WO2001057459A1 - Procede et appareil de refroidissement de produit par evaporation a point de rosee - Google Patents

Procede et appareil de refroidissement de produit par evaporation a point de rosee Download PDF

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Publication number
WO2001057459A1
WO2001057459A1 PCT/US2001/004081 US0104081W WO0157459A1 WO 2001057459 A1 WO2001057459 A1 WO 2001057459A1 US 0104081 W US0104081 W US 0104081W WO 0157459 A1 WO0157459 A1 WO 0157459A1
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WO
WIPO (PCT)
Prior art keywords
air
product
channels
ofthe
working
Prior art date
Application number
PCT/US2001/004081
Other languages
English (en)
Other versions
WO2001057459A9 (fr
Inventor
Valeriy Maisotsenko
Leland E. Gillan
Timothy L. Heaton
Alan D. Gillan
Original Assignee
Idalex Technologies, Inc.
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 Idalex Technologies, Inc. filed Critical Idalex Technologies, Inc.
Priority to AU2001234938A priority Critical patent/AU2001234938A1/en
Priority to US10/203,195 priority patent/US6776001B2/en
Publication of WO2001057459A1 publication Critical patent/WO2001057459A1/fr
Publication of WO2001057459A9 publication Critical patent/WO2001057459A9/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
    • F24F3/1423—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/0035—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using evaporation
    • 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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/10—Rotary wheel
    • F24F2203/1032—Desiccant wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/10—Rotary wheel
    • F24F2203/1056—Rotary wheel comprising a reheater
    • F24F2203/1064—Gas fired reheater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/10—Rotary wheel
    • F24F2203/1084—Rotary wheel comprising two flow rotor segments
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/54—Free-cooling systems

Definitions

  • the present invention relates to methods and apparatus for indirectly cooling a fluid by evaporation and more specifically to a method and an apparatus for cooling air, or a product other than air, to substantially the dew point temperature ofthe air used in the evaporative
  • Indirect evaporative cooling has been used for many years to cool high temperature fluids down to near the wet bulb temperatures for commercial and industrial processes such as refrigeration systems.
  • the use of indirect evaporative cooling for direct air conditioning has been used for many years to cool high temperature fluids down to near the wet bulb temperatures for commercial and industrial processes such as refrigeration systems.
  • the use of indirect evaporative cooling for direct air conditioning has been used for many years to cool high temperature fluids down to near the wet bulb temperatures for commercial and industrial processes such as refrigeration systems.
  • indirect evaporative cooling for direct air conditioning
  • the commercially available indirect evaporative cooling systems use a two-step process for cooling, indirect evaporative cooling ofthe air to less than half of the difference between the wet bulb temperature and then adiabatic cooling to the final temperature. With this process the
  • This patent describes a method and apparatus for Dew Point Indirect Evaporative Cooling that utilizes a highly efficient thermodynamic process of heat and mass exchange between air and
  • the dew point temperature ofthe entering fluid as opposed to the wet bulb temperature, and with little or no moisture added to the air.
  • the unit's inability to cool a product other than air is the unit's inability to cool a product other than air.
  • the unit lacked flow direction in channels causing air mixing and therefore temperature mixing preventing the greatest possible temperature differences across a
  • the plates did not have a common wick material making it difficult to wet the plates.
  • the design did not allow for non horizontal wetting of panels or using natural capillary transporting of water to wet moist surface.
  • the design requires higher-pressure drops and thus impaired efficient surface area use.
  • the apparatus uses multiple
  • working air streams that are first precooled and then passed in cross flow, or counter flow, over an indirect evaporative cooling plate.
  • the working air streams by evaporation, take heat from the heat exchange plate, which provides the interface between the working air and the
  • product stream fluid which in turn takes heat from the product fluid.
  • a further object is to obtain lower temperatures when air is used as the product fluid, by using
  • added cooling capacity by providing greater latent heat capacity. This may be done by direct heat input or by removing humidity from the entering air
  • Another object of this invention is to allow the humid working air exhaust to be used as the product and directed to the user for humidification of desired area, for example, in the winter, in residential areas.
  • the method and apparatus can be used in conjunction with existing desiccant dehumidification systems to cool building fresh makeup air taking advantage of relatively dry and cool building air making a very efficient process. It can also be used to cool dehumidified building recirculation air.
  • the plates in the apparatus are made of a layer of wick material with a thin waterproof or low permeability coating in dry zones.
  • Channel guides or corrugated sheets can be used to hold
  • the plate wick is wetted by wicking, or by natural capillary transportation of water out of a reservoir.
  • Figure 1 A is a schematic representation ofthe flow path ofthe present invention for
  • Figure IB is the reverse side ofthe plate in Fig. 1 A.
  • Figure 2 A is a schematic representation ofthe flow path ofthe present invention for the first side of a version of a plate.
  • Figure 2B is the reverse side ofthe plate shown in 2 A.
  • Figure 3 A is a schematic representation ofthe flow channels on the first side of a plate as
  • Figure 3B is a schematic representation of a stack of plates.
  • Figure 4 A is a schematic representation of a stack of square shaped plates.
  • Figure 4B is a schematic representation of a stack of diamond shaped plates.
  • Figure 5 A is a schematic of a plate such as in Fig. 1 A with the 4 th quadrant used as a direct evaporative cooling area.
  • Figure 5B is a view ofthe reverse side of plate in 5 A.
  • Figure 6 is a schematic of a fresh make-up-air drying and cooling system for a conditioned
  • Figure 7 is a schematic of a recirculation air-drying and cooling system for a
  • Figure 8 A is a schematic of an apparatus, wherein a plethora of plates set in a
  • Figure 8B is an individual plate from Fig. 8A.
  • Figure 9 is a schematic of an apparatus, wherein a plethora of plates set in a reservoir of
  • Figure 10 is a schematic of an apparatus, wherein a plethora of plates using corrugated
  • FIG 11 is a schematic of an apparatus, wherein a plethora of plates with a feeder wick water distribution system. Detailed Description of the Invention
  • Fig. 1 A illustrates one configuration ofthe top surface ofthe plate (7) as used in the apparatus.
  • the plate (7) is formed by wick material with a portion having a low permeability material surface, such as plastic.
  • the low permeability of the plastic layer prevents moisture from crossing the plate (7) from one side to the other.
  • the plastic coating if a separate layer, is thin and is placed onto the wick layer by painting, by lamination or other suitable means.
  • the top surface of plate (7) has a portion where the wick material is
  • Fig. 1 A shows working air channels (2), product air channels (1) and channel guides(l ⁇ ).
  • the wet zone (4) is exposed wick material.
  • the dry zone(3) is the wick material with the impermeable surface.
  • 1 A , IB, 2 A, and 2B are segmented into quadrants 51, 52, 53 and 54.
  • Fig. 3 A shows the overall square dimensions divided in four quadrants No. 51,52,53, & 54.
  • quadrants (51) is covered by plastic.
  • Quadrant 52 is covered by plastic over one-half of its area.
  • 53 is ofthe wick material and is not covered by plastic.
  • Quadrant 54 in this particular embodiment is omitted from the plate (7).
  • channel guides (10) are in parallel and spaced the desired spacing to accomplish the task of confining and directing the flow of fluids along the surface of plate (7).
  • the flow space is defined
  • the channel is designated a dry channel, or product channel (1) in as much as the liquid in the wick layer is prevented from evaporating into the channel fluid. While the channel is bounded by the wick layer of adjacent plates (7) the channel is designated as a wet channel or working channel (4) in as much as the liquid in the fiber interacts and evaporates with the fluid or air flowing in the working channel.
  • the dry zone (3) is in the comparable location to the dry zone on the bottom surface ofthe first plate (7). See Fig. IB and Fig. 2 A.
  • the dry zone ofthe surface of adjoining plates oppose each other across the space defined by those two plates.
  • channel or product channel (1), is created and bounded by plastic coated plate sections.
  • plate 2 also is a square with the fourth quadrant missing but it has
  • the first and second plate as product dry channel 61, 62, 63 and 64.
  • 61 and 62 are product dry channels.
  • 63 and 64 are the working air wet channels. In quadrant No.52 the working air passes over some surface that is plastic coated and some that is not.
  • the majority ofthe path in the quadrant is over plastic and thus primarily a dry channel.
  • channel 64 it is primarily over the wick area and thus a wet channel though it has some plastic or dry channel.
  • the channel guides are oriented 90 degrees from the orientation of the channel guides on the first plate.
  • a third plate channels 71, 72, 73 and 74 are formed and defined by the channel guides on the second plate , the top surface ofthe second plate and the bottom surface ofthe third plate.
  • the flow ofthe channels in 71 , 72, 73 and 74 are cross flow oriented to the flow in channels 61, 62, 63 and 64.
  • the channel guides- for the third plate are oriented in parallel to the channel guides on the first plate.
  • Channels 81 through 84 are flowing parallel to channels 61 through 64 while at the same time
