EP0627065B1 - Wärmetauscherzusammenbau - Google Patents

Wärmetauscherzusammenbau Download PDF

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Publication number
EP0627065B1
EP0627065B1 EP93905101A EP93905101A EP0627065B1 EP 0627065 B1 EP0627065 B1 EP 0627065B1 EP 93905101 A EP93905101 A EP 93905101A EP 93905101 A EP93905101 A EP 93905101A EP 0627065 B1 EP0627065 B1 EP 0627065B1
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EP
European Patent Office
Prior art keywords
heat exchanger
fluid section
fins
fluid
section
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.)
Expired - Lifetime
Application number
EP93905101A
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English (en)
French (fr)
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EP0627065A4 (de
EP0627065A1 (de
Inventor
Milne Jurisich
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Melanesia International Trust Co Ltd
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Melanesia International Trust Co Ltd
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Publication date
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Publication of EP0627065A1 publication Critical patent/EP0627065A1/de
Publication of EP0627065A4 publication Critical patent/EP0627065A4/de
Application granted granted Critical
Publication of EP0627065B1 publication Critical patent/EP0627065B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F42—AMMUNITION; BLASTING
    • F42B—EXPLOSIVE CHARGES, e.g. FOR BLASTING, FIREWORKS, AMMUNITION
    • F42B12/00—Projectiles, missiles or mines characterised by the warhead, the intended effect, or the material
    • F42B12/72—Projectiles, missiles or mines characterised by the warhead, the intended effect, or the material characterised by the material
    • F42B12/74—Projectiles, missiles or mines characterised by the warhead, the intended effect, or the material characterised by the material of the core or solid body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
    • 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
    • F28D1/0246—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 heat-exchange elements having several adjacent conduits forming a whole, e.g. blocks
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0083—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium
    • 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
    • F28F3/048—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 ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • 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
    • F28D2021/0084—Condensers
    • 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
    • F28D2021/0089—Oil coolers
    • 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
    • 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
    • F28D2021/0096—Radiators for space heating

Definitions

  • This invention relates to improved heat exchanger cores and in particular heat exchanger cores which incorporates a plurality of heat exchanger elements or modules which may be utilised in applications where heat energy is to be transferred from one fluid to another.
  • heat exchangers There are many types of heat exchangers known. These can be generally divided into two main groups, the first being shell-and-tube heat exchangers and the second being plate heat exchangers.
  • One example of a shell and tube heat exchanger comprises an array or bundle of tubes and a surrounding for external shell.
  • Plate heat exchangers may have plate-fin arrangements such as described in U.S.A. Patent 4,282,927 or a series of rectangular stacked plates creating flow channels from two or more fluids when the plates are sealingly stacked upon one another as described for example in U.S. Patent 4,823,867.
  • each of the two groups in order to manufacture the heat exchanger, a number of parts are usually fabricated and joined together.
  • shell and tube heat exchangers for example, a number of tubes are assembled into a bundle, and prior to having the ends of each tube sealed into corresponding apertures of a pair of tube sheets, baffles are installed along the length of the bundle.
  • the bundle of tubes, baffles and tube sheets are then placed inside a pressure vessel which seals a pair of end zones around the tube sheets so that there are two fluid flow paths defined, the first being around the outside of the tubes and between the tube sheets, and the second being inside the tubes and in end chambers of the pressure vessel.
  • the shell and tube configuration and the plate type heat exchanger there is a large amount of material dedicated to defining and sealing fluid flow paths, and since the flow paths are defined by joining fabricated parts, there is always the danger of one fluid leaking into another.
  • fabricated heat exchangers suffer from inefficiency brought about by a plurality of boundaries constituted by welds, joins or parts interconnecting adjacent components of the heat exchangers, the boundaries providing zones of resistance to the conduction of heat to heat transmission surfaces of the exchanger.
  • An integral part of heat exchangers formed by processes such as extrusion or casting are known as “primary structure” and must be differentiated from components welded or otherwise attached to the primary structure wherein such components including the boundaries are termed “secondary” structure.
  • surface(s) of primary structure are known as “primary” surface(s) and surface(s) of "secondary” structure known as “secondary" surface(s).
