EP0455660B1 - System und verfahren für die regelung der temperatur des heizdampfes bei zirkulierenden wirbelbetten - Google Patents

System und verfahren für die regelung der temperatur des heizdampfes bei zirkulierenden wirbelbetten Download PDF

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Publication number
EP0455660B1
EP0455660B1 EP90901818A EP90901818A EP0455660B1 EP 0455660 B1 EP0455660 B1 EP 0455660B1 EP 90901818 A EP90901818 A EP 90901818A EP 90901818 A EP90901818 A EP 90901818A EP 0455660 B1 EP0455660 B1 EP 0455660B1
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EP
European Patent Office
Prior art keywords
reheater
stage
steam
fluidized bed
temperature
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Expired - Lifetime
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EP90901818A
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English (en)
French (fr)
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EP0455660A1 (de
Inventor
Ponnusami K. Gounder
Timo M. Kauranen
Neil R. Raskin
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Amec Foster Wheeler Energia Oy
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Ahlstrom Corp
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Priority to AT90901818T priority Critical patent/ATE93038T1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D5/00—Devices using endothermic chemical reactions, e.g. using frigorific mixtures
    • 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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 present invention relates to a power plant including a two-stage steam turbine and a steam generator plant having a fluidized bed combustion system that includes a fluidized bed combustor, at least one separator, and a gas flue comprising a reheater and superheater.
  • the present invention relates also to a method of controlling reheater temperatures in a steam generator having a fluidized bed combustion system that includes a fluidized bed combustor, at least one hot separator, and a reheater in a gas flue.
  • reheater temperature control is the use of a system for gas bypass over the reheater.
  • Two separate flue gas passes are provided in the convection pass of the boiler (one for superheater and one for reheater), with means such as dampers downstream of each to vary the amount of flue gas flow over each section.
  • the outlet steam temperature of the reheater can be controlled by varying the amount of flue gas flow between the convection pass sections.
  • the main disadvantage of this system is that the dampers are located in a higher temperature (260-371°C) dust laden flue gas path making them susceptible to erosion and mechanical failure. Also, the steam temperature control range is limited with this type of system.
  • reheater outlet steam temperature control is by the use of external heat exchangers.
  • an externally mounted fluidized bed heat exchanger i.e. external heater exchanger (EHE)
  • EHE external heater exchanger
  • the quantity of heat transfer to the reheater and the reheater outlet steam temperature is controlled.
  • EHE external heater exchanger
  • the main disadvantages of this system are that the solids flow control valve is a high maintenance item and the reheat tube surface within the EHE is subject to erosion. This effects the availability of the unit.
  • EP-A-0 274 637 shows a power plant including a two-stage turbine and a steam generator plant having a fluidized bed combustor, particle separators, first and second or final stages of reheaters and a superheater.
  • the first and final stages of reheaters are according to EP-A- 0 274 637 sequentially disposed. Two stages of reheaters are disposed in separate external heat exchangers for cooling discharged ash. The final stage of reheater is disposed in a gas flue connected to the gas outlet of the fluidized bed combustor. The quantity of heat transferred to the first stages of reheaters and the reheater outlet temperature is controlled by varying the amount of solids flow to the external heat exchangers. This arrangement is not favored due to solids flow control valve maintenance problems as already mentioned earlier.
  • a further approach to the control of the reheater outlet steam temperature is by the use of spray desuperheater.
  • This approach utilizes spraying water for desuperheating and thereby controlling reheater outlet steam temperature. This is a simple approach, but not gererally accepted because it degrades the cycle efficiency.
  • a still further approach is by the use of gas recirculation.
  • gas recirculation By this approach, large quantities of flue gases are recirculated to achieve the rated reheater outlet steam temperature.
  • This approach requires the use of a gas recirculation fan for handling a hot dust laden gas and requires additional power consumption, which makes this approach disadvantageous.
  • the present invention is directed to an improved method and system for reheat steam temperature control.
  • a steam generator having a fluidized bed combustion system that includes a fluidized bed combustor, at least one separator, and a reheater in a flue gas pass and is characterized by
  • the boiler system designated generally by the numeral 10
  • the boiler system comprises a fluid bed combustor 12 having a combustion chamber 14 into which combustible material, non-combustible material, possibly additives or recirculated material, primary air and secondary air are fed.
  • the bed is maintained in fluidized state by having the correct inventory of bed material and flow of air.
  • the combustion chamber is provided with a bottom 16 having a grid-like construction through which fluidizing air is introduced.
