US3664928A - Dimpled heat transfer walls for distillation apparatus - Google Patents

Dimpled heat transfer walls for distillation apparatus Download PDF

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US3664928A
US3664928A US885116A US3664928DA US3664928A US 3664928 A US3664928 A US 3664928A US 885116 A US885116 A US 885116A US 3664928D A US3664928D A US 3664928DA US 3664928 A US3664928 A US 3664928A
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Prior art keywords
wall
dimples
heat transfer
inch
thickness
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US885116A
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Ernest Roth Roberts
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Aerojet Rocketdyne Inc
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Aerojet General Corp
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Assigned to MITSUI ENGINEERING AND SHIPBUILDING CO., LTD. reassignment MITSUI ENGINEERING AND SHIPBUILDING CO., LTD. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ENVIROGENICS SYSTEMS COMPANY
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    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • C—CHEMISTRY; METALLURGY
    • C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F1/00—Treatment of water, waste water, or sewage
    • C02F1/02—Treatment of water, waste water, or sewage by heating
    • C02F1/04—Treatment of water, waste water, or sewage by heating by distillation or evaporation
    • C02F1/08—Thin film 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
    • F28D3/00—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, in which the other heat-exchange medium flows in a continuous film, or trickles freely, over the conduits
    • 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
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A20/00—Water conservation; Efficient water supply; Efficient water use
    • Y02A20/124—Water desalination

Definitions

  • a heat transfer wall of a distillation apparatus is dimpled so that a plurality of dimples protrude from the evaporating surface of the heat transfer wall.
  • the dimples are preferrably arranged so that tortuous flow paths are formed between the dimples.
  • a distillation process is one whereby an impure liquid may be purified by vaporizing the liquid and thereafter condensing the vapors to obtain a condensate and a concentrate.
  • fresh water may be separated from saline water in a distillation process by bringing thin films of saline water into contact with a hot surface to vaporize part of the water and separate it from the salt or brine.
  • the vaporized water is then condensed on a cool surface and is recovered as fresh water.
  • a heat transfer wall separates the saline water from a source of heating fluid, such as steam.
  • the rate of vaporization of liquid is dependant, in part, upon the rate at which the heat is transferred to the saline water which in turn is dependant upon the thermal resistance of the heat transfer wall, and the thermal resistance of the layer of saline water on one side of the wall. It is desirable to construct the heat transfer wall from a suitable thermally conductive material, such as copper, and it is desirable to increase the surface area of the wall so that the condensation area and vaporization area are as large as practical.
  • distillation apparatus is provided with dimpled heat transfer walls.
  • the dimpled heat transfer walls enhance the overall effective heat transfer surface of the walls. Furthermore, when liquids are distributed on the dimpled surface in sufficient quantities to flood, most of the liquid flows through the low areas between the dimples so that extremely thin films of water are formed over the dimpled portion due to the surface tension of the flood. It is believed that fluid disposed in thin films over the dimpled portion more readily transfers heat than thicker films of liquid thereby achieving condensation of the heating fluid and evaporization of the saline water at a greater rate than heretofore provided by other types of walls.
  • the dimples may be of any configuration, such as spherical or even teardrop, and may be arranged in any desirable pattern.
  • Another optional and desirable feature of the present invention resides in the use of a shedder or baffle in connection with the dimpled wall to remove excess condensed fluids therefrom.
  • Another optional and desirable feature of the present invention resides in the arrangement of the dimples so that the flow paths of liquid over the wall surface are tortuous in a vertical direction.
  • FIG. 1 is a side view elevation in cutaway cross section of a simplified distillation apparatus in accordance with the present invention
  • FIG. 2 is a side view elevation of a dimpled heat transfer wall for use in the apparatus illustrated in FIG. 1;
  • FIG. 3 is a side view elevation in cutaway cross section of a portion of the dimpled heat transfer wall illustrated in FIG. 2;
  • FIG. 4 is a side view elevation in cutaway cross section of a modification of the wall illustrated in FIG. 2;
  • FIGS. 5A-5C are top view elevations of various dimple configurations for heat transfer walls in accordance with the present invention.
  • FIGS. 6A-6C, 7 and 9 are top view elevations of various dimple patterns for dimpled heat transfer walls in accordance with the present invention.
  • FIG. 8 is a section view taken at line 8-8 in FIG. 7.
