WO2017143018A1 - Système de climatisation multi-étagé à faible prg - Google Patents

Système de climatisation multi-étagé à faible prg Download PDF

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Publication number
WO2017143018A1
WO2017143018A1 PCT/US2017/018106 US2017018106W WO2017143018A1 WO 2017143018 A1 WO2017143018 A1 WO 2017143018A1 US 2017018106 W US2017018106 W US 2017018106W WO 2017143018 A1 WO2017143018 A1 WO 2017143018A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
temperature refrigerant
high temperature
stream
heat exchanger
Prior art date
Application number
PCT/US2017/018106
Other languages
English (en)
Inventor
Ankit Sethi
Samuel F. Yana Motta
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 CN202311193210.2A priority Critical patent/CN117213084A/zh
Priority to CN201780023799.8A priority patent/CN109073284A/zh
Priority to EP23216913.6A priority patent/EP4365513A2/fr
Priority to KR1020187026784A priority patent/KR20180107280A/ko
Priority to EP17753804.8A priority patent/EP3417215A4/fr
Priority to JP2018561927A priority patent/JP2019504985A/ja
Priority to CN202311190250.1A priority patent/CN117249595A/zh
Priority claimed from US15/434,400 external-priority patent/US10907863B2/en
Publication of WO2017143018A1 publication Critical patent/WO2017143018A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression 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
    • 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
    • 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
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
    • F25B2500/222—Detecting refrigerant leaks

Definitions

  • the present invention relates to high efficiency, low-global warming potential ("low GWP”) air conditioning and related refrigeration systems and methods that are safe and effective.
  • low GWP low-global warming potential
  • a compressor In a 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. In the condenser the vapor, at least in major proportion, is condensed to produce a liquid heat transfer fluid at a relatively high pressure. Typically 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 as in by passing 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 that it is intended to cool.
  • the cooled fluid is the indoor air of the dwelling being air conditioned.
  • the cooling may involve cooling the air inside of a cold box or storage unit. 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.
  • a complex and interrelated combination of factors and requirements is associated with forming efficient, effective and safe air conditioning systems that are at the same time environmentally friendly, that is, have both low GWP impact and low ozone depletion
  • ODP oxygen species impact.
  • efficiency and effectiveness it is important for the heat transfer fluid to operate in air conditioning systems with high levels of efficiency and high capacity. At the same time, since it is possible that the heat transfer fluid may escape over time into the atmosphere, it is important for the fluid to have low values for both GWP and ODP.
  • 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 for use 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 systems since such flammable and/or toxic fluids may inadvertently be released into the dwelling which is being cooled (or being heated in the case of heat-pump applications), thus exposing or potentially exposing the occupants thereof to dangerous conditions.
  • a refrigerant system is provided for
  • Preferred embodiments of such systems include at least a first heat transfer circuit, which preferably comprises a first heat transfer fluid in a vapor/compression circulation loop, located substantially outside of the dwelling.
  • This first circuit is sometimes referred to herein by way of convenience as the "outdoor loop.”
  • the outdoor loop preferably comprises a compressor, a heat exchanger which serves to condense the heat transfer fluid in the outdoor loop, preferably by heat exchange with outdoor ambient air, and an expansion device.
  • the preferred system also includes at least a second heat transfer circuit, which contains a second heat transfer fluid, which is different than said first heat transfer fluid, located substantially inside of the dwelling.
  • the indoor loop preferably comprises an evaporator heat exchanger which serves to evaporate the second heat transfer fluid in the indoor loop, preferably by heat exchange with indoor air.
  • the second heat transfer circuit does not include a vapor compressor.
  • the preferred systems preferably include at least one intermediate heat exchanger which permits exchange of heat between the first heat transfer fluid and the second heat transfer fluid such that heat is transferred to the first heat transfer fluid, preferably thereby evaporating the first heat transfer fluid, and from the second heat transfer fluid, thereby condensing the second heat transfer fluid.
  • the intermediate heat exchanger is located outside the dwelling or outside the area in which the air is being conditioned
  • the first heat transfer fluid 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
  • the second heat transfer fluid comprises a refrigerant that also has a GWP of not greater than about 500, more preferably not greater than about 400, and even more preferably less than 150 and which has a low flammability and a low toxicity, and even more preferably a flammability that is substantially less than the flammability of the refrigerant in the first heat transfer fluid and/or a toxicity that is substantially less than the toxicity of the refrigerant in said first heat transfer fluid.
