US20060186370A1 - Refrigerant composition for refrigeration systems - Google Patents

Refrigerant composition for refrigeration systems Download PDF

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Publication number
US20060186370A1
US20060186370A1 US11/331,824 US33182406A US2006186370A1 US 20060186370 A1 US20060186370 A1 US 20060186370A1 US 33182406 A US33182406 A US 33182406A US 2006186370 A1 US2006186370 A1 US 2006186370A1
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United States
Prior art keywords
refrigerant
molar percent
refrigeration
composition
refrigerant composition
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Abandoned
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US11/331,824
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English (en)
Inventor
Venkatarathanam Gandhiraju
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Indian Institutes of Technology
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Individual
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Assigned to INDIAN INSTITUTE OF TECHNOLOGY reassignment INDIAN INSTITUTE OF TECHNOLOGY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: VENKATARATHANARTH GANDHIRAJU
Publication of US20060186370A1 publication Critical patent/US20060186370A1/en
Assigned to INDIAN INSTITUTE OF TECHNOLOGY reassignment INDIAN INSTITUTE OF TECHNOLOGY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GADHIRAJU, VENKATARATHANAM
Priority to US11/851,100 priority Critical patent/US7582223B2/en
Abandoned legal-status Critical Current

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    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
    • C09K5/02—Materials undergoing a change of physical state when used
    • C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
    • C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
    • C09K5/042—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising compounds containing carbon and hydrogen only
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/10—Components
    • C09K2205/13—Inert gases
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/10—Components
    • C09K2205/132—Components containing nitrogen

Definitions

  • the present invention relates to a refrigerant composition for refrigeration systems, more particularly precooled mixed refrigeration systems with phase separators. Further, the present invention describes the process for refrigeration using the said refrigerant composition.
  • Simple refrigeration systems use a method called vapor compression cycle.
  • the vapor compression cycle is a method in which a compressor such as a piston compressor compresses a low-pressure refrigerant vapor.
  • a condenser condenses the warm compressed vapor, resulting in a partial or complete condensation of the vapor.
  • This condensed refrigerant then passes through a fine capillary tube or other constriction into a larger chamber at low pressure. As the refrigerant enters the larger chamber, it evaporates and absorbs heat, resulting in the vapor.
  • This refrigerant vapor is then routed to the intake of the compressor, thus closing the cycle. This is the so-called closed loop refrigeration system.
  • a single stage refrigerant system is used to achieve temperatures up to ⁇ 40° C.
  • temperatures in the range ⁇ 50° C. to ⁇ 80° C. a two-stage cascaded vapor compression system has been proposed. This method uses a single refrigerant per stage and two compressors, one for each stage. For still lower refrigeration temperatures, more cascaded stages are required.
  • four stage cascade vapor compression systems are proposed for reaching cryogenic temperatures, lower than ⁇ 150 ° C.
  • the low temperatures can be achieved using different process systems, some employing one or more phase separators and some that don't employ any phase separators.
  • Systems that employ phase separators are commonly known as multistage mixed refrigerant systems, and those that don't employ phase separators as single stage mixed refrigerant systems.
  • the high pressure refrigerant is cooled to a low temperature and expanded to a low pressure to provide the necessary refrigeration to cool a load.
  • the low pressure refrigerant leaving the evaporator provides the necessary refrigerant to cool the high pressure refrigerant to low temperatures.
  • Phase separators are employed to remove some of the high boiling point components and lubricating oil carried over from the compressor from reaching low temperatures where they may freeze.
  • the liquid consists mostly of the high boiling point components, and the vapour phase preferably does not contain any high boiling components.
  • the liquid is expanded to a lower pressure, mixed with the low pressure refrigerant returning from the evaporator at an intermediate temperature and returned to the compressor.
  • the expanded liquid also provides the necessary cooling to coo: and condense the vapour stream leaving the phase separator.
  • the use of phase separators also allow balancing the refrigeration needed to cool the high pressure refrigerant at different temperatures.
  • Precooling can be used in both single and multistage mixed refrigerant systems. Precooling essentially allows the system to operate at nearly same efficiency at all ambient temperatures.
  • phase separators reduces the oil carried over to the low temperatures and improves the reliability of the system.
  • the use of both phase separators and precooling improves the system reliability considerably by removing part of the oil carried over at low temperatures.
  • the present invention relates to a refrigerant composition for multistage refrigeration systems precooled to a temperature at least 20 K below the ambient temperature, and more preferably precooled to a temperature of 230 to 260 K.
  • the refrigerant composition depends on the type of system employed, the temperature at which precooling is done and whether phase separators are used or not.
  • the refrigerant composition leaving the compressor is cooled in its entirety to the refrigeration temperature.
  • part of the refrigerant returns back to the compressor at temperatures much above the refrigeration temperature.
  • the refrigerant composition compressed by the compressor in phase separator systems therefore needs to be different from that used with out phase separators.
  • composition of refrigerants for use in precooled multi stage mixed refrigerant systems to provide refrigeration below 110 Kelvin.
  • Applications for such composition of refrigerants include household or commercial refrigeration systems such as refrigerators, freezers, electronic circuit cooling, medical applications, cryo-vacuum pumps, storing of biological specimens and tissues at low temperatures, cooling of Gamma-ray, Infra Red and X-ray detectors, cryosurgery and the like.
  • the main object of the present invention is to provide a refrigerant composition for refrigeration systems, more particularly precooled multistage mixed refrigeration systems with phase separators.
  • the present invention provides a refrigerant composition which passes through a compressor of a precooled multi stage mixed refrigeration system with one or more phase separators comprising: more than 36 molar percent but less than 60 molar percent of Nitrogen, 15 to 40 molar percent of Methane, 5 to 30 molar percent of Ethane, Ethylene or combinations thereof, 0.1 to 20 molar percent of propane, n-Butane, Iso-Butane and combinations thereof, and up to 20 molar percent of Neon, Helium and combinations thereof.
  • the molar percent of nitrogen is preferably greater than 36 molar percent and less than 50 molar percent.
  • the molar percent of methane is preferably greater than 15 molar percent and less than 30 molar percent.
  • the molar percent of Ethane, Ethylene or combinations thereof is preferably in the range of 15 to 30 molar percent.
  • the Inventors have ascertained that a new combination of refrigerants as defined herein results in an efficient cooling system (higher refrigeration capacity, or higher efficiency or both) for precooled single and multistage mixed refrigerant systems with one or more phase separators.
  • the advantages in using the disclosed refrigerant composition are illustrated with the help of four examples. The following are common for all the examples for a precooled multistage system shown in FIG. 1 .
