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EP0384200A1 - Condenseur à vapeur - Google Patents

Condenseur à vapeur Download PDF

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Publication number
EP0384200A1
EP0384200A1 EP90102198A EP90102198A EP0384200A1 EP 0384200 A1 EP0384200 A1 EP 0384200A1 EP 90102198 A EP90102198 A EP 90102198A EP 90102198 A EP90102198 A EP 90102198A EP 0384200 A1 EP0384200 A1 EP 0384200A1
Authority
EP
European Patent Office
Prior art keywords
bundle
steam
bundles
cooler
sub
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
EP90102198A
Other languages
German (de)
English (en)
Other versions
EP0384200B1 (fr
Inventor
Francisco Dr. Blangetti
Vaclav Svoboda
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 Switzerland GmbH
ABB Asea Brown Boveri Ltd
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 EP0384200A1 publication Critical patent/EP0384200A1/fr
Application granted granted Critical
Publication of EP0384200B1 publication Critical patent/EP0384200B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • 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
    • 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
    • Y10S165/184—Indirect-contact condenser
    • Y10S165/205—Space for condensable vapor surrounds space for coolant
    • Y10S165/207—Distinct outlets for separated condensate and gas
    • Y10S165/211—Distinct outlets for separated condensate and gas including concave member adjacent to vapor outlet and partially covering a group of coolant tubes

