US20200333056A1 - Refrigeration cycle apparatus - Google Patents

Refrigeration cycle apparatus Download PDF

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Publication number
US20200333056A1
US20200333056A1 US16/770,991 US201816770991A US2020333056A1 US 20200333056 A1 US20200333056 A1 US 20200333056A1 US 201816770991 A US201816770991 A US 201816770991A US 2020333056 A1 US2020333056 A1 US 2020333056A1
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Prior art keywords
refrigerant
compressor
heat exchanger
refrigeration cycle
evaporator
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US16/770,991
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Inventor
Daisuke Ito
Shin Nakamura
Shun KATO
Akira Ishibashi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ISHIBASHI, AKIRA, ITO, DAISUKE, NAKAMURA, SHIN, KATO, SHUN
Publication of US20200333056A1 publication Critical patent/US20200333056A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B41/062—
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • 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
    • F25B2400/12—Inflammable refrigerants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
    • F25B2500/221—Preventing leaks from developing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/24—Low amount of refrigerant in the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a refrigeration cycle apparatus provided with a refrigerant circuit including a compressor, a condenser, a pressure-reducing device and an evaporator.
  • the present invention has been made to solve the problem described above, and has an object to obtain a refrigeration cycle apparatus capable of reducing an amount of refrigerant while suppressing degradation of a coefficient of performance.
  • a refrigeration cycle apparatus including a refrigerant circuit having a compressor, a condenser, a pressure-reducing device, and an evaporator; and a controller configured to control the refrigerant circuit, the refrigerant circulating in the refrigerant circuit including propane or propylene, and the controller setting a degree of superheat of the refrigerant at an entrance port of the compressor to be 10 degrees or more.
  • the amount of refrigerant in the refrigerant circuit can be reduced while suppressing degradation of the coefficient of performance of the refrigeration cycle apparatus.
  • FIG. 1 is a diagram depicting a configuration of a refrigeration cycle apparatus according to a first embodiment of the present invention.
  • FIG. 2 is a graph depicting a relation between a degree of superheat of refrigerant at an entrance port of a compressor shown in FIG. 1 and a rate of decrease of a required amount of refrigerant in the refrigerant circuit with respect to a permissible amount of refrigerant.
  • FIG. 3 is a graph depicting a relation between a degree of suction superheat of the compressor and theoretically derived coefficients of performance for R290 refrigerant, R32 refrigerant, and R410A refrigerant, respectively, used as the refrigerant in the refrigerant circuit shown in FIG. 1 .
  • FIG. 4 is a graph depicting a relation between a degree of suction superheat of a compressor of a refrigeration cycle apparatus according to a second embodiment of the present invention and a rate of decrease of a coefficient of performance according to the second embodiment with respect to that of a comparative example in which R32 refrigerant is used as refrigerant in a refrigerant circuit.
  • FIG. 5 is a diagram depicting a configuration of a refrigeration cycle apparatus according to a fourth embodiment of the present invention.
  • FIG. 6 is a diagram depicting a configuration of a refrigeration cycle apparatus according to a fifth embodiment of the present invention.
  • FIG. 1 is a diagram depicting a configuration of a refrigeration cycle apparatus according to a first embodiment of the present invention.
  • a refrigeration cycle apparatus 1 includes a refrigerant circuit 2 , in which refrigerant can circulate; and a controller 3 that controls the refrigerant circuit 2 .
  • the refrigeration cycle apparatus 1 is an air-conditioning apparatus.
  • propane that is R290 refrigerant, is used as refrigerant in the refrigerant circuit 2 .
  • the refrigerant circuit 2 includes a compressor 4 , a first heat exchanger 5 , an expansion valve 6 , a second heat exchanger 7 , and a four-way valve 8 .
  • the compressor 4 , the first heat exchanger 5 , the expansion valve 6 and the four-way valve 8 are provided in an outdoor unit, and the second heat exchanger 7 is provided in an indoor unit.
  • Each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the four-way valve 8 via a gas-side refrigerant pipe 9 .
  • a gas-side refrigerant path for guiding gaseous refrigerant is formed in each of the four-way valve 8 and the gas-side refrigerant pipe 9 .
  • each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the compressor 4 via the gas-side refrigerant path.
  • an inner diameter of the gas-side refrigerant path is 7.92 mm or more and 14.28 mm or less.
  • a length of the gas-side refrigerant path from the first heat exchanger 5 to the second heat exchanger 7 is 5 m or less.
  • each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the expansion valve 6 via a liquid-side refrigerant pipe 10 .
  • a liquid-side refrigerant path for guiding liquid refrigerant is formed in the liquid-side refrigerant pipe 10 .
  • each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the expansion valve 6 via the liquid-side refrigerant path.
  • an inner diameter of the liquid-side refrigerant path is 4.75 mm or more and 11.1 mm or less.