  • U.S. Patents 3,743,252; 4,352,008; 3,566,959, 4,567,074; 3,137,785 show that formation of one piece extrusions are not new and thus U.S. Patent 3,137,785 shows a one piece extrusion for use as a component in an electric heater comprising a body with longitudinally extending fins on each side of the body. Within the body are a plurality of extruded passages. However these internal passages are for receiving and containing tubular heating elements or thermally sensitive control elements and are not fluid passages.
  • U.S. Patent 3,566,959 concerns an aluminium extrusion for use as a heat sink in semi conductor rectifiers.
  • U.S. Patent 4,657,074 refers to a one piece aluminium extrusion tubular heat exchanger element which has a tubular body and a number of interior and exterior fins projecting integrally radially from the tubular body. However this reference is not considered relevant to this invention.
  • U.K. Patent 2 142 129 which describes a radiator formed from a rectangular elongate hollow body which is provided on each of two opposite sides with a plurality of spaced heat radiating fins to thus form a plurality of air channels located intermediate mutually adjacent fins.
  • a cover plate extends across outer edges of each set of fins to form with said fins a plurality of open ended channels through which can flow air which is heated by a transfer of heat from a hot fluid flowing through the elongate hollow body.
  • U.S. Patent 4,401,155 relates to a heat exchanger constructed from a plurality of stacked modules wherein each module has closed channels for high pressure flow and fins extending vertically up and/or down from the channels which form open channels suitable for low pressure flow when the modules are stacked parallel to each other along their length. It is specified that each fin be of uniform thickness and have an identical dimension perpendicular to the channels. Each module is generally formed from an aluminium extrusion.
  • the heat exchanger of U.S. Patent 4,401,155 is particularly directed at high pressure applications and especially where one heat exchange stream is at high pressure and another is at lows pressure. This has particular reference to cryogenic processes.
  • the heat exchanger assembly would not be efficient in relation to effective heat transfer because of the fact that the channel surface area is substantially the same as the fin surface area and in this regard it has been ascertained as described in more detail hereinafter that for efficient heat transfer to take place the surface area of the fins should be substantially greater than the surface area of the channels.
  • This is important in a situation wherein the density of one fluid which may pass through the fins (e.g. air) is significantly different to the density of the fluid passing through the channels (eg water). In this situation air has a density much less than water and this means that air will have a much less effective heat storage capacity than water.
  • heat exchangers formed as one piece extrusions having a plurality of fins generally will also be subject to the same disadvantages as described and thus references such as U.S. Patent 3,202,212, Australian Patent 85777/75, U.S. Patents 4,565,244; 3,743,252; 4,352,008; 3,566,959; 4,567,074; 3,137,785 and 3,467,180 will also be subject to these disadvantages.
  • thermoelectric cooler wherein semiconductor materials with dissimilar characteristics are connected electrically in series and thermally in parallel so that two junctions are created.
  • the semiconductor materials are N and P-type.
  • thermoelectrical cooler In a typical thermoelectrical cooler (TEC), alternative columns of these N-type and P-type semiconductor materials have their ends connected in a serpentine fashion by electrical conductors. These electrical conductors typically are metallisations formed on insulating or ceramic plates. With the application of direct current to the TEC, heat is absorbed on the cold side ceramic, passes through the semiconductor material and is dissipated at the hot side ceramic. A heat sink must be attached to the hot side ceramic for dissipating the heat from the TEC to the surrounding environment. Without a heat sink the TEC would overheat and fail within seconds.
  • a heat sink is a device that is generally associated with machines or apparatus which generates substantial amounts of heat such as a TEC, or a computer so that the heat may be rapidly dissipated. Therefore a heat sink is more effective when it may dissipate heat at greater rates.
  • U.S. Patent 5,042,257 therefore describes a heat sink for a TEC which includes a pair of opposed plates which have a plurality of fins on each of opposed faces wherein one array of fins on one face may be accommodated or interleaved between another array of fins on the other face whereby one array of fins may be retained in desired position by suitable retaining means such as a pair of relatively short fins which constitute thermal surface area contacts for sufficient exchange of heat.
