WO2017165764A1 - Low gwp cascade refrigeration system - Google Patents

Low gwp cascade refrigeration system Download PDF

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Publication number
WO2017165764A1
WO2017165764A1 PCT/US2017/024010 US2017024010W WO2017165764A1 WO 2017165764 A1 WO2017165764 A1 WO 2017165764A1 US 2017024010 W US2017024010 W US 2017024010W WO 2017165764 A1 WO2017165764 A1 WO 2017165764A1
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WO
WIPO (PCT)
Prior art keywords
poe
refrigerant
heat transfer
heat exchanger
weight
Prior art date
Application number
PCT/US2017/024010
Other languages
English (en)
French (fr)
Inventor
Samuel F. Yana Motta
Michael Petersen
Ankit Sethi
Gustavo Pottker
Elizabet Del Carmen VERA BECERRA
Original Assignee
Honeywell International Inc.
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 Honeywell International Inc. filed Critical Honeywell International Inc.
Priority to EP17771233.8A priority Critical patent/EP3433547A4/en
Priority to JP2018549961A priority patent/JP2019513966A/ja
Priority to CN202111609565.6A priority patent/CN114526561A/zh
Priority to CN201780019272.8A priority patent/CN108779940A/zh
Priority to KR1020187022656A priority patent/KR102421874B1/ko
Publication of WO2017165764A1 publication Critical patent/WO2017165764A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/10Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00Compressor arrangements
    • F25B31/002Lubrication
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00Subcoolers, desuperheaters or superheaters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/006Compression 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00General 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
    • F25B2400/12Inflammable refrigerants
    • F25B2400/121Inflammable refrigerants using R1234

Definitions

  • the present invention relates to high efficiency, low-global warming potential ("low GWP”) air conditioning and/or refrigeration systems and methods for providing cooling that are safe and effective.
  • low GWP low-global warming potential
  • a compressor In typical air conditioning and refrigerant systems, a compressor is used to compress a heat transfer vapor from a lower to a higher pressure, which in turn adds heat to the vapor. This added heat is typically rejected in a heat exchanger, commonly referred to as a condenser.
  • the heat transfer vapor that enters the condenser is condensed to produce a liquid heat transfer fluid at a relatively high pressure.
  • the condenser uses a fluid available in large quantities in the ambient environment, such as ambient outside air, as the heat sink.
  • the high-pressure heat transfer fluid undergoes a substantially isoenthalpic expansion, such would occur by passing the fluid through an expansion device or valve, where it is expanded to a lower pressure, which in turn results in the fluid undergoing a decrease in temperature.
  • the lower pressure, lower temperature heat transfer fluid from the expansion operation then is typically routed to an evaporator, where it absorbs heat and in so doing evaporates.
  • This evaporation process in turn results in cooling of the fluid or body to that it is intended to cool.
  • the cooled fluid is the air which is contained in the region to be cooled, such as the air in the dwelling being air conditioned or the air inside a walk-in cooler or a supermarket cooler or freezer. After the heat transfer fluid is evaporated at low pressure in the evaporator, it is returned to the compressor where the cycle begins once again.
  • fluids which satisfy this combination of requirements nevertheless suffer from the disadvantage of having deficiencies in connection with safety.
  • fluids which might otherwise be acceptable may be disfavored because of flammability properties and/or toxicity concerns.
  • Applicants have come to appreciate that the use of fluids having such properties is especially undesirable in typical air conditioning and in many refrigeration systems since such flammable and/or toxic fluids may inadvertently be released into the dwelling, walk-in, cold-box, chiller, freezer or transport refrigeration box which is being cooled, thus exposing or potentially exposing the occupants thereof to dangerous conditions.
  • a cascade refrigerant system for providing cooling of air, directly or indirectly but preferably directly, located in an enclosure that is occupied by or which will be exposed to humans or other animals during normal use.
  • enclosure means a space that is at least partially confined (e.g., the enclosure can be opened on one or more sides, or closed) and includes air that has been cooled.
