US20030145596A1 - Method for operating a steam turbine installation and a steam turbine installation that functions according thereto - Google Patents

Method for operating a steam turbine installation and a steam turbine installation that functions according thereto Download PDF

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Publication number
US20030145596A1
US20030145596A1 US10/168,686 US16868602A US2003145596A1 US 20030145596 A1 US20030145596 A1 US 20030145596A1 US 16868602 A US16868602 A US 16868602A US 2003145596 A1 US2003145596 A1 US 2003145596A1
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US
United States
Prior art keywords
steam
steam turbine
heat exchanger
temperature heat
temperature
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.)
Abandoned
Application number
US10/168,686
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English (en)
Inventor
Christoph Noelscher
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Siemens AG
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Siemens AG
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Filing date
Publication date
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NOELSCHER, CHRISTOPH
Publication of US20030145596A1 publication Critical patent/US20030145596A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
    • 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
    • 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]
    • Y02E20/18—Integrated gasification combined cycle [IGCC], e.g. combined with carbon capture and storage [CCS]

Definitions

  • the invention relates to a method of operating a steam turbine installation, in which method combustion gas generated by combustion of a fossil fuel is guided so as to exchange heat with a medium flowing in the water/steam cycle of a steam turbine. It also relates to a steam turbine installation operating according to this method.
  • the combustion gas expanded—with work output—and cooled to approximately 540° C., is guided in a waste-heat steam generator so as to exchange heat with a medium flowing in the water/steam cycle of a steam turbine in the form of a water/water/steam mixture.
  • the live steam generated in the process is expanded—with work output—at an inlet temperature of approximately 540° C. in the steam turbine.
  • PFBC pressurized fluidized bed combustion
  • PPCC pressurized pulverized coal combustion
  • coal is likewise burnt as the primary energy carrier and the cleaned combustion product is supplied as hot combustion gas directly to the gas turbine.
  • the combustion gas expanded—with work output—and cooled to approximately 500° C. to 550° C. in the gas turbine is guided in a waste-heat steam generator or heat exchanger so as to exchange heat with the medium flowing in the water/steam cycle of the steam turbine.
  • the steam generated in the process is superheated either in the waste-heat steam generator itself or in the combustion installation and again supplied as live steam to the steam turbine.
  • the cooled combustion gas is cleaned in an installation which removes oxides of nitrogen and/or sulfur (DENOX, REA plant) before it is exhausted to the surroundings through a chimney.
  • the hot combustion gas generated in the case of the EFCC process in a so-called slag tap firing process is first cleaned by ash separation and subsequently supplied to the high-temperature heat exchanger.
  • the parts of the latter exposed to the high combustion gas temperature for example tube bundles through which the compressed air flows and around which the hot combustion gas flows, consist of a ceramic or a metallic material involving a special high-temperature resistant alloy.
  • This new concept promises an increase in the installation efficiency, at between 51% and 53%, relative to the combined processes with integrated gasification combined cycle(IGCC), pressurized fluidized bed combustion (PFBC) or pressurized pulverized coal combustion (PPCC).
  • IGCC integrated gasification combined cycle
  • PFBC pressurized fluidized bed combustion
  • PPCC pressurized pulverized coal combustion
  • EFCC externally fired combustion cycle
  • the invention is based on the object of providing a method of operating a steam turbine installation in which, in a simple manner, as high as possible an installation efficiency is achieved by a live steam inlet temperature, for the steam turbine, which is as high as possible.
  • a particularly suitable steam turbine installation for carrying out the method is, in addition, to be provided.
  • the object is achieved according to the invention by the features of claim 1.
  • the hot combustion gas generated by combustion of a fossil fuel is first guided as the primary medium in a high-temperature heat exchanger so as to exchange heat with steam, flowing in the water/steam cycle of the steam turbine, as the secondary medium.
  • the steam heated in the process to a temperature of preferably more than 800° C. is supplied as live steam to the steam turbine.
  • the combustion gas cooled in the high-temperature heat exchanger is subsequently guided in a waste-heat steam generator so as to exchange heat with feed water flowing in the water/steam cycle in order to generate the steam.
  • the invention is based on the consideration that the mechanical compression energy for the electricity generation necessary in the EFCC process can be more favorably used if, instead of air, a liquid is compressed and subsequently thermally evaporated.
  • the heating of steam which is extracted from a conventional water/steam cycle of a steam turbine, is then particularly favorable.
  • This steam can then be heated in the high-temperature heat exchanger to a temperature of between 1200° C. and 1400° C. and subsequently expanded in a cooled high-temperature steam turbine.
  • the latter then drives a generator or also a feed-water pump.
  • the energy extracted from the high-temperature heat exchanger can be exergetically better used, as compared with the EFCC process.
  • a smaller installation volume can, in the case of the heating of steam for a steam turbine, be achieved for the same useful mechanical energy as compared with the EFCC process.
  • this is based on the fact that, for the same transmission of high-temperature heat, the fuel utilization is higher as compared with the EFCC process because, in the latter, the gas turbine waste heat is usually supplied to the combustion process.
  • the high-temperature heat exchanger can have a smaller configuration as compared with the EFCC process because the fuel utilization must, for the same effectiveness, be the same for the same useful mechanical energy.
  • the more efficient utilization of the high-temperature heat by the steam turbine additionally permits a reduction in the conventional steam constituent as compared with the EFCC process.
  • the air compressor necessary with the latter is dispensed with.
  • the steam produced in the waste-heat steam generator is first expanded—with work output—in a separate (conventional) steam turbine before this expanded steam is heated in the high-temperature heat exchanger to the live steam temperature of the steam turbine connected downstream of the high-temperature heat exchanger on the steam side.
  • the two steam turbines, together with a generator can then be seated on a common shaft (single-shaft embodiment) and can operate on a common condenser, which is connected upstream of the heating surfaces of the waste-heat steam generator within the water/steam cycle.
  • the steam turbine connected down-stream of the high-temperature heat exchanger on the steam side then forms, so to speak, the high-temperature part of the steam turbine connected upstream of the high-temperature heat exchanger on the steam side.
  • a cooling steam line by means of which steam extracted from the water/steam cycle can be supplied as cooling steam to the steam turbine, is guided to the latter.
  • the cooling steam line is expediently connected to a steam line connecting the high-temperature heat exchanger to the waste-heat steam generator.
  • the cooling steam line is, in the case of the embodiment with a separate steam turbine which [lacuna] expediently connected to a steam line connecting the latter to the high-temperature heat exchanger, by means of which steam line the steam to be heated or to be superheated is also guided.
  • FIG. 1 shows, diagrammatically, a steam turbine installation with a high-temperature heat exchanger for the generation of live steam for a cooled high-temperature steam turbine and
  • FIG. 2 shows, in a representation corresponding to FIG. 1, a steam turbine installation with two steam turbines in single-shaft embodiment.
  • the steam turbine installation shown in FIG. 1 comprises a combustion installation 1 in the form, for example, of an atmospheric pulverized coal firing with liquidized ash removal in a separator 2 (slag tap firing), together with a high-temperature heat exchanger 3 and a waste-heat steam generator 4 connected downstream of it on the combustion gas side.
  • the heating surfaces 5 of the waste-heat steam generator 4 are connected into the water/steam cycle 6 of a steam turbine 7 .
  • the high-temperature heat exchanger 3 is connected, on the steam side, downstream of the waste-heat steam generator 4 and upstream of the steam turbine 7 .
  • heating surfaces 8 of the high-temperature heat exchanger 3 consisting for example of ceramic material or of a special high-temperature resistant metal alloy, for example an oxide dispersion strengthened (ODS) alloy, are connected downstream, by means of a steam line 9 , to the heating surfaces 5 of the waste-heat steam generator 4 and upstream, by means of a high-temperature steam line 10 , to the steam turbine 7 .
  • ODS oxide dispersion strengthened
  • the live steam FD expanded—with work output—in the steam turbine 7 is condensed in a condenser 12 connected downstream of the steam turbine 7 .
  • the resulting condensate or feed water SW is supplied, by means of a feed-water pump 13 , to the heating surfaces 5 of the waste-heat steam generator 4 , in the form for example of a preheater and an evaporator connected downstream of it.
  • the steam WD generated in the waste-heat steam generator 4 is guided via the steam line 9 to the steam side of the high-temperature heat exchanger 3 .
  • the steam turbine 7 is cooled by means of cooling steam KD and is therefore preferably embodied as a high-temperature steam turbine.
  • the cooling steam KD is extracted from the water/steam cycle 6 from the steam line 9 .
  • a cooling steam line 14 is connected to the steam line 9 connecting the high-temperature heat exchanger 3 to the waste-heat steam generator 4 .
  • the steam turbine installation comprises, in addition to the high-temperature steam turbine 7 , a further steam turbine 15 , which drive the generator 11 via a common shaft 16 (single shaft).
  • the generation of the hot combustion gas RG takes place in a manner analogous to the exemplary embodiment of FIG. 1.
  • the hot combustion gas RG is again guided in the high-temperature heat exchanger 3 so that it exchanges heat with steam WD, which is extracted from the further steam turbine 15 in this case.
  • the steam turbine 15 is connected on the steam side between the waste-heat steam generator 4 and the high-temperature heat exchanger 3 .
  • the further steam turbine 15 is again connected on the exhaust steam side to the condenser 12 , into which the high-temperature steam turbine 7 also opens on the exhaust steam side.
  • the actual high-temperature part of the separate steam turbine 15 is embodied in the form of a high-temperature steam turbine 7 , whereas this high-temperature part is integrated into the steam turbine 7 in the exemplary embodiment of FIG. 1.
  • the steam turbine 7 operating as the high-temperature part, is again cooled by means of cooling steam KD.
  • the latter is extracted from a steam line 17 connecting the further or separate steam turbine 15 to the heating surfaces 8 of the high-temperature heat exchanger 3 and is guided by means of a cooling steam line 18 , which is connected to the steam line 17 , to the high-temperature steam turbine 7 .
  • the operating pressure of the steam turbine installation 1 is, in practice, approximately limited to between 15 bar and 30 bar at an operating temperature of 1400° C., by the strength of the high-temperature heat exchanger.
  • the operating pressure p in the water/steam cycle 6 , at 30 bar, is therefore relatively low in comparison with a conventional water/steam cycle at approximately 250 bar.
  • the operating pressure can be increased to 150 bar in the case of an operating temperature of 1000° C.

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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)
  • Engine Equipment That Uses Special Cycles (AREA)
US10/168,686 1999-12-21 2000-12-08 Method for operating a steam turbine installation and a steam turbine installation that functions according thereto Abandoned US20030145596A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19961808.9 1999-12-21
DE19961808 1999-12-21

Publications (1)

Publication Number Publication Date
US20030145596A1 true US20030145596A1 (en) 2003-08-07

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ID=7933670

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/168,686 Abandoned US20030145596A1 (en) 1999-12-21 2000-12-08 Method for operating a steam turbine installation and a steam turbine installation that functions according thereto

Country Status (7)

Country Link
US (1) US20030145596A1 (de)
EP (1) EP1240414B1 (de)
JP (1) JP2003518220A (de)
CN (1) CN1297732C (de)
CZ (1) CZ300521B6 (de)
DE (1) DE50015393D1 (de)
WO (1) WO2001046566A1 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102305424A (zh) * 2011-08-04 2012-01-04 际高建业有限公司 大温差低温辐射供暖系统
WO2013123037A1 (en) * 2012-02-13 2013-08-22 United Technologies Corporation Heat exchange system configured with a membrane contractor
US9140145B1 (en) * 2011-08-11 2015-09-22 Sandia Corporation PH adjustment of power plant cooling water with flue gas/fly ash
US9726155B2 (en) 2010-09-16 2017-08-08 Wilson Solarpower Corporation Concentrated solar power generation using solar receivers
SE541066C2 (en) * 2017-06-16 2019-03-26 Climeon Ab System and method for eliminating the presence of droplets in a heat exchanger
US10876521B2 (en) 2012-03-21 2020-12-29 247Solar Inc. Multi-thermal storage unit systems, fluid flow control devices, and low pressure solar receivers for solar power systems, and related components and uses thereof

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4123064B2 (ja) 2003-06-13 2008-07-23 株式会社日立製作所 蒸気タービンロータおよび蒸気タービンプラント
GB2519129A (en) * 2013-10-10 2015-04-15 Ide Technologies Ltd Pumping Apparatus
CN107023337B (zh) * 2017-03-28 2019-03-01 华电电力科学研究院 汽轮机抽凝背系统及其调节方法
CN106988803B (zh) * 2017-05-26 2018-12-25 中国华能集团公司 一种基于抽汽口的低压缸长叶片冷却系统及方法