  • the system shown in FIG. 1 can largely be divided into two parts, those that operate at temperatures greater than the precooling temperature, say 230 K and those that operate lower than the precooling temperature.
  • the parts of the system which are less than the precooling temperature is designated as the cold box in FIG. 1 , for the sake of convenience (In reality all the parts below ambient temperature can be placed inside an insulated cold box).
  • the low-pressure refrigerant composition (via line 12 ) is compressed in a compressor 100 .
  • the compressor can be a reciprocating, rotary piston, or other types normally employed in refrigeration and air conditioning systems.
  • the compressed refrigerant leaving the compressor via line 14 is cooled to ambient temperature in an after cooler and further cooled to the precooling temperature in a precooling system.
  • oil separators needs to be used if oil lubricated compressors are used.
  • the oil separation system, aftercooler and the precooling system are collectively designated as 102 in FIG. 1 .
  • a two stream heat exchanger where heat transfer occurs between the high and low pressure mixed refrigerant streams, can also be used between the after cooler and the precooler.
  • no heat exchanger has been assumed between the precooling system and the aftercooler.
  • the low pressure refrigerant leaving the mixed refrigerant system via line 12 is passed to the compressor directly.
  • a part of the high pressure refrigerant entering the cold box through line 16 is in the liquid phase and the rest in the vapour phase at this stage.
  • the liquid and vapour phases are separated in a phase separator 104 .
  • the high pressure vapour separated in the phase separator is passed to the first of the two heat exchangers, 106 .
  • the liquid separated from the phase separator (line 30 ) is expanded and mixed with the low pressure stream in line 28 .
  • the high pressure vapour stream (line 18 ) is cooled to a low temperature in the two heat exchangers 106 and 108 , and is expanded to a lower pressure in a throttling device 110 .
  • the low temperature and low pressure refrigerant provides the refrigeration to cool the load in the evaporator 112 .
  • the low pressure refrigerant leaving the evaporator 26 warms up in the two heat exchangers, and cools the high pressure refrigerant.
  • the low pressure refrigerant leaving 106 is passed to the compressor where it gets compressed to a higher pressure, thus completing the cycle.
  • the refrigerating temperature is considered to be the temperature of the refrigerant leaving the evaporator, and the ambient temperature is 300 K.
  • ex hp refers to the exergy of the high pressure refrigerant leaving the precooler via line 16 and entering the coldbox of the multistage refrigeration system
  • ex lp,out refers to the exergy of the low pressure stream leaving the refrigeration system to the compressor inlet via line 12 , in Joules per mol.
  • the table shows the refrigerant compositions passing through the compressor of a precooled multistage refrigeration systems described above at different operating conditions.
  • the minimum temperature difference in each of the heat exchanger and other operating/design conditions assumed to arrive at the above compositions is also given.
  • the compositions were arrived at for a compressor with a certain volumetric efficiency characteristic. The compositions will be different when the operating/design conditions and hardware such as the compressor used are different.
  • ⁇ T min refers to the minimum temperature approach between the streams in the heat exchangers 106 or 108 .
  • T JT,in is the temperature of the high pressure stream entering expansion device 110 via line 22 .
  • composition being claimed is workable only in precooled multistage mixed refrigerant system, although composition with minor changes could be workable in other refrigerant systems also but same has not been tried. It should be understood that the use of a refrigerant composition that falls within the claims in this specification is not to be taken in isolation, but in conjunction with other parameters such as those indicated below to achieve a high efficiency and high refrigeration. Only an appropriate composition can result in optimum performance. The efficiency and the quantity of refrigeration obtained from different systems depend not only on the type of refrigerant composition employed, but also on the hardware used as well as operating parameters such as the operating pressures used etc.
  • the type of system to be employed depends on several factors such as the temperature at which refrigeration is needed, type of lubricating oil used, type of oil separation/filtration systems used, compressor used, the quantity of refrigeration required, the type of precooler employed, the efficiency of the precooler etc.
  • the optimum composition for one type of system may not be optimum for other type of systems, operating temperatures and pressures.
  • the components used in the refrigerant composition also depend on other factors as well. For example, some refrigerant components may freeze at low temperatures. The complete refrigerant may also freeze at a certain temperature.
  • the refrigerant compositions claimed in this specification will result in high exergy efficiency and/or high refrigeration.
  • the methods to decide on the type of system to be employed, type of hardware and operating conditions and the components to be used in a composition are generally known to those practising the art of mixed refrigerant technology.
  • the minimum temperature approach between the streams was assumed to be 8 K, the same assumed in all the cases in Table 1.
  • the precooling temperature was assumed to be 243 K in the case of pure fluids.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Thermal Sciences (AREA)
  • Materials Engineering (AREA)
  • Organic Chemistry (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Lubricants (AREA)
  • Sorption Type Refrigeration Machines (AREA)
US11/331,824 2003-07-15 2006-01-16 Refrigerant composition for refrigeration systems Abandoned US20060186370A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/851,100 US7582223B2 (en) 2003-07-15 2007-09-06 Refrigerant composition for refrigeration systems