  • the heat exchanger assembly of the invention as claimed is formed from primary structure and comprises a core comprising a multiplicity of primary fluid sections and a plurality of secondary fluid sections wherein a respective primary fluid section is located adjacent to a respective secondary fluid section with each primary fluid section being substantially parallel to each secondary fluid section so that fluid flow which occurs in and is confined to each primary fluid section is substantially parallel to fluid flow which occurs in and is confined to each secondary fluid section characterised in that each primary fluid section is bounded by a peripheral wall and includes closed ends and access slots adjacent a respective closed end so that fluid enters or exits each primary fluid section normal to the direction of flow in each primary fluid section and that each secondary fluid section includes open ends as well as a first array of fins extending away from the peripheral wall of one adjoining primary fluid section and a second array of fins extending away from the peripheral wall of another adjoining fluid section wherein an individual first fin extends between each adjacent second fin in interleaved relationship wherein the surface area of each secondary fluid section is substantially greater than the surface area of each primary fluid section.
  • the primary fluid sections are provided with a plurality of webs wherein each web extends from opposed faces of the peripheral wall to thereby provide a number of parallel primary fluid passages.
  • the webs are useful for strengthening and reinforcement purposes to maintain the structural integrity of the core.
  • the tips of the first array of fins abut or are attached to an adjacent surface of the peripheral wall of said another adjoining fluid section.
  • the tips of the first array of fins are spaced from the adjacent surface.
  • the tips of the second array of fins may abut or be attached to an adjacent surface of the said one adjoining fluid section but more preferably are spaced therefrom.
  • each secondary fluid section may correspond to a single flow passage for secondary fluid.
  • a heat exchanger core which may be formed in one piece such as an extrusion formed from aluminium or other suitable metal.
  • the core be formed from a plurality of separate modules.
  • a particular module may include the peripheral wall which bounds the flow passages for primary fluid and both the first and second array of fins which extend away from external or outer surfaces of opposed parts of the peripheral wall respectively.
  • peripheral wall and the elongate fins of each module are each formed simultaneously in formation of the one piece extrusion or casting so that the heat exchanger module is formed from primary structure.
  • the primary fluid passages and the secondary fluid passages are substantially parallel to each other to form a parallel flow heat exchanger core which has advantages over cross flow heat exchangers of the type described previously. These advantages include the following -
  • the core of the heat exchanger apparatus may take any form consistent with the function of providing definition for flow of both primary and secondary fluids.
  • the core may comprise a continuous cross section of indefinite length with the flow passages being disposed in the direction of the indefinite length. Such a configuration has proved to be particularly amenable to continuous casting or extrusion.
  • each module is substantially rectangular having a pair of opposed substantially horizontal parts in use which are joined by a pair of opposed vertical parts.
  • the abovementioned webs of the primary fluid section formed by the peripheral wall are preferably substantially parallel to the vertical parts.
  • peripheral wall may have any other suitable shape such as being circular in cross section or triangular in cross section or polygonal in cross section.
  • the primary flow passages of the primary fluid section may have any suitable shape or configuration and thus may be round, rectangular or polygonal in cross section.
  • each fin may have any suitable shape.
  • each fin is of constant height and width although this is not absolutely essential.
  • each elongate fin is of constant height and width although this is not absolutely essential.
  • each elongate fin may taper in width from one end to the other if required if the heat exchange element of the invention is produced as a casting.
  • the elongate fins may also have projections or ribs on an outer surface to increase their surface area if required.
  • the heat exchanger cores of the invention may be provided with manifolding means adapted to supply the primary and secondary fluids to their respective flow sections and such manifolding means may take any appropriate form.
  • manifolding means may take any appropriate form.
  • a primary fluid inlet manifold and a primary fluid outlet manifold may be provided which enables primary fluid to communicate with each primary fluid section so that each of the inlet manifold and outlet manifold are in fluid communication with a plurality of corresponding access slots.
  • Each secondary fluid section of the core may be provided with an inlet duct and outlet duct which are each in fluid communication with a plurality of adjacent open ends.
  • the invention may also include within its scope the core as defined in claim 13.
  • the primary fluid is suitably an "operating fluid” i.e. a fluid which is being processed by the heat exchanger and which is to be recirculated through a suitable flow system to which the heat exchanger of the invention is being applied.
