WO2017088742A1 - Écran d'eau d'une chaudière supercritique à lit fluidisé circulant présentant une grande stabilité d'écoulement à faible charge, et procédé d'obtention d'un faible débit massique - Google Patents

Écran d'eau d'une chaudière supercritique à lit fluidisé circulant présentant une grande stabilité d'écoulement à faible charge, et procédé d'obtention d'un faible débit massique Download PDF

Info

Publication number
WO2017088742A1
WO2017088742A1 PCT/CN2016/106838 CN2016106838W WO2017088742A1 WO 2017088742 A1 WO2017088742 A1 WO 2017088742A1 CN 2016106838 W CN2016106838 W CN 2016106838W WO 2017088742 A1 WO2017088742 A1 WO 2017088742A1
Authority
WO
WIPO (PCT)
Prior art keywords
water
wall
furnace
flow rate
fluidized bed
Prior art date
Application number
PCT/CN2016/106838
Other languages
English (en)
Chinese (zh)
Inventor
徐鹏
胡修奎
巩李明
陈震宇
苏虎
杨雪芬
薛大勇
聂立
薛燕辉
王鹏
Original Assignee
东方电气集团东方锅炉股份有限公司
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
Application filed by 东方电气集团东方锅炉股份有限公司 filed Critical 东方电气集团东方锅炉股份有限公司
Publication of WO2017088742A1 publication Critical patent/WO2017088742A1/fr

Links

Images

Classifications

    • 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
    • F22B37/10—Water tubes; Accessories therefor

