EP2801759A1 - Dérivation de vapeur dans un générateur de vapeur à récupération de chaleur - Google Patents

Dérivation de vapeur dans un générateur de vapeur à récupération de chaleur Download PDF

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Publication number
EP2801759A1
EP2801759A1 EP13166589.5A EP13166589A EP2801759A1 EP 2801759 A1 EP2801759 A1 EP 2801759A1 EP 13166589 A EP13166589 A EP 13166589A EP 2801759 A1 EP2801759 A1 EP 2801759A1
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EP
European Patent Office
Prior art keywords
steam
heat recovery
superheater
pressure stage
steam generator
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Withdrawn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
EP13166589.5A
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German (de)
English (en)
Inventor
Ludwig Materi
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Priority to EP13166589.5A priority Critical patent/EP2801759A1/fr
Publication of EP2801759A1 publication Critical patent/EP2801759A1/fr
Withdrawn legal-status Critical Current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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/18—Controlling superheat temperature by by-passing steam around superheater sections

Definitions

  • the invention relates to a heat recovery steam generator and relates to a steam temperature control by means of steam diversion.
  • the invention further relates to a gas and steam turbine plant.
  • the steam temperature must be carefully controlled in the gas and steam turbine plant or limited to a maximum value.
  • injection coolers are used as a standard solution for steam temperature control.
  • the feed water is injected into the superheated steam, thereby achieving a cooling effect.
  • the object of the invention is therefore to provide a heat recovery steam generator of the type mentioned, which allows a high efficiency and a material-saving operation.
  • Another object of the invention is the specification of a gas and steam turbine plant.
  • the invention solves this problem by providing that in such a heat recovery steam generator, comprising a pressure stage with at least two superheaters, one of which is the last superheater of the pressure stage in the steam flow direction and the other of the penultimate superheater of the pressure stage, the penultimate and the last superheater are connected to each other via a steam line, a steam bypass to the penultimate superheater opens into the steam line.
  • the usual embeinspritzkühler be replaced by steam bypasses.
  • the provision of steam instead of water eliminates the risk of droplet entry. Furthermore, it is ensured by feeding the colder steam before the last superheater, that its material is not thermally overstressed during operation.
  • the heat recovery steam generator is designed as a multi-pressure boiler.
  • several (usually up to three) steam generators which operate at different pressure levels and each include superheater, evaporator and economizer, connected in series with one another on the flue gas side.
  • the steam temperature control can then either alternatively or additionally perform both in the medium-pressure stage and in the high-pressure stage, when the pressure stage with the vapor bypass is corresponding to a medium or high pressure stage.
  • the heat recovery steam generator is a drum boiler (forced circulation or natural circulation boiler), and in an alternative advantageous embodiment, the heat recovery steam generator is a forced flow boiler (e.g., Benson).
  • the steam bypass branches off in order to be as short as possible in the steam flow direction behind a mixing point of medium pressure steam and cold reheater steam from a steam line leading to the next to the last superheater.
  • the steam bypass can also take place before the mixing point from the cold reheater steam line.
  • the steam bypass is not limited to the bypass of a single superheater. If more than two superheaters provided in a pressure stage, it may be advantageous if the Steam bypass already branches off from a steam line leading to a first superheater of the pressure stage.
  • a gas and steam turbine plant comprises a gas turbine, a waste heat steam generator connected downstream of the gas turbine on the exhaust gas flow side, and a steam turbine downstream of the waste heat steam generator on the steam side.
  • One of the numerous advantages of the invention is the elimination of the intermediate sprays. Only the final spray for startup is needed, i. the injection cooler in the main steam line to the high-pressure part of the steam turbine or in the hot superheater line to the medium-pressure part of the steam turbine. During normal load operation, this spray is inactive, i. There is no danger from droplet entry. Likewise, thermal stresses due to large temperature differences in the injection of water during normal load operation no longer represent a danger.
  • forced-circulation boilers e.g., Benson
  • drum boilers forced circulation or natural circulation
  • FIG. 1 shows schematically and by way of example a gas and steam turbine plant 2 with a gas turbine 17, a steam turbine 18 and a heat recovery steam generator 1.
  • a gas and steam turbine plant 2 with a gas turbine 17, a steam turbine 18 and a heat recovery steam generator 1.
  • a shaft 19 a rotor of the gas turbine 17, a rotor of a generator 20 and a rotor of the steam turbine 18 are coupled together, the Runners of the steam turbine 18 and the rotor of the generator 20 via a clutch 21 are rotationally separable from one another and coupled.
  • the rotor of the generator 20 and the gas turbine 17 are rigidly connected to each other via the shaft 19.
  • An exhaust gas outlet 22 of the gas turbine 17 is connected via an exhaust pipe 23 to the heat recovery steam generator 1, which is provided for generating the operating steam of the steam turbine 18 from waste heat of the gas turbine 17.
  • a compressor 24 is driven by the rotating rotor of the gas turbine 17 via the shaft 19, which sucks combustion air from the environment and a combustion chamber 25 supplies.
  • the combustion air is mixed with fuel supplied from a fuel supply 26 and burned and the hot, pressurized exhaust gases are supplied to the turbine part 27 of the gas turbine 17 and there relaxed under the power of work.
  • the still about 550 to 650 ° C hot exhaust gases are then fed through the exhaust pipe 23 to the heat recovery steam generator 1 and flow through this from the exhaust gas inlet 53 to the exhaust outlet 54, and pass through a chimney 28 in the area.
  • the heat recovery steam generator 1 in the example of FIG. 1 is carried out as a multi-pressure boiler with natural circulation and includes a low pressure stage 29, a medium pressure stage 3 and a high-pressure stage 4.
  • the hot exhaust gas turbine 17 lead their heat a third high pressure superheater, ie the last superheater 6 of the high pressure stage 4 to , then a second reheater, ie the last superheater 5 of the medium-pressure stage 3, a second high-pressure superheater, ie the penultimate superheater 8 of the high-pressure stage 4, a first reheater, ie the penultimate superheater 7 of the medium-pressure stage 3, and a first high-pressure superheater 15, the other one High-pressure evaporator 30, a high-pressure preheater 31, then a medium-pressure superheater 32, a medium-pressure evaporator 33, a medium-pressure preheater 34, then a low-pressure superhea
  • Overheated steam in the third high-pressure superheater 6 is supplied to a high-pressure stage 39 of the steam turbine 18 by a steam discharge 38, where it is released under the power of work.
  • the partially relaxed in the high-pressure stage 39 hot steam is then fed together with steam from the medium pressure superheater 32 the reheaters 7, 5 there again or further superheated and fed via a derivative 40 a medium-pressure stage 41 of the steam turbine 18 and there under power of mechanical work relaxed.
  • the there partially relaxed steam is supplied via an internal supply line of a low pressure stage 42 of the steam turbine 18 and there further relaxed under the release of mechanical energy.
  • the expanded steam is condensed in the condenser 43 of the steam turbine 18, and the resulting condensate is directly via a condensate pump 44 after heating in the condensate preheater 37 of the low-pressure stage 29 of the heat recovery steam generator. 1 or via a feedwater pump 45 - and provided by this with appropriate pressure - the medium-pressure stage 3 or the high-pressure stage 4 of the heat recovery steam generator 1 fed where the condensate is evaporated. After steam generation and overheating, the steam is supplied via the corresponding outlets 38, 40 of the heat recovery steam generator 1 back to the steam turbine 18 for relaxation and performance of mechanical work.
  • FIG. 1 also shows injection cooler 46 - 49, for controlling the steam temperature in the steam discharge 38 after the last superheater 6 of the high-pressure stage 4, in the discharge line 40 after the last superheater 5 of the medium-pressure stage 3, in the steam line 9 between the penultimate superheater 7 and the last Superheater 5 of the medium-pressure stage 3 and in the steam line 10 between the penultimate 8 and last superheater 6 of the high pressure stage 4 are arranged and their use mainly brings a loss of efficiency, thermal stresses and the risk of droplet entry with it.
  • the desired steam temperature is achieved by a controlled mixture of the steam mass flows at different temperatures.
  • corresponding valves 51, 52 are provided in the vapor bypasses 11, 12.
  • throttle valves or throttle valves 56, 57 in the steam lines 14 and 16 in the steam flow direction either comparatively shortly after branching off of the steam bypasses 11, 12 or shortly before the steam bypasses 11, 12 are integrated ,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP13166589.5A 2013-05-06 2013-05-06 Dérivation de vapeur dans un générateur de vapeur à récupération de chaleur Withdrawn EP2801759A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13166589.5A EP2801759A1 (fr) 2013-05-06 2013-05-06 Dérivation de vapeur dans un générateur de vapeur à récupération de chaleur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13166589.5A EP2801759A1 (fr) 2013-05-06 2013-05-06 Dérivation de vapeur dans un générateur de vapeur à récupération de chaleur

Publications (1)

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EP2801759A1 true EP2801759A1 (fr) 2014-11-12

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EP13166589.5A Withdrawn EP2801759A1 (fr) 2013-05-06 2013-05-06 Dérivation de vapeur dans un générateur de vapeur à récupération de chaleur

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3121393A1 (fr) * 2015-07-23 2017-01-25 Mitsubishi Hitachi Power Systems, Ltd. Centrale électrique à cycle combiné et son procédé de démarrage
WO2025089041A1 (fr) * 2023-10-27 2025-05-01 三菱重工業株式会社 Système d'alimentation en vapeur

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0410111A1 (fr) * 1989-07-27 1991-01-30 Siemens Aktiengesellschaft Chaudière de récupération de chaleur pour une centrale à turbine à gaz et à vapeur
EP0736669A2 (fr) * 1995-04-05 1996-10-09 General Electric Company Turbine à gaz refroidi à la vapeur
US6178734B1 (en) * 1997-08-26 2001-01-30 Kabushiki Kaisha Toshiba Combined cycle power generation plant and operating method thereof
US7168233B1 (en) * 2005-12-12 2007-01-30 General Electric Company System for controlling steam temperature

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0410111A1 (fr) * 1989-07-27 1991-01-30 Siemens Aktiengesellschaft Chaudière de récupération de chaleur pour une centrale à turbine à gaz et à vapeur
EP0736669A2 (fr) * 1995-04-05 1996-10-09 General Electric Company Turbine à gaz refroidi à la vapeur
US6178734B1 (en) * 1997-08-26 2001-01-30 Kabushiki Kaisha Toshiba Combined cycle power generation plant and operating method thereof
US7168233B1 (en) * 2005-12-12 2007-01-30 General Electric Company System for controlling steam temperature

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DOLEZAL R: "REGELUNG DER DAMPFTEMPERATUR MIT HILFE DER TEILWEISEN SATTDAMPFUMLEITUNG", BWK BRENNSTOFF WARME KRAFT, SPRINGER VDI VERLAG, DUSSELDORF, DE, vol. 47, no. 5, 1 May 1995 (1995-05-01), pages 230/231, XP000504409, ISSN: 1618-193X *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3121393A1 (fr) * 2015-07-23 2017-01-25 Mitsubishi Hitachi Power Systems, Ltd. Centrale électrique à cycle combiné et son procédé de démarrage
JP2017025792A (ja) * 2015-07-23 2017-02-02 三菱日立パワーシステムズ株式会社 コンバインドサイクル発電プラント及びその起動方法
US10385736B2 (en) 2015-07-23 2019-08-20 Mitsubishi Hitachi Power Systems, Ltd. Combined cycle power plant and start-up method of the same
WO2025089041A1 (fr) * 2023-10-27 2025-05-01 三菱重工業株式会社 Système d'alimentation en vapeur

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