CN109442398B - Multipoint direct-injection bisection fast-mixing radial-injection low-nitrogen combustor - Google Patents
Multipoint direct-injection bisection fast-mixing radial-injection low-nitrogen combustor Download PDFInfo
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- CN109442398B CN109442398B CN201810787994.4A CN201810787994A CN109442398B CN 109442398 B CN109442398 B CN 109442398B CN 201810787994 A CN201810787994 A CN 201810787994A CN 109442398 B CN109442398 B CN 109442398B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
- F23D14/46—Details, e.g. noise reduction means
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Abstract
The invention provides a multipoint direct injection bisection fast mixing radial injection low-nitrogen combustor, which consists of a combustor gas path main pipe, a combustor head baffle, a central fuel supply pipe, a main path fuel injection device and an ignition path system, wherein the combustor head baffle is provided with a central fuel supply pipe; a radial open slot is formed between the tail end of the burner gas path main pipe and a burner head baffle, air flows out from two sides of the main path fuel injection device along the radial slot in an accelerated manner, gaseous fuel is transversely injected into accelerated air flow through small holes in two sides of the fuel injection device, air flows on two sides of the fuel injection device are intersected and sheared to accelerate mixing of the air and the fuel, and mixed gas is injected to a hearth through the radial slot; after the mixed gas flow collides with the hearth, one flow deflects downstream to form a main flow vortex, and the other flow deflects upstream to form an upstream vortex; the fuel is directly sprayed at multiple points, the equivalent ratio distribution is uniform, the flame impacts the wall surface of the hearth, the heat exchange is accelerated, the existence of upstream vortex forms the internal circulation of the flue gas, and the comprehensive characteristics play a role in reducing the emission of nitrogen oxides of the combustor.
Description
Technical Field
The invention relates to the technical field of burners, in particular to a multipoint direct-injection bisection fast-mixing radial-injection low-nitrogen burner which is a burner using gaseous fuel, is suitable for an industrial furnace or a gas boiler using the gaseous fuel, and can enable the combustion equivalence ratio to be distributed more uniformly, enable flue gas to circulate internally and reduce the emission of nitrogen oxides.
Background
At present, the first Beijing is seriously influenced by haze for one year, and the coal-fired boiler of the first Beijing is comprehensively transformed in the early stage to replace coal with gas, so that the emission of pollutants is reduced in terms of energy, and the effect of treating atmospheric pollution is achieved. The low-nitrogen modification of the gas-fired boiler in order to reduce the nitrogen oxide gas and the water vapor in the air is also a key engineering task in the clean air action plan of Beijing. At present, the gas boiler in Beijing is mainly a small boiler, the volume ratio of the gas boiler is about 47%, the volume ratio of the gas boiler is about 88% below 10 steam tons, and the average value of nitrogen oxides generated by the gas boiler in Beijing is about 146 mg/cubic meter.
In 2015, 6 and 10 days, the environmental protection agency in Beijing city releases local standards for emission of atmospheric pollutants, wherein the main purpose of revision of the emission standards for atmospheric pollutants of boilers is to strictly control emission of nitrogen oxides. From 2016, month 7, and day 1, the emission limits of the first stage of the standard will begin to be met, i.e., the emission limits of the newly built boiler will be tightened from the current 150 mg/m to 80 mg/m. And 4, 1, 4 and 2017, the newly-built boiler implements the second-stage emission limit, namely the nitrogen oxides are further severely reduced to 30 mg/cubic meter.
Aiming at the requirement of low nitrogen, each unit provides a special modification technical scheme for customizing different gas-fired boilers, which mainly comprises the following steps: replacing a novel low-nitrogen combustor, adopting various advanced technologies such as air classification, fuel classification and the like, controlling the combustion rate and expanding a reduction area; optimizing a combustion control system, and accurately adjusting the ratio of combustion-supporting air to fuel quantity; a flue gas recirculation system is added to control the oxygen content of the combustion area; and the fuel and air premixing mode is adopted to control the equivalence ratio distribution of the combustion zone. By the above measures, the generation of thermal type nitrogen oxides is suppressed, thereby reducing emissions.
