EP2625390B1 - Générateur de vapeur à combustibles fossiles - Google Patents

Générateur de vapeur à combustibles fossiles Download PDF

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Publication number
EP2625390B1
EP2625390B1 EP11766973.9A EP11766973A EP2625390B1 EP 2625390 B1 EP2625390 B1 EP 2625390B1 EP 11766973 A EP11766973 A EP 11766973A EP 2625390 B1 EP2625390 B1 EP 2625390B1
Authority
EP
European Patent Office
Prior art keywords
fossil
steam generator
pressure
supply line
fired steam
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.)
Active
Application number
EP11766973.9A
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German (de)
English (en)
Other versions
EP2625390A2 (fr
Inventor
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
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Siemens AG
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Publication date
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Priority to PL11766973T priority Critical patent/PL2625390T3/pl
Publication of EP2625390A2 publication Critical patent/EP2625390A2/fr
Application granted granted Critical
Publication of EP2625390B1 publication Critical patent/EP2625390B1/fr
Active legal-status Critical Current
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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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type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
    • F01K7/24—Control or safety 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
    • F01K21/00—Steam engine plants not otherwise provided for
    • 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

Definitions

  • the invention relates to a fossil-fired steam generator for a steam power plant with a number of flow path forming, flowed through by a flow medium M economizer, evaporator and superheater heating in a plurality of pressure stages, in which in a high-pressure stage an overflow line is connected on the input side to the flow path and leads to a flow medium in a middle-pressure stage upstream of a superheater heating in the flow path arranged injection valve.
  • a fossil-fueled steam generator produces superheated steam using the heat generated by burning fossil fuels.
  • Fossil fueled steam generators are mostly used in steam power plants, which are mainly used for power generation.
  • the steam is fed to a steam turbine.
  • the fossil-fueled steam generator also comprises a plurality of pressure stages with different thermal states of the respectively contained water-steam mixture.
  • the flow medium In the first (high) pressure stage, the flow medium first passes through economizers on its flow path, using residual heat to preheat the flow medium, and then various stages of evaporator and superheater heating surfaces.
  • the evaporator the flow medium is evaporated, then separated any residual moisture in a separator and further heated the remaining steam in the superheater. Thereafter, the superheated steam flows into the high-pressure part of the steam turbine, where it is expanded and fed to the following pressure stage of the steam generator. There it is overheated again and fed to the next pressure part of the steam turbine.
  • the heat output transferred to the superheaters can fluctuate greatly. Therefore, it is often necessary to control the superheat temperature. Usually, this is achieved in the high-pressure stage as well as in the medium-pressure stages for reheating usually by injection of feed water before or after individual Matterhitzersammlung inhabit for cooling, ie, an overflow branches off from the main stream of the flow medium and leads to there correspondingly arranged injection valves.
  • the injection is usually controlled by the temperature deviation from a predetermined temperature setpoint at the outlet of the superheater of the respective pressure stage.
  • Modern power plants not only require high levels of efficiency but also the most flexible mode of operation possible. Apart from short start-up times and high load change speeds, this also includes the possibility of compensating for frequency disturbances in the power grid. To meet these requirements, the power plant must be able to provide more power, for example, 5% and more within a few seconds.
  • Such power changes of a power plant block in the second range are possible only by a coordinated interaction of steam generator and steam turbine.
  • the contribution that the fossil-fueled steam generator can make is the use of its storage, d. H. of the steam but also of the fuel storage, as well as rapid changes of the control variables feedwater, injection water, fuel and air.
  • the overflow line has two supply lines, of which the first branches off the flow medium side from a high-pressure preheater and the second fluid side branches off behind the high-pressure preheater.
  • the invention is based on the consideration that injections of feedwater can make a further contribution to the rapid change in performance.
  • additional injections in the superheater namely the steam mass flow can be increased.
  • injections are triggered by reducing the temperature setpoint at the outlet of the respective pressure stage. The higher the enthalpy level of the injection water, the more injection mass flow is needed to meet the newly required Temperature setpoint to achieve. Accordingly, results from a higher enthalpy of the injection water a comparatively larger amount of steam.
  • This should be counteracted by the enthalpy of the injection water can be controlled as needed. This can be achieved by mixing the injection water withdrawn behind a high-pressure preheater with a small proportion of injection water withdrawn before the high-pressure preheater, so that the desired enthalpy of the injection water can be adjusted in this way.
  • two supply lines each lead from the flow medium side before and behind a high-pressure preheater to the overflow line to the injection valve of the reheat.
  • the second supply line branches off from the flow medium side behind all high-pressure preheaters.
  • the greatest possible enthalpy for the injection water is ensured, so that an optimum with regard to the amount of steam and release of power is achieved.
  • Design branches off the first supply fluid side from all high-pressure preheaters. Because of the removal in the coldest area, a reduction in the temperature of the injection medium can be achieved, even at a small admixing amount, which ensures a sufficient distance to the boiling line. Overall, the greatest possible temperature variance can be achieved by removing before and after all high-pressure preheaters.
  • a check valve is arranged in one of the supply lines and arranged in the other supply line, a flow control valve.
  • the mixture is then in a particularly simple manner on the determination of the injection quantity on the one hand, which is adjusted by the injection control valve and is provided in part via the supply line with the check valve, the check valve prevents backflow from the high pressure path in the low pressure path.
  • the admixing of the medium of the other temperature is controlled via the flow control valve of the other supply line.