Definitions

  • the invention relates to a circulating fluidized bed boiler, in particular to a circulating fluidized bed boiler water wall system with supercritical parameters.
  • the supercritical boiler generator set can obtain higher power generation efficiency.
  • the supercritical circulating fluidized bed boiler refers to the pressure and temperature of the steam output from the boiler is higher than the critical parameter of water vapor (22.12MPa, 374.15 °C).
  • the supercritical boiler water wall system uses a primary DC boiler, that is, the working fluid (water or water vapor) in the water wall passes through the water wall once.
  • the mass flow rate of the working fluid in the water wall is lower than that of the subcritical boiler natural circulation (or forced circulation), the water cooling wall tube is cooled by the working medium, the temperature of the water wall tube metal is higher, and the over temperature damage is prone to occur. problem.
  • the supercritical boiler water wall working fluid is once DC, the water wall working fluid outlet is superheated steam, and the furnace water wall is at different positions, such as the front wall water wall and the side wall water wall. Due to different positions and different lengths, the absorbed heat is different. It will cause the temperature of the working fluid in the water wall tube to be different, causing the temperature of the water wall material to be different. If the temperature difference is not controlled, in the bad case, the thermal stress will be cracked due to the temperature difference, and the water wall tube will be destroyed.
  • the water-cooled wall of the conventional supercritical pulverized coal boiler generally adopts the water-cooled wall structure of the "spiral coil", which reduces the flow area of the water-cooled wall tube, improves the mass flow rate of the working medium in the water-cooled wall tube, and simultaneously the spiral coil passes through the water-cooled wall in turn. Position, try to absorb heat evenly to solve the problem of water wall safety.
  • the mass flow rate of the water wall of the ultra-supercritical pulverized coal boiler is generally greater than 1000 kg/m 2 .s.
  • the circulating fluidized bed boiler has a large amount of circulating material in the furnace, and there is a large amount of adhering downflow material near the wall surface of the water wall.
  • the spiral coil structure water wall is severely worn by the adhering downflow and cannot be used in a circulating fluidized bed boiler.
  • the water cooling wall of the supercritical circulating fluidized bed boiler is arranged by a vertical pipe, and the mass flow rate of the water wall is generally low, generally less than 1000 kg/m 2 .s, which is called “vertical pipe low mass flow rate”.
  • the water-cooled wall system with low mass flow rate uses the "self-compensating property" of the working fluid to distribute the flow rate of the water wall, so that the heat-absorbing tube distributes more flow, enhances the tube cooling, and lowers the tube wall temperature.
  • the inventor of the present invention found in the research that the water-cooled wall of the supercritical CFB boiler with low mass flow rate has a serious problem of poor flow stability under low load: when the boiler is under low load operation, the flow rate of the water wall is reduced.
  • the stability of the flow of the working fluid (water or steam, or a mixture of the two) in the water wall tube is reduced, and is disturbed, for example, external heating is enhanced, or the flow rate is reduced, and the flow velocity of the working medium is liable to change drastically, and the water is heated.
  • Production The raw steam further blocks the waterwall tube, causing a decrease in flow, creating a negative feedback, which ultimately causes the wall temperature to rise.
  • the design of the water-cooled wall of the supercritical CFB boiler with low mass flow rate needs to solve the stability problem of flow at low load and prevent the negative feedback from occurring.
  • how to achieve the design of the water-cooled wall of supercritical CFB boilers with high flow stability under low load conditions under low-mass flow conditions is not disclosed.
  • the water-cooling wall of the super-critical CFB boiler with low mass flow rate adopts a primary-current boiler, that is, the working fluid (water or water vapor) in the water-cooling wall absorbs heat once through the water-cooling wall and is directly heated into superheated steam.
  • the proportion of heat absorption of the water-cooled wall of the supercritical boiler about 36-40%) increases the proportion of heat absorption of the critical water wall (less than 29%), and the water wall system must increase the area to meet the requirements. If no improvement measures are taken, the height of the boiler water wall will increase rapidly, resulting in an increase in boiler cost.
  • the heat transfer in the furnace of the circulating fluidized bed boiler depends on the circulating materials.
  • the water wall and the expansion screen are connected in series, and the water wall system has a high mass flow rate, especially the mass flow rate of the expansion screen.
  • the increase of the mass flow rate has a limited effect on reducing the temperature of the pipe wall, and also increases the resistance of the water wall, increases the energy consumption of the boiler feed water pump, and reduces the economic efficiency of the power plant.
  • the object of the invention is that the water-cooling wall of the supercritical CFB boiler realizes a low mass flow rate, and at the same time solves the problem of increasing the water wall area and the furnace height under the low mass flow rate; in particular, the water-cooling wall of the supercritical CFB boiler which solves the low mass flow rate flows under a low load;
  • the problem of stability degradation prevents the negative feedback of the water wall system from occurring.
  • a method for achieving a low mass flow rate in a water-cooled wall of a supercritical CFB boiler is as follows:
  • the flue gas flow (Q) generated by the combustion is calculated, and then the cross-sectional area of the furnace is obtained from the flue gas flow rate and the flue gas flow rate in the furnace: the main elemental carbon in the fuel (C) Hydrogen (H) Sulfur (S) combustion releases heat and also produces flue gas.
  • the amount of heat released and the amount of smoke produced are known from well-known chemical knowledge.
  • the flue gas flow rate Q can be calculated based on the heat that the steam needs to absorb and the heat generated by the combustion of the fuel.
  • the inner diameter and the number of the water wall tubes constituting the furnace are selected according to the mass flow rate range of 700 to 350 kg/m 2 .s, and the water wall of the furnace is separated by the surrounding water wall and the water cooling partition.
  • the wall is connected in parallel:
  • the inner diameter of the surrounding water wall tube is r1, the number of water wall tubes around the wall is m1, the inner diameter of the water-cooling partition wall tube is r2, and the number of water-cooling partition walls is m2;