  • a length of the liquid-side refrigerant path from the first heat exchanger 5 to the second heat exchanger 7 is 5 m or less.
  • a refrigeration cycle process is performed, in which refrigerant circulates through the compressor 4 , the first heat exchanger 5 , the expansion valve 6 and the second heat exchanger 7 while changing in phase, according to an operation of the compressor 4 .
  • the outdoor unit is provided with a first fan 11 that forcibly sends outdoor air to the first heat exchanger 5 .
  • the indoor unit is provided with a second fan 12 that forcibly sends indoor air to the second heat exchanger 7 .
  • each of the first heat exchanger 5 and the second heat exchanger 7 includes a heat transfer pipe in which refrigerant flows.
  • first heat exchanger 5 heat exchange is performed between refrigerant that flows in the heat transfer pipe of the first heat exchanger 5 and a current of outdoor air generated by an operation of the first fan 11 .
  • second heat exchanger 7 heat exchange is performed between refrigerant that flows in the heat transfer pipe of the second heat exchanger 7 and a current of indoor air generated by an operation of the second fan 12 .
  • an inner diameter of the heat transfer pipe of each of the first heat exchanger 5 and the second heat exchanger 7 is 5 mm.
  • the compressor 4 compresses gaseous refrigerant.
  • polyalkyleneglycol (PAG)-based oil having ether bond, polyolester (POE)-based oil having ester bond or the like is used as lubricant.
  • the expansion valve 6 is a pressure reducing device that causes liquid refrigerant to expand and thereby reduces a pressure of the refrigerant. According to the above-described operation, at an exit port of refrigerant of the expansion valve 6 , the refrigerant is in a gas-liquid two-phase state.
  • the expansion valve 6 is an electric expansion valve that can control a flow rate of refrigerant. The flow rate of refrigerant that flows through the expansion valve 6 is controlled according to an opening degree of the expansion valve 6 .
  • the four-way valve 8 is an electromagnetic valve that switches a flow direction of refrigerant flowing in a gas-side refrigerant path in response to the switching operation in the refrigeration cycle apparatus 1 between the cooling operation and the heating operation.
  • the four-way valve 8 during the cooling operation, leads refrigerant from the compressor 4 to the first heat exchanger 5 , and leads refrigerant from the second heat exchanger 7 to the compressor 4 .
  • the four-way valve 8 during the heating operation, leads the refrigerant from the compressor 4 to the second heat exchanger 7 , and leads the refrigerant from the first heat exchanger 5 to the compressor 4 .
  • a flow direction of refrigerant during the cooling operation is shown by a solid arrow
  • a flow direction of refrigerant during the heating operation is shown by a dashed arrow.
  • the controller 3 controls the four-way valve 8 , and thereby switches between the cooling operation and the heating operation of the refrigeration cycle apparatus 1 . Moreover, the controller 3 activates the compressor 4 , and thereby starts an operation of the refrigerant circuit 2 . The controller 3 starts the operation of the refrigerant circuit 2 in a state where the expansion valve 6 is fully opened.
  • gaseous refrigerant compressed by the compressor 4 is sent to the first heat exchanger 5 through a gas-side refrigerant path.
  • first heat exchanger 5 heat is radiated from the refrigerant flowing in the heat transfer pipe to outdoor air, and thereby the refrigerant is condensed.
  • the condensed refrigerant is sent to the expansion valve 6 through the liquid-side refrigerant path.
  • the expansion valve 6 the pressure of the liquid refrigerant is reduced, and the liquid refrigerant becomes refrigerant in a gas-liquid two-phase state.
  • the refrigerant with the pressure reduced by the expansion valve 6 is sent to the second heat exchanger 7 through the liquid-side refrigerant path. Then, the refrigerant with the reduced pressure absorbs heat from indoor air at the second heat exchanger 7 , and evaporates. The evaporated refrigerant returns to the compressor 4 through the gas-side refrigerant path.
  • the first heat exchanger 5 operates as a condenser
  • the second heat exchanger 7 operates as an evaporator.
  • gaseous refrigerant compressed by the compressor 4 is sent to the second heat exchanger 7 through the gas-side refrigerant path.
  • the second heat exchanger 7 heat is radiated from the refrigerant flowing in the heat transfer pipe to indoor air, and thereby the refrigerant is condensed.
  • the condensed refrigerant is sent to the expansion valve 6 through the liquid-side refrigerant path.
  • the expansion valve 6 the pressure of the liquid refrigerant is reduced, and the liquid refrigerant becomes refrigerant in a gas-liquid two-phase state.
  • the refrigerant with the pressure reduced by the expansion valve 6 is sent to the first heat exchanger 5 through the liquid-side refrigerant path. Then, the refrigerant with the reduced pressure absorbs heat from outdoor air at the first heat exchanger 5 , and evaporates. The evaporated refrigerant returns to the compressor 4 through the gas-side refrigeration path.
