WO2002077543A1 - Systeme de congelation faisant appel a un refrigerant melange de type non azeotropique - Google Patents

Systeme de congelation faisant appel a un refrigerant melange de type non azeotropique Download PDF

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Publication number
WO2002077543A1
WO2002077543A1 PCT/JP2001/002440 JP0102440W WO02077543A1 WO 2002077543 A1 WO2002077543 A1 WO 2002077543A1 JP 0102440 W JP0102440 W JP 0102440W WO 02077543 A1 WO02077543 A1 WO 02077543A1
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WO
WIPO (PCT)
Prior art keywords
temperature
refrigerant
compressor
pressure
working fluid
Prior art date
Application number
PCT/JP2001/002440
Other languages
English (en)
Japanese (ja)
Inventor
Toshio Seino
Original Assignee
Dairei Co.,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
Priority to JP27919299A priority Critical patent/JP2001099498A/ja
Application filed by Dairei Co.,Ltd. filed Critical Dairei Co.,Ltd.
Priority to PCT/JP2001/002440 priority patent/WO2002077543A1/fr
Publication of WO2002077543A1 publication Critical patent/WO2002077543A1/fr

Links

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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • 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
    • F25B2400/23—Separators

Definitions

  • the present invention relates to a refrigeration system such as a refrigerator unit.
  • CFCs have been widely used as refrigerants for freezers and refrigerators because of their excellent properties.However, CFCs containing chlorine destroy the ozone layer in the upper atmosphere, and many CFCs are greenhouse gases. These fluorocarbons are becoming internationally regulated and unusable because of their influence on dani. In response, attempts have been made to use so-called alternative chlorofluorocarbons that do not cause depletion of the ozone layer and are less affected by the greenhouse effect, and the development of new hydrocarbon-based refrigerants to replace these chlorofluorocarbon-based refrigerants has been promoted. ing.
  • the composition of the non-azeotropic refrigerant mixture and the type of each component substance can be selected widely, but the phase change characteristics of the non-azeotropic refrigerant mixture are constant at a dew point curve and a boiling point curve separated from each other. Liquefaction under the conditions of The start temperature and the liquefaction end temperature or the gasification start temperature and the vaporization end temperature are different.
  • cryogenic refrigerator system uses a non-azeotropic refrigerant mixture composed of two or more components, and the liquefaction of components with a low boiling point and a low critical temperature is necessary for the ability of the condenser to operate at room temperature. Because of the difficulty, a multi-component system that condenses in multiple stages for each component refrigerant is used.
  • Fig. 3 shows an example of this, in which a mixed refrigerant consisting of three types of refrigerants with different boiling points was used, and the mixed refrigerant compressed by one compressor (compressor) 1 was released through a condenser 2 Later, the first refrigerant having a higher boiling point is used for condensing a second refrigerant having a lower boiling point, and the second refrigerant is used for condensing a refrigerant having a lower boiling point which achieves a desired cooling temperature.
  • the first and second refrigerants are separated by gas-liquid separators 6 and 8, respectively, are passed through a throttle valve 4, and are cooled by heat exchange 7 and 9. To condense.
  • the third refrigerant having the lowest boiling point is vaporized by the evaporator 5 via the throttle valve 4 and cools the inside of the cooling tank (freezer) 50 to a desired temperature.
  • the present invention relates to a refrigeration system using a non-azeotropic mixed refrigerant containing two or more refrigerant components, wherein evaporation in a circulation path returning to the compressor via a compressor, a condenser, a throttle valve, and an evaporator.
  • This is a refrigeration system characterized by cooling the working fluid from the condenser to the throttle valve with a low-temperature working fluid that returns from the compressor to the compressor to promote liquefaction of low-boiling components.
  • a low-temperature working fluid that cools the working fluid between the evaporator and the throttle valve
  • the cooling ability is effectively improved by making the liquid high boiling point component wet, and the working fluid from the condenser to the throttle valve is cooled by the low-temperature working fluid returning from the evaporator to the compressor.
  • the discharge pressure of the working fluid from the compressor can be reduced.
  • the critical temperature of at least one component of the non-azeotropic mixed refrigerant is substantially equal to or lower than room temperature, it is possible to easily realize a refrigerator system capable of achieving an extremely low temperature.
  • FIG. 1 is a configuration diagram schematically showing a refrigerator system of the present invention
  • FIG. 2 is a comparative example showing a prior art of the present invention
  • FIG. Three-way system Indicates a refrigerator system.
  • FIG. 1 is a conceptual diagram of one embodiment of a refrigerator system of the present invention, in which a working fluid composed of a non-azeotropic mixed refrigerant adiabatically compressed by a compressor 1 radiates heat in a condenser 2.
  • the liquid is cooled to approximately room temperature and liquefied, passed through the drier 3 and sent to the evaporator 5 through the throttle valve 4 to expand and absorb, absorb the heat in the freezer, and return to the compressor again.
