US3757855A - Primary surface heat exchanger - Google Patents
Primary surface heat exchanger Download PDFInfo
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- US3757855A US3757855A US00189509A US3757855DA US3757855A US 3757855 A US3757855 A US 3757855A US 00189509 A US00189509 A US 00189509A US 3757855D A US3757855D A US 3757855DA US 3757855 A US3757855 A US 3757855A
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- wall
- projections
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- heat exchanger
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
- F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
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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
- F28D1/0391—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- 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
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- 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
- Y10S165/356—Plural plates forming a stack providing flow passages therein
- Y10S165/373—Adjacent heat exchange plates having joined bent edge flanges for forming flow channels therebetween
- Y10S165/374—Liquid to air heat exchanger having liquid passage formed by joined sheets
- Y10S165/376—Air passages defined by spacing projections of sheets
-
- 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, 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 substantially uniformly disposed unidirectional truncated conical wall-supporting projections formed from the wall.
- the projections are arranged so as to mate with and to 1 abut ,supporting projections of a similar adjacent wall.
- This invention relates to a thin metal or plastic plate heat exchange channel element having on a portion of its surface substantially uniformly disposed unidirectional wall-supporting truncated conical 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 primary 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 following reasons:
- the present invention overcomes the above drawbacks by providing an all-purpose, primary-surface heat exchange channel element having on at least a portion of its surface substantially uniform disposed unidirectional truncated conical wall-supporting projections.
- the heatexchange element is economical to fabricate and when employed in stacked units, they are admirably suited as a heat exchanger 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 andsubstantially uniformly disposed on a portion of its wall surface unidirectional wall-supporting truncated conical projections formed from the wall in a dimensional relationship to be discussed hereinafter.
- wall-supporting truncated conical projection have load bearing segments at their extremities which are shaped and arranged so as to mate with and abut against corresponding load bearing segments or wall-supporting truncated conical projections on a second surface.
- 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 canbe fed through one set of passages while a second cooler medium can be fed through theother 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.
- 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 sub stantially and directly between the plates and the fluid.
- a truncated conical projection from a wall of a thin sheet material is a protrusion in the wall of the material having a cone angle and a radius of curvature R as shown in FIG. 1A.
- Cone angle 0 equals the acute interior angle measured between the horizontal undeformed surface of the wall adjacent the protrusion and the substantially straight segment along the sloped side of the protrusion
- the radius of curvature R equals the radius of the surface segments on both sides of the bounding line of intersection formed by the protrusion and the undeformed surface of the wall adjacent the protrusion.
- the surface segment at the extremity of the truncated conical projection is a load bearing segment and is shaped so as to mate with, and abut against, similar type surface segments at the extremities of truncated conical projections on a second wall.
- the wall-supporting unidirectional truncated conical projections are disposed in a pre-aligned space relationship on the surface of each element so that when the walls are juxtaposed, the load bearing segments at the outer extremities of the wall-supporting projections hereafter referred to as buttons, will be in touching relationship.
- 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 wall with buttons matching those of the juxtaposed surface of the pair.
- the truncated conical projected wall of the channel element of this invention is designed as a primary-surface heat exchange channel element, 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 forfthe heat exchange channel element 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 mediumswithout intermixing of said mediums.
- At least one material selected from the group consisting of copper, steel, brass, titanium and Mylar is 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 truncated conical projections on the wall surface of the channel are somewhat restrictive depending on the end use environment of the heat exchange channel.
- the pattern of wallsupporting truncated conical projections can be arranged in a square, diamond, triangle or any other design conflguration 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 truncated conical projections should be designed and arranged in onlysuch 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. This will result in maximum primary-surface area being available for .heat transfer.
- ductive sheet of material by any conventional technique such as pressing, stamping, rolling or the like.
- a thermally conductive truncated conical projected sheet, so prepared, can be longitudinally folded upon itself with the projections facing either inwardly or outwardly, and the folded sheet segments spaced sufficiently apart so as to define a passage therebetween.
- the buttons project inwardly of the passage, they should match and contact with buttons extending inwardly across the passage from the opposite wall.
- the width of the passage so formed is thereby defined by the projected heights of the wall-supporting buttons from the undeformed surface of the walls. Since stress concentration may occur at the bending area of the sheet in its intended operationalenvironment, additional wall-supporting truncated conical projections may be disposed within the vicinity of such area 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 unidirec- 'tional wall-supporting truncated conical projected channel is then ready for use as a heat exchange element.
- 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 channels can be superimposed in button touching relationship wherein the heights of the projected buttons from the undeformed surface of the walls will define the size of the passage between adjacent channels.
- the channels will have to'be spaced apart by some external structure so as to define a passage between adjacent channels.
- a pressurized medium such as hot water
- a coolant medium such as cool air
- the wall-supporting truncated conical projected sheet could also be fabricated into a circular or spiral channel, or any multiple sided channel by appropriate bending and/or folding techniques.
- the heat exchange channelized elements so formed can also be shaped into any curvilinear configuration and then superimposed one on the other leaving defined passages therebetween to fonn a simple orcomplex geometry heat exchanger having multiple confined channelized passages and multiple separate passages defined by, and between, the outer surfaces of adjacent heat exchange channelized elements.
- the heat exchanger of this invention will provide a low frontal area and a low externalfluid pressure drop.
- Frontal area is the area of the projection of the entire array of heatexchange channels onto. a plane normal to the direction of fluid flow through the channclized passages.
- Lowexternal fluid pressure drop is the static pressure drop across the length of the flow path 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 A graph of applied pressure vs. surface deflection for 30 and 45 truncated conical projections in an aluminum wall.
- FIG. 1A Truncated cone surface.
- FIG. 2 Isometric view of an automobile radiator employing the heat exchange elements of this invention.
- FIG. 2A View taken of the longitudinal edges of a heat exchange element of FIG. 2.
- FIG. 2B Side view of elements 1 of FIG. 2.
- FIG. 2C Alternate embodiment of elements 1 of FIG. 2.
- FIG. 2D Alternate embodiment of the longitudinal edges of elements 1 of FIG; 2.
- FIG. 3 Isometric view of an array of truncated conical projected channels with outwardly projected buttons.
- FIG. 3A Cross-sectional view of channels in FIG. 3 taken along line 3A-3A.
- FIG. 3B Sectional side view of channels in FIG. 3 taken along line 38-38.
- FIG. 4 Isometric view of an array of truncated conical projected channels with inwardly projected buttons.
- FIG. 4A Sectional side view of channels in FIG. 4 taken along line 4A-4A.
- a truncated conical projected surface having a repeatable wall-supporting projection spacing D of between about 0.2 and about. 2.5 inch; a D/d ratio between about 3 and about 10, a HID ratio between about 0.05 and about 0.2, a cone angle 0 less than about 35, a R/D ratio of greater than about 0.075; and a sheet or wall thickness between about 0.003 and about 0.25 inch will be quite suitable.
- D wall-supporting projection spacing
- 0 is the acute interior anglemeasured between the horizontal undeformed surface of the wall adjacent the projected protrusion and the substantially straight segment along the sloped side of the protrusionyand R equals the radius of curvature of the surface segments on both sides of the bounding line of intersection formed by the protrusion and the undeformed surface of the wall adjacent the protrusion.
- the limitation on the D spacing is imposed because spacing less than 0.2 inch results in very small clearance passages on the projected side of the wall thereby being very susceptible to fouling, i.e., trapping of foreign matter between adjacent wall, which if excessive, would clog the passages for one of the fluid mediums. A high external fluid pressure drop per unit length of fluid flow path would also result.
- D/d ratio of less than 3 the allowable differential pressure across the wall of a channelized heat exchange element would go up, but a very large percentage of the surface area would be lost for heat exchange purposes.
- a D/d ratio greater than 10 would require tight manufacturing tolerance to insure the mating of bearing segments (buttons) on abutting walls and would also localize and concentrate the load at the contact point of the bearing segments and produce stresses sufficient to cause rupture or excessive deformation of the walls.
- a heat exchanger composed of truncated conical projected channels with a H/D ratio less than 0.05 would be susceptible to fouling and have a high external fluid pressure drop per unit length of fluid flow path.
- a H/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 R/ D ratio lower than 0.075 would result in excessive stresses along the bounding line of intersection formed by the conical projection and the undeformed surface of the wall adjacent the projection. In effect, the bounding line of intersection becomes a line of high stress concentration.
