CN213901064U - Double-fuel burner and boiler with graded ignition and graded air distribution and smoke recirculation - Google Patents
Double-fuel burner and boiler with graded ignition and graded air distribution and smoke recirculation Download PDFInfo
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- CN213901064U CN213901064U CN202022966139.5U CN202022966139U CN213901064U CN 213901064 U CN213901064 U CN 213901064U CN 202022966139 U CN202022966139 U CN 202022966139U CN 213901064 U CN213901064 U CN 213901064U
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Abstract
The utility model provides a hierarchical ignition is air-distribution in grades and is adopted two fuel combustor and boiler of flue gas recirculation, including ignition gas pipe, central tuber pipe, wind chamber, secondary plenum, main combustion chamber, precombustion chamber, burning torch, circulation plenum, central tuber pipe cover is established in the outside of ignition gas pipe, wind chamber cover is established in the outside of central tuber pipe once, secondary plenum cover is established in the outside of wind chamber once, main combustion chamber cover is established in the outside of secondary plenum, central tuber pipe, wind chamber, secondary plenum air outlet and ignition gas pipe, main combustion chamber's gas outlet are located inside the precombustion chamber, the burning torch is installed on the precombustion chamber, the circulation plenum sets up at the precombustion chamberAnd (3) an external part. Solves the problems of unsatisfactory low-nitrogen combustion effect, poor operation safety and the like of the conventional dual-fuel combustor, improves the combustion efficiency and reduces NOXThe purpose of the initial discharge.
Description
Technical Field
The utility model belongs to the technical field of the combustor, concretely relates to hierarchical ignition is air distribution in grades and is adopted flue gas recirculation's two fuel combustor and boiler.
Background
In view of the existing energy structure mainly based on coal and the continuous improvement of national energy-saving and emission-reducing standards in China, particularly along with the international energy cooperation and introduction dedicated by the nation in recent years, the supply of high-quality fuels such as natural gas and the like is greatly relieved, so that the novel low-nitrogen high-efficiency pulverized coal and gas combustion technology is greatly popularized and applied.
The industrial boiler plays an important role in the economic operation of China all the time. At present, the international situation is changing day by day, the surrounding environment is not stable, and the problem of energy safety still exists. Since a single fuel boiler may not be operated due to fuel supply problems, thereby causing a great economic loss, it is necessary to develop a new type of high-efficiency low-nitrogen burner suitable for both pulverized coal and gas fuel. The existing burners using two fuels, namely coal powder and fuel gas, are mostly simply combined, the operation safety is poor, and the low-nitrogen combustion effect is not ideal.
SUMMERY OF THE UTILITY MODEL
The utility model provides a hierarchical two fuel combustor and boiler that fire hierarchical air distribution adopted flue gas recirculation for it is unsatisfactory to solve present two fuel combustor low-nitrogen combustion effect, and operational safety is poor scheduling problem.
The utility model provides a pair of hierarchical ignition is air-distributing in grades and is adopted two fuel combustor and boiler of flue gas recirculation, including ignition gas pipe, central tuber pipe, wind chamber, secondary plenum, main combustion chamber, precombustion chamber, burning torch, circulation plenum, the outside at ignition gas pipe is established to central tuber pipe cover, wind chamber cover is established in the outside of central tuber pipe once, the outside at wind chamber once is established to the secondary plenum cover, main combustion chamber cover is established in the outside of secondary plenum, the gas outlet of central tuber pipe, wind chamber, secondary plenum air outlet and ignition gas pipe, main combustion chamber is located inside the precombustion chamber, the burning torch is installed on the precombustion chamber, the circulation plenum sets up in the precombustion chamber outside.
Preferably, the secondary air chamber is divided into an inner air chamber and an outer air chamber, wherein an inner secondary air swirl blade is arranged at an air outlet of the inner secondary air chamber, and an outer secondary air swirl blade is arranged at an air outlet of the outer secondary air chamber.
Preferably, an inner secondary adjusting baffle is arranged at the air inlet of the inner secondary air chamber, and an outer secondary adjusting baffle is arranged at the air inlet of the outer secondary air chamber.
Preferably, a central air cyclone is arranged at the air outlet of the central air pipe.
Preferably, the tail end of the ignition gas pipe is provided with a conical end face, the conical end face is provided with an inner circle of spray holes and an outer circle of spray holes, and the spray included angle of the two spray holes which are symmetrically arranged in the same circle is 90 degrees.
