WO2014110885A1 - 可抽气式煤粉锅炉 - Google Patents

可抽气式煤粉锅炉 Download PDF

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Publication number
WO2014110885A1
WO2014110885A1 PCT/CN2013/075703 CN2013075703W WO2014110885A1 WO 2014110885 A1 WO2014110885 A1 WO 2014110885A1 CN 2013075703 W CN2013075703 W CN 2013075703W WO 2014110885 A1 WO2014110885 A1 WO 2014110885A1
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WO
WIPO (PCT)
Prior art keywords
flue gas
passage
temperature
pulverized coal
air
Prior art date
Application number
PCT/CN2013/075703
Other languages
English (en)
French (fr)
Inventor
吴道洪
王胜美
吴玉林
鲁光明
陈琳
沈大平
Original Assignee
北京神雾环境能源科技集团股份有限公司
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
Priority claimed from CN201310019455.3A external-priority patent/CN103672869B/zh
Priority claimed from CN201310019500.5A external-priority patent/CN103940275B/zh
Priority claimed from CN2013200280376U external-priority patent/CN203323118U/zh
Application filed by 北京神雾环境能源科技集团股份有限公司 filed Critical 北京神雾环境能源科技集团股份有限公司
Priority to AU2013374018A priority Critical patent/AU2013374018B2/en
Priority to RU2015133247A priority patent/RU2612682C2/ru
Publication of WO2014110885A1 publication Critical patent/WO2014110885A1/zh
Priority to ZA2015/05206A priority patent/ZA201505206B/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23B—METHODS OR APPARATUS FOR COMBUSTION USING ONLY SOLID FUEL
    • F23B80/00—Combustion apparatus characterised by means creating a distinct flow path for flue gases or for non-combusted gases given off by the fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L15/00—Heating of air supplied for combustion
    • F23L15/02—Arrangements of regenerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/06—Flue or fire tubes; Accessories therefor, e.g. fire-tube inserts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2237/00—Controlling
    • F23N2237/20—Controlling one or more bypass conduits
    • 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
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery

Definitions

  • the invention relates to the field of industrial technology, and in particular to an extractable pulverized coal boiler. Background technique
  • coal used in China's pulverized coal boilers has lignite, long-flame coal, non-stick coal, gas coal, lean coal and a small amount of anthracite, among which lignite, long-flame coal and non-stick coal with higher volatile content are the largest.
  • China's anthracite reserves are abundant, accounting for about 19% of total coal reserves.
  • anthracite has low volatiles and is not easy to burn out.
  • the W flame boiler is the main furnace type that uses low-volatility coal. It basically solves the stability and reliability of large-scale boiler operation using low-volatility power generation, but there are still problems such as poor combustion effect.
  • Low volatile coal combustion requires sufficient air to adequately meet the amount of oxygen required for the combustion process.
  • low-volatility coals such as anthracite and lean coal have high ignition temperatures, and it is difficult to ignite and stabilize stable combustion of coal powder, which limits its application range.
  • the use of high-temperature air to ignite low-volatility coal such as anthracite and lean coal can effectively solve the problem of pulverized coal ignition and stable combustion, so that the energy can be rationally and fully utilized.
  • the existing pulverized coal boiler uses a metal air preheater for preheating recovery of flue gas.
  • the air required to preheat the pulverized coal is limited by the structure and material of the metal heat exchanger itself, and the flue gas needs to be reduced to below 500 °C.
  • Preheating and recycling the energy saving effect is poor, and the preheated air temperature is low, usually only 300 ⁇ 400 °C.
  • there is a problem of low temperature corrosion in the operation of, for example, a metal corrugated rotary air preheater and problems such as dust accumulation and clogging are easily caused by narrow gas distribution channels. Summary of the invention
  • an object of the present invention is to provide a pulverized coal-fired boiler that has a high air preheating temperature and is controllable.
  • An extractable pulverized coal boiler includes: a boiler body, wherein the boiler body defines a furnace; the regenerative rotary reversing heater, the regenerative rotary reversing heater comprises: a heat exchanger body; a driving device, wherein the driving device is configured to drive the heat exchanger body to rotate about a central axis thereof; a partitioning member, the partitioning member is disposed in the heat exchanger body along a direction of the central axis Separating the heat exchanger body into at least one pair of receiving portions, the pair of receiving portions being disposed diametrically opposite to the central axis; the heat carrier, the heat carrier being respectively received in the receiving portion
  • the heat carrier is formed of a non-metallic solid material; a flue gas passage, an inlet end of the flue gas passage is in communication with the furnace, and an outlet end is connected to the regenerative rotary reversing heater to The flue gas generated in the furnace is introduced into at least one of the pair of the accommodating portions and
  • the regenerative rotary reversing heater can recover the waste heat of the flue gas up to 1200 ° C, thereby The combustion air entering the furnace is fully preheated, so that low-volatile coal such as anthracite or lean coal can be stably and fully burned in the boiler.
  • extractable pulverized coal boiler according to the present invention may have the following additional technical features:
  • the extractable pulverized coal boiler further comprises: at least one low temperature pumping passage, the flue gas passage between one end of the low temperature pumping passage and the plurality of superheaters At least one of the portions is in communication with the other end of the flue gas passage being in communication with the outlet end of the flue gas passage, wherein the pumping control unit is configured to control a second flue gas supplied via the at least one cryogenic pumping passage the amount.
  • the heat carrier has a structure of a small spherical shape, a sheet shape or a porous shape.