  • an "operating fluid” i.e. a fluid which is being processed by the heat exchanger and which is to be recirculated through a suitable flow system to which the heat exchanger of the invention is being applied.
  • a fluid is suitably water.
  • the secondary fluid is preferably "an active fluid" which functions as a coolant for the operating fluid and which absorbs heat from the operating fluid after passage through the heat exchanger core.
  • an active fluid which functions as a coolant for the operating fluid and which absorbs heat from the operating fluid after passage through the heat exchanger core.
  • Such a fluid for vehicle radiators for example may comprise air.
  • the heat exchange modules for use in the invention may be adapted for vertical stacking or horizontal stacking as may be required.
  • each module may be provided with connection means for this purpose.
  • the connection means may be such that interconnection of the adjacent modules defines a suitable flow passage for secondary fluid.
  • each module has integrally extruded therewith connection means to enable adjacent modules of the invention to be assembled together.
  • the connection means may be of any suitable type and thus comprise for example male members or projections engageable with female members or sockets in snap fit or interference fit relationship.
  • each module includes a top connection member and bottom connection member which may engage with corresponding top and bottom connection members of an adjacent module.
  • the top or bottom connection member may comprise a panel rib or flange which may engage with a corresponding ratchet rib or flange of a mating top or bottom connection member of an adjacent module.
  • the number of modules or heat exchange elements utilised in a horizontal or vertical stacking arrangement may then depend upon the particular application desired.
  • Heat exchanger cores in accordance with the present invention may be used in gas/gas, liquid/gas or liquid/liquid application and are particularly suited to gas/air and liquid/air applications using impelled ambient air as the heat transfer fluid.
  • the cores can be placed in an enclosure suitable for natural or draft convection of air.
  • heat transfer fluids other than air may be employed, such as water, ethylene glycol, ammonia, fluorocarbon compounds, silicone compounds, mineral oils and the like.
  • the flow channels are manifolded in series, it is preferred to direct the flow of the first fluid countercurrently to the heat transfer fluid so as to obtain the maximum log mean temperature differential between the two fluids, and thus the most efficient heat transfer.
  • co-current flow may be utilised.
  • the heat exchanger cores of the present invention may be of any suitable material, the suitability of a material being generally determined with reference to the application to which it is to be put. For example, use in extreme high temperature applications may dictate that a ceramic material be used for its high temperature properties, whereas for lower temperature applications it has been found that aluminium or its alloys or other metals are suitable for their relatively high thermal conductivities, permitting thicker wall sections per unit efficiency and thus increasing mechanical strength.
  • FIG 1 there is shown heat exchanger core 10 in accordance with the invention including a vertical stack of modules 11.
  • Each module 11 includes a peripheral wall 12 of shallow rectangular configuration having opposed horizontal parts 13 and opposed vertical parts 14.
  • the peripheral wall 12 which is of a continuous nature defines a primary fluid section 15.
  • Webs 16 are included to define separate primary flow passages 17.
  • first array of fins 18 extending away from one horizontal part 13 and a second array of fins 19 extending away from the opposed horizontal part 13 of peripheral wall 12.
  • a section 20 for passage of secondary fluid is therefore defined by fins 18 extending between adjacent fins 19 and terminating short of an adjacent horizontal section 13 of wall 12 to define a space 21 and fins 19 extending between adjacent ribs 18 and terminating short of an adjacent horizontal section 13 of wall 12 to define a space 21.
  • Each adjacent module 11 is attached by ribs 23 of one module engaging with the ends 24 of vertical extensions 25A of terminal vertical parts 14 of each peripheral wall 12.
  • heat exchanger core 10 are primary fluid section(s) 15 and secondary fluid section(s) 20. Therefore ducts or manifolds communicating with sections 15 and 20 do so in the area between dotted lines AA and BB.
  • This means that the external fins 18A and 19A have no function in regard to heat exchanger apparatus of the invention 10 and may be omitted or cut off.
  • outer extensions 25A This will mean that the effective core of the heat exchanger apparatus of the invention is as shown in FIG 2. Ribs 23A may also be omitted.