The flue gas recirculation is divided into flue gas external circulation and flue gas internal circulation. The flue gas external circulation needs to build a set of flue gas external circulation system, which is widely applied at present, but the consumption of electric quantity is increased, and the complexity of the system is increased. The flue gas internal circulation is realized without adding a new system, and the scheme has high cost performance. At present, the internal circulation of flue gas also has a plurality of schemes, and most of the schemes are that the design is made at the head part of a combustor, so that airflow entering an industrial furnace or a gas boiler can flow back to generate internal circulation, or the internal circulation is realized by corner vortex backflow from the corner of a hearth, the circulation amount of the internal circulation is limited, and if the smoke amount of the internal circulation is further promoted, the smoke amount needs to be coupled with the hearth to generate backflow.
The lean premixed combustion is divided into surface combustion (namely metal mesh full-surface premixed combustion) and premixed flame-stabilized combustion. At present, the surface premixed combustion scheme is mature, but the risk of boiler explosion caused by metal mesh blockage exists; the premixing flame-stabilizing combustion has the problems of detonation of an ignition process and oscillation of a combustion process, which are the problems and challenges faced by the premixing combustion.
In summary, many modification techniques increase the construction cost and the operation cost for reducing the emission of nitrogen oxides of industrial furnaces or gas boilers, and premixed combustion brings unpredictable potential risks.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: overcome prior art's not enough, provide a multiple spot directly spout the low NOx burner of the pair of minutes of mixing radial injection, through the multiple spot directly spout the scheme design of the pair of minutes of mixing, the performance is analogized in the even advantage of premixing combustion equivalence ratio distribution, avoids again because of the tempering shock scheduling problem that brings in advance, adopts the radial injection mode moreover, through with the furnace coupling, produces two types of vortexes, makes the flue gas can the inner loop, and control combustion temperature is in order to reduce nitrogen oxide and discharges.
The technical scheme adopted by the invention for solving the technical problems is as follows: a multi-point direct injection bisection fast mixing radial injection low-nitrogen burner comprises a burner gas path main pipe, a burner head baffle, a central fuel supply pipe, a main path fuel injection device and a flame stabilizing path fuel injection pipe; the combustor needs to extend into the hearth of the industrial furnace or the gas boiler, and a certain combustor extension length is ensured; the burner head baffle and the tail end of the burner gas circuit main pipe are welded through a narrow interval section; the ignition electrode is fixed on a fuel pipe of an ignition path and is integrally inserted near a central fuel supply pipe in the combustor, so that the ignition electrode can work; firstly, air is introduced from an inlet of a gas path main pipe of a combustor, then gaseous fuel is independently supplied to a fuel pipe of an ignition path, and an ignition electrode works; when a high-temperature fuel gas for ignition is formed at the outlet of the fuel pipe of the ignition path, introducing a gaseous fuel into the central fuel supply pipe; a radial open slot is formed between the tail end of the burner gas path main pipe and a burner head baffle, air flows out from two sides of the main path fuel injection device along the radial slot in an accelerated manner, gaseous fuel is transversely injected into accelerated air flow through small holes in two sides of the fuel injection device, air flows on two sides of the fuel injection device are intersected and sheared to accelerate mixing of the air and the fuel, and mixed gas is injected to a hearth through the radial slot; the mixed gas flow is divided into two flows after colliding with the hearth, one flow deflects to the downstream to form a main flow vortex, and the other flow deflects to the upstream along the wall surface of the hearth to form an upstream vortex; the mixed gas flow forms a low-speed area near the wall surface of the hearth, is ignited and stabilized by high-temperature gas generated by the previous ignition path, and at the moment, the gaseous fuel of a fuel pipe of the ignition path is closed; the fuel is directly sprayed at multiple points, the combustion equivalence ratio is distributed uniformly, a high-temperature heat release area is reduced, in addition, the flame impacts the wall surface of a hearth, the heat exchange is accelerated, the combustion temperature is reduced, and the internal circulation of the flue gas is formed due to the existence of the upstream vortex flow.
The ratio of the extending length of the combustor to the diameter of an outer ring of a combustor gas circuit main pipe is 1-2; the ratio of the diameter of the outer ring of the burner gas circuit main pipe to the middle diameter of the hearth, namely the middle diameter of the hearth, is 0.15-0.5.