  • the pulverized coal is formed of at least one of anthracite and lean coal.
  • the pumping control unit comprises an electric or pneumatic high temperature flue gas regulating valve, and the high temperature flue gas regulating valve is disposed on the high temperature exhausting passage.
  • the pumping control unit comprises an electric or pneumatic high temperature flue gas regulating valve, and the high temperature flue gas regulating valve is disposed on the high temperature exhausting passage.
  • the pumping control unit further comprises: an electric or pneumatic low temperature flue gas regulating valve, the low temperature flue gas regulating valve being disposed on the at least one low temperature exhausting passage.
  • an electric or pneumatic low temperature flue gas regulating valve the low temperature flue gas regulating valve being disposed on the at least one low temperature exhausting passage.
  • the pumping control unit controls at least one of the high pressure flue gas regulating valve and the low temperature flue gas regulating valve such that the temperature of the air at the outlet of the air passage is 400 - 1000 °C.
  • a screen superheater and a wall superheater are disposed in sequence from the inlet end of the flue gas passage toward the outlet end of the flue gas passage.
  • an economizer is disposed in the flue gas passage adjacent to the outlet end of the flue gas passage.
  • FIG. 1 is an extractable pulverized coal boiler according to an embodiment of the present invention.
  • FIG. 2 is a plan view of a regenerative rotary reversing heater in an extractable pulverized coal boiler according to an embodiment of the present invention.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, features defining “first” and “second” may explicitly or implicitly include one or more of the features. In the description of the present invention, “multiple” means two or more unless otherwise stated.
  • Connected and “connected” should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or passed through The intermediate medium is indirectly connected and can be internal to the two components.
  • the specific meaning of the above terms in the present invention can be understood in a specific case by those skilled in the art.
  • an extractable pulverized coal boiler 100 includes: a boiler body 1, a regenerative rotary reversing heater 2, a flue gas passage 3, an air passage 4, and a high temperature pumping passage 5 And a pumping control unit 51.
  • the regenerative rotary reversing heater 2 is used for exchanging heat between the high temperature flue gas and the air to be preheated, thereby raising the temperature of the air to be preheated to a certain value.
  • the regenerative rotary reversing heater 2 comprises: a heat exchanger body 21, a driving device, a partition 22 and a heat carrier 23, as shown in Figs.
  • the drive means is used to drive the heat exchanger body 21 to rotate about its central axis 24.
  • the partition member 22 is disposed in the heat exchanger body 21 in the direction of the center axis 24, and partitions the heat exchanger body 21 into at least one pair of accommodating portions 25, each pair of accommodating portions 25 being disposed diametrically opposite to the center axis.
  • the heat carriers 23 are respectively accommodated in the accommodating portion 25, and the heat carrier 23 is formed of a non-metallic solid material.
  • the heat exchanger body 21 may be formed as a hollow cylinder, and the partition 22 may have a substantially plate shape extending in the direction of the center line axis of the heat exchanger body 21, thereby
  • the heat exchanger body 21 is partitioned into a pair of accommodating portions 25, and the heat carriers are respectively disposed in the two accommodating portions 25, and the heat carrier 23 may be made of a non-metallic solid material, and the flue gas and the air to be preheated are respectively introduced into the two accommodating portions 25
  • the heat exchanger main body 21 is driven to rotate by the driving device, the flue gas exchanges heat with the heat carrier in the accommodating portion 25 in which it is located, the air to be preheated, and the heat carrier in the accommodating portion thereof are exchanged, thereby The temperature of the air to be preheated is raised.
  • the separator 22 may also have a heat exchanger body 21 is divided into two pairs, three pairs or even multiple pairs of housing parts.
  • the outlet temperature of the flue gas after passing through the gas heat exchanger cannot be lowered below 130 ° C, because this causes the sulfuric acid to precipitate, resulting in the metal in the gas heat exchanger. Severe corrosion of the manufactured parts.
  • the heat carrier is formed of a non-metallic solid material such as SiC or ceramic, there is no need to worry about sulfur.
  • the outlet temperature of the high-temperature flue gas can be lowered to a temperature below the dew point of sulfur to maximize heat exchange.
  • the high temperature The outlet temperature of the flue gas leaving the gas heat exchanger is less than 130 ° C. Further, the outlet temperature of the high temperature flue gas leaving the gas heat exchanger is less than 70 degrees. This temperature is almost impossible to achieve in a conventional gas heat exchange system.
  • the water vapor condenses out as liquid water, releasing a large amount of latent heat (the amount of heat absorbed by the water vapor from 100 ° C to 100 ° C is equivalent to the water from 0 °C is increased to 3 times when absorbed at 100 °C).
  • the heat carrier is formed of a non-metallic solid material, after the sulfur deposition is performed to some extent, the heat carrier accommodated in the accommodating portion can be continuously used, thereby reducing the components existing in the conventional gas heat exchange system. The problem of increased costs caused by replacement.
  • the efficiency of the entire boiler can be increased by 0.5% for every 10 °C decrease in the outlet temperature, and the latent heat released is equivalent to Increases the efficiency of the entire boiler by 1.5%, so that when the flue gas temperature is lowered to, for example, 70 ° C, the efficiency of the entire boiler is increased by 4.5% or more (0.5% X6 + 1.5), thereby saving a large amount in the boiler.
  • Coal combustion while expanding the scope of application of coal, can reduce the grade of coal used, further reducing production costs.
  • the furnace body 1 defines a furnace 1 1 .
