EP0014481A2 - Elément de paroi d'échangeur de chaleur, élément de conduit d'échangeur de chaleur et échangeur de chaleur les utilisant - Google Patents

Elément de paroi d'échangeur de chaleur, élément de conduit d'échangeur de chaleur et échangeur de chaleur les utilisant Download PDF

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Publication number
EP0014481A2
EP0014481A2 EP80100693A EP80100693A EP0014481A2 EP 0014481 A2 EP0014481 A2 EP 0014481A2 EP 80100693 A EP80100693 A EP 80100693A EP 80100693 A EP80100693 A EP 80100693A EP 0014481 A2 EP0014481 A2 EP 0014481A2
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EP
European Patent Office
Prior art keywords
wall
channel element
load
projection portions
wall member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP80100693A
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German (de)
English (en)
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EP0014481A3 (fr
Inventor
Ray Wallace Cotter
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Union Carbide Corp
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Union Carbide Corp
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Publication date
Application filed by Union Carbide Corp filed Critical Union Carbide Corp
Publication of EP0014481A2 publication Critical patent/EP0014481A2/fr
Publication of EP0014481A3 publication Critical patent/EP0014481A3/fr
Withdrawn legal-status Critical Current

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    • 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
    • F28D1/0308—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 the conduits being formed by paired plates touching each other
    • F28D1/0316—Assemblies of conduits in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements

Definitions

  • This invention relates to a heat exchange channel element having a multiplicity of wall projection portions disposed on its surface and to a heat exchanger comprising channel elements formed from such wall members.
  • a multiplicity of the Kun heat exchange channel elements are serially stacked in an array and arranged so that the wall projections on one channel element mate with and abut against corresponding wall projections on an adjacent channel element.
  • a heat exchanger fabricated in this manner has a first set of passages defined by and bound within the channel wall members and a second set of passages defined by and disposed between the channel elements.
  • high internal coolant pressures (of the first heat exchange medium flowed through the interior passages of the channel elements) on the order of 20 psig and higher may be accommodated, since in the stacked array the internal pressure is balanced by the support function of the adjacent channel element projections.
  • the heat exchanger can thus be economically and quickly fabricated, with the stacked channel element assembly (heat exchanger core) being disposed within a mechanically simple load-bearing structural frame assembly.
  • the channel element in the manner of the aforementioned Kun patent permits the channel element to be readily formed of thin and lightweight materials of construction such as aluminum.
  • the channel element may be stamped from thin aluminum sheet stock having a thickness of for example on the order of 8 - 10 mils.
  • This ability to use thin sheet metal material in fabricating channel elements has several inherent advantages, particularly in application to automotive radiators and heaters.
  • the use of low material thicknesses for the heat exchanger channel elements is associated with reduced material costs and reduced material weight for the fabricated heat exchanger.
  • the reduction in weight permits a given automobile power plant (internal combustion engine) to provide increased transportation fuel efficiency, with obvious advantage in our present economic and energy climate.
  • the use of thin wall members for the heat exchange channel element permits high heat transfer performance of the heat exchanger to be achieved. Such result is attributable at least in part to a short heat conduction path normal to the surface of the heat exchange channel element.
  • the increase in heat transfer capability of the thin-walled channel elements permits a substantial reduction in size of the fabricated heat exchanger to be achieved.
  • the Kun radiator will operate with a lower gas velocity at the primary surface of the channel element than is characteristic of conventional radiators. Such lowered air-side gas velocity in turn reduces the air-side heat transfer. Inasmuch as air-side heat transfer represents the controlling or limiting resistance to heat transfer in the radiator, the lower air-side gas velocity and heat transfer disadvantageously reduce the advantages otherwise achieved by the radiator in employing thin wall members.
  • the wall projection portions are oriented on the wall member surface with the major axes of the load-bearing end segments of the wall projection portions aligned substantially parallel to one another.
  • the above-described heat exchange wall member is suitably employed in a heat channel element including two spaced exchange channel element including two spaced apart wall members of such type, wherein the heat exchange channel element extends longitudinally and hasan elongated cross section bound by the aforementioned two spaced-apart wall members as side walls spaced apart by edge walls, the channel element having a first fluid entrance opening at one end and a first fluid exit opening at the opposite end.
  • the wall projection portions extend across substantially the full width of the side wall and are oriented with the major axes of the wall projection portion.load bearing end segments substantially perpendicular to the longitudinal axis of the channel element.
  • Another aspect of the invention relates to a heat exchanger comprising a multiplicity of channel elements of the above-described type, the channel elements being longitudinally aligned in parallel spaced relation each with a first fluid entrance opening at one end and a first fluid exit opening at the opposite end, and common inlet manifold means and common exit manifold means respectively associated with said first fluid entrance openings and said first fluid exit openings.
  • the load-bearing end segments of wall projection portions of the channel elements are shaped and arranged for mating with and abutting against load-bearing end segments of the projection portions of an adjacent channel element wall member, with the wall surface portions between the projection portions thereby forming spaces between adjacent channels through which a second fluid may be flowed in heat exchange with the first fluid.
  • a multiplicity of channel elements are disposed in a stacked array with secondary surface plate-like members being disposed between adjacent channel elements with the load-bearing end segments of the wall projection portions of the channel elements being shaped and arranged for mating with and abutting against the secondary surface members, whereby the secondary surface members are maintained in thermal contact with the channel elements along the abutting load-bearing end segments thereof.
  • primary surfaces are those which bound the passage walls separating the two fluids in heat exchange.
  • the flow path between the fluids is merely the thickness of the passage wall so that heat flows substantially normal to the wall.
  • secondary surfaces are nct in direct contact with the first heat exchange fluid but rather are substantially surrounded by only the second fluid. Accordingly, the heat flow path through the secondary surface is substantially parallel to the surface.
  • Figure 1 is an isometric view of a portion of a heat exchange wall member according to the present invention stamped from thin sheet metal.
  • the wall member 11 is stamped with a surface comprising ridge projections 17 extending elongately across the top surface of the wall member with flat top surface portions 18 at the extremities of the ridge projections, the flat top surface portions 18 having an aspect ratio (d 2 /d l ) of ar least 10, wherein d 2 is the longitudinal dimension of the ridge projection flat top surface portion and d l is the transverse dimension of the ridge projection flat top surface portion.
  • the flat top surface portions are surrounded by top surface portions 20 having a concave elevational contour. Edge surface portions 19 are formed between the unstamped margins 16 of the wall member and the aforementioned flat top surface and concave surface portions of the wall member.
  • FIG. 2 is an isometric view of a portion of a heat exchange channel element according to the present invention.
  • the heat exchange channel element 10 includes two spaced-apart wall members 11 and 12 of thermally conductive material bounding a fluid flow channel 13.
  • a multiplicity of wall projection portions 17 are distributed across the wall member surface and extend from the wall member surface with load-bearing end segments 18 at their extremities, whereby the channel element may be supported abuttingly against an adjacent structural member by the load-bearing end segments of the wall projection portions.
