EP2625390A2 - Fossil befeuerter dampferzeuger - Google Patents
Fossil befeuerter dampferzeugerInfo
- Publication number
- EP2625390A2 EP2625390A2 EP11766973.9A EP11766973A EP2625390A2 EP 2625390 A2 EP2625390 A2 EP 2625390A2 EP 11766973 A EP11766973 A EP 11766973A EP 2625390 A2 EP2625390 A2 EP 2625390A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- fossil
- steam generator
- flow
- fired steam
- medium
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 7
- 238000010438 heat treatment Methods 0.000 claims description 12
- 239000012530 fluid Substances 0.000 claims description 4
- 238000002347 injection Methods 0.000 abstract description 51
- 239000007924 injection Substances 0.000 abstract description 51
- 238000000034 method Methods 0.000 abstract description 4
- 238000012986 modification Methods 0.000 abstract description 2
- 230000004048 modification Effects 0.000 abstract description 2
- 230000008569 process Effects 0.000 abstract description 2
- 238000013021 overheating Methods 0.000 abstract 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 19
- 238000003303 reheating Methods 0.000 description 5
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000004088 simulation Methods 0.000 description 3
- 238000009835 boiling Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 239000002803 fossil fuel Substances 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- 239000003570 air Substances 0.000 description 1
- 230000006399 behavior Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 239000003546 flue gas Substances 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
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
- 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 a flow path forming, flowed through by a flow medium medium M M economi--, evaporator and superheater in a plurality of pressure stages, in which ver in a high-pressure stage an overflow line on the inlet side with the flow ⁇ bunden and leads to a flow medium in a medium-pressure stage in front 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 supplied to a steam turbine ⁇ leads.
- the fossil-fueled steam generator also comprises a plurality of pressure stages with different thermal states of the respectively contained water-steam mixture.
- the first (high) pressure level the flow medium passing through the flow path on its first economiser, to use the residual heat Voricar ⁇ mung of the flow medium, and then various levels of dene ⁇ evaporator and superheater.
- 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 in the high pressure part of the steam turbine flows, is there decompressed, and the following print ⁇ stage of the steam generator is supplied.
- Such power changes of a power plant block in the se ⁇ customer area are possible only by a coordinated interaction of steam generator and steam turbine.
- the contribution of fossil fuel-fired steam generator can do this is by using his memory, ie the steam but also the fuel storage, as well as rapid changes in the controlling variable ⁇ SEN feedwater, injection water, fuel and air.
- 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 demanded to reach the temperature setpoint.
- results from a higher Enthalpielic of the injection water a ver ⁇ tively larger amount of steam.
- the second supply line branches strö ⁇ tion medium side from behind all high-pressure preheaters.
- the first supply line branches off from the flow medium side in front of all high-pressure preheaters. By taking in the coldest region, a reduction in the temperature of the inlet can in fact already at low addition amount are injection medium reaches that sufficient Ab ⁇ was a guaranteed to boiling. 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 carried out 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 non-return valve, wherein the return ⁇ flap valve prevents backflow from the high pressure path in the low pressure path.
- the return ⁇ flap valve prevents backflow from the high pressure path in the low pressure path.
- 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.
- Advantage ⁇ way legally branches beyond from the first lead of ei ⁇ ner feed pump. Since has a ver ⁇ tively higher pressure under the circumstances just upstream of the flow control valve, the flow medium, it is possible that the entire water path of the injector is on comparatively ⁇ as a lower pressure level. In addition, such an arrangement simplifies the control, and it is furthermore possible to use the feeding pumps with a corresponding branch for reheat injection, which are commonly used today, since the cool medium can also be coupled out in the same location in the present case.
- a flow measuring device is arranged downstream of the branch of the second Zulei ⁇ tion 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 burden of all the affected components such as injection point, heating surfaces and turbine ⁇ reduced the same power relief compared to previous concepts, as for the same power deduction 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 shows the flow medium side schematically the high-pressure and medium-pressure part of a fossil-fired steam ⁇ generator with optimized injection water supply line
- FIG. 3 shows a diagram with simulation results for improving the instantaneous reserve of a fossil-fired steam generator by increasing the injection enthalpy of reheating in an upper load range
- FIG. 4 shows a diagram with simulation results for improving the instantaneous reserve of a fossil-fired steam generator by increasing the injection enthalpy of reheating in a lower load range.
- FIG. 1 shows schematically 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. There it is first brought by Hochlichvormaschinern 10 to an elevated temperature, which can be operated for example with bleed steam. Then follow Economizersammlung- surfaces 12, in which usually flue gas waste heat is used for white ⁇ direct heating of the flow medium and Ver ⁇ dampfersammlung vom 14, in which the flow medium is vaporized by means of heat derived 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 be representative of a plurality of serially connected heating surfaces, which are not shown diffe ⁇ ren formulate for clarity.
