EP2998665B1 - Kühlvorrichtung - Google Patents

Kühlvorrichtung Download PDF

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Publication number
EP2998665B1
EP2998665B1 EP13884714.0A EP13884714A EP2998665B1 EP 2998665 B1 EP2998665 B1 EP 2998665B1 EP 13884714 A EP13884714 A EP 13884714A EP 2998665 B1 EP2998665 B1 EP 2998665B1
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EP
European Patent Office
Prior art keywords
refrigerant
expansion tank
oil return
return pipe
refrigeration cycle
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Application number
EP13884714.0A
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English (en)
French (fr)
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EP2998665A1 (de
EP2998665A4 (de
Inventor
Nobuya ISHIHARA
Jun MIENO
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2998665A1 publication Critical patent/EP2998665A1/de
Publication of EP2998665A4 publication Critical patent/EP2998665A4/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/16—Receivers
    • 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
    • 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

Definitions

  • the present invention relates to a refrigeration apparatus that prevents oil from stagnating in an expansion tank.
  • an expansion tank is connected between a suction side of a low temperature-side evaporator and an accumulator (see, for example, Patent Literature 1).
  • a capillary tube and a check valve are disposed between an expansion tank and a refrigeration cycle (see, for example, Patent Literature 2).
  • US 2009/0126389 A1 discloses a refrigeration apparatus according to the preamble of claim 1.
  • the present invention has been made to overcome the above problem, and an object of the invention is to provide a refrigeration apparatus which enables immediate oil return even if oil leaks into the expansion tank.
  • a refrigeration apparatus according to the present invention is set forth in claim 1.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration apparatus according to Embodiment 1.
  • a refrigeration cycle 100 of the refrigeration apparatus according to Embodiment 1 of the present invention includes a compressor 101, a condenser 102, an expansion valve 103, an evaporator 104, and a gas-liquid separator 105, which are sequentially connected by pipes so that refrigerant circulates therein.
  • an expansion tank 107 is connected between a suction side of the compressor 101 and the gas-liquid separator 105 via an oil return pipe 108, and the oil return pipe 108 is provided with a solenoid valve (regulating valve) 106.
  • the compressor 101 suctions refrigerant and compresses the refrigerant to have a high temperature and a high pressure.
  • the condenser 102 evaporates and gasifies or condenses and liquefies refrigerant by exchanging heat between air, for example, supplied from a blower, and refrigerant.
  • the blower is not shown in the drawings.
  • the expansion valve 103 depressurizes and expands refrigerant.
  • the evaporator 104 condenses and liquefies or evaporates and gasifies refrigerant by exchanging heat between air, for example, supplied from a blower, and refrigerant.
  • the blower is not shown in the drawings.
  • the gas-liquid separator 105 has a function of separating the refrigerant introduced thereinto a gas refrigerant and a liquid refrigerant.
  • the solenoid valve (regulating valve) 106 is opened and closed to control a flow of refrigerant.
  • the expansion tank 107 is configured to collect refrigerant to thereby prevent the pressure of the refrigeration cycle 100 from excessing an allowable pressure even when refrigerant in the refrigeration cycle 100 is completely gasified.
  • the refrigerant can be cooled to a lower temperature by using other cooling heat source (for example, coolant water), thereby decreasing the pressure of the refrigeration cycle 100.
  • other cooling heat source for example, coolant water
  • the expansion tank 107 is used in case of emergency such as electrical outage as an alternative means for reducing the pressure of the refrigeration cycle 100 so that it does not excess the allowable pressure.
  • the oil return pipe 108 allows the refrigerant collected in the expansion tank 107 and the oil stagnating in the expansion tank 107 to be returned to the refrigeration cycle 100.
  • High-temperature, high-pressure gas refrigerant which is discharged from the compressor 101 flows into the condenser 102, and is condensed and liquefied by exchanging heat with, for example, outside air, and becomes high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is decompressed in the expansion valve 103, becomes low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator 104.