Preferably, the ignition gas pipe is connected with a gas inlet pipeline through a hose, the gas inlet pipeline is connected with a gas matching valve group, and the gas matching valve group comprises a manual ball valve, a pneumatic ball valve and an electric regulating valve.
Preferably, the inner wall of the tail end of the circulating air chamber is provided with a fixed tangential rotational flow blade, and an included angle between the fixed tangential rotational flow blade and the axis of the fixed tangential rotational flow blade is 18 degrees.
Preferably, the included angle between the inner secondary air swirl vane and the axis thereof is 55 degrees, and the included angle between the outer secondary air swirl vane and the axis thereof is 25 degrees.
Preferably, the tail end of the main combustion chamber is provided with four groups of gas jet holes, and the four groups of gas jet holes are symmetrically arranged at the upper, lower, left and right positions on the circumference of the tail end of the main combustion chamber.
The utility model also provides a boiler, the boiler adopts the utility model discloses a hierarchical ignition is air distribution in grades and is adopted flue gas recirculation's double fuel combustor.
The utility model has the advantages that:
skillfully can respectively burn coal powder and fuel gasThe structure of the seed fuel is coupled together, and NO can be realized when the pulverized coal or the fuel gas is independently combustedXThe effect of low emissions; when the pulverized coal is used, concentrated phase powder conveying and secondary air graded distribution are adopted, the proportion is adjustable, the rotational flow strength is enhanced by adopting the guide of the rotational flow blades, and low-temperature flue gas is introduced from the precombustion chamber for recirculation, so that the low-nitrogen combustion of the pulverized coal is realized; when the gas is used, the fuel classification, cyclone air distribution and FIR + FGR flue gas internal and external dual circulation technology are adopted to make NOXDown to 30mg/Nm3The following.
Drawings
FIG. 1 is a schematic structural view of a dual-fuel burner for staged ignition and staged air distribution with flue gas recirculation according to the present invention;
FIG. 2 is a top view of the central air duct of the dual fuel burner of the present invention for staged ignition and staged air distribution with flue gas recirculation;
FIG. 3 is a cross-sectional view of the central air duct of the dual fuel burner of the present invention for staged ignition and staged air distribution with flue gas recirculation;
FIG. 4 is a schematic view of the fuel gas valve set of the dual fuel combustor for staged ignition and staged air distribution of the present invention with flue gas recirculation;
fig. 5 is a top view of the main combustion chamber air outlet of the dual-fuel burner of the present invention, which uses flue gas recirculation for staged ignition and staged air distribution.
The attached drawings are marked as follows:
1. an ignition gas pipe; 2. a central air duct; 3. a primary air chamber; 4. a secondary air chamber; 40. an inner secondary air chamber; 401. inner secondary air swirl vanes; 402. an inner secondary adjusting baffle; 41. an outer secondary air chamber; 411. an outer secondary air swirl vane; 412. an outer secondary adjusting baffle; 5. a main combustion chamber; 6. a precombustion chamber; 7. an ignition gun; 8. a circulating air chamber; 9. the fuel gas nozzle comprises a fixed tangential swirl vane 10, a fuel gas nozzle 11 and a nozzle; 12. a manual ball valve; 13. a pneumatic ball valve; 14. an electric control valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not to be construed as limiting the scope of the invention.
Examples
Referring to fig. 1, the dual-fuel burner for staged ignition and staged air distribution in the present embodiment adopts flue gas recirculation includes an ignition gas pipe 1, a central air pipe 2, a primary air chamber 3, a secondary air chamber 4, a main combustion chamber 5, a precombustion chamber 6, an ignition gun 7 and a circulation air chamber 8, wherein the central air pipe 2 is sleeved outside the ignition gas pipe 1, the primary air chamber 3 is sleeved outside the central air pipe 2, the secondary air chamber 4 is sleeved outside the primary air chamber 3, the main combustion chamber 5 is sleeved outside the secondary air chamber 4, an air outlet of the central air pipe 2, the primary air chamber 3, the secondary air chamber 4, an air outlet of the ignition gas pipe 1 and the main combustion chamber 5 are located inside the precombustion chamber 6, the ignition gun 7 is installed on the precombustion chamber 6, and the circulation air chamber 8 is arranged outside the precombustion chamber 6. The secondary air chamber 4 is divided into an inner air chamber and an outer air chamber: an inner secondary air plenum 40 and an outer secondary air plenum 41. The ignition gun 7 of the embodiment is of a pneumatic advance and retreat type, and exits from the precombustion chamber 6 after ignition to prevent damage caused by overheating, so that the service life is prolonged. The inner wall of the precombustion chamber 6 in the embodiment is cast by refractory materials and can resist high temperature.
