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WO2006013970A1 - Appareil a cycles de congelation - Google Patents

Appareil a cycles de congelation Download PDF

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Publication number
WO2006013970A1
WO2006013970A1 PCT/JP2005/014416 JP2005014416W WO2006013970A1 WO 2006013970 A1 WO2006013970 A1 WO 2006013970A1 JP 2005014416 W JP2005014416 W JP 2005014416W WO 2006013970 A1 WO2006013970 A1 WO 2006013970A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
low
stage compressor
refrigerant
expander
Prior art date
Application number
PCT/JP2005/014416
Other languages
English (en)
Japanese (ja)
Inventor
Takahiro Yamaguchi
Shuuji Fujimoto
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Publication of WO2006013970A1 publication Critical patent/WO2006013970A1/fr

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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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus including an expander for energy recovery.
  • Japanese Patent Laid-Open No. 2001-116371 discloses the following energy recovery type refrigeration cycle apparatus in the prior art.
  • a positive displacement expander that performs substantially isentropic expansion provided in a general refrigerant circuit is arranged coaxially with the compressor, and the energy recovered by the expander is used as power for the compressor.
  • the mass circulation amount of the refrigerant flowing through the compressor and the mass circulation amount of the refrigerant circulating through the expander must be equal, while the volume circulation amount passing through both is respectively Since it is determined by “cylinder volume X rotation speed”, the restriction of the constant density ratio shown in the following equation is imposed.
  • VC Volume circulation volume of refrigerant sucked into the compressor
  • VC and VE are values specific to the refrigeration cycle system, so VCZVE is It is a constant value.
  • Japanese Patent Laid-Open No. 2001-116371 solves this problem in the prior art.
  • a bypass circuit having a flow control valve interposed is provided in parallel with the expander. Then, by adjusting the flow rate of refrigerant flowing through the bypass circuit in response to changes in operating conditions, the flow rate of refrigerant passing through the expander is adjusted, and the constant density ratio and the restrictions on the refrigeration cycle are eliminated. To improve efficiency.
  • the refrigeration cycle apparatus has been made to solve the above-mentioned problems, and the first invention is a two-stage compression apparatus comprising a low-stage compressor and a high-stage compressor.
  • a decompressor including a radiator that cools the high-pressure gas refrigerant, an expander that expands the high-pressure refrigerant after being cooled by the radiator, an evaporator that evaporates the low-pressure refrigerant decompressed by the decompressor, and a decompression
  • a gas injection circuit that introduces the intermediate-pressure gas refrigerant decompressed by the apparatus to the suction side of the high-stage compression, and the expander and the low-stage compressor are connected coaxially.
  • the gas injection circuit for introducing the intermediate-pressure gas refrigerant to the suction side of the high-stage compressor is provided, the energy recovered in the expander that depressurizes the high-pressure gas refrigerant as compared with the prior arts 1 and 2. Although it decreases, the compression work in the two-stage compressor decreases. Further, the energy recovery efficiency in the prior art is not so great. Due to such factors, the present invention can improve the energy efficiency by reducing the energy consumption in the compressor.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 1.
  • FIG. 2 is a Mollier diagram of the refrigeration cycle apparatus.
  • FIG. 3 is a refrigeration (or cooling) COP ratio diagram in the refrigeration cycle apparatus according to Embodiment 1.
  • FIG. 4 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 2.
  • FIG. 5 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 3.
  • FIG. 6 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 4.
  • FIG. 7 is a Mollier diagram of the refrigeration cycle apparatus.
  • FIG. 8 is a hot water supply (or heating) COP ratio diagram in the refrigeration cycle apparatus according to Embodiment 5.
  • FIG. 9 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 6.
  • the refrigeration cycle apparatus includes a two-stage compressor 3 composed of a low-stage compressor 1 and a high-stage compressor 2.
  • the high-pressure gas refrigerant released from the compression device 3 is cooled by the radiator 4 and then separated by the gas-liquid separator 6 as an intermediate-pressure refrigerant decompressed by the expander 5.
  • the liquid separated from the gas by the gas-liquid separator 6 is depressurized to a low pressure by the expansion device 7 and then evaporated and evaporated by the evaporator 8 and sent to the suction port of the low-stage compressor 1 via the accumulator 9. .
  • the gas separated from the refrigerant liquid in the gas-liquid separator 6 is sent to the suction port of the high-stage compressor 2 through the gas injection circuit 10.
  • the low-stage and high-stage compressors 1 and 2 are constant capacity compressors such as a rotary compressor.
  • the low stage compressor 1 and the expander 5 are connected coaxially.