  • the first heat transfer fluid comprises a refrigerant which has a GWP of not greater than about 500 and that the second heat transfer fluid comprises a refrigerant that also has a GWP of not greater than about 500 and which has a flammability that is substantially less than the flammability of the refrigerant in the first heat transfer fluid and/or a toxicity that is substantially less than the toxicity of the refrigerant in said first heat transfer fluid.
  • the first heat transfer fluid comprises a refrigerant which has a GWP of not greater than about 400 and that the second heat transfer fluid comprises a refrigerant that also has a GWP of not greater than about 400 and which has a flammability that is substantially less than the flammability of the refrigerant in the first heat transfer fluid and/or a toxicity that is substantially less than the toxicity of the refrigerant in said first heat transfer fluid.
  • the first heat transfer fluid comprises a refrigerant which has a GWP of not greater than about 150 and that the second heat transfer fluid comprises a refrigerant that also has a GWP of not greater than about 150 and which has a flammability that is substantially less than the flammability of the refrigerant in the first heat transfer fluid and/or a toxicity that is substantially less than the toxicity of the refrigerant in said first heat transfer fluid.
  • 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- 1- chloro- 3,3,3-trifluoropropene (HCFO-1233zd(E)), and the first refrigerant has a flammability greater than, and preferably substantially greater than , the flammability of HCFO-1233zd(E).
  • 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- 1- chloro- 3,3,3-trifluoropropene (HCFO-1233zd(E)), and the first refrigerant has a flammability greater than, and preferably substantially greater than , the flammability of HCFO-1233zd(E).
  • Figure 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.
  • Figure 4 is a schematic representation of heat exchanger according to one embodiment of the present invention.
  • Figure 5 is a generalized process flow diagram of another preferred embodiment of an air conditioning system which can operate in both a cooling and a heating according to the present invention.
  • the second refrigerant comprises from about 95% by weight to about 99% 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.
  • 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 second refrigerant comprises from about greater than about 50% by weight to about 67.5 by weight of by weight of transl, 3,3,3- tetrafluoropropene (HFO-1234ze(E)) and from greater than about 9.7% to less than about 50% by weight of HFCO-1233zd(E), and even more preferably in some embodiments about 67% of transl,3,3,3-tetrafluoropropene (HFO-1234ze(E)) and about 33% by weight of HFCO- 1233zd(E).
  • the first refrigerant may comprise one or more components that would make the refrigerant substantially less desirable from a toxicity and/or flammability standard than the second refrigerant, and all such first refrigerants are included within the scope of the present invention.
  • the first refrigerant may include one or more of blends comprising one or more of HFC-32 (preferably in amounts of from about 0% to about 22% by weight), HFO-1234ze (preferably in amounts of from about 0% to about 78% by weight), HFO-1234yf (preferably in amounts of from about 0% to about 78% by weight) and propane.
  • the second heat transfer compositions of the present invention in contrast to the first heat transfer composition, generally does not include lubricant since this fluid is not required to pass through a compressor.
  • the first heat transfer composition also generally includes a lubricant, generally 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 and other optional components that are present in the system.
  • Other optional components include a compatibilizer, such as 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. 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.
  • FIG. 1 One preferred air conditioning system, designated generally at 10, is illustrated in Figure 1, wherein the dotted line represents the approximate boundary between the indoor and the outdoor loops, with the compressor 11, condenser 12, intermediate heat exchanger 13 and expansion valve 14, together with any of the associated conduits 15 and 16 and other connecting and related equipment (not shown) being located outdoors.
  • the outdoor loop which is also sometimes referred to herein as the "high temperature refrigerant circuit,” preferably comprises a first heat transfer composition, preferably according to one or more of the preferred
  • the indoor loop which is also sometimes referred to herein as the "low temperature refrigerant circuit,” preferably comprises at least a second heat transfer composition comprising a second refrigerant, wherein said second refrigerant has at least one safety property, such as flammability and toxicity, that is superior to the corresponding safety property of the first refrigerant.