  • the inlet end of the flue gas passage 3 communicates with the furnace 1 1 , and the outlet end of the flue gas passage 3 communicates with the regenerative rotary reversing heater 2 to pass the flue gas generated in the furnace 11 into at least a pair
  • One of the accommodating portions of the regenerative rotary reversing heater 2 is exchanged with the heat carrier accommodated in the accommodating portion, and a plurality of superheaters are disposed in the flue gas passage 3.
  • the air passage 4 is for introducing air into the other of the accommodating portions of the at least pair of the regenerative rotary reversing heaters 2 so that the heat carrier accommodated in the accommodating portion exchanges heat with the air.
  • the pumping control unit 51 is for controlling the amount of the first flue gas supplied via the high temperature pumping passage 5.
  • the heat exchanger body 21 is rotated counterclockwise, and the flue gas is introduced into the heat exchanger body 21 along the right side of the central axis, and the preheated air is introduced into the heat exchanger along the left side of the central axis.
  • the main body 21 will be described as an example.
  • a furnace 1 is defined in the boiler body 1 for accommodating coal powder, one end of the flue gas passage 3 is in communication with the furnace 1 1 , and the other end is connected to the regenerative rotary reversing heater 2 to
  • the flue gas generated in the furnace 1 1 is introduced into the first accommodating portion 21 1 of the regenerative rotary reversing heater 2 (for example, the right side of the regenerative rotary reversing heater 2 shown in Fig. 1) , in the second accommodating portion 212 of the regenerative rotary reversing heater 2 (for example, the left side of the regenerative rotary reversing heater 2 shown in FIG.
  • the flue gas exchanges heat with the heat carrier in the first accommodating portion 21 1 to increase the temperature of the heat carrier, and after the heat carrier absorbs heat, the heat exchanger body 21 rotates counterclockwise.
  • a receiving portion 21 1 is rotated to the left of the central axis Side
  • the second receiving portion 212 is rotated to the right side of the central axis
  • the heat carrier rotated into the first receiving portion 21 1 on the left side exchanges heat with the air to be heated to raise the temperature of the heated air, and at the same time, the smoke pair
  • the heat carrier rotated into the second accommodating portion 212 on the right side is heated.
  • the heat exchanger body 21 continues to rotate counterclockwise, at which time the first receiving portion 21 1 is rotated back to the right side of the center axis, and the second receiving portion 212 is rotated back to the left side of the center axis, rotating back to the second side of the left side.
  • the heat carrier in the accommodating portion 212 exchanges heat with the air to be heated, and the flue gas heats the heat carrier in the first accommodating portion 21 1 rotated back to the right side, and the cycle is repeated to complete the heating of the air to be heated.
  • one end of the high-temperature exhaust passage 5 can communicate with the upper portion of the furnace 1 1 , and the other end communicates with the outlet end of the flue gas passage 3 to pass the high-temperature flue gas into the heat storage.
  • the pumping control unit 51 is disposed on the high temperature pumping passage 5 to control the first flue gas supplied via the high temperature pumping passage 5, according to the extractable pulverized coal boiler 100 of the embodiment of the present invention,
  • the regenerative rotary reversing heater 2 can recover the residual heat of the flue gas up to 1200 ° C, thereby fully preheating the combustion air entering the furnace 11
  • low-volatile coal such as anthracite and lean coal can be stably and fully burned in the boiler.
  • the extractable pulverized coal boiler 100 further includes: at least one low temperature pumping passage 6, at least one of a portion of the flue gas passage 3 between one end of the low temperature pumping passage 6 and the plurality of superheaters One of the phases is in communication with the other end of which is in communication with the outlet end of the flue gas passage 3, wherein the pumping control unit 51 is for controlling the amount of second flue gas supplied via the at least one cryogenic pumping passage 6.
  • the air can be pumped from different parts of the pulverized coal boiler, so that the pumping amount and temperature of the flue gas can be controlled according to actual needs to meet the different requirements of the pulverized coal boiler for the air preheating temperature.
  • the number of the low temperature pumping passages 6 can be set according to actual requirements to better meet the actual requirements.
  • low-temperature evacuation passages 6 one end of which is disposed between the wall superheater 8 and the tail flue superheater 9, and the other end is connected to the flue gas passage 3
  • the outlet end of the other low temperature pumping passage 6 is disposed between the tail flue superheater 9 and the economizer 10, the other end of which is in communication with the outlet end of the flue gas passage 3, and the pumping control unit 51 is two And two pumping control units 51 are respectively disposed on the two low temperature pumping passages 6.
  • the heat carrier has a small spherical, sheet or porous structure.
  • the heat exchange efficiency between the flue gas and the air to be preheated and the heat carrier can be enhanced by increasing the contact area.
  • the pulverized coal is formed of at least one of anthracite and lean coal. It can be understood that the pulverized coal may also be lignite, long flame coal, non-stick coal, gas coal, and the like.
  • the pumping control unit 51 includes an electric or pneumatic high temperature flue gas regulating valve, and the high temperature flue gas regulating valve is disposed on the high temperature exhausting passage 5. That is, the pumping control unit 51 may be an electric high temperature flue gas regulating valve or a pneumatic high temperature flue gas regulating valve. Thus, by providing a high-temperature flue gas regulating valve, the amount of flue gas of the high-temperature flue gas in the high-temperature exhausting passage 5 can be adjusted.
  • the pumping control unit 51 further comprises: electric or pneumatic low temperature flue gas The regulating valve, the low temperature flue gas regulating valve is disposed on the at least one low temperature pumping passage 6. That is, the pumping control unit 51 may be an electric low temperature flue gas regulating valve, or a pneumatic low temperature flue gas regulating valve.
