EP1223400B1 - Wärmeaustauscherrohr und Verfahren zu dessen Herstellung - Google Patents

Wärmeaustauscherrohr und Verfahren zu dessen Herstellung Download PDF

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Publication number
EP1223400B1
EP1223400B1 EP02000425A EP02000425A EP1223400B1 EP 1223400 B1 EP1223400 B1 EP 1223400B1 EP 02000425 A EP02000425 A EP 02000425A EP 02000425 A EP02000425 A EP 02000425A EP 1223400 B1 EP1223400 B1 EP 1223400B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger tube
tube according
fins
metal heat
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
EP02000425A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1223400A3 (de
EP1223400A2 (de
Inventor
Andreas Dr. Dipl.-Phys. Beutler
Manfred Dipl.-Ing. Knab
Andreas Dipl.-Ing. Knöpfler
Axel Dipl.-Ing. Kriegsmann (Fh)
Klaus Dipl.-Ing. Menze
Gerhard Dr.-Ing. Schüz
Andreas Dipl.-Ing. Schwitalla
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.)
Wieland Werke AG
Original Assignee
Wieland Werke AG
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 Wieland Werke AG filed Critical Wieland Werke AG
Publication of EP1223400A2 publication Critical patent/EP1223400A2/de
Publication of EP1223400A3 publication Critical patent/EP1223400A3/de
Application granted granted Critical
Publication of EP1223400B1 publication Critical patent/EP1223400B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, bars, wire, tubes 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
    • B21C37/20—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes and tubes with decorated walls
    • B21C37/207—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes and tubes with decorated walls with helical guides
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/182—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing especially adapted for evaporator or condenser surfaces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49377—Tube with heat transfer means
    • Y10T29/49378—Finned tube
    • Y10T29/49385—Made from unitary workpiece, i.e., no assembly