  • channels 61 and 62 and channels 81 and 82 their flow is entirely in dry channels ofthe product cooling quadrant 51. Adjacent to them in the space above plate 2 are the channels 71 and 72, which are working channels (2) or wet channels. In quadrant 52over those portions of channels 71 and 72 that are in the wet area there is an area called the pre-cooling section. Through evaporation ofthe fluid in the wick like material that are on the floor and ceiling of channels 71 and 72, when the flow is in the pre-cooling area ,or later in the product cooling of quardrant 51,
  • channels 63, 64, 83, and 84 are precooled by the evaporation in channels 71 and 72 in quadrant 52. As the flow continues down channels 71 and 72 additional evaporation will occur in quadrant 51 further lowering the temperature ofthe
  • channels 71 and 72 and the product channels 81 and 82 and 61 and 62 is very high, maintaining a small temperature difference across the plates.
  • the temperature in channels 61 and 62 in the first space layer and channels 81 and 82 in the third space layer are lowered due to the low- temperature in channels 71 and 72 brought about by evaporation and pre-cooling.
  • the product flow of fluid entering channels 61 and 62 and channels 81 and 82 has its temperature
  • the product fluid or air in the second space contained in channels 73 and 74 are likewise cooled across the plastic barrier by the working air channels of 63 and 64 and 83 and 84 in the adjacent channel layer's in the stack as illustrated.
  • channel 72 has more cooling because there is more plastic covering channel 72 in quadrant 52.
  • the flow in channel 72 is precooled by the flow occurring in 63, 64, 83 and 84. Because there is more plastic in channel 72 there is more
  • the pre-cooling occurring in quadrant 52 lowers the temperatures of all the working air before
  • FIG. 1 The embodiments as shown in figures 1, 2 , 3 and 4A are of a square configuration of plates (7). There are alternatives, among them a diamond shape such as shown in Fig. 4B. The selection of a square shape or diamond shape would be determined by the design decisions as further explained.
  • a diamond shape has the advantages of having the working fluid flowing relative to the product fluid at an angle other that ninety degrees. Rather than being oriented at right angles to the
  • cooler through evaporation has more time to interact with the product fluid .
  • the product fluid is given more time to cool by heat transfer.
  • the working air temperature is lower due to its longer exposure to the evaporative surface in the wet zone.
  • the diamond shape there is a greater proportion ofthe area ofthe plate(7) on the perimeter, in as much as the square shape has more interior area.
  • the diamond shape gives proportionately more area on the perimeter, area that is cooler due to the ends of the working air channels are at the perimeter.
  • the amount of area and the differential temperatures in these areas will affect the amount of heat transfer that will occur.
  • the coolest part ofthe working fluid is at the perimeter, and inasmuch as the diamond gives more area at the
  • the diamond gives more proportion of its area to heat transfer where the temperature
  • the diamond shape gets greater heat transfer because of the distribution ofthe area in the diamond puts more ofthe coolest area at the perimeter, where the product fluid has the largest amount of area to interact with it. Thus there will be more area for heat exchange for the two flows and thus to have the sensible heat transfer across the plastic surface (3).
  • wicking function ofthe wick layer transports the evaporating fluid from the reservoir upward to the upper reaches ofthe wick layer. If the plates shape is a diamond shape this vertical height that must be wicked in order to wet the upper reaches ofthe wick layer will be lower.
  • the product air is cooled by the adjacent working air (2).
  • the 4 th quadrant would merely place adjacent layers of product air (presumable at the same temperature) next to each other. No gain in the product temperature is had. By omitting the 4 th quadrant less energy is
  • quadrant 4 (4) not be omitted but rather kept as an evaporative area for the product flow, see fig. 5 A. This added area of direct evaporative
  • the main feature or function ofthe within design may be to add humidity.
  • the ability to add humidity and at the same time control the temperature of the end product mixture enables the user to adjust humidity and temperature independently to accomplish the target conditions.
  • This apparatus allows the user to adjust the humidity without having to also
  • the apparatus by an additional feature can manipulate the latent heat capacity ofthe working fluid to accomplish a more efficient cooler.
  • additional latent heat capacity of the working air and additional evaporation capacity results to the system. If the working air has humidity above .001 1 to.0014 pounds of water per pound of air (wherein the
  • the flow of fluids, working air (2) or product air (1) can be aided by common mass transfer devices such as fans pumps or other devices common in industry.
  • the indirect evaporative cooler is enhanced if the working air(2) has a pressure drop at its exhaust which induces the flow of the working air through the working air channels (17).
  • the evaporative process in the working air channel will be enhanced as lower pressure aids evaporation..
  • Desiccants can also be used in the system as shown in Fig. 6 and 7.
  • evaporative cooler are in enhanced efficiencies ofthe evaporative process, control ofthe humidity of the working or product air, and the use of the by product of the heat generated during dehumidification to increase the latent heat capacity ofthe working air in the evaporative process
  • the desiccants wheel is illustrated (13).
  • outside air is first drawn through and dehumidified by the desiccant wheel.
  • the dehumidification raises the temperature ofthe dehumidified air due to the heat occurring by extracting the water from the outside air.
  • the dehumidified air is used as the product air, in order to control the humidity and yield cool dry air as product (1).
  • the working air is recirculated air from the condition space
  • recirculated air is used for both the product air and the working air. After recycling, the working air is exhausted and thus there is a net loss of air for circulation. To make up for this loss, outside air is used to supplement the system air. Before use the outside air may have to be dehumidified. After going through the desiccant wheel and becoming dehumidified this combination air is fed
  • the heat generated by the dehumidifier is used to enhance the evaporative process by going to the working air stream.
  • the heat gives added efficiency and capacity to the system.
  • the system of wetting the wick material in the plates (7) by evaporating fluid can be accomplished by pure wicking from a low point ofthe wick material immersed in a reservoir or by distributing the evaporating fluid by means of feeder wick that is positioned and interface with the wick material on the plates.
  • Fig. 11 illustrates a feeder wick where evaporating fluids are distributed
  • feeder wick which fits in a hole in the plates.
  • wick interfaces with the inside surface of the holes in the plates and the wicking layer on the plates.
  • Fig. 8A, 8B, and 9 illustrate the reservoir system where the plates are vertical or in a sloped position with their lower edge immersed in the reservoir holding the evaporating fluids.
  • the wicking from the reservoir replenishes that liquid for subsequent evaporation.
  • the plates In order to aid in the wicking the plates cannot be overly tall. This may be addressed by the use of a diamond shape as previously discussed rather than a square shape. Alternately the plates may be elevated at an angle rather than vertical. This minimizes the amount of gravity that must be overcome to wet the uppermost area ofthe wick material.
  • Fig. 10 illustrates an assembly where the individual plates (without the separate channel guides
  • inserts are separated by corrugated inserts. These inserts maintain the separation and also act as the channel guides for the flow of product air and workign air.
  • the inserts are preferred to be of an impermeable material such as plastic or resin impregnated cellulose or paper so that in the wet

