EP0840837B1 - Process for running a gas and steam turbine plant and plant run by this process - Google Patents
Process for running a gas and steam turbine plant and plant run by this process Download PDFInfo
- Publication number
- EP0840837B1 EP0840837B1 EP96922762A EP96922762A EP0840837B1 EP 0840837 B1 EP0840837 B1 EP 0840837B1 EP 96922762 A EP96922762 A EP 96922762A EP 96922762 A EP96922762 A EP 96922762A EP 0840837 B1 EP0840837 B1 EP 0840837B1
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- EP
- European Patent Office
- Prior art keywords
- steam
- pressure
- turbine
- preheater
- heat
- 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.)
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Classifications
-
- 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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
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- 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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
Definitions
- the invention relates to a gas and steam turbine plant with one of the gas turbines connected downstream of the exhaust gas Heat recovery steam generator, its high-pressure preheater in the water-steam cycle the one having a low pressure part Steam turbine is switched. It continues to focus on one Plant operated according to this procedure.
- the water-steam cycle includes several, e.g. two or three, pressure levels, each pressure level a preheater, an evaporator and a super heater having.
- the invention is therefore based on the object of a gas and Steam turbine plant and a suitable one for its operation To further develop methods such that by a further increase the use of the heat content in the exhaust gas of the gas turbine an increase in system efficiency is achieved.
- this problem is solved by a heat exchanger arranged outside the heat recovery steam generator, its primary side input to the output and its primary-side outlet to the inlet of the high-pressure preheater are connected, and the secondary side to a overflow line leading into the high pressure part of the steam turbine is switched.
- the heat exchanger is on the primary side a circulation pump and a control valve.
- a controller block serves to approximate the temperature of the via the heat exchanger High pressure preheater recirculated feed water to the temperature of the feed water fed directly to the high-pressure preheater with the aim that the temperatures at the mixing point of the high-pressure preheater are at least approximately the same.
- a first temperature sensor with the controller module Detection of the temperature of the secondary side from the heat exchanger outflowing feed water connected.
- a second with Temperature sensor connected to the controller module is used for detection the temperature of the high pressure preheater Feed water.
- a particularly effective adaptation of the heating surface of the high pressure preheater the temperature profile of the exhaust gas from the This turns the gas turbine inside the heat recovery steam generator achieved that the high-pressure preheater has two stages is. Therefore, in a further advantageous embodiment the high pressure preheater and a first high pressure preheater second high-pressure preheater downstream of feed water, the one in the waste heat steam generator on the exhaust side before the first High pressure preheater is arranged.
- This principle can be built up from three pressure levels Water-steam cycle can be further developed in that to that existing in a three-pressure ZÜ process Reheater a connected to this on the feed water side Medium pressure superheater is provided in the heat recovery steam generator arranged on the exhaust gas side before the reheater is. Furthermore, in order to further develop this principle Heat recovery steam generator arranged low pressure superheater provided be the output side with the secondary side Input of the heat exchanger is connected.
- the stated task is thereby solved that the steam turbine incoming low pressure steam by indirect heat exchange with a high pressure preheater withdrawn partial flow of preheated feed water overheated becomes.
- the cooled partial flow becomes the feed water to be preheated preferably mixed again at the inlet of the high pressure preheater, wherein a temperature approximation of the partial flow to the feed water to be preheated by adjusting the partial flow he follows.
- the advantages achieved with the invention are in particular in that on the one hand by overheating the low pressure steam through indirect heat exchange outside the heat recovery steam generator with feed water preheated in the high-pressure preheater Heat from the exhaust gas from the gas turbine for overheating can be used, and that on the other hand due to the an additional degree of freedom compared to indirect heat exchange a direct heat exchange with the exhaust gas is provided becomes.
- This additional degree of freedom enables heat transfer particularly favorable to the operating conditions present state of the low pressure steam from the steam turbine be adjusted. This makes it a particularly affordable one Exploitation of the heat content in the exhaust gas from the gas turbine too possible with changing load conditions.
- the invention also enables an increase the generator clamping power of the steam turbine.
- FIG. 1 An embodiment of the invention is based on a Drawing explained in more detail.
- the figure shows schematically a gas and steam turbine system with a separate heat exchanger for heating low pressure steam.
- the gas and steam turbine plant comprises one Gas turbine 2 and a steam turbine 4 and one from the hot Exhaust gas AG from the gas turbine 2 flows through the heat recovery steam generator 6.
- the steam turbine 4 comprises a high pressure part 4a and a medium pressure part 4b and a low pressure part 4c.
- the waste heat steam generator 6 is used to generate steam, wherein whose heating surfaces in a water-steam cycle 8 Steam turbine 4 are switched.
- the heat recovery steam generator 6 has a condensate line 10 connected condensate preheater 12 on the on the input side via a condensate pump 14 with one of the Steam turbine 4 downstream capacitor 16 is connected.
- the condensate preheater 12 is on the outlet side via a circulation pump 18 connected to its entrance. He is outgoing also via a feed line 20 with a feed water tank 22 connected.
- the feed water tank 22 is on the output side via a Feed water line 24, into which a pump 26 is connected, connected to a low pressure drum 28.
- a Feed water line 24 To the low pressure drum 28 is an evaporator via a circulation pump 30 connected.
- the low-pressure drum 28 is also on the steam side a low pressure superheater 34 connected via a Steam line 36 to an overflow line 38 from the medium pressure part 4b connected to the low pressure part 4c of the steam turbine 4 is.