  • the working fluid returning to the machine is at a low temperature, which is approximately the same as the internal temperature.
  • a heat exchanger 10 is installed in the path between the dryer and the throttle valve shown in the figure to mix before entering the throttle valve 4.
  • the refrigerant can be effectively cooled to lower the temperature to a temperature equal to or lower than room temperature.
  • Such a refrigerator system having a heat exchanger between the compressor and the evaporator has been often used in the past (for example, “Refrigeration and Air Conditioning” by Haruo Yamada, Yokendo Co., Ltd.) In this case, the seventh edition was issued on June 10, 1965, p. 77) .In this way, the gas coming from the evaporator was heated by the liquid high-temperature refrigerant and entered the compressor, while the liquid was deflected. The high-temperature refrigerant is supercooled well below the saturation temperature and enters the throttle valve without any residual gas mixed therein, and both the compressor and the evaporator can operate smoothly. However, these are performed in a single-component refrigerant, and are nothing more than the use of sensible heat to smooth the operation cycle of such a refrigerator.
  • the boiling point curve and the dew point curve are separated as described above.
  • the cooling in the step shifts the composition of the liquid phase toward the low-boiling-point refrigerant side, and the decrease in the vapor pressure due to the cooling suppresses the temperature rise during adiabatic compression, thereby further promoting this effect.
  • the boiling point differs depending on the composition of the liquid phase, and the boiling point of the mixed refrigerant on the lower boiling point side is lower.
  • the refrigerant which has shifted to the lower boiling point side composition has the maximum refrigeration capacity in the evaporation process. Can be demonstrated.
  • the refrigerant thus cooled in the condensing process has a reduced vapor pressure in accordance with the temperature thereof, so that the condensing process proceeds quickly at a lower pressure, and the operation of the entire refrigerator system is performed at a relatively low pressure.
  • «It is possible.
  • the discharge pressure of the compressor can be reduced, and the load can be reduced.
  • Combining a refrigerant with a higher boiling point and a critical temperature with respect to such a refrigerant having a lower boiling point, which can be easily condensed using a condenser operating at room temperature, is composed of two or more refrigerants.
  • a mixed refrigerant it is possible to easily exhibit ultra-low-temperature refrigeration capacity by a single-unit simple-structure refrigerator system using a condenser that operates at room temperature.
  • the feedback function works effectively in combination with increasing the cooling capacity using heat and sensible heat, so that a stable state can be maintained during steady-state operation, as well as easy start-up and quick steady state at the start of operation. It is possible to go into operation.
  • Such a feature of the refrigerator system of the present invention is that the temperature of the mixed refrigerant that cools the working fluid in front of the throttle valve and returns to the compressor is increased immediately before the compressor by heat exchange. Nevertheless, it can be seen that both the temperature and pressure at the compressor outlet are decreasing. That is, since the discharge pressure of the compressor is significantly reduced, the temperature rise due to adiabatic compression is suppressed, and such a process is immediately fed back to the refrigeration cycle.
  • the mixed refrigerant before entering the compressor is heated by heat exchange to increase the specific volume.
  • the remaining multi-phase liquid phase of the high-boiling components is also absorbed and does not hinder the operation of the compressor. State.
  • a commercially available double-walled copper pipe was 3 m long, and the outer pipe was returned and used as a refrigerant flow path.
  • Table 1 shows the pressure and temperature during these actual operation. Table 1: Temperature and pressure of each part of the refrigerator system (butane + R-116)
  • Example Discharge pressure and suction pressure are absolute values measured before and after the compressor.
  • Discharge pressure A
  • Discharge temperature A
  • Suction pressure B
  • Return temperature B
  • Heat exchange inlet temperature C
  • Heat exchange outlet temperature E
  • Evaporator inlet temperature G
  • Table 1 As shown in the figure, the return refrigerant used for cooling the refrigerant immediately before the throttle valve absorbs the heat of the refrigerant from the condenser and, as shown in the return temperature column, immediately before the compressor, has a 13.2-- Although the temperature rises by 9.4 ° C, the temperature after it is adiabatically compressed by the compressor decreases by 7.2 to 4.2 ° C.
  • Table 2 shows the relationship between the refrigerant temperature and the charge at the heat inlet and outlet.
  • Table 2 Relationship between refrigerant charge, discharge pressure and return refrigerant temperature
  • butane having a high boiling point circulates without being completely evaporated, and the wet gas containing the irreversible benzene reaches the heat exchanger, and the refrigerant from the compressor in the heat exchanger is removed.
  • the refrigerant By vaporizing through heat exchange, it greatly contributes to cooling of the refrigerant.