  • FIG 2 therefore defines a core 10A which has been constructed in accordance with the invention. This of course does not mean that core 10 cannot be utilised. It is just more convenient to use core 10A because of the saving in space or storage capacity within a heat exchanger system which also incorporates appropriate inlet and outlet manifolds.
  • FIG 3 shows a perspective view of an individual module for use in the core 10 and 10A shown in FIGS 1-2.
  • Each of fins 18 and 19 may be provided with peripheral ribs 18B and 19B of relatively thin cross section.
  • heat exchanger apparatus 26 in accordance with the invention which includes a gas or air inlet duct or manifold 27 having inlet 28, core 10A constructed of five modules 11, assembled as shown in FIGS 1-2, an air or gas outlet duct or manifold 28 with outlet 29, gas or air sections 20 including fins 18 and 19, liquid sections 15, welded areas 32 of liquid sections 15 which function as a plug or cover to prevent air or gas gaining access to sections 20, and liquid inlet manifold 33 with inlet conduits 34, 35, 36 and 37 and liquid outlet manifold 38 with associated outlet conduits 39, 40, 41 and 42.
  • the inlet manifold 33 has respective compartments 34A, 35A, 36A and 37A which register with inlet slots 34B (i.e.
  • outlet manifold 38 has outlet compartments 39A, 40A, 41A and 42A which register with outlet slots 39B (i.e. there are two of these slots), 40B, 41B and 42B respectively.
  • one manifold 27 may be utilised adjacent the inlet end of core 10A whereby forced air (e.g. by use of an air blower or air compressor) may be forced through core 10A or alternatively only one manifold 27 may be utilised adjacent the outlet end of core 10A whereby air may be forced through core 10A by use of an exhaust fan.
  • forced air e.g. by use of an air blower or air compressor
  • the heat exchanger apparatus 26 is used for gas and liquid heat transfer.
  • gas inlet and outlet manifolds are located at opposed ends of the core and liquid inlet and outlet manifolds are located on the same side or on different sides if appropriateor even on top and/or bottom of the core if appropriate.
  • the gas therefore may make one pass through the core and the liquid may also make a single pass through the core.
  • Each of the liquid manifolds may have a single inlet and single outlet if the same fluid is being processed or different inlets and outlets as shown in FIG 4 if different liquids are being processed by core 10A.
  • conduit 34 may be used for engine cooling water
  • conduit 35 used for engine oil
  • conduit 36 used for transmission oil
  • conduit 37 used for condensing liquid for air conditioning.
  • Conduits 39, 40, 41 and 42 have the same functions as an outlet conduit.
  • FIG 5 reference is shown to truck or vehicle 63 wherein fuel from engine 64 is passed through line 65 to a heat exchanger assembly 66 constructed in accordance with the invention.
  • the fuel tank 67 may also be utilised which then passes the fuel back to the engine 64 through line 68.
  • a heat exchanger core constructed in accordance with the invention will overcome the disadvantages of the prior art discussed in detail above because a uniform heat distribution will be obtained throughout the core by the location of fins 18 and 19 as illustrated whereby the tips of the fins 18 and 19 which are normally the coolest part of a conventional heat exchanger core are placed in close proximity to the hottest part of a conventional heat exchanger core which is the peripheral wall 12. It therefore follows that the temperature of the core at the tips of the fins 18 and 19 will be substantially the same or slightly less than the temperature of the peripheral wall 12. This will mean that a uniform heat distribution or temperature distribution will be obtained in each of the liquid sections 20 and this will bring about substantially improved heat exchanger efficiency. Heat exchanger efficiency will also be improved by the manufacture of core 10 or 10A as a single piece aluminium extrusion or alternatively being comprised of a stack of modular aluminium extrusions 10 or 10A.
  • FIG 6 shows the temperature distribution through an individual fin 18 or 19 and adjacent spaces 22A in relation to a conventional heat exchanger.
  • the heat exchanger apparatus of the invention will be most useful in regard to function as a vehicle radiator but this does not preclude its use as a heat exchanger in relation to processing of gas to gas or liquid to liquid applications as discussed above.
  • the thickness of peripheral wall 12 and also of vertical extensions 25 is substantially the same and is of relatively narrow thickness e.g., about 3 mm or less and more suitably 2 mm or less and of the order of 1.5 mm or 1.0 mm or less.
  • the surface area of the secondary flow sections 20 is at least twice the surface area and more preferably is at least 7 times the area of primary fluid sections 15.
  • spaces 21 should be substantially uniform and this also applies to the spaces 22 between adjacent fins 18 or 19. Naturally each fluid channel 17 should also be substantially of the same volume.

Claims (14)

  1. Wärmetauscheranordnung aus einer Primärstruktur, mit einem Kern mit einer Vielzahl Primärfluidabteile (15) und einer Mehrzahl Sekundärfluidabteile (20), wobei je ein Primärfluidabteil einem zugehörigen Sekundärfluidabteil benachbart, jedes Primärfluidabteil im wesentlichen parallel zu jedem Sekundärfluidabteil, angeordnet ist, so daß ein Fluidstrom, der in jedem Primärfluidabteil auftritt und auf dieses beschränkt ist, im wesentlichen parallel zu einem Fluidstrom ist, der in jedem Sekundärfluidabteil auftritt und auf dieses beschränkt ist, dadurch gekennzeichnet, daß jedes Primärfluidabteil (15) durch eine Umfangswand (12) begrenzt ist und geschlossene Enden und je einem zugehörigen geschlossenen Ende benachbart Zugangsschlitze (34b) aufweist, so daß Fluid in jedes bzw. aus jedem Primärfluidabteil normal zur Stromrichtung in jedem Primärfluidabteil ein- oder austritt, und daß jedes Sekundärfluidabteil offene Enden sowie eine von der Umfangswand eines angrenzenden Primärfluidabteils abstehende erste Gruppe Rippen (18) und eine von der Umfangswand eines anderen angrenzenden Fluidabteils abstehende zweite Gruppe Rippen aufweist, wobei sich je eine einzelne erste Rippe zwischen benachbarte zweite Rippen ineinandergreifend erstreckt, wobei die Oberfläche jedes Sekundärfluidabteils wesentlich größer als die Oberflächen jedes Primärfluidabteils ist.
  2. Wärmetauscheranordnung nach Anspruch 1, bei der jedes Primärfluidabteil mit einem oder mehreren von entgegengesetzten Seiten der Umfangswand abstehenden Stegen versehen ist.
  3. Wärmetauscheranordnung nach Anspruch 1, bei der die erste Gruppe Rippen je ein freies Ende oder eine Spitze hat, das bzw. die von einer benachbarten Oberfläche der Umfangswand des genannten anderen angrenzenden Fluidabteils beabstandet ist.
  4. Wärmetauscheranordnung nach Anspruch 1 bei der die zweite Gruppe Rippen je ein freies Ende oder eine Spitze hat, das bzw. die von einer benachbarten Fläche der Umfangswand des genannten einen angrenzenden Fluidabteils beabstandet ist.
  5. Wärmetauscheranordnung nach Anspruch 1, bei der der Kern eine Mehrzahl Module aufweist, wobei jedes Modul die genannte Umfangswand und die genannte erste Gruppe Rippen und die genannte zweite Gruppe Rippen aufweist.
  6. Wärmetauscheranordnung nach Anspruch 5, bei der die Umfangswand jedes Moduls im wesentlichen rechteckig ist.
  7. Wärmetauscheranordnung nach Anspruch 1, ferner mit einem Primärfluideinlaßverteiler und einem Primärfluidauslaßverteiler, wobei jeder genannte Einlaßverteiler und genannte Auslaßverteiler in Fluidverbindung mit einer Mehrzahl zugehöriger Zugangsschlitze ist.
  8. Wärmetauscheranordnung nach Anspruch 1, bei der jedes Sekundärfluidabteil mit einer Einlaßröhre und einer Auslaßröhre versehen ist, wobei jede genannte Einlaßröhre und genannte Auslaßröhre in Fluidverbindung mit einer Mehrzahl benachbarter offener Enden der Sekundärfluidabteile ist.