  • FIG. 1 there is illustrated a housing 10 separated by walls 11 and 12 into chambers 13, 14 and 15.
  • Inlet conduit 16 is provided through a wall of housing 10 to admit saline water into upper chamber 13.
  • Conduit 17 is provided through a wall of housing 10 to admit a heating fluid, such as steam, into chamber 14.
  • conduit 16 may be connected to any source of heated liquid or vapor, such as a boiler or the exhaust of a turbine.
  • Outlet conduit 18 permits removal of condensed steam from chamber 14, and outlet conduit 22 permits removal of steam vapor from chamber 14.
  • Tubes 19, 19a which may be arranged in a bundle, are constructed of suitable heat transfer material.
  • the tubes pass through chamber 14.
  • Outlet conduits 20 and 21 are associated with chamber 15 to remove concentrate (enriched liquid) and evaporate (vaporized water) from chamber 15, respectively.
  • the bundle of tubes may include any number of tubes, the two tubes being shown for sake of clarity.
  • FIG. 2 there is illustrated a portion of a heat transfer wall 30 in accordance with the presently preferred embodiment of the present invention.
  • Heat transfer wall 30 may be used for tubes 19, 19a in the distillation apparatus illustrated in FIG. 1.
  • Heat transfer wall 30 is constructed of a suitable heat conductive material, such as copper, copper-nickel allow, copperiron alloy, or aluminum-brass alloy, the particular material used being governed by such factors as durability, thermal conductivity in the range of temperatures contemplated, and availability.
  • Wall 30 includes a plurality of dimples 31 which are illustrated in greater detail in FIG. 3.
  • Dimples 31, may, for example, be formed in the configuration of a portion of a sphere.
  • the dimple is generated from a center point 29 and has a radius r to the inside surface of the dimple.
  • the dimple has a diameter d across the inside thereof between opposite points where the dimple joins surface 32 of wall 30.
  • Dimension d will be greater than the radius r and less than 2r.
  • Anglea is the angle between opposite portions of the cone generated by radius r as it traces about the circumference of the dimple.
  • angle a be between 60 and
  • the dimple has an inside height sagitta y from an extension of surface 32 of wall 30.
  • Dimension y is less than or equal to radius r.
  • the thickness of wall 30 in the undimpled portion thereof is represented by dimension t and the thickness of the dimpled portion of wall 30 is represented by dimension t
  • dimension t As will be observed from an examination of FIG. 3, 2,, is less than dimension t
  • the thickness I of the dimple is proportional to the product of the thickness of the wall t and the ratio of the projected area of the surface to the actual area of the dimple. Hence, the thickness 2,; of the wall forming the dimple can be approximated by the following formula;
  • the dimpled heat transfer walls are preferrably arranged so that the vaporizing surface of tubes 19, 19a has dimples protruding therefrom to form noncontinuous or tortuous flow paths thereon in a vertical direction for both the condensate and the vaporizing liquid.
  • the dimples preferrably protrude into tubes 19, 190, but it is to be understood that the dimples may protrude outwardly instead, or a combination of inwardly and outwardly protruding dimples may be used.
  • steam is admitted through conduit 17 and contacts the outside or condensing surface of heat transfer tubes 19, 19a. Some of the steam gives up its latent heat of condensation and condenses on the surface of heat transfer tubes 19, 190 at a temperature T (See FIG. 4). The force of gravity on the condensed steam on the outside of the tubes causes the condensed steam to run down the outside walls of the tubes to be discharged through conduit 22 from chamber 14.
  • Saline water admitted through conduit 16 flows, in a thin film, down the inside wall, or vaporizing surface, of tubes 19, 19a.
  • the temperature of the saline water is at some temperature T below the temperature T of the condensing steam. (See FIG. 4).
  • the saline water is heated and water is vaporized therefrom.
  • the concentrated salt solution or brine continues down the inside of the tube due to the force of gravity and is collected at the bottom of chamber where it is discharged through conduit 20.
  • the heat transfer capabilities of a wall constructed in accordance with the present invention are significantly greater than heretofore achieved in connection with other types of heat transfer walls for distillation apparatus. It is theorized that when a heat transfer wall is provided with corrugations or flutes in the form of continuous parallel or spiraling grooves, there is a continuous laminar flow of fluid through the grooves and the fluid tends to stratify in the groove and act as an insulator between the heat transfer wall and the bulk vapor. Hence, as steam condenses and as saline water is distributed onto continuous groove-type heat transfer walls, the saline water and the condensate flow in laminar films in the grooves to impose a significantly greater heat transfer resistance between the wall and the vapor.