  • the flow rate of the circuit 10 may be appropriately set by adjusting the opening degree of the on-off valve 12 of the gas instruction circuit 10.
  • the opening degree of the flow control valve 13 of the bypass circuit 11 is controlled by the suction pressure of the low-stage compressor 1.
  • the flow control valve 13 is controlled so that the opening degree of the refrigerant is increased when the pressure of the refrigerant sucked into the low-stage compressor 1 increases.
  • the expander 5 and the expansion device 7 constitute a decompression device in the present invention.
  • the refrigeration cycle apparatus configured in this manner is filled with a refrigerant that forms a normal refrigeration cycle such as HFC32 or HFC32 (a refrigerant that does not form a supercritical refrigeration cycle) as a refrigerant.
  • the refrigerant (a5) decompressed to the intermediate pressure is gas-liquid separated by the gas-liquid separator 6.
  • the separated gas refrigerant (a8) is introduced to the suction side of the high-stage compressor 2 as described above and mixed with the discharge gas (al) of the low-stage compressor 1 (a2).
  • the liquid refrigerant (a7) separated by the gas-liquid separator 6 is decompressed by the expansion device 7 to become a low-pressure refrigerant (a8).
  • This low-pressure refrigerant is evaporated and evaporated by the evaporator 8 (a9), and is sucked into the low-stage compressor 1 through the accumulator 9.
  • the accumulator 9 separates and stores the liquid refrigerant that has not evaporated in the suction side of the low-stage compressor 1 to store the liquid refrigerant in the low-stage compressor 1. This is to prevent this.
  • the opening degree of the flow control valve 13 of the bypass circuit 11 is minimized (that is, (Closed state) to satisfy the constraint of a constant density ratio.
  • the flow control valve 13 corresponds to the increase. Control is performed to increase the amount of refrigerant circulation in the bypass circuit 11 by increasing the opening.
  • surplus refrigerant that does not pass through the expander 5 among the high-pressure refrigerant cooled by the radiator 4 is caused to flow to the gas-liquid separator 6 through the bypass circuit 11.
  • the high-pressure refrigerant is reduced to an intermediate pressure by the flow control valve 13 (a6).
  • it is mixed with the intermediate-pressure refrigerant that has flowed to the gas-liquid separator 6 via the expander 5 described above, and the gas-liquid separator 6 performs gas-liquid separation.
  • the density is controlled by providing the no-pass circuit 11 including the flow control valve 13 in parallel with the expander 5 and controlling the amount of bypass to increase in response to the increase in the evaporation temperature. Since the constant constraint force is also released, it is possible to prevent the Mollier diagram from becoming an inefficient vertical diagram, and to improve efficiency.
  • FIG. 3 shows that when the refrigeration cycle apparatus of Embodiment 1 is a refrigeration apparatus (or a cooling apparatus), the refrigeration (or cooling) COP ratio corresponding to the change in the evaporation temperature can be compared with the prior art. It shows.
  • the refrigeration (or cooling) COP ratio in this case refers to the refrigeration (or cooling) COP at each evaporating temperature of an old general refrigeration apparatus (or cooling apparatus) that does not perform energy recovery by the expander 5. This is expressed as the ratio of COP in the first and second embodiments.
  • the low-stage compressor 1 of the first embodiment is of a variable capacity type, and a bypass circuit 11 having a flow control valve 13 and an on-off valve 12 in the gas injection circuit 10 are provided. It is omitted. Further, the low-stage compressor 1 and the expander 5 are accommodated in the same casing 21. That is, the casing 21 is divided into two chambers by the partition wall 22, the low-stage compressor 1 is stored in one chamber 23, and the expander 5 is stored in the other chamber 24. The outlet port of the accumulator 9 is connected to the compressor chamber 23, and the low-stage compressor 1 sucks the refrigerant in the compressor chamber 23.
  • the Mollier diagram in this refrigeration cycle apparatus is partially different from FIG.
  • the Mollier diagram is also a diagram in which the broken line portion showing the substantially isenthalpy change (a4 ⁇ a6) by the flow control valve 13 is omitted in FIG. It becomes.
  • a variable capacity swash plate compressor is used as the variable capacity low stage compressor 1 described above.
  • variable-capacity low-stage compressor 1 is controlled as follows. That is, when the evaporation temperature is the lowest temperature in the allowable operating range (for example, ⁇ 35 ° C.), the rotation speed of the low-stage compressor 1 is set to be the maximum. When the evaporation load of the evaporator 8 increases, the suction pressure of the low-stage compressor 1 increases. The capacity of the low-stage compressor 1 is controlled to decrease in response to the increase in the suction pressure of the high-stage compressor 2 accompanying this.
