provided in the refrigerant circuit (5) of the present embodiment.
  • the first expansion valve (37), the first gas-liquid separator (36), A second expansion valve (47) and a second gas-liquid separator (46) are arranged in order from the inlet end to the outlet end of the one-way flow pipe (6).
  • the inlet end of the one-way flow pipe (6) is connected to the inlet of the first gas-liquid separator (36) via the first expansion valve (37).
  • the first gas-liquid separator (36) has a gas refrigerant outlet port connected to the first injection pipe (35), and a liquid refrigerant outlet port is connected to the second gas-liquid separator via the second expansion valve (47). It is connected to the inlet of (46).
  • the gas refrigerant outlet is connected to the second injection pipe (45), and the liquid refrigerant outlet is connected to the main expansion valve (13).
  • evaporator refers to the outdoor heat exchanger (12) and the indoor heat exchanger (14) that operate as an evaporator
  • condenser refers to the outdoor One of the heat exchanger (12) and the indoor heat exchanger (14) operating as an evaporator.
  • the high-pressure refrigerant (refrigerant in the state of point D) flowing into the one-way flow pipe (6) through the bridge circuit (15) is the first expansion valve. expands as it passes through the (37) decreases the pressure until the P M1 from P H, the first gas-liquid separator becomes refrigerant in the state at the point F (gas-liquid two-phase state) to (36) Inflow.
  • the first gas-liquid separator (36) the refrigerant that has flowed in is separated into a saturated liquid refrigerant in the state of point F ′ and a saturated gas refrigerant in the state of point F ′′.
  • the saturated liquid refrigerant at the point F ′ flows out from the first gas-liquid separator (36) toward the second expansion valve (47).
  • the saturated gas refrigerant in the state of the point F ′′ is supplied to the first compression mechanism (71) of the compressor (50) through the first injection pipe (35).
  • the refrigerant in the state of point I (gas-liquid two-phase state) flows into the second gas-liquid separator (46).
  • the refrigerant that has flowed in is separated into a saturated liquid refrigerant in the state of point I ′ and a saturated gas refrigerant in the state of point I ′′.
  • the saturated gas refrigerant at the point I ′′ is supplied to the second compression mechanism (72) of the compressor (50) through the second injection pipe (45).
  • the 1st heat exchanger (30) and the 2nd heat exchanger (40) may be comprised by one member for heat exchange (100).
  • the heat exchanging member (100) is obtained by integrally joining four flat tubes (101 to 104) and six headers (111 to 116) by brazing or the like. It is.
  • Each of the flat tubes (101 to 104) has an oval cross section.
  • Each of the flat tubes (101 to 104) is formed with a plurality of fluid passages extending from one end to the other end.
  • the first flat tube (101) and the fourth flat tube (104) are stacked in a posture in which their axial directions are parallel to each other, and the flat portions of the respective outer surfaces are mutually connected. It is in close contact. Further, in the heat exchange member (100), the second flat tube (102) and the third flat tube (103) are laminated so that their axial directions are parallel to each other, and are flat portions of the respective outer surfaces. Are in close contact with each other.
  • Each header (111 to 116) is formed in a hollow cylindrical shape with both ends closed.
  • Each header (111 to 116) is arranged in a posture in which the respective axial directions are orthogonal to the axial direction of the flat tubes (101 to 104).
  • the first header (111) is connected to one end of the first flat tube (101).
  • the second header (112) is connected to the other end of the first flat tube (101).
  • one end of the second flat tube (102) is connected to the second header (112) from the side opposite to the first flat tube (101).
  • the other end of the second flat tube (102) is connected to the third header (113).
  • One end of the third flat tube (103) is connected to the fourth header (114).
  • the other end of the third flat tube (103) is connected to the fifth header (115).
  • one end of the fourth flat tube (104) is connected to the fifth header (115) from the side opposite to the third flat tube (103).
  • the internal space of the fifth header (115) is partitioned into a part communicating only with the third flat tube (103) and a part communicating only with the fourth flat tube (104).
  • the other end of the fourth flat tube (104) is connected to the sixth header (116).
  • Pipes constituting the refrigerant circuit (5) are connected to the heat exchange member (100) (see FIG. 13).
  • a unidirectional flow conduit (6) extending from the bridge circuit (15) is connected to the first header (111).
  • the second header (112) is connected to the inlet end of the second branch pipe (43).
  • a one-way flow pipe (6) extending toward the main expansion valve (13) is connected to the third header (113).
  • An outlet end of the second branch pipe (43) is connected to the fourth header (114).
  • a second injection pipe (45) is connected to a portion communicating with the third flat tube (103) in the fifth header (115).
  • An outlet end of the first branch pipe (33) is connected to a portion of the fifth header (115) connected to the fourth flat pipe (104).
  • a first injection pipe (35) is connected to the sixth header (116).
  • the first flat tube (101), the fourth flat tube (104), the first header (111), the second header (112), the fifth header (115), and the sixth header (116) constitutes the first heat exchanger (30).
  • the fluid passage of the first flat tube (101) constitutes the high-pressure channel (31) of the first heat exchanger (30)
  • the fourth flat tube (104 ) Constitutes the intermediate pressure side flow path (32) of the first heat exchanger (30).
  • the refrigerant flowing through the high-pressure channel (31) Heat exchange is performed with the refrigerant flowing through the intermediate pressure side flow path (32).
  • the second flat tube (102), the third flat tube (103), the second header (112), the third header (113), the fourth header (114), and the second flat tube (103) 5 header (115) comprises the 2nd heat exchanger (40).
  • the fluid passage of the second flat tube (102) constitutes the high-pressure channel (41) of the second heat exchanger (40)
  • the third flat tube (103 ) Constitutes the intermediate pressure side flow path (42) of the second heat exchanger (40).
  • the first compression mechanism (71) and the second compression mechanism (72) may be provided in separate compressors (50a, 50b).
  • the refrigerant circuit (5) of the first embodiment will be described with respect to the modification applied to the refrigerant circuit (5) of the first embodiment.
  • the refrigerant circuit (5) of the present modification is provided with a first compressor (50a) and a second compressor (50b).
  • the first compressor (50a) is a hermetic compressor including the first compression mechanism (71).
  • the casing (51a) of the first compressor (50a) includes a first compression mechanism (71), an electric motor (60a), and a drive shaft (65a) connecting the first compression mechanism (71) and the electric motor (60a). And is housed.
  • a discharge pipe (52a) is provided in the casing (51a), and a first suction pipe (53) is connected to the first compression mechanism (71).
  • the second compressor (50b) is a hermetic compressor including the second compression mechanism (72).
  • the casing (51b) of the second compressor (50b) includes a second compression mechanism (72), an electric motor (60b), and a drive shaft (65b) connecting the second compression mechanism (72) and the electric motor (60b). And is housed.
  • a discharge pipe (52b) is provided in the casing (51b), and a second suction pipe (54) is connected to the second compression mechanism (72).
  • the discharge pipe (52a) of the first compressor (50a) and the discharge pipe (52b) of the second compressor (50b) are both the first of the four-way switching valve (11). 1 port.
  • the first suction pipe (53) of the first compressor (50a) and the second suction pipe (54) of the second compressor (50b) are both four-way switching valves (11 ) To the second port.
  • the first injection pipe (35) is connected to the first injection port (89) of the first compression mechanism (71) provided in the first compressor (50a).
  • the second injection pipe (45) is connected to the second injection port (99) of the second compression mechanism (72) provided in the second compressor (50b).
  • the first compression mechanism (71) and the second compression mechanism (72) of the present modification may be a rotary fluid machine including one set of cylinder and piston, or a plurality of sets of cylinder and piston. It may be a rotary fluid machine.
  • the compressor (50) may be configured to perform two-stage compression.
  • the refrigerant circuit (5) of the first embodiment will be described with respect to the modification applied to the refrigerant circuit (5) of the first embodiment.
  • the compressor (50) of the present modification includes only one suction pipe (55).
  • the suction pipe (55) passes through the casing (51), and one end thereof is connected to the second suction port (96) of the second compression mechanism (72).
  • the compressor (50) is provided with a connection passage (57).
  • the connection passage (57) communicates the second discharge port (97) of the second compression mechanism (72) and the first suction port (86) of the first compression mechanism (71).
