US20080116592A1 - Method and Materials for Improving Evaporative Heat Exchangers - Google Patents

Method and Materials for Improving Evaporative Heat Exchangers Download PDF

Info

Publication number
US20080116592A1
US20080116592A1 US11/792,500 US79250006A US2008116592A1 US 20080116592 A1 US20080116592 A1 US 20080116592A1 US 79250006 A US79250006 A US 79250006A US 2008116592 A1 US2008116592 A1 US 2008116592A1
Authority
US
United States
Prior art keywords
water
core
heat exchange
wettable
air
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.)
Abandoned
Application number
US11/792,500
Other languages
English (en)
Inventor
Robert Wilton James
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.)
FF Seeley Nominees Pty Ltd
Original Assignee
FF Seeley Nominees Pty Ltd
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
Priority claimed from AU2005900235A external-priority patent/AU2005900235A0/en
Application filed by FF Seeley Nominees Pty Ltd filed Critical FF Seeley Nominees Pty Ltd
Assigned to FF SEELEY NOMINEES PTY LTD reassignment FF SEELEY NOMINEES PTY LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JAMES, ROBERT WILTON
Publication of US20080116592A1 publication Critical patent/US20080116592A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B3/00—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar form; Layered products having particular features of form
    • B32B3/26—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar form; Layered products having particular features of form characterised by a particular shape of the outline of the cross-section of a continuous layer; characterised by a layer with cavities or internal voids ; characterised by an apertured layer
    • B32B3/28—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar form; Layered products having particular features of form characterised by a particular shape of the outline of the cross-section of a continuous layer; characterised by a layer with cavities or internal voids ; characterised by an apertured layer characterised by a layer comprising a deformed thin sheet, i.e. the layer having its entire thickness deformed out of the plane, e.g. corrugated, crumpled
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B25/00—Layered products comprising a layer of natural or synthetic rubber
    • B32B25/10—Layered products comprising a layer of natural or synthetic rubber next to a fibrous or filamentary layer
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B29/00—Layered products comprising a layer of paper or cardboard
    • B32B29/06—Layered products comprising a layer of paper or cardboard specially treated, e.g. surfaced, parchmentised
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B29/00—Layered products comprising a layer of paper or cardboard
    • B32B29/08—Corrugated paper or cardboard
    • 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
    • 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
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • 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
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F25/00—Component parts of trickle coolers
    • F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
    • F28F25/08—Splashing boards or grids, e.g. for converting liquid sprays into liquid films; Elements or beds for increasing the area of the contact surface
    • F28F25/087—Vertical or inclined sheets; Supports or spacers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B2250/00—Layers arrangement
    • B32B2250/02—2 layers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B2255/00—Coating on the layer surface
    • B32B2255/12—Coating on the layer surface on paper layer
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B2307/00—Properties of the layers or laminate
    • B32B2307/50—Properties of the layers or laminate having particular mechanical properties
    • B32B2307/554—Wear resistance
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B2307/00—Properties of the layers or laminate
    • B32B2307/70—Other properties
    • B32B2307/724—Permeability to gases, adsorption
    • B32B2307/7242—Non-permeable
    • B32B2307/7246—Water vapor barrier
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B2307/00—Properties of the layers or laminate
    • B32B2307/70—Other properties
    • B32B2307/726—Permeability to liquids, absorption
    • B32B2307/7265—Non-permeable
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B32—LAYERED PRODUCTS
    • B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM
    • B32B2597/00—Tubular articles, e.g. hoses, pipes
    • 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
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T156/00—Adhesive bonding and miscellaneous chemical manufacture
    • Y10T156/10—Methods of surface bonding and/or assembly therefor
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T156/00—Adhesive bonding and miscellaneous chemical manufacture
    • Y10T156/10—Methods of surface bonding and/or assembly therefor
    • Y10T156/1002—Methods of surface bonding and/or assembly therefor with permanent bending or reshaping or surface deformation of self sustaining lamina

