EP2106520A1 - Ailette d'échangeur de chaleur - Google Patents

Ailette d'échangeur de chaleur

Info

Publication number
EP2106520A1
EP2106520A1 EP07853381A EP07853381A EP2106520A1 EP 2106520 A1 EP2106520 A1 EP 2106520A1 EP 07853381 A EP07853381 A EP 07853381A EP 07853381 A EP07853381 A EP 07853381A EP 2106520 A1 EP2106520 A1 EP 2106520A1
Authority
EP
European Patent Office
Prior art keywords
strip
louvers
fin
louver
rib
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.)
Granted
Application number
EP07853381A
Other languages
German (de)
English (en)
Other versions
EP2106520A4 (fr
EP2106520B1 (fr
Inventor
John A. Kolb
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.)
Vista-Pro Automotive LLC
Original Assignee
Proliance International Inc
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 US11/622,512 external-priority patent/US7866042B2/en
Priority claimed from US11/770,210 external-priority patent/US8408283B2/en
Application filed by Proliance International Inc filed Critical Proliance International Inc
Publication of EP2106520A1 publication Critical patent/EP2106520A1/fr
Publication of EP2106520A4 publication Critical patent/EP2106520A4/fr
Application granted granted Critical
Publication of EP2106520B1 publication Critical patent/EP2106520B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • B21D13/00—Corrugating sheet metal, rods or profiles; Bending sheet metal, rods or profiles into wave form
    • B21D13/04—Corrugating sheet metal, rods or profiles; Bending sheet metal, rods or profiles into wave form by rolling
    • 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
    • F28F1/128—Fins with openings, e.g. louvered 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
    • F28F2215/00—Fins
    • F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media

