EP0641978B1 - Verfahren und Vorrichtung zur Kühlung - Google Patents

Verfahren und Vorrichtung zur Kühlung Download PDF

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Publication number
EP0641978B1
EP0641978B1 EP94306390A EP94306390A EP0641978B1 EP 0641978 B1 EP0641978 B1 EP 0641978B1 EP 94306390 A EP94306390 A EP 94306390A EP 94306390 A EP94306390 A EP 94306390A EP 0641978 B1 EP0641978 B1 EP 0641978B1
Authority
EP
European Patent Office
Prior art keywords
cooling mode
refrigerant
thermal storage
storage means
vapour compression
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.)
Expired - Lifetime
Application number
EP94306390A
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English (en)
French (fr)
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EP0641978A1 (de
Inventor
Stephen Forbes Pearson
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.)
Star Refrigeration Ltd
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Star Refrigeration Ltd
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Publication date
Application filed by Star Refrigeration Ltd filed Critical Star Refrigeration Ltd
Publication of EP0641978A1 publication Critical patent/EP0641978A1/de
Application granted granted Critical
Publication of EP0641978B1 publication Critical patent/EP0641978B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube

Definitions

  • This invention relates to a refrigeration apparatus and refrigeration method, and in particular to refrigeration apparatus capable of operating in either a vapour compression mode or a natural cooling mode.
  • GB-B-2 233 080 describes a refrigeration apparatus which may be operated in a mechanical mode, or alternatively in a thermosyphon mode.
  • the apparatus operates in a conventional manner utilising a vapour compression cycle, with refrigerant vapour being compressed before being passed through a heat exchanger (condenser) where sensible heat is rejected to the atmosphere from the compressed refrigerant, then passing the resulting condensate through a restriction, typically an expansion valve, and finally passing the expanded and cooled refrigerant to a heat exchanger (evaporator) to absorb heat from a fluid to be chilled.
  • a heat exchanger typically an expansion valve
  • the refrigerant path may be reconfigured to bypass the compressor and the expansion valve such that the only cooling effect experienced by the refrigerant is the natural cooling obtained when the refrigerant is passed through the condenser, the evaporator being located below the condenser such that the refrigerant may circulate without the mechanical assistance normally provided by the compressor.
  • operation in the thermosyphon mode is more economical than the mechanical or vapour compression mode.
  • thermosyphon operation In a typical refrigerating unit incorporating this feature, several refrigerating systems are arranged so that the fluid to be chilled is passed through the evaporators in series. A number of the systems may cool the fluid by vapour compression operation while other systems operating with warmer inlet fluid may contribute a share of the required cooling by thermosyphon operation.
  • such units are expensive and involve high capital costs and in practice are restricted to very large units where stand-by equipment is specified. It has not yet been possible to use an individual two-mode system, as when the system changes from vapour compression refrigeration to thermosyphon refrigeration there is a period of delay while the heat rejection equipment, previously in contact with the compressed (and thus heated) refrigerant, cools to a temperature below that of the fluid being chilled.
  • US-A-5 211 029 discloses air-conditioning apparatus which includes a conventional condensing unit including a compressor and condenser, and a negative energy storage system including an insulated tank for containing negative heat energy storage material and through which refrigerant may be circulated. Both the condensing unit and the negative energy storage system may be connected to an evaporating unit to provide cooling to an associated air-conditioned space.
  • the apparatus does not provide an air-conditioning effect, refrigerant cooled by the action of the condensing unit and an expansion device being passed through the negative energy storage system to cool the material therein.
  • an air-conditioning effect is provided by circulating refrigerant through the evaporating unit and the negative energy storage system.
  • an air-conditioning effect is provided by circulating refrigerant through the evaporating unit and the condensing unit.
  • the negative energy storage system and the condensing unit combine to provide cooling of the refrigerant from the evaporating unit.
  • refrigeration apparatus capable of operating in i) vapour compression cooling mode or ii) natural cooling mode, the apparatus defining a refrigerant path comprising:
  • a refrigeration method including i) a vapour compression cooling mode or ii) a natural cooling mode, the method including the steps of:
  • the chilled fluid may be the fluid contained within a space to be cooled, for example a refrigerated compartment, but will usually be a liquid, such as water, to be utilised as a cooling medium for a region to be cooled, such as an air conditioned space, which may be remote from the refrigeration apparatus.
  • the thermal storage means i) is cooled by the chilled fluid while the apparatus operates in the vapour compression cooling mode and ii) chills the fluid on changeover to natural cooling mode.
  • operation in natural cooling mode is achieved without any mechanical circulation of the refrigerant, which, in the vapour compression cooling mode, is typically provided by the compression means.
  • the chilling means will be positioned below the heat rejection means.
