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US20190249925A1 - Heat exchanger and components and methods therefor - Google Patents

Heat exchanger and components and methods therefor Download PDF

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Publication number
US20190249925A1
US20190249925A1 US16/335,011 US201716335011A US2019249925A1 US 20190249925 A1 US20190249925 A1 US 20190249925A1 US 201716335011 A US201716335011 A US 201716335011A US 2019249925 A1 US2019249925 A1 US 2019249925A1
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US
United States
Prior art keywords
tube portion
discrete tubular
metal strip
tubular components
tube
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.)
Abandoned
Application number
US16/335,011
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English (en)
Inventor
Carl Morley
Nikolce Simonovski
Shashikiran Vatnal
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Air-Radiators Pty Ltd
Original Assignee
Air-Radiators Pty Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from AU2016903811A external-priority patent/AU2016903811A0/en
Application filed by Air-Radiators Pty Ltd filed Critical Air-Radiators Pty Ltd
Assigned to Air-Radiators Pty Ltd reassignment Air-Radiators Pty Ltd ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Morley, Carl, Simonovski, Nikolce, Vatnal, Shashikiran
Publication of US20190249925A1 publication Critical patent/US20190249925A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F28D1/04—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 tubular conduits
    • F28D1/053—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 tubular conduits the conduits being straight
    • F28D1/0535—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 tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P15/00—Making specific metal objects by operations not covered by a single other subclass or a group in this subclass
    • B23P15/26—Making specific metal objects by operations not covered by a single other subclass or a group in this subclass heat exchangers or the like
    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • 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
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/06—Arrangements for sealing elements into header boxes or end plates by dismountable joints
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K1/00—Soldering, e.g. brazing, or unsoldering
    • B23K1/0008—Soldering, e.g. brazing, or unsoldering specially adapted for particular articles or work
    • B23K1/0012—Brazing heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to heat exchangers.
  • the invention relates to a heat exchanger having separable tubular heat exchanger components extending between the tanks.
  • the invention also relates to a discrete tubular component for a heat exchanger and a method of constructing a discrete tubular component.
  • the specification is also directed to aluminium tubular components for heat exchangers, particularly for heavy duty on-road and off-road applications.
  • the inventions described herein may have application to air-to-air heat exchangers (charge air coolers) or liquid-to-air heat exchangers (water jacket coolers).
  • Heat exchangers particularly those used in vehicles and industrial machinery, come in a large variety tubing configurations, extending between a pair of header plates, between an inlet tank and an outlet tank.
  • a radiator is a common form of heat exchanger. Radiators are generally designed to have a high temperature coolant flow from an inlet tank within the radiator, through a set of finned tubes, and then to an outlet tank within the radiator. The coolant at the outlet tank is at a lower temperature than it was at the inlet tank. This cooling is mainly achieved through convection, wherein a cooler fluid, such as ambient air, passes over the surface of the tubes containing the heated coolant, and transfers away the thermal energy of the tubes.
  • a cooler fluid such as ambient air
  • the tubing may expand lengthwise.
  • Radiator cores generally come in a number of different types and the various different types each have their drawbacks.
  • monoblock cores the tubes and fins are consolidated, with each tube being joined to an adjacent fin which is adjoined to the next tube and so on.
  • One particular form of monoblock core is the bar and plate monoblock core. These constructions have tubes defined by bar and plate with inner fins inside the tubes. Additionally, external fins extend between adjacent plates.
  • the brazed joints between the inner fins and the plate are critical for maintaining the structural integrity and performance. There are many brazed joints between the inner fins and the adjacent plates and thus bar and plate monoblock cores are typically prone to failure through failure of these braze joints.
  • Extruded tube monoblock cores have extruded baffles or fins located internally of the tubes and are therefore less prone to failure at the baffle/tube junctions.
  • External fins are disposed between adjacent tubes.
  • the braze between the external fin and the tube wall is critical for thermal performance. However, these braze joints are prone to failure through corrosion and erosion (such as by grit blasting in the field).
  • An alternative to the monoblock core is the individual tube type cores where individual tubular components extend between the inlet tank and the outlet tank.
  • U.S. Pat. No. 3,391,732 assigned to Mesabi Cores Inc. exemplifies a radiator of this type.
  • the individual tubular components are typically constructed of copper which is heavy and has a high initial cost and so is prohibitive in some applications.
  • the cooling fins are usually connected to the tube portions through the use of lead solder. Given the safety concerns in dealing with lead, lead solder is expensive to use. Lead solder also has a relatively low strength, is prone to corrosion, relatively poor conductivity and has a limited temperature range of applications e.g. less than 200 degrees C.
  • the Mesabi tubular components are formed from tubes which have been flattened from round tubing, thus the end of the tube portions are still round.
  • the production of flattened tubes from round tubes necessitates an additional working step to produce the tubes of required configuration and additionally presents the risk that the tubes will not be correctly installed in the radiator core.
  • the correct installed position is with the flattened sides aligned with the direction of intended air flow through the core.
  • the rounded ends facilitate the prospect of misalignment and require additional steps in order to guarantee correct alignment.
  • Another objective of the present invention is to provide the public with a useful choice over known products.
  • a method of constructing discrete tubular components for a heat exchanger including:
  • metal strip which includes a substrate material and a second material different than the substrate material forming a layer on only one side of the metal strip;
  • the second material is preferably in the form of a coating or cladding applied to the substrate material.
  • the second material may be applied in a manner suitable for producing an adherent coating on the substrate material.
  • the metal strip may be rolled down from a composite billet of the substrate material and a sheet of the second material on one side.
  • the material for the substrate of the metal strip may be a work-hardenable alloy such as 3-series aluminium alloy, such as AL3003 with a melting point of approximately 660° C.
  • the tube portion preferably includes heat treatable metal and the method may further comprise a subsequent step of heat treating.
  • the preferred material for the tube portion is heat treatable 6-series aluminium alloy, most preferably AL6063 with a melting point of approximately 660° C.
  • the preferred metal for the substrate is also a 6-series aluminium allow, most preferably AL6063. Hence the same material could then be used for the substrate and the tube portion, enabling both the substrate and the tube portion to be heat treated.
  • the second material of the metal strip has a melting point range which is less than the melting point range of the substrate material and the tube portion.
  • the second material is a four series aluminium alloy, most preferably AL4343 having a melting point range of 577-600° C.
  • AL4343 has been selected partly due to availability and partly because it has a high range of useful brazing temperatures.
  • Alternatives include AL4045 and AL4047 and are possibly preferred where both the substrate and the tube portion are 6-series.
  • the heating of the second material is to a brazing temperature which exceeds the melting point of the second material.
  • the melting point of AL 4343 is 577-600° C.
  • the range of suitable brazing temperatures is 590-610° C.
  • the brazing temperature is below the melting point of the tube portion and substrate material.
  • a plurality of tubular components may be constructed by stacking the tubular components with one or more intervening spacer strips and then brazing the stack.
  • the melting point of the spacer strips is higher than the brazing temperature.
  • the spacers are stainless steel.
  • the second material and the substrate material are aluminium, bonding to the stainless steel strip is prevented or at least unlikely or minimal.
  • the metal strip should not bond to the spacer strip(s).
  • the stacks are held in compression during brazing.
  • the tubular components may be comprised of a tube portion and a fin portion.
  • the tube portion is preferably an extruded section, most preferably aluminium.
  • the tube portion is not coated with brazing material, this being difficult to achieve given the extruded construction.
  • the tube portion is of constant transverse section, throughout its length.
  • this transverse section is flat-sided with curved or arcuate ends.
  • the height to width ratio is 7 or larger.
  • the tube portion may be provided with internal baffles, more preferably two internal baffles.
  • the internal baffles suitably extend longitudinally.
  • the tube portion may be extruded with the integrally formed longitudinal baffles.
  • the or each fin portion may be arranged in any configuration relative to the flat sides of the tube portion. However, it is preferred that the fin portion extends longitudinally along the elongate tube portion.
  • the tube portion may have a transverse section which is of oblong shape, defining two opposite substantially flat sides. It is preferred that there are two continuous fin portions which extend along respective flat sides.
  • the fin portion may be corrugated such as configured in serpentine or sinuous folds. Alternatively, concertina folds are also possible. Preferably, there is a regular pattern of peaks and troughs in the repeated folds and the peaks and troughs are of even height and spacing.
  • the fin portions may have a dimpled surface to improve heat transfer characteristics.
  • the fin portions may include a series of louvred slots. In such louvred slots, the louvres are created from the planar material creating the fin portion. Creation of each louvre creates a consequent slot and the louvre lies out of the plane of the surrounding material. The louvres increase the air side pressure drop, enhance performance but lead to increased fouling of the core with debris.
  • the fin portions may be plain with no dimples or louvres.
