EP2715231A2 - Procédé permettant de faire fonctionner un générateur de vapeur à récupération de chaleur en circuit fermé - Google Patents

Procédé permettant de faire fonctionner un générateur de vapeur à récupération de chaleur en circuit fermé

Info

Publication number
EP2715231A2
EP2715231A2 EP12725677.4A EP12725677A EP2715231A2 EP 2715231 A2 EP2715231 A2 EP 2715231A2 EP 12725677 A EP12725677 A EP 12725677A EP 2715231 A2 EP2715231 A2 EP 2715231A2
Authority
EP
European Patent Office
Prior art keywords
evaporator
flue gas
pressure stage
steam generator
inlet
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.)
Withdrawn
Application number
EP12725677.4A
Other languages
German (de)
English (en)
Inventor
Jan BRÜCKNER
Martin Effert
Frank Thomas
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP2715231A2 publication Critical patent/EP2715231A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
    • F01K23/108—Regulating means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/02—Control systems for steam boilers for steam boilers with natural convection circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • F22D5/00—Controlling water feed or water level; Automatic water feeding or water-level regulators
    • F22D5/26—Automatic feed-control systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
    • Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply

Definitions

  • the invention relates to a method for operating a circulation heat recovery steam generator, wherein in a pressure stage of the circulation heat recovery steam generator for controlling the water level in a drum of the feedwater mass flow is guided by a predetermined setpoint.
  • a heat recovery steam generator is a heat exchanger that recovers heat from a hot gas stream.
  • Heat recovery steam generators are often used in gas and steam turbine (CCGT) plants, which are mainly used for power generation.
  • CCGT gas and steam turbine
  • a modern CCGT usually includes one to four gas turbines and at least one steam turbine, either each turbine each drives a generator (multi-shaft ⁇ system) or a gas turbine with the steam turbine on a common shaft drives a single generator (single-shaft system).
  • the hot exhaust gases of the gas turbine are used in the heat recovery steam generator for generating water vapor.
  • the steam is then fed to the steam turbine ⁇ leads.
  • Analogous to the various pressure stages of a steam turbine and the heat recovery steam generator includes a plurality of
  • the feedwater flow today is provided predominantly with a so-called three-component control.
  • the setpoint for the feedwater mass flow is selected.
  • the overall objective of this food ⁇ water control is compliance with the desired water level in the drum.
  • the current drum level serves as a correction control amount that causes depending from ⁇ deviation to the desired value, a direction change in the proper feed water mass flow. Due to the large water tank in the drum (buffer volume) which permits a slow response of the correction regulator also critical transients such are manageable In ⁇ play rapid load changes in boundaries in the context of a low-jitter and permissible water level in the drum.
  • the invention is based on the consideration that an increase in the operational flexibility of a circulation waste heat ⁇ steam generator can be achieved with an efficiency-related particularly small drum diameter by a suitable control of the level of the drum.
  • an even more flexibility is possible Swan ⁇ fluctuations of the drum water level can be effectively compensated by an appropriate dining ⁇ water control, minimizing the faster.
  • the water level in the drum is essentially dependent on how much flow medium is actually evaporated in the evaporator and is therefore nachzuspeisen via the economizer.
  • the vapor or water content of the flow medium at the evaporator outlet depends on the heat input into the evaporator.
  • the heat input into the evaporator is suitable as a predictive correction variable for controlling the water level in the drum.
  • the heat output introduced into the evaporator should be used as an input variable.
  • the temperature of the flue gas at the inlet of the steamer Ver ⁇ pressure stage is used as an input variable. From the ⁇ ser the specific enthalpy can be determined if the flue gas composition is known by a simp ⁇ chen linear relationship. The temperature can be measured directly by appropriate measuring devices at the evaporator inlet.
  • the flue gas temperature at the inlet of the steam generator is used in determining the temperature of the flue gas at the inlet of the evaporator of the pressure stage.