A small air gun is connected with an ignition gas pipe 1 to inject gas into the precombustion chamber 6 to serve as an ignition source, and the gas quantity and the air quantity entering the precombustion chamber 6 are controlled during ignition to prevent deflagration; after the flame is stabilized, the gas quantity and the air quantity are adjusted to reach the rated thermal power of the small air gun, and the whole ignition process is safe and controllable.
The combustor of this embodiment divides the air distribution in four stages during operation, and the first stage: the central air is distributed by the central air pipe 2, and the central air accounts for about 15 percent. The primary air is provided by a Roots blower, the primary air carries pulverized coal to be sprayed into the precombustion chamber 6 through the primary air chamber 3, the primary air accounts for about 5 percent, the wind speed is about 20m/s, and the concentration of the pulverized coal is 2.5-4kg/Nm3. The central wind drives the gas flame to fully contact and mix with the pulverized coal flow. Because the coal powder has high concentration and is easy to ignite, the initial combustion component of the coal powder is mainly volatile. The primary air and the central air supply oxygen in this stage. In the embodiment, the central wind power-driven regulating valve is arranged in front of the central wind inlet burner and can be used forAnd (5) adjusting and controlling air quantity.
And a second stage: the inner secondary air is distributed from the inner secondary air chamber 40 to provide oxygen for the continuous combustion of the pulverized coal. The inner secondary air accounts for about 45 percent, the wind speed is 30-35m/s, the inner secondary air is strong rotational flow, the turbulence intensity of the pulverized coal is enhanced, the pulverized coal is diffused to the periphery, and a backflow area is formed in the front.
And a third stage: the external secondary air is distributed from the external secondary air chamber 41, the external secondary air accounts for about 35 percent, the air speed is 38-42m/s, the external secondary air is weak rotational flow, the air speed of the external secondary air is higher than that of the internal secondary air, the external secondary air is coated on the periphery of the internal secondary air and is mixed with the pulverized coal later than the internal secondary air, and oxygen is continuously provided for the combustion of the pulverized coal. The outer secondary air has weak rotational flow and high flow speed, is restrained by the entity on the inner wall of the precombustion chamber 6, plays a role in shaping and restraining the inner pulverized coal jet flow, prevents the pulverized coal from being diffused and attenuated too fast, maintains the rigidity of the pulverized coal jet flow, and continuously supplements the oxygen demand for the pulverized coal combustion.
A fourth stage: circulating air is distributed from the circulating air chamber 8, the air speed is 38-42m/s, the circulating air is taken from low-temperature flue gas after the dust remover, and oxygen is continuously provided for the coal dust after being burnt out by utilizing the residual oxygen in the flue gas. The circulating air is adjustable according to the total air volume proportion of 10-20%.
The burner of the embodiment comprehensively utilizes the combination design of concentrated phase powder conveying, 4-section type grading air distribution technology and low-temperature flue gas recirculation introduced by the precombustion chamber 6 to regulate the oxygen supply of each stage of pulverized coal combustion, slow down the pulverized coal combustion process and reduce the pulverized coal combustion intensity. The low-temperature recirculated flue gas introduced into the outer wall of the precombustion chamber 6 can also reduce the temperature of the precombustion chamber 6, and effectively prevent coal dust from coking. Low-temperature recirculated flue gas is introduced, the temperature of a combustion center is further reduced, the generation of thermal NOx is reduced, the residual oxygen in the flue gas is supplied in place, and the coal powder burnout process is realized.
In order to adjust the intake of the inner secondary air and the outer secondary air, as a preferred embodiment of this embodiment, an inner secondary air swirl vane 401 is disposed at the air outlet of the inner secondary air chamber 40, and an outer secondary air swirl vane 411 is disposed at the air outlet of the outer secondary air chamber 41. The included angle between the inner secondary air swirl vane 401 and the axis thereof is 55 degrees, and the included angle between the outer secondary air swirl vane 411 and the axis thereof is 25 degrees.
As a preferred implementation of this embodiment, the inner secondary air chamber 40 is provided with an inner secondary adjustment baffle 402 at the air inlet, and the outer secondary air chamber 41 is provided with an outer secondary adjustment baffle 412 at the air inlet. The opening degrees of the inner secondary adjusting baffle 402 and the outer secondary adjusting baffle 412 are adjusted, and on the premise of keeping stable torch combustion, a certain reducing atmosphere (the excess air coefficient is less than or equal to 1) is formed in the high-temperature region in the center of the flame, so that the generation of fuel type NOx is inhibited.
As a preferred embodiment of this embodiment, a central air swirler 21 is disposed at an air outlet of the central air duct 2, and central air is diffused under the action of the central air swirler 21 to play a role of "coal spreading", and its disturbance effect makes pulverized coal fully contact with gas flame when the pulverized coal is ignited, so as to facilitate ignition of the pulverized coal. Referring to fig. 2 and 3, the tail end of the ignition gas pipe 1 is provided with a conical end face, the conical end face is provided with an inner circle of spray holes 11 and an outer circle of spray holes 11, the air injection included angle a of the two spray holes 11 which are symmetrically arranged in the same circle is 90 degrees, and the gas is sprayed out of the spray holes 11 and then diffuses outwards at an angle of 90 degrees, contacts with the central air of the outer circle and is fully mixed. The combined design of the ignition gas pipe 1 and the central air cyclone 21 ensures that the flame formed after the ignition of the burner of the embodiment completely covers the air and powder outlet of the primary air chamber 3, and the pulverized coal is easy to ignite. When the main gas is used, the small gas gun continuously operates, and the ignition gas pipe 1 provides 'on-duty flame' for the combustion of the main gas, so that the combustion stability is improved.
Referring to fig. 4, as a preferred embodiment of the present embodiment, the ignition gas pipe 1 is connected to an air inlet pipeline through a hose, the air inlet pipeline is connected to a gas matching valve set, and the gas matching valve set includes a manual ball valve 12, a pneumatic ball valve 13 and an electric regulating valve 14. The pneumatic ball valve 13 in the gas matching valve set can be opened and closed quickly, and the on-off of the gas is controlled. The opening degree of the electric control valve 14 is driven by an electric actuator and is linked with the central wind electric control valve. The electric control valve 14 is specially provided with a low fire level verification switch to ensure that the ignition program can be started only when the opening of the electric control valve is at a small fire level (set to be 20% of the total opening). During ignition, the opening degree of the electric control valve 14 is set to be a small fire position and is linked with the central wind electric control valve, so that a small amount of gas enters the combustor at the beginning of ignition, high-voltage electric sparks generated by the ignition gun 7 directly ignite the small fire position gas sprayed out of the ignition gas pipe 1, the gas quantity during ignition is controlled, and the hearth deflagration is prevented. After ignition, flame is monitored, after ignition success is detected, the electric regulating valve 14 is linked with the central wind electric regulating valve, slowly opened to a large degree and adjusted to a rated value, and at the moment, the thermal power of the small gas gun is enough to ignite pulverized coal or main gas.
The ignition gas pipe 1 is matched with the central air cyclone 21 to form a conical 'flame' which is diffused forwards and outwards, and when the pulverized coal is combusted, the primary air chamber 3 can be completely 'intercepted', so that the ignition of the pulverized coal is smoothly realized; the conical 'flame' can be continuously diffused to the nozzle of the main combustion chamber 5, and the main gas can be smoothly ignited when the gas is used.
The design of the spray hole 11 of the ignition gas pipe 1 interacts with the central wind cyclone 21, a stable combustion area with gas smoke backflow is generated in the front area of the central wind outlet after ignition, and NO is reduced in the area due to the internal circulation of high-temperature smokexAnd (4) generating.
As a preferred implementation mode of the embodiment, a fixed tangential swirl vane 9 is arranged on the inner wall of the tail end of the circulating wind chamber 8, and the included angle of the fixed tangential swirl vane 9 and the axis thereof is 18 degrees.
Referring to fig. 5, as a preferred embodiment of the present embodiment, the end of the main combustion chamber 5 has four sets of gas injection holes 10, and the four sets of gas injection holes 10 are symmetrically arranged at the upper, lower, left and right positions on the circumference of the end of the main combustion chamber 5. Main fuel gas is sprayed into the precombustion chamber 6 at a high speed through four groups of fuel gas spray holes 10, main fuel gas combustion air distribution is distributed in a swirling mode through the secondary air chamber 4, four flames of an upper flame, a lower flame, a left flame and a right flame are formed by taking an on-duty flame as a center, and the fuel gas flame sprayed at the high speed generates a Venturi effect to drive the low-quality flame to form internal smoke entrainment. When the main fuel gas is injected, the fuel flow is distributed on the combustion section in a thick and thin manner, the combustion rate is delayed, the internal flue gas circulation is formed, the flame temperature is reduced, and the thermal NO is reducedXIs performed.
The utility model also provides a boiler, this boiler can be horizontal or vertical, the boiler adopts the utility model discloses hierarchical ignition is air distribution in grades and is adopted flue gas recirculation's two fuel combustor, the combustor of this embodiment can be installed in the front wall of boiler, back wall, front and back wall offset or the overhead installation.
Claims (10)
1. The utility model provides a hierarchical two fuel combustor that wind distribution adopted flue gas recirculation that ignite, its characterized in that: including ignition gas pipe, central tuber pipe, primary plenum, secondary plenum, main combustion chamber, precombustion chamber, burning torch, circulation plenum, the outside at ignition gas pipe is established to central tuber pipe cover, primary plenum cover is established in the outside of central tuber pipe, the outside at primary plenum is established to the secondary plenum cover, the outside at secondary plenum is established to main combustion chamber cover, central tuber pipe, primary plenum, secondary plenum air outlet and ignition gas pipe, main combustion chamber's gas outlet is located inside the precombustion chamber, the burning torch is installed on the precombustion chamber, the setting of circulation plenum is outside the precombustion chamber.
2. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 1, wherein: the secondary air chamber is divided into an inner air chamber and an outer air chamber, wherein an inner secondary air swirl blade is arranged at an air outlet of the inner secondary air chamber, and an outer secondary air swirl blade is arranged at an air outlet of the outer secondary air chamber.
3. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 2, wherein: an inner secondary adjusting baffle is arranged at the air inlet of the inner secondary air chamber, and an outer secondary adjusting baffle is arranged at the air inlet of the outer secondary air chamber.
4. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 1, wherein: and a central air cyclone is arranged at the air outlet of the central air pipe.
5. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 1, wherein: the tail end of the ignition gas pipe is provided with a conical end face, the conical end face is provided with an inner circle of spray holes and an outer circle of spray holes, and the spray included angle of the two spray holes which are symmetrically arranged in the same circle is 90 degrees.
6. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 1 or 5, characterized in that: the ignition gas pipe is connected with a gas inlet pipeline through a hose, the gas inlet pipeline is connected with a gas matching valve set, and the gas matching valve set comprises a manual ball valve, a pneumatic ball valve and an electric regulating valve.
7. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 1, wherein: the inner wall of the tail end of the circulating air chamber is provided with a fixed tangential rotational flow blade, and an included angle between the fixed tangential rotational flow blade and the axis of the fixed tangential rotational flow blade is 18 degrees.
8. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 2, wherein: the included angle between the inner secondary air swirl blade and the axis of the inner secondary air swirl blade is 55 degrees, and the included angle between the outer secondary air swirl blade and the axis of the outer secondary air swirl blade is 25 degrees.
9. The staged ignition staged air distribution dual fuel burner with flue gas recirculation according to claim 1, wherein: the tail end of the main combustion chamber is provided with four groups of gas jet holes which are symmetrically arranged at the upper, lower, left and right positions of the circumference of the tail end of the main combustion chamber.
10. A boiler, characterized by: use of a dual fuel burner with flue gas recirculation with staged ignition staged air distribution as claimed in any of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022966139.5U CN213901064U (en) | 2020-12-10 | 2020-12-10 | Double-fuel burner and boiler with graded ignition and graded air distribution and smoke recirculation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022966139.5U CN213901064U (en) | 2020-12-10 | 2020-12-10 | Double-fuel burner and boiler with graded ignition and graded air distribution and smoke recirculation |
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| Publication Number | Publication Date |
|---|---|
| CN213901064U true CN213901064U (en) | 2021-08-06 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202022966139.5U Active CN213901064U (en) | 2020-12-10 | 2020-12-10 | Double-fuel burner and boiler with graded ignition and graded air distribution and smoke recirculation |
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|---|---|
| CN (1) | CN213901064U (en) |
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2020
- 2020-12-10 CN CN202022966139.5U patent/CN213901064U/en active Active
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