  • a discrete tubular component for a heat exchanger including:
  • each fin portion comprised of metal strip configured in repeated folds of peaks and troughs with one side of the metal strip facing the tube portion, the metal strip being substantially uniformly provided as a substrate material and a second material different to the substrate material, the second material forming a layer in the strip on only on said one side of the metal strip, the second material bonding the fin portion to the tube portion at the region of the troughs,
  • the second aspect of the invention may have any of the features described above or below in connection with other aspects of the invention.
  • the metal strip may be configured in sections or long lengths which are then cut, to be subsequently positioned on the tube portion and placed in a controlled atmosphere brazing (CAB) furnace to heat the second material.
  • CAB controlled atmosphere brazing
  • the second material may be contemporaneously heated to bond the metal strip to the tube portion.
  • a heat exchanger including:
  • the header plates having aligned apertures for receipt of the heat exchanger components which extend from the first header plate to the second header plate,
  • the corresponding aligned apertures in the first and second header plates are complimentary in shape to the external surface of the corresponding end portion of the tubular component
  • tubular components are arranged in an array across the direction of intended air flow, with the tubular components in the array being arranged in a staggered pattern relative to the direction of intended air flow.
  • the tubes are arranged in rows, the rows being evenly spaced along the direction of intended airflow. Additionally, the spacing of the tubes along each row may also be evenly spaced. When the tubes are arranged in rows, then each row may be staggered relative to its neighbouring rows.
  • the repeat pattern before a row is positioned directly behind a preceding row may be two rows or more.
  • the arrangement of the components which are oblong in transverse section is such that the lengthwise dimension of the section is arranged substantially aligned with the direction of intended airflow.
  • the tubular components may be comprised of a tube portion and a fin portion.
  • the tube portion is preferably an extruded section, most preferably aluminium.
  • the tube portion is of constant transverse section, throughout its length.
  • this transverse section is flat-sided with curved or arcuate ends.
  • the height to width ratio is 7 or larger.
  • the tube portion may be provided with internal baffles, more preferably two internal baffles.
  • the internal baffles suitably extend longitudinally.
  • the tube portion may be extruded with the integrally formed longitudinal baffles.
  • the tubular components are able to be assembled separately with at least one of the header plates.
  • the tubular components may be removable individually from at least one of the header plates. This allows for maintenance of individual components.
  • each aperture in the header plates are commensurate in shape with the end portions of the tubes.
  • each aperture may also accommodate a grommet which interfaces between the header plate and the end portion of the associated tube portion.
  • the grommet may have any of the features described in connection with our Australian patent application filed 21 Sep. 2016, for “Heat exchanger grommet”, the contents of which are incorporated herein by reference.
  • a tubular component for a heat exchanger including:
  • one or more fin portions attached to the tube portion the or each fin portion comprised of metal strip configured in repeated folds, the metal strip including a work hardenable metal.
  • the heat treatable metal in the tube portion is 6 series aluminium alloy.
  • the metal strip includes a 3 series work hardenable alloy.
  • the tubular component is artificially aged at 178° C. for 8 hours after the brazing of the components.
  • a method of heat treating a tubular component for a heat exchanger including a tube portion including heat treatable metal, and one or more fin portions brazed to the tube portion, the or each fin portion including metal strip configured in repeated folds, the method including:
  • the tube portion is heat treatable 6-series aluminium alloy.
  • the metal strip may include a work hardenable metal such as 3-series aluminium alloy.
  • the metal strip may also comprise heat treatable 6-series aluminium alloy.
  • a grommet for a heat exchanger including an annulus of resiliently deformable material, said annulus defining a through bore having opposite first and second openings, a depth, and transverse and longitudinal inner dimensions, the through bore having inner wall surfaces which converge inwardly, such that one or both of the inner dimensions vary through the depth of the bore, from one opening to the other, one or both of the inner dimensions being smallest in an intermediate portion of the bore disposed at an intermediate depth between the first and second openings, wherein the annulus further includes first and second outwardly extending flanges arranged to surround the first and second openings respectively.
  • the grommet may be used in assembly with the components described above in the foregoing aspects.
  • FIG. 1 is a perspective view of a tubular component according to a preferred embodiment of the present invention
  • FIG. 2 is a perspective view from another angle of the component in FIG. 1 ;
  • FIG. 3 is a detailed view of the tubular component of FIG. 1 ;
  • FIG. 4 is a perspective view illustrating a tube portion forming part of the tubular component of FIG. 1 ;
  • FIG. 5 is a longitudinal section across the width of the tube portion of FIG. 4 ;
  • FIG. 6 is a detailed view of A of FIG. 5 ;
  • FIG. 7 is an end view of the tube portion of FIG. 4 , showing the uniform transverse cross-section, across the width and thickness;
  • FIG. 8 is a view of a portion of the stacking arrangement to construct a plurality of tubular components in accordance with the preferred embodiment of the present invention.
  • FIG. 9 is a detail of L from FIG. 8 ;
  • FIG. 10 is a detailed G from FIG. 9 ;
  • FIG. 11 is a view similar to FIG. 8 ;
  • FIG. 12 is a detailed view of K from FIG. 11 ;
  • FIG. 13 is a detailed view of G from FIG. 12 ;
  • FIG. 14 is a perspective view of the stacking arrangement illustrated in FIGS. 8 and 11 ;
  • FIG. 15 is a detailed view of F from FIG. 14 ;
  • FIG. 16 is a side view of the stacking arrangement of FIG. 14 ;
  • FIG. 17 is an end view of the stacking arrangement of FIG. 16 ;
  • FIG. 18 is an exploded view showing the parts required to assemble a radiator in accordance with a preferred embodiment of the present invention.
  • FIG. 19 is an assembled view of the radiator of FIG. 18 , with a cutaway.
  • FIG. 20 is a detailed view of A from FIG. 19 ;
  • FIG. 21 is a perspective view of an alternative form of tubular component according to a second preferred embodiment of the present invention.
  • FIG. 22 is a detailed view of a portion of the tubular component of FIG. 21 ;
  • FIG. 23 is a side view of a portion of the tubular component of FIG. 21 ;
  • FIG. 24 is an end view of the tubular component of FIG. 21 ;
  • FIG. 25 is an output from a finite element analysis showing stress concentrations of a prior art grommet under simulated operating conditions
  • FIG. 26 is an output from a finite element analysis showing stress concentrations of a preferred grommet under simulated operating conditions
  • FIG. 27 is an isometric view of the preferred grommet
  • FIG. 28 is a plan view of the grommet in FIG. 27 ;
  • FIG. 29 is a bottom view of the grommet in FIG. 27
  • FIG. 30 is a cross-sectional view of the grommet in FIG. 29 taken along line A-A;
  • FIG. 31 is a cross-sectional view of the grommet in FIG. 29 taken along line A-A after insertion into a header plate;
  • FIG. 32 is a cross-sectional view of the grommet in FIG. 29 taken along line A-A after insertion into a header plate and the subsequent insertion of a heat exchanger tube into the grommet;
  • FIG. 33 is a perspective view showing the centre support assembly for supporting the tubes in the radiator core
  • FIG. 34 is a plan view showing the centre support assembly of FIG. 20 ;
  • FIG. 35 is a perspective view of a single centre support bracket
  • FIG. 36 is a plan view of the single centre support bracket
  • FIG. 37 is a perspective view of a first terminal block forming part of the centre support assembly
  • FIG. 38 is a plan view of the first terminal block forming part of the centre support assembly
  • FIG. 39 is a perspective view of a second terminal block forming part of the centre support assembly.
  • FIG. 40 is a plan view of the second terminal block forming part of the centre support assembly
  • FIGS. 1 and 2 illustrate the form of the tubular component 10 according to a preferred embodiment of the present invention.
  • the tubular component 10 includes a tube portion 12 .
  • the tube portion 12 is oblong in transverse section as shown in FIG. 3 with 2 flat longitudinal sides 14 .
  • Fin portions 16 are bonded to respective flat sides 14 .
  • the fin portions 16 are in the form of metal strip which has been folded, bent, corrugated or otherwise shaped into repeated folds 18 of troughs and peak.
  • the folds 18 are sinuous in shape and are of equal height and equal spacing between the folds.
  • the fin portions 16 extend for a substantial portion of the length of the tube portion 12 . However, the fin portions 16 fall short of the ends of the tube portion 12 and define end portions 20 which are free of the fin portions on both sides 14 .
  • FIGS. 4-7 show the form of the tube portion 12 in greater detail.
  • the tube portion 12 is extruded from a heat treatable alloy AL6063.
  • the extruded transverse section is illustrated in FIG. 7 .
  • the transverse sectional shape is oblong having two flat sides 14 as mentioned. Additionally, the longitudinal edges 22 have a radiused outer periphery 24 to define respective noses 24 .
  • the tube portion 12 also has 2 internal baffles 26 , dividing the internal bore of the tube portion 12 into three longitudinal passages 28 .