  • Such an assessment tion of the flue gas temperature at the evaporator inlet can be dispensed with expensive smoke gas-side measuring devices. This is made possible by the special property of circulating steam generators that the flow medium is continuously subject to saturation conditions and thus does not overheat at the evaporator outlet . This reduces the number of dependent parameters because z. B. a possible overheating of the flow ⁇ medium at the evaporator outlet does not have to be considered.
  • Characterized a parameter characteristic field can be determined in the course of a thermodynamic design reviews in advance, whose use on the basis of the flue gas temperature at the steam generator inlet in conjunction with a suitable Lastsig ⁇ nal (advantageously the flue gas mass flow rate), a characteristic value for the flue gas temperature can be determined at the evaporator inlet. This allows a ver ⁇ tively Seaunan Strukture determining the temperature of the flue gas at the evaporator inlet without additional Messein ⁇ direction.
  • the specific enthalpy of the smoke ⁇ gas at the inlet of the evaporator of the pressure stage zeitverzö ⁇ siege is used.
  • the re geltechnisch can be achieved with a time delay element higher order (PTn)
  • the time delay with the smoke gas side temperature changes are also noticeable for the flow medium in the evaporator can be replicated.
  • the flue gas paste is here dependent on the saturation temperature of the flow medium in the evaporator estimated and also as a function of the present gas composition in a corresponding flue gas enthalpy re ⁇ calculated. It is assumed that the flue gas temperature at the evaporator outlet is minimally greater than the saturation temperature of the fluid in the evaporator, and this temperature difference also reduces with decreasing load.
  • the heat output emitted by the flue gas to the evaporator heating surface can be precisely determined with the method described hitherto.
  • the on ⁇ ⁇ +1 rmspanne (enthalpy) of the flow medium in comparison should be used steam addition for the He ⁇ averaging of the feed-water mass flow, ie, advantageously in the determination of the desired value, the enthalpy difference of the flow medium between inlet and outlet of the evaporator the Pressure level used as input.
  • These are ermit ⁇ telt from the enthalpy of the saturated steam (based on the overall measured drum pressure) or the flow medium side gemes ⁇ Senen enthalpy at evaporator inlet.
  • the latter can be determined by a functional conversion of the measured quantities pressure and temperature. Is the enthalpy be true ⁇ in this manner for the evaporator inlet, then a slight hypothermia as ⁇ chhold present übli at the evaporator inlet in circulation systems are properly considered in the heat balance. Is entering a separate measurement of the temperature and the pressure at the evaporator is not provided or is not possible, the enthalpy of the saturated water can be used (also based on the measured drum pressure) iliafa ⁇ accordingly.
  • the required feedwater mass flow which is to be used as the basis for the fill level control, is known for each operating state, at least for stationary load operation.
  • the measures described so far make it possible to use the deviation of the actual drum water level from the predetermined setpoint value as a correction control variable of the flow generated with the predictive feedwater mass flow determination.
  • an intervention of this correction controller for reasons of control stability despite the improvements already described should still be carried out very slowly and with low controller gain.
  • Particularly strong temporary deviations from the predetermined setpoint which result from physical mechanisms as a result of highly unsteady operation of the waste heat boiler, may still not be avoided for this correction loop.
  • Opti ⁇ optimization measures of feed water setpoint determination should be taken which are described below.
  • the temporally delayed saturation temperature of the flow medium in the pressure stage is advantageously used as an input variable in the determination of the desired value.
  • this physical effect can be represented by control technology. the. It is approximately assumed that when the system pressure is modified, the change over time in terms of both the temperature of the flow medium and of the pipe wall are identical.
  • the input of the differentiating element is the ⁇ used according to calculated from the measured drum pressure saturation temperature of the flow medium.
  • the time-delayed density of the Strö ⁇ tion medium in the compression stage is used as an input variable in the determination of the desired value.
  • thermodynamic state values such. B. pressure and temperature.
  • changes in the specific volume or the density of the flow medium are inevitably linked in each heating surface of the heat recovery steam generator.
  • the speci ⁇ fish volume of the flow medium in a heating surface from (ie, the density increases), this can temporarily absorb more mass moderately fluid.
  • the heating surface can absorb less fluid at sin ⁇ kender density.
  • a suitable conversion means can be used to determine a representative sealant.
  • a change in this sealant is thus an indicator of fluid-side injection and withdrawal effects that can be quantitatively detected by a further differentiating element of the first order (DT1).
  • DT1 a further differentiating element of the first order
  • the correction signal determined in this way is to be superimposed additively to the calculated from the heat balance feedwater mass flow. In this way, fluctuations in the drum water level can be further reduced.
  • Limiting the density measurement to the economizer is based on the recognition that fluctuations in the average density in the evaporator itself (eg, via changes in inlet supercooling) have no appreciable effect on drum water level. Fluctuations in the mean density namely, in circulation systems, they equalize by different circulation numbers in the evaporator system, so that the drum water level remains unaffected. Therefore, a geson ⁇ -made considering density changes in the evaporator for an optimized level control is not necessary.
  • a recycle heat recovery steam generator operated by the above-described method is used in a gas and steam turbine power plant.
  • FIG. 1 shows a schematic representation of a pressure stage of a circulation heat recovery steam generator with a Re ⁇ gel circuit according to the present method.
  • FIG. 1 From the circulating heat recovery steam generator 1, only a single pressure stage is shown in the schematic representation of the FIG. The procedure described below can be used in any pressure stage. Furthermore, the FIG only shows the flow-medium-side interconnection of the individual Schuflä ⁇ chen, the flue gas side wiring is not illustrated ⁇ is.
  • Flow medium M typically flows from a condensate preheater not shown in detail in the flow path 2 of the Um- Run-off heat recovery steam generator 1.
  • the mass flow of the flow ⁇ medium M is controlled by a feedwater control valve 4.
  • the feedwater pump of the circuit is not closer Darge ⁇ provides.
  • the flow medium M enters the economizer 6, which is arranged on the flue gas side in the coldest region.
  • the illustration in the FIG can also stand for a plurality of heating surfaces in the economizer 6 as well as in the other heating surfaces to be described, which are arranged serially or in parallel.
  • the flow medium M flows into the drum 8. From here flows liquid Strö ⁇ mung medium M through downcomers 10 into the evaporator 12 where it is partially vaporized by heat transfer from the flue gas. After the flow through the evaporator 12, the flow ⁇ medium M is again guided into the drum 8, where the non ver ⁇ steamed, liquid part remains and again the evaporator 12 is supplied, while the evaporated part is discharged from the drum 8 upwards , The vaporized portion of the flow ⁇ medium M is replaced by the supplied via the economizer 6 flow medium M, so that a constant liquid level in the drum 8 is adjusted in the ideal case.
  • the FIG shows a natural circulation waste heat boiler, which manages without additional ⁇ circulating circulation pump in the circulation of the evaporator 12.
  • the method described below can also be used in a forced circulation waste heat boiler.
  • the vaporized flow medium M from the drum 8 enters the superheater 14, 16, which in each case an injection device 18, 20 is connected downstream of the temperature control.
  • the flow medium M is brought overheated and the ge ⁇ wished exit temperature and is then released in ei ⁇ ner not shown in detail steam turbine. From there it is fed to a condenser and fed again to the flow path 2 via the condensate preheater.
  • the level in the drum 8 may fluctuate.
  • small drum wall thicknesses are preferred because of a particularly ho ⁇ hen system flexibility, but on the other hand particularly high steam parameters are desirable because of a high efficiency, the drum should be construed 8 with the smallest possible inner diameter. However, this requires a minimization of the level ⁇ fluctuations in the drum 8, which is ensured by the scheme shown below.
  • a level measuring device 22 measures the level in the drum 8 and outputs the determined current level as a signal to a subtractor 24.
  • the current level in the drum 8 is subtracted from the value set at a Gresssoll- value transmitter 26, so that at the exit ⁇ gang of the subtractor 24, the deviation of the level from the setpoint is applied.