  • the number of water-cooled wall tubes m1 and the number of middle partition wall tubes m2 are too small, the flat steel is large in size, and the flat steel temperature will exceed the allowable value.
  • the product of the inner diameter area and the number of water wall tubes is the flow area of the furnace wall.
  • the optimum mass flow rate range is 700 to 350 kg/m 2 .s.
  • the mass flow rate is high.
  • the water flow wall has different deviations in the flow rate of the working fluid, and the temperature difference of the outlet is large. Too low mass flow rate may also cause flow to stop, resulting in heat transfer deterioration.
  • the low mass flow rate can be achieved by the above three steps of the patent, in particular the parallel arrangement of the surrounding water wall and the water cooled partition wall.
  • a water-cooling wall of a supercritical CFB boiler with high flow stability under low load comprising a water-cooled wall and a water-cooled partition wall around the furnace with a low mass flow rate, and a concentrated down pipe and a connecting pipe, the working fluid flows in the surrounding water wall and water cooling
  • the middle partition walls are connected in parallel.
  • the feed water of the boiler is led to the surrounding water wall and the water-cooled partition wall by the concentrated down pipe, and then led to the mixing box by the connecting pipe, and the steam at the outlet of the collecting box is led to the downstream superheater.
  • the inner diameter of the water-cooled wall and the water-cooled partition wall of the furnace is larger than the inner diameter of the lower portion at a steam ratio of more than 50%, and the cross-sectional area of the large inner diameter portion of the tube is 1.05 to 3 times the cross-sectional area of the small inner diameter portion.
  • the supercritical circulating fluidized bed water wall system of the patented device comprises a surrounding water wall and a water cooled partition wall.
  • the surrounding water wall and water-cooled partition walls are already used in boilers with small capacity, especially subcritical parameters.
  • the natural circulation (or forced circulation) water wall system consisting of the steam drum-down pipe-water wall-drum used in the boiler below the subcritical parameter cannot be adopted.
  • the patented water-cooled wall and water-cooled partition wall are designed in parallel to solve the problem of increasing water wall area and furnace height under low mass flow rate.
  • the inventor of the present invention finds that the surrounding water wall and the water-cooled partition wall The problem of low load flow stability unique to supercritical circulating fluidized bed boilers has emerged.
  • the conventional supercritical water wall diameter generally has a large inner diameter and a small inner diameter. This is because the upper working medium has a high temperature, and the use of a smaller inner diameter can increase the flow rate of the steam, enhance the cooling capacity of the pipe wall, and lower the wall temperature.
  • the upper pipe diameter is smaller than the lower portion in order to increase the ability of the pipe to withstand internal pressure. The boiler designer knows that the smaller the pipe diameter, the smaller the required wall thickness under the same pipe internal pressure.
  • the inventors of the present patent found in the study that a supercritical circulating fluidized bed boiler with a low mass flow rate is different from a conventional boiler, and when the stability problem is solved, the conventional method cannot be used.
  • the working fluid water, steam or soda mixture
  • the working fluid in the water-cooled wall and the water-cooled partition wall is heated during the flow, and the volume flow rate is increased as it is heated, in order to achieve a "self-compensating characteristic" of the low mass flow rate, Preventing the water from being heated and vaporized, the generated steam further blocks the water wall tube, causing the flow to decrease, and forming a negative feedback.
  • the inventor of the present invention needs to change according to the specific volume of the working medium in the upper part of the surrounding water wall and the water cooling partition wall.
  • the inner diameter of the tube in the upper part of the water wall and the water-cooling partition wall around the furnace is larger than the inner diameter of the lower part.
  • the position of the upper and lower pipe diameters of the surrounding water wall and water-cooled partition wall pipe should avoid the area where the working medium phase change (from water to steam), so the pipe is enlarged at a position where the steam ratio is more than 50%. path.
  • the cross-sectional area of the upper tube is 1.05 to 3 times the cross-sectional area of the lower tube.
  • the water-cooled partition wall extends from the bottom of the furnace to the top.
  • the cost is greatly increased.
  • the surrounding water wall and the water cooling partition wall disclosed in this patent have many advantages.
  • the prior art expansion screen if the height of the furnace of the supercritical circulating fluidized bed boiler is increased in the upper part of the furnace, the material concentration in the upper part of the furnace is lower, the heat transfer coefficient of the upper part is lowered, and the heat exchange efficiency of the expanded screen is low. To achieve the same amount of heat absorption, more material is needed.
  • the water-cooled partition wall of the patent extends from the bottom of the furnace to the top, and a water-cooled partition wall is arranged in the middle and lower part of the furnace, and the heat transfer coefficient is high, which can save materials.
  • the water-cooled partition wall is disposed on the furnace water wall opposite to the furnace flue gas outlet passage, and the water-cooled partition wall is welded to the furnace water wall at the joint position.
  • the water-cooled partition wall is arranged on the water wall of the furnace opposite to the flue gas outlet passage of the furnace, which is beneficial to the organized flow of the flue gas in the furnace to prevent irregular eddy currents and smoke wear and tear.
  • the water-cooled partition wall and the surrounding water wall are welded and connected, which is beneficial to prevent vibration and deformation of the water-cooled partition wall.
  • the water-cooled partition wall is heated on both sides, and the inner diameter of the tube constituting the water-cooled partition wall is larger than the inner diameter of the tube constituting the water wall around the furnace.
  • the water-cooled partition wall is in the furnace, and the pipe absorbs heat strongly.
  • the preferred method is that the pipe diameter of the water-cooled partition wall is larger than the diameter of the surrounding water wall.
  • the inner diameter of the tube where the water wall around the furnace is bent to form the flue gas outlet passage is larger than the inner diameter of the tube at other locations.