Definitions

  • the present invention relates to improvements in heat exchange capacity of evaporative heat exchangers.
  • one aspect of this invention relates to a material suited to use in forming heat exchange surfaces of evaporative heat exchangers. Additional inventions are disclosed that relate to the operation of evaporative coolers.
  • the aspects of this invention will be described in connection with the heat exchange core of counter flow evaporative coolers, as well as to methods, equipment and systems for the ventilation and cooling of enclosed spaces.
  • the various aspects of this invention can be applied to self-contained air conditioning units suitable for supplying cooled air to an enclosed space, and to self-contained conditioning units suitable for supplying cooled water for use in heat exchange units forming part of a system for the cooling of enclosed spaces.
  • evaporative air coolers for the cooling of enclosed spaces is well known in the art. These coolers are typically constructed with outer walls containing a wettable, permeable media, which is kept wet with water pumped from an internal reservoir. Air from outside the building is drawn through the wetted media by means of a fan located within the evaporative cooler, and delivered either directly into the enclosed space or through a system of ducting to the enclosed space.
  • the air delivered by an evaporative cooler is cooled to a temperature which is always greater than the Wet Bulb Temperature, to a degree determined by the efficiency of the design of the evaporative cooler.
  • the air delivered is also always more humid than the air entering the cooler.
  • This limitation in achievable temperature and the addition of moisture to the air severely limits the degree of cooling available by this method, as well as limiting the use of this means of cooling to relatively hot, dry climates.
  • the design condition for evaporative cooling is 38° C. Dry Bulb Temperature, 21° C. Wet Bulb Temperature.
  • a typical evaporative air cooler will deliver air at around 23.5° C., but which has been substantially humidified. This air is much less amenable to providing comfort conditions within the enclosed space than, say, a refrigeratively cooled air conditioning system, which might deliver air at 15° C., and to which no additional moisture has been added.
  • SU 979796 by Maisotsenko discloses a configuration wherein a main stream of air is passed along a dry duct, simultaneously passing an auxiliary air stream counter currently along a moist duct which is in heat-exchange relation with the dry duct.
  • the auxiliary stream is obtained by subdividing the total stream into main and auxiliary streams.
  • U.S. Pat. No. 4,977,753 A practical implementation and method of construction of the configuration of U.S. Pat. No. 4,977,753 is disclosed in U.S. Pat. No. 5,301,518 by Morozov et al.
  • U.S. Pat. No. 5,301,518 discloses a construction consisting of alternating dry ducts, which may be constructed from a variety of materials, and wet ducts constructed from capillary porous material.
  • the airflow configuration is arranged such that the air streams in the dry and wet ducts are in counter flow as in previous disclosures.
  • the configuration divides the heat exchanger into two separate stages for the purpose of achieving the requisite temperature reduction while relieving the high pressure drop inherent in the narrow air passages required for adequate heat transfer. Wetting of the porous material of the wet ducts is achieved by vertical wicking from a water reservoir beneath the heat exchanger.
  • a first aspect of the present invention provides a corrugated material for use in an evaporative heat exchanger, said material including a water retaining wettable surface and an opposed vapour resistant surface.
  • the shape of the corrugated pattern within the sheets may be varied to optimise thermal performance and airflow resistance when the corrugated material is used in a heat exchange core.
  • the present invention provides a method of making a corrugated laminate material as described herein, wherein a planar sheet of a water retaining medium is shaped with corrugations by being fed through corrugating rollers.
  • the present invention provides a heat exchange core for an evaporative heat exchanger formed from at least one sheet of corrugated material as described herein, wherein the at least one sheet is folded to form at least one pocket or fold such that the interior of each fold forms a wettable surface passage or channel or a vapour resistant passage or channel.
  • the present invention provides a heat exchange element for a core of an evaporative heat exchanger, said element being formed from at least two sheets of corrugated laminate material as described herein, wherein the two sheets are joined to form a passage having corrugated walls for airflow therethrough and wherein the corrugations on opposite sides of the passage are at intersecting angles.
  • the angle of intersection of the corrugations of adjacent corrugated sheets is varied so as to optimise thermal performance and airflow resistance of the heat exchange core.
  • a preferred indirect evaporative heat exchanger core is characterised by a construction consisting of individual corrugated wettable media sheets modified to include a vapour impermeable barrier on one side.
  • the individual sheets are constructed into open pockets sealed top and bottom with the vapour impermeable barrier on the inside of the pocket.
  • Said pockets are then assembled into a stack of pockets by sealing each of the non vapour barrier sides together at the air entry end of the stack of pockets such that a complete core is formed wherein warm, dry air enters the core through the pockets, passing all the way through the pockets.
  • a proportion of the air so delivered is returned through passages formed between the wettable non-vapour barrier sides of adjacent pockets, which form wet passages of the core.
  • the present invention provides a method of making a heat exchange core comprising taking a plurality of pairs of sheets of corrugated laminate material as described herein, forming a plurality of pockets from pairs of said sheets where the inner surfaces of each pocket are vapour resistant surfaces, adjacent edges of each pair of parallel spaced apart sides being sealed together to form open-ended pockets and stacking said pockets in parallel to form wettable surface airflow passages between each pair of adjacent pockets.
