EP0607839B1 - Wärmeaustauschrohr sowie Herstellungsverfahren und Verwendung desselben - Google Patents

Wärmeaustauschrohr sowie Herstellungsverfahren und Verwendung desselben Download PDF

Info

Publication number
EP0607839B1
EP0607839B1 EP94100288A EP94100288A EP0607839B1 EP 0607839 B1 EP0607839 B1 EP 0607839B1 EP 94100288 A EP94100288 A EP 94100288A EP 94100288 A EP94100288 A EP 94100288A EP 0607839 B1 EP0607839 B1 EP 0607839B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
tube
exchanger tube
distribution troughs
channels
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
EP94100288A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0607839A1 (de
Inventor
Klaus Dipl.-Ing. Menze
Gerhard Dr.-Ing. Schüz
Axel Dipl.-Ing. Kriegsmann (Fh)
Manfred Dipl.-Ing. Knab
Manfred Dr.-Ing. Hage
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 EP0607839A1 publication Critical patent/EP0607839A1/de
Application granted granted Critical
Publication of EP0607839B1 publication Critical patent/EP0607839B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites

Definitions

  • the invention relates to a heat exchange tube according to the preamble of claim 1.
  • a tube is known, for example, from EP-A-0 495 453.
  • the invention also relates to a method for producing and using such a tube.
  • the heat exchange tube is, for example, a heat exchange tube for spray evaporation in a tube bundle heat exchanger (see FIG. 1).
  • spray evaporators the medium to be evaporated is applied or sprayed onto the pipes in the jacket space.
  • the advantage is that the free volume between the tubes does not have to be filled with liquid. In this way, the filling quantity of such apparatus can be minimized.
  • the type of spraying must ensure that the pipes are always adequately covered with liquid.
  • Tubes are known from the area of absorption heat pumps, which have V-shaped grooves on the outer side to improve the distribution of the liquid in the axial direction of the tube. Such tubes have been developed for use in expellers (brochure "F-tube” from Furukawa Electric Co., Ltd.).
  • the invention has for its object to design a heat exchange tube of the type mentioned so that in addition to good distribution of the liquid on the surface, good evaporation properties are guaranteed at the same time.
  • the distribution channels run parallel to one another, in particular two groups of parallel distribution channels intersect at an angle ⁇ .
  • the distribution channels are spaced apart from one another — preferably the spacing is a 3 3 ⁇ t — or adjoin one another directly.
  • the distribution channels have the task of distributing liquid that is dripped or sprayed on the outer surface and supplying it to the channels underneath.
  • the distribution channels can have corresponding openings in addition to the overflows.
  • the shape of the openings can vary. So the openings can be hole-like, i.e. the flanks of the channels are pierced, while the ridges and the bottom of the channels pass through. On the other hand, the openings can be slit-like, i.e. the ridges run through and the bottom of the channel is broken, or conversely the ridges are broken and the bottom of the channel is continuous.
  • the simultaneous arrangement of different types of openings on a heat exchange tube can be advantageous.
  • the driving forces for the liquid distribution are the inertial forces, the capillary forces and (in the case of inclined or vertically oriented surfaces) gravity.
  • the crossed version the liquid is redistributed at each crossing point, so that the distribution effect is considerably better than with the parallel channels.
  • the channels and distribution channels run helically, in particular the distribution channels run at an angle of inclination ⁇ to the pipe longitudinal axis, 0 ° ⁇ ⁇ 60 ° and 120 ° ⁇ ⁇ ⁇ 180 °.
  • the inner surface of the heat exchange tube is structured or finned.
  • helical circumferential channels are first produced in that the material of the channel walls is obtained by displacing material out of the tube wall of a smooth tube to the outside by means of a rolling process (cf. the usual rolling method for producing finned tubes, for example according to US Pat. No. 3,327,512) , and then the distribution channels are produced by pressing in the channel walls by means of a rolling process with appropriately shaped toothed disks, pressure rollers or the like (cf. for example DE-OS 1.501.656).
  • a rolling process cf. the usual rolling method for producing finned tubes, for example according to US Pat. No. 3,327,512