  • the water-cooled partition wall has a different heating length, and the upper portion of the partition wall covers the refractory material for the tube having a short heat absorption length.
  • the width of the water-cooled partition wall does not exceed half the depth of the furnace. This program does not affect the organized flow of smoke in the furnace.
  • a plurality of water-cooled partition walls are arranged, and each water-cooled partition wall is symmetrically arranged on the furnace section.
  • a plurality of water-cooled partition walls may be arranged in the furnace formed by the surrounding water wall, and when the water cooling partition wall is arranged in multiple places, it shall be symmetrically arranged in the furnace, which is favorable for uniform furnace temperature. .
  • a flue gas outlet passage is arranged on both sides of the furnace of the boiler, and a plurality of water-cooled partition walls are arranged between the flue gas outlet passages on both sides and arranged in a row, and a flue gas is left between the water-cooled partition walls. aisle.
  • the invention has the beneficial effects that the water-cooling wall of the supercritical CFB boiler realizes a low mass flow rate, and at the same time solves the problem of increasing the water wall area and the furnace height under the low mass flow rate; in particular, solving the low-temperature flow rate supercritical CFB boiler water wall under low load
  • the problem of reduced flow stability prevents the negative feedback of the water wall system from occurring.
  • FIG. 1 is a schematic structural view of an embodiment of the present invention
  • FIG. 2 is a schematic view showing the arrangement structure of the water-cooled partition wall when the furnace flue gas outlet passage is arranged on both sides of the boiler;
  • 1 is the furnace
  • 2 is the separation device
  • 3 is the economizer
  • 5 is the tail flue
  • 6 is the returning device
  • 8 is the water wall
  • 11 is the surrounding water wall
  • 14 is the sinking box
  • 16 is the concentration
  • the down pipe 17 is a water-cooled partition wall
  • 18 is a flue gas outlet passage
  • 21 is a superheater.
  • a method for achieving a low mass flow rate in a water-cooled wall of a supercritical CFB boiler is as follows:
  • the flue gas flow (Q) generated by the combustion is calculated, and then the cross-sectional area of the furnace is obtained from the flue gas flow rate and the flue gas flow rate in the furnace: the main elemental carbon in the fuel (C) Hydrogen (H) Sulfur (S) combustion releases heat and also produces flue gas.
  • the amount of heat released and the amount of smoke produced are known from well-known chemical knowledge.
  • the flue gas flow rate Q can be calculated based on the heat that the steam needs to absorb and the heat generated by the combustion of the fuel.
  • the circumference (L) of the furnace is obtained according to the cross-sectional area of the furnace and the cross-sectional shape of the designed furnace; if the rectangular section furnace is selected, the length (a) of the furnace of the circulating fluidized bed boiler is comprehensively considered.
  • Proportion, a*b S, determine a, b.
  • Furnace circumference L 2 * (a + b).
  • the inner diameter and the number of the water wall tubes constituting the furnace are selected according to the mass flow rate range of 700 to 350 kg/m 2 .s, and the water wall of the furnace is separated by the surrounding water wall and the water cooling partition.
  • the wall is connected in parallel:
  • the inner diameter of the surrounding water wall tube is r1, the number of water wall tubes around the wall is m1, the inner diameter of the water-cooling partition wall tube is r2, and the number of water-cooling partition walls is m2;
  • a supercritical cycle boiler water wall system comprising a low temperature flow rate (the optimum mass flow rate range of 700 to 350 kg/m 2 .s) is surrounded by a water wall 11 and a water cooled partition wall 17
  • the feed water of the boiler is led from the concentrated downcomer to the water wall 11 and the water cooled partition 17 around the furnace.
  • the working medium is heated in the surrounding water wall 11 and the water-cooling partition wall 17, and the collecting box 14 is mixed by the connecting pipe.
  • the steam at the outlet of the header tank 14 is directed to the downstream superheater 21.
  • the pressure fluctuation and the flow instability caused by the endothermic expansion of the working fluid in the water-cooled wall 11 and the water-cooled partition wall 17 around the furnace are prevented, and the water-cooled wall 11 is formed around the furnace.
  • the inner diameter of the pipe in the upper part of the water-cooling partition wall 17 is larger than the inner diameter of the lower part, and the pipe diameter is increased at a position where the steam ratio is more than 50%, and the cross-sectional area of the upper pipe is 1.05 to 3 times the sectional area of the lower pipe.
  • the water-cooling partition wall 17 is disposed on the furnace water wall 11 facing the furnace flue gas outlet passage 18, and in the contact position, the water-cooling partition wall 17 is welded and connected to the surrounding water wall 11. This connection prevents the water-cooled partition wall 17 from vibrating.
  • the water-cooling partition wall 17 is heated on both sides, that is, the water-cooling partition wall 17 is placed in the furnace, and both sides are not connected and fixed to the surrounding water-cooling wall 11, and the inner diameter of the tube constituting the water-cooling partition wall 17 is larger than the composition furnace.
  • the inner diameter of the tube around which the water-cooling wall 11 is bent to form the flue gas outlet passage 18 is larger than the inner diameter of the tube at other positions.
  • the pipe having a short heat absorption length is covered with a refractory material in the upper portion of the water-cooling partition wall 17 to prevent the low load from being overheated due to the stagnation of the working medium.
  • the width dimension B of the water-cooling partition wall 17 is preferably not more than 0.5 A, that is, not more than half of the depth of the furnace.
  • a plurality of water-cooling partition walls 17 are arranged, they are preferably arranged symmetrically on the section of the furnace, that is, symmetrically arranged left and right along the left and right side walls of the furnace or symmetrically arranged along the front and rear walls.
  • the furnace flue gas outlet passage 18 when the furnace flue gas outlet passage 18 is disposed on both sides of the furnace of the boiler in the furnace chamber (such as the furnace flue gas outlet passage 18 disposed on the left and right sides of FIG. 2), the plurality of water-cooled partition walls 17 are arranged. Arranged in a row between the flue gas outlet passages 18 on both sides. In this case, there are more than 17 water-cooled partition walls, and a flue gas passage should be left between the water-cooled partition walls 17 to balance the flue gas pressure of the furnace.