  • the present invention provides an evaporative cooler including a heat exchange core formed from at least one sheet of corrugated laminate material as described herein, wherein the at least one sheet is folded to form at least one pocket or fold such that the interior of each fold forms a wettable surface passage or channel or a vapour resistant passage or channel.
  • the present invention provides a method of effecting heat exchange between counter current airflows in a heat exchanger, said heat exchanger including a heat exchange core comprising wet and dry airflow channels in counter flow, said channels being formed with corrugated walls and wherein entry air is passed down the dry channels to exit as conditioned air, a portion of the exit air being reversed to pass through the wet channels and effect heat exchange between the dry and wet channels before being exhausted.
  • This gradient can only be achieved by wicking water from a reservoir to the point where it is to evaporate in prior art arrangements. Any surplus of water over this requirement to evaporate and keep the surfaces wet will degrade thermal performance and it will no longer be possible to approach the Dew Point in delivered air temperature. If the wetted surfaces were to be flood irrigated as is the practice with direct evaporative cooling, it would only be possible for the delivered air temperature to approach the Wet Bulb temperature of the incoming air. This temperature can be considerably above the Dew Point depending on incoming air psychrometrics.
  • an evaporative cooler which includes a heat exchange core wherein adjacent wet and dry airflow channels are in counter current airflow heat exchange relationship with water being supplied to the wet channels in a descending flow pattern, characterised in that water is supplied to the wet channels over a plurality of segments from an air entry end to an air outlet end of said core during operation of said cooler and wherein water is circulated through each segment relatively separately from adjacent segments such that an appropriate temperature gradient is established from an air inlet end to an air outlet end of the core by maintaining different circulating water temperatures in each segment.
  • the method of the eighth aspect is further characterised by the delivery of water through each water distributor from a respective pumping means associated with each water reservoir.
  • the water reservoirs are each connected to a common water conduit such that water levels in each reservoir are allowed to reach an equilibrium level.
  • the present invention provides a method of operating an evaporative cooler which includes a heat exchange core adapted for heat exchange airflow therethrough via a plurality of heat exchange channels, at least some of said channels being wet channels with water being applied to and retained by wettable material in the wet channels, characterised in that water is applied to the wet channels in an intermittently and generally uniformly descending flow pattern across the entire core and wherein the application of water to the wet channels of the core is repeated before the wettable material has dried out.
  • a single pumping means, water spreader and reservoir applies water to the evaporative core periodically.
  • the present invention provides an evaporative cooler including a heat exchange core as described herein having corrugated wet and dry passages or channels, a water distribution system including a plurality of water distributors for wetting the wettable surfaces of the passages or channels, said water distributors being positioned above the core and disposed in spaced apart parallel relation transversely of the core relative to an airflow direction through the core, each water distributor being located within a respective space above the core separate from adjacent water distributor spaces, each water distributor being supplied from a respective reservoir, and further including flow restriction means at an airflow exit of the vapour resistant channels for effecting counter flow of a portion of the exit air through the wet channels to an exhaust.
  • Such an indirect evaporative air cooler typically comprises a fan means for the delivery of air, an indirect evaporative heat exchanger and an air delivery means including an airflow resistance means.
  • FIG. 1 is an isometric view of the construction of a prior art corrugated evaporative media
  • FIG. 2 shows schematic views of airflow paths and a water distribution method of a prior art indirect evaporative cooler
  • FIG. 3 is a sectional view of a dry channel showing the construction of an embodiment of corrugated media in accordance with the invention
  • FIG. 4 shows a sectional view and schematic of a segment of an indirect evaporative cooler core made from the corrugated media of FIG. 3 ;
  • FIG. 5 is an isometric view, which shows an embodiment of the construction of a pocket segment of an indirect evaporative cooler core employing corrugated media of the present invention
  • FIG. 6 is an isometric view of an assembly of pocket segments of FIG. 5 when formed into an indirect evaporative cooler core;
  • FIG. 7 is a schematic showing the water distribution system of another aspect of the present invention where the heat exchange core is divided into segments.
  • FIG. 8 is an isometric view of an assembled indirect evaporative cooler core detailing water and airflow systems.
  • the prior art corrugated media is shown as a block of sheets of corrugated, wettable media within which dry air and water on the wetted surfaces interact.
  • the block 1 is constructed from individual sheets 4 of corrugated media (typically treated paper of a type which readily wicks water along its surface).
  • Individual corrugations 6 are impressed in the media during manufacture and the sheets arranged such that the corrugations are set at an angle 8 to the edges of the block of media.
  • Adjacent sheets 4 are typically glued together with reversed corrugation angles creating complex air and water passages within the matrix of the block.
  • water is introduced in the direction 3 and applied to the top surface of the block of media.
  • the water 3 descends through the matrix, it encounters numerous points within the matrix where the corrugations 6 of adjacent sheets 4 meet. At each of these intersection points, part of the water is directed one way around the intersection, and the remainder of the water the opposite way around the intersection. Since there are numerous such intersections within the matrix, the water is quickly spread evenly throughout the block of media, thereby ensuring even wetting of the surfaces.