Definitions

  • the present invention relates to the manufacture of heat exchangers and the manufacture of fins for heat exchanger cores primarily used in motor vehicles.
  • serpentine fins formed from thin gauge metal strip such as copper or aluminum are placed between and in contact with the tubes which carry the fluid to be cooled.
  • the heat exchanger core tubes typically extend between the manifolds, or the inlet and outlet tanks, of the heat exchanger.
  • the fins are the chief heat exchange medium between the coolant and the ambient air. The ability of the fins to transfer heat from the tubes to the air passing over the fins greatly relies on the design of the fins, with some including dimples or protrusions to aid in the heat transfer. To increase the heat transfer rate even further, louvers have been incorporated into the fins.
  • the louvers turbulate the air in a manner which has been found to increase the efficiency of the radiator.
  • the louver configuration may be so-called full louvers, where each louver in the row extends over essentially the entire distance between the tubes, or split louvers, where two side-by-side banks of louvers are employed in the row, so that each of the two louvers extends over less than half of the distance between each tube.
  • serpentine fins in which a flat metal strip is folded into convolutions to create the multiple fins between spaced tubes.
  • louvers When louvers are incorporated into fins, the structural integrity of the fin is compromised, particularly where serpentine fins are used.
  • a process known as hard-tool forming is typically used in forming the serpentine fin, wherein the louvers are formed with a pair of dies which have a star configuration for forming the convolutions at the same time.
  • the complexity of the dies and machinery for performing the formation of the fins make the process costly.
  • the rolls only need to have the die formation for the louvers, and the star shape of the roll may be eliminated.
  • backpressure is applied at different locations to the metal strip to force the metal to buckle, create the convolutions in the strip of metal, and form the finished serpentine configuration in the desired fin per inch density.
  • the air-forming process often produces convolutions that are more random in placement with respect to the rows of louvers compared to the use of hard tooling.
  • the use of the air-forming process has been found to distort the full louvers, change the angle of the louvers, and sometimes close the louver opening altogether.
  • serpentine heat exchanger fins have been described in U.S. Patent Nos. 5,361,829 to Kreutzer et al and 6,918,432 to Ozaki. Such reinforcements have been added to serpentine fins for several reasons. The first, as stated by Kreutzer, is to provide support for flat heat exchanger tubes against bulging due to internal pressure. A second reason, as stated by Ozaki, is to prevent distortion of the fins during washing of the core with water at high pressure. Additionally, serpentine fins are subject to compressive forces during the heat exchanger manufacturing operation of stacking the fins and tubes to make a core assembly. The stacked assembly of fins and tubes is held clamped under pressure during the subsequent soldering or brazing of the core.
  • louvered serpentine fins using an air-forming process. It is another object of the present invention to provide a method for manufacturing split louvered serpentine fins which is cost-effective, yet produces a quality fin.
  • a further object of the invention is to provide a method for manufacturing louvered serpentine fins which does not decrease the structural integrity of the fin, and optionally adds increased structural integrity against forces created during the manufacturing process.
  • a further object of the invention is to provide a heat exchanger fin which will have exceptional strength against bulging of the core due to internal pressure, against distortion to the fins due to pressure washing, and against damage in service due to road debris.
  • Another object of the invention is to provide a heat exchanger fin which has a ribbed hem, for use in a serpentine or plate-type fin.
  • Yet another object of the invention is to provide an improved method of air forming a serpentine heat exchanger fin using a ribbed hem.
  • the present invention provides a serpentine fin for assembly between tubes in a heat exchanger core comprising a metal strip having a width between opposite strip edges and a length greater that the width.
  • the strip edges have a hem formed thereon comprising a double thickness of the strip material extending a portion of the distance inward from the edge.
  • the metal strip has folds extending across the strip width such that the strip forms a serpentine shape, with the folds being adapted to contact the tubes in the heat exchanger core.
  • the serpentine fin also includes at least one row of louvers between adjacent folds.
  • the at least one row of louvers comprises louvers having openings extending in the direction of the strip length and formed in adjacent, spaced louver banks extending at least a portion across of the width of the strip.
  • the serpentine fin further includes ribs substantially parallel to the louver openings adjacent the strip edges and in at least one center portion of the strip between the strip edges, the ribs extending across the louver banks.
  • the hem may extend over a portion of the rib, may extend fully into the rib, or may extend fully into the rib and associated louver.
  • the rib may form a V-shaped channel or a U-shaped channel.
  • the louvers are formed at an angle to a plane of the metal strip and the louver angle is between about 26 degrees and about 32 degrees.
  • the metal strip has a thickness and the ribs have a height extending from a plane of the metal strip, and the ratio of the height to the thickness of the metal strip is between about 4 and 5.
