WO2012065356A1 - 一种循环流化床锅炉各级过热器的布置结构 - Google Patents

一种循环流化床锅炉各级过热器的布置结构 Download PDF

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Publication number
WO2012065356A1
WO2012065356A1 PCT/CN2011/001713 CN2011001713W WO2012065356A1 WO 2012065356 A1 WO2012065356 A1 WO 2012065356A1 CN 2011001713 W CN2011001713 W CN 2011001713W WO 2012065356 A1 WO2012065356 A1 WO 2012065356A1
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Prior art keywords
superheater
boiler
temperature
superheaters
fluidized bed
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PCT/CN2011/001713
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English (en)
French (fr)
Inventor
肖峰
王冬福
黄建荣
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上海锅炉厂有限公司
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Publication of WO2012065356A1 publication Critical patent/WO2012065356A1/zh

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    • 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
    • F22B31/0007—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G7/00—Steam superheaters characterised by location, arrangement, or disposition
    • F22G7/14—Steam superheaters characterised by location, arrangement, or disposition in water-tube boilers, e.g. between banks of water tubes

Definitions

  • the invention relates to a circulating fluidized bed boiler, in particular to an arrangement structure of superheaters of various stages of a circulating fluidized bed boiler. Background technique
  • the circulating fluidized bed combustion technology was originally derived from the catalytic cracking of the chemical industry. Its purpose is to control the combustion temperature, so that the catalyst can improve the utilization rate of the catalyst in the optimal reaction temperature range.
  • the main feature of the circulating fluidized bed boiler is that the boiler furnace contains a large amount of materials. During the combustion process, a large amount of material is carried by the flue gas to the upper part of the furnace, and the separator is arranged at the outlet of the furnace to separate the material from the flue gas.
  • the non-mechanical return valve returns the material to the furnace combustion chamber, and adds desulfurizing agent (such as limestone) while continuously adding fuel to the source of the combustion chamber, because the fuel and the desulfurizing agent are in the circulation loop composed of the furnace combustion chamber and the separator.
  • desulfurizing agent such as limestone
  • Secondary cycle combustion usually controlling the temperature of the circulating fluidized bed boiler combustion chamber at 840 ° C ⁇ 900 ° C, which is the most favorable temperature range for the desulfurizer reaction, so that the device has higher combustion efficiency and higher utilization of desulfurizer rate.
  • circulating fluidized bed combustion technology belongs to medium-temperature or low-temperature space combustion, which is quite different from the pulverized coal boiler combustion technology (PC furnace) we usually mentioned.
  • the combustion temperature of pulverized coal boiler is higher than that of circulating fluidization.
  • the bed is much higher, generally above 1300 ° C.
  • the concentration of the material in the circulating fluidized bed combustion chamber is much higher than that of the pulverized coal boiler. Therefore, the difference between the combustion mode and the combustion temperature determines the furnace of the circulating fluidized bed boiler and is arranged in the furnace.
  • the heat transfer characteristics of the inner heating surface and the tail convection heating surface are also very different from those of the pulverized coal boiler.
  • the distribution of the heat absorption fraction of the furnace superheater and the tail superheater has a great influence on the steam temperature and wall temperature characteristics of the superheater of the CFB boiler, and most of the current cycles
  • the fluidized bed boiler is not enough to master the dynamic heat transfer characteristics of the circulating fluidized bed boiler during the load change process, which causes the CFB boiler to overheat or overspray the superheater system during the variable load operation. Phenomenon, serious impact
  • the heat transfer of the heating surface of the boiler is mostly through convection and radiation heat transfer.
  • the flue gas generated by the combustion of the boiler equipment is mainly fuel.
  • the flow rate during the surface, the radiation heat transfer is mainly related to the temperature of the medium.
  • the arrangement of the heating surface of the boiler varies according to the flow of the flue gas.
  • the heat transfer characteristics are also different. Usually, it is arranged on the heating surface of the high temperature zone such as the furnace.
  • the heat is mainly transferred by means of radiation, and is arranged in the convection flue of the tail of the boiler.
  • the heat transfer is mainly based on convective heat transfer.
  • the temperature of the flue gas in each part changes with the change of the boiler load. Therefore, the heat transfer characteristics of the heating surfaces along the flue gas flow will also change greatly with the change of the boiler load.
