US20170191702A1 - High efficiency air conditioning systems and methods - Google Patents

High efficiency air conditioning systems and methods Download PDF

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Publication number
US20170191702A1
US20170191702A1 US15/400,891 US201715400891A US2017191702A1 US 20170191702 A1 US20170191702 A1 US 20170191702A1 US 201715400891 A US201715400891 A US 201715400891A US 2017191702 A1 US2017191702 A1 US 2017191702A1
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Prior art keywords
refrigerant
pressure
vapor
compressor
heat
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Abandoned
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US15/400,891
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English (en)
Inventor
Michael Petersen
Samuel F. Yana Motta
Ankit Sethi
Elizabet del Carmen Vera Becerra
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Honeywell International Inc
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Honeywell International Inc
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Publication date
Priority to KR1020187022482A priority Critical patent/KR20180091950A/ko
Priority to US15/400,891 priority patent/US20170191702A1/en
Priority to PCT/US2017/012627 priority patent/WO2017120539A1/en
Priority to JP2018535410A priority patent/JP2019507304A/ja
Application filed by Honeywell International Inc filed Critical Honeywell International Inc
Assigned to HONEYWELL INTERNATIONAL INC. reassignment HONEYWELL INTERNATIONAL INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PETERSEN, MICHAEL, SETHI, ANKIT, VERA BECERRA, ELIZABET DEL CARMEN, YANA MOTTA, SAMUEL F
Priority to US15/434,400 priority patent/US10907863B2/en
Priority to US15/468,292 priority patent/US20180017292A1/en
Publication of US20170191702A1 publication Critical patent/US20170191702A1/en
Priority to US16/404,246 priority patent/US20190331366A1/en
Priority to US16/410,190 priority patent/US10907862B2/en
Priority to JP2021178482A priority patent/JP2022017439A/ja
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
    • C09K5/044—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 halogenated compounds
    • 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
    • C09K5/044—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 halogenated compounds
    • C09K5/045—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 halogenated compounds containing only fluorine as halogen
    • 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B41/40—Fluid line arrangements
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • 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
    • 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
    • C09K2205/12—Hydrocarbons
    • C09K2205/126—Unsaturated fluorinated hydrocarbons
    • 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
    • F25B2400/12—Inflammable refrigerants
    • 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
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
    • 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

  • This invention relates generally to air conditioning systems and more particularly to such systems which utilize centrifugal compressors and have a refrigeration capacity in the range of up to about 30 tons.
  • halogenated olefins including the compounds 1-chloro-3,3,3-trifluoropropene (HFCO-1233zd) and 1,3,3,3-tetrafluoropropene (HFO-1234ze) have been suggested to use in vapor compression refrigeration systems. See U.S. Pat. No. 7,833,433, A standard vapor compression system is described in the '433 patent as including a compressor for compressing refrigerant vapor to produce a relatively elevated pressure and temperature vapor. An example of such a system is illustrated herein as FIG. P.
  • a refrigerant is introduced at a relatively low pressure into the suction side of a compressor 11 via a conduit 19 A and a high pressure refrigerant is discharged and sent via conduit 19 B to condenser 12 .
  • Heat is removed from this high temperature refrigerant vapor by condensing the refrigerant vapor in condenser 12 to produce a relatively high pressure liquid refrigerant which enters a conduit 15 A.
  • the relatively high pressure liquid then undergoes a nominally isoenthalpic reduction in pressure in an expansion device 14 to produce a relatively low temperature, low pressure liquid, which is then vaporized by heat transferred from the body or fluid to be cooled in evaporator 24 .
  • the low pressure vapor thus produced is returned to the suction side of the compressor via conduit 19 A, thus completing the cycle.
  • centrifugal chillers are large capacity systems, that is, systems having capacities greater than 50 tons. Most typically such systems are in the range of 50 to 150 tons of refrigerating capacity, with certain systems going as high as 8500 tons.