The ratio of the width of a slot with a radial opening formed between the tail end of the main pipe of the gas circuit of the combustor and the baffle plate at the head part of the combustor to the diameter of the outer ring of the main pipe of the gas circuit of the combustor is 0.1-0.2.
The main path fuel injection device is composed of a gas collecting box section and a flow guide conical section, wherein injection holes are distributed on two sides of the flow guide conical section and respectively comprise fuel multi-point injection front distribution holes and fuel multi-point injection rear distribution holes, the two rows of holes are staggered in the circumferential direction, and the number of each row of holes is 25-50.
The ratio of the diameter of the inner ring of the central fuel supply pipe to the diameter of the outer ring of the combustor gas circuit main pipe is 0.2-0.4. The central fuel supply pipe is connected with the gas collecting tank section of the main path fuel injection device through a plurality of fuel branch pipes, the number of the fuel branch pipes is 6-10, and the ratio of the diameters of the fuel branch pipes to the diameter of the inner ring of the central fuel supply pipe is 0.2-0.4.
The diameter of the fuel injection pipe of the flame stabilizing path is the same as that of the fuel branch pipe. The fuel injection pipe of the flame stabilizing path penetrates through the center of the baffle plate of the head part of the combustor.
The working principle of the invention is as follows: firstly, air is introduced from an inlet of a gas path main pipe of a combustor, then gaseous fuel is independently supplied to a fuel pipe of an ignition path, and an ignition electrode works; when a high-temperature fuel gas for ignition is formed at the outlet of the fuel pipe of the ignition path, the central fuel supply pipe is filled with gaseous fuel; air flows out from two sides of the main path fuel injection device along the radial slot in an accelerated manner, gaseous fuel is transversely injected into accelerated air flow through small holes in two sides of the fuel injection device, air flows on two sides of the fuel injection device are intersected and sheared, mixing of the air and the fuel is accelerated, and mixed gas is injected to a hearth through the radial slot; the mixed gas flow is divided into two flows after colliding with the hearth, one flow deflects to the downstream to form a main flow vortex, and the other flow deflects to the upstream along the wall surface of the hearth to form an upstream vortex; the mixed gas flow forms a low-speed area near the wall surface of the hearth, is ignited and stabilized by high-temperature gas generated by the previous ignition path, and closes the gaseous fuel of a fuel pipe of the ignition path.
Compared with the prior art, the invention has the following advantages:
(1) the low-nitrogen combustor disclosed by the invention adopts a mixing mode of multipoint direct injection and split mixing, so that the rapid mixing of fuel and air is realized, the equivalence ratio distribution is more uniform, and the heat release concentration is reduced;
(2) the low-nitrogen combustor adopts radial injection organization for stabilizing fire, and the combustor is coupled with a hearth to generate vortex, so that the internal circulation of flue gas is realized, and the circulation quantity of the flue gas can be increased;
(3) the low-nitrogen combustor has the advantages of simple structure, easiness in processing and low cost.
Drawings
FIG. 1 is a schematic diagram of the system of the present invention;
FIG. 2 is a schematic view of the internal structure of the burner head of the present invention;
FIG. 3 is a schematic view of the exterior configuration of the burner head of the present invention;
fig. 4 is a schematic structural view of a burner fuel injection device of the present invention.
In the figure: the main burner gas path pipe 1, the burner head baffle 2, the central fuel supply pipe 3, the main path fuel injection device 4, the flame stabilizing fuel injection pipe 5, the furnace chamber 6, the burner depth length 7, the interval narrow section 8, the ignition electrode 9, the ignition fuel pipe 10, the slot 11, the slot width 12, the main flow vortex 13, the upstream vortex 14, the outer ring diameter of the burner gas path main pipe 15, the furnace chamber middle diameter 16, the gas collecting tank section 17, the guide cone section 18, the fuel multi-point injection front distribution hole 19, the fuel multi-point injection rear distribution hole 20, the central fuel supply pipe inner ring diameter 21, the fuel branch pipe 22 and the fuel branch pipe diameter 23.
Detailed Description
The invention is further described with reference to the following figures and detailed description.