  • the distribution of water within the matrix is further enhanced by the property of the media to readily wick water along its surface. Thus any deficiencies in the evenness of water distribution throughout the surfaces of the matrix are readily compensated and corrected.
  • Hot, dry air 5 enters the matrix and also encounters numerous intersections of the adjacent corrugated sheets. At each intersection, the air is divided into two streams ensuring uniform movement of air throughout the matrix. At each of these intersections there is intense interaction between the air and the wetted surfaces due to the rapid and frequent changes in direction of the airflow. This intense interaction results in rapid evaporation of water from the wetted surfaces, thereby humidifying the air and cooling the waters on the wetted surfaces. Since the wetted surfaces are then considerably cooler than the hot dry incoming air, heat exchange will then occur between the air and the wetted surface, thereby cooling the air. Air leaves the matrix block as cooled, humidified air 7 . The heat exchange during this process is also intensified due to the numerous interaction sites at the intersections of corrugations for the same reasons as for intensified evaporation espoused above.
  • FIG. 2 a prior art indirect evaporative cooler construction is shown. Hot, dry air 10 enters the dry air passage 12 , proceeding past the dry air passage boundary 14 . When the construction has been operating for at least a short period, the dry air passage boundary 14 will be cooler than the dry air entering the passage 12 . Heat exchange will occur and the dry air will be progressively cooled as it proceeds down the dry air passage.
  • the incoming hot dry air 10 has been cooled considerably when it leaves the dry air passage 14 at 15 .
  • a flow resistance device 28 is installed in the airflow path thereby causing an increase in air pressure at 15 .
  • This increase in pressure causes some of the now cool, dry air to turn at 26 , and proceed through the wet air passage 16 .
  • the wet air passage contains a wetted media 18 , kept moist by the wicking of water from a water reservoir 22 . Since the air has not yet had any change in its moisture content, evaporation takes place from the wetted media 18 thereby humidifying the air and cooling the water within the wetted media by the same mechanism described above for evaporative media.
  • Air which flows through the flow resistance 28 becomes the delivered air 24 .
  • This air has been cooled without the addition of moisture.
  • the temperature of delivered air 24 can approach the Dew Point of the incoming air.
  • FIG. 3 shows an element of the construction of the current invention.
  • a corrugated wettable media 40 (which may be made using similar materials and manufacturing methods to that of individual sheets 4 of the evaporative media described above) is manufactured with a vapour resistant membrane 42 adhered to one side.
  • the membrane 42 may be a polymer material, although the only essential property is that it resist the flow of water vapour. It may be applied by a number of methods, including hot calendaring of plastic, adhering plastic film or the application of liquid polymers (e.g. paint), or it may be formed by treatment of the surface of the wettable media.
  • the vapour membrane should be kept as thin as practicable for maximum heat transfer.
  • the wettable media 40 should also be as thin as practicable consistent with its requirement to keep the surface wet and wick water to areas not directly wetted in the constructed cooler.
  • the wettable media 40 from which the core elements 44 are made can be manufactured from any material which can be readily wetted. Practical materials include treated, wettable paper, moulded paper fibre slurry, wettable particulate sintered polymers and metallic or polymer films with treated or modified surfaces to promote wetting. Those skilled in the art will be aware of other wettable materials which may be used in the construction of the current invention.
  • the core elements 44 may be produced using a moulding process wherein the shape of the corrugated passages may be modified to further facilitate the optimisation of airflow and heat transfer.
  • the air passages through which exhaust air leaves the core may be shaped to reduce the airflow pressure losses associated with turning the air within the core from the general flow direction to a general exhaust direction.
  • FIG. 4 shows the component part described in FIG. 3 as part of the heat exchanger and evaporation core of the indirect evaporative cooler, the current invention.
  • dry, hot airflows through the dry air passage 50 where the dry air passage is contained between the vapour resistant surfaces 42 of the corrugated sheets 44 .
  • Adjacent wet passages 52 are formed between the wettable media surfaces 40 . Airflows through the dry passages 50 in general counter flow to the wet passages 52 .
  • the angle at which corrugations are set to the general direction of airflow is illustrated by the angle 54 .
  • This angle may be varied over a wide range to optimise the efficiency of heat transfer and resistance to airflow in the core. In general, a shallower angle 54 will result in lower airflow resistance at the penalty of reduced heat transfer efficiency.
  • the angle of corrugation 54 within the core is made relatively shallow, typically in the range 20 degrees to 35 degrees.
  • the shallow angles of corrugation significantly reduce the airflow resistance through the core to the detriment of heat transfer efficiency. Heat transfer efficiency can be regained by extending the overall length of the core. It is found that within the range of angles stated herein, an optimised combination of reduced airflow resistance and increased core length can be achieved for each construction, consistent with adequate heat transfer efficiency.
  • FIG. 5 shows the detail of construction of the components described in FIG. 4 to achieve the flow patterns and directions required.
  • Individual pockets 88 are constructed from two corrugated sheets with vapour resistant membranes 44 .
  • Each corrugated sheet 44 is positioned with the vapour resistant membrane 42 facing the vapour resistant membrane of the adjacent sheet.