  • the low temperature flue gas regulating valve One or a low temperature flue gas regulating valve may be disposed on one of the plurality of low temperature exhausting passages 6, or the number of low temperature flue gas regulating valves is less than the number of the low temperature exhausting passages 6, and the low temperature flue gas regulating valve is provided
  • the number of the low temperature flue gas regulating valves is equal to the number of the low temperature exhausting passages 6 on some of the plurality of low temperature exhausting passages 6, and the plurality of low temperature flue gas regulating valves are respectively disposed on the plurality of low temperature exhausting passages 6 . Thereby, the amount of flue gas of the low-temperature flue gas in the low-temperature exhaust passage 6 can be adjusted by providing the low-temperature flue gas regulating valve.
  • the pumping control unit 51 controls at least one of the high pressure flue gas regulating valve and the low temperature flue gas regulating valve such that the temperature of the air at the outlet of the air passage 4 is 400-1000 °C. That is to say, the pumping control unit 51 can also have a control device (not shown), and the pumping control unit 51 can control only the high pressure flue gas regulating valve or only the low temperature flue gas regulating valve by the control device, as long as it is guaranteed The temperature of the preheated air to be introduced into the furnace 1 1 is 400-1000 ° C.
  • a screen superheater 7 and a wall superheater 8 are disposed in order from the inlet end of the flue gas passage 3 toward the outlet end of the flue gas passage 3.
  • a screen superheater 7 and a wall superheater 8 are sequentially disposed at a communication between the furnace 1 1 and the flue gas passage 3.
  • the economizer 10 is disposed in the flue gas passage 3 near the outlet end of the flue gas passage 3.
  • the regenerative rotary reversing heater 2 is used to alternately switch the flue gas and air to flow through the heat carrier, thereby maximally recovering the physical heat of the high-temperature flue gas, thereby greatly saving energy and improving the thermal efficiency of the thermal equipment. . Since the temperature of the air to be preheated entering the furnace 1 1 is higher, the combustion zone is expanded by the tissue combustion, and the flame boundary is extended to the boundary of the furnace 1 1 to make the temperature distribution in the furnace uniform; the regenerative rotary reversing heater 2