  • This state often occurs in a refrigerator system that normally uses a non-azeotropic mixed refrigerant, and is in a state called frost.
  • frost forms around the piping from the evaporator to the compressor, causing damage to the refrigeration equipment. Also.
  • the present invention not only eliminates this frosting phenomenon, but also significantly reduces the discharge pressure by utilizing the cooling capacity of the return refrigerant component that does not contribute to the refrigeration capacity, thereby reducing the load. Can be improved.
  • Table 3 shows the physical properties of R-116, butane.
  • the butane-R23 mixed refrigerant was replaced with a refrigerator system model F-14 (manufactured by UN I DAD).
  • the temperature and pressure at each part A to H of the refrigerator system were measured while changing the filling amount of the refrigerator in the range of 140 to 270 g.
  • Discharge pressure and suction pressure are absolute values measured before and after the compressor.
  • the boiling point of R23 is lower than that of R-116, and the critical temperature is high.
  • the vapor pressure is extremely high, but the temperature and pressure of the condensing process rise even for these mixed refrigerants. Therefore, it is difficult to use with the capacity of the conventional refrigerator.
  • the temperature of the return refrigerant in the heat exchange significantly decreases as the refrigerant charge increases, and in conjunction with these, the discharge pressure and the heat exchange ⁇ outlet It can be seen that the temperature of the refrigerant drops significantly. In this way, the refrigeration capacity of the butane R23-based refrigerant can be maximized. In this case, as in the case described above, there is an almost constant appropriate range in the cooling capacity of the returned refrigerant from the filling amount, and the refrigeration capacity does not improve even if the filling amount of the refrigerant is further increased.
  • the principle of the present invention is that, as seen from the boiling point curve of the gas-liquid equilibrium curve of the mixed refrigerant, the composition of the liquid phase shifts to the low boiling point component side as the temperature decreases in the condensation process of the non-azeotropic mixed refrigerant.
  • it utilizes the fact that the boiling point of the liquid phase also decreases, thereby making it possible to further lower the refrigeration temperature and significantly reduce the required compression pressure to significantly improve the refrigeration capacity. be able to.
  • these effects are obtained by using a refrigerant with a low boiling point or a high vapor pressure that cannot be liquefied at room temperature as a mixed refrigerant.
  • the type and number of these refrigerants are selected based on the relationship between the boiling point, critical temperature and critical pressure according to the target refrigerator maintenance temperature and the capacity of the refrigerator compressor, etc. And can be appropriately combined.
  • the configuration of the refrigeration system is basically based on the above embodiment, and for a lower temperature use, a heat exchange structure with a larger capacity may be used to promote the condensation process of the low-temperature boiling point refrigerant in the heat exchanger.
  • a spiral tube or a laminated structure may be used instead of the double tube.
  • the refrigeration system according to the present invention can achieve an ultra-low temperature efficiently with a simple configuration, and can be widely used in various fields such as preservation of biological tissue for medical use. it can.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente invention concerne un système de machine de congélation faisant appel à un réfrigérant mélangé de type non azéotropique contenant au moins deux composants réfrigérants, dans lequel au moyen d'un fluide actif à basse température, qui est présent dans un passage de circulation s'étendant à travers un compresseur (1), un condensateur (2), une soupape d'étranglement (4) et un évaporateur (5) avant de retourner vers le compresseur et qui retourne de l'évaporateur vers le compresseur, le fluide actif présent dans une zone s'étendant du condensateur à la soupape d'étranglement, est refroidi par un échangeur thermique (10), diminuant ainsi la température et la pression de vapeur du réfrigérant, diminuant également ainsi la température et la pression lors des étapes de compression et de condensation, diminuant ainsi la pression de travail du système de machine de congélation, favorisant la condensation et la liquéfaction des composants réfrigérants en faible ébullition, à pression de vapeur élevée. Par conséquent, il est possible de diminuer la pression de travail du système de machine de congélation et d'obtenir facilement des températures cryogéniques à l'aide d'un réfrigérant à pression critique élevée, à température critique basse comme composant réfrigérant mélangé.
PCT/JP2001/002440 1999-09-30 2001-03-27 Systeme de congelation faisant appel a un refrigerant melange de type non azeotropique WO2002077543A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP27919299A JP2001099498A (ja) 1999-09-30 1999-09-30 非共沸系混合冷媒を用いた冷凍システム
PCT/JP2001/002440 WO2002077543A1 (fr) 1999-09-30 2001-03-27 Systeme de congelation faisant appel a un refrigerant melange de type non azeotropique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP27919299A JP2001099498A (ja) 1999-09-30 1999-09-30 非共沸系混合冷媒を用いた冷凍システム
PCT/JP2001/002440 WO2002077543A1 (fr) 1999-09-30 2001-03-27 Systeme de congelation faisant appel a un refrigerant melange de type non azeotropique

