EP1134514A1 - Système frigorifique - Google Patents

Système frigorifique Download PDF

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Publication number
EP1134514A1
EP1134514A1 EP00105695A EP00105695A EP1134514A1 EP 1134514 A1 EP1134514 A1 EP 1134514A1 EP 00105695 A EP00105695 A EP 00105695A EP 00105695 A EP00105695 A EP 00105695A EP 1134514 A1 EP1134514 A1 EP 1134514A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
refrigeration
liquid
evaporator
refrigeration system
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP00105695A
Other languages
German (de)
English (en)
Inventor
Richard-Charles Ives
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Societe des Produits Nestle SA
Nestle SA
Original Assignee
Societe des Produits Nestle SA
Nestle SA
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 Societe des Produits Nestle SA, Nestle SA filed Critical Societe des Produits Nestle SA
Priority to EP00105695A priority Critical patent/EP1134514A1/fr
Priority to US09/796,639 priority patent/US20010023594A1/en
Priority to JP2001075123A priority patent/JP2001304704A/ja
Publication of EP1134514A1 publication Critical patent/EP1134514A1/fr
Withdrawn legal-status Critical Current

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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
    • 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

  • This 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 according to the invention provides an energy efficient refrigeration.
  • the refrigeration system is particular suitable for an application in the food industry.
  • the invention also relates to a method of refrigeration.
  • Refrigeration industry is faced with a number of issues that is making it more difficult to use conventional refrigerants and system designs.
  • CFC's Chloro-Fluoro-Carbons
  • Other refrigerants such as Hydro-Chloro-Fluoro- Carbons (e.g. HCFC-22) will soon also be phased out for the same reason.
  • the use of the new replacement refrigerants Hydro-Flouro-Carbons(HFC's) may be restricted due to their high global warming potentials.
  • concerns about global warming are expected to raise an increasing pressure toward more energy efficient operations.
  • US patent No. 5,042,262 described a Food Freezer, which used CO 2 as a low temperature refrigerant, being cooled in cascade by another evaporating refrigerant operating at higher temperatures.
  • US patent No. 5,042,262 recommended pressures in the CO 2 evaporator to between 60.4 psig and 120 psig. It also recommended a pressure in the whole CO 2 system to 325 psig.
  • the invention provides a refrigeration system.
  • the refrigeration system comprises:
  • the refrigeration system according to the invention allows the required operation conditions of the system to be set so that it matches the needs of the user, particularly the evaporating pressure of the first refrigerant, which determines the corresponding saturated evaporating temperature. Due to the refrigeration systems ability to work at high operation pressures, it is possible to select a pressure in the evaporators that corresponds to a saturation temperature in the range from -44°F to -10°F.
  • the resulting system is significantly safer than ammonia systems due to replacing ammonia in the manufacturing areas with CO 2 , which is significantly less toxic.
  • the refrigeration system has shown to be competitive in capital cost and energy efficiency.
  • this invention provides a method of refrigeration.
  • the method of refrigeration comprises
  • the operation pressure throughout the first refrigeration circuit is between 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 through out in the first refrigeration circuit is in the range from 120 psig to about 580 psig. Operating the system in indicated ranges improves the energy efficiency of the cascade system, by allowing the evaporators to operate at a pressure that most suits the needs of the medium being cooled and to optimise the heat transfer conditions between the first and second refrigerants.
  • the first compressor 4 advantageously has an operation pressures above 325 psig. at the discharge of the compressor 4, preferably from 325 psig to about 580 psig, more preferably from 350 psig to about 425 psig.
  • the operation pressure throughout the second refrigeration circuit is below 350 psig. so that standard refrigeration components can be used.
  • the higher operating pressure of the CO 2 circuit allows selection of the optimum conditions for heat exchange between the CO 2 and the second refrigerant in the cascade heat exchanger, improving system efficiency.
  • the first evaporator is operating at pressures from 120 psig to about 580 psig, more preferably from 120 psig to about 180 psig, most preferably from about 122 to about 160 psig.
  • the first refrigeration circuit comprises means for cooling the first refrigerant liquid subsequent to its condensing in the first condenser.
  • the means for cooling the first refrigerant may comprise an Economiser vessel connected to the first compressor allowing vapour resulting from the cooling to be forwarded to the compressor.
  • a heat exchanger may be used for cooling the first refrigerant liquid.
  • the refrigeration systems efficiency is improved by cooling the liquid CO 2 by evaporation in the economiser vessel or in the heat exchanger prior to going to the low pressure part of the CO 2 system, with the resulting vapour going to the economiser port on the CO 2 compressor. It has been found that it is particular advantageous to apply these measures to the first refrigeration to make it more energy efficient.
  • 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 in the first condenser.
  • this temperature difference should be as low as 5 °F (2°C).
  • Figure 1 shows a refrigeration system having a first refrigeration circuit 17 and a second refrigeration circuit 18 arranged in cascade.
  • the first refrigerant is according to the invention CO 2 .
  • Liquid CO 2 is by means of a pump 2 from a low-pressure CO 2 vessel 1 sent 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 in the CO 2 side of each evaporator.
  • the liquid supply could be achieved without a pump, using natural circulation.
  • the evaporators 3 may be of any conventional type, but designed for working pressures, corresponding to the needs of the medium being cooled e.g. plate evaporators, fin-coil units, scraped surface evaporators, tubular coolers
  • the mixture of CO 2 liquid and vapour returns to the Low-pressure CO 2 vessel 1, where they are separated.