  • the heat transferred by the radiation in the heating surface of the boiler changes slowly with the boiler load, while the convective heat transfer changes significantly with the load. Therefore, it is possible to study the heat transfer of the superheater on the heating surface of the CFB boiler with the change of the load.
  • the position of the heating surface along the flue gas flow and the heat absorption share of the superheater of the CFB boiler can be properly arranged (the heat of each superheater is absorbed).
  • the ratio of the amount of heat absorbed by the entire superheater is improved by the characteristics of radiation heat transfer and convective heat transfer with changes in boiler load to improve the steam temperature and wall temperature characteristics of the superheater heating surfaces of the boiler.
  • the invention provides an arrangement structure of superheaters of various circulating fluidized bed boilers, which greatly improves the steam temperature and wall temperature characteristics of the superheater of the boiler under various loads, and improves the safety and service life of the boiler operation. .
  • the arrangement structure of the superheater of the circulating fluidized bed boiler of the present invention comprises an economizer disposed in the convection flue of the tail of the boiler, and a steam drum connected to the economizer by the pipeline (or steam and water separation) And a pipe connected to the furnace water wall of the steam drum (or steam separator).
  • the arrangement structure of the superheaters of the circulating fluidized bed boiler further comprises a plurality of tail superheaters, low temperature superheaters and high temperature superheaters which are connected by pipelines to form a closed circuit.
  • the high temperature superheater may be arranged in a single stage or in multiple stages.
  • the multi-stage arrangement of the high temperature superheater comprises a line-connected intermediate temperature superheater and a high temperature superheater (also known as a final stage superheater).
  • the arrangement structure of the superheater of the circulating fluidized bed boiler further comprises a reheater system, wherein the reheater system comprises a plurality of low temperature reheater high temperature reheaters (hereinafter referred to as the final stage) which are connected by pipelines to form a closed loop. Reheater).
  • the reheater system comprises a plurality of low temperature reheater high temperature reheaters (hereinafter referred to as the final stage) which are connected by pipelines to form a closed loop. Reheater).
  • the high temperature superheater is disposed in a furnace of a boiler, and the low temperature superheater is disposed in a tail flue of the boiler.
  • the high temperature reheater is disposed in the furnace of the boiler, and the low temperature reheater is disposed in the tail flue of the boiler.
  • the superheater of the circulating fluidized bed boiler superheater is arranged in the furnace, and the heat absorbed by the heated surface of the high temperature superheater disposed in the combustion chamber of the furnace accounts for 48-58% of the total heat absorbed by the superheater system.
  • good steam temperature characteristics can be obtained, and the wall temperature of the tubes on the heating surface of the superheater of each stage is also greatly improved, as long as the boiler meets the full load, the heating surface of the superheater is not overheated, and the low load will not Over temperature, improve the safety of boiler low load operation.
  • Boiler superheater radiation and convection characteristics are well matched.
  • the boiler has good steam temperature characteristics under various loads, so that the superheater's desuperheater spray water changes little, and the desuperheater water spray can be reduced in the design. the design of.
  • 1 is a schematic structural view of a first embodiment of an arrangement structure of superheaters of a circulating fluidized bed boiler provided by the present invention
  • 2 is a schematic structural view showing a second embodiment of an arrangement structure of superheaters of the circulating fluidized bed boiler provided by the present invention
  • FIG. 3 is a schematic structural view showing a third embodiment of an arrangement structure of superheaters of the circulating fluidized bed boiler provided by the present invention.
  • Fig. 4 is a graph showing changes in steam temperature and load of superheaters of various circulating fluidized bed boilers according to the present invention. The best way to implement the invention
  • FIG. 1 it is a schematic structural view of a first embodiment of an arrangement structure of superheaters of circulating fluidized bed boilers provided by the present invention, and boiler feed water passes through a water supply pipe 1 into an economizer 10 disposed in a tail convection flue.
  • the steam is introduced into the tail cladding superheater 30 through the steam drum to the tail cladding superheater connection pipe 29, and the heated steam enters the low temperature superheater 31 disposed in the tail convection flue, and passes through the first stage water spray desuperheater 32. Thereafter, the superheated steam enters the intermediate temperature superheater 35 disposed in the boiler furnace, and then passes through the secondary water spray desuperheater 38 to enter the high temperature superheater 40 disposed in the boiler furnace. Qualified steam is taken from the boiler to the turbine generator.