- the low pressure drum 28 and the low pressure evaporator 32 together with the low pressure superheater 34 and the low pressure part 4c a low pressure stage of the water-steam cycle 8.
- the feed water tank 22 is also on the output side a feed water line 40 into which a pump 42 is connected is connected to a first high-pressure preheater 44 which via a connecting line 46 to the input of a second High pressure preheater 48 is connected.
- a medium pressure drum 52 via a line 50 connected, to which in turn via a circulation pump 54 Medium pressure evaporator 56 is connected.
- the medium pressure drum 52 is on the steam side with a medium pressure superheater 56 connected, the output side with the input of a reheater 58 is connected.
- the reheater 58 is on the input side of the high pressure part 4a and on the output side connected to the medium pressure part 4b of the steam turbine 4.
- the medium pressure drum 52 and the medium pressure evaporator 56 as well as the medium pressure superheater 57 together with the Intermediate superheater 58 and the medium pressure part 4b of the steam turbine 4 a medium pressure stage of the water-steam cycle 8th.
- the second high-pressure preheater 48 is on the output side via a Connection line 60 and a valve 62 with a high pressure drum 64 connected to the via a circulation pump 66 High pressure evaporator 68 is connected.
- the high pressure drum 64 is on the steam side via a high-pressure superheater 70 the high pressure part 4a of the steam turbine 4 connected.
- the High pressure preheaters 44, 48 and the high pressure drum 64 as well the high pressure evaporator 68 and the high pressure superheater 70 together with the high pressure part 4a of the steam turbine 4 a high-pressure stage of the water-steam cycle 8.
- a heat exchanger 72 switched. Is primary the heat exchanger 72 on the input side via a line 74 the line 60 connected and thus with the output of the second high pressure preheater 48 connected.
- the primary side Output of the heat exchanger 72 is via a line 76, in a pump 78 and a control valve 80 are connected with connected to the input of the second high pressure preheater 48.
- the line 76 opens at a mixing point 82 in the the two high pressure preheaters 44 and 48 connecting line 46.
- the condensate preheater becomes 12 via the pump 14 and the condensate line 10 capacitor K supplied from the capacitor 16. It can all or part of the condensate preheater 12 can be bypassed.
- the condensate K is warmed up in the condensate preheater 12 and at least partially via the circulation pump 18 circulated.
- the warmed condensate K is on the line 20 led into the feed water tank 22, where in a manner not shown a warming up of the Feed water takes place by means of bleed steam from the steam turbine 4.
- the heated feed water S is the one hand Low pressure drum 28 and on the other hand via the first high pressure preheater 44 of the medium pressure drum 52 and the second high pressure preheater 48 fed to the high pressure drum 64.
- the feed water S fed to the low pressure stage is evaporated at low pressure in the low-pressure evaporator 32, the one separated in the low pressure drum 28 Low pressure steam ND supplied to the low pressure superheater 34 becomes.
- the overheated low pressure steam ND is there before Heat exchanger 72 led into the overflow line 38.
- the feed water fed into the medium pressure drum 52 S evaporated in the medium pressure evaporator 56.
- the Indian Medium pressure drum 52 separated, under medium pressure Standing steam is passed over the medium pressure superheater 57 and as superheated medium pressure steam MD the medium pressure part 4b of the steam turbine 4 supplied.
- second high pressure preheater or economizer 48 preheated Feed water S in the high pressure evaporator 68 under high pressure evaporates, the one separated in the high pressure drum 64
- High pressure steam HD in the high pressure superheater 70 overheated and in overheated state in the high pressure part 4a of the steam turbine 4 is performed.
- the steam released in the high pressure part 4a becomes overheated again in reheater 58 and in superheated Condition together with that overheated in the medium pressure superheater 56
- Medium pressure steam MD the medium pressure part 4b of the steam turbine 4 fed.
- the steam in the medium-pressure part 4b of the steam turbine 4, which is under low pressure, is passed through the overflow line 38 and overheated in the heat exchanger 72 by indirect heat exchange with a partial flow t S of the feed water S preheated in the high-pressure preheater 48.
- the steam flowing out of the medium-pressure part 4b is mixed with the low-pressure steam ND overheated in the low-pressure superheater 34 before the heat exchanger 72.
- the low-pressure steam ND overheated in the heat exchanger 72 is expanded in the low-pressure part 4c of the steam turbine 4 and fed to the condenser 16 for condensation.
- the amount of the partial flow t S of the feed water S preheated in the second high-pressure preheater 48 supplied to the heat exchanger 72 per unit of time is set by means of the control valve 80.
- the setting is such that the temperature T 1 of the partial flow t S and the temperature T 2 of the feed water S to be preheated at the mixing point 82 are approximated to one another, preferably the same.
- a controller module 84 is connected to the control valve 80 via a control line 85.
- the controller module 84 is also connected via a control line 86 to a first temperature sensor 87 for detecting the temperature T 1 and via a control line 88 to a second temperature sensor. 89 connected to the detection of the temperature T 2 .
- the clamping power which can be drawn from a (not shown) steam turbine generator increases by 1.3% to 2%. If the entire low-pressure steam quantity is correspondingly overheated in a two-pressure process, the increase in steam turbine output which is achieved in this way is more than 2.6%.