  • the ribs are preferably elongated, plastically deformed sections and include at least one angled leg connected to an adjacent louver.
  • the present invention provides a plate-type flat fin for a heat exchanger core having at least one hem along at least a portion of an edge, wherein the hem comprises a double thickness of the strip material extending a portion of the distance inward from the edge; and at least one rib in the hem formed by plastically deforming the metal strip.
  • the fin plate preferably includes louvers.
  • the present invention is also directed to a method of manufacturing serpentine fins for assembly between tubes in a heat exchanger core.
  • the method includes providing a flat metal strip for making heat exchanger fins, the strip having a width between opposite strip edges and a length greater than the width and forming in the strip, while the strip is substantially flat, multiple rows of split louvers.
  • Each row of louvers has louvers with openings extending in the direction of the strip length and formed in adjacent, spaced louver banks extending at least a portion across of the width of the strip.
  • Each row includes at least one rib formed in the strip substantially parallel to the louver openings and extending across the pair of louver banks.
  • the metal strip has unformed portions extending across the strip width between rows of split louvers and at least one rib for forming folds across the width of the strip.
  • an initial pressure is applied to the metal strip to cause the substantially flat strip to buckle in the unformed portions and begin to form folds in the strip.
  • At least one row of louvers is between adjacent folds along the length of the strip.
  • further pressure is applied to the metal strip to complete formation of the folds of the strip to form the serpentine fin.
  • the distance between the adjacent folds conforms to the desired spacing distance between the heat exchanger core tubes.
  • the ribs formed in the strip may be along the edges of the strip or the ribs may be in a center portion between the edges.
  • the strip will have ribs formed both in the center portion and along the edges.
  • the ribs are elongated, plastically deformed sections and may include at least one angled leg connected to an adjacent louver.
  • the ribs have a height extending from a plane of the metal strip and the ratio of the height to the thickness of the metal strip is preferably between about 4 and 5.
  • the louvers have ends adjacent the unformed portions of the metal strip and after applying the further pressure to the metal strip, the distance between the louver ends and the folds at the unformed portions may be substantially equal.
  • the louvers are formed at an angle to a plane of the metal strip and the louver angle is preferably between about 26 degrees and about 32 degrees.
  • the strip may be continually moving such that the initial pressure is a backpressure applied by contacting the strip at a first location and such that the further pressure is a further backpressure applied by contacting the strip at a second location downstream of the first location with respect to strip movement.
  • the present invention further provides an improved method for manufacturing louvered serpentine fins by air forming.
  • the preferred method comprises providing a flat metal strip for making heat exchanger fins, the strip having a width between opposite strip edges and a length greater than the width.
  • Each of the opposite strip edges is a hemmed edge comprising a double thickness of the flat metal strip and extending a portion of the distance inward from the edges to form a hem.
  • the method includes forming in the strip, while the strip is substantially flat, multiple rows of louvers.
  • Each row of louvers comprises louvers having openings extending in the direction of the strip length and formed in adjacent, spaced louver banks extending at least a portion across of the width of the strip.
  • At least one rib is formed in the strip, which rib is substantially parallel to the louver openings and extends across the louver banks.
  • the metal strip has unformed portions extending across the strip width between rows of strip louvers and ribs for forming folds across the width of the strip.
  • the method includes applying an initial pressure to the metal strip to cause the substantially flat strip to buckle in the unformed portions and begin to form folds in the strip, with at least one row of louvers between adjacent folds along the length of the strip, and thereafter applying further pressure to the metal strip to complete formation of the folds of the strip to form the serpentine fin.
  • the distance between the adjacent folds conforms to the desired spacing distance between the heat exchanger core tubes.
  • the method preferably includes folding each of the opposite strip edges to form the hemmed edge, such that the hem extends over a portion of the rib, the hem extends fully into the rib, or the hem extends fully into the rib and associated louver.
  • the strip is continually moving.
  • the initial pressure is a backpressure applied by contacting the strip at a first location and the further pressure is a further backpressure applied by contacting the strip at a second location downstream of the first location with respect to strip movement.
  • the rib may be formed adjacent the strip edges and/or in a center portion of the strip between the strip edges.
  • the rib is preferably an elongated, plastically deformed section and may include at least one angled leg connected to an adjacent louver.
  • the louvers preferably have ends adjacent the unformed portions of the metal strip and wherein after applying the further pressure to the metal strip, the distance between the louver ends and the folds at the unformed portions is substantially equal.
  • the invention is directed to a serpentine fin for assembly between tubes in a heat exchanger core.
  • the serpentine fin comprises a metal strip having a width between opposite strip edges and a length greater than the width and having multiple rows of split louvers.
  • Each row of split louvers comprises louvers having openings extending in the direction of the strip length and formed in a pair of adjacent, spaced louver banks extending at least a portion across of the width of the strip.
  • the strip includes ribs formed in the strip substantially parallel to the louver openings adjacent the strip edges and in a center portion of the strip between the strip edges and extending across the pair of louver banks.
  • the metal strip has unformed portions extending across the strip width between rows of strip louvers and ribs, wherein the strip has folds along the unformed portions extending across the strip width such that the strip forms a serpentine shape with at least one row of split louvers between adjacent folds.
  • the folds are adapted to contact the tubes in the heat exchanger core.
  • Fig. 1 is a top plan view of a metal strip having split louvers formed therein in accordance with the present invention.
  • Fig. 2 is a cross sectional view of the split louvers of Fig. 1 along line 2-2.
  • Fig. 3 is a close up view of the portion of Fig. 2 in the vicinity of the end rib in the split louvers, wherein the strip edge has a single thickness.
  • Fig. 4 is a close up view of the portion of Fig. 2 in the vicinity of the center rib in the split louvers.
  • Fig. 5 is a close up view of the portion of Fig. 2 in the vicinity of the end rib in the split louvers, wherein the strip edge has a double thickness, hemmed edge extending toward the end rib.
  • Fig. 6 is an alternate embodiment of Fig. 5, wherein the double thickness of the hemmed edge extends fully over the end rib.
  • Fig. 7 is another embodiment of Fig. 5, wherein the double thickness of the hemmed edge extends fully into the end rib and the associated louver.
  • Fig. 8 is yet another embodiment of Fig. 5, wherein the rib is a sharp peak with the hemmed edge extending thereunder.
  • Fig. 9 is a further embodiment of Fig. 5, wherein the rib is a downward facing curved peak with the hemmed edge extending thereover.
  • Fig. 10 is another embodiment of Fig. 5, wherein the rib is an upward facing curved peak with the hemmed edge extending thereunder.
  • Fig. 11 is a cross-sectional elevational view, perpendicular to the length of the metal strip, showing the progressive formation of the hemmed edges.
  • Figs. 12-15 are side elevational views of an air forming machine showing the forming of the louvers and ribs by fin rolls, and the progression of the forming of the convolutions of the serpentine strip.
  • Fig. 16 is a front view of a portion of a heat exchanger core face showing a serpentine split louver fin of the present invention between heat exchanger core tubes.
  • Fig. 17 is an end view of a heat exchanger core showing a serpentine split louver fin of the present invention between heat exchanger core tubes.
  • Fig. 18 is a perspective view of a portion of a heat exchanger core showing serpentine split louver fins of the present invention sandwiched between heat exchanger core tubes.
  • Figs. 1-4 depict a split louver fin configuration formed in a flat metal strip in accordance with the present invention, prior to forming the serpentine convolutions.
  • a length of metal strip 12 of aluminum or preferably copper has split louvers 40 extending in rows 25 across the width of the strip, ribs 18a and 18b formed adjacent the louvers within the rows, and unformed portions 22 extending across the strip width between rows of the louvers.
  • the louvers are formed by cutting the strip and twisting and plastically deforming the cut portions. The opposite ends of each of the louvers maintain connection with the remaining metal strip by a twist portion.
  • Each row 25 of split louvers is made up of a pair of banks 25a, 25b of individual louvers 40, which are separated from each other by unformed portion 24 extending in the direction of the strip width.
  • the adjacent, spaced louver banks 25a, 25b extend across at least a portion of the width of the strip 12, and preferably extend across substantially all of the strip width.
  • the louvers 40, the openings between the louvers, and ribs 18a, 18b extend in the direction of the strip length 21.
  • Ribs 18a, 18b are plastically deformed in the strip substantially parallel to the louver openings in the direction of the strip length and extend substantially completely across the pair of louver banks 25a, 25b, including across the unformed strip portion 24 between the louver banks. End ribs 18a are located near the strip edges 27 and center ribs 18b are located in center portions of the strip between the strip edges. Ribs 18a, 18b extend across the pair of louver banks, but not beyond the ends of the louvers into the unformed sections 22 separating the rows of louvers. End ribs 18a shown in the detailed view of Fig.
  • rib 3 have plastically deformed portions and include one angled leg 18'a extending at an angle downward from the plane 30 of the undeformed metal strip and a bent portion 18"a that connects to the adjacent louver 40.
  • the end ribs are ultimately positioned, after assembly of the fin in the core, near the upstream and downstream ends of the fin relative to the direction of cooling airflow.
  • Center ribs 18b shown in the detailed view of Fig. 4 also have plastically deformed portions with angled legs 18'b extending at an angle downward from an undeformed metal strip portion in plane 30 and bent portions 18"b that connect to the adjacent split louvers 40.
  • each split louver 40 has a total height L and is angled at an angle ⁇ from the neutral plane 30 of the undeformed metal strip 12.
  • the strip and louvers have a thickness of about 0.0022 in. (0.056 mm), and the louvers have angle ⁇ of about 30° and height L of about 0.023 in. (0.58 mm).
  • the ribs have a height distance h in one direction from the neutral plane of about 0.0104 in. (0.26 mm).
  • the ratio of h/s is about 4.7, and signifies that the height of the rib is about 4.7 times the thickness of the fin material.
  • the metal strip may be made with a single thickness edge as shown in Fig. 3, where edge 27 is of the same thickness as the remainder of the strip material.
  • the metal strip may include a hem along each of the opposite edges along which the end ribs are formed.
  • the hem comprises a double thickness of the metal strip material and extends at least a portion inward from the edge. The distance to which the hem extends inward may vary as shown in the embodiments of Figs. 5-7.
  • the hem 88 is formed by folding a portion of the original cut metal strip edge 27 (Figs.
  • the invention having the hemmed edges also includes end ribs 18a having a plastically deformed angled leg 18'a and a bent portion 18"a.
  • the embodiment shown in Fig. 5 has the hem extending only a portion of the distance from the hem edge 80 to the end rib 18a, wherein no portion of the end rib 18a or the associated louver 40' is in the hemmed area.
  • the hem 88' extends from the hem edge 80 to a point partially or fully encompassing the end rib 18a, and more preferably, the hem 88" extends fully into the end rib and partially or fully into the associated louver 40'.
  • the end rib adjacent the edges of the metal strip may comprise a double thickness of the metal strip in part of the rib, in the entire rib or the entire rib along with a portion or the entirety of the associated louver.
  • the associated louver 40' is defined as the louver formed with and is attached to the adjacent end rib 18a.
  • the formed hem of double thickness provides structural integrity to the fin, both from forces encountered during use of the heat exchanger, and from compression forces incurred during the manufacturing of the heat exchanger.
  • This structural reinforcement is improved further when the end rib 18a is formed in the hemmed area, either partially embedded in the hem or fully embedded in the hem.
  • the hem may extend far enough inward to also incorporate the associated louver either partially or fully, increasing the resistance to external forces even further. This embodiment results in exceptional rigidity and provides superior resistance to fin and core damage.
  • Figs. 8-10 shows examples of a rib 82 embedded in the hemmed area wherein the rib has various cross-sectional patterns.
  • Fig. 8 shows a rib having cross-sectional pattern with a sharp peak formed by angled legs 82', 82" with the tip of the peak positioned upward in the same direction as the open edge 85 of the associated louver with respect to the neutral plane 30 of the unformed metal strip.
  • Fig. 9 shows a rib having a curved peak 86 with the crest of the peak 86' downward facing, opposite the direction of the open edge of the associated louver and
  • Fig. 10 has a curved peak 86 with the crest of the peak facing upward in the same direction as the open edge of the associated louver.
  • the variations in the cross sectional patterns of the rib, the distance to which the hem extends to or into the rib and associated louver, and the direction the peak of the rib faces may be further combined in a multitude of embodiments not specifically described.
  • the ribbing of the hemmed area may also be incorporated into the design and manufacturing of plate-type flat fins.
  • the plate-type fin is hemmed along at least one of the fin edges and includes at least one rib formed in the hemmed area.
  • This embodiment is not formed into a serpentine fin, but remains essentially flat, and gives the plate-type fin resistance to damage during handling of the fins during manufacture and transport and against stresses during use of the heat exchanger core.
  • the fin of the present invention employing a ribbed hem may be made by conventional hard tooling or by air forming.
  • the process of air forming the serpentine split louver fins of the present invention is shown in Figs. 11-15, and begins by providing a coil of unformed metal strip for continuous feeding through a modified prior art air forming machine 10. If the hemmed edges are to be employed, folding of the unformed metal strip edges to produce hemmed edges may be completed before the metal strip enters the air forming machine or as a step during the process of forming the heat exchanger fin after the metal strip is fed into the air forming machine.
  • Fig. 11 shows the partial folding of cut strip edges 27 to a first position 27' and subsequently to the final folded position 27" to form hem 88.
  • the air forming machine 10 comprises a front roller 50 which guides the metal strip through a pair of opposing wiping pads 52, one on each side of the metal strip, for cleaning any contamination thereon.
  • a pair of counter rotating fin rolls 60, 62 having a cylindrical shape are positioned downstream from the wiping pads with respect to the metal strip. If formation of the hem is to be made in the air forming machine, the folding operation may be made immediately after the wiping stage and prior to contact with the fin rolls. Fin rolls 60, 62 are sufficiently close to one another to exert a compression force on the surface of the moving metal strip in a direction normal to the strip plane, as well as move the strip continuously in direction 21.
  • each of the fin rolls 60, 62 have a plurality of meshing cutter blades and tool patterns 44 which cut and form the split louvers 40 and ribs 18a, 18b in the metal strip, to the configuration shown in Figs. 1-4.
  • each folding shaft 70, 72 has a plurality of arms extending outward from the axis of rotation, and the ends of the arms are parallel to the strip width. As shown in Fig. 12, the metal strip contacts arms of the rotating lower folding shaft 72 and upper folding shaft, which arms provide an initial backpressure in a direction opposite to the motion of the strip in direction 21.
  • the metal strip contacts one of the lower folding shaft 72 arms forcing an unformed portion 22 into a radius formed between shaft arms, creating the initial backpressure on the metal strip between the backing plate 68 and the lower folding shaft 72.
  • strip 12 begins to buckle along a first unformed portion 22 between backing plate 68 and lower folding shaft 72.
  • the unformed portions 22 of the metal strip have the least amount of structural integrity against forces which tend to make the metal strip bend across its width, while the split louvers and the ribs inhibit buckling and folding in the louver rows.
  • air forming refers to the fact that the folds are made in a controlled fashion in air without the necessity to use male and female tool sections conforming to the desired degree of folding.
  • Fig. 13 shows the result of the initial backpressure causing the metal strip to buckle along the unformed portions 22' a creating a fold in one direction, and to buckle along the unformed portion 22'b creating a fold in the opposite direction.
  • the metal strip moves from backing plate 68 to folding shafts 70, 72, it continues to buckle, and additional folds 22'a, 22'b created along the adjacent unformed portions 22 to create the folds or convolutions in the strip between each row 25 of split louvers.
  • the fold angles continue to increase as the strip approaches and passes between the folding shafts, as shown in Figs. 14 and 15, which show the progression of the strip folding.
  • a further backpressure is applied to the convoluted strip by a gathering station downstream of the folding shafts, again in a direction opposite to the strip movement direction 21.
  • this gathering station has fingers 96, preferably in the form of a metal brush, mounted on an adjustable lever 98 which sequentially contact the upper folds 22' of the convoluted strip as it passes in direction 21.
  • the force of fingers 96 urges the convoluted strip against a second base portion 48b, and may be adjusted to apply sufficient backpressure to create the desired density of strip convolutions, i.e., the number of straight portions containing split louver fins 25 (between folds) in a distance D of formed serpentine fin strip 12'.
  • This fin strip density is typically described as number of fins per inch. Increased backpressure at the gathering station produces a higher fin density, while lower backpressure at the gathering station results in a lower fin density.
  • the air forming process continues until the final fold angle is obtained at folded unformed portions 22' to form the desired number of folds into a length of fin strip 12'.
  • the fin strip 12' is subsequently cut to create the desired number of fins corresponding to the length of the tubes in the heat exchanger core.
  • Figs. 16, 17 and 18 show the completed serpentine fin strips 12' integrated with tubes 30 to form heat exchanger core 50. As shown in Fig. 18, incoming air flowing in direction 35 enters core 50 at leading fin edge 31 and exits at trailing fin edge 33.
  • the serpentine fin strips 12' are stacked in an alternating pattern with the tubes, and then compressed and brazed to form the completed core.
  • Fig. 16 One particular advantage of the use of ribs with the split louver serpentine fin made by air forming is shown in Fig. 16 with respect to the location of the ends of the individual louvers 40 from adjacent tubes 30. It is desirable to ensure that there is sufficient distance xi and x 2 between the louver ends and the tubes, so that the fold is confined to the unformed area between louver rows, and the ends of the louvers are not distorted, closed or crushed, or the louver angle changed, by the folding process.
  • the present invention of air forming a split louver serpentine fin has been shown to provide such distance to avoid damage to the louvers, and more importantly, provide a consistent distance X 1 , x 2 between the louver ends and the tubes, preferably where X 1 is substantially equal to x 2j to permit the as-built heat exchanger to come closer to the theoretical performance of the design.
  • the ribs formed within the split louver give the louver banks more integrity in the structure during the air forming of the convolutions as well as in the production of the radiator core when the tubes and fin strips are stacked and brazed.
  • a serpentine fin which has a hemmed leading edge where the air enters the heat exchanger, and preferably hemmed leading and trailing edges, will provide for a heat exchanger which has greater structural integrity during the manufacturing process and during use.
  • the hemmed edges, and particularly the hemmed edges having ribs therein allow for greater compression of the stacked fins and tubes without damaging or distorting the fins.
  • the hemmed edges give the fins protection from distortion or damage from the installer and, in use of the final product, the hemmed edges protect the fins from damage due to road debris, power washing, and repair.
  • the hemmed edges also aid in reinforcing the tubes during pressure cycling of the heat exchanger where the tubes have a tendency to expand or bulge from internal pressure of the heat exchanger.
  • the present invention provides an improved method for manufacturing split louvered serpentine fins using an air-forming process, which is cost-effective, yet produces a quality fin having consistently high efficiency and heat transfer rates.
  • the invention also provides a serpentine fin with a hemmed leading edge and preferably, hemmed leading and trailing edges, including split louvers and reinforcement ribs which add increased structural integrity against forces created during the manufacturing process.
  • Preferably at least one of the ribs is formed partially or fully within the hemmed area to provide exceptional rigidity to the leading and trailing edges of the heat exchanger fin, whether it is serpentine or plate- type.
  • the resulting increased rigidity provides superior resistance to fin and core damage resulting from handling, shipping and installation, and from pressure washing and road debris in use in the vehicle. This increased rigidity permits the use of thinner fin materials while preserving the aforementioned fin resistance to core damage.