Definitions

  • the invention relates to a metallic heat exchanger tube, in particular for the evaporation of liquids from pure substances or mixtures on the tube outside, according to the preamble of claim 1.
  • Evaporation occurs in many areas of refrigeration and air conditioning technology as well as in process and energy technology.
  • Tube heat exchangers are frequently used in industry in which liquids of pure substances or mixtures on the outside of the tube evaporate, cooling a brine or water on the inside of the tube.
  • Such apparatuses are referred to as flooded evaporators.
  • the size of the evaporator can be greatly reduced. As a result, the production costs of such apparatuses decrease.
  • the necessary filling quantity of refrigerant which can account for a not inconsiderable share of the total investment costs in today's predominantly used chlorine-free safety refrigerants, is decreasing. In the case of toxic or flammable refrigerants, the danger potential can be reduced by reducing the filling quantity.
  • the standard high performance pipes today are about three times more efficient than smooth pipes of the same diameter.
  • the present invention relates to structured pipes in which the heat transfer coefficient is intensified on the pipe outside.
  • the heat transfer coefficient on the inside usually also needs to be intensified.
  • An increase in the heat transfer on the inside of the pipe usually results in an increase in the pipe-side pressure drop.
  • Heat exchanger tubes for shell and tube heat exchangers usually have at least one structured area and smooth end pieces and possibly smooth spacers.
  • the smooth end or intermediate pieces limit the structured areas. So that the tube can be easily installed in the shell and tube heat exchanger, the outer diameter of the structured areas must not be greater than the outer diameter of the smooth end and intermediate pieces.
  • nucleation sites are usually small gas or steam inclusions. Such nucleation sites can already be produced by roughening the surface. When the growing bubble reaches a certain size, it detaches from the surface. If in the course of bladder detachment the germinal site is flooded by inflowing liquid, the gas or vapor inclusion may be displaced by liquid. In this case, the germinal site is inactivated. This can be avoided by a suitable design of the germinal sites. For this purpose, it is necessary that the opening of the nucleus is smaller than that under the Opening cavity.
  • Integrally rolled finned tubes are understood to mean finned tubes in which the fins have been formed from the wall material of a smooth tube.
  • various methods are known with which the channels located between adjacent ribs are closed in such a way that connections between the channel and the surroundings remain in the form of pores or slots. Since the opening of the pores or slots is smaller than the width of the channels, the channels are suitably shaped cavities that promote formation and stabilization of nucleation sites.
  • substantially closed channels are formed by bending or flipping the rib (US 3,696,861, US 5,054,548), splitting and upsetting the fin (DE 2,758,526, US 4,577,381), and notching and upsetting the rib (US 4,660,630, EP 0,713,072, US 4,216,826).
  • the object is achieved according to the invention in a heat exchanger tube of the type mentioned, in which recesses are arranged in the region of the groove bottom of the helically extending primary grooves between the ribs, that the recesses are formed in the form of undercut secondary grooves.
  • An undercut secondary groove offers significantly better conditions for the formation and stabilization of bubble nuclei than the simple indentations proposed in EP 0.222.100.
  • the location of the undercut secondary grooves in the vicinity of the primary groove bottom is particularly favorable for the evaporation process, since at the groove bottom, the Wandübertemperatur is greatest and therefore there is the highest driving temperature difference for the bubble formation available.
  • Claims 2 to 14 relate to preferred embodiments of the heat exchanger tube according to the invention.
  • the ribs after the ribs have been formed by suitable additional tools, material is displaced from the region of the rib flanks toward the groove bottom, so that incomplete cavities are formed there, which represent the desired undercut secondary grooves.
  • the cavities extend from the primary groove bottom to the fin tip, extending to at most 45% of the fin height H, typically up to 20% of the fin height H.
  • the rib height H is thereby measured from the deepest point of the groove bottom, which was formed by the largest rolling disk, to the fin tip of the completely shaped finned tube.
  • the invention further provides, according to claims 15 to 20, various processes for the production of the heat exchanger tube according to the invention.
  • the integrally rolled finned tube 1 according to FIGS. 2 to 7 has helical circumferential ribs 3 on the tube outside, between which a primary groove 4 is formed.
  • Material of the rib flanks 5 is suitably displaced, so that in the region of the groove bottom 6 not completely closed cavities 7 are formed, which constitute the undercut secondary grooves according to the invention.
  • Material of the rib tips 8 is displaced such that the rib gaps are closed to form channels 9 to pores 26.
  • the production of the finned tube according to the invention takes place by means of a rolling process (cf., US Pat. Nos. 1,865,575 / 3,327,512) by means of the devices shown in FIGS.
  • the tool holder 10 are each arranged offset by 360 ° / n on the circumference of the finned tube.
  • the tool holder 10 are radially deliverable. They are in turn arranged in a stationary (not shown) rolling head.
  • the smooth tube 2 which enters the device in the direction of the arrow, is set in rotation by the driven rolling tools 11 arranged on the circumference, the axes of the rolling tools 11 running obliquely to the tube axis.
  • the rolling tools 11 consist in a conventional manner of several juxtaposed rolling disks 12 whose diameter increases in the direction of the arrow.
  • the centrally arranged rolling tools 11 form the helically extending ribs 3 from the tube wall of the smooth tube 2, wherein in the forming zone, the tube wall is supported by a rolling mandrel 27.
