EP0088756A1 - Method and installation for decreasing the losses when starting and shutting off a thermal station, and to increase the power available and to improve the control capacity in a thermal station. - Google Patents
Method and installation for decreasing the losses when starting and shutting off a thermal station, and to increase the power available and to improve the control capacity in a thermal station.Info
- Publication number
- EP0088756A1 EP0088756A1 EP82900106A EP82900106A EP0088756A1 EP 0088756 A1 EP0088756 A1 EP 0088756A1 EP 82900106 A EP82900106 A EP 82900106A EP 82900106 A EP82900106 A EP 82900106A EP 0088756 A1 EP0088756 A1 EP 0088756A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- steam
- power
- heat
- power plant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
- F01K3/004—Accumulation in the liquid branch of the circuit
Definitions
- the invention relates to a method and a system for reducing start-up and shutdown losses, for increasing the usable power and for improving the regulatability of a thermal power plant.
- start-up and shutdown times are up to one hour and more, depending on the state of the plant.
- many conventional power plant units have to be switched off regularly on weekends and at night. the so that the amount of heat released during these start-up and shutdown periods makes up a significant proportion of the total thermal energy converted.
- Control deviations of the electrical power of a power plant block from the power setpoint can only be compensated for with the time behavior of steam generation and the limited storage capacity of the steam generator, which decisively determines the control capacity of the power plant block.
- the invention has for its object to improve the economy of a power plant by reducing the start-up and start-up losses and increasing its usable performance. Another object of the invention is to improve the controllability of a power plant.
- This object is achieved in that one or more pressure heat stores are integrated into the water-steam cycle of the power station, which are recharged by supplying excess heat generated in the power station and increased heat demand by releasing storage heat in the water-steam cycle .
- the pressure heat accumulators are charged with start-up steam or shutdown steam of the power plant during the start-up and shutdown processes. During periods of high load or periods of increased power requirements for electrical power generation, the pressure heat stores return their charging energy to the water / steam cycle of the power plant.
- control deviations of the electrical power from the power setpoint of a power plant unit are at least partially compensated for by changes in the charging or discharging flow of the pressure heat accumulators.
- the power block the steam flows successively through a high pressure turbine 31, ei ⁇ nen intermediate superheater 34, an intermediate pressure turbine 32, and a double-flow low pressure turbine 33.
- the sator in a Konden ⁇ 1 condensate is ump through condensate p '2 and low- Medium-pressure preheaters 4a to 4n are fed into a feed water tank 6 and from there via a feed water pump 7 back into the steam generator.
- a bypass condensate store is designated.
- a pressure heat accumulator 21 is connected to the condensate system on the water side via lines 23, 26 and a pump 22 in shunt.
- a pressure line after the discharge pump 22 opens between the last medium-pressure low-pressure preheater 4n and in front of the feed water tank 6 into a condensate line 30.
- the pressure line can also lead directly into the feed water tank 6.
- the pressure heat accumulator 21 is connected via a line 27 to the medium pressure or reheater network of the power station block and / or to other economically suitable steam networks and steam systems with a higher steam pressure than it
- Steam is charged from the medium-pressure reheater network to charge the pressure heat accumulator 21 during an arrival or departure Via line 27, possibly with the interposition of a reducing station, introduced into the pressure heat store 21, which is pre-filled with cold condensate, and the condensate filling is heated.
- the anode shutdown steam heats a condensate flow in a regulated or unregulated manner directly or via a steam reducing station to a boiling water or hot water flow with which the pressure heat accumulator 21 is charged.
- the pressure heat accumulator 21 In power mode, the pressure heat accumulator 21 is charged with hot condensate via the low pressure / medium pressure preheaters 4a to 4n in low or partial load periods and the hot condensate flow from the same withdrawal 28, which also supplies the feed water tank 6 with steam, in a mixing preheating and degassing stage, not shown in the figure, immediately warmed up immediately before the pressure heat accumulator 21.
- hot condensate from the pressure heat accumulator is mixed via line 26, the expansion vessel 24 and the discharge pump 22, to the condensate flowing in line 30 to the feed water tank 6. If the pressure heat accumulator 21 is operated temporarily with increased pressure compared to the feed water tank 6, the hot storage discharge current in the expansion vessel 24 can be expanded to the pressure in the feed water tank 6 and introduced into the condensate line 30.
- the expansion steam flow is led via a line 35 directly into the feed water tank 6 or into a steam line 25 leading to the feed water tank 6.
- thermodynamic states of the discharge current and the feed water tank content are achieved.
- the expansion vessel 24 and the line 35 can be dispensed with and the discharge current can be conducted directly into the condensate line 30 with the enthalpy of the pressure heat storage content.
- a control safety circuit is therefore necessary which allows evaporation in the condensate line 30 and on the feed prevents water tank entry.
