EP2698507A1 - System und Verfahren zur Temperatursteuerung eines wieder aufgeheizten Dampfes - Google Patents

System und Verfahren zur Temperatursteuerung eines wieder aufgeheizten Dampfes Download PDF

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Publication number
EP2698507A1
EP2698507A1 EP12180786.1A EP12180786A EP2698507A1 EP 2698507 A1 EP2698507 A1 EP 2698507A1 EP 12180786 A EP12180786 A EP 12180786A EP 2698507 A1 EP2698507 A1 EP 2698507A1
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EP
European Patent Office
Prior art keywords
steam
turbine
temperature
reheater
line
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
Application number
EP12180786.1A
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English (en)
French (fr)
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EP2698507B1 (de
Inventor
Christian Dicker
Julia Kirchner
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General Electric Technology GmbH
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Alstom Technology AG
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Publication date
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Priority to EP12180786.1A priority Critical patent/EP2698507B1/de
Priority to PCT/EP2013/066929 priority patent/WO2014026995A2/en
Publication of EP2698507A1 publication Critical patent/EP2698507A1/de
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Publication of EP2698507B1 publication Critical patent/EP2698507B1/de
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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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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
    • 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
    • F01K7/226—Inter-stage steam injection
    • 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
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/12—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays
    • F22G5/14—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays by live steam