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WO2002077543A1 true WO2002077543A1 (fr) 2002-10-03

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1577619A1 (fr) * 2002-12-03 2005-09-21 Nihon Freezer Co., Ltd. Systeme refrigerant a melange non-azeotrope, et melange non-azeotrope pour tres basses temperatures utilise pour ce systeme
EP1669694A1 (fr) * 2003-09-05 2006-06-14 Daikin Industries, Ltd. Congelateur

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001099498A (ja) * 1999-09-30 2001-04-13 Dairei:Kk 非共沸系混合冷媒を用いた冷凍システム
JP2003013050A (ja) * 2001-07-03 2003-01-15 Nihon Freezer Kk ３成分系超低温用冷媒
JP2003013049A (ja) * 2001-07-03 2003-01-15 Nihon Freezer Kk ３成分系超低温用冷媒
KR100833696B1 (ko) * 2005-04-13 2008-05-29 니혼 프리자 가부시키가이샤 비공비 냉매를 이용한 냉동기 시스템 및 그 시스템을이용하는 초 저온용 비공비 냉매
JP6957026B2 (ja) * 2018-05-31 2021-11-02 伸和コントロールズ株式会社 冷凍装置及び液体温調装置

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06241589A (ja) * 1992-12-04 1994-08-30 Mitsuhiro Kanao 機器内のフロン対策方法
JPH06317358A (ja) * 1993-05-07 1994-11-15 Hitachi Ltd 冷凍装置
JPH0748562A (ja) * 1993-08-05 1995-02-21 Nippon Furiithe- Kk フルオロカーボン系混合冷媒
JPH0748563A (ja) * 1993-08-03 1995-02-21 Tabai Espec Corp 混合冷媒
JPH08166172A (ja) * 1994-12-14 1996-06-25 Sanyo Electric Co Ltd 冷凍装置
JPH09151370A (ja) * 1995-11-30 1997-06-10 Asahi Glass Co Ltd 混合冷媒およびこれを用いる冷却装置
JPH10332212A (ja) * 1997-06-02 1998-12-15 Toshiba Corp 空気調和装置の冷凍サイクル
JP2000205676A (ja) * 1998-12-30 2000-07-28 Praxair Technol Inc 冷凍を提供する方法
JP2001099498A (ja) * 1999-09-30 2001-04-13 Dairei:Kk 非共沸系混合冷媒を用いた冷凍システム

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06241589A (ja) * 1992-12-04 1994-08-30 Mitsuhiro Kanao 機器内のフロン対策方法
JPH06317358A (ja) * 1993-05-07 1994-11-15 Hitachi Ltd 冷凍装置
JPH0748563A (ja) * 1993-08-03 1995-02-21 Tabai Espec Corp 混合冷媒
JPH0748562A (ja) * 1993-08-05 1995-02-21 Nippon Furiithe- Kk フルオロカーボン系混合冷媒
JPH08166172A (ja) * 1994-12-14 1996-06-25 Sanyo Electric Co Ltd 冷凍装置
JPH09151370A (ja) * 1995-11-30 1997-06-10 Asahi Glass Co Ltd 混合冷媒およびこれを用いる冷却装置
JPH10332212A (ja) * 1997-06-02 1998-12-15 Toshiba Corp 空気調和装置の冷凍サイクル
JP2000205676A (ja) * 1998-12-30 2000-07-28 Praxair Technol Inc 冷凍を提供する方法
JP2001099498A (ja) * 1999-09-30 2001-04-13 Dairei:Kk 非共沸系混合冷媒を用いた冷凍システム

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1577619A1 (fr) * 2002-12-03 2005-09-21 Nihon Freezer Co., Ltd. Systeme refrigerant a melange non-azeotrope, et melange non-azeotrope pour tres basses temperatures utilise pour ce systeme
EP1577619A4 (fr) * 2002-12-03 2010-06-23 Nihon Freezer Co Ltd Systeme refrigerant a melange non-azeotrope, et melange non-azeotrope pour tres basses temperatures utilise pour ce systeme
EP1669694A1 (fr) * 2003-09-05 2006-06-14 Daikin Industries, Ltd. Congelateur
EP1669694A4 (fr) * 2003-09-05 2009-04-08 Daikin Ind Ltd Congelateur
US7640762B2 (en) 2003-09-05 2010-01-05 Daikin Industries, Ltd. Refrigeration apparatus

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