  • the wall thicknesses along the flat sides 14 is the thinnest wall thickness of the transverse section, as shown.
  • the wall thickness of the internal baffles 26 is slightly greater.
  • each outer longitudinal passage 28 and the corresponding nose 24 is the thickest. This provides suitable protection for the tube portions 12 against the harsh conditions. In particular, the extra thickness in the tube portion 12 around the nose 24 guards against debris puncturing the tube.
  • one of the noses 24 will face upstream of airflow and will be the most exposed to airborne particles as they travel through the heat exchanger core. Additionally, the upstream nose 24 will be subjected to pressure washing.
  • tubular components 10 The construction of the tubular components 10 will now be described with particular reference to FIGS. 8-20 .
  • the extruded material is cut to length to form the tube portion 10 . Additionally, the folded fin portions are also cut to length. At this point, it is to be noted that the fin portions are formed from metal strip 30 , a portion of which is illustrated in FIG. 10 .
  • the metal strip 30 includes a substrate 32 comprised of a substrate material, aluminium AL 3003 having a melting point of approximately 660° C.
  • a second material 34 is provided as a coating or cladding on the substrate 32 .
  • the second material is AL 4343 which has a melting point range of between 577 and 600° C. Only one side of the substrate 32 is clad with the second material 34 .
  • one fin portion 16 is placed on each flat side 14 of the tube portion 12 .
  • the fin portion 16 is placed on the tube portion 12 so that the cladding of the second material 34 is in contact with the tube portion 12 .
  • the other unclad side of the metal strip 30 should not be placed in contact with the tube portion 12 . Otherwise, the cladding 34 will not bond to the tube portion 12 and will instead bond to the spacers 38 .
  • the assembly order is as follows. Initially, a strongback 36 is placed on the bottom of the stack 37 .
  • the stack may be assembled in a suitable assembly jig (not shown).
  • a first spacer 38 is placed on top of the strongback 36 .
  • the spacer 38 is a longitudinal strip of stainless steel. Each end of the strip has cut outs defining a central projecting portion 40 .
  • the strip On each side of the central projecting portion 40 , the strip has upstands 42 .
  • Each pair of upstands 42 is provided towards each end of the spacer 38 and the pairs are spaced apart a suitable distance to accommodate the fin portion 16 therebetween.
  • a combination of fin portion 16 , tube portion 12 and fin portion 16 is then stacked on top of the first spacer 38 (otherwise referred to as a bundle or sandwich of fin, tube, and fin portions).
  • a second spacer 38 is then placed in the inverted orientation on top of the upper fin portion 16 .
  • the end of the fin portion 16 should contact the upstand 42 as shown in the case of the lower fin portion 16 .
  • the cladding 34 on the fin portions 16 is placed in contact with the tube portion 10 .
  • the unclad side of the fin portion 16 should be in contact with the spacers 38 .
  • Another spacer 38 is placed on top of the current stack in an upright manner. Then the stacking continues.
  • the brazing is controlled atmosphere brazing (CAB).
  • CAB controlled atmosphere brazing
  • the stack is laid on its side to pass through the brazing furnace.
  • the brazing occurs at temperatures in the range of 590-610° C.
  • the cladding 34 has a melting point in the range of 577 to 600° C.
  • the cladding 34 will bond the fin portion 16 onto the tube portion 12 .
  • the brazing temperature range is below the melting point of the substrate material 32 and the material of the tube portions 12 , both of which have a melting point of approximately 660° C.
  • the cladding 34 is melted but not the substrate 32 , nor the tube portion 12 .
  • the unclad side of the substrate 32 is in contact with the spacers 38 . Accordingly, there should be no bonding between the fin portion 16 and the spacers 38 .
  • the wires 44 are cut and removed.
  • the brazed tubular components 10 should then separate easily from the spacers 38 .
  • the strongbacks 36 are typically constructed from stainless steel 304-316 and are typically 25 ⁇ 25 ⁇ 2 SHS.
  • the spacers 38 are typically the same material as the strong backs, being stainless steel 304-316 and are typically 1.2 mm sheet.
  • the cladding 34 is typically 10% single side cladding with aluminium alloy AL 4343.
  • the cladding thickness is 10% of the material thickness of the fin material. Typically the fin material is 0.1 mm thick. So 10% of that means that the cladding thickness is 0.01 mm thick.
  • aluminium components 10 with stainless steel strongbacks 36 and spacers 38 This combination of materials is chosen because of the low susceptibility of bonding under brazing conditions.
