US3757856A - Primary surface heat exchanger and manufacture thereof - Google Patents

Primary surface heat exchanger and manufacture thereof Download PDF

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Publication number
US3757856A
US3757856A US00189659A US3757856DA US3757856A US 3757856 A US3757856 A US 3757856A US 00189659 A US00189659 A US 00189659A US 3757856D A US3757856D A US 3757856DA US 3757856 A US3757856 A US 3757856A
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wall
isostress
heat exchanger
inch
projections
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L Kun
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Katalistiks International Inc
Honeywell UOP LLC
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Union Carbide Corp
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Assigned to MORGAN GUARANTY TRUST COMPANY OF NEW YORK, AND MORGAN BANK ( DELAWARE ) AS COLLATERAL ( AGENTS ) SEE RECORD FOR THE REMAINING ASSIGNEES. reassignment MORGAN GUARANTY TRUST COMPANY OF NEW YORK, AND MORGAN BANK ( DELAWARE ) AS COLLATERAL ( AGENTS ) SEE RECORD FOR THE REMAINING ASSIGNEES. MORTGAGE (SEE DOCUMENT FOR DETAILS). Assignors: STP CORPORATION, A CORP. OF DE.,, UNION CARBIDE AGRICULTURAL PRODUCTS CO., INC., A CORP. OF PA.,, UNION CARBIDE CORPORATION, A CORP.,, UNION CARBIDE EUROPE S.A., A SWISS CORP.
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Assigned to UOP, DES PLAINES, IL., A NY GENERAL PARTNERSHIP reassignment UOP, DES PLAINES, IL., A NY GENERAL PARTNERSHIP ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KATALISTIKS INTERNATIONAL, INC.
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/02—Stamping using rigid devices or tools
    • B21D22/04—Stamping using rigid devices or tools for dimpling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/04—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of sheet metal
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
    • 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
    • F28D1/00—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 is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—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 is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0391—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 is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits a single plate being bent to form one or more conduits
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/442—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
    • 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
    • Y10T29/49366—Sheet joined to sheet

Definitions

  • ABSTRACT An all purpose primary surface heat exchanger, and manufacture thereof, comprising an array of parallel channels formed and bounded by thin heat conductive walls, at least one wall of which has on at least a portion of its surface isostress contours with substantially uni form disposed unidirectional wall-supporting projections formed from the wall.
  • the projections are arranged so as to mate with, and to abut supportingly against, correspond wall-supporting projections of a similar adjacent isostress wall.
  • the walls, so arranged, are sealed at the wall edges in a manner to form and isolate alternate enclosed channels from intervening open channels so that the alternate channelsmay contain and conduct a first fluid, and the intervening channels may contain and conduct a second fluid at a different temperature, thereby effecting heat exchange between the fluids.
  • This invention relates to a thin metal or plastic plate heat exchange channel element, and manufacture thereof, having on a portion of its surface isostress contours with substantially uniformly disposed unidirectional wall-supporting projections.
  • the present invention enables such walls to be fabricated from thinner thermally conductive material than is presently required of conventional type primary heat exchangers.
  • the walls of conventional type pr'imary'heat exchangers have to be stayed by means of numerous support members so as to reduce stress in the walls.
  • stayed walls are normally not practical because of the followingreasons:
  • the present invention overcomes the above drawbacks by providing an isostress contoured heat exchange surface which upon being subjected to a differential pressure across its wall will result in a substantially uniform fiber stress distribution in the wall. This uniform stress distribution substantially eliminates stress concentration points in the wall of a heat exchange element thereby permitting the element to be fabricated from rather thin sheets of thermally conductive material.
  • the present invention is directed to an all-purpose, primary-surface heat exchange channelized element having on at least a portion of its surface isostress con tours with substantially uniformly disposed unidirectional wall-supporting projections.
  • the heat exchange element is economical to fabricate and when employed in stacked units, they are admirably suited as a heat ex changer for use with internal combustion engines.
  • the primary-surface heat exchanger of this invention basically comprises at least one channel element formed and bound by at least one thin walled, thermally conductive metal or plastic material, such channel element having an entrance opening, an exit opening and a multiplicity of isostress contours on a portion of its wall surface with substantially uniformly disposed unidirectional wall-supporting projections formed from the wall in a dimensional relationship to be discussed hereinafter.
  • the wall-supporting" projections are arranged so as to mate with and abut against corresponding wall-supporting projections on a similar adjacent isostress wall.
  • At least two such channels when aligned in juxtaposed relationship, will form a heat exchanger having a first set of passages defined by and bound within the conductive walls of each channel, and a second set of passages defined by, and disposed between, the juxtaposed channels so that a first medium can be fed through one set of passages while a second cooler medium can be fed through the other set of passages thereby effecting a heat exchange between the mediums without having the mediums intermix.
  • primary-surface heat exchanger refers to heat exchangers wherein substantially all the material which conducts heat between two media comprises the walls separating the two media.
  • secondary surface heat exchangers contain a substantial amount of material in the form of fins which do not separate the media but are contacted onvir'tually all surfaces by a single medium.
  • substantially all of the heat exchanger material is stressed pneumatically.
  • primary surface heat exchanger refers to a heat exchanger consisting primarily of plates or sheets and having no separate or additional internal members, such as fins, so that the exchanger is constructed of plates or sheets each side of which is in contact with a different fluid, and heat transfer is substantially and directly between the plates and the fluid.
  • An isostress surface is a continuously curved surface having a multiplicity of isostress contours'wherein each contour has a multiplicity of radii with theoretically no flat segments and resembles the curve contour of a shear-free soap bubble membrane.
  • the lack of flat or pointed surface segments substantially eliminates stress concentration points that are present in conventional type dimpled surfaces when such-surfaces are subjected to a differential pressure across their surface areas.
  • substantially pure tension or pure compression loading is obtained by utilizing the thin walled isostress contoured channelized element of this invention. Pure tension or pure compression loading of a finite thickness, pressure bearing wall results in the substantially uniformly distribution of fiber stress through the cross-sectional area of the wall parallel to its surface.
  • wall-supporting unidirectional projections are disposed in a pre-aligned space relationship on the surface of each element so that when the walls are juxtaposed, the outer extremities of the wall-supporting projections, hereafter referred to as buttons, will be in touching relationship.
  • buttons the outer extremities of the wall-supporting projections
  • buttons of both walls project inward into the space between the walls, the forces due to the pressure either external or internal of the pair will be substantially balanced, i.e., the secured contact between the buttons will sustain by tension or compression the entire force due to the pressure and no other structural member will be needed to absorb the load.
  • pressure force will be counter-balanced by'a restraining force developed within the pair ot'walls without the ne cessity of any external structure.
  • the pressure either external or internal of the pair will not be balanced and a member external of the pair will be needed on each exposed face of the pair to absorb the load by supportive contact with the buttons in either tension or compression.
  • a restraining force will not be developed within the pair of walls to counterbalance the pressure force.
  • the member external of the pair may be yet another isostress contoured wall with buttons matching those of the juxtaposed surface of the pair.
  • the isostress contoured channel is designed as a primary-surface heat exchange channel, its wall material need not be highly conductive and thus can be selected from at least one of the groups consisting of metals, metal alloys, metal clads, plastics (such as Mylar), plastic-coated metals and the like.
  • the criteria of the material selected for the heat exchange isostress channel is that it be only sufficiently thermally conductive so that as a hot medium is passed through the channel, the heat of the medium will be conducted through the wall of the channel to a cooler medium external of, and adjacent to, the channel which can absorb the heat thereby successfully effecting a heat transfer between the mediums without intermixing of said mediums.
  • Materials such as aluminum, copper, steel, brass, titanium and Mylar are suitable for this application.
  • Substantially uniformly disposed wall-supporting projections is intended to be broad enough to include a pattern of wall-supporting projections having a progressive variation in spacing along at least one axis of the heat exchange element.
  • additional wall-supporting projections can be provided along the curved portion of the channel which may have a spacing relationship different from that of wall-supporting projections occupying the central portion of the heat exchanger element.
  • the dimensions of, and the dimensional relationship between, the wall-supporting projected buttons on the isostress contoured surface are somewhat restrictive depending on the end use environment of the heat exchange channel.
  • the pattern of wall-supporting projected buttons can be arranged in a square, diamond, triangle or any other design configuration depending somewhat on the actual shape of the channel and the intended differential pressure to which the wall of the channel will be subjected in its intended environment.
  • the wall-supporting projected buttons of selected shape should be designed and arranged in only such size, number and pattern as will provide the restraint necessary to withstand the maximum differential pressure for which the channel wall is designed in its intended environment.
  • the isostress contoured surface necessary for maximum heat transfer in an intended end use pressurized environment, can be imparted to the surface of a thin-walled thermally conductive sheet of material along with the'wall-supporting projected button contours by any conventional technique such as pressing, stamping,'rolling or the like.
  • a thermally conductive isostress contoured, wallsupporting button projected sheet, so prepared, can be longitudinally folded upon itself with the projected buttons facing either inwardly or outwardly, and the folded sheet segments spaced sufficiently apart so as to define tained.
  • the heat exchanger of this invention will provide a low frontal area and a low external fluid pressuredrop.
  • Frontal area is the area of the projection of the entire array of heat exchange channel-s onto a plane normal to the direction of fluid flow through the channelized passages.
  • Low external fluid pressure drop is the static pressure drop across the length of the flow a passage therebetween.
  • the width of the passage so formed is thereby defined by the projected heights of the wall-supporting buttons. Since stress concentration may occur at the bending area of the sheet in its intended operational environment, additional wallsupporting projections may be disposed within the .vicinity of such areas so as to equalize the stresses throughout the channel structure.
  • the longitudinally mating edges of the sheet can then be suitably sealed by conventional techniques, i.e., soldering, brazing, welding or with an adhesive filled lock-seam joint, to make it leak-tight.
  • This isostress contoured, unidirectional wall-supporting button projected channel is then ready, for use as a heat exchange element.
  • buttons projecting inwardly and when intendedfor internal pressurization then the button contacting surfaces within the passages should be bonded together by conventional means as soldering, brazing or with an adhesive.
  • An array of channels so formed with the wall-supporting projected buttons in touching relationship can then be appropriately assembled to'produce a compact, efficient primary-surface heat exchanger.
  • the wallsupporting projected buttons are disposed outwardly, then the channels can be superimposed in button touching relationship wherein the heights of the projected buttons will define the size of the passage between adjacent channels.
  • the wall-supporting projected buttons are disposed inwardly, then the channels will have to be spaced apart by some additional means so as to define apassage between adjacent channels.
  • a pressurized medium such as hot water
  • a coolant medium such as cool air
  • the isostress contoured, wall-supporting button projected sheet could also be fabricated into a circular or spiral channel, or any multiple sided channel by appropriate bending and/or folding techniques.
  • Theheat exchange cannelized elements so formed can also be shaped into any curvilinear configuration and then superimposed one on the other leaving defined passages therebepath of the external coolant medium.
  • the mediums can be fed through their respective passages in a mutually parallel relationship, a perpendicular relationship or at any angle relationship therebetween.
  • FIG. 1 lsostress contoured surface.
  • FIG. 2 lsostress die casting apparatus.
  • FIG. 2A View taken along line 2A--2A of FIG. 2.
  • FIG. 2B Apparatus of FIG. 2 operating'under vacuum.
  • FIG. 3 Log-Log graph of stress vs. surface height of an isostresscontoured surface in a 0.007 inch thick aluminum sheet.
  • FIG. 3A lsostress contoured surface.
  • FIG. 4 A graph of applied pressure vs. surface deflection for various aluminum contoured surfaces.
  • FIG. 4A Truncated cone surface.
  • FIG. 5 4 Isometric view of an automobile radiator employing the heat exchange elementsof this invention.
  • FIG. 5A View taken of the longitudinal edges of a heat exchange element of FIG. 5.
  • FIG. 5B Side view of elements 1 of FIG. 5.
  • FIG. 5C Alternate embodiment of elements 1 of FIG. 5.
  • FIG. 5D Alternate embodiment of the longitudinal edges of elements 1 of FIG 5.
  • FIG. 6 Isometric view of an array of isostress channels with outwardly projected buttons.
  • FIG. 6A Cross-sectional view of channels in FIG. 6 taken along line 6A6A.
  • FIG. 6B Sectional side view of channels in FIG. 6 taken along line 6B-6B.
  • FIG. 7 Isometric view of an array of isostress channels with inwardly projected buttons.
  • FIG. 7A Sectional side view of channels in FIG. 7 taken along line 7A-7A.
  • Subjecting a thin structure, having an isostress contour as shown in FIG. 1, to a differential pressure across its wall area C will result in imparting substantially pure tension or pure compression to the wall void of any appreciable shear or bending forces thereto, i.e., pure tension or pure compression results in uniform distribution of fiber stress in the crosssectional area I of wall A parallel to its surface area C as shown by the arrows in FIG. 1.
  • a thin membrane having an isostress contour can withstand greater differential pressure without deforming or rupturing than a non-isostress membrane of identical size and thickness.
  • An isostress contoured wall can be fabricated using the following equation which is developed for an ideal shear-free, soap bubble membrane.
  • equation A is applicable for any pattern of supports as long as the typical symmetrical segment is chosen to suit the specific pattern employed such that the conditions at the boundaries of such symmetrical segment are known.
  • equation A is applicable for any pattern of supports as long as the typical symmetrical segment is chosen to suit the specific pattern employed such that the conditions at the boundaries of such symmetrical segment are known.
  • the partial derivative of the normal to any edge of a symmetrical segment with respect to an axis perpendicular to the plane containing the support points is zero.
  • the slope at the boundary edges of a symmetrical segment with respect to the plane containing the supports is zero which indicates no vertical component of force.
  • triangle I For a square pattern of supports B as shown in FIG. 1, the smallest typical symmetrical segment of the area A is triangle I defined by edges E, F and G.
  • Triangle J is a symmetrical segment because area A contains eight such identical triangles.
  • the tip of the triangle .I covered by support 8 is excludedfrom the symmetrical segment of the area.
  • the partial derivative of Z(X, Y) with respect to the normal to such edges is zero; e.g., dZ/dN 0 where N is any line parallel to the reference plane XY and normal to edges E, F and G, respectively, of triangle J.
  • a value for (AP/6) can be obtained.
  • the designer may select values for two of the terms AP, S and t and calculate the other.
  • a square aluminum isostress contoured wall 0.009 inch thick having a dimension H of 0.030 inch at its center, a D dimension of 0.4 inch and a support B dimension radius of 0.060 inch, was calculated as having a fiber stress S of 4,000 lb/in when subjected to a pressure differential of 25 lb/in.
  • values may be assigned to AP, S and t and a solution for H may be rendered in terms of D. This allows the designer to choose between numerous sets of values of D and H to suit fluid flow and heat transfer requirements.
  • Still another use of the equation is to map the surface contour. Assume that boundary conditions have been established and that values for AP, S, t, D and H have been assigned. The equation can be solved for an array of X, Y values to obtain corresponding values of Z. This provides a listing of coordinates at numerous points on the surface which can be employed, for example, to produce a forming die.
  • Truncated cone impressed surfaces as shown in FIG. 4A, if fabricated from the same material and having the same thickness and size as the 0.4 inch square isostress contoured wall segment above, could not function under a differential pressure of 25 lb/in as well as the isostress surface and would be more susceptible to failure due to fatigue loading, fatigue loading being the intermittent loading and unloading of a structure.
  • a thinwalled thermally conductive material such as aluminum below about 0.02 inch thick, impressed with an isostress contoured surface with wall-supporting unidirectional projections and then'formed into a channelized structure will produce a heat exchange element admirably suited for various heat transfer applications such as radiators for internal combustion engines.
  • a method for making dies having an isostress contoured surface with spaced apart wall-supporting unidirectional projections for use in the fabrication of heat exchange elements would consist basically in fabricating a block having on its surface multiple verical projection supports forming a pattern and being dimensionally sized to correlate to the pattern and size of the wall-supporting projections desired in an isostress contoured surface. Upwardly extending sides are provided around the edges of the block, thereby producing a recess or cavity which contains the vertical supports.
  • the cavity would be connected to pressurizing means so that when a flexible material is tensionally secured across the top of the cavity and also contacting and supported by the vertical projected supports, the pressurizing means can be operated to force the unsupported portion of said flexible material into the cavity while the vertical projected supports prevent deflection of the supported portion of the flexible material thereby causing the flexible material to assume an isostress contour having wall-supporting projections.
  • the pressurizing means can be deactivated.
  • the cured material having the isostress contoured surface with substantially uniformly disposed unidirectional wallsupporting projections is then ready to be used as a die for fabricating isostress contoured heat exchange elements of this invention.
  • pressure block 21 has openings 22 interconnected to passage 23 which in turn is coupled to vacuum pump 24, bleed valve 25 and monometer 32.
  • a flexible membrane 29 such as natural or a synthetic rubber, is tensionally stretched onto frame 27 and secured thereat by tack means or the like (not shown). Preferably flexible membrane 29 rests on top of projections 26.
  • a second frame 30, substantially similar to frame 27, is placed on top of frame 27 and is secured to frame 27 at its corners and/ or around the .entire frame at preselected spacings by screw means 31.
  • vacuum pump 24 is activated whereupon flexiblemembrane 29 is suctioned into the openings 35 between projections 26 as shown' in FIG. 28.
  • vacuum pump 24 By regulating the pressure created by vacuum pump '24, as indicated on monometer 32, via bleed valve 25, an isostress contour can be imparted toflexible membrane 29 between projections 26.
  • Projections -26 should be of a sufficient height so as to prevent flexible membrane 29 from deformably touching surface 33 of openings 35.
  • a form setting material 34 such as epoxy resins, thermoplastics, concrete, cement or the like, is deposited into frame -where it is sup.- ported by the flexible membrane 29.'Form setting material 34 is then allowed to cure.
  • the horizontal surface 36' of projections 26 impart to flexible membrane 29, and, thus, to form setting material 34, inward projections 37 each having a horizontal button segment 38.
  • this horizontal button segment 38 of each inward projection 37 is shown flat, it may be curved, wavy or suitably ridged as long as it is shaped to mate with other button segments on similar type projections.
  • an isostress contoured surface as illustrated in FIG. 3A, having a repeatable wall-supporting projection spacing D of between about 0.2 and about 2.5 inch; a "/d ratio between about 3 and about 10, a ratio between about 0.05 and about 0.2 and a sheet or wall thickness between about 0.003 and about 0.25 inch will be quite suitable.
  • a repeatable wall-supporting projection spacing D of between about 0.2 and about 2.5 inch; a "/d ratio between about 3 and about 10, a ratio between about 0.05 and about 0.2 and a sheet or wall thickness between about 0.003 and about 0.25 inch
  • H equals the maximum height measured perpendicularly from a surface which contains the extremities of the wall-supporting projections (X-Y plane) to the innermost crest of the isostress surface of said element (along the Z axis)
  • D equals the spacing between the center of the closest adjacent wall-supporting projections on the surface of said element
  • d is the equivalent diameter of the projection defined by the ratio 4a/p whereby a equals the area of the load bearing segment (button) of the wall-supporting projection and p equals the perimeter of said load bearing segment.
  • d is equal to the diameter of such circle as shown in FIGS. 1 and 3A.
  • the load bearing segment is shaped to mate in touching. relationship with similar type load bearing segments on wall-supporting projections on a second heat exchange wall.
  • D spacing is imposed because spacing less than 0.2 inch results in very small hydraulic radii on the concave side of the isostress wall thereby being very susceptible to fouling, i.e., trapping of foreign matter between adjacent walls, which if excessive, would clog the passages for one of the fluid mediums. A high externalfluid pressure drop per unit length of fluid flow path would also result. Spacing D above 2.5 inches would result in a small heat exchange area per cubic foot of heat exchange volume thus resulting in excessive manufacturing cost and decreased efficiency. Also the ability of the material to withstand a differential pressure across its wall thickness would be decreased.
  • a "/D ratio smaller than 0.05 would result in an isostress surface having very small hydraulic radii on the concave side steadily approaching almost a flat surface whereupon. the advantages of the isostress contour would vanish.
  • a heat exchanger composed of isostress channels with such a small "/D ratio would also be susceptible to fouling and have a high external fluid pressure drop per unit length of fluid flow path. For a "/D ratio of greater than 0.2, a small heat exchange area per cubic foot of heat exchange volume would result thereby resulting in excessive manufacturing cost and decreased efficiency.
  • a material thickness of less than 0.003 inch would be unsuitable due to local imperfections in the metal, produced during rolling or as a result of pitting (corrosion) or erosion.
  • a material thickness to above 0.25 inch is not suited to this invention when employed within the imposed limits of D, H and d, because full or near-full utilization of the material strength implies extremely high pressure differentials.
  • Embodiments wherein pressureforces are not balanced within the channels require massive external structures to absorb the loads, while force-balanced embodiments wherein wallsupporting projections are bonded together and loaded in tension would be characterized by severe stress concentration in such bonded areas.
  • a repeatable distance D between about 0.2 and about 0.6 inch, a "Id ratio of between about 3 and about 7; a "/D ratio of between about 0.05 and about 0.12; and a sheet or wall thickness between about 0.003 and about 0.02 inch.
  • the preferred dimensions of an isostress contoured surface for automobile radiator applications are a repeatable D of about 0.4 inch, a height H of about 0.035 inch, a button dimension width d of about 0.09, a "/d ratio of about 4.8, a "/D ratio of about 0.08 and a sheet or wall thickness of about 0.008 inch.
  • a log-log graph of stress versus height H (same as H in FIG. 1) of an isostress contoured surface having uniformly spaced wallsupporting projections in a square pattern on an aluminum sheet 0.007 inch thick was plotted as shown in FIG. 3 using the aid of a computer.
  • Repeatable wallsupporting projection spacings D of 0.2, 0.4 and 0.8 inch, measured between the closest adjacent projected supports as illustrated in FIG. 3A, produced three parallel lines as shown in FIG. 3.
  • the cross-hatched area may serve as a guide for producing a multiple-curved isostress contoured surface in a thin wall aluminum sheet which upon being fabricated into channel structures as described above will yield an effective and efficient heat transfer radiator for the internal combustion engine. If stronger material and/or lower factors of safety were used then the allowable stress ranges would move upward. Thus the allowable D-dimension range would increase for the same limits of the H-dimension.
  • the 30 cone surface is an embodiment of the above-identified copending application.
  • the data obtained using both the 30 cone and 45 cone projected sheets is also shown plotted as curves on the graph of FIG. 4.
  • the cone angle 0 is the acute interior angle measured between the horizontal undeformed surface of the wall adjacent the projected indentation and the substantially straight segment along the sloped side of the conical indentation.
  • Deflections of the crest of the surface tending to flatten the wall are objectionable and should be minimized even though such deflections may be safely below the buckling point of the material.
  • dried represent deviations from the ideal soap the membrane contour. If the deflections are excessive, the ideal contour cannot be closely approached under service pressure differentials even employing allowances are made in the design.
  • the material is usu ally stressed in bending and shear as member deflects, and when deflections are excessive the material may experience stresses approaching the yield point in localized areas. If such deflections are imposed repeatedly in service, the material may be fatigued and crack after a relatively short service life.
  • deflecv tions reduce the available space between the heat exchange walls in the lower pressure passages, and result either in higher fluid pressure drop or in reduced rate of fluid flow.
  • isostress contoured wall used in the tests exhibited virtually no deflection at the crest for pressure differentials as high as 35 psi.
  • the cone surface deflected severely at low pressure differentials.
  • the data shows the increase in stress resulting from use of the 30 and 45 cone surfaces over the isostress contour surface. It should be noted that in order to achieve the isostress wall of this invention, it is essential that all the surface area exclusive of the wall-bearing supports be unrestricted so as to be free to deflect and therefore be devoid of local mechanical loading.
  • a die can be prepared as described above. The die can then be used in conventional type apparatus toimpart the desired isostress wall supporting projections facing inward or outward.
  • two sheets may be prepared and formed appropriately at the longitudinal edges for bonding and then spaced apart bysuitable means to form a flattened tube-like configuration.
  • the longitudinal edges of the sheets could be flared a specific amount so that when said longitudinal edges of two sheets are juxtaposed in touching relationship, they will provide the desired spacing within the channel.
  • the edges of the sheets can be potted as with epoxy resin to seal the sheets leaktightly together to form tube-like configurations, an array of which can be sealed leak-tightly into a header to form a radiator assembly.
  • flattened tube-like heat exchange elements 1 can be air-tightly sealed along their edges 2-3 using a lock-seam joint filled with an adhesive 14, such as a suitable epoxy type adhesive.
  • the heat exchange elements 1 having an isostress contoured surface 4 with spaced apart wall-supporting pro jections 5, can be superimposed with the surface extremities l7 (buttons) in touching relationship to form a multiple layer'heat exchanger.
  • the touching projected buttons 17 provide passages 15 between adjacent heat exchange elements 1 defined by the isostress contoured surfaces 4 of the adjacent elements 1, and in addition, the contacting buttons 17 act as a restraint against internal pressure in the heat exchange elements I.
  • the projected button 5' could be offset or non-symmetrically disposed on opposite sides of each element 1', as shown in FIG. 5C, thereby altering the passage area of element 1'.
  • the ends 6 of ele-' ments 1 are slightly depressed, if necessary, to provide a clearance for the teeth 7 of comb-shaped members 8.
  • Members 8 retain elements 1 in proper relationship and provide an outer plate segment 9 adaptable for securing header 10 thereto.
  • members 8 must also produce a leak-tight seal to header 10 and to the channel elements 1 so that in the operational mode a fluid fed through the elements 1 via'the header 10 will not leak into the space between adjacent elements 1.
  • header 10 can be secured to members 8 by using an adhesive type joint arrangement.
  • a suitable resin for use in adhesive type joints for aluminum is Resin Type EA-914, manufactured by I-Iysol Division of Dexter Corporation, California. However, this resin must be used in conjunction with an Alodine process for pretreating the surfaces to be bonded.
  • An Alodine pretreatment process would basically consist of the following steps:
  • Alodine No. 1200 is manufactured by Amchem Products, Inc., Freemont, California, and contains acidic chromates and fluorides);
  • FIGS. 6, 6A and 6B ahsow an array of elements 21 with outwardly protruding wall supports 22.
  • Passages 23 in elements 21 define one set of confined passages independent of and separate from a second set of passages 24 formed between adjacent elements 21.
  • One fluid shown as solid line arrows, can be fed through passages 23 in elements 21 while simultaneously a second cooler fluid, shown as broken line arrows, can be fed through passages 24to effectively cause a transfer of heat from the hotter fluid to the cooler fluid without having them intermixed.
  • a rigid frame or support similar to support 12 of FIG. 5 is required so as to constrain the stack of elements 21 along the sides.
  • FIGS. 7 and 7A illustrate a similar array of elements 30 except that the wall-supporting projections 31 are inwardly projected. Passages 32 within elements 30 are independent of and separate from passage 33 formed between adjacent elements 30.
  • One fluid shown as solid line arrows, can be fed through passages 32 while simultaneously a second cooler fluid, shown as broken line arrows, can be fed through passages 33 to effectively cause a transfer of heat from the hotter fluid to the cooler fluid without having them intermixed.
  • spacers 34 are required to space the elements 30 sufficiently apart so as to define passages 33. It is to be understood that the spacer 34 could be similar to the comb-like structure 8 as shown in FIG. 5, which in turn could be coupled directly to a header similar to header 10 illustrated also in FIG. 5.
  • edges 2 and 3 may be extended to provide a secondary surface heat dissipating fin 16 as shown in FIG. 5D.
  • the fin which could also be added to the elements by conventional securing means, can be provided with dimplings to promote turbulence, or provided with slots or assume any other desirable geometric configuration which would enhance the performance of the heat exchange elements.
  • side bars could be used to separate the elements as shown in US. Pat. No. 3,291,206 or edge ribs, as shown in US. Pat. No. 3,106,242.
  • the primary-surface heat exchange element of this invention can be employed in any type heat exchanger wherein a heat transfer between a heated medium and a coolant medium is to be accomplished without an intermixing of the media occurring.
  • the design flexibility of the primary-surface heat exchange elements of this invention makes them admirably suited for complex type heat exchanger applications including pre-heaters for gas turbines and low grade heat rejectors for atomic power plants.
  • Mylar is a tradename of E. I. DuPont Company and Alodine is a tradename of Amchem Products, Inc.
  • a primary surface heat exchanger comprising at least one channel element bound by two thermally conductive walls being spaced by edge portions, said channel element having an entrance opening at one end, an exit opening at the opposite end, and a multiplicity of isostress contours on a portion of each wall surface with substantially uniformly disposed unidirectional wall-supporting projections formed from each wall, said projections having load-bearing segments at their extremities which are shaped for mating over a substantial area with similar type load-bearing segments on wall-supporting projections of a second isostress surface and formed with the wall between and surrounding said load-bearing segments being continuously curved and devoid of local mechanical loading; said isostress contours and wall-supporting projections having a dimensional relationship therebetween defined by a "/D ratio of between about 0.05 and about 0.2; a "/d ratio of between about 3 and about 10, a D dimension of between about 0.2 and 2.5 inches and a wall thickness between about 0.003 and about 0.25 inch; wherein H equals the
  • thermally conductive heat exchange element is made from g at least one material selected from the group consisting of metals, metal alloys, metal clads, plastics and plastic coated metals.
  • change element is made of aluminum having a wall thickness of about 0.008 inch; said "/D ratio is about 0.08; said "/d ratio is about 4.8 and said D dimension is about 0.4 inch.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Re-Forming, After-Treatment, Cutting And Transporting Of Glass Products (AREA)
US00189659A 1971-10-15 1971-10-15 Primary surface heat exchanger and manufacture thereof Expired - Lifetime US3757856A (en)

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JP (1) JPS5146293B2 (de)
AU (1) AU464105B2 (de)
BR (1) BR7207156D0 (de)
CA (1) CA976953A (de)
DE (2) DE2265349B2 (de)
ES (2) ES211434Y (de)
FR (1) FR2161913B1 (de)
GB (3) GB1412444A (de)
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US4023618A (en) * 1975-08-18 1977-05-17 Union Carbide Corporation Heat exchanger headering arrangement
US4119140A (en) * 1975-01-27 1978-10-10 The Marley Cooling Tower Company Air cooled atmospheric heat exchanger
US4184543A (en) * 1976-07-06 1980-01-22 Olin Corporation Heat exchanger exhibiting improved mechanical and thermal stability
EP0014481A2 (de) * 1979-02-12 1980-08-20 Union Carbide Corporation Wandteil für Wärmetauscher, Kanalelement für Wärmetauscher und sie verwendender Wärmetauscher
US4291759A (en) * 1979-08-28 1981-09-29 Hisaka Works, Limited Cross-current type plate heat exchanger
US4341601A (en) * 1980-02-20 1982-07-27 E. I. Du Pont De Nemours And Company Water evaporation process
US4424098A (en) 1980-11-12 1984-01-03 E. I. Du Pont De Nemours And Company Falling film evaporator
US4497689A (en) * 1980-08-22 1985-02-05 Energiagazdalkodasi Intezet Heat engineering apparatus for carrying out thermodynamical processes comprising a pair of mutually opposite phase transitions of a work medium
US4512393A (en) * 1983-04-11 1985-04-23 Baker Colony Farms Ltd. Heat exchanger core construction and airflow control
US4624305A (en) * 1981-02-25 1986-11-25 Institut Francais Du Petrole Heat exchanger with staggered perforated plates
US4671856A (en) * 1984-04-26 1987-06-09 Superstill Technology, Inc. Method for recyclying energy in counterflow heat exchange and distillation
US4869067A (en) * 1982-09-02 1989-09-26 Superstill Corporation Method of generating power
US4874035A (en) * 1987-11-17 1989-10-17 Shinwa Sangyo Co., Ltd. Heat exchanger for cooling tower
US4896411A (en) * 1985-05-02 1990-01-30 Carrier Corporation Method of making a multiple cell condensing heat exchanger
US4947548A (en) * 1985-09-20 1990-08-14 Carrier Corporation Method of making a heat exchanger for condensing furnace
US5036911A (en) * 1989-02-24 1991-08-06 Long Manufacturing Ltd. Embossed plate oil cooler
US5111577A (en) * 1990-01-22 1992-05-12 Atd Corporation Pad including heat sink and thermal insulation areas
US5186250A (en) * 1990-05-11 1993-02-16 Showa Aluminum Kabushiki Kaisha Tube for heat exchangers and a method for manufacturing the tube
US5271151A (en) * 1990-04-23 1993-12-21 Wallis Bernard J Method of making a high pressure condenser
US5369883A (en) * 1989-02-24 1994-12-06 Long Manufacturing Ltd. Method for making an in tank oil cooler
US5375328A (en) * 1992-02-18 1994-12-27 Miralfin S.R.L. Method of making an oil radiator structure having flanges with external flat surfaces
US5441105A (en) * 1993-11-18 1995-08-15 Wynn's Climate Systems, Inc. Folded parallel flow condenser tube
WO1996010158A1 (en) * 1994-09-26 1996-04-04 Stellan Grunditz Heat exchanger
US5538077A (en) * 1989-02-24 1996-07-23 Long Manufacturing Ltd. In tank oil cooler
US5560425A (en) * 1988-08-12 1996-10-01 Calsonic Corporation Multi-flow type heat exchanger
US5576470A (en) * 1994-08-29 1996-11-19 Henkel Corporation Polyol esters of ether carboxylic acids and fiber finishing methods
US5603159A (en) * 1994-09-29 1997-02-18 Zexel Corporation Method of producing heat exchangers
US5730213A (en) * 1995-11-13 1998-03-24 Alliedsignal, Inc. Cooling tube for heat exchanger
US5768782A (en) * 1993-10-29 1998-06-23 Zexel Corporation Flat tube for heat exchanger and method for manufacturing it
US5800905A (en) * 1990-01-22 1998-09-01 Atd Corporation Pad including heat sink and thermal insulation area
US6186223B1 (en) 1998-08-27 2001-02-13 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
US6209202B1 (en) 1999-08-02 2001-04-03 Visteon Global Technologies, Inc. Folded tube for a heat exchanger and method of making same
US6244333B1 (en) 1998-08-27 2001-06-12 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
US20010047860A1 (en) * 2000-02-28 2001-12-06 Carlos Martins Heat-exchange module, especially for a motor vehicle
US6378604B1 (en) * 1999-06-28 2002-04-30 Jon Charles Feind To heat exchanger
US6382312B2 (en) * 2000-01-28 2002-05-07 Valeo Thermique Moteur Heat-exchange module, for a motor vehicle in particular
GB2384299A (en) * 2002-01-22 2003-07-23 Llanelli Radiators Ltd Automotive heat exchanger
US20030196785A1 (en) * 2002-03-30 2003-10-23 Wolfgang Knecht Heat exchanger
US6648067B1 (en) * 1999-11-17 2003-11-18 Joma-Polytec Kunststofftechnik Gmbh Heat exchanger for condensation laundry dryer
US6688378B2 (en) 1998-12-04 2004-02-10 Beckett Gas, Inc. Heat exchanger tube with integral restricting and turbulating structure
US20040149424A1 (en) * 2001-02-07 2004-08-05 Stephen Memory Heat exchanger
US20050067156A1 (en) * 2003-07-15 2005-03-31 Rottmann Edward G. Pressure containing heat transfer tube and method of making thereof
US20060185835A1 (en) * 2005-02-03 2006-08-24 Toyoaki Matsuzaki Heat exchange plate
US20080029243A1 (en) * 2003-11-25 2008-02-07 O'donnell Michael J Heat exchanger tube with integral restricting and turbulating structure
US20080223945A1 (en) * 2007-03-12 2008-09-18 Lau George H K Heat exchanger
US20110017440A1 (en) * 2009-07-24 2011-01-27 Denso Corporation Heat exchanger
US20120037346A1 (en) * 2009-04-20 2012-02-16 Kim Young Mo Heat exchanger
US20120198882A1 (en) * 2009-10-19 2012-08-09 Showa Denko K.K. Evaporator
DE102013218444A1 (de) * 2012-09-17 2014-03-20 Behr Gmbh & Co. Kg Wärmetauscher
US9359952B2 (en) 2012-02-03 2016-06-07 Pratt & Whitney Canada Corp Turbine engine heat recuperator plate and plate stack
US20180372413A1 (en) * 2017-06-22 2018-12-27 Rheem Manufacturing Company Heat Exchanger Tubes And Tube Assembly Configurations
WO2021014092A1 (fr) 2019-07-25 2021-01-28 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur
WO2021014091A1 (fr) 2019-07-25 2021-01-28 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur
WO2021014094A1 (fr) 2019-07-25 2021-01-28 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur
FR3100058A1 (fr) 2019-08-23 2021-02-26 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d’un tel échangeur de chaleur
US11073344B2 (en) 2019-04-24 2021-07-27 Rheem Manufacturing Company Heat exchanger tubes
US11131511B2 (en) * 2018-05-29 2021-09-28 Cooler Master Co., Ltd. Heat dissipation plate and method for manufacturing the same
US20220023931A1 (en) * 2019-04-03 2022-01-27 Safran Nacelles Method for manufacturing a structural surface heat exchanger for a nacelle
US11421949B2 (en) * 2017-12-21 2022-08-23 Mahle International Gmbh Flat tube for an exhaust gas cooler
US11913725B2 (en) 2018-12-21 2024-02-27 Cooler Master Co., Ltd. Heat dissipation device having irregular shape

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FR2504667A1 (fr) * 1981-04-23 1982-10-29 Vape Sa Ets Connexion pour alimentation en eau d'echangeurs thermiques
DE3120173A1 (de) * 1981-05-21 1982-12-09 Hoechst Ag Flaechenhaftes flexibles waermeaustauscherelement
FR2647198B1 (fr) * 1989-05-22 1991-07-19 Packinox Sa Echangeur thermique a conduits a plaques
FR2786559B1 (fr) * 1998-11-30 2001-03-30 Valeo Thermique Moteur Sa Echangeur de chaleur depourvu d'ailettes, en particulier pour vehicule automobile
DE102009059692A1 (de) 2009-12-19 2011-06-22 Modine Manufacturing Co., Wis. Wärmetauscherblock und Herstellungsverfahren
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Cited By (80)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002201A (en) * 1974-05-24 1977-01-11 Borg-Warner Corporation Multiple fluid stacked plate heat exchanger
US4081025A (en) * 1974-05-24 1978-03-28 Borg-Warner Corporation Multiple fluid stacked plate heat exchanger
US4119140A (en) * 1975-01-27 1978-10-10 The Marley Cooling Tower Company Air cooled atmospheric heat exchanger
US4023618A (en) * 1975-08-18 1977-05-17 Union Carbide Corporation Heat exchanger headering arrangement
US4184543A (en) * 1976-07-06 1980-01-22 Olin Corporation Heat exchanger exhibiting improved mechanical and thermal stability
EP0014481A2 (de) * 1979-02-12 1980-08-20 Union Carbide Corporation Wandteil für Wärmetauscher, Kanalelement für Wärmetauscher und sie verwendender Wärmetauscher
EP0014481A3 (de) * 1979-02-12 1980-09-03 Union Carbide Corporation Wandteil für Wärmetauscher, Kanalelement für Wärmetauscher und sie verwendender Wärmetauscher
US4291759A (en) * 1979-08-28 1981-09-29 Hisaka Works, Limited Cross-current type plate heat exchanger
US4341601A (en) * 1980-02-20 1982-07-27 E. I. Du Pont De Nemours And Company Water evaporation process
US4497689A (en) * 1980-08-22 1985-02-05 Energiagazdalkodasi Intezet Heat engineering apparatus for carrying out thermodynamical processes comprising a pair of mutually opposite phase transitions of a work medium
US4424098A (en) 1980-11-12 1984-01-03 E. I. Du Pont De Nemours And Company Falling film evaporator
US4624305A (en) * 1981-02-25 1986-11-25 Institut Francais Du Petrole Heat exchanger with staggered perforated plates
US4869067A (en) * 1982-09-02 1989-09-26 Superstill Corporation Method of generating power
US4512393A (en) * 1983-04-11 1985-04-23 Baker Colony Farms Ltd. Heat exchanger core construction and airflow control
US4671856A (en) * 1984-04-26 1987-06-09 Superstill Technology, Inc. Method for recyclying energy in counterflow heat exchange and distillation
US4896411A (en) * 1985-05-02 1990-01-30 Carrier Corporation Method of making a multiple cell condensing heat exchanger
US4947548A (en) * 1985-09-20 1990-08-14 Carrier Corporation Method of making a heat exchanger for condensing furnace
US4874035A (en) * 1987-11-17 1989-10-17 Shinwa Sangyo Co., Ltd. Heat exchanger for cooling tower
US5560425A (en) * 1988-08-12 1996-10-01 Calsonic Corporation Multi-flow type heat exchanger
US5369883A (en) * 1989-02-24 1994-12-06 Long Manufacturing Ltd. Method for making an in tank oil cooler
US5538077A (en) * 1989-02-24 1996-07-23 Long Manufacturing Ltd. In tank oil cooler
US5036911A (en) * 1989-02-24 1991-08-06 Long Manufacturing Ltd. Embossed plate oil cooler
US5800905A (en) * 1990-01-22 1998-09-01 Atd Corporation Pad including heat sink and thermal insulation area
US5111577A (en) * 1990-01-22 1992-05-12 Atd Corporation Pad including heat sink and thermal insulation areas
US5271151A (en) * 1990-04-23 1993-12-21 Wallis Bernard J Method of making a high pressure condenser
US5186250A (en) * 1990-05-11 1993-02-16 Showa Aluminum Kabushiki Kaisha Tube for heat exchangers and a method for manufacturing the tube
US5375328A (en) * 1992-02-18 1994-12-27 Miralfin S.R.L. Method of making an oil radiator structure having flanges with external flat surfaces
US5768782A (en) * 1993-10-29 1998-06-23 Zexel Corporation Flat tube for heat exchanger and method for manufacturing it
US5441105A (en) * 1993-11-18 1995-08-15 Wynn's Climate Systems, Inc. Folded parallel flow condenser tube
US5576470A (en) * 1994-08-29 1996-11-19 Henkel Corporation Polyol esters of ether carboxylic acids and fiber finishing methods
WO1996010158A1 (en) * 1994-09-26 1996-04-04 Stellan Grunditz Heat exchanger
US5603159A (en) * 1994-09-29 1997-02-18 Zexel Corporation Method of producing heat exchangers
US5730213A (en) * 1995-11-13 1998-03-24 Alliedsignal, Inc. Cooling tube for heat exchanger
US6186223B1 (en) 1998-08-27 2001-02-13 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
US6244333B1 (en) 1998-08-27 2001-06-12 Zeks Air Drier Corporation Corrugated folded plate heat exchanger
US20100258280A1 (en) * 1998-12-04 2010-10-14 O'donnell Michael J Heat exchange tube with integral restricting and turbulating structure
US7255155B2 (en) 1998-12-04 2007-08-14 Beckett Gas, Inc. Heat exchanger tube with integral restricting and turbulating structure
US6688378B2 (en) 1998-12-04 2004-02-10 Beckett Gas, Inc. Heat exchanger tube with integral restricting and turbulating structure
US6378604B1 (en) * 1999-06-28 2002-04-30 Jon Charles Feind To heat exchanger
US6209202B1 (en) 1999-08-02 2001-04-03 Visteon Global Technologies, Inc. Folded tube for a heat exchanger and method of making same
US6648067B1 (en) * 1999-11-17 2003-11-18 Joma-Polytec Kunststofftechnik Gmbh Heat exchanger for condensation laundry dryer
US6382312B2 (en) * 2000-01-28 2002-05-07 Valeo Thermique Moteur Heat-exchange module, for a motor vehicle in particular
US20010047860A1 (en) * 2000-02-28 2001-12-06 Carlos Martins Heat-exchange module, especially for a motor vehicle
US6899167B2 (en) * 2000-02-28 2005-05-31 Valeo Thermique Moteur Heat-exchange module, especially for a motor vehicle
US20040149424A1 (en) * 2001-02-07 2004-08-05 Stephen Memory Heat exchanger
US7032313B2 (en) * 2001-02-07 2006-04-25 Modine Manufacturing Company Method of fabricating a heat exchanger
GB2384299A (en) * 2002-01-22 2003-07-23 Llanelli Radiators Ltd Automotive heat exchanger
GB2384299B (en) * 2002-01-22 2006-03-22 Llanelli Radiators Ltd Automotive heat exchanger
US6920918B2 (en) * 2002-03-30 2005-07-26 Modine Manufacturing Company Heat exchanger
US20030196785A1 (en) * 2002-03-30 2003-10-23 Wolfgang Knecht Heat exchanger
US20050067156A1 (en) * 2003-07-15 2005-03-31 Rottmann Edward G. Pressure containing heat transfer tube and method of making thereof
US8459342B2 (en) 2003-11-25 2013-06-11 Beckett Gas, Inc. Heat exchanger tube with integral restricting and turbulating structure
US20080029243A1 (en) * 2003-11-25 2008-02-07 O'donnell Michael J Heat exchanger tube with integral restricting and turbulating structure
US20060185835A1 (en) * 2005-02-03 2006-08-24 Toyoaki Matsuzaki Heat exchange plate
US20080223945A1 (en) * 2007-03-12 2008-09-18 Lau George H K Heat exchanger
US9250021B2 (en) * 2009-04-20 2016-02-02 Kyungdong Navien Co., Ltd. Heat exchanger
US20120037346A1 (en) * 2009-04-20 2012-02-16 Kim Young Mo Heat exchanger
US9074820B2 (en) * 2009-07-24 2015-07-07 Denso Corporation Heat exchanger
US20110017440A1 (en) * 2009-07-24 2011-01-27 Denso Corporation Heat exchanger
US20120198882A1 (en) * 2009-10-19 2012-08-09 Showa Denko K.K. Evaporator
US9359952B2 (en) 2012-02-03 2016-06-07 Pratt & Whitney Canada Corp Turbine engine heat recuperator plate and plate stack
DE102013218444A1 (de) * 2012-09-17 2014-03-20 Behr Gmbh & Co. Kg Wärmetauscher
US11774179B2 (en) 2017-06-22 2023-10-03 Rheem Manufacturing Company Heat exchanger tubes and tube assembly configurations
US20180372413A1 (en) * 2017-06-22 2018-12-27 Rheem Manufacturing Company Heat Exchanger Tubes And Tube Assembly Configurations
US11421949B2 (en) * 2017-12-21 2022-08-23 Mahle International Gmbh Flat tube for an exhaust gas cooler
US11448470B2 (en) 2018-05-29 2022-09-20 Cooler Master Co., Ltd. Heat dissipation plate and method for manufacturing the same
US11680752B2 (en) 2018-05-29 2023-06-20 Cooler Master Co., Ltd. Heat dissipation plate and method for manufacturing the same
US11131511B2 (en) * 2018-05-29 2021-09-28 Cooler Master Co., Ltd. Heat dissipation plate and method for manufacturing the same
US11913725B2 (en) 2018-12-21 2024-02-27 Cooler Master Co., Ltd. Heat dissipation device having irregular shape
US11883874B2 (en) * 2019-04-03 2024-01-30 Safran Nacelles Method for manufacturing a structural surface heat exchanger for a nacelle
US20220023931A1 (en) * 2019-04-03 2022-01-27 Safran Nacelles Method for manufacturing a structural surface heat exchanger for a nacelle
US11073344B2 (en) 2019-04-24 2021-07-27 Rheem Manufacturing Company Heat exchanger tubes
FR3099239A1 (fr) 2019-07-25 2021-01-29 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d’un tel échangeur de chaleur
FR3099238A1 (fr) 2019-07-25 2021-01-29 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d’un tel échangeur de chaleur
FR3099240A1 (fr) 2019-07-25 2021-01-29 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d’un tel échangeur de chaleur
WO2021014094A1 (fr) 2019-07-25 2021-01-28 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur
WO2021014091A1 (fr) 2019-07-25 2021-01-28 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur
WO2021014092A1 (fr) 2019-07-25 2021-01-28 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur
WO2021038152A1 (fr) 2019-08-23 2021-03-04 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d'un tel échangeur de chaleur
FR3100058A1 (fr) 2019-08-23 2021-02-26 Valeo Systemes Thermiques Echangeur de chaleur notamment pour véhicule automobile et procédé de fabrication d’un tel échangeur de chaleur

Also Published As

Publication number Publication date
ES211434U (es) 1976-05-16
FR2161913A1 (de) 1973-07-13
JPS4847644A (de) 1973-07-06
SE404304B (sv) 1978-10-02
IT966340B (it) 1974-02-11
ES436532A1 (es) 1977-01-01
DE2250233B2 (de) 1980-06-04
DE2250233A1 (de) 1973-04-19
AU464105B2 (en) 1975-08-14
ES211434Y (es) 1976-10-16
FR2161913B1 (de) 1976-06-04
JPS5146293B2 (de) 1976-12-08
GB1412444A (en) 1975-11-05
SE7513072L (sv) 1975-11-20
SE387155B (sv) 1976-08-30
CA976953A (en) 1975-10-28
GB1412442A (en) 1975-11-05
DE2265349A1 (de) 1977-08-18
AU4772972A (en) 1974-04-26
BR7207156D0 (pt) 1973-07-19
DE2265349B2 (de) 1980-09-18
GB1412443A (en) 1975-11-05

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