US20030168209A1 - Heat transfer tube with ribbed inner surface - Google Patents

Heat transfer tube with ribbed inner surface Download PDF

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Publication number
US20030168209A1
US20030168209A1 US10/382,378 US38237803A US2003168209A1 US 20030168209 A1 US20030168209 A1 US 20030168209A1 US 38237803 A US38237803 A US 38237803A US 2003168209 A1 US2003168209 A1 US 2003168209A1
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United States
Prior art keywords
ribs
zones
zone
heat transfer
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
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US10/382,378
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English (en)
Inventor
Christoph Walther
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
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Wieland Werke AG
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Assigned to WIELAND-WERKE AG reassignment WIELAND-WERKE AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WALTHER, CHRISTOPH
Publication of US20030168209A1 publication Critical patent/US20030168209A1/en
Abandoned 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
    • F28F1/12—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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • 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
    • 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
    • F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation

Definitions

  • the invention relates to a heat transfer tube having a structured inner surface for evaporation of liquids or condensation of gases, consisting of pure substances or mixtures, on the inside of the tube.
  • climate-control devices are often designed to be able to switch over between summer (cooling) and winter (heating) operation
  • the fin-and-tube heat exchanger and thus the heat transfer tubes of the inside or outside unit of a climate-control system must be operated, depending on the type of operation, sometimes in the evaporation and sometimes in the condensation mode. Accordingly, tubes with good performance characteristics in both modes are often demanded.
  • DE 196 28 280 C2 discloses, in circumferential direction of the tube, an alternating change in rib direction taking place in sections.
  • a helical flow cannot develop here because of the lacking unidirectional orientation of the structure in contrast to the helix-shaped structures.
  • This type of structuring of the inner surface is little suited for evaporation since clearly lower evaporation performances are achieved than in tubes where the surface has a clear predominant direction for flow near the wall.
  • this structure shows during condensation excellent heat transfer performances at, however, also a clearly increased pressure drop, because a complete wetting of the surface is not supported by the structure and thus the film thickness in the upper half of the tube limiting the heat transfer during condensation is kept thin.
  • U.S. Pat. No. 6,229,909 B1 is similar to the DE 196 28 280 C2 in that in the circumferential direction of the tube, an alternating change in rib direction takes place in sections.
  • the rib height was reduced in the transition area between two sections by suitably designing the tool with the disadvantage that the wall thickness increases in this transition area, and the weight of the tube is thus increased without utilizing this additional material neither for improving the heat transfer performance nor for improving the mechanical characteristics.
  • this structure shows very good condensation results, however, compared to the state of the art, clearly inferior evaporation results.
  • EP 1 087 198 A1 and JP-OS 10-047880 are similar to the DE 196 28 280 C2 in that in the circumferential direction of the tube, an alternating change in rib direction takes place in sections.
  • the zones are here designed alternately with different widths so that again a dominating helical-shaped predominant direction of flow can be created, which during evaporation supports the complete wetting of the circumference of the tube and promotes the heat transfer.
  • the helical structure is sufficiently often interrupted so that this structure shows, regarding the condensation performance, similarly good values like the structures according to the DE 196 28 280 C2.
  • Disadvantageous, however, and similar to the DE 196 28 280 C2 is an occurrence of a high pressure drop in the tubes.
  • JP-OS 04-158193 where the inner surface of the tube is divided into sections in circumferential direction of the tube, the rib geometry changes in sections with respect to the helix angle, number of ribs and height of ribs.
  • JP-OS 2000-283680 (Kobe Steel) wherein circumferential direction of the tube a change takes place in sections between zones with ribs extending inclined with respect to the longitudinal axis and zones wherein these ribs are additionally notched.