  • the combustion chamber walls are preferably constructed with membrane type tube walls, with or without a refractory covering.
  • First and second stages of superheaters 18 and 20 are located within the combustion chamber.
  • the combustion chamber materials are carried from the combustion chamber by way of flues 22 to a hot separator 24 wherein the solids are separated from the flue gases for return by way of particle recycling system 26, 28 and 30 to the bottom of the combustion chamber for recirculation. These may be passed through fluidized bed coolers or the like prior to return to the combustion chamber.
  • Flue gases from the hot separator pass along by way of flue 32 to a convection pass 34.
  • a single stage superheater 38 is placed or located in the convection pass with reheaters 40 and 42 located downstream of the superheater 38 and upstream of an economizer surface 44.
  • the reheater is illustrated as two stages with 42 being a first stage and 40 being a second or final stage.
  • the reheater may have more than two stages, with the final stage just down stream from superheater 38 such as 40 is located. These are arranged as counter flow heat exchangers with the gas flow direction down and the reheat steam flow direction up.
  • the placement of the superheater 38 within this pass helps keep the temperature of the gas flow to reheater 40 below the critical temperature. This arrangement together with the bypass feature as will be explained enables a unique and effective control of the temperatures within the reheater sections.
  • the generating system as illustrated in Fig. 1 is supplying steam to a two-stage turbine.
  • steam from superheater 38 flows via an outlet header 46 and supply line 48 by way of valve 50 to the inlet side of the high pressure turbine (HPT) 52.
  • HPT high pressure turbine
  • Cold steam leaving the turbine 52 returns by way of return line 53 to the reheaters 42 and 40.
  • a bypass line 54 joins the return line 53 at 55 and bypasses a portion of the cold steam with the remaining portion of the steam going by way of differential control valve 56 to the inlet header 58 of the first stage reheater 42.
  • the steam passing through the reheater 42 exits by way of a header 60 and rejoins or combines with the bypass portion of the cold steam at 62.
  • a flow control valve 64 is provided in the bypass line 54 for control of the flow between the inlet manifold of the first stage reheater 42 and the bypass line.
  • the recombined steam at 62 flows into inlet header 66 of the second or final stage reheater 40 where it is further heated and flows by way of outlet header 68, supply line 70 and valve 72 to the second stage or lower stage of the turbine (IPT) 74.
  • IPT second stage or lower stage of the turbine
  • the location of the first stage reheater 42 along the flue gas path is so chosen that bypassing the required portion of the cold reheat steam directly to the second stage reheater 40 cannot increase the steam temperature leaving the first stage reheater to more than the allowed metal temperature for the reheater tube material.
  • a limit will be set to protect the first stage reheater materials from exceeding their allowable metal temperature.
  • the value of 566°C is a typical limit and may vary depending upon the actual design conditions.
  • the purpose of the system is such that the maximum tube outside surface temperature will not exceed the allowable metal temperature limit for the material selected.
  • control valves 56 and 64 are so chosen that controllability is achieved throughout the steam temperature control range and permits all reheater surfaces to be placed in the convection pass of the boiler, eliminating the need for in furnace reheater surfaces. This also makes feasible a simplified start-up scheme when more than one boiler for example is connected to a common turbine system. In this arrangement, the set of valves provide a means for reheat steam flow balancing under various operating conditions.
  • the combustion takes place in a fluidized bed of inert material.
  • the fluidized bed material leaving the combustor is returned by means of a hot collector (such as a hot cyclone) through suitable sealing device.
  • a hot collector such as a hot cyclone
  • air and fuel are delivered to the combustion chamber 14 wherein the bed material is maintained in a fluidized state by having the correct flow of air and bed material.
  • the fluidizing air is introduced through a grid-like grating or construction at 16 in the bottom of the chamber.
  • the flue gas and combustion products, along with the carry over solids, first convey heat to the superheaters 18 and 20 and are conveyed by way of flue 22 into the hot separator 24 wherein the solids are separated and returned to the combustion chamber through the recycling arrangement 26, 28 and 30.
  • the hot flue gases are then conveyed from the hot separator(s) by way of flue 32 to the convection pass section 34 wherein the final stage superheater 38 and the reheater stages 40 and 42 are located.
  • Three superheater stages are disposed in the described system, these being 18 and 20 and 38, with 38 being in the flue gas convection pass.
  • Desuperheaters may be positioned between the superheater stages for steam temperature control if necessary.
  • the two stages 40 and 42 of the reheater are positioned in the convection pass 34 and in conjunction with the control valves and interconnecting piping so that precise control of the reheater outlet steam temperature is possible.
