EP0619466B1 - Condenseur de vapeur - Google Patents

Condenseur de vapeur Download PDF

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Publication number
EP0619466B1
EP0619466B1 EP94103311A EP94103311A EP0619466B1 EP 0619466 B1 EP0619466 B1 EP 0619466B1 EP 94103311 A EP94103311 A EP 94103311A EP 94103311 A EP94103311 A EP 94103311A EP 0619466 B1 EP0619466 B1 EP 0619466B1
Authority
EP
European Patent Office
Prior art keywords
steam
tubes
cooler
compartments
condenser
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
EP94103311A
Other languages
German (de)
English (en)
Other versions
EP0619466A2 (fr
EP0619466A3 (fr
Inventor
Francisco Dr. Blangetti
Andreas Kost
Günter Volks
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.)
ABB AG Germany
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0619466A2 publication Critical patent/EP0619466A2/fr
Publication of EP0619466A3 publication Critical patent/EP0619466A3/fr
Application granted granted Critical
Publication of EP0619466B1 publication Critical patent/EP0619466B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/10—Auxiliary systems, arrangements, or devices for extracting, cooling, and removing non-condensable gases

Definitions

  • Such a steam condenser is known from CH-PS 423 819 and DE-OS 1 948 073.
  • the condenser tubes are arranged in several, so-called sub-bundles in a condenser housing.
  • the steam flows through an exhaust pipe into the condenser housing and is distributed in the room through flow channels (steam entry lanes).
  • the free inflow of steam to the outside tubes of the partial bundles is ensured.
  • the steam then flows through the bundles with little resistance due to the low depth of the tube rows.
  • the partial bundles in the condenser are arranged side by side in such a way that flow channels arise between them, which in the sectional view appear to be of the same order of magnitude as the partial bundles themselves.
  • the tubes form in the successive rows a permeable enclosure, which preferably represents the same hydraulic resistance throughout.
  • This known condenser has the advantage that due to the loose arrangement of the sub-bundles, all peripheral tubes of a sub-bundle are well supplied with steam without a noticeable loss of pressure. On the other hand, the requirement for at least approximately the same "wall thickness" or. Resistance of the tube bundle around the cavity a relatively large overall height of the bundle. This results in the excellent suitability of this partial bundle concept for large capacitors, in which a plurality of partial bundles are arranged side by side.
  • the capacitors working under vacuum require a well-functioning suction system so that incoming, non-condensable gases are always removed from the condensation area will. Cooling tubes that are surrounded or flowed around by these gases mixed with steam are almost completely lost as a condensation surface, which reduces the output.
  • the incoming gases cannot keep the vacuum at the lowest possible value.
  • non-condensable gases mostly air - already in concentrations of 1% molar fraction, with temperature differences between the wall and the steam core of 4-5 K, a reduction in the heat transfer on the steam side - with quasi-still steam - to 30-40% of that value, which can be achieved with pure steam.
  • the vacuum loss is thus expressed in a lower efficiency of the circulatory system.
  • the inert gas enrichment zone is formed in two parts. It consists of a funnel-shaped "pre-air cooler", there called “post-condensation part”, and an encapsulated air cooler that communicates with the pre-air cooler and a downstream suction channel (header) via a double row of evenly distributed cooler inlet orifices and radiator outlet orifices.
  • This encapsulated air cooler is geometrically designed in such a way that the deterioration of the heat transfer on the steam side is partially compensated for by an increase in the speed of the gas phase. Since the encapsulated air cooler adapts to an approximate temperature curve of the cooling water in the neighboring pipes, it therefore ensures that suitable ventilation of the pre-air cooler is approximately proportional to the resulting, non-condensable gases.
  • the invention is therefore based on the object of providing a capacitor of the type mentioned at the outset which, while maintaining the known advantages of the partial bundle concept, is furthermore distinguished by low production costs.
  • the heat exchanger shown is a surface condenser in a rectangular design, as it is suitable for a so-called underfloor arrangement.
  • Parts that are not essential to the invention, such as the condenser neck, condensation chamber, condenser jacket, water chambers, tube sheets, condensate collection vessel, etc. are omitted, but are briefly explained below in connection with the invention.
  • the steam flows into the condenser neck via an evaporation nozzle with which the condenser is connected to the turbine.
  • the best possible homogeneous flow field is generated therein in order to carry out a clean steam purging of the bundles 20 arranged downstream over their entire length.
  • the condensation space inside the capacitor jacket contains several bundles arranged side by side.
