EP0110101A1 - Saturated steam turbine plant - Google Patents

Saturated steam turbine plant Download PDF

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Publication number
EP0110101A1
EP0110101A1 EP83110462A EP83110462A EP0110101A1 EP 0110101 A1 EP0110101 A1 EP 0110101A1 EP 83110462 A EP83110462 A EP 83110462A EP 83110462 A EP83110462 A EP 83110462A EP 0110101 A1 EP0110101 A1 EP 0110101A1
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EP
European Patent Office
Prior art keywords
reheater
saturated steam
pressure
connecting line
low
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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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EP83110462A
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German (de)
French (fr)
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EP0110101B1 (en
Inventor
Peter Dr. von Böckh
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General Electric Switzerland GmbH
ABB Asea Brown Boveri Ltd
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BBC Brown Boveri AG Switzerland
ABB Asea Brown Boveri Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G1/00—Steam superheating characterised by heating method
    • F22G1/005—Steam superheating characterised by heating method the heat being supplied by steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D13/00—Combinations of two or more machines or engines
    • F01D13/02—Working-fluid interconnection of machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/26—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by steam
    • F01K3/262—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by steam by means of heat exchangers
    • F01K3/265—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by steam by means of heat exchangers using live steam for superheating or reheating

Definitions

  • the present invention relates to a saturated steam turbine system according to the preamble of the claim.
  • the steam coming from the high-pressure turbine is dried and then overheated.
  • the steam can then be expanded in the low-pressure turbine until final wetting.
  • the steam is usually dried and superheated in combined water separator reheaters.
  • the reheaters are designed as tube bundle heat exchangers, the steam to be heated flowing around the tubes and being heated by the steam condensing in the tubes.
  • heating is carried out with live steam, while in the case of multi-stage superheating, tap and live steam are used.
  • Reheaters of the horizontal design usually work with 1-2% purge steam, based on the total heating steam consumption.
  • the one to avoid operational cases required safety devices, which can lead to the destruction of the tube bundle, for example, by gushing and / or plug flow, are extensive and complex.
  • the flushing steam requirement is lower, but their space requirement is considerably larger.
  • thermodynamic efficiency is therefore much better than in systems without reheaters.
  • the object of the present invention is to be seen in creating a saturated steam turbine plant in which a better efficiency than with two-stage water separation can be achieved without an intermediate superheater, and in which the intermediate superheater can be arranged in any installation position without any particular effort.
  • the advantage of the arrangement according to the invention can be seen in particular in the shorter line routing between the high-pressure and low-pressure part, and in the small space requirement of the reheater bundles, since their installation and installation downstream of the high-speed water separator mean that the installation position is arbitrary, i.e. according to the space available, and the flow cross-section of the reheater is approximately the same compared to the connecting line. Furthermore, the total pressure loss is reduced by this arrangement, and the acceleration and deceleration phases in the working steam are eliminated. In conventional superheating, about 10%, but in the inventive arrangement of the reheater, only about 5% live steam is required.
  • 1 and 2 1 denotes a high-pressure turbine, the exhaust steam of which is fed via connecting lines 2 to low-pressure turbines 3.
  • two low-pressure turbines 3 are provided, the high-pressure turbine l, the two low-pressure turbines 3 and a generator 4 are connected by a common shaft 5.
  • a high-speed water separator 6 and a reheater bundle 7 are arranged downstream of the high-pressure turbine 1 in the underflow and upstream connecting lines 2, which require little space and whose flow cross section differs only insignificantly from the cross section of the connecting lines.
  • a flap valve 8 is provided between each reheater bundle 7 and the respective low-pressure turbine 3, but it is easily possible to omit the flap valves 8 without causing damage to the low-pressure turbines 3 due to excessive speeds.
  • FIG 3 shows a possible arrangement of the reheater bundle 7 with a trap flap 8 in the connecting line 2 between the low-pressure turbine 3 and the entry of the working steam from the high-speed water separator (not shown).
  • the working steam flows through the superheater tubes 9 arranged in the intermediate superheater 7 in the direction of the arrow in a cross flow the condensate flows off.
  • the intermediate superheaters for example L-shaped or U-shaped, and also spiral-shaped to compensate for the differential expansions that occur.
  • the reheater can be easily adapted to the local conditions.
  • Heater 7 in the connecting lines 2 Due to the arrangement of the intermediate according to the invention Heater 7 in the connecting lines 2, a multi-stage superheating is possible without additional space requirement, and since the reheater 7 forms part of the connecting lines 2, any installation position is possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Abstract

In einer aus einer Hochdruck- (1) mindestens einer Niederdruckturbine (3) und einem Generator (4) bestehenden Sattdampfturbinenanlage, in welcher zwischen der Hochdruck- (1) und der Niederdruckturbine (3) in der Verbindungsleitung (2) ein Hochgeschwindigkeits-Wasserabscheider (6) vorgesehen ist, ist stromabwärts desselben zwischen die Unterström- und Überströmverbindungsleitung (2) ein Zwischenüberhitzer (7) mit geringem Platzbedarf angeordnet. Der Zwischenüberhitzer (7) ist im Kreuzstrom vom Heizdampf geschaltet und weist annähernd denselben Durchflussquerschnitt auf wie die Verbindungsleitung (2), so daß er ein Teil derselben ist.In a saturated steam turbine system consisting of a high-pressure (1) at least one low-pressure turbine (3) and a generator (4), in which a high-speed water separator (2) between the high-pressure (1) and the low-pressure turbine (3) 6) is provided, an intermediate superheater (7) with a small space requirement is arranged downstream thereof between the underflow and overflow connecting line (2). The reheater (7) is connected in cross flow from the heating steam and has approximately the same flow cross-section as the connecting line (2), so that it is part of the same.

Description

Die vorliegende Erfindung betrifft eine Sattdampfturbinenanlage gemäss dem Oberbegriff des Patentanspruches.The present invention relates to a saturated steam turbine system according to the preamble of the claim.

Zur Verbesserung des Wirkungsgrades der Niederdruckturbine in derartigen Anlagen und zur Vermeidung von Erosion-Korrosion wird der aus der Hochdruck-Turbine kommende Dampf getrocknet und anschliessend überhitzt. In der Niederdruck- Turbine kann dann der Dampf bis zum Endnässen entspannt werden. Die Trocknung und Ueberhitzung des Dampfes erfolgt üblicherweise in kombinierten Wasserabscheider-Zwischenüberhitzern. Die Zwischenüberhitzer sind als Rohrbündelwärmeaustauscher ausgebildet, wobei der zu überhitzende Dampf die Rohre umströmt und vom in den Rohren kondensierenden Dampf aufgeheizt wird. Bei einer einstufigen Ueberhitzung erfolgt die Beheizung mit Frischdampf, während bei einer mehrstufigen Ueberhitzung Anzapf- und Frischdampf verwendet wird.In order to improve the efficiency of the low-pressure turbine in such systems and to avoid erosion-corrosion, the steam coming from the high-pressure turbine is dried and then overheated. The steam can then be expanded in the low-pressure turbine until final wetting. The steam is usually dried and superheated in combined water separator reheaters. The reheaters are designed as tube bundle heat exchangers, the steam to be heated flowing around the tubes and being heated by the steam condensing in the tubes. In the case of single-stage superheating, heating is carried out with live steam, while in the case of multi-stage superheating, tap and live steam are used.

Zwischenüberhitzer der horizontalen Bauweise arbeiten üblicherweise mit 1-2 % Spüldampf, bezogen auf den gesamten Heizdampfverbrauch. Die zur Vermeidung von Betriebsfällen erforderlichen Sicherheitseinrichtungen, die beispielsweise durch Schwall- und/oder Pfropfenströmung zur Zerstörung der Rohrbündel führen können, sind umfangsreich und aufwendig. Bei Zwischenüberhitzern der vertikalen Bauweise ist zwar der Spüldampfbedarf geringer, jedoch ist deren Platzbedarf wesentlich grösser.Reheaters of the horizontal design usually work with 1-2% purge steam, based on the total heating steam consumption. The one to avoid operational cases required safety devices, which can lead to the destruction of the tube bundle, for example, by gushing and / or plug flow, are extensive and complex. In the case of reheaters of the vertical design, the flushing steam requirement is lower, but their space requirement is considerably larger.

Zwischenüberhitzer werden zur Optimierung des Gesamtwirkungsgrades eingesetzt. Der thermodynamische Wirkungsgrad ist dadurch wesentlich besser als bei Anlagen ohne Zwischenüberhitzer.Reheaters are used to optimize overall efficiency. The thermodynamic efficiency is therefore much better than in systems without reheaters.

Es ist auch bekanntgeworden, in Verbindung mit Hochgeschwindigkeitsabscheidern eine zweistufige Wasserabscheidung ohne Ueberhitzung vorzunehmen'(B. Andrieu: "Evolution des condenseurs, des postes d'eau et des separateurs de vapeur". AINI Liege, Centrales electriques modernes - 1981).It has also become known to carry out a two-stage water separation without overheating in connection with high-speed separators (B. Andrieu: "Evolution des condenseurs, des postes d'eau et des separateurs de vapeur". AINI Liege, Centrales electriques Moderne - 1981).

Bei der zweistufigen Wasserabscheidung ohne Ueberhitzung treten zwar die bekannten Probleme des Zwischenüberhitzers nicht auf, jedoch wird der Wirkungsgrad der Turbinengruppe verringert. Ausserdem ist eine zusätzliche Mitteldruck-Turbine, sowie erosion-korrosionsfestes Material für die Mittel- und Niederdruckturbinen erforderlich.With the two-stage water separation without overheating, the known problems of the reheater do not occur, but the efficiency of the turbine group is reduced. In addition, an additional medium-pressure turbine and erosion-corrosion-resistant material for the medium and low-pressure turbines are required.

Die Aufgabe der vorliegenden Erfindung ist darin zu sehen, eine Sattdampfturbinenanlage zu schaffen, bei welcher ein besserer Wirkungsgrad als mit zweistufiger Wasserabscheidung ohne Zwischenüberhitzer erzielt werden kann, und bei welcher die Zwischenüberhitzer ohne besonderen Aufwand in beliebiger Einbaulage angeordnet werden können.The object of the present invention is to be seen in creating a saturated steam turbine plant in which a better efficiency than with two-stage water separation can be achieved without an intermediate superheater, and in which the intermediate superheater can be arranged in any installation position without any particular effort.

Die vorgenannte Aufgabe wird erfindungsgemäss durch das Kennzeichen des Patentanspruches gelöst. Weitere vorteilhafte Ausbildungsformen ergeben sich aus den Kennzeichen der abhängigen Unteransprüche.The above object is achieved according to the invention by the characterizing part of the patent claim. Another advantage Adherent forms of training result from the characteristics of the dependent subclaims.

Der Vorteil der erfindungsgemässen Anordnung ist insbesondere in der kürzeren Leitungsführung zwischen Hochdruck-und Niederdruckteil, sowie im geringen Platzbedarf der Zwischenüberhitzerbündel zu erblicken, da durch deren Ausbildung und den Einbau stromabwärts des Hochgeschwindigkeits-Wasserabscheiders die Einbaulage beliebig, d.h. den Platzgegebenheiten entsprechend, erfolgen kann und der Durchflussquerschnitt des Zwischenüberhitzers gegenüber der Verbindungsleitung annähernd gleich ist. Weiterhin wird der Gesamtdruckverlust durch diese Anordnung herabgesetzt, und es entfallen die Beschleunigungs- und Abbremsphasen beim Arbeitsdampf. Bei der klassischen Ueberhitzung werden etwa 10 %, bei der.erfindungsgemässen Anordnung des Zwischenüberhitzers jedoch nur etwa 5 % Frischdampf erforderlich.The advantage of the arrangement according to the invention can be seen in particular in the shorter line routing between the high-pressure and low-pressure part, and in the small space requirement of the reheater bundles, since their installation and installation downstream of the high-speed water separator mean that the installation position is arbitrary, i.e. according to the space available, and the flow cross-section of the reheater is approximately the same compared to the connecting line. Furthermore, the total pressure loss is reduced by this arrangement, and the acceleration and deceleration phases in the working steam are eliminated. In conventional superheating, about 10%, but in the inventive arrangement of the reheater, only about 5% live steam is required.

In der Zeichnung ist ein Ausführungsbeispiel des Erfindungsgegenstandes vereinfacht dargestellt.In the drawing, an embodiment of the subject matter of the invention is shown in simplified form.

Es zeigt:

  • Fig. 1 und 2 eine beispielsweise Anordnung einer erfindungsgemässen Sattdampfturbinenanlage,
  • Fig. 3 eine Detail-Anordnung eines Zwischenüberhitzers in einer Verbindungsleitung.
It shows:
  • 1 and 2 an example arrangement of a saturated steam turbine plant according to the invention,
  • Fig. 3 shows a detailed arrangement of a reheater in a connecting line.

Gemäss den Fig. 1 und 2 ist mit 1 eine Hochdruck-Turbine bezeichnet, deren Abdampf über Verbindungsleitungen 2 Niederdruckturbinen 3 zugeführt wird. Im vorliegenden Fall sind zwei Niederdruckturbinen 3 vorgesehen, wobei die Hochdruck- turbine l, die beiden Niederdruckturbinen 3 und ein Generator 4 durch eine gemeinsame Welle 5 verbunden sind. In den Unterström- und Oberström-Verbindungsleitungen 2 ist jeweils stromabwärts der Hochdruckturbine 1 ein Hochgeschwindigkeits-Wasserabscheider 6 und ein Zwischenüberhitzerbündel 7 angeordnet, das einen geringen Platzbedarf erfordert und dessen Durchflussquerschnitt nur unwesentlich von dem Querschnitt der Verbindungsleitungen abweicht. Zwischen jedem Zwischenüberhitzerbündel 7 und der jeweiligen Niederdruck- turbine 3 ist je eine Abfangklappe 8 vorgesehen, jedoch ist es ohne weiteres möglich, die Abfangklappen 8 wegzulassen, ohne dass Schäden durch Ueberdrehzahlen an den Niederdruckturbinen 3 entstehen.1 and 2, 1 denotes a high-pressure turbine, the exhaust steam of which is fed via connecting lines 2 to low-pressure turbines 3. In the present case, two low-pressure turbines 3 are provided, the high-pressure turbine l, the two low-pressure turbines 3 and a generator 4 are connected by a common shaft 5. A high-speed water separator 6 and a reheater bundle 7 are arranged downstream of the high-pressure turbine 1 in the underflow and upstream connecting lines 2, which require little space and whose flow cross section differs only insignificantly from the cross section of the connecting lines. A flap valve 8 is provided between each reheater bundle 7 and the respective low-pressure turbine 3, but it is easily possible to omit the flap valves 8 without causing damage to the low-pressure turbines 3 due to excessive speeds.

In der Fig. 3 ist eine mögliche Anordnung des Zwischenüberhitzerbündels.7 mit Abfangklappe 8 in der Verbindungsleitung 2 zwischen der Niederdruckturbine 3 und dem Eintritt des Arbeitsdampfes vom Hochgeschwindigkeits-Wasserabscheider (nicht dargestellt) gezeigt. Der Arbeitsdampf durchströmt.in Pfeilrichtung im Kreuzstrom die im Zwischenüberhitzer 7 angeordneten Ueberhitzerrohre 9. Durch einen Stutzen 10 tritt Heizdampf in den Zwischenüberhitzer 7 ein, umströmt die Ueberhitzerrohre 9, erwärmt den die Ueberhitzerrohre durchströmenden Arbeitsdampf und kondensiert an den Ueberhitzerrohren 9. Durch einen Austrittsstutzen 11 fliesst das Kondensat ab.3 shows a possible arrangement of the reheater bundle 7 with a trap flap 8 in the connecting line 2 between the low-pressure turbine 3 and the entry of the working steam from the high-speed water separator (not shown). The working steam flows through the superheater tubes 9 arranged in the intermediate superheater 7 in the direction of the arrow in a cross flow the condensate flows off.

Es ist auch möglich, zur Kompensation der auftretenden Differenzdehnungen die Zwischenüberhitzer beispielsweise L- oder U-förmig, sowie spiralförmig auszubilden. Dadurch können die Zwischenüberhitzer auf einfache Weise den örtlichen Gegebenheiten angepasst werden.It is also possible to make the intermediate superheaters, for example L-shaped or U-shaped, and also spiral-shaped to compensate for the differential expansions that occur. As a result, the reheater can be easily adapted to the local conditions.

Durch die erfindungsgemässe Anordnung der Zwischenüberhitzer 7 in den Verbindungsleitungen 2 ist eine mehrstufige Ueberhitzung ohne zusätzlichen Platzbedarf möglich, und da der Zwischenüberhitzer 7 einen Teil der Verbindungsleitungen 2 bildet, ist eine beliebige Einbaulage möglich.Due to the arrangement of the intermediate according to the invention Heater 7 in the connecting lines 2, a multi-stage superheating is possible without additional space requirement, and since the reheater 7 forms part of the connecting lines 2, any installation position is possible.

Claims (3)

1. Sattdampfturbinenanlage, im wesentlichen bestehend aus einer Hochdruck-Turbine (1), mindestens einer Niederdruck-Turbine (3) und einem Generator (4), wobei in der Verbindungsleitung (2) zwischen der Hochdruck- Turbine (1) und der Niederdruck-Turbine (3) mindestens ein Hochgeschwindigkeits-Wasserabscheider (6) vorgesehen ist, dadurch gekennzeichnet, dass stromabwärts des Hochgeschwindigkeits-Wasserabscheiders (6) zwischen der Unterström- und Ueberström-Verbindungsleitung (2) mindestens ein im Kreuzstrom von Heizdampf angeströmter Zwischenüberhitzer mit geringem Platzbedarf (7) angeordnet ist.1. saturated steam turbine plant, consisting essentially of a high-pressure turbine (1), at least one low-pressure turbine (3) and a generator (4), wherein in the connecting line (2) between the high-pressure turbine (1) and the low-pressure Turbine (3) at least one high-speed water separator (6) is provided, characterized in that downstream of the high-speed water separator (6) between the underflow and overflow connecting line (2) at least one reheater flowed in by cross flow of heating steam with a small space requirement ( 7) is arranged. 2. Sattdampfturbinenanlage nach Anspruch 1, dadurch gekennzeichnet, dass der Zwischenüberhitzer (7) annähernd denselben Durchflussquerschnitt aufweist wie die Verbindungsleitung (2).2. saturated steam turbine plant according to claim 1, characterized in that the reheater (7) has approximately the same flow cross-section as the connecting line (2). 3. Sattdampfturbinenanlage nach Anspruch 2, dadurch gekennzeichnet, dass der Zwischenüberhitzer (7) ein Teil der Verbindungsleitung (2) ist.3. saturated steam turbine plant according to claim 2, characterized in that the reheater (7) is part of the connecting line (2).
EP83110462A 1982-11-24 1983-10-20 Saturated steam turbine plant Expired EP0110101B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH684582 1982-11-24
CH6845/82 1982-11-24

Publications (2)

Publication Number Publication Date
EP0110101A1 true EP0110101A1 (en) 1984-06-13
EP0110101B1 EP0110101B1 (en) 1987-09-02

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ID=4315923

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EP83110462A Expired EP0110101B1 (en) 1982-11-24 1983-10-20 Saturated steam turbine plant

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US (1) US4589258A (en)
EP (1) EP0110101B1 (en)
JP (1) JPS59105907A (en)
CA (1) CA1235301A (en)
DE (1) DE3373322D1 (en)
ZA (1) ZA838579B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2860362A1 (en) 2013-10-11 2015-04-15 König, Harald Desmodromic valve control

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US5199264A (en) * 1991-02-11 1993-04-06 Westinghouse Electric Corp. Steam operated turbine-generator installations
ATE261567T1 (en) * 1997-01-10 2004-03-15 Framatome Anp Gmbh METHOD AND DEVICE FOR SUPERHEATING STEAM
JP4636906B2 (en) * 2004-03-18 2011-02-23 日立Ｇｅニュークリア・エナジー株式会社 Nuclear power generation system
JP6081544B1 (en) * 2015-08-19 2017-02-15 三菱日立パワーシステムズ株式会社 Steam turbine plant
JP6538989B2 (en) 2016-01-20 2019-07-10 クリメオン エービー Heat recovery system and method of converting heat to electrical energy using a heat recovery system
US11506088B2 (en) * 2018-06-22 2022-11-22 Gas Technology Institute Hydro-turbine drive methods and systems for application for various rotary machineries

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BE360228A (en)
GB234165A (en) * 1924-02-15 1925-05-15 English Electric Co Ltd Improvements in and relating to the utilisation of steam power in steam turbines
CH458398A (en) 1965-05-26 1968-06-30 Ass Elect Ind Steam turbine plant
DE1551209A1 (en) 1966-06-11 1970-03-19 Siemens Ag Turbine unit with steam-heated intermediate superheating
DE2312725A1 (en) 1973-03-14 1974-09-26 Kraftwerk Union Ag Satd. steam turbine interstage moisture separator and heaters - for PWR and BWR power plants inhibiting line erosion

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JPS5578110A (en) * 1978-12-08 1980-06-12 Toshiba Corp Method of draining steam of turbine plant
JPS5652506A (en) * 1979-10-08 1981-05-11 Mitsubishi Heavy Ind Ltd Steam turbine plant

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
BE360228A (en)
GB234165A (en) * 1924-02-15 1925-05-15 English Electric Co Ltd Improvements in and relating to the utilisation of steam power in steam turbines
CH458398A (en) 1965-05-26 1968-06-30 Ass Elect Ind Steam turbine plant
DE1551209A1 (en) 1966-06-11 1970-03-19 Siemens Ag Turbine unit with steam-heated intermediate superheating
DE2312725A1 (en) 1973-03-14 1974-09-26 Kraftwerk Union Ag Satd. steam turbine interstage moisture separator and heaters - for PWR and BWR power plants inhibiting line erosion

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2860362A1 (en) 2013-10-11 2015-04-15 König, Harald Desmodromic valve control

Also Published As

Publication number Publication date
ZA838579B (en) 1984-07-25
US4589258A (en) 1986-05-20
CA1235301A (en) 1988-04-19
EP0110101B1 (en) 1987-09-02
DE3373322D1 (en) 1987-10-08
JPS59105907A (en) 1984-06-19

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