US20010023594A1 - Refrigeration system - Google Patents

Refrigeration system Download PDF

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Publication number
US20010023594A1
US20010023594A1 US09/796,639 US79663901A US2001023594A1 US 20010023594 A1 US20010023594 A1 US 20010023594A1 US 79663901 A US79663901 A US 79663901A US 2001023594 A1 US2001023594 A1 US 2001023594A1
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Prior art keywords
refrigerant
liquid
pressure side
refrigerant vapor
vapor
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Abandoned
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US09/796,639
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English (en)
Inventor
Richard-Charles Ives
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Nestec SA
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Nestec SA
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Assigned to NESTEC S.A. reassignment NESTEC S.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IVES, RICHARD-CHARLES
Publication of US20010023594A1 publication Critical patent/US20010023594A1/en
Abandoned legal-status Critical Current

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    • 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
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • the invention relates to a refrigeration system comprising a first and a second closed refrigeration circuit, the second refrigeration circuit being arranged to refrigerate the first refrigeration circuit by means of a cascade heat exchange connection.
  • the refrigeration system provides refrigeration that is energy efficient.
  • the refrigeration system is particularly suitable for use in the food industry.
  • the invention also relates to a method of refrigeration using the refrigeration system of the invention.
  • U.S. Pat. No. 5,042,262 describes a food freezer, which uses CO 2 as a low temperature refrigerant, being cooled in cascade by another evaporating refrigerant operating at a higher temperature.
  • the patent recommends pressures in the CO 2 evaporator of between 60.4 psig and 120 psig. Also recommended is a compressor pressure of less than 325 psig.
  • the specifically recommended pressure limits disclosed in this patent makes the system significantly less efficient than a conventional industrial refrigeration system. The users of the system will be operating the system with evaporation pressures below 120 psig, which corresponds to a saturation temperature of ⁇ 44° F.
  • the present invention relates to a refrigeration system.
  • the refrigeration system includes a first closed refrigeration circuit for containing a first refrigerant comprising a high pressure side and a low pressure side, a first evaporator for evaporating a first refrigerant liquid to provide a first refrigerant vapor, a first compressor for compressing the first refrigerant vapor, a first condenser for condensing the first refrigerant vapor, and a first control valve for controlling the pressure difference between a high pressure side and a low pressure side of the first refrigeration circuit; a second closed refrigeration circuit for containing a second refrigerant, comprising a high pressure side and a low pressure side, a second evaporator for evaporating a second refrigerant liquid to provide a second refrigerant vapor, a second compressor for compressing the second refrigerant vapor, a second condenser for condensing the second refrigerant vapor, and a second control valve for controlling
  • the first evaporator may be at a pressure of between about 120 psig and 1056 psig, preferably about 120 psig and 580 psig.
  • the first compressor may compresses the first refrigerant vapor to a pressure above about 325 psig., preferably to a pressure of from about 325 psig to 580 psig and the second compressor may compresses the second refrigerant vapor to a pressure below about 325 psig.
  • the refrigeration system may further include an open flash economizer vessel subsequent to the first condenser to cool the first liquid refrigerant to a temperature intermediate between the temperature of the first refrigerant liquid in the high pressure side and the temperature of the first refrigerant liquid in the low pressure side by evaporating some of the first liquid refrigerant to provide a first refrigerant vapor, wherein the economizer vessel is connected to an economizer port of the first compressor so that the first refrigerant vapor can be compressed by the compressor.
  • the refrigeration system further includes a heat exchanger subsequent to the first condenser to cool the first liquid refrigerant to a temperature intermediate between the temperature of the first refrigerant liquid in the high pressure side and the first refrigerant liquid in the low pressure side by evaporating some of the first liquid refrigerant to provide a first refrigerant vapor, wherein the heat exchanger is connected to the economizer port of the first compressor so that first refrigerant vapor can be compressed by the compressor.
  • the second evaporator may be operated at a pressure such that the temperature difference between the second evaporator and the first condenser is no more than about 5° F.
  • the refrigeration system may further include a package refrigeration system in the first refrigeration circuit to control the pressure in the first refrigeration circuit by cooling the CO 2 when the refrigeration system is not being used.
  • the second refrigerant may be ammonia, a hydrofluorocarbon, or a hydrocarbon.
  • the invention further relates to a method of refrigerating an article.
  • the method involves providing a first refrigerant of CO 2 in a first refrigeration circuit and second refrigerant in a second refrigeration circuit;
  • the method of the invention uses the refrigeration system of the invention.
  • FIG. 1 is a schematic depicting the refrigeration system of the invention.