  • one aspect of the present invention provides a refrigeration system of the type having a heat source to be cooled and a heat sink into which heat can be rejected, said system preferably having a capacity of from about 2 to about 30 tons and comprising:
  • a heat transfer composition comprising a refrigerant comprising at least about 80% by weight of trans1-chloro-3,3,3-trifluoropropene (HCFO-1233zd(E)) or at least about 80% by weight of trans1,3,3,3-tetrafluoropropene (HFO-1234ze(E)),
  • a centrifugal compressor having: (i) a refrigerant suction for receiving a relatively low-pressure refrigerant vapor at a pressure of from about 40 to about 350 kPa and (ii) a discharge for discharging a relatively high pressure refrigerant vapor at a pressure wherein the discharge:suction pressure ratio is at least about 2:1;
  • a condenser fluidly connected to said refrigerant discharge of said compressor for receiving at least a portion of said compressor discharge refrigerant vapor and condensing at least a substantial portion of said refrigerant vapor, and preferably substantially all of said refrigerant vapor, by heat transfer with said heat sink to produce a relatively high pressure refrigerant liquid at temperature in the range of from about 10° C. to about 60° C.;
  • a high efficiency evaporator preferably a flooded evaporator, fluidly connected to said expander for receiving said low pressure refrigerant liquid from said expander and evaporating said low pressure refrigerant liquid by absorbing heat from said source to be cooled to produce a relatively low pressure refrigerant vapor at a pressure of from about 40 to about 350 kPa, said refrigerant vapor exiting from said evaporator preferably having no substantial superheat;
  • At least one heat exchanger fluidly connected between said evaporator and said refrigerant suction of said compressor, said at least one heat exchanger receiving at least a portion of said low pressure refrigerant vapor from said evaporator and heating said low pressure refrigerant vapor to produce a low pressure refrigerant vapor having a temperature at least about 5° C. greater than the temperature of the vapor entering said at least one heat exchanger, said high temperature refrigerant vapor from said at least one heat exchanger fluidly connected to said compressor suction for providing low-pressure refrigerant vapor to said compressor.
  • the term “capacity” defined in terms of number of “tons” refers to a heat transfer rate equivalent to the amount of heat required to melt one ton (2000 lb; 907 kg) of ice at 0 C (32 F) in 24 hours and generally equates to about 12,000 BTU/hour.
  • FIG. P is an illustration of a prior art heat transfer system
  • FIG. 1 is a generalized process flow diagram of one preferred embodiment of an air conditioning system according to the present invention.
  • FIG. 2 is a generalized process flow diagram of another preferred embodiment of an air conditioning system according to the present invention.
  • FIG. 3 is a generalized process flow diagram of another preferred embodiment of an air conditioning system according to the present invention.
  • FIG. 4A is a generalized process flow diagram of another preferred embodiment of an air conditioning system according to the present invention.
  • FIG. 4B is a more specific process flow diagram of a preferred embodiment of an air conditioning system having a flame suppression feature according to one aspect of the present invention.
  • the system includes a heat transfer composition comprising refrigerant and preferably but not necessarily a lubricant for the compressor.
  • the refrigerant comprises at least about 70% by weight, or at least about 80% by weight of trans1-chloro-3,3,3-trifluoropropene (HCFO-1233zd(E)) or of trans1,3,3,3-tetrafluoropropene (HFO-1234ze(E)), and is a low flammability and low toxicity refrigerant, preferably with a Class A toxicity according to ASHRAE Standard 2013 and a flammability of Class 1 or Class 2 or Class 2L according to ASHRAE Standard 34-2013 and described in Appendix B1 to ASHRAE Standard 34-2013.
  • the refrigerant comprises at least about 95% by weight, and in some embodiments consists essentially of or consists of, HFCO-1233zd(E)
  • the refrigerant comprises from about 1% by weight to about 5% by weight of a five carbon saturated hydrocarbon, preferably one or more of iso-pentane, n-pentane or neo-pentane, and in preferred aspects of such embodiments the combination of said HFCO-1233zd(E) and said pentane is in the form of an azeotropic composition.