Abstract

L'invention concerne un écran d'eau d'une chaudière supercritique à lit fluidisé circulant présentant une grande stabilité d'écoulement à faible charge, et un procédé d'obtention d'un faible débit massique. La chaudière à lit fluidisé circulant comprend un écran d'eau environnant (11) et un écran d'eau à cloison médiane (17) d'un four (1) de faible débit massique; et un fluide de travail s'écoule dans l'écran d'eau environnant (11) et l'écran d'eau à cloison médiane (17) reliés en parallèle. Les tubes de l'écran d'eau environnant (11) et de l'écran d'eau à cloison médiane (17) présentent un diamètre intérieur plus grand à des emplacements dont la teneur en vapeur est supérieure à 50% qu'à des emplacements dont la teneur en vapeur est inférieure à 50%, et la partie des tubes de diamètre intérieur plus grand présente une section transversale 1,05 à 3 fois plus grande qu'une zone de section transversale de la partie des tubes présentant le plus petit diamètre intérieur. L'écran d'eau de la chaudière supercritique à lit fluidisé circulant présente un faible débit massique, et résout le problème consistant à devoir augmenter la zone d'écran d'eau et la hauteur du four lorsque le débit massique est faible, tout comme il résout le problème de la stabilité d'écoulement qui est plus faible à faible charge, en empêchant la survenue d'une rétroaction négative dans un système d'écran d'eau.
PCT/CN2016/106838 2015-11-25 2016-11-23 Écran d'eau d'une chaudière supercritique à lit fluidisé circulant présentant une grande stabilité d'écoulement à faible charge, et procédé d'obtention d'un faible débit massique WO2017088742A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510830264.4 2015-11-25
CN201510830264.4A CN105299634B (zh) 2015-11-25 2015-11-25 低负荷下高流动稳定性的超临界循环流化床锅炉水冷壁