  • path (57) may be comprised by piping exposed outside the casing (51), and is comprised by the space formed inside the main-body part (70) of a compressor (50). It may be.
  • the first injection pipe (35) is connected to the first injection port (89) of the first compression mechanism (71), as in the case of the first embodiment.
  • a second injection pipe (45) is connected to the second injection port (99) of the second compression mechanism (72).
  • FIG. 16 is a Mollier diagram showing a two-stage compression refrigeration cycle performed in the refrigerant circuit (5) of the present modification.
  • the low-pressure refrigerant in the state of point A is sucked into the compressor (50) of this modification.
  • the low-pressure refrigerant flowing into the suction pipe (55) of the compressor (50) is sucked into the second compression chamber (95) of the second compression mechanism (72).
  • the compressed low-pressure refrigerant sucked second compression chamber (95) is, with refrigerant in the second compression chamber (95) in the direction from the state at the point A to the state of point B 1 It will change.
  • the second intermediate pressure gas refrigerant in the state of point J is introduced into the second compression mechanism (72) from the second injection pipe (45).
  • the refrigerant discharged from the second compression mechanism (72) is sucked into the first compression mechanism (71) through the connection passage (57).
  • the compressed refrigerant sucked first compression chamber (85) is, with refrigerant in the first compression chamber (85) in the direction from the state at the point M to a state of point C 1 change I will do it.
  • the first intermediate pressure gas refrigerant in the state of point G is introduced into the first compression mechanism (71) from the first injection pipe (35).
  • the first intermediate-pressure gas refrigerant is mixed, and the mixed refrigerant is compressed to a point D state.
  • a 1st compression mechanism (71) discharges the refrigerant
  • the refrigerant discharged from the first compression mechanism (71) is sent out of the casing (51) through the discharge pipe (52).
  • the compressor (50) of the present modification includes the low-pressure refrigerant (mass flow rate m e ) fed from the evaporator and the first intermediate-pressure gas refrigerant (mass) supplied through the first injection pipe (35).
  • the flow rate m i1 ) and the second intermediate pressure gas refrigerant (mass flow rate m i2 ) supplied through the second injection pipe (45) are sucked and compressed.
  • the mass flow rate m c of high-pressure refrigerant discharged toward the condenser from the compressor (50), the low pressure refrigerant compressor (50) draws a first intermediate-pressure gas refrigerant, and the second intermediate-pressure gas refrigerant (M c m e + m i1 + m i2 ).
  • the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant generated by the enthalpy reduction means (20) are The air is sucked into the compressor (50). That is, according to this modification, both the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having different pressures can be sucked into the compressor (50) that performs the two-stage compression. Therefore, according to this modification, the first intermediate pressure gas refrigerant and the second intermediate pressure gas refrigerant having different pressures can be processed while using only two compression mechanisms (71, 72), and the number of compression mechanisms is increased. It is possible to eliminate problems such as an increase in mechanical loss of the compressor (50) and an increase in manufacturing cost of the air conditioner (1) due to the above.
  • the first injection pipe (35) may be connected to the connection passage (57) instead of the first compression mechanism (71). In this case, in the first compression mechanism (71), the first injection port (89) is omitted.
  • the second injection pipe (45) is connected to the second compression mechanism (72) in the same manner as the refrigerant circuit (5) described in FIG.
  • FIG. 18 is a Mollier diagram showing a two-stage compression refrigeration cycle performed in the refrigerant circuit (5) of the present modification.
  • the low-pressure refrigerant in the state of point A is sucked into the compressor (50).
  • the low-pressure refrigerant flowing into the suction pipe (55) of the compressor (50) is sucked into the second compression chamber (95) of the second compression mechanism (72).
  • the compressed low-pressure refrigerant sucked second compression chamber (95) is, with refrigerant in the second compression chamber (95) in the direction from the state at the point A to the state of point B 1 It will change.
  • the second intermediate pressure gas refrigerant in the state of point J is introduced into the second compression mechanism (72) from the second injection pipe (45).
