EP1061318B1 - Geripptes Wärmetauscherrohr und dessen Herstellung - Google Patents

Geripptes Wärmetauscherrohr und dessen Herstellung Download PDF

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Publication number
EP1061318B1
EP1061318B1 EP00420129A EP00420129A EP1061318B1 EP 1061318 B1 EP1061318 B1 EP 1061318B1 EP 00420129 A EP00420129 A EP 00420129A EP 00420129 A EP00420129 A EP 00420129A EP 1061318 B1 EP1061318 B1 EP 1061318B1
Authority
EP
European Patent Office
Prior art keywords
tube
ribs
profile
heat exchange
spaces
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00420129A
Other languages
English (en)
French (fr)
Other versions
EP1061318A1 (de
Inventor
André Bailly
Romuald Jurkowski
Marc Altazin
Slimane Meziani
Jean-Marie Michaud
Jean-Michel Navarro
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.)
Compagnie Industrielle dApplications Thermiques SA CIAT
Original Assignee
Compagnie Industrielle dApplications Thermiques SA CIAT
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Filing date
Publication date
Application filed by Compagnie Industrielle dApplications Thermiques SA CIAT filed Critical Compagnie Industrielle dApplications Thermiques SA CIAT
Publication of EP1061318A1 publication Critical patent/EP1061318A1/de
Application granted granted Critical
Publication of EP1061318B1 publication Critical patent/EP1061318B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element

Definitions

  • the invention relates to a heat exchange tube, and to its manufacturing process, as well as to a heat exchanger incorporating such a tube.
  • the coefficient of heat exchange in two-phase phase between a smooth metal tube, such as a copper tube, and a heat transfer fluid, such as di-fluoro-chloromethane varies between 1500 and 3000 W / m 2 / ° C as a function of the heat flow transferred, that is to say as a function of the nature of the fluid in which the tube is immersed, which may be a liquid or a gas.
  • this coefficient can be increased to values between approximately 3,800 W / m 2 / ° C and approximately 6,000 W / m 2 / ° C depending on the case, which constitutes a significant increase. .
  • JP-A-02 097 896 It is also known from JP-A-02 097 896 to provide that part of the internal ribs of a tube are inclined, the other ribs being symmetrical with respect to a radius which crosses them in their center. This non-uniform geometry of the ribs promotes flow turbulence. In addition, given their geometry, the inclined ribs are deformed essentially by crushing, which does not guarantee a precise conformation of the internal face of the tube and requires significant efforts. The value of the heat exchange coefficient obtained is not guaranteed with precision and remains relatively low.
  • the invention aims to increase the value of the heat exchange coefficient of a tube, for its internal part without disturbingly increasing the coefficient of friction of the fluid on the internal surface of the tube or of the plate, in order to limit the pressure losses induced.
  • the invention relates to a heat exchange tube provided, on its internal surface, with ribs able to be shaped, characterized in that these ribs have, before their shaping, an asymmetrical profile, the apex of the profile of these ribs being offset relative to the base of this profile.
  • the spaces defined between two adjacent ribs of the tube or the plate appear, on one side, as a re-entrant cavity, that is to say with a partition inclined inward, which allows '' Significantly increase the heat exchange coefficient.
  • the shaping of the ribs which can be obtained during the crimping of external fins of the tube, is facilitated by the fact that the top of their profile is, before this setting shape, offset from its base because the effort to be exerted is a folding effort or to accentuate their inclination, this effort being significantly less than a pure crushing effort which should be exerted if the top was located at the base of the profile.
  • the invention makes it possible to adapt, during the shaping of the ribs, the geometry of the internal surface of the tube, therefore its heat exchange coefficient, to the nature of the fluid or fluids with which it will be used.
  • the fact that the top of the profile is offset relative to its base before this shaping makes it possible to effectively control the final geometry obtained by modulating the force exerted, for example by means of olives of preselected dimensions, during the crimping of fins external to the tube.
  • re-entrant cavity is meant a cavity whose edges are closed at their opening relative to their bottom. Such a cavity tends to "trap” the fluid it contains, which promotes the creation of vapor bubbles and increased heat exchange.
  • the top offset can be modifiable by crushing the ribs.
  • the ribs have, before shaping, a profile such that all the spaces defined between the ribs have an opening towards the center of the tube offset angularly relative to at the bottom of these spaces.
  • the spaces between the ribs are as many re-entrant cavities, on at least one side, which consequently promotes the heat exchanges and makes it possible to achieve the above-mentioned heat exchange coefficient values.
  • the width of the opening of the spaces between ribs is less than that of their bottom. This increases the "re-entrant cavity” effect obtained.
  • the invention also relates to a heat exchanger comprising a tube as described above, the thermal efficiency of which is substantially better than that of the prior art.
  • the invention finally relates to a method of manufacturing a tube of the aforementioned type and, more specifically, a method which consists in shaping the ribs by moving, by radial pressure, the top of the profile of each rib, which is in offset from its base, towards an internal surface of the tube. This process creates spaces between the ribs, one side of which approaches the geometry of a re-entrant cavity, while the intensity of the force exerted can be precisely controlled.
  • this crushing is carried out during the crimping of fins on the external face of the tube.
  • the combination of the two operations makes it possible to obtain the additional function sought without appreciable increase in the cost price of the tube.
  • the tube 1 shown in Figure 1 has a generally cylindrical profile, centered on an axis XX '.
  • 1 a the internal surface of the tube and 1 b its external surface.
  • the tube 1 On its inner surface 1 a, the tube 1 is provided with two ribs whose profile P, that is to say the section perpendicular to the axis XX 'is substantially triangular, the side faces P 1 and P 2 being straight before crimping.
  • S the apex of the profile P, this apex being the trace of an internal edge of the ribs 2 which can be rectilinear or helical depending on the geometry chosen for the ribs.
  • R the radius connecting the axis XX 'to the lateral edge L of the base B of each rib 2 closest to the vertex S.
  • R the radius connecting the axis XX 'to the lateral edge L of the base B of each rib 2 closest to the vertex S.
  • E the space defined between two contiguous ribs.
  • the shape of the rib 2 which adjoins it is such that the space E resembles a re-entrant cavity in which the thermal contact between the fluid which circulates in the tube and the wall 1 internal 1 a of the tube is optimized, in particular during boiling in the case of use with a two-phase fluid.
  • d 1 the width of the bottom F of each space E.
  • d 2 the width of the opening O of each space E towards the axis XX '.
  • the opening O of each space E is angularly offset around the axis XX 'relative to the bottom F because of the inclination and the crushing of the ribs 2.
  • the width d 2 is less than the width d 1 , which accentuates the fact that the spaces E appear as the re-entrant cavities for the fluid which they contain when using the tube 1 .
  • the invention is applicable to all types of tubes, whether they are formed "flat", that is to say shaped, rolled and then welded, or grooved internally in a conventional manner.
  • a tube produced by the invention may or may not have external cooling fins and can be used with a two-phase or single-phase fluid.
  • a tube is used, the height of the ribs of which remains less than 0.5 mm whereas their number is important because the surface tension of the di -fluoro-methane is weaker than that of water.
  • the heat exchange coefficient obtained can be of the order of 10,000 W / m 2 / ° C. In this case, the profile P is curved, as shown in Figures 4 to 6.
  • a heat exchanger comprising tubes as previously described is more efficient than those of the prior art because its overall heat exchange coefficient is higher.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)