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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)
- Control Of Turbines (AREA)
Abstract
PCT No. PCT/EP81/00204 Sec. 371 Date May 13, 1983 Sec. 102(e) Date May 13, 1983 PCT Filed Dec. 23, 1981 PCT Pub. No. WO83/01090 PCT Pub. Date Mar. 31, 1983.In a method for reducing the start-up and stabilization period losses, for increasing the usable power and to improve the controllability of a thermal power plant, there are integrated into the power plant's steam cycle pressurized heat storage reservoirs which are charged by feeding them with excess heat produced in the said power plant as, for example, during the start-up and load stabilizing periods or during periods of reduced electrical power production and, when there is an increased demand for heat, the said heat storage reservoirs are discharged by the release of stored heat into the water-steam cycle. Control deviations in the electrical power while the power plant is in full operation are counterbalanced by changes in the charging and discharging streams of the pressurized heat storage reservoirs. In the apparatus for carrying out this method, pressurized heat storage reservoirs are connected, on the water-side, to the condensate system and, on the steam side, to the medium pressure of intermediate superheater network of the steam cycle or also to the power plant's medium pressure or low pressure turbine extraction points.
Description
Verfahren und Anlage zur Verringerung der An- und Abfahrver- ϊuste, zur Erhöhung der nutzbaren Leistung und zur Verbesse¬ rung der Regelfähigkeit eines Wärmekraftwerkes Process and system for reducing start-up and shutdown losses, for increasing the usable power and for improving the controllability of a thermal power plant
Die Erfindung betrifft ein Verfahren und eine Anlage zur Ver¬ ringerung der An- und Abfahrverluste, zur Erhöhung der nutz¬ baren Leistung und zur Verbesserung der Regεlfähigkeit eines Wä-rmekraftwerkes.The invention relates to a method and a system for reducing start-up and shutdown losses, for increasing the usable power and for improving the regulatability of a thermal power plant.
Bei konventionell betriebenen Wärmekraftwerken müssen während der An- und Abfahrperioden große Dampfmengen unter Umgehung der Turbinengrύppe über den Kondensator gefahren werden. Über das Kondensatorkühlwasser und den Kühlturπ** werden, dabei enorme Wärmemengen ungenutzt in die Atmosphäre abgegeben.In conventionally operated thermal power plants, large amounts of steam have to be passed over the condenser bypassing the turbine group during the start-up and shutdown periods. While enormous amounts of heat via the condenser cooling water and the Kühlturπ ** discharged unused into the atmosphere.
Insbesondere bei großen Kra twerkseinheiten betragen die An- und Abfahrzeiten abhängi'g vom Anlagenzustaπd bis zu einer Stunde und mehr. Zudem müssen viele kon entionelle Kraftwerkseinhei¬ ten regelmäßig an den Wochenenden und nachts abgeschaltet wer-
den, so daß die während dieser An- und- Abfahrperioden ungenutzt abgegebene Wärmemenge einen bedeutenden Anteil der insgesamt umgesetzten Wärmeenergie ausmacht.In the case of large power plant units in particular, the start-up and shutdown times are up to one hour and more, depending on the state of the plant. In addition, many conventional power plant units have to be switched off regularly on weekends and at night. the so that the amount of heat released during these start-up and shutdown periods makes up a significant proportion of the total thermal energy converted.
Als unbefriedigend wird auch empfunden, daß ein Kraftwerksblock nicht an seiner Leistungsgrenze, insbesondere der zulässigen Feuerwärmeleistung, geregelt betrieben werden kann, da für ei¬ nen Leistungsregelbetrieb eine gewisse Leistungs-Regelreserve zum Ausgleich von Leistungsschwankungen vorgehalten werden muß.It is also perceived as unsatisfactory that a power plant block cannot be operated in a controlled manner at its power limit, in particular the permissible heat output, since a certain power control reserve must be maintained for power control operation to compensate for power fluctuations.
Der Ausgleich von Regelabweichungen der elektrischen Leistung eines Kraftwerksblockes vom Leistungssollwert kann nur mit dem Zeitverhalten der Dampf erzeugung und der begrenzten Speicher¬ fähigkeit des Dampferzeugers erfolgen, der die Regelf hϊgkeit des Kraftwerksblockes maßgeblich bestimmt.Control deviations of the electrical power of a power plant block from the power setpoint can only be compensated for with the time behavior of steam generation and the limited storage capacity of the steam generator, which decisively determines the control capacity of the power plant block.
Der Erfindung liegt die Aufgabe zugrunde, die Wirtschaftlichkeit eines Kraf werkes zu verbessern durch Verringerung der Ab- und Anfahrverluste sowie du Erhöhung seiner nutzbaren Leistung. Ein weiteres Ziel der Erfindung ist es, die Regelfähigkeit eines Kraftwerkes zu verbessern.The invention has for its object to improve the economy of a power plant by reducing the start-up and start-up losses and increasing its usable performance. Another object of the invention is to improve the controllability of a power plant.
Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß in den Wasser-Dampf¬ kreislauf des Kraftwerkes ein oder mehrere Druckwärmspeicher integriert wer den, die durch Zufuhr von im Kraftwerk erzeugter Überschußwärme aufgeladen bei erhöhtem Wärmebedarf durch Abgabe von Speicherwärme in den Wasser-Dampf kreislauf wieder entladen werden.This object is achieved in that one or more pressure heat stores are integrated into the water-steam cycle of the power station, which are recharged by supplying excess heat generated in the power station and increased heat demand by releasing storage heat in the water-steam cycle .
Die Druckwärmespeicher werden während der An- und Abfahrvorgänge mit Anfahr dampf bzw. Abfahrdampf des Kraftwerkes aufgeladen.
Während Hochlastperioden oder Perioden erhöhter Leistungsanfor derung an die elektrische Energieerzeugung geben die Druckwärm speicher ihre Ladeenergie in den Wasser-Da pfkreislauf des. Kraftwerkes zurück.The pressure heat accumulators are charged with start-up steam or shutdown steam of the power plant during the start-up and shutdown processes. During periods of high load or periods of increased power requirements for electrical power generation, the pressure heat stores return their charging energy to the water / steam cycle of the power plant.
Mit dem erfindungsgemäßen Verfahren gelingt es somit, einen we sentlichen Anteil der bisher beim An- und Abfahre eines Kraft werksblockεs ungenutzt in die Atmosphäre abgegebenen Energie zu speichern und sie in Perioden erhöhter Leistungsanforderung zu nutzen.With the method according to the invention it is thus possible to store a substantial portion of the energy previously released into the atmosphere unused when starting and stopping a power plant block and to use it in periods of increased power demand.
Zur weiteren Erhöhung der Leistungsgrenze ist es zudem vorteil haft, den Druckwärmespeicher während 'Schwach- oder Tεillast- perioden der elektrischen Energieerzeugung mit Entnahme-Dampf aus dem Mitteldruck-Dampfnetz und/oder geeigneten Mitteldruck- und/oder Niederdruckturbinenentnahmen über Mitteldruck/Nieder¬ druck-Vorwärmer mit heißem Kondensat aufzuladen.In order to further increase the performance limit, it is also advantageous to use pressure heat storage during low or partial load periods of electrical energy generation with steam extraction from the medium-pressure steam network and / or suitable medium-pressure and / or low-pressure turbine withdrawals via medium-pressure / low-pressure Charge the preheater with hot condensate.
In weiterer Ausgestaltung des erfindungsgemäßen Verfahrens wer den Regelabweichungen der elektrischen Leistung vom Leistungs¬ sollwert eines Kraftwerksblockes zumindest teilweise, durch Än¬ derungen des Be- oder Entlsdestromes der Druckwärmespeicher ausgeglichen.In a further embodiment of the method according to the invention, the control deviations of the electrical power from the power setpoint of a power plant unit are at least partially compensated for by changes in the charging or discharging flow of the pressure heat accumulators.
Dadurch ist es darüber hinaus möglich, über das Regelvermögen der Druckwärmespeicher die notwendigerweise vorzuhaltende Lei¬ stungsregelreserve eines Kraftwerksblockes um die Regelleistung
der Druckwärmespeicher zu verkleinern- und die Blocknennleistung entsprechend zu erhöhen.As a result, it is also possible, via the control capacity of the pressure heat accumulator, to maintain the power reserve of a power plant block that is necessarily to be kept around the control power to reduce the pressure heat storage and to increase the nominal block output accordingly.
Weitere Erläuterungen zu der Erfindung sind dem in der Figur schematisch dargestellten Ausführungsbeispiel zu entnehmen. Im in der Figur beispielhaft dargestellten Kraftwerksblock durchströmt der Dampf nacheinander eine Hochdruckturbine 31, ei¬ nen Zwischenüberhitzer 34, eine Mitteldruckturbine 32 sowie eine doppelflutige Niederdruckturbine 33. Das in einem Konden¬ sator 1 anfallende Kondensat wird über Kondensat-p'umpen 2 und Niederdruck-Mitteldruckvorwärmer 4a bis 4n in einen Speise¬ wasserbehälter 6 geleitet und gelangt von dort über eine Speise¬ wasserpumpe 7 wieder in den Dampferzeuger. Mit 3 ist ein Ne¬ benschluß-Kondensatspeicher bezeichnet.Further explanations of the invention can be found in the exemplary embodiment shown schematically in the figure. In the example shown in the figure, the power block, the steam flows successively through a high pressure turbine 31, ei¬ nen intermediate superheater 34, an intermediate pressure turbine 32, and a double-flow low pressure turbine 33. The sator in a Konden¬ 1 condensate is ump through condensate p '2 and low- Medium-pressure preheaters 4a to 4n are fed into a feed water tank 6 and from there via a feed water pump 7 back into the steam generator. With 3 a bypass condensate store is designated.