  • Another combination could be copper tubular components with graphite strongbacks and spacers.
  • the tubular components 10 are then artificially aged at 178° C. for 8 hours. This heat treatment is expected to increase the strength of the extruded tube portion 12 which is made from AL6063 by promoting precipitation of Mg 2 Si in the tube portion alloy microstructure.
  • the tubular components are air quenched after heat treatment until they return back to ambient temperature.
  • the result of the heat treatment is an increase in strength observed in the order of 30%, an increase in the hardness observed in the order of 45%. This equates to a temper close to the T6 condition.
  • FIG. 18 is an exploded view illustrating the components required to assemble a heat exchanger 50 in accordance with a preferred embodiment of the present invention.
  • the heat exchanger 50 includes first and second tanks 52 , 54 .
  • One is an inlet tank 52 and the other is an outlet tank 54 .
  • Both tanks 52 , 54 have header plates 56 , 58 , one of which is shown more clearly in FIG. 20 .
  • the tubular components 10 extend between the header plates 56 , 54 as is known in the art.
  • Each end portion 20 is received in a respective aperture in the header plate 56 , 58 with a respective grommet 60 provided at the interface between the end portion 20 and the header plate 56 , 58 .
  • the grommets 60 may be of any suitable form known in the art.
  • One preferred form is similar to the known grommets used for the Mesabi radiator discussed above, except that the form would be oblong instead of round with the Mesabi grommets.
  • Another preferred grommet 110 is in the form described below in connection with FIGS. 25 to 32 .
  • FIGS. 19 and 20 illustrate the arrangement of the tubular components 10 in the header plate 56 .
  • the tubular portions 10 are arranged in rows which extend along the length of the heat exchanger 50 . These rows lie perpendicular to the direction of intended airflow Y through the heat exchanger. Each row is staggered relative to the row immediately in front of it. Thus, each tube portion is offset from its immediately adjacent tube portion in the row in front of it, the offset direction being perpendicular to the direction of intended airflow Y.
  • the repeat pattern is 2.
  • tubular components 10 are arranged with the length dimension of their oblong cross-section aligned with the direction of intended airflow Y.
  • FIGS. 21-24 illustrate another embodiment for the tubular components 10 ′.
  • the fin portions 16 ′ have been cut, either post-assembly with the tube portion 12 , or post brazing, to define bevelled profiles 70 on the fin portions 16 ′. This brings about improvements in performance.
  • FIG. 27 shows an isometric view of a preferred embodiment of the heat exchanger grommet 110 .
  • the grommet 110 includes an annulus of resiliently deformable material, said annulus defining a through bore 111 .
  • the bore 111 has first and second openings 112 and 113 , with the bore 111 having a depth, and transverse and longitudinal inner dimensions.
  • the bore is elongate, and in this embodiment is depicted as being of an oblong shape, in particular of approximately stadium shape, with opposite inner side wall surfaces 114 extending in the longitudinal direction, defining a linear central portion of the oblong to approximately suit the shape of the heat exchanger tube.
  • Inner side wall surfaces 114 are connected by inner end wall surfaces 117 at opposing ends.
  • the overall shape of the grommet 110 in this embodiment is reflective of the shape of the bore, that is, the shape of the grommet is of an oblong annulus.
  • the material surrounding the bore 111 is substantially equally distributed along the periphery of the bore 111 .
  • the material surrounding the bore 111 is substantially equally distributed along the periphery of the bore 111 .
  • FIG. 30 is a cross-sectional view of the grommet taken along section A-A of FIG. 29 .
  • Inner side wall surfaces 114 converge inwardly, in other words, are convex.
  • the inner side wall surfaces 114 are illustrated as mirroring each other or being symmetrical about a central longitudinal plane of the grommet 110 .
  • the smallest inner dimension is at a central depth between the first and second openings 112 and 113 .
  • the smallest inner dimension need not be at a central depth. It may be at any intermediate portion between the first and second openings 112 and 113 .
  • the inward convergence of inner side wall surfaces 114 are depicted as being pronounced for illustrative purposes. However the degree of this convergence may vary. In practice, considerations such as the size and shape of the tubing, and the expected loading conditions the grommet is expected to encounter may influence the degree of convergence of the inner side wall surfaces 114 .
  • the inner side wall surfaces 114 may also be symmetrical about a plane at a central depth of the grommet 110 . However, as shown in FIG. 30 , the inner transverse dimension is greater at the opening 112 than at the opening 113 .