- a heat exchange wall having truncated conical projections with a cone angle of greater than 35 would result in excessive deflections of the unsupported areas disposed between the projections when pressure is applied to the wall. If such deflections are imposed repeatedly in service, then the material may be fatigued and crack after a relatively short sevice life. Additionally, deflections reduce the available space between heat exchange walls in the lower pressure passages, and result either in higher fluid pressure drop or in reduced rate of fluid flow.
- a material thickness t of less than about 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 pressure forces are not balanced within the channels require massive external structures to absorb the loads, while force-balanced embodiments wherein wall-supporting projections are bonded together and loaded in tension would be characterized by severe stress concentration in such bonded areas.
- the allowable ranges expressed above have to be narrowed to the following: a repeatable distance D between about 0.2 and about 0.6 inch, a D/d ratio of between about 3 and about 7; a H/d ratio of between about 0.05 and about 0.12; an angle 0 of less than about 35, preferably less than about 30, R/D ratio of greater than about 0.075; and a sheet or wall thickness between about 0.003 and about 0.02 inch.
- the preferred dimensions of a truncated concial projected 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/d ratio of about 4.8; a H/D ratio of about 0.08; an angle 0 less than about 30; a R/D ratio of greater than about 0.075; and a sheet or wall thickness of about 0.008 inch.
- the sheets were stamped with wall-supporting truncated conical projections arranged in a square pattern.
- the D spacing between the projected supports was 0.4 inch and the height H was 0.035 inch as shown in FIG. 1A.
- Pressure was applied to the surface of the aluminum sheet of the indented side of the sheet such as to place the cone material under compression, and the deflection at the center fo the diagonals of the square pattern was measured. This data for cone angle surfaces of 30 and 45 is shown plotted as curves on the graph of FIG. 1.
- deflections of the material tending to distort the wall are objectionable and should be minimized even though such deflections may be safely below the buckling point of the material.
- the material is usually stressed in bending and shear as it 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. Additionally, deflections 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.
- the stress in the material was also measured directly be means of strain gauges at 30 psi differential pressure.
- the stress was measured on the diagonal at the point where the inclined surface of the conical indentations met the flat undeformed segment of the material, i.e., in the radius R are. The following data was taken;
- the data shows the increase in stress resulting from use of the 45 cone surface over the 30 cone surface thus. demonstrating the high stress in the radius R are of the 45 cone surface.
- a die or the like can be prepared by conventional techniques.
- the die can be used in conventional type apparatus to impart by pressing, stamping or rolling the desired truncated conical projections onto a thin-walled thermally conductive sheet, such as aluminum.
- a thin-walled thermally conductive sheet such as aluminum.
- a rectangular aluminum sheet can be stamped or the like with the truncated conical projections. If the sheet is to be folded, then the central folding area shall be left free of the projections.
- the sheet which may have any desired thickness, as specified above, although about a 0.008 inch thick sheet is preferable, can then be longitudinally folded at the center forming a flattened tube-like configuration with thewall-supporting truncated conical projections facing inward or outward.
- two sheets may be prepared and formed appropriately at the longitudinal edges for bonding and then spaced apart by suitable 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 leak-tightly together to form tube-like configurations, an array of which can also be sealed leak-tightly into a header to form a radiator assembly.
- flattened tube-like heat exchange elements I can be air-tightly sealed along their edges 2-3 using a lock-seam joint filled with an adhesive I4, such as a suitable epoxy type adhesive.
- the heat exchange elements I having an horizontal surface 4 with spaced apart wall-supporting projections 5, can be superimposed with the surface extremities l7 (buttons) in touching relationship to form a multiple layer heat exchanger.
- the couching projected buttons 17 provide passages 15 between adjacent heat exchange elements I defined by the horizontal 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. 2C, thereby altering the passage area of element 1.
- the ends 6 of elements 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 l0 thereto.
- members 8 must also produce a leak-tight seal to header l0 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 11.