  • the liquid is then available to be sent back to the evaporators.
  • the CO 2 vapour goes to a CO 2 compressor 4, where it is compressed to a pressure preferably exceeding 325 psig, but less than the CO 2 critical point (1056 psig).
  • This compressor 4 may advantageously be fitted with an "economiser port” to take additional vapour from a CO 2 economiser vessel 7 to improve system efficiency.
  • the compressors 4 may be any type suitable for the required duty.
  • the preferred compressor type would be an oil injected screw compressor with gravity and coalescing oil separator. Suitable compressors may be obtained from Mycom, Sabroe or Kobelco. If needed tertiary oil separation may be provided using activated carbon or similar.
  • An example of a compressor type, which may be suitable for the present application, is a natural gas compressor. Adaptation of the natural gas compressor may be needed e.g. adaptation of sealing materials, oil separation, oil injection points, removing explosion proofing.
  • 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 to permit the use of standard commercial refrigeration components in the second refrigerant circuit.
  • a plate type heat exchanger is preferred to minimise the temperature difference between the condensing CO 2 and the evaporating second refrigerant - improving system efficiency.
  • 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 CO 2 Economiser 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 similar function to 19.
  • 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/vapour mixture flows to the low-pressure vessel 1, where the liquid and vapour components are separated.
  • the vapour goes to the CO 2 compressor 4 with the vapour from the evaporator 3. This completes the closed circulation of the CO 2 .
  • the liquid may first go through a control valve 19 to a CO 2 economiser vessel or heat exchanger 7, operating at a pressure 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 vapour is separated from the liquid and goes to the "economiser port" on the compressor 4.
  • the high-pressure CO 2 vessel 6 and CO 2 economiser vessel 7 may also have connected additional evaporators 9 and 8 respectively to provide cooling at operating temperatures higher than the main evaporators 3.
  • Method of liquid and vapour circulation is the same as for 3.
  • the vessels, evaporators and heat exchangers may be fitted with safety relief valves and/or other pressure activated devices to release vapour from the CO 2 circuit, reducing the pressure.
  • any or each vessel, evaporator and 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.
  • 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 stored as vapour at pressures below the safe working pressure of the system usually referred to as a "fade out" vessel.
  • the single stage CO 2 compressor 4 may be replaced by 2 or more compressors operating in series, with the vapour being cooled and desuperheated between them (i.e. multi-stage operation with intercooler).
  • the advantage of this is to improve the system efficiency.
  • 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 feed could be pumped or by natural circulation. Feed rate 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 mixture of second refrigerant liquid and vapour returns to the low-pressure vessel 11, where they are separated.
  • the liquid is then available to be sent back to the cascade heat exchanger 5.
  • the separated second refrigerant vapour goes to the compressor 12, where it is compressed to an appropriate pressure that permits condensing in the condenser 13.
  • This compressor may also be fitted with an "economiser port” to take additional vapour from an economiser vessel 15 to improve system efficiency. There may be multiple compressors operating in parallel if necessary.
  • the compressed second refrigerant is cooled and condensed in the second condenser 13, which 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 stored in a high-pressure vessel 14, until it is needed in the cascade heat exchanger 5.
  • storage could be 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 similar function to 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/vapour mixture flows to the low-pressure vessel 11, where the liquid and vapour components are separated.
  • the vapour goes to the second refrigerant compressor 12 with the vapour from the second evaporator 5. This, completes the closed circulation of the second refrigerant.
  • the liquid may first go through a control valve 20 to an economiser vessel or heat exchanger 15, operating at a pressure 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 vapour is separated from the liquid and goes to the "economiser port" on the compressor 12.
  • the low-pressure vessel 11 may also have connected evaporators 16 to provide cooling at temperatures higher than the operating conditions of the CO 2 circuit.
  • Method of liquid and vapour circulation is the same as for the CO 2 evaporators 3.
  • the preferred second refrigerant is Ammonia. However, it may be any available refrigerant that can operate at acceptable pressures coinciding with the design saturated condensing temperature of the condenser 13. Examples of other suitable refrigerants are HFC-134A.
  • the preferred construction method of the second refrigerant circuit is using all standard available refrigeration components. Suitable components may e.g. be obtained from Mycom, York, and GEA/Grasso. High-pressure heat exchangers are e.g. known from the petrochemical industry. Such high-pressure heat exchangers may be adapted to include circuiting to handle evaporating and condensing refrigerants etc.
  • the single stage compressor 12 may be replaced by 2 or more compressors operating in series, with the vapour being cooled and desuperheated between them (i.e. multi-stage operation with intercooler).
  • the advantage of this is that system efficiency is improved.
  • the refrigeration system according to the invention may be applied in any freezers or coolers.
  • the refrigeration system has been found to be particular suitable for an application in food freezers due to its safety, efficiency and environment friendly operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP00105695A 2000-03-17 2000-03-17 Système frigorifique Withdrawn EP1134514A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP00105695A EP1134514A1 (fr) 2000-03-17 2000-03-17 Système frigorifique
US09/796,639 US20010023594A1 (en) 2000-03-17 2001-03-02 Refrigeration system
JP2001075123A JP2001304704A (ja) 2000-03-17 2001-03-16 冷却システム