  • the two spaced-apart wall members 11 and 12 of the Figure 2 channel element constitute side walls of the channel element. These side walls are spaced apart by edge walls comprising edge wall portions 14 and 15.
  • the edge walls of the channel element may be formed separately from the side walls and joined to the latter as for example by braising or welding to form the completed channel element, however, it is more advantageous in general to form upper and lower halves of the channel element from unitary sheets of material as shown more 'clearly in Figure 4, so that the upper half of the channel element comprises (side) wall member 11, edge wall portion 14 and flange-like margins, and with the lower half of the channel element being similarly formed.
  • the upper and lower channel element halves may be joined to one another by welding, braising, adhesive bonding or other suitable joining method along the mating surfaces of the margins 16.
  • the side walls and edge walls of the Figure 2 channel element may suitably have a thickness of between about 0.003 and 0.25 inch.
  • the walls desirably have a thickness of between about 0.003 and 0.100 inch.
  • the channel element is formed in such manner that the wall projection portions 17 are provided in the form of ridges extending across substantially the full width of the side wall 11, with the wall member surface 20 between adjacent wall projection portions being concavely curved.
  • the wall projection portions 17 extend elongately on the wall member surface with the load-bearing segments 18 thereof having major axes which are substantially perpendicular to the longitudinal axis L-L of the channel element.
  • the load-bearing end segments 18 of the wall projection portions 17 intersect the edge wall portions 14, 15 of the channel element at edge wall surfaces 19,_which preferably-are convexly contoured as shown in Figure 3 to decrease hydrodynamic drag and pressure drop when a second heat exchange medium is flowed over the external surfaces of the channel element, from left to right as shown in Figure 4, in heat exchange with a first heat exchange medium flowing through the channel element interior flow channel 13.
  • the illustratively shown channel element in Figure 2 is a portion of a longitudinally extending element having its unillustrated extremity formed in the same manner as the extremity shown. Each extremity is provided with an end section 9 having flat side wall end portions 21.
  • the channel elements may be stacked in an array of such elements to form a heat exchanger core, with the side wall end portions 21 of adjacent channel elements mating abuttingly with one another in a manner as shown more fully hereinafter.
  • Figure 3 shows a sectional, elevational view of a portion of the Figure.2 heat exchange channel element along the longitudinal axis L-L.
  • the features of the channel element in Figure 3 are numbered correspondingly with respect to Figure 2.
  • the upper and lower wall members 11 and 12 of the channel element 10 are similarly formed with a concavely contoured wall surface between adjacent wall projection portions and with the upper and lower wall members 11 and 12 oriented with respect to one another so that the innermost point on the wall surface between adjacent wall projection portions of one wall member is vertically aligned with a load-bearing end segment of a wall projection portion of the other wall member.
  • the innermost point on the wall surface 20 of upper wall member 11 is vertically aligned with the load-bearing end segment 18a of lower wall member 12.
  • Figure 3 shows the geometric and dimensional characteristics of the channel element.
  • the wall surface between adjacent wall projection portions in this embodiment is concavely curved; specifically, the elevational contour of such wall surface is concavely circular, i.e., the surface in elevation has a uniform radius of curvature R1between the load-bearing end segments of adjacent wall projection portions.
  • the relative "depth" of the depression between adjacent wall projection portions is measured with reference to the base plane P of the wall member, which is a plane containing the extremities of wall surface projections extending outwardly from the wall member surface to a uniform extent.
  • all wall projection portions of the channel element extend outwardly from the wall member surface to a uniform extent, and the load-bearing end segments are flat and horizontally aligned as shown, so that the load-bearing end segments in this embodiment lie fully in the base plane P of the wall member.
  • the remaining dimensional parameters in Figure 3 are measured by reference to the above-described base plane of the wall member.
  • the dimension H which in the Figure 3 embodiment provides a measure of the "depth" of the concavely contoured surface between adjacent wall projections, is the maximum height measured perpendicularly from the base plane P of the wall member to the innermost point (i.e., the furthest point from the base plane) on the wall member surface between adjacent wall surface projections.
  • the dimension d l is the length of the minor axis of the wall projection portion load-bearing end segment measured in the base plane of the wall member.
  • the length of the load-bearing end segment minor axis is simply the measured lateral dimension of the load-bearing end segment and this dimension is uniform across the width of the channel element along which the load-bearing end segment elongately extends.
  • the characteristic dimension of the load-bearing end segment in the direction of elongation of the associated wall projection portion (not shown in Figure 3), as shown more fully hereinafter, is the major axis of the load-bearing end segment.
  • the D dimension is the spacing between the respective points of intersection of major and minor axes of load-bearing end segments of adjacent wall projection portions, as measured in the base plane of the wall member.
  • the minimum channel clearance for the channel element is shown as dimension C L .
  • Figure 4 is a sectional elevational view of the Figure 1 channel element taken in cross section at a wall projection portion 17 of the upper wall member 11.
  • the channel element has an elongated cross section bound by the two spaced-apart wall members 11 and 12 as side walls spaced apart by edge walls formed by edge wall portions 14 and 15.
  • the channel element disembodiment is formed from corresponding upper and lower distinct integral halves which are bonded together along the facing surfaces of peripheral flange-like margins 16 ' .
  • the upper and lower halves of the channel element may suitably be prepared from sheet metal stock with the illustrated surface configuration by conventional fabricating techniques such as pressing, stamping, rolling or the like.
  • edge wall portion 14 adjacent the wall projection 17 has an elevational contour of convex slope.
  • edge wall surface 19 could be provided with a straight or concave contour.
  • the convex contour shown is generally preferred in practice, inasmuch as it allows the edge walls in the region of the wall projection portions to accommodate higher internal pressures than can be tolerated with linear or concave contours of the edge wall surface 19.
  • the convex edge wall surface 19 greatly reduces the frictional drag that would otherwise be associated with a blunt edge wall.
  • Figures 5 and 6 are sectional, elevational views of wall projection portions having elevational contours such as have usefully been employed in practice.
  • Figure 5 shows an elevational contour of the type shown more generally in the Figure 3 drawing, in which the side walls of the projection 17 intersect the flat load-bearing surface 18 at a sharp corner.
  • Figure 5 shows an alternative elevational contour in which the side walls of the projection 17 intersect the flat load-bearing surface 18 with a convex contour in the region of intersection.
  • the length of the major axis of the wall projection load-bearing end segment thus provides a measure of the extent of the wall support bearing surface provided at the extremity of the wall projection portion, between the extremities of the load-bearing end segment surface at opposite edges of the channel element as shown in Figure 7 where the extremities of the load-bearing end segment surface intersects the edge wall surface portions 19.
  • the minor axis d 1 is a measure of the dimensional extent of the wall projection load bearing surface along a direction transverse to the direction of elongation of the wall projection (substantially perpendicular to the channel element longitudinal axis in the embodiment of Figure 7).
  • the major axis and the minor axis of the wall projection load-bearing end segment are measured in the base plane of the wall member.
  • the wall projection load-bearing end segments of the channel element lie in the base plane of the channel element wall member, so that the major and minor axes of the load-bearing end segment are merely the length and width dimensions of the end segment.
  • the wall projection portions extend elongately on the wall member surface of the channel element with the load-bearing segments thereof having an aspect ratio (d 2 /d l ) of at least 10.
  • the reason for such minimum value of the aspect ratio is to provide a sufficient extent of elongation so that the channel element wall member has sufficient rigidity to accommodate high internal coolant pressure levels.
  • channel elements of the type shown in Figure 2-7 are able to be employed with significantly higher internal coolant pressures than have been achievable in thin-walled channel elements of the prior art, including those of Run U. S. Patent No. 3,757,856.
  • the channel element of the instant invention is particularly advantageous in application of the channel element of the instant invention to fabrication of automobile radiators, since in such application increased coolant pressures serve to increase the boiling temperature of the coolant, thereby permitting the radiator to accommodate higher engine temperatures and to function with the same degree of efficiency in a more compact radiator configuration.
  • the aspect ratio d 2 /d l is at least 30.
  • the wall projection portions of the channel element in accordance with the present invention are oriented on the wall member surface with the major axes of the load-bearing end segments of the wall projection portions aligned substantially parallel to one another.
  • the distribution of wall projection portions across the wall member surface of the channel element is characterized by dimension D, which equals the spacing between the major axes of load-bearing end segments of adjacent wall projection portions, as measured perpendicularly to the major axes in the base plane of the wall member.
  • the base plane of the wall member is a plane containing the extremities of wall surface projections extending outwardly from the wall member surface to a uniform extent.
  • the wall projection portions on the wall member surface of the channel element have a dimensional size and a dimensional relationship therebetween defined by a D dimension of between about 0.2 and 3.0 inch, a H/D ratio of between about 0.05 and 0.5, and a D/d l ratio of between about 1.5 and 50.
  • the upper limit on the D dimension of 3.0.inch is imposed because at spacings above such value the heat exchange area per cubic foot of heat exchange volume of the channel element or stacked array of channel elements decreases disproportionately and the ability of the channel element wall member to accommodate increasing differential pressure across the wall is undesirably reduced.
  • the lower limit on the D dimension about 0.2 inch dictated by pressure drop considerations for the external heat exchange medium flowed over the exterior surfaces of the channel element; at spacing values of less than about 0.2 inch, the pressure drop tends to become unduly large, so that the advantages of the invention, of maintaining low external heat exchange medium pressure drop consistent with high heat transfer performance, are increasingly difficult to achieve.
  • H the maximum height measured perpendicularly from the base plane of the wall member to the innermost point on the wall member surface between adjacent wall surface projections, is related to the aforementioned D dimension by the constraint that the ratio H/D is between about 0.005 and 0.5.
  • the parametric range of values permissible for the H/D ratio is associated with maximum and minimum values which are based on considerations of the maximum and minimum allowable values for the D dimension, as discussed above, and the maximum and minimum allowable values for the parameter H.
  • the maximum allowable value for H in a given application is determined by the requirement of achieving a necessary minimum level of heat exchange area per cubic foot of heat exchange volume, as necessary for efficient hear transfer.
  • the lower limit on H is imposed by heat exchange surface area considerations, however, in this case the limit is dictated by the incremental cost required in providing the contoured surface as compared with the additional area provided by such contoured surface when compared with an uncontoured planar wall member. All of these various considerations are effectively accommodated by a H/D ratio of between about 0.05 and 0.5.
  • D/d l ratio of between about 1.5 and 50 is based on the various considerations for maximum and minimum values of D, as discussed above, and maximum and minimum allowable values of d 1 .
  • the minor axis dimension on the load-bearing surface of the wall projection portion, dl is fixed by two competing considerations. As the value of d 1 increases, the maximum allowable differential pressure across the channel element wall member will increase, while the available surface area of the channel wall element for heat exchange will decrease. As a result, in any application of the channel element of the invention, the relative degree of importance of the heat exchange considerations as opposed to strength considerations for the channel element will set the upper limit on the value of dl.
  • the lower limit on the minor axis dimension of the projection load-bearing segment is determined by manufacturing tolerances, by strength considerations, i.e., the need to insure that the load which is concentrated at the load-bearing surface does not produce stresses sufficient to deform or rupture the walls of the channel element, and by fabrication limitations associated with the material thickness of the channel element wall member. Tnese various considerations may be effectively accommodated under D/d l ratio of between about 1.5 and 50.
  • the channel element is preferably formed with the following geometric and dimensional characteristics: an H value of between about 0.035 and 0.080 inch; a D value of between about 0.4 and 1.1 inch; and a d 1 of between about 0.01 and 0.05 inch.
  • the H/D ratio is preferably between about 0.05 and 0.4, on the basis of the previously discussed considerations applicable to such parameter.
  • the elevational contour of the wall member projection portions should be such as to maintain at acceptable levels in both the projection portions and the other portions of the channel wall.
  • the projection portions should have an elevational contour such that the ratio 6/R is between about 4° and 2500° per inch, and most preferably between about 4° and 100° per inch for a wall member wherein the wall surface between adjacent projection portions has an elevational contour which is concavely circular, i.e., the radius of curvature of the wall member surface between the load-bearing end segments of adjacent wall projections is constant.
  • ⁇ is the included angle between a tangent to the wall projection side wall at the point of intersection with the load-bearing segment of the projection and a plane para- lellel to the base plane of the wall member.
  • R 1 is the minimum radius of curvature of the wall projection side walls. The minimum radius of curvature R 1 may be measured readily conveniently by the well-known optical comparator. In general, if ⁇ is relatively low, then R 1 (the minimum radius of curvature) can be relatively small. If the wall projection angle ⁇ is large in value, then R 1 should also be relatively large in magnitude.
  • the upper limit on the ⁇ /R 1 ratio of 2500°/inch is based on wall projection portions having a truncated conical elevation contour, such as is shown in Figure 10 - 12, described hereinafter in greater detail.
  • the magnitude of the projection angle ⁇ should not exceed 35°.
  • the lower limit. for ⁇ /R 1 of 4°/inch is based on a wall projection having a concavely curved projection side wall contour and a flat load-bearing end segment, with minimum contour height H and the largest value of spacing D permitted based on structural stress considerations.
  • the two spaced-apart wall members 111 at 112 constitute side walls of the channel element which are spaced apart by edge walls made up edge wall portions 114 and 115.
  • the channel element is fabricated from upper and lower halves, with the upper half of the channel element being stamped from a single piece of sheet metal,so that the upper and lower side walls and their associated edge wall portions are formed from a unitary sheet of material.
  • the channel element halves so formed are provided with peripheral margins 116 which are not deformed and thus permit mating and bonding of the upper and lower channel element halves in the manner previously described in connection with Figure 2 herein.
  • the channel has a first fluid entrance opening 131 at one end and a first fluid exit opening 130 at the opposite end, with the end sections 121a and 121b of the channel element being characterized by flat side walls which form mating surfaces for stacking of a series of channel elements on top of one another in an array to form a heat exchanger core assembly, as descirbed hereinafter in greater detail.
  • Figure 9 is a plan view of a portion of the channel element 110 of Figure 8, showing the dimensional characteristics thereof. As shown, each of the wall surface projection portions 117, in contrast to the wall projection portions of the embodiment of Figures 2 - 7, do not extend substantially across the full width of the channel element, but rather only a portion of the width.
  • FIG 11 is an isometric view of a portion of the heat channel element of Figure 10, showing the details of the wall member projection portion thereof.
  • the channel element includes two spaced-apart wall members 220 as side walls spaced apart from one another by edge 214 and 215 so that the side and edge wall members together bound and enclose a fluid flow channel 213, whereby a first heat transfer fluid medium may be flowed through the interior channel 213 in heat exchange with a second heat transfer medium flowed over the exterior surfaces of the channel element.
  • On the exterior surface of the channel element wall member 220 is disposed a multiplicity of wall projection portions 217 having flat load-bearing surface 218 at their extremities.
  • the channel element shown in Figure 11 differs from those of Figure 2 - 9 in that the former has a wall surface between adjacent projections which is planar and not continuously curved as in the preceding described embodiments.
  • the wall projection portions in the Figure 12 embodiment may be formed from the wall members as by stamping, pressing, rolling and the like, as in the case of the preceding described embodiments, or, alternatively, the wall projection portions may be provided as separate and distinct structural elements which are bonded or otherwise affixed to the flat wall member surface of the channel elements.
  • the provision of the wall member 220 as a separate and distinct structural part of the channel element from the wall projection portion 217 permits the fabrication of the channel element to be potentially simplified, inasmuch as no stamping, rolling or other forming step is necessary for the side wall surface.
  • the channel element could be fabricated from a flattened tube by soddering, braizing, or otherwise joining the projection portion 217 to the exterior wall member surface 220, with the wall projection portion being machined, cast or otherwise constructed by any suitable forming method.
  • Figure 12 is an elevational view of a stacked array of two channel elements of the type shown in Figures 10 and 11,. showing the abutment and mating of the load-bearing segments of wall projections portions of adjacent channel elements in the array.
  • the channel elements 210 and 210a are each provided with a multiplicity of wall projection portions 217 distributed across their wall surfaces.
  • Each wall projection portion 217 is provided with a flat load-bearing surface 218 at its extremity, so that the projection portions have a truncated conical elevational contour characterized by a wall projection angle 8 of preferably less than 35° and a ratio ⁇ /R 1 suitably having a value of between 4° and 2500° per inch, as discussed earlier herein.
  • the minimum radius of curvature of the wall projection, R I is measured in the region of the intersection of the projection side wall and the flat surface 220 of the channel element wall member.
  • each channel element is structurally identical with the wall projection portions of the topside and bottomside of the channel element being vertically aligned.
  • the load-bearing end segments of wall projection portions of the channel element are shaped and arranged for mating with and abutting against load-bearing end.segments of the projection portions of the adjacent channel element side wall, so that the wall surface portions between the projection portions thereby form spaces between adjacent channel through which a second fluid may be flowed in heat exchange with first fluid passed through the interior channel of the respective channel elements.
  • Figure 13 shows an array wherein the channel elements are formed with their upper and lower wall projections staggered with respect to another.
  • the channel elements in Figurel3 are generally similar in construction to the channel elements employed in the array of Figure 12, the choice alternative Figure 12 and Figure 13 array configurations being a matter of choice to the heat exchanger designer in a given application.
  • Figure 13 is an isometric view of a channel element according to the present invention, formed in a manner similar to that shown and described in connection with Figures 2 - 7, but with a secondary surface fin at one edge thereof.
  • FIGresponding features of the Figure 14 channel element are numbered correspondingly with rescect to Figures 2 - 7, but with the respective reference n:nbers in Figure 14 being numbered with respect to the Figureis 2 - 4 drawings by addition of 200 to the corresponding reference number in Figures 2 - 4.
  • the numbering of Figure 14 is also common to Figures 15 and 16 , as heraim- after described.
  • the secondary surface fins shown in Figures 14'- 16 are of a type as described in Kun U. S. Patent No.
  • the secondary surface fin members are joined to the primary surface channel element at the edge wall margins 316 and, in practice, it may be des able to form the channel member with the secondary surface fin member integral with one or the other of the halve; of the channel element.
  • a single fin member 350 is joined to the channel element at one edge thereof along margin 316.
  • the fin is, consistent with the teachings of the above-mentioned Kun patents, suitably provided with slots or louvers 351 along substantially the entire length of the fin.
  • the channel element shown in Figure 15 represents a modification of the Figure 14 channel element wherein the latter is provided with an additional fin 352 having louvered surface distortions 353 distributed across its surface along the length thereof, the additional fin being provided on the opposite edge wall from the first fin 350.
  • the channel element is provided with dual fins 354 and 356 at its opposite edges, the fins having surface distortions 355 and 357. in the form of "louvered slots of the type described previously in connection with Figures 14.
  • each channel element is finless, so that when the channel elements are stacked in array to form a heat exchanger core assembly, they can be easily headered in the heat exchanger final assembly by prior art headering means.
  • the fins in the Figures 14 - 16 embodiments can be separately attached to the longitudinal edge of the channel element, as for example by welding or braizing, but, as mentioned, the fins are preferably integral with the edge walls of the channel elements. Such integral construction greatly improves the heat transfer performance of the fins.
  • Figure 17 is an elevational view of a portion of a stacked array of heat exchange channel elements of the type shown in Figures 2 - 7.
  • the stacked array 400 is made up of heat exchange channel elements 110 to form a heat exchanger core assembly.
  • the channel elements in the Figure 17 array are longitudinally aligned in parallel spaced relation, i.e., to provide spaces between adjacent channels through which second fluid may be flowed in heat excha. ge with a first fluid being conducted through the channel interior passages.
  • Each channel element has a first fluid entrance opening at one end and a first fluid exit opening at the opposite end, as previously described.
  • the channel elements 410 in the array have wall projection portions 417 having load-bearing end segments which are shaped and arranged for mating with and abutting against load-bearing end segments of the projection portions of an adjacent channel element side wall, with the abutting load-bearing surfaces of the channel element facing projections being adhesively bonded to one another by bonding medium 402.
  • bonding of the mating and abutting load-bearing surfaces of the channel element wall projections is not essential in the practice of the invention, and in some instances it is preferable to mate an abut the opposed wall projection end-segments against one another without any interposed bonding medium.
  • the end sections 421 of the channel element in the stacked array are of enlarged cross section relative to the intermediate sections of the channel elements and, as previously described, are provided with flat side wall portions which permit mating of adjacent channel elements in the manner shown.
  • adhesive bonding medium 401 it is generally desirable to adhesively bond the channel element . in section flat side wall portions to one another by adhesive bonding medium 401, so as to insure leak tightness of the associated inlet or outlet face of the stacked array at the extremities of the tubes, i.e., so that the first fluid introduced to or withdrawn from the channel element at its extremity does not leak out of the heat exchanger between adjacent channel element end section.
  • the bonding media 401 and 402 may suitably comprise an epoxy or other conventional adhesive material.
  • Figure 18 is a modification of the form of channel element stacked array shown in Figure 17.
  • the multiple channel elements 410 are disposed in the stacked array 400 with secondary surface plate-like members 403 being disposed between adjacent channel elements with the load-bearing end segments 418 of the wall projection portions 417 of the channel elements being shaped and arranged for mating with and abutting against the secondary surface members, whereby the secondary surface members are maintained in thermal contact with the channel elements along the abutting load-bearing end segments thereof.
  • the sequential projections of varying height mate abuttingly with complimentary projections of the adjacent channel element so that the channel elements are oriented parallelly with respect to one another, i.e., so that their longitudinal axes are parallel with respect to one another.
  • the load-bearing extremities of all of the wall projections are flat and parallel to the channel element wall surface between adjacent wall projections.
  • each channel element has associated therewith two base planes, base plane P 1 associated with the shorter wall projections of the channel element and base plane P 2 associated with the taller wall projections of the channel element.
  • base plane of the channel element wall member is a plane containing the extremities of wall surface projections extending outwardly from the wall member surface to a uniform extent.
  • the channel element likewise is characterized by two values of the H parameter, the maximum height measured perpendicularly from the base plane of the wall member to the innermost point on the wall member surface between adjacent wall surface projections.
  • the H value associated with base plane P I is H 1 and the H value associated with base plane P 2 is H2 .
  • each value must satisfy the dimensional criteria of the invention, e.g., the H/D ratio must be between about 0.05 and 0.5.
  • the D spacing parameter will have the same numerical value as measured in either base plane associated with adjacent wall projections of different height, when the major axes of the wall projections under consideration are projected into the given base plane.
  • Figure 20 is an elevational view of two aligned channel elements 60 and 61 adapted for mating with one another along the surfaces of their load-bearing end segments.
  • chamel element 60 has disposed on its upper wall member surface wall projections 65 having a male load-bearing end segment 72 with a minor axis of length D 1 , as measured by the projected length of such minor axis in base plane P 1 containing the extremities of the wall surface projection on the upper wall surface of the channel element.
  • wall projection portions 66 On the lower wall member surface of channel element 60 are disposed wall projection portions 66 having female load-bearing surfaces 71 at their extremities, with the outermost extremities of the wall projection portions lying in base plane P .
  • the H dimension on the upper surface of the channel element, H u may be different from that associated with the lower wall surface, H 1 .
  • the channel element 61 in the Figure 20 array is similarly provided with wall projection portion 67 on its upper surface having male load-bearing end segements 69 and wall projection portion 68 on its lower wall member with female load-bearing segments at their extremities.
  • the adjacent channel element 60 and 61 may be mated with one another so that the male and female-load-bearing surfaces 69 and 71 of associated wall projections . 67 and 66 interfit with an abut against one another.
  • FIG 21 is an isometric view of a portion of a heat exchange channel element according to another embodiment of the invention, having two distinct alternative configurations disposed on its upper wall member surface.
  • the channel element 74 includes two spaced apart members 78 and 79 of thermally conductive material bounding a fluid flow channel 77 and having 'the wall section portions 80 and 82 disposed on its wall member surface 75 and extending therefrom with load-bearing end segments 81 and 83 respectively at their extremities, whereby a channel element may be supported abuttingly against an adjacent structural member by the load-bearing end segments of the wall projection portions.
  • the wall members 78 and 79 constitute side walls of the channel element spaced apart by edge walls 76.
  • Each of the wall projection portions 80 and 82 extend elongately on the wall member surface 75 across the width of the channel element along a direct substantially perpendicular to the longitudinal axis L-L of the channel element.
  • The-load-bearing end segments of the wall projection portions shown in Figure 21 differ from those previously described in that the load-bearing surface as a continuously varying elevation along the major axis direction of the wall projection, the first wall projection 80 having a load-bearing surface 81 which is undulate in elevational contour along the major axis direction, while the second wall projection 82 has a load-bearing surface 83 is of saw-tooth form along the major axis direction of the projection.
  • the length d of the major axis of the wall projection portion load-bearing end segment is measured as the projected length of the major axis in the base plane of the wall member, in the same manner that the non-linear elevational contour of the load-bearing end segment in the minor axis dimension is measured as the projected length of the minor axis, or, more simply, as the projected width of the load-bearing surface in the base plane of the channel element, as shown in Figure 20.
  • the channel elements are "nested" with the ridge projection load-bearing segments 454 bearing against the crest of the concave surface portion 455 of an adjacent channel element.
  • Such an arrangement permits very close stacking of the constituent channel elements and thereby provides a highly compact heat exchanger assembly.
  • FIG 23 is an isometric view of a portion of a stacked array of heat exchange channel elements according to the invention, as interleaved with secondary surface plate-like members to form a heat exchanger core assembly.
  • the heat exchanger core assembly 500 comprises a multiplicity of channel elements 510 of a type similar to that shown in Figure 15.
  • the structual features of the primary surface of the channel element is numbered correspondingly with respect to Figure 2 by addition of 500 to the corresponding reference numerals of Figure 2.
  • the secondary surface fins of the channel elements are numbered correspondingly with respect to Figure 15 by addition of 200 to the corresponding reference numerals for the secondary surface fins in Figure 15.
  • a multiplicity of channel elements are disposed with secondary surface plate-like members 503 being disposed between adjacent channel elements with the load-bearing end segments of the wall projection portions of the channel elements being shaped and arranged for mating with and abutting against the secondary surface members, whereby the secondary surface members are maintained in thermal contact with the channel elements along the abutting load-bearing end segments thereof.
  • the secondary surface plate-like members in this embodiment have a multiplicity of surface distortions 560 distributed across portions of their surfaces which are not in abutting contact with channel element load-bearing segments. More specifically, these plate-like member distortions comprise parallel slats and slotted apertures arranged in a louvered configuration across the width of the secondary surface member.
  • Figure 25 is sectional, elevational view of the plate-like member of Figure 24, taken along line A-A thereof.
  • the raised portion 605 and depressed portions 604 are punched in such manner that respective portions are parallelly aligned in elevational view with the undeformed surface 606 of the plate member 603.
  • This form of surface distortions of the plate-like secondary surface member permits highly efficient heat transfer along the gas flow path traversing the plate member in the direction shown in Figure 23.
  • the wind tunnel of Figure 2 6 is used to regulate the rate and temperature of an air flow through the passages formed between adjacent heat exchange channel elements in the radiator heat exchanger being tested.
  • Air entering the tunnel was first passed through a calibrated orifice 760, whichmeasures the air volume flow into a four cubic foot plenum chamber 761, and then fed through flow straightening screens 762 into a tapered adapter sections 763.
  • the adapter section 763 was provided to effect a smooth transition in the air flow between the plenum chamber 762 and a one square foot wind tunnel duct 764 coupled to a test radiator 765.
  • a blower (not shown) was positioned downstream of the radiator for controlling the air flow therethrough.
  • thermocouples Two grids, 772 and 773, containing four thermocouples, each of which was placed in the center of one-quarter of the flow passage area of the radiator 765, measured the average inlet and exit air temperature through the test radiators765.
  • an accurate test circuit was provided for measuring the heat transfer capacity of the test radiators.
  • test results based on evaluation of heat exchangers constructed in accordance with the present invention and heat exchangers constructed with the prior art, as derived from evaluation of the various test heat exchangers in the wind tunnel apparatus of Figure 24 are presented and discussed in detail hereinafter.
  • FIG 27 is an exploded assembly drawing of a portion of a heat exchanger according to the invention, comprising a stacked array of heat exchange channel elements of the type shown in Figure 15. As shown, the heat exchanger assembly comprises a stacked array 850 of heat exchange channel elements 851.
  • Each channel element has a longitudinal axis and is bounded by thermally conductive pressure withholding walls, with a first fluid entrance opening at one end, a first fluid exit opening at the opposite end, and end sections each having a cross-section bounded by flat side walls and by edge walls comprising edge wall portions extending outwardly from the side walls and convergently with respect to each other, with the outermost ends of the edge wall portions being contiguous and coextensive with respect to one another to form a leak-tight edge wall.
  • Adjacent channel elements in the array are stacked with their end section side walls in wall to wall contacting relationship and their end section edge walls in alignment to form a first fluid entrance face at one end of the array and a first fluid exit face at the opposite end of the array.
  • Each face has a perimeter defined by edge wall ends 854 of the stacked channel elements and outermost side wall ends 855 of the outermost channel elements 852 and 853 in the array.
  • the pressure withholding walls of adjacent channel elements in the interior of the array are disposed in spaced relationship with respect to each other for flow -of a second fluid through the array in the space between the channel elements in heat exchange with the first fluid.
  • the heat exchanger assembly shown in Figure 25 is of the cross-flow type and is constructed and arranged for flow of the second fluid through the array in a direction normal to the longitudinal asis of the channel elements.
  • the channel elements are disposed in the stacked array with their longitudinal axes lying in a common plane.
  • each sealing member is bonded to the abutted channel element egge walls associated therewith, and suitably has a length as measured parallel to the channel element longitudinal axes of at least 0.2 inch which is substantially greater than the thickness of the sealing member as measured perpendicular to the channel ele- m ent longitudinal axes at a lower extremity of the grooves in the bearing surface thereof.
  • clip members 869 are provided having a transversely extending first segment 870 a leak-tightly abutting the outer end. 857a of the sealing member 858, a longitudinally extending second segment 870b integrally joined to the transversely extending first segment and adhesively bonded to an exterior surface of the sealing member, and a third end segment 871integrally joined to the longitudinally extending second segment 870b.
  • the header tank means in Figure 27 comprise a header tank member 874 having enclosure end wall 877 and side wall875, 876 portions and a transversely outwardly extending flange protion880 at an end of each side wall portion.
  • the header tank member is provided with conduit 881 for first fluid introduction to or discharge from the heat exchanger assembly.
  • header tank member 874 and clip member869 are disposed in position as assembled, the third end segment 871 of the clip member is deformed contiguously around the transversely outwardly extending flange portion 880 of the header tank member to secure the header tank member in position.
  • apertures 879 in the flange portion 880 of the header tank member are brought into register with the apertures 873 in the transverse tabs of the clip members 869, apertures 865 in the transverse portion 864 of the angle brace member 861 and apertures 868 in the flange portion 867 of tie bar 866, so that bolt or screw means may be inserted through the aligned apertures so as to secure the assembly together.
  • apertures 879 in side wall 876 of the header tank member 874 are brought into alignment with apertures 863 in the longitudinally extending portion 862 of the angle brace member 861, so that screw or bolt means can be passed through the aligned apertures for additional securement of the assembly.
  • Figure 28 is a sectional plan view of a portion of the Figure 27 heat exchanger assembly, showing the details of construction thereof.
  • Channel elements 851 in the array 850 are stacked with their end section side walls 890, 891 in wall to wall contacting relationship adhesively bonded together by adhesive 893 such as epoxy.
  • the channel element and sections each have a cross-section bonded by flat side walls and by edge walls 854.comprising edge wall portions 854a, 854b extending outwardly from the side walls and convergently with respect to each other, with the outermost ends 895 of the edge wall portions being contiguous and coextensive with respect to one another to form a leak-tight edge wall.
  • a first fluid face is formed at an end of the array., having a perimeter defined by edge wall ends of the stacked channel elements and outmost side wall ends 892 of the outermost channel element 853 in the array.
  • the serpentine-shaped sealing member 858 extends along the end section edge walls of the channel element at a side of the stacked array.
  • the sealing member 858 has a bearing surface with a generally corrugated contour of grooves 859 and interposted ridges 860 shaped so that the grooves surround and abut the edge wall of a single channel element of the array with the interposed ridges extending inwardly and abutting the facing edge wall portions of adjacent channel elements.
  • the bearing surface of the sealing member 858 is bonded to the abutted channel element edge walls associated therewith by means of adhesive medium 897.
  • the exterior surface of the sealing member 858 is adhesively bonded to the longitudinally extending second segment 870b of the clip member 869 by means of adhesive medium 898.
  • the side wall of the outermost channel element 853 in the stacked array is adhesively bonded to tie bar 866.
  • the third end segment 871 of the clip member 869 is deformed contiguously around the transversely outwardly extending flange portion 880 of the header tank member to secure the header tank member in position.
  • Figure 29 is a sectional elevational view of. a portion of the heat exchanger assembly of Figure 27 .
  • the channel element 900 has an end section 901 and edge wall portions 902 having outer ends 903 which form a leak-tight edge wall.
  • the channel element features a secondary surface fin 904 with slatted, louver-type surface distortions 905 thereon.
  • the header tank member 874 has a transversely outwardly extending flange portion 680 at an end of the side wall portion 875.
  • the sealing member 858 has bearing surface with a generally corrugated contour of grooves 859 and interposed ridges 860, with each of the grooves shaped so as to surround and abut the edge wall of a single channel element of the array with the interposed ridges extending inwardly and abutting the facing edge wall portions of adjacent channel elements.
  • the bearing surface of the sealing member 858 is bonded to the abutted channel element edge walls associated therewith by adhesive bonding medium 910.
  • Sealing element 858 suitably has a length as measured parallel to the channel element longitudinal axis of at least 0.2 inch which is substantially greater than the thickness t of the sealing member as measured perpendicular to the channel element longitudinal axis at a lower extremity of the grooves in the bearing surface thereof.
  • the headering arrangement comprises clip member 869 having a transversely extending first segment 870 leak-tightly abutting the outer end 858a of the sealing member 858, a longitudinally extending second segment 906 integrally joined to the transversely extending first segment 870 and adhesively bonded. to an exterior surface of the sealing member by adhesive bonding medium 909, and a third end segment 871 integrally joined to the longitudinally extending second segment 906 and deformed contiguously arround the transversely outwardly extending flange portion 880 of the header tank member 874 to secure the header tank member in position.
  • the clip member second segment 906 is also adhesively bonded to the header tank member enclosure side wall portion 875 by adhesive 908 to further secure the header tank member in position.
  • FIG 30 is an isometric view of a portion of a heat exchanger assembly employing another type of headering arrangement which may suitably be employed in a heat exchanger according to the present invention.
  • the heat exchanger core 799 comprises a stacked array of channel elements 800 each having edge wall portions 802 which form a leak-tight edge wall.
  • the header tank member 874 has a transversely outwardly extending flange portion 880 at an end of the side wall portion 875.
  • the sealing member 858 has a bearing surface with a generally corrugated contour of grooves 859 and interposed ridges 860, with each of the grooves shaped so as to surround and abut the edge wall of a single channel element of the array with the interposed ridges extending inwardly and abutting the facing edge wall portions of adjacent channel elements.
  • the bearing surface of the sealing member 858 is suitably bonded to the abutted channel element edge walls associated therewith by an adhesive bonding medium as described hereinabove in connection with Figure 29.
  • Sealing element 858 preferably has a length as measured parallel to the channel element longitudinal axisof at least 0.2 inch which is substantially greater than the thickness of the sealing member as measured perpendicular to the channel element longitudinal axis at a lower extremity of the grooves in the hearing surface thereof.
  • the headering arrangement comprises clip member 869 having a transversely extending first segment 870 leak-tightly abutting the outer end 858a of the sealing member 858, a longitudinally extending second segment 806 integrally joined to the transversely extending first segment 870 which may be adhesively bonded to an exterior surface of the sealing member 858 by any suitable adhesive bonding medium, and a third end segment 871 integrally joined to the longitudinally extending second segment 806 and deformed contiguously around the transversely outwardly extending flange portion 880 of the header tank member 874 to secure the header tank member in position.
  • Figure 31 is a graph of convective heat transfer effectiveness factor plotted as a function of Reynold's number, for various heat exchanger embodiments of the present invention and for a heat exchanger constructed in accordance with Kun U. S. Patent No. 3,810,509.
  • the data from which the curve shown in Figure 31 were plotted were generated with radiator heat exchanger test samples, as hereinafter described, in the wind tunnel test apparatus shown in Figure 26 and described hereinabove.
  • the inlet air velocity was maintained at 90°F with a 100°F temperature difference between the inlet air and the temperature of the coolant fluid introduced into the radiator at the inlet face of the heat exchanger core assembly.
  • the coolant fluid circulated through the interior passages of channel elements in the radiator samples during the tests was a mixture of 45% ethylene glycol.,in water; this coolant was circulated through the radiator samples at the rate of 14.5 gallons per minute per foot width of the radiator, the width of the radiator being measured in a plane containing the longitudinal axes of the stacked channel elements, in a direction perpendicular to the channel element longitudinal axes.
  • Curve A of Figure 31 is based on data for a radiator sample constructed in accordance with the prior art.
  • Each channel element in the radiator sample was fabricated from 0.008 inch thick aluminum in the manner taught in Kun U. S. Patent No. 3,810,509.
  • Each channel element was 1.112 inches wide and the primary surface wall member was provided with eliptical shaped wall-supporting projection portions having an effective diameter, d as defined in the Kun patent of 0.137 inch.
  • the wall-supporting projection portions were provided in a triangular array with an effective spacing D of 0.48 inch between adjacent projections.
  • Each wall-supporting projection portion of the channel element wall member had a height H of 0.043 inch.
  • Secondary surface fins were provided fore and aft on the edge walls of the channel elements, each fin having a fin angle Y of 30°, a slot angle ⁇ of 90° and a slat angle of 45°, all as defined in the Kun patent.
  • Each secondary surface fin was 0.389 inch wide with an individual slat dimension for the louvered surface distortions on the fin of 0.035 inch by 0.327 inch.
  • the radiator heat exchanger constructed from the above-described channel elements had a density of 100 ⁇ channel elements per foot width of the heat exchanger, with the width of the stacked array being measured in a common plane containing the channel element longitudinal axes, in a direction perpendicular to the channel element longitudinal axes.
  • the ordinant of the Figure 31 draft is the dimensionless ratio of the Colburn factor j to the Fanning friction factor f. This ratio is a convective heat transfer effectiveness factor, with a value of 0.5 being the theoretical maximum value.
  • the abscissa of the draft is the Reynold's number, with the Reynold's number being based on the flow of air through the radiator heat exchanger interchannel spaces in a direction normal to the aforementioned common plane containing the longitudinal axes of the stacked channel elements in the radiator's core assembly.
  • a radiator fabricated from primary surface heat exchange channel elements, as described hereinabove, which is typical of the teachings of the aforementioned Kun patent, has a j/f value of about 0.225 at a Reynold's number of 600 which decreases to a j/f value of about 0.156 at a Reynold's number of about 4,000.
  • the heat exchange channel elements in the radiators were fabricated from 0.008 inch thick aluminum. Each channel element was 0.94 inch in width.
  • Each radiator had88 channel elements per foot width thereof, with the width of the raidator being measured in a common plane containing the longitudinal axes of the channel elements, as measured in a direction perpendicular to the channel element longitudinal axes.
  • Curve C is a plot of the heat transfer data for a radiator having a core as shown in Figure 16 herein.
  • the plotted data show that this radiator at a j/f value of 0.320 at a Reynold's number of 600 and a value of about 0.232 at a Reynold's number of 4,000.
  • This performance represents a 42% increase at the lower Reynold's number value of 600 and a 49% increase at the upper value of 4,000 relative to the prior art.radiator of curve A.
  • the radiator of curve C represents a 16% improvement in heat-transfer effectiveness factor at the lower Reynold's number value of 600 and a 6% increase at the upper value of 4,000, relative to the radiator of curve B.
  • the radiator of curve B is superior to the radiator of curve C in other respects, as will be shown more fully hereinafter.
  • Curve D is a plot of the heat transfer data for a radiator comprising channel elements formed similarly to the channel element of Figure 14 herein, with each channel element being provided with a single front longitudinal secondary surface fin and a single rear longitudinal fin.
  • the secondary surface fins each had slatted, slotted louvered surfac distortions in the manner taught by Kun U. S. Patent No. 3,845,814.
  • the front fin had an angle of orientation .; of 30°, while the rear fin had an angle of orientation of 0°.
  • Each fin had a slot angle a of 90° with a slat angle 9 of 45°.
  • the fins were each 0.324 inch in width with the individual slats having a dimension of 0.25 inch by 0.35 inch.
  • the fin angles ⁇ , ⁇ and ⁇ referred to above are as defined in the aforementioned Kun patent. These finned channel elements were stacked in the heat exchanger core as shown in Figure 17, with a smooth secondary surface plate-like member being disposed between the adjacent channel elements.
  • This radiator had a j/f value of 0.382 at a Reynold's number of 600 and a j/f value of 0.287 at a Reynold's number of 4,000.
  • This performance represents a 70% increase in the convective heat transfer efficiency factor at the lower Reynold's number value of 600 and an increase of 84% at the upper Reynold's number value of 4,000 relative to the prior art radiator of curve A.
  • Curve E plots the heat transfer data for radiator constructed in the same manner as the radiator of curve D, but without secondary surface plate-like members disposed between adjacent channel elements in the radiator core. Otherwise, tne radiator for curve E was identical in all dimensional respects to the radiator of curve D. as shown, the radiator of curve E had a j/f value of 0.422 at a Reynold's number of 600, and a value of 0.318 at a Reynold's number of 4,000. These end-point values for the particular Reynold's number range considered represent convective heat transfer performance improvement of 88% and 104%, respectively, relative to the prior art radiator of curve A.
  • the radiators constructed in accordance with the present invention all provided substantial improvement in convective heat transfer efficiency over the full Reynold's number range considered relative to the prior art radiator (curve A) constructed in accordance with the teachings of Kun U. S. Patent No. 3,810,509.
  • Figures 32 is a graph of heat transfer material effectiveness for the radiators previously described in connection with Figure 31, plotted as-a function of gas flow velocity at the face of the radiator.
  • the curve designations B - D in Figure 32 refer to the same radiators described in connection with the correspondingly labeled curves in Figure 31.
  • the ordinate of Figure 32 is the material effectiveness of the radiator, expressed in units BTU/lb. of metal in the radiator core, representing the amount of heat transferred, in BTUs, from the coolant flowing through the interior passages of the channel elements to the external heat transfer medium (air) flowing over the exterior surfaces of the channel elements and secondary surface members, if " present.
  • the abscissa of Figure 32 is the face velocity of the air flow through the radiator, measured in units of feet per minute; the face velocity is the gas velocity measured at the forward base of the radiator in the test assembly, as measured in a direction perpendicular to the plane containing the longitudinal axes of the stacked channel elements in the radiator core.
  • the use of secondary surface plate-like members between adjacent channel elements in the radiator represented by curves B and D, provided significant improvement in the heat transfer capacity per unit weight of metal employed in the radiator as compared to the material effectiveness values for the corresponding heat exchanger lacking such secondary surface plate-like members, represented by curves C and E, respectively.
  • the channel elements of the present invention also afford a substantial advantage relative to the. channel elements of the previously mentioned Kun patents with respect to the pressure loadings and differentials which the channel elements can accommodate.
  • Figure 33 is a graph of channel element wall member deflection plotted as a function of internal vacuum pressure and also as a function of internal buckling pressure for a channel element according to the present invention (represented by the curves labeled "M”) and a channel element according to Kun U. S. Patent No. 3,810,509 (represented by curves labeled " N ').
  • the channel element according to the present invention which was tested to yield the curves labeled "M" in the graph of Figure 33, was fabricated from aluminum of 0.008 inch thickness and had the dimensional parameters set forth in Table I herein under the heading "Figure 5 Elevational Contour".
  • the deflection measured for the prior art channel element curve N was about 0.43 mm while the wall deflection of the channel element according to the present invention at the same vacuum pressure level was - only 0.04 mm.
  • the deflection of the channel element according to the present invention was thus over 90% lower than the wall deflection of the channel element according to the prior art, at the vacuum pressure level of -20 in. Hg. f
  • the right hand plot in Figure 33 shows deflection of the channel element wall member as a function of positive internal pressure in the channel element interior passage.
  • the deflection values characteristic of the prior art channel element (curve N) are substantially and increasingly greater than the deflection values for the channel element according to the present invention (curve M).
  • the prior art channel element of curve N exhibited a wall deflection of approximately .37 mm, while the channel element according to the present invention exhibited a deflection of only 0.097 mm, a value 74% lower than deflection level of the prior art channel element.
  • the channel - element of the present invention can accommodate increasing internal pressure levels of up to 60 psi without undue or rapidly increasing deflection.
  • the deflection of the wall member according to the present invention is only about .12 mm, a deflection value which is already exceeded by the prior art channel element at an internal pressure of only 20 psi.
  • the various curves in Figure 33 thus clearly show the striking, substantial and unexpected improvement in channel element structural strength and integrity which is achieved by the channel element of the present invention -over prior art channel elements.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP80100693A 1979-02-12 1980-02-11 Elément de paroi d'échangeur de chaleur, élément de conduit d'échangeur de chaleur et échangeur de chaleur les utilisant Withdrawn EP0014481A3 (fr)

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FR2536161A1 (fr) * 1982-11-16 1984-05-18 Sueddeutsche Kuehler Behr Refroidisseur d'huile a plaques
FR2786559A1 (fr) * 1998-11-30 2000-06-02 Valeo Thermique Moteur Sa Echangeur de chaleur depourvu d'ailettes, en particulier pour vehicule automobile
GB2523243A (en) * 2013-12-23 2015-08-19 Snecma Heat Exchanger of a Turbomachine
CN107234432A (zh) * 2017-07-03 2017-10-10 湖北秀山智能科技股份有限公司 一种散热器芯体装配机及其装配方法

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JP6799680B2 (ja) * 2017-05-25 2020-12-16 株式会社日阪製作所 プレート式熱交換器
JP6799681B2 (ja) * 2017-05-25 2020-12-16 株式会社日阪製作所 プレート式熱交換器

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GB191119653A (en) * 1911-05-09 1911-12-14 Victor Luypaerts Improvements in Water Cooling Radiators.
US1472954A (en) * 1920-03-18 1923-11-06 Behringer Emil Radiator
DE2007400A1 (de) * 1970-02-12 1971-08-19 Rosenblad Corp Verfahren zum Formen von Beulenplatten Heizelementen fur Wärmetauscher unter An Wendung von hydrostatischem Druck
US3757856A (en) * 1971-10-15 1973-09-11 Union Carbide Corp Primary surface heat exchanger and manufacture thereof
US3810509A (en) * 1971-10-15 1974-05-14 Union Carbide Corp Cross flow heat exchanger

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Publication number Priority date Publication date Assignee Title
FR2536161A1 (fr) * 1982-11-16 1984-05-18 Sueddeutsche Kuehler Behr Refroidisseur d'huile a plaques
GB2130354A (en) * 1982-11-16 1984-05-31 Sueddeutsche Kuehler Behr Oil cooler of plate construction
FR2786559A1 (fr) * 1998-11-30 2000-06-02 Valeo Thermique Moteur Sa Echangeur de chaleur depourvu d'ailettes, en particulier pour vehicule automobile
GB2523243A (en) * 2013-12-23 2015-08-19 Snecma Heat Exchanger of a Turbomachine
GB2523243B (en) * 2013-12-23 2020-03-04 Snecma Heat Exchanger of a Turbomachine
CN107234432A (zh) * 2017-07-03 2017-10-10 湖北秀山智能科技股份有限公司 一种散热器芯体装配机及其装配方法
CN107234432B (zh) * 2017-07-03 2023-06-13 湖北秀山智能科技股份有限公司 一种散热器芯体装配机及其装配方法

Also Published As

Publication number Publication date
ES488390A0 (es) 1981-02-16
EP0014481A3 (fr) 1980-09-03
ES8103361A1 (es) 1981-02-16
BR8000793A (pt) 1980-10-29
JPS55107898A (en) 1980-08-19

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