WO2020194945A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2020194945A1
WO2020194945A1 PCT/JP2019/050262 JP2019050262W WO2020194945A1 WO 2020194945 A1 WO2020194945 A1 WO 2020194945A1 JP 2019050262 W JP2019050262 W JP 2019050262W WO 2020194945 A1 WO2020194945 A1 WO 2020194945A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
refrigeration cycle
expander
degree
supercooling
Prior art date
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Ceased
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PCT/JP2019/050262
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English (en)
Japanese (ja)
Inventor
小林　直樹
長谷川　泰士
直也 三吉
亮 ▲高▼田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Publication of WO2020194945A1 publication Critical patent/WO2020194945A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • 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

Definitions

  • This disclosure relates to a refrigeration cycle device.
  • the refrigerating cycle apparatus of Patent Document 1 has a main refrigerant circuit in which a compressor, a radiator, an internal heat exchanger, an expander, and an evaporator are connected in series, and a first flow control valve branched from the inlet side of the expander. It is provided with a bypass flow path connecting the outlet side of the expander via the internal heat exchanger.
  • the turbo refrigerating device used as a heat source for district heating and cooling is provided with a centrifugal turbine type turbo compressor driven by an electric motor, as is well known.
  • HFC Hydro-Fluoro-Carbon
  • GWP global warming potential
  • HFO Hydro-Fluoro-Olefin
  • HFC-134a and the like are high-pressure refrigerants, among HFO (Hydro-Fluoro-Olefin) refrigerants, for example, HFO-1233zd (E) and the like are low-pressure used at a maximum pressure of less than 0.2 MPaG. It is a refrigerant.
  • HFO Hydrofluoro-Fluoro-Olefin
  • a low-pressure refrigerant such as HFO-1233zd (E) uses a high-pressure refrigerant because the pressure on the inlet side of the expansion nozzle is low, so that the droplets are not easily miniaturized in the nozzle. Nozzle efficiency and turbine efficiency are lower than in the case of Further, in the expander, the greater the degree of supercooling at the nozzle inlet, the lower the nozzle efficiency.
  • the refrigeration cycle apparatus of the present disclosure includes a compressor, a condenser that condenses the refrigerant discharged from the compressor, a subcooler that imparts a degree of supercooling to the refrigerant that flows out of the condenser, and decompresses the refrigerant that flows out of the subcooler.
  • An expander that uses a gas-liquid two-phase refrigerant, an overcooling degree adjustment mechanism that adjusts the degree of overcooling of the refrigerant that flows into the expander, and a gas-liquid separator that separates the gas-liquid two-phase refrigerant that flows out of the expander.
  • An expansion valve for reducing the pressure of the liquid refrigerant separated by the gas-liquid separator, and an evaporator for evaporating the liquid refrigerant flowing out of the expansion valve and sucking the outflowing refrigerant into the compressor are provided. ..
  • the refrigeration cycle device of the present invention is provided with a refrigerant flow path in which a condenser and an expander are connected and a subcooler 15 is provided.
  • the supercooling degree adjusting mechanism in this refrigeration cycle apparatus is preferably provided in a bypass flow path parallel to the refrigerant flow path and a flow rate adjustment provided in the bypass flow path to adjust the flow rate of the refrigerant flowing through the bypass flow path. It is equipped with a valve.
  • the opening degree of the flow rate adjusting valve in the present invention is preferably adjusted based on the performance information regarding the degree of supercooling in the expander.
  • the refrigeration cycle apparatus of the present invention is preferably operated by fixing the opening degree of the flow rate adjusting valve when the supercooling degree measured in advance based on the performance information corresponds to the supercooling degree.
  • the opening degree of the flow rate adjusting valve is fixed at the start of operation.
  • the supercooling degree adjusting mechanism for adjusting the supercooling degree of the refrigerant flowing into the expander is provided, expansion is performed while maintaining the efficiency of the refrigeration cycle even if a low pressure refrigerant is used. It is possible to prevent a decrease in efficiency in the machine.