  9. Wärmetauscheranordnung nach Anspruch 1, bei der in einer Seite, der Ober- oder Unterseite des Kerns Primärfluidzugangsschlitze angeordnet sind, um das Eintreten oder Austreten von Primärfluid in bzw. aus dem Kern zu erleichtern.
  10. Wärmetauscheranordnung nach Anspruch 9, bei der Primärfluidzugangsschlitze in einer Seite des Kerns jedem Ende benachbart vorgesehen sind.
  11. Wärmetauscheranordnung nach Anspruch 5, bei der jedes Modul darin integrierte Verbindungsmittel hat, damit benachbarte Module miteinander verbindbar sind.
  12. Wärmetauscheranordnung nach Anspruch 1, bei der die Oberfläche jedes Sekundärfluidabteils wenigstens siebenmal so groß wie die Oberfläche jedes Primärfluidabteils ist.
  13. Kern für eine Wärmetauscheranordnung aus einer Primärstruktur, mit einer Vielzahl Primärfluidabteile (15) und einer Mehrzahl Sekundärfluidabteile (20), wobei je ein Primärfluidabteil einem zugehörigen Sekundärfluidabteil benachbart, jedes Primärfluidabteil im wesentlichen parallel zu jedem Sekundärfluidabteil, angeordnet ist, so daß ein Fluidstroms, der in jedem Primärfluidabteil auftritt und auf dieses beschränkt ist, im wesentlichen parallel zu einem Fluidstrom ist, der in jedem Sekundärfluidabteil auftritt und auf dieses beschränkt ist, dadurch gekennzeichnet, daß jedes Sekundärfluidabteil (15) durch eine Umfangswand (12) begrenzt ist und geschlossene Enden und einem zugehörigen geschlossenen Ende benachbart Zugangsschlitze (34b) aufweist, so daß Fluid in jedes bzw. aus jedem Primärfluidabteil normal zur Stromrichtung in jedem Primärfluidabteil ein- oder austritt, und daß jedes Sekundärfluidabteil offene Enden sowie eine von der Umfangswand eines angrenzenden Primärfluidabteils abstehende erste Gruppe Rippen (18), und eine von der Umfangswand eines anderen angrenzenden Fluidabteils abstehende zweite Gruppe Rippen umfaßt, wobei sich je eine einzelne erste Rippe zwischen benachbarte zweite Rippen ineinandergreifend erstreckt, wobei die Oberfläche jedes Sekundärfluidabteils wesentlich größer als die Oberfläche jedes Primärfluidabteils ist.
  14. Kern nach Anspruch 13, bei dem jedes Primärfluidabteil mit einem oder mehreren von entgegengesetzten Seiten der Umfangswand abstehenden Stegen vershen ist.
EP93905101A 1992-02-28 1993-03-01 Wärmetauscherzusammenbau Expired - Lifetime EP0627065B1 (de)

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AUPL112992 1992-02-28
AU1129/92 1992-02-28
PCT/AU1993/000085 WO1993017290A1 (en) 1992-02-28 1993-03-01 Heat exchanger assembly

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EP0627065A1 EP0627065A1 (de) 1994-12-07
EP0627065A4 EP0627065A4 (de) 1995-06-28
EP0627065B1 true EP0627065B1 (de) 1999-05-26

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CA (1) CA2117566A1 (de)
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DE102007043992A1 (de) * 2007-09-14 2009-03-19 Pierburg Gmbh Ladeluftmodul für eine Verbrennungskraftmaschine
DE102007043992B4 (de) * 2007-09-14 2009-08-27 Pierburg Gmbh Ladeluftmodul für eine Verbrennungskraftmaschine
EP4071435A1 (de) * 2021-04-06 2022-10-12 General Electric Company Wärmetauscher und verfahren zum herstellen davon
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Also Published As

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ES2133389T3 (es) 1999-09-16
CA2117566A1 (en) 1993-09-02
AU663168B2 (en) 1995-09-28
JPH07504264A (ja) 1995-05-11
KR950700529A (ko) 1995-01-16
AU3622693A (en) 1993-09-13
US20010040025A1 (en) 2001-11-15
WO1993017290A1 (en) 1993-09-02
EP0627065A4 (de) 1995-06-28
EP0627065A1 (de) 1994-12-07

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