US20040182559A1 - Heat exchanger tube - Google Patents

Heat exchanger tube Download PDF

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Publication number
US20040182559A1
US20040182559A1 US09/814,508 US81450801A US2004182559A1 US 20040182559 A1 US20040182559 A1 US 20040182559A1 US 81450801 A US81450801 A US 81450801A US 2004182559 A1 US2004182559 A1 US 2004182559A1
Authority
US
United States
Prior art keywords
tube
walls
web
abutted
heat exchanger
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
US09/814,508
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English (en)
Inventor
Scott Kent
James Anders
Henry Beamer
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Individual
Original Assignee
Individual
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
Application filed by Individual filed Critical Individual
Priority to US09/814,508 priority Critical patent/US20040182559A1/en
Priority to DE60209994T priority patent/DE60209994T2/de
Priority to EP02075849A priority patent/EP1243884B1/de
Priority to JP2002060495A priority patent/JP3631214B2/ja
Publication of US20040182559A1 publication Critical patent/US20040182559A1/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
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0391—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits a single plate being bent to form one or more conduits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
    • B21C37/15—Making tubes of special shape; Making tube fittings
    • B21C37/22—Making finned or ribbed tubes by fixing strip or like material to tubes
    • B21C37/225—Making finned or ribbed tubes by fixing strip or like material to tubes longitudinally-ribbed tubes
    • 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
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements

Definitions

  • This invention relates to heat exchangers in general, and specifically to a novel construction for a fabricated heat exchanger tube.
  • Cross flow automotive heat exchangers such as radiators, condensers, and heater cores have, for decades, followed the same general design of a basic core bordered by two side tanks or header tanks.
  • the basic core consists of a plurality of parallel flow tubes, stacked with brazed corrugated air fins between, the ends of which tubes are brazed leak tight into regularly spaced slots in the header tanks.
  • the header tanks feed a flow medium into and out of the tubes, while air is blown across the tubes and air fins in a perpendicular or “cross” flow direction.
  • One of the two standard manufacturing methods for the tubes are the one piece extruded tube, in which a billet of hot metal, generally aluminum, is forced through a die that gives a constant cross section to the tube all along its length. Any part, produced in one, integral piece is generally thought to be more economical than a multi part piece, but, as noted, other considerations may apply.
  • Extruded tubes have proven difficult to surface coat with braze material. Consequently, the surface coating of braze material necessary to braze all parts of the core together must generally be applied to the corrugated fin material that contacts the outside of the extruded, one piece tube.
  • braze material is abrasive and deleterious to the fin forming machinery, and the fin material must be made thicker and heavier than otherwise needed in order to allow successful braze material coating.
  • Fabricated, multi piece tubes are formed from flat stock that can easily be coated with braze material first, obviating the need to coat the fins.
  • a design that attempts to combine the advantages of fabricated and extruded designs uses a single piece of metal stock folded in a general Z shape, with the center of the Z being corrugated to provide the inner web, and the top and bottom of the Z folded down over the center corrugation from opposite directions to form integral outer walls of the tube.
  • An example may be seen in U.S. Pat. No. 2,757,628. While one piece, such a design is limited insofar as both the central corrugation and top and bottom walls must have the same material and thickness, meaning that the integral internal web may well be thicker and heavier than it would otherwise have to be. In addition, the internal web will inevitably be coated with the same braze material as the outer integral walls.
  • a variation of the Z design bends the two outer walls only half way down over the width of the tube, into abutment with a single central wall, giving only two, rather than several, divided compartments in the tube.
  • An example is shown in U.S. Pat. No. 4,633,056, which also shows that the edges of the outer walls, where they are brazed to the single central wall, may either be sharp, or bent over in a curved foot, the latter obviously giving more surface to surface braze contact, although requiring an extra bending step in processing.
  • corrugations are regular or symmetric. This gives both a uniform size for all of the flow paths (but for the outboard pair, which are often inevitably smaller in cross section), and gives a uniform internal pressure resistance to the tube all across its width.
  • the invention is a novel tube construction that has the central strengthening feature of the B tube design described above, but with divided flow paths provided by a specially designed, separate inner corrugated web.
  • the outer shell of the tube is formed in a general “B” shape, with two 90 degree walls that abut at the center.
  • the edges of the abutting 90 degree walls are curved upwardly, rather than being sharp.
  • the edges of the 90 degree walls do not directly contact the inner surface of the tube.
  • a corrugated inner web is placed inside the tube as it is folded down, and is captured between the under surface of the 90 degree wall edges and the opposed inner surface of the tube.
  • the corrugated web rather than being regular and symmetric, has a widened and flattened central channel that allows it to be captured without deforming the corrugations to either side.
  • both the inner and outer surfaces of the outer tube are braze coated, so that the inner web need not be.
  • one side of the web channel brazes to the undersurface of the 90 degree wall edges, and the other side of the web channel brazes to the opposed inner surface of the tube, solidly anchoring and locating the web within the tube.
  • the net effect is that the abutted 90 degree walls strengthen the tube, even without direct contact across both sides of the tube.
  • the web can be formed with any desired thickness, independent of the outer tube wall thickness and, as noted, need not be braze coated, though it can be. Small, divided flow paths inside the tube are created both by the regular corrugations located to either side of the central web channel, and by the location of the abutted 90 degree walls within the central web channel.
  • the decoupling of the web and tube material allows the optimal material to be independently used for both, but the end result is similar to a one piece extruded tube in terms of strength and function.
  • FIG. 1 is a perspective view of the end of a preferred embodiment of a tube made according to the invention.
  • FIG. 2 is an end view of a piece of tube stock prior to the manufacturing operation
  • FIG. 3 is an end view of the tube stock after a first bending operation
  • FIG. 4 is an end view of the tube stock after a second bending operation
  • FIG. 5 is an end view of the tube stock after a third bending operation
  • FIG. 6 is an end view of the tube stock after a fourth bending operation, and showing the web
  • FIG. 7 is an end view of the tube stock after a fifth bending operation, and showing the web in place;
  • FIG. 8 is an end view of the tube stock after a sixth bending operation, and showing the web in place and anchored down.
  • Tube 10 is a brazed, fabricated tube, having only two basic components, one of which is an outer shell formed with two inner chambers, like the so called “B tube” configuration described in UK patent 1,149,923 noted above.
  • n 2 (the number of inner chambers), and only n ⁇ 1, or one, piece of tube stock is needed to form the outer shell, in a manner described in more detail below.
  • the outer shell though unitary, can be conceptualized as a single, full width lower wall 12 spaced from a pair of upper walls 14 which preferably, but not necessarily, are equal in width.
  • Upper walls 14 are integral to a pair of equal height, abutted 90 degree walls 16 , each of which terminates in a curved, out turned foot 18 .
