US3385356A - Heat exchanger with improved extended surface - Google Patents

Heat exchanger with improved extended surface Download PDF

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US3385356A
US3385356A US639544A US63954467A US3385356A US 3385356 A US3385356 A US 3385356A US 639544 A US639544 A US 639544A US 63954467 A US63954467 A US 63954467A US 3385356 A US3385356 A US 3385356A
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extended surface
elements
path
thermal conductivity
surface elements
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US639544A
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Dalin David
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Individual
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Priority to US473366D priority Critical patent/USB473366I5/en
Application filed by Individual filed Critical Individual
Priority to US639544A priority patent/US3385356A/en
Priority to NL6802663A priority patent/NL6802663A/xx
Priority to DE19681751241 priority patent/DE1751241A1/de
Priority to CH627168A priority patent/CH508188A/de
Priority to GB21038/68A priority patent/GB1170553A/en
Priority to FR152492A priority patent/FR95406E/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • F24H1/282—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes with flue gas passages built-up by coaxial water mantles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K20/00—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating
    • B23K20/22—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating taking account of the properties of the materials to be welded
    • B23K20/227—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating taking account of the properties of the materials to be welded with ferrous layer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • F24H3/10—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by plates
    • F24H3/105—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by plates using fluid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/0005—Details for water heaters
    • F24H9/001—Guiding means
    • F24H9/0026—Guiding means in combustion gas channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/124—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and being formed of pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • 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
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49377—Tube with heat transfer means
    • Y10T29/49378—Finned tube

Definitions

  • ABSTRACT OF THE DISCLOSURE A heat exchanger for effecting indirect transfer of heat between two media separated by a metal wall, one of which media flows along a path partially defined by said wall, the wall having extended surface elements fixed thereon and projecting into the path of the fiowing medium, so that the temperature difference between the media diminishes along said path of flow.
  • All of the extended surface elements have the same external surface area and for a substantial part of the length of said path the extended surface elements are bimetallic in cross section and consist of both high and low conductivity metal.
  • the thermal conductivity of the elements is progressively less along said path in the direction of the downward gradient of the temperature difference, the reduction in thermal conductivity of the bimetallic elements being determined by the amount of high conductivity metal they contain.
  • Patent No. 2,469,- 635 the ability of a fluid medium to effect heat transfer between itself and a surface of a solid exposed to it, which ability is known as surface conductance, is not the same for all fluid media.
  • surface conductance of steam or water, i.e. boiler fluid is at least one hundred times greater than that of combustion gases, and at 50 C. and with both media flowing at the same velocity, the surface conductance of oil is only nine percent (9%) that of water.
  • the partition wall separating the two media must have extended surface elements fixed to it and extending into the lower surface conductance medium, and preferably these extended surface elements are metal rods or wires, either round or substantially rectangular in cross section, but solidly welded at one end to the partition wall and projecting endwise therefrom.
  • the copper was encased in a steel sheath or a steel core extended through the copper element.
  • the extended surface elements located in those portions of the system where the difference in the temperatures of the two media is greatest and where the maximum rate of heat transfer naturally occurs have the greatest amount of high conductivity metal, while the elements in those portions of the system where minimum rates of heat transfer will occur, have the least amount of high conductivity metal and in fact may be formed entirely of iron or other suitable inexpensive low conductivity metal. This assures the lowest possible initial cost of the equipment without any sacrifice of operating efiiciency.
  • iron can withstand high concentrations of sulphuric acid much better than copper, whereas copper is much more resistant to low concentrations of sulphuric acid. Therefore, by using iron for the elements in that part of the system where temperature is lowest and maximum condensation takes place, as in the downstream end portion of the gas pass, and restricting the use of copper, either solid or steel clad, to the portion of the system where the temperature is greatest, a two fold advantage is gained-cost reduction and longer life for the extended surface.
  • FIGURE 1 is a vertical sectional view through a steam or hot water boiler equipped with extended surface in accordance with this invention
  • FIGURE 2 is a cross sectional view through FIG- URE 1 on the plane of the line 22;
  • FIGURE 3 is a horizontal cross sectional view through a hot air furnace, also equipped with the extended surface of this invention.
  • FIGURE 4 is a vertical sectional view through the hot air furnace on the plane of the line 4-4 in FIG- URE 3;
  • FIGURE 5 is a vertical sectional view through FIG- URE 3 on the planes indicated by the lines 55;
  • FIGURE 6 is a horizontal sectional view through a water heater especially adapted to utilize waste heat, showing another form of extended surface embodying this invention
  • FIGURE 7 is a longitudinal sectional view through FIGURE 6 on the plane of the line 77;
  • FIGURE 8 is a fragmentary sectional view through a portion of a heat exchanger equipped with one form of the extended surface elements of this invention.
  • FIGURE 9 is a sectional view through FIGURE 8 on the plane of the line 9-9;
  • FIGURES 10 and 11 are views similar to FIGURE 8 illustrating other forms of extended surface elements embodying this invention.
  • FIGURE 12 illustrates still another form of extended surface embodying this invention
  • FIGURE 13 is a view illustrating how the extended surface of FIGURE 12 may be produced
  • FIGURE 14 is a sectional view through FIGURE 12 on the plane of the line 14-14;
  • FIGURE 15 is a graph portraying the thermal conductivity of bimetallic extended surface elements having different proportions of high and low conductivity metal
  • FIGURE 16 is a sectional view through several successive portions of a partition wall equipped with bimetallic extended surface elements of progressively lower thermal conductivity in accordance with this invention
  • FIGURE 17 is a plan view of the structure shown in FIGURE 16;
  • FIGURES 18 and 19 are diagrammatic views illustrating one step in the production of the bimetallic elements shown in FIGURES 16 and 17;
  • FIGURES 20, 21, 22 and 23 are cross sectional views through the extended surface elements of FIGURE 16, as indicated thereon by the lines 20-26; 21-21, 22-22 and 23-23.
  • the numeral 5 designates generally a steam boiler or hot water generator having a combustion chamber 6 in the lower portion of an inner shell 7, which as shown may be fired by an oil burner.
  • An outer shell 8 surrounds the inner shell and cooperates therewith to provide a water space 9 provided with an inlet 10 and an outlet 11.
  • the outer shell is jacketed as at 12 to provide heat insulation and, as seen in FIGURE 2, the entire structure is cylindrical in cross section.
  • the alpha value of water is about one hundred times greater than that of a gaseous medium, such as the hot flue gases flowing across the walls of the drum 13, the cylindrical wall. of the water drum has extended surface elements 18 fixed thereto and projecting therefrom substantially across the entire annular space 16.
  • the size, shape and distribution of; these extended surface elements 18 is such that the ability of the elements to effect heat transfer between themselves and the combustion gases in contact therewith is substantially uniform throughout the entire length of the path of these gases as they flow upwardly across the cylindrical wall of the water drum.
  • the heat exchange between the combustion gases or flowing fluid medium in contact with the extended surface elements is abstraction of heat from the gases and transfer thereof to the water in the drum 13.
  • the individual extended surface elements must have the ability to conduct the heat which they abstract, to the wall of the drum 13 and through it to the water in the drum. Whether or not the elements possess this needed capability depends upon the thermal conductivity, i.e. the lambda value, of the metal of which they are made. The need for using metal having a sufficiently high lambda value so as to assure the needed conductivity has been understood for years and is fully discussed in the Dalin et al. Patent No.
  • the elements 18 in the boiler 5 are divided into four groups designated 1, II, III and IV, as indicated in FIGURE 1.
  • the only difference between these several groups of elements is in their thermal conductivity, and this difference may be obtained in a number of ways, some of which are shown in FIGURES 8 to 11, inclusive, in all of which the amount of high conductivity metal used is greatest in Group I and progressively less in the succeeding groups.
  • the desired gradation in thermal conductivity in the succeeding groups may be obtained as shown in FIG- URE 8, wherein all of the extended surface elements are bimetallic and consist of a high conductivity core 19 encased in a sheath 20 of low conductivity metal, as in the Dalin Patent No. 2,719,354.
  • the core is formed of copper, though it could be made of aluminum, while the sheath is formed of mild steel.
  • the proportions of high to low conductivity metal may be 85 to 15. This gives the elements ample thermal conductivity to successfully cope with the highest temperatures attained by the combustion gases flowing over the extended surface.
  • the percentage of high conductivity metal to low conductivity metal present in the elements is reduced stepwise so that the thermal conductivity of the elements approximately matches the declining temperature gradient of the combustion gases as the heat thereof is abstracted therefrom.
  • the thermal conductivity, that is, the lambda value, of the elements is suflicient to conduct all of the heat abstracted thereby to the wall of the water drum, the performance requirements are met; but to gain the advantages of this invention the lambda value of the elements should not greatly exceed the performance requirements.
  • Example I on this chart depicts the situation for extended surface elements having a 5 mm. outside diameter, a copper core of 4.5 mm. diameter, and a 0.25 mm. thick iron sheath.
  • the copper content is 82% and the iron content 18% of the whole; and as shown in the chart, the lambda value of the element is 283 K. caL/ m./h. C.
  • Example II the proportions of copper to iron are reversed from what they are in Example I.
  • the lambda value is 94.
  • the lambda value can be readily determined from the chart.
  • FIGURE 10 which, incidentally, includes a fifth group V.
  • the elements of Group I the highest conductivity group
  • the elements of Group V are of solid iron, and hence have the lowest thermal conductivity
  • the elements of the intervening groups II, III and IV have iron cores of stepwise increased diameter Within copper sheaths with correspondingly thinner walls.
  • iron for the elements that are located in that part of the system Where the temperature differential between the two media is least and copper where the temperature differential is greatest, is especially advantageous in the case of the convection surfaces of steam boilers where the extended surface elements are swept by sulphur containing flue gases, for as noted hereinbefore, iron is better able than copper to withstand the higher concentrations of sulphuric acid resulting from the greater condensation that takes place in the downstream portion of the gas pass, whereas copper is more resistant to the lower concentrations of sulphuric acid in the higher temperature portion of the gas pass.
  • FIGURE 11 Another way of gaining the desired stepwise reduction in amount of high conductivity metal used for the extended surface elements is illustrated in FIGURE 11, wherein the elements of Group I are of solid copper and all the rest are tubular with stepwise reduced wall thicknesses.
  • the use of such hollow elements is particularly advantageous when it is desired to have a large heat collecting or dissipating surface exposed to one medium and a minimum amount of material for conveying the heat to or from the other medium.
  • FIGURES 8 to 11, inclusive are merely illustrative and that in actual practice there are many more extended surface elements arranged or distributed along the path of the medium flowing thereover.
  • the numeral 22 designates the wall separating the two media between which heat exchange is to take place, which in the case of the boiler 5 in FIGURES l and 2, is the Wall of the water drum 13; and that the numeral 23 designates a part of the means which confines the flowing media to a defined path across which the extended surface elements project.
  • the extended surface elements on both sides of the partition walls are divided into the four groups I, II, III and IV, heretofore described, with the Group I elements located in the hottest portions of the zones to which the heating medium and the medium to be heated are confined.
  • the air chamber is divided into several successively communicating passages by vertical walls 31 and 32 and horizontal walls 33 through which the air to be heated flows from an inlet 34 to an outlet 35, the arrangement being such that the air which abstracts heat from the extended surface elements 29 and 3t) flows downward, and hence countercurrent to the rising combustion gases.
  • duct 35 In the duct 35 is a group or bank of serpentine tubes 36, the ends of each of which are connected with inlet and outlet headers 37 and 38 so that water, boiler fluid or the like can be circulated through the tubes to be heated by the flue gases flowing through the duct 35.
  • the serpentine tubes 36 have extended surface elements as fixed thereto as in FIGURES l and 2 of the Dalin patent No. 2,584.189; and since the fluid heating medium flowing through the duct successively engages the several legs of each tube, the extended surface elements on the legs of the tubes first contacted by the flowing medium have greater thermal conductivity than those last con tacted by the flowing medium. This condition is depicted by Groups IV and V in FIGURE 6. Obviously, of course, in this unit the walls of the serpentine tubes 36 separate the two media from one another, and the medium to be heated flows through the tubes.
  • the extended surface elements have been rods or wires, but the invention is not limited to that form of extended surface.
  • the extended surface might take the form of flat fingers 45, as shown in FIGURES 12, 13 and 14-. These fingers may be formed by shearing strip stock 46 into two comb-like sections, as shown in FIG- URE 13, and to give the fingers their desired bimetallic formation, the strip can be a flattened tube with a core 47 of copper and :a mild steel sheath 48.
  • This form of extended surface is especially suitable for use on tubes, since it combines the more effective finger-like shape with ease of attachment to the tubes, since the combs can be spirally wrapped around the tubes with their continuous back edges in contact with the tubes to which they are, of course, secured in good heat transfer relation.
  • FIGURES 16 to 23, inclusive Still another way of providing extended surface elements with tailor-made thermal conductivity is illustrated in FIGURES 16 to 23, inclusive.
  • the individual elements 50 are cut from lengths of bimetallic bands or ribbons produced in the manner diagrammatically illustrated in FIGURES l8 and 19.
  • a bimetallic wire 51 that is round in cross section and has a core 52 of copper within a steel sheath 53, is flattened by passage between a pair of rolls 54, into a band or ribbon 55.
  • the band or ribbon 55 has flat sides and rounded parallel edges. To provide bands or ribbons of the desired thickness, the band or ribbon 55 is run through more closely spaced rolls, one pair of which, designated 54, is shown in FIGURE 19, the band or ribbon 55 which issues from this pair of rolls being thinner than the band or ribbon 55.