Publications (1)

Publication Number Publication Date
WO2017088742A1 true WO2017088742A1 (fr) 2017-06-01

Family

ID=55197213

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2016/106838 WO2017088742A1 (fr) 2015-11-25 2016-11-23 Écran d'eau d'une chaudière supercritique à lit fluidisé circulant présentant une grande stabilité d'écoulement à faible charge, et procédé d'obtention d'un faible débit massique

Country Status (2)

Country Link
CN (1) CN105299634B (fr)
WO (1) WO2017088742A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108534118A (zh) * 2018-03-30 2018-09-14 东方电气集团东方锅炉股份有限公司 一种超临界或超超临界直流锅炉水冷壁结构
CN109611816A (zh) * 2019-01-14 2019-04-12 西安热工研究院有限公司 700℃二次再热卧式侧墙对冲锅炉的水冷壁及工作方法
CN113294774A (zh) * 2021-04-06 2021-08-24 苏州西热节能环保技术有限公司 低温再热器壁温超温的调整方法、系统、存储介质、终端
CN116542172A (zh) * 2023-04-18 2023-08-04 南方电网电力科技股份有限公司 一种锅炉水动力相变点的评估方法、系统和设备

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105299634B (zh) * 2015-11-25 2017-07-28 东方电气集团东方锅炉股份有限公司 低负荷下高流动稳定性的超临界循环流化床锅炉水冷壁
CN105698165B (zh) * 2016-04-15 2018-03-13 东方电气集团东方锅炉股份有限公司 一种循环流化床锅炉的炉膛结构
CN113834090B (zh) * 2021-09-16 2023-03-21 东方电气集团东方锅炉股份有限公司 一种降低超超临界w炉水冷壁壁温差的方法
CN114562717A (zh) * 2022-03-28 2022-05-31 江苏海德利热能设备制造有限公司 一种直流盘管锅炉结构

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2962005A (en) * 1958-05-16 1960-11-29 Babcock & Wilcox Co Forced flow vapor generating unit
US3288117A (en) * 1965-12-01 1966-11-29 Combustion Eng Arrangement of tube circuits in supercritical forced through-flow vapor generator
US3301224A (en) * 1965-12-13 1967-01-31 Combustion Eng Steam generator organization
DE3028240A1 (de) * 1979-08-01 1981-02-05 Mitsubishi Heavy Ind Ltd Druckstroemungs-einmaldurchgangsboiler
CN103353104A (zh) * 2012-10-10 2013-10-16 北京巴布科克·威尔科克斯有限公司 对冲燃烧锅炉低质量流速水循环系统设计方法
CN204063017U (zh) * 2014-07-25 2014-12-31 太原锅炉集团有限公司 一种单面曝光的水冷屏隔墙膜式壁
CN105299634A (zh) * 2015-11-25 2016-02-03 东方电气集团东方锅炉股份有限公司 低负荷下高流动稳定性的超临界循环流化床锅炉水冷壁

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100523606C (zh) * 2006-12-07 2009-08-05 中国科学院工程热物理研究所 带水冷柱的循环流化床锅炉炉膛
CN101749697A (zh) * 2009-12-22 2010-06-23 浙江大学 带大十字贯穿中隔墙结构的循环流化床锅炉炉膛
CN102635854B (zh) * 2012-04-24 2014-11-26 清华大学 一种带缓冲床的大型循环流化床锅炉
CN203628635U (zh) * 2013-11-25 2014-06-04 东方电气集团东方锅炉股份有限公司 超临界循环流化床锅炉