  • azeotrope and azeotrope-like compositions are disclosed in U.S. Pat. No. 8,802,874, U.S. Pat. No. 8,163,196, and U.S. Pat. No. 8,703,006, each of which is incorporated herein by reference.
  • Heat transfer compositions of the present invention which include refrigerant compositions as described in this paragraph preferable include lubricant comprising or consisting of POE and/or mineral oil and/or alkyl benzene.
  • the refrigerant comprises from about 85% to about 90% by weight of by weight of trans1,3,3,3-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 trans1,3,3,3-tetrafluoropropene (HFO-1234ze(E)) and about 12% by weight of 1,1,1,2,3,3,3-heptafluoropropane (HFC-227ea).
  • Heat transfer compositions of the present invention which include refrigerant compositions as described in this paragraph preferable include lubricant comprising or consisting of POE.
  • the heat transfer compositions of the present invention generally include a lubricant.
  • embodiments of the present invention include systems and methods which utilize compressors which do not require a lubricant and/or does not require the lubricant to be combined with the refrigerant.
  • the lubricant is preferably present in the system in amounts of from about 30 to about 50 percent by weight of the heat transfer composition based on the total weight of the refrigerant in the system and the total weight of the lubricant in the system, with other optional components as described hereinafter also being possibly present.
  • heat transfer composition of the present invention particularly in the form of the carry-over vapor from the compressor and in the form of the liquid from the condenser and entering the evaporator, comprises from about 97% to about 99.5% by weight of refrigerant of the present invention and from about 0.5 to about 3% by weight of lubricant, with such lubricant preferably being POE lubricant and/or, mineral oil lubricant.
  • compatibilizer such as propane
  • propane for the purpose of aiding compatibility and/or solubility of the lubricant.
  • compatibilizers including propane, butanes and pentanes, are preferably present in amounts of from about 0.5 to about 5 percent by weight of the composition.
  • Combinations of surfactants and solubilizing agents may also be added to the present compositions to aid oil solubility, as disclosed by U.S. Pat. No. 6,516,837, the disclosure of which is incorporated by reference.
  • 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 of the present invention are selected from POEs and mineral oils and alkyl benzenes.
  • the present refrigeration systems and methods are particularly well adapted for use in low capacity air conditioning systems, that is, systems having a capacity of 30 tons or less, particularly in residential air conditioning, particularly residential air conditioning having a capacity of from about 2 to about 5 tons, and commercial packaged rooftop air conditioning units, particularly having a capacity of from about 5 to about 30 tons.
  • FIG. 1 A preferred air conditioning system, designated generally at 10 , is illustrated in FIG. 1 .
  • Such a preferred air conditioning system comprises compressor 11 , condenser 12 , evaporator 24 (preferably a flooded evaporator), expansion valve 14 , and suction-line heat exchanger 30 , together with any of the associated conduits 15 A, 15 B, 16 A and 16 B and other connecting and related equipment (not shown).
  • the refrigerant according to the present invention is discharged from compressor 11 as a relatively high pressure refrigerant vapor, which may include entrained lubricant, and which then is transported via conduit 19 C to condenser 12 .
  • the refrigerant vapor transfers a portion of its heat, preferably via a phase change and preferably to ambient air, and produces an effluent stream comprising at least partially, and preferably substantially fully, condensed refrigerant.
  • the refrigerant effluent from the condenser 12 is transported via conduit 15 A to suction-line heat exchanger 30 where it loses additional heat to the effluent from the evaporator 24 , as is explained more fully hereinafter.
  • the effluent from the suction/liquid line heat exchanger 30 is then transported via conduit 15 B to expansion valve 14 where the pressure of the refrigerant is reduced, preferably substantially isoenthalpically, which in turn reduces the temperature of the refrigerant.
  • the relatively cold liquid refrigerant from the expansion valve 14 flows to receiver tank 18 which provides a reservoir of cold liquid refrigerant that is fed by way of a control valve (not shown) in conduit 19 A into the evaporator 24 where it absorbs heat from the body or fluid being cooled, preferably the ambient air within a dwelling or other space being cooled.