As shown in fig. 1, the embodiment of the invention mainly comprises a combustor gas path main pipe 1, a combustor head baffle 2, a central fuel supply pipe 3 and a main path fuel injection device 4; the burner is required to extend into a hearth 6 of an industrial furnace or a gas boiler, and a certain extending length 7 of the burner is ensured;
as shown in fig. 2, the ignition electrode 9 is fixed on the ignition path fuel pipe 10 and is integrally inserted near the central fuel supply pipe 3 in the burner, so as to ensure that the ignition electrode 9 can work; a radial opening slot 11 is formed between the tail end of the combustor gas path main pipe 1 and the combustor head baffle 2, the width 12 of the slot and the outer ring diameter 15 of the combustor gas path main pipe have a certain proportion range, and the accelerated radial injection of airflow to the wall surface of the hearth 6 is ensured to form an upstream vortex 14 and a main vortex 13;
as shown in fig. 3, the burner head baffle 2 is welded with the tail end of the burner gas circuit main pipe 1 through a plurality of narrow sections 8; the fuel injection pipe 5 of the flame stabilizing path penetrates through the center of the burner head baffle 2;
as shown in fig. 4, the main path fuel injection device 4 is composed of a gas collecting tank section 17 and a flow guiding conical section 18, wherein the injection holes are distributed on two sides of the flow guiding conical section 18, and are respectively a fuel multi-point injection front distribution hole 19 and a fuel multi-point injection rear distribution hole 20, the two rows of holes are staggered in the circumferential direction, and the number of each row of holes is required to ensure circumferential uniformity.
The invention has not been described in detail and is within the skill of the art.
The above description is only a part of the embodiments of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention.
Claims (6)
1. The utility model provides a multiple spot is directly spouted and is cut fast mixing radial injection low NOx burner which characterized in that: the device is composed of a combustor gas path main pipe (1), a combustor head baffle (2), a central fuel supply pipe (3), a main path fuel injection device (4) and a flame stabilizing path fuel injection pipe (5); the burner is required to extend into a hearth (6) of an industrial furnace or a gas boiler, and a certain extending length (7) of the burner is ensured; the burner head baffle (2) and the tail end of the burner gas circuit main pipe (1) are welded through a narrow interval section (8); the ignition electrode (9) is fixed on a fuel pipe (10) of an ignition circuit and is integrally inserted near a central fuel supply pipe (3) in the combustor to ensure that the ignition electrode (9) can work; firstly, air is introduced from an inlet of a gas path main pipe (1) of the combustor, then gaseous fuel is independently supplied to a fuel pipe (10) of an ignition path, and an ignition electrode (9) works; when a high-temperature gas for ignition is formed at the outlet of the fuel pipe (10) of the ignition path, gaseous fuel is introduced into the central fuel supply pipe (3); a radial open slot (11) is formed between the tail end of the burner gas path main pipe (1) and the burner head baffle (2), the slot width (12) is the length of the interval narrow section (8), air flows out from two sides of the main path fuel injection device (4) along the radial slot (11) in an accelerated manner, gaseous fuel is transversely injected into accelerated air flow through small holes at two sides of the fuel injection device (4), the air flow at two sides of the fuel injection device is intersected and sheared to accelerate the mixing of the air and the fuel, and mixed gas is injected to the hearth (6) through the radial slot (11); the mixed gas flow is divided into two flows after colliding with the hearth (6), one flow deflects to the downstream to form a main flow vortex (13), and the other flow deflects to the upstream along the wall surface of the hearth to form an upstream vortex (14); the mixed gas flow forms a low-speed area near the wall surface of the hearth, is ignited and stabilized by high-temperature gas generated by the previous ignition path, and at the moment, the gaseous fuel of a fuel pipe (10) of the ignition path is closed; the fuel is directly sprayed at multiple points, the combustion equivalence ratio is distributed uniformly, a high-temperature heat release area is reduced, in addition, the flame impacts the wall surface of the hearth (6) to accelerate heat exchange, the combustion temperature is reduced, and in addition, the internal circulation of the flue gas is formed due to the flowing existence of the upstream vortex (14).
2. The multipoint direct injection tangential fast mixing radial injection low-nitrogen combustor according to claim 1, characterized in that: the ratio of the extending length (7) of the combustor to the outer ring diameter (15) of the combustor gas circuit main pipe (1) is 1-2; the ratio of the outer ring diameter (15) of the burner gas circuit main pipe to the middle diameter of the hearth (6), namely the hearth middle diameter (16), is 0.15-0.5.