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2962005A (en) * 1958-05-16 1960-11-29 Babcock & Wilcox Co Forced flow vapor generating unit
US3288117A (en) * 1965-12-01 1966-11-29 Combustion Eng Arrangement of tube circuits in supercritical forced through-flow vapor generator
US3301224A (en) * 1965-12-13 1967-01-31 Combustion Eng Steam generator organization
DE3028240A1 (de) * 1979-08-01 1981-02-05 Mitsubishi Heavy Ind Ltd Druckstroemungs-einmaldurchgangsboiler
CN103353104A (zh) * 2012-10-10 2013-10-16 北京巴布科克·威尔科克斯有限公司 对冲燃烧锅炉低质量流速水循环系统设计方法
CN204063017U (zh) * 2014-07-25 2014-12-31 太原锅炉集团有限公司 一种单面曝光的水冷屏隔墙膜式壁
CN105299634A (zh) * 2015-11-25 2016-02-03 东方电气集团东方锅炉股份有限公司 低负荷下高流动稳定性的超临界循环流化床锅炉水冷壁

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108534118A (zh) * 2018-03-30 2018-09-14 东方电气集团东方锅炉股份有限公司 一种超临界或超超临界直流锅炉水冷壁结构
CN108534118B (zh) * 2018-03-30 2023-10-31 东方电气集团东方锅炉股份有限公司 一种超临界或超超临界直流锅炉水冷壁结构
CN109611816A (zh) * 2019-01-14 2019-04-12 西安热工研究院有限公司 700℃二次再热卧式侧墙对冲锅炉的水冷壁及工作方法
CN109611816B (zh) * 2019-01-14 2023-12-19 西安热工研究院有限公司 700℃二次再热卧式侧墙对冲锅炉的水冷壁及工作方法
CN113294774A (zh) * 2021-04-06 2021-08-24 苏州西热节能环保技术有限公司 低温再热器壁温超温的调整方法、系统、存储介质、终端
CN116542172A (zh) * 2023-04-18 2023-08-04 南方电网电力科技股份有限公司 一种锅炉水动力相变点的评估方法、系统和设备

Also Published As

Publication number Publication date
CN105299634B (zh) 2017-07-28
CN105299634A (zh) 2016-02-03

Similar Documents

Publication Publication Date Title
WO2017088742A1 (fr) Écran d'eau d'une chaudière supercritique à lit fluidisé circulant présentant une grande stabilité d'écoulement à faible charge, et procédé d'obtention d'un faible débit massique
CN102889570B (zh) 一种具有两次再热器的塔式锅炉
US9488370B2 (en) Arrangement structure suitable for inverted pulverized coal boiler with ultra-high steam temperature steam parameters
US8904790B2 (en) M-type pulverized coal boiler suitable for ultrahigh steam temperature
JP4242564B2 (ja) 化石燃料用ボイラ
CN201327013Y (zh) 一种100t/h燃油或燃气注汽锅炉
CN202881214U (zh) 一种气化炉
CN105805735A (zh) 带尾部扩展受热面的超临界循环流化床锅炉和尾部烟道
JP4489307B2 (ja) 化石燃料貫流ボイラ
US8555820B2 (en) Boiler
CN103727519A (zh) 一种防止省煤器受热面低温腐蚀的装置
CN108591986B (zh) 一种蒸汽发生器
CN205897096U (zh) 循环流化床锅炉炉膛屏式受热面布置结构
JP2016529467A (ja) ツーパスボイラ構造を備える連続流動蒸気発生器
CN211625215U (zh) 一种蒸汽过热器
CN105318307A (zh) 一种双锅筒横置式沉降室喷淋脱硝角管锅炉
CN210179588U (zh) 超临界二氧化碳塔式锅炉炉墙受热面布置结构
CN205299491U (zh) 低负荷下高流动稳定性的超临界循环流化床锅炉水冷壁
JP4463825B2 (ja) 貫流ボイラ
CN105318309B (zh) 一种双锅筒喷淋脱硝沉降分离角管锅炉
CN203656895U (zh) 一种防止省煤器受热面低温腐蚀的装置
JP5709995B2 (ja) 強制貫流蒸気発生器
CN208025489U (zh) 一种全膜式壁锅炉水冷壁循环结构
CN220793122U (zh) 一种流化床锅炉水冷系统
WO2013024201A1 (fr) Amélioration d'un transfert de chaleur d'un lit fluidisé vers une conduite d'échangeur de chaleur

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16867965

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 16867965

Country of ref document: EP

Kind code of ref document: A1