  • refrigerant circulation means may be provided for use in the natural cooling mode.
  • the present invention allows changeover from compression mode to natural cooling mode without the period of delay that occurs in conventional two-mode systems as the heat rejection means cools to a temperature below that of the fluid being chilled; during this changeover period the present invention provides for chilling of the fluid by the thermal storage means.
  • the invention may operate at full capacity in the vapour compression cooling mode irrespective of cooling load, any excess capacity being utilised to cool the thermal storage means.
  • the thermal storage means On the thermal storage means reaching a condition where it cannot be cooled further, the fluid temperature will drop sharply, allowing a thermostatic switch to reconfigure the valve means to provide the natural cooling mode. The thermal storage means then begins to chill the fluid, preventing an immediate rise in temperature of the fluid and allowing time for the apparatus to adjust to natural cooling mode.
  • the thermal storage means contains a phase change material which will absorb or reject heat at a substantially constant temperature.
  • a phase change material which will absorb or reject heat at a substantially constant temperature.
  • Substances suitable for use in such means include acetic acid and lactic acid.
  • the apparatus includes ducting 10 which partially defines a refrigerant path around which refrigerant is cycled in either i) a mechanical or vapour compression cooling mode or ii) a thermosyphon or natural cooling mode.
  • vapour compression mode the refrigerant is first subject to compression by a positive displacement compressor 12, from which the high pressure refrigerant passes to heat rejection means in the form of a condenser 14, which is exposed to ambient air.
  • the refrigerant passes to restriction means in the form of an expansion valve 16, which causes a sufficient portion of the refrigerant to vaporise to reduce the temperature of the remaining liquid to that consistent with the lower pressure.
  • the expanded and cooled refrigerant is then passed to a heat exchanger in the form of a chiller 18 where the refrigerant absorbs heat from fluid to be cooled.
  • the refrigerant now in the form of low pressure vapour, returns to the compressor 12.
  • the chiller 18 forms part of a secondary cooling circuit around which a fluid, such as water, is circulated. Following chilling, the water passes through a thermal store 20 which contains a phase change material. The water then passes through a region to be cooled 22, before returning to the chiller 18, circulation of the fluid around the cooling circuit being achieved by means of a fluid pump 24.
  • a fluid such as water
  • the refrigeration circuit includes a three-way valve 26 and a two-way ball valve 28, and for operation in the vapour compression mode the valves 26, 28 are configured such that refrigerant is passed through the compressor 12 and the expansion valve 16.
  • the valves 26, 28 may be configured to bypass the compressor 12 and valve 16, such that the refrigerant is cooled solely by ambient air as it passes through the condenser 14.
  • the chiller 18 is positioned below the condenser 14 and the ducting 10 is arranged such that the refrigerant will circulate in this thermosyphon mode without mechanical assistance, thus minimising the energy consumption of the apparatus.
  • the compressor 12 While operating in vapour compression mode, the compressor 12 may operate at full capacity, irrespective of the cooling load, any excess cooling of the water being absorbed by the thermal store 20, in which the excess cooling capacity is utilised to solidify a liquid, at constant temperature.
  • the phase change material When the phase change material has completely solidified there will be a sharp decrease in the temperature of the water, which may be detected by a thermostat 30 which operates to switch the apparatus from vapour compression mode to thermosyphon mode, that is by shutting down the compressor 12 and reconfiguring the valves 26, 28 to bypass the compressor 12 and the expansion valve 16.
  • the refrigerant in the ducting 10 downstream of the compressor 12 and upstream of the expansion valve 16 will be at a higher temperature than the water and it takes some time for the refrigerant and the condenser hardware and ducting to be cooled to a level where its temperature is lower than that of the water. Also, in order for circulation of refrigerant to take place without mechanical assistance, the temperature of the refrigerant in the condenser 14 must fall below the temperature at the outlet from the chiller 18, the reverse of the situation in the vapour compression mode. During this transition period the water is chilled by the thermal store 20, as the phase change material in the store is melted by the circulating water.
  • this embodiment of the invention provides an arrangement in which refrigeration apparatus capable of operating in a thermosyphon mode may be utilised on an individual basis, and not necessarily as part of a larger system. Further, the provision of the thermal store 20 allows the system to be operated at full capacity in vapour compression mode, which is of course more efficient than operating at part capacity.
  • the present invention may be utilised in a wide variety of applications, but is particularly useful where the cooling load is to be maintained at a relatively high temperature, such as in air conditioning systems for building which chill the ceilings of rooms and corridors.
  • air conditioning is particularly suitable for thermosyphon cooling techniques as the chilled ceilings must be kept at a temperature higher than the dew point of the room air.