  • One of the objectives of this is that even during plant operation a partial cut-off on the cooling water side can be carried out, for example for the purpose of an inspection of a switched-off bundle on the cooling water side.
  • the independent cooling water supply is expressed by the fact that the water chambers of the condenser are divided into compartments by partitions.
  • a bundle 20 consists of a number of tubes, of which only one cooling tube designated 13s is shown in FIG. 1. At both ends, the cooling tubes are fastened in tube sheets. The water chambers are arranged beyond the tube sheets. The condensate draining from the bundles is collected in a condensate collection vessel and from there it enter
  • the bundles 20 are designed in such a way that all tubes 13s of the periphery have a good flow of steam without a noticeable loss of pressure.
  • the existing flow paths between the bundles on the one hand and between the outer bundles and their adjacent condenser wall are designed accordingly:
  • the condensation part of the bundle 20, which is only partially visualized by the dotted surface, is designated by 1.
  • the continuous support plates 5, which serve to support the cooling tubes 13 the sub-bundles are divided into compartments 10.
  • a cavity 19 is formed inside each bundle 2, in which the vapor enriched with non-condensable gases - hereinafter called air - collects.
  • An air cooler is accommodated in this cavity 19. The steam-air mixture flows through this air cooler, with most of the steam condensing. The rest of the mixture is suctioned off at the cold end.
  • the air cooler located inside the tube bundle has the effect that the steam-gas mixture is accelerated within the condenser bundle. This improves the situation in that there are no small flow velocities that could impair the heat transfer.
  • the air cooler is arranged in the interior of the bundle at the level at which the bundle of pressure runs through a relative minimum on both sides of the bundle.
  • the air cooler is thus in the middle of the bundle.
  • the bundle is designed in such a way that the steam suction into the cavity 19 - taking into account the effective pressure at the pipe periphery and due to the different pipe row thickness - acts homogeneously in the radial direction over all pipes adjacent in the cavity 19. This results in a homogeneous pressure gradient and thus a clear flow direction of the steam and the non-condensable gases towards the air cooler.
  • the cavity 19 upstream has an internal compensation lane 12, which ensures that the air-enriched steam from the core of the front half of the bundle also finds a smooth path to the air cooler.
  • the air cooler has the task of removing the non-condensable gases from the condenser. During this process, the steam losses are to be kept as low as possible. This is achieved by moving the steam / air mixture towards Suction channel is accelerated. The high speed results in good heat transfer, which leads to extensive condensation of the residual steam. In order to accelerate the mixture, the cross section in the direction of flow is increasingly smaller.
  • FIG. 1 shows the cooling system mentioned at the outset and known from DE-OS 1 948 073. It consists of the pre-cooler 2s, of which the cooling tube 14s is shown, and the encapsulated air cooler 3s, of which the cooling tube 15s is shown.
  • the space 11s for pressure equalization is arranged between the two. This unthreaded space 11s is also mainly required in order to be able to weld the sheet metal wall 7s separating the air cooler 3s from the precooler 2s to the support plates 5.
  • the panels 9s are arranged in the sheet metal wall 7s.
  • Orifices 6s are also provided in the sheet metal wall 8s provided at the outlet of the cooler 3s, via which the non-condensable gases are drawn off into the suction space 4s. The installation of these throttling points ensures that the pressure difference that is necessary in any case at the beginning and end of the condensation process is mainly reduced in the orifices.
  • the cooling tubes 15 of the cooler 3 are arranged in a funnel shape for this purpose.
  • the funnel walls 16, which isolate the cooler 3 from the condensation space 1, are connected to one another at an acute angle.
  • the funnel 16 is provided with a cover plate 17, which is placed over the tubes of the cooler toward the cavity 19 and protects them from the steam and condensate flow flowing from top to bottom. This also specifies the direction of flow of the mixture to be cooled, namely from the rear cavity to the front towards the funnel tip.
  • these funnel walls simultaneously form the partition 7 to the suction channel 4.
  • the screens 6 are arranged in the immediate area of the funnel tip. It can be seen from FIG.
  • the non-condensable gases are sucked off via the orifices 6 into the channel 4, from which they are led out of the condenser in the longitudinal direction.
  • the suction line 4 penetrates one of the tube sheets (not shown) and the corresponding water chamber.
  • the different cross-sectional requirements per compartment can be covered by appropriate arrangement of a plurality of bores with different diameters and / or different pitches. Orifice diameter and orifice spacing should be selected so that the local, non-condensable mass flow is extracted at the locally available pressure difference.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (1)

  1. Condenseur de vapeur, dans lequel la vapeur est précipitée sur des tubes (13) rassemblés en faisceaux séparés (20) parcourus par l'eau de refroidissement,
    - dans lequel chaque faisceau est subdivisé en compartiments (10) par des plaques d'appui (5) disposées perpendiculairement aux tubes,
    - dans lequel les tubes d'un faisceau disposés en rangées entourent un espace creux (19), dans lequel est disposé un refroidisseur (3) pour les gaz non condensables,
    - dans lequel les gaz non condensables venant du refroidisseur (3) pénètrent par des diaphragmes (6) dans un canal d'aspiration (4) commun pour tous les compartiments (10), qui s'étend sur toute la longueur des tubes (13),
    - et dans lequel le refroidisseur (3) n'est pas encapsulé et est séparé de l'espace de condensation (1) par des parois d'entonnoir (16), le canal d'aspiration (4) se raccordant directement aux parois d'entonnoir,
    - et dans lequel les sections de passage des diaphragmes (6) dans les compartiments (10) sont dimensionnées de telle façon que le courant massique local non condensable soit aspiré sous la différence de pression locale disponible.
EP94103311A 1993-04-05 1994-03-04 Condenseur de vapeur Expired - Lifetime EP0619466B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4311118 1993-04-05
DE4311118A DE4311118A1 (de) 1993-04-05 1993-04-05 Dampfkondensator

Publications (3)

Publication Number Publication Date
EP0619466A2 EP0619466A2 (fr) 1994-10-12
EP0619466A3 EP0619466A3 (fr) 1995-12-13
EP0619466B1 true EP0619466B1 (fr) 1997-11-19

Family

ID=6484760

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94103311A Expired - Lifetime EP0619466B1 (fr) 1993-04-05 1994-03-04 Condenseur de vapeur

Country Status (3)

Country Link
US (1) US5465784A (fr)
EP (1) EP0619466B1 (fr)
DE (2) DE4311118A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6269867B1 (en) * 1994-12-02 2001-08-07 Hitachi, Ltd Condenser and power plant
JP3735405B2 (ja) * 1995-12-15 2006-01-18 株式会社東芝 復水器
DE19610237A1 (de) * 1996-03-15 1997-09-18 Asea Brown Boveri Dampfkondensator
DE19642100B4 (de) * 1996-10-12 2011-09-29 Alstom Dampfkondensator
WO1999050610A1 (fr) 1998-03-27 1999-10-07 Siemens Aktiengesellschaft Tuyau echangeur thermique, son procede de production et un condensateur
JP2000304464A (ja) * 1999-04-15 2000-11-02 Toshiba Corp 復水器
DE10016080A1 (de) * 2000-03-31 2001-10-04 Alstom Power Nv Kondensator
JP4913206B2 (ja) * 2006-03-27 2012-04-11 バラット ヘビー エレクトリカルズ リミテッド ２管路式管巣体構造の復水器
CN201203306Y (zh) * 2007-08-21 2009-03-04 高克联管件(上海)有限公司 一种带气体折流板的冷凝器
WO2015111318A1 (fr) * 2014-01-23 2015-07-30 三菱日立パワーシステムズ株式会社 Condenseur

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE423819C (de) * 1924-07-17 1926-01-11 Hermann Johs Schwabe Fa Verfahren und Vorrichtung zum Impraegnieren des auf Strick-, Wirk- u. dgl. Maschinen zu verarbeitenden Fadens
DE505357C (de) * 1928-12-19 1930-08-20 Timken Roller Bearing Co Kegelrollenlager mit einer Anlaufrippe
US2224877A (en) * 1939-08-25 1940-12-17 Westinghouse Electric & Mfg Co Condensing apparatus
CH423819A (de) * 1965-01-15 1966-11-15 Bbc Brown Boveri & Cie Kondensationsanlage für Dampfturbinen-Abdampf
BE755389A (fr) * 1969-08-29 1971-02-01 Bbc Brown Boveri & Cie Procede pour la condensation de la vapeur d'eau et installationpour la mise en oeuvre de ce procede
JPS5914682B2 (ja) * 1980-09-29 1984-04-05 株式会社日立製作所 給水加熱器
EP0325758B1 (fr) * 1988-01-22 1991-03-06 Asea Brown Boveri Ag Condenseur de vapeur

Also Published As

Publication number Publication date
EP0619466A2 (fr) 1994-10-12
DE59404596D1 (de) 1998-01-02
US5465784A (en) 1995-11-14
DE4311118A1 (de) 1994-10-06
EP0619466A3 (fr) 1995-12-13

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