  • the piping system is such that cold steam reentering this system at pipe 53 is selectively divided into two streams at the juncture 55 thereof with the bypass line 54.
  • One stream passes to the first stage reheater and is distributed through inlet header 58.
  • the other steam goes to the second stage reheater by way of valve 64 and inlet header 66.
  • the selective division of the stream will be in proportion to the temperature control necessary, which is accomplished by the valves 56 and 64.
  • the hot steam leaving the first stage reheater from the outlet header 60 is mixed with the cold steam via the bypass line 54 after or down stream of the flow control valve 64 and the blended stream enters the second stage reheater by way of the inlet header 66.
  • the flow through the first stage reheater is controlled by proper manipulation of the two control valves 56 and 64, which in turn control the steam temperature leaving the second stage reheater 40.
  • Hot steam from the second or final stage reheater is directed back to the turbine by way of the hot reheat steam line 70.
  • a differential pressure responsive control unit 80 controls the setting of valve 56 for controlling the pressure differential available for the control valve 64.
  • the control unit 80 is responsive to the pressure differential between the cold steam return line 53 and the outlet pressure at juncture 62 of the outlet of reheater 42 and the bypass line 54. This is indicated by phantom line 84 in Fig. 1.
  • the control unit 80 is set to control the valve 56 as a function of load on the boiler.
  • the valve 64 in the bypass line 54 is controlled by temperature responsive control unit 82 which responds to the temperature of the outlet steam from the second or final stage reheater 40. This is indicated by phantom line 86 in Fig. 1.
  • the temperature of reheater 40 is maintained within the limit of about 538°C, plus or minus 10 °C.
  • the valve 64 is opened to bypass additional cold steam directly to reheater 40.
  • the valve 64 is closed to reduce the flow of bypass cold steam to the second stage 40.
  • Fig. 2 a system identical to Fig. 1, but with superheater 38 located between the reheaters 40 and 42, is disclosed.
  • a single staged superheater 38 is placed in the convection pass, with second stage reheater 40 located upstreams and first stage reheater 42 downstream of the superheater. This is in contrast to what was shown in Fig. 1.
  • An economizer 44 is located downstream of the superheater 38.
  • the placement of the second stage reheater 40 upstream of the superheater 38 allows it to pick up more heat at lower loads. This gives it the potential to extend its steam temperature control range, while having little if any effect on the superheater control range. This potential extension of the reheat steam temperature control range will enhance the coupling of two units to one turbine easier as to temperature matching capabilities.
  • a system identical to Fig. 1, but with a duplicate boiler is disclosed.
  • the components of the first and the second boiler arrangements are identified by the same reference numerals as in Fig. 1, with the second boiler arrangement being identified with the same numbers primed. Therefore, in this arrangement, a boiler turbine system is disclosed wherein two boilers are supplying steam to a single turbine.
  • One essential feature required for this type of system is that means be provided for controlling the amount of reheat steam flow to each boiler, so that the steam temperature at reheat outlet is within limits at all possible operating conditions.
  • duplicate controls and piping are provided for the two boilers.
  • the control valves 56 and 64 for the reheat steam temperature control can be used for flow balancing and maintaining the reheater outlet temperature within limits under both normal and abnormal operating conditions.
  • pressure reducing valves 80 and 82, along with desuperheaters 76 and 78, provide for flexibility during cold start-up, hot start-up and also when starting the second unit while the first one is on line.
  • This simple system eliminates the need for a sophisticated steam blending system. It provides a simple and effective system and method for reheat outlet steam temperature control under varying load conditions.
  • combustion is initiated in the combustion chamber 14 with the introduction of fuel and combustion air.
  • the hot gases of combustion move upward in the combustion chamber transferring heat to the water in the combustion chamber walls and to superheaters 18 and 20.
  • the hot gas, combustion products, and solids pass from the combustion chamber along flue 22 into the hot separator 24 where the solids are separated for return to the combustion chamber.
  • the hot flue gas passes along flue 32 into the convection pass 34 where the heat is transferred in sequence to the superheater 38, the second or final stage reheater 40, and the first stage reheater 42.
  • the flow of hot gas through the system begins before the flow of cold steam.
  • the boiler is fired and fuel burns for a period of time providing hot gas before steam is generated and starts the turbine.
  • Cold reheat steam does not start flowing until after the turbine starts.
  • the temperature drops so that it is less at each successive stage. It should be noted that the gas temperature leaving the combustion chamber outlet at full load will be in the range of 843 to 927°C. The greater the temperature differential between the gas and the water, the greater the heat transfer will be, and the cooler the gas will be as it passes from the respective heater.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Control Of Turbines (AREA)

Claims (10)

  1. Kraftwerk bestehend aus einer zweistufigen Dampfturbine und einer Dampferzeugungsanlage mit einer Wirbelschicht-Verbrennungssystem, das eine Wirbelschichtfeuerung (12), mindestens einen Abscheider (24), mindestens eine erste und eine zweite oder Endstufe des Zwischenüberhitzers, die hintereinander angeordnet sind, und einen Überhitzer (38) aufweist, gekennzeichnet durch
    - Anordnung der ersten Stufe des Zwischenüberhitzers (42) und der zweiten oder Endstufe des Zwischenüberhitzers (40) hintereinander in einem gemeinsamen Gaskanal (34),
    - Organe (54, 64) zur Aufteilung des Kaltdampfes von einer Turbine (52) in einen selektiven ersten und zweiten Teil und Leitung besagten ersten Teils durch die erste Stufe des Zwischenüberhitzers (42), und
    - Organe (62) zur Wiedervereinigung des ersten und zweiten Teils und Leitung derselben durch die zweite Stufe des Zwischenüberhitzers (40).
  2. Kraftwerk gemäß Anspruch 1, dadurch gekennzeichnet, daß der Überhitzer (38) stromabwärts von der genannten zweiten Stufe des Zwischenüberhitzers (40) angeordnet ist.
  3. Kraftwerk gemäß Anspruch 1, dadurch gekennzeichnet, daß die Organe (54, 64) zur Aufteilung des Kaltdampfes eine Bypaßleitung (54) mit mindestens einem Stromregelventil (64) zur Umleitung eines selektierten Teils des Kaltdampfes aus einer Turbine an der ersten Stufe des Zwischenüberhitzers (42) vorbei direkt in die zweite oder Endstufe des Zwischenüberhitzers (40) aufweisen.
  4. Kraftwerk gemäß Anspruch 1, gekennzeichnet durch mindestens ein Druckregelventil (56) am Eintritt zur ersten Stufe des Zwischenüberhitzers (42), welches Ventil auf die Differenz zwischen Rücklaufdampfdruck und Austrittsdampfdruck der ersten Stufe des Zwischenüberhitzers anspricht.
  5. Kraftwerk gemäß Anspruch 1, dadurch gekennzeichnet, daß die Organe (64) zur Aufteilung des Kaltdampfes auf die Austrittstemperatur der zweiten Stufe des Zwischenüberhitzers (40) ansprechen.
  6. Verfahren zur Regelung von Zwischenüberhitzer-Temperaturen in einem Dampferzeuger mit einem Wirbelschicht-Verbrennungssystem, das eine Wirbelschichtfeuerung, mindestens einen Heißabscheider und einen Zwischenüberhitzer aufweist, dadurch gekennzeichnet, daß
    - der Zwischenüberhitzer in eine erste und eine zweite oder Endstufe des Zwischenüberhitzers aufgeteilt ist und die erste und zweite Stufe des Zwischenüberhitzers in einem gemeinsamen Gaskanal hintereinander angeordnet sind,
    - der zum Zwischenüberhitzer zurückfließende Kaltdampf in einen selektiven ersten und zweiten Teil aufgeteilt wird und der erste Teil durch die erste Stufe des Zwischenüberhitzers geleitet wird, und
    - der erste Teil und der zweite Teil wiedervereinigt und durch die zweite oder Endstufe des Zwischenüberhitzers geleitet werden.
  7. Verfahren gemäß Anspruch 6, dadurch gekennzeichnet, daß die Temperatur der zweiten Stufe des Zwischenüberhitzers auf etwa 538 °C, plus minus 10 °C gehalten wird.
  8. Verfahren gemäß Anspruch 6, dadurch gekennzeichnet, daß der zweite Teil des geteilten Kaltdampfes durch eine Bypaßleitung geleitet wird, die sich zwischen einem Eintritt und einem Austritt der ersten Stufe des Zwischenüberhitzers erstreckt.
  9. Verfahren gemäß Anspruch 6, dadurch gekennzeichnet, daß die Dampftemperatur der zweiten oder Endstufe des Zwischenüberhitzers zur Aufteilung des Kaltdampfes in einen ersten und einen zweiten Teil geregelt wird.
  10. Verfahren gemäß Anspruch 6, dadurch gekennzeichnet, daß die Druckdifferenz zwischen dem Rücklaufdampfdruck und dem Austrittsdampfdruck der ersten Stufe des Zwischenüberhitzers zur Aufteilung des Kaltdampfes in einen ersten und einen zweiten Teil geregelt wird.
EP90901818A 1989-01-24 1990-01-23 System und verfahren für die regelung der temperatur des heizdampfes bei zirkulierenden wirbelbetten Expired - Lifetime EP0455660B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90901818T ATE93038T1 (de) 1989-01-24 1990-01-23 System und verfahren fuer die regelung der temperatur des heizdampfes bei zirkulierenden wirbelbetten.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US301621 1981-09-14
US30162189A 1989-01-24 1989-01-24