Definitions

  • This invention relates generally to a method and system for controlling the hot reheater outlet steam temperature, particularly at low turbine load.
  • a modern steam generator can include a complex configuration of various thermal and hydraulic units for preheating and evaporating water, and for superheating steam.
  • the surfaces of such units are arranged to facilitate: a complete and efficient fuel combustion while minimizing emissions of particulate and gaseous pollutants; steam generation at a desired pressure, temperature and flow rate; and to maximize recovery of the heat produced upon combustion of the fuel.
  • reheaters and superheaters are specially designed tube bundles capable of increasing the temperature of saturated steam. Additionally, reheaters and superheaters are designed to obtain specific steam outlet temperatures, while keeping metal temperatures from becoming too elevated, and limiting steam flow pressure losses.
  • a reheater or a superheater is a single-phase heat exchanger comprising tubes through which steam flows, and across which the combustion or flue gas passes on the outside of the tubes. Reheater and superheater tube bundles are often made of a steel alloy capable of withstanding high operating temperatures.
  • the reheater typically provides the steam for a second turbine following the first turbine, which is typically fed directly from the feed water cycle going through the steam generator.
  • the first turbine is typically known as high-pressure or HP turbine and the second turbine or turbine group as intermediate pressure or IP turbine or turbine group.
  • the reheater receives its feed stream from the steam which exits the HP turbine.
  • reheater outlet temperature (RHO) required at main continuous rated (MCR) conditions may not be achieved at certain load levels. As a consequence the IP turbine will not receive steam heated to the optimal operational temperature.
  • a known method to control reheat steam temperature is by water spray, also called direct contact attemperation or de-superheating, by which a cooling water spray is added to the fluid entering the reheater.
  • This method can have a negative effect on cycle efficiency.
  • Another method is to use excess air supplied to the boiler for reheater steam temperature control. This method can have a negative effect on boiler efficiency.
  • Other solutions include drawing off steam from the super heater and/or reheater, leaving however the problem of finding a disposal path for the extracted steam. The methods described above can only be applied if the steam is too hot.
  • a temperature control system including a by-pass line with a by-pass control valve branching off a live steam circuit to a first turbine in a sequence of at least two turbines, with a steam exit line of the first turbine merging with the by-pass line into the inlet of a reheater heated by a steam generator and connected to a second turbine of the sequence of at least two turbines, and having a steam mixing chamber at or after the point of merging and before the inlet into the reheater.
  • the steam mixing chamber has preferable a first inlet connected to the by-pass line and a second inlet connected to the steam exit line of the first turbine.
  • the steam mixing chamber includes preferably a static steam mixer.
  • the line to the by-pass can be preferably connected to the main/live steam line at a location between the steam generator and the main steam inlet of the first turbine or at a location within the steam generator downstream the primary superheater, e.g. as intermediate boiler extraction.
  • a method for controlling the outlet temperature of a reheater positioned in the steam path between a first turbine and a second turbine in a sequence of at least two turbines wherein at low unit loads the steam temperature at the inlet to the reheater is raised at a pressure lower than the main continuous rated operation pressure by extracting steam from a live steam line connecting the steam generator with the first turbine and mixing the extracted steam with the steam from the first turbine such that the inlet steam temperature to the reheater is raised to a temperature sufficient to maintain the outlet temperature at the desired level, e.g. close to the MCR temperature or closer to the HP turbine/live steam temperature.
  • Fig. 1 shows a schematic diagram of a section of a steam power plant designed to provide power to a public power grid.
  • the steam is generated in a boiler 10.
  • the boiler 10 receives water from condenser (not shown) or a source external to the plant.
  • the water passes through a feed water preheater 11 as shown before entering the boiler.
  • the boiler 10 can be fired directly by fossil fuels such as coal or gas or by a non-convention heat source in form of a secondary heat exchange cycle or as is otherwise known in the industry.
  • the live steam is generated within a cascade of heat exchangers 12 before exiting the boiler into the main/live steam pipework 13.
  • the feed pipe 13 directs the steam into the inlet of a first turbine 14, which is in this example a high-pressure (HP) turbine within several turbine stages of.
  • the main steam control valve 131 controls the amount of steam entering the HP turbine 14.
  • the partially expanded steam is returned in the cold reheat (CRH) line 15 to the inlet of a reheater section 16 of the boiler.
  • CSH cold reheat
  • the partially expanded steam is reheated using the heat generated in the boiler 10.
  • the reheat outlet (RHO) is connected through the hot reheater (HRH) line 17 with the inlet of a second turbine 18, which is in this example an intermediate-pressure (IP) turbine within several turbine stages.
  • IP intermediate-pressure
  • the turbines share a single rotor 19 which drives a generator (not shown).
  • Further turbine stages may include additional IP turbines or one or more low pressure (LP) turbines with or without additional reheating circuits.
  • the principles of the present invention can be applied to any steam power plant with a reheating system and at least two turbines connected through a reheating system.
  • the system of FIG. 1 further includes a by-pass line 132 connecting the main steam line 13 with the CRH line 15.
  • the amount of live steam taken from the main line is controlled by a by-pass valve 133.
  • a spray cooler 134 is installed at the outlet of the HP by-pass valve to control the temperature T2 in the HP by-pass exhaust line.
  • the by-pass line directs steam into a mixing chamber 151 within the CRH line 15.
  • the second inlet to the mixing chamber 151 is connected to the exit of the HP turbine 14. From the mixing chamber 151 the CRH line 15 connects to the inlet of the reheater 16.
  • the mixing chamber 151 of this example is a static mixer with fixed elements made of steel or steel alloy suitable for the steam temperature required for this application.
  • Such mixers are commercially available for example as STATIFLOTM series 800/850.
  • HP bypass system During operation in a conventional power plant with a by-pass the HP bypass system has the following standard functions according to the standard ANSI/ISA-77.13.01-1999:
  • the by-pass line 132 typically includes a de-superheater 134, which can be a spray cooling chamber located within or after the by-pass valve 133.
  • reheater outlet (RHO) steam temperature T4 In contrast to known applications for reheat temperature control, it is the aim of the present example to raise the inlet temperature T3 of the steam to the reheater section 16, which will, assuming a constant or similar heat input into the boiler, result in an increased reheater outlet (RHO) steam temperature T4.
  • the HP bypass valve 133 is operated in a way to control the RHO temperature T4 by means of by-passing live steam around the HP turbine 14 directly into the cold reheat (CRH) line 15.
  • the pressure of the live steam is reduced to the pressure of the cold reheat (CRH) steam. This leads to a temperature reduction of the life steam by throttling (Joule-Thompson-Effect).
  • the steam downstream the HP by-pass valve 133 has a temperature T2 higher than the temperature T1 of CRH steam coming from the HP turbine exhaust.
  • T2 the temperature of CRH steam coming from the HP turbine exhaust.
  • the above basic steps to increase the temperature can be refined to match any existing design parameters of the power plant.
  • the reduction of pressure in the HP by-pass valve 132 can be adjusted to maximum the pressure of the cold reheat (CRH) steam design values.
  • the temperature T2 of the by-pass steam can be reduced by suitable cooling such as spray water cooling in the de-superheater 134.
  • suitable cooling such as spray water cooling in the de-superheater 134.
  • the mixing can take place in the standard CRH piping 15.
  • the by-pass mass flow required to achieve a high CRH inlet temperature T3 may be larger than in the first example above. But the loss of efficiency can be offset by the reduced costs in implementing this variant of the invention.
  • This kind of operation reduces the mass flow through the HP turbine more than the solution without using spraywater. As a large amount of spray water is required, the mass flow to the second turbine is much greater than when not using spray water.
  • FIG. 2 An example of this variant of the invention is shown in FIG. 2 .
  • the by-pass line 132 extracts steam from an intermediate point in the superheater section 12, which is located after the steam/water separator 101.
  • the live steam temperature T5 may be increased.
  • the temperature T2 after the throttling will however be lower as the steam temperature T6, this is again due to the Joule-Thompson rule.
  • the hot reheater outlet temperature (HRH temperature) T4 is controlled by adjusting the cold reheater inlet temperature (CRH temperature) T3.
  • the CRH temperature T3 is set such that a desired HRH temperature can be obtained with the heat input from the boiler 10 into the reheater 16. This heat input can be calculated from the boiler and boiler fuel feed parameters.
  • the CRH temperature after mixing the mass flow from the turbine 14 with the mass flow from the by-pass 132 can be adjusted by enthalpy balances over the HP 14 turbine and the HP by-pass valve 133.
  • the enthalpy balance over the HP turbine yields temperature T1 at the exit of the HP turbine 14.
  • an enthalpy balance over the HP by-pass 132 delivers the temperature T2 downstream the HP bypass valve.
  • the mixing temperature T3 can then be calculated.
  • the HP by-pass valve exhaust temperature T2 can be adjusted by spraying water in the de-superheater 134.
  • the pressure drop over the HP by-pass valve 133 is controlled in a similar way as the temperature.
  • the pressure in the HP bypass exhaust line 132 must be slightly higher than the CRH pressure, to be sure that the HP by-pass exhaust steam can enter the CRH line 15.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)
EP12180786.1A 2012-08-17 2012-08-17 System und Verfahren zur Temperatursteuerung eines wieder aufgeheizten Dampfes Not-in-force EP2698507B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12180786.1A EP2698507B1 (de) 2012-08-17 2012-08-17 System und Verfahren zur Temperatursteuerung eines wieder aufgeheizten Dampfes
PCT/EP2013/066929 WO2014026995A2 (en) 2012-08-17 2013-08-13 System and method for temperature control of reheated steam