  • the intermediate temperature superheater 35 and the high temperature superheater 40 in the high temperature superheater along the steam flow are arranged in the furnace, and the heat absorption accounts for the entire superheater system.
  • the heat absorption share of 48-58% of the superheater has good steam temperature and wall temperature characteristics.
  • FIG. 2 is a schematic structural view of a second embodiment of an arrangement structure of superheaters of the circulating fluidized bed boiler provided by the present invention, and the boiler feed water enters the low temperature economizer ⁇ disposed in the tail convection flue and enters The high-temperature economizer then enters the water in the steam drum 2 ⁇ steam drum from the boiler drum connecting pipe 11 through the down pipe 21 into the water cooling wall lower header 2, and the water is in the furnace water wall 3 (3a, 3b, 3c, 3d is a membrane type) The four walls of the water wall are heated to form a steam-water mixture from the furnace to the steam drum connecting pipe 22 into the steam drum 2Q steam drum 20.
  • the steam-water mixture formed in the water-cooling wall 3 is subjected to steam-water separation water into the downcomer 21, and the saturated steam passes through the steam.
  • the tail is covered by a double flue arrangement, and the heated steam enters the low temperature superheater 31 disposed in the tail convection double flue, after passing through the first stage water desuperheater 32.
  • the superheated steam enters the intermediate temperature superheater 35 disposed in the boiler furnace, and then passes through the secondary water spray desuperheater 38 to enter the high temperature superheater 40 disposed in the boiler furnace, and the qualified steam is taken out from the boiler to the steam turbine generator.
  • the reheated steam first enters the tail low temperature reheater 51, and the low temperature reheater 51 is disposed in the other flue in the tail convection double flue, and then passes through the reheater water spray desuperheater 53 to enter the high temperature disposed in the furnace.
  • Heater 55, qualified reheat steam is drawn out of the boiler into the turbine generator.
  • the intermediate temperature superheater 35 and the high temperature superheater 40 in the high temperature superheater along the steam flow are disposed in the furnace, and the heat absorption accounts for 48-58% of the total heat absorption of the superheater system.
  • the heating surfaces of the superheaters of each stage have good steam temperature and wall temperature characteristics.
  • FIG. 3 it is a schematic structural view of a third embodiment of an arrangement structure of superheaters of circulating fluidized bed boilers provided by the present invention.
  • the boiler feed water enters the low temperature economizer 10 disposed in the tail convection flue, after heating Entering the high temperature economizer 12, and then entering the lower tank of the furnace water wall by the connecting pipe 11, the water is heated in the furnace water wall 3 (3a, 3b, 3c, 3d is the four walls of the membrane water wall) to form a steam and water mixture
  • superheated steam enters the steam separator 20 from the furnace to the steam drum connecting pipe 22, and the steam separator 20 performs steam-water separation of the steam-water mixture formed in the water-cooling wall 3 (in the boiler starting stage or low load), and the water enters the starting system.
  • the steam is introduced into the tail cladding superheater 30 through the steam drum to the tail cladding superheater connection pipe 29.
  • the tail is covered by a double flue arrangement, and the heated steam enters the tail convection double flue.
  • the low temperature superheater 31 after passing through the first stage water desuperheater 32, the superheated steam enters the intermediate temperature superheater 35 disposed in the boiler furnace, and then passes through
  • the secondary water spray desuperheater 38 enters the high temperature superheater 40 disposed in the boiler furnace, and the qualified steam is taken out from the boiler to the steam turbine generator, and the hot steam first enters the tail low temperature reheater 51, and the low temperature reheater is disposed at In the other flue in the tail convection double flue, the reheater water spray desuperheater 53 then enters the high temperature reheater 55 disposed in the furnace, and the qualified reheat steam is led out of the boiler into the turbine generator.
  • the intermediate temperature superheater 35 and the high temperature superheater 40 in the high temperature superheater along the steam flow are disposed in the furnace, and the heat absorption accounts for 48-58% of the total heat absorption of the superheater system.
  • the heating surfaces of the superheaters of each stage have good steam temperature and wall temperature characteristics.
  • FIG. 4 it is a variation curve of steam temperature and load of the superheater of the circulating fluidized bed boiler according to the present invention.
  • the superheater outlet temperature is controlled according to the requirements of the boiler steam generator in the conventional sense.
  • a constant value 540 ° C in this case
  • the temperature of the high temperature superheater inlet decreases with the load.
  • the temperature of the inlet and outlet of the medium temperature superheater also follows.
  • the load is reduced and lowered, which means that during the variable load operation, the temperature of the superheater inlet and outlet of each stage is lower than that of the full load (BMCR). Therefore, in the boiler design, as long as the boiler is full load, the heating surfaces of all levels are satisfied. Safety, the boiler is safe at other low loads, and the CFB boiler does not explode at low load and over temperature.
  • the steam temperature is the highest.
  • materials with high temperature resistance such as SA213T91, SUS304, SA213TP347, etc. are usually used, and the temperature fluctuation will cause fatigue damage of the material.
  • the invention emphasizes that the last stage high temperature superheater of the circulating fluidized bed boiler is arranged in the furnace because the combustion temperature of the furnace of the circulating fluidized bed boiler changes slowly with load, and the steam temperature of the outlet of the final superheater can be reduced by Warm water spray or other combustion adjustment means to control, so in the process of boiler load change, the wall temperature of the high temperature superheater is relatively stable, the wall temperature fluctuation is small, and the safety of the heating surface of the high temperature superheater is improved.

Description

一种循环流化床锅炉各级过热器的布置结构 技术领域
本发明涉及循环流化床锅炉， 尤其涉及一种循环流化床锅炉各级过热器 的布置结构。 背景技术
循环流化床燃烧技术最早来源于化工工业的催化裂化， 其目的是控制燃 烧温度， 使催化剂在最佳的反应温度区间， 提高催化剂的利用率， 德国鲁奇
(Lurgi)公司最先把该技术使用到燃煤锅炉， 幵发出了工业上广泛运用的循 环流化床锅炉燃烧技术。
循环流化床锅炉的主要特点是锅炉炉膛内含有大量的物料， 在燃烧过程 中大量的物料被烟气携带到炉膛上部， 经过布置在炉膛出口的分离器， 将物 料与烟气分开， 并经过非机械式回送阀将物料回送至炉膛燃烧室， 在向燃烧 室源源不断加入燃料的同时加入脱硫剂（如石灰石等)， 由于燃料和脱硫剂在 炉膛燃烧室、 分离器组成的循环回路内多次循环燃烧， 通常控制循环流化床 锅炉燃烧室温度在 840°C〜900°C这样一个最有利于脱硫剂反应的温度区 间， 使得该装置具有较高的燃烧效率和较高的脱硫剂利用率。
从燃烧意义上定义循环流化床燃烧技术属于中温或低温的空间燃烧， 与 我们通常提到的煤粉锅炉燃烧技术（PC炉）有较大的差别， 煤粉锅炉燃烧温 度要比循环流化床高得多， 一般在 1300°C以上， 另外循环流化床燃烧室内物 料浓度要比煤粉锅炉高得多， 因此燃烧方式和燃烧温度的差别决定了循环流 化床锅炉炉膛以及布置在炉内的受热面、 尾部对流受热面的传热特性与煤粉 锅炉也存在非常大的差异。 因此在流化床锅炉过热器受热面的布置上， 炉膛 过热器和尾部过热器吸热份额的分配对 CFB 锅炉各级过热器汽温和管壁温 度特性的影响非常大， 而目前大多数的循环流化床锅炉在设计对循环流化床 锅炉在负荷变化过程中动态传热特性的掌握程度不够，造成 CFB锅炉在变负 荷运行过程中经常发生过热器系统管子超温或喷水量过大的现象， 严重影响
1
确 认 本 了锅炉安全稳定运行。
锅炉受热面的热量传递大部分通过对流和辐射传热， 按照对流和辐射的 原理， 影响对流传热的主要因素是介质的流速， 对锅炉设备主要是燃料燃烧 所产生的烟气在流过受热面时的流速， 辐射传热主要与介质温度有关。 锅炉 受热面的布置根据烟气的流程的不同， 传热的特性也不同， 通常布置在炉膛 等高温区的受热面， 热量主要通过辐射的方式进行热量传递， 而布置在锅炉 尾部对流烟道的受热面， 由于烟气温度低， 热量传递主要是以对流传热为主。 锅炉在运行中， 各部位的烟气温度随着锅炉负荷的变化而变化， 因此沿着烟 气流程上的各级受热面传热特性也将随着锅炉负荷的变化发生较大的变化， 一般地， 在锅炉受热面中以辐射传热的热量随锅炉负荷变化比较缓慢， 而对 流传热随负荷变化比较显著。因此研究 CFB锅炉各级过热器受热面传热随着 负荷的变化而变化的特 可以通过合理布置 CFB锅炉各级过热器受热面沿 烟气流程的位置以及吸热份额 （每级过热器吸热量占整个过热器吸热量的比 例 利用辐射传热与对流传热随锅炉负荷变化而不同的特性来改善锅炉各级 过热器受热面的汽温和管壁温度特性。
过热器分级的定义： 对于锅炉过热器分级布置的定义， 从通常意义上来 说如果级过热器受热面进出口蒸汽温度不连续， 之间有汽温控制的装置或调 节措施， 认为是分级的， 如高温级过热器和中温级过热器之间有喷水减温器 来调节温度， 如果没有可以认为是一级过热器。 发明的公开
本发明提供的一种循环流化床锅炉各级过热器的布置结构, 使锅炉各级 过热器在各种负荷下的汽温和壁温特性得到大大改善， 提高了锅炉运行的安 全性和使用寿命。
为了达到上述目的， 本发明一种循环流化床锅炉各级过热器的布置结 构， 包含布置在锅炉尾部对流烟道内的省煤器、 管路连接所述省煤器的汽包 (或者汽水分离器)、 以及管路连接所述汽包（或者汽水分离器）的炉膛水冷 壁。
所述的循环流化床锅炉各级过热器的布置结构还包含若干通过管路连接 组成密闭回路的尾部包复过热器、 低温过热器、 高温级过热器。 所述的高温级过热器可以单级布置， 也可以多级布置。
所述的多级布置的高温级过热器包含管路连接的中温过热器和高温过热 器 （又称末级过热器）。
所述的循环流化床锅炉各级过热器的布置结构还包含再热器系统， 该再 热器系统包含若干通过管路连接组成密闭回路的低温再热器高温再热器 (又 称末级再热器）。
所述的高温级过热器布置在锅炉的炉膛内， 所述的低温过热器布置在锅 炉的尾部烟道内。
所述的高温再热器布置在在锅炉的炉膛内， 所述的低温再热器布置在锅 炉的尾部烟道内。
本发明具有以下优点：
1、循环流化床锅炉过热器高温级过热器布置在炉膛内， 布置在炉膛燃烧 室内的高温级过热器受热面吸热量占整个过热器系统的吸热量在 48-58%的 份额范围内， 可以得到良好的汽温特性， 各级过热器受热面管子的壁温也得 到大大的改善， 只要锅炉在设计中满足满负荷各级过热器受热面不超温， 低 负荷时也不会超温， 提高锅炉低负荷运行的安全性。
2、 对于循环流化床锅炉， 炉内布置高温级过热器， 增加了传热温压， 同 时使锅炉受热面布置简单， 从循环流化床锅炉发展趋势来看， 超临界， 超超 临界循环流化床锅炉由于过热 （再热） 蒸汽温度的提高， 必须要求高温级受 热器具有一定的传热温压， 循环流化床锅炉的燃烧特性是低温燃烧， 要在锅 炉各种负荷下获得尽量高的传热温压， 减少过热器受热面。
3、锅炉过热器辐射和对流特性良好的匹配， 锅炉在各种负荷下具有好的 汽温特性， 使过热器各级减温器喷水变化小， 在设计中可以减少减温器喷水 量的设计。
4、 各级过热器的汽温、 壁温变化平稳且变化幅度小， 有利于减少受热面 管子的交变应力， 提高受热面的安全性和使用寿命。 附图的简要说明
图 1是本发明提供的循环流化床锅炉各级过热器的布置结构的第一实施 例的结构示意图； 图 2是本发明提供的循环流化床锅炉各级过热器的布置结构的第二实施 例的结构示意图；
图 3是本发明提供的循环流化床锅炉各级过热器的布置结构的第三实施 例的结构示意图； '
图 4是采用本发明后循环流化床锅炉各级过热器蒸汽温度与负荷的变化 曲线。 实现本发明的最佳方式
以下根据图 1〜图 4， 具体说明本发明的较佳实施例：
如图 1所示， 是本发明提供的循环流化床锅炉各级过热器的布置结构的 第一实施例的结构示意图， 锅炉给水通过给水管道 1进入布置在尾部对流烟 道内的省煤器 10， 加热后通过省煤器至锅炉汽包连接管道 11进入汽包 20， 汽包内的水通过下降管 21进入水冷壁下集箱 2， 水在炉膛水冷壁 3 (3a、 3b、 3c、 3d为膜式水冷壁的四个墙） 中加热后形成汽水混合物由炉膛至汽包连接 管道 22进入汽包 20汽包 20把水冷壁 3中形成的汽水混合物进行汽水分离 水进入下降管 21， 饱和蒸汽通过汽包至尾部包复过热器连接管道 29把蒸汽 引入到尾部包复过热器 30， 加热后的蒸汽进入布置在尾部对流烟道中的低温 过热器 31， 经过一级喷水减温器 32后， 过热蒸汽进入布置在锅炉炉膛内的 中温过热器 35， 然后再经过二级喷水减温器 38进入布置在锅炉炉膛内的高 温过热器 40， 合格的蒸汽从锅炉引出至汽轮发电机， 本实例中， 沿蒸汽流程 的高温级过热器中的中温过热器 35和高温过热器 40布置在炉膛内， 并且吸 热量占整个过热器系统的吸热量份额 48-58%各级过热器都具有良好的汽温 和壁温特性。
如图 2所示， 是本发明提供的循环流化床锅炉各级过热器的布置结构的 第二实施例的结构示意图， 锅炉给水进入布置在尾部对流烟道内的低温省煤 器 ια加热后进入高温省煤器 然后由锅炉汽包连接管道 11进入汽包 2α 汽包内的水通过下降管 21进入水冷壁下集箱 2， 水在炉膛水冷壁 3 (3a、 3b、 3c、 3d为膜式水冷壁的四个墙） 中加热后 成汽水混合物由炉膛至汽包连接 管道 22进入汽包 2Q汽包 20把水冷壁 3中形成的汽水混合物进行汽水分离 水进入下降管 21， 饱和蒸汽通过汽包至尾部包复过热器连接管道 29把蒸汽 引入到尾部包复过热器 30， 本实例中， 尾部包复为双烟道的布置， 加热后的 蒸汽进入布置在尾部对流双烟道中的低温过热器 31，经过一级喷水减温器 32 后， 过热蒸汽进入布置在锅炉炉膛内的中温过热器 35， 然后再经过二级喷水 减温器 38进入布置在锅炉炉膛内的高温过热器 40, 合格的蒸汽从锅炉引出 至汽轮发电机， 再热蒸汽首先进入尾部低温再热器 51， 低温再热器 51布置 在尾部对流双烟道中的另外一个烟道中，然后经过再热器喷水减温器 53进入 布置在炉膛内的高温再热器 55， 合格的再热蒸汽引出锅炉进入汽轮发电机。 本实例中， 沿蒸汽流程的高温级过热器中的中温过热器 35和高温过热器 40 布置在炉膛内， 并且吸热量占整个过热器系统的吸热量份额 48-58%的范围 内， 各级过热器受热面具有良好的汽温和壁温特性。
如图 3所示， 是本发明提供的循环流化床锅炉各级过热器的布置结构的 第三实施例的结构示意图， 锅炉给水进入布置在尾部对流烟道内的低温省煤 器 10， 加热后进入高温省煤器 12， 然后由连接管道 11进入炉膛水冷壁下集 箱， 水在炉膛水冷壁 3 (3a、 3b、 3c、 3d为膜式水冷壁的四个墙） 中加热后 形成汽水混合物或过热蒸汽后由炉膛至汽包连接管道 22 进入汽水分离器 20, 汽水分离器 20把水冷壁 3中形成的汽水混合物进行汽水分离（在锅炉启 动阶段或低负荷时)， 水进入启动系统， 蒸汽通过汽包至尾部包复过热器连接 管道 29把蒸汽引入到尾部包复过热器 30， 本实例中， 尾部包复为双烟道的 布置， 加热后的蒸汽进入布置在尾部对流双烟道中的低温过热器 31， 经过一 级喷水减温器 32后， 过热蒸汽进入布置在锅炉炉膛内的中温过热器 35， 然 后再经过二级喷水减温器 38进入布置在锅炉炉膛内的高温过热器 40， 合格 的蒸汽从锅炉引出至汽轮发电机， 再热蒸汽首先进入尾部低温再热器 51， 低 温再热器布置在尾部对流双烟道中的另外一个烟道中， 然后经过再热器喷水 减温器 53进入布置在炉膛内的高温再热器 55， 合格的再热蒸汽引出锅炉进 入汽轮发电机。 