  • the low-pressure gas-liquid two-phase refrigerant which has flowed into the evaporator 104 is heated, for example, by air in a refrigeration storage (while cooling the air in the refrigeration storage), evaporates and becomes low-pressure gas refrigerant. Then, the low-pressure gas refrigerant flowing out of the evaporator 104 flows into the compressor 101, and is compressed again.
  • the liquid refrigerant can be stored in the gas-liquid separator 105, while only the gas refrigerant can be allowed to flow into the compressor 101, because the gas-liquid separator 105 is disposed on the suction side of the compressor 101.
  • the solenoid valve (regulating valve) 106 is set to be open when power is not supplied to the refrigeration apparatus. Accordingly, the solenoid valve (regulating valve) 106 is open during electrical outage since power is not supplied to the refrigeration apparatus. As a result, the volume of the refrigerant flow path increases by the amount of the oil return pipe 108 and the expansion tank 107 (the volume of the refrigeration cycle 100 temporarily increases). The refrigerant in the refrigeration cycle 100 flows into the expansion tank 107, thereby reducing the pressure of the refrigeration cycle 100.
  • the solenoid valve (regulating valve) 106 is set to close when power is supplied to the refrigeration apparatus. Accordingly, the solenoid valve (regulating valve) 106 closes on recovery from power outage, since power is supplied to the refrigeration apparatus. Since refrigerant is expected to stagnate in the expansion tank 107, the solenoid valve (regulating valve) 106 is set to close after the refrigerant in the expansion tank 107 is collected (when a predetermined period of time had elapsed after the recovery from power outage).
  • the pressure of the refrigeration cycle 100 can be reduced even when the pressure of the refrigeration cycle 100 increases in case of emergency such as electrical outage.
  • Fig. 2 is an enlarged view of an essential part of a refrigerant circuit of the refrigeration apparatus according to Embodiment 1.
  • the oil return pipe 108 is connected at a lower part of the expansion tank 107, as illustrated in Fig. 2 . Since this configuration can increase a level of oil from the oil return pipe 108, an increased oil return rate is also attained.
  • the oil stored in the lower part can be collected by the oil return pipe 108 provided in the lower part of the expansion tank 107.
  • oil return from the expansion tank 107 can be immediately and reliably performed, stagnation of oil in the expansion tank 107 can be prevented, and damaging to the compressor can be avoided.
  • a position of connection between the refrigeration cycle 100 and the expansion tank 107 is at a low-pressure side (suction side) of the compressor 101 so as to generate a pressure difference between the refrigeration cycle 100 and the expansion tank 107 and facilitate immediate oil return from the expansion tank 107 to the refrigeration cycle 100.
  • Fig. 3 is an enlarged view of an essential part of a refrigerant circuit of the refrigeration apparatus according to Embodiment 2.
  • Embodiment 2 described below redundancy is avoided by omitting descriptions for the same elements as those of Embodiment 1.
  • Reference numbers in the one hundreds in Embodiment 1 are modified to those in the two hundreds in Embodiment 2.
  • the position of connection between a refrigeration cycle 200 and an expansion tank 107 is at a gas-liquid separator 205.
  • gas refrigerant separated by the gas-liquid separator 205 can be collected into the expansion tank 207. Accordingly, the amount of oil leaking into the expansion tank 207 decreases, thereby avoiding stagnation of oil in the expansion tank 207. Further, refrigerant can be prevented from returning into the compressor 201 caused by refrigerant flowing back to the gas-liquid separator 205 from the expansion tank 207 can be prevented.
  • Fig. 4 is an enlarged view of an essential part of a refrigerant circuit of the refrigeration apparatus according to Embodiment.
  • Embodiment 3 described below, redundancy is avoided by omitting the description for the same elements as those of Embodiments 1 and 2.
  • Reference numbers in the one hundreds in Embodiment 1 are modified to those in the three hundreds in Embodiment 3.
  • an oil return pipe 308 which connects a gas-liquid separator 305 and an expansion tank 307 is provided with a trap 309 with a hole 309a formed in a lower part as shown in Fig. 4 .
  • oil can be further prevented from leaking into the expansion tank 307 by allowing oil to stagnate in the trap 309 and to be discharged from the hole 309a formed in the lower part when oil leaks into the oil return pipe 308.
  • Fig. 5 is an enlarged view of an essential part of a refrigerant circuit of the refrigeration apparatus according to Embodiment 4 of the present invention.
  • Embodiment 4 described below redundancy is avoided by omitting the description for the same elements as those of Embodiments 1 to 3.
  • Reference numbers in the one hundreds in Embodiment 1 are modified to those in the four hundreds in Embodiment 4.
  • an oil return pipe 408 which connects a gas-liquid separator 405 and an expansion tank 407 is provided with a check valve 410 parallel to a solenoid valve (regulating valve) 406 as shown in Fig. 5 .
  • the oil return pipe 408 has a diameter on a side on which the solenoid valve (regulating valve) 406 is disposed, that is, from which oil leaks into the expansion tank 407, the diameter being smaller than a diameter of the oil return pipe 408 on a side on which the check valve 410 is disposed, that is, the side from which oil is returned from the expansion tank 407.
  • Fig. 6 is an enlarged view of an essential part of a refrigerant circuit of the refrigeration apparatus according to Embodiment 5 of the present invention.
  • Embodiment 5 described below, redundancy is avoided by omitting the description for the same elements as those of Embodiments 1 to 4. Reference numbers in the one hundreds in Embodiment 1 are modified to those in the five hundreds in Embodiment 5.
  • an evaporation pressure regulating valve (EPR) 506 is provided instead of a solenoid valve (regulating valve) as shown in Fig. 6 .
  • control of the solenoid valve can be simplified since the evaporation pressure regulating valve 506 is a valve that does not open until a predetermined pressure difference is generated on both sides of the evaporation pressure regulating valve 506.
  • Embodiment 6 described below redundancy is avoided by omitting the description for the same elements as those of Embodiments 1 to 5.
  • an oil return pipe is connected to a lower part of an expansion tank similar to Embodiment 1 in Embodiments 2 to 5.
  • Fig. 7 is a refrigerant circuit diagram of the refrigeration apparatus according to Embodiment 7.
  • Embodiment 7 described below redundancy is avoided by omitting the description for the same elements as those of Embodiments 1 to 6.
  • Reference numbers in the one hundreds in Embodiment 1 are modified to those in the six hundreds in Embodiment 7.
  • a refrigeration cycle 600 of the refrigeration apparatus is a two-stage refrigeration cycle which is composed of a high temperature-side refrigeration cycle 600a and a low temperature-side refrigeration cycle 600b.
  • the high temperature-side refrigeration cycle 600a includes a high temperature-side compressor 601a, a condenser 602, a high temperature-side expansion valve 603a, and a high temperature-side flow path of a cascade heat exchanger 611, which are sequentially connected by pipes so that refrigerant circulates therein.
  • the low temperature-side refrigeration cycle 600b includes a low temperature-side compressor 601b, a low temperature-side flow path of the cascade heat exchanger 611, a low temperature-side expansion valve 603b, an evaporator 604, and a gas-liquid separator 605, which are sequentially connected by pipes so that refrigerant which becomes a supercritical state within a range of a designed temperature (for example, such as carbon dioxide or R23) circulates therein.
  • a designed temperature for example, such as carbon dioxide or R23
  • an expansion tank 607 is connected by an oil return pipe 608 between a suction side of the low temperature-side compressor 601b of the low temperature-side refrigeration cycle 600b and the gas-liquid separator 605, and the oil return pipe 608 is provided with a solenoid valve (regulating valve) 606.
  • High-temperature, high-pressure gas refrigerant which is discharged from the high temperature-side compressor 601a of the high temperature-side refrigeration cycle 600a flows into the condenser 602, and is condensed and liquefied by exchanging heat with, for example, outside air, and becomes high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is decompressed in the high temperature-side expansion valve 603a, becomes low-pressure gas-liquid two-phase refrigerant, and flows into the high temperature-side flow path of the cascade heat exchanger 611.
  • the low-pressure gas-liquid two-phase refrigerant on the high temperature-side is heated by refrigerant which flows in the low temperature-side flow path in the cascade heat exchanger 611, evaporates and becomes low-pressure gas refrigerant, and then, flows into the high temperature-side compressor 601a and is compressed again.
  • high-temperature, high-pressure gas refrigerant which is discharged from the low temperature-side compressor 601b flows into the low temperature-side flow path of the cascade heat exchanger 611, and is condensed and liquefied by refrigerant which flows in the high temperature-side flow path, and becomes high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant flows into the low temperature-side expansion valve 603b.
  • the high-pressure liquid refrigerant which has flowed into the low temperature-side expansion valve 603b is decompressed, becomes a low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator 604.
  • the low-pressure gas-liquid two-phase refrigerant which has flowed into the evaporator 604 is heated, for example, by air in a refrigeration storage (while cooling the air in the refrigeration storage), evaporates and becomes low-pressure gas refrigerant. Then, the low-pressure gas refrigerant flowing out of the evaporator 31 flows into the low temperature-side compressor 601b, and is compressed again.
  • the liquid refrigerant can be stored in the gas-liquid separator 605, while only the gas refrigerant can be allowed to flow into the low temperature-side compressor 601b, since the gas-liquid separator 605 is disposed on the suction side of the low temperature-side compressor 601b.
  • the amount of refrigerant that becomes a supercritical state within a range of a designed temperature of the low temperature-side can be reduced compared with a case of an air cooling type unitary refrigeration cycle by adopting a two-stage refrigeration cycle which uses a refrigerant that becomes a supercritical state within a range of a designed temperature as the low temperature-side refrigeration cycle 600b. Accordingly, an absolute value of the amount of oil stagnation in the expansion tank 607 can be reduced compared with a case of an air cooling type unitary refrigeration cycle.
  • the reason that the two-stage refrigeration cycle can reduce the amount of refrigerant that becomes a supercritical state compared with the air cooling type unitary refrigeration cycle is that the two-stage refrigeration cycle uses the cascade heat exchanger 611 for a heat exchanger on the low temperature-side and the high temperature-side, which enables reduction of the amount of refrigerant compared with a unitary cycle which uses an air cooling type condenser.
  • an oil filling amount can be reduced (a smaller amount of refrigerant is necessary in a cascade heat exchanger (plate type heat exchanger) 611 compared with an air cooling type condenser) and an absolute amount of refrigerant can be reduced, oil stagnation in the expansion tank 607 can be avoided even if it leaks into the expansion tank 607.
  • tetrafluoropropene such as 2, 3, 3, 3-tetrafluoropropene (HFO-1234yf), or a mixed refrigerant which contains tetrafluoropropene may be used.
  • HFO-1234yf 2, 3, 3, 3-tetrafluoropropene
  • a mixed refrigerant which contains tetrafluoropropene may be used.
  • Fig. 8 is a refrigerant circuit diagram of the refrigeration apparatus according to Embodiment 8.
  • Embodiment 8 described below redundancy is avoided by omitting the description for the same elements as those of Embodiments 1 to 7.
  • Reference numbers in the one hundreds in Embodiment 1 are modified to those in the seven hundreds in Embodiment 8.
  • low temperature-side expansion valves 703b1, 703b2 are connected in series in a low temperature-side refrigeration cycle 700b as shown in Fig. 8 .
  • the low temperature-side expansion valves 703b1, 703b2 are provided as a two-stage configuration, refrigerant which can exist in a liquid single-phase state in a pipe in conventional configurations can be in a two-phase gas-liquid state in the present configuration.
  • the refrigerant in a two-phase gas-liquid state has a density lower than that in a liquid single-phase state, thereby reducing the refrigerant amount in the whole cycle. Accordingly, oil stagnation in the expansion tank 707 can be further prevented.
  • Embodiments 1 to 8 can be appropriately combined, for example, Embodiments 1 and 7, or Embodiments 2 and 8.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Air Conditioning Control Device (AREA)
  • Compressor (AREA)