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EP12180786.1A EP2698507B1 (de) 2012-08-17 2012-08-17 System und Verfahren zur Temperatursteuerung eines wieder aufgeheizten Dampfes

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EP2698507B1 EP2698507B1 (de) 2017-03-01

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103925021A (zh) * 2014-04-15 2014-07-16 上海平安高压调节阀门有限公司 高低压旁路系统
CN105781630A (zh) * 2016-03-02 2016-07-20 王欣 电力发电汽轮机旁路控制系统
JP2018063063A (ja) * 2016-10-11 2018-04-19 住友重機械工業株式会社 ボイラシステム
CN108474268A (zh) * 2015-12-22 2018-08-31 西门子能源有限公司 联合循环动力装置中的烟囱能量控制
CN108836110A (zh) * 2018-08-18 2018-11-20 吴联凯 一种基于温度测量装置的蒸汽发生器及其控制方法
CN110529210A (zh) * 2019-09-11 2019-12-03 东方电气集团东方锅炉股份有限公司 一种供热抽汽再加热的方法及系统
CN114635766A (zh) * 2022-01-06 2022-06-17 国核电力规划设计研究院有限公司 压水堆核电机组供热抽汽管道阀门设置与控制系统及方法
WO2024013695A1 (en) * 2022-07-13 2024-01-18 Keppel Seghers Belgium Nv Method for generating steam in combination with a power generation process as well as plant to this end

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE821790C (de) * 1950-08-17 1951-11-19 Borsig A G Einrichtung zur Temperatur- und Mengenregelung von Dampfturbinen mit Zwischenueberhitzung
DE3149772A1 (de) * 1980-12-22 1982-07-29 General Electric Co., Schenectady, N.Y. "heizdampfkuehlregelanordnung"
JPS5810104A (ja) * 1981-07-10 1983-01-20 Hitachi Ltd タ−ビンプラントおよびその制御方法
US4455836A (en) * 1981-09-25 1984-06-26 Westinghouse Electric Corp. Turbine high pressure bypass temperature control system and method
SU1554954A1 (ru) * 1988-06-02 1990-04-07 Завод-Втуз При Производственном Объединении Турбостроения "Ленинградский Металлический Завод" Устройство дл смешивани газов
US5605118A (en) 1994-11-15 1997-02-25 Tampella Power Corporation Method and system for reheat temperature control
JP2012135737A (ja) * 2010-12-27 2012-07-19 Shimadzu Corp 静止型ミキシング機構

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE821790C (de) * 1950-08-17 1951-11-19 Borsig A G Einrichtung zur Temperatur- und Mengenregelung von Dampfturbinen mit Zwischenueberhitzung
DE3149772A1 (de) * 1980-12-22 1982-07-29 General Electric Co., Schenectady, N.Y. "heizdampfkuehlregelanordnung"
JPS5810104A (ja) * 1981-07-10 1983-01-20 Hitachi Ltd タ−ビンプラントおよびその制御方法
US4455836A (en) * 1981-09-25 1984-06-26 Westinghouse Electric Corp. Turbine high pressure bypass temperature control system and method
SU1554954A1 (ru) * 1988-06-02 1990-04-07 Завод-Втуз При Производственном Объединении Турбостроения "Ленинградский Металлический Завод" Устройство дл смешивани газов
US5605118A (en) 1994-11-15 1997-02-25 Tampella Power Corporation Method and system for reheat temperature control
JP2012135737A (ja) * 2010-12-27 2012-07-19 Shimadzu Corp 静止型ミキシング機構

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103925021B (zh) * 2014-04-15 2016-02-17 上海平安高压调节阀门有限公司 高低压旁路系统
CN103925021A (zh) * 2014-04-15 2014-07-16 上海平安高压调节阀门有限公司 高低压旁路系统
US10808578B2 (en) 2015-12-22 2020-10-20 Siemens Aktiengesellschaft Stack energy control in combined cycle power plant using heating surface bypasses
CN108474268A (zh) * 2015-12-22 2018-08-31 西门子能源有限公司 联合循环动力装置中的烟囱能量控制
CN105781630A (zh) * 2016-03-02 2016-07-20 王欣 电力发电汽轮机旁路控制系统
JP2018063063A (ja) * 2016-10-11 2018-04-19 住友重機械工業株式会社 ボイラシステム
CN108836110A (zh) * 2018-08-18 2018-11-20 吴联凯 一种基于温度测量装置的蒸汽发生器及其控制方法
CN110529210A (zh) * 2019-09-11 2019-12-03 东方电气集团东方锅炉股份有限公司 一种供热抽汽再加热的方法及系统
CN110529210B (zh) * 2019-09-11 2024-05-03 东方电气集团东方锅炉股份有限公司 一种供热抽汽再加热的方法及系统
CN114635766A (zh) * 2022-01-06 2022-06-17 国核电力规划设计研究院有限公司 压水堆核电机组供热抽汽管道阀门设置与控制系统及方法
CN114635766B (zh) * 2022-01-06 2024-02-09 国核电力规划设计研究院有限公司 压水堆核电机组供热抽汽管道阀门设置与控制系统及方法
WO2024013695A1 (en) * 2022-07-13 2024-01-18 Keppel Seghers Belgium Nv Method for generating steam in combination with a power generation process as well as plant to this end
BE1030715B1 (nl) * 2022-07-13 2024-02-12 Keppel Seghers Belgium Nv Werkwijze voor het opwekken van stoom in combinatie met een energieopwekkingsproces alsook installatie hiervoor

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WO2014026995A3 (en) 2014-08-07
WO2014026995A2 (en) 2014-02-20
EP2698507B1 (de) 2017-03-01

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