EP2462378B1 - Method for operating a forced-flow steam generator operating at a steam temperature above 650°c and forced-flow steam generator - Google Patents
Method for operating a forced-flow steam generator operating at a steam temperature above 650°c and forced-flow steam generator Download PDFInfo
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- EP2462378B1 EP2462378B1 EP10752274.0A EP10752274A EP2462378B1 EP 2462378 B1 EP2462378 B1 EP 2462378B1 EP 10752274 A EP10752274 A EP 10752274A EP 2462378 B1 EP2462378 B1 EP 2462378B1
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- steam
- working medium
- transfer system
- preheater
- heat transfer
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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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
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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
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/02—Controlling, e.g. stopping or starting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B29/00—Steam boilers of forced-flow type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
- F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
- F22D1/32—Feed-water heaters, i.e. economisers or like preheaters arranged to be heated by steam, e.g. bled from turbines
- F22D1/325—Schematic arrangements or control devices therefor
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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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
Definitions
- the invention relates to a method for operating a forced-circulation steam generator operating in sliding pressure and with a steam temperature of over 650 ° C and lowering the forced minimum flow, wherein the forced-circulation steam generator is integrated into the water / steam cycle of a power plant and the economizer of the forced-circulation steam generator in water / Steam cycle direction seen upstream at least one HD preheater and / or a heat transfer system for further preheating of the feed water, wherein the / the HP preheater is heated by turbine steam and the heat transfer system external heat to the circulation medium water / steam is supplied.
- Continuous or forced circulation steam generators are from the publication " Kraftwerkstechnik”, Springer-Verlag, 2nd edition 1994, Chapter 4.4.2.4-Forced circulation (pages 171 to 174 ), Prof. Dr.-Ing. Karl Strauss known, which are used in power plants for the production of electrical energy by combustion of, for example, fossil fuels.
- a continuous flow or continuous flow steam generator the heating of the combustion chamber or the throttle cable forming evaporator tubes - in contrast to a natural circulation or forced circulation steam generator with only partial evaporation of circulating water-steam mixture - leads to evaporation of the flow or working medium in the evaporator tubes in a single pass.
- the desire for steam generators with higher efficiencies and the resulting with respect to the working medium steam resulting from development of the "700 ° C power plant" to increase efficiency, including the CO2 emissions into the atmosphere help reduce, among other things, to increase the steam parameters of the steam generator.
- Achieving or realization of higher steam parameters, ie higher pressures and temperatures of the working medium steam at the outlet of the steam generator places high demands on the steam generator itself or on the method for operating such a steam generator.
- the turbine control valve With further load reduction in forced continuous operation, the turbine control valve would have to be throttled, the pressure loss at 30% load of the continuous steam generator would be about 40-50 bar (energetic loss, wear on the turbine control valve with frequent driving in this load range). If throttling is not desired for the aforementioned reasons, the load range for the forced continuous operation of the continuous steam generator is limited to 40-100% of the full load. When fired with hard coal Power plants is a forced continuous operation of the continuous steam generator with pure coal fire up to a partial load of about 25% theoretically feasible.
- a forced flow steam generator is known, which is integrated in the water / steam leading working medium circuit of a power plant.
- An economizer of the once-through steam generator viewed in the working-medium circulation direction, has upstream a heat-displacement system for preheating the working medium.
- the working medium absorbs heat from a supplied external heat flow in the heat transfer system.
- the object of the invention is therefore to provide a method for operating a forced-circulation steam generator operating in sliding pressure and with a steam temperature of over 650 ° C and lowering it of the forced passage minimum load, in which the aforementioned disadvantages are avoided or a lowering of the forced passage minimum load is achieved to about 30% of the full load. It is a further object of the invention to provide a forced once-through steam generator for carrying out the method.
- the temperature increase is reduced by the heat absorption of the feedwater after feed water pump on the HP preheater and / or the heat transfer system by up to about 50 Kelvin, so that the water outlet temperature due economizer due to the slightly improved Temperaturgrädtechnik the economizer heating surface falls by up to about 40 Kelvin, thereby ensuring sufficient subcooling at the evaporator inlet.
- the reduction of heat absorption by means of a control valve which regulates the amount of the HP pre-heater supplied turbine tap steam.
- the control valve is advantageously arranged in the bleed steam line, by means of which the Turbinenanzapfdampfstrom is guided from the turbine tap to the HD preheater.
- the amount to the HD preheater and thus at the same time the heat absorption can be changed by the working medium and controlled influence on the medium temperature at the economizer outlet.
- the same measure can be applied to the heat transfer system, in which the supply of the external heat flow is controlled by means of a control device and at the same time the heat absorption is controlled by the working medium.
- the control device is advantageously arranged in the supply line or the supply channel, by means of which the external heat flow is conducted from a foreign source to the heat transfer system.
- bypassing a part of the working medium flow the pressure loss in the HP preheater or in the heat displacement system is reduced.
- the preheater or the heat transfer system can be switched off and taken out of service.
- An advantageous embodiment provides that the reduction of the heat absorption by dividing the working medium flow into two partial flows (A T1 , A T2 ), wherein the first partial flow (A T1 ) through the HP preheater and the second partial flow (A T2 ) via a Bypass line is guided and the two partial streams (A T1 , A T2 ) are controlled by means of at least one control valve.
- a further advantageous embodiment provides that the reduction of the heat absorption by dividing the working medium flow into two partial flows (A T3 , A T4 ), wherein the first partial flow (A T3 ) through the water / steam circuit side component of the heat transfer system and the second partial flow (A T4 ) is guided via a bypass line and the two partial flows (A T3 , A T4 ) are controlled by means of at least one control valve.
- the amount of partial flow of the working medium flowing through the HP preheater or through the water / steam circuit side component of the heat transfer system can be influenced by the heat absorption thereof by changing the partial flow amount.
- the predetermined temperature difference T D is 20 Kelvin. This ensures that evaporation on the economizer and segregation of the circulated working medium at the inlet of the evaporator is avoided.
- An advantageous embodiment provides that 50% of the full load is taken as a predetermined partial load point L T to reduce heat absorption.
- An advantageous embodiment provides that the heat transfer system is arranged in the direction of circulation of the working medium circuit seen upstream of the HP preheater.
- a further advantageous embodiment provides for the heat-displacement system to be arranged in the direction of circulation of the working-medium circuit between the high-pressure preheaters.
- the thermal displacement system is arranged parallel to the HP preheater in a parallel circuit when viewed in the direction of the circulation of the working medium cycle. This measure can easily further heat be supplied to the working medium for preheating or be absorbed by this.
- FIG. 1 schematically shows the water / steam leading working medium cycle 1 of a continuous flow or continuous flow steam generator (both terms mean the same thing, namely the generation of steam within the steam generator in a single pass) formed power plant on.
- the steam expanded in the MD / LP steam turbine (medium pressure / low pressure steam turbine) 17 is cooled in at least one condenser 2 and the condensate is then heated in at least one LP preheater (low pressure preheater) 3.1, 3.2 and by means of a feedwater pump 4 returned to the circuit 1 or to the desired operating pressure.
- the feedwater is then further heated in one or more HD preheaters (high-pressure preheaters) 7.1, 7.2 and the economizer 9 and evaporated in the evaporator 10 and then superheated in the superheater 13 to 700 ° C, for example.
- the exiting from the superheater 13 700 ° C hot steam is the HP steam turbine (high-pressure steam turbine) 14 is supplied, partially relaxed and then overheated again in a reheater 16 and the MD / LP steam turbine 17 fed, in which the steam is largely relaxed before he is fed back to the aforementioned circuit 1.
- the water / steam working medium which is passed through tubes of heating mediums arranged in the continuous steam generator, is heated in the economizer heating surfaces 9, the evaporator heating surfaces 10, the superheater heating surfaces 13 and the reheater heating surfaces 16 of flue gases the combustion of fossil fuel in the combustion chamber, not shown, of the continuous steam generator arise.
- the aforementioned heating surfaces 9, 10, 13 and 16 are all arranged in the continuous steam generator either as a radiation or as a contact heating.