  • Preferred embodiments of the present systems include at least a first evaporator which is located within the enclosure and is part of a first, relatively low temperature heat transfer circuit.
  • the low temperature heat transfer circuit preferably comprises a first heat transfer fluid in a vapor compression circulation loop comprising at least: a compressor for raising the pressure of the first heat transfer composition; a heat exchanger for condensing at least a portion of the first heat transfer composition from the compressor at a relatively high pressure; an expansion device for lowering the pressure of the heat transfer composition from the condenser; and an evaporator for absorbing heat from the enclosure to be cooled into the heat transfer composition.
  • a compressor for raising the pressure of the first heat transfer composition
  • a heat exchanger for condensing at least a portion of the first heat transfer composition from the compressor at a relatively high pressure
  • an expansion device for lowering the pressure of the heat transfer composition from the condenser
  • an evaporator for absorbing heat from the enclosure to be cooled into the heat transfer composition.
  • the systems of the present invention also preferably include a second heat transfer circuit located substantially outside the enclosure, which is sometimes referred to herein by way of convenience as the "high temperature" loop.
  • the high temperature loop preferably comprises a second heat transfer fluid in a vapor compression circulation loop comprising at least a compressor, a heat exchanger which serves to condense the heat transfer fluid in the high temperature loop, preferably by heat exchange with ambient air outside of the enclosure, and an expansion device for reducing the pressure of the second heat transfer fluid from the compressor.
  • thermoly coupled with the high temperature circuit by virtue of rejecting heat into the second heat transfer fluid, preferably by causing at least a substantial portion of said second heat transfer fluid to evaporate.
  • the condenser of the low temperature circuit and the evaporator of the high temperature circuit are thermally coupled in this heat exchanger, which is sometimes referred to for convenience as "a cascade heat exchanger" in the systems and methods of the present invention.
  • Another important aspect of the present invention in preferred embodiments comprises the presence in the high temperature loop of a heat exchanger which has been found to advantageously and unexpectedly improve system performance by transferring heat from the second heat transfer fluid exiting from the high temperature condenser to the portion of the second heat transfer fluid which is traveling to the suction side of the compressor.
  • This heat exchanger is sometimes referred to herein for convenience as a "suction line heat exchanger.”
  • the first heat transfer fluid which is circulating in the low temperature loop comprises a refrigerant which has a GWP of not greater than about 500, more preferably not greater than about 400, and even more preferably not greater than about 150 and furthermore that the first heat transfer fluid has a flammability that is substantially less than the flammability of the second heat transfer fluid.
  • the second heat transfer fluid which is circulating in the high temperature loop also comprises a refrigerant which has a GWP of not greater than about 500, more preferably not greater than about 400, and even more preferably not greater than about 150, but since in normal operation this heat transfer fluid will never enter the enclosure, applicants have found that is advantageous to use a fluid in this high temperature loop that has one or properties that would be considered disadvantageous if it circulated within the enclosure, for example, flammability, toxicity and the like. In this way, the present systems allow additional possible unexpected advantages over systems that would rely only of the first heat transfer composition or only the second heat transfer composition, as explained in detail below.
  • the second refrigerant comprises, more preferably comprises at least about 50% by weight and even more preferably at least about 75% by weight, of trans-l,3,3,3-trifluoropropene (HFO-1234ze(E) and/or HFO-1234yf, and the second refrigerant has a flammability greater than , and preferably substantially greater than about, the flammability of C02.
  • the second refrigerant comprises, more preferably comprises at least about 75% by weight and even more preferably at least about 80% by weight, of trans-l,3,3,3-trifluoropropene (HFO-1234ze(E) and/or HFO- 1234yf.
  • Figure 1 is a generalized process flow diagram of one preferred embodiment of an air conditioning system according to the present invention.