  • the refrigeration cycle device 10 is operated in a two-stage compression and two-stage expansion refrigeration cycle to which the low-pressure refrigerant R1233zd (E) is applied.
  • the refrigeration cycle device 10 controls the degree of supercooling at the inlet of the expander 19 by providing a bypass flow path L4 provided with a flow rate adjusting valve 17 in parallel with the subcooler 15 and adjusting the bypass amount of the refrigerant according to the operating state. (Fig. 1).
  • the opening degree of the flow rate adjusting valve 17 based on the relationship between the nozzle efficiency and the degree of supercooling (FIG. 3), which is known in advance, the nozzle is maintained while maintaining the efficiency of the refrigeration cycle device 10.
  • the refrigeration cycle device 10 can be operated with a degree of supercooling that does not reduce efficiency.
  • the refrigerating cycle apparatus 10 includes a compressor 11 that compresses the refrigerant and a condenser that condenses the refrigerant gas, which is a high-temperature and high-pressure fluid compressed by the compressor 11, with cooling water.
  • a subcooler 15 that supercools the liquid phase refrigerant (liquid refrigerant) condensed by the condenser 13 is provided.
  • the refrigeration cycle device 10 includes an expander 19 that expands the liquid refrigerant that has passed through the subcooler 15, and a gas-liquid separator 21 that supplies the refrigerant that has passed through the expander 19.
  • the refrigeration cycle device 10 has an expansion valve 23 that reduces the pressure of the liquid refrigerant separated by the gas-liquid separator 21 to a low pressure, and the refrigeration cycle device 10 evaporates the liquid refrigerant expanded by the expansion valve 23 and the refrigerant. It is provided with an evaporator 25 that exchanges heat between and cold water.
  • the refrigeration cycle device 10 constitutes a refrigeration cycle by connecting the compressor 11, the condenser 13, the subcooler 15, the expander 19 and the evaporator 25 by the refrigerant flow paths L1, L2, L3, L5, L6, L7 and L9. ing.
  • the refrigeration cycle device 10 includes a bypass flow path L4 parallel to the refrigerant flow paths L2 and L3 connected to the subcooler 15, and the bypass flow path L4 is provided with a flow rate adjusting valve 17. ing.
  • the bypass flow path L4 and the flow rate adjusting valve 17 constitute the supercooling degree adjusting mechanism of the present invention.
  • the refrigeration cycle device 10 includes an injection flow path L8 for injecting the gas refrigerant separated / evaporated by the gas-liquid separator 21 into the compressor 11.
  • the refrigeration cycle device 10 includes a control device 30 that controls the compressor 11 and the flow rate adjusting valve 17 in response to inputs from each sensor.
  • the compressor 11 is composed of, for example, a centrifugal two-stage compressor, and is driven by an electric motor whose rotation speed is controlled by an inverter that changes the input frequency from the power supply.
  • the two-stage compression type compressor 11 includes a compression mechanism on the low-stage side and a compression mechanism on the high-stage side, and the intermediate-pressure refrigerant gas compressed by the compression mechanism on the low-stage side is passed through the injection flow path L8. , The gas refrigerant separated and evaporated by the gas-liquid separator 21 is injected.
  • the subcooler 15 is provided on the downstream side of the condenser 13 and is provided so as to supercool the condensed refrigerant.
  • a cooling heat transfer tube (not shown) for cooling these is inserted into the condenser 13 and the subcooler 15, and the refrigerant gas is condensed using the cooling water as a cooling source.
  • the flow rate adjusting valve 17 controls the flow rate of the refrigerant flowing through the subcooler 15 by adjusting the flow rate of the refrigerant flowing through the bypass flow path L4 according to the instruction of the control device 30.
