EP0584072A1 - GAS AND STEAM TURBINE SYSTEM. - Google Patents
GAS AND STEAM TURBINE SYSTEM.Info
- Publication number
- EP0584072A1 EP0584072A1 EP92900067A EP92900067A EP0584072A1 EP 0584072 A1 EP0584072 A1 EP 0584072A1 EP 92900067 A EP92900067 A EP 92900067A EP 92900067 A EP92900067 A EP 92900067A EP 0584072 A1 EP0584072 A1 EP 0584072A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gas
- steam
- turbine
- heat exchanger
- air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- 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 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.
- 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 aim is to enable existing modules to be used to the greatest possible extent.
- a first adjustable partial quantity of the exhaust gas cooled in a heat exchanger can be supplied as combustion air from the gas turbine of the combustion system, in that a second adjustable partial quantity of the cooled exhaust gas can be supplied to a heat exchanger for heating air for the coal mill and that a third adjustable subset of the cooled waste gases can be mixed with the flue gas flowing through the steam generator from the furnace.
- the heat exchanger or cooler through which the exhaust gas from the gas turbine flows is expediently switched into 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 fed to the first part of the cooled exhaust gas from the gas turbine.
- the air warmed up 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 partial quantities additional use of the heat contained in the exhaust gases 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 illustration 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 coupled generator 5 and a gas turbine 6 connected upstream of the steam generator 2 with a coupled generator 7.
- the steam generator 2 comprises a firing 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 gas 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 effluent from the gas turbine 6 hot exhaust gas A is cooled in heat exchanger 20 to about 400 * C, so that the walls of the heated as Rauch ⁇ gas channels formed partial flow lines 26, 27 and 28 is not more than 400 "C
- the exhaust gas a is divided into three adjustable subsets tl, t2 and t3.
- the partial quantity tl flowing via the partial flow line 26 is determined by the combustion system 8's need for combustion air, i. H . in particular depending on the operating state of the system.
- the air compressor 35 is connected to the partial flow line 26 via an air line 36 connected to the heat exchanger 29 on the secondary side. To set the required amount of air is in the air line
- the part of the exhaust gases a not required for the combustion system 8 is passed 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 t.3 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 da s 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 then mixed in 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 in the hot
- 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 for different operating conditions. 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)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Air Supply (AREA)
Abstract
L'installation comprend un générateur de vapeur (2) monté à la suite de la turbine à gaz (6) côté évacuation des gaz, pour la production de vapeur pour la turbine à vapeur (4) dans un circuit eau-vapeur (3), le générateur de vapeur (2) présentant un fourneau (8) monté à la suite d'un broyeur à charbon (10). L'invention a pour but d'obtenir une rendement global élevé dans une installation existante de turbine à vapeur à laquelle est adjointe une turbine à gaz. Conformément à l'invention, une première quantité partielle réglable (t1) du gaz d'échappement (a) provenant de la turbine à gaz (6), refroidi dans un premier échangeur de chaleur (20), est envoyée dans le fourneau (8) en tant qu'air de combustion. Une deuxième quantité partielle réglable (t2) du gaz d'échappement refroidi (a) est envoyée dans un deuxième échangeur de chaleur (29) pour le réchauffage de l'air (1) pour le broyeur à charbon (10). Une troisième quantité partielle réglable (t3) du gaz d'échappement refroidi (a) est mélangée aux gaz de fumée (r) provenant du fourneau (8) et traversant le générateur de vapeur (2).The installation comprises a steam generator (2) mounted after the gas turbine (6) on the gas discharge side, for the production of steam for the steam turbine (4) in a water-steam circuit (3) , the steam generator (2) having a furnace (8) mounted after a coal mill (10). The object of the invention is to obtain a high overall efficiency in an existing steam turbine installation to which a gas turbine is added. According to the invention, a first adjustable partial quantity (t1) of the exhaust gas (a) from the gas turbine (6), cooled in a first heat exchanger (20), is sent into the furnace (8). ) as combustion air. A second adjustable partial quantity (t2) of the cooled exhaust gas (a) is sent to a second heat exchanger (29) for reheating the air (1) for the coal mill (10). A third adjustable partial quantity (t3) of the cooled exhaust gas (a) is mixed with the flue gases (r) coming from the furnace (8) and passing through the steam generator (2).
