EP0619466A2 - Condenseur de vapeur - Google Patents
Condenseur de vapeur Download PDFInfo
- Publication number
- EP0619466A2 EP0619466A2 EP94103311A EP94103311A EP0619466A2 EP 0619466 A2 EP0619466 A2 EP 0619466A2 EP 94103311 A EP94103311 A EP 94103311A EP 94103311 A EP94103311 A EP 94103311A EP 0619466 A2 EP0619466 A2 EP 0619466A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- tubes
- cooler
- steam
- bundle
- compartments
- 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
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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 next to one another 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, which communicates with the pre-air cooler and a downstream suction channel (header) via a double row of evenly distributed cooler inlet orifices or 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.
- this is achieved in that only one cooler is provided, to which the suction channel is directly connected, and that the flow cross-sections of the orifices in the compartments are dimensioned such that the local, non-condensable mass flow is sucked off at the locally available pressure difference.
- 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 upstream cavity 19 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)
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 true EP0619466A2 (fr) | 1994-10-12 |
EP0619466A3 EP0619466A3 (fr) | 1995-12-13 |
EP0619466B1 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) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999050610A1 (fr) | 1998-03-27 | 1999-10-07 | Siemens Aktiengesellschaft | Tuyau echangeur thermique, son procede de production et un condensateur |
Families Citing this family (9)
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 |
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 |
CN101031767B (zh) * | 2006-03-27 | 2012-01-25 | 布哈拉特强电有限公司 | 两通路蒸汽冷凝器 |
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 |
US10502492B2 (en) * | 2014-01-23 | 2019-12-10 | Mitsubishi Hitachi Power Systems, Ltd. | Condenser for condensing steam from a steam turbine |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH423819A (de) * | 1965-01-15 | 1966-11-15 | Bbc Brown Boveri & Cie | Kondensationsanlage für Dampfturbinen-Abdampf |
DE1948073A1 (de) * | 1969-08-29 | 1971-03-25 | Bbc Brown Boveri & Cie | Verfahren zum Kondensieren von Wasserdampf und Anlage zur Durchfuehrung dieses Verfahrens |
EP0325758A1 (fr) * | 1988-01-22 | 1989-08-02 | Asea Brown Boveri Ag | Condenseur de vapeur |
Family Cites Families (4)
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 |
JPS5914682B2 (ja) * | 1980-09-29 | 1984-04-05 | 株式会社日立製作所 | 給水加熱器 |
-
1993
- 1993-04-05 DE DE4311118A patent/DE4311118A1/de not_active Withdrawn
-
1994
- 1994-03-04 EP EP94103311A patent/EP0619466B1/fr not_active Expired - Lifetime
- 1994-03-04 DE DE59404596T patent/DE59404596D1/de not_active Expired - Fee Related
- 1994-04-05 US US08/222,918 patent/US5465784A/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH423819A (de) * | 1965-01-15 | 1966-11-15 | Bbc Brown Boveri & Cie | Kondensationsanlage für Dampfturbinen-Abdampf |
DE1948073A1 (de) * | 1969-08-29 | 1971-03-25 | Bbc Brown Boveri & Cie | Verfahren zum Kondensieren von Wasserdampf und Anlage zur Durchfuehrung dieses Verfahrens |
EP0325758A1 (fr) * | 1988-01-22 | 1989-08-02 | Asea Brown Boveri Ag | Condenseur de vapeur |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999050610A1 (fr) | 1998-03-27 | 1999-10-07 | Siemens Aktiengesellschaft | Tuyau echangeur thermique, son procede de production et un condensateur |
Also Published As
Publication number | Publication date |
---|---|
EP0619466B1 (fr) | 1997-11-19 |
DE4311118A1 (de) | 1994-10-06 |
EP0619466A3 (fr) | 1995-12-13 |
US5465784A (en) | 1995-11-14 |
DE59404596D1 (de) | 1998-01-02 |
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