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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)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Other Air-Conditioning Systems (AREA)

Claims (16)

  1. Kühlvorrichtung, die in der Lage ist, i) im Kühlmodus mit Dampfkompression oder ii) im Modus mit natürlicher Kühlung zu arbeiten, wobei die Vorrichtung eine Kältemittelbahn bildet, die folgende Komponenten umfaßt:
    Kompressionsmittel (12) zum Verdichten eines Kältemittels;
    Wärmeabfuhrmittel (14) zum Kühlen des verdichteten Kältemittels;
    Restriktionsmittel (16) zum Ausdehnen des Kältemittels;
    Abkühlmittel (18), um die Absorption von Wärme aus einem abzukühlenden Fluid durch das Kältemittel zu ermöglichen;
    Ventilmittel (26, 28), die konfiguriert werden können, um das Kältemittel selektiv so zu leiten, daß es i) durch das Kompressionsmittel (12) und das Restriktionsmittel (16) strömt oder ii) daß es das Kompressionsmittel (12) und das Restriktionsmittel (16) umgeht; und
    Wärmespeichermittel (20), um i) gekühlt zu werden, während die Vorrichtung im Kühlmodus mit Dampfkompression arbeitet, und ii) bei der Umschaltung auf den Modus mit natürlicher Kühlung eine abkühlende Wirkung auf das Fluid auszuüben.
  2. Vorrichtung nach Anspruch 1, bei der das abgekühlte Fluid ein Kühlmittel für einen zu kühlenden Bereich (22) ist.
  3. Vorrichtung nach Anspruch 1 oder Anspruch 2, bei der das Wärmespeichermittel (20) i) so angeordnet ist, daß es durch das abgekühlte Fluid gekühlt wird, während die Vorrichtung im Kühlmodus mit Dampfkompression arbeitet, und ii) so angeordnet ist, daß es das Fluid bei der Umschaltung auf den Modus mit natürlicher Kühlung abkühlt.
  4. Vorrichtung nach Anspruch 1, 2 oder 3, bei der das Abkühlmittel (18) unter dem Wärmeabfuhrmittel (14) angeordnet ist, um ohne jede mechanische Umwälzung den Betrieb im Modus mit natürlicher Kühlung zu ermöglichen.
  5. Vorrichtung nach Anspruch 1, 2 oder 3, bei der für die Nutzung im Modus mit natürlicher Kühlung ein Kältemittel-Umwälzmittel vorgesehen ist.
  6. Vorrichtung nach einem der vorhergehenden Ansprüche, bei der das Wärmespeichermittel (20) so angeordnet ist, daß die Vorrichtung im Kühlmodus mit Dampfkompression ungeachtet der Kühllast bei voller Kapazität betrieben werden kann, wobei jedwede überschüssige Kapazität dazu genutzt wird, das Wärmespeichermittel (20) zu kühlen.
  7. Vorrichtung nach Anspruch 6, die außerdem einen Wärmeschalter (30) umfaßt, um das Ventilmittel (26, 28) vom Modus mit Dampfkompression auf den Modus mit natürlicher Kühlung umstellen zu können, wenn das Wärmespeichermittel (20) einen Zustand erreicht, in dem es nicht weiter gekühlt werden kann.