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
IN573/CHE/2003 2003-07-15
IN573CH2003 2003-07-15
PCT/IB2004/002283 WO2005005569A1 (fr) 2003-07-15 2004-07-14 Composition refrigerante pour systemes de refrigeration

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PCT/IB2004/002283 Continuation WO2005005569A1 (fr) 2003-07-15 2004-07-14 Composition refrigerante pour systemes de refrigeration

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US11/851,100 Division US7582223B2 (en) 2003-07-15 2007-09-06 Refrigerant composition for refrigeration systems

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US11/851,100 Expired - Fee Related US7582223B2 (en) 2003-07-15 2007-09-06 Refrigerant composition for refrigeration systems

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WO (1) WO2005005569A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080053145A1 (en) * 2003-07-15 2008-03-06 Indian Institute Of Technology Refrigerant composition for refrigeration systems

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100140286A1 (en) * 2008-12-08 2010-06-10 Michael Christopher Quinn Portable beverage machine
WO2011150940A1 (fr) * 2010-06-03 2011-12-08 Arctiko A/S Système de refroidissement et mélange non azéotrope de fluides frigorigènes constitué de fluides frigorigènes respectueux de l'environnement
EP3162870A1 (fr) * 2015-10-27 2017-05-03 Linde Aktiengesellschaft Réfrigérant mélangé basse température pour pré-refroidissement d'hydrogène à grande échelle
CN112831314A (zh) * 2020-12-25 2021-05-25 青岛营上电器有限公司 一种自复叠制冷低温级混合制冷剂

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5441658A (en) * 1993-11-09 1995-08-15 Apd Cryogenics, Inc. Cryogenic mixed gas refrigerant for operation within temperature ranges of 80°K- 100°K
US5706663A (en) * 1995-11-20 1998-01-13 Apd Cryogenics, Inc. High efficiency throttle cryogenic refrigerator based on one stage compressor
US5875651A (en) * 1997-06-12 1999-03-02 Apd Cryogenics, Inc. Low vibration throttling device for throttle-cycle refrigerators
US6463744B1 (en) * 1998-05-12 2002-10-15 Messer Griesheim Gmbh Method and device for producing cold
US6513338B1 (en) * 1998-05-12 2003-02-04 Messer Griesheim Gmbh Refrigerant mixture for a mixture-throttling process

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1336982A (en) * 1970-11-25 1973-11-14 Flinn D Power packs
GB1336892A (en) 1971-05-17 1973-11-14 Nii Kriogennoi Elektroniki Refrigerant for a cryogenic throttling unit
WO2005005569A1 (fr) 2003-07-15 2005-01-20 Indian Institute Of Technology Composition refrigerante pour systemes de refrigeration

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5441658A (en) * 1993-11-09 1995-08-15 Apd Cryogenics, Inc. Cryogenic mixed gas refrigerant for operation within temperature ranges of 80°K- 100°K
US5706663A (en) * 1995-11-20 1998-01-13 Apd Cryogenics, Inc. High efficiency throttle cryogenic refrigerator based on one stage compressor
US5875651A (en) * 1997-06-12 1999-03-02 Apd Cryogenics, Inc. Low vibration throttling device for throttle-cycle refrigerators
US6463744B1 (en) * 1998-05-12 2002-10-15 Messer Griesheim Gmbh Method and device for producing cold
US6513338B1 (en) * 1998-05-12 2003-02-04 Messer Griesheim Gmbh Refrigerant mixture for a mixture-throttling process

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080053145A1 (en) * 2003-07-15 2008-03-06 Indian Institute Of Technology Refrigerant composition for refrigeration systems
US7582223B2 (en) 2003-07-15 2009-09-01 Indian Institute Of Technology Refrigerant composition for refrigeration systems

Also Published As

Publication number Publication date
US20080053145A1 (en) 2008-03-06
US7582223B2 (en) 2009-09-01
WO2005005569A1 (fr) 2005-01-20
WO2005005569A8 (fr) 2005-03-31

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