  • the invention relates to an efficient refrigeration system that uses CO 2 .
  • the refrigeration system comprises:
  • a first closed refrigeration circuit for containing a first refrigerant comprising a high pressure side and a low pressure side, a first evaporator for evaporating a first refrigerant liquid to provide a first refrigerant vapor, a first compressor for compressing the first refrigerant vapor, a first condenser for condensing the first refrigerant vapor, and a first control valve for controlling the pressure difference between a high pressure side and a low pressure side of the first refrigeration circuit,
  • a second closed refrigeration circuit for containing a second refrigerant, comprising a high pressure side and a low pressure side, a second evaporator for evaporating a second refrigerant liquid to provide a second refrigerant vapor, a second compressor for compressing the second refrigerant vapor, a second condenser for condensing the second refrigerant vapor, and a second control valve for controlling the pressure difference between the high pressure side and the low pressure side of the second circuit, and
  • a cascade heat exchanger comprising the first condenser and the second evaporator arranged so that the first condenser is cooled by evaporation of the second refrigerant liquid in the second evaporator, wherein the first refrigerant comprises CO 2 and the first evaporator is operated at pressures above about 120 psig.
  • the high pressure side is the part of the refrigeration circuit between the exit of the compressor and the entry of the control valve.
  • the low pressure side is the rest of the circuit; i.e., between the exit of the valve and the entry of the compressor.
  • the refrigeration system according to the invention allows the operating conditions of the system to be set so that they match the needs of the user.
  • the evaporating pressure of the first refrigerant which determines the corresponding evaporating temperature, can be set by the user. Due to the refrigeration systems ability to work at high pressures, it is possible to select a pressure in the evaporators that corresponds to an evaporation temperature in the range from about ⁇ 44° F. to ⁇ 10° F.
  • the resulting system is significantly safer than ammonia systems since the ammonia in the manufacturing areas is replaced with CO 2 , which is significantly less toxic.
  • the refrigeration system has been shown to be competitive in capital costs and energy efficiency.
  • the operating pressure throughout the first refrigeration circuit is between about 120 psig and 1056 psig.
  • 1056 psig is the critical point for CO 2 , above which CO 2 cannot be condensed to liquid.
  • a more preferred operation pressure throughout the first refrigeration circuit is from about 120 psig to 580 psig.
  • the first compressor 4 preferably has an operation pressures above about 325 psig at the discharge of the compressor 4 , more preferably from about 325 psig to 580 psig, and most preferably from about 350 psig to about 425 psig. With these operating pressures in the first circuit and the first compressor a particularly energy efficient cascade refrigeration system is obtained.
  • the operation pressure throughout the second refrigeration circuit is below about 350 psig so that standard refrigeration components can be used.
  • the first evaporator is operated at pressures from about 120 psig to 580 psig, more preferably from about 120 psig to 180 psig, most preferably from about 122 to 160 psig.
  • the first refrigeration circuit comprises means for cooling the first refrigerant liquid subsequent to it condensing in the first condenser.
  • the means for cooling the first refrigerant may comprise an open flash economizer vessel connected to the first compressor in which some of the first refrigerant liquid is evaporated, cooling the rest of the first refrigerant liquid to a temperature intermediate between the temperature of the first refrigerant liquid in the high pressure vessel and the temperature of the first refrigerant liquid in the low pressure vessel, and allowing the vapor to be forwarded to the economizer port of the first compressor.
  • a heat exchanger may be used to cool the first refrigerant liquid.
  • the operating pressure of the second evaporator corresponds to a saturation temperature that is as close as possible to the saturation temperature equivalent to the pressure of the first refrigerant in the first condenser.
  • this temperature difference should be about 5° F. (2° C.).
  • FIG. 1 showing an example of a preferred refrigeration system according to the invention.
  • FIG. 1 shows a refrigeration system having a first refrigeration circuit 17 and a second refrigeration circuit 18 arranged in cascade.
  • the first refrigerant is CO 2 .
  • Liquid CO 2 is pumped by means of a pump 2 from a low-pressure CO 2 vessel 1 to one or more evaporators 3 operating in parallel, where it evaporates, removing heat (Q) from the medium being cooled.
  • the pumping rate to the evaporators is at least equal to the evaporation rate; but could be more to ensure wetting on the CO 2 side of each evaporator.
  • the liquid can be supplied without a pump by using natural circulation.