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- Combustion & Propulsion (AREA)
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Description
Die Erfindung bezieht sich auf eine Gas- und Dampfturbinenanlage mit einem der Gasturbine abgasseitig nachgeschalteten Abhitzedampferzeuger, dessen Hochdruckvorwärmer in den Wasser-Dampf-Kreislauf der einen Niederdruckteil aufweisenden Dampfturbine geschaltet ist. Sie richtet sich weiter auf eine nach diesem Verfahren betriebene Anlage.The invention relates to a gas and steam turbine plant with one of the gas turbines connected downstream of the exhaust gas Heat recovery steam generator, its high-pressure preheater in the water-steam cycle the one having a low pressure part Steam turbine is switched. It continues to focus on one Plant operated according to this procedure.
Bei einer Gas- und Dampfturbinenanlage wird die im entspannten Arbeitsmittel aus der Gasturbine enthaltene Wärme zur Erzeugung von Dampf für die Dampfturbine genutzt. Die Wärmeübertragung erfolgt mittels einer Anzahl von Heizflächen, die in Form von Rohren oder Rohrbündeln in einem der Gasturbine abgasseitig nachgeschalteten Abhitzedampferzeuger angeordnet sind. Diese wiederum sind in den Wasser-Dampf-Kreislauf der Dampfturbine geschaltet. Der Wasser-Dampf-Kreislauf umfaßt mehrere, z.B. zwei oder drei, Druckstufen, wobei jede Druckstufe einen Vorwärmer, einen Verdampfer und einen Überhitzer aufweist.In a gas and steam turbine plant, the is relaxed Work equipment contained heat from the gas turbine for generation used by steam for the steam turbine. The heat transfer takes place by means of a number of heating surfaces which in the form of tubes or tube bundles in one of the gas turbines Waste steam generator arranged downstream on the exhaust gas side are. These in turn are in the water-steam cycle Steam turbine switched. The water-steam cycle includes several, e.g. two or three, pressure levels, each pressure level a preheater, an evaporator and a super heater having.
Um bei der Wärmeübertragung einen möglichst hohen Wirkungsgrad der Anlage zu erreichen, ist die Anordnung der Heizflächen innerhalb des Abhitzedampferzeugers an den Temperaturverlauf des Abgases angepaßt. Bei einem Dreidruck-Prozeß mit Zwischenüberhitzung, dem sogenannten Dreidruck-ZÖ-Prozeß, wird dabei bei vorgegebener Gasturbinenleistung eine besonders hohe Dampfturbinenleistung und damit ein besonders hoher Gesamtwirkungsgrad der Anlage erreicht. Eine nach dem Dreidruck-ZÜ-Prozeß arbeitende Gas- und Dampfturbinenanlage ist aus der EP 0 436 536 B1 bekannt. Aber auch bei dieser bekannten Anlage ist der Gesamtwirkungsgrad auf etwa 55% begrenzt. To ensure the highest possible efficiency in heat transfer to reach the system is the arrangement of the heating surfaces within the heat recovery steam generator to the temperature curve adapted to the exhaust gas. With a three-pressure process with Reheating, the so-called three-pressure ZÖ process, becomes a special one with a given gas turbine output high steam turbine output and thus a particularly high one Overall system efficiency achieved. One after the three-pressure ZÜ process working gas and steam turbine plant is known from EP 0 436 536 B1. But also with this well-known Plant, the overall efficiency is limited to around 55%.
Der Erfindung liegt daher die Aufgabe zugrunde, eine Gas- und Dampfturbinenanlage sowie ein zu deren Betrieb geeignetes Verfahren derart weiterzubilden, daß durch eine weitere Steigerung der Nutzung des Wärmeinhalts im Abgas der Gasturbine eine Steigerung des Anlagenwirkungsgrades erzielt wird.The invention is therefore based on the object of a gas and Steam turbine plant and a suitable one for its operation To further develop methods such that by a further increase the use of the heat content in the exhaust gas of the gas turbine an increase in system efficiency is achieved.
Bezüglich der Anlage wird diese Aufgabe gelöst durch einen außerhalb des Abhitzedampferzeugers angeordneten Wärmetauscher, dessen primärseitiger Eingang an den Ausgang und dessen primarseitiger Ausgang an den Eingang des Hochdruck-vorwärmers angeschlossen sind, und der sekundärseitig an eine in den Hochdruckteil der Dampfturbine mündende Überströmleitung geschaltet ist.With regard to the system, this problem is solved by a heat exchanger arranged outside the heat recovery steam generator, its primary side input to the output and its primary-side outlet to the inlet of the high-pressure preheater are connected, and the secondary side to a overflow line leading into the high pressure part of the steam turbine is switched.
In zweckmäßiger Weiterbildung sind dem Wärmetauscher primärseitig eine Umwälzpumpe und ein Regelventil nachgeschaltet.In an expedient development, the heat exchanger is on the primary side a circulation pump and a control valve.
Zur Einstellung der Menge von dem Wärmetauscher primärseitig pro Zeiteinheit zugeführtem Speisewasser ist zweckmäßigerweise ein Reglerbaustein vorgesehen. Der Reglerbaustein dient zur Annäherung der Temperatur des über den Wärmetauscher zum Hochdruckvorwärmer zurückgeführten Speisewassers an die Temperatur des dem Hochdruckvorwärmer direkt zugeführten Speisewassers mit dem Ziel, daß die Temperaturen an der Mischstelle des Hochdruckvorwärmers mindestens annähernd gleich sind. Dazu ist mit dem Reglerbaustein ein erster Temperatursensor zur Erfassung der Temperatur des aus dem Wärmetauscher sekundärseitig abströmenden Speisewassers verbunden. Ein zweiter mit dem Reglerbaustein verbundener Temperatursensor dient zur Erfassung der Temperatur des dem Hochdruckvorwärmer zugeführten Speisewassers.To adjust the amount of the heat exchanger on the primary side feed water supplied per unit of time is expedient a controller block is provided. The controller block serves to approximate the temperature of the via the heat exchanger High pressure preheater recirculated feed water to the temperature of the feed water fed directly to the high-pressure preheater with the aim that the temperatures at the mixing point of the high-pressure preheater are at least approximately the same. To is a first temperature sensor with the controller module Detection of the temperature of the secondary side from the heat exchanger outflowing feed water connected. A second with Temperature sensor connected to the controller module is used for detection the temperature of the high pressure preheater Feed water.
Eine besonders effektive Anpassung der Heizfläche des Hochdruckvorwärmers an den Temperaturverlauf des Abgases aus der Gasturbine innerhalb des Abhitzedampferzeugers wird dadurch erreicht, daß der Hochdruckvorwärmer zweistufig ausgebildet ist. Daher ist in einer weiteren vorteilhaften Ausgestaltung der Hochdruckvorwärmer ein einem ersten Hochdruckvorwärmer speisewasserseitig nachgeschalteter zweiter Hochdruckvorwärmer, der im Abhitzedampferzeuger abgasseitig vor dem ersten Hochdruckvorwärmer angeordnet ist.A particularly effective adaptation of the heating surface of the high pressure preheater the temperature profile of the exhaust gas from the This turns the gas turbine inside the heat recovery steam generator achieved that the high-pressure preheater has two stages is. Therefore, in a further advantageous embodiment the high pressure preheater and a first high pressure preheater second high-pressure preheater downstream of feed water, the one in the waste heat steam generator on the exhaust side before the first High pressure preheater is arranged.
Dieses Prinzip kann bei einm aus drei Druckstufen aufgebauten Wasser-Dampf-Kreislauf dadurch weitergebildet werden, daß zusätzlich zu dem bei einem Dreidruck-ZÜ-Prozeß vorhandenen Zwischenüberhitzer ein mit diesem speisewasserseitig verbundener Mitteldruck-Überhitzer vorgesehen ist, der im Abhitzedampferzeuger abgasseitig vor dem Zwischenüberhitzer angeordnet ist. Ferner kann zur Weiterbildung dieses Prinzips ein im Abhitzedampferzeuger angeordneter Niederdruck-Überhitzer vorgesehen sein, der ausgangsseitig mit dem sekundärseitigen Eingang des Wärmetauschers verbunden ist.This principle can be built up from three pressure levels Water-steam cycle can be further developed in that to that existing in a three-pressure ZÜ process Reheater a connected to this on the feed water side Medium pressure superheater is provided in the heat recovery steam generator arranged on the exhaust gas side before the reheater is. Furthermore, in order to further develop this principle Heat recovery steam generator arranged low pressure superheater provided be the output side with the secondary side Input of the heat exchanger is connected.
Bezüglich des Verfahrens wird die genannte Aufgabe dadurch gelöst, daß der Dampfturbine zuströmender Niederdruckdampf durch indirekten Wärmetausch mit einem dem Hochdruckvorwärmer entnommenen Teilstrom vorgewärmten Speisewassers überhitzt wird.With regard to the method, the stated task is thereby solved that the steam turbine incoming low pressure steam by indirect heat exchange with a high pressure preheater withdrawn partial flow of preheated feed water overheated becomes.
Der abgekühlte Teilstrom wird dem vorzuwärmenden Speisewasser vorzugsweise am Eingang des Hochdruckvorwärmers wieder zugemischt, wobei eine Temperaturannäherung des Teilstroms an das vorzuwärmende Speisewasser durch Einstellen des Teilstroms erfolgt.The cooled partial flow becomes the feed water to be preheated preferably mixed again at the inlet of the high pressure preheater, wherein a temperature approximation of the partial flow to the feed water to be preheated by adjusting the partial flow he follows.
Bei einem aus drei Druckstufen aufgebauten Wasser-Dampf-Kreislauf wird im Abhitzdampferzeuger überhitzter Niederdruckdampf weiter überhitzt, indem dieser dem durch indirekten Wärmetausch zu überhitzenden Niederdruckdampf zugemischt wird.With a water-steam cycle built up from three pressure levels becomes superheated low pressure steam in the heat recovery steam generator further overheated by the indirect Heat exchange admixed to superheating low pressure steam becomes.
Die mit der Erfindung erzielten Vorteile bestehen insbesondere darin, daß einerseits durch die Überhitzung des Niederdruckdampfs durch indirekten Wärmetausch außerhalb des Abhitzedampferzeugers mit im Hochdruckvorwärmer vorgewärmtem Speisewasser Wärme aus dem Abgas der Gasturbine zur Überhitzung herangezogen werden kann, und daß andererseits aufgrund des indirekten Wärmetauschs ein zusätzlicher Freiheitsgrad gegenüber einem direkten Wärmetausch mit dem Abgas bereitgestellt wird. Durch diesen zusätzlichen Freiheitsgrad kann der Wärmetransfer besonders günstig an den jeweils betriebsbedingt vorliegenden Zustand des Niederdruckdampfes aus der Dampfturbine angepaßt werden. Dadurch ist eine besonders günstige Ausnutzung des Wärmeinhalts im Abgas aus der Gasturbine auch bei wechselnden Lastzuständen möglich. Zusätzlich zu der somit erreichbaren Wirkungsgradsteigerung der Gas- und Dampfturbinenanlage ermöglicht die Erfindung aber auch eine Steigerung der Generator-Klemmleistung der Dampfturbine.The advantages achieved with the invention are in particular in that on the one hand by overheating the low pressure steam through indirect heat exchange outside the heat recovery steam generator with feed water preheated in the high-pressure preheater Heat from the exhaust gas from the gas turbine for overheating can be used, and that on the other hand due to the an additional degree of freedom compared to indirect heat exchange a direct heat exchange with the exhaust gas is provided becomes. This additional degree of freedom enables heat transfer particularly favorable to the operating conditions present state of the low pressure steam from the steam turbine be adjusted. This makes it a particularly affordable one Exploitation of the heat content in the exhaust gas from the gas turbine too possible with changing load conditions. In addition to that achievable increase in efficiency of the gas and steam turbine plant the invention also enables an increase the generator clamping power of the steam turbine.