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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)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un procédé et un appareil permettant d'effectuer un refroidissement indirect amélioré par évaporation d'air, d'eau, de combustible ou d'autres fluides, tout en régulant l'humidité. Cette conception permet un refroidissement jusqu'au point de rosée sans entrée d'énergie en plus de l'énergie nécessaire pour produire l'écoulement de fluide voulu. On utilise des plaques composites empilées (7) pourvues de voies pour l'écoulement fluidique entre les plaques adjacentes. Sur les surfaces opposées de ces plaques, on trouve des zones humides (4) ou des zones sèches (3). Les zones humides (4) permettent un refroidissement par évaporation classique utilisé également pour refroidir les fluides en contact avec les zones sèches (3). L'avantage de cette invention est le transfert thermique contrôlé qui permet un refroidissement sélectionné d'écoulement fluidique de manière à atteindre des températures aussi basses que le point de rosée.
PCT/US2001/004081 2000-02-07 2001-02-07 Procede et appareil de refroidissement de produit par evaporation a point de rosee WO2001057459A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2001234938A AU2001234938A1 (en) 2000-02-07 2001-02-07 Method and apparatus for dew point evaporative product cooling
US10/203,195 US6776001B2 (en) 2000-02-07 2001-02-07 Method and apparatus for dew point evaporative product cooling