- the HP preheaters 7.1, 7.2 are heated by bleed steam, which is taken at tapping points 15 and / or 18 at the HP steam turbine 14 and / or at the MD / LP steam turbine 17.
- the LP preheaters 3.1, 3.2 can also be heated by bleed steam from the MD / LP steam turbine 17 (not shown), which can be removed at the tapping point 18.
- the or between the evaporator 10 and superheater 13 arranged (s) cyclone 11 are only used to separate in the startup and shutdown of the forced flow steam generator and in the load range below the forced minimum flow not evaporated water and upstream of the economizer 9 by means of a circulation pump 12 the water / Supply steam cycle 1 again.
- a heat transfer system 5 is parallel to (see FIG. 2 ) or upstream (see FIG. 3 ) of the HP preheater 7.1, 7.2 integrated in the circuit 1, wherein the heat transfer system 5 according to the FIG. 2 is arranged in a parallel to the circuit 1 parallel circuit 28.
- a foreign heat flow 22 for example, steam, flue gas or hot air from a foreign source, not shown, heat for further heating of the feed water to the heat transfer system 5.
- the heat transfer system 5 uses its own heat transfer medium, which circulates within the heat transfer system 5 by means of a circulation pump 5.3, the heat transfer circulation circuit also comprising a shut-off valve 5.4.
- the component 5.2 of the heat transfer system 5 is through the supply line or supply channel (in flue gas or hot air as Fremd Anlagenstrom) 31 a Fremdtage 22 is supplied and transferred or moved by means of the heat transfer to the lying in the circuit 1 component 5.1 of the heat transfer system 5, from which the heat transferred to the feed water or to the working fluid of the circuit 1 is discharged.
- the two components 5.1, 5.2 of the heat transfer system 5 thus each have the function of a heat exchanger.
- the heat transfer system 5 seen in the direction of circulation of the working medium circuit 1 between the HP preheaters 7.1, 7.2 may be arranged (not shown).
- FIG. 1 In full load operation as well as in partial load operation down to a predetermined partial load point L T down the water / steam working medium is usually by all in FIG. 1 respectively.
- FIG. 2 respectively.
- FIG. 3 listed heating surfaces or heat exchanger of the water / steam circuit 1 passed and heated or heated therein except for the capacitor 2 therein.
- the predetermined partial load point L T when the predetermined partial load point L T is not reached, the heat absorption of individual or several HP preheaters 7.1, 7.2 and / or the heat transfer system 5 is reduced such that the temperature of the working medium water / steam at the outlet of the economizer is at a predetermined temperature difference T D below which is based on the corresponding economizer outlet pressure boiling temperature.
- the temperature difference T D is defined as the temperature difference of the determined boiling temperature derived from the measured medium pressure at the economizer outlet minus the measured medium temperature at the economizer outlet.
- the medium temperature at the economizer outlet has a predetermined temperature difference T D compared to the boiling temperature at the corresponding economizer outlet pressure and the predetermined temperature difference T D represents a positive amount, the working fluid temperature at the economizer outlet below the boiling point is.
- the predetermined temperature difference T D is preferably 20 Kelvin, ie, that the medium temperature at the economizer outlet is preferably 20 Kelvin below the boiling point based on the corresponding economizer outlet pressure.
- the temperature difference T D can also be at least 15 Kelvin or more than 20 Kelvin.
- a control valve 19, 20 is arranged in the tapping steam line 29, 30 by means of which or which tapping steam from the turbine tap 15, 18 to the HP preheater 7.1, 7.2 is performed.
- the supply quantity of the turbine bleed steam flow to the / the HD preheater (s) 7.1, 7.2 and thus the heat absorption of the feedwater or working fluid after feed pump 4 can be controlled and adjusted so that the desired feedwater temperature with the predetermined temperature difference T D is achieved at the economizer outlet or sets. If, in addition to or instead of reducing the heat absorption of the HD preheater (s) 7.1, 7.2, the reduction of the heat absorption of the heat transfer system 5 is regulated, the amount of extraneous heat flow 22 supplied to the heat transfer system 5 can be regulated by a control device 21 arranged in the supply line 31 be managed.
- the currently determined temperature difference T D at the economizer outlet is such that at the measuring point 23 at the economizer outlet, the current medium temperature and the current medium pressure are measured and these two values are fed to a process computer. From the determined current medium pressure, the process computer determines the associated boiling temperature and compares them with the currently measured medium temperature. By this comparison, the current temperature difference T D is determined, which should have a related to the medium pressure at the economizer outlet predetermined value and, as stated above, should preferably be 20 Kelvin.
- the process computer can send a corresponding control signal to the control valve (s) 19, 20, 24.1, 24.2, 25.1, 25.2, 26, 27 or control device 21 in order to regulate the reduction of the heat absorption in the HD preheater (s) 7.1, 7.2 and / or in the heat transfer system 5 accordingly.
- the reduction of the heat absorption on the HD preheater (s) 7.1, 7.2 and / or on the heat transfer system 5 can be so far that by completely closing the / the control valve (s) 19, 20 and / or the control device 21 no more heat supply passes through the Anzapfdampfstrom to / the HD preheater 7.1, 7.2 or by the external heat flow to the heat transfer system 5 and thus no heat absorption takes place.
- the medium side pressure loss can be reduced by means of the bypass line (s) 8.1, 8.2, 6 Partial flow or the entire mass flow of the working medium is passed past the aforementioned components.
- the HD preheater 7.1, 7.2 and / or the heat transfer system 5 can be switched off.
- the control valve 27 is opened and the control valve 26 is closed.
- the shutdown of the heat transfer system 5 can be done either in addition to or instead of the shutdown of the HP preheater 7.1, 7.2.
- the two partial flows A T1 , A T2 can be controlled by means of at least one control valve 24.1, 24.2, 25.1, 25.2, either directly upstream or downstream (not shown) of / the HD preheater 7.1, 7.2 is located or in the respective bypass line 8.1 , 8.2 is arranged.
- the partial flows A T1 can be different with regard to the partial flow quantity in the respective HP preheaters 7.1, 7.2, which consequently also applies to the partial flows A T2 in the respective bypass lines 8.1, 8.2 of the HP preheater 7.1, 7.2 applies.
- the control valves can receive from a processor, not shown, the corresponding controlled variables that the processor determines or creates from the data that it receives from the measuring point 23 at the economizer outlet.
- the reduction of the heat absorption within the / the HD preheater 7.1, 7.2 by means of the control valves 24.1, 24.2, 25.1, 25.2 can without or with the inclusion of the control valves 19, 20, the supply amount of the bleed steam to the / the HD preheater (s) 7.1 7.2. Furthermore, the reduction of heat absorption within the component 5.1 of the heat transfer system 5 by means of the control valves 26, 27 without or with the involvement of the control device 21, which controls the supply amount of the external heat flow 22 to the component 5.2 of the heat transfer system 5, take place.
- control device 21 In addition to the control device 21 is within the heat transfer system 5 the ability to close the shut-off 5.4 of the heat transfer circulation and turn off the circulation pump 5.3 to prevent the supply of heat to the component 5.1 of the heat transfer system 5, which is synonymous with the shutdown of the heat transfer system 5 and the heat absorption by the working medium in the heat transfer system. 5
- a predetermined partial load point L T for reducing the heat absorption in at least one of the HP preheater 7.1, 7.2 and / or in the heat transfer system 5 preferably 50% of the full load can be taken.
- the predetermined partial load point L T may also be in the range between 40 and 60% of the full load.
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Description
Die Erfindung bezieht sich auf ein Verfahren zum Betreiben eines im Gleitdruck und mit einer Dampftemperatur von über 650°C operierenden Zwangdurchlaufdampferzeugers und dessen Absenken der Zwangdurchlaufmindestlast, wobei der Zwangdurchlaufdampferzeuger in den Wasser/Dampf-Kreislauf eines Kraftwerkes eingebunden ist und der Economiser des Zwangdurchlaufdampferzeugers in Wasser/Dampf-Kreislaufrichtung gesehen stromaufwärts wenigstens einen HD-Vorwärmer und/oder ein Wärmeverschiebesystem zur weiteren Vorwärmung des Speisewassers aufweist, wobei der/die HD-Vorwärmer mittels Turbinenanzapfdampf beheizt wird und über das Wärmeverschiebesystem Fremdwärme dem Kreislaufmedium Wasser/Dampf zugeführt wird.The invention relates to a method for operating a forced-circulation steam generator operating in sliding pressure and with a steam temperature of over 650 ° C and lowering the forced minimum flow, wherein the forced-circulation steam generator is integrated into the water / steam cycle of a power plant and the economizer of the forced-circulation steam generator in water / Steam cycle direction seen upstream at least one HD preheater and / or a heat transfer system for further preheating of the feed water, wherein the / the HP preheater is heated by turbine steam and the heat transfer system external heat to the circulation medium water / steam is supplied.
Durchlauf- bzw. Zwangdurchlaufdampferzeuger sind aus der Druckschrift "
Der Wunsch nach Dampferzeugern mit höheren Wirkungsgraden und die bezüglich des Arbeitsmediums Dampf daraus resultierende Entwicklung des "700°C Kraftwerkes" zur Wirkungsgradssteigerung, die unter anderem den CO2-Ausstoss in die Atmosphäre verringern helfen, führt unter anderem zur Erhöhung der Dampfparameter des Dampferzeugers. Die Erzielung bzw. Realisierung von höheren Dampfparametern, d. h. höheren Drücken und Temperaturen des Arbeitsmediums Dampfes am Austritt des Dampferzeugers, stellt hohe Anforderungen an den Dampferzeuger selbst bzw. an das Verfahren zum Betreiben eines solchen Dampferzeugers. Die momentan geplanten und gebauten Durchlaufdampferzeuger mit hohen Dampfparametern von bis zu 600°C/285 bar, bezogen auf den Frischdampfzustand, sind mit den z. Zt. vorhandenen bzw. zugelassenen Werkstoffen realisierbar und ein Zwischenschritt zu Durchlaufdampferzeugern mit noch höheren Dampfparametern von über 650°C/ca. 320 bar, bezogen auf den Frischdampfzustand, die in Zukunft realisiert werden sollen.The desire for steam generators with higher efficiencies and the resulting with respect to the working medium steam resulting from development of the "700 ° C power plant" to increase efficiency, including the CO2 emissions into the atmosphere help reduce, among other things, to increase the steam parameters of the steam generator. Achieving or realization of higher steam parameters, ie higher pressures and temperatures of the working medium steam at the outlet of the steam generator, places high demands on the steam generator itself or on the method for operating such a steam generator. The currently planned and built continuous steam generator with high steam parameters of up to 600 ° C / 285 bar, based on the live steam condition, with the z. Currently available or approved materials feasible and an intermediate step to continuous steam generators with even higher steam parameters of about 650 ° C / approx. 320 bar, based on the live steam condition, which are to be realized in the future.
Bei den zukünftigen Kraftwerksanlagen mit einer Dampftemperatur von über 650°C (mit den 650°C ist die Frischdampftemperatur gemeint) wird derzeit von einem Betrieb analog der 600°C Kraftwerksanlagen ausgegangen, d. h. modifizierter Gleitdruck herab bis ca. 40% Last und festgehaltenem Druck < ca. 40% Last. Auf Grund der höheren Dampfparameter im Turbinen- bzw. Wasser/Dampfkreislauf steigt die Speisewassertemperatur über die Vorwärmstrecke um ca. 30 Kelvin gegenüber einem vergleichbaren 600°C-Prozess bzw. einer 600°C Kraftwerksanlage. Trotz Auslegung des Economisers mit geringer Aufwärmspanne kann eine ausreichende Unterkühlung am Economiser-Austritt bei Teillast (< 40%) im Zwangdurchlaufbetrieb für alle möglichen Betriebszuständen nicht mehr sichergestellt werden. Bei weiterer Lastabsenkung im Zwangdurchlaufbetrieb müsste das Turbinenregelventil angedrosselt werden, der Druckverlust bei 30% Last des Durchlaufdampferzeugers wäre ca. 40-50 bar (energetischer Verlust, Verschleiß am Turbinenregelventil bei häufiger Fahrweise in diesem Lastbereich). Wird ein Androsseln aus vorgenannten Gründen nicht gewünscht, so wird der Lastbereich für den Zwangdurchlaufbetrieb des Durchlaufdampferzeugers auf 40-100% der Volllast eingeschränkt. Bei mit Steinkohle befeuerten Kraftwerksanlagen ist ein Zwangdurchlaufbetrieb des Durchlaufdampferzeugers mit reinem Kohlefeuer bis zu einer Teillast von ca. 25% theoretisch machbar. Die oben beschriebene Einschränkung auf einen Dampferzeugerlastbereich von 40-100% ist für den Kraftwerksbetreiber ein Nachteil in der Flexibilität der Anlage, da der Dampferzeuger bei Lastfällen < 40% in den Umwälzbetrieb geht, was gleichbedeutend ist mit einem Temperaturabsturz an den dickwandigen Bauteilen des Durchlaufdampferzeugers und einer damit verbundenen Verkürzung der Lebensdauer dieser Bauteile.At the future power plants with a steam temperature of over 650 ° C (with the 650 ° C is meant the live steam temperature) is currently assumed to operate analogous to the 600 ° C power plants, ie modified sliding pressure down to about 40% load and retained pressure about 40% load. Due to the higher steam parameters in the turbine or water / steam cycle, the feedwater temperature rises by approx. 30 Kelvin over the preheating section compared to a comparable 600 ° C process or a 600 ° C power plant. Despite the design of the economizer with a small warm-up period, sufficient subcooling at the economizer outlet at part load (<40%) in forced continuous operation can no longer be ensured for all possible operating states. With further load reduction in forced continuous operation, the turbine control valve would have to be throttled, the pressure loss at 30% load of the continuous steam generator would be about 40-50 bar (energetic loss, wear on the turbine control valve with frequent driving in this load range). If throttling is not desired for the aforementioned reasons, the load range for the forced continuous operation of the continuous steam generator is limited to 40-100% of the full load. When fired with hard coal Power plants is a forced continuous operation of the continuous steam generator with pure coal fire up to a partial load of about 25% theoretically feasible. The above-described restriction to a steam generator load range of 40-100% is a disadvantage for the power plant operator in the flexibility of the plant, since the steam generator in the case of load cases <40% goes into circulation, which is equivalent to a temperature crash on the thick-walled components of the continuous steam generator and an associated shortening of the life of these components.
Am Umschaltpunkt vom Zwangdurchlauf- in den Umwälzbetrieb stürzen üblicherweise die Mediumtemperaturen des Arbeitsmediums Wasser/Dampf am HD-Austritt (HD = Hockdruck), ZÜ-Austritt (ZÜ = Zwischenüberhitzer) und in den Zyklonabscheidern deutlich ab. Liegt der Umschaltpunkt anstatt bei etwa 100 bar (600°C-Anlage) bei etwa 150 bar (700°C-Anlage), so ist der Temperaturabsturz des Mediums Dampf bei vergleichbarer Auslegung der Heizflächen wesentlich größer. Grund hierfür ist der unterschiedliche Verlauf der Isothermen und der Sattdampflinie im Nassdampfgebiet im h-p-Diagramm.At the changeover point from forced to circulating mode, the medium temperatures of the working medium water / steam at the HP outlet (HD = high pressure), ZÜ outlet (ZÜ = reheater) and in the cyclone separators usually plummet. If the switching point instead of at about 100 bar (600 ° C system) at about 150 bar (700 ° C system), so the temperature drop of the medium vapor with a comparable design of the heating surfaces is much larger. The reason for this is the different course of the isotherms and the saturated steam line in the wet steam area in the h-p diagram.
Aus
Aufgabe der Erfindung ist es nun, ein Verfahren zum Betreiben eines im Gleitdruck und mit einer Dampftemperatur von über 650°C operierenden Zwangdurchlaufdampferzeugers und dessen Absenken der Zwangdurchlaufmindestlast zu schaffen, bei dem die vorgenannten Nachteile vermieden werden bzw. ein Absenken der Zwangdurchlaufmindestlast auf etwa 30% der Volllast erreicht wird. Es ist ferner eine Aufgabe der Erfindung, einen Zwangdurchlaufdampferzeuger zur Durchführung des Verfahrens zu schaffen.The object of the invention is therefore to provide a method for operating a forced-circulation steam generator operating in sliding pressure and with a steam temperature of over 650 ° C and lowering it of the forced passage minimum load, in which the aforementioned disadvantages are avoided or a lowering of the forced passage minimum load is achieved to about 30% of the full load. It is a further object of the invention to provide a forced once-through steam generator for carrying out the method.