  • FIG. 28 shows a plan view of the grommet 110 .
  • the inner end wall surfaces 117 may converge in the same manner as described above for the inner side wall surfaces 114 so that the cross-section is constant all the way around the periphery of the grommet 110 .
  • the inner end wall surfaces 117 may taper inwardly, such that the longitudinal dimension adjacent the first opening 112 is greater than the longitudinal dimension adjacent the second opening 113 .
  • FIG. 29 shows a bottom view of the grommet 110 .
  • First and second outwardly extending flanges 115 and 116 are shown, with first outwardly extending flange 115 being the tube-side flange of the grommet 110 , and the second outwardly extending flange 116 being the header-side flange.
  • the tube side-flange 115 has a greater bulk of material than the header-side flange 116 .
  • Inner edges 119 located between the top surface of tube-side flange 115 and inner side wall surfaces 114 are radiused to facilitate the insertion of the heat exchanger tubing.
  • Header-side flange 116 includes bevelled edges 118 , located between the surface adjacent the second opening 113 of the header-side flange 116 and the peripheral edge of the header-side flange 116 . This allows for easier insertion of the grommet 10 into the header plate.
  • a grommet 110 In use, a grommet 110 would be situated at or adjacent both ends of the tubular components 10 , meaning the grommet 110 is intended to be used in both orientations. In the orientation of FIG. 27 or 30 , the grommet 110 would be inserted into a lower header plate 58 , with a grommet 110 oriented in reverse orientation inserted in an upper header plate 56 .
  • the tube-side and header-side flanges 115 and 116 define an annular groove 120 in the outer wall surface of the grommet 110 .
  • the annular groove 20 is adapted to receive a header plate 58 .
  • Tube-side flange 115 has a substantially flat underside edge 121 . This surface is intended to be substantially parallel with an inner side 124 of the header plate 58 upon insertion.
  • header-side flange 116 has a substantially flat shoulder edge 122 . This surface is intended to be substantially parallel with an outer side 125 of the header plate 58 upon insertion.
  • Reference to ‘inner’ and ‘outer’ in this context are references to the relationship with the radiator core being ‘inner’ and the header plates and tanks being ‘outer’.
  • FIG. 31 illustrates an embodiment of the grommet 110 , after it has been inserted into a hole of a header plate 58 .
  • the depth of the annular groove 120 is sized to accommodate the inner peripheral edge of the insertion hole 126 , such that both the tube-side and the header-side flanges 115 , 116 act as shoulders, and overlap the inner peripheral portion surrounding the insertion hole 126 of the header plate 58 .
  • the underside edge 121 of the tube-side flange 115 is in contact with the inner peripheral portion surrounding the insertion hole 126 of an inner side 124 of the header plate 58 .
  • shoulder edge 122 of the header-side flange 116 is in contact with the inner peripheral portion surrounding the insertion hole 126 of an outer side 125 of the header plate 58 .
  • the depth of the annular groove 120 is substantially equal to the thickness of the header plate 58 .
  • the flat sides and sharp transition in the faces of the annular groove 120 provide positive insertion notification when the grommet 110 is accurately positioned in the header plate 58 . This shape also increases the pop-out pressure by about 100 kPa over prior art grommets to 600 kPa.
  • FIG. 32 shows the grommet 10 inserted into a hole of a header plate 58 with a tubular component 10 also inserted.
  • the induced interference from the convex inner side wall surfaces 114 create a seal between the end portion 20 and the inner side wall surfaces 114 as well as a seal between the annular groove 120 and the header plate 58 .
  • the convex side wall surfaces 114 of the grommet 110 aids the material to absorb the cyclic loading experienced by the grommet 110 when in service. This occurs as the curved inner side wall surfaces 114 are compressed in the transverse direction of the grommet 110 , leading to less displacement and/or flexure of the grommet material 110 at the flanges 115 , 116 .
  • ELASTOSIL® R 756/50 is a peroxide curing high consistency silicone rubber whose vulcanizates possess excellent resistance to hot air, good tear resistance, low compression set, resistance to hydrocarbon, and is highly elastic.
  • the material is suitable for high temperature applications, as it is rated to withstand temperatures of 300° C. for at least seven days when combined with a suitable stabiliser.
  • the material is also able to withstand up to 270° C. for extended periods of time up to the life of the radiator.
  • Other materials possessing some or all of the above qualities may also be suitable for the grommet 110 .
  • Hydrocarbon, petrochemical and coolant resistance is also a desirable property of the material.
  • the grommets 110 are injection moulded by compression or injection moulding.
  • FIG. 25 shows an example of a prior art heat exchanger grommet 1 of the kind shown in U.S. Pat. No. 6,247,232.
  • This grommet only has a tube side flange 3 in its natural unloaded configuration.
  • a defacto flange 5 is created on the header side by deformation of the grommet material.
  • Finite element analysis was carried out on this prior art grommet 1 , with simulated service conditions.
  • Prior art grommets such as this suffer from the fact that under cyclic loading conditions experienced in service, forces transferred from the tubing to the grommet 1 lead to high tensile loaded areas, which the material of the grommet is not suitable for.
  • FIG. 26 shows a finite element analysis carried out on the present heat exchanger grommet 110 .
  • the maximum stress 9 is a compressive load, which is absorbed by the material.
  • the material the grommet is manufactured from is a material that performs well under compressive loading but relatively poor under tensile loading. This figure also shows that the grommet 110 can provide a more evenly distributed load along the sealing path of the grommet 110 and a heat exchanger tube 10 and the header plate 58 .
  • FIGS. 33 to 40 illustrate the form of the centre support assembly to support the core 50 .
  • Each component 10 has an associated centre support bracket 80 extending therearound.
  • the brackets 80 are of the form shown in FIGS. 35 and 36 and are made of flexible plastic material to flex to slide around the component 10 .
  • the brackets 80 interconnect as shown in FIG. 34 .
  • Terminator blocks 82 and 84 as shown in FIGS. 37 to 40 are provided at the front and rear of the core 50 and interconnect with the front and rear rows of the brackets 80 .
  • the terminator blocks 82 and 84 are mounted to front and rear centre support bars (not shown).
  • the core 50 of components 10 are reinforced to increase rigidity and reduce vibration.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US16/335,011 2016-09-21 2017-09-20 Heat exchanger and components and methods therefor Abandoned US20190249925A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
AU2016903811 2016-09-21
AU2016903811A AU2016903811A0 (en) 2016-09-21 Heat exchanger grommet
AU2016903835A AU2016903835A0 (en) 2016-09-22 Heat exchanger and components and methods therefor
AU2016903835 2016-09-22
PCT/AU2017/051024 WO2018053585A1 (fr) 2016-09-21 2017-09-20 Échangeur de chaleur et éléments et systèmes associés

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EP (1) EP3515630A4 (fr)
AU (1) AU2017329245A1 (fr)
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US12078431B2 (en) 2020-10-23 2024-09-03 Carrier Corporation Microchannel heat exchanger for a furnace

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CN114322105B (zh) * 2021-03-29 2023-07-25 杭州三花微通道换热器有限公司 换热器和空调系统

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US5042574A (en) * 1989-09-12 1991-08-27 Modine Manufacturing Company Finned assembly for heat exchangers
US5433268A (en) * 1993-12-03 1995-07-18 L & M Radiator, Inc. Radiator construction
US5553770A (en) * 1994-03-07 1996-09-10 Texas Instruments Incorporated Heat exchanger assemblies-material for use therin, and a method of making the material
JP2002361405A (ja) * 2000-09-25 2002-12-18 Showa Denko Kk 熱交換器の製造方法
EP1440759B8 (fr) * 2003-01-27 2007-11-07 SPX-Cooling Technologies GmbH Méthode pour fabriquer un échangeur de chaleur
EP1579942A1 (fr) * 2004-03-26 2005-09-28 Balcke-Dürr GmbH Procédé de fabrication d'un échangeur de chaleur
CN103502768B (zh) * 2011-04-25 2016-08-17 马勒国际有限公司 制造具有增强材料系统的换热器的方法
US20150027679A1 (en) * 2012-01-18 2015-01-29 Holtec International Finned tube assemblies for heat exchangers
US9302337B2 (en) * 2012-08-09 2016-04-05 Modine Manufacturing Company Heat exchanger tube, heat exchanger tube assembly, and methods of making the same
WO2015081274A1 (fr) * 2013-11-27 2015-06-04 Brayton Energy, Llc Echangeur thermique a enveloppe aplatie

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Publication number Priority date Publication date Assignee Title
US12078431B2 (en) 2020-10-23 2024-09-03 Carrier Corporation Microchannel heat exchanger for a furnace

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WO2018053585A1 (fr) 2018-03-29
EP3515630A1 (fr) 2019-07-31
EP3515630A4 (fr) 2020-04-29

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