  • the refrigerant effluent vapor from the evaporator 24 which is preferably a substantially saturated refrigerant vapor with substantially no super heat (e.g. the superheat of the vapor leaving the evaporator is less than about 1° C.
  • the vapor leaving the suction line heat exchanger has a temperature that is at least about 5° C., and even more preferably at least about 7° C., higher than the substantially saturated vapor which enters the suction line heat exchanger.
  • the high temperature refrigerant vapor is then transported to the suction of the compressor 11 where it is compressed as described above.
  • the operating conditions correspond to the values described in the table below:
  • PREFERRED RANGE COMPRESSOR Pressure 45-75 SUCTION kPa Temperature, 0°-10° ° C.
  • COMPRESSOR Pressure 105-520 DISCHARGE kPa Temperature, 20°-70° ° C.
  • CONDENSER Pressure 105-520 kPa Temperature, 10°-60° ° C. EVAPORATOR Pressure, 45-75 kPa Temperature, 0°-10° C.°
  • the operating conditions correspond to the values described in the table below:
  • PREFERRED RANGE COMPRESSOR Pressure 210-310 SUCTION kPa Temperature, 0°-10° ° C.
  • COMPRESSOR Pressure 420-1600 DISCHARGE kPa Temperature, 20°-70° ° C.
  • CONDENSER Pressure 420-1600 kPa Temperature, 10°-60° ° C.
  • EVAPORATOR Pressure 210-310 kPa Temperature, 0°-10° ° C.
  • FIG. 2 A further preferred air conditioning system, designated generally at 10 , is illustrated in FIG. 2 .
  • a preferred air conditioning system comprises a multi-stage compressor, shown as a two stage compressor 11 , condenser 12 , evaporator 24 (which is preferably a flooded evaporator in some embodiments), expansion valve 14 , and vapor-injection heat exchanger 40 , including associated intermediate expansion valve 41 , together with any of the associated conduits 15 A- 15 C and 19 A- 19 D and other connecting and related equipment (not shown and/or not labeled).
  • the refrigerant according to the present invention is discharged from compressor 11 as a relatively high pressure refrigerant vapor, which may include entrained lubricant, and which then is transported via conduit 19 D to condenser 12 .
  • condenser 12 the refrigerant vapor transfers a portion of its heat, preferably via a phase change and preferably to ambient air, and produces an effluent stream comprising at least partially, and preferably substantially fully, condensed refrigerant.
  • the refrigerant effluent from the condenser 12 is transported via conduit 15 A, and a portion of the refrigerant effluent is routed via conduit 15 B to an intermediate expansion device 41 and another portion of the effluent, preferably the remainder of the effluent, is transported to the vapor injection heat exchanger 40 .
  • the intermediate expansion device 41 lets the pressure of the effluent stream down, preferably substantially isoenthalpically, to about the pressure of the second stage suction of compressor 11 or sufficiently above such pressure to account for the pressure-drop through the heat exchanger 41 and associated conduits, fixtures and the like.
  • the pressure drop across the expansion device 41 the temperature of the refrigerant flowing to the heat exchanger 40 is reduced relative to the temperature of the high pressure refrigerant which flows to the heat exchanger 40 .
  • Heat is transferred in the heat exchanger 40 from the high pressure stream to the stream that passed through the expansion valve 41 .
  • the temperature of the intermediate pressure stream which exits the heat exchanger 40 is higher, preferably by a temperature of at least about 5° C., than the temperature of the inlet stream, thereby producing a super-heated vapor stream that is transported to the second stage of the compressor 11 via conduit 19 C.
  • conduit 15 A As the higher pressure stream transported by conduit 15 A travels through the heat exchanger 40 it loses heat to the lower pressure stream exiting expansion devise 41 and exits the heat exchanger through conduit 15 C and then flows to receiver tank 18 which provides a reservoir of cold liquid refrigerant that is fed by way of a control valve (not shown) in conduit 19 A into the evaporator 24 .