Ein Ausführungsbeispiel der Erfindung wird anhand einer Zeichnung näher erläutert. Darin zeigt die Figur schematisch eine Gas- und Dampfturbinenanlage mit einem separaten Wärmetauscher zur Erhitzung von Niederdruckdampf.An embodiment of the invention is based on a Drawing explained in more detail. The figure shows schematically a gas and steam turbine system with a separate heat exchanger for heating low pressure steam.
Die Gas- und Dampfturbinenanlage gemäß der Figur umfaßt eine
Gasturbine 2 und eine Dampfturbine 4 sowie einen vom heißen
Abgas AG aus der Gasturbine 2 durchströmten Abhitzedampferzeuger
6. Die Dampfturbine 4 umfaßt einen Hochdruckteil 4a
und einen Mitteldruckteil 4b sowie einen Niederdruckteil 4c.
Der Abhitzedampferzeuger 6 dient zur Dampferzeugung, wobei
dessen Heizflächen in einen Wasser-Dampf-Kreislauf 8 der
Dampfturbine 4 geschaltet sind.The gas and steam turbine plant according to the figure comprises one
Gas turbine 2 and a
Dazu weist der Abhitzedampferzeuger 6 einen an eine Kondensatleitung
10 angeschlossenen Kondensatvorwärmer 12 auf, der
eingangsseitig über eine Kondensatpumpe 14 mit einem der
Dampfturbine 4 nachgeschalteten Kondensator 16 verbunden ist.
Der Kondensatvorwärmer 12 ist ausgangsseitig über eine Umwälzpumpe
18 mit seinem Eingang verbunden. Er ist ausgangsseigig
außerdem über eine Speiseleitung 20 mit einem Speisewasserbehälter
22 verbunden. For this purpose, the heat recovery steam generator 6 has a
Der Speisewasserbehälter 22 ist ausgangsseitig über eine
Speisewasserleitung 24, in die eine Pumpe 26 geschaltet ist,
mit einer Niederdruck-Trommel 28 verbunden. An die Niederdruck-Trommel
28 ist über eine Umwälzpumpe 30 ein Verdampfer
angeschlossen. Die Niederdruck-Trommel 28 ist dampfseitig mit
einem Niederdruck-Überhitzer 34 verbunden, der über eine
Dampfleitung 36 an eine Überströmleitung 38 von dem Mitteldruckteil
4b zum Niederdruckteil 4c der Dampfturbine 4 angeschlossen
ist. Die Niederdruck-Trommel 28 und der Niederdruck-Verdampfer
32 bilden zusammen mit dem Niederdruck-Überhitzer
34 und dem Niederdruckteil 4c eine Niederdruckstufe
des Wasser-Dampf-Kreislaufs 8.The
Der Speisewasserbehälter 22 ist ausgangsseitig außerdem über
eine Speisewasserleitung 40, in die eine Pumpe 42 geschaltet
ist, mit einem ersten Hochdruckvorwärmer 44 verbunden, der
über eine Verbindungsleitung 46 mit dem Eingang eines zweiten
Hochdruckvorwärmers 48 verbunden ist. An die Verbindungsleitung
46 ist über eine Leitung 50 eine Mitteldruck-Trommel 52
angeschlossen, an die wiederum über eine Umwälzpumpe 54 ein
Mitteldruck-Verdampfer 56 angeschlossen ist. Die Mitteldruck-Trommel
52 ist dampfseitig mit einem Mitteldruck-Überhitzer
56 verbunden, der ausgangsseitig mit dem Eingang eines Zwischenüberhitzers
58 verbunden ist. Der Zwischenüberhitzer 58
ist eingangsseitig an den Hochdruckteil 4a und ausgangsseitig
an den Mitteldruckteil 4b der Dampfturbine 4 angeschlossen.
Die Mitteldruck-Trommel 52 und der Mitteldruck-Verdampfer 56
sowie der Mitteldruck-Überhitzer 57 bilden zusammen mit dem
Zwischenüberhitzer 58 und dem Mitteldruckteil 4b der Dampfturbine
4 eine Mitteldruckstufe des Wasser-Dampf-Kreislaufs
8.The
Der zweite Hochdruckvorwärmer 48 ist ausgangsseitig über eine
Verbindungsleitung 60 und ein Ventil 62 mit einer Hochdruck-Trommel
64 verbunden, an die über eine Umwälzpumpe 66 ein
Hochdruckverdampfer 68 angeschlossen ist. Die Hochdruck-Trommel
64 ist dampfseitig über einen Hochdruck-Überhitzer 70 an
den Hochdruckteil 4a der Dampfturbine 4 angeschlossen. Die
Hochdruck-Vorwärmer 44, 48 und die Hochdruck-Trommel 64 sowie
der Hochdruck-Verdampfer 68 und der Hochdruck-Überhitzer 70
bilden zusammen mit dem Hochdruckteil 4a der Dampfturbine 4
eine Hochdruckstufe des Wasser-Dampf-Kreislaufs 8.The second high-
In die Überströmleitung 38 zwischen dem Mitteldruckteil 4b
und dem Niederdruckteil 4c der Dampfturbine 4 ist die Sekundärseite
eines Wärmetauschers 72 geschaltet. Primärseitig ist
der Wärmetauscher 72 eingangsseitig über eine Leitung 74 an
die Leitung 60 angeschlossen und somit mit dem Ausgang des
zweiten Hochdruck-Vorwärmers 48 verbunden. Der primärseitige
Ausgang des Wärmetauschers 72 ist über eine Leitung 76, in
die eine Pumpe 78 und ein Regelventil 80 geschaltet sind, mit
dem Eingang des zweiten Hochdruck-Vorwärmers 48 verbunden.
Dabei mündet die Leitung 76 an einer Mischstelle 82 in die
die beiden Hochdruck-Vorwärmer 44 und 48 verbindende Leitung
46.In the
Beim Betrieb der Gas- und Dampfturbinenanlage wird dem Kondensatvorwärmer
12 über die Pumpe 14 und die Kondensatleitung
10 Kondensator K aus dem Kondensator 16 zugeführt. Dabei kann
der Kondensat-Vorwärmer 12 ganz oder teilweise umführt werden.
Das Kondensat K wird in dem Kondensat-Vorwärmer 12 aufgewärmt
und dazu mindestens teilweise über die Umwälzpumpe 18
umgewälzt. Das aufgewärmte Kondensat K wird über die Leitung
20 in den Speisewasserbehälter 22 geführt, wobei dort in
nicht näher dargestellter Art und Weise eine Aufwärmung des
Speisewassers mittels Anzapfdampf aus der Dampfturbine 4 erfolgt.
Das aufgewärmte Speisewasser S wird einerseits der
Niederdruck-Trommel 28 und andererseits über den ersten Hochdruck-Vorwärmer
44 der Mitteldruck-Trommel 52 sowie über den
zweiten Hochdruck-Vorwärmer 48 der Hochdruck-Trommel 64 zugeführt.
Das der Niederdruckstufe zugeführte Speisewasser S
wird im Niederdruck-Verdampfer 32 bei niedrigem Druck verdampft,
wobei der in der Niederdruck-Trommel 28 abgetrennte
Niederdruckdampf ND dem Niederdruck-Überhitzer 34 zugeführt
wird. Der dort überhitzte Niederdruckdampf ND wird vor dem
Wärmetauscher 72 in die Überströmleitung 38 geführt.When the gas and steam turbine system is operated, the condensate preheater becomes
12 via the
Ebenso wird das in die Mitteldruck-Trommel 52 geführte Speisewasser
S im Mitteldruck-Verdampfer 56 verdampft. Der in der
Mitteldruck-Trommel 52 abgetrennte, unter mittlerem Druck
stehende Dampf wird über den Mitteldruck-Überhitzer 57 geführt
und als überhitzter Mitteldruckdampf MD dem Mitteldruckteil
4b der Dampfturbine 4 zugeführt. Analog wird das im
zweiten Hochdruck-Vorwärmer oder -Economizer 48 vorgewärmte
Speisewasser S im Hochdruck-Verdampfer 68 unter hohem Druck
verdampft, wobei der in der Hochdruck-Trommel 64 abgetrennte
Hochdruckdampf HD im Hochdruck-Überhitzer 70 überhitzt und im
überhitzten Zustand in den Hochdruckteil 4a der Dampfturbine
4 geführt wird. Der im Hochdruckteil 4a entspannte Dampf wird
im Zwischenüberhitzer 58 erneut überhitzt und in überhitztem
Zustand zusammen mit dem im Mitteldruck-Überhitzer 56 überhitzten
Mitteldruckdampf MD dem Mitteldruckteil 4b der Dampfturbine
4 zugeführt.Likewise, the feed water fed into the medium pressure drum 52
S evaporated in the
Der im Mitteldruckteil 4b der Dampfturbine 4 entspannte, unter
niedrigem Druck stehende Dampf wird über die Überströmleitung
38 geführt und im Wärmetauscher 72 durch indirekten
Wärmetausch mit einem über die Leitung 74 geführten Teilstrom
tS des im Hochdruck-Vorwärmers 48 vorgewärmten Speisewassers
S überhitzt. Dabei wird dem aus dem Mitteldruckteil 4b abströmenden
Dampf vor dem Wärmetauscher 72 der im Niederdruck-Überhitzer
34 überhitzte Niederdruckdampf ND zugemischt. Der
im Wärmetauscher 72 überhitzte Niederdruckdampf ND wird im
Niederdruckteil 4c der Dampfturbine 4 entspannt und zur Kondensation
dem Kondensator 16 zugeführt.The steam in the medium-
Die Menge des dem Wärmetauscher 72 pro Zeiteinheit zugeführten
Teilstroms tS des im zweiten Hochdruck-Vorwärmer 48 vorgewärmten
Speisewassers S wird mittels des Regelventils 80
eingestellt. Dabei erfolgt die Einstellung derart, daß die
Temperatur T1 des Teilstroms tS und die Temperatur T2 des
vorzuwärmenden Speisewassers S an der Mischstelle 82 einander
angenähert, vorzugsweise einander gleich, sind. Dazu ist ein
Reglerbaustein 84 über eine Steuerleitung 85 mit dem Regelventil
80 verbunden. Der Reglerbaustein 84 ist dazu außerdem
über eine Steuerleitung 86 mit einem ersten Temperatursensor
87 zur Erfassung der Temperatur T1 und über eine Steuerleitung
88 mit einem zweiten Temperatursensor. 89 zur Erfassung
der Temperatur T2 verbunden.The amount of the partial flow t S of the feed water S preheated in the second high-
Durch die Einschaltung des Wärmetauschers 72 in die Überströmleitung
38 zur Überhitzung des Niederdruckdampfes ND
mittels des dem Hochdruck-Vorwärmer 48 entnommenen Teilstroms
tS erhöht sich die an einem (nicht dargestellten) Dampfturbinen-Generator
entnehmbare Klemmleistung um 1,3% bis 2%. Wird
in einem Zwei-Druck-Prozeß die gesamte Niederdruck-Dampfmenge
in entsprechender Weise überhitzt, so beträgt die damit erreichte
Steigerung der Dampfturbinenleistung mehr als 2,6%.By switching on the
Claims (10)
- Gas-turbine and steam-turbine plant with a waste-heat steam generator (6) which is located downstream of the gas turbine (2) on the exhaust-gas side and the high-pressure preheater (48) of which is connected into the water/steam circuit (8) of the steam turbine (4) having a low-pressure part (4c), characterized by a heat exchanger (72) which is arranged outside the waste-heat steam generator (6) and of which the primary-side inlet is connected to the outlet of the high-pressure preheater (48) and of which the primary-side outlet is connected to the inlet of the high-pressure preheater (48) and which is connected on the secondary side into an overflow conduit (38) opening into the low-pressure part (4c) of the steam turbine (4).
- Plant according to Claim 1, characterized in that a circulating pump (78) and a regulating valve (80) are located downstream of the heat exchanger (72) on the primary side.
- Plant according to Claim 1 or 2, characterized by a controller module (84) for adjusting the quantity of feed water (ts) supplied per unit time to the heat exchanger (72) on the primary side.
- Plant according to Claim 3, characterized by a first temperature sensor (87), connected to the controller module (84), for recording the temperature (T1) of the feed water (ts) flowing off from the heat exchanger (72) on the secondary side and by a second temperature sensor (89), connected to the controller module (84), for recording the temperature (T2) of the feed water (S) supplied to the high-pressure preheater (48).
- Plant according to one of Claims 1 to 4, characterized in that the high-pressure preheater (48) is a second high-pressure preheater which is located downstream of a first high-pressure preheater (44) on the feed-water side and which is arranged upstream of the first high-pressure preheater (44) in the waste-heat steam generator (6) on the exhaust-gas side.
- Plant according to one of Claims 1 to 5, characterized by a low-pressure superheater (34) which is arranged in the waste-heat steam generator (6) and which is connected on the outlet side to the secondary-side inlet of the heat exchanger (72).
- Method for operating a gas-turbine and steam-turbine plant, in which heat contained in the expanded working medium (AG) from the gas turbine (2) is utilized for generating steam for the steam turbine (4) connected into a water/steam circuit (8) composed of at least two pressure stages, feed water (S) which flows in the water/steam circuit (8) being preheated in a high-pressure preheater (48) arranged in the waste-heat steam generator (6), characterized in that low-pressure steam (ND) flowing into the steam turbine (4) is superheated as a result of indirect heat exchange with a part stream (ts) of preheated feed water (S), the said part stream being extracted from the high-pressure preheater (48).
- Method according to Claim 7, characterized in that the cooled part stream (ts) is admixed with the feed water (S) to be preheated, the temperature (T1) of the part stream (ts) and the temperature (T2) of the feed water (S) to be preheated being approximated to one another.
- Method according to Claim 8, characterized in that the temperature approximation is carried out by adjusting the part stream (ts).
- Method according to one of Claims 7 to 9, with a water/steam circuit (8) composed of three pressure stages, characterized in that low-pressure steam (ND) superheated in the waste-heat steam generator (6) is admixed with the low-pressure steam (ND) to be superheated by indirect heat exchange.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19527537A DE19527537C1 (en) | 1995-07-27 | 1995-07-27 | Combined gas and steam turbine plant |
| DE19527537 | 1995-07-27 | ||
| PCT/DE1996/001244 WO1997005366A1 (en) | 1995-07-27 | 1996-07-10 | Process for running a gas and steam turbine plant and plant run by this process |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0840837A1 EP0840837A1 (en) | 1998-05-13 |
| EP0840837B1 true EP0840837B1 (en) | 2001-08-29 |
Family
ID=7767972
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP96922762A Expired - Lifetime EP0840837B1 (en) | 1995-07-27 | 1996-07-10 | Process for running a gas and steam turbine plant and plant run by this process |
Country Status (11)
| Country | Link |
|---|---|
| US (1) | US5992138A (en) |
| EP (1) | EP0840837B1 (en) |
| JP (1) | JPH11509901A (en) |
| KR (1) | KR19990029030A (en) |
| CN (1) | CN1093215C (en) |
| DE (2) | DE19527537C1 (en) |
| ES (1) | ES2163641T3 (en) |
| RU (1) | RU2153080C2 (en) |
| TW (1) | TW308627B (en) |
| UA (1) | UA41457C2 (en) |
| WO (1) | WO1997005366A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1997007323A1 (en) * | 1995-08-18 | 1997-02-27 | Siemens Aktiengesellschaft | Gas and steam turbine plant and process for operating such a plant, also waste heat steam generator for a gas and steam turbine plant |
| AT410695B (en) * | 1996-03-08 | 2003-06-25 | Beckmann Georg Dr | DEVICE AND METHOD FOR GENERATING ENERGY |
| JP4126108B2 (en) * | 1998-02-25 | 2008-07-30 | 三菱重工業株式会社 | Gas turbine combined plant, operation method thereof, and gas turbine high temperature section steam cooling system |
| DE19829088C2 (en) * | 1998-06-30 | 2002-12-05 | Man Turbomasch Ag Ghh Borsig | Electricity generation in a composite power plant with a gas and a steam turbine |
| US6796240B2 (en) * | 2001-06-04 | 2004-09-28 | Quad/Tech, Inc. | Printing press register control using colorpatch targets |
| CN1948720B (en) * | 2006-10-31 | 2011-08-10 | 章祖文 | Permanent magnet driving low temperature multistage turbogenerator |
| DE102008057490B4 (en) * | 2008-11-14 | 2010-09-30 | Siemens Aktiengesellschaft | Combined gas and steam turbine power plant and method of operation |
| US9435534B2 (en) * | 2009-08-31 | 2016-09-06 | Holistic Engineering Inc | Energy-recovery system for a production plant |
| RU2553477C2 (en) * | 2013-01-23 | 2015-06-20 | Аркадий Ефимович Зарянкин | Combined-cycle plant |
| US11008897B2 (en) * | 2016-06-17 | 2021-05-18 | Siemens Energy Global GmbH & Co. KG | Condensate recirculation |
| FI20210068A1 (en) * | 2021-11-10 | 2023-05-11 | Loeytty Ari Veli Olavi | Method and apparatus for improving energy efficiency in current gas turbine combi plants |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH432555A (en) * | 1965-02-15 | 1967-03-31 | Sulzer Ag | Steam power plant with steam generator and with gas turbine |
| DE3804605A1 (en) * | 1988-02-12 | 1989-08-24 | Siemens Ag | METHOD AND SYSTEM FOR THE PRODUCTION OF HEAT-STEAM |
| EP0410111B1 (en) * | 1989-07-27 | 1993-01-20 | Siemens Aktiengesellschaft | Heat recovery boiler for a gas and steam turbine plant |
| DE4029991A1 (en) * | 1990-09-21 | 1992-03-26 | Siemens Ag | COMBINED GAS AND STEAM TURBINE SYSTEM |
| JPH04298604A (en) * | 1990-11-20 | 1992-10-22 | General Electric Co <Ge> | Combined cycle power plant and steam supply method |
| DE59205640D1 (en) * | 1991-05-27 | 1996-04-18 | Siemens Ag | Process for operating a gas and steam turbine plant and corresponding plant |
| DE59203883D1 (en) * | 1991-07-17 | 1995-11-09 | Siemens Ag | Process for operating a gas and steam turbine plant and plant for carrying out the process. |
| ES2083627T3 (en) * | 1991-07-17 | 1996-04-16 | Siemens Ag | PROCEDURE FOR THE OPERATION OF A GAS AND STEAM TURBINE INSTALLATION AND INSTALLATION FOR THE PERFORMANCE OF THE PROCEDURE. |
-
1995
- 1995-07-27 DE DE19527537A patent/DE19527537C1/en not_active Expired - Fee Related
-
1996
- 1996-07-10 CN CN96192448A patent/CN1093215C/en not_active Expired - Fee Related
- 1996-07-10 WO PCT/DE1996/001244 patent/WO1997005366A1/en active IP Right Grant
- 1996-07-10 KR KR1019980700333A patent/KR19990029030A/en active IP Right Grant
- 1996-07-10 JP JP9507079A patent/JPH11509901A/en active Pending
- 1996-07-10 UA UA98010414A patent/UA41457C2/en unknown
- 1996-07-10 ES ES96922762T patent/ES2163641T3/en not_active Expired - Lifetime
- 1996-07-10 RU RU98103240/06A patent/RU2153080C2/en not_active IP Right Cessation
- 1996-07-10 DE DE59607594T patent/DE59607594D1/en not_active Expired - Lifetime
- 1996-07-10 EP EP96922762A patent/EP0840837B1/en not_active Expired - Lifetime
- 1996-07-26 TW TW085109131A patent/TW308627B/zh active
-
1998
- 1998-01-27 US US09/014,158 patent/US5992138A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| DE19527537C1 (en) | 1996-09-26 |
| UA41457C2 (en) | 2001-09-17 |
| CN1093215C (en) | 2002-10-23 |
| JPH11509901A (en) | 1999-08-31 |
| DE59607594D1 (en) | 2001-10-04 |
| ES2163641T3 (en) | 2002-02-01 |
| CN1177995A (en) | 1998-04-01 |
| KR19990029030A (en) | 1999-04-15 |
| WO1997005366A1 (en) | 1997-02-13 |
| RU2153080C2 (en) | 2000-07-20 |
| EP0840837A1 (en) | 1998-05-13 |
| TW308627B (en) | 1997-06-21 |
| US5992138A (en) | 1999-11-30 |
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