EP2910872A1 - Tiefkühlvorrichtung - Google Patents

Tiefkühlvorrichtung Download PDF

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Publication number
EP2910872A1
EP2910872A1 EP12886969.0A EP12886969A EP2910872A1 EP 2910872 A1 EP2910872 A1 EP 2910872A1 EP 12886969 A EP12886969 A EP 12886969A EP 2910872 A1 EP2910872 A1 EP 2910872A1
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EP
European Patent Office
Prior art keywords
low
temperature side
compressor
pressure
refrigerant
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.)
Granted
Application number
EP12886969.0A
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English (en)
French (fr)
Other versions
EP2910872B1 (de
EP2910872A4 (de
Inventor
Takeshi Sugimoto
So Nomoto
Tomotaka Ishikawa
Takashi Ikeda
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2910872A1 publication Critical patent/EP2910872A1/de
Publication of EP2910872A4 publication Critical patent/EP2910872A4/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B45/00—Arrangements for charging or discharging 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
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/01—Timing
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2600/23—Time delays
    • 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
    • F25B2600/2523—Receiver valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • This invention relates to a refrigeration apparatus including circulation circuits (refrigeration cycles) that circulate a refrigerant.
  • a refrigeration apparatus which operates a binary refrigeration cycle with a high-temperature side circulation circuit (high-temperature side refrigeration cycle) and a low-temperature side circulation circuit (low-temperature side refrigeration cycle) cascade-connected via a cascade capacitor.
  • An existing refrigeration apparatus which, when a compressor of a low-temperature side circulation circuit is stopped, operates a compressor of a high-temperature side circulation circuit to cool a refrigerant in the low-pressure side circulation circuit to thereby suppress an increase in pressure of the low-temperature side circulation circuit (see Patent Literature 1).
  • the compressor of the high-temperature side circulation circuit is operated with the compressor of the low-temperature side circulation circuit stopped. Further, when the compressor of the low-temperature side circulation circuit in the stopped (thermo-off) state is restarted, the compressor of the low-temperature side circulation circuit is restarted after the lapse of a predetermined time from the start of the compressor of the high-temperature side circulation circuit.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2004-190917 (paragraphs [0008] to [0023] and Fig. 1 )
  • the existing refrigeration apparatus however, has an issue in that the compressor of the high-temperature side circulation circuit needs to be uselessly operated despite the state in which a cooling operation is not performed with the compressor of the low-temperature side circulation circuit stopped.
  • the compressor of the high-temperature side circulation circuit needs to be operated for an extra time of approximately 30 minutes to approximately 40 minutes in the defrosting operation for the evaporator of the low-temperature side circulation circuit in order to keep the design pressure of the low-temperature side circulation circuit no higher than approximately 3 MPa to approximately 4 MPa.
  • the defrosting operation takes place about four times to five times a day.
  • the compressor of the high-temperature side circulation circuit is not operated when the compressor of the low-temperature side circulation circuit is stopped, and if the compressor of the low-temperature side circulation circuit is stopped for a long time, the refrigerant in the low-temperature side circulation circuit is warmed to about outside air temperature, resulting in an increase in pressure.
  • the structure of members forming the low-temperature side circulation circuit needs to be strong.
  • refrigerant pipes need to be thick. This leads to an issue of an increase in manufacturing cost.
  • the pressure of the refrigerant in the low-temperature side circulation circuit is increased to exceed the design pressure, the refrigerant may be discharged from a safety valve. In this case, the low-temperature side circulation circuit needs to be refilled with a refrigerant.
  • This invention has been made to solve the above-described issues, and obtains a refrigeration apparatus capable of suppressing the increase in pressure of the refrigerant in the low-temperature side circulation circuit when the compressor of the low-temperature side circulation circuit is stopped.
  • This invention also obtains a refrigeration apparatus capable of suppressing the increase in pressure of the refrigerant in the low-temperature side circulation circuit without operating the compressor of the high-temperature side refrigerant circuit when the compressor of the low-temperature side circulation circuit is stopped or restarted.
  • This invention further obtains a refrigeration apparatus capable of reducing the design pressure of the low-temperature side circulation circuit.
  • a refrigeration apparatus includes a first circulation circuit including a first compressor, a first condenser, a first expansion device, and a first evaporator sequentially connected by piping to circulate a refrigerant therethrough, a second circulation circuit including a second compressor, a second condenser, a second expansion device, and a second evaporator sequentially connected by piping to circulate a refrigerant therethrough, a cascade capacitor formed of the first evaporator and the second condenser to exchange heat between the refrigerant flowing through the first evaporator and the refrigerant flowing through the second condenser, and a plurality of expansion tanks connected to a pipe between the second evaporator and the second compressor via an opening and closing valve.
  • the first compressor, the first condenser, the first expansion device, the first evaporator, the second compressor, and the second condenser are mounted in an outdoor unit, and the plurality of expansion tanks are mounted in an expansion tank unit.
