EP1979699B1 - Echangeur de chaleur a faisceau de tubes - Google Patents

Echangeur de chaleur a faisceau de tubes Download PDF

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Publication number
EP1979699B1
EP1979699B1 EP07702370A EP07702370A EP1979699B1 EP 1979699 B1 EP1979699 B1 EP 1979699B1 EP 07702370 A EP07702370 A EP 07702370A EP 07702370 A EP07702370 A EP 07702370A EP 1979699 B1 EP1979699 B1 EP 1979699B1
Authority
EP
European Patent Office
Prior art keywords
tube
transition piece
heat exchanger
tubes
gas flow
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.)
Active
Application number
EP07702370A
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German (de)
English (en)
Other versions
EP1979699A1 (fr
Inventor
Jiri Jekerle
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.)
General Electric Technology GmbH
Original Assignee
Alstom Technology 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 Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP1979699A1 publication Critical patent/EP1979699A1/fr
Application granted granted Critical
Publication of EP1979699B1 publication Critical patent/EP1979699B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28F1/003—Multiple wall conduits, e.g. for leak detection
    • 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
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/185—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding with additional preformed parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding
    • F28F2275/067—Fastening; Joining by welding by laser welding

Definitions

  • the invention relates to a tube bundle heat exchanger with tubes which are held on both sides in tube plates or oval tube collector tube plates and connected thereto by means of weld, for cooling a guided through the tubes hot gas flow through a surrounding the tubes coolant, comprising at least one gas inlet chamber from which the hot gas stream is introduced into the individual tubes and which is bounded on one side by the input tube plate or oval tube collector tube plate and at least one gas outlet chamber in which the gas flow passed through the tubes is collected and removed and on one side is limited by the output side tube plate or oval tube header tube plate.
  • heat exchangers for the cooling of gases in numerous process engineering plants, such as. B. gasification plants, thermal and catalytic cracking systems, steam reforming plants, etc.
  • heat exchangers in particular tube bundle heat exchanger (cooler), used in the flow of gases to be cooled through straight tubes and thereby the latent heat of the hot gas through the pipe wall to the medium surrounding the tubes, in particular cooling medium.
  • the gases to be cooled are often under a high pressure and a high temperature and enter the straight tubes of the heat exchanger at a high speed.
  • a high heat flux density is achieved at the pipe inlet or the first pipe section, which cause both a high temperature and a high thermal stress in the tubes of the heat exchanger or in the connection Rohrplatte- tube.
  • the gas-carrying pipes are welded into the tube plates, wherein the weld between the tube plate and tube is mounted either on the outer or inner wall of the tube plate or within the tube plate opening.
  • the publication DE 37 15 713 C2 points, for example a welded joint of the pipe or pipes with the outer wall of the tube plate or the oval tube header tube plate.
  • the disadvantage of this known embodiment is that the gas facing contour or surface of the transition from tube to tube plate or oval tube collector tube plate has no exact aerodynamic shape.
  • the use of an inserted sleeve is usually for several different reasons, i.a. a narrowing of the gas-side cross-section and insufficient cooling of the sleeve, undesirable.
  • the object of the present invention is to provide a tube bundle heat exchanger in which the aforementioned disadvantages are avoided or the transition from the tube plate or the oval tube header tube plate to the tubes on the gas side has a streamlined contour and on the cooling medium side and the gas side no disturbing elements are present.
  • connection of the tubes with the input tube plate or oval tube collector tube plate is formed in each case by means of a conical and / or trumpet-shaped transition piece whose cross-section decreases seen in the gas flow direction, that seen in the gas flow direction input end of the transition piece jerky is connected to the tube plate or oval tube header tube plate and the inner and outer contours of the transition piece and the Sch mentionharms Schemees to the tube plate or oval tube collector tube plate gap and edge free and straight and / or formed with an add on the outer contour radius of equal to or greater than 5 mm ,
  • the length Lu of the transition piece is at least 1.5 times the inner diameter di of the heat exchanger tube and / or the inner diameter Di of the transition piece at the inlet at least 1.2 times the inner diameter di of the heat exchanger tube to a to achieve optimized aerodynamic transition of the tube plate or the oval tube collector tube plate to the respective heat exchanger tubes.
  • the transition piece is formed from a separate pipe part and seen in the gas flow direction output end of the transition piece is jerkily connected to the pipe by a weld.
  • a separate pipe part complicated transition pieces (for example, several different transition radii) can be made much easier and cheaper in their shape become.
  • the inner and outer contours of the transition piece and the weld connection area to the tube plate or oval tube collector tube plate and the pipe gap and edge free and straight and / or formed with a radius equal to or greater than 2 mm.