  • the abutted 90 degree walls 16 form a central seam running the entire length of the outer shell of tube 10 , and form a central strengthening member therefor. While the coincidental provision of two divided chambers within tube 10 would provide some heat transfer advantage, by the obvious expedient of providing a greater ratio of conductive perimeter surface per enclosed volume, that effect is minimal, for such a minimal subdivision of the inner volume.
  • the primary advantage of the abutted 90 degree walls 16 is simply the additional stiffening and strengthening and outer shell, and the location of the inevitable at least one seam down the central upper surface of the tube 10 , rather than down the side edge.
  • the end of tube 10 is ultimately brazed into a header slot, as with any headered cross flow heat exchanger, and it is easier to control the geometry of the slot-tube end braze interface along the width of the slot, rather than at the edge of the slot.
  • the other basic component of tube 10 is a corrugated inner web, a preferred embodiment of which is indicated generally at 20 .
  • Web 20 would likely be same basic material as the outer shell of tube 10 , or at least similar enough to prevent a significant galvanic differential.
  • web 20 need not be identical to the outer shell of tube 10 , since it is not integral therewith. Therefore, it can be, preferably, thinner, as shown, and need not be coated with braze material on its outer surface (though it can be, as described in more detail below).
  • web 20 has a width W1 and is formed with a series of corrugations 22 which may be, but need not be, generally sinusoidal and regular in shape, with rounded crests and sloped sides.
  • the entire width of web 20 is not comprised of regular, symmetrical corrugations, as is conventional. Instead, a widened, intermediate channel 24 of width C, is formed, which is flattened at the bottom, and open at the top, for a purpose described below.
  • the channel 24 is also central to the web 20 , with an equal number of regular corrugations 22 located to either side, though, again, it need not absolutely be centrally located.
  • FIGS. 2 through 5 the initial steps in the manufacture of the outer shell of tube 10 are illustrated.
  • a single, flat piece of flat metal stock S is braze coated on at least one surface, that which will ultimately comprise the outer surface of tube 10 and, preferably, on the other surface, as well, though not necessarily on more than the outer surface.
  • stock S would be pulled from a continuous coil of stock, and run through a progressive series of rollers, that would continually and gradually form it into the subsequent shapes illustrated, rather than being bent incrementally in individual dies.
  • the first step in the gradual formation of the final shell shape is the bending of the curved feet 18 , each of which has a total width F, shown in FIG. 3.
  • FIG. 3 the first step in the gradual formation of the final shell shape
  • each upper wall 14 is preferably one half the total outside width W2 of lower wall 12 , “upper” and “lower” being terms of convenience, of course.
  • the upper walls 14 are bent progressively farther over and, eventually, the web 20 settles onto the inner surface of lower wall 12 .
  • the web width W1 is comparable to the width W2 of lower wall 12 , less by approximately twice the wall thickness of stock S, so as to facilitate the location of web 20 inside of tube 10 .
  • the upper walls 14 are bent over far enough to abut, and the under surfaces of the feet 18 pass by the crests of the two inner most corrugations 22 and down to engage the upper surface of web channel 24 , anchoring its lower surface to the inner surface of lower wall 12 .
  • the height H of the 90 degree walls 16 is set so as to assure that the tops and bottoms of the web corrugations 22 make close contact, without crushing, with the inner surfaces of both the upper walls 14 and the lower wall 12 .
  • the total width of the out turned feet 18 is just slightly less than the width C of web channel 24 , so as to assure a close fit into the channel 24 without binding, but still serving to help positively locate the web 20 accurately within the interior of tube 10 , with a limited side to side play.
  • the fully nested and abutted composite of the bent metal stock S and separate, anchored inner web 20 are brazed together in a conventional braze oven to complete tube 10 .
  • This is best done as part of an entire core with tubes 10 .
  • braze material melted from and near the interfaces of the abutted component surfaces is drawn by capillary action into those closely abutted interfaces, later hardening to create strong bonds.
  • clad material on the air centers could provide what was needed for a bolted walls 16 , so bare tube stock S could be used. Or, all surfaces could be coated, on both. Any such combination would provide a supply of melted braze material to the various interfaces.
  • the under surfaces of the feet 18 would braze to the upper surface of the flattened channel 24
  • the under surface of channel 24 would braze to the inner surface of tube lower wall 12 , ultimately securing the upper walls 14 to the lower wall 12 .
  • the abutted 90 degree walls alone 16 add a degree of strengthening to the tube 10 , and the presence of the intermediate bonded corrugations add to that strengthening, depending on the thickness of the material of web 20 .
  • the width F of the curved feet 18 could be varied, in absolute terms, but making the width of the feet 18 together approximately equal to the width of two corrugations 22 serves to subdivide the channel 24 into two flow paths approximately equal to the size of the flow paths created by each of the corrugations 22 , and so yields a measure of structural symmetry across the entire width of tube 10 .
  • the degree of curvature of the feet 18 could be made more or less, but flattened edges, or sharp edges, instead of a curvature would not be preferred. Such edges would not braze as well to the upper surface of the channel 24 , and would not be as likely to fold past the adjacent web corrugations 22 without binding as the upper walls 14 were folded down.
  • the abutted 90 degree walls are central, and the upper walls 12 consequently of equal width, but they could be shifted to one side or the other, if desired, especially if the relative width of the feet 18 and the corrugations 22 noted above were maintained, since the effect on the inner structural symmetry of the tube 10 would not be severe. Therefore, it will be understood that it is not intended to limit the invention to just the embodiment disclosed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US09/814,508 2001-03-22 2001-03-22 Heat exchanger tube Abandoned US20040182559A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US09/814,508 US20040182559A1 (en) 2001-03-22 2001-03-22 Heat exchanger tube
DE60209994T DE60209994T2 (de) 2001-03-22 2002-03-05 Wärmetauscherrohr
EP02075849A EP1243884B1 (de) 2001-03-22 2002-03-05 Wärmetauscherrohr
JP2002060495A JP3631214B2 (ja) 2001-03-22 2002-03-06 熱交換器伝熱管

