EP0584072B1 - Gas-turbine/steam-turbine installation - Google Patents
Gas-turbine/steam-turbine installation Download PDFInfo
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- EP0584072B1 EP0584072B1 EP92900067A EP92900067A EP0584072B1 EP 0584072 B1 EP0584072 B1 EP 0584072B1 EP 92900067 A EP92900067 A EP 92900067A EP 92900067 A EP92900067 A EP 92900067A EP 0584072 B1 EP0584072 B1 EP 0584072B1
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- gas
- steam
- turbine
- heat exchanger
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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
- F01K23/103—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 afterburner in exhaust boiler
Definitions
- the invention relates to a gas and steam turbine system with a steam generator connected downstream of the gas turbine on the exhaust gas side for generating steam for the steam turbine in a water-steam cycle, the steam generator comprising a combustion system connected downstream of a coal mill.
- Such a gas and steam turbine system with a steam generator with associated combustion system and upstream coal mill is known from US-A-3,095,699.
- the exhaust gas stream of the gas turbine is divided into partial streams, one partial stream being used as combustion air for the furnace and another partial stream for drying coal, and further a partial stream for preheating the feed water.
- US-A-3,314,231 it is also known to first lead the exhaust gas from a gas turbine system via a heat recovery steam generator before it is fed to a firing system of a downstream steam generator.
- the invention is therefore based on the object of achieving the highest possible overall efficiency when retrofitting an existing steam turbine system with a gas turbine in all operating states.
- the greatest possible utilization of existing assemblies should be made possible.
- a first adjustable subset of the exhaust gas cooled in a heat exchanger can be supplied as combustion air from the gas turbine of the furnace, that a second adjustable subset of the cooled exhaust gas can be supplied to a heat exchanger for heating air for the coal mill and that one third subset of the cooled exhaust gas the flue gas flowing through the steam generator from the combustion system can be admixed.
- the heat exchanger or cooler through which the exhaust gas flows from the gas turbine is expediently connected to the water-steam circuit of the steam turbine.
- the exhaust gas from the gas turbine is advantageously cooled to the maximum temperature permitted in the design of the existing flue gas ducts of the steam turbine system.
- part of the air warmed up in the second heat exchanger can be supplied to the first part of the cooled exhaust gas from the gas turbine.
- the air heated in the second heat exchanger can be mixed with cold air for the coal mill.
- the advantages achieved by the invention consist in particular in that, on the one hand, by cooling the exhaust gases from the gas turbine in a heat exchanger, overheating of already existing flue gas ducts of the steam turbine system is reliably avoided, and on the other hand, by dividing the cooled exhaust gases into controllable portions, additional use of the the exhaust gases contain heat for the overall process and thus a high overall efficiency of the system is achieved regardless of the operating state.
- FIG. 1 shows a schematic representation of a gas and steam turbine system with a division of the exhaust gases from the gas turbine into three controllable partial flows.
- the gas and steam turbine system comprises a steam generator 2 and a steam turbine 4 connected to a water-steam circuit 3 with a connected generator 5 as well as a gas turbine 6 upstream of the steam generator 2 with a coupled generator 7.
- the steam generator 2 comprises a combustion system 8 which is connected to a coal mill 10 via a fuel line 9.
- a condenser 15 and a pump 16 connected downstream of the condenser 15 and a preheater 17 arranged in the steam generator 2 are connected in the water-steam circuit 3 of the steam turbine 4, which is shown in simplified form.
- the preheater 17 is connected via a first branch 18, into which a valve 19 is connected, to a heat exchanger 20 heated by the hot exhaust gas a from the gas turbine 6.
- the preheater 17 is also connected via a second branch 22 to a heating device 24 arranged in the steam generator 2 in the region of a combustion chamber 23.
- the heat exchanger 20 is connected on the output side to the steam turbine 4 via a steam line 21.
- the heat exchanger 20 is connected on the primary side to an exhaust line 25 connected to the gas turbine 6.