  • the raised portion of the dimple area is covered with a significantly thinner film of fluid because the surface tension of the fluid pulls the fluid into the depressed portions between the dimples causing it to flow in the depressed paths between the dimples.
  • any thick flow occuring on the wall will occur only between the dimples, and the dimples cause a turbulent flow.
  • any collection of fluid is divided by dimples downstream, or below the region of thick film formation. Hence, the fluid flow is maintained turbulent.
  • the condensate accumulates and flows through the lower regions of the surface.
  • the vaporizing fluid forms thin films on the internal raised portion opposite the depressed portion of the dimples and turbulent films form in the depressions opposite the outwardly protruding dimples. If the dimples protrude inwardly, the thin film is formed on the dimple by the vaporizing liquid, and the condensate forms thin films on the raised portion opposite the inside depressed portions. As illustrated in FIG. 4, some dimples may protrude inwardly while some protrude outwardly so that the advantages of both may be obtained.
  • the fluid on the raised portion of the dimples is so thin that heat transfer resistance of the fluid on the dimples is relatively low, thereby permitting rapid release of latent heat of condensation by the condensing vapor and rapid absorption of latent heat of vaporization by the evaporating liquid. Furthermore, due to the thinner wall thickness of the dimpled portions of the wall, the heat transfer resistance of the wall is lower in the dimpled portions than the other portions. Since the wall thinning occurs at the same position as where the film of liquid is the thinnest, the heat transfer resistance is minimized and heat transfer capability is maximized. Furthermore, since the depressed portions of the wall, between the dimples, is tortuous, some condensing fluid will shed and fall free when a sufficient flow is established. Hence, when water vapor is condensed onto the outside surface of tubes 19, 19a, excessive condensate falls free from the wall to expose the wall and lower the heat transfer resistance.
  • condensed steam forms on surface 33 as the layer illustrated in 34.
  • a sufficient quantity of steam has condensed on surface 33 to initiate flooding, it is removed by means of shedder or baffle 39.
  • the saline water preferrably flows between dimples 37 on surface 36 of the wall in a tortuous path to induce turbulent flow.
  • the dimples may be in any desired shape.
  • dimple 40 comprises a substantially spherical portion whereas in FIG. 5B dimple 41 is somewhat teardropped shaped.
  • dimple 42 is in a shape of a two-way teardrop which is substantially semi-spherical with teardropped tongues at opposite ends.
  • the elongated tongues at opposite ends of the two-way teardrop illustrated in FIG. 5C are arranged in line with the force ofgravity along arrow 44.
  • FIGS. 6A, 6B and 6C illustrate various patterns of dimples.
  • the dimples 43 are arranged in a square or rectangular configuration and are separated by pitch distance P. However, the configuration is off-set from a horizontal line by angle 6.
  • the flow of fluid under the influence of gravity is illustrated by arrow 44.
  • FIG. 68 illustrates a different dimple configuration wherein dimples 45 are arranged in a substantially equilateral triangular grid each separated from the next dimple by a pitch distance P. Like the grid illustrated in FIG. 6A, the grid illustrated in FIG. 6B is off-set from the horizon by angle 6.
  • FIG. 6A the dimples 43 are arranged in a square or rectangular configuration and are separated by pitch distance P. However, the configuration is off-set from a horizontal line by angle 6.
  • the flow of fluid under the influence of gravity is illustrated by arrow 44.
  • FIG. 68 illustrates a different dimple configuration wherein dimples 45 are arranged in a substantially equilateral triangular grid
  • FIGS. 6C another triangular grid of dimples 46 is illustrated except that the triangular grid is in a form of an isosceles triangle wherein one side P is shorter than the other two sides P, of the triangle. Like the grids illustrated in FIGS. 6A and 68, it is preferred that the grid be off-set from the horizon by some angle 9.
  • angle 6 may vary between 0 and depending upon the configuration.
  • FIG. 7 illustrated another type of grid pattern wherein the dimples are substantially diamond-shaped dimples 47 having flow paths 48 formed between them.
  • FIG. 8 illustrates a cross section of the dimple pattern illustrated in FIG. 7 wherein flow passages 48 are formed in a substantially diamond grid.
  • FIG. 9 is a top view elevation of another type of diamond-shaped grid of dimples 49 having flow channels disposed 45 from the vertical flow path of fluid.
  • the shortest pitch P of any arrangement of dimples is between about 0.1875 and 1.250 inch.
  • the diameter d across the dimples ordinarily is about 0.125 to 0.750 inch.
  • the inside height y of the dimples is ordinarily between about 0.0084 and 0.3875 inch while the radius r of dimpling is ordinarily between about 0.0625 and 0.3875 inch.
  • Angle a is ordinarily between about 60 and 180.
  • the thickness 2,, of an undimpled wall portion is ordinarily between about 0.020 and 0.650 inch and the thickness t in the dimpled area is ordinarily between about 0.015 and 0.610 inch.
  • the pitch-to-diameter ratio P/d for the smallest pitch in any arrangement is between about 1.06 and 1.66 and the ratio of dimple height to diameter y/d is between about 0.134 and 0.50.
  • Distillation apparatus having heat transfer walls in accordance with the present invention are more effective in operation than heat transfer walls heretofore used in distillation apparatus and they provide effective maintenance-free operation of the distillation apparatus.
  • the heat transfer walls in accordance with the present invention are easily fabricated and used and are durable.
  • a distillation apparatus comprising: a bundle of vertically disposed rigid, metallic heat transfer tubes, each providing an evaporating surface on one side of the metallic tubular wall and a condensing surface on the other side, an array of a plurality of dimples in said tubular wall and protruding thru the outer surface of the wall to form liquid flow paths thereon between said dimples, said dimples being structurally free of contact with adjacent tubes and their dimples and suitable for the formation of thin liquid films thereover and acting to improve the heat transfer capability of the metallic wall with the wall thickness r of the dimpled portions of said heat transfer wall being less than the wall thickness r of the undimpled portions of said heat transfer wall, a first means for supplying a thin film of a liquid undergoing evaporation to the evaporating surface of said wall, and a second means for supplying a heat-transferring vapor to the condensing side of said wall, and wherein the thickness t,, of the undimpled portions of said wall
  • Apparatus according to claim 4 further including a second array of a plurality of second dimples in said wall and protruding thru the inner surface.
  • Apparatus according to claim 1 wherein the inner surface has an array of a second plurality of dimples protruding inwardly therefrom to form second flow paths on said opposite surface between the second dimples.
  • a bundle or rigid, metallic heat transfer tubes each providing an evaporating surface on one side of the tubular wall and a condensing surface on the other side, an array of a plurality of dimples in said tubular wall and protruding thru the outer surface to form liquid flow paths thereon between said dimples, said dimples being structurally free from contact with adjacent tubes and suitable for the formation of thin liquid films thereover and acting to improve the heat transfer capability of the wall with the wall thickness r of the dimpled portions of said heat transfer wall being less than the wall thickness r,, of the undimpled portions of said heat transfer wall and wherein t, is approximately equal to where y is the inside sagitta of the dimples, r is the radius of the dimpling, and K is a constant.
  • a distillation apparatus comprising: a bundle of rigid, metallic heat transfer tubes, each providing an evaporating surface on one side of the tubular walls and a condensing surface on the other side, an array of a plurality of dimples in said tubular wall and protruding thru the exterior surface to form liquid flow paths thereon, said dimples being structurally free from contact with adjacent tubes and suitable for the formation of thin liquid films thereover and acting to improve the heat transfer capability of the wall with the wall thickness t,, of the dimpled portions of said heat transfer wall being less than the wall thickness t,, of the undimpled portions of said heat transfer wall and wherein the smallest pitch P between adjacent dimples is between about 0.1875 and 1.250 inch, the inside sagitta y of each dimple is between about 0.0084 and 0.3875 inch, and the dimpling radius r is between about 0.0625 and 0.3875 inch.
  • a distillation apparatus comprising: a bundle of rigid, metallic heat transfer tubes, each providing an evaporating surface on one side of the tubular wall and a condensing surface on the other side, an array of a plurality of dimples in said tubular wall and protruding radially outwardly from the exterior surface to form liquid flow paths thereon, said dimples being structurally free of contact with adjacent tubes and their dimples and suitable for the formation of thin liquid films thereover and acting to improve the heat transfer capability of the wall with the surface opposite the first surface having an array of a second plurality of dimples protruding radially inwardly therefrom to form second flow paths on said opposite surface between the second dimples and wherein the thickness of r of the dimpled portions of the heat transfer wall is less than the wall thickness t of the undimpled portions of said wall and wherein 1), is approximately equal to l M (1 and where y is the inside sagitta of the dimples, r is the radius of
  • a bundle of rigid, metallic heat transfer tubes providing an evaporating surface on one side of the tubular wall and a condensing surface on the other side, an array of a plurality of dimples in said tubular wall and protruding radially outwardly from the outer surface to form liquid flow paths thereon between said dimples, said dimples being structurally free from contact with adjacent tubes and their dimples and suitable for the formation of thin liquid films thereover and acting to improve the heat transfer capability of the wall and wherein the inner surface has an array of a second plurality of dimples protruding radially inwardly therefrom to form second flow paths on said inner surface between the second dimples and wherein the smallest pitch P between adjacent dimples is between about 0.1875 and 1.250 inch, the inside sagitta y of each dimple is between about 0.0084 and 0.3875 inch, and the dimpling radius r is between about 0.0625 and 0.3875 inch.
  • the interior surface has an array of a second plurality of dimples protruding radially inwardly therefrom to form second flow paths on said interior surface between the second dimples and wherein the thickness t of the undimpled portions of the wall is between about 0.020 and 0.650 inch and the thickness r of the dimpled portion of the wall is between about 0.015 and 0.610 inch, r being less than t IIK 4K

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydrology & Water Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Water Supply & Treatment (AREA)
  • Chemical & Material Sciences (AREA)
  • Organic Chemistry (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Heat Treatment Of Water, Waste Water Or Sewage (AREA)
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US20140100388A1 (en) * 2012-10-05 2014-04-10 Formic Acid-Hydrogen Energy Development Corporation Formic acid producing apparatus and method for producing formic acid using the same
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US4511436A (en) * 1982-05-24 1985-04-16 D.V.T. Buro Fur Anwendung Deutscher Verfahrenstechnik H. Morsy Apparatus for the desalination of sea water
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US5224538A (en) * 1991-11-01 1993-07-06 Jacoby John H Dimpled heat transfer surface and method of making same
US6006823A (en) * 1992-03-31 1999-12-28 Kiknadze; Gennady Iraklievich Streamlined surface
US5950716A (en) * 1992-12-15 1999-09-14 Valeo Engine Cooling Ab Oil cooler
US6428656B1 (en) * 1999-02-18 2002-08-06 Psi-Ets, A North Dakota Partnership Water-cooled distilling apparatus
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US20050006074A1 (en) * 2000-06-17 2005-01-13 Behr Gmbh & Co. Heat exchanger for motor vehicles
US6892806B2 (en) * 2000-06-17 2005-05-17 Behr Gmbh & Co. Heat exchanger for motor vehicles
US7347254B2 (en) 2000-06-17 2008-03-25 Behr Gmbh & Co. Heat exchanger for motor vehicles
US6722134B2 (en) * 2002-09-18 2004-04-20 General Electric Company Linear surface concavity enhancement
US6761031B2 (en) 2002-09-18 2004-07-13 General Electric Company Double wall combustor liner segment with enhanced cooling
US20040079082A1 (en) * 2002-10-24 2004-04-29 Bunker Ronald Scott Combustor liner with inverted turbulators
US7104067B2 (en) 2002-10-24 2006-09-12 General Electric Company Combustor liner with inverted turbulators
US6681578B1 (en) 2002-11-22 2004-01-27 General Electric Company Combustor liner with ring turbulators and related method
US20060099122A1 (en) * 2002-11-25 2006-05-11 Vida Nikolaus M Method and device for generating mixtures of fluids in a boundary layer
US20070193726A1 (en) * 2003-03-19 2007-08-23 Nikolaus Vida Three-dimensional surface structure for reduced friction resistance and improved heat exchange
US20050039899A1 (en) * 2003-07-22 2005-02-24 Viktor Brost Turbulator for heat exchanger
WO2005038271A1 (en) * 2003-10-07 2005-04-28 Nikolaus Vida Surface with reduced particle deposition and reduced ice formation
US6984102B2 (en) 2003-11-19 2006-01-10 General Electric Company Hot gas path component with mesh and turbulated cooling
US20050118023A1 (en) * 2003-11-19 2005-06-02 General Electric Company Hot gas path component with mesh and impingement cooling
US20050106021A1 (en) * 2003-11-19 2005-05-19 General Electric Company Hot gas path component with mesh and dimpled cooling
US20050106020A1 (en) * 2003-11-19 2005-05-19 General Electric Company Hot gas path component with mesh and turbulated cooling
US7186084B2 (en) 2003-11-19 2007-03-06 General Electric Company Hot gas path component with mesh and dimpled cooling
US7182576B2 (en) 2003-11-19 2007-02-27 General Electric Company Hot gas path component with mesh and impingement cooling
US20050211424A1 (en) * 2003-12-01 2005-09-29 Miroslav Podhorsky Duct
US20050241605A1 (en) * 2004-04-29 2005-11-03 Bedwell Donald R Fluid flow surface with indentations
US20060099073A1 (en) * 2004-11-05 2006-05-11 Toufik Djeridane Aspherical dimples for heat transfer surfaces and method
US20060185835A1 (en) * 2005-02-03 2006-08-24 Toyoaki Matsuzaki Heat exchange plate
US20090090423A1 (en) * 2005-03-04 2009-04-09 Gennady Iraklievich Kiknadze Method of forming a current that generates Tornado Like Jets (TLJ) embedded into the flow, and the surface for its implementation
EP1860330A4 (en) * 2005-03-04 2011-02-16 Gennady Iraklievich Kiknadze METHOD FOR GENERATING A SWIVELED RAY IN A CURRENT FLOW AND SURFACE FOR IMPLEMENTING THE PROCESS
US20060231241A1 (en) * 2005-04-18 2006-10-19 Papapanu Steven J Evaporator with aerodynamic first dimples to suppress whistling noise
US20090314475A1 (en) * 2006-09-21 2009-12-24 Halla Climate Control Corp. Heat exchanger
US8128399B1 (en) * 2008-02-22 2012-03-06 Great Southern Flameless, Llc Method and apparatus for controlling gas flow patterns inside a heater chamber and equalizing radiant heat flux to a double fired coil
WO2011013144A3 (en) * 2009-07-29 2011-04-28 Thermax Limited Heat exchanger tube
RU2493445C2 (ru) * 2011-03-10 2013-09-20 НОРМА Германи ГмбХ Трубопровод для текучей среды, оптимизированный в отношении потока
US20150121944A1 (en) * 2011-12-02 2015-05-07 Vkr Holding A/S Phase change material pack
US20130299036A1 (en) * 2012-05-13 2013-11-14 Ronald Lee Loveday Conduit for improved fluid flow and heat transfer
US9845902B2 (en) * 2012-05-13 2017-12-19 InnerGeo LLC Conduit for improved fluid flow and heat transfer
US20140100388A1 (en) * 2012-10-05 2014-04-10 Formic Acid-Hydrogen Energy Development Corporation Formic acid producing apparatus and method for producing formic acid using the same
US20140251587A1 (en) * 2013-03-08 2014-09-11 Danfoss A/S Double dimple pattern heat exchanger
US10113814B2 (en) * 2013-03-08 2018-10-30 Danfoss A/S Double dimple pattern heat exchanger
US10145625B2 (en) 2013-03-08 2018-12-04 Danfoss A/S Dimple pattern gasketed heat exchanger
US20150231946A1 (en) * 2014-02-14 2015-08-20 Unique Fabricating, Inc. Noise attenuated air duct
US11083105B2 (en) * 2017-03-07 2021-08-03 Ihi Corporation Heat radiator including heat radiating acceleration parts with concave and convex portions for an aircraft
RU201460U1 (ru) * 2019-08-07 2020-12-15 Общество с ограниченной ответственностью "Реиннольц ЛАБ" Греющая камера выпарного аппарата
US20250020080A1 (en) * 2023-07-14 2025-01-16 Raytheon Technologies Corporation Bead protrusions heat transfer surface structure of fluid conduits and manifolds

Also Published As

Publication number Publication date
BE760325A (fr) 1971-05-17
GB1290050A (enrdf_load_html_response) 1972-09-20
FR2073720A5 (enrdf_load_html_response) 1971-10-01
DE2053544B2 (de) 1980-11-20
DE2053544A1 (enrdf_load_html_response) 1971-06-16
DE2053544C3 (de) 1981-08-20
IL35480A0 (en) 1970-12-24
ES384271A1 (es) 1973-01-16

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