  • the low-stage compressor 1 is used as a variable displacement compressor, and the capacity of the low-stage compressor 1 is controlled in response to changes in operating conditions.
  • the Mollier diagram can be prevented from becoming an inefficient vertical diagram.
  • the capacity of the low-stage compressor 1 as compared to the case where the expansion unit is bypassed and the constant density ratio is released as in the case of the first embodiment 1, The efficiency can be further improved.
  • the low-stage compressor 1 is a variable capacity swash plate compressor, the density ratio of the refrigerant flowing into the expander 5 and the density ratio of the refrigerant flowing into the high-stage compressor 2 And adjust steplessly Energy efficiency can be further improved.
  • the low-stage compressor 1, the gas-liquid separator 6, and the accumulator 9 of the second embodiment are integrated. That is, in the third embodiment, the lower part of the compressor chamber 23 is an accumulator.
  • the outlet port of the evaporator 8 is directly connected to the compressor chamber 23, and the low-stage compressor 1 directly sucks the refrigerant in the compressor chamber 23. Therefore, the liquid refrigerant returning from the evaporator 8 is stored in the lower part of the compressor chamber 23, so that the compressor chamber 23 also functions as an accumulator.
  • the expander chamber 24 is also used as a gas-liquid separator.
  • the outlet port of the expander 5 is opened in the expander chamber 24, and a part of the expander chamber 24 is connected to the evaporator 8 via the expansion device 7.
  • the intermediate pressure refrigerant that has passed through the expander 5 is discharged into the compressor chamber 23.
  • the intermediate-pressure refrigerant in the gas-liquid mixture is separated into gas and liquid by the difference in gravity in the space of the compressor chamber 23. Further, the separated liquid refrigerant flows out to the evaporator 8 through the expansion device 7.
  • the Mollier diagram of this embodiment is the same as that of Embodiment 2, and the energy efficiency with respect to the change in evaporation temperature is shown in FIG.
  • the stage side compressor 1 and the expander 5 are accommodated in the same casing 21 partitioned by the partition wall 22, and further, the low stage side compressor 1 is accommodated.
  • the compressor chamber 23 is also used as an accumulator. Therefore, in the refrigeration cycle apparatus according to the third embodiment, the apparatus is more compact and the accumulator can be installed in other units as compared to the case where the low-stage compressor 1, the expander 5 and the accumulator are individually manufactured and installed. Piping connected to equipment is simplified.
  • the expander chamber 24 containing the expander 5 is used as a gas-liquid separator, a low-stage compressor, an expander, a gas-liquid separator, and an accumulator are individually manufactured and attached. Compared to the refrigeration cycle device, the equipment is compact and the piping connecting these equipment is simplified.
  • the refrigeration cycle equipment consists of a two-stage compression device 3 consisting of a low-stage compressor 1 and a high-stage compressor 2, a radiator 4, a throttling device 31, a throttling device 31, an intermediate-pressure refrigerant and the remaining high-pressure refrigerant.
  • a heat exchanger 32 for exchanging heat with each other, an expander 33 for reducing the intermediate pressure refrigerant cooled by the heat exchanger 32 to a low pressure, an evaporator 8 and an accumulator 9 are configured.
  • the heat exchange 32 is connected to the high-pressure side path 32a through which the high-pressure refrigerant flows and the intermediate pressure-side path 32b through which the intermediate pressure refrigerant flows. And are arranged close to each other.
  • the inlet of the high-pressure side path 32 a of the heat exchanger 32 is connected to the outlet of the radiator 4, and the outlet of the high-pressure side path 32 a is connected to the expander 33.
  • the inlet of the intermediate pressure side passage 32b is connected to the expansion device 31, and the outlet is connected to the suction port of the high stage compressor 2 by the gas injection circuit 34.
  • the low-stage compressor 1 is a variable capacity swash plate compressor
  • the high-stage compressor 2 is a constant capacity compressor such as a single compressor.
  • the low-stage compressor 1 and the expander 33 are connected to the same shaft. It shall be filled with a refrigerant that forms a normal refrigeration cycle such as HFC32 or HFC32 (a refrigerant that does not form a supercritical refrigeration cycle).
  • radiator 4 (b4) A part of the high-pressure refrigerant (b4) cooled by the radiator 4 is decompressed to an intermediate pressure by the throttling device 31 under a pressure-reducing action of a substantially isenthalpy change (b
  • the decompressed refrigerant (b8) is vaporized by exchanging heat with the remaining high-pressure refrigerant by heat exchange (b
  • the high-pressure refrigerant (b5) cooled by the heat exchanger 32 is decompressed to a low pressure by undergoing a substantially isentropic change by the expander 33 (b6).
  • the energy recovered by the expander 33 is used as energy for rotating the low-stage compressor 1.
  • the low-pressure refrigerant (b6) evaporates and evaporates in the evaporator 8 (b7) and is sucked into the low-stage compressor 1.
  • the variable capacity low stage compressor 1 is controlled in the same manner as in the second embodiment.
  • the evaporation temperature is set to the lowest temperature within the allowable operating range (for example, -35 ° C)
  • the constant density ratio is restricted.
  • the evaporation load of the evaporator 8 increases and the suction pressure of the high-stage compressor 2 increases, the capacity of the low-stage compressor 1 is reduced corresponding to the increase.
  • the low-stage compressor 1 is a variable displacement swash plate compressor, and therefore, the density ratio on the suction side of the compressor is adjusted in response to changes in operating conditions. This prevents the Mollier diagram from becoming an inefficient vertical diagram.
  • the expander 33 expands the remaining high-pressure refrigerant after being cooled by the radiator 4 and the heat exchanger 32 to a low pressure between the high-pressure side path of the heat exchanger 32 and the evaporator 8. Is provided. Accordingly, energy corresponding to the decompression of the refrigerant is recovered by the expander 33. In this case, the energy recovered by the expander 33 is circulated to the high-stage compressor 2 through the gas injection circuit 34 as an intermediate pressure gas refrigerant. Accordingly, the amount of compression work in the low-stage compressor 1 is reduced by the amount of refrigerant circulating introduced into the high-stage compressor 2 via the heat exchanger 32, so that energy efficiency is improved.
  • This embodiment is a refrigeration cycle apparatus using carbon dioxide as a refrigerant in the refrigerant circuit of the first embodiment.
  • water is heated in the radiator 4 and the hot water obtained by this is used for hot water supply or heating.
  • the Mollier diagram in this case is a force supercritical cycle in the cycle as shown in Fig. 2, and the high-pressure refrigerant discharged from the high-stage compressor 2 outlet and the high-pressure refrigerant cooled by the radiator 4 are These are high-pressure gas refrigerants having a pressure higher than the critical point. Therefore, there is no room for liquid refrigerant in the high-pressure circuit, and the amount of refrigerant is adjusted by the accumulator 9.
  • the size of the accumulator 9 is set to a size that allows excess refrigerant to be stored.
  • FIG. 8 shows the effect of the hot water supply (or heating) COP ratio on the change in hot water temperature at the outlet of the radiator 4 (indirectly, change in high pressure) in the refrigeration cycle apparatus of the fifth embodiment.
  • the hot water (or heating) COP ratio in this case is defined as the hot water temperature at the condenser outlet of a hot water supply device (or heating device) that applies an old general refrigeration cycle device that does not recover energy by the expander 5.
  • FIG. 7 shows the ratio of the COP of Embodiment 5 to the hot water supply (or heating) COP when changed.
  • the hot water temperature at the radiator 4 outlet is low (that is, when the high pressure is low)
  • the suction pressure of the high-stage compressor 2 is also low, and the amount of refrigerant bypassed from the bypass circuit 11 is reduced. Therefore, the amount of energy recovered by the expander 5 increases, and the hot water supply (or heating) COP ratio increases.
  • the amount of reduction in compression energy in the two-stage compressor 3 is greater than the reduction in recovered energy by the expander 5.
  • the hot water supply (or heating) COP ratio increases.
  • a refrigeration cycle apparatus in the same refrigerant circuit as in the first embodiment, a non-displacement turbine type expander is used as the expander 5, and a non-displacement turbine type compressor is used as the low-stage compressor 1. is doing.
  • carbon dioxide can be used as a refrigerant as in the fifth embodiment.
  • the refrigeration cycle is a supercritical cycle.
  • the power using a variable capacity swash plate type compressor as the variable capacity low stage side compressor 1 is not limited to this, but is an inverter driven rotary compressor, etc. It can also be used as a compressor of other types using other capacity variable methods.
  • the force with which the low-stage compressor 1, the accumulator 9, the expander 5 and the gas-liquid separator 6 are combined is required to be integrated with each other. Absent. Any one of these can be integrated to simplify the equipment configuration and equipment connection piping.
  • the low stage compressor 1 is not a variable capacity compressor, but a fixed capacity compressor, and in parallel with the expander 33 as in the first embodiment, the flow rate A bypass circuit having a control valve may be provided to control the opening degree of the flow control valve to increase as the suction pressure of the high-stage compressor increases.