  • a second intermediate-pressure gas refrigerant is mixed refrigerant after mixing in a state of being compressed point C 1.
  • the refrigerant discharged from the second compression mechanism (72) flows into the connection passage (57).
  • the first intermediate pressure gas refrigerant in the state of point G is introduced into the connection passage (57) from the first injection pipe (35).
  • the refrigerant is mixed with the first intermediate-pressure gas refrigerant in the state of the refrigerant and the point G in the state of point C 1 of the point C 2 states.
  • the first compression mechanism (71) sucks the refrigerant in the state at the point C 2 from the connecting passage (57).
  • the compressed refrigerant sucked first compression chamber (85) is, refrigerant in the first compression chamber (85) in the changes from the state of point C 2 to the state of point D .
  • a 1st compression mechanism (71) discharges the refrigerant
  • the refrigerant discharged from the first compression mechanism (71) is sent out of the casing (51) through the discharge pipe (52).
  • the second injection pipe (45) may be connected to the connection passage (57) instead of the second compression mechanism (72).
  • the second injection port (99) is omitted.
  • the first injection pipe (35) is connected to the first compression mechanism (71) in the same manner as the refrigerant circuit (5) described in FIG.
  • the low-pressure refrigerant in the state of point A is sucked into the compressor (50).
  • Low-pressure refrigerant flowing suction pipe (55) of the compressor (50) is being compressed is sucked second compression chamber of the second compression mechanism (72) to (95), from the state of point A at point B 1 state To change.
  • the second compression mechanism (72) discharges refrigerant in the state of point B 1.
  • the refrigerant discharged from the second compression mechanism (72) flows into the connection passage (57). Further, the second intermediate pressure gas refrigerant in the state of point J is introduced into the connection passage (57) from the second injection pipe (45). In the connection passage (57), the refrigerant is mixed with the second intermediate-pressure gas refrigerant in the state of the refrigerant and the point J in the state of point B 1 of the point B 2 state.
  • the first compression mechanism (71) sucks the refrigerant in the state at the point B 2 from the connecting passage (57).
  • the compressed refrigerant sucked first compression chamber (85) is, with refrigerant in the first compression chamber (85) in the direction from the state at the point B 2 to the state of point C 1 It will change.
  • the first intermediate pressure gas refrigerant in the state of point G is introduced into the first compression mechanism (71) from the first injection pipe (35).
  • First compression chamber of the first compression mechanism (71) in (85) the refrigerant that is being compressed and flows in a state of point B 2 first compression chamber (85), flows from the first injection pipe (35)
  • the first intermediate-pressure gas refrigerant thus mixed is mixed, and the mixed refrigerant is compressed to a state of point D.
  • a 1st compression mechanism (71) discharges the refrigerant
  • the refrigerant discharged from the first compression mechanism (71) is sent out of the casing (51) through the discharge pipe (52).
  • the first compression mechanism (71) and the second compression mechanism (72) may be provided in separate compressors (50a, 50b).
  • the first compressor (50a) is a hermetic compressor including the first compression mechanism (71).
  • the casing (51a) of the first compressor (50a) includes a first compression mechanism (71), an electric motor (60a), and a drive shaft (65a) connecting the first compression mechanism (71) and the electric motor (60a). And is housed.
  • a discharge pipe (52a) is provided in the casing (51a), and a first suction pipe (53) is connected to the first compression mechanism (71).
  • the second compressor (50b) is a hermetic compressor including the second compression mechanism (72).
  • the casing (51b) of the second compressor (50b) includes a second compression mechanism (72), an electric motor (60b), and a drive shaft (65b) connecting the second compression mechanism (72) and the electric motor (60b). And is housed.
  • a discharge pipe (52b) is provided in the casing (51b), and a second suction pipe (54) is connected to the second compression mechanism (72).
  • the discharge pipe (52a) of the first compressor (50a) is connected to the first port of the four-way switching valve (11), and the second compressor (50b) is connected to the second port.
  • the suction pipe (54) is connected to the second port of the four-way switching valve (11).
  • the discharge pipe (52b) of the second compressor (50b) and the first suction pipe (53) of the first compressor (50a) are connected to each other by a connection pipe (58).