  • a check valve is arranged in the first supply line and arranged in the second supply line, a flow control valve. That is, the check valve is located in the supply line with the medium of the lower temperature level.
  • the first supply line branches off from a feed pump. Since under these circumstances, only upstream of the flow control valve, the flow medium has a relatively higher pressure, it is possible that the entire water path of the injector is at a relatively lower pressure level.
  • such an arrangement simplifies the control, and it is furthermore possible to use the currently used feed pumps with a corresponding branch for the reheat injection, since even in the present case, the cool medium can be coupled in the same place.
  • a flow measuring device is arranged downstream of the branch of the second supply line in the flow path flow medium side. Under these circumstances, the withdrawal quantity need not be taken into account for the feedwater control via additional measurement or separate balancing.
  • a steam power plant comprises such a fossil-fired steam generator.
  • the advantages achieved by the invention are, in particular, that a sufficient supercooling of the injection water can always be ensured by the mixing of injection water for reheating from leads before and after Hochlichvorskarn one hand, on the other hand with regard to the provision of an immediate reserve in absolutely safe injection operation without vapor formation a maximum can be realized on additional power relief via a correspondingly increased injection quantity.
  • the load of all the affected components such as injection point, heating surfaces and turbine can be reduced at the same power release compared to previous concepts, since for the same power release a lesser drop in temperature of the steam is expected.
  • interconnection and the associated increase in the power deduction by using the injection system is independent of other measures, so that, for example, throttled turbine valves can be additionally opened to increase the power increase of the steam turbine yet.
  • the effectiveness of the procedure remains largely unaffected by these parallel measures.
  • the degree of throttling of the turbine valves can be reduced, should the use of the injection system for increasing the power used.
  • the desired benefit release can be among these Circumstances then even with less, in the best case, even without any additional throttling can be achieved.
  • the plant can be operated in the usual load operation, where it must be available for an immediate reserve, with a relatively greater efficiency, which also reduces the operating costs.
  • FIG. 1 schematically represents a part of the flow path 6 of the flow medium M.
  • the flow medium M is first fed by a feed pump 8 in the high-pressure part 2.
  • Hochschervormaschinern 10 is first brought by Hochlichvormaschinern 10 to an elevated temperature, which can be operated for example with bleed steam.
  • economizer heating surfaces 12 in which flue gas waste heat is usually used for further heating of the flow medium
  • evaporator heating surfaces 14 in which the flow medium is evaporated by means of the heat obtained from fossil fuel.
  • the spatial arrangement of the individual heating surfaces 12, 14 in the hot gas duct is not shown and may vary.
  • the illustrated heating surfaces 12, 14 may each represent a plurality of serially connected heating surfaces, which are not shown differentiated due to the clarity.
  • an injection valve 18 is arranged on the flow medium side.
  • cooler and unevaporated flow medium M for controlling the outlet temperature at the outlet 20 of the medium-pressure part 4 of the fossil-fired steam generator 1 can be injected.
  • the introduced into the injection valve 18 amount of flow medium M is controlled by an injection control valve 22.
  • the flow medium M is supplied via a previously branched off in the flow path 2 overflow 24.
  • the injection system is designed for an increase in the enthalpy of the injection water as required.
  • the overflow line 24 has a first supply line 26, which branches off directly in the feed pump 8 and feeds flow medium M at a relatively low temperature to the overflow line 24. This ensures adequate subcooling of the injection medium.
  • the first supply line 26 also includes a check valve 28 which prevents backflow of fluid from the injection system.
  • the overflow line has a second supply line 30 whose flow is controlled by a flow control valve 32.
  • the second supply line branches off behind all high-pressure preheaters 10 in front of the economizer heating surfaces 12, so that here flow medium M is introduced into the overflow line 24 with a comparatively higher temperature.
  • the flow measuring device 34 is arranged in the flow path 6 behind both branches of the supply lines 26, 30, so that the quantity of the branched flow medium M for the feedwater control need not be taken into account here.
  • FIG. 2 shows an alternative embodiment, which is essentially the FIG. 1 corresponds, but here the locations of flow control valve 32 and check valve 28 are reversed.
  • the first supply line 26 thus has a control valve 32 and the second supply line 30 a check valve 28.
  • This embodiment is also possible, however, the entire injection path for higher pressures is interpreted.
  • an additional branch 36 is provided for the first supply line 26, since due to the higher pressure level, flow medium M can not be decoupled at any point of the feed pump 8.
  • FIG. 3 shows a diagram with simulation results using the interconnection described. Is applied the percent additional power in relation to full load 38 versus time 40 in seconds after a sudden decrease in the temperature setpoint for the temperature at the exit 20 of the mid-pressure member 4 by 20 ° C at 95% load.
  • the curve 42 shows the results without heated injection fluid, so according to the usual system, the curve 44, the results with as described above interconnected injection system.
  • the maximum of the curve 44 is higher than the curve 42. The additionally released power is thus higher.
  • FIG. 4 is opposite FIG. 3 only slightly modified and shows the simulated curves 42, 44 for 40% load, all other parameters coincide FIG. 3
  • both curves 42, 44 show a flat course and in addition a comparatively high power increase about 60 seconds after changing the setpoint, which then rapidly drops again to go to the maximum of the flat course ,
  • the curve 44 is higher in each time range than the curve 42.
  • a higher power deduction is also possible here, in spite of the load at only 40% sufficient subcooling of the injected medium is guaranteed.
  • a steam power plant equipped with such a fossil-fueled steam generator 1 is capable of rapidly increasing the output via an instant power output of the steam turbine, which serves to support the frequency of the composite power network.
  • This power reserve is achieved by a double use of the injection fittings in addition to the usual temperature control, a permanent throttling of the steam turbine valves to provide a reserve can be reduced or eliminated, whereby a particularly high efficiency is achieved during normal operation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)

Claims (8)

  1. Générateur ( 1 ) de vapeur à combustible fossile pour une centrale à vapeur ayant un certain nombre de surfaces ( 12, 14, 16 ) de chauffe d'économiseur, d'évaporateur et de surchauffeur, formant un trajet ( 2 ) de courant et parcourues par un fluide M en écoulement en une pluralité d'étages ( 2, 4 ) de pression, dans lequel, dans un étage ( 2 ) de haute pression, un conduit ( 24 ) de débordement communique, du côté de l'entrée, avec le trajet ( 2 ) de courant et mène à un robinet ( 18 ) d'injection, monté dans le trajet ( 2 ) de courant dans un étage ( 4 ) de moyenne pression, du côté du fluide en écoulement, avant une surface ( 16 ) de chauffe de surchauffeur,
    caractérisé en ce que
    le conduit ( 24 ) de débordement a deux conduits ( 26, 30 ) d'arrivée, dont le premier bifurque, du côté du fluide en écoulement, avant un préchauffeur ( 10 ) de haute pression et le deuxième bifurque, du côté du fluide en écoulement, derrière le préchauffeur ( 10 ) de haute pression.
  2. Générateur ( 1 ) de vapeur à combustible fossile suivant la revendication 1,
    caractérisé en ce que
    la deuxième arrivée ( 26 ) bifurque, du côté du fluide en écoulement, derrière tous les préchauffeurs ( 10 ) de haute pression.
  3. Générateur ( 1 ) de vapeur à combustible fossile suivant l'une des revendications précédentes,
    caractérisé en ce que
    la première arrivée ( 30 ) bifurque, du côté du fluide en écoulement, avant tous les préchauffeurs de haute pression.
  4. Générateur ( 1 ) de vapeur à combustible fossile suivant l'une des revendications précédentes,
    caractérisé en ce que
    dans l'une des arrivées ( 26, 30 ) est monté un clapet anti-retour ( 28 ) et dans l'autre arrivée est montée une vanne ( 32 ) de régulation du débit.
  5. Générateur ( 1 ) de vapeur à combustible fossile suivant l'une des revendications précédentes,
    caractérisé en ce que
    dans la première arrivée ( 26 ) est monté un clapet anti-retour ( 28 ) et dans la deuxième arrivée ( 30 ) est montée une vanne ( 32 ) de régulation du débit.
  6. Générateur ( 1 ) de vapeur à combustible fossile suivant la revendication 5,
    caractérisé en ce que
    la première arrivée ( 26 ) bifurque d'une pompe ( 8 ) d'alimentation.
  7. Générateur ( 1 ) de vapeur à combustible fossile suivant l'une des revendications précédentes,
    caractérisé en ce que
    un dispositif ( 34 ) de mesure du débit est monté dans le trajet ( 2 ) de courant, du côté du fluide en écoulement, derrière la bifurcation de la deuxième arrivée ( 30 ).
  8. Centrale à vapeur ayant un générateur ( 1 ) de vapeur à combustible fossile suivant l'une des revendications précédentes.
EP11766973.9A 2010-10-05 2011-09-30 Générateur de vapeur à combustibles fossiles Active EP2625390B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL11766973T PL2625390T3 (pl) 2010-10-05 2011-09-30 Opalana paliwami kopalnymi wytwornica pary

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010041962 DE102010041962B3 (de) 2010-10-05 2010-10-05 Fossil befeuerter Dampferzeuger
PCT/EP2011/067125 WO2012045677A2 (fr) 2010-10-05 2011-09-30 Générateur de vapeur à combustibles fossiles

Publications (2)

Publication Number Publication Date
EP2625390A2 EP2625390A2 (fr) 2013-08-14
EP2625390B1 true EP2625390B1 (fr) 2015-10-28

Family

ID=44764142

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11766973.9A Active EP2625390B1 (fr) 2010-10-05 2011-09-30 Générateur de vapeur à combustibles fossiles

Country Status (9)

Country Link
US (1) US9506376B2 (fr)
EP (1) EP2625390B1 (fr)
JP (1) JP5723013B2 (fr)
KR (1) KR101817777B1 (fr)
CN (1) CN103154443B (fr)
DE (1) DE102010041962B3 (fr)
DK (1) DK2625390T3 (fr)
PL (1) PL2625390T3 (fr)
WO (1) WO2012045677A2 (fr)

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK118672B (da) * 1964-03-13 1970-09-21 Siemens Ag Reguleringsapparat til tvangscirkulationskedler.
US3385270A (en) * 1967-02-03 1968-05-28 Siemens Ag Steam power plant with forced-flow boiler system, particularly for supercritical pressure, and a superimposed circulating system
CH582851A5 (fr) 1974-09-17 1976-12-15 Sulzer Ag
DE3607210A1 (de) * 1986-03-05 1986-08-28 Jürgen Dipl.-Ing. Rimmelspacher (FH), 8068 Pfaffenhofen Dampferzeuger mit no(pfeil abwaerts)x(pfeil abwaerts)-minderungsanlage
DE4029991A1 (de) * 1990-09-21 1992-03-26 Siemens Ag Kombinierte gas- und dampfturbinenanlage
JP2955085B2 (ja) 1991-10-23 1999-10-04 三菱重工業株式会社 変圧貫流ボイラ
JPH06313506A (ja) 1993-04-30 1994-11-08 Babcock Hitachi Kk ボイラ過熱器スプレイ系統の切替方式
JPH07293809A (ja) 1994-04-22 1995-11-10 Babcock Hitachi Kk 過熱低減器の注水制御方法および装置
DE4432960C1 (de) 1994-09-16 1995-11-30 Steinmueller Gmbh L & C Verfahren zum Betrieb eines Dampfkraftwerkes und Dampfkraftwerk
JP3755910B2 (ja) 1994-10-25 2006-03-15 バブコック日立株式会社 再熱蒸気系減温器の注水制御装置
US6205762B1 (en) * 1997-04-15 2001-03-27 Mitsubishi Heavy Industries, Ltd. Combined cycle power generating plant and method of supplying cooling steam for gas turbine in same
DE19749452C2 (de) * 1997-11-10 2001-03-15 Siemens Ag Dampfkraftanlage
JPH11350921A (ja) 1998-06-05 1999-12-21 Babcock Hitachi Kk 排熱回収ボイラ
DE19849740A1 (de) 1998-10-28 2000-01-05 Siemens Ag Gas- und Dampfturbinenanlage
DE10227709B4 (de) 2001-06-25 2011-07-21 Alstom Technology Ltd. Dampfturbinenanlage sowie Verfahren zu deren Betrieb
JP4131859B2 (ja) * 2004-06-11 2008-08-13 株式会社日立製作所 蒸気温度制御装置及び蒸気温度制御方法並びにこれらを用いた発電プラント
US8104283B2 (en) * 2007-06-07 2012-01-31 Emerson Process Management Power & Water Solutions, Inc. Steam temperature control in a boiler system using reheater variables

Also Published As

Publication number Publication date
CN103154443B (zh) 2015-04-01
KR101817777B1 (ko) 2018-02-21
US9506376B2 (en) 2016-11-29
DE102010041962B3 (de) 2012-02-16
DK2625390T3 (en) 2016-02-08
US20130205785A1 (en) 2013-08-15
WO2012045677A3 (fr) 2013-01-17
EP2625390A2 (fr) 2013-08-14
WO2012045677A2 (fr) 2012-04-12
JP5723013B2 (ja) 2015-05-27
JP2013543573A (ja) 2013-12-05
KR20130100148A (ko) 2013-09-09
CN103154443A (zh) 2013-06-12
PL2625390T3 (pl) 2016-04-29

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