  • the pipe part used as a transition piece is designed as a forging.
  • FIG. 1 shows a tube bundle heat exchanger 1 shown schematically in longitudinal section.
  • Such tube bundle heat exchanger 1 are used in numerous process engineering systems, such. As gasification plants, thermal and catalytic crackers, steam reforming plants, etc., required, in which a process gas, an exhaust gas or the like. Is produced.
  • the tube bundle heat exchanger 1 is generally used for cooling the aforementioned hot gas 18, which is introduced through a line not shown in the gas inlet chamber 8 of the heat exchanger 1 and passed from here through a plurality of straight tubes 2, then in the gas outlet chamber 9 of the Heat exchanger 1 is collected and discharged by means not shown line from the heat exchanger 1.
  • connection of the tubes according to the invention 2 with the input-side tube plate 3 (see FIGS. 2 to 4 ) or oval tube header tube plate 5 (see FIG. 5 ) are each formed by means of a cone-shaped and / or trumpet-shaped transition piece 10, whose cross-section is seen in the gas flow direction (see arrow) is reduced.
  • the entrance side end 16 of the transition piece 10 as seen in the gas flow direction is jerkily connected to the tube plate 3 or oval tube header tubes 5 and the inner and outer contours 11, 12 of the transition piece 10 and the weld joint portion 13 to the tube plate 3 or oval tube header tube plate 5 free of edges and straight and / or with an attaching to the outer contour 12 radius, which is at least 5 mm formed.
  • the inventive design of the transition of tube plate 3 and of oval tube header tube plate 5 on the tube 2 an aerodynamic contour 11, 12 creates both on the gas-contacting as well as on thedemediumberlickt side of the tubes 2, the transition piece 10 and the tube plate 3 or oval tube-collector tube plate 5, which has at no point a column, an edge or a square transition. All transitions, including the weld connection region 13 on the inner and outer contours 11, 12, are accordingly designed according to the invention either straight or flat and / or with a radius.
  • FIG. 2 and 5 is the transition piece 10, for example, mechanically expanded end 16 of the tube 2.
  • the transition piece 10 which consists of a separate pipe part 15 and is usually easier to manufacture, since the pipe part 15. relative to the entire tube 2 is much shorter and thus is easier to work.
  • a further weld seam 22 is required, which forms the weld joint region 14 between the pipe 2 and the pipe part 15.
  • This weld joint region 14 is advantageously formed either on the inner contour as well as on the outer contour 11, 12 either straight or flat and / or with a radius, ie the region 14 is edge-and gap-free.
  • the transition pieces 10 according to the FIGS. 2 to 5 have at their input end 16, based on the outer contour 12 of the transition pieces 10, for example, a radius R 1 of 5 mm. According to the Figures 2 . 3 and 5 This is followed by another radius R 2 of, for example, 60 mm, whereas at the transition piece 10 according to FIG. 4 the first radius is followed by a conical constriction with a subsequent radius of, for example, 20 mm.
  • the inner contour 11 of the transition pieces 10 according to the Figures 2 and 5 then has corresponding radii, which are larger by the wall thickness s of the transition piece 10.
  • the transition between the two wall thicknesses s and t is within the weld connection area 13
  • the wall thickness t of the tube plate 3, 5 does not correspond to the wall thickness s of the tube 2
  • the transition between the two wall thicknesses s and t is within the weld connection area 13
  • a different wall thickness t of the tube plate 3, 5 with respect to the wall thickness s of the tube 2 can according to the Figures 3 and 4 be compensated with a trained as a tubular member 15 transition piece 10 by the respective wall thicknesses at the tube ends of the tube member 15 to the wall thicknesses t and s of the tube plate 3, 5 and the tube 2 are adjusted. That is, seen in the gas flow direction, within the pipe section 15, the wall thickness t is continuously reduced or increased to the wall thickness s.
  • the tube part 15 may advantageously be formed as a forged piece.
  • the length L of the transition piece 10 is advantageously 1.5 times the inner diameter di of the tube 2 and the inner diameter Di of the transition piece 10 directly at the entrance into the transition piece 10 is advantageously 1.2 times the inner diameter di of the tube. 2
  • FIG. 4 For example, instead of a trumpet-shaped transition piece 10 has a cone-shaped transition piece 10, which in turn is formed from a separate tube member 15. Again, the pipe member 15 is connected by two welds 7, 22 with the tube plate 3 and the tube 2.
  • FIG. 5 shows a tube bundle heat exchanger 1 with double tubes 2, 21, in which the cooling medium 19 circulates in the annular cross-section between the inner tube 2 and the outer tube 21.
  • the cooling medium 19 leading, outer tubes 21 is the otherwise, and as in FIG. 1 shown, required outer heat exchanger jacket 23 unnecessary.
  • the cooling medium 19 according to the FIG. 5 supplied or removed by means of oval tube collector 20.
  • the connection of the transition piece 10 according to the invention takes place in this case with the oval tube header tube plate fifth
  • water can be used, which is partially or completely evaporated by the heat supply.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Lubricants (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Claims (8)

  1. Echangeur de chaleur à faisceau tubulaire avec des tuyaux (2), qui sont maintenus des deux côtés dans des plaques tubulaires (3, 4) ou des plaques tubulaires collectrices à tuyau ovale (5, 6) et sont reliés chacun à ces plaques au moyen d'une soudure (7), pour le refroidissement d'un flux de gaz (18) chaud conduit dans les tuyaux (2) par un réfrigérant (19) entourant les tuyaux (2), présentant
    au moins une chambre d'entrée de gaz (8), à partir de laquelle le flux de gaz (18) chaud est introduit dans les tuyaux (2) individuels et qui est délimitée sur un côté par la plaque tubulaire (3) côté entrée ou la plaque tubulaire collectrice à tuyau ovale (5) et au moins une chambre de sortie de gaz (9), dans laquelle le flux de gaz (18) conduit à travers les tuyaux (2) est collecté et évacué et qui est délimitée sur un côté par la plaque tubulaire (4) côté sortie ou la plaque tubulaire collectrice à tuyau ovale (6)
    caractérisé en ce que la liaison des tuyaux (2) avec la plaque tubulaire (3) côté entrée ou la plaque tubulaire collectrice à tuyau ovale (5) est formée respectivement au moyen d'une pièce de raccord (10) en forme de cône et/ou en forme de trompette, dont la section se réduit, vu dans le sens d'écoulement du gaz,
    en ce que l'extrémité (16), côté entrée vu dans le sens d'écoulement du gaz, de la pièce de raccord (10) est reliée par intermittence à la plaque tubulaire (3) ou la plaque tubulaire collectrice à tuyau ovale (5),
    et les contours intérieurs et extérieurs (11, 12) de la pièce de raccord (10) et de la zone de liaison par soudure (13) avec la plaque tubulaire (3) ou la plaque tubulaire collectrice à tuyau ovale (5) sont formés sans fente et sans arête ainsi que droits et/ou avec un rayon (R), commençant sur le contour extérieur (12), d'au moins 5 mm.
  2. Echangeur de chaleur à faisceau tubulaire selon la revendication 1, caractérisé en ce que la longueur (Lü) de la pièce de raccord (10) représente au moins 1,5 fois le diamètre intérieur (di) du tuyau (2).
  3. Echangeur de chaleur à faisceau tubulaire selon la revendication 1, caractérisé en ce que le diamètre intérieur (Di) de la pièce de raccord (10) représente, vu dans le sens d'écoulement du gaz, sur son entrée au moins 1,2 fois le diamètre intérieur (di) du tuyau (2).
  4. Echangeur de chaleur à faisceau tubulaire selon la revendication 1, caractérisé en ce que la pièce de raccord (10) est formée par un élargissement mécanique sur l'extrémité (16), côté entrée vu dans le sens d'écoulement du gaz, du tuyau (2).
  5. Echangeur de chaleur à faisceau tubulaire selon la revendication 1, caractérisé en ce que la pièce de raccord (10) est formée par une partie de tuyau (15) séparée et l'extrémité (17), côté sorti, vu dans le sens d'écoulement du gaz, de la pièce de raccord (10) est reliée par intermittence au tuyau (2) par une soudure (22).
  6. Echangeur de chaleur à faisceau tubulaire selon la revendication 5, caractérisé en ce que les contours intérieurs et extérieurs (11, 12) de la zone de liaison par soudure (14) entre la pièce de raccord (10) et le tuyau (2) sont conçus sans fente et sans arête ainsi que droits et/ou avec un rayon (R), commençant sur le contour extérieur (12), d'au moins 5 mm.
  7. Echangeur de chaleur à faisceau tubulaire selon l'une quelconque des revendications précédentes, caractérisé en ce que les contours intérieurs et extérieurs (11, 12) de la pièce de raccord (10) et de la zone de liaison par soudure (13, 14) avec la plaque tubulaire (3) ou la plaque tubulaire collectrice à tuyau ovale (5) et avec le tuyau (2) sont conçus sans fente et sans arête ainsi que droits et/ou avec un rayon (R), commençant sur le contour extérieur (12), d'au moins 2 mm.
  8. Echangeur de chaleur à faisceau tubulaire selon l'une quelconque des revendications précédentes, caractérisé en ce que la partie de tuyau (15) est conçue sous forme de pièce forgée.
EP07702370A 2006-01-23 2007-01-19 Echangeur de chaleur a faisceau de tubes Active EP1979699B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006003317A DE102006003317B4 (de) 2006-01-23 2006-01-23 Rohrbündel-Wärmetauscher
PCT/DE2007/000089 WO2007082515A1 (fr) 2006-01-23 2007-01-19 Échangeur de chaleur à faisceau de tubes

Publications (2)

Publication Number Publication Date
EP1979699A1 EP1979699A1 (fr) 2008-10-15
EP1979699B1 true EP1979699B1 (fr) 2009-04-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07702370A Active EP1979699B1 (fr) 2006-01-23 2007-01-19 Echangeur de chaleur a faisceau de tubes

Country Status (11)

Country Link
US (2) US9534850B2 (fr)
EP (1) EP1979699B1 (fr)
JP (1) JP2009524004A (fr)
CN (1) CN101371097B (fr)
AT (1) ATE427470T1 (fr)
AU (1) AU2007207217B2 (fr)
DE (2) DE102006003317B4 (fr)
DK (1) DK1979699T3 (fr)
ES (1) ES2324500T3 (fr)
WO (1) WO2007082515A1 (fr)
ZA (1) ZA200806306B (fr)

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CN107787244B (zh) * 2015-04-21 2020-11-24 Ti集团车辆系统有限责任公司 燃料过滤器壳体
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KR102343408B1 (ko) * 2017-11-17 2021-12-27 주식회사 엘지화학 열 교환기
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ES2324500T3 (es) 2009-08-07
EP1979699A1 (fr) 2008-10-15
US10914527B2 (en) 2021-02-09
AU2007207217A1 (en) 2007-07-26
DE102006003317B4 (de) 2008-10-02
CN101371097B (zh) 2011-10-05
US20090065185A1 (en) 2009-03-12
AU2007207217B2 (en) 2010-04-29
ATE427470T1 (de) 2009-04-15
US9534850B2 (en) 2017-01-03
DE502007000563D1 (de) 2009-05-14
CN101371097A (zh) 2009-02-18
DE102006003317A1 (de) 2007-08-02
WO2007082515A1 (fr) 2007-07-26
US20170074593A1 (en) 2017-03-16
JP2009524004A (ja) 2009-06-25
DK1979699T3 (da) 2009-06-29
ZA200806306B (en) 2009-05-27

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