本实例中， 沿蒸汽流程的高温级过热器中的中温过热器 35 和高温过热器 40布置在炉膛内，并且吸热量占整个过热器系统的吸热量份额 48-58%的范围内， 各级过热器受热面具有良好的汽温和壁温特性。
如图 4所示， 是采用本发明后循环流化床锅炉各级过热器蒸汽温度与负 荷的变化曲线， 从图 4可以看出， 由于布置在炉膛内的过热器具有良好的辐 射特性， 高温过热器出口温度按照常规意义的锅炉蒸汽发生装置的要求是控 制在某一恒定值（本案例为 540°C )， 随着负荷的降低， 高温过热器进口的温 度随着负荷的降低而降低， 沿着蒸汽的流程， 中温过热器进出口的温度也随 着负荷的降低而降低， 这就说明锅炉在变负荷运行过程中， 各级过热器进出 温度都比满负荷 （BMCR) 时低， 因此在锅炉设计中只要满足锅炉满负荷时 各级受热面的安全性， 锅炉在其它低负荷时安全， 不会发生 CFB锅炉在低负 荷超温爆管的现象。
在锅炉整个过热器蒸汽流程中， 蒸汽温度最高， 在布置中通常使用耐高 温性能好的材料 （如： SA213T91、 SUS304、 SA213TP347等）， 往往温度波 动会造成材料的疲劳损坏。 本发明强调循环流化床锅炉最末级高温过热器布 置在炉膛内， 因为其对于循环流化床锅炉炉膛燃烧温度随负荷的变化比较缓 慢， 而末级过热器出口的蒸汽温度是可以通过减温喷水或其它燃烧调整手段 来进行控制的， 因此在锅炉负荷变化过程中， 高温过热器的壁温比较稳定， 壁温波动小， 提高了高温级过热器受热面的安全性。
尽管本发明的内容已经通过上述优选实施例作了详细介绍， 但应当认识 到上述的描述不应被认为是对本发明的限制。 在本领域技术人员阅读了上述 内容后， 对于本发明的多种修改和替代都将是显而易见的。 因此， 本发明的 保护范围应由所附的权利要求来限定。

Claims

权利要求
1. 一种循环流化床锅炉各级过热器的布置结构，包含布置在锅炉尾部对流烟 道内的省煤器、管路连接所述省煤器的汽包、 以及管路连接所述汽包的炉 膛水冷壁， 还包含若干通过管路连接组成密闭回路的尾部包复过热器、低 温过热器、 高温级过热器， 其特征在于，
所述的高温级过热器布置在锅炉的炉膛内。
2. 如权利要求 1 所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于， 所述的高温级过热器的吸热量占整个过热器系统的吸热量份额的 48-58%。
3. 如权利要求 1 所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于， 所述的低温过热器布置在锅炉的尾部烟道内。
4. 如权利要求 1 所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于， 所述的高温级过热器单级布置， 或者多级布置。
5. 如权利要求 4所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于，所述的多级布置的高温级过热器包含管路连接的中温过热器和高温过 热器。
6. 如权利要求 1 所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于， 所述的循环流化床锅炉各级过热器的布置结构还包含再热器系统。
7. 如权利要求 6所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于， 所述的再热器系统包含若干通过管路连接组成密闭回路的低温再热 器、 局温再热器
8. 如权利要求 7所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于， 所述的高温再热器布置在在锅炉的炉膛内。
9. 如权利要求 7所述的循环流化床锅炉各级过热器的布置结构， 其特征在 于， 所述的低温再热器布置在锅炉的尾部烟道内。
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