Publications (2)

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EP0455660A1 EP0455660A1 (de) 1991-11-13
EP0455660B1 true EP0455660B1 (de) 1993-08-11

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EP (1) EP0455660B1 (de)
JP (1) JP2532750B2 (de)
KR (1) KR0147059B1 (de)
CN (1) CN1020951C (de)
AU (1) AU639437B2 (de)
CA (1) CA2045571C (de)
CZ (1) CZ284932B6 (de)
DD (1) DD291803A5 (de)
DE (1) DE69002758T2 (de)
ES (1) ES2045903T3 (de)
LT (1) LT3379B (de)
LV (1) LV11061B (de)
PL (1) PL166038B1 (de)
UA (1) UA24009C2 (de)
WO (1) WO1990008917A1 (de)

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DE10039317A1 (de) * 2000-08-11 2002-04-11 Alstom Power Boiler Gmbh Dampferzeugeranlage

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FI120658B (fi) 2005-05-04 2010-01-15 Metso Power Oy Välitulistushöyryn lämmönsäätömenetelmä, lämmönsäätöjärjestelmä sekä voimalaitos
CN101893232B (zh) * 2010-06-24 2012-02-01 东南大学 火电机组再热汽温改进受限广义预测控制方法
DE112013004744B4 (de) * 2012-09-26 2017-04-06 Shanghai Fubo Ep Equipment Co., Ltd. Indirekter Abgaswiedererhitzer mit natiirlicher Zirkulation
KR102051101B1 (ko) * 2013-07-19 2019-12-02 한국전력공사 유동층 보일러의 가변 열교환 장치
JP6317652B2 (ja) 2014-09-12 2018-04-25 株式会社東芝 プラント制御装置及びコンバインドサイクル発電プラント
CN105889899B (zh) * 2014-12-16 2018-06-15 华北电力大学（保定） 一种适用于scr低负荷下投运的过热汽温调节系统及方法
CN104501425A (zh) * 2014-12-19 2015-04-08 中国科学院电工研究所 带过热器启动保护的太阳能热发电控制循环吸热器
CN106545833B (zh) * 2016-10-28 2018-07-17 杭州红山热电有限公司 锅炉汽水系统
CN110914594B (zh) * 2017-07-27 2021-09-10 住友重机械福惠能源有限公司 流化床锅炉设备以及预热流化床锅炉设备中的燃烧气体的方法
KR102093302B1 (ko) * 2018-07-19 2020-04-23 한국생산기술연구원 복수의 라이저부를 구비한 유동사 하강형 순환유동층 보일러 및 이의 운전방법
WO2020073830A1 (zh) * 2018-10-10 2020-04-16 北京润能科技有限公司 一种提高朗肯循环效率的方法
CN113753237B (zh) * 2021-09-21 2023-04-07 中国航空工业集团公司西安飞机设计研究所 一种制冷组件温度控制解耦方法

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Publication number Priority date Publication date Assignee Title
DE10039317A1 (de) * 2000-08-11 2002-04-11 Alstom Power Boiler Gmbh Dampferzeugeranlage

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UA24009C2 (uk) 1998-08-31
AU4941990A (en) 1990-08-24
CN1020951C (zh) 1993-05-26
CA2045571A1 (en) 1990-07-25
CZ284932B6 (cs) 1999-04-14
CS33090A3 (en) 1992-03-18
CN1045168A (zh) 1990-09-05
CA2045571C (en) 1995-09-12
DE69002758D1 (de) 1993-09-16
JPH04503095A (ja) 1992-06-04
DD291803A5 (de) 1991-07-11
KR910700434A (ko) 1991-03-15
AU639437B2 (en) 1993-07-29
EP0455660A1 (de) 1991-11-13
KR0147059B1 (ko) 1998-08-17
LTIP842A (en) 1995-02-27
LT3379B (en) 1995-08-25
PL166038B1 (pl) 1995-03-31
JP2532750B2 (ja) 1996-09-11
LV11061B (en) 1996-06-20
WO1990008917A1 (en) 1990-08-09
DE69002758T2 (de) 1993-12-16
LV11061A (lv) 1996-02-20
ES2045903T3 (es) 1994-01-16

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