  • the use of low calorific value fuels, low volatile fuels can achieve stable, continuous combustion by means of high temperature preheated air, improve fuel burn-up rate, and expand the application range of low volatile fuels.

Abstract

一种可抽气式煤粉锅炉（100），其包括锅炉本体（1），锅炉本体（1）内限定有炉膛（11）；蓄热式旋转换向加热器（2）；烟气通道（3），其入口端与炉膛（11）相连通，出口端与蓄热式旋转换向加热器（2）相连通以将炉膛（11）内的烟气通入至少成对的容纳部分（25）中的一个内并与其中容纳的热载体（23）换热，烟气通道（3）内设置有多个过热器；空气通路（4），用于将空气至少通入成对的容纳部分（25）中的另一个内，以使得其中容纳的热载体（23）与空气进行换热；高温抽气通路（5），其一端与烟气通道（3）的朝向炉膛（11）的一端相连通，另一端与烟气通道（3）的出口端相连通；抽气控制单元（51），用于控制经由高温抽气通路（5）供给的第一烟气量。该煤粉锅炉在提高空气预热温度的同时实现了可控操作，提高了锅炉的热效率，同时解决了利用低挥发份发电大型锅炉运行的稳定性和可靠性问题。

Description

可抽气式煤粉锅炉
技术领域
本发明涉及工业技术领域， 尤其是涉及一种可抽气式煤粉锅炉。 背景技术
目前， 我国煤粉锅炉用煤有褐煤、 长焰煤、 不粘煤、 气煤、 贫煤以及少量的无烟煤， 其中以挥发份较高的褐煤、 长焰煤、 不粘煤的用量最大。 我国无烟煤储量丰富， 占总煤 炭储量的 19%左右， 但是无烟煤挥发份低、 不易燃尽等特性， 其在利用过程中存在能源 系统效率偏低、 动力煤的产品较低、 污染排放较严重等问题。 W 火焰锅炉是燃用低挥 发分煤的主力炉型， 它基本解决了利用低挥发分发电大型锅炉运行的稳定性和可靠性， 但是仍然存在燃烧效果较差等问题。低挥发分煤燃烧需要充足的空气， 充分满足燃烧过 程所需要的氧量。 同时， 无烟煤、 贫煤等低挥发分煤着火温度高， 点火及实现稳定煤粉 稳定燃烧比较困难， 使其应用范围受限。
为了解决低挥发分煤的点火与燃烧稳定， 采用高温空气点燃无烟煤、 贫煤等低挥发 分煤能有效解决煤粉点燃及稳定燃烧问题， 使得能源得到合理、 充分利用。 但是， 现有 煤粉锅炉采用金属空气预热器进行烟气预热回收， 预热煤粉所需的空气， 受到金属换热 器本身结构和材质的限制， 烟气需降低至 500°C以下再进行预热回收， 节能效果较差， 预热空气温度较低， 通常只能达到 300~400 °C。 此外， 在例如金属波纹板回转式空气预 热器的运行中还存在低温腐蚀问题， 且由于气体的流通渠道狭窄， 很容易造成积灰和堵 灰等问题。 发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。 为此， 本发明的一个目的在 于提出一种空气预热温度高且可控的可抽气式煤粉锅炉。
根据本发明实施例的可抽气式煤粉锅炉， 包括： 锅炉本体， 所述锅炉本体内限定有 炉膛； 蓄热式旋转换向加热器， 所述蓄热式旋转换向加热器包括： 换热器主体； 驱动装 置， 所述驱动装置用于驱动所述换热器主体绕其中心轴线旋转； 分隔件， 所述分隔件沿 着所述中心轴线的方向设置在所述换热器主体内，且将所述换热器主体分隔成至少一对 容纳部分， 所述每对容纳部分相对所述中心轴线成径向相对设置； 热载体， 所述热载体 分别容纳在所述容纳部分中， 所述热载体由非金属固体材料所形成； 烟气通道， 所述烟 气通道的入口端与所述炉膛相连通， 且出口端与所述蓄热式旋转换向加热器相连通， 以 将炉膛内产生的烟气通入至少所述成对的所述容纳部分中的一个内并与其中容纳的所 述热载体换热， 所述烟气通道内设置有多个过热器； 以及空气通路， 所述空气通路用于 将空气至少通入所述成对的所述容纳部分中的另一个内，以使得其中容纳的所述热载体 与所述空气进行换热； 高温抽气通路， 所述高温抽气通路的一端与所述烟气通道的朝向 所述炉膛的一端相连通，所述高温抽气通路的另一端与所述烟气通道的所述出口端相连 通； 以及抽气控制单元， 所述抽气控制单元用于控制经由所述高温抽气通路供给的第一 烟气量。
根据本发明实施例的可抽气式煤粉锅炉， 通过设置蓄热式旋转换向加热器， 该蓄热 式旋转换向加热器可将温度高达 1200°C的烟气余热进行极限回收， 从而将进入炉膛的 助燃空气进行充分预热， 进而使得无烟煤、 贫煤等低挥发分煤可在锅炉内进行稳定、 充 分地燃烧。
另外， 根据本发明的可抽气式煤粉锅炉还可具有如下附加技术特征：
根据本发明的一个实施例， 所述可抽气式煤粉锅炉进一步包括： 至少一个低温抽气 通路，所述低温抽气通路的一端与所述多个过热器之间的所述烟气通道部分中的至少一 个相连通， 其另一端与所述烟气通道的所述出口端相连通， 其中所述抽气控制单元用于 控制经由所述至少一个低温抽气通路供给的第二烟气量。由此，通过设置低温抽气通路， 可从煤粉锅炉的不同部位进行抽气， 从而可根据实际需求， 控制烟气的抽气量和温度以 满足煤粉锅炉对空气预热温度的不同要求。
可选地， 所述热载体具有小球状、 片状或者多孔状的结构。
可选地， 所述煤粉由无烟煤、 贫煤中的至少一种所形成。