Claims (10)

  1. Wärmetauscherrohr (1), das an seiner inneren Oberfläche (1a) mit Rippen ausgestattet ist, die geformt werden können, dadurch gekennzeichnet, daß alle Rippen (2) vor dem Formen ein symmetrisches Profil (P) besitzen, wobei der Scheitelpunkt (S) des Profils der Rippen in bezug auf die Basis (B) des Profils versetzt ist.
  2. Rohr nach Anspruch 1, dadurch gekennzeichnet, daß die seitlichen Oberflächen (P1, P2) des Profils (P) vor dem Formen im wesentlichen geradlinig sind.
  3. Rohr nach Anspruch 1, dadurch gekennzeichnet, daß die seitlichen Oberflächen (P1, P2) des Profils (P) vor dem Formen global gekrümmt sind, wobei die Krümmungsradien (R1, R2) der zwei Seiten (2) einer Rippe unterschiedlich sind.
  4. Rohr nach Anspruch 1, dadurch gekennzeichnet, daß die seitlichen Oberflächen (P1, P2) des Profils (P) vor dem Formen global gekrümmt sind, wobei die Krümmungsmittelpunkte (C1, C2) der zwei Seiten einer Rippe (2) einen Absatz bilden.
  5. Rohr nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Versatz des Scheitelpunkts (S) durch eine Druckverformung der Rippen (2) geändert werden kann.
  6. Rohr (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Rippen (2) vor dem Formen ein derartiges Profil (P) aufweisen, daß alle zwischen den Rippen definierten Räume (E) eine Öffnung (0) zum Zentrum (XX') des Rohrs aufweisen, die in bezug auf den Boden (F) der Räume winklig versetzt ist.
  7. Rohr nach Anspruch 6, dadurch gekennzeichnet, daß die Breite (d2) der Öffnung (0) kleiner ist als die Breite (d1) des Bodens (F) der Räume (E).
  8. Wärmetauscher, dadurch gekennzeichnet, daß er wenigstens ein Rohr (1) nach einem der vorhergehenden Ansprüche umfaßt.
  9. Verfahren zum Herstellung eines Wärmetauscherrohrs (1), das mit formbaren Rippen ausgestattet ist, dadurch gekennzeichnet, daß es daraus besteht, die Rippen (2) zu formen, indem mittels eines radialen Drucks der Scheitelpunkt (S) des Profils (P) jeder Rippe, der in bezug auf seine Basis (B) versetzt ist, in Richtung auf eine innere Oberfläche (1a) des Rohrs verschoben wird.
  10. Verfahren nach Anspruch 9, dadurch gekennzeichnet, daß die Druckverformung während der Bördelverbindung von Stegen (4) auf der äußere Oberfläche (1b) des Rohrs (1) ausgeführt wird.
EP00420129A 1999-06-16 2000-06-15 Geripptes Wärmetauscherrohr und dessen Herstellung Expired - Lifetime EP1061318B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9907865 1999-06-16
FR9907865A FR2795168B1 (fr) 1999-06-16 1999-06-16 Element d'echange thermique pourvu de nervures et son procede de fabrication, echangeur de chaleur pourvu d'un tel element

Publications (2)

Publication Number Publication Date
EP1061318A1 EP1061318A1 (de) 2000-12-20
EP1061318B1 true EP1061318B1 (de) 2003-09-10

Family

ID=9547080

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00420129A Expired - Lifetime EP1061318B1 (de) 1999-06-16 2000-06-15 Geripptes Wärmetauscherrohr und dessen Herstellung

Country Status (6)

Country Link
EP (1) EP1061318B1 (de)
AT (1) ATE249610T1 (de)
DE (1) DE60005089T2 (de)
ES (1) ES2202024T3 (de)
FR (1) FR2795168B1 (de)
PT (1) PT1061318E (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2216615A2 (de) 2009-02-04 2010-08-11 Wieland-Werke AG Wärmeübertragerrohr und Verfahren zu dessen Herstellung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6997248B2 (en) * 2004-05-19 2006-02-14 Outokumpu Oyj High pressure high temperature charge air cooler
DE102008030423B4 (de) 2007-12-05 2016-03-03 GIB - Gesellschaft für Innovation im Bauwesen mbH Rohr mit einer durch Noppen Oberflächenprofil-modifizierten Außenmantelfläche

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2193188B1 (de) * 1972-07-14 1976-09-17 Universal Oil Prod Co
JPH0297896A (ja) * 1988-09-30 1990-04-10 Matsushita Refrig Co Ltd 熱交換器の製造方法
FR2706197B1 (fr) 1993-06-07 1995-07-28 Trefimetaux Tubes rainurés pour échangeurs thermiques d'appareils de conditionnement d'air et de réfrigération, et échangeurs correspondants.
US5415225A (en) * 1993-12-15 1995-05-16 Olin Corporation Heat exchange tube with embossed enhancement
GB9420946D0 (en) * 1994-10-18 1994-12-07 Univ Manchester Heat transfer tube

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2216615A2 (de) 2009-02-04 2010-08-11 Wieland-Werke AG Wärmeübertragerrohr und Verfahren zu dessen Herstellung
DE102009007446A1 (de) 2009-02-04 2010-08-12 Wieland-Werke Ag Wärmeübertragerrohr und Verfahren zu dessen Herstellung
DE102009007446B4 (de) * 2009-02-04 2012-03-29 Wieland-Werke Ag Wärmeübertragerrohr und Verfahren zu dessen Herstellung
EP2216615A3 (de) * 2009-02-04 2013-12-04 Wieland-Werke AG Wärmeübertragerrohr und Verfahren zu dessen Herstellung
US8899308B2 (en) 2009-02-04 2014-12-02 Wieland-Werke Ag Heat exchanger tube and method for producing it

Also Published As

Publication number Publication date
EP1061318A1 (de) 2000-12-20
ES2202024T3 (es) 2004-04-01
ATE249610T1 (de) 2003-09-15
PT1061318E (pt) 2004-02-27
FR2795168B1 (fr) 2001-08-03
DE60005089D1 (de) 2003-10-16
FR2795168A1 (fr) 2000-12-22
DE60005089T2 (de) 2004-07-08

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