Die vorstehend genannte Aufgabe wird hinsichtlich des Verfahrens durch die kennzeichnenden Merkmale des Patentanspruches 1 und hinsichtlich des Zwangdurchlaufdampferzeugers zur Durchführung des Verfahrens durch die kennzeichnenden Merkmale des Patentanspruches 8 gelöst.The above object is achieved in terms of the method by the characterizing features of
Vorteilhafte Ausgestaltungen der Erfindung sind den Unteransprüchen zu entnehmen.Advantageous embodiments of the invention can be found in the dependent claims.
Durch die erfindungsgemäße Lösung wird ein Verfahren zum Betreiben eines im Gleitdruck und mit einer Dampftemperatur von über 650°C operierenden Zwangdurchlaufdampferzeugers und dessen Absenken der Zwangdurchlaufmindestlast sowie ein Zwangdurchlaufdampferzeuger zur Durchführung des Verfahrens geschaffen, das bzw. der die nachfolgenden Vorteile aufweist:
- Größere Flexibilität für den Betrieb des Zwangdurchlaufdampferzeugers und somit der Kraftwerksanlage,
- längere Lebensdauer der dickwandigen Bauteile des Zwangdurchlaufdampferzeugers,
- geringere Belastung des Turbinenregelventils hinsichtlich Verschleiß,
- Eventuell energetischer Vorteil für den Gesamtprozess (statt 50 bar Druckverlust über Turbinenregelventil mit 30 Grad kälterem Speisewasser).
- Greater flexibility for the operation of the once-through steam generator and thus of the power plant,
- longer life of the thick-walled components of the once-through steam generator,
- lower load on the turbine control valve with regard to wear,
- Eventually energetic advantage for the entire process (instead of 50 bar pressure loss via turbine control valve with 30 degrees colder feed water).
Durch die erfindungsgemäßen Maßnahmen wird erreicht, dass die Temperaturerhöhung durch die Wärmeaufnahme des Speisewassers nach Speisewasserpumpe über die HD-Vorwärmer und/oder das Wärmeverschiebesystem um bis zu ca. 50 Kelvin reduziert wird, so dass die Wasseraustrittstemperatur nach Economiser bedingt durch die leicht verbesserte Temperaturgrädigkeit an der Economiserheizfläche um bis zu ca. 40 Kelvin fällt und dadurch eine ausreichende Unterkühlung am Verdampfereintritt sichergestellt ist.By the measures according to the invention it is achieved that the temperature increase is reduced by the heat absorption of the feedwater after feed water pump on the HP preheater and / or the heat transfer system by up to about 50 Kelvin, so that the water outlet temperature due economizer due to the slightly improved Temperaturgrädigkeit the economizer heating surface falls by up to about 40 Kelvin, thereby ensuring sufficient subcooling at the evaporator inlet.
In vorteilhafter Ausgestaltung der Erfindung erfolgt die Reduzierung der Wärmeaufnahme mittels eines Regelventils, das die Menge des dem HD-Vorwärmer zugeführten Turbinenanzapfdampfstromes regelt. Das Regelventil ist dabei vorteilhaft in der Anzapf-Dampfleitung angeordnet, mittels der der Turbinenanzapfdampfstrom von der Turbinenanzapfstelle zum HD-Vorwärmer geführt wird. Durch diese Maßnahme kann gezielt bzw. geregelt die Menge zu dem HD-Vorwärmer und damit gleichzeitig die Wärmeaufnahme durch das Arbeitsmedium verändert werden und auf die Mediumtemperatur am Economiseraustritt Einfluss genommen werden. Die gleiche Maßnahme kann an dem Wärmeverschiebesystem angewandt werden, in dem die Zufuhr des Fremdwärmestromes mittels einer Regeleinrichtung geregelt wird und damit gleichzeitig die Wärmeaufnahme durch das Arbeitsmedium geregelt wird. Die Regeleinrichtung ist dabei vorteilhaft in der Zufuhrleitung bzw. dem Zufuhrkanal angeordnet, mittels der der Fremdwärmestrom von einer Fremdquelle zum Wärmeverschiebesystem geführt wird.In an advantageous embodiment of the invention, the reduction of heat absorption by means of a control valve, which regulates the amount of the HP pre-heater supplied turbine tap steam. The control valve is advantageously arranged in the bleed steam line, by means of which the Turbinenanzapfdampfstrom is guided from the turbine tap to the HD preheater. By this measure, the amount to the HD preheater and thus at the same time the heat absorption can be changed by the working medium and controlled influence on the medium temperature at the economizer outlet. The same measure can be applied to the heat transfer system, in which the supply of the external heat flow is controlled by means of a control device and at the same time the heat absorption is controlled by the working medium. The control device is advantageously arranged in the supply line or the supply channel, by means of which the external heat flow is conducted from a foreign source to the heat transfer system.
Zweckmäßig kann es sein, dass die Reduzierung der Wärmeaufnahme mittels eines Regelventils erfolgt, wobei die Zufuhr des Turbinenanzapfdampfstromes zu dem(n) HD-Vorwärmer(n) mittels Regelventil(en) bzw. die Zufuhr des Fremdwärmestromes zu dem Wärmeverschiebesystem völlig unterbunden wird und zumindest ein Teil des Arbeitsmediumstromes an dem HD-Vorwärmer bzw. an dem Wärmeverschiebesystem mittels Bypassleitung vorbeigeführt wird. Durch das Bypassen eines Teiles des Arbeitsmediumstromes wird der Druckverlust im HD-Vorwärmer bzw. im Wärmeverschiebesystem verringert. Im Falle der kompletten Bypassung des Arbeitsmediumstromes kann der/die Vorwärmer bzw. das Wärmeverschiebesystem abgeschaltet und außer Betrieb genommen werden.Appropriately, it may be that the reduction of heat absorption by means of a control valve, wherein the supply of turbine steam flow to the (n) HP preheater (s) by means of control valve (s) or the supply of the extraneous heat flow to the heat transfer system is completely prevented and at least a portion of the working medium flow is passed to the HP preheater or to the heat transfer system by means of bypass line. By bypassing a part of the working medium flow, the pressure loss in the HP preheater or in the heat displacement system is reduced. In case of complete bypass of the Arbeitsmediumstromes the preheater or the heat transfer system can be switched off and taken out of service.
Eine vorteilhafte Ausbildung sieht vor, dass die Reduzierung der Wärmeaufnahme durch Aufteilung des Arbeitsmediumstromes in zwei Teilströme ( AT1, AT2 ) erfolgt, wobei der erste Teilstrom ( AT1 ) durch den HD-Vorwärmer und der zweite Teilstrom ( AT2) über eine Bypassleitung geführt wird und die zwei Teilströme ( AT1, AT2) mittels wenigstens einem Regelventil geregelt werden. Eine weitere vorteilhafte Ausbildung sieht vor, dass die Reduzierung der Wärmeaufnahme durch Aufteilung des Arbeitsmediumstromes in zwei Teilströme ( AT3, AT4 ) erfolgt, wobei der erste Teilstrom ( AT3 ) durch die Wasser/Dampfkreislaufseitige Komponente des Wärmeverschiebesystem und der zweite Teilstrom ( AT4 ) über eine Bypassleitung geführt wird und die zwei Teilströme ( AT3, AT4 ) mittels wenigstens einem Regelventil geregelt werden. Damit kann auf die durch den HD-Vorwärmer bzw. durch die Wasser/Dampf-kreislaufseitige Komponente des Wärmeverschiebesystems strömende Teilstrommenge des Arbeitsmediums Einfluss auf deren Wärmeaufnahme genommen werden, indem die Teilstrommenge verändert wird.An advantageous embodiment provides that the reduction of the heat absorption by dividing the working medium flow into two partial flows (A T1 , A T2 ), wherein the first partial flow (A T1 ) through the HP preheater and the second partial flow (A T2 ) via a Bypass line is guided and the two partial streams (A T1 , A T2 ) are controlled by means of at least one control valve. A further advantageous embodiment provides that the reduction of the heat absorption by dividing the working medium flow into two partial flows (A T3 , A T4 ), wherein the first partial flow (A T3 ) through the water / steam circuit side component of the heat transfer system and the second partial flow (A T4 ) is guided via a bypass line and the two partial flows (A T3 , A T4 ) are controlled by means of at least one control valve. In this way, the amount of partial flow of the working medium flowing through the HP preheater or through the water / steam circuit side component of the heat transfer system can be influenced by the heat absorption thereof by changing the partial flow amount.