Description
Gas- und DampfturbinenanlageGas and steam turbine plant
Die Erfindung betrifft eine Gas- und Dampfturbinenanlage mit einem der Gasturbine abgasseitig nachgeschalteten Dampferzeu- ger zur Erzeugung von Dampf 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 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.
Bei der Planung und beim Bau einer Gas- und Da pfturbinen- anläge, insbesondere bei einer An opplung einer Gasturbinen¬ anlage an eine bestehende Dampfturbinenanlage mit einer 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 Gas¬ turbine üblicherweise als Verbrennungsluft für die Feuerungs¬ anlage des Dampferzeugers genutzt wird, führt eine Änderung der Dampferzeugerleistung, z.B. durch eine Absenkung derWhen planning and building a gas and steam turbine system, especially when a gas turbine system is connected to an existing steam turbine system with a combustion system, the interdependent performance of the gas turbine and the steam turbine and the steam generator must be achieved in order to achieve a high overall efficiency be coordinated. 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, e.g. by lowering the
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.Flame temperature of the furnace, to a mismatch between the amount of exhaust gas from the gas turbine and the amount of air or oxygen required for the furnace. As a result, the efficiency of the system can only be optimized to a limited extent, particularly 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 weitest- gehende 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 aim is to enable existing modules to be used to the greatest possible extent.
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 einstell¬ bare Teilmenge des abgekühlten Abgases einem Wärmetauscher zum Aufwärmen von Luft für die Kohlemühle zuführbar ist und daß eine dritte einstellbare Teilmenge des abgekühlten Ab- gases dem den Dampferzeuger durchströmenden Rauchgas aus der Feuerungsanlage zumischbar ist.This object is achieved according to the invention in that a first adjustable partial quantity of the exhaust gas cooled in a heat exchanger can be supplied as combustion air from the gas turbine of the combustion system, in that a second adjustable partial quantity of the cooled exhaust gas can be supplied to a heat exchanger for heating air for the coal mill and that a third adjustable subset of the cooled waste gases can be mixed with the flue gas flowing through the steam generator from the furnace.
Zur Erzeugung von zusätzlichem Dampf für die Dampfturbine ist zweckmaßigerweise der vom Abgas aus der Gasturbine durchström¬ te Wärmetauscher oder Kühler in den Wasser-Dampf-Kreislauf der Dampfturbine geschaltet. Dabei wird das Abgas aus der Gas¬ turbine vorteilhafterweise auf die bei der Auslegung der be¬ stehenden Rauchgaskanäle der Dampfturbinenanlage zugelassene Höchsttemperatur abgekühlt.To generate additional steam for the steam turbine, the heat exchanger or cooler through which the exhaust gas from the gas turbine flows is expediently switched into 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 auf¬ gewärmten Luft der ersten Teilmenge des abgekühlten Abgases aus der Gasturbine zuführbar.To enrich the combustion air for the furnace with oxygen, part of the air warmed up in the second heat exchanger can be fed to the first part of the cooled exhaust gas from the gas turbine.
Zur Regelung der Temperatur in der Kohlemühle ist der im zwei¬ ten Wärmetauscher aufgewärmten Luft für die Kohlemühle kalte Luft zumischbar.To regulate the temperature in the coal mill, the air warmed up 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 ver- mieden ist und daß andererseits durch eine Aufteilung der ab¬ gekühlten Abgase in regelbare Teilmengen eine zusätzliche Nutzung der in den Abgasen enthaltenen Wärme für den Gesamt¬ prozeß und damit ein ho her Gesamtwirkungsgrad der Anlage unabhängig vom Betriebszustand errei cht 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 partial quantities additional use of the heat contained in the exhaust gases 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 Zei chnung ein Ausführungsbeispiel beschrieben . Darin zeigt die Figur in schematischer Darstellung eine Gas- und Dampf¬ turbinenanlage mit einer Aufteilung der Abgase aus der Gas- turbine 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 illustration 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 Wa sser-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-steam circuit 3 with a coupled generator 5 and a gas turbine 6 connected upstream of the steam generator 2 with a coupled generator 7. The steam generator 2 comprises a firing system 8 which is connected to a coal mill 10 via a fuel line 9.