  • This invention includes the expansion tanks connected to the pipe between the second evaporator and the second compressor via the opening and closing valve, and therefore is capable of suppressing the increase in pressure of the refrigerant in the low-temperature side circulation circuit without operating the compressor of the high-temperature side refrigerant circuit.
  • Fig. 1 is a refrigerant circuit diagram of a refrigeration apparatus in Embodiment 1 of this invention.
  • the refrigeration apparatus includes a high-temperature side circulation circuit A and a low-temperature side circulation circuit (load side circuit) B.
  • the high-temperature side circulation circuit A and the low-temperature side circulation circuit B are cascade-connected via a cascade capacitor 8.
  • the refrigeration apparatus operates a binary refrigeration cycle by circulating a refrigerant in each of the high-temperature side circulation circuit A and the low-temperature side circulation circuit B.
  • the levels and so forth of the temperature, the pressure, and so forth of configurations referred to as the low-temperature side and the high-temperature side are not particularly determined by the relationship thereof with respective absolute values, but are relatively determined by the state, the operation, and so forth of the refrigeration apparatus.
  • refrigeration apparatuses include a refrigeration apparatus including three or more refrigeration cycles (a multiple refrigeration apparatus).
  • the high-temperature side circulation circuit A includes a high-temperature side compressor 1, a high-temperature side condenser 2, a high-temperature side expansion valve 3, and a high-temperature side evaporator 4.
  • the high-temperature side compressor 1, the high-temperature side condenser 2, the high-temperature side expansion valve 3, and the high-temperature side evaporator 4 are connected in series by refrigerant pipes.
  • the high-temperature side compressor 1, the high-temperature side condenser 2, the high-temperature side expansion valve 3, and the high-temperature side evaporator 4 are stored in a later-described outdoor unit 14.
  • a refrigerant having a relatively small global warming potential (e.g., an R410A, R134a, R32, or HFO refrigerant) is used as the refrigerant circulated through the high-temperature side circulation circuit A.
  • GWP global warming potential
  • the high-temperature side compressor 1 suctions the refrigerant flowing through the high-temperature side circulation circuit A.
  • the high-temperature side compressor 1 compresses the suctioned refrigerant and discharges the refrigerant at a high temperature and high pressure.
  • the high-temperature side condenser 2 exchanges heat between air and the refrigerant discharged from the high-temperature side compressor 1.
  • the high-temperature side expansion valve 3 expands the refrigerant flowing from the high-temperature side condenser 2 by reducing the pressure of the refrigerant.
  • the high-temperature side evaporator 4 exchanges heat between the refrigerant reduced in pressure by the high-temperature side expansion valve 3 and the refrigerant flowing through a low-temperature side condenser 7 of the low-temperature side circulation circuit B.
  • the high-temperature side evaporator 4 and the low-temperature side condenser 7 form the cascade capacitor 8.
  • the cascade capacitor 8 is formed of a plate-type heat exchanger, for example.
  • the cascade capacitor 8 is not limited to the plate-type heat exchanger, and may be a shell-and-tube-type heat exchanger or a double pipe-type heat exchanger.
  • the high-temperature side compressor 1 corresponds to "a first compressor" of the present invention.
  • the high-temperature side condenser 2 corresponds to "a first condenser" of the present invention.
  • the high-temperature side expansion valve 3 corresponds to "a first expansion device" of the present invention.
  • the high-temperature side evaporator 4 corresponds to "a first evaporator" of the present invention.
  • the low-temperature side circulation circuit B includes a low-temperature side compressor 5, an auxiliary capacitor 6, the low-temperature side condenser 7, a liquid receiver 9, a low-temperature side flow control valve 10, a low-temperature side first solenoid valve 11, a low-temperature side evaporator 12, a low-temperature side high pressure sensor 27, and a low-temperature side low pressure sensor 28.
  • the low-temperature side compressor 5, the auxiliary capacitor 6, the low-temperature side condenser 7, the liquid receiver 9, the low-temperature side first solenoid valve 11, the low-temperature side flow control valve 10, and the low-temperature side evaporator 12 are connected in series by refrigerant pipes.
  • a pipe between the low-temperature side condenser 7 and the low-temperature side compressor 5 is connected to an expansion tank 18a, an expansion tank 18b, and an expansion tank 18c via a low-temperature side second solenoid valve 17.
  • the low-temperature side high pressure sensor 27 detects the pressure on a discharge side of the low-temperature side compressor 5.
  • the low-temperature side low pressure sensor 28 detects the pressure on a suction side of the low-temperature side compressor 5.
  • the low-temperature side compressor 5, the auxiliary capacitor 6, the low-temperature side condenser 7, the liquid receiver 9, the low-temperature side high pressure sensor 27, and the low-temperature side low pressure sensor 28 are stored in the later-described outdoor unit 14.
  • the low-temperature side first solenoid valve 11, the low-temperature side flow control valve 10, and the low-temperature side evaporator 12 are stored in a cooling unit 13.
  • the cooling unit 13 is used as a refrigerator-freezer showcase or a unit cooler, for example.
  • the cooling unit 13 is connected to the low-temperature side circulation circuit B by a liquid pipe 15 and a gas pipe 16.
  • the expansion tanks 18a, 18b, and 18c (hereinafter simply referred to as “the expansion tanks 18" where no distinction is made therebetween) are stored in a later-described expansion tank unit housing 31.
  • the expansion tank unit housing 31 corresponds to "an expansion tank unit” of the present invention.
  • the outdoor unit 14, the cooling unit 13, and the expansion tank unit housing 31 are carried separately and connected by pipes at a designated site.
  • a carbon dioxide (CO2) refrigerant having a global warming potential (GWP) of 1, for example, is used as the refrigerant circulated through the low-temperature side circulation circuit B.
  • CO2 carbon dioxide
  • GWP global warming potential
  • the low-temperature side compressor 5 suctions the refrigerant flowing through the low-temperature side circulation circuit B.
  • the low-temperature side compressor 5 compresses the suctioned refrigerant and discharges the refrigerant at a high temperature and high pressure.
  • the auxiliary capacitor 6 exchanges heat between air and the refrigerant discharged from the low-temperature side compressor 5.
  • the low-temperature side condenser 7 exchanges heat between the refrigerant flowing from the auxiliary capacitor 6 and the refrigerant flowing through the high-temperature side evaporator 4 of the high-temperature side circulation circuit A.
  • the liquid receiver 9 stores a surplus of the refrigerant flowing from the low-temperature side condenser 7.
  • the low-temperature side flow control valve 10 expands the refrigerant flowing from the liquid receiver 9 by reducing the pressure of the refrigerant.
  • the low-temperature side flow control valve 10 is a thermostatic automatic expansion valve or an electronic expansion valve.
  • the low-temperature side evaporator 12 exchanges heat between the refrigerant reduced in pressure by the low-temperature side flow control valve 10 and a fluid (e.g., air, water, refrigerant, brine, or the like).
  • a fluid e.g., air, water, refrigerant, brine, or the like.
  • the low-temperature side second solenoid valve 17 is a solenoid valve that is closed when supplied with power.
  • the expansion tanks 18 store therein the refrigerant.
  • the expansion tanks 18 each have an outer diameter of 400 mm or less, for example.
  • the low-temperature side compressor 5 corresponds to "a second compressor" of the present invention.
  • the low-temperature side condenser 7 corresponds to "a second condenser" of the present invention.
  • the low-temperature side flow control valve 10 corresponds to "a second expansion device.”
  • the low-temperature side evaporator 12 corresponds to "a second evaporator" of the present invention.
  • the low-temperature side second solenoid valve 17 corresponds to "an opening and closing valve" of the present invention.
  • the refrigerant flowing into the high-temperature side condenser 2 is condensed and liquefied by heat exchange with air and becomes a liquid-phase refrigerant at a high pressure.
  • the liquid-phase refrigerant at a high pressure flowing from the high-temperature side condenser 2 is reduced in pressure by the high-temperature side expansion valve 3 and becomes a two-phase gas-liquid refrigerant at a low temperature and low pressure.
  • the two-phase gas-liquid refrigerant at a low temperature and low pressure evaporates by exchanging heat with the refrigerant flowing through the low-temperature side condenser 7 of the low-temperature side circulation circuit B, and becomes a gas-phase refrigerant at a low pressure.
  • the refrigerant flowing from the high-temperature side evaporator 4 is again suctioned by the high-temperature side compressor 1.
  • auxiliary capacitor 6 heat is exchanged between air and the gas-phase refrigerant at a high temperature and high pressure, and the refrigerant is cooled and slightly reduced in temperature.
  • the refrigerant cooled by the auxiliary capacitor 6 flows into the low-temperature side condenser 7 forming the cascade capacitor 8.
  • the two-phase gas-liquid refrigerant at a low temperature and low pressure evaporates by exchanging heat with the refrigerant flowing through the low-temperature side condenser 7 of the low-temperature side circulation circuit B, and becomes a gas-phase refrigerant at a low pressure.
  • the refrigerant flowing into the low-temperature side condenser 7 is condensed by exchanging heat with the refrigerant flowing through the high-temperature side evaporator 4 of the high-temperature side circulation circuit A, and becomes a liquid-phase refrigerant at a low temperature and high pressure.
  • a portion of the refrigerant flowing into the liquid receiver 9 is stored as a surplus refrigerant, and the remaining portion of the refrigerant flows into the low-temperature side flow control valve 10.
  • the liquid-phase refrigerant at a high pressure flowing into the low-temperature side flow control valve 10 is reduced in pressure and becomes a two-phase gas-liquid refrigerant.
  • the two-phase gas-liquid refrigerant at a low temperature and low pressure flows into the low-temperature side evaporator 12.
  • the refrigerant evaporates by exchanging heat with a fluid (e.g., air), and becomes a gas-phase refrigerant at a high temperature and low pressure.
  • a fluid e.g., air
  • the gas-phase refrigerant at a low pressure flowing from the low-temperature side evaporator 12 is again suctioned by the low-temperature side compressor 5.
  • liquid receiver 9 is connected as one of the component elements of the low-temperature side circulation circuit B in Embodiment 1, the present invention is not limited thereto, and the liquid receiver 9 may not be connected.
  • liquid receiver 9 such as an accumulator may be connected to the suction side of the low-temperature side compressor 5.
  • whether or not to connect the liquid receiver 9 and the choice of the type of the liquid receiver 9 may be determined based on, for example, the purpose of the refrigeration apparatus and the refrigerant to be used.
  • Fig. 2 is a configuration diagram of the refrigeration apparatus in Embodiment 1 of this invention.
  • the outdoor unit 14 includes a high-temperature side housing 19 and a low-temperature side housing 20.
  • the high-temperature side housing 19 and the low-temperature side housing 20 have the same external shape.
  • the high-temperature side housing 19 and the low-temperature side housing 20 share a bottom plate that serves as a common table 21.
  • the high-temperature side housing 19 and the low-temperature side housing 20 are installed adjacent to each other on the common table 21.
  • the high-temperature side compressor 1, the high-temperature side condenser 2, the high-temperature side expansion valve 3, a high-temperature side fan 22, and a high-temperature side controller 24 are installed in the high-temperature side housing 19.
  • the high-temperature side fan 22 is installed in an upper part of the high-temperature side housing 19, and supplies air to the high-temperature side condenser 2.
  • the high-temperature side controller 24 executes a variety of controls of high-temperature side devices.
  • the low-temperature side compressor 5, the auxiliary capacitor 6, the liquid receiver 9, the cascade capacitor 8, a low-temperature side fan 23, and a low-temperature side controller 26 are installed in the low-temperature side housing 20.
  • the low-temperature side fan 23 is installed in an upper part of the low-temperature side housing 20, and supplies air to the high-temperature side condenser 2.
  • the low-temperature side controller 26 executes a variety of controls of low-temperature side devices.
  • the low-temperature side controller 26 controls the low-temperature side second solenoid valve 17.
  • the cascade capacitor 8 extending to both the high-temperature side and the low-temperature side may be disposed in either one of the high-temperature side housing 19 and the low-temperature side housing 20 with the arrangement and so forth taken into account.
  • the low-temperature side controller 26 corresponds to "a controller" of the present invention.
  • Fig. 3 is a configuration diagram of the outdoor unit in Fig. 2 viewed from direction A.
  • the expansion tank unit housing 31 is disposed beside and spaced from the high-temperature side housing 19 and the low-temperature side housing 20.
  • the expansion tanks 18a, 18b, and 18c are stored in the expansion tank unit housing 31.
  • the expansion tank unit housing 31 includes an expansion tank unit table 30, a support 31 b, and a support 31 c.
  • the expansion tank 18a is mounted on the expansion tank unit table 30.
  • the expansion tank 18b is mounted on the support 31 b.
  • the expansion tank 18c is mounted on the support 31 c.
  • expansion tanks 18a, 18b, and 18c are mounted in the expansion tank unit housing 31 to be aligned in the vertical direction.
  • a pipe 32a is connected to a lower portion of the expansion tank 18a.
  • a pipe 32b is connected to a lower portion of the expansion tank 18b.
  • a pipe 32c is connected to a lower portion of the expansion tank 18c.
  • the pipes 32a, 32b, and 32c are assembled to a pipe 32 and connected to the low-temperature side second solenoid valve 17.
  • the pipes 32a, 32b, and 32c are connected to the lower portions of the expansion tanks 18a, 18b, and 18c so as to reliably collect refrigerating machine oil.
  • Embodiment 1 Although a case having a single low-temperature side second solenoid valve 17 will be described in Embodiment 1, the present invention is not limited thereto, and the low-temperature side second solenoid valve 17 may be provided to each of the expansion tanks 18a, 18b, and 18c.
  • expansion tanks 18a, 18b, and 18c which are stored in the expansion tank unit housing 31, may be stacked upon one another.
  • the expansion tanks 18a, 18b, and 18c each have an outer diameter of 270 mm (a thickness of 8 mm) and a length of approximately 1500 mm.
  • the depth of the expansion tank unit housing 31 is approximately 400 mm.
  • the depth of the high-temperature side housing 19 and the low-temperature side housing 20 is approximately 800 mm.
  • a suction space of 300 mm is secured for the high-temperature side condenser 2 and the auxiliary capacitor 6.
  • Fig. 4 is a diagram illustrating the relationship between the circuit internal volume and the circuit internal pressure in Embodiment 1 of this invention.
  • Fig. 4 illustrates the relationship between the pressure of the refrigerant in the low-temperature side circulation circuit B and the circuit internal volume of the low-temperature side circulation circuit B when the circulation of the refrigerant is stopped in the high-temperature side circulation circuit A and the low-temperature side circulation circuit B and the refrigerant temperature is increased to ambient temperature under the following conditions.
  • the refrigerant in the low-temperature side circulation circuit B is carbon dioxide.
  • the ambient temperature (outside air temperature) of the outdoor unit 14 is 46 degrees Celsius.
  • the nominal output from the low-temperature side compressor 5 of the low-temperature side circulation circuit B is approximately 28 kW (approximately 10 horsepower).
  • the internal volume of the low-temperature side evaporator 12 is approximately 72 liters.
  • the internal volume of the low-temperature side compressor 5, the auxiliary capacitor 6, the low-temperature side condenser 7, and the liquid receiver 9 is approximately 40 liters.
  • the extension pipes have a length of 70 m, the internal volume thereof is approximately 48 liters.
  • the value resulting from adding the internal volume of the expansion tanks 18a, 18b, and 18c to approximately 160 liters corresponds to the circuit internal volume of the low-temperature side circulation circuit B.
  • the required circuit internal volume (black triangles in the drawing) is approximately 400 liters.
  • the outer diameter and the length thereof are 270 mm (a thickness of 8 mm) and approximately 1500 mm, respectively.
  • the required circuit internal volume (black rhombi in Fig. 4 ) is approximately 300 liters.
  • two expansion tanks 18 having an outer diameter of 270 mm (a thickness of 8 mm) and a length of approximately 1500 mm may suffice.
  • the internal volume and the number of the expansion tanks 18 are not limited to those of the above-described configurations, and may be selected as appropriate in accordance with the necessary internal volume.
  • the pipe diameter of the gas pipe 16 is 31.75 mm if R410A is used, whereas it is possible to set the pipe diameter of the gas pipe 16 to 19.05 mm if carbon dioxide is used.
  • the internal volume is increased by approximately 40 liters.
  • the capacity of the expansion tanks 18 has been calculated on the assumption that the ambient temperature is 46 degrees Celsius under the above-described conditions, the internal volume and the number of the expansion tanks 18 may be selected as appropriate in accordance with the temperature environment in which the refrigeration apparatus is used.
  • the capacity or the number of the expansion tanks 18 may be reduced.
  • the specifications of a copper pipe (hairpin) passing through the plate fin tube-type low-temperature side evaporator 12 include a diameter of approximately 9.52 mm (a thickness of 0.8 mm).
  • the specifications of the hairpin in the low-temperature side evaporator 12 include a diameter of approximately 9.52 mm (a thickness of 0.35 mm).
  • the refrigeration apparatus with the low-temperature side circulation circuit B having a design pressure of 4.15 MPa or lower is capable of reducing the manufacturing cost to half or less compared with the refrigeration apparatus with the low-temperature side circulation circuit B having a design pressure of 8.5 MPa.
  • Fig. 5 is a flowchart illustrating an operation of the refrigeration apparatus in Embodiment 1 of this invention.
  • the low-temperature side controller 26 acquires the pressure on the discharge side of the low-temperature side compressor 5 detected by the low-temperature side high pressure sensor 27 and the pressure on the suction side of the low-temperature side compressor 5 detected by the low-temperature side low pressure sensor 28.
  • the low-temperature side controller 26 determines whether or not at least one of the pressure on the suction side and the pressure on the discharge side of the low-temperature side compressor 5 is equal to or higher than a preset pressure value P1.
  • the low-temperature side controller 26 repeats step S1.
  • the pressure value P1 is set in accordance with, for example, the design pressure of the low-temperature side circulation circuit B. For example, if the design pressure is 4.15 MPa, the pressure value P1 is set to 4 MPa in consideration of measurement errors of the sensors, operating times of the solenoid valves, and so forth.
  • the pressure value P1 corresponds to "a first pressure value" of the present invention.
  • the low-temperature side controller 26 opens the low-temperature side second solenoid valve 17.
  • the refrigerant in the low-temperature side circulation circuit B flows into each of the expansion tanks 18a, 18b, and 18c. That is, the circuit internal volume of the low-temperature side circulation circuit B is increased, and the pressure of the refrigerant is reduced.
  • the low-temperature side controller 26 determines whether or not the pressure on the suction side or the pressure on the discharge side of the low-temperature side compressor 5 is equal to or lower than a preset pressure value P2.
  • the low-temperature side controller 26 If the pressure on the suction side or the pressure on the discharge side of the low-temperature side compressor 5 is not equal to or lower than the preset pressure value P2, the low-temperature side controller 26 returns to step S2 to maintain the low-temperature side second solenoid valve 17 in the open state.
  • the pressure value P2 is set to a value lower than the pressure value P1.
  • the pressure value P2 corresponds to "a second pressure value" of the present invention.
  • the low-temperature side controller 26 closes the low-temperature side second solenoid valve 17 and returns to step S1.
  • the low-temperature side second solenoid valve 17 is closed to stop the flow of the refrigerant into the expansion tanks 18. It is thereby possible to collect the refrigerant in a short time when the low-temperature side compressor 5 is restarted.
  • Power supply to the refrigeration apparatus may be stopped for a long time owing to a power failure, for example.
  • the low-temperature side second solenoid valve 17 in Embodiment 1 is a solenoid valve that is closed when supplied with power. Even when the low-temperature side compressor 5 is stopped owing to a power failure or the like, therefore, the low-temperature side second solenoid valve 17 is open, increasing the circuit internal volume of the low-temperature side circulation circuit B and reducing the pressure of the refrigerant.
  • the low-temperature side controller 26 opens the low-temperature side second solenoid valve 17 for a preset time.
  • the low-temperature side controller 26 opens the low-temperature side second solenoid valve 17 when the low-temperature side compressor 5 is started, and closes the low-temperature side second solenoid valve 17 after the lapse of a preset time.
  • steps S3 and S4 described above may be omitted to maintain the low-temperature side second solenoid valve 17 in the open state. Further, the low-temperature side second solenoid valve 17 may be closed after the lapse of a preset time from the restart of the low-temperature side compressor 5.
  • Embodiment 1 includes the expansion tanks 18 connected to the pipe between the low-temperature side evaporator 12 and the low-temperature side compressor 5 via the low-temperature side second solenoid valve 17.
  • the design pressure of the low-temperature side circulation circuit B is set to 4.15 MPa, which is equal to the design pressure in the case using the R410A refrigerant.
  • materials employed in a case using the versatile HFC refrigerant are usable in the low-temperature side compressor 5, the auxiliary capacitor 6, the cascade capacitor 8, the liquid receiver 9, the low-temperature side evaporator 12 (a showcase or a unit cooler), the liquid pipe 15, the gas pipe 16, and the expansion tanks 18, which are components of the low-temperature side circulation circuit B.
  • the low-temperature side second solenoid valve 17 is a solenoid valve that is closed when supplied with power, it is possible to suppress the increase in pressure of the refrigerant in the low-temperature side circulation circuit B even if power supply to the refrigeration apparatus is stopped for a long time owing to a power failure or the like.
  • Fig. 6 is a configuration diagram of a refrigeration apparatus in Embodiment 2 of this invention.
  • a pipe 33a is inserted in the expansion tank 18a from an upper portion of the expansion tank 18a.
  • An end portion of the pipe 33a is disposed at a position near the bottom of the expansion tank 18a.
  • a pipe 33b is inserted in the expansion tank 18b from an upper portion of the expansion tank 18b. An end portion of the pipe 33b is disposed at a position near the bottom of the expansion tank 18b.
  • a pipe 33c is inserted in the expansion tank 18c from an upper portion of the expansion tank 18c. An end portion of the pipe 33c is disposed at a position near the bottom of the expansion tank 18c.
  • the pipes 33a, 33b, and 33c are assembled to a pipe 33 and connected to the low-temperature side second solenoid valve 17.
  • the end portions of the pipes 33a, 33b, and 33c are disposed at the positions near the bottoms of the expansion tanks 18a, 18b, and 18c so as to reliably collect the refrigerating machine oil.
  • Embodiment 2 Effects similar to those of Embodiment 1 are also obtainable in Embodiment 2.
  • Fig. 7 is a configuration diagram of a refrigeration apparatus in Embodiment 3 of this invention.
  • an expansion tank table 35 is provided below the common table 21 for the high-temperature side housing 19 and the low-temperature side housing 20.
  • the expansion tanks 18a, 18b, and 18c are mounted on the expansion tank table 35.
  • the expansion tank table 35 is disposed below and adjacent to the high-temperature side housing 19 and the low-temperature side housing 20, and the expansion tanks 18a, 18b, and 18c are mounted on the expansion tank table 35 to be aligned in the horizontal direction.
  • the expansion tank table 35 corresponds to "an expansion tank unit" of the present invention.
  • a pipe 34a is connected to a lower portion of the expansion tank 18a.
  • a pipe 34b is connected to a lower portion of the expansion tank 18b.
  • a pipe 34c is connected to a lower portion of the expansion tank 18c.
  • the pipes 34a, 34b, and 34c are assembled to a pipe 34 and connected to the low-temperature side second solenoid valve 17.
  • the pipes 34a, 34b, and 34c are connected to the lower portions of the expansion tanks 18a, 18b, and 18c so as to reliably collect the refrigerating machine oil.
  • Embodiment 3 Effects similar to those of Embodiment 1 are also obtainable in Embodiment 3.
  • expansion tank table 35 is provided below the common table 21 for the high-temperature side housing 19 and the low-temperature side housing 20, it is possible to make the installation widths (depths) of the expansion tanks 18a and the outdoor unit 14 less than those in Embodiment 1 described above.
  • each of the expansion tanks 18 is 300 mm or less, it is possible to set the depth of the outdoor unit 14 to 1000 mm or less.
  • Fig. 8 is a configuration diagram of a refrigeration apparatus in Embodiment 4 of this invention.
  • a pipe 36a is inserted in the expansion tank 18a from an upper portion of the expansion tank 18a.
  • An end portion of the pipe 36a is disposed at a position near the bottom of the expansion tank 18a.
  • a pipe 36b is inserted in the expansion tank 18b from an upper portion of the expansion tank 18b. An end portion of the pipe 36b is disposed at a position near the bottom of the expansion tank 18b.
  • a pipe 36c is inserted in the expansion tank 18c from an upper portion of the expansion tank 18c. An end portion of the pipe 36c is disposed at a position near the bottom of the expansion tank 18c.
  • the pipes 36a, 36b, and 36c are assembled to a pipe 36 and connected to the low-temperature side second solenoid valve 17.
  • the end portions of the pipes 36a, 36b, and 36c are disposed at the positions near the bottoms of the expansion tanks 18a, 18b, and 18c so as to reliably collect the refrigerating machine oil.
  • Embodiment 4 Effects similar to those of Embodiment 3 are also obtainable in Embodiment 4.
  • Embodiments 1 to 4 described above the description has been given of the refrigeration apparatus in which the high-temperature side circulation circuit A and the low-temperature side circulation circuit B are cascade-connected.
  • Embodiment 5 description will be given of a refrigeration apparatus that performs two-stage compression.
  • Fig. 9 is a refrigerant circuit diagram of the refrigeration apparatus in Embodiment 5 of this invention.
  • the refrigeration apparatus of Embodiment 5 includes a circulation circuit in which a low-stage side compressor 55, a high-stage side compressor 51, an intermediate cooler 54, a low-stage side first solenoid valve 57, a low-stage side first flow control valve 56, and a low-stage side evaporator 58 are sequentially connected by pipes to circulate a refrigerant therethrough.
  • the refrigeration apparatus of Embodiment 5 further includes an intermediate pressure circuit that branches from an outlet side of a gas cooler 52 and supplies the refrigerant passed through an intermediate cooling flow control valve 53 and the intermediate cooler 54 and reduced in pressure to between the low-stage side compressor 55 and the high-stage side compressor 51.
  • a pipe between the low-stage side evaporator 58 and the low-stage side compressor 55 is connected to an expansion tank 63a, an expansion tank 63b, and an expansion tank 63c via a low-stage side second solenoid valve 62.
  • a carbon dioxide (CO2) refrigerant having a global warming potential (GWP) of 1 is used as the refrigerant circulated through the circulation circuit and the intermediate pressure circuit of the refrigeration apparatus in Embodiment 5.
  • CO2 carbon dioxide
  • GWP global warming potential
  • a low-stage side high pressure sensor 64 detects the pressure on a discharge side of the low-stage side compressor 55.
  • a low-stage side low pressure sensor 65 detects the pressure on a suction side of the low-stage side compressor 55.
  • the low-stage side first flow control valve 56, the low-stage side first solenoid valve 57, and the low-stage side evaporator 58 are stored in a low-stage side cooling unit 59.
  • the low-stage side cooling unit 59 is used as a refrigerator-freezer showcase or a unit cooler, for example.
  • the low-stage side cooling unit 59 is connected to the circulation circuit by a low-stage side liquid pipe 60 and a low-stage side gas pipe 61.
  • the low-stage side second solenoid valve 62 is a solenoid valve that is closed when supplied with power.
  • the low-stage side second solenoid valve 62 is controlled by a controller 66.
  • the internal volume and the number of the expansion tanks 63a, 63b, and 63c may be selected as appropriate based on the relationship between the circuit internal volume and the circuit internal pressure and the design pressure with the application of the technical concept described in Embodiment 1.
  • the low-stage side compressor 55 corresponds to "a first-stage compressor" of the present invention.
  • the high-stage side compressor 51 corresponds to "a second-stage compressor" of the present invention.
  • the gas cooler 52 corresponds to "a radiator" of the present invention.
  • the low-stage side first flow control valve 56 corresponds to "an expansion device" of the present invention.
  • the low-stage side evaporator 58 corresponds to "an evaporator" of the present invention.
  • the low-stage side second solenoid valve 62 corresponds to "an opening and closing valve" of the present invention.
  • the controller 66 corresponds to "a controller" of the present invention.
  • Fig. 10 is a Mollier chart illustrating the operation of the refrigeration apparatus in Embodiment 5 of this invention.
  • a gas-phase refrigerant at a low pressure flowing from the low-stage side evaporator 58 (point F in Fig. 10 ) is suctioned by the low-stage side compressor 55 and compressed to an intermediate pressure.
  • Superheated vapor discharged from the low-stage side compressor 55 joins a refrigerant at an intermediate pressure flowing from the intermediate cooler 54 (point H in Fig. 10 ) and enters the high-stage side compressor 51.
  • the gas refrigerant compressed by the high-stage side compressor 51 (point J in Fig. 10 ) is cooled by the gas cooler 52 to be slightly subcooled (point K in Fig. 10 ).
  • the subcooled liquid refrigerant flowing into the low-stage side first flow control valve 56 is reduced in pressure and becomes a two-phase gas-liquid refrigerant (point Q in Fig. 10 ).
  • the two-phase gas-liquid refrigerant at a low temperature and low pressure flows into the low-stage side evaporator 58.
  • the refrigerant evaporates by exchanging heat with a fluid (e.g., air), and becomes a gas-phase refrigerant at a high temperature and low pressure.
  • a fluid e.g., air
  • the gas-phase refrigerant at a low pressure flowing from the low-stage side evaporator 58 (point F in Fig. 10 ) is again suctioned by the low-stage side compressor 55.
  • the refrigerant branching from the outlet side of the gas cooler 52 becomes a refrigerant reduced in pressure to the intermediate pressure by the intermediate cooling flow control valve 53 (point N in Fig. 10 ).
  • the refrigerant at the intermediate pressure flows into an intermediate-pressure side of the intermediate cooler 54.
  • the refrigerant flowing into the intermediate-pressure side of the intermediate cooler 54 exchanges heat with the refrigerant flowing on the high-pressure side of the intermediate cooler 54 to increase the degree of subcooling of the high-pressure gas flowing toward the low-stage side first solenoid valve 57 (point K in Fig. 10 ) (point M in Fig. 10 ).
  • a technical concept similar to that of the control operation of the low-temperature side second solenoid valve 17 in Embodiment 1 described above is applicable to the control operation of the low-stage side second solenoid valve 62.
  • Fig. 11 is a flowchart illustrating the operation of the refrigeration apparatus in Embodiment 5 of this invention.
  • the controller 66 acquires the pressure on the discharge side of the low-stage side compressor 55 detected by the low-stage side high pressure sensor 64 and the pressure on the suction side of the low-stage side compressor 55 detected by the low-stage side low pressure sensor 65.
  • the controller 66 determines whether or not at least one of the pressure on the suction side and the pressure on the discharge side of the low-stage side compressor 55 is equal to or higher than a preset pressure value P1.
  • step S11 If at least one of the pressure on the suction side and the pressure on the discharge side of the low-stage side compressor 55 is not equal to or higher than the preset pressure value P1, the controller 66 repeats step S11.
  • the pressure value P1 is set in accordance with, for example, the design pressure of the circulation circuit. For example, if the design pressure is 4.15 MPa, the pressure value P1 is set to 4 MPa in consideration of measurement errors of the sensors, operating times of the solenoid valves, and so forth.
  • the pressure value P1 corresponds to "a first pressure value" of the present invention.
  • the controller 66 opens the low-stage side second solenoid valve 62.
  • the refrigerant in the circulation circuit flows into each of the expansion tanks 63a, 63b, and 63c. That is, the circuit internal volume of the circulation circuit is increased, and the pressure of the refrigerant is reduced.
  • the controller 66 determines whether or not the pressure on the suction side or the pressure on the discharge side of the low-stage side compressor 55 is equal to or lower than a preset pressure value P2.
  • the controller 66 If the pressure on the suction side or the pressure on the discharge side of the low-stage side compressor 55 is not equal to or lower than the preset pressure value P2, the controller 66 returns to step S12 to maintain the low-stage side second solenoid valve 62 in the open state.
  • the pressure value P2 is set to a value lower than the pressure value P1.
  • the pressure value P2 corresponds to "a second pressure value" of the present invention.
  • the controller 66 closes the low-stage side second solenoid valve 62 and returns to step S11.
  • the low-stage side second solenoid valve 62 is closed to stop the flow of the refrigerant into the expansion tanks 63. It is thereby possible to collect the refrigerant in a short time when the low-stage side compressor 55 is restarted.
  • Power supply to the refrigeration apparatus may be stopped for a long time owing to a power failure, for example.
  • the low-stage side second solenoid valve 62 in Embodiment 5 is a solenoid valve that is closed when supplied with power. Even when the low-stage side compressor 55 is stopped owing to a power failure or the like, therefore, the low-stage side second solenoid valve 62 is open, increasing the circuit internal volume of the circulation circuit and reducing the pressure of the refrigerant.
  • the controller 66 opens the low-stage side second solenoid valve 62 for a preset time.
  • the controller 66 opens the low-stage side second solenoid valve 62 when the low-stage side compressor 55 is started, and closes the low-stage side second solenoid valve 62 after the lapse of a preset time.
  • steps S13 and S14 described above may be omitted to maintain the low-stage side second solenoid valve 62 in the open state. Further, the low-stage side second solenoid valve 62 may be closed after the lapse of a preset time from the restart of the low-stage side compressor 55.
  • Embodiment 5 includes the expansion tanks 63 connected to the pipe between the low-stage side evaporator 58 and the low-stage side compressor 55 via the low-stage side second solenoid valve 62.
  • the low-stage side second solenoid valve 62 is a solenoid valve that is closed when supplied with power, it is possible to suppress the increase in pressure of the refrigerant in the circulation circuit even if power supply to the refrigeration apparatus is stopped for a long time owing to a power failure or the like.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP12886969.0A 2012-10-22 2012-10-22 Tiefkühlvorrichtung Active EP2910872B1 (de)

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CN113950602A (zh) * 2019-06-12 2022-01-18 大金工业株式会社 空调机

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JP6727422B2 (ja) 2017-04-25 2020-07-22 三菱電機株式会社 二元冷凍装置
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CN113932504B (zh) * 2021-12-21 2022-03-01 中国飞机强度研究所 一种飞机测试充注系统及充注方法

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WO2014064744A1 (ja) 2014-05-01
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EP2910872A4 (de) 2016-10-19
JPWO2014064744A1 (ja) 2016-09-05

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