  • the sheets are sealed together at the top seal 84 and bottom seal 86 , thus forming a complete pocket with all inner surfaces lined with a vapour resistant membrane 42 .
  • the top seal 84 and bottom seal 86 can be formed by methods including clinching, adhesives, plastics welding or fillers.
  • one of either the top seal or bottom seal can be formed by folding of a double size sheet of media and membrane combination.
  • This construction results in a sealed lined pocket through which hot dry air can flow with no physical contact with the wettable media in passage 80 .
  • FIG. 6 shows the stacking of several of the pockets 88 formed into an indirect cooler core 94 .
  • adjacent wettable media surfaces then form the wet passage 82 .
  • Air flowing through the wet passage 82 has no physical contact with the dry passage 80 , but heat exchange between the wet and dry passages and evaporation within the wet passage can readily take place with the intensity promoted by the corrugated construction.
  • Adjacent pockets 88 need to have the wet passages 82 separated from the dry passages 80 at the end of the core through which hot, dry air enters the core. This is achieved by sealing together adjacent pockets on the wettable media side with a seal line 90 formed by similar methods to the seals at the top and bottom of the pockets ( 84 and 86 ). With this construction, hot, dry air entering from 92 can only enter and flow through the pockets 88 lined with vapour resistant membranes 42 , and must travel all the way through the pocket until it exits at the opposite end 96 .
  • FIG. 7 shows an arrangement in accordance with an embodiment of the eighth aspect of the present invention for wetting of the wettable media in the wet passages in a segmented manner.
  • FIG. 1 divides the core 94 into a number of segments 62 (shown as five segments in FIG. 7 , but a lesser or greater number of segments could be used).
  • Each segment has its own pumping means 60 , its own water reservoir 66 and its own water distribution system 68 .
  • the segment 62 of core 94 with its corrugated construction tends to pass water from the water distributor 68 , through the core 94 to the water reservoir 66 with little mixing of water from adjacent segments. Since, in operation, all segments are circulating water simultaneously, any tendency of the circulating water in a segment to pass through to an adjacent segment is approximately balanced by an equal and opposite tendency for water to come back from that adjacent segment. Thus, for each segment water is circulated relatively independently of each of the adjacent segments.
  • the circulating water temperature in each of the segments can therefore be different, thus providing the temperature gradient necessary to thermal performance of the indirect evaporative cooler, and thus allow the delivered air temperature to approach the Dew Point.
  • This arrangement for water supply to the core has several advantages over the prior art, including removal of the restriction on core height due to the wicking capability of the wettable media; water flow surplus to the requirement for evaporation flushes away any salt concentration due to evaporation and water quality can be easily monitored for salt concentration and diluted before critical concentrations are reached.
  • the segmented water distribution system of FIG. 7 is replaced with a single, general uniform means of distributing water over the entire core, a single water pump means, and a single water reservoir at the bottom of the core 94 .
  • water is applied to the core intermittently.
  • the single water pump 60 is operated for a short period of time sufficient to uniformly wet all of the internal surfaces of the core, and is then turned off.
  • the indirect evaporative cooler is then continued in operation, cooling by means of evaporation of the water contained on its internal surfaces.
  • the wetted surfaces of the core will cool to temperatures similar to the temperatures of an indirect evaporative core wetted by means of wicking as in the prior art.
  • the requirements of thermal gradient within the wetted passages are met, and thermal performance of the core is not significantly degraded.
  • the wetting operation by means of the pump 60 is repeated before the wetted surfaces of the core are dried out, resulting in some degradation of thermal performance during the wetting phase.
  • the core can be wetted in 30-60 seconds, and the indirect cooler operated without further wetting for 15-20 minutes without the wetted surfaces in the core drying out significantly.
  • FIG. 8 shows the complete core 94 with the water distribution system 68 and the airflow system 104 in place.
  • Each water distributor is located within a space 101 kept separate from the water distributor space of adjacent segments by barriers 100 .
  • the sealed spaces 101 and barriers 100 are necessary to prevent airflow exiting from the wet passages of the core thereby causing air in the wet passages to travel all the way along the wet passages.
  • a similar sealing system is necessary to separate the water reservoir 66 from adjacent water reservoirs.
  • Each water reservoir 66 is sealed to the core by barriers 102 thus preventing any air from leaving the wet passages through the water reservoirs.
  • the wet passage space is left open at 106 .
  • the opening 106 allows the now moist, warn air flowing in the wet passages to exhaust from the core 94 .
  • an exhaust opening 106 is provided at both the top and bottom of the core although only the top opening is shown in FIG. 8 .
  • the opening 106 at the bottom of the core is impracticable, satisfactory performance can still be achieved with only the opening 106 at the top with some degradation of thermal performance.
  • the ratio of delivered air to exhaust air is adjusted by means of a flow restriction 108 in the delivered air stream.
  • Closing flow restriction 108 increases the pressure in chamber 109 at the delivery end of the core 94 , thereby increasing the flow of air back through the wet air passages.
US11/792,500 2005-01-11 2006-01-04 Method and Materials for Improving Evaporative Heat Exchangers Abandoned US20080116592A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AU2005900235 2005-01-11
AU2005900235A AU2005900235A0 (en) 2005-01-11 Indirect Evaporative Cooler
PCT/AU2006/000025 WO2006074508A1 (en) 2005-01-11 2006-01-04 Method and materials for improving evaporative heat exchangers

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU2006/000025 A-371-Of-International WO2006074508A1 (en) 2005-01-11 2006-01-04 Method and materials for improving evaporative heat exchangers

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/082,993 Division US8636269B2 (en) 2005-01-11 2011-04-08 Method and materials for improving evaporative heat exchangers

Publications (1)

Publication Number Publication Date
US20080116592A1 true US20080116592A1 (en) 2008-05-22

Family

ID=36677299

Family Applications (2)

Application Number Title Priority Date Filing Date
US11/792,500 Abandoned US20080116592A1 (en) 2005-01-11 2006-01-04 Method and Materials for Improving Evaporative Heat Exchangers
US13/082,993 Active 2026-06-02 US8636269B2 (en) 2005-01-11 2011-04-08 Method and materials for improving evaporative heat exchangers

Family Applications After (1)

Application Number Title Priority Date Filing Date
US13/082,993 Active 2026-06-02 US8636269B2 (en) 2005-01-11 2011-04-08 Method and materials for improving evaporative heat exchangers

Country Status (12)

Country Link
US (2) US20080116592A1 (xx)
EP (1) EP1836046B1 (xx)
CN (1) CN101102888B (xx)
CA (1) CA2594528C (xx)
DE (1) DE06700305T1 (xx)
EG (1) EG25380A (xx)
ES (1) ES2293873T3 (xx)
IL (1) IL183562A0 (xx)
MX (2) MX345482B (xx)
TR (1) TR200704377T1 (xx)
WO (1) WO2006074508A1 (xx)
ZA (1) ZA200711185B (xx)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010020997A1 (en) * 2008-08-18 2010-02-25 Sumaya Hmx Systems Private Limited Direct evaporative heat exchangers, methods of manufacture thereof and applications thereof to multi-stage cooling systems
EP2199726A1 (en) 2008-12-19 2010-06-23 SPX Cooling Technologies Inc. Fill pack assembly and method with bonded sheet pairs
US20100319892A1 (en) * 2008-04-02 2010-12-23 United Technologies Corporation Heat exchanging structure
US9057530B2 (en) * 2010-04-12 2015-06-16 Lg Hausys, Ltd. Humidifying medium having excellent lifespan characteristics and method of manufacturing the same
US9234705B2 (en) 2013-01-03 2016-01-12 F.F. Seeley Nominees Pty Ltd Scaleable capacity indirect evaporative cooler
CN106767051A (zh) * 2017-01-14 2017-05-31 陈祖卫 间接蒸发换热器及其冷却塔
US20170276383A1 (en) * 2014-09-08 2017-09-28 Seeley International Pty Ltd Compact indirect evaporative cooler
JP2021527797A (ja) * 2018-09-25 2021-10-14 ブレントウッド・インダストリーズ・インコーポレイテッドＢｒｅｎｔｗｏｏｄ Ｉｎｄｕｓｔｒｉｅｓ， Ｉｎｃ． クロス波形媒体及び関連方法
WO2023099945A1 (en) * 2021-12-02 2023-06-08 Freshape Sa Multi-stage adsorber device and uses thereof for chilling and/or atmospheric water harvesting

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8783054B2 (en) * 2008-11-13 2014-07-22 F.F. Seeley Nominees Pty. Ltd. Indirect evaporative cooler construction
KR101596831B1 (ko) * 2009-05-29 2016-03-07 엘지전자 주식회사 환기장치 및 환기장치의 제어방법
CN105393069B (zh) * 2013-06-19 2018-09-11 F·F·西里茂米尼有限公司 减小蒸发式冷却装置中的水垢积聚
EP2821744A1 (en) 2013-07-03 2015-01-07 Seeley International Pty Ltd Improved efficiency indirect evaporative cooler
EP2821746A1 (en) 2013-07-03 2015-01-07 Seeley International Pty Ltd Indirect evaporative cooler system with scaleable capacity
US20150048528A1 (en) * 2013-08-19 2015-02-19 Sean Anderson Barton Fill material for direct-contact heat/mass exchangers
CN104165540A (zh) * 2014-07-31 2014-11-26 中化工程沧州冷却技术有限公司 开式循环水气液正交膜板式空冷器
AU2015371632B2 (en) * 2014-12-23 2021-03-25 Evapco, Inc. Bi-directional fill for use in cooling towers
CN104534604B (zh) * 2015-01-23 2017-05-31 天津大学 外置分流结构的逆流板式露点间接蒸发冷却器及通道隔板
IT201700073781A1 (it) * 2017-06-30 2018-12-30 Impresind S R L Impianto di raffrescamento adiabatico con proprietà fotocatalitiche per la depurazione dell’aria
CN109137145A (zh) * 2018-07-16 2019-01-04 绍兴百慧科技有限公司 一种溶液静电纺丝的溶剂回收装置
CN112577140A (zh) * 2020-12-14 2021-03-30 昆山亚冠过滤技术研究院有限公司 一种吊顶式全屋加湿器
IT202100023189A1 (it) * 2021-09-08 2023-03-08 Gigola & Riccardi S P A Pannelli evaporativi con bordi sagomati per l'accoppiamento con pannelli adiacenti o con rispettive strutture di supporto.
US11920823B2 (en) 2022-01-26 2024-03-05 Hog Slat, Inc. Automated evaporative system flush

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3450393A (en) * 1964-07-10 1969-06-17 Carl Georg Munters Gas and liquid contact apparatus
US3542636A (en) * 1965-07-28 1970-11-24 Kurt Wandel Corrugated board
US3664095A (en) * 1968-10-21 1972-05-23 Gunnar C F Asker Exchange packing element
US3983190A (en) * 1974-02-22 1976-09-28 Aktiebolaget Carl Munters Liquid-gas contact apparatus and method for making the same
US4099928A (en) * 1975-07-18 1978-07-11 Aktiebolaget Carl Munters Method of manufacturing a heat exchanger body for recuperative exchangers
US4708832A (en) * 1984-01-20 1987-11-24 Aktiebolaget Carl Munters Contact body
US5124086A (en) * 1989-06-05 1992-06-23 Munters Eurform Gmbh Fill pack for heat and mass transfer
US5167879A (en) * 1989-04-07 1992-12-01 Balcke-Durr Aktiengesellschaft Open-surface component
US20020136885A1 (en) * 1999-10-22 2002-09-26 Yaeger Ronald J. Contact media for evaporative cooler
US6502807B1 (en) * 1998-08-25 2003-01-07 Agam Energy Systems Ltd. Evaporative media unit for cooling tower
US20030047821A1 (en) * 2000-01-18 2003-03-13 Egon Zich Packing for heat-and material-exchange columns
US6581402B2 (en) * 2000-09-27 2003-06-24 Idalex Technologies, Inc. Method and plate apparatus for dew point evaporative cooler
US20040061245A1 (en) * 2002-08-05 2004-04-01 Valeriy Maisotsenko Indirect evaporative cooling mechanism
US6854278B2 (en) * 2001-08-20 2005-02-15 Valeriy Maisotsenko Method of evaporative cooling of a fluid and apparatus therefor
US20060124287A1 (en) * 2002-10-31 2006-06-15 Reinders Johannes Antonius M Heat exchanger and method of manufacture thereof
US20060292349A1 (en) * 2005-05-05 2006-12-28 Seeley Frederic F An evaporative material system and method of manufacture

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE307963B (xx) * 1962-06-27 1969-01-27 Munters C
SE311371B (xx) * 1966-01-26 1969-06-09 Munters C
SE315380C (xx) * 1967-02-06 1975-04-03 Fagerstataket Ab
US3659623A (en) * 1969-12-02 1972-05-02 Baltimore Aircoil Co Inc Water supply system
GB1376308A (en) * 1971-06-04 1974-12-04 Cooling Dev Ltd Art of evaporative cooling
SU979796A1 (ru) 1976-08-17 1982-12-07 Одесский Инженерно-Строительный Институт Установка дл косвенно-испарительного охлаждени воздуха
SE7809801L (sv) * 1978-09-14 1980-03-15 Lagerquist Roy Forangnings- kondensationsforfarande for vermeanleggningar
US4544513A (en) * 1983-04-15 1985-10-01 Arvin Industries, Inc. Combination direct and indirect evaporative media
US4610902A (en) * 1985-09-10 1986-09-09 Manville Service Corporation Roofing membranes and system
RU1778453C (ru) * 1987-05-12 1992-11-30 Одесский Инженерно-Строительный Институт Способ обработки воздуха в помещении
US5212956A (en) * 1991-01-18 1993-05-25 Ari-Tec Marketing, Inc. Method and apparatus for gas cooling
US5315843A (en) * 1992-08-13 1994-05-31 Acma Limited Evaporative air conditioner unit
CN2146686Y (zh) * 1993-01-01 1993-11-17 余宗宁 一种用于喷射泵系统的冷凝器
DE19518270C1 (de) * 1995-05-18 1996-08-22 Fraunhofer Ges Forschung Rutschfester Fußbodenbelag und Verfahren zu seiner Herstellung
US6186223B1 (en) * 1998-08-27 2001-02-13 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
BE1013160A6 (nl) * 1999-11-30 2001-10-02 Offringa Dirk Dooitze Werkwijze en inrichting voor het koelen van lucht.
US6776001B2 (en) * 2000-02-07 2004-08-17 Idalex Technologies, Inc. Method and apparatus for dew point evaporative product cooling
WO2001057459A1 (en) * 2000-02-07 2001-08-09 Idalex Technologies, Inc. Method and apparatus for dew point evaporative product cooling
DE60135308D1 (de) * 2000-02-23 2008-09-25 Schlom Leslie Wärmetauscher zum kühlen und zur verwendung im vorkühler der turbinenluft-aufbereitung
US6497107B2 (en) * 2000-07-27 2002-12-24 Idalex Technologies, Inc. Method and apparatus of indirect-evaporation cooling
KR100409265B1 (ko) * 2001-01-17 2003-12-18 한국과학기술연구원 재생형 증발식 냉방기
US6533253B1 (en) * 2001-03-29 2003-03-18 General Shelters Of Texas, S.B. Ltd. Light attenuating evaporative cooling pad
JP4634659B2 (ja) 2001-07-05 2011-02-16 東罐興業株式会社 段ボールシートおよびこれを用いた包装箱
RU2320947C2 (ru) * 2001-12-12 2008-03-27 Айдалекс Текнолоджиз, Инк. Способ испарительного охлаждения до точки росы и пластинчатое устройство для испарительного охладителя
NL1023471C2 (nl) * 2003-01-23 2004-07-26 Oxycell Holding Bv Dauwpuntskoeler met antimicrobiele voorzieningen.
US7093452B2 (en) * 2004-03-24 2006-08-22 Acma Limited Air conditioner

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3450393A (en) * 1964-07-10 1969-06-17 Carl Georg Munters Gas and liquid contact apparatus
US3542636A (en) * 1965-07-28 1970-11-24 Kurt Wandel Corrugated board
US3664095A (en) * 1968-10-21 1972-05-23 Gunnar C F Asker Exchange packing element
US3983190A (en) * 1974-02-22 1976-09-28 Aktiebolaget Carl Munters Liquid-gas contact apparatus and method for making the same
US4099928A (en) * 1975-07-18 1978-07-11 Aktiebolaget Carl Munters Method of manufacturing a heat exchanger body for recuperative exchangers
US4708832A (en) * 1984-01-20 1987-11-24 Aktiebolaget Carl Munters Contact body
US5167879A (en) * 1989-04-07 1992-12-01 Balcke-Durr Aktiengesellschaft Open-surface component
US5124086A (en) * 1989-06-05 1992-06-23 Munters Eurform Gmbh Fill pack for heat and mass transfer
US6502807B1 (en) * 1998-08-25 2003-01-07 Agam Energy Systems Ltd. Evaporative media unit for cooling tower
US20020136885A1 (en) * 1999-10-22 2002-09-26 Yaeger Ronald J. Contact media for evaporative cooler
US20030047821A1 (en) * 2000-01-18 2003-03-13 Egon Zich Packing for heat-and material-exchange columns
US6581402B2 (en) * 2000-09-27 2003-06-24 Idalex Technologies, Inc. Method and plate apparatus for dew point evaporative cooler
US6854278B2 (en) * 2001-08-20 2005-02-15 Valeriy Maisotsenko Method of evaporative cooling of a fluid and apparatus therefor
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
US20060292349A1 (en) * 2005-05-05 2006-12-28 Seeley Frederic F An evaporative material system and method of manufacture