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US18081900P 2000-02-07 2000-02-07
US60/180,819 2000-02-07
US26554801P 2001-01-31 2001-01-31
US60/265,548 2001-01-31

Publications (2)

Publication Number Publication Date
WO2001057459A1 true WO2001057459A1 (fr) 2001-08-09
WO2001057459A9 WO2001057459A9 (fr) 2002-10-24

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PCT/US2001/004082 WO2001057460A1 (fr) 2000-02-07 2001-02-07 Mecanisme de refroidissement par evaporation indirecte

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7007453B2 (en) 2002-07-20 2006-03-07 Idalex Technologies, Inc. Power system and method
US8191872B2 (en) 2003-10-17 2012-06-05 Oxycom Beheer B.V. Heat exchange laminate
CN102767877A (zh) * 2012-06-26 2012-11-07 澳蓝（福建）实业有限公司 自冷式多级蒸发制冷的系统及其制冷方法

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EP1465721B1 (fr) * 2001-12-12 2018-01-24 F.F. Seeley Nominees Pty Ltd. Procede et appareil a plaques pour un refroidisseur par evaporation au point de rosee
NL1022794C2 (nl) * 2002-10-31 2004-09-06 Oxycell Holding Bv Werkwijze voor het vervaardigen van een warmtewisselaar, alsmede met de werkwijze verkregen warmtewisselaar.
EP1836046B1 (fr) * 2005-01-11 2021-12-29 Seeley International Pty Ltd Procede et materiaux permettant d'ameliorer des echangeurs de chaleur a evaporation
US20060292349A1 (en) * 2005-05-05 2006-12-28 Seeley Frederic F An evaporative material system and method of manufacture
EP2821746A1 (fr) * 2013-07-03 2015-01-07 Seeley International Pty Ltd Système de refroidisseurs par évaporation indirecte à capacité évolutive
CN107687677B (zh) * 2017-09-22 2023-04-07 清华大学 空气净化片及空气净化模组
AU2018286567B1 (en) * 2018-12-24 2020-05-07 Commonwealth Scientific And Industrial Research Organisation Evaporative Cooling System, Device and Method of Construction
CN112815757A (zh) * 2020-12-28 2021-05-18 华为技术有限公司 换热器、间接蒸发冷却机组及其控制方法

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US3683591A (en) * 1969-07-17 1972-08-15 Munters Carl Georg Process of drying air and apparatus intended therefor
US4002040A (en) * 1973-07-08 1977-01-11 Aktiebolaget Carl Munters Method of cooling air and apparatus intended therefor
US5453223A (en) * 1994-09-12 1995-09-26 Acma Limited Method of air cooling and heat exchange apparatus

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US7007453B2 (en) 2002-07-20 2006-03-07 Idalex Technologies, Inc. Power system and method
US8191872B2 (en) 2003-10-17 2012-06-05 Oxycom Beheer B.V. Heat exchange laminate
CN102767877A (zh) * 2012-06-26 2012-11-07 澳蓝（福建）实业有限公司 自冷式多级蒸发制冷的系统及其制冷方法
CN102767877B (zh) * 2012-06-26 2015-08-19 澳蓝（福建）实业有限公司 自冷式多级蒸发制冷的系统及其制冷方法

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AU2001234938A1 (en) 2001-08-14
AU2001234939A1 (en) 2001-08-14

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