  • the first heat exchanger 5 operates as an evaporator
  • the second heat exchanger 7 operates as a condenser.
  • a suction temperature sensor 21 for detecting temperature of refrigerant is arranged at the entrance port for refrigerant of the compressor 4 .
  • a first refrigerant port temperature sensor 22 for detecting temperature of refrigerant is arranged at a refrigerant port on the expansion valve 6 side of the first heat exchanger 5 .
  • the refrigerant port on the expansion valve 6 side of the first heat exchanger 5 is an exit port for refrigerant of the first heat exchanger 5 when the first heat exchanger 5 operates as a condenser, and is an entrance port for refrigerant of the first heat exchanger 5 when the first heat exchanger 5 operates as an evaporator.
  • a second refrigerant port temperature sensor 23 for detecting temperature of refrigerant.
  • the refrigerant port on the expansion valve 6 side of the second heat exchanger 7 is an exit port for refrigerant of the second heat exchanger 7 when the second heat exchanger 7 operates as a condenser, and is an entrance port for refrigerant of the second heat exchanger 7 when the second heat exchanger 7 operates as an evaporator.
  • Data about the temperatures detected by the suction temperature sensor 21 , the first refrigerant port temperature sensor 22 and the second refrigerant port temperature sensor 23 are sent to the controller 3 .
  • the controller 3 causes the refrigerant circuit 2 to start operation, and then controls the opening degree of the expansion valve 6 based on the data about the temperatures detected by the suction temperature sensor 21 , the first refrigerant port temperature sensor 22 and the second refrigerant port temperature sensor 23 .
  • R290 refrigerant that circulates through the refrigerant circuit 2 is combustible refrigerant.
  • an amount of the refrigerant enclosed in the refrigerant circuit 2 is required to be less than or equal to a permissible amount of refrigerant so that even when the combustible refrigerant leaks out in a room from the refrigerant circuit 2 , a concentration of the refrigerant in air is less than the lower limit of a combustible concentration.
  • the permissible amount of refrigerant is determined based on a floor area of the room, an installation height of the indoor unit, and the lower limit of the combustible concentration of refrigerant in air, as regulated by IEC 60335-2-40 ED6.
  • FIG. 2 is a graph depicting a relation between a degree of superheat SH of refrigerant at the entrance port of the compressor 4 shown in FIG. 1 and a rate of decrease of a required amount of refrigerant in the refrigerant circuit 2 with respect to a permissible amount of refrigerant.
  • a degree of superheat SH of refrigerant at the entrance port of the compressor 4 in the following, referred to as a “degree of suction superheat SH of the compressor 4 ”
  • a gas region in the heat exchanger of the first heat exchanger 5 and the second heat exchanger 7 that operates as an evaporator becomes greater.
  • the required amount of refrigerant in the refrigerant circuit 2 becomes smaller.
  • the required amount of refrigerant in the refrigerant circuit 2 is found to be less than or equal to the permissible amount of refrigerant when the degree of suction superheat SH of the compressor 4 is greater than or equal to 10 degrees.
  • the degree of suction superheat SH of the compressor 4 is obtained based on the temperature of refrigerant at the entrance port of the compressor 4 and the temperature of refrigerant at the entrance port of the evaporator. Moreover, the degree of suction superheat SH of the compressor 4 is adjustable by controlling the opening degree of the expansion valve 6 .
  • the controller 3 controls the opening degree of the expansion valve 6 based on the temperature of refrigerant at the entrance port of the compressor 4 and the temperature of refrigerant at the entrance port of the evaporator, and thereby makes the degree of suction superheat SH of the compressor 4 greater than or equal to 10 degrees.
  • the temperature of refrigerant at the entrance port of the compressor 4 is detected by the suction temperature sensor 21 .
  • the temperature of refrigerant at the entrance port of the evaporator during the cooling operation is detected by the second refrigerant port temperature sensor 23 .
  • the temperature of refrigerant at the entrance port of the evaporator during the heating operation is detected by the first refrigerant port temperature sensor 22 .
  • the controller 3 controls the opening degree of the expansion valve 6 based on the data about the temperatures detected by the suction temperature sensor 21 and the second refrigerant port temperature sensor 23 , respectively, and thereby makes the degree of suction superheat SH of the embodiment 4 greater than or equal to 10 degrees.
  • the controller 3 controls the opening degree of the expansion valve 6 based on the data about the temperatures detected the suction temperature sensor 21 and the first refrigeration port temperature sensor 22 , respectively, and thereby the degree of suction superheat SH of the embodiment 4 greater than or equal to 10 degrees. Accordingly, the amount of refrigerant circulating through the refrigerant circuit 2 is made less than or equal to the permissible amount of refrigerant.