- any residual moisture present is separated off in a water separation device, not shown in more detail, and the remaining steam supplied to superheater heating surfaces (not shown). Subsequently, the superheated steam is expanded in the high pressure ⁇ part of a steam turbine. Subsequently, the flow medium M flows into the medium-pressure part 4 of the Dampferzeu ⁇ gers, where it is superheated in a number of intermediate superheater 16 again and is then supplied to the medium-pressure part of the steam turbine.
- An injection valve 18 is arranged upstream of the reheater heating surfaces on the flow medium side. Here cooler and unevaporated flow medium M for regulating 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 for a required, increasing the enthalpy of the water injection ⁇ is designed.
- the overflow line 24 has a ⁇ ers te supply line 26 which branches directly into the feed pump 8, and supplying flow medium M with a relatively low temperature of the overflow 24th 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 in this case in the flow path 6 behind two branch locations of the leads 26, 30, so that the amount of derive ⁇ branched flow medium M for the feedwater control need not be considered here.
- 2 shows an alternative embodiment which corresponds Wesent ⁇ union of Figure 1, but here are the locations of the flow control valve 32 and check valve 28 ver ⁇ exchanged.
- the first supply line 26 thus has a control valve 32 and the second supply line 30 has a non-return valve 28.
- This embodiment is also possible, however, the entire injection path must be designed for higher pressures.
- an additional branch 36 is provided for the first supply line 26, since due to the higher pressure level can not be coupled ei ⁇ ner arbitrary point of the feed pump 8 fluid medium M.
- FIG. 3 shows a diagram with simulation results using the described interconnection. Is applied the percentage of additional power with respect to full load 38 to the time 40 seconds after a sudden reduction of the temperature desired value for the temperature at the off ⁇ takes 20 of the medium-pressure part 4 by 20 ° C at 95% load.
- the curve 42 shows the results without heated injection fluid, that is to say according to the usual system
- the curve 44 shows the results with the injection system connected as described above. It can be seen in FIG. 2 that the maximum of the curve 44 is higher than the curve 42. The additionally released power is thus higher.
- FIG. 4 is modified only slightly compared with FIG. 3 and shows the simulated curves 42, 44 for 40% load, all other parameters are identical to FIG. 3, as well as the meaning of the curves 42, 44. Both curves show here
Landscapes
- 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)
Abstract
Description
Claims
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 (de) | 2010-10-05 | 2011-09-30 | Fossil befeuerter dampferzeuger |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2625390A2 true EP2625390A2 (de) | 2013-08-14 |
EP2625390B1 EP2625390B1 (de) | 2015-10-28 |
Family
ID=44764142
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11766973.9A Active EP2625390B1 (de) | 2010-10-05 | 2011-09-30 | Fossil befeuerter dampferzeuger |
Country Status (9)
Country | Link |
---|---|
US (1) | US9506376B2 (de) |
EP (1) | EP2625390B1 (de) |
JP (1) | JP5723013B2 (de) |
KR (1) | KR101817777B1 (de) |
CN (1) | CN103154443B (de) |
DE (1) | DE102010041962B3 (de) |
DK (1) | DK2625390T3 (de) |
PL (1) | PL2625390T3 (de) |
WO (1) | WO2012045677A2 (de) |
Family Cites Families (17)
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 (de) * | 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 |
CA2257292C (en) * | 1997-04-15 | 2001-08-28 | Mitsubishi Heavy Industries, Ltd. | Combined cycle power plant and cooling steam supply method for gas turbine therein |
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 |
-
2010
- 2010-10-05 DE DE201010041962 patent/DE102010041962B3/de not_active Expired - Fee Related
-
2011
- 2011-09-30 KR KR1020137008642A patent/KR101817777B1/ko active IP Right Grant
- 2011-09-30 US US13/877,729 patent/US9506376B2/en active Active
- 2011-09-30 DK DK11766973.9T patent/DK2625390T3/en active
- 2011-09-30 EP EP11766973.9A patent/EP2625390B1/de active Active
- 2011-09-30 JP JP2013532143A patent/JP5723013B2/ja active Active
- 2011-09-30 CN CN201180048132.6A patent/CN103154443B/zh active Active
- 2011-09-30 WO PCT/EP2011/067125 patent/WO2012045677A2/de active Application Filing
- 2011-09-30 PL PL11766973T patent/PL2625390T3/pl unknown
Also Published As
Publication number | Publication date |
---|---|
DE102010041962B3 (de) | 2012-02-16 |
DK2625390T3 (en) | 2016-02-08 |
CN103154443A (zh) | 2013-06-12 |
JP5723013B2 (ja) | 2015-05-27 |
KR101817777B1 (ko) | 2018-02-21 |
EP2625390B1 (de) | 2015-10-28 |
WO2012045677A3 (de) | 2013-01-17 |
PL2625390T3 (pl) | 2016-04-29 |
JP2013543573A (ja) | 2013-12-05 |
CN103154443B (zh) | 2015-04-01 |
WO2012045677A2 (de) | 2012-04-12 |
US20130205785A1 (en) | 2013-08-15 |
US9506376B2 (en) | 2016-11-29 |
KR20130100148A (ko) | 2013-09-09 |
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