  • the expander 19 connects a generator (not shown) to a turbine which is a component of the expander 19, extracts generated power generated by the rotation of the turbine, and drives an electric motor 11 and other refrigeration. It serves as a power source for the drive source of auxiliary equipment in the cycle device 10. That is, the expander 19 and the compressor 11 are not coaxially connected.
  • the expander 19 has a configuration in which an expansion nozzle and an impulse turbine are combined, and guides the refrigerant that has passed through the subcooler 15 or the mixed refrigerant of the refrigerant and the refrigerant that has passed through the bypass flow path L4 to the expansion nozzle to the impulse turbine. Squirt toward. As a result, the impeller of the impulse turbine is rotated to convert velocity energy into motive energy.
  • the evaporator 25 is a device that produces a refrigerant gas having a rated temperature (for example, 7 ° C.) by absorbing heat using cold water.
  • a chilled water heat transfer tube (not shown) is inserted through the evaporator 25.
  • R1233zd which is one of the HCFO (hydrochlorofluoroolefin) refrigerants having both low global warming potential (GWP) and ozone depletion potential (ODP)
  • GWP global warming potential
  • ODP ozone depletion potential
  • E It is assumed that the required amount of refrigerant is filled. It is known that this R1233zd (E) refrigerant is a low-pressure refrigerant and has a low density, and has a density of about one-fifth that of a high-pressure refrigerant such as R134a refrigerant, which is one of the HFC refrigerants.
  • the gas refrigerant (P6) sucked into the compressor 11 is compressed by the compression mechanism on the lower stage side of the compressor 11 (P7), and the compressed refrigerant is the gas refrigerant flowing from the gas-liquid separator 21. (P8), the gas is further compressed by the compression mechanism on the higher stage side, and then discharged from the compressor 11.
  • the high-temperature and high-pressure gas refrigerant (P1) discharged from the compressor 11 flows into the condenser 13.
  • the refrigerant that has flowed into the condenser 13 exchanges heat with water to condense, and then flows out of the condenser 13.
  • the high-temperature, high-pressure liquid refrigerant (P2) flowing out of the condenser 13 flows into the subcooler 15 to be supercooled, and then flows into the expander 19.
  • the refrigerant that has flowed into the expander 19 is expanded and depressurized by the expander 19 (P3), becomes a gas-liquid two-phase refrigerant, and flows into the gas-liquid separator 21.
  • the gas-liquid two-phase refrigerant flowing into the gas-liquid separator 21 is gas-liquid separated by the gas-liquid separator 21, and the liquid refrigerant (P4) having a low enthalpy goes to the expansion valve 23 via the refrigerant flow path L6 and is liquid.
  • the gas refrigerant having a higher enthalpy than the refrigerant goes to the compressor 11 via the injection flow path L8.
  • the liquid refrigerant flowing from the gas-liquid separator 21 into the expansion valve 23 is expanded and depressurized by the expansion valve 23 (P5), becomes a gas-liquid two-phase refrigerant, and flows into the evaporator 25.
  • the gas-liquid two-phase refrigerant flowing into the evaporator 25 exchanges heat with water and evaporates, becomes a gas refrigerant, and flows out from the evaporator 25.
  • the gas refrigerant (P6) flowing out of the evaporator 25 is sucked into the compressor 11 again and compressed by the compression mechanism on the lower stage side (P7).
  • FIG. 3 shows the relationship between the supercooling degree and the nozzle efficiency, which is an example of the performance information regarding the supercooling degree in the expander 19. As shown in FIG. 3, as the degree of supercooling increases, the nozzle efficiency decreases and the characteristics of the expander 19 also decrease. The trends in supercooling and nozzle efficiency shown in FIG. 3 are unique to low pressure refrigerants such as HFO-1233zd (E).
  • the refrigerating cycle device 10 is provided with the flow rate adjusting valve 17 and flows into the expander 19 by adjusting the amount of the refrigerant passing through the subcooler 15 by adjusting the opening degree of the flow rate adjusting valve 17.
  • the opening degree of the flow rate adjusting valve 17 is controlled based on an instruction from the control device 30.
  • the control device 30 holds information about the relationship between the degree of supercooling and the nozzle efficiency shown in FIG. Further, the control device 30 holds a program related to the control procedure of the flow rate adjusting valve 17 shown in FIG. 4, and adjusts the opening degree of the flow rate adjusting valve 17 based on this program.
  • the control procedure of the flow rate adjusting valve 17 will be described with reference to FIG.
  • the control device 30 determines the magnitude relationship between the pressure of the refrigerant (condensation pressure) in the condenser 13 and the set pressure (FIG. 4, S101). In this step, it is determined whether the refrigerant flowing through the refrigeration cycle device 10 corresponds to a low-pressure refrigerant or a high-pressure refrigerant. It can be said that this step is unnecessary because the refrigerant flowing through the refrigeration cycle device 10 is usually known, but in the present embodiment, this step is executed with the meaning of confirmation.
  • the refrigerant flowing through the refrigeration cycle device 10 is a high-pressure refrigerant. If the refrigerant is a high-pressure refrigerant, the nozzle efficiency does not tend to decrease as the degree of supercooling shown in FIG. 3 increases, so that the degree of supercooling does not need to be adjusted. On the other hand, if the condensing pressure is less than the set pressure (S101 YES), the refrigerant flowing through the refrigeration cycle apparatus 10 is a low-pressure refrigerant, so the procedure for adjusting the degree of supercooling after S103 in FIG. 3 is executed.
  • the opening degree of the flow rate adjusting valve 17, which had been fully closed until then, is once fully opened (S103).
  • the amount of refrigerant flowing into the subcooler 15 is reduced as compared with the case when the flow rate adjusting valve 17 is fully closed, and the ratio of the refrigerant flowing through the subcooler 15 to the refrigerant flowing through the bypass flow path L4 is, for example, 1: 1. Therefore, the degree of supercooling of the refrigerant flowing into the expander 19 becomes low.
  • the ratio of the refrigerant flowing through the subcooler 15 to the refrigerant flowing through the bypass flow path L4 can be appropriately adjusted by, for example, the resistance when the refrigerant flows through the subcooler 15 and the flow rate adjusting valve 17.
  • the arrow C of the alternate long and short dash line in the process of expansion indicates the case where the expansion valve is provided instead of the expander 19, and the arrow B of the broken line indicates the case where the expansion valve is simply replaced with the expander. ing.
  • the isentropic change can be performed, so that heat loss can be suppressed.
  • This heat loss is given as the difference in the X-axis (vertical axis) direction at the tip (end point) of the dashed arrow C and the dashed arrow B.
  • the present embodiment is indicated by a solid arrow A, and in FIG.
  • the control device 30 has a supercooling degree (SC) measured for the refrigerant flowing into the expander 19 and a set supercooling degree (setting SC) in a state where the opening degree of the flow rate adjusting valve 17 is fully opened. ) Is determined (S105 SC ⁇ setting SC).
  • the supercooling degree (setting SC) to be set is set as follows. As shown in FIG. 3, the nozzle efficiency in the expander 19 tends to decrease as the degree of supercooling increases. On the other hand, the amount of heat exchanged in the evaporator 25 increases as the degree of supercooling increases, and the performance of the refrigeration cycle tends to improve.
  • the setting SC is determined in consideration of two contradictory tendencies regarding this degree of supercooling. This setting SC is held in advance in the control device 30, and is compared with the measured SC.
  • the degree of supercooling can be calculated by calculation based on the temperature of the refrigerant flowing into the expander 19 and the pressure of the refrigerant in the subcooler 15. Therefore, a thermometer is provided in the refrigerant flow path L3 and a pressure gauge is provided in the subcooler 15, and the control device 30 acquires information on the temperature measured by the thermometer and the pressure measured by the pressure gauge. SC can be calculated.
