EP0201665A1 - Elément de transfert de chaleur comportant des tubes parallèles à ailettes - Google Patents

Elément de transfert de chaleur comportant des tubes parallèles à ailettes Download PDF

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Publication number
EP0201665A1
EP0201665A1 EP86101327A EP86101327A EP0201665A1 EP 0201665 A1 EP0201665 A1 EP 0201665A1 EP 86101327 A EP86101327 A EP 86101327A EP 86101327 A EP86101327 A EP 86101327A EP 0201665 A1 EP0201665 A1 EP 0201665A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
tubes
ribs
exchanger according
corrugations
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.)
Granted
Application number
EP86101327A
Other languages
German (de)
English (en)
Other versions
EP0201665B1 (fr
Inventor
Roland Diethelm
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.)
Sulzer AG
Original Assignee
Sulzer AG
Gebrueder Sulzer 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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0201665A1 publication Critical patent/EP0201665A1/fr
Application granted granted Critical
Publication of EP0201665B1 publication Critical patent/EP0201665B1/fr
Expired 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
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/454—Heat exchange having side-by-side conduits structure or conduit section
    • Y10S165/50—Side-by-side conduits with fins
    • Y10S165/501—Plate fins penetrated by plural conduits
    • Y10S165/504—Contoured fin surface
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/903—Convection