  • a relatively low temperature vapor compression loop comprising a compressor, an expander and an evaporator in fluid communication in said loop, and a first heat transfer composition in said loop comprising a first refrigerant and preferably lubricant for the compressor, said evaporator being located in an enclosure containing air to be cooled and being capable of absorbing heat from said air at about said relatively low temperature;
  • a relatively high temperature vapor compression loop comprising a compressor, a condenser, an expander, and a suction line heat exchanger in fluid communication in said loop, and a second heat transfer composition in said loop comprising a second refrigerant and preferably lubricant for the compressor, said condenser being capable of transferring heat to a heat sink located outside said enclosure;
  • a cascade heat exchanger for condensing said first refrigerant and evaporating said second refrigerant by heat exchange between said first and second refrigerant, wherein said suction line heat exchanger is in fluid communication with said cascade heat exchanger for receiving at least a portion of said second heat transfer composition exiting said cascade heat exchanger and increases the temperature thereof by absorbing heat from said first heat transfer composition exiting said condenser and thereby reducing the temperature of said first heat transfer composition prior to said first heat transfer composition entering said first loop expander.
  • the terms “relatively low temperature” and “relatively high temperature,” when used together with respect to the first and second heat transfer loops, and unless otherwise indicated, are used in a relative sense to designate the relative temperature of the indicated heat transfer compositions, where those differences are least about 5°C.
  • the first refrigerant has a flammability that is substantially less than the flammability of the second refrigerant.
  • the first refrigerant has a flammability according to ASHRAE Standard 34 (which specifies measurement according to ASTM E681) that is classified as Al and the second refrigerant has a flammability according to ASHRAE Standard 34 that is classified as A2L or a higher flammability than A2L, although A2L classification for the second refrigerant is preferred.
  • the first and the second refrigerant each have a Global Warming Potential (GWP) that is less than about 150.
  • GWP Global Warming Potential
  • the first refrigerant circulating in the low temperature loop comprises carbon dioxide, preferably consists essentially of carbon dioxide and more preferably in some embodiments consists of carbon dioxide.
  • the second refrigerant comprises one or more of transl, 3, 3, 3- tetrafluoropropene (HFO-1234ze(E)), 2,3,3,3-tetrafluoropropene (HFO-1234yf), R-227ea, and R-32 and combinations of two or more of these.
  • the second refrigerant comprises at least about 50%, more preferably at least about 80% by weight of 2, 3,3,3-tetrafluoropropene (HFO-1234yf).
  • the second refrigerant comprises at least about 50%, more preferably at least about 80% by weight of or at least about 75%) by weight, more preferably at least about 80%> by weight of transl, 3,3,3-tetrafluoropropene (HFO-1234ze(E)).
  • the second refrigerant comprises at least about 95% by weight, and in some embodiments consists essentially of or consists of HFO- 1234ze(E), HFO-1234yf or combinations of two or more of these.
  • the second refrigerant comprises from about 70% by weight to about 90% of HFO-1234yf, preferably about 80% by weight of HFO-1234yf and from about 10% by weight to about 30% by weight of R32, preferably about 20% by weight of R-32.
  • the second refrigerant comprises from about 70% by weight to about 90% of HFO-1234ze(E), preferably about 80% by weight of HFO-1234ze(E) and from about 10% by weight to about 30% by weight of R32, preferably about 20% by weight of R-32.
  • the second refrigerant comprises from about 85% to about 90%) by weight of by weight of transl,3,3,3-tetrafluoropropene (HFO-1234ze(E)) and from about 10% by weight to about 15% by weight of 1, 1,1,2,3,3,3-heptafluoropropane (HFC- 227ea), and even more preferably in some embodiments about 88% of transl, 3,3,3- tetrafluoropropene (HFO-1234ze(E)) and about 12% by weight of 1, 1,1,2,3,3,3- heptafluoropropane (HFC-227ea).
  • HFO-1234ze(E) transl,3,3,3-tetrafluoropropene
  • HFC- 227ea 1, 1,1,2,3,3,3-heptafluoropropane
  • the preferred embodiments of the present invention provide the advantage of utilizing only the safe (relatively low toxicity and low flammability) low GWP refrigerants within the enclosure to be cooled and a relatively less safe, but preferably low GWP refrigerant in the high temperature loop which is located entirely outside of the enclosure.
  • the terms “safe” and “relatively less safe,” when used together with respect to the first and second heat transfer loops, and unless otherwise indicated, are used in a relative sense to designate the relative safety of the indicated heat transfer compositions.
  • Such configuration especially when the high temperature system includes the preferred suction line heat exchanger, makes the systems and methods of the invention highly preferred for use in a location proximate to the humans or other animals occupying or using the enclosure, as is commonly encountered in walk-in freezers, supermarket coolers and the like.
  • the first heat transfer composition and the second heat transfer compositions also each generally include a lubricant, generally in amounts of from about 30 to about 50 percent by weight of the heat transfer composition, with the balance comprising refrigerant and other optional components that may be present.
  • a lubricant generally in amounts of from about 30 to about 50 percent by weight of the heat transfer composition, with the balance comprising refrigerant and other optional components that may be present.
  • Combinations of surfactants and solubilizing agents may also be added to the present compositions to aid oil solubility, as disclosed by U.S. Patent No. 6,516,837, the disclosure of which is incorporated by reference.
  • Commonly used refrigeration lubricants such as Polyol Esters (POEs) and Poly Alkylene Glycols (PAGs), silicone oil, mineral oil, alkyl benzenes (ABs) and poly(alpha-olefin) (PAO) that are used in refrigeration machinery with hydrofluorocarbon (HFC) refrigerants may be used with the refrigerant compositions of the present invention.
  • the preferred lubricants are POEs.
  • the use of the suction line heat exchanger as described herein preferably produces at least a 2% COP improvement, more preferably at least about 3% COP improvement, and even more preferably a 4% COP improvement compared to the same system but without a suction-line heat exchanger according to the present invention.
  • the refrigeration system is designated generally as 10.
  • the boundaries designates generally as 100 represent schematically the enclosure.
  • the low temperature loop comprises compressor 11, condensing side 12A of the cascade exchange 12, expansion valve 14 and evaporator 15.
  • evaporator 15 is located within enclosure 100, together with any of the associated conduits and other connecting and related equipment to transport the first heat transfer composition to and from the enclosure boundary.
  • the evaporator 14 is preferably located inside the enclosure, and is disclosed in the illustrated figure as being located inside of the enclosure 100, it will be appreciated that in certain embodiments it may be desirable and/or necessary to provide the expander 14 outside of the enclosure.
  • the high temperature loop comprises compressor 21, evaporating side 12B of the cascade exchange 12, expansion valve 24 and condenser 25, all located outside of enclosure 100, together with any of the associated conduits and other connecting and related equipment.
  • the high temperature circuit also includes suction line heat exchanger 50 which enables the exchange of heat between the second heat transfer composition stream 30 exiting condenser 25 and the second heat transfer composition stream 31 exiting the evaporating side 12B of the cascade heat exchanger 12.
  • first and second refrigeration loops may vary widely within the scope hereof, applicants have found that highly advantageous results can be achieved in certain embodiments by judicious selection of the relative sizes of the refrigeration loops. More specifically, it is contemplated and understood that under normal operating conditions the heat transfer composition contained in the first refrigeration loop and in the second refrigeration loop will never mix or intermingle. However, applicants have come to appreciate that the possibility of such intermixing of first and second refrigerants might occur for example, in the case of leakage in the cascade heat exchanger. This mixed refrigerant stream may then, in the event of a leak within the enclosure being cold, become exposed to humans or other animals located in or near the enclosure. Accordingly, in order to ensure continued safe operation even in the case of such leakage, applicants have come to appreciate that careful and judicious selection of the relative refrigeration loop sizes can result in a safe system even in the event of such a leakage.
  • the term "transport refrigeration box” is used to designate cold/insulated boxes which are located on or comprise a portion or substantially all of a truck trailer.
  • the capacity of the system according to the present invention is less than about 30 kW. In preferred applications the capacity of the system according to the present invention is less than about 15 kW, and in yet further applications the capacity of the system according to the present invention is less than about 10 kW.
  • First Refrigerant is C02 and Second Refrigerant is R-1234ze(E)
  • the weight ratio of the loading of the first refrigerant (e.g. C02) in the low temperature loop to the second refrigerant (e.g. R-1234ze(E)) is not less than about 1.2.
  • the system of the present invention will remain safe, i.e., contain only nonflammable refrigerant, even in the event of complete intermixing between the first and the second refrigerant compositions.
  • First Refrigerant is C02 and Second Refrigerant is SR26
  • the weight ratio of the loading of the first refrigerant (e.g. C02) in the low temperature loop to the second refrigerant (e.g. SR26) is not less than about 1.0.
  • the system of the present invention will remain safe, i.e., contain only nonflammable refrigerant, even in the event of complete intermixing between the first and the second refrigerant compositions.
  • First Refrigerant is C02 and Second Refrigerant is R-32
  • the weight ratio of the loading of the first refrigerant (e.g. C02) in the low temperature loop to the second refrigerant (e.g. SR26) is not less than about 0.9.
  • the system of the present invention will remain safe, i.e., contain only nonflammable refrigerant, even in the event of complete intermixing between the first and the second refrigerant compositions.
  • First Refrigerant is C02 and Second Refrigerant is Ethane
  • first refrigerant consists of C02
  • second refrigerant consists of ethane
  • the weight ratio of the loading of the first refrigerant (e.g. C02) in the low temperature loop to the second refrigerant (e.g. SR26) is not less than about 1.7.
  • the system of the present invention will remain safe, i.e., contain only nonflammable refrigerant, even in the event of complete intermixing between the first and the second refrigerant compositions.
  • First Refrigerant is C02 and Second Refrigerant is Propane
  • the weight ratio of the loading of the first refrigerant (e.g. C02) in the low temperature loop to the second refrigerant (e.g. propane) is greater than 4.
  • the system of the present invention will remain safe, i.e., contain only nonflammable refrigerant, even in the event of complete intermixing between the first and the second refrigerant compositions.
  • Comparative Example CI as described below is based on a typical walk cooler refrigeration system as illustrated in the following figure.
  • the boundaries of the cooler are represented schematically by the box 100.
  • the evaporator 15 and expander 14 are located outside the cooler box 100.
  • the refrigerant circulating within this refrigeration loop is refrigerant R-404A (52 wt.% R-143a, 44 wt.% R-125 and 4 wt.% R-134a).
  • Condensing temperature of condenser 200 45°C
  • a hybrid system based on the typical refrigeration system as illustrated in Example 1 is formed but a suction line heat exchanger is inserted so as to absorb heat into the R-404A exiting the evaporator and thereby increasing the temperature of R-404A entering the compressor by absorbing heat from R-404A exiting the condenser prior to that stream entering expander. Operation using a suction line heat exchanger with Effectiveness values varying from 35% to 85%) are evaluated. The results are reported in the following Table HI, together with the result of comparative Example CI for comparison:
  • a cascade refrigeration system having a suction line heat exchanger as illustrated in Figure 1 is operated using each of the following refrigerants in the low temperature loop (the second refrigerant): HFO-1234ze(E); HFO-1234yf; SR21( 80 wt% HFO-1234yf and 20 wt% R- 32); SR26 ( 80 wt% HFO-1234ze(E) and 20 wt% R-32); and SR31( 88 wt% HFO-1234ze(E) and 12 wt% R-32).
  • the refrigerant in the high temperature loop is CO2.
  • the cascade system of the present invention is operated according to the following parameters:
  • Suction-line Liquid-line heat exchanger Effectiveness vary from 0% to 85%.