  • the notching of the ribs requires a second rolling step and an additional tool, and thus increases the production cost.
  • the weight of the tube is not reduced in spite of the forming of the notches since the material is merely displaced into the earlier formed troughs between the ribs.
  • JP-OS 02-280933 (Furukawa) features a lattice-like rib structure on the entire circumference of the tube. Indeed the secondary ribs are located in the troughs between the primary ribs and hinder the creation of a helical flow and thus a complete wetting of the circumference of the tube, which wetting promotes evaporation, since areas with a clear zone not disturbed by secondary ribs does not exist.
  • the purpose of the invention is to provide a heat transfer tube having a structured inner surface which optimizes the following demands: a heat transfer performance which is good or improved compared to the state of the art, during both condensation and evaporation, a low pressure drop, a tube weight which is as low as possible, and a reduced production cost calculated according to the number of structure embossing steps.
  • the purpose is attained inventively in heat transfer tubes by dividing in circumferential direction the inner surface of the tubes into at least two zones (Z 1 , Z 2 , . . . Z n ) extending parallel to the longitudinal axis of the tube, whereby the zones can be differentiated into at least two zone classes (K 1 , K 2 , . . . , K m ), and zones of a different zone class alternate in circumferential direction at any desired sequence, whereby in zones of at least one zone class (K 1 , K 2 , . . .
  • K j there extend ribs with a rib height h 1 and at a helix angle ⁇ 1 with respect to the longitudinal direction of the tube so that, when several zone classes (K 1 , K 2 , . . . , K j ) exist, they differ in at least one of the characteristics of rib height and helix angle, and wherein in zones of at least one further zone class (K j+1 , K j+2 , . . .
  • this helical flow is in each case briefly broken down by the, preferably, however, not necessarily, narrower zones having a lattice-like pattern which assures a creation of turbulence and a destruction of temperature and concentration boundary layers and can thus further increase the heat transfer prior to the flow being again reestablished in the preferred helical direction.
  • , is preferably 30° to 90°.
  • the helical structure exhibiting a predominant direction characteristic is sufficiently often interrupted and a helical flow is disturbed, by the zones of the zone classes (K j+1 , K j+2 , . . . , K m ) having ribs intersecting in a lattice-like pattern so that, in the upper half of the tube, a removal of the condensate occurs which results in a reduction of the film thickness of the condensate.
  • This structure shows therefore a very good condensation performance.
  • the width of the zones of intersecting ribs is preferably chosen to be narrower than the zones with a straight ribbing; in particular, the width of the zones of intersecting ribs should be 3-70% of the width of the zones having straight ribbing.
  • the inventive structure has compared to the state of the art in EP 1 087 198 a reduced pressure drop resulting from the reduction of the height of the ribs in the zones of a lattice-like pattern of the zone classes (K j+1 , K j+2 , . . . , K m ), which zones extend parallel with respect to the longitudinal direction of the tube.
  • the ribs are in comparison to the ribs of the height h 1 designed with a preferably lower rib height h 2 or h 3 .
  • the flow following the helix encounters, in contrast to the state of the art according to EP 1 087 198, merely elevations of a lesser height.
  • the material available through the reduction of the height of the elevations does not cause, as this is the case in U.S. Pat. No. 6,298,909, an unnecessary local reinforcement of the wall thickness and thus in an unnecessary increase in the weight of the tube, but is instead utilized according to the invention for the construction of the lattice-like pattern or the intersecting ribs for the further enhancement of the heat transfer surface and lastly the performance, whereas the wall thickness is uniform in circumferential direction of the tube when measured at the base of the grooves between the ribs of the height h 1 in the zones of the zone classes (K 1 , K 2 , . . .
  • a further advantage of the inventive structure is that this structuring can be achieved in one single rolling step and with one single rolling tool. Compared with notched structures, the production expense calculated according to the number of rolling and operating steps is in this manner reduced. However, an additional notching of the ribs in individual zones of the zone classes (K 1 , K 2 , . . . , K j ) can show further advantages, in particular with regard to a further increase in performance.
  • the inventive heat transfer tube is manufactured based, for example, on the method described in greater detail hereinafter.
  • copper or a copper alloy is used as the material for the heat transfer tube, however, the present invention is not limited in this manner. Rather any type of metal can be used, for example, aluminum.
  • a metallic flat strip is subjected to a one-step embossing step by being guided between an emboss roll having a surface design complementary to the inventive structure and a support roller.
  • One side of the flat strip receives thereby the inventive structure, whereas the second side remains smooth or has also a structuring here not described in detail.
  • the edge areas of the first side which edge areas are used for the subsequent welding, may possibly be structured otherwise or may also remain non-structured.
  • the structured flat strip is formed into an open seam tube, is longitudinally seam welded during a welding process, and the tube is, if necessary, during a subsequent drawing process brought to the desired outside diameter.
  • a possible influence on the heat transfer ability of the inventive heat transfer tube through the area surrounding the welding seam, otherwise structured or also non-structured is insignificant and can be neglected.
  • FIG. 1 illustrates a fin-and-tube heat exchanger according to the state of the art
  • FIG. 2 isometrically illustrates a fragment of an internally ribbed heat transfer tube, in which a welding-seam section extends in a longitudinal direction of the tube;
  • FIG. 3 isometrically illustrates a top view of a flattened inventive heat transfer tube having a ribbed inner surface
  • FIG. 4 isometrically illustrates the definition of the helix angle ⁇
  • FIG. 5 isometrically illustrates a top view of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 3, in which in the zones of even numbers the intersecting ribs form a lattice-like pattern;
  • FIG. 6 isometrically illustrates a top view of a further embodiment of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 3;
  • FIG. 7 isometrically illustrates a top view of a further embodiment of a flattened inventive heat transfer tube having a ribbed inner surface, in which in the zones of uneven numbers the helix angle differs from zone to zone;
  • FIG. 8 isometrically illustrates a top view of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 7, in which the width of the zones differs;
  • FIG. 9 isometrically illustrates a top view of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 5, in which the ribs are notched in the zones of uneven numbers (Z 1 , Z 3 , . . . );
  • FIG. 10 illustrates in an enlarged scale a cross section taken along the line A-A in FIG. 9.
  • FIG. 11 schematically illustrates the design of an embossing roller for the manufacture of the inventive heat transfer tubes.
  • FIG. 1 illustrates a fin-and-tube heat exchanger according to the state of the art with horizontally arranged heat transfer tubes 4 and fins not identified in detail.
  • FIG. 2 illustrates a longitudinal section of a longitudinally seam-welded heat transfer tube 4 having an outside diameter D.
  • the heat transfer tube 4 has a plain outer surface, a structured inner surface and a welding-seam section 7 .
  • the performance of an inventive heat transfer tube 4 is not significantly influenced by the slight interruption of the structure of the inner surface at the welding-seam section 7 and is negligible.
  • the welding-seam section 7 extends parallel to the longitudinal axis of the tube and lies between two zones Z, which will be illustrated in greater detail in the following figures, without noticeably influencing the effect of the zone change.
  • FIG. 3 illustrates schematically a top view of the flattened inner surface of an inventive heat transfer tube 4 .
  • the inner surface is divided in circumferential direction into five zones (Z 1 to Z 5 ) of different width (B 1 to B 5 ), whereby in zones (Z 1 , Z 3 , . . . ) of the zone class K 1 ribs 1 extend at a helix angle ⁇ 1 with respect to the longitudinal direction of the tube.
  • Ribs 2 in the zones (Z 2 , Z 4 , . . . ) of the zone class K 2 extend at a helix angle ⁇ 2 and at the same rib height h 2 , the ribs 2 being intersected by ribs 3 of the same height.
  • the associated zones have within one zone class K the same structuring with respect to the rib pattern, the rib height and the helix angle.
  • the respective helix angle ⁇ 2 and ⁇ 3 differ from one another at the intersecting ribs 2 and 3 in the zones of the zone class K 2 .
  • Also illustrated is the core-wall thickness t.
  • the widths of the zones of one zone class are in each case the same, whereas the zones (Z 1 , Z 3 , Z 5 ) of the zone class K 1 are designed wider than the zones (Z 2 , Z 4 ) of the zone class K 2 .
  • FIG. 4 schematically illustrates the definition of the helix angles ⁇ .
  • the longitudinal direction of the tube is thereby identified as the zero degree point (0°)
  • the ribs 1 a which extend away from the 0° line to the right in longitudinal direction of the tube, are described as a positive angle ( ⁇ >0)
  • ribs 1 b which extend away from the 0° line to the left in longitudinal direction of the tube, are described as a negative angle ( ⁇ 0).
  • FIG. 5 schematically illustrates the top view of a flattened, inventive heat transfer tube having a ribbed inner surface analogous to FIG. 3, in which in the zones of the zone class K 2 the intersecting ribs 2 and 3 form an intersection angle, calculated as the amount of the smaller one of the two complementary angles
  • the intersecting ribs 2 and 3 completely enclose thereby a cavity 5 in the zones of the zone class K 2 by forming a closed diamond-shaped rib pattern 6 . A lattice-like pattern is thus created.
  • the ribs 2 and 3 in the zones of the zone class K 2 are thereby designed to have a rib height of h 2 or h 3 smaller than the height h 1 of the ribs 1 in the zones of the zone class K 1 .
  • the ribs 3 extend at an angle ⁇ 3 with respect to the longitudinal direction of the tube.
  • the core-wall thickness t of the heat transfer tube 4 measured at the base of the groove 9 between the ribs 1 in the zones (Z 1 , Z 3 , . . . ) of the zone class K 1 or in the cavities 5 between the ribs 2 , 3 in the zones (Z 2 , Z 4 , . . . ) of the zone class K 2 outside of a welding-seam section 7 , is uniform in circumferential direction of the tube.
  • FIG. 6 schematically illustrates a top view of a further embodiment of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 3, in which in the zones, (Z 2 , Z 4 , . . . ) of the zone class K 2 the intersecting ribs 2 and 3 form an intersection angle, calculated as the amount of the smaller one of the two complementary angles
  • FIG. 7 illustrates schematically a top view of a further embodiment of a flattened inventive heat transfer tube having a ribbed inner surface, in which the zones Z 1 to Z 5 are divided into three zone classes K 1 to K 3 .
  • the helix angle of the ribs 1 is ⁇ 1 in the zones (Z 1 , Z 5 ) of the zone class K 1 , whereas the helix angle is ⁇ 1 * in the zone Z 3 of the zone class K 2 .
  • the helix angle of the ribs 1 with respect to the longitudinal direction of the tube is, in the illustrated embodiment, alternately changed in the zones of uneven number (Z 1 , Z 3 , Z 5 ) from zone to zone between ⁇ 1 and ⁇ 1 *.
  • the intersecting ribs 2 and 3 form in the zones (Z 2 , Z 4 ) of the zone class K 3 a lattice-like pattern by completely enclosing several cavities 5 each in a closed diamond-shaped rib pattern 6 .
  • FIG. 8 illustrates schematically a top view of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 7, in which the width of the zones of the zone class K 3 (B 2 , B 4 ) is only approximately 50% of the width of the zones of the zone classes K 1 and K 2 (B 1 , B 3 , B 5 ).
  • FIG. 9 schematically illustrates a top view of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 5, in which the ribs have notches 8 in individual zones. That is, the ribs 1 of the zone Z 3 of the zone class K 2 have notches 8 in the illustrated embodiment, which notches lie in alignment one behind the other on lines which extend at a helix angle ⁇ 4 with respect to the longitudinal direction of the tube.
  • the depth k of the notches 8 according to the illustration in FIG. 10 is at least 20% of the rib height h 1 of the ribs 1 .
  • FIG. 11 schematically illustrates the design of an embossing roller 11 for the manufacture of the inventive heat transfer tube 4 .
  • the roller 11 is composed of several circular discs 12 . Grooves 13 , 14 , 15 are recessed into the peripheral surface of the individual discs 12 , which grooves produce, when the roller 11 rolls on the sheet metal strip 10 supported by a smooth surface support roller 16 , the ribs 1 , 2 , 3 in the individual zones Z 1 to Z 5 during one rolling operation.
  • the sheet metal strip 10 is formed into an open seam tube and is welded along a longitudinal seam so that a welding-seam section 7 results.
  • One embodiment of a flattened inventive heat transfer tube having a ribbed inner surface analogous to FIG. 5 is featured by an outer diameter of the tube being 9.52 mm and an inner surface which is divided in the circumferential direction of the tube into seven zones of different width.
  • the width of the zones is alternately specified by a circumferential angle of 72° (4 wide zones) or 24° (3 narrow zones).
  • ⁇ 1 helix angle
  • ⁇ 2 ⁇ 1
  • the ribs 2 are intersected by ribs 3 in the zones of even numbers, which ribs 3 extend at an opposite helix angle ⁇ 3 of ⁇ 20° with respect to the longitudinal direction of the tube, so that the intersection angle between the ribs 2 and 3 is 40°.
  • the rib height h 3 is 0.15 mm.
  • the density of the ribs 3 in the zones of even numbers (Z 2 , Z 4 , . . . ), measured as number of ribs per unit of length in direction of the ribs 2 is 1.45 per millimeter.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
US10/382,378 2002-03-07 2003-03-06 Heat transfer tube with ribbed inner surface Abandoned US20030168209A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10210016A DE10210016B9 (de) 2002-03-07 2002-03-07 Wärmeaustauschrohr mit berippter Innenoberfläche
DE10210016.0 2002-03-07

Publications (1)

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US20030168209A1 true US20030168209A1 (en) 2003-09-11

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US10/382,378 Abandoned US20030168209A1 (en) 2002-03-07 2003-03-06 Heat transfer tube with ribbed inner surface

Country Status (5)

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US (1) US20030168209A1 (de)
EP (1) EP1342971A3 (de)
JP (1) JP2003262486A (de)
CN (1) CN1444003A (de)
DE (1) DE10210016B9 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070001325A1 (en) * 2005-06-17 2007-01-04 Basf Aktiengesellschaft Method and apparatus for vaporizing thermally sensitive substances
US20150219405A1 (en) * 2014-02-05 2015-08-06 Lennox Industries Inc. Cladded brazed alloy tube for system components
US20160363395A1 (en) * 2014-02-27 2016-12-15 Kaboshiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Plate for use as heat exchange plate and method for manufacturing such base plate

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1930679B1 (de) 2006-12-01 2009-07-15 Basf Se Verfahren und Vorrichtung zur Kühlung von Reaktoren mit siedenden Flüssigkeiten
DE102008030423B4 (de) 2007-12-05 2016-03-03 GIB - Gesellschaft für Innovation im Bauwesen mbH Rohr mit einer durch Noppen Oberflächenprofil-modifizierten Außenmantelfläche
DE102009040558A1 (de) * 2009-09-08 2011-03-10 Krones Ag Röhrenwärmetauscher
JP7151253B2 (ja) * 2018-08-01 2022-10-12 株式会社デンソー 伝熱管および熱交換器

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US6298909B1 (en) * 2000-03-01 2001-10-09 Mitsubishi Shindoh Co. Ltd. Heat exchange tube having a grooved inner surface
US6336501B1 (en) * 1998-12-25 2002-01-08 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Tube having grooved inner surface and its production method
US6631758B2 (en) * 2000-08-25 2003-10-14 Wieland-Werke Ag Internally finned heat transfer tube with staggered fins of varying height
US6883597B2 (en) * 2001-04-17 2005-04-26 Wolverine Tube, Inc. Heat transfer tube with grooved inner surface

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JPH02280933A (ja) * 1989-04-18 1990-11-16 Furukawa Electric Co Ltd:The 伝熱管とその製造方法
JP3014432B2 (ja) * 1990-10-23 2000-02-28 古河電気工業株式会社 伝熱管の製造方法
JP2730824B2 (ja) * 1991-07-09 1998-03-25 三菱伸銅株式会社 内面溝付伝熱管およびその製造方法
MX9305803A (es) * 1992-10-02 1994-06-30 Carrier Corp Tubo de transferencia de calor con nervaduras internas.
CN1084876C (zh) * 1994-08-08 2002-05-15 运载器有限公司 传热管
US5791405A (en) * 1995-07-14 1998-08-11 Mitsubishi Shindoh Co., Ltd. Heat transfer tube having grooved inner surface
JP3286171B2 (ja) * 1996-08-06 2002-05-27 株式会社神戸製鋼所 内面溝付き伝熱管
JP2000283680A (ja) * 1998-12-25 2000-10-13 Kobe Steel Ltd 内面溝付管及びその製造方法
JP3296325B2 (ja) * 1999-04-08 2002-06-24 ダイキン工業株式会社 内面溝付伝熱管
JP2000310495A (ja) * 1999-04-26 2000-11-07 Mitsubishi Shindoh Co Ltd 内面溝付伝熱管

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
US6336501B1 (en) * 1998-12-25 2002-01-08 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Tube having grooved inner surface and its production method
US6298909B1 (en) * 2000-03-01 2001-10-09 Mitsubishi Shindoh Co. Ltd. Heat exchange tube having a grooved inner surface
US6631758B2 (en) * 2000-08-25 2003-10-14 Wieland-Werke Ag Internally finned heat transfer tube with staggered fins of varying height
US6883597B2 (en) * 2001-04-17 2005-04-26 Wolverine Tube, Inc. Heat transfer tube with grooved inner surface

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070001325A1 (en) * 2005-06-17 2007-01-04 Basf Aktiengesellschaft Method and apparatus for vaporizing thermally sensitive substances
US20150219405A1 (en) * 2014-02-05 2015-08-06 Lennox Industries Inc. Cladded brazed alloy tube for system components
US20160363395A1 (en) * 2014-02-27 2016-12-15 Kaboshiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Plate for use as heat exchange plate and method for manufacturing such base plate

Also Published As

Publication number Publication date
DE10210016B4 (de) 2004-01-08
EP1342971A2 (de) 2003-09-10
DE10210016B9 (de) 2004-09-09
EP1342971A3 (de) 2003-10-08
JP2003262486A (ja) 2003-09-19
CN1444003A (zh) 2003-09-24
DE10210016A1 (de) 2003-09-25

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Owner name: WIELAND-WERKE AG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WALTHER, CHRISTOPH;REEL/FRAME:013860/0737

Effective date: 20030205

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION