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WO2018140896A1 - Régénérateur de chaleur rotatif utilisant des supports de plaques parallèles - Google Patents

Régénérateur de chaleur rotatif utilisant des supports de plaques parallèles Download PDF

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Publication number
WO2018140896A1
WO2018140896A1 PCT/US2018/015784 US2018015784W WO2018140896A1 WO 2018140896 A1 WO2018140896 A1 WO 2018140896A1 US 2018015784 W US2018015784 W US 2018015784W WO 2018140896 A1 WO2018140896 A1 WO 2018140896A1
Authority
WO
WIPO (PCT)
Prior art keywords
media
parallel
wheel
regenerator
plate
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.)
Ceased
Application number
PCT/US2018/015784
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English (en)
Inventor
Keith Robinson
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.)
Airxchange Inc
Original Assignee
Airxchange 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 Airxchange Inc filed Critical Airxchange Inc
Publication of WO2018140896A1 publication Critical patent/WO2018140896A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
    • F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
    • F28D19/041—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier with axial flow through the intermediate heat-transfer medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • 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
    • F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
    • F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
    • F28D19/041—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier with axial flow through the intermediate heat-transfer medium
    • F28D19/042—Rotors; Assemblies of heat absorbing masses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • 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
    • F24F2203/104—Heat exchanger 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
    • F24F2203/1048—Geometric details
    • 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
    • F24F2203/1068—Rotary wheel comprising one rotor
    • 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]
    • Y02B30/56—Heat recovery units

Definitions

  • Regenerator heat exchange devices or regenerators are known for effecting the transfer of heat and moisture between two counter-flowing air streams. Such heat exchange devices are used, for example, in heating, ventilation and cooling (HVAC) systems to conserve energy within buildings.
  • HVAC heating, ventilation and cooling
  • One type of regenerator is the rotary air-to-air heat exchanger, which is typically in the form of a rotary heat exchange wheel including a matrix of heat exchange material. When rotated through counter-flowing air streams, the rotating wheel matrix is heated by the air stream with the higher temperature and, in turn, heats the lower temperature air stream. In addition, the rotating wheel may transfer moisture between the counter-flowing air streams.
  • the wheel heat exchange matrix can be made from, or coated with, a moisture adsorbent desiccant material. Examples of such prior art rotary regenerator wheels are shown in Figures 1-2.
  • Figure 1 represents a cross sectional view of a rotary wheel heat exchanger assembly within an enclosure having two flow chambers separated by a divider.
  • the first airflow being directed through the top chamber and through the top half of the rotary wheel
  • the second airfow being directed though the bottom chamber and through the bottom half of the wheel in a counter direction to the first airflow.
  • Figure 2 represents a face on view of the rotary heat exchange assembly showing 100 the top rotary wheel media exposed to the first airflow, and the bottom rotary wheel media exposed to the second airflow in a counter direction to the first airflow.
  • the wheel is shown sealed circumferentially around it's perimeter to the wheel casing, and horizontally to the divider across the diameter of the wheel.
  • Turbulence or turbulent flow is a flow regime in fluid dynamics characterized by chaotic changes in pressure and flow velocity. It is in contrast to a laminar flow regime, which occurs when a fluid flows in parallel layers, with no disruption between those layers.
  • Laminar flow means that along the boundary layer or wall of each layer of heat transfer material, the fluid velocity is non-turbulent. Therefore, this boundary layer fluid does not mix with the fluid flowing away from the boundary layer, and heat transfer from the heat transfer media surface through the fluid is decreased.
  • Turbulent flow means that the velocity of the fluid along boundary layer is high enough for the specific passageway geometry that the boundary layer fluid is mixed with the fluid away from the boundary layer, and heat transfer from the heat transfer media surface through the fluid is increased.
  • a matrix of a rotary heat exchange wheel can include strips of thin film material wound about an axis of the wheel so as to provide a plurality of layers.
  • the layers must have spacing means to create gas passageways extending through the wheel parallel with the axis.
  • the layers are uniformly spaced apart so that the gas passageways are of uniform height throughout their length for greatest efficiency.
  • Transverse elongated embossments have been provided in a plastic strip to form the gas passageways between the layers of the regenerator matrix. Numerous closely spaced transverse embossments are needed to maintain parallelism between layers if used alone to form the passageways.
  • Typical rotary wheel regenerators whether made from plastic, metallic or paper media— are produced using heat transfer media substrate surfaces formed using a corrugated arrangement where every other layer is flat, and every other layer is corrugated.
  • Figure 3-6 depicts examples of prior art configurations of heat exchange media used for regenerators.
  • An example of a prior parallel layer media arrangement having continually corrugated layers positioned between flat layers creating essentially triangular shaped passageways (fluted) is shown in Figure 7.
  • dimples can provide a desirable high aspect ratio between layers, they unfortunately allow appreciable circumferential gas leakage in those situations where there is a high pressure differential between the counter-flowing air streams, thereby reducing the heat exchange effectiveness of the regenerator. Additionally, such dimples are not practically applicable to certain materials such as thin-gauge aluminum or other metallic materials due to, for example, stress concentrations and other structural problems.
  • An aspect of the present disclosure includes a parallel-plate rotary wheel regenerator including: a plurality of plates that are parallel, wherein the plurality of plates includes at least one central plate having a plurality of embossments that touch and physically separate the central plate from two other adjacent plates.
  • the central plate can be made of aluminum
  • One or both of the adjacent plates can be made of aluminum.
  • the aluminum can have a thickness of, e.g., about 1 to about 5 mils.
  • the aluminum can include 1100 series aluminum alloy.
  • the plurality of embossments can include a compressed sine wave shape.
  • the compressed sign wave shape includes features joined at an angle in the range of approximately 5 degrees to approximately 15 degrees.
  • FIG. 1 depicts a side view of an example of a prior art air-to-air heat exchanger including a rotary heat exchange wheel having a regenerator matrix.
  • FIG. 2 depicts an end elevation view of the prior art heat exchanger of Figure 1 as viewed from cutting plane 2— 2.
  • Fig. 3 depicts a perspective view of an embossed strip and an un-embossed strip being wound to form the regenerator matrix of Figure 1.
  • Fig. 4 depicts an enlarged view of a portion of the embossed strip of the prior art regenerator matrix of Figure 1.
  • Fig. 5 depicts an enlarged plan view of a portion of the embossed strip of the prior art regenerator matrix of Figure 1.
  • Fig. 6 depicts a sectional view of the embossed strip of Figure 5 taken along cutting plane 6— 6.
  • Fig. 7 depicts an example of a prior art layered media arrangement having continually corrugated layers positioned between flat layers creating essentially triangular-shaped fluted passageways.
  • Fig. 8 depicts an example of a parallel-plate arrangement according to the present disclosure.
  • FIGs. 9A-9D depict further example of a parallel-plate arrangements according to the present disclosure.
  • This parallel-plate geometry can also provide for media less prone to clogging due to contaminants in the air, and more easily cleaned if clogging does occur.
