EP0641978A1 - Procédé et appareil de réfrigération - Google Patents

Procédé et appareil de réfrigération Download PDF

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Publication number
EP0641978A1
EP0641978A1 EP94306390A EP94306390A EP0641978A1 EP 0641978 A1 EP0641978 A1 EP 0641978A1 EP 94306390 A EP94306390 A EP 94306390A EP 94306390 A EP94306390 A EP 94306390A EP 0641978 A1 EP0641978 A1 EP 0641978A1
Authority
EP
European Patent Office
Prior art keywords
mode
refrigerant
thermosyphon
thermal storage
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.)
Granted
Application number
EP94306390A
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German (de)
English (en)
Other versions
EP0641978B1 (fr
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/fr
Application granted granted Critical
Publication of EP0641978B1 publication Critical patent/EP0641978B1/fr
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 thermosyphon mode.
  • UK Patent GB 2 233 080 B 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 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.
  • refrigeration apparatus capable of operating in i) vapour compression mode or ii) thermosyphon mode, the apparatus defining a refrigerant path comprising: compression means for compressing a refrigerant; heat rejection means for cooling the compressed refrigerant; restriction means for expanding the refrigerant; chilling means for permitting the absorption of heat by the refrigerant from a fluid to be chilled; valve means configurable for selectively directing refrigerant i) to pass through the compression means and restriction means or ii) to bypass the compression means and restriction means; and thermal storage means for i) being cooled while the apparatus operates in the vapour compression mode and ii) providing a chilling effect during changeover to thermosyphon mode.
  • a refrigeration method including i) a vapour compression mode or ii) a thermosyphon mode, the method including the steps of: rejecting heat from a refrigerant; chilling a fluid with the refrigerant; and
  • 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 mode and ii) chills the fluid on changeover to thermosyphon mode.
  • thermosyphon mode operation in thermosyphon mode is achieved without any mechanical circulation of the refrigerant, which, in the vapour compression 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 thermosyphon mode.
  • the present invention allows changeover from compression mode to thermosyphon 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 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 thermosyphon 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 thermosyphon 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 mode or ii) a thermosyphon 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.
  • 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.

Landscapes

  • 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)
  • Other Air-Conditioning Systems (AREA)
EP94306390A 1993-09-04 1994-08-31 Procédé et appareil de réfrigération Expired - Lifetime EP0641978B1 (fr)

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 true EP0641978A1 (fr) 1995-03-08
EP0641978B1 EP0641978B1 (fr) 1998-01-07

Family

ID=10741530

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94306390A Expired - Lifetime EP0641978B1 (fr) 1993-09-04 1994-08-31 Procédé et appareil de réfrigération

Country Status (4)

Country Link
EP (1) EP0641978B1 (fr)
DE (2) DE641978T1 (fr)
DK (1) DK0641978T3 (fr)
GB (1) GB9318385D0 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005001345A1 (fr) 2003-06-25 2005-01-06 Star Refrigeration Limited Systeme de refroidissement ameliore
WO2007021293A1 (fr) * 2005-08-18 2007-02-22 Ice Energy, Inc. Systeme de stockage d'energie thermique et de refroidissement a isolation secondaire par fluide frigorigene alimente par gravite
US7421846B2 (en) 2004-08-18 2008-09-09 Ice Energy, Inc. Thermal energy storage and cooling system with gravity fed secondary refrigerant isolation
US7503185B2 (en) 2004-05-25 2009-03-17 Ice Energy, Inc. Refrigerant-based thermal energy storage and cooling system with enhanced heat exchange capability
US7690212B2 (en) 2004-04-22 2010-04-06 Ice Energy, Inc. Mixed-phase regulator for managing coolant in a refrigerant based high efficiency energy storage and cooling system
US7854129B2 (en) 2003-10-15 2010-12-21 Ice Energy, Inc. Refrigeration apparatus
DE102010025504A1 (de) * 2010-06-29 2011-12-29 Blz Geotechnik Gmbh Verfahren und Anordnung zur Erzeugung von Wärme und Kälte mit einer Kältemaschine
US8234876B2 (en) 2003-10-15 2012-08-07 Ice Energy, Inc. Utility managed virtual power plant utilizing aggregated thermal energy storage
WO2015081997A1 (fr) 2013-12-04 2015-06-11 Electrolux Appliances Aktiebolag Système de réfrigération
US9939201B2 (en) 2010-05-27 2018-04-10 Johnson Controls Technology Company Thermosyphon coolers for cooling systems with cooling towers

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011512508A (ja) 2008-02-15 2011-04-21 アイス エナジー インコーポレーテッド 共通の蒸発器コイルと伴に複数の冷媒および冷却ループを用いた熱エネルギ蓄積および冷却システム
JP2014535253A (ja) 2011-05-26 2014-12-25 アイス エナジー テクノロジーズ インコーポレーテッド 統計的配電制御を用いたグリッド効率向上のためのシステムおよび装置
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