- a suitable resin for use in adhesive type joints for aluminum is Resin Type EA-9l4, manufactured by Hysol 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 follow ing steps:
- Alodine 1200 immersing the surfaces in Alodine 1200 at room temperature for 5 to 20 minutes (Alodine 1200 is manufactured by Amchem Products, Inc., Freemont, California, and contains acidic chromates and fluorides);
- FIGS. 3, 3A and 3B show 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.
- FIGS. 4 and 4A illustrate a similar array of elements 30 except that the wall-supporting projections 31 are inwardly projected. Passages 32 within elements 31 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 havingthem intermixed.
- a second cooler fluid shown as broken line arrows
- 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. 2, i
- header 10 which in turn could be coupled directly to a header similar to header 10 illustrated also in FIG. 2.
- 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 av coolant medium is to be accomplished without anintermixing of the media occurring.
- the design flexibility of the primary-surface heat exchange elements of this invention makes them admirably's'uited for complex type heat exchanger applications including'preheat ers for gas turbines and low gradc'heat rejectors for atomic power plants.
- Mylar is a tradename of E. l. DuPont Company
- 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 beingspaced by edge portions, said chan? nel element having an entrance opening at one end, an exit opening at the opposite end and on at least a portion of each wall surface substantially uniformly disposed only outwardly extending truncated conical wallsupporting projections formed from the wall, said projections having load bearingsegments at their extremities which are shaped for mating with and abutting against similar type load bearing segments on wallsupporting only outwardly extending projections of a second channel.
- said wall-supporting outwardly extending truncated conical projections having a dimensional size and a dimensional relationship therebetween defined by a H/D ratio of between about 0.05 and about 0.2; a D/d ratio of between about 3 and about 10, a l) dimension of between about 0.2 and 2.5
- H equals the maximum height measured perpendicularly from a surface which contains the extremities of the wallsupporting outwardly extending projections to the plane containing the undeformed surface of the wall adjacent the projection
- D equals the spacing between the centers of the closest adjacent wall-supporting outwardly extending projections on the surface of the wall
- d equals the equivalent diameter defined by the ratio 4a/p whereby a equals the area of the load bearing segment of the wall-supporting outwardly extending projection and p equals the perimeter of said load bearing segment
- 0 equals the acute angle measured between the horizontal undeformed surface of the wall adjacent the outwardly extending projection and the substantially straight segment along the sloped side of the projection
- R equals the radius of curvature of the surface segments on both sides of the bounding line of in-
- thermally conductive'heat exchange element is made from at least one material selected from the group consisting of metals, metal alloys, metal clads, plastics and plastic coated metals.
- heat exchanger of claim 3 wherein the heat exchange element is made of aluminum having a wall thickness of about 0.008 inch; said H/D ratio is about 0.08; said D/d ratio is about 4.8 and said D dimension is about 0.4 inch.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims (6)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US18950971A | 1971-10-15 | 1971-10-15 |