  • the output of the subtractor 24 is connected to a regulator member 28, which may be configured as a P or PI controller, ie outputs a value (in the latter case proportional to the deviation) when the level of the fill level is sufficiently large.
  • the pressure in the drum 8 is measured by a pressure measuring device 34 and provided for regulation.
  • the saturated ⁇ steam temperature is determined in a calculating member 36 from the pressure.
  • an adder 38 the determined in a calculating member 40 ⁇ temperature difference added at the so-called pinch point which is exactly the difference in temperature between saturated medium flow and flue gas temperature at the gas-side evaporator outlet DAR represents, so that here the flue gas temperature at the outlet of the evaporator 12 results. Since the temperature difference at the pinch point is load-dependent, the computing element 40 receives the flue gas mass flow from an encoder element 42 as an input signal. This can be measured or provided by the block-level.
  • the computing element 44 From the voltage applied to the output of the adder 38 temperature of the flue gas mass flow at the gas side evaporator outlet calculated at known flue gas composition, the computing element 44, the specific flue gas enthalpy at the gas side evaporator outlet.
  • the specific Rauchgasenthalpie the gas ⁇ side evaporator inlet is determined in the calculating member 46 from the time-delayed in delay element 48 pTn-gemesse- NEN or estimated exhaust gas temperature at the gas-side evaporator inlet 50th
  • the estimation is possible, especially in circulation steam generator, wherein the flue gas temperature is determined from the flue gas temperature at the inlet of the waste heat circulation steam generator 1 at the evaporator inlet by way of parame ⁇ terkennfeldes at a given load.
  • the parameters ⁇ map is determined in advance based on measurements, but can be found in an alternative embodiment also by appropriate calculations.
  • the determined at the inlet and outlet of the evaporator 12 spe ⁇ -specific enthalpies from the arithmetic elements 46 and 44 are subtracted from each other in the subtractor 52nd
  • the difference is given to a multiplier 54, where it is multiplied by the flue gas mass flow from the donor member 42.
  • the multiplier 54 the output from the flue gas to the evaporator 12 heat output.
  • the ratio so obtained in the dividing member 68 is a Indi ⁇ er for future level changes in the drum 8 and is supplied to the adder 32nd
  • correction values are switched via the adder 30 to the level deviation signal from the control element 28 and placed in a sensor element 98, where it is provided a setpoint for the feedwater mass flow. This is applied to a subtractor 100 in which the current measuring device in a mass flow medium side 102 measured before the feedwater control valve 4 mass flow of the flow medium ⁇ M is peeled off.
  • the error signal is supplied to a PI control member 104, the flow rate of the feedwater control valve 4 kor ⁇ rigiert at a corresponding deviate ⁇ monitoring.
  • the illustrated control or the illustrated control ⁇ method it is possible by minimizing level fluctuations in the drum 8 in circulation heat recovery steam generator 1 with small drum 8 and thus high mögli ⁇ Chen steam parameters and efficiencies to a high operational flexibility guarantee.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un procédé permettant de faire fonctionner un générateur de vapeur à récupération de chaleur en circuit fermé (1), procédé selon lequel le flux massique d'eau d'alimentation est guidé selon une valeur de consigne prédéterminée dans un étage de pression du générateur de vapeur à récupération de chaleur en circuit fermé (1) pour la régulation du niveau d'eau dans un tambour (8). L'invention vise à atteindre un rendement particulièrement élevé tout en assurant une plus grande flexibilité opérationnelle d'un générateur de vapeur à récupération de chaleur en circuit fermé. A cet effet, on utilise comme grandeur d'entrée pour la détermination de la valeur de consigne la puissance thermique introduite dans un évaporateur (12) de l'étage de pression.
EP12725677.4A 2011-06-06 2012-05-23 Procédé permettant de faire fonctionner un générateur de vapeur à récupération de chaleur en circuit fermé Withdrawn EP2715231A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011076968A DE102011076968A1 (de) 2011-06-06 2011-06-06 Verfahren zum Betreiben eines Umlauf-Abhitzedampferzeugers
PCT/EP2012/059575 WO2012168074A2 (fr) 2011-06-06 2012-05-23 Procédé permettant de faire fonctionner un générateur de vapeur à récupération de chaleur en circuit fermé

Publications (1)

Publication Number Publication Date
EP2715231A2 true EP2715231A2 (fr) 2014-04-09

Family

ID=46208467

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12725677.4A Withdrawn EP2715231A2 (fr) 2011-06-06 2012-05-23 Procédé permettant de faire fonctionner un générateur de vapeur à récupération de chaleur en circuit fermé

Country Status (8)

Country Link
US (1) US9518481B2 (fr)
EP (1) EP2715231A2 (fr)
JP (1) JP5855240B2 (fr)
KR (1) KR101606293B1 (fr)
CN (1) CN103797302B (fr)
BR (1) BR112013031458A2 (fr)
DE (1) DE102011076968A1 (fr)
WO (1) WO2012168074A2 (fr)

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EP2065641A3 (fr) * 2007-11-28 2010-06-09 Siemens Aktiengesellschaft Procédé de fonctionnement d'un générateur de vapeur en flux continu, ainsi que générateur de vapeur en flux à sens unique
EP2194320A1 (fr) * 2008-06-12 2010-06-09 Siemens Aktiengesellschaft Procédé de fonctionnement d'un générateur de vapeur à passage unique et générateur de vapeur à passage unique
DE102011076968A1 (de) * 2011-06-06 2012-12-06 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Umlauf-Abhitzedampferzeugers
DE102013202249A1 (de) * 2013-02-12 2014-08-14 Siemens Aktiengesellschaft Dampftemperatur-Regeleinrichtung für eine Gas- und Dampfturbinenanlage
JP6082620B2 (ja) * 2013-02-18 2017-02-15 株式会社日本サーモエナー ボイラの供給水量制御システムおよび供給水量制御方法
DE102014222682A1 (de) 2014-11-06 2016-05-12 Siemens Aktiengesellschaft Regelungsverfahren zum Betreiben eines Durchlaufdampferzeugers
EP3048366A1 (fr) 2015-01-23 2016-07-27 Siemens Aktiengesellschaft Générateur de vapeur à récupération de chaleur
CN104776416B (zh) * 2015-04-13 2017-01-04 河南华润电力古城有限公司 汽包锅炉主汽温度控制方法及系统
EP3647657A1 (fr) * 2018-10-29 2020-05-06 Siemens Aktiengesellschaft Régulation de l'eau d'alimentation pour générateur de vapeur à récupération de chaleur à circulation forcée
CN111581891B (zh) * 2020-05-28 2022-06-17 江苏方天电力技术有限公司 一种燃气-蒸汽联合循环机组燃烧温度智能监测方法
CN114811562B (zh) * 2021-01-28 2023-08-29 华能北京热电有限责任公司 燃气–蒸汽联合循环机组锅炉汽包水位的联锁控制方法

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KR20140037185A (ko) 2014-03-26
JP5855240B2 (ja) 2016-02-09
DE102011076968A1 (de) 2012-12-06
CN103797302A (zh) 2014-05-14
WO2012168074A3 (fr) 2014-03-13
JP2014519009A (ja) 2014-08-07
CN103797302B (zh) 2016-04-13
KR101606293B1 (ko) 2016-03-24
BR112013031458A2 (pt) 2016-12-06
US20140109547A1 (en) 2014-04-24
US9518481B2 (en) 2016-12-13
WO2012168074A2 (fr) 2012-12-13

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