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US09/814,508 US20040182559A1 (en) 2001-03-22 2001-03-22 Heat exchanger tube

Publications (1)

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US20040182559A1 true US20040182559A1 (en) 2004-09-23

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US09/814,508 Abandoned US20040182559A1 (en) 2001-03-22 2001-03-22 Heat exchanger tube

Country Status (4)

Country Link
US (1) US20040182559A1 (de)
EP (1) EP1243884B1 (de)
JP (1) JP3631214B2 (de)
DE (1) DE60209994T2 (de)

Cited By (12)

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Publication number Priority date Publication date Assignee Title
US20050006082A1 (en) * 2003-06-21 2005-01-13 Viktor Brost Flat heat exchanger tube
US20090133865A1 (en) * 2006-10-06 2009-05-28 Gianfranco Natali Process for producing heat exchanger tubes and heat exchanger tubes
US20100025027A1 (en) * 2008-07-29 2010-02-04 Daniel Borst Heat exchanger with collecting tube, collecting tube, and method for producing the same
US20100028139A1 (en) * 2006-06-27 2010-02-04 Airbus France Turbojet for aircraft
US20130180694A1 (en) * 2010-07-16 2013-07-18 Behr Gmbh & Co. Kg Solderable fluid channel for a heat exchanger of aluminium
US20140000853A1 (en) * 2010-06-30 2014-01-02 Valeo Systemes Thermiques Fluid Circulation Tube And A Heat Exchanger Comprising Such Tubes
GB2509762A (en) * 2013-01-14 2014-07-16 Halla Visteon Climate Control Tube for a heat exchanger
CN104792210A (zh) * 2014-01-16 2015-07-22 泰安鼎鑫冷却器有限公司 三部件组合散热管
US20150241132A1 (en) * 2012-10-02 2015-08-27 Mitsubishi Electric Corporation Double pipe heat exchanger and refrigeration cycle device
WO2015163808A1 (en) * 2014-04-22 2015-10-29 Titanx Engine Cooling Holding Ab Vehicle heat exchanger tube and vehicle radiator comprising such a tube
US20180106556A1 (en) * 2016-10-14 2018-04-19 Hanon Systems B-tube reform for improved thermal cycle performance
WO2025157194A1 (zh) * 2024-01-26 2025-07-31 杭州三花微通道换热器有限公司 一种换热器和一种换热器的加工方法

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DE10304692A1 (de) * 2003-02-06 2004-08-19 Modine Manufacturing Co., Racine Gewellter Einsatz für ein Wärmetauscherrohr
BRPI0513873B1 (pt) 2004-07-28 2021-05-04 Valeo, Inc Conjunto trocador de calor e método para fabricar conjunto trocador de calor
FR2881218B1 (fr) * 2005-01-24 2007-06-01 Valeo Systemes Thermiques Tube plat avec insert pour echangeur de chaleur
DE102005043093A1 (de) * 2005-09-10 2007-03-15 Modine Manufacturing Co., Racine Wärmetauscherrohr
JP4974327B2 (ja) * 2005-12-15 2012-07-11 株式会社デンソー 熱交換器用チューブの製造方法および熱交換器
KR100990508B1 (ko) 2007-12-13 2010-10-29 주식회사 한국번디 열교환기의 제조방법
JP2010008018A (ja) * 2008-06-30 2010-01-14 Showa Denko Kk インナーフィン付き熱交換管およびこれを用いた熱交換器
FR2962202B1 (fr) * 2010-06-30 2015-12-11 Valeo Systemes Thermiques Tube pour echangeur de chaleur et echangeur de chaleur equipe d'un tel tube
FR2962203B1 (fr) * 2010-06-30 2015-06-26 Valeo Systemes Thermiques Tube pour echangeur de chaleur et echangeur de chaleur equipe d'un tel tube
FR2972523A1 (fr) * 2011-03-08 2012-09-14 Peugeot Citroen Automobiles Sa Echangeur thermique optimise et procede d'obtention d'un tel echangeur
FR2980739B1 (fr) * 2011-10-04 2014-06-20 Valeo Systemes Thermiques Tube de radiateur de refroidissement pour vehicule automobile et radiateur de refroidissement pour vehicule automobile comprenant un tel tube.
DE102011085935A1 (de) 2011-11-08 2013-05-08 Behr Gmbh & Co. Kg Flachrohr und Wärmeübertrager mit einem solchen Flachrohr
JP2012193950A (ja) * 2012-05-14 2012-10-11 Keihin Thermal Technology Corp 熱交換器用扁平管
DE102012211350A1 (de) 2012-06-29 2014-01-02 Behr Gmbh & Co. Kg Flachrohr und Wärmeübertrager mit einem solchen Flachrohr
DE102014200708A1 (de) 2014-01-16 2015-07-16 MAHLE Behr GmbH & Co. KG Flachrohr
CN104807357A (zh) * 2014-01-24 2015-07-29 泰安鼎鑫冷却器有限公司 一种组合式散热管
DE112015000904T5 (de) * 2014-02-21 2016-11-17 Hanon Systems Rohr für Wärmetauscher
KR102191901B1 (ko) * 2014-03-05 2020-12-17 한온시스템 주식회사 열교환기용 튜브
KR102189621B1 (ko) * 2015-01-29 2020-12-11 한온시스템 주식회사 열교환기용 튜브
FR3062901A1 (fr) * 2016-12-09 2018-08-17 Valeo Systemes Thermiques Tube d’echangeur thermique, echangeur thermique et procede d’assemblage du tube correspondants
DE102017208210A1 (de) * 2017-05-16 2018-11-22 Hanon Systems Wärmetauscher
DE102018111585A1 (de) * 2017-06-22 2018-12-27 Hanon Systems Vorrichtung zur Wärmeübertragung sowie Verfahren zum Herstellen der Vorrichtung
US20200271393A1 (en) * 2019-02-27 2020-08-27 GM Global Technology Operations LLC Heat exchanger tube

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US5295302A (en) * 1991-10-29 1994-03-22 Calsonic Corporation Method of manufacturing an aluminum heat exchanger
US5441106A (en) * 1992-06-24 1995-08-15 Llanelli Radiators Limited Heat exchange tubes
US6000461A (en) * 1997-03-21 1999-12-14 Livernois Research And Development Co. Method and apparatus for controlled atmosphere brazing of folded tubes
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Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7665512B2 (en) * 2003-06-21 2010-02-23 Modine Manufacturing Company Flat heat exchanger tube
US20050006082A1 (en) * 2003-06-21 2005-01-13 Viktor Brost Flat heat exchanger tube
US8235657B2 (en) * 2006-06-27 2012-08-07 Airbus Operations Sas Turbojet for aircraft
US20100028139A1 (en) * 2006-06-27 2010-02-04 Airbus France Turbojet for aircraft
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DE60209994T2 (de) 2006-09-07
EP1243884A3 (de) 2002-10-09
EP1243884A2 (de) 2002-09-25
JP2002327994A (ja) 2002-11-15
DE60209994D1 (de) 2006-05-11
EP1243884B1 (de) 2006-03-22
JP3631214B2 (ja) 2005-03-23

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