EP2426435A2 - Kühlsystem mit niedrigem Energieverbrauch - Google Patents

Kühlsystem mit niedrigem Energieverbrauch Download PDF

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Publication number
EP2426435A2
EP2426435A2 EP11004604A EP11004604A EP2426435A2 EP 2426435 A2 EP2426435 A2 EP 2426435A2 EP 11004604 A EP11004604 A EP 11004604A EP 11004604 A EP11004604 A EP 11004604A EP 2426435 A2 EP2426435 A2 EP 2426435A2
Authority
EP
European Patent Office
Prior art keywords
primary
cooling circuit
cooling
coolant
compressor
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Withdrawn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
EP11004604A
Other languages
English (en)
French (fr)
Inventor
Petrus Carolus van Beveren
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.)
Schutter Rotterdam BV
Original Assignee
Schutter Rotterdam BV
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 Schutter Rotterdam BV filed Critical Schutter Rotterdam BV
Publication of EP2426435A2 publication Critical patent/EP2426435A2/de
Withdrawn legal-status Critical Current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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/005—Adaptations for refrigeration plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/04—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled condensation heat from one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/08—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with working fluid of one cycle heating the fluid in another cycle
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant

Definitions

  • the present invention relates to a cooling system with low energy consumption.
  • the invention is intended for reducing the energy consumption of industrial cooling installations.
  • a cooling liquid such as ammonia for example, evaporates whereby a quantity of heat is extracted from the object to be cooled, such as a freezer room for example.
  • the ammonia vapour is then compressed again by a compressor, whereby the temperature and pressure of the coolant increases, to then be cooled in a condenser to a temperature and pressure that, after releasing the pressure, is again suitable to be guided back to the object to be cooled in order to evaporate again and extract heat from the object to be cooled.
  • COP Coefficient of Performance
  • Another source of energy loss is the loss of heat that is stored in the compressed coolant, and which is partly released in a condenser that is cooled with for instance water, and is lost with the cooling water.
  • a further disadvantage is that the cooling installation is quite large and thus takes up a lot of space.
  • the purpose of the present invention is to provide a solution to the aforementioned disadvantages and other disadvantages.
  • the invention concerns a cooling installation for low energy consumption, consisting of a primary cooling circuit in which there is an object to be cooled, a compressor, a primary condenser and a primary turbine that drives an electricity generator or is directly coupled to the primary compressor, whereby the primary condenser is coupled to a secondary cooling circuit that follows a Rankine cycle or a "Trilateral Flash Cycle System” (TFC), whereby heat from the primary cooling circuit is utilised in the secondary cooling circuit that contains a secondary turbine that is coupled to an electricity generator, or is directly coupled to the primary compressor, and further contains a secondary condenser and a pressure pump.
  • TFC Trilateral Flash Cycle System
  • An advantage of such a cooling system is that part of the heat that is carried off in the primary cooling circuit is converted into electrical energy by means of a primary and a secondary turbine.
  • This double recuperation ensures that the coefficient of performance (COP) can be increased from 3 to 7.41 in the example below. This means that the quantity of external energy needed to achieve the desired cooling effect can be reduced by more than half.
  • Another advantage of such a cooling installation is that the electrical energy generated can be reused locally to supply the compressor, which lowers the supply of externally purchased energy.
  • Another advantage of such a cooling installation is that besides to drive the primary compressor, no external energy has to be supplied, such as for example the input of energy from the environment by a heat pump.
  • the primary cooling circuit only contains one compressor and only one condenser
  • the secondary cooling circuit only contains one turbine and this secondary cooling circuit only cools one condenser in the primary cooling circuit.
  • An advantage of such a cooling installation with only one primary condenser and only one compressor in the primary cooling circuit is that multistage compressors are avoided, and multiple condensers are avoided.
  • the secondary cooling circuit contains only one secondary turbine.
  • no additional external energy is supplied to the primary cooling circuit such as external heat from a heat pump or any other energy source.
  • An advantage of such a cooling system is that the system can be of a much more compact construction (sometimes up to half as compact) compared to a traditional cooling system, whereby the space and materials required can be limited.
  • the primary coolant of the primary cooling circuit differs from the secondary coolant of the secondary cooling circuit.
  • Another advantage of the cooling installation with low energy consumption is that the primary coolant and the secondary coolant and the tertiary coolant can be optimally chosen according to their role.
  • the primary coolant can be ammonia
  • the secondary coolant can be optimised for a Rankine cycle, or a TFC cycle.
  • an organic coolant can be chosen that evaporates and condenses at lower temperatures.
  • Such an organic coolant can be chosen such that, upon expansion, the coolant stays in the supercritical region and thus never transforms to the liquid form.
  • Organic coolants also offer the advantage that they have a lower heat of evaporation than water, and thereby a greater share of the heat can be utilised for heating the secondary coolant, which is advantageous when it comes to utilising the residual heat.
  • a compact organic Rankine cycle is known that uses toluene as a coolant and achieves an efficiency of 22%.
  • Other organic coolants are used such as isopentane or butane or fluorine compounds.
  • the TFC system is intended for recovering energy from a low temperature heat source.
  • the use of a mixture of pentane and neopentane has been described herein.
  • the tertiary coolant can differ from the secondary coolant and/or the primary coolant.
  • the secondary condenser in the Rankine cycle or the TFC cycle can use water or air as a tertiary coolant, for example, that carries the residual heat away or can still be used as a heating source.
  • the compressor in the primary cooling circuit is of the dry type, which means that the compressor is not cooled with oil, and is not lubricated with oil either.
  • An advantage of this dry type of compressor is that the heat generated by the compression cannot be emitted into the oil used as a coolant or lubricant, and stays in the cooling circuit whereby a greater fraction of heat can be converted to electrical energy.
  • FIG. 1 shows a cooling installation 1 consisting of a primary cooling circuit 2 and a secondary cooling circuit 3.
  • the primary cooling circuit 2 contains an object 4 to be cooled, in this case a fractionation unit, a primary coolant 5, a primary compressor 6a driven by an electric motor 6b, a primary condenser 7, and a primary turbine 8a.
  • the secondary cooling circuit 3 contains a secondary coolant 9, and goes through the primary condenser 7, a secondary turbine 8b, and a secondary condenser 10 through which a tertiary coolant 11 also flows.
  • the secondary coolant 8 flows further to a pressure pump 12 and to the primary condenser 7 with which the secondary cooling circuit 3 is closed.
  • the operation of the cooling installation 1 can be described as follows.
  • the primary coolant 5, such as ammonia for example, is evaporated whereby heat is extracted from an object to be cooled, such as a fractionation unit for vegetable oils in this case.
  • the evaporated primary coolant 5 is then carried to a primary compressor 6a, which is preferably of the dry type. This means that the compressor 6a is not cooled or lubricated by oil. As a result, the heat generated by the compression in the primary coolant 5 stays in the primary cooling circuit 2 and then more of this heat can be recovered by conversion into electricity.
  • the compressed primary coolant 5 is further guided to the primary condenser 7, where the primary coolant 5 is cooled by means of a secondary coolant 9 and is further guided to the primary turbine 8a.
  • the primary coolant 5 is further expanded in the primary turbine 8a, which is coupled to a generator (not shown) to generate electricity.
  • the expanded primary coolant 5 is further guided to the object 4 to be cooled where it evaporates again and the primary cooling cycle can begin again.
  • the secondary cooling circuit 3 contains a secondary coolant 9, such as an organic coolant for example, with which the primary coolant 5 is cooled in the primary condenser 7.
  • the heated secondary coolant 9 is further guided to the secondary turbine 8b, where the secondary coolant 9 is expanded and drives the turbine 8b, which is coupled to a generator (not shown) in order to generate electricity, or is directly coupled to the primary compressor.
  • the expanded secondary coolant 9 is then guided to a secondary condenser 10 where it is cooled by means of a tertiary coolant 11.
  • a tertiary coolant 11 consists of water, but air can also be used as a coolant.
  • the secondary coolant 9 is further guided to a pressure pump 12 that leads the coolant further through the primary condenser 7 in order to cool the primary coolant 5 again, with which the secondary cooling circuit 3 is closed.
  • the following table shows how much energy in kW is supplied to the primary compressor 6a and the pressure pump 12, and how much energy in kW is recovered by the primary turbine 8a and the secondary turbine 8b, such that the total net supplied energy in kW can be calculated and compared to the quantity of energy that is extracted from the object 4 to be cooled.
  • Table I energy expressed in kW consumed (-) and produced (+) in the cooling installation according to the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP11004604A 2010-06-11 2011-06-07 Kühlsystem mit niedrigem Energieverbrauch Withdrawn EP2426435A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
BE2010/0354A BE1019372A3 (nl) 2010-06-11 2010-06-11 Koelsysteem met laag energieverbruik.

Publications (1)

Publication Number Publication Date
EP2426435A2 true EP2426435A2 (de) 2012-03-07

Family

ID=43607730

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11004604A Withdrawn EP2426435A2 (de) 2010-06-11 2011-06-07 Kühlsystem mit niedrigem Energieverbrauch

Country Status (2)

Country Link
EP (1) EP2426435A2 (de)
BE (1) BE1019372A3 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016039655A1 (en) * 2014-09-08 2016-03-17 Siemens Aktiengesellschaft System and method for recovering waste heat energy
WO2019123243A1 (en) * 2017-12-18 2019-06-27 Exergy S.P.A. Process, plant and thermodynamic cycle for production of power from variable temperature heat sources
WO2022202585A1 (ja) * 2021-03-22 2022-09-29 いすゞ自動車株式会社 トリラテラルサイクルシステム

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2829134C2 (de) * 1978-07-03 1980-10-02 Otmar Dipl.-Ing. 8000 Muenchen Schaefer Heizanlage mit einer Wärmepumpe
DE3402955A1 (de) * 1984-01-28 1984-11-08 Genswein, geb.Schmitt, Annemarie, 5160 Düren Dampfkraftmaschinen-kreisprozess mit rueckfuehrung der abwaerme mittels eines mehrstufigen waermepumpenprozesses, insbesondere fuer dampfkraftwerke (heiss- und kaltdampf)
US6962056B2 (en) * 2002-11-13 2005-11-08 Carrier Corporation Combined rankine and vapor compression cycles
NZ556092A (en) * 2004-12-24 2009-08-28 Renewable Energy Systems Ltd Methods and apparatus for power generation
JP2008106946A (ja) * 2005-02-10 2008-05-08 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016039655A1 (en) * 2014-09-08 2016-03-17 Siemens Aktiengesellschaft System and method for recovering waste heat energy
WO2019123243A1 (en) * 2017-12-18 2019-06-27 Exergy S.P.A. Process, plant and thermodynamic cycle for production of power from variable temperature heat sources
WO2022202585A1 (ja) * 2021-03-22 2022-09-29 いすゞ自動車株式会社 トリラテラルサイクルシステム

Also Published As

Publication number Publication date
BE1019372A3 (nl) 2012-06-05

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