EP2821744A1 - Refroidisseur par évaporation indirecte à efficacité améliorée - Google Patents

Refroidisseur par évaporation indirecte à efficacité améliorée Download PDF

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Publication number
EP2821744A1
EP2821744A1 EP13275152.0A EP13275152A EP2821744A1 EP 2821744 A1 EP2821744 A1 EP 2821744A1 EP 13275152 A EP13275152 A EP 13275152A EP 2821744 A1 EP2821744 A1 EP 2821744A1
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EP
European Patent Office
Prior art keywords
passages
air
dry
wet
air flow
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Withdrawn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
EP13275152.0A
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German (de)
English (en)
Inventor
Robert Gilbert
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.)
Seeley Interational Pty Ltd
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Seeley Interational Pty Ltd
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Publication date
Application filed by Seeley Interational Pty Ltd filed Critical Seeley Interational Pty Ltd
Priority to EP13275152.0A priority Critical patent/EP2821744A1/fr
Publication of EP2821744A1 publication Critical patent/EP2821744A1/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
    • F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
    • F28C1/14—Direct-contact trickle coolers, e.g. cooling towers comprising also a non-direct contact heat exchange
    • F28C2001/145—Direct-contact trickle coolers, e.g. cooling towers comprising also a non-direct contact heat exchange with arrangements of adjacent wet and dry passages

Definitions

  • This invention relates to evaporatively cooled heat exchangers utilised in the cooling of air for the comfort cooling of buildings.
  • These heat exchangers are generally constructed from adjacent wet and dry passages arranged such that air through the adjacent passages flows in relative counter flow.
  • the present invention concerns a method and means for significantly improving the operating efficiency of indirect evaporative cooling systems.
  • the pressure required to drive the proportion of air through the wet passages is produced by applying a restriction, or baffle, to the supply air exiting the dry passages.
  • a restriction or baffle
  • the Morozov design passes the full air flow only through the first heat exchanger dry passages, which are shorter in length to achieve the same cooling relative to the original Maisotsenko design and therefore result in less pressure drop through those dry passages.
  • Air flow through the dry passages of the second heat exchanger dry passages is much less (generally about half) the air flow through the dry passages of the first heat exchanger thereby requiring less pressure drop associated with the air flow.
  • the pressure losses in this design are reduced, but the energy loss through the baffle on the supply air is still significant.
  • Maisotsenko describes an alternative design utilising a combination of counter flow and cross flow paths within the heat exchanger.
  • air in the dry passages is progressively passed through to the wet passages via holes in the heat exchanger walls between adj acent dry and wet passages. Each hole dimensioned to allow only a pre-determined rate of flow between dry and wet passages. Once in a wet passage, air then travels in a cross flow direction to be exhausted at the end of the wet passage.
  • Air flow within the exchanger is controlled by the geometry of the air passages and holes between wet and dry passages and no baffle is required to induce air to flow into the wet passages. Energy in the air flow is still dissipated when passing through the holes between wet and dry passages, but the design does not subject all of the airflow to pressure loss as in the former design. Energy losses are reduced, but at some compromise to thermodynamic efficiency of the cooler.
  • an indirect evaporative cooler comprising:
  • the first fan is located upstream of the dry passages.
  • the first fan is located downstream of the dry passages
  • the present invention provides a method of indirect evaporative cooling wherein a lower than ambient pressure is applied to exhaust outlets of wet passages of a heat exchanger having alternating wet and dry air flow passages and comprising passing a first air flow through the dry passages before drawing off a portion thereof as secondary air through the wet passages by said lower than ambient pressure.
  • FIG. 1 shows a known airflow configuration for an indirect evaporative cooler to function.
  • Incoming air 10 is directed through the dry passages 12 of heat exchanger 20.
  • the air stream is divided into supply air 18 and return air 22, directed into the wet passages 14.
  • the wet passages have a hydrophilic inner surface 16 which is capable of being kept continuously wet. Air from the wet passages emerges through exhaust opening 22 where it is exhausted to atmosphere.
  • Such an arrangement of indirect evaporative cooling is capable of producing supply air 18 at temperatures approaching the Dew Point of incoming air 10 without the addition of moisture to the air.
  • FIGS 2 and 3 show perspective and section views, respectively, of a practical arrangement for a device exploiting the advantages of indirect evaporative cooling.
  • Air enters from the external ambient through fan 42 which supplies high pressure air to the chamber 44.
  • Heat exchanger 40 is manifolded such that high pressure air from chamber 44 can only flow through the dry channels of the heat exchanger, and air which flows through the dry channels must flow all the way through the dry channels, emerging into chamber 48.
  • a proportion of the air emerging from the dry channels into chamber 48 is required to be turned around to flow back through the wet channels spaced between the dry channels of heat exchanger 40.
  • This pressure is achieved by applying a baffle or restriction 50 to the flow of air leaving chamber 48 through supply air duct 47, the pressure differential across baffle 50 at the required flow rate results in an increased static pressure in chamber 44.
  • Fan 42 is required to pressurise air to overcome the pressure loss associated with passing all of the air supplied through the dry channels, plus the static pressure in chamber 48.
  • the static pressure in chamber 48 is sufficient to overcome the flow resistance of the proportion of air flowing through the wet channels to exhaust 46.
  • the static pressure in chamber 48 is regulated by adjusting baffle 50 thereby producing a static pressure differential across the baffle.
  • the air flow through the baffle 50 at such a differential pressure represents a loss of power equal to the product of the air flow and pressure differential. This loss is an additional power load on fan 42 which provides no additional cooling or otherwise useful energy to the air flow.
  • Fan 42 is shown schematically as an axial flow fan, in practice a centrifugal or combined flow fan is generally used due to the high pressures required.
  • FIG. 4 shows a section through a first embodiment of an indirect evaporative cooler in accordance with the current invention.
  • the high pressure fan delivering air to the entrance of the heat exchanger has been replaced by separate fans 64, 66 on the air supply side and the exhaust, respectively.
  • the static pressure immediately before fan 66 will be the sum of the static pressure in chamber 68 and the pressure differential required for the air flow through the wet passages of the heat exchanger 60.
  • the operation of the fans 64 and 66 can be controlled through electronic speed controllers or other means to produce a desired ratio of air flow between the supply air and exhaust air. Furthermore, the magnitude and/or ratio of these air flows can be readily adjusted by varying the speeds of the two fans 64, 66 thereby enabling optimisation of the performance of the indirect evaporative cooler.
  • Such control is desirable, for example, in the initial cooling of, say, a living space which is initially at a high temperature.
  • the relatively high delivery of supply air quickly purges the living space or premises of hot air. Once the hot air is purged, the indirect cooler can then be re-set for temperature and air delivery by adjustment of the speeds of the two fans 64, 66.
  • the required air pressure in chamber 68 would be -450 Pa to provide the necessary 450 Pa differential across the dry passages.
  • the power required to be imparted to the air flow by fan 64 at n units of supply airflow will be 450 X n.
  • the power required to be imparted to the wet passage air flow will be 600 x n.
  • the total power to be imparted by both fans is therefore 1,050 x n power units. This is less than the 1,200 x n power units required by the prior art design and therefore the design subject of the current invention provided for an increase in efficiency of the indirect evaporative cooler for the equivalent air flow and cooling.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP13275152.0A 2013-07-03 2013-07-03 Refroidisseur par évaporation indirecte à efficacité améliorée Withdrawn EP2821744A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13275152.0A EP2821744A1 (fr) 2013-07-03 2013-07-03 Refroidisseur par évaporation indirecte à efficacité améliorée

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13275152.0A EP2821744A1 (fr) 2013-07-03 2013-07-03 Refroidisseur par évaporation indirecte à efficacité améliorée

Publications (1)

Publication Number Publication Date
EP2821744A1 true EP2821744A1 (fr) 2015-01-07

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EP13275152.0A Withdrawn EP2821744A1 (fr) 2013-07-03 2013-07-03 Refroidisseur par évaporation indirecte à efficacité améliorée

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EP (1) EP2821744A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018051156A1 (fr) * 2016-09-19 2018-03-22 Aurae Technologies Limited Procédé de refroidissement indirect par évaporation en deux étapes pour bâtiments et dispositifs
WO2024019798A1 (fr) * 2022-07-18 2024-01-25 Baryon Inc. Échangeur de chaleur amélioré avec des générateurs thermoélectriques

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002040A (en) * 1973-07-08 1977-01-11 Aktiebolaget Carl Munters Method of cooling air and apparatus intended therefor
SU979796A1 (ru) 1976-08-17 1982-12-07 Одесский Инженерно-Строительный Институт Установка дл косвенно-испарительного охлаждени воздуха
US4977753A (en) 1987-05-12 1990-12-18 Maisotsenko Valery S Method for indirect-evaporative air cooling
US5301518A (en) 1992-08-13 1994-04-12 Acma Limited Evaporative air conditioner unit
BE1013160A6 (nl) * 1999-11-30 2001-10-02 Offringa Dirk Dooitze Werkwijze en inrichting voor het koelen van lucht.
US20040061245A1 (en) 2002-08-05 2004-04-01 Valeriy Maisotsenko Indirect evaporative cooling mechanism
WO2004065857A1 (fr) * 2003-01-23 2004-08-05 Oxycell Holding Bv Refroidisseur evaporatif a dispositions antimicrobiennes
EP1574804A2 (fr) * 2004-03-08 2005-09-14 Baltimore Aircoil Company, Inc. Méthode de contrôle du fonctionnement d'un échangeur de chaleur
US20060124287A1 (en) 2002-10-31 2006-06-15 Reinders Johannes Antonius M Heat exchanger and method of manufacture thereof
WO2006074508A1 (fr) 2005-01-11 2006-07-20 F F Seeley Nominees Pty Ltd Procede et materiaux permettant d'ameliorer des echangeurs de chaleur a evaporation
US20080018001A1 (en) * 2004-12-23 2008-01-24 Az Evap, Llc Non Uniform Water Distribution System for an Evaporative Cooler
US20120171943A1 (en) * 2010-12-30 2012-07-05 Munters Corporation Systems for removing heat from enclosed spaces with high internal heat generation

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002040A (en) * 1973-07-08 1977-01-11 Aktiebolaget Carl Munters Method of cooling air and apparatus intended therefor
SU979796A1 (ru) 1976-08-17 1982-12-07 Одесский Инженерно-Строительный Институт Установка дл косвенно-испарительного охлаждени воздуха
US4977753A (en) 1987-05-12 1990-12-18 Maisotsenko Valery S Method for indirect-evaporative air cooling
US5301518A (en) 1992-08-13 1994-04-12 Acma Limited Evaporative air conditioner unit
BE1013160A6 (nl) * 1999-11-30 2001-10-02 Offringa Dirk Dooitze Werkwijze en inrichting voor het koelen van lucht.
US20040061245A1 (en) 2002-08-05 2004-04-01 Valeriy Maisotsenko Indirect evaporative cooling mechanism
US20060124287A1 (en) 2002-10-31 2006-06-15 Reinders Johannes Antonius M Heat exchanger and method of manufacture thereof
WO2004065857A1 (fr) * 2003-01-23 2004-08-05 Oxycell Holding Bv Refroidisseur evaporatif a dispositions antimicrobiennes
EP1574804A2 (fr) * 2004-03-08 2005-09-14 Baltimore Aircoil Company, Inc. Méthode de contrôle du fonctionnement d'un échangeur de chaleur
US20080018001A1 (en) * 2004-12-23 2008-01-24 Az Evap, Llc Non Uniform Water Distribution System for an Evaporative Cooler
WO2006074508A1 (fr) 2005-01-11 2006-07-20 F F Seeley Nominees Pty Ltd Procede et materiaux permettant d'ameliorer des echangeurs de chaleur a evaporation
US20120171943A1 (en) * 2010-12-30 2012-07-05 Munters Corporation Systems for removing heat from enclosed spaces with high internal heat generation

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018051156A1 (fr) * 2016-09-19 2018-03-22 Aurae Technologies Limited Procédé de refroidissement indirect par évaporation en deux étapes pour bâtiments et dispositifs
WO2024019798A1 (fr) * 2022-07-18 2024-01-25 Baryon Inc. Échangeur de chaleur amélioré avec des générateurs thermoélectriques

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