  • the second refrigerant is preferably of sufficiently low toxicity to be designated as Class A according to ASHRAE Standard 34, and also preferably is of sufficiently low flammability to have a Class 1 or 2L flammability rating.
  • the second refrigerant comprises, preferably consists essentially of, and in some embodiments consists of, HFCO-1233zd, and even more preferably transHFCO- 1233zd.
  • the second refrigerant comprises, preferably consists essentially of, and in some embodiments consists of, combinations of HFO-1234ze(E) and 1,1,1,2,3,3,3-heptafluoropropane (HFC-227ea).
  • the preferred configurations and selection of refrigerants permit the provision of systems which benefit from the use of refrigerants that have many desirable properties, such as capacity, efficiency, low GWP and low ODP, but at the same time, possess one or more properties which would otherwise make them highly disadvantageous and/or preclude their use in proximity to the humans or other animals in a confined and/or closed location.
  • Such combinations provide exceptional advantages in terms of all the desirably properties for such refrigerant systems.
  • the first refrigerant may comprise, for example, one or more of blends comprising one or more of HFC-32 (preferably in amounts of from about 0% to about 22% by weight), HFO-1234ze (preferably in amounts of from about 0% to about 78% by weight), HFO-1234yf (preferably in amounts of from about 0% to about 78% by weight) and propane.
  • the heat transfer fluid in the outdoor circuit will generally and preferably include lubricant for the compressor generally in amounts of from about 30 to about 50 percent by weight of the heat transfer fluid, with the balance comprising refrigerant and other optional components that may be present.
  • Other optional components include a compatibilizer, such as 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. 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 second refrigerant according to the present invention circulates through the circuit by flowing through the intermediate heat exchanger 13, wherein it transfers heat to the first refrigerant, and in so doing, condenses at least a portion, and preferably substantially all of the second refrigerant to liquid form where it exits the intermediate heat exchanger through conduit 17.
  • the second refrigerant exiting the intermediate heat exchanger enters a receiver 18, wherein a liquid reservoir of the second refrigerant is provided.
  • receiver 18 is shown in the Figure as being located indoors, this vessel may also be located outdoors, and it may also be preferred to locate pump 20, when present, outdoors. Liquid refrigerant from the separation vessel is conducted to the evaporator via conduit 21.
  • a liquid pump 20 is shown as assisting in the transport of the liquid refrigerant through conduits 21, 22 and valve 23 to the evaporator 24.
  • the second refrigerant liquid can be transported from the receiver using other means or techniques that can be used either alone or in combination with a liquid pump.
  • transport of the liquid refrigerant may be accomplished by using a gravity feed of the liquid to the evaporator, while in other embodiments, a thermal siphon arrangement can be utilized to transport the second liquid refrigerant to the evaporator 24 and from the evaporator to the intermediate heat exchanger 13.
  • the operating conditions correspond to the values described in the table below: HIGH TEMPERATURE CIRCUIT PREFERRED RANGE
  • FIG. 2 Another preferred embodiment of the present invention is illustrated in Figure 2, with the compressor 11, condenser 12, intermediate heat exchanger 13, expansion valve 14, and suction- line heat exchanger 30, together with any of the associated conduits 15A, 15B, 16A and 16B and other connecting and related equipment (not shown) being located outdoors.
  • the outdoor loop which is also sometimes referred to herein as the "high temperature refrigerant circuit,” preferably comprises a first heat transfer composition comprising a first refrigerant and lubricant for the compressor, with at least the refrigerant circulating in the circuit by way of a conduits 17, 19, 21 and 22 and other related conduits and equipment.
  • the indoor loop is configured substantially the same as described above in connection with the indoor loop of Figure 1, and the first and second heat transfer compositions are also preferably as otherwise indicated herein.
  • the first 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 enters condenser 12 where it transfers heat, preferably to ambient air, and at least partially condenses.
  • the refrigerant effluent from the condenser 12 is transported via conduit 15A to suction-line heat exchanger 30 where it loses additional heat to the effluent from the intermediate heat exchanger 13.
  • the effluent from the suction/liquid line heat exchanger 30 is then transported via conduit 15B to expansion valve 14 where the pressure of the refrigerant is reduced, which in turn reduces the temperature of the refrigerant.