  • Ambient air to be cooled loses heat to the cold liquid refrigerant in the evaporator which in turn vaporizes the liquid refrigerant and produces refrigerant vapor with little or no super heat, and this vapor then flows to the first stage of compressor 11 .
  • the operating conditions correspond to the values described in the table below:
  • PREFERRED RANGE COMPRESSOR Pressure 45-75 SUCTION kPa Temperature, 0°-10° ° C.
  • COMPRESSOR Pressure 105-520 DISCHARGE kPa Temperature, 20°-70° ° C.
  • CONDENSER Pressure 105-520 kPa Temperature, 10°-60° ° C.
  • EVAPORATOR Pressure 45-75 kPa Temperature, 0°-10° ° C.
  • the operating conditions correspond to the values described in the table below:
  • PREFERRED RANGE COMPRESSOR Pressure 210-310 SUCTION kPa Temperature, 0°-10° ° C.
  • COMPRESSOR Pressure 420-1600 DISCHARGE kPa Temperature, 20°-70° ° C.
  • CONDENSER Pressure 420-1600 kPa Temperature, 10°-60° ° C.
  • EVAPORATOR Pressure 210-310 kPa Temperature, 0°-10° ° C.
  • FIG. 3 A further preferred air conditioning system, designated generally at 10 , is illustrated in FIG. 3 .
  • a preferred air conditioning system comprises a compressor 11 , which may be a multi-stage compressor of the type as described herein but in the illustrated embodiment is shown as a single stage compressor, condenser 12 , evaporator 24 (which is preferably a flooded evaporator in some embodiments), expansion valve 14 , a flash gas separator 18 , together with any of the associated conduits 15 A- 15 C and 19 A- 19 C and other connecting and related equipment (not shown and/or not labeled).
  • a compressor 11 which may be a multi-stage compressor of the type as described herein but in the illustrated embodiment is shown as a single stage compressor, condenser 12 , evaporator 24 (which is preferably a flooded evaporator in some embodiments), expansion valve 14 , a flash gas separator 18 , together with any of the associated conduits 15 A- 15 C and 19 A- 19 C and other connecting and related equipment
  • the refrigerant according to the present invention is discharged from compressor 11 as a relatively high pressure refrigerant vapor, which may include entrained lubricant, and which then is transported via conduit 19 C to condenser 12 .
  • condenser 12 the refrigerant vapor transfers a portion of its heat, preferably via a phase change and preferably to ambient external air, and produces an effluent stream comprising at least partially, and preferably substantially fully, condensed refrigerant.
  • the refrigerant effluent from the condenser 12 is transported via conduit 15 A to expansion device 14 .
  • the lower pressure stream exiting expander 14 flows through conduit 15 B to flash gas separator 18 , which provides a reservoir of cold liquid refrigerant that is fed by way of a control valve (not shown) in conduit 15 C into the evaporator 24 .
  • Ambient air to be cooled loses heat to the cold liquid refrigerant in the evaporator 24 , which in turn vaporizes the liquid refrigerant and produces refrigerant vapor with little or no super heat, and this vapor then flows to the first stage of compressor 11 . Flash gas generated during the pressure let-down in expansion device 14 then flows through conduit 19 B to the suction side of the compressor 11 .
  • the operating conditions correspond to the values described in the table below:
  • the operating conditions correspond to the values described in the table below:
  • PREFERRED RANGE COMPRESSOR Pressure 210-310 SUCTION kPa Temperature, 0°-10° ° C.
  • COMPRESSOR Pressure 420-1600 DISCHARGE kPa Temperature, 20°-70° ° C.
  • CONDENSER Pressure 420-1600 kPa Temperature, 10°-60° ° C.
  • EVAPORATOR Pressure 210-310 kPa Temperature, 0°-10° ° C.
  • FIG. 4A a further preferred air conditioning systems, designated generally at 10 , is illustrated in FIG. 4A .
  • a preferred air conditioning system comprises a compressor 11 , which may be a multi-stage compressor of the type as described herein, condenser 12 , evaporator 24 (which is preferably a flooded evaporator in some embodiments), expansion valve 14 , a high pressure receiver, together with any of the associated conduits 15 A- 15 C and 19 A- 19 B and other connecting and related equipment (not shown and/or not labeled).
  • the refrigerant according to the present invention is discharged from compressor 11 as a relatively high pressure refrigerant vapor, which may include entrained lubricant, and which then is transported via conduit 19 B to condenser 12 .
  • condenser 12 the refrigerant vapor transfers a portion of its heat, preferably via a phase change and preferably to ambient external air, and produces an effluent stream comprising at least partially, and preferably substantially fully, condensed refrigerant.
  • the refrigerant effluent from the condenser 12 is transported via conduit 15 A to a high pressure receiver 50 , which provides a reservoir of liquid refrigerant.
  • a sensor activated relief valve 60 is connected via a port or other form of connection to conduit 15 A.
  • the sensor activated relief valve includes and/or is in communication connection with, a sensor that monitors for flame, smoke, flammable gas concentration or other indicia that a flame is present or more likely to occur, said sensor being located in vicinity of some portion of the refrigeration system, preferably within the dwelling or other area being cooled. Since the preferred refrigerants of the present invention have flammability suppression properties, if the sensor detects flame and/or smoke (or other indicia of the existence of possibility or increased likelihood of fire), the sensor activated relief valve will open and release refrigerant into the area in which it is located, thus assisting with inhibition and/or elimination of the fire.
  • the use of a high pressure receiver ensures that a relatively large reservoir of high pressure liquid refrigerant will be available in the event of such an emergency situation.
  • the remainder of the refrigeration system can operate according to any one or more of the embodiments described herein.
  • An air conditioning system uses a refrigerant consisting of HCFO-1233zd(E) according to the following parameters:
  • operation according to the embodiment of the invention as illustrated in FIG. 1 produces at least about 5° C. of superheat at the compressor discharge for the whole range of condensing temperatures tested.
  • Example 2A is repeated except that a series of azeotropic refrigerant blends based on HCFO-1233zd(E) as described in Table 2B below are used in place of the refrigerant consisting of only 1233zd(E) as used in Example 2A. Acceptable operation is achieved.
  • FIG. 1 An air conditioning system according to the present invention as illustrated in FIG. 1 is tested using a suction line heat exchanger (SLHX) with an SLHX effectiveness of 0.5 and 0.7 and using a refrigerant consisting of HCFO-1233zd(E) is tested according to the same operating parameters of Example 1.
  • This testing provides a comparison of the relative effectiveness of such systems with the system described in Example 1 (both systems using a compressor efficiency of 80%) which does not use a SLHX, and this comparison is reported in Table 3A below:
  • An air conditioning system using a two stage compressor according to the system configuration as illustrated in FIG. 2 using a refrigerant consisting of HCFO-1233zd(E) is tested over a series of condensing temperatures ranging from 30 C to 60 C.
  • the operating conditions for the compressor at an isentropic efficiency of 80% and an evaporator temperature of 7 C for each of these condenser temperatures is reported in Table 4A1:
  • An air conditioning system using a flash gas separator as illustrated in FIG. 3 and using a refrigerant consisting of HCFO-1233zd(E) and the blends identified in Table 5 below are s tested according to the same operating parameters of Example 1 for a single stage compressor operating at 80% isentropic efficiency.
  • the evaporator is operated in flooded configuration and results in a reduced pressure drop across the evaporator and hence a higher suction pressure in the compressor.
  • compact heat exchangers made from low cost materials can be use.
  • round tube-fin and/or microchannel heat exchangers could be made of aluminum instead of copper. This configuration offers superior heat transfer performance, low weight and compact heat transfer systems.
  • An air conditioning system using a sensor activated relief valve as illustrated in FIGS. 4A and 4B and using a refrigerant consisting of HCFO-1233zd(E) and each of the refrigerants disclosed in Table 2B is tested.
  • the sensor activated relief valve is preferably a solenoid type valve.
  • the sensor that is used measures the natural gas concentration in a residential furnace unit. In case of a fuel leak, such as for example a natural gas leak, of the burner set up of the furnace the sensor would detect elevated gas concentrations, for example 1000 ppm, activating the solenoid valve. The activated valve would open and release the R1233zd(E) into this flammable natural gas atmosphere.
  • the likeliness of a fire would be reduced by inhibiting and/or eliminating the fire condition in proximity to the relief valve which is located in proximity to the sensed flammable atmosphere.
  • fire conditions or conditions indicating an increased likelihood of a fire is detected by the sensor and the relief valve is opened, inhibiting and/or eliminating the fire condition in proximity to the relief valve which is located in proximity to the sensed flame and/or sensed condition.
  • An air conditioning system uses a refrigerant consisting of about 88% by weight of HFO-1234ze(E) and about 12% by weight of R227ea according to the following parameters:
  • An air conditioning system using a suction line heat exchanger (SLHX) as illustrated in FIG. 1 and using a refrigerant consisting of about 88% by weight of HFO-1234ze(E) and about 12% by weight of R227ea is tested according to the same operating parameters of Example 7 for a single stage compressor operating at 80% isentropic efficiency.
  • SSHX suction line heat exchanger
  • refrigerant consisting of about 88% by weight of HFO-1234ze(E) and about 12% by weight of R227ea
  • operation according to the embodiment of the invention as illustrated in FIG. 1 produces at least about 5° C. of superheat at the compressor discharge for the whole range of condensing temperatures tested.
  • FIG. 1 An air conditioning system according to the present invention as illustrated in FIG. 1 is tested using a suction line heat exchanger (SLHX) with an SLHX effectiveness of 0.5 and 0.7 and using a refrigerant consisting of about 88% by weight of HFO-1234ze(E) and about 12% by weight of R227ea is tested according to the same operating parameters of Example 7A.
  • This testing provides a comparison of the relative effectiveness of such systems with the system described in Example 7A (both systems using a compressor efficiency of 80%) which does not use a SLHX, and this comparison is reported in Table 7C below:
  • An air conditioning system using a two stage compressor and a three stage compressor according to the system configurations as illustrated in FIG. 2 using a refrigerant consisting of about 88% by weight of HFO-1234ze(E) and about 12% by weight of R227ea is tested and compared to a single compressor stage operating according to the configuration in Example 1.
  • a refrigerant consisting of about 88% by weight of HFO-1234ze(E) and about 12% by weight of R227ea is tested and compared to a single compressor stage operating according to the configuration in Example 1.
  • the same set of comparative tests are run for the refrigerant consisting of R134a.
  • Table 8A The results of these comparative tests are reported in Table 8A below:
  • the system includes plastic components that in operation are in contact with the refrigerant. These materials from which these components are made are compatible and/or stable. Applicants have tested the stability of various plastic materials when exposed to transHFCO-1233zd. Testing comprises submerging samples of various plastics in transHFCO-1233zd under ambient pressure conditions at room temperature (approximately 24° C.-25° C.) for two (2) weeks, after which the samples were removed from the transHFCO-1233zd and allowed to outgas for 24 hours. The results are reported in Table 9 below:

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US15/400,891 US20170191702A1 (en) 2016-01-06 2017-01-06 High efficiency air conditioning systems and methods
PCT/US2017/012627 WO2017120539A1 (en) 2016-01-06 2017-01-06 High efficiency air conditioning systems and methods
JP2018535410A JP2019507304A (ja) 2016-01-06 2017-01-06 高効率空調システム及び方法
US15/434,400 US10907863B2 (en) 2016-01-06 2017-02-16 Air conditioning systems and methods
US15/468,292 US20180017292A1 (en) 2016-01-06 2017-03-24 Low gwp cascade refrigeration system
US16/404,246 US20190331366A1 (en) 2016-01-06 2019-05-06 Low gwp cascade refrigeration system
US16/410,190 US10907862B2 (en) 2016-01-06 2019-05-13 High efficiency air conditioning systems and methods
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