  • the process proceeds to step S109. If the measured supercooling degree (SC) is less than the set supercooling degree (set SC) (S105 YES), the control device 30 closes the flow rate adjusting valve 17 to reduce the valve opening degree (S105 YES). S107). When the opening degree of the flow rate adjusting valve 17 is reduced, the amount of the refrigerant passing through the subcooler 15 increases, so that the degree of supercooling of the refrigerant flowing into the expander 19 increases.
  • the control device 30 continues to determine the magnitude of the measured supercooling degree (SC) and the set supercooling degree (set SC) while reducing the opening degree of the flow rate adjusting valve 17, and the former (SC) It is determined whether or not the latter (setting SC) matches (S109).
  • the control device 30 stops reducing the opening degree of the flow rate adjusting valve 17 and fixes the opening degree of the flow rate adjusting valve 17 at that time (S111). After that, the operation of the refrigeration cycle device 10 is continued with the opening degree of the fixed flow rate adjusting valve 17.
  • the refrigeration cycle device 10 is provided with a bypass flow path L4 provided with a flow rate adjusting valve 17 in parallel with the subcooler 15, and can adjust the degree of supercooling at the inlet of the expander 19. Therefore, the refrigeration cycle device 10 can operate the refrigeration cycle device 10 with a degree of supercooling that does not reduce the nozzle efficiency in the expander 19 while maintaining the efficiency of the refrigeration cycle device 10.
  • the set supercooling degree (setting SC) was described as a specific value as an example.
  • the present disclosure is not limited to this, and the set SC can be specified as a range, for example, t1 ° C. to t2 ° C.
  • SC measured supercooling degree
  • control procedure shown in FIG. 4 is to be performed at the start of operation.
  • present disclosure is not limited to the time of operation disclosure, and the same control procedure can be periodically repeated in the process of fixing the opening degree of the flow rate adjusting valve 17 and continuing the operation.
  • control procedure of the opening degree of the flow rate adjusting valve 17 described based on FIG. 4 can be replaced with the control procedure shown in FIG. That is, in the control procedure shown in FIG. 5, after confirming that the refrigerant is a low-pressure refrigerant, the opening degree of the flow rate adjusting valve 17, which was fully open until then, is fully closed (FIG. 5, S104), and then the refrigerant in the subcooler 15 is used. The magnitude of the pressure and the set pressure of the refrigerant in the subcooler 15 is determined (S105 SC ⁇ set SC).
  • the control device 30 continuously opens the flow rate adjusting valve 17 to increase the opening degree (S108).
  • the opening degree of the flow rate adjusting valve 17 is increased, the amount of the refrigerant passing through the subcooler 15 is reduced, so that the degree of supercooling of the refrigerant flowing into the expander 19 is reduced.
  • the control device 30 determines whether or not the pressure of the refrigerant in the subcooler 15 and the set pressure of the refrigerant in the subcooler 15 match while increasing the opening degree of the flow rate adjusting valve 17 (S109). If the pressure of the refrigerant in the subcooler 15 and the set pressure of the refrigerant in the subcooler 15 match (YES in S109), the control device 30 stops increasing the opening degree of the flow rate adjusting valve 17, and the flow rate adjusting valve at that time is stopped. The opening degree of 17 is fixed (S111).
  • a bypass flow path L4 is provided in parallel with the refrigerant flow paths L2 and L3 in which the subcooler 15 is provided.
  • FIG. 6 An example is shown in FIG.
  • the refrigeration cycle device 20 shown in FIG. 6 is the same as the refrigeration cycle device 10 described above in that the flow rate adjusting valve 17 is provided in parallel with the subcooler 15.
  • the flow rate adjusting valve 17 in the refrigeration cycle device 20 is provided in the bypass flow path L10 that branches from the refrigerant flow path L1 and is connected to the refrigerant flow path L3.
  • the bypass flow path L10 and the flow rate adjusting valve 17 constitute the supercooling degree adjusting mechanism of the present disclosure. Also in the refrigeration cycle device 20, the amount of refrigerant flowing through the subcooler 15 can be controlled by adjusting the opening degree of the flow rate adjusting valve 17. Also in this refrigeration cycle device 20, the degree of supercooling of the refrigerant flowing into the expander 19 can be optimally controlled for the operation of the refrigeration cycle device 20.

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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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un dispositif à cycle frigorifique qui est capable d'empêcher une dégradation du rendement d'un détendeur tout en maintenant l'efficacité d'un cycle frigorifique même lors de l'utilisation d'un fluide frigorigène à basse pression tel que le HFO-1233zd(E).　Ce dispositif à cycle frigorifique comprend : un compresseur; un condenseur qui condense un fluide frigorigène refoulé du compresseur; un sous-refroidisseur qui applique un degré de surfusion au fluide frigorigène qui s'est écoulé hors du condenseur; un détendeur qui dépressurise le fluide frigorigène, qui s'est écoulé hors du sous-refroidisseur, en un fluide frigorigène biphasé gaz-liquide; un mécanisme de réglage de degré de surfusion qui ajuste le degré de surfusion du fluide frigorigène s'écoulant dans le détendeur; un séparateur gaz-liquide qui effectue une séparation gaz-liquide sur le fluide frigorigène biphasé gaz-liquide qui s'est écoulé hors du détendeur; un détendeur qui dépressurise le fluide frigorigène en phase liquide séparé par le séparateur gaz-liquide; et un évaporateur qui évapore le fluide frigorigène en phase liquide qui s'est écoulé hors du détendeur, et dans lequel le fluide frigorigène qui s'est écoulé est aspiré dans le compresseur.
PCT/JP2019/050262 2019-03-27 2019-12-23 Dispositif à cycle frigorifique Ceased WO2020194945A1 (fr)

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JP2019061006A JP7267063B2 (ja) 2019-03-27 2019-03-27 冷凍サイクル装置
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JP7125639B1 (ja) 2021-03-30 2022-08-25 ダイキン工業株式会社 圧縮機

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6042557A (ja) * 1983-08-18 1985-03-06 株式会社前川製作所 容積型二相流の膨脹機を用いる動力回収方法
EP1046869A1 (fr) * 1999-04-20 2000-10-25 Sanden Corporation Système de réfrigération et d'air conditionné
JP2008008523A (ja) * 2006-06-28 2008-01-17 Hitachi Appliances Inc 冷凍サイクル及び温水器
JP2008014602A (ja) * 2006-07-10 2008-01-24 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
WO2016009516A1 (fr) * 2014-07-16 2016-01-21 三菱電機株式会社 Dispositif de réfrigération et de climatisation
JP2018521295A (ja) * 2015-07-31 2018-08-02 ビツァー キュエールマシーネンバウ ゲゼルシャフト ミット ベシュレンクテル ハフツング 蒸気冷却プロセスを実施する装置及び方法

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6042557A (ja) * 1983-08-18 1985-03-06 株式会社前川製作所 容積型二相流の膨脹機を用いる動力回収方法
EP1046869A1 (fr) * 1999-04-20 2000-10-25 Sanden Corporation Système de réfrigération et d'air conditionné
JP2008008523A (ja) * 2006-06-28 2008-01-17 Hitachi Appliances Inc 冷凍サイクル及び温水器
JP2008014602A (ja) * 2006-07-10 2008-01-24 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
WO2016009516A1 (fr) * 2014-07-16 2016-01-21 三菱電機株式会社 Dispositif de réfrigération et de climatisation
JP2018521295A (ja) * 2015-07-31 2018-08-02 ビツァー キュエールマシーネンバウ ゲゼルシャフト ミット ベシュレンクテル ハフツング 蒸気冷却プロセスを実施する装置及び方法

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