  • expansion devices 7 and 31 various devices such as an electric expansion valve, a capillary tube, and a temperature-sensitive expansion valve can be used.
  • a non-displacement type turbine expander as in the sixth embodiment may be used as the expander 5 or the low-stage compressor 1.
  • the combined starting load of the expander 5 and the low-stage compressor 1 can be reduced.
  • the expander 5 or the low-stage compressor 1 is a volumetric expander, for example, a rotary type, scroll type, screw type, vane type, swash plate type, or bankel type.
  • a helical type may be used.
  • a constant flow type gear type, roots type, or screw type may be used as the expander 5 or the low-stage compressor 1.
  • the load at startup is reduced.
  • a positive displacement compressor equipped with a starting load reducing device that can be used may be used to reduce the starting load of the low-stage compressor 1.
  • the starting load reducing device applicable in this case may be a general device such as a method of decelerating the number of rotations at the time of starting, or a method of reducing the suction volume. In this case, if a non-volumetric expander such as a turbine type is used as the expander, the starting load can be further reduced.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention est relative à un appareil à cycles de congélation comprenant un dispositif de compression à deux étages (3) possédant un compresseur bas (1) et un compresseur haut (2), un radiateur (4) pour refroidir un réfrigérant gazeux à haute pression, un dispositif de réduction de pression comprenant un dispositif de dilatation (5) pour dilater le réfrigérant à haute pression après qu'il ait été refroidi par le radiateur (4), un évaporateur (8) pour évaporer un réfrigérant à basse pression dont la pression est réduite par le dispositif de réduction de pression, et un circuit d'injection de gaz (10) pour introduire un réfrigérant gazeux à pression intermédiaire dont la pression est réduite par le dispositif de réduction de pression dans le côté d'aspiration du compresseur haut (2). Le dispositif de dilatation (5) et le compresseur bas (1) sont connectés d'une façon coaxiale.
PCT/JP2005/014416 2004-08-06 2005-08-05 Appareil a cycles de congelation WO2006013970A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2004231629 2004-08-06
JP2004-231629 2004-08-06
JP2004-285343 2004-09-29
JP2004285343A JP2006071257A (ja) 2004-08-06 2004-09-29 冷凍サイクル装置

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Publication Number Publication Date
WO2006013970A1 true WO2006013970A1 (fr) 2006-02-09

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101162756B1 (ko) * 2007-02-24 2012-07-05 삼성전자주식회사 수냉식 공기조화기 및 그 제어방법
JP4997024B2 (ja) * 2007-08-28 2012-08-08 日立アプライアンス株式会社 ヒートポンプ給湯装置
CN102257332B (zh) * 2008-12-22 2013-08-14 松下电器产业株式会社 制冷循环装置
JP2011153825A (ja) * 2011-05-20 2011-08-11 Mitsubishi Electric Corp 冷凍空調装置
WO2015198475A1 (fr) * 2014-06-27 2015-12-30 三菱電機株式会社 Dispositif à cycle frigorifique

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JPS5855655A (ja) * 1981-09-30 1983-04-02 株式会社東芝 冷凍サイクル用タ−ビン
JPS62228843A (ja) * 1986-03-31 1987-10-07 株式会社東芝 冷凍サイクル
JP2001141315A (ja) * 1999-11-10 2001-05-25 Aisin Seiki Co Ltd 冷凍空調機
JP2003074999A (ja) * 2001-08-31 2003-03-12 Daikin Ind Ltd 冷凍機
JP2004101033A (ja) * 2002-09-06 2004-04-02 Hoshizaki Electric Co Ltd 冷却貯蔵庫の冷凍回路
JP2004150749A (ja) * 2002-10-31 2004-05-27 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
JP2004183913A (ja) * 2002-11-29 2004-07-02 Mitsubishi Electric Corp 空気調和機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5855655A (ja) * 1981-09-30 1983-04-02 株式会社東芝 冷凍サイクル用タ−ビン
JPS62228843A (ja) * 1986-03-31 1987-10-07 株式会社東芝 冷凍サイクル
JP2001141315A (ja) * 1999-11-10 2001-05-25 Aisin Seiki Co Ltd 冷凍空調機
JP2003074999A (ja) * 2001-08-31 2003-03-12 Daikin Ind Ltd 冷凍機
JP2004101033A (ja) * 2002-09-06 2004-04-02 Hoshizaki Electric Co Ltd 冷却貯蔵庫の冷凍回路
JP2004150749A (ja) * 2002-10-31 2004-05-27 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
JP2004183913A (ja) * 2002-11-29 2004-07-02 Mitsubishi Electric Corp 空気調和機

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