  • the first injection pipe (35) is connected to the first injection port (89) of the first compression mechanism (71) provided in the first compressor (50a).
  • the second injection pipe (45) is connected to the second injection port (99) of the second compression mechanism (72) provided in the second compressor (50b).
  • the refrigerant circuit (5) shown in FIG. 21 is different from the refrigerant circuit (5) shown in FIG. 20 only in the connection position of the first injection pipe (35).
  • the first injection pipe (35) is connected to the connection pipe (58) instead of the first compression mechanism (71).
  • the first injection port (89) is omitted.
  • the second compression mechanism (72) of the second compressor (50b) includes the low-pressure refrigerant sucked from the second suction pipe (54) and the second refrigerant flowing from the second injection pipe (45). 2
  • the intermediate pressure gas refrigerant is compressed and discharged.
  • the first compression mechanism (71) of the first compressor (50a) includes the refrigerant discharged from the second compressor (50b) and the first flow that flows from the first injection pipe (35) into the connection pipe (58).
  • One intermediate pressure gas refrigerant is sucked from the first suction pipe (53), and the sucked refrigerant is compressed and discharged.
  • the second injection pipe (45) is connected to the connection pipe (58) instead of the second compression mechanism (72).
  • the second compression mechanism (72) the second injection port (99) is omitted.
  • the second compression mechanism (72) of the second compressor (50b) compresses and discharges the low-pressure refrigerant sucked from the second suction pipe (54).
  • the first compression mechanism (71) of the first compressor (50a) includes the refrigerant discharged from the second compressor (50b) and the first flow that flows from the second injection pipe (45) into the connection pipe (58). 2.
  • the intermediate pressure gas refrigerant is sucked from the first suction pipe (53).
  • first intermediate pressure gas refrigerant is introduced into the first compression mechanism (71) from the first injection pipe (35).
  • the first compressor (50a) compresses and discharges the refrigerant discharged from the second compressor (50b), the second intermediate pressure gas refrigerant, and the first intermediate pressure gas refrigerant.
  • the first compression mechanism (71) and the second compression mechanism (72) of the present modification may be a rotary fluid machine including one set of cylinder and piston, or a plurality of sets of cylinder and piston. It may be a rotary fluid machine.
  • the present invention is useful for a refrigeration apparatus that performs gas injection for supplying an intermediate-pressure gas refrigerant to a compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'invention porte sur un circuit de fluide frigorigène (5) d'un climatiseur (1) qui effectue un cycle de réfrigération à compression à un étage. Dans le circuit de fluide frigorigène (5), un second échangeur de chaleur (40) est disposé en aval d'un premier échangeur de chaleur (30). Le premier échangeur de chaleur (30) refroidit un fluide frigorigène haute pression dans un trajet d'écoulement haute pression (31) en amenant le fluide frigorigène haute pression à échanger de la chaleur avec un premier fluide frigorigène à pression intermédiaire dans un trajet d'écoulement à pression intermédiaire (32). Un premier fluide frigorigène gazeux à pression intermédiaire généré par le premier échangeur de chaleur (30) est distribué à un premier mécanisme de compression (71). Un second fluide frigorigène à pression intermédiaire ayant une pression inférieure à celle du premier fluide frigorigène à pression intermédiaire est distribué à un trajet d'écoulement à pression intermédiaire (42) du second échangeur de chaleur (40). Le second échangeur de chaleur (40) refroidit encore davantage le fluide frigorigène haute pression dans un trajet d'écoulement haute pression (41) en amenant le fluide frigorigène à haute pression à échanger de la chaleur avec le second fluide frigorigène à pression intermédiaire dans le trajet d'écoulement à pression intermédiaire (42). Un second fluide frigorigène gazeux à pression intermédiaire généré par le second échangeur de chaleur (40) est distribué à un second mécanisme de compression (72).
PCT/JP2009/006561 2008-12-05 2009-12-02 Dispositif de réfrigération Ceased WO2010064427A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
KR1020117012681A KR101254433B1 (ko) 2008-12-05 2009-12-02 냉동장치
AU2009323588A AU2009323588B2 (en) 2008-12-05 2009-12-02 Refrigerating apparatus
US13/132,836 US20110232325A1 (en) 2008-12-05 2009-12-02 Refrigerating apparatus
EP09830197.1A EP2357427A4 (fr) 2008-12-05 2009-12-02 Dispositif de refrigeration
CN200980148808.1A CN102227599B (zh) 2008-12-05 2009-12-02 制冷装置