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100319892A1 (en) * 2008-04-02 2010-12-23 United Technologies Corporation Heat exchanging structure
WO2010020997A1 (en) * 2008-08-18 2010-02-25 Sumaya Hmx Systems Private Limited Direct evaporative heat exchangers, methods of manufacture thereof and applications thereof to multi-stage cooling systems
EP2199726A1 (en) 2008-12-19 2010-06-23 SPX Cooling Technologies Inc. Fill pack assembly and method with bonded sheet pairs
US20100159209A1 (en) * 2008-12-19 2010-06-24 Spx Cooling Technologies, Inc. Fill pack assembly and method with bonded sheet pairs
US8771457B2 (en) * 2008-12-19 2014-07-08 Spx Cooling Technologies, Inc. Fill pack assembly and method with bonded sheet pairs
US9057530B2 (en) * 2010-04-12 2015-06-16 Lg Hausys, Ltd. Humidifying medium having excellent lifespan characteristics and method of manufacturing the same
US9234705B2 (en) 2013-01-03 2016-01-12 F.F. Seeley Nominees Pty Ltd Scaleable capacity indirect evaporative cooler
US20170276383A1 (en) * 2014-09-08 2017-09-28 Seeley International Pty Ltd Compact indirect evaporative cooler
CN106767051A (zh) * 2017-01-14 2017-05-31 陈祖卫 间接蒸发换热器及其冷却塔
JP2021527797A (ja) * 2018-09-25 2021-10-14 ブレントウッド・インダストリーズ・インコーポレイテッドＢｒｅｎｔｗｏｏｄ Ｉｎｄｕｓｔｒｉｅｓ， Ｉｎｃ． クロス波形媒体及び関連方法
WO2023099945A1 (en) * 2021-12-02 2023-06-08 Freshape Sa Multi-stage adsorber device and uses thereof for chilling and/or atmospheric water harvesting

Also Published As

Publication number Publication date
ZA200711185B (en) 2008-10-29
EP1836046A1 (en) 2007-09-26
DE06700305T1 (de) 2008-05-21
ES2293873T3 (es) 2022-04-07
US8636269B2 (en) 2014-01-28
CN101102888B (zh) 2011-01-19
EP1836046A4 (en) 2013-12-11
ES2293873T1 (es) 2008-04-01
IL183562A0 (en) 2007-09-20
EG25380A (en) 2011-12-22
MX345482B (es) 2017-01-18
WO2006074508A1 (en) 2006-07-20
CA2594528C (en) 2014-06-17
EP1836046B1 (en) 2021-12-29
MX2007008386A (es) 2007-11-08
US20110220333A1 (en) 2011-09-15
CN101102888A (zh) 2008-01-09
TR200704377T1 (tr) 2007-08-21
CA2594528A1 (en) 2006-07-20

Similar Documents

Publication Publication Date Title
US8636269B2 (en) Method and materials for improving evaporative heat exchangers
US9140471B2 (en) Indirect evaporative coolers with enhanced heat transfer
US7197887B2 (en) Method and plate apparatus for dew point evaporative cooler
FI57478C (fi) Saett foer kylning av luft
AU2001294882B2 (en) Method and plate apparatus for dew point evaporative cooler
TWI421462B (zh) 高效率熱交換器及除濕機
US20130340449A1 (en) Indirect evaporative cooler using membrane-contained liquid desiccant for dehumidification and flocked surfaces to provide coolant flow
US20030033821A1 (en) Method of evaporative cooling of a fluid and apparatus therefor
US6776001B2 (en) Method and apparatus for dew point evaporative product cooling
KR102060704B1 (ko) 열 교환 매트릭스
CA2173722A1 (en) Intensification of evaporation and heat transfer
RU2320947C2 (ru) Способ испарительного охлаждения до точки росы и пластинчатое устройство для испарительного охладителя
WO2001057459A9 (en) Method and apparatus for dew point evaporative product cooling
AU2006206035B2 (en) Method and materials for improving evaporative heat exchangers
EP3314169B1 (en) Enthalpy-exchanging unit for reducing the influence of surface tension, enthalpy exchanger and method for producing an enthalpy-exchanging unit
AU696886B2 (en) Intensification of evaporation and heat transfer
MXPA96001441A (en) Intensification of evaporation and deca transfer

Legal Events

Date Code Title Description
AS Assignment

Owner name: FF SEELEY NOMINEES PTY LTD, AUSTRALIA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:JAMES, ROBERT WILTON;REEL/FRAME:019433/0995

Effective date: 20070605

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION