EP2644849B1 - Zirkulierung einer fluidisierten Bettkesselvorrichtung - Google Patents

Zirkulierung einer fluidisierten Bettkesselvorrichtung Download PDF

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Publication number
EP2644849B1
EP2644849B1 EP12161881.3A EP12161881A EP2644849B1 EP 2644849 B1 EP2644849 B1 EP 2644849B1 EP 12161881 A EP12161881 A EP 12161881A EP 2644849 B1 EP2644849 B1 EP 2644849B1
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EP
European Patent Office
Prior art keywords
steam
pressure turbine
high pressure
boiler
heat exchanger
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Application number
EP12161881.3A
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English (en)
French (fr)
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EP2644849A1 (de
Inventor
Christian Enault
Philippe Dreisler
Pierre Gauville
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General Electric Technology GmbH
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General Electric Technology GmbH
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Publication date
Application filed by General Electric Technology GmbH filed Critical General Electric Technology GmbH
Priority to EP12161881.3A priority Critical patent/EP2644849B1/de
Priority to CN201380017178.0A priority patent/CN104246152B/zh
Priority to IN7824DEN2014 priority patent/IN2014DN07824A/en
Priority to PCT/IB2013/052371 priority patent/WO2013144821A2/en
Publication of EP2644849A1 publication Critical patent/EP2644849A1/de
Application granted granted Critical
Publication of EP2644849B1 publication Critical patent/EP2644849B1/de
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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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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

Definitions

  • the present invention is related to a circulating fluidized bed (CFB) boiler device, including a reactor where the solid particles are fluidized and where chemical reactions and/or combustion reactions can take place.
  • the circulating fluidized regime enhances the mixing of particles along with potential exothermic or endothermic chemical reactions.
  • the furnace of a conventional fluidized bed boiler is defined by four external side walls, a bottom and a roof and potentially inner walls to ensure the sealing with the outside if multiple fluidizing grates are used. All the walls constitute an ash-tight enclosure in which the solid particles including the fuel material are fluidized.
  • the furnace enclosure is usually made of gastight panels formed of thin tubes. The heat released from the combustion of fuel is transferred to the water or steam flowing inside the tubes and also allowing the tubes to be cooled.
  • Air is introduced into the furnace to fluidize the solid particles and also brings the needed oxygen for combustion.
  • Two air streams can be used.
  • Primary air is mostly used to fluidize the particles, flows through the fluidizing grate which constitutes the bottom of the furnace.
  • Secondary air is the additional air required for a complete combustion and is introduced through several ports located over the external side walls and/or inner walls if the bottom part of the furnace comprises a dual fluidizing grate and whose shape can be described like a pant leg.
  • Additional heating surfaces are located in the furnace and/or in external devices placed outside the furnace.
  • External devices for instance fluidized bed heat exchangers (FBHE)
  • FBHE fluidized bed heat exchangers
  • Other additional heat exchangers are located on the flue gas path and constitute the heat recovery boiler.
  • the flue gas is usually cooled from 800-950°C which is the temperature at the furnace exit up to 300-350°C before entering the air pre-heater.
  • the first step was to develop a single reheat system.
  • the steam at a high pressure (HP) turbine exhaust goes through one or multiple heat exchangers of the boiler in order to be reheated up to high temperature before feeding a middle pressure - low pressure (MP - LP) turbine.
  • MP - LP middle pressure - low pressure
  • the spray water injection for controlling the final reheat steam temperature at the rated temperature leads to a decay of gross plant heat rate by typically 0.2% when the spray water flow increases by 1% of the main steam flow.
  • the pressure drop of the reheat system from the HP turbine exhaust up to the MP turbine inlet also impacts the gross plant heat rate. The pressure drop is usually closed to 8 to 10% of the steam pressure at the HP turbine exhaust. When increasing the pressure drop from 8 to 10% the gross plant heat rate increases by 0.2%.
  • one or several reheat heat exchangers are installed into the external devices.
  • the heat pick-up and so the final steam temperature are controlled by changing the solid flow through the external device.
  • the control of the solid flow may be fulfilled with a control valve or by any other system. All these systems require an appropriate steam pressure drop to allow a safe and cost-effective material selection. Steam by-pass is also used but can lead to a high pressure drop if some deviation in operating conditions happens.
  • GB 774 225 and GB 765 140 disclose a boiler with a heat exchanger to transfer heat from steam upstream the high pressure turbine to the steam between the high pressure turbine and the middle pressure turbine.
  • US 5 209 188 discloses attemperators between the high pressure turbine and middle pressure turbine, and GB 774 225 and GB 765 140 disclose water injection into the steam supplied into the heat exchanger for heat transfer.
  • an object of the present invention is to provide a circulating fluidized bed boiler device as to solve the above-described problems.
  • the device comprises controlling means for controlling the steam flow entering the heat exchanger.
  • the controlling means includes a valve mounted on a pipe for routing the steam produced in the boiler into the heat exchanger and a valve mounted on a pipe for routing the steam produced in the boiler downstream the heat exchanger.
  • the device can comprise temperature controlling means for controlling the temperature of the steam at the inlet of the middle pressure turbine as a function of the heat transferred in the heat exchanger.
  • the steam exiting the high pressure turbine can be reheated in at least one reheater prior to being supplied to the middle pressure turbine.
  • the temperature of the steam flowing upstream the high pressure turbine can be between 450 and 600°, preferably between 500 and 600°C
  • the temperature of the steam located between the high pressure turbine and the middle pressure turbine i.e. entering the heat exchanger
  • the device preferably does not include any water injection means to control the reheat steam temperature.
  • a steam generator such as a boiler produces steam which is provided to a high pressure (HP) turbine through a plurality of steam admission valves. Steam exiting the high pressure turbine is reheated in a conventional reheater prior to being supplied to a lower pressure turbine, the exhaust from which is conducted into a condenser where the exhaust steam is converted to water and supplied to the boiler to complete the cycle.
  • HP turbines high pressure turbines
  • MP medium pressure turbine
  • LP low pressure
  • the turbines are generally coupled to drive a synchronous electric power generator at constant speed for producing electric utility power which is transmitted over a transmission link to various users.
  • FIG. 1 illustrates a simplified block diagram of a fossil-fired single reheat steam turbine generator unit, by way of example.
  • the turbine system 1 includes a plurality of turbines in the form of high pressure (HP) turbine 2, and at least one or more lower pressure turbines which, in the case of FIG. 1 , include medium pressure (MP) and low pressure (LP) turbine 3.
  • HP high pressure
  • MP medium pressure
  • LP low pressure
  • the turbines are connected to a common shaft to drive an electrical generator 4 which supplies power to a load such as an electrical grid network (not illustrated).
  • a steam generating system that is a circulating fluidized bed boiler 5 operated by fossil fuel, generates steam which is heated to proper operating temperatures and conducted through a pipe 6 to the high pressure turbine 2, the flow of steam being governed by a set of steam admission valves.
  • Steam exiting the high pressure turbine 2 via the high pressure turbine exhaust outlet and steam pipe 7 is conducted to one or several reheaters R i-1 , R i , R i+1 (as illustrated in Figure 2 ) and thereafter provided via the steam pipe 7 to the medium pressure turbine 3 for instance under control of valving arrangement. Thereafter, the exhaust from the MP-LP turbine 3 is provided to a condenser 8 via steam pipe 9 and converted to water.
  • the water is provided back to the boiler 5 via the path including water pipe 10, low pressure pipe 11, water pipe 12, reheater 13, water pipe 14, boiler feed water container 15, water pipe 16, high pressure pump 17, water pipe 18, reheater 19 and water pipe 20.
  • water treatment equipment is generally provided in the return line so as to maintain a precise chemical balance and a high degree of purity of the water.
  • the device according to the invention includes a heat exchanger R i, S i+1 for exchanging heat between the steam located upstream the high pressure turbine and the steam located between the high pressure turbine and the middle pressure turbine.
  • S is the steam path of the heat exchanger R i, S i+1 supplied with high steam pressure, i.e. with steam from the boiler and located upstream the high pressure turbine
  • R is the steam path of the heat exchanger R i, S i+1 supplied with low pressure, i.e. with steam from the high pressure turbine and located upstream the medium pressure turbine.
  • the steam path S can include other heat exchangers S i , S i+2 , ...S n and the steam path R can include other heat reheaters R i-1 , R i+1 , ... R n .
  • the steam temperature at the outlet of the finishing hot reheater R n is controlled by modulating the heat pick-up in the heat exchanger R i , S i+1 .
  • the amount of the heat transferred is controlled by regulating the high-pressure steam flow through the S i+1 steam path with control valves Va,Vb.
  • a valve Vb is mounted on a pipe for routing the steam produced in the boiler into the heat exchanger R i, S i+1 and a valve Va is mounted on a pipe for routing the steam produced in the boiler downstream the heat exchanger
  • the pressure drop of the low pressure steam path R is constant whatever the opening of control valves.
  • the device preferably comprises temperature controlling means for setting the temperature of the steam upstream the high pressure turbine to a value comprised between 500 and 600°C and for setting the temperature of the steam located between the high pressure turbine and the middle pressure turbine to a value comprised between 400 and 500°C.
  • the device according to the invention provides that no water spray is needed during continuous stable operation and that a low pressure drop is obtained despite possible deviations in the operating conditions.

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)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)

Claims (4)

  1. Eine Kesselvorrichtung (1), umfassend:
    - einen zirkulierenden Wirbelschichtkessel (5), in dem eine Verbrennung zum Erzeugen von Dampf verwendet wird,
    - eine Hochdruckturbine (2), in die der im Kessel (5) erzeugte Dampf eintritt,
    - eine Mitteldruckturbine (3), in die Dampf von der Hochdruckturbine (2) geleitet wird,
    wobei die Vorrichtung (1) ferner einen Wärmetauscher (Ri, Si+1) zum Übertragen von Wärme von vor der Hochdruckturbine (2) strömendem Dampf auf zwischen der Hochdruckturbine (2) und der Mitteldruckturbine (3) strömenden Dampf umfasst,
    wobei die Vorrichtung (1) Steuerungsmittel zum Steuern des in den Wärmetauscher (Ri, Si+1) eintretenden Dampfstroms umfasst,
    dadurch gekennzeichnet, dass die Steuerungsmittel ein an einem Rohr montiertes Ventil (Vb) zum Leiten des im Kessel erzeugten Dampfes in den Wärmetauscher (Ri, Si+1) sowie ein an einem Rohr montiertes Ventil (Va) zum Leiten des in dem dem Wärmetauscher (Ri, Si+1 nachgelagerten Kessel erzeugten Dampfes umfassen.
  2. Eine Vorrichtung (1) nach Anspruch 1, dadurch gekennzeichnet, dass sie temperatursteuernde Mittel zum Steuern der Temperatur des Dampfes am Einlass der Mitteldruckturbine(3) als eine Funktion der im Wärmetauscher (Ri, Si+1) übertragenen Wärme umfasst.
  3. Eine Vorrichtung (1) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der die Hochdruckturbine (2) verlassende Dampf in zumindest einem Zwischenerhitzer zwischenerhitzt wird, bevor er zur Mitteldruckturbine (3) geleitet wird.
  4. Eine Vorrichtung (1) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Temperatur des vor der Hochdruckturbine (2) strömenden Dampfes zwischen 500 und 600 °C liegt, während die Temperatur des zwischen der Hochdruckturbine (2) und der Mitteldruckturbine (3) befindlichen Dampfes zwischen 300 und 450 °C liegt.
EP12161881.3A 2012-03-28 2012-03-28 Zirkulierung einer fluidisierten Bettkesselvorrichtung Active EP2644849B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP12161881.3A EP2644849B1 (de) 2012-03-28 2012-03-28 Zirkulierung einer fluidisierten Bettkesselvorrichtung
CN201380017178.0A CN104246152B (zh) 2012-03-28 2013-03-26 循环流化床锅炉装置
IN7824DEN2014 IN2014DN07824A (de) 2012-03-28 2013-03-26
PCT/IB2013/052371 WO2013144821A2 (en) 2012-03-28 2013-03-26 Circulating fluidized bed boiler device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12161881.3A EP2644849B1 (de) 2012-03-28 2012-03-28 Zirkulierung einer fluidisierten Bettkesselvorrichtung

Publications (2)

Publication Number Publication Date
EP2644849A1 EP2644849A1 (de) 2013-10-02
EP2644849B1 true EP2644849B1 (de) 2018-11-07

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Application Number Title Priority Date Filing Date
EP12161881.3A Active EP2644849B1 (de) 2012-03-28 2012-03-28 Zirkulierung einer fluidisierten Bettkesselvorrichtung

Country Status (4)

Country Link
EP (1) EP2644849B1 (de)
CN (1) CN104246152B (de)
IN (1) IN2014DN07824A (de)
WO (1) WO2013144821A2 (de)

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE523035C (de) * 1931-04-18 Aeg Dampfkraftanlage mit mehrstufiger Dampfkraftmaschine mit Frischdampf- und Zwischendampf-UEberhitzer
GB662102A (en) * 1948-06-21 1951-11-28 Fritz Marguerre Improvements relating to steam plants
DE820600C (de) * 1950-05-21 1951-11-12 Grosskraftwerk Mannheim A G Dampfkraftanlage, deren Kessel seine Verbrennungsluft aus einer Luftturbine erhaelt
GB774225A (en) * 1953-12-23 1957-05-08 Sulzer Ag Steam turbine power plants with intermediate reheating between turbines
GB765140A (en) * 1954-01-28 1957-01-02 Sulzer Ag Steam power plants with intermediate reheaters
CH344426A (de) * 1955-09-27 1960-02-15 Hellmut Dipl Ing Eickemeyer Verfahren zum Betreiben einer Dampfkraftanlage mit Zwischenüberhitzung durch Frischdampf
US3973402A (en) * 1974-01-29 1976-08-10 Westinghouse Electric Corporation Cycle improvement for nuclear steam power plant
US5209188A (en) * 1992-06-01 1993-05-11 The Babcock & Wilcox Company Fluid bed combustion reheat steam temperature control
WO2007078269A2 (en) * 2005-12-15 2007-07-12 Ineos Usa Llc Power recovery process
EP2126467A2 (de) * 2007-03-20 2009-12-02 Siemens Aktiengesellschaft Verfahren und vorrichtung zur befeuerten zwischenüberhitzung bei solarer direktverdampfung in einem solarthermischen kraftwerk

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
IN2014DN07824A (de) 2015-05-15
WO2013144821A3 (en) 2014-07-24
CN104246152B (zh) 2017-04-19
CN104246152A (zh) 2014-12-24
EP2644849A1 (de) 2013-10-02
WO2013144821A2 (en) 2013-10-03

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