- a first partial flow line 26 is connected to the exhaust line 25 and opens into the combustion system 8.
- the exhaust gas line 25 is also connected via a second partial flow line 27 to an inlet 2a of the steam generator 2.
- the exhaust line 25 also has a third partial flow line 28, into which a second heat exchanger 29 is connected.
- Flaps 30, 31 and 32 for example throttle valves or other control elements, are connected in the partial flow lines 26, 27 and 28. The flaps 30, 31 and 32 can be actuated by motors, not shown.
- the hot exhaust gas a flowing out of the gas turbine 6 is cooled in the heat exchanger 20 to about 400 ° C., so that the walls of the partial flow lines 26, 27 and 28 designed as flue gas channels are not heated above 400 ° C.
- the exhaust gas a is divided into three adjustable subsets t1, t2 and t3.
- the partial quantity t1 flowing via the partial flow line 26 is adjusted to the combustion air system 8's need for combustion air, ie in particular as a function of the operating state of the system.
- the partial quantity t1 compressed and preheated in the heat exchanger 29 air L from an air compressor 35 can be added.
- the air compressor 35 is connected to the partial flow line 26 via an air line 36 connected in the heat exchanger 29 on the secondary side.
- a flap 37 is connected in the air line 36 to set the required amount of air.
- the part of the exhaust gases a not required for the combustion system 8 is conducted via the partial flow lines 27 and 28 on the one hand into the steam generator 2 and on the other hand via the second heat exchanger 29.
- the partial quantity t3 of the exhaust gas a flowing via the partial flow line 27 is mixed with the flue gas r generated in the combustion system 8.
- the partial quantity t3 of the exhaust gas a and the flue gas r leave the steam generator 2 via its outlet 2b and via a gas filter 40 in the direction of a chimney (not shown).
- the adjustable partial quantity t2 of the exhaust gas a conducted via the partial flow line 28 heats the air L flowing through the air line 36 in the heat exchanger 29 and is subsequently mixed with the flue gas r flowing out of the steam generator 2 behind the gas filter 40.
- the temperature of the air L for the coal mill 10 is adjusted by admixing an amount of cold air that can be adjusted by means of the flap 46 to the heated air L from the heat exchanger 29.
- the flue gas r from the combustion system 8 and the partial quantity t3 of the exhaust gas a flowing into the steam generator 2 via the partial flow line 27 serve to generate steam for the steam turbine 4.
- water from the condenser 15 is pumped into the flue gas r and pumped by the exhaust gas a preheater 17 and preheated there.
- the heated water flowing over the branch 22 is evaporated and overheated in the heating surfaces 24 heated by the hot flue gases r from the furnace 8.
- the superheated steam is fed to the steam turbine 4 via a steam line 50.
- the heated water flowing via the branch 18 is likewise evaporated and overheated in the heat exchanger 20 and fed to the steam turbine 4. There, the superheated steam is expanded and then condensed in the condenser 15.
- the gas turbine 6 Due to the inventive division of the cooled exhaust gases a from the gas turbine 6 into three adjustable subsets t1, t2 and t3, on the one hand the gas turbine 6 is decoupled from the requirements of the combustion system with regard to the amount of air required in different operating states. On the other hand, the steam generator 2 and thus the steam process can be operated independently of the load state of the gas turbine 6.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
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Abstract
Description
Die Erfindung betrifft eine Gas- und Dampfturbinenanlage mit einem der Gasturbine abgasseitig nachgeschalteten Dampferzeuger zur Erzeugung von Dapf für die Dampfturbine in einem Wasser-Dampf-Kreislauf, wobei der Dampferzeuger eine einer Kohlemühle nachgeschaltete Feuerungsanlage umfaßt.The invention relates to a gas and steam turbine system with a steam generator connected downstream of the gas turbine on the exhaust gas side for generating steam for the steam turbine in a water-steam cycle, the steam generator comprising a combustion system connected downstream of a coal mill.