可选地， 所述抽气控制单元包括电动或者气动高温烟气调节阀， 所述高温烟气调节 阀设置在所述高温抽气通路上。 由此， 通过设置高温烟气调节阀， 可调节高温抽气通路 中的高温烟气的烟气量。
根据本发明的一个实施例， 所述抽气控制单元进一步包括： 电动或者气动低温烟气 调节阀， 所述低温烟气调节阀设置在所述至少一个低温抽气通路上。 由此， 通过设置低 温烟气调节阀， 可调节低温抽气通路中的低温烟气的烟气量。
可选地， 所述抽气控制单元控制所述高压烟气调节阀和所述低温烟气调节阀中的至 少一个， 以使所述空气通路的出口处的所述空气的温度为 400 - 1000 °C。
根据本发明的一个实施例， 从所述烟气通道的所述入口端朝向所述烟气通道的所述 出口端依次设置有屏式过热器、 包墙过热器。
根据本发明的一个实施例， 在靠近所述烟气通道的所述出口端的所述烟气通道内设 置有省煤器。
本发明的附加方面和优点将在下面的描述中部分给出， 部分将从下面的描述中变得 明显， 或通过本发明的实践了解到。 附图说明
本发明的上述和 /或附加的方面和优点从结合下面附图对实施例的描述中将变得明 显和容易理解， 其中- 图 1是根据本发明一个实施例的可抽气式煤粉锅炉的示意图；
图 2是根据本发明一个实施例的可抽气式煤粉锅炉中蓄热式旋转换向加热器的俯视 图。 具体实施方式
下面详细描述本发明的实施例， 所述实施例的示例在附图中示出， 其中自始至终相 同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附 图描述的实施例是示例性的， 仅用于解释本发明， 而不能理解为对本发明的限制。
在本发明的描述中， 需要理解的是， 术语"中心"、 "上"、 "下"、 "前"、 "后"、 "左" 、 "右" 、 "竖直" 、 "水平" 、 "顶" 、 "底" 、 "内" 、 "外"等指示的方 位或位置关系为基于附图所示的方位或位置关系， 仅是为了便于描述本发明和简化描 述， 而不是指示或暗示所指的装置或元件必须具有特定的方位、 以特定的方位构造和操 作， 因此不能理解为对本发明的限制。 此外， 术语 "第一" 、 "第二 "仅用于描述目的， 而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。 由此， 限 定有 "第一" 、 "第二" 的特征可以明示或者隐含地包括一个或者更多个该特征。 在本 发明的描述中， 除非另有说明， "多个" 的含义是两个或两个以上。
在本发明的描述中， 需要说明的是， 除非另有明确的规定和限定， 术语 "安装" 、
"相连" 、 "连接 "应做广义理解， 例如， 可以是固定连接， 也可以是可拆卸连接， 或 一体地连接； 可以是机械连接， 也可以是电连接； 可以是直接相连， 也可以通过中间媒 介间接相连， 可以是两个元件内部的连通。 对于本领域的普通技术人员而言， 可以具体 情况理解上述术语在本发明中的具体含义。
下面参考图 1描述根据本发明实施例的可抽气式煤粉锅炉 100。
如图 1所示， 根据本发明实施例的可抽气式煤粉锅炉 100包括： 锅炉本体 1、 蓄热 式旋转换向加热器 2、 烟气通道 3、 空气通路 4、 高温抽气通路 5以及抽气控制单元 51。
蓄热式旋转换向加热器 2用于将高温烟气和待预热空气进行热交换， 从而使待预热 空气的温度升高到某一定值。 蓄热式旋转换向加热器 2包括： 换热器主体 21、 驱动装 置、 分隔件 22和热载体 23， 如图 1、 2中所示。 其中， 驱动装置用于驱动换热器主体 21绕其中心轴线 24旋转。分隔件 22沿着中心轴线 24的方向设置在换热器主体 21内， 且将换热器主体 21分隔成至少一对容纳部分 25， 每对容纳部分 25相对中心轴线成径 向相对设置。 热载体 23分别容纳在容纳部分 25中， 热载体 23由非金属固体材料所形 成。
在本发明的其中一个示例中， 换热器主体 21可形成为中空的圆柱体， 分隔件 22可 大致呈板形， 该分隔间沿着换热器主体 21 中心线轴线的方向延伸， 从而将换热器主体 21分隔成一对容纳部分 25， 热载体分别设在两个容纳部分 25中， 热载体 23可由非金 属固体材料制成， 烟气和待预热空气分别通入两个容纳部分 25中， 然后通过驱动装置 驱动换热器主体 21旋转、烟气和与其所在的容纳部分 25中的热载体进行热交换、待预 热空气和与其所在的容纳部分中的热载体进行热交换， 从而使得待预热空气温度升高。
当然， 本发明不限于此， 在本发明的另一些示例中， 分隔件 22还可将换热器主体 21分隔成两对、 三对甚至多对容纳部分。
在现有的气体换热系统中， 烟气在通过该气体换热器之后的出口温度是不能降低到 130°C以下， 因为这会导致硫酸析出， 从而导致对该气体换热器内由金属制造的部件的 严重腐蚀。但是， 在本发明的上述蓄热式旋转换向加热器 2中 （针对例如含硫的高温烟 气），由于热载体由例如 SiC、陶瓷等的非金属固体材料所形成，从而不用顾虑硫在 130 °C 存在露点所导致的腐蚀性问题，而可以把高温烟气的出口温度降低到硫的露点之下的温 度， 从而最大程度地进行换热， 根据本发明的一个实施例， 所述高温烟气离开所述气体 换热器的出口温度小于 130°C， 进一步地， 所述高温烟气离开所述气体换热器的出口温 度小于 70度。 该温度在传统的气体换热系统中是几乎不可能实现的。 此外， 在将出口 温度降低到露点的温度之下， 水蒸汽冷凝析出为液体水， 释放了大量的潜热（液体水从 100°C变为 100°C的水蒸汽吸收的热量相当于水从 0 °C升高至 100°C时所吸收热量的 3 倍） 。 由于热载体由非金属固体材料所形成， 所以在硫沉积一定程度之后， 对该容纳部 分中所容纳的热载体清洗即可以继续使用，从而降低了传统的气体换热系统中所存在的 零部件替换所导致的成本增加的问题。此外， 根据发明人使用该领域内的公认计算方法 计算， 在例如燃烧锅炉的尾气换热过程中， 出口温度每降低 10°C， 整个锅炉的效率可 以提高 0.5%， 而所释放的潜热相当于提高了整个锅炉效率的 1.5%， 从而在烟气温度降 低到例如 70°C时， 则整个锅炉的效率提高了 4.5%或者更多 （0.5%X6+1.5 ) ， 从而节省 了在锅炉中的大量煤炭燃烧， 同时扩大了煤炭的适用范围， 即可以降低所使用的煤的品 位， 进一步地降低了生产成本。
其中， 锅炉本体 1 内限定有炉膛 1 1。 烟气通道 3的入口端与炉膛 1 1相连通， 且烟 气通道 3的出口端与蓄热式旋转换向加热器 2相连通， 以将炉膛 1 1 内产生的烟气通入 至少成对的蓄热式旋转换向加热器 2的容纳部分中的一个内，并与容纳部分中容纳的热 载体换热， 烟气通道 3内设置有多个过热器。空气通路 4用于将空气通入至少成对的蓄 热式旋转换向加热器 2的容纳部分中的另一个内，以使得容纳部分中容纳的热载体与空 气进行换热。 高温抽气通路 5的一端与烟气通道 3的朝向炉膛 1 1的一端相连通， 高温 抽气通路 5的另一端与烟气通道 3的出口端相连通。 抽气控制单元 51用于控制经由高 温抽气通路 5供给的第一烟气量。
在下面的描述中， 以换热器主体 21 逆时针转动， 且烟气沿着中心轴线的右侧通入 换热器主体 21内， 待预热空气沿着中心轴线的左侧通入换热器主体 21为例进行说明。
如图 1所示， 锅炉本体 1 内限定出炉膛 1 1 以用于容纳煤粉， 烟气通道 3的一端与 炉膛 1 1相通， 其另一端与蓄热式旋转换向加热器 2相通， 以将炉膛 1 1 内产生的烟气通 入蓄热式旋转换向加热器 2的第一容纳部分 21 1中（例如为图 1中所示的蓄热式旋转换 向加热器 2的右侧） ， 蓄热式旋转换向加热器 2的第二容纳部分 212 中 （例如为图 1 中所示的蓄热式旋转换向加热器 2的左侧） 用于通入待预热空气， 在换热器主体 21处 于未旋转状态时， 烟气和第一容纳部分 21 1中的热载体换热以使热载体的温度升高， 热 载体吸收热量后， 换热器主体 21逆时针旋转， 第一容纳部分 21 1旋转到中心轴线的左 侧， 第二容纳部分 212旋转到中心轴线的右侧， 旋转到左侧的第一容纳部分 21 1 内的热 载体与待加热空气进行换热以使带加热空气温度升， 同时， 烟气对旋转到右侧的第二容 纳部分 212内的热载体进行加热。
换热器主体 21继续逆时针转动， 此时第一容纳部分 21 1被旋转回到中心轴线的右 侧， 第二容纳部分 212 被旋转回到中心轴线的左侧， 旋转回左侧的第二容纳部分 212 内的热载体与待加热空气进行热交换，烟气对旋转回右侧的第一容纳部分 21 1内的热载 体进行加热， 如此循环重复， 以完成对待加热空气的加热。
由于炉膛 1 1上部的烟气温度较高， 因此高温抽气通路 5的一端可与炉膛 1 1上部相 通， 其另一端与烟气通道 3的出口端相连通以将高温烟气通入蓄热式旋转换向加热器 2 内， 抽气控制单元 51设在高温抽气通路 5上以控制经由高温抽气通路 5供给的第一烟 根据本发明实施例的可抽气式煤粉锅炉 100， 通过设置蓄热式旋转换向加热器 2， 该蓄热式旋转换向加热器 2可将温度高达 1200°C的烟气余热进行极限回收， 从而将进 入炉膛 1 1 的助燃空气进行充分预热， 进而使得无烟煤、 贫煤等低挥发分煤可在锅炉内 进行稳定、 充分地燃烧。
根据本发明的一个实施例， 可抽气式煤粉锅炉 100进一步包括： 至少一个低温抽气 通路 6， 低温抽气通路 6的一端与多个过热器之间的烟气通道 3部分中的至少一个相连 通， 其另一端与烟气通道 3的出口端相连通， 其中抽气控制单元 51用于控制经由至少 一个低温抽气通路 6供给的第二烟气量。 由此， 通过设置低温抽气通路 6， 可从煤粉锅 炉的不同部位进行抽气， 从而可根据实际需求， 控制烟气的抽气量和温度以满足煤粉锅 炉对空气预热温度的不同要求。可以理解的是， 低温抽气通路 6的数量可以根据实际要 求设置， 以更好地满足实际要求。
例如在图 1的示例中， 低温抽气通路 6为两个， 一个低温抽气通路 6的一端设在包 墙过热器 8和尾部烟道过热器 9之间， 其另一端与烟气通道 3的出口端相通， 另一个低 温抽气通路 6的一端设在尾部烟道过热器 9和省煤器 10之间， 其另一端与烟气通道 3 的出口端相通， 抽气控制单元 51为两个， 且两个抽气控制单元 51分别设在两个低温抽 气通路 6上。
可选地， 热载体具有小球状、 片状或者多孔状的结构。 由此， 可通过增大接触面积 来加强烟气和待预热空气与热载体之间的换热效率。
可选地， 煤粉由无烟煤、 贫煤中的至少一种所形成。 可以理解的是， 煤粉还可以是 褐煤、 长焰煤、 不粘煤、 气煤等。
在本发明的一个实施例中， 抽气控制单元 51 包括电动或者气动高温烟气调节阀， 高温烟气调节阀设置在高温抽气通路 5上。 也就是说， 抽气控制单元 51可以是电动高 温烟气调节阀， 或气动高温烟气调节阀。 由此， 通过设置高温烟气调节阀， 可调节高温 抽气通路 5中的高温烟气的烟气量。
在本发明的一个实施例中， 抽气控制单元 51 进一步包括： 电动或者气动低温烟气 调节阀， 低温烟气调节阀设置在至少一个低温抽气通路 6上。 也就是说， 抽气控制单元 51 可以是电动低温烟气调节阀， 或气动低温烟气调节阀， 当可抽气式煤粉锅炉 100包 括多个低温抽气通路 6时，低温烟气调节阀可为一个且一个低温烟气调节阀设在多个低 温抽气通路 6的其中一个上， 或低温烟气调节阀的个数少于低温抽气通路 6的个数， 低 温烟气调节阀设在多个低温抽气通路 6的其中一些上，或低温烟气调节阀的个数等于低 温抽气通路 6的个数， 多个低温烟气调节阀分别设在多个低温抽气通路 6上。 由此， 通 过设置低温烟气调节阀， 可调节低温抽气通路 6中的低温烟气的烟气量。
可选地， 抽气控制单元 51 控制高压烟气调节阀和低温烟气调节阀中的至少一个， 以使空气通路 4的出口处的空气的温度为 400-1000°C。 也就是说， 抽气控制单元 51还 可具有控制装置 （图未示出） ， 抽气控制单元 51通过控制装置可只控制高压烟气调节 阀， 或只控制低温烟气调节阀， 只要保证将待预热空气通入炉膛 1 1 内的温度为 400-1000°C即可。
在本发明的一个实施例中， 从烟气通道 3的入口端朝向烟气通道 3的出口端依次设 置有屏式过热器 7、 包墙过热器 8。 在图 1的示例中， 在炉膛 1 1和烟气通道 3的连通处 依次设有屏式过热器 7、 包墙过热器 8。
在本发明的一个实施例中， 在靠近烟气通道 3的出口端的烟气通道 3内设置有省煤 器 10。
采用蓄热式旋转换向加热器 2， 交替切换烟气、 空气， 使之流经热载体,能够最大限 度地回收高温烟气的物理热， 从而可大幅度节约能源， 提高热工设备的热效率。 由于进 入炉膛 1 1 的待预热空气温度较高， 通过组织燃烧， 扩展了火焰燃烧区域， 火焰边界几 乎扩展到炉膛 1 1边界， 使得炉内温度分布均匀； 蓄热式旋转换向加热器 2的使用， 使 得低热值的燃料、 低挥发份燃料能借助高温预热的空气可获得稳定、 连续燃烧， 提高燃 料的燃尽率， 扩展了低挥发分燃料的应用范围。 从根本上解决了无烟煤、 贫煤等低挥发 分煤应用过程中的能源系统效率偏低、 动力煤的产品较低、 污染排放较严重等问题； 同 时解决了利用低挥发分发电大型锅炉运行的稳定性和可靠性问题。
在本说明书的描述中， 参考术语 "一个实施例"、 "一些实施例"、 "示意性实施例"、 "示 例"、 "具体示例"、 或 "一些示例"等的描述意指结合该实施例或示例描述的具体特征、 结 构、 材料或者特点包含于本发明的至少一个实施例或示例中。 在本说明书中， 对上述术语 的示意性表述不一定指的是相同的实施例或示例。 而且， 描述的具体特征、 结构、 材料或 者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例， 本领域的普通技术人员可以理解： 在不脱 离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、 修改、 替换和变型， 本发明的范围由权利要求及其等同物限定。

Claims

权利要求书
1、 一种可抽气式煤粉锅炉， 其特征在于， 包括：
锅炉本体， 所述锅炉本体内限定有炉膛；
蓄热式旋转换向加热器， 所述蓄热式旋转换向加热器包括：
换热器主体；
驱动装置， 所述驱动装置用于驱动所述换热器主体绕其中心轴线旋转； 分隔件， 所述分隔件沿着所述中心轴线的方向设置在所述换热器主体内， 且将 所述换热器主体分隔成至少一对容纳部分，所述每对容纳部分相对所述中心轴线成径向 相对设置；
热载体， 所述热载体分别容纳在所述容纳部分中， 所述热载体由非金属固体材 料所形成；
烟气通道， 所述烟气通道的入口端与所述炉膛相连通， 且出口端与所述蓄热式旋转 换向加热器相连通，以将炉膛内产生的烟气通入至少所述成对的所述容纳部分中的一个 内并与其中容纳的所述热载体换热， 所述烟气通道内设置有多个过热器； 以及
空气通路， 所述空气通路用于将空气至少通入所述成对的所述容纳部分中的另一个 内， 以使得其中容纳的所述热载体与所述空气进行换热；
高温抽气通路， 所述高温抽气通路的一端与所述烟气通道的朝向所述炉膛的一端相 连通， 所述高温抽气通路的另一端与所述烟气通道的所述出口端相连通； 以及
抽气控制单元， 所述抽气控制单元用于控制经由所述高温抽气通路供给的第一烟气
2、 根据权利要求 1所述的可抽气式煤粉锅炉， 其特征在于， 进一步包括： 至少一个低温抽气通路， 所述低温抽气通路的一端与所述多个过热器之间的所述烟 气通道部分中的至少一个相连通， 其另一端与所述烟气通道的所述出口端相连通， 其中 所述抽气控制单元用于控制经由所述至少一个低温抽气通路供给的第二烟气量。
3、 根据权利要求 1 所述的可抽气式煤粉锅炉， 其特征在于， 所述热载体具有小球 状、 片状或者多孔状的结构。
4、 根据权利要求 1 所述的可抽气式煤粉锅炉， 其特征在于， 所述煤粉由无烟煤、 贫煤中的至少一种所形成。
5、 根据权利要求 2所述的可抽气式煤粉锅炉， 其特征在于， 所述抽气控制单元包 括电动或者气动高温烟气调节阀， 所述高温烟气调节阀设置在所述高温抽气通路上。
6、 根据权利要求 5 所述的可抽气式煤粉锅炉， 其特征在于， 所述抽气控制单元进 一步包括： 电动或者气动低温烟气调节阀， 所述低温烟气调节阀设置在所述至少一个低 温抽气通路上。
7、 根据权利要求 6所述的可抽气式煤粉锅炉， 其特征在于， 所述抽气控制单元控 制所述高压烟气调节阀和所述低温烟气调节阀中的至少一个，以使所述空气通路的出口 处的所述空气的温度为 400-1000 °C。
8、 根据权利要求 1 所述的可抽气式煤粉锅炉， 其特征在于， 从所述烟气通道的所 述入口端朝向所述烟气通道的所述出口端依次设置有屏式过热器、 包墙过热器。
9、 根据权利要求 1 所述的可抽气式煤粉锅炉， 其特征在于， 在靠近所述烟气通道 的所述出口端的所述烟气通道内设置有省煤器。
PCT/CN2013/075703 2013-01-18 2013-05-16 可抽气式煤粉锅炉 WO2014110885A1 (zh)

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