  • R32 refrigerant having a global warming potential (GWP) greater than that of R290 refrigerant is used as refrigerant in the refrigerant circuit 2
  • GWP global warming potential
  • the degree of suction superheat SH of the compressor is limited to be within a range of 0° C. to 2° C., in order to prevent a failure of the compressor due to the rise of the temperature of refrigerant.
  • an upper limit of the discharge temperature of refrigerant at the exit port of the compressor is set to fall within a range of 100° C. to 120° C.
  • a rise amount of discharge temperature of refrigerant per 1° C. of temperature rise of the degree of suction superheat SH of the compressor is 1.13° C./° C. in the case where R32 refrigerant is used in the refrigerant circuit, but 0.95° C./° C. in the case where R290 refrigerant is used in the refrigerant circuit.
  • the rise amount of the discharge temperature of refrigerant at the exit port of the compressor with respect to the amount of rise of the degree of suction superheat SH of the compressor in the case of using R290 refrigerant as the refrigerant in the refrigerant circuit is less than that in the case of using R32 refrigerant as the refrigerant in the refrigerant circuit.
  • the rise of the discharge temperature of refrigerant at the exit port of the compressor 4 is controlled to be less than that in the comparative example, and the degree of suction superheat SH of the compressor 4 can be made greater than or equal to 10 degrees.
  • FIG. 3 is a graph depicting a relation between the degree of suction superheat SH of the compressor 4 and theoretically derived coefficients of performance (in the following, referred to as a “theoretical COP”) for R290 refrigerant, R32 refrigerant, and R410A refrigerant, respectively, used as refrigerant in the refrigerant circuit 2 shown in FIG. 1 .
  • theoretical COP for the R32 refrigerant and the theoretical COP for the R410A refrigerant becomes smaller as the degree of suction superheat SH of the compressor 4 increases.
  • the theoretical COP for the R290 refrigerant is found to become greater as the degree of suction superheat SH of the compressor 4 increases.
  • the above-described difference in the theoretical COP reflects difference between the physical property of the R290 refrigerant and the physical properties of the R32 and R410A refrigerants.
  • an evaporation latent heat of the R290 refrigerant is 1.2 times greater than the evaporation latent heat of the R32 refrigerant.
  • refrigeration effect of the R290 refrigerant against the increase of the degree of suction superheat SH of the compressor 4 is greater than that of the R32 refrigerant.
  • the refrigeration effect is expressed by a difference between enthalpies of refrigerant at the entrance port and the exit port of the evaporator.
  • an amount of R290 refrigerant required for obtaining a predetermined performance of the refrigeration cycle apparatus is 0.8 times as great as an amount of R32 refrigerant.
  • the decrease in the amount of refrigerant due to the increase of the degree of suction superheat SH of the compressor 4 can be compensated by an effect of refrigeration.
  • workload in the compressor 4 becomes smaller according to the decrease in the amount of refrigerant circulating through the refrigerant circuit 2 .
  • the coefficient of performance (COP) of the refrigeration cycle apparatus 1 is prevented from degrading.
  • R290 refrigerant i.e. propane
  • the degree of suction superheat SH of the compressor 4 is set to be greater than or equal to 10 degrees under the control of the controller 3 .
  • the degree of suction superheat SH of the compressor 4 can be made greater while preventing the discharge temperature of refrigerant at the exit port of the compressor 4 from increasing.
  • the amount of refrigerant circulating through the refrigerant circuit 2 can be made less than or equal to the permissible amount of refrigerant.
  • R290 refrigerant is used as refrigerant circulating through the refrigerant circuit 2 , even when the amount of refrigerant circulating through the refrigerant circuit 2 becomes smaller due to the increase of the degree of suction superheat SH of the compressor 4 , the coefficient of performance (COP) of the refrigeration cycle apparatus 1 is prevented from degrading.
  • the inner diameter of the heat transfer pipe of each of the first heat exchanger 5 and the second heat exchanger 7 is 5 mm. Then, an efficiency of heat exchange between air and refrigerant can be improved in each of the first heat exchanger 5 and the second heat exchanger 7 .
  • the inner diameter of the heat transfer pipe of each of the first heat exchanger 5 and the second heat exchanger 7 is set to 5 mm, the amount of refrigerant circulating through the refrigerant circuit 2 can be further and certainly reduced. Specifically, the amount of refrigerant circulating through the refrigerant circuit 2 can be further and certainly reduced to the permissible amount of refrigerant or less, while suppressing degradation of the coefficient of performance (COP) of the refrigeration cycle apparatus 1 .
  • COP coefficient of performance
  • the inner diameter of the gas-side refrigerant path is 7.92 mm or more and 14.28 mm or less.
  • the inner diameter of the liquid-side refrigerant path is 4.75 mm or more and 11.1 mm or less.