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 an¬ geordneter Vorwärmer 17 geschaltet. Der Vorwärmer 17 ist aus- gangsseitig über einen ersten Zweig 18, in den ein Ventil 19 geschaltet ist, an einen vom heißen Abgas a aus der Gasturbi¬ ne 6 beheizten Wärmetauscher 20 angeschlossen. Der Vorwärmer 17 ist außerdem über einen zweiten Zweig 22 an eine im Dampf¬ erzeuger 2 im Bereich eines Feuerraums 23 angeordnete Heiz- einrichtung 24 angeschlossen.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. On the output side, 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.
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 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.
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 außer¬ dem 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 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 gas 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.
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 Rauch¬ gaskanäle ausgebildeten Teilstromleitungen 26, 27 und 28 nicht über 400" C aufgeheizt werden. In Strömungsrichtung der Ab gase a hinter dem Wärmetauscher 20 wird das Abgas a i n drei einstellbare Teilmengen tl , t2 u nd t3 a ufgeteilt. Dabei wird die über die Teilstromleitung 26 strömend e Teilmenge tl auf den Bedarf der Feuerungsanlage 8 an Verbrennungsluft , d . h . insbesondere in Abhängigkeit vom Be tri ebszustand der Anlage , eingestellt. Dabei kann der Tei lmenge tl verdichtete und im Wärmetauscher 29 vorgewärmte Luft L aus einem LuftverdichterDuring operation of the combined cycle power plant, the effluent from the gas turbine 6 hot exhaust gas A is cooled in heat exchanger 20 to about 400 * C, so that the walls of the heated as Rauch¬ gas channels formed partial flow lines 26, 27 and 28 is not more than 400 "C In the direction of flow of the From gases a behind the heat exchanger 20, the exhaust gas a is divided into three adjustable subsets tl, t2 and t3. In this case, the partial quantity tl flowing via the partial flow line 26 is determined by the combustion system 8's need for combustion air, i. H . in particular depending on the operating state of the system. In this case, the partial quantity T1 compressed and preheated air L in the heat exchanger 29 from an air compressor
35 zugemischt werden. Da zu ist der Luftverdichter 35 über eine sekundärseitig in den Wärmetauscher 29 geschaltete Luft- leitung 36 an die Teilstromleitung 26 angeschlossen. Zur Ein¬ stellung der erforderlichen Luftmenge ist in die Luftleitung35 are added. The air compressor 35 is connected to the partial flow line 26 via an air line 36 connected to the heat exchanger 29 on the secondary side. To set the required amount of air is in the air line
36 eine Klappe 37 geschaltet.36 a flap 37 switched.
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 üb er den zweiten Wärmetauscher 29 geführt. Dabei wird die über die Teilstromleitung 27 strömende Teil- menge t.3 des Abgases a dem in der Fe uerungsanlage 8 erzeugten Rauchgas r zugemischt. Die Teilmenge t3 des Abgases a und da s Rauchgas r verlassen den Dampferzeuger 2 üb er 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 passed 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 t.3 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 da s 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).
Die über die Teilstromleitung 28 gefüh rte einstellbare Teil¬ menge t2 des Abgases a erwärmt im Wärmetauscher 29 die über die Luftleitung 36 strömende Luft L u nd 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 partial flow line 28 heats the air L flowing through the air line 36 in the heat exchanger 29 and is then mixed in with the flue gas r flowing out of the steam generator 2 behind the gas filter 40.
Die von der zweiten Teilmenge t2 im Wärmetauscher 29 aufge¬ wärmte Luft L aus dem Luftverdichter 36 strömt über einen Zweig 41 der Luftleitung 36 in die Ko hlemühle 10. Sie dient dort einerseits als Wärmemedium zum Tr ocknen der der Ko hle¬ mühle 10 über eine Kohleleitung 42 zugefüh rten Kohle k und andererseits als Transportmittel zum Zufüh ren der in der Kohlemühle 10 zermahlenen Ko hle k üb er 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 up by the second subset t2 in the heat exchanger 29 from the air compressor 36 flows via a branch 41 of the air line 36 into the coal mill 10 Coal line 42 supplied coal k and, on the other hand, as a means of transport for feeding the coal milled in the coal mill 10, the fuel line 9 into the firing system 8 outgoing branch 41, in which a flap 44 is connected, opens a cold air line 45 connected in front of the heat exchanger 29 to the air line 36, into which a flap 46 is connected. 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.
Das Rauchgas r aus der Feuerungsanlage 8 und die über die Teilstromleitung 27 in den Dampferzeuger 2 einströmende Teil¬ menge 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 heißenThe 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. For this purpose, 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 in the hot
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 Wärmetau- scher 20 ebenfalls verdampft und überhitzt und der Dampfturbi¬ ne 4 zugeführt. Dort wird der überhitzte Dampf entspannt und anschließend im Kondensator 15 kondensiert.Flue gases r from the furnace 8 heated heating surfaces 24 evaporated and overheated. 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.
Durch die erfindungsgemäße Aufteilung der abgekühlten Abgase a aus der Gasturbine 6 in drei einstellbare Teilmengen tl, t2 und t3 ist einerseits die Gasturbine 6 von den Anforderungen der Feuerungsanlage bezüglich der bei unterschiedlichen Be- triebszuständen erforderlichen Luftmenge entkoppelt. Anderer¬ seits kann der Dampferzeuger 2 und damit der Dampfprozeß un- abhängig 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 for different operating conditions. 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
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4116065A DE4116065A1 (en) | 1991-05-16 | 1991-05-16 | GAS AND STEAM TURBINE SYSTEM |
| DE4116065 | 1991-05-16 | ||
| PCT/DE1991/000952 WO1992020905A1 (en) | 1991-05-16 | 1991-12-06 | Gas-turbine/steam-turbine installation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0584072A1 true EP0584072A1 (en) | 1994-03-02 |
| EP0584072B1 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 (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08503060A (en) * | 1992-11-17 | 1996-04-02 | アパラーテバウ ローテミューレ ブラント ウント クリッツラー ゲゼルシャフト ミット ベシュレンクテル ハフツング | Combustion equipment |
| 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 |
| RU2124134C1 (en) * | 1998-02-13 | 1998-12-27 | Буров Валерий Дмитриевич | Combination steam-gas power plant and method of its operation |
| 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 |
Family Cites Families (10)
| 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 not_active Ceased
- 1991-12-06 EP EP92900067A patent/EP0584072B1/en not_active Expired - Lifetime
- 1991-12-06 DE DE59107850T patent/DE59107850D1/en not_active Expired - Fee Related
- 1991-12-06 UA UA93002431A patent/UA27727C2/en unknown
- 1991-12-06 RU RU9193058484A patent/RU2090761C1/en active
- 1991-12-06 JP JP50027392A patent/JP3231761B2/en not_active Expired - Fee Related
-
1993
- 1993-11-16 US US08/153,181 patent/US5367870A/en not_active Expired - Fee Related
Non-Patent Citations (1)
| Title |
|---|
| See references of WO9220905A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| WO1992020905A1 (en) | 1992-11-26 |
| UA27727C2 (en) | 2000-10-16 |
| RU2090761C1 (en) | 1997-09-20 |
| DE59107850D1 (en) | 1996-06-27 |
| US5367870A (en) | 1994-11-29 |
| JP3231761B2 (en) | 2001-11-26 |
| DE4116065A1 (en) | 1992-11-19 |
| EP0584072B1 (en) | 1996-05-22 |
| JPH06507459A (en) | 1994-08-25 |
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