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CH637184A5 (de) * 1979-04-12 1983-07-15 Sulzer Ag Kombinierte waermekraftanlage mit einer gasturbinengruppe.
AT395635B (de) * 1981-09-22 1993-02-25 Elin Union Ag Kombinierte gasturbine - dampfkraftanlage
JPS6060207A (ja) * 1983-09-13 1985-04-06 Toshiba Corp 蒸気タ−ビンプラント
EP0158629B1 (de) * 1984-03-23 1990-08-16 Herbert Dipl.-Ing. Dr. Univ. Prof. Jericha Dampfkreislauf für Dampfkraftanlagen
DE3613300A1 (de) * 1986-04-19 1987-10-22 Bbc Brown Boveri & Cie Verfahren zum erzeugen von elektrischer energie mit einer eine wirbelschichtfeuerung aufweisenden kombinierten gasturbinen-dampfkraftanlage sowie anlage zur durchfuehrung des verfahrens
JPH07145706A (ja) * 1993-11-24 1995-06-06 Mitsubishi Heavy Ind Ltd 蒸気タービン
US5628183A (en) * 1994-10-12 1997-05-13 Rice; Ivan G. Split stream boiler for combined cycle power plants
JPH08232609A (ja) * 1995-02-27 1996-09-10 Yoshiharu Tachibana 蒸気圧縮再熱再生サイクル
SE9501886L (sv) * 1995-05-19 1996-11-20 Nykomb Synergetics Technology System och anordningar för kraftgenerering på basis av char
JP3697310B2 (ja) * 1996-03-04 2005-09-21 株式会社東芝 コンバインドサイクルプラントの停止方法およびその停止装置
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JPH11211012A (ja) * 1998-01-21 1999-08-06 Ishikawajima Harima Heavy Ind Co Ltd 加圧流動層複合発電設備
JPH11343863A (ja) * 1998-06-02 1999-12-14 Hitachi Ltd ガス化複合発電プラント

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9726155B2 (en) 2010-09-16 2017-08-08 Wilson Solarpower Corporation Concentrated solar power generation using solar receivers
US10280903B2 (en) 2010-09-16 2019-05-07 Wilson 247Solar, Inc. Concentrated solar power generation using solar receivers
US11242843B2 (en) 2010-09-16 2022-02-08 247Solar Inc. Concentrated solar power generation using solar receivers
CN102305424A (zh) * 2011-08-04 2012-01-04 际高建业有限公司 大温差低温辐射供暖系统
US9140145B1 (en) * 2011-08-11 2015-09-22 Sandia Corporation PH adjustment of power plant cooling water with flue gas/fly ash
WO2013123037A1 (en) * 2012-02-13 2013-08-22 United Technologies Corporation Heat exchange system configured with a membrane contractor
US9403102B2 (en) 2012-02-13 2016-08-02 United Technologies Corporation Heat exchange system configured with a membrane contactor
US10876521B2 (en) 2012-03-21 2020-12-29 247Solar Inc. Multi-thermal storage unit systems, fluid flow control devices, and low pressure solar receivers for solar power systems, and related components and uses thereof
SE541066C2 (en) * 2017-06-16 2019-03-26 Climeon Ab System and method for eliminating the presence of droplets in a heat exchanger

Also Published As

Publication number Publication date
EP1240414A1 (de) 2002-09-18
JP2003518220A (ja) 2003-06-03
EP1240414B1 (de) 2008-10-08
WO2001046566A1 (de) 2001-06-28
CZ300521B6 (cs) 2009-06-10
CN1297732C (zh) 2007-01-31
DE50015393D1 (de) 2008-11-20
CZ20022493A3 (cs) 2003-05-14
CN1411530A (zh) 2003-04-16

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Legal Events

Date Code Title Description
AS Assignment

Owner name: SIEMENS AKTIENGESELLSCHAFT, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:NOELSCHER, CHRISTOPH;REEL/FRAME:013247/0540

Effective date: 20020527

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION