CN107355807B - Optimization method for air distribution mode of W-shaped flame boiler - Google Patents

Optimization method for air distribution mode of W-shaped flame boiler Download PDF

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CN107355807B
CN107355807B CN201610389050.2A CN201610389050A CN107355807B CN 107355807 B CN107355807 B CN 107355807B CN 201610389050 A CN201610389050 A CN 201610389050A CN 107355807 B CN107355807 B CN 107355807B
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combustor
coal
boiler
burner
flue gas
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CN107355807A (en
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刘彦鹏
张志刚
张新
陈坤洋
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China Datang Corp Science and Technology Research Institute Co Ltd
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    • 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
    • F23L9/00—Passages or apertures for delivering secondary air for completing combustion of fuel 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C5/00—Disposition of burners with respect to the combustion chamber or to one another; Mounting of burners in combustion apparatus
    • F23C5/08—Disposition of burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K1/00—Preparation of lump or pulverulent fuel in readiness for delivery to combustion apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M5/00—Casings; Linings; Walls
    • F23M5/08—Cooling thereof; Tube walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N3/00—Regulating air supply or draught
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2201/00—Staged combustion
    • F23C2201/30—Staged fuel supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K2201/00—Pretreatment of solid fuel
    • F23K2201/10—Pulverizing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2239/00—Fuels
    • F23N2239/02—Solid fuels
    • 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

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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)

Abstract

The invention relates to a W-shaped flame boiler air distribution mode optimization method, which analyzes the acquired operation condition of a boiler and determines that the downdip angle of F wind and the opening degree of D, E wind are as follows: and (4) rear wall: f, wind declination angle: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5; front wall: f, wind declination angle: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5. The invention improves the combustion condition in the furnace, reduces the carbon content of fly ash while reducing CO.

Description

Optimization method for air distribution mode of W-shaped flame boiler
Technical Field
The invention relates to an optimization method for an air distribution mode of a W-shaped flame boiler.
Background
Currently, the W-type flame boiler exposes some problems, among which poor combustion stability is one of the important problems. During operation, when high-load operation oxygen content is high (O2 is more than 2%), a fire detection signal begins to flicker, the combustion condition is worsened, and therefore the unit needs to operate at low oxygen under high load, the carbon content of CO and fly ash is higher, and the boiler efficiency is low. The reasons for poor combustion stability include two main points: firstly, when the boiler is in high load, the primary air jet flow speed is high, the ignition point moves downwards, flame and secondary air are mixed early, the flame becomes unstable, the negative pressure fluctuation of a hearth is increased, and a fire detection signal becomes unstable; secondly, when the load is high, the secondary air quantity in the furnace is increased, excessive secondary air is mixed into primary pulverized coal airflow which is not ignited in time, and the flame also becomes unstable. The secondary air of the F layer under the arch accounts for 50-60% of the total air volume of the secondary air, the secondary air is horizontally fed in by the original design, the F air is vertically and violently mixed with the insufficient coal dust airflow during combustion, and the coal dust is easy to catch fire and is unstable during combustion. Therefore, the negative pressure fluctuation of the hearth is easily caused by adding wind under high load, the boiler is forced to operate under low oxygen, larger heat losses of q3 and q4 are caused, and the efficiency of the boiler is lower. The secondary air of the F layer under the arch is horizontally fed to block the downward flow of the primary coal dust, so that the airflow stroke of the coal dust is insufficient, the downward backflow area of the arch is small, and the lower hearth is not fully utilized. If the secondary air of the F layer is sent into the hearth by a certain angle of declination, the problems can be effectively solved, so the declination technology of the secondary air of the W flame boiler is developed.
As shown in figure 1, the W flame boiler is mainly technically characterized in that a double-cyclone separation type burner is combined with a double-inlet double-outlet positive pressure direct-blowing powder making system. The double-cyclone separation type burner is vertically arranged on an arch and mainly comprises a coal powder input pipe, a grid separator, a double-cyclone cylinder, a light coal powder airflow pipe, a despin blade and the like. The primary coal dust airflow passes through the coal dust input pipe, is uniformly divided into two parts by the grid separator, and enters the two cyclones. In each cyclone, two thick and thin coal powder air flows are formed under the action of inertial separation and vertically enter a hearth through a nozzle of the cyclone and an outlet of a thin coal powder air flow pipe. The secondary air is divided into an arch upper part and an arch lower part. The secondary air on the arch accounts for about 30 percent of the total amount of the secondary air, and annular secondary air is formed beside the dense-dilute airflow and is sprayed into the hearth. The secondary air under the arch accounts for about 70% of the total amount of the secondary air, and is supplied to the hearth in three stages through a slit type nozzle formed between the vertical water cooling walls. The structure is shown in fig. 2.
In view of the above-mentioned defects, the present designer is actively making research and innovation to create an optimization method for the air distribution mode of the W-type flame boiler, so that the optimization method has industrial utilization value.
Disclosure of Invention
In order to solve the technical problems, the invention aims to provide the optimization method for the air distribution mode of the W-shaped flame boiler, which solves the technical problems of poor burnout performance and poor stability under high load of the W-shaped flame boiler and improves the burnout rate of pulverized coal.
The invention relates to a method for optimizing the air distribution mode of a W-shaped flame boiler, wherein a front wall and a rear wall form an arch inwards at the position of 1/3 th of a hearth, and 2 multiplied by 12 double-cyclone burners are arranged on the arch; secondary air chambers are arranged on the front wall and the rear wall of the lower hearth and are divided into an arch-up secondary air chamber and an arch-down secondary air chamber through partition plates, the arch-down secondary air chamber is divided into independent secondary air chambers by longitudinal partition plates according to the positions and the number of burners, and twelve independent air chambers are respectively arranged on the front wall and the rear wall; the double-cyclone burners are in one-to-one correspondence with the independent air chambers, wherein the front wall sequentially comprises a burner C1, a burner B1, a burner C2, a burner B2, a burner C3, a burner B3, a burner C4, a burner B4, a burner C5, a burner B5, a burner C6 and a burner B6 from left to right; the rear wall comprises a combustor D1, a combustor A1, a combustor D2, a combustor A2, a combustor D3, a combustor A3, a combustor D4, a combustor A4, a combustor D5, a combustor A5, a combustor D6 and a combustor A6 from left to right in sequence; the secondary air under the arch is divided into three parts of an upper part (D), a middle part (E) and a lower part (F) in the vertical direction, the flow of each part of secondary air is adjusted by a baffle, and the air quantity is controlled by different baffles (A, B, C, D, E, F) in the circulating secondary air box on the arch of the hearth;
the formula optimization specifically comprises the following steps:
acquiring the operation conditions of the boiler at different F-layer secondary air declination angles under the preset coal types and loads, wherein the operation conditions at least comprise the following steps: NOx, CO, O2 of the economizer outlet flue gas; NOx, CO, O2 of the air preheater outlet flue gas; the thermal efficiency of the boiler; coal as fired industry, element analysis; sampling and analyzing fly ash and slag; the temperature of the flue gas at the outlet of the economizer; the temperature of the flue gas at the outlet of the air preheater; sampling raw coal; ambient temperature, humidity and atmospheric pressure;
analyzing the obtained operation condition of the boiler, and determining the downdip angle of the F wind and the opening degree of D, E wind as follows:
and (4) rear wall: f wind declination angles of the burner D1, the burner a1, the burner D2, the burner a2, the burner D3, the burner A3, the burner D4, the burner a4, the burner D5, the burner a5, the burner D6 and the burner A6 respectively from left to right: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5;
front wall: f wind declination angles of the combustor C1, the combustor B1, the combustor C2, the combustor B2, the combustor C3, the combustor B3, the combustor C4, the combustor B4, the combustor C5, the combustor B5, the combustor C6 and the combustor B6 are respectively corresponding from left to right: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5.
Further, under the predetermined load, the different downward inclination angles of the F wind specifically include: (1) under 325MW load, the F-wind down angle is 0 °, 10 °, 15 °, 20 °, 30 ° lower boiler operating conditions; (2) under 300MW load, the F-wind down angles of 5 °, 10 °, 20 °, 30 ° lower boiler operating conditions; (3) under 260MW load, the F wind down angles of 5 °, 10 °, 20 °, and 30 ° lower boiler operating conditions.
Furthermore, the arch is provided with SOFA nozzles, four front walls and four rear walls are arranged, three of the front walls and three of the rear walls are oppositely flushed, and the right side of the front wall and the left side of the rear wall are respectively provided with one nozzle.
Further, the W-shaped flame boiler adopts a staged combustion mode to combust coal, and specifically comprises: selecting combustible coal and anthracite in a preset proportion, and reacting the combustible coal with oxygen to form first-stage combustion; the anthracite is ignited under the high-temperature smoke atmosphere formed in the first stage to form second-stage combustion, wherein the content of volatile components of the inflammable coal is higher than that of the anthracite, the content of the volatile components is more than 25%, and the ratio of the bituminous coal to the anthracite is more than 1: 1.
Furthermore, the ratio of the bituminous coal to the anthracite coal is 3: 1.
Furthermore, the content of ash-free base volatile components of the dried coal as fired is kept to be more than 15 percent and less than Vdaf and less than 20 percent, the low-level heating value of the coal as fired is kept to be more than 20MJ/kg and less than Qnet, ar is less than 22.5MJ/kg, and the Vdaf is more than 10 percent when bituminous coal, lean coal and anthracite are combusted in a grading way.
Furthermore, the W-shaped flame boiler is provided with four coal mills, wherein the first coal mill and the third coal mill are used for grinding anthracite, the second coal mill and the fourth coal mill are used for grinding coal mixture of bituminous coal and anthracite, the grinding outlet temperatures of the first coal mill and the third coal mill are 118 ℃, and the grinding outlet temperature of the third coal mill is 109 ℃.
Furthermore, 4 ventilation gaps are longitudinally formed in the wing wall to blow secondary air inwards, the outer diameter of a water wall tube at the wing wall is 120.65mm, the center distance is 146.4mm, the tube gap of the water wall tube is 25.4mm, the outer diameter of the upper tube and the lower tube at the wing wall is 69.85mm, the water wall tube and the upper tube and the lower tube at the wing wall are connected through a reducer tube, the outer diameter of the water wall tube at four ventilation bands for ventilation is less than 120.65mm, the tube gap of the water wall tube at the four ventilation bands for ventilation is 76.55mm, and the height of each ventilation band is set to be the total length of the wing wall tube or is arranged at the upper half part of the wing wall. Further, the calculation formula of the boiler thermal efficiency is as follows:
Figure GDA0001124677180000041
in the formula:
ηg-boiler thermal efficiency,%;
Hf-fuel application base lower heating value, kJ/kg;
b-corresponds to the total input physical heat of each kilogram of fuel entering the furnace, kJ/kg;
l is the total heat loss of each kilogram of boiler fuel, and is calculated according to the condition of the boiler according to the following formula:
L＝LUC+L'G+Lmf+LH+LMA+Lco+Lβ+LUN
LUC-heat loss of unburned carbon in ash, kJ/kg;
L'G-dry flue gas heat loss, kJ/kg;
Lmf-heat loss due to moisture in the fuel entering the furnace, kJ/kg;
LHheat loss due to moisture formation from hydrogen combustion, kJ/kg；
LMAHeat loss due to moisture in the air, kJ/kg;
LCOheat loss due to the formation of carbon monoxide, kJ/kg;
Lβ-heat losses by surface radiation and convection, kJ/kg;
LUNnot measurable heat loss (constant according to the boiler plant design value), kJ/kg.
Furthermore, a grid method is adopted for measuring NOx, CO and O2 of the flue gas at the outlet of the economizer, five measuring points are taken in each side of the flue, each flue is mixed into a flue gas sample for analysis, the arithmetic mean value of the flue gas components at the outlet of the air preheater at each side is taken, and the arithmetic mean value of 2 flues is taken as the boiler exhaust flue gas components;
the measurement of NOx, CO and O2 of the flue gas at the outlet of the air preheater also adopts a grid method, five measuring points are taken by each side of flue, each flue is mixed into a flue gas sample for analysis, the arithmetic mean value of the flue gas components at the outlet of the air preheater at each side is taken, and the arithmetic mean value of 2 flues is taken as the boiler exhaust flue gas components;
the exit flue gas temperature of the economizer is measured by adopting a grid method, and the arithmetic mean of each measuring point at each side is taken as the exit average flue gas temperature;
the flue gas temperature at the outlet of the air preheater is measured by adopting a grid method, 2 flues are totally adopted, and the arithmetic mean value of the measurement points is taken as the average flue gas temperature at the outlet of the air preheater at each side.
By the scheme, the invention at least has the following advantages:
(1) the wind direction of secondary air entering the hearth under the arch is adjusted. When the actual coal quality for combustion of the boiler deviates from the design value, the optimal secondary air inclination angle under the arch can be determined according to different coal qualities, so that high pulverized coal combustion heat efficiency can be obtained, and the phenomenon that the flame scours the cold ash bucket due to overlarge inclination angle to cause serious slag bonding of a hearth can be prevented. The secondary air enters the hearth at a proper inclination angle, so that the flame stroke can be prolonged, the flame fullness of the lower hearth is enhanced, and the burnout effect of the pulverized coal can be improved.
(2) The secondary air under the arch is sent into the hearth along a certain inclination angle, so that the early encounter of primary pulverized coal airflow and the secondary air under the arch is delayed, and the collision of the secondary air on the front wall and the rear wall under the arch is delayed, so that the combustion stability of the boiler is ensured; the total air supply quantity can be greatly improved, the problem of difficult air supply under high load of the boiler can be effectively solved, the heat loss caused by incomplete combustion of gas and solid due to low running air quantity of the boiler is reduced, the CO content in flue gas is reduced to 0, the combustible substance of fly ash is reduced, and the heat efficiency of the boiler can be improved.
(3) The W-shaped flame furnace adopting the technology improves the adaptability of coal types and improves the combustion stability of the boiler under high load.
The foregoing description is only an overview of the technical solutions of the present invention, and in order to make the technical solutions of the present invention more clearly understood and to implement them in accordance with the contents of the description, the following detailed description is given with reference to the preferred embodiments of the present invention and the accompanying drawings.
Drawings
FIG. 1 is a diagram of a W flame boiler combustion mechanism;
FIG. 2 is a schematic view of a W-flame boiler;
FIG. 3 is a schematic view of the burner arrangement on the crown of the furnace of the present invention;
FIG. 4 is a schematic view of an under-arch overfire air jet arrangement;
FIG. 5 is a front sectional view of the overall structure of the downdip secondary air device of the present invention;
FIG. 6 is a schematic structural view of an under-arch secondary air inclination angle oscillating device according to the present invention;
FIG. 7 is a sectional view A-A of the individual plenum of the present invention;
FIG. 8 is a schematic view of the mounting of the adjustment blade, adjustment arm and pivot shaft of the present invention;
FIG. 9 is a schematic view of the linkage of the pull rod, pivot arm, adjustment arm and link of the present invention;
the device comprises a combustor 1, a partition plate 2, a first adjusting blade 3, a lower secondary air chamber 4, a connecting rod 5, a pull rod 6, a flow equalizing pore plate 7, an adjusting arm 8, a rotating arm 9, a back-pull water wall tube 10, a vertical water wall tube 11, a hearth 12, a first longitudinal partition plate 13, a transverse partition plate 14, a second longitudinal partition plate 15, a second adjusting blade 16, a third longitudinal partition plate 17, a fourth longitudinal partition plate 18, a rotating shaft 19, a side-pull water wall tube 20, a wide seam air chamber 21, a narrow seam air chamber 22, a pin hole 24 and a sliding groove 25.
Detailed Description
The following detailed description of embodiments of the present invention is provided in connection with the accompanying drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
As shown in fig. 1 to 8, at about 1/3 of the height of the furnace, the front wall and the rear wall form an inward furnace arch, and 2 × 12 double-cyclone burners are arranged on the arch, wherein the front wall sequentially comprises a burner C1, a burner B1, a burner C2, a burner B2, a burner C3, a burner B3, a burner C4, a burner B4, a burner C5, a burner B5, a burner C6 and a burner B6 from left to right; the rear wall comprises a combustor D1, a combustor A1, a combustor D2, a combustor A2, a combustor D3, a combustor A3, a combustor D4, a combustor A4, a combustor D5, a combustor A5, a combustor D6 and a combustor A6 from left to right. The double-cyclone burner consists of a lattice bar distribution box, two cyclones, two main combustion nozzles, two exhaust gas baffles, two exhaust gas nozzles and corresponding pipelines. After the primary air-powder mixture enters the lattice bar distribution box through the pipeline, the primary air-powder mixture is divided into two equal jet flows which respectively enter the two cyclones along the tangential direction, the fuel is separated out under the action of centrifugal force, the concentration of the coal powder is adjusted through an exhaust baffle arranged in an exhaust pipe, and the rotation strength is adjusted through a despin blade arranged in a main burner. The combustion-supporting secondary air from the annular header is divided into arch top air and arch bottom water-cooled wall vertical wall surface air. The arch top wind is divided into three parts: one is fed into the furnace through a nozzle concentric with the exhaust gas nozzle (A), the other is fed into the furnace through a nozzle concentric with the main burner (B), and the other is provided with an oil gun for combustion-supporting ignition (C). The secondary air under the arch is divided into three parts of upper (D), middle (E) and lower (F) in the vertical direction. The G baffle is used for controlling the wing wall to prevent coking wind. The flow of each secondary air can be adjusted by a baffle. The upper part of the hearth is provided with a screen type superheater, the upper part of the flame folding angle and the vestibule are provided with a high-temperature superheater and a high-temperature reheater, and the temperature of the reheated steam is adjusted by a flue gas baffle. Each furnace air and smoke system is provided with two three-bin rotary air preheaters, two movable blade adjustable axial-flow blowers and two movable blade adjustable axial-flow induced fans; the secondary air adopts a graded air supply mode, and the air quantity is controlled by different baffles (A, B, C, D, E, F) in the circulating secondary air box on the arch of the hearth.
As shown in fig. 3 to 8, the method for optimizing the air distribution mode of the W-type flame boiler of the embodiment has a device that the secondary air under the arch can swing at an inclination angle, and can solve the problems that the inclination angle of the secondary air under the arch cannot be adjusted after the coal quality changes, and the secondary air cannot enter the hearth according to the inclination angle of the guide vanes, so that the burnout rate of pulverized coal is difficult to improve. Comprises a pull rod, an adjusting arm, an adjusting blade and a longitudinal clapboard.
The front wall and the rear wall of the lower hearth are provided with secondary air chambers which are divided into an arch-up secondary air chamber and an arch-down secondary air chamber by partition plates. In the secondary air chamber under the arch, the longitudinal baffle plates are used to separate the secondary air chamber according to the position and number of the burners to form an independent secondary air chamber, and twelve independent air chambers are arranged on the front wall and the rear wall.
As shown in fig. 3, in the independent air chamber corresponding to each burner, the front wall sequentially comprises a burner C1, a burner B1, a burner C2, a burner B2, a burner C3, a burner B3, a burner C4, a burner B4, a burner C5, a burner B5, a burner C6 and a burner B6 from left to right; the rear wall comprises a combustor D1, a combustor A1, a combustor D2, a combustor A2, a combustor D3, a combustor A3, a combustor D4, a combustor A4, a combustor D5, a combustor A5, a combustor D6 and a combustor A6 from left to right in sequence;
in the independent air chamber corresponding to each combustor, a rectangular nozzle is formed between the back-pull water wall tube and two adjacent vertical water wall tubes. Eight adjusting blades are arranged in each air chamber along the height direction of the hearth, and the adjusting blades are arranged on the rotating shaft. The middle position of each adjusting blade is connected with the rotating shaft 19 through a bolt. The rotating shafts in the same independent air chamber at the same height penetrate through the first, second, third and fourth longitudinal partition plates to connect the adjusting blades in each air chamber, and are arranged in the air chambers through the rotating shafts, so that eight rotating shafts are arranged in each air chamber along the height direction of the hearth. Each rotating shaft 19 is fixedly connected with an adjusting arm 8, and the adjusting arms 8 are connected with the connecting rods 5 through hinges to connect the eight rotating shafts 19. A rotating arm 9 is mounted on one of the rotating shafts 19, and a pull rod 6 is connected to the rotating arm 9. The pull rod 6 is connected with the rotating arm 9 through a hinge, a sliding groove 25 is arranged at the hinged part of the rotating arm 9 and the pull rod 6, and a pin hole 24 is arranged at the connecting part of the end part of the pull rod 6 and the rotating arm 9.
And when the actual coal quality for combustion of the boiler deviates from the design value, adjusting the inclination angle of the secondary air under the arch according to different coal qualities.
The secondary air chamber under the W-shaped flame furnace arch is provided with a swing device for adjusting the inclination angle of the blades, so that the air direction of the secondary air under the arch entering the hearth is adjusted. When the actual coal quality for combustion of the boiler deviates from the design value, the optimal secondary air inclination angle under the arch can be determined according to different coal qualities, so that high pulverized coal combustion efficiency can be obtained, and the serious slag bonding of a hearth caused by the fact that flame scours a cold ash hopper due to overlarge declination angle can be prevented. The secondary air enters the hearth at a proper inclination angle, so that the flame stroke can be prolonged, the flame fullness of the lower hearth is enhanced, and the burnout effect of the pulverized coal can be improved.
Example 1
As shown in fig. 3, the method for optimizing the air distribution mode of the W-type flame boiler of the embodiment is characterized in that at about 1/3 of the height of the furnace, a front wall and a rear wall form an arch inwards, and 2 × 12 double-cyclone burners are arranged on the arch; secondary air chambers are arranged on the front wall and the rear wall of the lower hearth and are divided into an arch-up secondary air chamber and an arch-down secondary air chamber through partition plates, the arch-down secondary air chamber is divided into independent secondary air chambers by longitudinal partition plates according to the positions and the number of burners, and twelve independent air chambers are respectively arranged on the front wall and the rear wall; the double-cyclone burners are in one-to-one correspondence with the independent air chambers, wherein the front wall sequentially comprises a burner C1, a burner B1, a burner C2, a burner B2, a burner C3, a burner B3, a burner C4, a burner B4, a burner C5, a burner B5, a burner C6 and a burner B6 from left to right; the rear wall comprises a combustor D1, a combustor A1, a combustor D2, a combustor A2, a combustor D3, a combustor A3, a combustor D4, a combustor A4, a combustor D5, a combustor A5, a combustor D6 and a combustor A6 from left to right in sequence; the secondary air under the arch is divided into three parts of an upper part (D), a middle part (E) and a lower part (F) in the vertical direction, the flow of each part of secondary air is adjusted by a baffle, and the air quantity is controlled by different baffles (A, B, C, D, E, F) in the circulating secondary air box on the arch of the hearth;
the formula optimization specifically comprises the following steps:
acquiring the operation conditions of the boiler at different F-layer secondary air declination angles under the preset coal types and loads, wherein the operation conditions at least comprise the following steps: NOx, CO, O2 of the economizer outlet flue gas; NOx, CO, O2 of the air preheater outlet flue gas; the thermal efficiency of the boiler; coal as fired industry, element analysis; sampling and analyzing fly ash and slag; the temperature of the flue gas at the outlet of the economizer; the temperature of the flue gas at the outlet of the air preheater; sampling raw coal; ambient temperature, humidity and atmospheric pressure;
analyzing the obtained operation condition of the boiler, and determining the downdip angle of the F wind and the opening degree of D, E wind as follows:
and (4) rear wall: f wind declination angles of the burner D1, the burner a1, the burner D2, the burner a2, the burner D3, the burner A3, the burner D4, the burner a4, the burner D5, the burner a5, the burner D6 and the burner A6 respectively from left to right: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5;
front wall: f wind declination angles of the combustor C1, the combustor B1, the combustor C2, the combustor B2, the combustor C3, the combustor B3, the combustor C4, the combustor B4, the combustor C5, the combustor B5, the combustor C6 and the combustor B6 are respectively corresponding from left to right: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5.
Namely the following table:
Figure GDA0001124677180000091
example 2
In the method for optimizing the air distribution mode of the W-shaped flame boiler, on the basis of the embodiment 1, the arch is provided with SOFA nozzles, four front walls and four rear walls are arranged, three of the SOFA nozzles are arranged in a three-to-three opposite direction, and the right side of the front wall and the left side of the rear wall are respectively provided with one nozzle.
Because the boiler reheater has more serious overtemperature phenomenon, the mode of stopping the operation of the nozzle in an overtemperature area is adopted to solve the overtemperature problem of the reheater in normal time operation.
The energy in the middle position of the boiler is considered to be concentrated, and the symptom is relieved by adjusting the declination angle of the F wind and the air distribution of the F wind.
The downdip angle of the F wind and the opening degree of the D, E wind adopt the formula modes described in the following table, and the operation mode has better effects on reducing the wall temperature of the reheater and reducing the carbon content of fly ash.
The F-layer secondary air downward-inclination adjustable diversion baffle has an obvious effect on reducing the carbon content of fly ash, the effect is better when the load is larger, the carbon content of 30-degree fly ash under F air at 325MW load can be reduced by 10.82%, the carbon content of 20-degree fly ash under F air at 300MW load can be reduced by 3.13%, the carbon content of 20-degree fly ash under F air at 260MW load can be reduced by 2.72%, and if the whole is adjusted, the effect of 20-degree downward inclination on reducing the carbon content of fly ash is better.
Example 3
In the method for optimizing the air distribution mode of the W-shaped flame boiler of this embodiment, the W-shaped flame boiler combusts coal types in a staged combustion mode, and specifically includes: selecting combustible coal and anthracite in a preset proportion, and reacting the combustible coal with oxygen to form first-stage combustion; the anthracite is ignited under the high-temperature smoke atmosphere formed in the first stage to form second-stage combustion, wherein the content of volatile components of the inflammable coal is higher than that of the anthracite, the content of the volatile components is more than 25%, and the ratio of the bituminous coal to the anthracite is more than 1: 1. Preferably, the ratio of the bituminous coal to the anthracite coal is 3: 1.
In this embodiment, the W-type flame boiler is provided with four coal mills, the first coal mill and the third coal mill are used for grinding anthracite, the second coal mill and the fourth coal mill are used for grinding coal mixture of bituminous coal and anthracite, the mill outlet temperatures of the first coal mill and the third coal mill are 118 ℃, and the mill outlet temperature of the third coal mill is 109 ℃. The volatile content of the dry ash-free base of the coal as fired is kept to be more than 15 percent and less than Vdaf and less than 20 percent, the low-level heating value of the coal as fired is kept to be more than 20MJ/kg and less than Qnet, ar is less than 22.5MJ/kg, and the Vdaf is more than 10 percent when bituminous coal, lean coal and anthracite are combusted in a grading way.
In the embodiment, the characteristics of anthracite for burning and long ignition distance of the W-shaped flame boiler are fully utilized, and a certain amount of combustible coal is proportioned, so that the characteristics of high volatile component, small activation energy and low ignition temperature of the combustible coal are fully utilized in the initial combustion stage, the combustible coal quickly reaches the ignition point and reacts with oxygen to form first-stage combustion; the high-temperature flue gas atmosphere formed in the first stage is wrapped by the high-temperature flue gas to ignite anthracite with higher ignition point and low volatile component, so that the second-stage combustion is formed.
Example 4
The method for optimizing the air distribution mode of the W-shaped flame boiler is based on the embodiment 1 and aims to improve the coking condition of the lower hearth of the boiler. The wing wall is vertically opened 4 ventilation gaps and is inwards blown with secondary air, the outer diameter of a water-cooled wall pipe at the wing wall is 120.65mm, the center distance is 146.4mm, the pipe gap is 25.4mm, the outer diameter of the upper pipe and the lower pipe of the wing wall is 69.85mm, two ends of the water-cooled wall pipe at the wing wall are connected through a reducer pipe, thick pipes at four ventilated ventilating belts are replaced by thin pipes, the pipe gap is 76.55mm, and the height of each ventilating belt is set to be the total length of the wing wall pipe or is arranged at the upper half part of the wing wall.
The wing wall is vertically opened 4 ventilation gaps and is inwards blown with secondary air, the outer diameter of the water wall pipe at the wing wall is large (120.65mm), the center distance is 146.4mm, the pipe gap is 25.4mm, the outer diameters of the upper part and the lower part of the wing wall are small (69.85mm), the two ends of the original design are connected through a reducer pipe, only a thick pipe at the position of four ventilation belts needing ventilation is required to be replaced by a thin pipe (the large and small ends of the upper part are moved downwards), the pipe gap can be widened to 76.55mm, the ventilation effect is good, large-area coking of the water wall pipe of the wing wall can be prevented, and the optimized scheme for preventing the wing wall from being burnt and blown is increased. The height of the ventilation belt can be set to be the total length of the pipe of the wing wall, and can also be only set in the upper half part of the wing wall, and the effect is more obvious when the ventilation belt is longer.
By adopting the method, the wing wall burning guarding belt does not need to be removed in a large area, and only 1 burning guarding belt on each of the two sides of the ventilation groove needs to be removed, so that the influence on the combustion is small. In the scheme, after the positions of the upper large head and the lower large head are moved downwards, the light pipes with the same specification can be directly used according to water circulation calculation and analysis, and the water circulation calculation is safe.
Reducing the laying area of burning guarding belt
According to the similarity theory, the suggestion of treating the wing wall burning defending zone is as follows: the wing wall pipe water circulation is safe; if the wing wall burning-protecting belt is removed, the temperature of the fin end of the fin is close to 600 ℃, and the fin is easily damaged due to overheating. The refractory belts are generally not removed from the long term safety of the boiler.
Sanitary burning area improvement scheme I
According to the actual operation boiler design and operation experience of a plurality of domestic boilers and the condition that coal quality is operated in the future (Vdaf is more than or equal to 15%) in the project, a guard burning zone transformation scheme is implemented (the area of the guard burning zone is related to the lowest oil-throwing-free stable burning load, and the area of the guard burning zone and the minimum oil-throwing-free stable burning load are in an inverse proportion relation). The minimum fuel-throwing-free stable combustion load is estimated to be less than or equal to 45 percent of BMCR.
Sanitary burning area improvement scheme II
If the coal quality is operated in the future (Vdaf is less than or equal to 12%), the scheme II can be referred to for the guard burning zone modification (the area of the guard burning zone is related to the lowest oil-free stable burning load, and the area and the minimum oil-free stable burning load are in an inverse relation). The estimated minimum fuel-injection-free stable combustion load is less than or equal to 40 percent BMCR
Sanitary burning area improvement scheme III
If the coal quality (Vdaf is less than or equal to 12%) is operated in the future of the project, the actual multi-side consideration of the owner is combined, the guard burning zone can be transformed according to the third scheme (the area of the guard burning zone is related to the lowest oil-free and combustion-stable load, and the area of the guard burning zone and the lowest oil-free and combustion-stable load are in an inverse proportion relation), and the lowest oil-free and combustion-stable load is estimated to be less than or equal to 40%.
The coking condition of the boiler is obviously improved after the implementation. The original wing wall is not coked in a large block any more, and only loose coke blocks with the thickness less than 50mm exist, so that the safe operation of the unit is not threatened. The coking condition of the front wall and the rear wall is greatly improved, and the thickness of the coke block is obviously reduced. NOx emissions also decrease.
In the embodiments, the measurement of NOx, CO and O2 of the flue gas at the outlet of the economizer adopts a grid method, five measuring points are taken in each side flue, each flue is mixed into a flue gas sample for analysis, the arithmetic mean value of the flue gas components at the outlet of the air preheater at each side is taken, and the arithmetic mean value of 2 flues is taken as the boiler exhaust flue gas components;
the measurement of NOx, CO and O2 of the flue gas at the outlet of the air preheater also adopts a grid method, five measuring points are taken by each side of flue, each flue is mixed into a flue gas sample for analysis, the arithmetic mean value of the flue gas components at the outlet of the air preheater at each side is taken, and the arithmetic mean value of 2 flues is taken as the boiler exhaust flue gas components;
the exit flue gas temperature of the economizer is measured by adopting a grid method, and the arithmetic mean of each measuring point at each side is taken as the exit average flue gas temperature;
the flue gas temperature at the outlet of the air preheater is measured by adopting a grid method, 2 flues are totally adopted, and the arithmetic mean value of the measurement points is taken as the average flue gas temperature at the outlet of the air preheater at each side.
In the above embodiments, the calculation formula of the boiler thermal efficiency is as follows:
Figure GDA0001124677180000131
in the formula:
ηg-boiler thermal efficiency,%;
Hf-fuel application base lower heating value, kJ/kg;
b-corresponds to the total input physical heat of each kilogram of fuel entering the furnace, kJ/kg;
l is the total heat loss of each kilogram of boiler fuel, and is calculated according to the condition of the boiler according to the following formula:
L＝LUC+L'G+Lmf+LH+LMA+Lco+Lβ+LUN
LUC-heat loss of unburned carbon in ash, kJ/kg;
L'G-dry flue gas heat loss, kJ/kg;
Lmf-heat loss due to moisture in the fuel entering the furnace, kJ/kg;
LHheat loss due to moisture generated by hydrogen combustion, kJ/kg;
LMAheat loss due to moisture in the air, kJ/kg;
LCOheat loss due to the formation of carbon monoxide, kJ/kg;
Lβ-heat losses by surface radiation and convection, kJ/kg;
LUNnot measurable heat loss (constant according to the boiler plant design value), kJ/kg.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, it should be noted that, for those skilled in the art, many modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims (8)

1. A method for optimizing the air distribution mode of a W-shaped flame boiler is characterized in that at the position of the height 1/3 of a hearth, a front wall and a rear wall form an arch inwards, and 2 x 12 double-cyclone burners are arranged on the arch; secondary air chambers are arranged on the front wall and the rear wall of the lower hearth and are divided into an arch-up secondary air chamber and an arch-down secondary air chamber through partition plates, the arch-down secondary air chamber is divided into independent secondary air chambers by longitudinal partition plates according to the positions and the number of burners, and twelve independent air chambers are respectively arranged on the front wall and the rear wall; the double-cyclone burners are in one-to-one correspondence with the independent air chambers, wherein the front wall sequentially comprises a burner C1, a burner B1, a burner C2, a burner B2, a burner C3, a burner B3, a burner C4, a burner B4, a burner C5, a burner B5, a burner C6 and a burner B6 from left to right; the rear wall comprises a combustor D1, a combustor A1, a combustor D2, a combustor A2, a combustor D3, a combustor A3, a combustor D4, a combustor A4, a combustor D5, a combustor A5, a combustor D6 and a combustor A6 from left to right; the secondary air under the arch is divided into an upper part (D), a middle part (E) and a lower part (F) in the vertical direction, the flow of each secondary air is adjusted by a baffle, and the air quantity is controlled by different baffles in the circulating secondary air box on the arch of the hearth;
the method is characterized in that the optimization of the air distribution mode specifically comprises the following steps:
acquiring the operation conditions of the boiler at different F-layer secondary air declination angles under the preset coal types and loads, wherein the operation conditions at least comprise the following steps: NOx, CO, O2 of the economizer outlet flue gas; NOx, CO, O2 of the air preheater outlet flue gas; the thermal efficiency of the boiler; coal as fired industry, element analysis; sampling and analyzing fly ash and slag; the temperature of the flue gas at the outlet of the economizer; the temperature of the flue gas at the outlet of the air preheater; sampling raw coal; ambient temperature, humidity and atmospheric pressure;
analyzing the obtained operation condition of the boiler, and determining the downdip angle of the F wind and the opening degree of D, E wind as follows:
and (4) rear wall: f wind declination angles of the combustor D1, the combustor a1, the combustor D2, the combustor a2, the combustor D3, the combustor A3, the combustor D4, the combustor a4, the combustor D5, the combustor a5, the combustor D6 and the combustor A6 are respectively corresponding from left to right: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5;
front wall: f wind declination angles of the combustor C1, the combustor B1, the combustor C2, the combustor B2, the combustor C3, the combustor B3, the combustor C4, the combustor B4, the combustor C5, the combustor B5, the combustor C6 and the combustor B6 are respectively corresponding from left to right: 25. 25, 5, 30, 5, 25; e, wind opening degree: 25. 25, 5, 20, 5, 10; d, wind opening degree: 5. 5, 5;
the method further comprises the following steps: the arch is provided with SOFA nozzles, four front walls and four rear walls are arranged, three of the front walls and three of the rear walls are arranged in a hedging manner, the right side of the front wall and the left side of the rear wall are respectively provided with a nozzle, and the overtemperature problem of the reheater is solved by stopping operation of the nozzles in an overtemperature area during normal operation;
the method further comprises the following steps: 4 ventilation gaps are longitudinally formed in the wing wall to blow secondary air inwards, the outer diameter of a water wall tube at the wing wall is 120.65mm, the center distance is 146.4mm, the tube clearance of the water wall tube is 25.4mm, the outer diameter of the tube at the upper part and the lower part of the wing wall is 69.85mm, the water wall tube is connected with the upper part and the lower part of the wing wall through a reducer pipe, the outer diameter of the water wall tube at four ventilation belts is less than 120.65mm, the tube clearance of the water wall tube at the four ventilation belts is 76.55mm, and the height of each ventilation belt is set to be the total length of the wing wall tube or the upper half part of the wing wall.
2. The optimization method for the air distribution mode of the W-shaped flame boiler according to claim 1, wherein under the preset load, the conditions of different downdip angles of F wind specifically comprise: (1) under 325MW load, the F-wind down angle is 0 °, 10 °, 15 °, 20 °, 30 ° lower boiler operating conditions; (2) under 300MW load, the F-wind down angles of 5 °, 10 °, 20 °, 30 ° lower boiler operating conditions; (3) under 260MW load, the F wind down angles of 5 °, 10 °, 20 °, and 30 ° lower boiler operating conditions.
3. The method for optimizing the air distribution mode of the W-shaped flame boiler according to claim 1, wherein the W-shaped flame boiler combusts coal by adopting a staged combustion mode, and specifically comprises the following steps: selecting combustible coal and anthracite in a preset proportion, and reacting the combustible coal with oxygen to form first-stage combustion; the anthracite is ignited under the high-temperature smoke atmosphere formed in the first stage to form second-stage combustion, wherein the content of volatile components of the inflammable coal is higher than that of the anthracite, the content of the volatile components is more than 25%, and the ratio of the bituminous coal to the anthracite is more than 1: 1.
4. The optimization method for the air distribution mode of the W-shaped flame boiler according to claim 3, wherein the ratio of bituminous coal to anthracite coal is 3: 1.
5. The method for optimizing the air distribution mode of a W-shaped flame boiler according to claim 3, wherein the dry ash-free volatile content of the coal as fired is kept to be 15% < Vdaf < 20%, the low calorific value of the coal as fired is kept to be 20MJ/kg < Qnet, ar < 22.5MJ/kg, and Vdaf is required to be more than 10% when bituminous coal, lean coal and anthracite are combusted in a graded manner.
6. The method for optimizing the air distribution mode of the W-shaped flame boiler according to claim 3, wherein the W-shaped flame boiler is provided with four coal mills, the first coal mill and the third coal mill are used for grinding anthracite, the second coal mill and the fourth coal mill are used for grinding bituminous coal and coal mixture of the anthracite, and the outlet temperatures of the first coal mill and the third coal mill are 118 ℃.
7. The optimization method for the air distribution mode of the W-shaped flame boiler according to claim 1, wherein the calculation formula of the boiler thermal efficiency is as follows:
Figure FDA0002193435430000031
in the formula:
eta g-boiler thermal efficiency,%;
hf-fuel application base lower calorific value, kJ/kg;
b-corresponds to the total input physical heat of each kilogram of fuel entering the furnace, kJ/kg;
l is the total heat loss of each kilogram of boiler fuel, and is calculated according to the condition of the boiler according to the following formula:
L＝LUC+L'G+Lmf+LH+LMA+Lco+Lβ+LUN
LUC-unburned carbon heat loss in ash, kJ/kg;
l' G-heat loss of dry flue gas, kJ/kg;
Lmf-Heat loss due to moisture in the fuel entering the furnace, kJ/kg;
LH-heat loss from combustion of hydrogen to produce moisture, kJ/kg;
LMA-Heat loss due to moisture in the air, kJ/kg;
LCO-Heat loss due to carbon monoxide production, kJ/kg;
l β -heat loss by surface radiation and convection, kJ/kg;
LUN-unmeasurable heat loss, constant, kJ/kg, was taken as the boiler plant design value.
8. The optimization method of the air distribution mode of the W-shaped flame boiler according to the claim 1, characterized in that the measurement of NOx, CO and O2 of the flue gas at the outlet of the economizer adopts a grid method, five measuring points are taken in each side flue, each flue is mixed into a flue gas sample for analysis, the arithmetic mean value of the flue gas at the outlet of each side air preheater is taken as the flue gas component, and the arithmetic mean value of 2 flue gas components discharged from the boiler is taken as the flue gas component;
the measurement of NOx, CO and O2 of the flue gas at the outlet of the air preheater also adopts a grid method, five measuring points are taken by each side of flue, each flue is mixed into a flue gas sample for analysis, the arithmetic mean value of the flue gas components at the outlet of the air preheater at each side is taken, and the arithmetic mean value of 2 flues is taken as the boiler exhaust flue gas components;
the exit flue gas temperature of the economizer is measured by adopting a grid method, and the arithmetic mean of all measuring points on each side is taken as the exit average flue gas temperature.
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0268403A (en) * 1988-09-02 1990-03-07 Babcock Hitachi Kk Solid fuel burner
CN101324340A (en) * 2008-08-05 2008-12-17 贵州电力试验研究院 Apparatus for adjusting secondary wind direction under W type flame oven arch

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0268403A (en) * 1988-09-02 1990-03-07 Babcock Hitachi Kk Solid fuel burner
CN101324340A (en) * 2008-08-05 2008-12-17 贵州电力试验研究院 Apparatus for adjusting secondary wind direction under W type flame oven arch

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
拱下二次风下倾角度可调的W型火焰锅炉燃烧特性试验分析;石践等;《热力发电》;20130108;第41卷(第12期);第25-29页，所有图表 *

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