Definitions

  • the invention relates to a heat exchanger with a plurality of mutually parallel tubes which carry a first medium, which are arranged in a plurality of mutually parallel rows and are provided with corrugated sheet metal fins which are distributed over their length and extend transversely to the tube axis and are connected to the tubes in a heat-conducting manner , with a second medium flowing in the spaces remaining between the ribs.
  • Such a heat exchanger is known from DE-OS 23 05 056, in which the sheet metal fins are corrugated throughout and are also provided with holes.
  • the holes are said to improve the heat transfer from the fins to the second medium by swirling it and partially flowing from one side of a sheet metal fin to the other side.
  • the improvement in heat transfer is bought with relatively high pressure losses.
  • the production of the known heat exchanger is made considerably more difficult because of the corrugations also present in the penetration area of the pipes, since the corrugations in the area mentioned can only be formed by means of complicated shaping tools and in several work steps. The manufacturing costs for the molds are also considerable.
  • each rib is only outside an area which surrounds the associated tube and extends against the adjacent tube of the same row of tubes, and in that the corrugations are free of perforations. Because the pipe penetration area of the fins is free from corrugations, the production of the fins is significantly easier and cheaper than the continuously corrugated sheet metal fins of the known heat exchanger, which also contributes to the fact that the molding tool is less expensive. The fact that the corrugations in the ribs are free of perforations results in significantly lower pressure losses for the second medium.
  • this feature leads to clear, manageable flow patterns of the second medium, which enable a theoretical recording of the physical processes in the heat exchanger according to the invention, so that its thermodynamic behavior - in contrast to the known heat exchanger - is relatively easy to calculate.
  • Another advantage is that because of the lack of holes in the corrugations improve the strength properties of the new heat exchanger. It has moreover been shown that the lack of holes in the heat exchanger has a heat transfer coefficient which far exceeds that of the known heat exchanger, which is due to the fact that the heat conduction in the sheet metal fins is not disturbed by holes. This prevents local heat build-up and the resulting thermal stress.
  • the shape of the ribs according to claim 5 leads to particularly low pressure losses, since the offset of the area of the ribs penetrated by the tubes is prevented from flowing through the second medium.
  • Claim 6 characterizes a production-friendly way of designing ribs in the area of the pipe penetrations.
  • the arrangement of aerodynamic bodies according to claim 8 further improves the flow conditions and is of considerable importance if the second medium is deflected upstream and / or downstream of the heat exchanger.
  • the heat exchanger according to FIGS. 1 and 2 has many straight tubes 2, which are arranged one above the other in several parallel rows and carry a first medium, for example hot water.
  • the tubes 2 are connected to one another via many fins 3, and a second medium, for example cooling air (arrows L), flows through the heat exchanger thus formed in the direction of the rows of tubes.
  • the ribs 3 are made of sheet metal and are closed arranged parallel to each other distributed over the length of the tubes 2.
  • each rib 3 has an undulated section 3 'and two corrugated sections 3 "adjoining it on the outside.
  • the section 3' lies in the penetration area of the tubes 2 and, with the corrugated sections 3", has an offset 6 each connected.
  • a necked collar 7 is provided for each tube 2, which in the assembled state of the heat exchanger encloses one tube and via which the rib is connected to the tube in a heat-conducting manner, e.g. by welding.
  • each rib 3 are shaped such that waves with a constant wavelength w adjoin one another in the direction of flow of the second medium.
  • the wave crests 5 of the waves form a straight line which starts in FIG. 2 from the upper edge of the crank 6.
  • the wave troughs 5 'of the waves lying between the wave crests 5 also originate from the upper edge of the cranks 6 and, after an arcuate transition, run essentially parallel to the wave crests 5.
  • In the foreground of FIG 2 shows approximately half of the corrugated sections 3 ′′. The other half, not shown, is symmetrical and ends at the upper edge of the corresponding offset of the adjacent row of pipes.
  • All ribs 3 are the same among themselves and are placed on the pipes for the purpose of mounting the heat exchanger and pushed together so far that the crankings 6 touch one another. Since the height of the cranks is the same in each case, there are between two adjacent ribs 3 in their corrugated ab cut spaces 4 and between the non-corrugated flat sections 3 'spaces 4'. The distance between the corrugations of two adjacent rib sections 3 "is therefore constant.
  • the ribs 3 with the shafts, the crankings 6 and the collar 7 are produced in a single operation from flat sheet metal strips by means of an appropriate molding tool.
  • the cooling air flows in the spaces 4 and 4 1 , and the hot water to be cooled flows in the pipes 2 transversely thereto.
  • the heat is distributed over the walls of the pipes 2 into the fins 3, in which they accumulate without accumulation spreads out in a straight line.
  • the spaces 4 between the corrugated sheet metal sections 3 ′′ there is practically no swirling of the cooling air due to the lack of breakthroughs, so that in this air pressure losses essentially only occur due to friction; these losses are therefore very small.
  • the repeated changes in direction of the air flowing through occur the waves of the sections 3 "lead to small pressure fluctuations, which constantly result in the dismantling of the boundary layer which is formed, which ensures good heat transfer in the corrugated spaces.
  • the spaces 4 'penetrated by the tubes between the flat rib sections 3' are relatively small and, overall, cause only a slight pressure loss.
  • the cranks 6 effectively separate these spaces 4 'from the corrugated spaces 4.
  • the hot water to be cooled is opened in a straight, rectangular cross section pointing pipes 12 which touch each other within a row.
  • the shape of the tubes 12 is also advantageous in that the distance between their long sides and the respectively adjacent corrugated fin section 3 "is smaller 1 and 2, so that there are better heat transfer conditions.
  • a hyperbolic cooling tower 15 has a vertical, ring-shaped air inlet in its lower region, while the air outlet in its upper region is horizontal and circular.
  • Thirty-two heat exchangers 1 according to FIGS. 1 and 2 are delta-shaped around the air inlet of the cooling tower. Hot water to be cooled flows in the tubes 2 of these heat exchangers, e.g. from a power plant, so that the cooling air entering the cooling tower is heated.
  • each heat exchanger 1 has an inflow body 8 and an outflow body 9 in the region of the intermediate spaces 4 '. These bodies 8 and 9, which improve the flow profile of the cooling air (arrows 16), are arranged with their boundary surfaces in alignment with the cranks 6.
  • the heat exchanger has vertical, straight pipes 22 which carry a first medium and are arranged in rows, only one of which is shown here represents is.
  • the tubes 22 are provided with horizontal, likewise parallel ribs 23 made of sheet metal. These ribs define gaps 24 through which a second medium flows at right angles to the plane of the drawing. They have corrugated sections 23 "and flat sections 23 'on both sides of them, which merge directly into one another without cranking.
  • the wave crests 25 of sections 23" lie in the same plane as the flat sections 23.
  • Collars 27 in sections 23' each comprise a tube 22 and at the same time determine the distance between adjacent ribs 23.
  • the spaces between the flat sections 23 'and part of the spaces 24 directly adjoining them, namely the transition area from the flat to the corrugated sections, are filled with packing elements 26.
  • These fillers - viewed perpendicular to the plane of the drawing - extend along the entire depth of the heat exchanger. They can consist of different materials, eg rubber, plastic, epoxy or cast aluminum, and can be made in one or more parts for each row of pipes.
  • the distance between the ribs can be varied, for example, with the height of the individual ribs, and the wavelength w need not necessarily be constant.
  • the type of transition from flat to undulating region may be structured differently by the corrugated sections are for example welded to the cranks or glued.
  • the cranks do not have to be flat or vertical.
  • the pipes can also run horizontally or inclined and do not have to be straight.
  • the ribs do not necessarily have to be flat in the pipe penetration area, and the longitudinal axis of the pipes can also be arranged inclined to the sheet metal ribs.
  • a cross-section other than a rectangular matrix can be provided transversely to the longitudinal axis of the tubes.
  • the tubes can have other cross-sectional shapes, for example oval or the cross-section is variable along the longitudinal axis of the tube. Because of special strength and / or thermal requirements, it may be possible to use pipes and / or fins with different wall thicknesses within the same heat exchanger. If necessary, the collars 7, 27 can be tightly connected to one another, for example by soldering, so that they form the tubes themselves.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP86101327A 1985-05-15 1986-02-01 Elément de transfert de chaleur comportant des tubes parallèles à ailettes Expired EP0201665B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2076/85 1985-05-15
CH2076/85A CH666538A5 (de) 1985-05-15 1985-05-15 Waermeuebertrager mit mehreren parallelen rohren und auf diesen angebrachten rippen.