Ein Druckwärmespeicher 21 ist wasserseitig über Leitungen 23, 26 und ein Pumpe 22 im Nebenschluß mit dem Kondensatsystem ver¬ bunden. Im gezeichneten Beispiel mündet eine Druckleitung nach der Entladepumpe 22 zwischen dem letzten Mitteldruck-Nieder¬ druck-Vorwärmer 4n und vor dem Speisewasserbehälter 6 in eine Kondensatleitung 30. Die Druckleitung kann jedoch auch unmittel¬ bar in den Speisewasserbehälter 6 führen.A pressure heat accumulator 21 is connected to the condensate system on the water side via lines 23, 26 and a pump 22 in shunt. In the example shown, a pressure line after the discharge pump 22 opens between the last medium-pressure low-pressure preheater 4n and in front of the feed water tank 6 into a condensate line 30. However, the pressure line can also lead directly into the feed water tank 6.
Dampfseitig ist der Druckwärmespeicher 21 einmal über eine Lei¬ tung 27 mit dem Mitteldruck- bzw. Zwischenüberhitzer-Netz des Kraftwerksblocks und/oder mit anderen wirtschaftlich geeigne¬ ten Dampfnetzen und DampfSystemen mit höherem Dampfdruck als erOn the steam side, the pressure heat accumulator 21 is connected via a line 27 to the medium pressure or reheater network of the power station block and / or to other economically suitable steam networks and steam systems with a higher steam pressure than it
C H
im Druckwärmespeicher 21 herrscht, z."B. mit einer Entnahme 28, die auch den Speisewasserbehälter 6 mit Dampf versorgt, ver¬ bunden. Zum Aufladen des Druckwärmespeichers 21 während einer An- oder Abfahrt wird Dampf aus dem Mitteldruck- Zwischenüber- hitzer-Netz über die Leitung 27, ggf. unter Zwischenschaltung einer Reduzierstation, in den mit kaltem Kondensat vorgefüllte Druckwärmespeicher 21 eingeleitet und die Kondensatfüllung er¬ hitzt. CH there is pressure in the pressure heat accumulator 21, for example with a withdrawal 28, which also supplies the feed water tank 6 with steam. Steam is charged from the medium-pressure reheater network to charge the pressure heat accumulator 21 during an arrival or departure Via line 27, possibly with the interposition of a reducing station, introduced into the pressure heat store 21, which is pre-filled with cold condensate, and the condensate filling is heated.
In einer anderen Anfahr- und Abfahrschaltung heizt der An- ode Abfahrdampf direkt oder über eine Dampfreduzierstation einen Kondensatstrom geregelt oder ungeregelt zu einem Siedewasser¬ oder Heißwasserstrom auf, mit dem der Druckwärmespeicher 21 aufgeladen wird.In another start-up and shutdown circuit, the anode shutdown steam heats a condensate flow in a regulated or unregulated manner directly or via a steam reducing station to a boiling water or hot water flow with which the pressure heat accumulator 21 is charged.
Im Leistungsbetrieb wird in Schwach- oder Teillastperioden der Druckwärmespeicher 21 über die Niederdruck/Mitteldruck-Vorwär¬ mer 4a bis 4n mit heißem Kondensat geladen und der Heißkonden¬ satstrom aus der gleichen Entnahme 28, die auch den Speisewas¬ serbehälter 6 mit Dampf versorgt, in einer in der Figur nicht gezeichneten Mischvorwär - und Entgasungsstufe unmittelbar vor dem Druckwärmespeicher 21 weiter aufgewärmt.In power mode, the pressure heat accumulator 21 is charged with hot condensate via the low pressure / medium pressure preheaters 4a to 4n in low or partial load periods and the hot condensate flow from the same withdrawal 28, which also supplies the feed water tank 6 with steam, in a mixing preheating and degassing stage, not shown in the figure, immediately warmed up immediately before the pressure heat accumulator 21.
Zur Entladung wird heißes Kondensat aus dem Druckwärmespeicher über die Leitung 26 ,- das Entspannungsgefäß 24 und die Entlade¬ pumpe 22, dem in der Leitung 30 zum Speisewasserbehälter 6 fließenden Kondensat zugemischt.
Wird der Druckwärmespeicher 21 zeitweάse mit erhöhtem Druck ge genüber dem Speisewasserbehälter 6 betrieben, so kann der heiß Speicher-Entladestrom in dem Entspannungsgefäß 24 auf den Druc im Speisewasserbehälter 6 entspannt und in die Kondensatleitun 30 eingeleitet werden.To discharge, hot condensate from the pressure heat accumulator is mixed via line 26, the expansion vessel 24 and the discharge pump 22, to the condensate flowing in line 30 to the feed water tank 6. If the pressure heat accumulator 21 is operated temporarily with increased pressure compared to the feed water tank 6, the hot storage discharge current in the expansion vessel 24 can be expanded to the pressure in the feed water tank 6 and introduced into the condensate line 30.
Der Entspannungsdampfström wird über eine Leitung 35 unmittelb in den Speisewasserbehälter 6 bzw. in eine zum Speisewasserbe¬ hälter 6 führende Dampfleitung 25 geführt.The expansion steam flow is led via a line 35 directly into the feed water tank 6 or into a steam line 25 leading to the feed water tank 6.
Damit werden gleiche thermodynamische Zustände von Entladestro und Speisewasserbehälterinhalt erreicht.In this way, the same thermodynamic states of the discharge current and the feed water tank content are achieved.
In einer vereinfachten Schaltung können das Entspannungsgefäß 24 und die Leitung 35 entfallen und der Entladestrom kann mit der Entalpie des Druckwärmespeicherinhaltes direkt in die Kon¬ densatleitung 30 geführt werden. Damit ist allerdings eine Be¬ grenzung des Entladestromes im unteren Lastbereich verbunden, wenn der Druck im Druckwärmespeicher 21 größer ist als im Spei sewasserbehälter 6. In dieser vereinfachten wärmetechnischen Schaltung wird daher eine Regelsicherheitsschaltung notwendig, die eine Ausdampfung in der Kondensatleitung 30 und am Speise¬ wasserbehältereintritt verhindert.In a simplified circuit, the expansion vessel 24 and the line 35 can be dispensed with and the discharge current can be conducted directly into the condensate line 30 with the enthalpy of the pressure heat storage content. However, this limits the discharge current in the lower load range if the pressure in the pressure heat accumulator 21 is greater than in the feed water tank 6. In this simplified thermal circuit, a control safety circuit is therefore necessary which allows evaporation in the condensate line 30 and on the feed prevents water tank entry.
Durch den Einsatz der Be- und Entladeströme des Druckwärmespei chers 21 als Stellströme in einer Leistungsregelung können wäh
rend des Leistungsbetriebes des Kraftwerkes auftretende Regel¬ abweichungen der elektrischen Leistung vom Leistungssollwert im gebotenen Leistungsregelbereich einfach und schnell ausger-egelt werden.By using the loading and unloading currents of the Druckwärmespei chers 21 as actuating currents in a power control can wäh Control deviations of the electrical power from the power setpoint in the power control range provided can be corrected simply and quickly during the power operation of the power plant.
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Claims
P'atentansprüche :Patent claims:
1-. Verfahren zur Verringerung der An- und Abfahrverluste, zur Erhöhung der nutzbaren Leistung und zur Verbesserung der Regelfähigkeit eines Wärme¬ kraftwerkes, dadurch gekennzeichnet, daß in den VJasser-Dampfkreislauf d Kraftwerkes ein oder mehrere Druckwärmespeicher integriert werden, die durch Zufuhr von im Kraftwerk erzeugter Überschußwärme aufgeladen und b erhöhtem Wärmebedarf durch Abgabe von Speicherwärme in den Wasser-Dampf kreislauf wieder entladen werden.1-. Process for reducing the start-up and shutdown losses, for increasing the usable power and for improving the controllability of a thermal power plant, characterized in that one or more pressure heat stores are integrated into the VJasser steam cycle of the power plant, which supply excess heat generated in the power plant charged and b increased heat demand by releasing storage heat into the water-steam cycle.
2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß die Druckwärme¬ speicher während der An- und Abfahrvorgänge mit Anfahr- bzw. Abfahr¬ dampf des Kraftwerkes aufqeladen werden. ^*-rz-n -"Ϊ—- 2. The method according to claim 1, characterized in that the Druckwärme¬ accumulator are charged during the start-up and shutdown processes with start-up or shutdown steam of the power plant. ^ * -rz- n - " Ϊ —-
3. Verfahren nach Anspruch 2, dadurch gekennzeichne , daß die Druckwärmespeicher durch gleichzeitiges Einleiten von kal¬ tem Kondensat und An- bzw. Abfahrdampf aufgeladen werden.3. The method according to claim 2, characterized in that the pressure heat accumulator are charged by simultaneously introducing kal¬ tem condensate and start-up or shutdown steam.
4. Verfahren nach Anspruch 2, dadurch gekennzeichnet, daß die Druckwärmespeicher durch Aufwärmen einer Kalt-Kondensatfül- lung mit An- bzw. Abfahrdampf aufgeladen werden.4. The method according to claim 2, characterized in that the pressure heat accumulator are charged by warming up a cold condensate filling with start-up and shutdown steam.
5. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß die Druckwärmespeicher im Leistungsbetrieb in Schwach- und/oder Teillastperioden der elektrischen Energieerzeugung und/oder bei vorübergehenden Leistungsminderungen mit heißem Konden¬ sat aus Mitteldruck-/Niederdruck-Vorwärmern, die an Mittel- druck/Niederdruckturbinenentπahmen angeschlossen sind, und Entnahmedampf aus einer Mitteldruck-Turbiπenentnahme aufge-5. The method according to claim 1, characterized in that the pressure heat accumulator in power operation in low and / or partial load periods of electrical power generation and / or in the case of temporary power reductions with hot condensate sat from medium pressure / low pressure preheaters connected to medium pressure / Low-pressure turbine extractors are connected, and extraction steam from a medium-pressure turbine extraction
"- -laden werden."- -load.
6. Verfahren nach einem, der Ansprüche 1 bis 5, dadurch gekenn¬ zeichnet, daß im Leistungsbetrieb die Druckwärmespeicher in Hochlas'tperioden und/oder Perioden erhöhter Lastanforderung der elektrischen Energieerzeugung und/oder bei vorübergehen¬ den Leistungserhöhungen in den Wasser-Dampfkreislauf vor ei¬ nem Speisewasserbehälter oder unmittelbar in den Speisewas¬ serbehälter entladen werden.6. The method according to any one of claims 1 to 5, characterized gekenn¬ characterized in that the pressure heat storage in Hochlast ' tperiods and / or periods of increased load requirement of electrical power generation and / or in the case of transient increases in power in the water-steam cycle before egg ¬ be discharged into a feed water tank or directly into the feed water tank.
7. Verfahren nach einem der Ansprüche 1 bis 6, dadurch gekenn¬ zeichnet, daß in dem Wasser-Dampf reislauf ein Nebenschluß- Kondensatspeicher vorgesehen ist, und daß über den Wasser- Dampfkreislauf ein Massenaustausch im Wechsel zwischen den Druckwärmespeichern und dem Nebeπschluß-Kondensatspeich'er erfolgt.7. The method according to any one of claims 1 to 6, characterized gekenn¬ characterized in that in the water-steam cycle a shunt Is condensate reservoir, and in that via the water-steam cycle, a mass exchange alternating between the pressure and the heat storage Nebeπschluß-Kondensatspeich 'er.
8. Verfahren nach Anspruch 6 und/oder 7, dadurch gekennzeichne daß der thermodynamische Zustand des Entladestromes aus den Druckwärmespeichern dem ther odynamischen Zustand des Spei- sewasserbehälter-Inhaltes angeglichen wird.8. The method according to claim 6 and / or 7, characterized in that the thermodynamic state of the discharge current from the pressure heat accumulators is adjusted to the thermodynamic state of the feed water tank content.
9. Verfahren nach einem der Ansprüche 1 bis 8, dadurch gekenn¬ zeichnet, daß Regelabweichungen der elektrischen Leistung vom Leistungssollwert durch Änderungen des Be- bzw. Entlade¬ stromes der Druckwärmespeicher ausgeglichen werden.9. The method according to any one of claims 1 to 8, characterized gekenn¬ characterized in that control deviations of the electrical power from the power setpoint are compensated by changes in the loading or Entlade¬ current of the heat accumulator.
10. Anlage zur Durchführung des Verfahrens nach den Ansprüchen10. Plant for performing the method according to the claims
1 bis 9, dadurch gekennzeichnet, daß ein oder mehrere Druck¬ wärmespeicher (21) wasserseitig im Nebenschluß über Lei¬ tungen (23), (26) und eine Pumpe (22) mit einem Kondensat¬ system -und dampfseitig mit einem Mitteldruck- oder Zwi- schenüberhitzer-Metz eines Wasser-Dampfkreisiaufes und/oder Mitteldruck- und/oder Niederdruckturbinenentnahmen eines Kraftwerkes verbunden sind.1 to 9, characterized in that one or more Druck¬ heat accumulators (21) on the water side bypass via lines (23), (26) and a pump (22) with a condensate system and steam side with a medium pressure or Intermediate superheater-Metz of a water-steam circuit and / or medium-pressure and / or low-pressure turbine withdrawals from a power plant.
11. Anlage nach Anspruch 10, dadurch gekennzeichnet, daß die11. Plant according to claim 10, characterized in that the
Druckwärmespeicher (21) wasserseitig im Nebenschluß über die Leitungen (23), (26) und die Pumpe (22) mit einer Konden-Compressed heat accumulator (21) on the water side in a shunt via the lines (23), (26) and the pump (22) with a condenser
OMPI 1JOMPI 1y
satleitung (30) hinter einem letzten Mitteldruck-Nieder- druckvorwämer (4n) und vor einem Speisewasserbehälter (6) verbunden sind.sat line (30) behind a last medium-pressure low-pressure preheater (4n) and in front of a feed water tank (6).
12. Anlage nach Anspruch 10, dadurch gekennzeichnet, daß die12. Plant according to claim 10, characterized in that the
Druckwärmespeicher (21) wasserseitig im Nebenschluß über die Leitungen (23), (26) und die Pumpe (22) mit dem Speisewas¬ serbehälter (6) verbunden sind.Compressed heat accumulators (21) on the water side are connected to the feed water tank (6) via the lines (23), (26) and the pump (22).
13. Anlage nach einem der Ansprüche 10 bis 12, dadurch gekenn¬ zeichnet, daß zwischen die Durckwärmespeicher (21) und den Speisewasserbehälter (6) ein Entspannungsgefäß (24) geschal¬ tet ist, und daß das Entspannungsgefäß (24) dampfseitig mit dem Dampfraum des Speisewasserbehälters (6) oder einer Dampf anschlußleitung (25) zum Speisewasserbehälter (6) oder ei¬ nem Dampfnetz mit niedrigerem Dampfdruck verbunden ist. 13. Plant according to one of claims 10 to 12, characterized gekenn¬ characterized in that between the pressure heat accumulator (21) and the feed water tank (6) a relaxation vessel (24) is switched, and that the expansion vessel (24) on the steam side with the steam chamber the feed water tank (6) or a steam connection line (25) to the feed water tank (6) or a steam network with a lower steam pressure is connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT82900106T ATE18931T1 (en) | 1981-09-19 | 1981-12-23 | PROCESS AND PLANT FOR REDUCING START-UP AND SHUT-DOWN LOSSES, INCREASING THE USABLE PERFORMANCE AND IMPROVING THE CONTROL ABILITY OF A THERMAL POWER PLANT. |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3137371 | 1981-09-19 | ||
| DE3137371A DE3137371C2 (en) | 1981-09-19 | 1981-09-19 | System to reduce start-up and shutdown losses, to increase the usable power and to improve the controllability of a thermal power plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0088756A1 true EP0088756A1 (en) | 1983-09-21 |
| EP0088756B1 EP0088756B1 (en) | 1986-04-02 |
Family
ID=6142158
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP82900106A Expired EP0088756B1 (en) | 1981-09-19 | 1981-12-23 | Method and installation for decreasing the losses when starting and shutting off a thermal station, and to increase the power available and to improve the control capacity in a thermal station |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US4549401A (en) |
| EP (1) | EP0088756B1 (en) |
| JP (1) | JPS58501473A (en) |
| AT (1) | ATE18931T1 (en) |
| DE (1) | DE3137371C2 (en) |
| WO (1) | WO1983001090A1 (en) |
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|---|---|---|---|---|
| DE4124678A1 (en) * | 1990-08-21 | 1992-02-27 | Abb Patent Gmbh | METHOD AND DEVICE FOR RESTORING THE TURBINE CONTROL RESERVE AFTER REGULATING A PERFORMANCE SETPOINT CHANGE IN A STEAM POWER PLANT |
| JP2006233931A (en) * | 2005-02-28 | 2006-09-07 | Miura Co Ltd | Boiler drive electric power supply system |
| US20090192530A1 (en) | 2008-01-29 | 2009-07-30 | Insightra Medical, Inc. | Fortified mesh for tissue repair |
| US8616323B1 (en) | 2009-03-11 | 2013-12-31 | Echogen Power Systems | Hybrid power systems |
| WO2010121255A1 (en) | 2009-04-17 | 2010-10-21 | Echogen Power Systems | System and method for managing thermal issues in gas turbine engines |
| EP2446122B1 (en) | 2009-06-22 | 2017-08-16 | Echogen Power Systems, Inc. | System and method for managing thermal issues in one or more industrial processes |
| WO2011017476A1 (en) | 2009-08-04 | 2011-02-10 | Echogen Power Systems Inc. | Heat pump with integral solar collector |
| US8869531B2 (en) | 2009-09-17 | 2014-10-28 | Echogen Power Systems, Llc | Heat engines with cascade cycles |
| US8813497B2 (en) | 2009-09-17 | 2014-08-26 | Echogen Power Systems, Llc | Automated mass management control |
| US8613195B2 (en) | 2009-09-17 | 2013-12-24 | Echogen Power Systems, Llc | Heat engine and heat to electricity systems and methods with working fluid mass management control |
| US8096128B2 (en) | 2009-09-17 | 2012-01-17 | Echogen Power Systems | Heat engine and heat to electricity systems and methods |
| US8616001B2 (en) | 2010-11-29 | 2013-12-31 | Echogen Power Systems, Llc | Driven starter pump and start sequence |
| US8857186B2 (en) | 2010-11-29 | 2014-10-14 | Echogen Power Systems, L.L.C. | Heat engine cycles for high ambient conditions |
| US8783034B2 (en) | 2011-11-07 | 2014-07-22 | Echogen Power Systems, Llc | Hot day cycle |
| WO2013055391A1 (en) | 2011-10-03 | 2013-04-18 | Echogen Power Systems, Llc | Carbon dioxide refrigeration cycle |
| PL2589761T3 (en) | 2011-11-03 | 2017-10-31 | General Electric Technology Gmbh | Steam power plant with heat reservoir and method for operating a steam power plant |
| CN104302975B (en) | 2012-01-19 | 2016-11-16 | 西门子公司 | Auxiliary steam maker system for power plant |
| BR112015003646A2 (en) | 2012-08-20 | 2017-07-04 | Echogen Power Systems Llc | supercritical working fluid circuit with one turbo pump and one starter pump in configuration series |
| US9341084B2 (en) | 2012-10-12 | 2016-05-17 | Echogen Power Systems, Llc | Supercritical carbon dioxide power cycle for waste heat recovery |
| US9118226B2 (en) | 2012-10-12 | 2015-08-25 | Echogen Power Systems, Llc | Heat engine system with a supercritical working fluid and processes thereof |
| US9322295B2 (en) | 2012-10-17 | 2016-04-26 | General Electric Company | Thermal energy storage unit with steam and gas turbine system |
| US9376962B2 (en) | 2012-12-14 | 2016-06-28 | General Electric Company | Fuel gas heating with thermal energy storage |
| US9638065B2 (en) | 2013-01-28 | 2017-05-02 | Echogen Power Systems, Llc | Methods for reducing wear on components of a heat engine system at startup |
| CA2899163C (en) | 2013-01-28 | 2021-08-10 | Echogen Power Systems, L.L.C. | Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle |
| KR20160028999A (en) | 2013-03-04 | 2016-03-14 | 에코진 파워 시스템스, 엘엘씨 | Heat engine systems with high net power supercritical carbon dioxide circuits |
| US10570777B2 (en) | 2014-11-03 | 2020-02-25 | Echogen Power Systems, Llc | Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system |
| US11187112B2 (en) | 2018-06-27 | 2021-11-30 | Echogen Power Systems Llc | Systems and methods for generating electricity via a pumped thermal energy storage system |
| US11435120B2 (en) | 2020-05-05 | 2022-09-06 | Echogen Power Systems (Delaware), Inc. | Split expansion heat pump cycle |
| MA61232A1 (en) | 2020-12-09 | 2024-05-31 | Supercritical Storage Company Inc | THREE-TANK ELECTRIC THERMAL ENERGY STORAGE SYSTEM |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1770256A (en) * | 1924-12-31 | 1930-07-08 | Smekal Josef | Steam-accumulator plant |
| DE628717C (en) * | 1926-10-13 | 1936-04-15 | Christian Christians | Steam system to compensate for fluctuations |
| GB446061A (en) * | 1935-08-22 | 1936-04-23 | Ruths Arca Accumulators Ltd | Improvements in or relating to steam plants including hot-water accumulators |
| CH204975A (en) * | 1938-01-21 | 1939-05-31 | Sulzer Ag | Method and device for operating a high-pressure steam power plant. |
| NL78792C (en) * | 1952-01-05 | |||
| GB887274A (en) * | 1957-03-02 | 1962-01-17 | Siemens Schuckertwerkd Ag | A steam boiler and turbine installation |
| DE1128437B (en) * | 1960-05-13 | 1962-04-26 | Siemens Ag | Steam power plant, in particular block plant with once-through boiler |
| US3564677A (en) * | 1967-11-06 | 1971-02-23 | Johnson & Johnson | Method and apparatus of treating material to change its configuration |
| JPS4711600U (en) * | 1971-03-01 | 1972-10-11 | ||
| DE2609622A1 (en) * | 1976-03-09 | 1977-09-15 | Babcock Ag | METHOD AND DEVICE FOR STORAGE OF ENERGY IN POWER PLANTS |
| DE2620023A1 (en) * | 1976-05-06 | 1977-11-17 | Babcock Ag | METHOD AND DEVICE FOR STORAGE OF ENERGY IN POWER PLANTS |
| DE2907068C2 (en) * | 1978-05-09 | 1983-09-15 | BBC Aktiengesellschaft Brown, Boveri & Cie., 5401 Baden, Aargau | Steam power plant for base load operation with equipment to cover load peaks |
-
1981
- 1981-09-19 DE DE3137371A patent/DE3137371C2/en not_active Expired
- 1981-12-23 JP JP57500196A patent/JPS58501473A/en active Pending
- 1981-12-23 AT AT82900106T patent/ATE18931T1/en not_active IP Right Cessation
- 1981-12-23 EP EP82900106A patent/EP0088756B1/en not_active Expired
- 1981-12-23 WO PCT/EP1981/000204 patent/WO1983001090A1/en not_active Application Discontinuation
- 1981-12-23 US US06/494,765 patent/US4549401A/en not_active Expired - Fee Related
Non-Patent Citations (1)
| Title |
|---|
| See references of WO8301090A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58501473A (en) | 1983-09-01 |
| DE3137371C2 (en) | 1984-06-20 |
| WO1983001090A1 (en) | 1983-03-31 |
| EP0088756B1 (en) | 1986-04-02 |
| DE3137371A1 (en) | 1983-04-14 |
| US4549401A (en) | 1985-10-29 |
| ATE18931T1 (en) | 1986-04-15 |
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