  • a heat exchanger having wall means separating a flowing medium from another medium and coacting with other wall means to define a path of flow for the flowing medium, and having extended surface elements fixed to said wall means and projecting into said path of the flowing medium, said heat exchanger being characterized in that:
  • the extended surface elements are of such size and shape and so distributed along said path that as the flowing medium wipes across them the heat transfer which takes place between the extended surface elements and the flowing medium effects a reduction in the difference in temperature between the media, which difference diminishes progressively from one end of said path to the other;
  • thermal conductivity of the extended surface elements substantially matches the downward gradient of the difference in temperature of said media along said path.
  • a heat exchanger having wall means separating a flowing medium from another medium and coacting with other wall means to define a path of flow for the flowing medium, and having extended surface elements fixed to said wall means and projecting into said path of the flowing medium, said heat exchanger being characterized in that:
  • the extended surface elements are of such size and shape and so distributed along said path that as the flowing medium wipes across them the heat transfer which takes place between the extended surface elements and the flowing medium effects a reduction in the difference in temperature between the media, which difference diminishes progressively from one end of said path to the other;
  • thermo conductivity of the bimetallic extended surface elements substantially matches the downward gradient of the difference in temperature of said media in contact therewith;
  • a heat exchanger having wall means separating a flowing medium from another medium and coacting with other wall means to define a path of flow for the flowing medium, and having extended surface elements fixed to said wall means and projecting into said path of the flowing medium, said heat exchanger being characterized in that:
  • the extended surface elements are of such size and shape and so distributed along said path that as the flowing medium wipes across them the heat transfer whch takes place between the extended surface elements and the flowing medium effects a reduction in the difference in temperature between the media, which difference diminishes progressively from one end of said path to the other;
  • thermal conductivity of the extended surface elements substantially matches the downward gradient of the difference in temperature of said media along said path.
  • a heat exchanger having wall means separating a hot gaseous flowing medium from another medium to be heated, and defining a path of flow for the hot medium having upstream and downstream ends, the wall means having extended surface elements fixed thereto and projecting into the hot gaseous flowing medium to cooperate with the wall means in effecting indirect heat exchange between the media, said heat exchanger being characterized in that:
  • the extended surface elements are divided into groups arranged in succession along said path, with each group comprising a series of banks of elements spaced along said path;
  • a heat exchanger having wall means separating a hot gaseous flowing medium from another medium to be heated, and defining a path of flow for the hot medium having upstream and downstream ends, the wall means having extended surface elements fixed thereto and projecting into the hot gaseous flowing medium to cooperate with the wall means in effecting indirect heat exchange between the media, said heat exchanger being characterized in that:
  • thermal conductivity of the extended surface elements substantially matches the downward gradient of the difference in temperature of the media along said path.
  • a heat exchanger having wall means separating a flowing medium from another medium and coacting with other wall means to define a path of flow for the flowing medium, and having extended surface elements fixed to said wall means and projecting into said path of the longing medium, said heat exchanger being characterized in t at:
  • the extended surface elements are of such size and shape and so distributed along said path that as the flowing medium Wipes across them the heat transfer which takes place between the extended surface elements and the flowing medium effects a reduction in the difference in temperature between the media, which difference diminishes progressively from one end of said path to the other;
  • the extended surface elements along a substantial portion of the length of said path are bimetallic in cross section and composed of both high and low thermal conductivity metal;
  • the thickness of the high conductivity metal portion of the bimetallic elements is progressively less along said path in the direction of the downward gradient of the temperature difference between the media, so that the thermal conductivity of the successive elements along said path substantially matches the downward gradient of the temperature difference.
  • a heat exchanger having wall means separating a flowing medium from another medium and coating with other wall means to define a path of flow for the flowing medium, and having extended surface elements fixed to said wall means and projecting into said path of the flowing medium, said heat exchanger being characterized in that:
  • the extended surface elements are of such size and shape and so distributed along said path that as the flowing medium wipes across them the heat transfer which takes place between the extended surface elements and the flowing medium effects the reduction in the difference in temperature between the media, which difference diminishes progressively from one end of said path to the other;
  • the extended surface elements along a substantial portion of the length of said path are bimetallic in cross section and composed of both high and low thermal conductivity metal;
  • all of said bimetallic elements are formed of band stock having flat sides and parallel edges, the width of which varies but little in the successive elements along said path but the thickness of which is progressively less along said path in the direction of the downward gradient of the temperature difference between the media,
  • the cross sectional area of the elements and the thickness of the high conductivity portion of the elements and hence the thermal conductivity of said bimetallic elements is progressively less along said path in the direction of the downward gradient of the difference in temperature of said media.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US639544A 1965-07-20 1967-05-18 Heat exchanger with improved extended surface Expired - Lifetime US3385356A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US473366D USB473366I5 (bg) 1965-07-20
US639544A US3385356A (en) 1965-07-20 1967-05-18 Heat exchanger with improved extended surface
NL6802663A NL6802663A (bg) 1965-07-20 1968-02-26
DE19681751241 DE1751241A1 (de) 1965-07-20 1968-04-26 Waermeaustauscher
CH627168A CH508188A (de) 1965-07-20 1968-04-26 Wärmeaustauscher
GB21038/68A GB1170553A (en) 1965-07-20 1968-05-03 Improvements in or relating to Heat Exchangers
FR152492A FR95406E (fr) 1965-07-20 1968-05-20 Échangeur de chaleur.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US47333665A 1965-07-20 1965-07-20
US639544A US3385356A (en) 1965-07-20 1967-05-18 Heat exchanger with improved extended surface