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2008-311505 2008-12-05
JP2008311505 2008-12-05
JP2009-227151 2009-09-30
JP2009227151A JP4569708B2 (ja) 2008-12-05 2009-09-30 冷凍装置

Publications (1)

Publication Number Publication Date
WO2010064427A1 true WO2010064427A1 (fr) 2010-06-10

Family

ID=42233085

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/006561 Ceased WO2010064427A1 (fr) 2008-12-05 2009-12-02 Dispositif de réfrigération

Country Status (7)

Country Link
US (1) US20110232325A1 (fr)
EP (1) EP2357427A4 (fr)
JP (1) JP4569708B2 (fr)
KR (1) KR101254433B1 (fr)
CN (1) CN102227599B (fr)
AU (1) AU2009323588B2 (fr)
WO (1) WO2010064427A1 (fr)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101252173B1 (ko) * 2010-11-23 2013-04-05 엘지전자 주식회사 히트 펌프 및 그 제어방법
KR101249898B1 (ko) 2011-01-21 2013-04-09 엘지전자 주식회사 히트 펌프
JP6176470B2 (ja) * 2011-02-04 2017-08-09 三菱重工サーマルシステムズ株式会社 冷凍機
US9903625B2 (en) * 2012-09-07 2018-02-27 Mitsubishi Electric Corporation Air-conditioning apparatus
CN104101125B (zh) * 2013-04-09 2016-10-05 珠海格力电器股份有限公司 空调器
KR102103360B1 (ko) * 2013-04-15 2020-05-29 엘지전자 주식회사 공기조화기 및 그 제어방법
KR102122252B1 (ko) * 2013-04-15 2020-06-12 엘지전자 주식회사 공기조화기
CN105358918B (zh) * 2013-07-02 2017-06-27 三菱电机株式会社 制冷剂回路和空调装置
CN106104172B (zh) * 2014-03-17 2019-05-28 三菱电机株式会社 制冷循环装置
KR102240070B1 (ko) * 2014-03-20 2021-04-13 엘지전자 주식회사 공기조화기 및 그 제어방법
KR102207263B1 (ko) * 2014-04-29 2021-01-25 엘지전자 주식회사 공기 조화기 및 그 제어방법
JP6038402B2 (ja) * 2014-05-15 2016-12-07 三菱電機株式会社 蒸気圧縮式冷凍サイクル
WO2016092512A1 (fr) * 2014-12-11 2016-06-16 Angelantoni Cleantech S.R.L. Dispositif de réfrigération
KR101702736B1 (ko) 2015-01-12 2017-02-03 엘지전자 주식회사 공기 조화기
CN105444453B (zh) * 2015-12-18 2018-01-23 珠海格力电器股份有限公司 一种双温制冷及制热系统
CN106382760B (zh) * 2016-08-31 2022-08-12 广东美芝制冷设备有限公司 压缩机及具有其的制冷系统
CN106225295A (zh) * 2016-08-31 2016-12-14 广东美芝制冷设备有限公司 制冷系统
CN106152606B (zh) * 2016-08-31 2018-10-02 广东美芝制冷设备有限公司 制冷剂的换向装置及具有其的制冷系统
CN106705475B (zh) * 2016-11-30 2019-06-14 广东美芝制冷设备有限公司 制冷系统及制冷系统的控制方法
CN107763875B (zh) * 2017-10-25 2020-01-07 广东美的暖通设备有限公司 空调系统
FI4030122T3 (fi) * 2019-09-09 2023-07-28 Mitsubishi Electric Corp Ulkoyksikkö ja jäähdytyskiertolaitteisto
WO2021082331A1 (fr) * 2019-10-28 2021-05-06 广东美的制冷设备有限公司 Climatiseur
JP7092169B2 (ja) * 2020-08-31 2022-06-28 株式会社富士通ゼネラル 冷凍サイクル装置
JPWO2022215108A1 (fr) * 2021-04-05 2022-10-13