Eine derartige Gas- und Dampfturbinenanlage mit einem Dampferzeuger mit zugehöriger Feuerungsanlage und vorgeschalteter Kohlemühle ist aus der US-A-3,095,699 bekannt. Bei der bekannten Anlage ist der Abgasstrom der Gasturbine in Teilströme unterteilt, wobei ein Teilstrom als Verbrennungsluft für die Feuerungsanlage und ein weiterer Teilstrom zur Kohletrocknung sowie ferner ein Teilstrom zur Speisewasservorwarmung verwendet werden. Aus der US-A-3,314,231 ist es darüber hinaus bekannt, das Abgas aus einer Gasturbinenanlage zunächst über einen Abhitzedampferzeuger zu führen, bevor es einer Feuerungsanlage eines nachgeschalteten Dampferzeugers zugeführt wird.Such a gas and steam turbine system with a steam generator with associated combustion system and upstream coal mill is known from US-A-3,095,699. In the known system, the exhaust gas stream of the gas turbine is divided into partial streams, one partial stream being used as combustion air for the furnace and another partial stream for drying coal, and further a partial stream for preheating the feed water. From US-A-3,314,231 it is also known to first lead the exhaust gas from a gas turbine system via a heat recovery steam generator before it is fed to a firing system of a downstream steam generator.
Bei der Planung und beim Bau einer Gas- und Dampfturbinenanlage, insbesondere bei einer Ankopplung einer Gasturbinenanlage an eine bestehende Dampfturbinenanlage mit eriner Feuerungsanlage, müssen die voneinander abhängigen Leistungen der Gasturbine und der Dampfturbine sowie des Dampferzeugers zur Erzielung eines hohen Gesamtwirkungsgrades aufeinander abgestimmt werden. Dabei ist der Gesamtwirkungsgrad um so höher, je länger die Gasturbine mit Vollast betrieben wird. Da allerdings bei einer derartigen Anlage das Abgas der Gasturbine üblicherweise als Verbrennungsluft für die Feuerungsanlage des Dampferzeugers genutzt wird, führt eine Änderungder Dampferzeugerleistung, z.B. durch eine Absenkung der Flammentemperatur der Feuerungsanlage, zu einem Mißverhältnis zwischen der Abgasmenge der Gasturbine und der erforderlichen Luft- oder Sauerstoffmenge für die Feuerungsanlage.Dadurch ist, insbesondere im Teillastbereich, der Wirkungsgrad der Anlage nur begrenzt optimierbar.When planning and building a gas and steam turbine system, especially when coupling a gas turbine system to an existing steam turbine system with an internal combustion system, the interdependent performance of the gas turbine and the steam turbine and the steam generator must be coordinated to achieve a high overall efficiency. The overall efficiency is higher the longer the gas turbine is operated at full load. However, since in such a system the exhaust gas from the gas turbine is usually used as combustion air for the combustion system of the steam generator, a change in the steam generator output, for example due to a reduction in the flame temperature of the combustion system, leads to an imbalance between the amount of exhaust gas from the gas turbine and the amount of air or oxygen required for the furnace, which means that the efficiency of the system can only be optimized to a limited extent, especially in the partial load range.
Der Erfindung liegt daher die Aufgabe zugrunde, bei einer Nachrüstung einer bestehenden Dampfturbinenanlage mit einer Gasturbine bei allen Betriebszuständen einen möglichst hohen Gesamtwirkungsgrad zu erreichen. Dabei soll eine weitestgehende Ausnutzung bestehender Baugruppen ermöglicht werden.The invention is therefore based on the object of achieving the highest possible overall efficiency when retrofitting an existing steam turbine system with a gas turbine in all operating states. The greatest possible utilization of existing assemblies should be made possible.
Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß eine erste einstellbare Teilmenge des in einem Wärmetauscher abgekühlten Abgases aus der Gasturbine der Feuerungsanlage als Verbrennungsluft zuführbar ist, daß eine zweite einstellbare Teilmenge des abgekühlten Abgases einem Wärmetauscher zum Aufwärmen von Luft für die Kohlemühle zuführbar ist und daß eine dritte Teilmenge des abgekühlten Abgases dem den Dampferzeuger durchströmenden Rauchgas aus der Feuerungsanlage zumischbar ist.This object is achieved in that a first adjustable subset of the exhaust gas cooled in a heat exchanger can be supplied as combustion air from the gas turbine of the furnace, that a second adjustable subset of the cooled exhaust gas can be supplied to a heat exchanger for heating air for the coal mill and that one third subset of the cooled exhaust gas the flue gas flowing through the steam generator from the combustion system can be admixed.
Zur Erzeugung von zusätzlichem Dampf für die Dampfturbine ist zweckmaßigerweise der vom Abgas aus der Gasturbine durchströmte Wärmetauscher oder Kühler in den Wasser-Dampf-Kreislauf der Dampfturbine geschaltet. Dabei wird das Abgas aus der Gasturbine vorteilhafterweise auf die bei der Auslegung der bestehenden Rauchgaskanäle der Dampfturbinenanlage zugelassene Höchsttemperatur abgekühlt.To generate additional steam for the steam turbine, the heat exchanger or cooler through which the exhaust gas flows from the gas turbine is expediently connected to the water-steam circuit of the steam turbine. The exhaust gas from the gas turbine is advantageously cooled to the maximum temperature permitted in the design of the existing flue gas ducts of the steam turbine system.
Zur Anreicherung der Verbrennungsluft für die Feuerungsanlage mit Sauerstoff ist ein Teil der im zweiten Wärmetauscher aufgewärmten Luft der ersten Teilmenge des abgekühlten Abgases aus der Gasturbine zuführbar.To enrich the combustion air for the combustion system with oxygen, part of the air warmed up in the second heat exchanger can be supplied to the first part of the cooled exhaust gas from the gas turbine.
Zur Regelung der Temperatur in der Kohlemühle ist der im zweiten Wärmetauscher aufgewärmten Luft für die Kohlemühle kalte Luft zumischbar.To regulate the temperature in the coal mill, the air heated in the second heat exchanger can be mixed with cold air for the coal mill.
Die mit der Erfindung erzielten Vorteile bestehen insbesondere darin, daß einerseits durch eine Abkühlung der Abgase aus der Gasturbine in einem Wärmetauscher eine Überhitzung bereits bestehender Rauchgaskanäle der Dampfturbinenanlage sicher vermieden ist und daß andererseits durch eine Aufteilung der abgekühlten Abgase in regelbare Teilmengen eine zusätzliche Nutzung der in den Abgasen enthaltenen Wärme für den Gesamtprozeß und damit ein hoher Gesamtwirkungsgrad der Anlage unabhängig vom Betriebszustand erreicht wird.The advantages achieved by the invention consist in particular in that, on the one hand, by cooling the exhaust gases from the gas turbine in a heat exchanger, overheating of already existing flue gas ducts of the steam turbine system is reliably avoided, and on the other hand, by dividing the cooled exhaust gases into controllable portions, additional use of the the exhaust gases contain heat for the overall process and thus a high overall efficiency of the system is achieved regardless of the operating state.
Zur näheren Erläuterung der Erfindung wird anhand einer Zeichnung ein Ausführungsbeispiel beschrieben. Darin zeigt die Figur in schematischer Darstellung eine Gas- und Dampfturbinenanlage mit einer Aufteilung der Abgase aus der Gasturbine in drei regelbare Teilströme.For a more detailed explanation of the invention, an embodiment is described with reference to a drawing. The figure shows a schematic representation of a gas and steam turbine system with a division of the exhaust gases from the gas turbine into three controllable partial flows.
Die Gas- und Dampfturbinenanlage gemäß der Figur umfaßt einen Dampferzeuger 2 und eine in einen Wasser-Dampf-Kreislauf 3 geschaltete Dampfturbine 4 mit angekoppeltem Generator 5 sowie eine dem Dampferzeuger 2 vorgeschaltete Gasturbine 6 mit angekoppeltem Generator 7. Der Dampferzeuger 2 umfaßt eine Feuerungsanlage 8, die über eine Brennstoffleitung 9 an eine Kohlemühle 10 angeschlossen ist.The gas and steam turbine system according to the figure comprises a steam generator 2 and a steam turbine 4 connected to a water-
In den vereinfacht dargestellten Wasser-Dampf-Kreislauf 3 der Dampfturbine 4 ist ein Kondensator 15 und eine dem Kondensator 15 nachgeschaltete Pumpe 16 sowie ein im Dampferzeuger 2 angeordneter Vorwärmer 17 geschaltet. Der Vorwärmer 17 ist ausgangsseitig über einen ersten Zweig 18, in den ein Ventil 19 geschaltet ist, an einen vom heißen Abgas a aus der Gasturbine 6 beheizten Wärmetauscher 20 angeschlossen. Der Vorwärmer 17 ist außerdem über einen zweiten Zweig 22 an eine im Dampferzeuger 2 im Bereich eines Feuerraums 23 angeordnete Heizeinrichtung 24 angeschlossen.A
Der Wärmetauscher 20 ist ausgangsseitig über eine Dampfleitung 21 an die Dampfturbine 4 angeschlossen. Der Wärmetauscher 20 ist primärseitig in eine an die Gasturbine 6 angeschlossene Abgasleitung 25 geschaltet.The
Zum Zuführen einer ersten Teilmenge tl des Abgases a aus der Gasturbine 6 in die Feuerungsanlage 8 ist an die Abgasleitung 25 eine erste Teilstromleitung 26 angeschlossen, die in die Feuerungsanlage 8 mündet. Die Abgasleitung 25 ist außerdem über eine zweite Teilstromleitung 27 mit einem Eingang 2a des Dampferzeugers 2 verbunden. Die Abgasleitung 25 weist außerdem eine dritte Teilstromleitung 28 auf, in die ein zweiter Wärmetauscher 29 geschaltet ist. In die Teilstromleitungen 26, 27 und 28 sind Klappen 30, 31 bzw. 32, beispielsweise Drosselklappen oder andere Regelorgane, geschaltet. Die Klappen 30, 31 bzw. 32 können dabei von nicht dargestellten Motoren betätigt werden.In order to supply a first partial quantity tl of the exhaust gas a from the gas turbine 6 into the combustion system 8, a first
Beim Betrieb der Gas- und Dampfturbinenanlage wird das aus der Gasturbine 6 abströmende heiße Abgas a im Wärmetauscher 20 auf etwa 400° C abgekühlt, so daß die Wände der als Rauchgaskanäle ausgebildeten Teilstromleitungen 26, 27 und 28 nicht über 400° C aufgeheizt werden. In Strömungsrichtung der Abgase a hinter dem Wärmetauscher 20 wird das Abgas a in drei einstellbare Teilmengen t1, t2 und t3 aufgeteilt. Dabei wird die über die Teilstromleitung 26 strömende Teilmenge t1 auf den Bedarf der Feuerungsanlage 8 an Verbrennungsluft, d.h. insbesondere in Abhängigkeit vom Betriebszustand der Anlage, eingestellt. Dabei kann der Teilmenge t1 verdichtete und im Wärmetauscher 29 vorgewärmte Luft L aus einem Luftverdichter 35 zugemischt werden. Dazu ist der Luftverdichter 35 über eine sekundärseitig in den Wärmetauscher 29 geschaltete Luftleitung 36 an die Teilstromleitung 26 angeschlossen. Zur Einstellung der erforderlichen Luftmenge ist in die Luftleitung 36 eine Klappe 37 geschaltet.During operation of the gas and steam turbine system, the hot exhaust gas a flowing out of the gas turbine 6 is cooled in the
Bei abnehmender Last und damit bei vermindertem Bedarf an Verbrennungsluft für die Feuerungsanlage 8 wird der nicht für die Feuerungsanlage 8 benötigte Teil der Abgase a über die Teilstromleitungen 27 und 28 einerseits in den Dampferzeuger 2 und andererseits über den zweiten Wärmetauscher 29 geführt. Dabei wird die über die Teilstromleitung 27 strömende Teilmenge t3 des Abgases a dem in der Feuerungsanlage 8 erzeugten Rauchgas r zugemischt. Die Teilmenge t3 des Abgases a und das Rauchgas r verlassen den Dampferzeuger 2 über dessen Ausgang 2b und über einen Gasfilter 40 in Richtung auf einen (nicht dargestellten) Kamin.With a decreasing load and thus with a reduced need for combustion air for the combustion system 8, the part of the exhaust gases a not required for the combustion system 8 is conducted via the
Die über die Teilstromleitung 28 geführte einstellbare Teilmenge t2 des Abgases a erwärmt im Wärmetauscher 29 die über die Luftleitung 36 strömende Luft L und wird anschließend dem aus dem Dampferzeuger 2 abströmenden Rauchgas r hinter dem Gasfilter 40 zugemischt.The adjustable partial quantity t2 of the exhaust gas a conducted via the
Die von der zweiten Teilmenge t2 im Wärmetauscher 29 aufgewärmte Luft L aus dem Luftverdichter 36 strömt über einen Zweig 41 der Luftleitung 36 in die Kohlemühle 10. Sie dient dort einerseits als Wärmemedium zum Trocknen der der Kohlemühle 10 über eine Kohleleitung 42 zugeführten Kohle k und andererseits als Transportmittel zum Zuführen der in der Kohlemühle 10 zermahlenen Kohle k über die Brennstoffleitung 9 in die Feuerungsanlage 8. In den von der Luftleitung 36 ausgehenden Zweig 41, in den eine Klappe 44 geschaltet ist, mündet eine vor dem Wärmetauscher 29 an die Luftleitung 36 angeschlossene Kaltluftleitung 45, in die eine Klappe 46 geschaltet ist. Dabei wird durch Zumischen einer mittels der Klappe 46 einstellbaren Kaltluftmenge zur aufgewärmten Luft L aus dem Wärmetauscher 29 die Temperatur der Luft L für die Kohlemühle 10 eingestellt.The air L warmed by the second subset t2 in the
Das Rauchgas r aus der Feuerungsanlage 8 und die über die Teilstromleitung 27 in den Dampferzeuger 2 einströmende Teilmenge t3 des Abgases a dienen zur Erzeugung von Dampf für die Dampfturbine 4. Dazu wird Wasser aus dem Kondensator 15 über die Pumpe 16 in den vom Rauchgas r und vom Abgas a beheizten Vorwärmer 17 gepumpt und dort vorgewärmt. Das über den Zweig 22 strömende aufgewärmte Wasser wird in den von den heißen Rauchgasen r aus der Feuerungsanlage 8 beheizten Heizflächen 24 verdampft und überhitzt. Der überhitzte Dampf wird über eine Dampfleitung 50 der Dampfturbine 4 zugeführt. Das über den Zweig 18 strömende aufgewärmte Wasser wird im Wärmetauscher 20 ebenfalls verdampft und überhitzt und der Dampfturbine 4 zugeführt. Dort wird der überhitzte Dampf entspannt und anschließend im Kondensator 15 kondensiert.The flue gas r from the combustion system 8 and the partial quantity t3 of the exhaust gas a flowing into the steam generator 2 via the
Durch die erfindungsgemäße Aufteilung der abgekühlten Abgase a aus der Gasturbine 6 in drei einstellbare Teilmengen t1, t2 und t3 ist einerseits die Gasturbine 6 von den Anforderungen der Feuerungsanlage bezüglich der bei unterschiedlichen Betriebszuständen erforderlichen Luftmenge entkoppelt. Andererseits kann der Dampferzeuger 2 und damit der Dampfprozeß unabhängig vom Lastzustand der Gasturbine 6 betrieben werden.Due to the inventive division of the cooled exhaust gases a from the gas turbine 6 into three adjustable subsets t1, t2 and t3, on the one hand the gas turbine 6 is decoupled from the requirements of the combustion system with regard to the amount of air required in different operating states. On the other hand, the steam generator 2 and thus the steam process can be operated independently of the load state of the gas turbine 6.
Claims (4)
- Gas and steam turbine installation having a steam generator (2), which is connected downstream of the gas turbine (6) on the waste gas side, for generating steam for the steam turbine (4) in a water-steam loop (3), wherein the steam generator (2) comprises a furnace installation (8) which is connected downstream of a coal mill (10),- wherein a first adjustable fractional quantity (t1) of the waste gas (a) from the gas turbine (6), which waste gas is cooled in a first heat exchanger (20), can be supplied to the furnace installation (8) as combustion air,- wherein a second adjustable fractional quantity (t2) of the cooled waste gas (a) can be supplied to a second heat exchanger (29) for the purpose of heating air (1) for the coal mill (10),
and- wherein a third adjustable fractional quantity (t3) of the cooled waste gas (a) can be admixed with the flue gas (r) from the furnace installation (8) flowing through the steam generator (2). - Gas and steam turbine installation according to claim 1, characterised in that the heat exchanger (20), through which the waste gas (a) from the gas turbine (6) flows, is connected into the water-steam loop (3) of the steam turbine (4).
- Gas and steam turbine installation according to claim 1 or 2, characterised in that a fraction of the air (L) which is heated in the second heat exchanger (29) can be supplied to the first fractional quantity (t1) of the cooled waste gas (a).
- Gas and steam turbine installation according to one of the claims 1 to 3, characterised in that cold air (L) can be admixed with the air (L) heated in the second heat exchanger (29) for the coal mill (10).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4116065 | 1991-05-16 | ||
| DE4116065A DE4116065A1 (en) | 1991-05-16 | 1991-05-16 | GAS AND STEAM TURBINE SYSTEM |
| PCT/DE1991/000952 WO1992020905A1 (en) | 1991-05-16 | 1991-12-06 | Gas-turbine/steam-turbine installation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0584072A1 EP0584072A1 (en) | 1994-03-02 |
| EP0584072B1 true EP0584072B1 (en) | 1996-05-22 |
Family
ID=6431811
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP92900067A Expired - Lifetime EP0584072B1 (en) | 1991-05-16 | 1991-12-06 | Gas-turbine/steam-turbine installation |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US5367870A (en) |
| EP (1) | EP0584072B1 (en) |
| JP (1) | JP3231761B2 (en) |
| DE (2) | DE4116065A1 (en) |
| RU (1) | RU2090761C1 (en) |
| UA (1) | UA27727C2 (en) |
| WO (1) | WO1992020905A1 (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5673634A (en) * | 1992-11-17 | 1997-10-07 | Apparatebau Rothemuhle Brandt & Kritzler Gmbh | Incineration plant with heat exchanger |
| ES2064242B1 (en) * | 1992-12-02 | 1997-09-01 | Ingenieria Y Promocion Ind S A | SYSTEM OF REGULATION OF GASES OF EXHAUST OF GAS TURBINES IN A RECOVERY BOILER AND CORRESPONDING BOILER. |
| DE4304124C1 (en) * | 1993-01-23 | 1994-03-31 | Steinmueller Gmbh L & C | Method to generate electricity in combination power station - waste gas is separated from coal dust after grinding drying, and preheated fresh air transports coal dust |
| AT411183B (en) * | 1994-10-28 | 2003-10-27 | Ae Energietechnik Gmbh | METHOD AND COMBINED POWER PLANT FOR THERMAL PERFORMANCE |
| DE19542917A1 (en) * | 1994-12-21 | 1996-06-27 | Abb Management Ag | Combined turbine generating set |
| DE19626011A1 (en) * | 1996-06-28 | 1998-01-02 | Lentjes Kraftwerkstechnik | Combined gas-steam power plant and process |
| DE10001997A1 (en) * | 2000-01-19 | 2001-07-26 | Alstom Power Schweiz Ag Baden | Composite power plant and method for operating such a composite power plant |
| EP1174591A1 (en) * | 2000-07-21 | 2002-01-23 | Siemens Aktiengesellschaft | Primary regulation process with combined gas- and steam turbines plants |
| DE10225126B4 (en) * | 2001-06-13 | 2014-05-15 | Alstom Technology Ltd. | A method for firing a solid and / or pasty fuel and a dust-fired steam generator for carrying out the method |
| ITVE20090055A1 (en) * | 2009-10-02 | 2011-04-03 | Giovanni Parise | INCREASE OF EFFICIENCY OF THERMO-ELECTRIC SYSTEMS |
| CN103170398A (en) * | 2013-03-26 | 2013-06-26 | 上海理工大学 | Drying and crushing machine system using waste heat of micro power station |
| JP6351389B2 (en) * | 2014-06-10 | 2018-07-04 | 大阪瓦斯株式会社 | Exhaust reburning system |
| US11319874B1 (en) * | 2020-10-30 | 2022-05-03 | Doosan Heavy Industries & Construction Co., Ltd. | Air supplying apparatus and method of hybrid power generation equipment |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2055385A (en) * | 1933-08-08 | 1936-09-22 | Bbc Brown Boveri & Cie | Pulverizing plant |
| FR927969A (en) * | 1946-04-26 | 1947-11-14 | Heating of the steam during expansion in a machine by the exhaust gases of a gas thermal engine | |
| US3095699A (en) * | 1958-12-18 | 1963-07-02 | Babcock & Wilcox Co | Combined gas-steam turbine power plant and method of operating the same |
| GB904536A (en) * | 1960-04-08 | 1962-08-29 | Mini Of Mines & Technical Surv | Combined steam and gas turbine plant |
| US3314231A (en) * | 1965-12-29 | 1967-04-18 | Combustion Eng | Steaming feedwater system utilizing gas turbine exhaust |
| FR2030500A5 (en) * | 1969-01-31 | 1970-11-13 | Stein Industrie | |
| CH528702A (en) * | 1970-09-08 | 1972-09-30 | Sulzer Ag | Exhaust steam generator |
| DE2044620A1 (en) * | 1970-09-09 | 1972-03-30 | Farbenfabriken Bayer Ag, 5090 Leverkusen | Azole indolines and azole indoline dyes |
| JPH0678536B2 (en) * | 1985-08-27 | 1994-10-05 | 三菱重工業株式会社 | Combined plant |
| EP0215330B1 (en) * | 1985-09-02 | 1990-01-17 | Siemens Aktiengesellschaft | Combined gas and steam turbine power station |
-
1991
- 1991-05-16 DE DE4116065A patent/DE4116065A1/en not_active Withdrawn
- 1991-12-06 WO PCT/DE1991/000952 patent/WO1992020905A1/en active IP Right Grant
- 1991-12-06 DE DE59107850T patent/DE59107850D1/en not_active Expired - Fee Related
- 1991-12-06 RU RU9193058484A patent/RU2090761C1/en active
- 1991-12-06 JP JP50027392A patent/JP3231761B2/en not_active Expired - Fee Related
- 1991-12-06 EP EP92900067A patent/EP0584072B1/en not_active Expired - Lifetime
- 1991-12-06 UA UA93002431A patent/UA27727C2/en unknown
-
1993
- 1993-11-16 US US08/153,181 patent/US5367870A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| US5367870A (en) | 1994-11-29 |
| RU2090761C1 (en) | 1997-09-20 |
| WO1992020905A1 (en) | 1992-11-26 |
| EP0584072A1 (en) | 1994-03-02 |
| UA27727C2 (en) | 2000-10-16 |
| JP3231761B2 (en) | 2001-11-26 |
| JPH06507459A (en) | 1994-08-25 |
| DE4116065A1 (en) | 1992-11-19 |
| DE59107850D1 (en) | 1996-06-27 |
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