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US3385356A true US3385356A (en) 1968-05-28

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US639544A Expired - Lifetime US3385356A (en) 1965-07-20 1967-05-18 Heat exchanger with improved extended surface

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CH (1) CH508188A (bg)
DE (1) DE1751241A1 (bg)
FR (1) FR95406E (bg)
GB (1) GB1170553A (bg)
NL (1) NL6802663A (bg)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3835923A (en) * 1972-09-13 1974-09-17 Saab Scania Ab Heat exchanger for fluid media having unequal surface conductances
US3857367A (en) * 1972-05-23 1974-12-31 Beondu Ag Boiler
US3897198A (en) * 1972-04-17 1975-07-29 Radiation Ltd Gaseous fuel burners
JPS5043249Y1 (bg) * 1970-05-27 1975-12-10
US4033714A (en) * 1972-04-17 1977-07-05 Radiation Limited Gaseous fuel burners
US4137905A (en) * 1972-04-17 1979-02-06 T. I. Domestic Appliances Limited Gaseous fuel burners
EP0185340A2 (en) * 1984-12-21 1986-06-25 CEM S.p.A. Burner
EP0797058A1 (en) * 1996-03-22 1997-09-24 F.I.M.- Fonderia Industrie Meccaniche SpA Heat exchanging plate
US20040027781A1 (en) * 2002-08-12 2004-02-12 Hiroji Hanawa Low loss RF bias electrode for a plasma reactor with enhanced wafer edge RF coupling and highly efficient wafer cooling
US20060043065A1 (en) * 2004-08-26 2006-03-02 Applied Materials, Inc. Gasless high voltage high contact force wafer contact-cooling electrostatic chuck
US20120216788A1 (en) * 2011-02-24 2012-08-30 Benedetti Joseph A Heating device

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Publication number Priority date Publication date Assignee Title
US728724A (en) * 1902-10-16 1903-05-19 James H Jones Internal-combustion engine.
US761927A (en) * 1903-08-13 1904-06-07 Charles E Van Norman Cooling device for explosive-engine cylinders.
US2055549A (en) * 1934-05-18 1936-09-29 Modine Mfg Co Heat exchange device
US2613065A (en) * 1947-11-21 1952-10-07 Chausson Usines Sa Cooling radiator
US2719354A (en) * 1950-11-13 1955-10-04 Svenska Maskinverken Ab Method of making extended surface heat exchanger
US2875986A (en) * 1957-04-12 1959-03-03 Ferrotherm Company Heat exchanger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US728724A (en) * 1902-10-16 1903-05-19 James H Jones Internal-combustion engine.
US761927A (en) * 1903-08-13 1904-06-07 Charles E Van Norman Cooling device for explosive-engine cylinders.
US2055549A (en) * 1934-05-18 1936-09-29 Modine Mfg Co Heat exchange device
US2613065A (en) * 1947-11-21 1952-10-07 Chausson Usines Sa Cooling radiator
US2719354A (en) * 1950-11-13 1955-10-04 Svenska Maskinverken Ab Method of making extended surface heat exchanger
US2875986A (en) * 1957-04-12 1959-03-03 Ferrotherm Company Heat exchanger

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5043249Y1 (bg) * 1970-05-27 1975-12-10
US3897198A (en) * 1972-04-17 1975-07-29 Radiation Ltd Gaseous fuel burners
US4033714A (en) * 1972-04-17 1977-07-05 Radiation Limited Gaseous fuel burners
US4137905A (en) * 1972-04-17 1979-02-06 T. I. Domestic Appliances Limited Gaseous fuel burners
US3857367A (en) * 1972-05-23 1974-12-31 Beondu Ag Boiler
US3835923A (en) * 1972-09-13 1974-09-17 Saab Scania Ab Heat exchanger for fluid media having unequal surface conductances
EP0185340A2 (en) * 1984-12-21 1986-06-25 CEM S.p.A. Burner
EP0185340A3 (en) * 1984-12-21 1986-08-06 Cem S.P.A. High-effifciency thermal group
EP0797058A1 (en) * 1996-03-22 1997-09-24 F.I.M.- Fonderia Industrie Meccaniche SpA Heat exchanging plate
US20040027781A1 (en) * 2002-08-12 2004-02-12 Hiroji Hanawa Low loss RF bias electrode for a plasma reactor with enhanced wafer edge RF coupling and highly efficient wafer cooling
US20060043065A1 (en) * 2004-08-26 2006-03-02 Applied Materials, Inc. Gasless high voltage high contact force wafer contact-cooling electrostatic chuck
US7479456B2 (en) 2004-08-26 2009-01-20 Applied Materials, Inc. Gasless high voltage high contact force wafer contact-cooling electrostatic chuck
US20120216788A1 (en) * 2011-02-24 2012-08-30 Benedetti Joseph A Heating device
US8915240B2 (en) * 2011-02-24 2014-12-23 Innovative Hearth Products Llc Heating device

Also Published As

Publication number Publication date
DE1751241A1 (de) 1971-02-18
CH508188A (de) 1971-05-31
NL6802663A (bg) 1968-11-19
GB1170553A (en) 1969-11-12
USB473366I5 (bg)
FR95406E (fr) 1970-11-06

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