Publications (1)
Publication Number | Publication Date |
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US3757855A true US3757855A (en) | 1973-09-11 |
Family
ID=22697629
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US00189509A Expired - Lifetime US3757855A (en) | 1971-10-15 | 1971-10-15 | Primary surface heat exchanger |
Country Status (11)
Country | Link |
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US (1) | US3757855A (en) |
JP (2) | JPS4847643A (en) |
AU (1) | AU465923B2 (en) |
BR (1) | BR7207153D0 (en) |
CA (1) | CA969533A (en) |
DE (1) | DE2250222B2 (en) |
ES (1) | ES407585A1 (en) |
FR (1) | FR2156359B1 (en) |
GB (1) | GB1403063A (en) |
IT (1) | IT966339B (en) |
SE (1) | SE377826B (en) |
Cited By (41)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3866675A (en) * | 1973-08-03 | 1975-02-18 | Modine Mfg Co | Method of making a heat exchanger and a heat exchanger |
US4023618A (en) * | 1975-08-18 | 1977-05-17 | Union Carbide Corporation | Heat exchanger headering arrangement |
US4263967A (en) * | 1977-08-23 | 1981-04-28 | Hayes Timber Pty. Limited, Et Al. | Heat transfer pack |
US4291754A (en) * | 1978-10-26 | 1981-09-29 | The Garrett Corporation | Thermal management of heat exchanger structure |
US4298061A (en) * | 1980-08-15 | 1981-11-03 | The Singer Company | Heat exchanger with crimped flange seam |
US4461733A (en) * | 1983-03-28 | 1984-07-24 | Arvin Industries, Inc. | Capillary fin media |
US4544513A (en) * | 1983-04-15 | 1985-10-01 | Arvin Industries, Inc. | Combination direct and indirect evaporative media |
US4569391A (en) * | 1984-07-16 | 1986-02-11 | Harsco Corporation | Compact heat exchanger |
US4771826A (en) * | 1985-04-23 | 1988-09-20 | Institut Francais Du Petrole | Heat exchange device useful more particularly for heat exchanges between gases |
US4800954A (en) * | 1986-12-18 | 1989-01-31 | Diesel Kiki Co., Ltd. | Laminated heat exchanger |
US5077894A (en) * | 1989-05-30 | 1992-01-07 | The Charles Stark Draper Laboratory | Method of making a shell with an integral passage |
US5172762A (en) * | 1989-10-20 | 1992-12-22 | Sanden Corporation | Heat exchanger |
US5195580A (en) * | 1992-02-11 | 1993-03-23 | Ehrhardt Tool And Machine Co., Inc. | Heat exchanger seam and method of making same |
US5271151A (en) * | 1990-04-23 | 1993-12-21 | Wallis Bernard J | Method of making a high pressure condenser |
US5318114A (en) * | 1991-09-05 | 1994-06-07 | Sanden Corporation | Multi-layered type heat exchanger |
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 |
US5582241A (en) * | 1994-02-14 | 1996-12-10 | Yoho; Robert W. | Heat exchanging fins with fluid circulation lines therewithin |
US5632331A (en) * | 1993-09-30 | 1997-05-27 | Sanden Corporation | Heat exchanger |
US6035931A (en) * | 1995-05-30 | 2000-03-14 | Sanden Corporation | Header of heat exchanger |
US6311768B1 (en) | 1999-06-02 | 2001-11-06 | Long Manufacturing Ltd. | Clip on manifold heat exchanger |
US6321835B1 (en) * | 1996-12-24 | 2001-11-27 | Behr Gmbh & Co. | Heat transfer device, particularly exhaust gas heat transfer device |
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US7121002B1 (en) * | 1999-08-20 | 2006-10-17 | Max Roth | Heat exchanger |
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US20080223945A1 (en) * | 2007-03-12 | 2008-09-18 | Lau George H K | Heat exchanger |
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US20140345839A1 (en) * | 2011-12-01 | 2014-11-27 | Valeo Termico, S.A. | Heat Exchanger For Gas, Particularly For Engine Exhaust Gases |
US20160137019A1 (en) * | 2013-06-20 | 2016-05-19 | Valeo Systemes Thermiques | Tube Having A Container Of Phase Change Material For A Heat Exchange Bundle, In Particular For An Evaporator Of An Air Conditioning System Of A Vehicle |