  • a cascade refrigeration system having no suction line heat exchanger and a suction line heat exchanger as illustrated in Figure 1 is operated using each of the following refrigerants in the low temperature loop (the second refrigerant) and C0 2 in the high temperature loop (showing the GWP of each refrigerant):
  • a cascade refrigeration system having no suction line heat exchanger and a suction line heat exchanger as illustrated in Figure 1 is operated using each of the following refrigerants in the low temperature loop (the second refrigerant) and C02 in the high temperature loop:
  • each refrigerant produces an acceptable discharge temperature (i.e., within the scope of preferred discharge temperature range).
  • the discharge temperature is acceptable.
  • each of EX10 - EX13 refrigerants produce unacceptable discharge temperatures for the desired effectiveness values of 85% or above.
  • Only EX 14 and EX 15 provide acceptable discharge temperatures for suction line heat exchangers having any of the tested effectiveness values.
  • a cascade refrigeration system having no suction line heat exchanger and a suction line heat exchanger as illustrated in Figure 1 is operated using each of the following refrigerants in the high temperature loop (the second refrigerant) and C0 2 in the low temperature loop (showing the GWP of each refrigerant): Component»> R-1234yf, R-32, wt% GWP
  • a cascade refrigeration system having no suction line heat exchanger and a suction line heat exchanger as illustrated in Figure 1 is operated using each of the following refrigerants in the low temperature loop (the second refrigerant) and C02 in the high temperature loop:
  • each refrigerant produces an acceptable discharge temperature (i.e., within the scope of preferred discharge temperature range).
  • the discharge temperature is acceptable.
  • each of refrigerants EX20 - EX22 produces unacceptable discharge temperatures for the desired effectiveness values of 85% or above.
  • Only EX 23, EX24 and EX 25 provide acceptable discharge temperatures for suction line heat exchangers for all tested effectiveness values.
  • the use of the refrigerant of Examples 24 and 25 in all tested systems of the present invention which include a suction-line heat exchanger not only show at least an additional 2% improvement versus the system of the present invention without the suction-line heat exchanger, such refrigerants (as shown in Table 21/25 - DT) have an acceptable discharge temperature for all levels of suction line heat exchanger effectiveness tested.
  • the use of the refrigerant of Examples 22 and 23 in tested systems of the present invention which include a suction-line heat exchanger with an effectiveness of 55% show not only at least an additional 2% improvement versus the system of the present invention without the suction-line heat exchanger but (as shown in Table 21/25 - DT) also have an acceptable discharge temperature.
  • Example 20 does not demonstrate at least a 2% improvement for any values of heat exchanger effectiveness
  • Examples 21 and 22 show at least a 2% improvement for heat exchanger effectiveness values of 75% and 85%
  • these values of heat exchanger effectively do not does not provide an acceptable discharge, as shown in Table 20/25 - DT, this refrigerant does not for this conditions.

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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)
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PCT/US2017/024010 2016-03-25 2017-03-24 Low gwp cascade refrigeration system WO2017165764A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP17771233.8A EP3433547A4 (en) 2016-03-25 2017-03-24 CASCADE COOLING SYSTEM WITH LOW HEATING POTENTIAL
JP2018549961A JP2019513966A (ja) 2016-03-25 2017-03-24 低gwpカスケード冷却システム
CN202111609565.6A CN114526561A (zh) 2016-03-25 2017-03-24 低gwp级联制冷系统
CN201780019272.8A CN108779940A (zh) 2016-03-25 2017-03-24 低gwp级联制冷系统
KR1020187022656A KR102421874B1 (ko) 2016-03-25 2017-03-24 저gwp 캐스케이드 냉동 시스템

Applications Claiming Priority (4)

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US201662313177P 2016-03-25 2016-03-25
US62/313,177 2016-03-25
US15/468,292 2017-03-24
US15/468,292 US20180017292A1 (en) 2016-01-06 2017-03-24 Low gwp cascade refrigeration system

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EP3492838A1 (en) * 2017-11-29 2019-06-05 JTL Systems Limited A condenser device for a refrigeration system and method of controlling thereof

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