  • the rolling mandrel 27 can be profiled.
  • the distance between the centers of two adjacent ribs measured along the tube axis is referred to as the rib pitch T.
  • the rolling discs are profiled on their outer periphery so that the shaped ribs 3 have a substantially trapezoidal cross-section. Only in the transition region 13 between rib edge 5 and groove bottom 6, the rib deviates from the ideal trapezoidal shape. This transition region 13 is commonly referred to as Rippenfuß. The radius formed there is required to allow an unobstructed flow of material during the rib formation.
  • the undercut secondary grooves 7 are produced in the region of the base 6 of the primary grooves 4.
  • Three different embodiments can be used here:
  • a cylindrical disc 14 is engaged, whose diameter is smaller than the diameter of the largest rolling disc (Fig. 2).
  • the thickness D of this cylindrical disk 14 is slightly larger than the width B of the primary groove 4 formed by the rolling disks 12, in which case the width B of the primary groove 4 is measured at the point at which the rib edge 5 merges into the radius region of the rib foot 13.
  • the thickness D of the cylindrical disc is 50% to 80% of the rib pitch T.
  • the cylindrical disc 14 displaces material from the rib flank 5 towards the groove bottom 6.
  • the displaced material is displaced by the appropriate choice of the tool geometry such that it forms over the groove bottom 6 material projections 15 and thus directly on the groove base 6, a not completely closed cavity 7 is formed (Fig. 3).
  • This cavity 7 extends in the circumferential direction with a nearly constant cross-section.
  • the cavity 7 constitutes an undercut secondary groove according to the invention.
  • the disc 14 may prove expedient to provide the disc 14 on its lateral surface along its circumference with a completely or partially concave profile, so as to favor the displacement of the material of the rib flank 5.
  • This embodiment is an extension of embodiment 1: After the cylindrical disc 14 is in the second embodiment, a gear-like notching disc 16 is engaged, the diameter of which is larger than the diameter of the cylindrical disc 14, but at most as large as the diameter of the largest rolled disc of the rolling tool 11 (Fig. 4).
  • the formed by the cylindrical disc 14, extending in the circumferential direction with constant cross-section cavity is divided by the notch disc 16 by circumferentially regularly arranged indentations 17.
  • circumferential, undercut secondary grooves 7, whose cross-section is varied at regular intervals arise in the circumferential direction (FIG. 5).
  • the notching disc 16 may be straight or obliquely toothed.
  • the thickness D 'of the notching disc 19 is slightly larger than the width B of the primary discs 4 formed by the rolling discs 12, in which case the width B of the primary groove 4 is measured at the point at which the rib edge 5 merges into the radius range of the rib foot 13.
  • the thickness D 'of this notch disc 50% to 80% of the rib pitch T.
  • the notching disc 19 may be straight or obliquely toothed.
  • the notching disc 19 displaces material from the region of the rib flanks 5 and from the radius region at the rib base 13 and leaves there spaced from each other indentations 20.
  • the displaced material is preferably displaced in the unprocessed area between the indentations 20, so that there pronounced dams 21 am Groove base 6 arise, which extend transversely to the primary grooves 4 between the ribs 3.
  • the now following roll plate 22 of constant diameter deforms the upper portions of these dams 21 in the direction of the tube circumference, so that between the deformed upper portions 23 of the dams 21 and the groove bottom 6 small cavities 7 between two adjacent dams 21 are formed (Fig. 7). These cavities 7 represent the undercut secondary grooves according to the invention.
  • the diameter of the roll-over disc 22 must be selected to be smaller than the diameter of the base notch disc 19.
  • the rib tips 8 are notched by means of a gear-type notching disc 24. This is shown in Figures 2/4/6. Subsequently, the upsetting of the notched rib tips by one or more compression rollers 25. The ribs 3 are thus given a substantially T-shaped cross-section, and the grooves 9 between the ribs 3 are closed except for pores 26 (see Figures 3/5/7) ,
  • the fin height H is measured on the finished finned tube 1 from the lowest point of the groove bottom 6 to the fin tip of the fully formed finned tube.
  • the undercut secondary grooves 7 according to the invention at the base 6 of the primary grooves 4 extend from the groove bottom 6 to the rib tip, extending to a maximum of 45% of the rib height H, typically up to 20% of the rib height H.
  • FIG. 8 shows the photograph of an undercut secondary groove 7 according to the invention on the groove bottom 6.
  • the sectional plane is perpendicular to the circumferential direction of the tube.
  • Embodiment 1 an example according to Embodiment 1 is shown.
  • the apparent asymmetry of the structure is due to unavoidable tolerances in tooling and pre-material dimensions.
  • the projections 15 are made of material which has been displaced from the rib flanks 5 to the groove bottom 6.
  • FIG. 9 shows in comparison the performance of two structured tubes on evaporation of the refrigerant R-134a on the outside of the tube, one of the tubes having undercut secondary grooves being made on the groove bottom. Shown is the external heat transfer coefficient over the Schuvinbelastung. The saturation temperature is 14.5 ° C. It can be seen that a performance advantage is achieved by the undercut secondary grooves at the bottom of the groove, which is about 30% for small Bankmatibelastache, with large Bank perennial marlastache about 20%.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
  • Making Paper Articles (AREA)
EP02000425A 2001-01-16 2002-01-08 Wärmeaustauscherrohr und Verfahren zu dessen Herstellung Expired - Lifetime EP1223400B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10101589A DE10101589C1 (de) 2001-01-16 2001-01-16 Wärmeaustauscherrohr und Verfahren zu dessen Herstellung
DE10101589 2001-01-16

Publications (3)

Publication Number Publication Date
EP1223400A2 EP1223400A2 (de) 2002-07-17
EP1223400A3 EP1223400A3 (de) 2005-11-30
EP1223400B1 true EP1223400B1 (de) 2007-03-14

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EP02000425A Expired - Lifetime EP1223400B1 (de) 2001-01-16 2002-01-08 Wärmeaustauscherrohr und Verfahren zu dessen Herstellung

Country Status (8)

Country Link
US (2) US6913073B2 (pt)
EP (1) EP1223400B1 (pt)
JP (1) JP3935348B2 (pt)
CN (1) CN1313794C (pt)
AT (1) ATE356966T1 (pt)
DE (2) DE10101589C1 (pt)
ES (1) ES2283470T3 (pt)
PT (1) PT1223400E (pt)

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DE102008013929B3 (de) * 2008-03-12 2009-04-09 Wieland-Werke Ag Verdampferrohr mit optimierten Hinterschneidungen am Nutengrund
DE102011121733A1 (de) 2011-12-21 2013-06-27 Wieland-Werke Ag Verdampferrohr mit optimierter Außenstruktur
DE102014002829A1 (de) 2014-02-27 2015-08-27 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
DE102016006914A1 (de) 2016-06-01 2017-12-07 Wieland-Werke Ag Wärmeübertragerrohr
DE102018004701A1 (de) 2018-06-12 2019-12-12 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
DE202020005625U1 (de) 2020-10-31 2021-11-10 Wieland-Werke Aktiengesellschaft Metallisches Wärmeaustauscherrohr
DE202020005628U1 (de) 2020-10-31 2021-11-11 Wieland-Werke Aktiengesellschaft Metallisches Wärmeaustauscherrohr
WO2022089773A1 (de) 2020-10-31 2022-05-05 Wieland-Werke Ag Metallisches wärmeaustauscherrohr
WO2022089772A1 (de) 2020-10-31 2022-05-05 Wieland-Werke Ag Metallisches wärmeaustauscherrohr

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* Cited by examiner, † Cited by third party
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DE102008013929B3 (de) * 2008-03-12 2009-04-09 Wieland-Werke Ag Verdampferrohr mit optimierten Hinterschneidungen am Nutengrund
EP2101136A2 (de) 2008-03-12 2009-09-16 Wieland-Werke Ag Verdampferrohr mit opitmierten Hinterschneidungen am Nutengrund
US8281850B2 (en) 2008-03-12 2012-10-09 Wieland-Werke Ag Evaporator tube with optimized undercuts on the groove base
EP2101136A3 (de) * 2008-03-12 2013-08-07 Wieland-Werke AG Verdampferrohr mit opitmierten Hinterschneidungen am Nutengrund
DE102011121733A1 (de) 2011-12-21 2013-06-27 Wieland-Werke Ag Verdampferrohr mit optimierter Außenstruktur
WO2013091759A1 (de) 2011-12-21 2013-06-27 Wieland-Werke Ag VERDAMPFERROHR MIT OPTIMIERTER AUßENSTRUKTUR
US11073343B2 (en) 2014-02-27 2021-07-27 Wieland-Werke Ag Metal heat exchanger tube
DE102014002829A1 (de) 2014-02-27 2015-08-27 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
DE102016006914A1 (de) 2016-06-01 2017-12-07 Wieland-Werke Ag Wärmeübertragerrohr
WO2017207089A1 (de) 2016-06-01 2017-12-07 Wieland-Werke Ag Wärmeübertragerrohr
DE102016006914B4 (de) 2016-06-01 2019-01-24 Wieland-Werke Ag Wärmeübertragerrohr
US10996005B2 (en) 2016-06-01 2021-05-04 Wieland-Werke Ag Heat exchanger tube
DE102018004701A1 (de) 2018-06-12 2019-12-12 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
DE202020005625U1 (de) 2020-10-31 2021-11-10 Wieland-Werke Aktiengesellschaft Metallisches Wärmeaustauscherrohr
DE202020005628U1 (de) 2020-10-31 2021-11-11 Wieland-Werke Aktiengesellschaft Metallisches Wärmeaustauscherrohr
WO2022089773A1 (de) 2020-10-31 2022-05-05 Wieland-Werke Ag Metallisches wärmeaustauscherrohr
WO2022089772A1 (de) 2020-10-31 2022-05-05 Wieland-Werke Ag Metallisches wärmeaustauscherrohr

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CN1313794C (zh) 2007-05-02
US6786072B2 (en) 2004-09-07
CN1366170A (zh) 2002-08-28
US20020092644A1 (en) 2002-07-18
ES2283470T3 (es) 2007-11-01
EP1223400A3 (de) 2005-11-30
US6913073B2 (en) 2005-07-05
ATE356966T1 (de) 2007-04-15
JP3935348B2 (ja) 2007-06-20
EP1223400A2 (de) 2002-07-17
DE50209693D1 (de) 2007-04-26
PT1223400E (pt) 2007-05-31
US20030024121A1 (en) 2003-02-06
DE10101589C1 (de) 2002-08-08
JP2002277188A (ja) 2002-09-25

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