Vorteilhaft ist es, dass die vorbestimmte Temperaturdifferenz TD 20 Kelvin beträgt. Damit ist sichergestellt, dass eine Verdampfung am Economiser sowie eine Entmischung des im Kreislauf geführten Arbeitsmediums am Eintritt des Verdampfers vermieden wird.It is advantageous that the predetermined
Eine vorteilhafte Ausbildung sieht vor, dass als vorbestimmter Teillastpunkt LT zur Reduzierung der Wärmeaufnahme 50% der Volllast genommen wird.An advantageous embodiment provides that 50% of the full load is taken as a predetermined partial load point L T to reduce heat absorption.
Eine vorteilhafte Ausbildung sieht vor, dass das Wärmeverschiebesystem in Kreislaufrichtung des Arbeitsmedium-Kreislaufes gesehen stromaufwärts des HD-Vorwärmers angeordnet ist. Bei mehreren vorhandenen HD-Vorwärmern sieht eine weitere vorteilhafte Ausgestaltung vor, das Wärmeverschiebesystem in Kreislaufrichtung des Arbeitsmedium-Kreislaufes gesehen zwischen den HD-Vorwärmern anzuordnen. Schließlich sieht eine weitere vorteilhafte Ausbildung vor, das Wärmeverschiebesystem in Kreislaufrichtung des Arbeitsmedium-Kreislaufes gesehen parallel zu dem HD-Vorwärmer in einem Parallel-Kreislauf anzuordnen. Durch diese Maßnahme kann in einfacher Weise weitere Wärme dem Arbeitsmedium zur Vorwärmung zugeführt werden bzw. von diesem aufgenommen werden.An advantageous embodiment provides that the heat transfer system is arranged in the direction of circulation of the working medium circuit seen upstream of the HP preheater. In the case of several existing high-pressure preheaters, a further advantageous embodiment provides for the heat-displacement system to be arranged in the direction of circulation of the working-medium circuit between the high-pressure preheaters. Finally, a further advantageous embodiment provides for the thermal displacement system to be arranged parallel to the HP preheater in a parallel circuit when viewed in the direction of the circulation of the working medium cycle. This measure can easily further heat be supplied to the working medium for preheating or be absorbed by this.
Nachstehend sind Ausführungsbeispiele der Erfindung an Hand der Zeichnung und der Beschreibung näher erläutert.Embodiments of the invention with reference to the drawings and the description are explained in more detail below.
Es zeigt:
- Fig. 1
- schematisch dargestellt den Wasser/Dampf-Kreislauf eines mit einem Zwangdurchlaufdampferzeuger ausgebildeten Kraftwerkes,
- Fig. 2
- wie
, jedoch alternative Ausführung,Figur 1 - Fig. 3
- wie
, jedoch alternative Ausführung.Figur 1
- Fig. 1
- schematically shows the water / steam cycle of a trained with a forced once-through steam generator power plant,
- Fig. 2
- as
FIG. 1 but alternative design, - Fig. 3
- as
FIG. 1 , but alternative design.
Der bzw. die zwischen Verdampfer 10 und Überhitzer 13 angeordnete(n) Zyklonabscheider 11 dienen lediglich dazu, im Anfahr- bzw. Abfahrbetrieb des Zwangdurchlaufdampferzeugers sowie im Lastbereich unterhalb der Zwangdurchlaufmindestlast nicht verdampftes Wasser abzuscheiden und stromaufwärts des Economisers 9 mittels einer Umwälzpumpe 12 dem Wasser/Dampf-Kreislauf 1 wieder zuzuführen.The or between the evaporator 10 and
Bei dem Wasser/Dampf-Kreislauf 1 gemäß der
Im Volllastbetrieb sowie im Teillastbetrieb bis zu einem vorbestimmten Teillastpunkt LT herab wird das Wasser/Dampf-Arbeitsmedium in der Regel durch alle in
Durch das erfindungsgemäße Verfahren wird sichergestellt, dass hinsichtlich der Verhinderung einer Verdampfung am Economiser 9 sowie einer Entmischung des im Kreislauf 1 geführten Arbeitsmediums am Eintritt des Verdampfers 10 eine ausreichende Sicherheit gegeben ist, da die Mediumtemperatur am Economiseraustritt eine vorbestimmte Temperaturdifferenz TD gegenüber der Siedetemperatur bei dem entsprechenden Economiseraustrittsdruck aufweist und die vorbestimmte Temperaturdifferenz TD einen positiven Betrag darstellt, wobei die Arbeitsmediumstemperatur am Economiseraustritt unterhalb der Siedetemperatur liegt. Die vorbestimmte Temperaturdifferenz TD beträgt vorzugsweise 20 Kelvin, d.h., dass die Mediumtemperatur am Economiseraustritt vorzugsweise 20 Kelvin unterhalb der auf den entsprechenden Economiseraustrittsdruck bezogenen Siedetemperatur liegt. Die Temperaturdifferenz TD kann auch minimal 15 Kelvin oder mehr als 20 Kelvin betragen.By the method according to the invention it is ensured that with regard to the prevention of evaporation on the
Die Reduzierung der Wärmeaufnahme des/der HD-Vorwärmer(s) 7.1, 7.2 bzw. des Wärmeverschiebesystems 5 kann dabei, abhängig von der aktuell ermittelten oben genannten Temperaturdifferenz TD, vorzugsweise geregelt erfolgen, um eine ausreichende Unterkühlung am Austritt des Economisers 9 bei optimalem Wirkungsgrad des Wasser/Dampf-Prozesses zu erreichen. Dazu wird in der Anzapf-Dampfleitung 29, 30 mittels der bzw. denen Anzapfdampf von der Turbinenanzapfung 15, 18 zum HD-Vorwärmer 7.1, 7.2 geführt wird, ein Regelventil 19, 20 angeordnet. Mittels dieses Regelventils 19, 20 kann die Zufuhrmenge des Turbinen-Anzapfdampfstromes zu dem/den HD-Vorwärmer(n) 7.1, 7.2 und somit die Wärmeaufnahme des Speisewassers bzw. Arbeitsmediums nach Speisepumpe 4 so geregelt und eingestellt werden, dass die gewünschte Speisewassertemperatur mit der vorbestimmten Temperaturdifferenz TD am Economiser-Austritt erzielt wird bzw. sich einstellt. Wird zusätzlich zu oder anstatt der Reduzierung der Wärmeaufnahme des/der HD-Vorwärmer(s) 7.1, 7.2 die Reduzierung der Wärmeaufnahme des Wärmeverschiebesystems 5 geregelt, so kann durch eine in der Zufuhrleitung 31 angeordnete Regeleinrichtung 21 die Menge des dem Wärmeverschiebesystem 5 zugeführten Fremdwärmestromes 22 geregelt werden.The reduction of the heat absorption of the / the HD preheater (s) 7.1, 7.2 or the
Die aktuell ermittelte Temperaturdifferenz TD am Economiser-Austritt erfolgt derart, dass an der Messstelle 23 am Economiser-Austritt die aktuelle Mediumtemperatur und der aktuelle Mediumdruck gemessen werden und diese beiden Werte einem Prozessrechner zugeführt werden. Aus dem ermittelten aktuellen Mediumdruck ermittelt der Prozessrechner die dazugehörige Siedetemperatur und vergleicht sie mit der aktuell gemessenen Mediumtemperatur. Durch diesen Vergleich wird die aktuelle Temperaturdifferenz TD ermittelt, die einen auf den Mediumdruck am Economiseraustritt bezogenen vorbestimmten Wert haben soll und der, wie oben schon angeführt, vorzugsweise 20 Kelvin betragen soll. Weicht die aktuell ermittelte Temperaturdifferenz TD von dem Soll-Wert ab, so kann der nicht dargestellte Prozessrechner ein entsprechendes Regelsignal an das/die Regelventil(e) 19, 20, 24.1, 24.2, 25.1, 25.2, 26, 27 bzw. Regeleinrichtung 21 geben, um die Reduzierung der Wärmeaufnahme in den/dem HD-Vorwärmer(n) 7.1, 7.2 und/oder in dem Wärmeverschiebesystem 5 entsprechend zu regeln.The currently determined temperature difference T D at the economizer outlet is such that at the