  • Embodiments of the present disclosure can also provide for manufacturing less media length per wheel to produce a lighter and more cost effective media
  • An aspect of the present disclosure provides a rotary wheel regenerator using polymer, paper, metallic (e.g., aluminum, etc.) or other substrate having a parallel-plate heat transfer surface configuration.
  • the substrate media can be either non-desiccant-coated "sensible” substrate, or "enthalpic” desiccant coated substrate.
  • spirally wound substrate media strips are arranged in a parallel-plate manner using an embossed formation periodically to hold the strips in a parallel-plate configuration.
  • the strip layers may be arranged so that every other layer has embossments and each alternating layer may be flat without embossments.
  • embossed standoffs or embossments— are not intended to be aligned with one another periodically, and a parallel-plate arrangement is achieved, rather than a typical triangular shaped arrangement.
  • the benefits of a parallel-plate geometry media over other typically used geometries include higher thermal performance resulting in increased energy savings, lower pressure drop to reduce fan power energy required and reduce structural load on the wheel frame, less clogging due to contaminates resulting in better long term savings, longer life, and less frequent cleaning, less material required to manufacture for lower cost and weight.
  • FIG. 8 depicts an example of a parallel-plate substrate media configuration 800 according to the present disclosure.
  • a rotary wheel shown as 801
  • Four such plates 804(1)- 804(4) are shown, but any practical number may be used.
  • the parallel plates 804(l)-804(4) are spaced apart creating parallel flow passageways 805(l)-805(3) to allow airflow through the rotary wheel in the direction of wheel depth.
  • the resultant parallel plates shown as curved in this application
  • the resultant parallel-plate passageways are not divided into small triangular, square, or round finite small passageways.
  • Figures 9A-9D depict further examples of a parallel-plate plate substrate media configurations 900A-900D according to the present disclosure.
  • Figure 9A depicts a section 900A of a concentric circular rotary wheel media having parallel and concentric plates that are not wound per se but assembled adjacent to one another in a nested circular fashion as shown.
  • Figure 9B depicts a section 900B of a concentric square rotary wheel media (fitting within the shape of a rotary wheel) having parallel and concentric plates that are not wound per se but assembled adjacent to one another in a nested arrangement of squares (or rhomboids or rectangles) as shown.
  • Figure 9C depicts a section 900C of a wheel media having parallel plates that are in a stacked flat and parallel arrangement as shown.
  • Figure 9D represents a section 900D of a spirally wound rotary wheel media showing three layers or plates of a parallel-plate configuration with embossments.
  • the section 900D includes a central layer 902 and two adjacent layers 904(1) -904(2).
  • the adjacent layers or plates 904(1)- 904(2) are shown to be flat layers, while the middle or central layer or plate 902 is show to have periodically spaced standoffs, or embossments, 910(1)-910(3) to create the parallel-plate configuration.
  • the embossments 910(1)-910(3) touch and physically separate the central plate 902 from two other adjacent plates 904(l)-904(2).
  • the periodic spacing of the standoff embossments (such a 910A-910C) is not critical to the increased performance of parallel- plate designs described herein, as long as it is frequent enough to keep the layers from deforming or sagging thereby losing parallel configuration, and not too frequent to essentially create a square finite flute configuration rather than a parallel-plate configuration.
  • the spacing between the embossments thus, may be dependent upon the material(s) used for the layers or plates and the thickness of the layers or plates, and/or the desired height of the embossments.
  • the embossments are preferably the full width of the matrix for leakage mitigation purposes, whatever the width is (e.g., 1" to 12").
  • the embossments can be uniform across their length, e.g., with the profile as shown in Figure 9D.
  • the crimped embossment can have a compressed sign-wave-like shape, in exemplary embodiments.
  • Such a shape offers the advantages of centering the middle formed layer between flat layers uniformly and creating a structural support between the surface of one flat layer though the middle formed layer to the surface of the next flat layer.
  • This sign wave shaped embossment helps to keep the wheel media from collapsing as it is spirally wound from a small diameter to large diameter while maintaining a uniform parallel- plate media configuration.
  • Such an embossment can be made by any suitable method or technique.
  • embossments may be made by crimping or stamping or forming the media as required.
  • One method of creating the sine wave formation would be to create a stamping die of the profile desired (e.g., a machined die set), and stamp that formation into a media layer at the desired frequency or spacing by drawing the layer strip through the die, and actuating the die at a rate coincidental to the rate of the strip to create the formations at the desired periodic spacing.
  • Such embossments may, in exemplary embodiments, have features joined at an angle in the range of approximately 5 degrees to approximately 15 degrees.
  • the layers or plates are made of 1100 series alumni having a uniform thickness in the range of between about 1 mil (0.001 inch) and about 5 mil (0.005 inch), e.g., 1 mil, 2 mil, 3 mil, 4 mil, or 5 mil.
  • 1 mil, 2 mil, 3 mil, 4 mil, or 5 mil can be used.
  • embossments By employing embossments with such a configuration, a number of advantages are afforded. These advantages include, but are not limited to, the ability to use thin gauge metal for the matrix media, e.g., aluminum, aluminum alloys, stainless steel alloys (e.g., 300 series including 304 and 310), titanium, titanium alloys, and the like.
  • RER recovery efficiency ratio
  • Embodiments of the present disclosure can provide a much lower recovery efficiency ratio (RER) compared with prior art design.
  • the RER a well-known parameter in the HVAC energy recovery field, is defined as energy recovered over the energy expended in the recovery.
  • Embodiments of the present disclosure can improve either or both of the numerator and denominator of the RER.
  • the challenge in designing heat transfer media passageway geometry is the tradeoff between having more heat transfer media surface area for better thermal performance and less heat transfer media surface area for lower friction, i.e. pressure drop through the regenerator.
  • the laminar flow ratio (f/j) is a parameter that describes the friction to heat transfer media geometry for various passageway configurations.
  • the letter f stands for the friction coefficient, and the letter j for the Coburn heat transfer factor. It has been shown that as the f/j ratio becomes smaller, the tradeoff between friction loss and heat transfer capability is optimized.
  • f/j ratios have been calculated to support the idea that parallel-plate heat transfer media geometry has a higher performing configuration than round ducts, square ducts, triangular ducts, or random packed ducts.
  • the f/j factors can be calculated for various media geometries using the following formula:
  • Pr designates the Prandtl number for gas (0.7 for most gasses).
  • (f * Re) is the resultant of multiplying the friction factor (f) of the geometry and the Reynolds number (Re).
  • Nu is the Nusselt number resulting from the given geometry.
  • Nu and f * Re values e.g., from Kays and London Compact Heat Exchangers - third edition 1984, p. 120
  • f/j factors can be calculated for specific media geometries, giving f/j factors of 4.79 for triangular passageways, 4.23 for square ducts, 3.88 for round ducts, and 2.8 for parallel-plate ducts. This reveals that the parallel-plate geometry under laminar flow conditions exhibits superior performance (tradeoff between pressure loss and thermal transfer) per unit of media face area.
  • any dust or dirt particles in the space caught in the HVAC system will pass through the wheel, further dirtying and restricting the passageways.
  • the wheel media passageways become restricted due to clogging, thermal performance is degraded and pressure drop through the wheel is increased resulting in lower energy savings, increased operational costs, higher structural loads to the wheel frame, and potentially decreased supply of ventilation air through the wheel.
  • the shape of the parallel plate geometry does not necessarily have tight corners to collect dust and dirt, and the length of the passageway is typically shorter, e.g., between 1 inches up to 6 inches depending on the design and size of the wheel.
  • the parallel- plate media can flex since it lacks the high structural rigidity of the corrugated, triangular shape. This flexing can allow contaminants to more readily pass through the media rather than collect within a rigid finite passageway.
  • the velocity profile across the wheel and within each parallel passageway is more uniform than the corrugated triangular fluted media at each diameter (due to the lack of tight passageways and increased area for open flow per diameter), helping prevent lower flow velocities that would allow a build-up of contaminants and thus flow blockages.
  • the flexible matrix geometry allows slight motion during operation which will also help in keeping potentially clogging particles moving through the short passageway.
  • the parallel-plate design prevents the amount of blockage inherent to a corrugated design, the pressure drop is not expected to rise during use as it would in its corrugated counterpart.
  • the parallel plate not only decreases the potential for clogging of the media and improves the clean-ability of the wheel, but also reduces the overall pressure drop through the wheel over time. Due to the potential of contaminants and other non-air substances flowing through the passageways of the wheel, the parallel-plate design is better suited than the fluted or corrugated design to applications with any possibility of contaminants that may foul the wheel.
  • a rotary wheel regenerator with parallel plate media geometry design can provide one or more of the following advantages:
  • one method of creating parallel plate rotary wheel media is to create an intermediate layer, between two flat layers, having embossed formations sufficiently periodically spaced intended to stand the layers apart thus creating parallel plates.
  • Variations to this method could include a variety of other methods of spacing the layers apart including inserting periodically small pins into a layer or layers, perpendicular to the face of the layers, to hold the layers uniformly apart, applying a spot of glue or polymer material of the appropriate thickness periodically to hold the layers uniformly apart, fastening thin spacers periodically extending across the wheel width from wheel face to wheel face to hold the layers uniformly apart, piercing small formations (e.g., like so-called "chads" on ballot cards) into the surface of each flat layer to create standoffs to hold the layers uniformly apart.
  • small formations e.g., like so-called "chads" on ballot cards
  • Another method of holding the parallel plates apart could be to install a series of thin rods or wires from the outer diameter of the wheel rim, through all of the layers, and into the hub of the wheel, perpendicular to the wheel axis.
  • Each layer in this case all flat layers
  • Each layer would be pierced by the rods and held in their appropriate positions to create uniform spacings and passageways between the flat layers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un régénérateur à roue rotative qui utilise un substrat en polymère, papier, métal ou autre ayant une configuration de surface ou de support de transfert de chaleur à plaques parallèles. Le support de substrat peut être soit un substrat "sensible" non revêtu de déshydratant, soit un substrat revêtu d'un déshydratant "enthalpique". Selon des modes de réalisation donnés à titre d'exemple, les bandes de support de substrat enroulées en spirale sont agencées sous forme de plaques parallèles à l'aide d'une formation gaufrée périodiquement pour maintenir les bandes dans une configuration de plaques parallèles. Les couches de bande sont agencées de telle sorte qu'une couche est gaufrée et qu'une autre couche est sans gaufrure. Les entretoises gaufrées n'ont pas besoin d'être alignées les unes sur les autres périodiquement, et un agencement de plaques parallèles est obtenu.
PCT/US2018/015784 2017-01-27 2018-01-29 Régénérateur de chaleur rotatif utilisant des supports de plaques parallèles Ceased WO2018140896A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201762451288P 2017-01-27 2017-01-27
US62/451,288 2017-01-27