Publications (2)

Publication Number Publication Date
EP0201665A1 true EP0201665A1 (fr) 1986-11-20
EP0201665B1 EP0201665B1 (fr) 1989-05-24

Family

ID=4225343

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86101327A Expired EP0201665B1 (fr) 1985-05-15 1986-02-01 Elément de transfert de chaleur comportant des tubes parallèles à ailettes

Country Status (6)

Country Link
US (1) US4789027A (fr)
EP (1) EP0201665B1 (fr)
JP (1) JPS61265498A (fr)
CH (1) CH666538A5 (fr)
DE (1) DE3663589D1 (fr)
HU (1) HU195316B (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4789027A (en) * 1985-05-15 1988-12-06 Sulzer Brothers Limited Ribbed heat exchanger
FR2622283A1 (fr) * 1987-10-21 1989-04-28 Sanyo Radiator Co Ltd
DE19644674A1 (de) * 1996-10-28 1998-04-30 Schilling Heinz Kg Lamellenrohr-Wärmeaustauscher in Blockbauweise zur Wärmeübertragung zwischen gas-, dampfförmigen oder flüssigen Medien mit horizontalen Trennflächen
WO2004068052A1 (fr) 2003-01-31 2004-08-12 Heinz Schilling Kg Echangeur de chaleur a air et a eau a parcours partiels de l'eau
DE102011050275A1 (de) * 2011-05-11 2012-11-15 Gea Energietechnik Gmbh Luftbeaufschlagter Trockenkühler

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9003020U1 (fr) * 1990-03-13 1990-06-21 Sueddeutsche Kuehlerfabrik Julius Fr. Behr Gmbh & Co Kg, 7000 Stuttgart, De
US5529120A (en) * 1994-02-01 1996-06-25 Hubbell Incorporated Heat exchanger for electrical cabinet or the like
US6346159B1 (en) * 1998-11-02 2002-02-12 Lacks Industries, Inc. Vehicle wheel construction process
US6536255B2 (en) 2000-12-07 2003-03-25 Brazeway, Inc. Multivoid heat exchanger tubing with ultra small voids and method for making the tubing
US20030131976A1 (en) * 2002-01-11 2003-07-17 Krause Paul E. Gravity fed heat exchanger
US6598295B1 (en) 2002-03-07 2003-07-29 Brazeway, Inc. Plate-fin and tube heat exchanger with a dog-bone and serpentine tube insertion method
CN1228591C (zh) * 2002-07-12 2005-11-23 株式会社电装 用于冷却空气的制冷剂循环系统
DE102004011608A1 (de) * 2004-03-18 2005-10-13 Obrist Engineering Gmbh Wärmetauscher einer Fahrzeugklimaanlage
US20070119566A1 (en) * 2005-11-30 2007-05-31 Xue-Wen Peng Heat dissipation device
FR2932551B1 (fr) * 2008-06-11 2013-08-23 Atlantic Industrie Sas Radiateur a fluide caloporteur a lames chauffantes et son procede de fabrication.
CN103245244B (zh) * 2013-05-10 2016-03-16 丹佛斯微通道换热器（嘉兴）有限公司 换热器
CN103940284B (zh) * 2014-03-21 2016-09-14 丹佛斯微通道换热器（嘉兴）有限公司 换热器及其连接方法
US11054186B2 (en) * 2016-04-15 2021-07-06 Mitsubishi Electric Corporation Heat exchanger
US11774187B2 (en) * 2018-04-19 2023-10-03 Kyungdong Navien Co., Ltd. Heat transfer fin of fin-tube type heat exchanger

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BE404347A (fr) *
GB580917A (en) * 1944-12-01 1946-09-24 Bowman E J Birmingham Ltd Improvements in condensers or coolers primarily for refrigerators
GB735384A (en) * 1953-04-29 1955-08-17 Wellington Tube Works Ltd Tubular heat exchangers
CH310032A (de) * 1953-02-21 1955-09-30 A & P Kaesermann Geb Querlamelle für Röhrenkühler.
US2983483A (en) * 1955-12-19 1961-05-09 Modine Mfg Co Method of radiator core fin assembly and fin element therefor
GB1038556A (en) * 1962-04-16 1966-08-10 Dirk Johannes Oosterbaan Improvements in or relating to heat exchangers
US3515207A (en) * 1968-07-17 1970-06-02 Perfex Corp Fin configuration for fin and tube heat exchanger
FR2250088A1 (fr) * 1973-10-31 1975-05-30 Philips Nv
US3902551A (en) * 1974-03-01 1975-09-02 Carrier Corp Heat exchange assembly and fin member therefor
FR2350167A1 (fr) * 1976-05-06 1977-12-02 Chausson Usines Sa Procede pour la fabrication d'echangeurs de chaleur du type a tubes et dissipateurs et echangeur obtenu par ce procede
DE2720189B1 (de) * 1977-03-23 1978-06-22 Bbc Brown Boveri & Cie Verfahren zum zweistufigen Kuehlen eines in geschlossenem Kreis zirkulierenden Mediums,z.B. des Kondensator-Kuehlwassers einer Waermekraftanlage in einem Waermetauscher und Oberflaechenwaermetauscher zur Durchfuehrung des Verfahrens
FR2478806A1 (fr) * 1980-03-19 1981-09-25 Sueddeutsche Kuehler Behr Radiateur pour moteurs a combustion interne de vehicules automobiles
FR2480924A1 (fr) * 1980-04-22 1981-10-23 Orszagos Koolaj Gazipari Echangeur de chaleur a ailettes en tole

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CH519151A (de) * 1969-06-13 1972-02-15 Schoell Guenter Rippenrohr, Verfahren zu seiner Herstellung, und Vorrichtung zur Ausführung des Verfahrens
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JPS58182092A (ja) * 1982-04-19 1983-10-24 Nippon Radiator Co Ltd コルゲ−トフイン型熱交換器コア
CH666538A5 (de) * 1985-05-15 1988-07-29 Sulzer Ag Waermeuebertrager mit mehreren parallelen rohren und auf diesen angebrachten rippen.
US4592420A (en) * 1985-06-27 1986-06-03 Modine Manufacturing Company Reinforced plate fin heat exchanger

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE404347A (fr) *
GB580917A (en) * 1944-12-01 1946-09-24 Bowman E J Birmingham Ltd Improvements in condensers or coolers primarily for refrigerators
CH310032A (de) * 1953-02-21 1955-09-30 A & P Kaesermann Geb Querlamelle für Röhrenkühler.
GB735384A (en) * 1953-04-29 1955-08-17 Wellington Tube Works Ltd Tubular heat exchangers
US2983483A (en) * 1955-12-19 1961-05-09 Modine Mfg Co Method of radiator core fin assembly and fin element therefor
GB1038556A (en) * 1962-04-16 1966-08-10 Dirk Johannes Oosterbaan Improvements in or relating to heat exchangers
US3515207A (en) * 1968-07-17 1970-06-02 Perfex Corp Fin configuration for fin and tube heat exchanger
FR2250088A1 (fr) * 1973-10-31 1975-05-30 Philips Nv
US3902551A (en) * 1974-03-01 1975-09-02 Carrier Corp Heat exchange assembly and fin member therefor
FR2350167A1 (fr) * 1976-05-06 1977-12-02 Chausson Usines Sa Procede pour la fabrication d'echangeurs de chaleur du type a tubes et dissipateurs et echangeur obtenu par ce procede
DE2720189B1 (de) * 1977-03-23 1978-06-22 Bbc Brown Boveri & Cie Verfahren zum zweistufigen Kuehlen eines in geschlossenem Kreis zirkulierenden Mediums,z.B. des Kondensator-Kuehlwassers einer Waermekraftanlage in einem Waermetauscher und Oberflaechenwaermetauscher zur Durchfuehrung des Verfahrens
FR2478806A1 (fr) * 1980-03-19 1981-09-25 Sueddeutsche Kuehler Behr Radiateur pour moteurs a combustion interne de vehicules automobiles
FR2480924A1 (fr) * 1980-04-22 1981-10-23 Orszagos Koolaj Gazipari Echangeur de chaleur a ailettes en tole

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4789027A (en) * 1985-05-15 1988-12-06 Sulzer Brothers Limited Ribbed heat exchanger
FR2622283A1 (fr) * 1987-10-21 1989-04-28 Sanyo Radiator Co Ltd
DE19644674A1 (de) * 1996-10-28 1998-04-30 Schilling Heinz Kg Lamellenrohr-Wärmeaustauscher in Blockbauweise zur Wärmeübertragung zwischen gas-, dampfförmigen oder flüssigen Medien mit horizontalen Trennflächen
WO2004068052A1 (fr) 2003-01-31 2004-08-12 Heinz Schilling Kg Echangeur de chaleur a air et a eau a parcours partiels de l'eau
DE102011050275A1 (de) * 2011-05-11 2012-11-15 Gea Energietechnik Gmbh Luftbeaufschlagter Trockenkühler

Also Published As

Publication number Publication date
DE3663589D1 (en) 1989-06-29
EP0201665B1 (fr) 1989-05-24
US4789027A (en) 1988-12-06
JPS61265498A (ja) 1986-11-25
CH666538A5 (de) 1988-07-29
HUT41531A (en) 1987-04-28
HU195316B (en) 1988-04-28

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