Claims (5)

  1. Kühlvorrichtung, umfassend:
    einen Kühlkreislauf (400, 500), der einen Kompressor (401, 501), einen Kondensator (102), ein Expansionsventil (103) und einen Verdampfer (104) umfasst, die nacheinander durch Rohre derart verbunden sind, dass das Kühlmittel in diesen zirkuliert;
    einen Ausgleichsbehälter (407, 507) zum Auffangen des Kühlmittels und zum Verringern eines Drucks des Kühlkreislaufes (400, 500);
    ein Ölrücklaufrohr (408, 508) zum Rückführen des im Ausgleichbehälter (107) aufgefangenen Kühlmittels und zum Rückführen von Öl, das sich im Ausgleichsbehälter (407, 507) absetzt, zum Kühlkreislauf (400, 500); und
    ein Regelventil (406, 506), das in dem Ölrücklaufrohr (408, 508) angeordnet und so konfiguriert ist, dass es sich zum Steuern eines Strömens des Kühlmittels öffnet und schließt, worin das Ölrücklaufrohr (408, 508) eine Ansaugseite des Kompressors (101) und einen unteren Teil des Ausgleichsbehälters (407, 507) verbindet,
    dadurch gekennzeichnet, dass
    das Ölrücklaufrohr (408, 508) ein Rückschlagventil (410, 510) umfasst, das parallel zum Regelventil (406, 506) vorgesehen ist, das Ölrücklaufrohr (408, 508) einen Durchmesser auf einer Seite aufweist, auf der das Regelventil (406, 506) vorgesehen ist, wobei der Durchmesser kleiner als ein Durchmesser des Ölrücklaufrohrs auf einer Seite ist, auf der das Rückschlagventil (410, 510) vorgesehen ist.
  2. Kühlvorrichtung nach Anspruch 1, ferner umfassend eine Gas-Flüssigkeits-Trenneinrichtung (405, 505), die auf einer Ansaugseite des Kompressors (401, 501) vorgesehen ist, worin das Ölrücklaufrohr (408, 508) die Gas-Flüssigkeits-Trenneinrichtung (405, 505) und einen unteren Teil des Ausgleichsbehälters (407, 507) verbindet.
  3. Kühlvorrichtung nach Anspruch 2, worin das Ölrücklaufrohr (408, 508) mit einer Falle (409, 509) ausgestattet ist, die ein in einem unteren Teil ausgebildetes Loch (309a) aufweist, sodass Öl, das in das Ölrücklaufrohr (408, 508) austritt, sich in der Falle (409, 509) absetzt und aus dem Loch (409a, 509a) austreten gelassen wird.
  4. Kühlvorrichtung nach einem der Ansprüche 1 bis 3, worin das Regelventil (406, 506) auf offen eingestellt ist, wenn diesem keine Leistung zugeführt wird, und auf geschlossen, wenn diesem Leistung zugeführt wird, und auf geschlossen eingestellt ist, nachdem das Kühlmittel im Ausgleichsbehälter (407, 507) aufgefangen worden ist, oder wenn eine vorbestimmte Zeitdauer nach Wiederherstellung nach einem Leistungsausfall vergangen ist.
  5. Kühlvorrichtung nach einem der Ansprüche 1 bis 4, worin das Regelventil (506) ein Verdampfungsdruckregelventil (506) ist, das konfiguriert ist, sich erst zu öffnen, wenn ein vorbestimmter Druckunterschied auf beiden Seiten von diesem erzeugt wird.
EP13884714.0A 2013-05-16 2013-05-16 Kühlvorrichtung Active EP2998665B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/063693 WO2014184931A1 (ja) 2013-05-16 2013-05-16 冷凍装置

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EP2998665A1 EP2998665A1 (de) 2016-03-23
EP2998665A4 EP2998665A4 (de) 2017-05-31
EP2998665B1 true EP2998665B1 (de) 2018-03-21

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WO (1) WO2014184931A1 (de)

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JP5627417B2 (ja) * 2010-11-26 2014-11-19 三菱電機株式会社 二元冷凍装置

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JP6116684B2 (ja) 2017-04-19
WO2014184931A1 (ja) 2014-11-20
EP2998665A1 (de) 2016-03-23
JPWO2014184931A1 (ja) 2017-02-23
EP2998665A4 (de) 2017-05-31

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