Publications (1)

Publication Number Publication Date
WO2018140896A1 true WO2018140896A1 (fr) 2018-08-02

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WO (1) WO2018140896A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE543027C2 (en) * 2017-10-13 2020-09-29 Flexit Sverige Ab Rotating heat exchanger with improved heat transfer capacity
US12061050B2 (en) * 2018-11-07 2024-08-13 Carrier Corporation Heat recovery ventilator
CN112050449A (zh) * 2020-07-20 2020-12-08 中国舰船研究设计中心 一种船用全热回收节能型空调器

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US4093435A (en) * 1973-11-23 1978-06-06 Wing Industries Inc. Total heat energy exchangers
WO2002029325A1 (fr) * 2000-10-04 2002-04-11 Airxchange, Inc. Matrice de regenerateur avec bossages pour echangeur de chaleur
JP2002155332A (ja) * 2000-11-17 2002-05-31 Sumitomo Light Metal Ind Ltd 成形性及びろう付け性に優れた熱交換器用アルミニウム合金フィン材
JP3583057B2 (ja) * 2000-06-06 2004-10-27 大阪ガスエンジニアリング株式会社 ロータリー式熱交換器
US20060254756A1 (en) * 2003-03-03 2006-11-16 Jack Kaser Heat exchanger having powder coated elements

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US3155153A (en) * 1959-07-10 1964-11-03 Lizenzia A G Rotatable body for transfer of moisture or/and heat
US3664095A (en) * 1968-10-21 1972-05-23 Gunnar C F Asker Exchange packing element
US3810509A (en) * 1971-10-15 1974-05-14 Union Carbide Corp Cross flow heat exchanger
US3910344A (en) * 1974-03-27 1975-10-07 Gen Motors Corp Regenerator matrix
US4744410A (en) * 1987-02-24 1988-05-17 The Air Preheater Company, Inc. Heat transfer element assembly
CA2195282C (fr) * 1997-01-16 2004-05-11 Frederic Lagace Echangeur thermique autonome pour le transfert air-air de vapeur d'eau et d'enthalpie
US6029462A (en) * 1997-09-09 2000-02-29 Denniston; James G. T. Desiccant air conditioning for a motorized vehicle
AU739021B2 (en) * 1998-01-06 2001-10-04 Airxchange, Inc. Rotary heat exchange wheel
EP2482955B1 (fr) * 2009-10-02 2013-08-28 Donaldson Company, Inc. Cartouche filtrante avec dérive centrale, collecteurs de poussière et procédés

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4093435A (en) * 1973-11-23 1978-06-06 Wing Industries Inc. Total heat energy exchangers
JP3583057B2 (ja) * 2000-06-06 2004-10-27 大阪ガスエンジニアリング株式会社 ロータリー式熱交換器
WO2002029325A1 (fr) * 2000-10-04 2002-04-11 Airxchange, Inc. Matrice de regenerateur avec bossages pour echangeur de chaleur
JP2002155332A (ja) * 2000-11-17 2002-05-31 Sumitomo Light Metal Ind Ltd 成形性及びろう付け性に優れた熱交換器用アルミニウム合金フィン材
US20060254756A1 (en) * 2003-03-03 2006-11-16 Jack Kaser Heat exchanger having powder coated elements

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