Definitions

  • the invention relates to a steam condenser for ground-level arrangement with a steam turbine, the steam being deposited on pipes through which cooling water flows and which are combined in separate sub-bundles, and wherein the pipes of a bundle arranged in rows enclose a cavity in which a cooler for the non-condensable gases is arranged ,
  • Such a steam condenser for the so-called underfloor arrangement, is known from Swiss Patent No. 423 819.
  • 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. These narrow in the general direction of the flow in such a way that the flow velocity of the steam in these channels remains at least approximately constant.
  • the free inflow of steam to the outside tubes of the partial bundles is ensured.
  • the steam then flows through the bundles with a small resistance due to the low pipe depth.
  • the sub-bundles in the condenser are arranged next to each other in such a way that flow channels are created between them, which appear in the sectional view in the same order of magnitude as the sub-bundles themselves. Furthermore, the tubes in the successive rows form a self-contained wall, which is preferably continuous is of the same thickness.
  • This known condenser has the advantage that due to the loose arrangement of the partial bundles, all peripheral tubes of a partial bundle are well charged with steam without any noticeable pressure loss.
  • the requirement for at least approximately the same "wall thickness" of the tube-shaped sub-bundle around the cavity results in a relatively large overall height of the sub-bundle.
  • This known solution is less suitable for steam condensers of power plants, in which the condenser and the turbine are located approximately at the same height of the machine house foundation, for example due to a limitation in the height. In such cases, the capacitor can be arranged coaxially with the turbine shaft or laterally along the turbine. Underfloor arrangements are also not possible with watercraft driven by a steam turbine with a shallow draft.
  • 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.
  • this is achieved by - that the partial bundles are oriented horizontally in their longitudinal extent, that several sub-bundles are arranged one above the other in the vertical, - And that the cooler is formed asymmetrically within the sub-bundle and that its intake cross-section has its center of gravity below the longitudinal center line of the sub-bundle.
  • the tubes of the cooler are provided in the cavity of the bundle with a cover plate, which is also designed as a closed suction channel that communicates with the cooler zone via panels.
  • the multifunctional cover plate protects the cooler pipes from the condensate running down.
  • the heat exchanger shown is a surface condenser in a rectangular design, as it is suitable for the so-called "on floor” arrangement. As a rule, such capacitors have useful power ranges of ⁇ 300 MWe.
  • the steam flows into the condenser neck 1 via an evaporation nozzle 10, 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 2 arranged downstream over their entire length.
  • the condensation space inside the condenser jacket contains four separate bundles 2. This has the aim, among other things, that a partial shutdown on the cooling water side can also be carried out during system operation, for example for the purpose of an inspection of a shutdown bundle on the cooling water side.
  • the independent application of cooling water is expressed in that the water chambers 7 (FIG. 2) are divided into compartments by horizontal partition walls (not shown).
  • the bundles consist of a number of tubes 5, which are fastened at their two ends in tube plates 6. Beyond the tube sheets, the water chambers 7 are arranged. The condensate flowing off from the bundles 2 is collected in the condensate collecting vessel 12 and from there it reaches the water / steam circuit, not shown.
  • a cavity 13 is formed in the interior of each bundle 2, in which the cavity contains gases that cannot be condensed - hereinafter called air - collects enriched steam.
  • An air cooler 14 is accommodated in this cavity 13. 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.
  • a cuboidal capacitor shell - the shape of the four bundles 2 is adapted so that the following goals are achieved: - Good use of the temperature gradient - Small pressure drop in the tube bundle despite the high packing density of the tubing - No stagnant air accumulation in the steam lanes and the bundles - No undercooling of the condensate - Good degassing of the condensate.
  • the bundles are designed in such a way that all pipes in the periphery have a good flow of steam without noticeable pressure loss.
  • the existing flow paths between the four bundles 2 on the one hand and between the outer bundles and their adjacent condenser wall are designed as follows:
  • the steam is now decelerated to zero speed with a simultaneous pressure recovery. This is achieved by making the second part of the flow path divergent. It should also be noted here that the channel expansion does not have to be optically recognizable due to the increasing decrease in the mass flow. It is important that the residual steam flowing towards the condenser bottom 8 generates a dynamic pressure there. This deflects the steam and also supplies the lower parts of the bundle.
  • the increase in temperature caused by the dynamic pressure benefits the condensate flowing down from pipe to pipe by heating up again if it has cooled below the saturation temperature. This ensures two advantages: There are no thermodynamic losses due to condensate hypothermia and the oxygen content of the condensate is reduced to a minimum.
  • the air cooler 14 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 therefore located in the rear half of the sub-bundle.
  • the bundle is designed so that the vapor intake into the hollow Room 13 - taking into account the effective pressure at the pipe periphery and due to the different pipe row thickness - acts homogeneously in the radial direction across all pipes in the cavity 13. This results in a homogeneous pressure gradient and thus a clear direction of flow of the steam and the non-condensable gases in the direction of the air cooler 14.
  • the cavity 13 opens upstream into a compensation lane 16 inside the bundle, which also ensures that the air-enriched steam from the core of the front half the bundle finds a smooth way to the air cooler.
  • the sheets cover the bundles, but in any case leave enough free space for pressure equalization and for pressure regeneration by stagnation of the residual steam speed at the end of the condensation path, i.e. impossible in the region of the capacitor bottom 8.
  • the resulting steam cushion causes any condensate subcooling to regress and the residual degassing of the condensate, which is finely divided at this point.
  • the entire condenser shell assembly ie housing, as well as partial bundles and condensate collecting plates, is in the longitudinal direction of the pipe slightly inclined about the turbine axis 24 in order to promote the rapid drainage of the condensate.
  • the air coolers within the partial bundles are asymmetrical in shape and of an ascentric position within the cavity 13.
  • the bundles 2 are subjected to a highly asymmetrical load when installed horizontally, since gravity and the inertial force of the vapor velocity are almost perpendicular to each other.
  • this asymmetry mainly relates to the condensate load in the bundle, which also leads to an asymmetrical localization of the pressure minimum in the pipe structure with regard to the geometrical bundle contours.
  • the location of the minimum pressure dictates the location of the air cooler as it is the location of the accumulation of non-condensable gases.
  • the condensate raining down from above increases the steam-side pressure loss in the lower half of the bundle and thus causes the pressure minimum to shift downwards.
  • the air cooler is therefore configured and arranged in such a way that it takes account of the asymmetry mentioned.
  • the air is drawn in below the longitudinal center line 22 of the bundle due to the chosen cooler configuration.
  • the air cooler 14 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 in that the steam / air mixture is accelerated in the direction of the suction duct 17. 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, as can be seen in FIG. 5. The air is sucked off through orifices 18 into the channel 17.
  • These covers, which are attached to the youngest part of the radiator cover are the physical separation of the condensation space from the suction channel. They are distributed several times over the entire length of the pipe and, by creating a pressure loss, ensure that the suction effect is homogeneous in all compartments of the condenser.
  • Part of the wall of the suction channel 17 is also designed as a funnel-shaped cover plate 19. This sheet is placed over the pipes of the cooler and protects them from the steam and condensate flow flowing from top to bottom. This also specifies the direction of entry of the mixture to be cooled, namely from the back to the front towards the screens 18.
  • the drainage of the suction channel 17 takes place through holes 23 arranged several times in the longitudinal direction of the channel at the lowest point of the channel.
  • a corresponding number of tubes 5 are left out of the bundles 2. Depending on the size and staggering of the tubes 5, this involves omitting either one or two rows of tubes. A plurality of suction lines 20 penetrating the bundle upward are led out through this recess. Parallel to the bundle, these suction lines are led to the condenser bottom 8, where they open into a collecting line 15 leading to the suction device.
  • vapor barriers The free space created by the omission of the pipes is filled with vapor barriers.
  • the primary goal of these is to prevent steam bypass.
  • these are dummy pipes which do not prevent the vertical exchange of steam or condensate. In the direction of the steam lane / cooler, they form a flow obstacle that should have the same pressure loss as the original pipe.
  • these blind pipes can also be used as support anchors between the pipe support plates, not shown.
  • the invention is not limited to the exemplary embodiment shown and described.
  • longitudinal, staggered, baffle-like sheets could be used as vapor barriers instead of the dummy pipes.
  • the vapor barriers could also be dispensed with entirely if the non-condensable gases are led out of the condenser in the longitudinal direction of the tube instead of across the bundle.
  • the suction channel respectively. the suction line connected to it penetrate one of the two tube plates 6 and the corresponding water chamber 7.
  • the condenser can of course also be divided into two and arranged on both sides of the turbine. Likewise, it can be set up in the extension of the turbine axis.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP90102198A 1989-02-23 1990-02-05 Condenseur à vapeur Expired - Lifetime EP0384200B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH670/89 1989-02-23
CH67089 1989-02-23

Publications (2)

Publication Number Publication Date
EP0384200A1 true EP0384200A1 (fr) 1990-08-29
EP0384200B1 EP0384200B1 (fr) 1993-09-22

Family

ID=4192419

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90102198A Expired - Lifetime EP0384200B1 (fr) 1989-02-23 1990-02-05 Condenseur à vapeur

Country Status (5)

Country Link
US (1) US5018572A (fr)
EP (1) EP0384200B1 (fr)
JP (1) JP2930647B2 (fr)
DE (1) DE59002779D1 (fr)
HU (1) HU212653B (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19523923A1 (de) * 1995-06-30 1997-01-02 Abb Management Ag Niederdruck-Dampfturbine
DE19642100A1 (de) * 1996-10-12 1998-04-16 Asea Brown Boveri Dampfkondensator
DE19715492A1 (de) * 1997-04-14 1998-10-15 Siemens Ag Dampfturbinenanlage
EP0957325A1 (fr) 1998-05-14 1999-11-17 Asea Brown Boveri AG Condenseur de vapeur
EP0976998A1 (fr) 1998-07-30 2000-02-02 Asea Brown Boveri AG Condenseur de vapeur
EP1126227A1 (fr) 2000-02-09 2001-08-22 ALSTOM POWER (Schweiz) AG Condenseur de vapeur
US6550249B2 (en) 2000-07-11 2003-04-22 Alstom (Switzerland) Ltd Condenser neck between a steam turbine and a condenser
WO2013117730A2 (fr) 2012-02-10 2013-08-15 Alstom Technology Ltd Cycle eau/vapeur et son procédé d'actionnement
EP2264286A3 (fr) * 2009-05-28 2014-05-14 General Electric Company Configuration de basse pression à double débit pour turbine à vapeur

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2576292B2 (ja) * 1991-01-29 1997-01-29 株式会社日立製作所 復水器及びそれを用いた発電プラント
DE4422344A1 (de) * 1994-06-27 1996-01-04 Siemens Ag Kondensator
DE69530047T2 (de) 1994-12-02 2004-01-29 Hitachi Ltd Kondensator und Kraftwerk
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
DE10016080A1 (de) * 2000-03-31 2001-10-04 Alstom Power Nv Kondensator
US6526755B1 (en) * 2001-05-07 2003-03-04 Joseph W. C. Harpster Condensers and their monitoring
US7765628B2 (en) 2006-06-09 2010-08-03 Whirlpool Corporation Steam washing machine operation method having a dual speed spin pre-wash
US7730568B2 (en) 2006-06-09 2010-06-08 Whirlpool Corporation Removal of scale and sludge in a steam generator of a fabric treatment appliance
US7941885B2 (en) 2006-06-09 2011-05-17 Whirlpool Corporation Steam washing machine operation method having dry spin pre-wash
US7681418B2 (en) 2006-08-15 2010-03-23 Whirlpool Corporation Water supply control for a steam generator of a fabric treatment appliance using a temperature sensor
US7665332B2 (en) 2006-08-15 2010-02-23 Whirlpool Corporation Steam fabric treatment appliance with exhaust
US7841219B2 (en) 2006-08-15 2010-11-30 Whirlpool Corporation Fabric treating appliance utilizing steam
US7886392B2 (en) 2006-08-15 2011-02-15 Whirlpool Corporation Method of sanitizing a fabric load with steam in a fabric treatment appliance
US7707859B2 (en) 2006-08-15 2010-05-04 Whirlpool Corporation Water supply control for a steam generator of a fabric treatment appliance
US7753009B2 (en) 2006-10-19 2010-07-13 Whirlpool Corporation Washer with bio prevention cycle
JP2008241211A (ja) * 2007-03-28 2008-10-09 Toshiba Corp 水平流入型復水器およびその運転方法
US8393183B2 (en) 2007-05-07 2013-03-12 Whirlpool Corporation Fabric treatment appliance control panel and associated steam operations
US8037565B2 (en) 2007-08-31 2011-10-18 Whirlpool Corporation Method for detecting abnormality in a fabric treatment appliance having a steam generator
US7690062B2 (en) 2007-08-31 2010-04-06 Whirlpool Corporation Method for cleaning a steam generator
US7918109B2 (en) 2007-08-31 2011-04-05 Whirlpool Corporation Fabric Treatment appliance with steam generator having a variable thermal output
US7966683B2 (en) 2007-08-31 2011-06-28 Whirlpool Corporation Method for operating a steam generator in a fabric treatment appliance
JP6207957B2 (ja) * 2013-10-04 2017-10-04 三菱重工業株式会社 復水器
EP2878907A1 (fr) 2013-11-28 2015-06-03 Alstom Technology Ltd Condenseur intégré
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
CN113513924B (zh) * 2021-07-23 2022-04-01 杭州国能汽轮工程有限公司 一种圆形侧向布置的剪刀形管束凝汽器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1812591A (en) * 1930-11-26 1931-06-30 Worthington Pump & Mach Corp Condenser
US2939685A (en) * 1955-12-14 1960-06-07 Lummus Co Condenser deaerator
CH423819A (de) * 1965-01-15 1966-11-15 Bbc Brown Boveri & Cie Kondensationsanlage für Dampfturbinen-Abdampf
DE1501339A1 (de) * 1966-04-02 1969-12-04 Weser Ag Dampfkondensator

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1578031A (en) * 1921-08-04 1926-03-23 Westinghouse Electric & Mfg Co Condenser
US2848197A (en) * 1955-09-02 1958-08-19 Lummus Co Condenser
US2869833A (en) * 1957-04-03 1959-01-20 Worthington Corp Modular heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1812591A (en) * 1930-11-26 1931-06-30 Worthington Pump & Mach Corp Condenser
US2939685A (en) * 1955-12-14 1960-06-07 Lummus Co Condenser deaerator
CH423819A (de) * 1965-01-15 1966-11-15 Bbc Brown Boveri & Cie Kondensationsanlage für Dampfturbinen-Abdampf
DE1501339A1 (de) * 1966-04-02 1969-12-04 Weser Ag Dampfkondensator

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19523923C2 (de) * 1995-06-30 2003-09-18 Alstom Niederdruck-Dampfturbine
US5779435A (en) * 1995-06-30 1998-07-14 Asea Brown Boveri Ag Low-pressure steam turbine
DE19523923A1 (de) * 1995-06-30 1997-01-02 Abb Management Ag Niederdruck-Dampfturbine
DE19642100A1 (de) * 1996-10-12 1998-04-16 Asea Brown Boveri Dampfkondensator
EP0841527A2 (fr) 1996-10-12 1998-05-13 Asea Brown Boveri AG Condenseur de vapeur
EP0841527A3 (fr) * 1996-10-12 1998-12-02 Asea Brown Boveri AG Condenseur de vapeur
US5941301A (en) * 1996-10-12 1999-08-24 Asea Brown Boveri Ag Steam condenser
DE19642100B4 (de) * 1996-10-12 2011-09-29 Alstom Dampfkondensator
DE19715492A1 (de) * 1997-04-14 1998-10-15 Siemens Ag Dampfturbinenanlage
DE19715492C2 (de) * 1997-04-14 1999-08-12 Siemens Ag Dampfturbinenanlage
EP0957325A1 (fr) 1998-05-14 1999-11-17 Asea Brown Boveri AG Condenseur de vapeur
EP0976998A1 (fr) 1998-07-30 2000-02-02 Asea Brown Boveri AG Condenseur de vapeur
US6360543B2 (en) 2000-02-09 2002-03-26 Alstom (Schweiz) Ag Steam condenser
EP1126227A1 (fr) 2000-02-09 2001-08-22 ALSTOM POWER (Schweiz) AG Condenseur de vapeur
US6550249B2 (en) 2000-07-11 2003-04-22 Alstom (Switzerland) Ltd Condenser neck between a steam turbine and a condenser
EP2264286A3 (fr) * 2009-05-28 2014-05-14 General Electric Company Configuration de basse pression à double débit pour turbine à vapeur
WO2013117730A2 (fr) 2012-02-10 2013-08-15 Alstom Technology Ltd Cycle eau/vapeur et son procédé d'actionnement
US9453428B2 (en) 2012-02-10 2016-09-27 Alstom Technology Ltd Water/steam cycle and method for operating the same

Also Published As

Publication number Publication date
HU900903D0 (en) 1990-05-28
US5018572A (en) 1991-05-28
EP0384200B1 (fr) 1993-09-22
JPH02242088A (ja) 1990-09-26
HUT56919A (en) 1991-10-28
HU212653B (en) 1996-09-30
DE59002779D1 (de) 1993-10-28
JP2930647B2 (ja) 1999-08-03

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