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US20190101338A1 (en) * | 2017-02-28 | 2019-04-04 | General Electric Company | Additively Manufactured Heat Exchanger |
US11421949B2 (en) * | 2017-12-21 | 2022-08-23 | Mahle International Gmbh | Flat tube for an exhaust gas cooler |
US11913729B2 (en) * | 2020-07-17 | 2024-02-27 | Daikin Industries, Ltd. | Heat exchanger |
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DE3043045A1 (en) * | 1980-11-14 | 1982-06-24 | Metzeler Kautschuk GmbH, 8000 München | HEAT EXCHANGE ELEMENT MADE OF FLEXIBLE MATERIAL |
DE3141719A1 (en) * | 1981-10-21 | 1983-04-28 | Schäfer Werke GmbH, 5908 Neunkirchen | RADIATOR FOR THE DELIVERY OF HEAT TO ITS SURROUNDINGS, IN PARTICULAR COOLING RADIATOR FOR OIL-FILLED THREE-PHASE TRANSFORMERS |
JPH0619982Y2 (en) * | 1985-11-29 | 1994-05-25 | 株式会社東芝 | Counterflow heat exchanger |
CA1231014A (en) * | 1986-09-04 | 1988-01-05 | Zenon Todorski | Heating stove with plate heat exchanger and the method of manufacture thereof |
KR940010978B1 (en) * | 1988-08-12 | 1994-11-21 | 갈소니꾸 가부시끼가이샤 | Multi-flow type heat exchanger |
US5186250A (en) * | 1990-05-11 | 1993-02-16 | Showa Aluminum Kabushiki Kaisha | Tube for heat exchangers and a method for manufacturing the tube |
DE9203394U1 (en) * | 1992-03-13 | 1993-07-08 | Klingenburg GmbH, 4390 Gladbeck | Cross-flow heat exchanger |
JPH07167581A (en) * | 1993-10-22 | 1995-07-04 | Zexel Corp | Tube elements of lamination type heat exchanger |
DE19509787A1 (en) * | 1995-03-17 | 1996-09-19 | Behr Gmbh & Co | Heat exchanger built up of panels |
US6371201B1 (en) * | 1996-04-03 | 2002-04-16 | Ford Global Technologies, Inc. | Heat exchanger and method of assembly for automotive vehicles |
FR2784455B1 (en) * | 1998-10-07 | 2001-04-27 | Valeo Thermique Moteur Sa | FOLDED TUBE FOR AN ASSEMBLED HEAT EXCHANGER, PARTICULARLY A MOTOR VEHICLE, CORRESPONDING FOLDED TUBE BEAM AND HEAT EXCHANGER |
DE19909881A1 (en) * | 1999-03-06 | 2000-09-07 | Behr Gmbh & Co | Cross-flow heat exchanger of plate stack between cover plates uses knob or pleat forms of stack plates to define flow path between inlet and outlet using oval knobs and specified flow path dimensions. |
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WO2009057623A1 (en) * | 2007-10-31 | 2009-05-07 | Calsonic Kansei Corporation | Heat exchanger |
FR2991760B1 (en) * | 2012-06-11 | 2018-06-15 | Valeo Systemes Thermiques | THERMAL EXCHANGER AND METHOD FOR PRODUCING AN ASSOCIATED COLLECTOR |
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FR617047A (en) * | 1926-04-23 | 1927-02-12 | Laengerer & Reich Kuehler | Radiator for water cooling |
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- 1972-10-13 FR FR7236402A patent/FR2156359B1/fr not_active Expired
- 1972-10-13 GB GB4723772A patent/GB1403063A/en not_active Expired
- 1972-10-13 ES ES407585A patent/ES407585A1/en not_active Expired
- 1972-10-13 SE SE7213244A patent/SE377826B/xx unknown
- 1972-10-13 IT IT53372/72A patent/IT966339B/en active
- 1972-10-13 BR BR007153/72A patent/BR7207153D0/en unknown
- 1972-10-13 AU AU47728/72A patent/AU465923B2/en not_active Expired
- 1972-10-13 DE DE2250222A patent/DE2250222B2/en not_active Withdrawn
- 1972-10-13 JP JP47102623A patent/JPS4847643A/ja active Pending
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Cited By (55)
Publication number | Priority date | Publication date | Assignee | Title |
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US3866675A (en) * | 1973-08-03 | 1975-02-18 | Modine Mfg Co | Method of making a heat exchanger and a heat exchanger |