  • the distribution channels are produced by pressing in the channel walls by means of a rolling process with appropriately shaped toothed disks, pressure rollers or the like (cf. for example DE-OS 1.501.656).
  • first helically circumferential channels in the tube wall of a smooth tube are produced by a drawing process with a stationary or rotating drawing die, and then the distribution channels are produced by pressing the channel walls in with a rolling process with appropriately shaped toothed disks, spinning rollers or the like.
  • spiral channels are first produced in that the material of the channel walls is obtained by displacing material from the tube wall of a smooth tube to the outside by means of a rolling process and the distribution channels are then produced by a drawing process with a stationary or rotating drawing die.
  • helical circumferential channels are first produced in the tube wall of a smooth tube by a drawing process with a stationary or rotating drawing die, and then the distribution channels are produced by a drawing process with a stationary or rotating drawing die.
  • the heat exchange tube according to the invention is preferably used for spray evaporation in a tube-bundle heat exchanger with horizontally or inclined heat exchange tubes.
  • a metallic heat exchange tube 1 according to FIGS. 2 to 4 has a first medium 2 on one side and a second medium 3 to be evaporated on the other side.
  • the tube 1 On this other side, the tube 1 has channels 4 (with channel walls 5) which are parallel to one another and whose dimensions of pitch t, height h and wall thickness s are also entered.
  • the channels 4 are crossed by distribution channels 6 for the second medium 3, which are formed by laterally displaced material of the channel walls 5.
  • the channels 6 are essentially V-shaped.
  • the depth of the channels 6 calculated from the upper edge of the channel walls 5 is denoted by T, the opening angle of which is denoted by ⁇ (here the V-shaped channels 6 are drawn with a tapering channel bottom. Normally, however, the channel bottom will be widened).
  • the channels 6 are provided with overflows 7 and / or openings 8.
  • the overflows 7 and / or openings 8 are designed differently (cf. in particular FIG. 6).
  • slot-like openings 8 have formed.
  • the channels 6 are spaced from one another, so that when the second medium 3 evaporates, the steam (see arrow “steam”) can escape through the remaining intermediate spaces 9.
  • the distance a is calculated between the bottom of adjacent channels 6.
  • the openings 8 serve at the same time for the liquid to enter and to exit the steam (see arrows "liquid” and "steam").
  • FIG. 5 shows the surface condition of a heat exchange tube 1 according to the invention with intersecting distribution channels 6 (intersection angle ⁇ / intersection points K). To simplify the illustration of overflows 7 and openings 8 has been omitted. The remaining gaps 9 for the steam outlet are highlighted.
  • FIG. 6 shows various possibilities for the formation of the overflows 7 and openings 8 (cf. view according to section plane A - A through the channel bottom according to FIG. 2).
  • the openings 8 are hole-like, i.e. the flanks 10 of the channels 6 are pierced, whereby combs 11 and channel bottom 12 each pass through.
  • the combs 11 run through, but the channel bottom 12 is broken through, in the case of FIG. 6c the reverse is the case.
  • FIG. 7 schematically shows a heat exchange tube 1 with channels 4 (or channel walls 5) and distribution channels 6 that run helically on the outer surface and distribution channels 6.
  • the angle of inclination of the distribution channels 6 to the pipe longitudinal axis is designated by ⁇ .
  • the distance a between the channel base 12 of adjacent channels 6 is also entered.
  • the channels 6 have been drawn in a simplified manner without overflows 7 or openings 8.
  • steel, aluminum and aluminum alloys, copper and copper alloys, stainless steels and titanium come into consideration as materials for the heat exchange tube 1.
  • ammonia and safety refrigerants such as R22, R134a etc., are available as the medium 3 to be evaporated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP94100288A 1993-01-22 1994-01-11 Wärmeaustauschrohr sowie Herstellungsverfahren und Verwendung desselben Expired - Lifetime EP0607839B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4301668A DE4301668C1 (de) 1993-01-22 1993-01-22 Wärmeaustauschwand, insbesondere für Sprühverdampfung
DE4301668 1993-01-22

Publications (2)

Publication Number Publication Date
EP0607839A1 EP0607839A1 (de) 1994-07-27
EP0607839B1 true EP0607839B1 (de) 1996-09-11

Family

ID=6478714

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94100288A Expired - Lifetime EP0607839B1 (de) 1993-01-22 1994-01-11 Wärmeaustauschrohr sowie Herstellungsverfahren und Verwendung desselben

Country Status (4)

Country Link
US (1) US5513699A (hu)
EP (1) EP0607839B1 (hu)
DE (2) DE4301668C1 (hu)
DK (1) DK0607839T3 (hu)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5458191A (en) * 1994-07-11 1995-10-17 Carrier Corporation Heat transfer tube
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
TW327205B (en) * 1995-06-19 1998-02-21 Hitachi Ltd Heat exchanger
US6176302B1 (en) * 1998-03-04 2001-01-23 Kabushiki Kaisha Kobe Seiko Sho Boiling heat transfer tube
US6182743B1 (en) 1998-11-02 2001-02-06 Outokumpu Cooper Franklin Inc. Polyhedral array heat transfer tube
US6176301B1 (en) 1998-12-04 2001-01-23 Outokumpu Copper Franklin, Inc. Heat transfer tube with crack-like cavities to enhance performance thereof
MX2007015046A (es) * 2005-06-07 2008-01-18 Wolverine Tube Inc Superficie de trasferencia de calor para el enfriamiento de componentes electronicos.
DE102005028032A1 (de) * 2005-06-17 2006-12-21 Basf Ag Verfahren und Vorrichtung zur Verdampfung thermisch empfindlicher Stoffe
DE102006008083B4 (de) 2006-02-22 2012-04-26 Wieland-Werke Ag Strukturiertes Wärmeaustauscherrohr und Verfahren zu dessen Herstellung
EP1930679B1 (de) 2006-12-01 2009-07-15 Basf Se Verfahren und Vorrichtung zur Kühlung von Reaktoren mit siedenden Flüssigkeiten
CN100498187C (zh) * 2007-01-15 2009-06-10 高克联管件(上海)有限公司 一种蒸发冷凝兼备型传热管
CN101338987B (zh) * 2007-07-06 2011-05-04 高克联管件(上海)有限公司 一种冷凝用传热管
US9844807B2 (en) * 2008-04-16 2017-12-19 Wieland-Werke Ag Tube with fins having wings
DE102009007446B4 (de) * 2009-02-04 2012-03-29 Wieland-Werke Ag Wärmeübertragerrohr und Verfahren zu dessen Herstellung
US8490679B2 (en) * 2009-06-25 2013-07-23 International Business Machines Corporation Condenser fin structures facilitating vapor condensation cooling of coolant
EP2619420A2 (en) * 2010-09-20 2013-07-31 State of Oregon acting by and through the State Board of Higher Education on behalf of Oregon State University A system and method for storing energy and purifying fluid
DE102011121436A1 (de) * 2011-12-16 2013-06-20 Wieland-Werke Ag Verflüssigerrohre mit zusätzlicher Flankenstruktur
DE102014002829A1 (de) * 2014-02-27 2015-08-27 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
CN111854502A (zh) * 2020-07-08 2020-10-30 珠海格力电器股份有限公司 换热管及空调机组

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE669560A (hu) * 1964-12-28
US3326283A (en) * 1965-03-29 1967-06-20 Trane Co Heat transfer surface
US3566514A (en) * 1968-05-01 1971-03-02 Union Carbide Corp Manufacturing method for boiling surfaces
US3906605A (en) * 1973-06-18 1975-09-23 Olin Corp Process for preparing heat exchanger tube
JPS6033240B2 (ja) * 1981-07-24 1985-08-01 三井アルミニウム工業株式会社 熱交換用管状体の製造法
JPS5946490A (ja) * 1982-09-08 1984-03-15 Kobe Steel Ltd 沸騰型熱交換器用伝熱管
JPS6064194A (ja) * 1983-09-19 1985-04-12 Sumitomo Light Metal Ind Ltd 伝熱管
JPH0612222B2 (ja) * 1985-08-12 1994-02-16 三菱重工業株式会社 内壁に交差溝を有する伝熱管
US4733698A (en) * 1985-09-13 1988-03-29 Kabushiki Kaisha Kobe Seiko Sho Heat transfer pipe
JPS62237295A (ja) * 1986-04-04 1987-10-17 Kobe Steel Ltd 異形伝熱管及びその製造方法
JPH0244165A (ja) * 1988-08-04 1990-02-14 Yazaki Corp 流下液膜式蒸発器用伝熱管
JP2788793B2 (ja) * 1991-01-14 1998-08-20 古河電気工業株式会社 伝熱管
US5203404A (en) * 1992-03-02 1993-04-20 Carrier Corporation Heat exchanger tube
US5332034A (en) * 1992-12-16 1994-07-26 Carrier Corporation Heat exchanger tube

Also Published As

Publication number Publication date
DK0607839T3 (hu) 1997-03-17
EP0607839A1 (de) 1994-07-27
DE4301668C1 (de) 1994-08-25
US5513699A (en) 1996-05-07
DE59400607D1 (de) 1996-10-17

Similar Documents

Publication Publication Date Title
EP0607839B1 (de) Wärmeaustauschrohr sowie Herstellungsverfahren und Verwendung desselben
DE3332282C2 (de) Wärmetauschrohr
DE3780648T2 (de) Kondensator.
DE4404357C1 (de) Wärmeaustauschrohr zum Kondensieren von Dampf
DE2546444C3 (de) Wärmeaustauscherwand und Verfahren zu ihrer Herstellung
DE4420756C1 (de) Mehrgängiges Rippenrohr und Verfahren zu dessen Herstellung
DE19728247C2 (de) Flache Röhre für einen Wärmetauscher
EP2859295B1 (de) Wärmeübertrager
DE10025362A1 (de) Wärmetauscher mit strukturiertem Mehrloch-Röhrchen
EP0394718B1 (de) Rieseleinbauelement
EP1182416B1 (de) Innenberipptes Wärmeaustauschrohr mit versetzt angeordneten Rippen unterschiedlicher Höhe
DE2657307A1 (de) Rohrbuendel fuer einen waermetauscher
DE3606253C2 (hu)
DE2222269C2 (de) Rieselkolonne zum Rektifizieren von Flüssigkeiten
DE112015000146B4 (de) Verdampfer
DE69729836T2 (de) Verdampfer
DE10054158A1 (de) Mehrkammerrohr mit kreisförmigen Strömungskanälen
WO2017167458A1 (de) Gewickelter wärmeübertrager
DE2613747B2 (de) Röhrenwärmetauscher
DE19716836A1 (de) Plattenwärmetauscher, insbesondere Verdampfer für Klimatisierungskreislauf
DD147912A5 (de) Fluessigkeitsverteiler fuer waermeaustauscher mit vertikalen rohren
DE10210016B9 (de) Wärmeaustauschrohr mit berippter Innenoberfläche
DE60006321T2 (de) Verdampferkondensor mit hartgelöteten Platten und deren Verwendung in einer Luftdestillationsvorrichtung
DE3634871A1 (de) Doppelspiralwaermeaustauscher
DE1451156A1 (de) Waerme- und Stoffaustauschelement

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19940111

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE DK FR GB

17Q First examination report despatched

Effective date: 19950724

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE DK FR GB

REF Corresponds to:

Ref document number: 59400607

Country of ref document: DE

Date of ref document: 19961017

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19961025

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 19970130

Year of fee payment: 4

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980202

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20120202

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20120131

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20120111

Year of fee payment: 19

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20130111

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20130930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130801

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59400607

Country of ref document: DE

Effective date: 20130801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130111

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130131