  • the evaporators 3 may be any conventional evaporator, but designed for working pressures that correspond to the nature of the medium being cooled. Suitable evaporators for use in the invention include, but are not limited to, plate evaporators, fin-coil units, scraped surface evaporators, and tubular coolers. Subsequently the mixture of CO 2 liquid and vapor returns to the low-pressure CO 2 vessel 1 , where the liquid and vapor are separated. The liquid is then available to be sent back to the evaporators. The CO 2 vapor goes to a CO 2 compressor 4 , where it is compressed to a pressure preferably exceeding about 325 psig, but less than the CO 2 critical point (1056 psig). To improve system efficiency, the compressor 4 may advantageously be fitted with an “economizer port” to accept additional vapor from a CO 2 economizer vessel 7 .
  • the compressors 4 may be any type suitable for the required duty.
  • the preferred compressor type is an oil injected screw compressor with gravity and coalescing oil separator. Suitable compressors may be obtained from Mycom Chemical Process Corp. of Torrance, Calif.; Sabroe Refrigeration AB of Sweden; or FES Corp of York, Pa., for example. If needed tertiary oil separation may be provided using activated carbon or other similar material.
  • Another type of a compressor which is suitable for the present application is a reciprocating compressor.
  • the compressed CO 2 is then cooled and condensed in a cascade heat exchanger 5 , which is cooled by the evaporation of a second refrigerant that can operate at higher saturation temperatures than CO 2 with pressures below 350 psig in order to permit the use of standard commercial refrigeration components in the second refrigerant circuit.
  • a plate type heat exchanger is preferred to minimize the temperature difference between the condensing CO 2 and the evaporating second refrigerant in order to improve the efficiency of the system.
  • a purpose built shell and tube heat exchanger may be used.
  • the condensed CO 2 is stored in a high-pressure CO 2 vessel 6 , until it is needed in the evaporators 3 .
  • storage could be in the low pressure CO 2 vessel 1 or the CO 2 economizer vessel 7 .
  • a control valve is needed after the cascade heat exchanger 5 to maintain pressure in the cascade heat exchanger 5 (the first condenser). This control valve has a function similar to control valve 19 described below.
  • liquid CO 2 is fed to the low-pressure CO 2 vessel 1 through a control valve 19 where pressure is decreased to that of the low-pressure vessel 1 , with a portion of the CO 2 evaporating to cool the liquid.
  • the resulting liquid/vapor mixture flows to the low-pressure vessel 1 , where the liquid and vapor components are separated.
  • the vapor is combined with the vapor from the evaporator 3 , with both going to the compressor 4 . This completes the closed circulation of the CO 2 .
  • the liquid may first go through a control valve 19 to a CO 2 economizer vessel or heat exchanger 7 , operating at a pressure intermediate between that of the high-pressure CO 2 vessel 6 and the low-pressure CO 2 vessel 1 . At this intermediate pressure, some of the liquid CO 2 evaporates, cooling the remainder of the liquid. The vapor is separated from the liquid and goes to the “economizer port” on the compressor 4 .
  • the high-pressure CO 2 vessel 6 and CO 2 economizer vessel 7 are connected to additional evaporators 9 and 8 , respectively, to provide cooling at operating temperatures higher than that of the main evaporators 3 .
  • the method of liquid and vapor circulation is the same as for evaporator 3 .
  • the vessels, evaporators, and heat exchangers may be fitted with safety relief valves and/or other pressure activated devices to release vapor from the CO 2 circuit, reducing the pressure.
  • any or each vessel, evaporator, or heat exchanger in the CO 2 circuit may be connected to a small package refrigeration system 10 , to control the pressure by cooling the CO 2 when the main plant is shut down.
  • package refrigeration system means a small single stage refrigeration device about the size of a domestic freezer.
  • the pressure control during shutdown may also be achieved by installing an additional vessel that permits all of the CO 2 in the circuit to be stored as vapor at pressures below the safe working pressure of the system. These vessels are usually referred to as a “fade out” vessel.
  • the second refrigeration circuit 18 comprises a second liquid refrigerant.
  • the second refrigerant is fed from a low-pressure vessel 11 , to the cascade heat exchanger 5 , where it evaporates, cooling and condensing the CO 2 .
  • the liquid second refrigerant can be pumped or fed by natural circulation to the cascade heat exchanger 5 .
  • the feed rate of the liquid second refrigerant will at least equal the evaporation rate, but could be higher to ensure wetting of the second refrigerant side of the heat exchanger 5 .
  • the compressed second refrigerant is cooled and condensed in the second condenser 13 .
  • the second condenser is cooled by air, water, or other suitable cooling medium.
  • the rejected heat may be recovered and used for other purposes to improve overall system efficiency.
  • the condensed second refrigerant may then be stored in a high-pressure vessel 14 , until it is needed in the cascade heat exchanger 5 .
  • the condensed second refrigerant may be stored in the low-pressure vessel 11 .
  • a control valve is needed after the condenser 13 to maintain pressure in the second condenser 13 .
  • This control valve has a function similar to the function of control valve 19 .
  • liquid second refrigerant goes to the low pressure vessel 11 through a control valve 20 where pressure is decreased to that of the low-pressure vessel 11 , with a portion of the second refrigerant evaporating to cool the liquid.
  • the resulting liquid/vapor mixture flows to the low-pressure vessel 11 , where the liquid and vapor components are separated.
  • the vapor goes to the second refrigerant compressor 12 and is combined with the vapor from the second evaporator 5 . This, completes the closed circulation of the second refrigerant.
  • the liquid second refrigerant may first go through a control valve 20 to an economizer vessel or heat exchanger 15 , operating at a pressure intermediate between that of the high-pressure vessel 14 and the low-pressure vessel 11 . At this intermediate pressure, some of the liquid evaporates, cooling the remainder of the liquid. The vapor is then separated from the liquid and goes to the “economizer port” on the compressor 12 .
  • the low-pressure vessel 11 may also be connected to evaporators 16 to provide cooling at temperatures higher than the operating conditions of the CO 2 circuit.
  • the method of liquid and vapor circulation is the same as for the CO 2 evaporators 3 .
  • the second refrigerant is ammonia. It may, however, be any available refrigerant that can operate at pressures that are compatible with the saturated condensing temperature of the condenser 13 .
  • An example of another suitable refrigerant is HFC-134A.
  • the second refrigerant circuit is constructed using all standard available refrigeration components. Suitable components may be obtained from Mycom Chemical Process Corp.; York International Corporation of York, Pa.; and Grasso Inc. of Evansville, Ind., for example. High-pressure heat exchangers are well known in the petrochemical industry. Such high-pressure heat exchangers may be adapted to include circuitry for evaporating and condensing refrigerants.
  • the refrigeration system according to the invention may be used in any freezer or cooler.
  • the refrigeration system has been found to be particularly suitable for use in food freezers due to its safety, efficiency, and environmentally friendly operation.
  • A. Plate freezers wherein the product to be frozen is placed between plates and held at low temperatures until they are frozen.
  • the product is usually packed in boxes that are loaded and discharged by an automatic loading and discharging system.
  • the heat transfer is by direct contact between the plates and the boxed product.
  • the plates are the first evaporation circuit.
  • the cooling results from CO 2 evaporating inside the plates.
  • a preferred evaporation pressure is about 122 psig corresponding to a saturation temperature of ⁇ 43° F. ( ⁇ 42° C.).
  • the cooling apparatus is contained inside an insulated enclosure.
  • This conveyor can be a spiral or straight belt, for example.
  • the product is cooled by re-circulated air that is cooled by a fin-coil air cooler by evaporating CO 2 in a first refrigeration circuit.
  • the fin-coil air coolers are cooled by CO 2 evaporating inside the coils.
  • the evaporation pressure is about 122 psig corresponding to a saturation temperature of ⁇ 43° F. ( ⁇ 42° C.).
  • C. Scraped surface coolers wherein a liquid or paste product is cooled as it is pumped through a cylindrical barrel. Inside the barrel is a rotating scraper that agitates the product and removes frozen product from the barrel walls. The barrel is cooled by CO 2 evaporating inside the surrounding jacket. CO 2 circulation is achieved by a natural thermosyphon effect or by being pumped. A preferred evaporation pressure is about 158 psig corresponding to a saturation temperature of 30° F. ( ⁇ 34° C.). Product temperature may be controlled by varying the CO 2 pressure in the barrel.
  • a second aspect, this invention provides a method of refrigeration.
  • the method of refrigeration comprises:
  • circulating the first refrigerant in the first refrigeration circuit and evaporating the first refrigerant at a pressure greater than about 120 psig provide a first refrigerant vapor and to cool a medium, compressing the first refrigerant vapor to provide a compressed first refrigerant vapor, and condensing the compressed first refrigerant vapor to provide a first refrigerant liquid;
  • the method of the invention uses the refrigeration system of the invention and the preferred operation conditions mentioned in relation thereto.
US09/796,639 2000-03-17 2001-03-02 Refrigeration system Abandoned US20010023594A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP00105695A EP1134514A1 (de) 2000-03-17 2000-03-17 Kühlsystem
EPEP00105695.1 2000-03-17

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