US4023618A (en) * | 1975-08-18 | 1977-05-17 | Union Carbide Corporation | Heat exchanger headering arrangement |
US4263967A (en) * | 1977-08-23 | 1981-04-28 | Hayes Timber Pty. Limited, Et Al. | Heat transfer pack |
US4291754A (en) * | 1978-10-26 | 1981-09-29 | The Garrett Corporation | Thermal management of heat exchanger structure |
US4298061A (en) * | 1980-08-15 | 1981-11-03 | The Singer Company | Heat exchanger with crimped flange seam |
US4461733A (en) * | 1983-03-28 | 1984-07-24 | Arvin Industries, Inc. | Capillary fin media |
US4544513A (en) * | 1983-04-15 | 1985-10-01 | Arvin Industries, Inc. | Combination direct and indirect evaporative media |
US4569391A (en) * | 1984-07-16 | 1986-02-11 | Harsco Corporation | Compact heat exchanger |
US4771826A (en) * | 1985-04-23 | 1988-09-20 | Institut Francais Du Petrole | Heat exchange device useful more particularly for heat exchanges between gases |
US4800954A (en) * | 1986-12-18 | 1989-01-31 | Diesel Kiki Co., Ltd. | Laminated heat exchanger |
US5077894A (en) * | 1989-05-30 | 1992-01-07 | The Charles Stark Draper Laboratory | Method of making a shell with an integral passage |
US5172762A (en) * | 1989-10-20 | 1992-12-22 | Sanden Corporation | Heat exchanger |
US5271151A (en) * | 1990-04-23 | 1993-12-21 | Wallis Bernard J | Method of making a high pressure condenser |
US5318114A (en) * | 1991-09-05 | 1994-06-07 | Sanden Corporation | Multi-layered type heat exchanger |
US5195580A (en) * | 1992-02-11 | 1993-03-23 | Ehrhardt Tool And Machine Co., Inc. | Heat exchanger seam and method of making same |
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 |
US5632331A (en) * | 1993-09-30 | 1997-05-27 | Sanden Corporation | Heat exchanger |
US5582241A (en) * | 1994-02-14 | 1996-12-10 | Yoho; Robert W. | Heat exchanging fins with fluid circulation lines therewithin |
US6035931A (en) * | 1995-05-30 | 2000-03-14 | Sanden Corporation | Header of heat exchanger |
US6944947B1 (en) * | 1995-11-01 | 2005-09-20 | Behr Gmbh & Co. | Heat exchanger for cooling exhaust gas and method of manufacturing same |
US7246437B2 (en) * | 1995-11-01 | 2007-07-24 | Behr Gmbh & Co. | Heat exchanger for cooling exhaust gas and method of manufacturing same |
US6321835B1 (en) * | 1996-12-24 | 2001-11-27 | Behr Gmbh & Co. | Heat transfer device, particularly exhaust gas heat transfer device |
US6530424B2 (en) | 1999-06-02 | 2003-03-11 | Long Manufacturing Ltd. | Clip on manifold heat exchanger |
US6332495B1 (en) | 1999-06-02 | 2001-12-25 | Long Manufacturing Ltd. | Clip on manifold heat exchanger |
US6311768B1 (en) | 1999-06-02 | 2001-11-06 | Long Manufacturing Ltd. | Clip on manifold heat exchanger |
US7121002B1 (en) * | 1999-08-20 | 2006-10-17 | Max Roth | Heat exchanger |
US6543530B2 (en) | 2000-04-06 | 2003-04-08 | Sanden Corporation | Heat exchanger having an improved pipe connecting structure |
US6595273B2 (en) * | 2001-08-08 | 2003-07-22 | Denso Corporation | Heat exchanger |
EP1331462A3 (en) * | 2002-01-22 | 2007-01-17 | Calsonic Kansei UK Limited | Automotive heat exchanger |
WO2006027761A2 (en) * | 2004-09-08 | 2006-03-16 | Ep Technology Ab | Heat exchanger with indentation pattern |
US20070261829A1 (en) * | 2004-09-08 | 2007-11-15 | Ep Technology Ab | Heat Exchanger With Indentation Pattern |
WO2006027761A3 (en) * | 2004-09-08 | 2006-05-18 | Ep Technology Ab | Heat exchanger with indentation pattern |
US20110180247A1 (en) * | 2004-09-08 | 2011-07-28 | Ep Technology Ab | Heat exchanger |
US8091619B2 (en) | 2004-09-08 | 2012-01-10 | Ep Technology Ab | Heat exchanger with indentation pattern |
US20080314574A1 (en) * | 2005-11-18 | 2008-12-25 | Methanol Casale S.A. | Method for the Production of a Plate Type Heat Exchanger and Related Heat Exchanger |
US7941921B2 (en) * | 2005-11-18 | 2011-05-17 | Methanol Casale S.A. | Method for the production of a plate type heat exchanger and related heat exchanger |
US20120312517A1 (en) * | 2006-10-06 | 2012-12-13 | Faist Componenti S.P.A. | Process for producing heat exchanger tubes and heat exchanger tubes |
US20090133865A1 (en) * | 2006-10-06 | 2009-05-28 | Gianfranco Natali | Process for producing heat exchanger tubes and heat exchanger tubes |
US8656987B2 (en) * | 2006-10-06 | 2014-02-25 | Faist Componenti S.P.A. | Process for producing heat exchanger tubes and heat exchanger tubes |
US8220152B2 (en) * | 2006-10-06 | 2012-07-17 | Faist Componenti S.P.A. | Process for producing heat exchanger tubes and heat exchanger tubes |
US20080223945A1 (en) * | 2007-03-12 | 2008-09-18 | Lau George H K | Heat exchanger |
FR2944591A1 (en) * | 2009-04-17 | 2010-10-22 | Valeo Systemes Thermiques | REFRIGERANT FLUID CIRCULATION TUBE, HEAT EXCHANGE BEAM AND HEAT EXCHANGER HAVING SUCH TUBES |
WO2010119100A1 (en) * | 2009-04-17 | 2010-10-21 | Valeo Systemes Thermiques | Coolant circulation tube, heat exchange bundle, and heat exchanger comprising such tubes |
US20140345839A1 (en) * | 2011-12-01 | 2014-11-27 | Valeo Termico, S.A. | Heat Exchanger For Gas, Particularly For Engine Exhaust Gases |
US9958216B2 (en) | 2012-09-28 | 2018-05-01 | Behr Gmbh & Co. Kg | Connecting system for a heat exchanger |
DE102012217873A1 (en) * | 2012-09-28 | 2014-04-03 | Behr Gmbh & Co. Kg | Connection system for a heat exchanger |
CN103712511A (en) * | 2012-09-28 | 2014-04-09 | 贝洱两合公司 | Connecting system for a heat exchanger |
US10144266B2 (en) * | 2013-06-20 | 2018-12-04 | Valeo Systems Thermiques | Tube having a container of phase change material for a heat exchange bundle, in particular for an evaporator of an air conditioning system of a vehicle |
US20160137019A1 (en) * | 2013-06-20 | 2016-05-19 | Valeo Systemes Thermiques | Tube Having A Container Of Phase Change Material For A Heat Exchange Bundle, In Particular For An Evaporator Of An Air Conditioning System Of A Vehicle |
US20190101338A1 (en) * | 2017-02-28 | 2019-04-04 | General Electric Company | Additively Manufactured Heat Exchanger |
US10502502B2 (en) * | 2017-02-28 | 2019-12-10 | General Electric Company | Additively manufactured heat exchanger |
US10830540B2 (en) | 2017-02-28 | 2020-11-10 | General Electric Company | Additively manufactured heat exchanger |
US11421949B2 (en) * | 2017-12-21 | 2022-08-23 | Mahle International Gmbh | Flat tube for an exhaust gas cooler |
CN109019511A (en) * | 2018-10-11 | 2018-12-18 | 广东索特能源科技有限公司 | A kind of methane reformer system using SOFC high-temperature flue gas |
US11913729B2 (en) * | 2020-07-17 | 2024-02-27 | Daikin Industries, Ltd. | Heat exchanger |
Also Published As
Publication number | Publication date |
---|---|
AU4772872A (en) | 1974-04-26 |
DE2250222B2 (en) | 1979-07-26 |
JPS5346502B2 (en) | 1978-12-14 |
BR7207153D0 (en) | 1973-07-19 |
IT966339B (en) | 1974-02-11 |
AU465923B2 (en) | 1975-10-09 |
DE2250222A1 (en) | 1973-04-19 |
CA969533A (en) | 1975-06-17 |
JPS5289853A (en) | 1977-07-28 |
FR2156359B1 (en) | 1976-06-04 |
FR2156359A1 (en) | 1973-05-25 |
ES407585A1 (en) | 1975-11-16 |
SE377826B (en) | 1975-07-28 |
GB1403063A (en) | 1975-08-13 |
JPS4847643A (en) | 1973-07-06 |
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Owner name: MORGAN GUARANTY TRUST COMPANY OF NEW YORK, AND MOR Free format text: MORTGAGE;ASSIGNORS:UNION CARBIDE CORPORATION, A CORP.,;STP CORPORATION, A CORP. OF DE.,;UNION CARBIDE AGRICULTURAL PRODUCTS CO., INC., A CORP. OF PA.,;AND OTHERS;REEL/FRAME:004547/0001 Effective date: 19860106 |
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