  • the relatively cold liquid refrigerant from the expansion valve then enters the intermediate heat exchanger 13 where it gains heat from the second refrigerant vapor leaving the evaporator 24 in the indoor loop.
  • the first refrigerant effluent vapor from the intermediate heat exchanger is then transported via conduit 16A to the suction/liquid line heat exchanger 30 where it gains heat from the condenser effluent from conduit 15A and produces second refrigerant vapor at a higher temperature, which is transported by conduit 16B to the inlet of the compressor 11
  • the evaporator effluent is transported receiver conduit 19 to the intermediate heat exchanger 13 where it loses heat to the effluent from the suction line heat exchanger, which is transported to the intermediate heat exchanger via conduit 15B, and produces a relatively cold stream of the second refrigerant.
  • This cold stream of second refrigerant exiting from the intermediate heat exchanger 13 is transported to receiver tank 18 which provides a reservoir of cold liquid refrigerant which is transported from the tank via conduit 21 and is then fed by way of control valve 23 into the evaporator 24.
  • a pump 20 is provided to provide a flow of liquid to the control valve 23.
  • 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 back to the intermediate heat exchanger 13.
  • the operating conditions correspond to the values described in the table below:
  • FIG. 3 Another preferred embodiment of the present invention is illustrated in Figure 3, with the two-stage compressor 11, condenser 12, intermediate heat exchanger 13, expansion valve 14, and vapor- injection heat exchanger 40, including associated intermediate expansion valve 41, together with any of the associated conduits 15A - 15 and other connecting and related equipment (not shown and/or not labeled), being located outdoors.
  • the outdoor loop which is also sometimes referred to herein as the "high temperature refrigerant circuit,” preferably comprises a first heat transfer composition comprising a first refrigerant and lubricant for the compressor, with at least the refrigerant circulating in the circuit by way of a conduits 15 and 16 and other related conduits and equipment .
  • the indoor loop is configured substantially the same as described above in connection with the indoor loop of Figure 1, and the first and second heat transfer compositions are also preferably as otherwise indicated herein.
  • the first refrigerant according to the present invention which may include entrained lubricant, is discharged from compressor 11 as a relatively high pressure refrigerant vapor, which may include entrained lubricant, and which then enters condenser 12 where is its transfers heat, preferably to ambient air and at least partially condenses.
  • the effluent stream from the condenser 12 comprising at least partially, and preferably substantially fully, condensed refrigerant.
  • the refrigerant effluent from the condenser 12 is transported via conduit 15A, and a portion of the refrigerant effluent is routed via conduit 15B 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 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, 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 19C.
  • conduit 15A As the higher pressure stream transported by conduit 15A travels through the heat exchanger 40 it loses heat to the lower pressure stream exiting expansion device 41 and exits the heat exchanger through conduit 15C and then flows to expansion device 14 and is heat then forwarded to the intermediate heat exchanger where it gains heat and is transported to the first stage of the compressor suction.
  • the operating conditions correspond to the values described in the table below:
  • FIG. 5 The embodiment disclosed in Figure 5 is similar to the embodiment of Figure 1 except the system is equipped with a reversible valve so that it can operate in a heating mode, as described below.
  • FIG. 1 One preferred air conditioning system operable in both a cooling and heating mode is designated generally at 10, is illustrated in Figure 1, wherein the indicatd line represents the approximate boundary between the indoor and the outdoor loops, with the compressor 11, outdoor coil 12, intermediate heat exchanger 13, expansion valve 14, and reversing valve 500, together with any of the associated conduits 15 and 16 and other connecting and related equipment (not shown) being located outdoors.
  • the outdoor loop preferably comprises a first heat transfer composition, preferably according to one or more of the preferred embodiments described above, comprising a first refrigerant and lubricant for the compressor , with at least the first refrigerant circulating in the circuit by way of a conduits 15 and 16 and other related conduits and equipment .
  • the indoor loop preferably comprises at least a second heat transfer composition comprising a second refrigerant, wherein said second refrigerant has at least one safety property, such as flammability and toxicity, that is superior to the corresponding safety property of the first refrigerant.
  • the second refrigerant is preferably of sufficiently low toxicity to be designated as Class A according to ASHRAE Standard 34, and also preferably is of sufficiently low flammability to have a Class 1 or 2L flammability rating.
  • the second refrigerant comprises, preferably consists essentially of, and in some embodiments consists of, HFCO-1233zd, and even more preferably transHFCO-1233zd.
  • the second refrigerant comprises, preferably consists essentially of, and in some embodiments consists of, combinations of HFO-1234ze(E) and 1,1,1,2,3,3,3-heptafluoropropane (HFC-227ea).
  • the preferred configurations and selection of refrigerants permit the provision of systems which benefit from the use of refrigerants that have many desirable properties, such as capacity, efficiency, low GWP and low ODP, but at the same time, possess one or more properties which would otherwise make them highly disadvantageous and/or preclude their use in proximity to the humans or other animals in a confined and/or closed location.
  • Such combinations provide exceptional advantages in terms of all the desirably properties for such refrigerant systems.
  • the first refrigerant may comprise, for example, one or more of blends comprising one or more of HFC-32 (preferably in amounts of from about 0% to about 22% by weight), HFO-1234ze (preferably in amounts of from about 0% to about 78% by weight), HFO-1234yf (preferably in amounts of from about 0% to about 78% by weight) and propane.
  • the heat transfer fluid in the outdoor circuit will generally and preferably include lubricant for the compressor generally in amounts of from about 30 to about 50 percent by weight of the heat transfer fluid, with the balance comprising refrigerant and other optional components that may be present.
  • Other optional components include a compatibilizer, such as 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. 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 second refrigerant according to the heating mode embodiment of Figure 5 of the present invention circulates through the circuit by flowing through the intermediate heat exchanger 13, wherein it picks-up heat from the first refrigerant, and in so doing, vaporizes at least a portion, and preferably substantially all of the second refrigerant to vapor form where it exits the intermediate heat exchanger through conduit 17.
  • Vaporous refrigerant is conducted to the condenser via conduit 21 where it rejects heat into the dwelling as it condenses.
  • a liquid pump 20 is shown as assisting in the transport of the liquid refrigerant through conduits 21, 22 and valve 23 to the condenser 24.
  • this indoor loop also includes a reversible valve 501 which allows the system to operate in both the heating and the cooling mode.
  • the refrigerant comprises at least about 90% by weight, preferably consisting essentially of, and preferably consisting of, either HCFO- 1233zd(E) or HFO-1234ze(E).
  • An air conditioning system according to a typical arrangement which uses R-410A as the refrigerant is operated according to the following parameters: Operating Conditions - R410A Basic Cycle
  • the capacity and COP of this system is determined using as base-line values for determining the relative capacity and COP in the following examples.
  • a system configured as illustrated herein in Figure 1 is operated according to the following operating parameters using a series of different first (outdoor) and second (indoor) refrigerants:
  • each of the air-conditioning systems according to the present invention were capable of providing a precise capacity match to a prior R410A air- conditioning system operated as indicated and a COP (efficiency) that in all cases is at least 85% relative to such prior systems.
  • the system utilizes refrigerants that each have a GWP of less than 150, which is approximately a 10 times improvement of the refrigeration system based upon R-410A. The ability to achieve this combination of properties this is a highly beneficial but unexpected result.
  • Example IB Figure 1 Operating Conditions
  • a system configured as illustrated herein in Figure 1 is operated according to the same operating parameters using a series of different first (outdoor) and second (indoor) refrigerants , except that the condensing temperature is adjusted for each blend in order to obtain an efficiency that substantially matches the efficiency achieved according to Comparative Example 1.
  • the results are provided in Table IB below:
  • the efficiency according to the present methods is preferably increased, without reducing or altering the comparative condenser temperature, by providing a slight increase in heat transfer area in the condenser compared to the amount of heat transfer area in the condenser used with the comparative R-410A system.
  • the system according to Figure 2 which utilizes a suction line heat exchanger shows an advantageous improvement in efficiency compared even to the configuration of the present invention without such a heat exchanger as reported in Example 1A.
  • Example 1A A system configured as illustrated herein in Figure 1 is operated according to the same operating parameters as Example 1A using a series of different first (outdoor) and second (indoor) refrigerants, except that the ambient temperature is adjusted to 35C, 45C and 55C for each blend.
  • the results are provided in Table 1C below:
  • a system configured as illustrated herein in Figure 2 is operated according to the following operating parameters using a series of different first (outdoor) and second (indoor) refrigerants:
  • each of the air-conditioning systems according to the present invention were capable of providing a precise capacity match to a prior R410A air- conditioning system operated as indicated and a COP (efficiency) that in all cases is at least 90% relative to such prior systems.
  • the system utilizes refrigerants that each have a GWP of less than 150, which is approximately a 10 times improvement of the
  • a system configured as illustrated herein in Figure 2 is operated according to the same operating parameters as Example 2A using a series of different first (outdoor) and second (indoor) refrigerants, except that the condensing temperature is adjusted for each blend in order to obtain an efficiency that substantially matches the efficiency achieved according to
  • the efficiency according to the present methods is preferably increased, without reducing or altering the comparative condenser temperature, by providing a slight increase in heat transfer area in the condenser compared to the amount of heat transfer area in the condenser used with the comparative R-410A system.
  • Example 2C A system configured as illustrated herein in Figure 2 is operated according to the same operating parameters as Example 2A using a series of different first (outdoor) and second (indoor) refrigerants, except that the ambient temperature is adjusted to 35C, 45C and 55C for each blend.
  • the results are provided in Table 2C below:
  • Vapor Injection Heat Exchanger Effectiveness 35%, 55%, 75%, 85%
  • each of the air-conditioning systems according to the present invention were capable of providing a precise capacity match to a prior R410A air- conditioning system operated as indicated and a COP (efficiency) that in all cases is at least 90% relative to such prior systems.
  • the system utilizes refrigerants that each have a GWP of less than 150, which is approximately a 10 times improvement of the refrigeration system based upon R-410A. The ability to achieve this combination of properties this is a highly beneficial but unexpected result.
  • Example 3A A system configured as illustrated herein in Figure 3 is operated according to the same operating parameters as Example 3A using a series of different first (outdoor) and 100% transHFCO-1233zd as the indoor refrigerant, except that the condensing temperature is adjusted for each blend in order to obtain an efficiency that substantially matches the efficiency achieved according to Comparative Example 1.
  • Table 3B The results are provided in Table 3B below:
  • the efficiency according to the present methods is preferably increased, without reducing or altering the comparative condenser temperature, by providing a slight increase in heat transfer area in the condenser compared to the amount of heat transfer area in the condenser used with the comparative R-410A system.
  • Example 3 A system configured as illustrated herein in Figure 3 is operated according to the same operating parameters as Example 2A using a series of different first (outdoor) and second (indoor) refrigerants, except that the ambient temperature is adjusted to 35C, 45C and 55C for each blend.
  • the results are provided in Table 3C below:
  • Example 1 The air conditioning system of Example 1 is operated with an indoor refrigerant comprising various binary mixtures of transHCFO-1233zd and transHFO-1234ze using evaporator temperatures ranging from about -1C to about IOC, which generally encompasses the condenser temperatures that are used in many important air conditioning systems.
  • evaporator temperatures ranging from about -1C to about IOC, which generally encompasses the condenser temperatures that are used in many important air conditioning systems.
  • compositions in which the amount of transHFO-1234ze is at least about 50% by weight, as illustrated above in Table 4, permit the indoor circuit to operate under pressures greater than one atmosphere, thereby avoiding the need for a purge system, while at the same time providing a system pressure sufficiently low to allow the use of relatively low-cost vessels and conduits and/or to advantageously avoid refrigerant leaks that might otherwise occur in high pressure systems.
  • applicants have tested the flammability of transHFO- 1234ze/transHCFO-1233zd the blends on fractionation flammability, which is relevant to the flammability of the refrigerant in the event of a leak from the system, and the result of this work is reported in Table 4B below:
  • the air conditioning system of Example 1 is operated under a condition in which there is an inadvertent leak of the high temperature refrigerant, which is a A2L refrigerant into the low temperature non-flammable refrigerant according to ASHRAE 34 comprising any of the preferred low temperature refrigerants of the present invention, including refrigerants comprising HFO-1234ze(E), HFCO-1233zd(E) and combinations of these.