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57120972U (fr) * 1981-01-22 1982-07-27
JPS625055A (ja) * 1985-07-01 1987-01-12 株式会社神戸製鋼所 スクリユ式ヒ−トポンプ
JPH07190520A (ja) * 1993-12-27 1995-07-28 Kobe Steel Ltd 冷凍装置
JPH1193874A (ja) 1997-09-18 1999-04-06 Daikin Ind Ltd ロータリ圧縮機
JP2002188865A (ja) 2000-10-13 2002-07-05 Mitsubishi Heavy Ind Ltd 多段圧縮式冷凍機
JP2003130477A (ja) * 2001-10-30 2003-05-08 Hitachi Ltd 冷凍装置
JP2004183913A (ja) 2002-11-29 2004-07-02 Mitsubishi Electric Corp 空気調和機
JP2005315506A (ja) * 2004-04-28 2005-11-10 Kobe Steel Ltd ２段スクリュ冷凍機
JP2007232280A (ja) * 2006-03-01 2007-09-13 Daikin Ind Ltd 冷凍装置

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6230691Y2 (fr) * 1981-05-15 1987-08-06
JPS58145859A (ja) * 1982-02-24 1983-08-31 株式会社日立製作所 二段スクリユ−冷凍装置
DE3526364A1 (de) * 1985-07-19 1987-01-22 Siemens Ag Schaltungsanordnung zur netzunabhaengigen spannungsversorgung einer an ein busnetzwerk angeschlossenen verteileinrichtung fuer datenstationen
JPH05322334A (ja) * 1992-05-20 1993-12-07 Hitachi Ltd 多段圧縮冷凍サイクルおよびその起動方法
SG89409A1 (en) * 2000-10-13 2002-06-18 Mitsubishi Heavy Ind Ltd Multistage compression refrigeration machine for supplying refrigerant from intercooler to cool rotating machine and lubricating oil
US6694750B1 (en) * 2002-08-21 2004-02-24 Carrier Corporation Refrigeration system employing multiple economizer circuits
JP3832468B2 (ja) * 2003-12-26 2006-10-11 ダイキン工業株式会社 圧縮機
JP2006258331A (ja) * 2005-03-15 2006-09-28 Daikin Ind Ltd 冷凍装置
JP2007232263A (ja) * 2006-02-28 2007-09-13 Daikin Ind Ltd 冷凍装置
ES2666596T3 (es) * 2006-12-29 2018-05-07 Carrier Corporation Intercambiador de calor de economizador
EP2149018A4 (fr) * 2007-04-24 2012-09-12 Carrier Corp Système de compression de vapeur de réfrigérant muni de circuits économiseurs doubles