  8. Vorrichtung nach einem der vorhergehenden Ansprüche, bei der das Wärmespeichermittel (20) ein Material für Phasenumwandlung enthält, das bei einer im wesentlichen konstanten Temperatur Wärme absorbiert oder abführt.
  9. Vorrichtung nach Anspruch 8, bei der das Material für Phasenumwandlung entweder Essigsäure oder Milchsäure ist.
  10. Kühlverfahren, das i) einen Kühlmodus mit Dampfkompression oder ii) einen Modus mit natürlicher Kühlung einschließt, wobei das Verfahren die folgenden Schritte einschließt:
    Bereitstellen eines Wärmeabfuhrmittels und Nutzen des Mittels, um Wärme von einem Kältemittel abzuführen;
    Abkühlen eines Fluids mit dem Kältemittel; und
    i) bei der Arbeit im Kühlmodus mit Dampfkompression schließt das Verfahren außerdem die folgenden Schritte ein:
    a) Verdichten des Kältemittels;
    b) Ausdehnen des Kältemittels; und
    c) Kühlen eines Wärmespeichermittels; und
    ii) bei der Arbeit im Modus mit natürlicher Kühlung schließt das Verfahren außerdem den folgenden Schritt ein:
    a) Ausüben einer abkühlenden Wirkung auf das Fluid unter Nutzung des Wärmespeichermittels, zumindest während der anfänglichen Umschaltung vom Kühl modus mit Dampfkompression auf den Modus mit natürlicher Kühlung.
  11. Verfahren nach Anspruch 10, bei dem das abgekühlte Fluid ein Kühlmittel für einen zu kühlenden Bereich darstellt.
  12. Verfahren nach Anspruch 10 oder Anspruch 11, bei dem das Wärmespeichermittel i) im Kühlmodus mit Dampfkompression durch das abgekühlte Fluid gekühlt wird und ii) das Fluid während der Umschaltung auf den Modus mit natürlicher Kühlung abkühlt.
  13. Verfahren nach Anspruch 10, 11 oder 12, bei dem das Kältemittel im Modus mit natürlicher Kühlung ohne jede mechanische Umwälzung zirkuliert.
  14. Verfahren nach einem der Ansprüche 10 bis 13, bei dem der Betrieb im Kühlmodus mit Dampfkompression ungeachtet der Kühllast bei voller Kapazität erfolgt, wobei jedwede überschüssige Kapazität dazu genutzt wird, das Wärmespeichermittel zu kühlen.
  15. Verfahren nach Anspruch 14, bei dem der Betriebsmodus vom i) Kühlmodus mit Dampfkompression auf den ii) Modus mit natürlicher Kühlung übergeht, wenn das Wärmespeichermittel einen Zustand erreicht, in dem es nicht weiter gekühlt werden kann.
  16. Verfahren nach einem der Ansprüche 10 bis 15, bei dem das Wärmespeichermittel bei einer im wesentlichen konstanten Temperatur Wärme absorbiert oder abführt.
EP94306390A 1993-09-04 1994-08-31 Verfahren und Vorrichtung zur Kühlung Expired - Lifetime EP0641978B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB939318385A GB9318385D0 (en) 1993-09-04 1993-09-04 Improvements in and relating to refrigeration method and apparatus
GB9318385 1993-09-04

Publications (2)

Publication Number Publication Date
EP0641978A1 EP0641978A1 (de) 1995-03-08
EP0641978B1 true EP0641978B1 (de) 1998-01-07

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EP94306390A Expired - Lifetime EP0641978B1 (de) 1993-09-04 1994-08-31 Verfahren und Vorrichtung zur Kühlung

Country Status (4)

Country Link
EP (1) EP0641978B1 (de)
DE (2) DE69407699T2 (de)
DK (1) DK0641978T3 (de)
GB (1) GB9318385D0 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8181470B2 (en) 2008-02-15 2012-05-22 Ice Energy, Inc. Thermal energy storage and cooling system utilizing multiple refrigerant and cooling loops with a common evaporator coil
US8505313B2 (en) 2004-08-18 2013-08-13 Ice Energy Holdings, Inc. Thermal energy storage and cooling system with secondary refrigerant isolation
US8528345B2 (en) 2003-10-15 2013-09-10 Ice Energy, Inc. Managed virtual power plant utilizing aggregated storage
US9203239B2 (en) 2011-05-26 2015-12-01 Greener-Ice Spv, L.L.C. System and method for improving grid efficiency utilizing statistical distribution control
US9212834B2 (en) 2011-06-17 2015-12-15 Greener-Ice Spv, L.L.C. System and method for liquid-suction heat exchange thermal energy storage

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Publication number Priority date Publication date Assignee Title
GB0314803D0 (en) 2003-06-25 2003-07-30 Star Refrigeration Improved cooling system
US7854129B2 (en) 2003-10-15 2010-12-21 Ice Energy, Inc. Refrigeration apparatus
JP4864876B2 (ja) 2004-04-22 2012-02-01 アイス エナジー インコーポレーテッド 冷媒の圧力および流量を調節するための閉鎖システムならびに冷媒の圧力および流量を制御する方法
KR101236121B1 (ko) 2004-05-25 2013-02-21 아이스 에너지 홀딩스, 인크. 향상된 열교환 용량을 갖는 냉매계 열에너지 저장 및 냉각시스템
US7421846B2 (en) 2004-08-18 2008-09-09 Ice Energy, Inc. Thermal energy storage and cooling system with gravity fed secondary refrigerant isolation
CN110118493A (zh) 2010-05-27 2019-08-13 江森自控科技公司 用于具有冷却塔的冷却系统的热虹吸冷却器
DE102010025504A1 (de) * 2010-06-29 2011-12-29 Blz Geotechnik Gmbh Verfahren und Anordnung zur Erzeugung von Wärme und Kälte mit einer Kältemaschine
WO2015081997A1 (en) 2013-12-04 2015-06-11 Electrolux Appliances Aktiebolag Refrigeration system

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8528345B2 (en) 2003-10-15 2013-09-10 Ice Energy, Inc. Managed virtual power plant utilizing aggregated storage
US8505313B2 (en) 2004-08-18 2013-08-13 Ice Energy Holdings, Inc. Thermal energy storage and cooling system with secondary refrigerant isolation
US8707723B2 (en) 2004-08-18 2014-04-29 Ice Energy Holdings, Inc. Multiple refrigerant thermal energy storage and cooling system with secondary refrigerant isolation
US8181470B2 (en) 2008-02-15 2012-05-22 Ice Energy, Inc. Thermal energy storage and cooling system utilizing multiple refrigerant and cooling loops with a common evaporator coil
US9203239B2 (en) 2011-05-26 2015-12-01 Greener-Ice Spv, L.L.C. System and method for improving grid efficiency utilizing statistical distribution control
US9212834B2 (en) 2011-06-17 2015-12-15 Greener-Ice Spv, L.L.C. System and method for liquid-suction heat exchange thermal energy storage

Also Published As

Publication number Publication date
EP0641978A1 (de) 1995-03-08
DE641978T1 (de) 1995-10-12
DE69407699D1 (de) 1998-02-12
DK0641978T3 (da) 1998-09-07
GB9318385D0 (en) 1993-10-20
DE69407699T2 (de) 1998-08-27

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