3. The multipoint direct injection tangential fast mixing radial injection low-nitrogen combustor according to claim 1, characterized in that: the ratio of the width (12) of a slot forming a radial opening between the tail end of the burner gas path main pipe (1) and the head baffle (2) of the burner to the diameter (15) of the outer ring of the burner gas path main pipe is 0.1-0.2.
4. The multipoint direct injection tangential fast mixing radial injection low-nitrogen combustor according to claim 1, characterized in that: the main path fuel injection device (4) is composed of a gas collecting box section (17) and a flow guide conical section (18), wherein injection holes are distributed on two sides of the flow guide conical section (18) and respectively comprise a fuel multi-point injection front distribution hole (19) and a fuel multi-point injection rear distribution hole (20), the number of rows of the front distribution hole and the rear distribution hole is 1-5, the front distribution hole and the rear distribution hole are circumferentially staggered, and the number of each row of holes is 10-80.
5. The multipoint direct injection split-fast mixing radial injection low-nitrogen burner as claimed in claim 4, characterized in that: the ratio of the inner ring diameter (21) of the central fuel supply pipe (3) to the outer ring diameter (16) of the combustor gas circuit main pipe (1) is 0.2-0.4; the central fuel supply pipe (3) is connected with a gas collecting tank section (17) of the main fuel injection device (4) through a plurality of fuel branch pipes (22), the number of the fuel branch pipes (22) is 6-10, and the ratio of the diameter (23) of the fuel branch pipes (22) to the diameter (21) of an inner ring of the central fuel supply pipe (3) is 0.2-0.4.
6. The multipoint direct injection tangential fast mixing radial injection low-nitrogen combustor according to claim 5, characterized in that: the diameter of the fire stabilizing path fuel injection pipe (5) is the same as the diameter (23) of the fuel branch pipe (22), and the fire stabilizing path fuel injection pipe (5) penetrates through the center of the burner head baffle (2).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810787994.4A CN109442398B (en) | 2018-07-18 | 2018-07-18 | Multipoint direct-injection bisection fast-mixing radial-injection low-nitrogen combustor |
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| CN201810787994.4A CN109442398B (en) | 2018-07-18 | 2018-07-18 | Multipoint direct-injection bisection fast-mixing radial-injection low-nitrogen combustor |
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| CN110145737A (en) * | 2019-04-19 | 2019-08-20 | 王晓峰 | A kind of rotational-flow stable-flame radial spray low NO |
| CN111578283A (en) * | 2020-05-06 | 2020-08-25 | 郑州博纳热能设备有限公司 | Natural gas burner with low nitrogen oxide emission |
| CN111780107B (en) * | 2020-07-07 | 2021-11-09 | 中国科学院过程工程研究所 | Gas decoupling combustor and using method thereof |
| CN114688533A (en) * | 2020-12-30 | 2022-07-01 | 西安航天源动力工程有限公司 | Nozzle of fuel pipe, ignition device and gasification furnace |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3815311A1 (en) * | 1988-05-05 | 1989-11-16 | Koerting Ag | Mixing device for oil burners |
| US5211536A (en) * | 1991-05-13 | 1993-05-18 | General Electric Company | Boltless turbine nozzle/stationary seal mounting |
| JP2000074329A (en) * | 1998-08-27 | 2000-03-14 | Ishikawajima Harima Heavy Ind Co Ltd | EXHAUST GAS SELF-RECIRCULATING TYPE LOW NOx BURNER |
| CN100483029C (en) * | 2006-01-12 | 2009-04-29 | 中国科学院工程热物理研究所 | Combustion chamber of miniature gas turbine with double premixed channel using natural gas |
| ATE461363T1 (en) * | 2006-07-27 | 2010-04-15 | Magneti Marelli Spa | FUEL INJECTION VALVE FOR A DIRECT INJECTION INTERNAL COMBUSTION ENGINE |
| CN107131499A (en) * | 2013-02-17 | 2017-09-05 | 乌鲁木齐九品芝麻信息科技有限公司 | The premixed secondary fuel burner nozzle of mechanical adjustment and method |
| CN106196051B (en) * | 2016-07-19 | 2018-05-18 | 北京航空航天大学 | A kind of tubule premixed swirl low stain gas burner |
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