Wenn es die aktuell ermittelte Temperaturdifferenz TD erfordert, kann die Reduzierung der Wärmeaufnahme an dem/den HD-Vorwärmer(n) 7.1, 7.2 und/oder an dem Wärmeverschiebesystem 5 so weit erfolgen, dass durch völliges Schließen des/der Regelventils(e) 19, 20 und/oder der Regeleinrichtung 21 keine Wärmezufuhr mehr durch den Anzapfdampfstrom an den/die HD-Vorwärmer 7.1, 7.2 bzw. durch den Fremdwärmestrom an das Wärmeverschiebesystem 5 gelangt und somit auch keine Wärmeaufnahme mehr erfolgt. In diesem Fall kann durch das Bypassen des Arbeitsmediums an dem/den HD-Vorwärmer(n) 7.1, 7.2 und/oder an dem Wärmeverschiebesystem 5 der mediumseitige Druckverlust reduziert werden, indem mittels der/den Bypassleitung(en) 8.1, 8.2, 6 ein Teilstrom oder der gesamte Massenstrom des Arbeitsmediums an den vorgenannten Komponenten vorbeigeleitet wird. Im Falle des Bypassens des kompletten Arbeitsmediummassenstromes kann der/die HD-Vorwärmer 7.1, 7.2 und/oder das Wärmeverschiebesystem 5 abgeschaltet werden. Dazu wird bezüglich des/der HD-Vorwärmer 7.1, 7.2 das/die Regelventil(e) 25.1, 25.2 geöffnet und das/die Regelventil(e) 24.1, 24.2 geschlossen und bezüglich des Wärmeverschiebesystems 5 das Regelventil 27 geöffnet und das Regelventil 26 geschlossen. Die Abschaltung des Wärmeverschiebesystems 5 kann entweder zusätzlich zur oder anstatt der Abschaltung der HD-Vorwärmer 7.1, 7.2 erfolgen.If it requires the currently determined temperature difference T D , the reduction of the heat absorption on the HD preheater (s) 7.1, 7.2 and / or on the
Ferner kann die Reduzierung der Wärmeaufnahme innerhalb des/der HD-Vorwärmer(s) 7.1, 7.2 und/oder des Wärmeverschiebesystems 5 durch Aufteilung des Arbeitsmediumstromes in zwei Teilströme AT1, AT2 und/oder AT3, AT4 erfolgen, wobei der erste Teilstrom AT1 durch den/die HD-Vorwärmer 7.1, 7.2 und/oder AT3, durch das Wärmeverschiebesystem 5 (genaugenommen durch die im Kreislauf 1 liegende Komponente 5.1 des Wärmeverschiebesystems 5) und der zweite Teilstrom AT2 über eine Bypassleitung 8.1, 8.2 des jeweiligen HD-Vorwärmers und/oder AT4 über eine Bypassleitung 6 des Wärmeverschiebesystems 5 geführt wird. Die zwei Teilströme AT1, AT2 können dabei mittels wenigstens einem Regelventil 24.1, 24.2, 25.1, 25.2 geregelt werden, das entweder direkt stromaufwärts oder stromabwärts (nicht dargestellt) des/der HD-Vorwärmer 7.1, 7.2 liegt oder in der jeweiligen Bypassleitung 8.1, 8.2 angeordnet ist. D.h., dass bezüglich des/der HD-Vorwärmer(s) 7.1, 7.2 entweder der Teilstrom AT1 durch das direkt stromaufwärts oder stromabwärts (nicht dargestellt) des/der HD-Vorwärmer 7.1, 7.2 angeordnete Regelventil 24.1, 24.2 oder der Teilstrom AT2 durch das in der Bypassleitung 8.1, 8.2 angeordnete Regelventil 25.1, 25.2 oder beide Teilströme AT1, AT2 durch die Regelventile 24.1, 24.2, 25.1, 25.2 geregelt werden. Bei mehreren HD-Vorwärmern 7.1, 7.2 können die Teilströme AT1 hinsichtlich der Teilstrommenge in den jeweiligen HD-Vorwärmern 7.1, 7.2 unterschiedlich ausfallen, was dann konsequenterweise auch für die Teilströme AT2 in den jeweiligen Bypassleitungen 8.1, 8.2 der HD-Vorwärmer 7.1, 7.2 zutrifft.Furthermore, the reduction of heat absorption within the / the HD preheater (s) 7.1, 7.2 and / or the
Bezüglich des Wärmeverschiebesystems 5 wird entweder der Teilstrom AT3 durch das direkt stromaufwärts oder stromabwärts (nicht dargestellt) der Komponente 5.1 des Wärmeverschiebesystems 5 angeordnete Regelventil 26 oder der Teilstrom AT4 durch das in der Bypassleitung 6 angeordnete Regelventil 27 oder beide Teilströme AT3, AT4 durch die Regelventile 26, 27 geregelt. Die Regelventile können beispielsweise von einem nicht dargestellten Prozessor die entsprechenden Regelgrößen erhalten, die der Prozessor aus den Daten ermittelt bzw. erstellt, die er von der Messstelle 23 am Economiseraustritt erhält. Durch die Veränderung der Menge des durch den HD-Vorwärmer 7.1, 7.2 und/oder durch die Komponente 5.1 des Wärmeverschiebesystems 5 strömenden Arbeitsmediumstromes kann gleichzeitig die Wärmeaufnahme dieses Teilstromes verändert bzw. geregelt werden.With respect to the
Die Reduzierung der Wärmeaufnahme innerhalb des/der HD-Vorwärmer 7.1, 7.2 mittels der Regelventile 24.1, 24.2, 25.1, 25.2 kann ohne oder mit Einbeziehung der Regelventile 19, 20, die die Zufuhrmenge des Anzapfdampfstromes zu dem/den HD-Vorwärmer(n) 7.1, 7.2 regelt, erfolgen. Des weiteren kann die Reduzierung der Wärmeaufnahme innerhalb der Komponente 5.1 des Wärmeverschiebesystems 5 mittels der Regelventile 26, 27 ohne oder mit Einbeziehung der Regeleinrichtung 21, die die Zufuhrmenge des Fremdwärmestromes 22 zu der Komponente 5.2 des Wärmeverschiebesystems 5 regelt, erfolgen. Neben der Regeleinrichtung 21 besteht innerhalb des Wärmeverschiebesystems 5 die Möglichkeit, das Absperrventil 5.4 des Wärmeträger-Zirkulationskreislaufes zu schließen und die Zirkulationspumpe 5.3 abzustellen, um die Wärmezufuhr zu der Komponente 5.1 des Wärmeverschiebesystems 5 zu unterbinden, was gleichbedeutend ist mit der Abschaltung des Wärmeverschiebesystems 5 und der Wärmeaufnahme seitens des Arbeitsmediums im Wärmeverschiebesystem 5.The reduction of the heat absorption within the / the HD preheater 7.1, 7.2 by means of the control valves 24.1, 24.2, 25.1, 25.2 can without or with the inclusion of the
Als vorbestimmten Teillastpunkt LT zur Reduzierung der Wärmeaufnahme in wenigstens einem der HD-Vorwärmer 7.1, 7.2 und/oder im Wärmeverschiebesystem 5 kann vorzugsweise 50% der Volllast genommen werden. Bei der Unterschreitung dieses Teillastpunktes LT wird dann wie oben beschrieben erfindungsgemäß die Wärmeaufnahme in einem oder mehreren der HD-Vorwärmer 7.1, 7.2 und/oder im Wärmeverschiebesystem 5 reduziert. Der vorbestimmte Teillastpunkt LT kann jedoch auch im Bereich zwischen 40 und 60 % der Volllast betragen.As a predetermined partial load point L T for reducing the heat absorption in at least one of the HP preheater 7.1, 7.2 and / or in the
Durch den Zwangdurchlaufbetrieb des Durchlaufdampferzeugers bis zu einem Teillastbereich von 25% herab wird vermieden, dass innerhalb des Teillastbereiches des Durchlaufdampferzeugers der Zwangdurchlaufbetrieb auf Umwalzbetrieb verändert werden muss und somit an dessen Umschaltpunkt die Arbeitsmediumtemperaturen am HD-Austritt (Frischdampfaustritt am Überhitzer 13), ZÜ-Austritt (Zwischenüberhitzer-Dampfaustritt am Zwischenüberhitzer 16) und in den Zyklonabscheidern 11 nicht mehr so stark abstürzen. Ferner wird die Androsselung der Turbinenregelventile und deren Verschleiß vermieden. Die Verschiebung des Umschaltpunktes zu kleinerer Last führt aufgrund des Verlaufs der Isothermen und Sattdampflinie im h-p-Diagramm zu geringeren Temperaturstürzen an den dickwandigen Bauteilen.Due to the forced continuous operation of the continuous steam generator down to a partial load range of 25%, it is avoided that the forced continuous operation must be changed to Umwalzbetrieb within the partial load range of the continuous steam generator and thus at the switching point the working medium temperatures at the HP outlet (live steam outlet at the superheater 13), ZÜ outlet (Reheater steam outlet at the reheater 16) and in the
- 11
- Wasser/Dampf- bzw. Arbeitsmedium-KreislaufWater / steam or working medium cycle
- 22
- Kondensatorcapacitor
- 3.13.1
- ND-VorwärmerND preheater
- 3.23.2
- ND-VorwärmerND preheater
- 44
- SpeisewasserpumpeFeedwater pump
- 55
- WärmeverschiebesystemHeat transfer system
- 5.15.1
- Komponentecomponent
- 5.25.2
- Komponentecomponent
- 5.35.3
- Zirkulations-PumpeCirculation pump
- 5.45.4
- Absperrventilshut-off valve
- 66
- Bypassleitungbypass line
- 7.17.1
- HD-VorwärmerHP heaters
- 7.27.2
- HD-VorwärmerHP heaters
- 8.18.1
- Bypassleitungbypass line
- 8.28.2
- Bypassleitungbypass line
- 99
- Economisereconomizer
- 1010
- VerdampferEvaporator
- 1111
- Zyklonabscheidercyclone
- 1212
- Umwälzpumpecirculating pump
- 1313
- Überhitzersuperheater
- 1414
- HD-DampfturbineHP steam turbine
- 1515
- Anzapfungen an HD-TurbineTaps on HD turbine
- 1616
- ZwischenüberhitzerReheater
- 1717
- MD/ND-DampfturbineIP / LP steam turbine
- 1818
- Anzapfungen an MD-/ND-TurbineTaps on MD / LP turbine
- 1919
- Regelventil für Anzapfdampf von HD-TurbineControl valve for bleed steam from HP turbine
- 2020
- Regelventil für Anzapfdampf von MD-/ND-TurbineControl valve for bleed steam from MD / LP turbine
- 2121
- Regeleinrichtung für FremdwärmeControl device for external heat
- 2222
- FremdwärmestromForeign heat flow
- 2323
- Messstelle am Economiser-AustrittMeasuring point at the economizer outlet
- 24.124.1
- Regelventilcontrol valve
- 24.224.2
- Regelventilcontrol valve
- 25.125.1
- Regelventilcontrol valve
- 25.225.2
- Regelventilcontrol valve
- 2626
- Regelventilcontrol valve
- 2727
- Regelventilcontrol valve
- 2828
-
Paralleler Kreislauf zu Kreislauf 1 im Bereich der HD-VorwärmerParallel circuit to
circuit 1 in the area of the HD preheater - 2929
- Anzapf-DampfleitungTap-steam line
- 3030
- Anzapf-DampfleitungTap-steam line
- 3131
- Zufuhrleitung bzw. ZufuhrkanalSupply line or supply channel
Claims (15)
- Method for operating a once-through steam generator operating with sliding pressure and at a steam temperature above 650°C and for lowering its forced-flow minimum load, the once-through steam generator being incorporated into the water/steam-carrying working medium circuit of a power station, and the economizer of the once-through steam generator having upstream, as seen in the working medium circulation direction, at least one HP preheater and/or one heat transfer system for preheating the working medium,
the working medium absorbing heat from a supplied turbine bleed steam stream within the HP preheater or preheaters and/or absorbing heat from a supplied auxiliary heat stream in the heat transfer system, characterized in that, if a predetermined part load point (LT) is undershot, the heat absorption of the working medium within at least one HP preheater and/or the heat transfer system is reduced in such a way that the temperature of the water/steam as a working medium at the outlet of the economizer lies at a distance of a predetermined temperature difference (TD) below the boiling temperature related to the corresponding economizer outlet pressure. - Method according to Claim 1, characterized in that the reduction in heat absorption takes place by means of a controlling valve which regulates the quantity of the turbine bleed steam stream supplied to the HP preheater.
- Method according to either one of Claims 1 and 2, characterized in that the reduction in heat absorption takes place by means of a controlling valve, the supply of the turbine bleed steam stream to the HP preheater being prevented completely by means of the controlling valve, and at least part of the water/steam working medium stream being routed past the HP preheater by means of a bypass line.
- Method according to at least one of the abovementioned claims, characterized in that the reduction in heat absorption is carried out by dividing the working medium stream into two substreams (AT1, AT2), the first substream (AT1) being routed through the HP preheater and the second substream (AT2) being routed via a bypass line of the HP preheater, and the two substreams (AT1, AT2) being regulated by means of at least one controlling valve.
- Method according to at least one of the abovementioned claims, characterized in that the reduction in heat absorption takes place by means of a controlling device which regulates the quantity of the auxiliary heat stream supplied to the heat transfer system.
- Method according to at least one of the abovementioned claims, characterized in that the reduction in heat absorption takes place by means of a controlling device, the supply of the auxiliary heat stream to the heat transfer system being prevented completely by means of the controlling device, and at least part of the water/steam working medium stream being routed past the component, located in the water/steam circuit, of the heat transfer system by means of a bypass line.
- Method according to at least one of the abovementioned claims, characterized in that the reduction in heat absorption is carried out by dividing the working medium stream into two substreams (AT3, AT4), the first substream (AT3) being routed through the water/steam circuit-side component of the heat transfer system and the second substream (AT4) being routed via a bypass line of the heat transfer system, and the two substreams (AT3, AT4) being regulated by means of at least one controlling valve.
- Once-through steam generator for carrying out the method according to Claim 1, comprising a once-through steam generator operable with sliding pressure and at a steam temperature above 650°C and suitable for lowering the once-through minimum load,
the once-through steam generator being incorporated into the water/steam-carrying working medium circuit (1) of a power station, and the economizer (9) of the once-through steam generator having upstream, as seen in the working medium circulation direction, at least one HP preheater (7.1, 7.2) and/or one heat transfer system (5) for preheating the working medium,
heat being capable of being absorbed by the working medium within the HP preheater or preheaters (7.1, 7.2) from a turbine bleed steam stream supplied by at least one bleed steam line (29, 30) and/or heat being capable of being absorbed by the working medium in the heat transfer system (5) from an auxiliary heat stream (22) supplied by a supply line (31),
characterized in that the once-through steam generator is designed such that, if a predetermined part load point (LT) is undershot, said once-through steam generator reduces the heat absorption of the working medium within at least one HP preheater (7.1, 7.2) and/or the heat transfer system (5) in such a way that the temperature of the water/steam as a working medium at the outlet of the economizer lies at the distance of a predetermined temperature difference (TD) below the boiling temperature related to the corresponding economizer outlet pressure. - Once-through steam generator according to Claim 8, characterized in that the bleed steam line (29, 30) is designed for controlling the turbine bleed steam stream by means of a controlling valve (19, 20) and/or the supply line (31) for auxiliary heat (22) is designed for controlling the auxiliary heat stream by means of a controlling device (21).
- Once-through steam generator according to Claim 8, characterized in that the heat transfer system (5) is arranged upstream of the HP preheater (7.1, 7.2), as seen in the direction of circulation of the working medium circuit (1).
- Once-through steam generator according to Claim 8, characterized in that, if a plurality of HP preheaters (7.1, 7.2) are present, the heat transfer system (5) is arranged between the HP preheaters (7.1, 7.2), as seen in the direction of circulation of the working medium circuit (1).
- Once-through steam generator according to Claim 8, characterized in that the heat transfer system (5) is arranged parallel to the HP preheater (7.1, 7.2) in a parallel circuit (28), as seen in the direction of circulation of the working medium circuit (1).
- Once-through steam generator according to Claim 8, characterized in that the HP preheater (7.1, 7.2) has a bypass line (8.1, 8.2) and/or in that the heat transfer system (5) has a bypass line (6).
- Once-through steam generator according to Claim 8, characterized in that the the HP preheater (7.1, 7.2) and/or the heat transfer system (5), has a controlling valve (24.1, 24.2; 26) upstream or downstream of the PH preheater (7.1, 7.2) or of the heat transfer system (5) as seen in the direction of circulation of the working medium circuit (1, 28).
- Once-through steam generator according to Claim 13, characterized in that the bypass line (6, 8.1, 8.2) has a controlling valve (25.1, 25.2, 27).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009036064A DE102009036064B4 (en) | 2009-08-04 | 2009-08-04 | in order to operate a forced-circulation steam generator operating at a steam temperature of more than 650 ° C, as well as forced circulation steam generators |
PCT/DE2010/000906 WO2011015185A2 (en) | 2009-08-04 | 2010-07-30 | Method for operating a forced-flow steam generator operating at a steam temperature above 650°c and forced-flow steam generator |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2462378A2 EP2462378A2 (en) | 2012-06-13 |
EP2462378B1 true EP2462378B1 (en) | 2016-04-06 |
Family
ID=43430085
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10752274.0A Active EP2462378B1 (en) | 2009-08-04 | 2010-07-30 | Method for operating a forced-flow steam generator operating at a steam temperature above 650°c and forced-flow steam generator |
Country Status (10)
Country | Link |
---|---|
US (1) | US8959917B2 (en) |
EP (1) | EP2462378B1 (en) |
CN (1) | CN102575840B (en) |
DE (1) | DE102009036064B4 (en) |
HU (1) | HUE028706T2 (en) |
IN (1) | IN2012DN01926A (en) |
PL (1) | PL2462378T3 (en) |
RU (1) | RU2538994C2 (en) |
WO (1) | WO2011015185A2 (en) |
ZA (1) | ZA201200762B (en) |
Families Citing this family (16)
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EP2546476A1 (en) * | 2011-07-14 | 2013-01-16 | Siemens Aktiengesellschaft | Steam turbine installation and method for operating the steam turbine installation |
EP2589760B1 (en) * | 2011-11-03 | 2020-07-29 | General Electric Technology GmbH | Steam power plant with high-temperature heat reservoir |
EP2682568B1 (en) * | 2012-01-19 | 2016-03-30 | Alstom Technology Ltd | Heating system for a thermal electric power station water circuit |
DE202012100381U1 (en) | 2012-02-05 | 2012-02-20 | Untha Recyclingtechnik Gmbh | Device for determining at least one category of at least one insulating medium |
DE102012100922B4 (en) | 2012-02-05 | 2018-12-13 | Urt Umwelt- Und Recyclingtechnik Gmbh | Method and device for determining at least one category of at least one insulating medium and / or for determining at least one blowing agent in an insulating medium |
US9617874B2 (en) * | 2013-06-17 | 2017-04-11 | General Electric Technology Gmbh | Steam power plant turbine and control method for operating at low load |
JP6230344B2 (en) * | 2013-09-06 | 2017-11-15 | 株式会社東芝 | Steam turbine plant |
KR20150083374A (en) * | 2014-01-09 | 2015-07-17 | 두산중공업 주식회사 | Apparatus and method for reactor power control of steam turbine power generation system |
EP2980475A1 (en) * | 2014-07-29 | 2016-02-03 | Alstom Technology Ltd | A method for low load operation of a power plant with a once-through boiler |
US20160102926A1 (en) | 2014-10-09 | 2016-04-14 | Vladimir S. Polonsky | Vertical multiple passage drainable heated surfaces with headers-equalizers and forced circulation |
CN107075977B (en) | 2014-10-27 | 2020-03-13 | 西门子公司 | Low load turndown for combined cycle power plant |
ES2846148T3 (en) | 2015-04-21 | 2021-07-28 | General Electric Technology Gmbh | Molten Salt Single Pass Steam Generator |
DE102015118098A1 (en) * | 2015-10-23 | 2017-04-27 | Mitsubishi Hitachi Power Systems Europe Gmbh | Process for feedwater preheating a steam generator of a power plant |
JP6737611B2 (en) | 2016-03-25 | 2020-08-12 | 三菱日立パワーシステムズ株式会社 | Thermal power generation system and method for controlling thermal power generation system |
JP6224858B1 (en) * | 2017-03-17 | 2017-11-01 | 三菱日立パワーシステムズ株式会社 | Power plant and operation method thereof |
JP6891090B2 (en) * | 2017-10-04 | 2021-06-18 | 三菱パワー株式会社 | Power plant and its operation method |
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US3411300A (en) * | 1967-05-31 | 1968-11-19 | Combustion Eng | Method and apparatus for sliding pressure operation of a vapor generator at subcritical and supercritical pressure |
JPS5124438A (en) * | 1974-08-09 | 1976-02-27 | Hitachi Ltd | Karyokuburantono kyusokufukaseigensochi |
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JPS61205309A (en) * | 1985-03-08 | 1986-09-11 | Hitachi Ltd | Protective operating method and its device of feed water heater |
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KR100439080B1 (en) * | 1997-06-30 | 2004-07-05 | 지멘스 악티엔게젤샤프트 | Waste heat steam generator |
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-
2009
- 2009-08-04 DE DE102009036064A patent/DE102009036064B4/en not_active Expired - Fee Related
-
2010
- 2010-07-30 IN IN1926DEN2012 patent/IN2012DN01926A/en unknown
- 2010-07-30 US US13/387,033 patent/US8959917B2/en not_active Expired - Fee Related
- 2010-07-30 WO PCT/DE2010/000906 patent/WO2011015185A2/en active Application Filing
- 2010-07-30 PL PL10752274.0T patent/PL2462378T3/en unknown
- 2010-07-30 EP EP10752274.0A patent/EP2462378B1/en active Active
- 2010-07-30 RU RU2012108101/06A patent/RU2538994C2/en active
- 2010-07-30 HU HUE10752274A patent/HUE028706T2/en unknown
- 2010-07-30 CN CN201080045664.XA patent/CN102575840B/en active Active
-
2012
- 2012-01-31 ZA ZA2012/00762A patent/ZA201200762B/en unknown
Also Published As
Publication number | Publication date |
---|---|
PL2462378T3 (en) | 2016-10-31 |
US20120272649A1 (en) | 2012-11-01 |
DE102009036064A1 (en) | 2011-02-10 |
RU2012108101A (en) | 2013-09-10 |
HUE028706T2 (en) | 2016-12-28 |
EP2462378A2 (en) | 2012-06-13 |
IN2012DN01926A (en) | 2015-07-24 |
WO2011015185A2 (en) | 2011-02-10 |
CN102575840B (en) | 2014-12-17 |
ZA201200762B (en) | 2013-05-29 |
DE102009036064B4 (en) | 2012-02-23 |
US8959917B2 (en) | 2015-02-24 |
WO2011015185A3 (en) | 2012-03-29 |
RU2538994C2 (en) | 2015-01-10 |
CN102575840A (en) | 2012-07-11 |
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