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57120972U (fr) * 1981-01-22 1982-07-27
JPS625055A (ja) * 1985-07-01 1987-01-12 株式会社神戸製鋼所 スクリユ式ヒ−トポンプ
JPH07190520A (ja) * 1993-12-27 1995-07-28 Kobe Steel Ltd 冷凍装置
JPH1193874A (ja) 1997-09-18 1999-04-06 Daikin Ind Ltd ロータリ圧縮機
JP2002188865A (ja) 2000-10-13 2002-07-05 Mitsubishi Heavy Ind Ltd 多段圧縮式冷凍機
JP2003130477A (ja) * 2001-10-30 2003-05-08 Hitachi Ltd 冷凍装置
JP2004183913A (ja) 2002-11-29 2004-07-02 Mitsubishi Electric Corp 空気調和機
JP2005315506A (ja) * 2004-04-28 2005-11-10 Kobe Steel Ltd ２段スクリュ冷凍機
JP2007232280A (ja) * 2006-03-01 2007-09-13 Daikin Ind Ltd 冷凍装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2357427A4 *

Also Published As

Publication number Publication date
AU2009323588A1 (en) 2011-06-30
KR101254433B1 (ko) 2013-04-12
KR20110090998A (ko) 2011-08-10
JP2010156536A (ja) 2010-07-15
EP2357427A4 (fr) 2016-04-27
AU2009323588B2 (en) 2013-03-21
CN102227599A (zh) 2011-10-26
JP4569708B2 (ja) 2010-10-27
US20110232325A1 (en) 2011-09-29
CN102227599B (zh) 2014-03-12
EP2357427A1 (fr) 2011-08-17

Similar Documents

Publication Publication Date Title
JP4569708B2 (ja) 冷凍装置
CN101688695B (zh) 带增强器回路的co2制冷剂系统
US9103571B2 (en) Refrigeration apparatus
CN101668998B (zh) 增强式制冷系统
KR101201062B1 (ko) 냉동 장치
CN102016446B (zh) 制冷装置
JP2020038054A (ja) 積層コイル区間を有する熱交換器
JP5698160B2 (ja) 空気調和機
CN101878402A (zh) 冷冻装置
JP2006071174A (ja) 冷凍装置
JP2009270745A (ja) 冷凍システム
JP5018724B2 (ja) エジェクタ式冷凍サイクル
JP2011214753A (ja) 冷凍装置
WO2020071299A1 (fr) Dispositif à cycle frigorifique
CN101878401B (zh) 冷冻装置
WO2009098899A1 (fr) Système de réfrigération
JP5786481B2 (ja) 冷凍装置
EP1645818A2 (fr) Climatiseur avec un circuit de réfrigérant double
WO2007063798A1 (fr) Dispositif de refrigeration
EP1564507A2 (fr) Appareil à cycle frigorifique
JP5895662B2 (ja) 冷凍装置
JP4468887B2 (ja) 過冷却装置及び過冷却装置を備える空気調和装置
JP2007078317A (ja) 冷却装置用熱交換器及び冷却装置
JP2010112618A (ja) 空気調和装置
JP5090932B2 (ja) エコノマイザを備えた遷臨界運転のための冷却装置

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200980148808.1

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09830197

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 20117012681

Country of ref document: KR

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 13132836

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

REEP Request for entry into the european phase

Ref document number: 2009830197

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2009830197

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2009323588

Country of ref document: AU

Date of ref document: 20091202

Kind code of ref document: A