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00105695A EP1134514A1 (fr) 2000-03-17 2000-03-17 Système frigorifique

Publications (1)

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EP1134514A1 true EP1134514A1 (fr) 2001-09-19

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Country Status (3)

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US (1) US20010023594A1 (fr)
EP (1) EP1134514A1 (fr)
JP (1) JP2001304704A (fr)

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WO2004042291A2 (fr) * 2002-10-30 2004-05-21 Delaware Capital Formation, Inc. Systeme de refrigeration
US6915652B2 (en) 2001-08-22 2005-07-12 Delaware Capital Formation, Inc. Service case
WO2008112569A2 (fr) * 2007-03-09 2008-09-18 Johnson Controls Technology Company Système de réfrigération
WO2009063055A1 (fr) * 2007-11-15 2009-05-22 Shell Internationale Research Maatschappij B.V. Procédé et appareil permettant de refroidir un flux de traitement
DE10138255B4 (de) * 2001-08-03 2012-06-06 Gea Grasso Gmbh Anordnung für Kaskadenkälteanlage
EP2552182A1 (fr) * 2011-07-29 2013-01-30 ABB Research Ltd. Thermosiphon à double boucle pour refroidir des composants électriques et électroniques
US8544283B2 (en) 2011-06-13 2013-10-01 Fred Lingelbach Condenser evaporator system (CES) for decentralized condenser refrigeration system
US8631666B2 (en) 2008-08-07 2014-01-21 Hill Phoenix, Inc. Modular CO2 refrigeration system
EP2261570A3 (fr) * 2009-05-27 2014-03-19 Sanyo Electric Co., Ltd. Appareil de réfrigération
EP2330368A3 (fr) * 2009-11-20 2015-04-22 LG ELectronics INC. Appareil de refroidissement/chauffage de type pompe à chaleur
DE102005016180B4 (de) * 2005-04-08 2015-08-20 Gea Grasso Gmbh Verfahren und Vorrichtung an einer Kälteanlage mit mehreren Schraubenverdichtern
EP2924372A4 (fr) * 2012-11-20 2016-09-28 Mitsubishi Electric Corp Dispositif de réfrigération
US9513033B2 (en) 2011-06-13 2016-12-06 Aresco Technologies, Llc Refrigeration system and methods for refrigeration
CN106247656A (zh) * 2016-08-24 2016-12-21 中南焦作氨阀股份有限公司 一种复叠制冷系统
CN106288475A (zh) * 2016-08-24 2017-01-04 中南焦作氨阀股份有限公司 一种复叠制冷系统
US9541311B2 (en) 2010-11-17 2017-01-10 Hill Phoenix, Inc. Cascade refrigeration system with modular ammonia chiller units
CN106322806A (zh) * 2016-08-24 2017-01-11 中南焦作氨阀股份有限公司 一种复叠制冷系统
US9657977B2 (en) 2010-11-17 2017-05-23 Hill Phoenix, Inc. Cascade refrigeration system with modular ammonia chiller units
US9664424B2 (en) 2010-11-17 2017-05-30 Hill Phoenix, Inc. Cascade refrigeration system with modular ammonia chiller units
GB2559658A (en) * 2016-12-08 2018-08-15 G A H Refrigeration Ltd Multi-function heat exchanger and temperature control system

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DE10203772A1 (de) * 2002-01-30 2004-04-15 Robert Bosch Gmbh Klimaanlage mit Heizfunktion und Verfahren zum Betrieb einer Klimaanlage mit Heizfunktion
US6796139B2 (en) 2003-02-27 2004-09-28 Layne Christensen Company Method and apparatus for artificial ground freezing
US6877342B2 (en) * 2003-07-03 2005-04-12 Cohand Technology Co., Ltd. Controlled method for the energy-saving and energy-releasing refrigerating air conditioner
KR100639104B1 (ko) 2003-08-01 2006-10-27 오원길 케스케이드 열교환기를 갖는 이원냉동사이클을 이용한냉난방 및 급탕용 히트펌프시스템
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WO2009048463A1 (fr) * 2007-10-10 2009-04-16 Carrier Corporation Système de réfrigération multi-étagé à différents types de compresseurs de type différent
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SG184789A1 (en) 2010-04-29 2012-11-29 Carrier Corp Refrigerant vapor compression system with intercooler
KR101190492B1 (ko) 2010-05-20 2012-10-12 엘지전자 주식회사 히트펌프 연동 급탕장치
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JP5557830B2 (ja) * 2011-12-22 2014-07-23 八洋エンジニアリング株式会社 冷凍装置並びにその運転方法
CA2771113A1 (fr) * 2012-03-08 2012-05-22 Serge Dube Systeme de refrigeration au co2 pour surfaces de sport sur glace
US10288325B2 (en) * 2013-03-14 2019-05-14 Rolls-Royce Corporation Trans-critical vapor cycle system with improved heat rejection
CA2815783C (fr) 2013-04-05 2014-11-18 Marc-Andre Lesmerises Systeme de refroidissement au co2 et procede de fonctionnement de celui-ci
US9874382B2 (en) 2014-07-10 2018-01-23 Heatcraft Refrigeration Products Llc Refrigeration system with full oil recovery
CN104729135A (zh) * 2015-04-13 2015-06-24 福建雪人股份有限公司 一种co2/nh3复叠式制冷系统
US11656005B2 (en) 2015-04-29 2023-05-23 Gestion Marc-André Lesmerises Inc. CO2 cooling system and method for operating same
GB2543086B (en) * 2015-10-08 2018-05-02 Isentra Ltd Water-cooled carbon dioxide refrigeration system
US10543737B2 (en) 2015-12-28 2020-01-28 Thermo King Corporation Cascade heat transfer system
CN106091459A (zh) * 2016-06-06 2016-11-09 济南欧菲特制冷设备有限公司 一种一体式载冷系统机组
EP3737894B1 (fr) 2018-01-11 2023-04-05 Vilter Manufacturing LLC Système de réfrigération d'échangeur de chaleur à double cascade et procédé de fonctionnement associé
US11378318B2 (en) * 2018-03-06 2022-07-05 Vilter Manufacturing Llc Cascade system for use in economizer compressor and related methods
US11371756B2 (en) * 2020-02-27 2022-06-28 Heatcraft Refrigeration Products Llc Cooling system with oil return to accumulator
US11384969B2 (en) * 2020-02-27 2022-07-12 Heatcraft Refrigeration Products Llc Cooling system with oil return to oil reservoir
CN111912130A (zh) * 2020-06-17 2020-11-10 西安交通大学 一种基于co2复叠制冷两次节流制备固-气流态干冰的系统

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DE29906359U1 (de) * 1999-04-09 1999-08-05 Fuhrmann & Schreiner Gmbh Anlage zur Erzeugung von Kälte auf einem hohen und einem niedrigen Temperaturniveau

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