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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)

Abstract

L'invention porte sur une ailette en serpentin pour un assemblage entre des tubes dans un noyau d'échangeur de chaleur, et sur un procédé de fabrication de celle-ci à partir d'une bande métallique. Les bordures de bande ont, de préférence, un ourlet comprenant une double épaisseur du matériau de bande s'étendant vers l'intérieur à partir de la bordure. La bande métallique a des plis s'étendant à travers la largueur de bande de telle sorte que la bande forme un serpentin, les plis étant aptes à entrer en contact avec les tubes dans le noyau d'échangeur de chaleur. De multiples rangées de volets d'aération fendus sont disposées entre des plis adjacents. Chaque rangée de volets d'aération fendus comprend des volets d'aération ayant des ouvertures s'étendant dans la direction de la longueur de bande et formés dans une paire de bancs de volets d'aération espacés, adjacents. Des nervures sont disposées parallèlement aux ouvertures de volets d'aération adjacents aux bordures de bande et dans au moins une partie centrale de la bande entre les bordures de bande, et s'étendent à travers la paire de bancs de volets d'aération. De préférence, la bande a des nervures formées à la fois dans la partie centrale et le long des bordures. Après la formation des rangées de volets d'aération fendus, une pression est appliquée à la bande pour amener la bande plate à se gauchir le long de parties non formées, s'étendant à travers la largeur de bande entre des rangées de volets d'aération fendus, formant ainsi des plis dans la bande conduisant à l'ailette en serpentin.
EP07853381.7A 2007-01-12 2007-12-14 Ailette d'échangeur de chaleur Not-in-force EP2106520B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US11/622,512 US7866042B2 (en) 2007-01-12 2007-01-12 Method for producing a split louver heat exchanger fin
US11/770,210 US8408283B2 (en) 2007-06-28 2007-06-28 Heat exchanger fin with ribbed hem
PCT/US2007/025559 WO2008085279A1 (fr) 2007-01-12 2007-12-14 Ailette d'échangeur de chaleur

Publications (3)

Publication Number Publication Date
EP2106520A1 true EP2106520A1 (fr) 2009-10-07
EP2106520A4 EP2106520A4 (fr) 2012-08-01
EP2106520B1 EP2106520B1 (fr) 2014-11-19

Family

ID=39608933

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07853381.7A Not-in-force EP2106520B1 (fr) 2007-01-12 2007-12-14 Ailette d'échangeur de chaleur

Country Status (4)

Country Link
EP (1) EP2106520B1 (fr)
CA (1) CA2672218A1 (fr)
MX (1) MX2009005538A (fr)
WO (1) WO2008085279A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2941040B1 (fr) 2009-01-15 2012-08-31 Valeo Systemes Thermiques Intercalaire d'echange de chaleur pour un dispositif d'echange de chaleur
CN101846479B (zh) * 2009-03-25 2012-02-22 三花丹佛斯（杭州）微通道换热器有限公司 用于换热器的翅片以及采用该翅片的换热器
EP2657637A4 (fr) * 2011-01-21 2014-07-09 Daikin Ind Ltd Échangeur de chaleur et climatiseur
JP2023072100A (ja) * 2020-04-06 2023-05-24 三菱電機株式会社 熱交換器、熱交換器を搭載した空気調和機、及び熱交換器の製造方法

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6218583U (fr) * 1985-07-18 1987-02-04
DE4142019A1 (de) 1991-12-19 1993-06-24 Behr Gmbh & Co Wellrippe fuer flachrohrwaermetauscher
JPH06180192A (ja) * 1992-12-08 1994-06-28 Nippondenso Co Ltd 熱交換器
JP2000154989A (ja) * 1998-11-18 2000-06-06 Daikin Ind Ltd 空気熱交換器
JP4456750B2 (ja) 2000-11-10 2010-04-28 株式会社ティラド コルゲートフィン型熱交換器およびその製造方法
JP2002372389A (ja) 2001-06-13 2002-12-26 Denso Corp 熱交換器

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2008085279A1 *

Also Published As

Publication number Publication date
EP2106520A4 (fr) 2012-08-01
EP2106520B1 (fr) 2014-11-19
CA2672218A1 (fr) 2008-07-17
WO2008085279A1 (fr) 2008-07-17
MX2009005538A (es) 2009-06-08

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