  • the length of each of the gas-side refrigerant path and the liquid-side refrigerant path is 5 m or less. Then, the inner diameter and the length of each of the gas-side refrigerant path and the liquid-side refrigerant path can be determined according to the changing in phase of the refrigerant. Thus, it is possible to suppress degradation of efficiency of circulation of refrigerant through the refrigerant circuit 2 , and the performance of the refrigeration cycle apparatus 1 can be improved.
  • the inner diameter of the heat transfer pipe of each of the first heat exchanger 5 and the second heat exchanger 7 is 5 mm.
  • the inner diameter of the heat transfer pipe of each of the first heat exchanger 5 and the second heat exchanger 7 may be less than 5 mm.
  • the efficiency of heat exchange can be further improved in each of the first heat exchanger 5 and the second heat exchanger 7 .
  • the amount of refrigerant circulating through the refrigerant circuit 2 can be further and certainly reduced to the permissible amount of refrigerant or less, while suppressing degradation of the coefficient of performance (COP) of the refrigeration cycle apparatus 1 .
  • COP coefficient of performance
  • FIG. 4 is a graph depicting a relation between a degree of suction superheat SH of a compressor of a refrigeration cycle apparatus according to a second embodiment of the present invention and a rate of decrease of a coefficient of performance (COP) according to the second embodiment with respect to that of the comparative example in which R32 refrigerant is used as refrigerant in a refrigerant circuit.
  • FIG. 4 shows a coefficient of performance (COP) for an operation of the refrigeration cycle apparatus taking into account an influence of pressure loss in refrigerant circulating through the refrigerant circuit.
  • a configuration of the refrigeration cycle apparatus according to the second embodiment is the same as the configuration of the refrigeration cycle apparatus 1 according to the first embodiment shown in FIG. 1 .
  • R290 refrigerant is used as refrigerant circulating through the refrigerant circuit 2 .
  • COP coefficient of performance
  • the degree of suction superheat SH of the compressor 4 becomes less than about 17.5 degrees, a workload of the compressor 4 increases and the coefficient of performance (COP) of the refrigeration cycle apparatus 1 degrades.
  • the degree of suction superheat SH of the compressor 4 becomes greater than about 17.5 degrees, a gas region in the evaporator increases and a performance of the evaporator degrades.
  • the decrease in the evaporation temperature leads to an increase in a compression ratio of refrigerant in the compressor 4 , and thereby increases the workload of the compressor 4 . Accordingly, even when the degree of suction superheat SH of the compressor 4 becomes greater than about 17.5 degrees, the coefficient of performance (COP) of the refrigeration cycle apparatus 1 degrades.
  • the addition amount of refrigerant in order to improve the coefficient of performance (COP) of the refrigeration cycle apparatus 1 becomes greater than the addition amount of refrigerant when the degree of suction superheat SH of the compressor 4 becomes less than about 17.5 degrees.
  • R290 refrigerant to the refrigerant in the refrigerant circuit 2 is allowed until the amount of the refrigerant in the refrigerant circuit 2 reaches the permissible amount of refrigerant.
  • the degree of suction superheat SH of the compressor 4 is less than about 17.5 degrees
  • R290 refrigerant is added to the refrigerant in the refrigerant circuit 2 as long as the amount of the refrigerant in the refrigerant circuit 2 is less than or equal to the permissible amount of refrigerant
  • the coefficient of performance (COP) of the refrigeration cycle apparatus 1 is the same as that of the comparative example.
  • the degree of suction superheat SH of the compressor 4 is greater than about 17.5 degrees
  • R290 refrigerant is added to the refrigerant in the refrigerant circuit 2 as long as the amount of the refrigerant in the refrigerant circuit 2 is less than or equal to the permissible amount of refrigerant
  • the coefficient of performance (COP) of the refrigeration cycle apparatus 1 is the same as that of the comparative example.
  • the coefficient of performance (COP) of the refrigeration cycle apparatus can be made the same as that of the comparative example, while maintaining the amount of the refrigerant circulating in the refrigerant circuit 2 less than or equal to the permissible amount of refrigerant, if the degree of suction superheat SH of the compressor 4 is greater than or equal to 15.4 degrees and less than or equal to 20.6 degrees.
  • the opening degree of the expansion valve 6 is controlled by the controller 3 , and thereby the degree of suction superheat SH of the compressor 4 is made greater than or equal to 15.4 degrees and less than or equal to 20.6 degrees.
  • Other configurations of the second embodiment are the same as those of the first embodiment.
  • the degree of suction superheat SH of the compressor 4 is controlled by the controller 3 and caused to fall within a range from 15.4 degrees to 20.6 degrees, it is possible to further and certainly suppress degradation of the coefficient of performance (COP) of the refrigeration cycle apparatus 1 , while maintaining the amount of refrigerant circulating in the refrigerant circuit 2 less than or equal to the permissible amount of refrigerant.
  • COP coefficient of performance
  • a configuration of a refrigeration cycle apparatus is the same as the configuration of the refrigeration cycle apparatus 1 according to the first embodiment, shown in FIG. 1 , except for a state of an expansion valve 6 when an operation of a refrigerant circuit 2 starts.
  • a controller 3 in the third embodiment causes the operation of the refrigerant circuit 2 to start in a state where an opening degree of the expansion valve 6 is smaller than an opening degree of the expansion valve 6 in a full open state.
  • the controller 3 controls the opening degree of the expansion valve 6 based on data about temperatures detected at a suction temperature sensor 21 and a second refrigerant port temperature sensor 23 , respectively, after a set period of time from when the refrigerant circuit 2 starts its operation.
  • the controller 3 controls the opening degree of the expansion valve 6 based on data about temperatures detected at the suction temperature sensor 21 and a first refrigerant port temperature sensor 22 , respectively, after the set period of time from when the refrigerant circuit 2 starts its operation.
  • the controller 3 controls the opening degree of the expansion valve 6 , and thereby set the degree of suction superheat SH of the compressor 4 to 10 degrees or more.
  • Other configurations are the same as those in the first embodiment.
  • the operation of the refrigerant circuit 2 starts.
  • enlarging the degree of suction superheat SH of the compressor 4 can be accelerated, and increasing the discharge temperature of refrigerant at the exit port of the compressor 4 can be accelerated.
  • the discharge temperature of refrigerant at the exit port of the compressor 4 with R290 refrigerant used in the refrigerant circuit 2 is lower than that with R32 refrigerant used in the refrigerant circuit 2 .
  • the discharge temperature when R290 refrigerant is used as refrigerant of the refrigerant circuit 2 is 63° C.
  • the discharge temperature when R32 refrigerant is used as refrigerant of the refrigerant circuit 2 is 89° C.
  • the configuration of starting the operation of the refrigerant circuit 2 in the state where the opening degree of the expansion valve 6 is less than that in the full open state of the expansion valve 6 is applied to the refrigeration cycle apparatus 1 according to the first embodiment.
  • the configuration of starting the operation of the refrigerant circuit 2 in the state where the opening degree of the expansion valve 6 is less than that in the full open state of the expansion valve 6 may be applied to the refrigeration cycle apparatus 1 according to the second embodiment.
  • FIG. 5 is a diagram depicting a configuration of a refrigeration cycle apparatus according to a fourth embodiment of the present invention.
  • a first inner temperature sensor 24 for detecting temperature of refrigerant is provided in a heat transfer pipe of a first heat exchanger 5 .
  • a length of the heat transfer pipe between a refrigerant port on the expansion valve 6 side of the first heat exchanger 5 and the first inner temperature sensor 24 is 66% to 88% of the length of the heat transfer pipe between one refrigerant port of the first heat exchanger 5 and the other refrigerant port.
  • a first refrigerant port temperature sensor 22 is provided at an entrance port of the first heat exchanger 5 when the first heat exchanger 5 is an evaporator. Moreover, when the first heat exchanger 5 is an evaporator, a length of the heat transfer pipe between the entrance port of the first heat exchanger 5 and the first inner temperature sensor 24 is 66% to 88% of a length of the heat transfer pipe between the entrance port and the exit port of the first heat exchanger 5 .
  • a second inner temperature sensor 25 for detecting temperature of refrigerant is provided in a heat transfer pipe of a second heat exchanger 7 .
  • a length of the heat transfer pipe between a refrigerant port on the expansion valve 6 side of the second heat exchanger 7 and the second inner temperature sensor 25 is 66% to 88% of the length of the heat transfer pipe between one refrigerant port of the second heat exchanger 7 and the other refrigerant port.
  • a second refrigerant port temperature sensor 23 is provided at an entrance port of the second heat exchanger 7 when the second heat exchanger 7 is an evaporator. Moreover, when the second heat exchanger 7 is an evaporator, a length of the heat transfer pipe between the entrance port of the second heat exchanger 7 and the second inner temperature sensor 25 is 66% to 88% of a length of the heat transfer pipe between the entrance port and the exit port of the second heat exchanger 7 .
  • Data about the temperatures detected at the suction temperature sensor 21 , the first refrigerant port temperature sensor 22 , the second refrigerant port temperature sensor 23 , the first inner temperature sensor 24 and the second inner temperature sensor 25 are sent to the controller 3 .
  • the controller 3 controls the opening degree of the expansion valve 6 based on the data about the temperatures detected at the suction temperature sensor 21 , the first refrigerant port temperature sensor 22 , the second refrigerant port temperature sensor 23 , the first inner temperature sensor 24 and the second inner temperature sensor 25 .
  • the controller 3 sets the degree of suction superheat SH of the compressor 4 to a value of 10 degrees or more by controlling the opening degree of the expansion valve 6 , as in the first embodiment. Moreover, during the cooling operation, the controller 3 controls the opening degree of the expansion valve 6 so that the temperature detected at the second inner temperature sensor 25 is higher than the temperature detected at the second refrigerant port temperature sensor 23 . Furthermore, during the heating operation, the controller 3 controls the opening degree of the expansion valve 6 so that the temperature detected at the first inner temperature sensor 24 is higher than the temperature detected at the first refrigerant port temperature sensor 22 .
  • the controller 3 controls the refrigerant circuit 2 so that the temperature Twmid detected at the inner temperature sensor of the first and second inner temperature sensors 24 and 25 that is provided at the entrance port of the evaporator is higher than the temperature Tein detected at the refrigerant port temperature sensor of the first and second refrigerant port temperature sensors 22 and 23 that is provided at the entrance port of the evaporator. That is, the controller 3 controls the opening degree of the expansion valve 6 so that a relation (detected temperature Twmid) ⁇ (detected temperature Tein)>0 is satisfied.
  • Other configurations are the same as those in the first embodiment.
  • the length of the heat transfer pipe between the entrance port of the evaporator and the inner temperature sensor is 66% to 88% of the length of the heat transfer pipe between the entrance port of the evaporator and the exit port of the evaporator.
  • the controller 3 controls the refrigerant circuit 2 so that the temperature Twmid detected at the inner temperature sensor is higher than the temperature Tein detected at the refrigerant port temperature sensor.
  • the configuration of controlling the refrigerant circuit 2 so that the temperature Twmid detected at the inner temperature sensor provided in the evaporator is higher than the temperature Tein detected at the refrigerant port temperature sensor provided at the entrance port of the evaporator is applied to the refrigeration cycle apparatus according to the first embodiment.
  • the configuration of controlling the refrigerant circuit 2 so that the temperature Twmid detected at the inner temperature sensor is higher than the temperature Tein detected at the refrigerant port temperature sensor may be applied to the refrigeration cycle apparatuses according to the second and third embodiments.
  • FIG. 6 is a diagram depicting a configuration of a refrigeration cycle apparatus according to a fifth embodiment of the present invention.
  • the refrigeration cycle apparatus 1 is provided with a refrigerant circuit 2 including a compressor 4 , a first heat exchanger 5 , an expansion valve 6 and a second heat exchanger 7 .
  • a four-way valve is not present in the refrigeration cycle apparatus 1 .
  • the refrigeration cycle apparatus 1 according to the fifth embodiment is not provided with a function of switching between a cooling operation and a heating operation.
  • Refrigerant circulating in the refrigerant circuit 2 is R290 refrigerant.
  • the refrigeration cycle apparatus is applied to a refrigerator.
  • Each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the compressor 4 via a gas-side refrigerant pipe 9 . According to the above-described configuration, each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the compressor 4 via a gas-side refrigerant path for guiding refrigerant.
  • each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the expansion valve 6 via a liquid-side refrigerant pipe 10 .
  • each of the first heat exchanger 5 and the second heat exchanger 7 is connected to the expansion valve 6 via a liquid-side refrigerant path for guiding refrigerant.
  • a refrigeration cycle process is performed, in which refrigerant circulates through the compressor 4 , the first heat exchanger 5 , the expansion valve 6 and the second heat exchanger 7 while changing in phase, according to the operation of the compressor 4 .
  • refrigerant circulating in the refrigerant circuit 2 flows along a direction indicated by an arrow.
  • the compressor 4 and the first heat exchanger 5 and the expansion valve 6 are provided in an outdoor unit, and the second heat exchanger 7 is provided in an indoor unit.
  • the outdoor unit is provided with a first fan 11 that forcibly sends outdoor air to the first heat exchanger 5 .
  • the indoor unit is provided with a second fan 12 that forcibly sends indoor air to the second heat exchanger 7 .
  • first heat exchanger 5 heat exchange is performed between refrigerant that flows in the heat transfer pipe of the first heat exchanger 5 and a current of outdoor air generated by an operation of the first fan 11 .
  • second heat exchanger 7 heat exchange is performed between refrigerant that flows in the heat transfer pipe of the second heat exchanger 7 and a current of indoor air generated by an operation of the second fan 12 .
  • gaseous refrigerant compressed in the compressor 4 is sent to the first heat exchanger 5 through the gas-side refrigerant path.
  • refrigerant is condensed according to heat dissipation from the refrigerant flowing through the heat transfer pipe to the outdoor air.
  • the first heat exchanger 5 operates as a condenser.
  • the condensed refrigerant is sent to the expansion valve 6 through the liquid-side refrigerant path.
  • the expansion valve 6 a pressure of the liquid refrigerant is reduced, and the liquid refrigerant becomes refrigerant in a gas-liquid two-phase state.
  • the refrigerant with the pressure reduced by the expansion valve 6 is sent to the second heat exchanger 7 through the liquid-side refrigerant path. Then, the refrigerant with the reduced pressure absorbs heat from indoor air at the second heat exchanger 7 , and evaporates. Thus, the second heat exchanger 7 operates as an evaporator. The refrigerant evaporates at the second heat exchanger 7 , which operates as an evaporator, and returns to the compressor 4 through the gas-side refrigerant path.
  • a second refrigerant port temperature sensor 23 is provided at the entrance port of the second heat exchanger 7 , which is an evaporator.
  • the controller 3 controls the opening degree of the expansion valve 6 based on temperatures of refrigerants detected by a suction temperature sensor 21 and the second refrigerant port temperature sensor 23 , respectively, and thereby sets the degree of suction superheat SH of the compressor 4 to a value of 10 degrees or more.
  • Other configurations are the same as those in the first embodiment.
  • R290 refrigerant is used as refrigerant circulating in the refrigerant circuit 2 , it is possible to suppress degradation of the coefficient of performance (COP) of the refrigeration cycle apparatus 1 , even when the amount of refrigerant circulating in the refrigerant circuit 2 becomes smaller.
  • COP coefficient of performance
  • the degree of suction superheat SH of the compressor 4 may be limited so as to fall within a range from 15.4 degrees to 20.6 degrees, according to the control by the controller 3 , as in the second embodiment. In this way, it is possible to certainly suppress degradation of the coefficient of performance (COP) of the refrigeration cycle apparatus 1 , while maintaining the amount of refrigerant circulating through the refrigerant circuit 2 at the permissible amount of refrigerant or less.
  • COP coefficient of performance
  • the configuration of the refrigeration cycle apparatus 1 which is not provided with the function of switching between a cooling operation and a heating operation is applied to the refrigeration cycle apparatus 1 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus 1 which is not provided with the function of switching between a cooling operation and a heating operation may be applied to the refrigeration cycle apparatuses 1 according to the third and fourth embodiments.
  • R290 refrigerant is used as refrigerant circulating through the refrigerant circuit 2 .
  • R1270 refrigerant which is propylene, may be used as refrigerant circulating through the refrigerant circuit 2 . Because R1270 refrigerant has the same property as that of R290 refrigerant, even when R1270 refrigerant is used as refrigerant circulating through the refrigerant circuit 2 , the same effect as that in the case of using R290 refrigerant in the refrigerant circuit 2 can be obtained.
  • R290 refrigerant that contains only propane is used as refrigerant circulating through the refrigerant circuit 2 .
  • the refrigerant has the property that the theoretical COP increases as the degree of suction superheat SH of the compressor 4 increases.
  • propane or propylene is contained in the refrigerant, it is possible to use the refrigerant as refrigerant circulating through the refrigerant circuit 2 .
  • the degree of suction superheat SH of the compressor 4 is controlled by controlling the expansion valve 6 based on the temperature of refrigerant at the entrance port of the compressor 4 and the temperature of refrigerant at the entrance port of the evaporator.
  • the degree of suction superheat SH of the compressor 4 may be controlled by controlling the expansion valve 6 based on the discharge temperature of refrigerant at the exit port of the compressor 4 and the temperature of refrigerant at the entrance port of the evaporator.
  • a discharge temperature sensor for detecting the temperature of refrigerant is provided at the exit port of the compressor 4 .
  • the controller 3 controls the opening degree of the expansion valve 6 based on the data about the temperatures detected at the refrigerant port temperature sensor provided at the entrance port of the evaporator and the discharge temperature sensor provided at the exit port of the compressor 4 , respectively.
  • the degree of suction superheat SH of the compressor 4 is controlled by controlling the opening degree of the expansion valve 6 .
  • the degree of suction superheat SH of the compressor 4 may be controlled by controlling the output of the compressor 4 .
  • the present invention is not limited to the above-described embodiments, and may be changed and implemented within the scope of the invention. Furthermore, the present invention may be implemented by combining the above-described embodiments.
  • 1 refrigeration cycle apparatus 2 refrigerant circuit, 3 controller, 4 compressor, 5 first heat exchanger (condenser or evaporator), 6 expansion valve (pressure-reducing device), 7 second heat exchanger (evaporator or condenser), 22 first refrigerant port temperature sensor, 23 second refrigerant port temperature sensor, 24 first inner temperature sensor, 25 second inner temperature sensor.

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WO2019171588A1 (ja) 2019-09-12
CN111801535B (zh) 2021-12-07
ES2913802T3 (es) 2022-06-06
CN111801535A (zh) 2020-10-20
JPWO2019171588A1 (ja) 2020-10-01
EP3764025A4 (de) 2021-03-17
EP3764025A1 (de) 2021-01-13
JP6847299B2 (ja) 2021-03-24
EP3764025B1 (de) 2022-04-13

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