  • the A2L (mildly- flammable) refrigerant mixes with non-flammable low temperature refrigerant in the case of an inadvertent leak inside intermediate heat exchanger.
  • the resulting mixture of low temperature refrigerant (e.g., R1233zd(E)) and A2L refrigerant could eventually leak into the indoors.
  • the leak into the indoors will be a non-flammable material.
  • the accumulator can be used, together with appropriate controls, to ensure that the proper charge ratio is maintained between high side and low side to ensure nonflammable mixture. It may also be possible to incorporate into the present systems A device or devices that can detect a leak of flammable refrigerant into the indoor loop and release all such refrigerant outside the home.
  • One such leak detection system is disclosed in US Application 15/400,891, filed January 6, 2017 (see particularly Figures 4A and 4B) and Provisional
  • Table 6 shows the charge ratio which in case of a leak event can prevent a hazardous situation to happen inside the dwelling.
  • a reversible heat pump system according to typical prior art arrangement which uses R- 410A as the refrigerant is operated in heating mode according to the following parameters:
  • the capacity and COP of this system is determined using as base-line values for determining the relative capacity and COP in the following Examples 7A and 7B according to the present invention.
  • a system configured as illustrated herein in Figure 6 is operated according to the following operating parameters using a series of different first (outdoor) and second (indoor) refrigerants:
  • each of the air-conditioning systems according to the present invention were capable of providing a precise capacity match to a prior R410A air- conditioning system operated as indicated and a COP (efficiency) that in all cases is at least 90% relative to such prior systems.
  • the system utilizes refrigerants that each have a GWP of less than 150, which is approximately a 10 times improvement of the refrigeration system based upon R-410A. The ability to achieve this combination of properties this is a highly beneficial but unexpected result.
  • a system configured as illustrated herein in Figure 5 is operated according to the same operating parameters using a series of different first (outdoor) and second (indoor) refrigerants , except that the condensing temperature is adjusted for each blend in order to obtain an efficiency that substantially matches the efficiency achieved according to Comparative Example 2.
  • the results are provided in Table 7B below:
  • the efficiency according to the present methods is preferably increased, without reducing or altering the comparative condenser temperature, by providing a slight increase in heat transfer area in the condenser compared to the amount of heat transfer area in the condenser used with the comparative R-410A system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubricants (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne des systèmes frigorifiques destinés au conditionnement de l'air et/ou d'articles situés à l'intérieur d'une habitation occupée par des êtres humains ou animaux, les systèmes comprenant de préférence au moins un premier circuit de transfert de chaleur contenant un premier fluide de transfert de chaleur dans une boucle de circulation à compression de vapeur, situé sensiblement à l'extérieur de l'habitation, et au moins un second circuit de transfert de chaleur contenant un second fluide de transfert de chaleur différent du premier fluide de transfert de chaleur, situé sensiblement à l'intérieur de l'habitation. Dans des modes de réalisation préférés, le second circuit de transfert de chaleur ne comprend pas un compresseur de vapeur, mais le système comprend au moins un échangeur de chaleur intermédiaire permettant l'échange de chaleur entre le premier fluide de transfert de chaleur et le second fluide de transfert de chaleur, de sorte que la chaleur soit transférée au premier fluide de transfert de chaleur afin d'évaporer ainsi de préférence le premier fluide de transfert de chaleur, et depuis le second fluide de transfert de chaleur afin de condenser ainsi le second fluide de transfert de chaleur. De préférence, l'échangeur de chaleur intermédiaire est situé à l'extérieur de l'habitation. Le premier fluide de transfert de chaleur comprend un fluide frigorigène présentant un potentiel de réchauffement global (PRG) inférieur à environ 500 et le second fluide de transfert de chaleur comprend un fluide frigorigène offrant également un PRG maximal de à 500 et une faible inflammabilité et une faible toxicité, et de préférence encore une inflammabilité sensiblement inférieure à l'inflammabilité du fluide frigorigène dans le premier fluide de transfert de chaleur et/ou une toxicité sensiblement inférieure à la toxicité du fluide frigorigène dans ledit premier fluide de transfert de chaleur.
PCT/US2017/018106 2016-02-16 2017-02-16 Système de climatisation multi-étagé à faible prg WO2017143018A1 (fr)

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CN202311193210.2A CN117213084A (zh) 2016-02-16 2017-02-16 多级低gwp空气调节系统
CN201780023799.8A CN109073284A (zh) 2016-02-16 2017-02-16 多级低gwp空气调节系统
EP23216913.6A EP4365513A2 (fr) 2016-02-16 2017-02-16 Système de climatisation à faible prg à plusieurs étages
KR1020187026784A KR20180107280A (ko) 2016-02-16 2017-02-16 다단계 저 gwp 에어 컨디셔닝 시스템
EP17753804.8A EP3417215A4 (fr) 2016-02-16 2017-02-16 Système de climatisation multi-étagé à faible prg
JP2018561927A JP2019504985A (ja) 2016-02-16 2017-02-16 多段低ｇｗｐ空調システム
CN202311190250.1A CN117249595A (zh) 2016-02-16 2017-02-16 多级低gwp空气调节系统

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US15/434,400 US10907863B2 (en) 2016-01-06 2017-02-16 Air conditioning systems and methods

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FR3085468A1 (fr) * 2018-09-03 2020-03-06 Arkema France Procede de conditionnement d'air
EP3642541A1 (fr) * 2017-06-21 2020-04-29 Honeywell International Inc. Systèmes et procédés de réfrigération
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FR3102009A1 (fr) 2019-10-15 2021-04-16 Arkema France Procédé de régulation de la température d’une batterie d’un véhicule automobile
FR3102010A1 (fr) 2019-10-15 2021-04-16 Arkema France Procédé de régulation de la température d’une batterie comprenant un sel de lithium
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US11702976B2 (en) 2020-03-18 2023-07-18 Rolls-Royce North American Technologies Inc. Vapor leak pressure relief and diversion system
WO2024081532A1 (fr) * 2022-10-12 2024-04-18 Daikin Comfort Technologies Manufacturing, L.P. Système de pompe à chaleur à climatisation froide en cascade

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EP4063762A1 (fr) 2021-03-26 2022-09-28 Mitsubishi Electric R&D Centre Europe B.V. Système de pompe à chaleur en cascade à refrigérant à faible effet de serre
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EP3642541A1 (fr) * 2017-06-21 2020-04-29 Honeywell International Inc. Systèmes et procédés de réfrigération
EP4328283A3 (fr) * 2017-06-21 2024-05-01 Honeywell International Inc. Systèmes et procédés de réfrigération
EP3642541A4 (fr) * 2017-06-21 2021-03-24 Honeywell International Inc. Systèmes et procédés de réfrigération
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WO2019197783A1 (fr) * 2018-04-13 2019-10-17 Arkema France Procede de refroidissement et/ou de chauffage d'un corps ou d'un fluide dans un vehicule automobile
WO2020049239A1 (fr) * 2018-09-03 2020-03-12 Arkema France Procede de conditionnement d'air
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WO2021074497A1 (fr) 2019-10-15 2021-04-22 Arkema France Procédé de regulation de la température d'une batterie d'un vehicule automobile
FR3102010A1 (fr) 2019-10-15 2021-04-16 Arkema France Procédé de régulation de la température d’une batterie comprenant un sel de lithium
FR3120992A1 (fr) 2019-10-15 2022-09-23 Arkema France Procédé de régulation de la température d’une batterie d’un véhicule automobile
FR3102009A1 (fr) 2019-10-15 2021-04-16 Arkema France Procédé de régulation de la température d’une batterie d’un véhicule automobile
US11702976B2 (en) 2020-03-18 2023-07-18 Rolls-Royce North American Technologies Inc. Vapor leak pressure relief and diversion system
US11365909B2 (en) * 2020-06-11 2022-06-21 Rolls-Royce North American Technologies Inc. Vapor leak separation and detection system
CN111981648A (zh) * 2020-08-25 2020-11-24 Tcl空调器(中山)有限公司 空调器制热控制方法、装置、空调器及可读存储介质
WO2024081532A1 (fr) * 2022-10-12 2024-04-18 Daikin Comfort Technologies Manufacturing, L.P. Système de pompe à chaleur à climatisation froide en cascade

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