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB440306A (en) * 1935-04-23 1935-12-24 J & E Hall Ltd Improvements in refrigerating systems for cooling perishable goods in ships' holds
US2244312A (en) * 1938-03-31 1941-06-03 Honeywell Regulator Co Refrigeration system
GB615037A (en) * 1945-01-05 1948-12-31 Georges Jean Henri Trepaud Improvements in and relating to liquid circuit refrigerating plants with cold accumulator reservoir
US2512576A (en) * 1947-10-29 1950-06-20 Mojonnier Bros Co Inc Refrigerating method and apparatus
US3744264A (en) * 1972-03-28 1973-07-10 Trane Co Refrigeration apparatus and method of operating for powered and non-powered cooling modes
US4283925A (en) * 1979-11-15 1981-08-18 Robert Wildfeuer System for cooling
US4295342A (en) * 1977-10-27 1981-10-20 James Parro Heat exchange method using natural flow of heat exchange medium
US4518514A (en) * 1982-04-16 1985-05-21 Hitachi, Ltd. Heat storage material
US4565069A (en) * 1984-11-05 1986-01-21 Maccracken Calvin D Method of cyclic air conditioning with cogeneration of ice
US4720984A (en) * 1986-05-23 1988-01-26 Transphase Systems, Inc. Apparatus for storing cooling capacity
US5211029A (en) * 1991-05-28 1993-05-18 Lennox Industries Inc. Combined multi-modal air conditioning apparatus and negative energy storage system
WO1994002257A2 (fr) * 1992-07-14 1994-02-03 Buckley Theresa M Materiaux de regulation thermique a changement de phase et appareils et procede associes

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB440306A (en) * 1935-04-23 1935-12-24 J & E Hall Ltd Improvements in refrigerating systems for cooling perishable goods in ships' holds
US2244312A (en) * 1938-03-31 1941-06-03 Honeywell Regulator Co Refrigeration system
GB615037A (en) * 1945-01-05 1948-12-31 Georges Jean Henri Trepaud Improvements in and relating to liquid circuit refrigerating plants with cold accumulator reservoir
US2512576A (en) * 1947-10-29 1950-06-20 Mojonnier Bros Co Inc Refrigerating method and apparatus
US3744264A (en) * 1972-03-28 1973-07-10 Trane Co Refrigeration apparatus and method of operating for powered and non-powered cooling modes
US4295342A (en) * 1977-10-27 1981-10-20 James Parro Heat exchange method using natural flow of heat exchange medium
US4283925A (en) * 1979-11-15 1981-08-18 Robert Wildfeuer System for cooling
US4518514A (en) * 1982-04-16 1985-05-21 Hitachi, Ltd. Heat storage material
US4565069A (en) * 1984-11-05 1986-01-21 Maccracken Calvin D Method of cyclic air conditioning with cogeneration of ice
US4720984A (en) * 1986-05-23 1988-01-26 Transphase Systems, Inc. Apparatus for storing cooling capacity
US5211029A (en) * 1991-05-28 1993-05-18 Lennox Industries Inc. Combined multi-modal air conditioning apparatus and negative energy storage system
WO1994002257A2 (fr) * 1992-07-14 1994-02-03 Buckley Theresa M Materiaux de regulation thermique a changement de phase et appareils et procede associes

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005001345A1 (fr) 2003-06-25 2005-01-06 Star Refrigeration Limited Systeme de refroidissement ameliore
US8234876B2 (en) 2003-10-15 2012-08-07 Ice Energy, Inc. Utility managed virtual power plant utilizing aggregated thermal energy storage
US7854129B2 (en) 2003-10-15 2010-12-21 Ice Energy, Inc. Refrigeration apparatus
US7690212B2 (en) 2004-04-22 2010-04-06 Ice Energy, Inc. Mixed-phase regulator for managing coolant in a refrigerant based high efficiency energy storage and cooling system
US8109107B2 (en) 2004-04-22 2012-02-07 Ice Energy, Inc. Mixed-phase regulator
US7503185B2 (en) 2004-05-25 2009-03-17 Ice Energy, Inc. Refrigerant-based thermal energy storage and cooling system with enhanced heat exchange capability
US7827807B2 (en) 2004-05-25 2010-11-09 Ice Energy, Inc. Refrigerant-based thermal energy storage and cooling system with enhanced heat exchange capability
US7793515B2 (en) 2004-08-18 2010-09-14 Ice Energy, Inc. Thermal energy storage and cooling system with isolated primary refrigerant loop
US7421846B2 (en) 2004-08-18 2008-09-09 Ice Energy, Inc. Thermal energy storage and cooling system with gravity fed secondary refrigerant isolation
US7363772B2 (en) 2004-08-18 2008-04-29 Ice Energy, Inc. Thermal energy storage and cooling system with secondary refrigerant isolation
WO2007021293A1 (fr) * 2005-08-18 2007-02-22 Ice Energy, Inc. Systeme de stockage d'energie thermique et de refroidissement a isolation secondaire par fluide frigorigene alimente par gravite
US9939201B2 (en) 2010-05-27 2018-04-10 Johnson Controls Technology Company Thermosyphon coolers for cooling systems with cooling towers
US10295262B2 (en) 2010-05-27 2019-05-21 Johnson Controls Technology Company Thermosyphon coolers for cooling systems with cooling towers
US10302363B2 (en) 2010-05-27 2019-05-28 Johnson Controls Technology Company Thermosyphon coolers for cooling systems with cooling towers
US10451351B2 (en) 2010-05-27 2019-10-22 Johnson Controls Technology Company Thermosyphon coolers for cooling systems with cooling towers
DE102010025504A1 (de) * 2010-06-29 2011-12-29 Blz Geotechnik Gmbh Verfahren und Anordnung zur Erzeugung von Wärme und Kälte mit einer Kältemaschine
WO2015081997A1 (fr) 2013-12-04 2015-06-11 Electrolux Appliances Aktiebolag Système de réfrigération

Also Published As

Publication number Publication date
DK0641978T3 (da) 1998-09-07
EP0641978B1 (fr) 1998-01-07
DE69407699D1 (de) 1998-02-12
DE641978T1 (de) 1995-10-12
GB9318385D0 (en) 1993-10-20
DE69407699T2 (de) 1998-08-27

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