CN103868065A - Combustor and combustion system - Google Patents
Combustor and combustion system Download PDFInfo
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- CN103868065A CN103868065A CN201410135512.9A CN201410135512A CN103868065A CN 103868065 A CN103868065 A CN 103868065A CN 201410135512 A CN201410135512 A CN 201410135512A CN 103868065 A CN103868065 A CN 103868065A
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Abstract
The invention relates to a combustor and a combustion system. The combustor comprises a primary combustion section and a secondary combustion section, wherein the primary combustion section is of a hollow pipe structure and comprises a mixing area and a primary combustion area, the mixing area and the primary combustion area are communicated through fluid, the mixing area is close to the outer side of the primary combustion section, the secondary combustion section is of a hollow pipe structure and connected to the inner end of the primary combustion section and comprises a secondary combustion area, the secondary combustion area and the primary combustion area are communicated through fluid, a fuel inlet and a primary combustion air inlet are formed in the outer side of the mixing area, and a secondary combustion air inlet is formed in the outer side of the secondary combustion area. When the combustor is used for production, the amount of discharged NOx can be effectively reduced, and environment protection is facilitated.
Description
Technical field
The present invention relates to high-temp combustion technical field, particularly a kind of burner.In addition, the invention still further relates to a kind of combustion system that comprises described burner.
Background technology
Industrial furnace adopts burner to produce conventionally, adopts burner can obtain thermal-flame.When production, burner is fuel and combustion air mixing after-combustion, thereby obtains high-temperature flue gas.But the burner of available technology adopting can produce a large amount of NOx in combustion process, as example, in order to make the fire box temperature of combustion furnace reach 1200 ℃, the in the situation that of air pre-mixing coefficient a=1, NOx discharge capacity reaches 5000ppm when high-temp combustion.Therefore, be badly in need of a kind of burner of low NOx drainage amount.
Summary of the invention
For above-mentioned problem, the present invention proposes a kind of burner, use this burner to produce and can effectively reduce NOx discharge capacity, be beneficial to environmental protection.In addition, the invention allows for a kind of combustion system that comprises said burner.
According to a first aspect of the invention, proposed a kind of burner, it comprises: primary combustion section, and it is configured to the pipeline section of hollow, and comprises mixed zone and primary combustion zone that fluid is communicated with, and mixed zone is near the outside of primary combustion section; Second-time burning section, the inner end that it is configured to the pipeline section of hollow and is connected in primary combustion section, it comprises intermediate zone, intermediate zone is communicated with primary combustion zone fluid; Wherein, the arranged outside of mixed zone has fuel inlet and primary air entrance, and the arranged outside of intermediate zone has secondary combustion-supporting air intake.
While adopting burner of the present invention to produce, due to the quantity delivered of primary air and secondary combustion-supporting air is less than respectively given fuel can the required combustion air total amount of completing combustion, therefore, fuel is burn incompletely in primary combustion zone and intermediate zone respectively, particularly in primary combustion zone, the oxygen concentration that participates in burning is low, also has the reduction reaction of NO simultaneously, thereby reduced to a certain extent the generation of NOx in flame.
On the sidewall of second-time burning section in one embodiment,, be provided with fluid and be communicated with the inner side of second-time burning section and the burner hearth exhaust gases passes of intermediate zone.Adopt such structure, the burner hearth flue gas that can by burner hearth exhaust gases passes entrainment combustion furnace while burning in intermediate zone enters into intermediate zone, therefore in burner hearth, the oxygen concentration of sneaking into while making second-time burning of flue gas reduces, thereby suppress the flame temperature of second-time burning, therefore effectively reduced the generation of NOx.
In a preferred embodiment, burner hearth exhaust gases passes extends to the outer end of second-time burning section.Make thus the mist that enters into intermediate zone from primary combustion zone be mixed by secondary combustion-supporting air and burner hearth flue gas, thereby effectively reduce combustion flame oxygen concentration around simultaneously.Further, the connectivity part of burner hearth exhaust gases passes and intermediate zone is enlarging shape towards intermediate zone.Accelerate thus the diffusion of burner hearth flue gas in intermediate zone, be beneficial to the reduction of oxygen concentration in intermediate zone.
On the sidewall of primary combustion section in one embodiment,, be provided with along axis direction the secondary combustion-supporting air duct being communicated with secondary combustion-supporting air intake.Can supply with in the outside of primary combustion section thus primary air and secondary combustion-supporting air simultaneously, improve the convenience that combustion air is supplied with.
In one embodiment, the aperture of mixed zone is not more than the aperture of primary combustion zone, and mixed zone is configured to be from inside to outside enlarging shape.Adopt the object of such structure to be, guarantee that fuel can fully mix in mixed zone with primary air, in the time burning in primary combustion zone, can guarantee that in addition primary combustion Duan Buhui bears excessive pressure.
In one embodiment, the aperture of primary combustion zone is less than the aperture of intermediate zone.Owing to importing secondary combustion-supporting air in intermediate zone, even burner hearth flue gas also can enter into wherein, and the aperture that the aperture of primary combustion zone is less than intermediate zone can guarantee that second-time burning Duan Buhui bears excessive pressure, guarantees the reliability of burner product.
In one embodiment, fuel inlet is gas nozzle, and primary air entrance is arranged at gas nozzle around.Be convenient to thus the supply of fuel, and can make primary air fully to mix with fuel.
In one embodiment, gas nozzle is silicon nitride combined silicon carbide material, and/or burner block is high temperature mould material.Improve the heat-resisting ability of burner.
According to a second aspect of the invention, also provide a kind of combustion system, this combustion system comprises combustion furnace and according to burner mentioned above, the burner hearth of combustion furnace is arranged at the inner side of second-time burning section.In the time adopting such combustion system to produce, the combustion flame producing in intermediate zone sprays in burner hearth.
It should be noted that, directional terminology used in the present invention " interior " refers to that in the time that burner is mounted on combustion furnace near the burner hearth of combustion furnace be " interior ", and is " outward " away from the direction of the burner hearth of combustion furnace.
Compared with prior art, the invention has the advantages that, the burner hearth flue gas that can by burner hearth exhaust gases passes entrainment combustion furnace while burning in intermediate zone enters into intermediate zone, has reduced thus the concentration of oxygen in intermediate zone.Burner hearth exhaust gases passes extends to the outer end of second-time burning section.Make thus the mist that enters into intermediate zone from primary combustion zone be mixed by secondary combustion-supporting air and burner hearth flue gas, thereby effectively reduce combustion flame oxygen concentration around simultaneously.Further, the connectivity part of burner hearth exhaust gases passes and intermediate zone is enlarging shape towards intermediate zone.Accelerate thus the diffusion of burner hearth flue gas in intermediate zone, be beneficial to the reduction of oxygen concentration in intermediate zone.
Accompanying drawing explanation
To be described in more detail the present invention based on embodiment and with reference to accompanying drawing hereinafter.Wherein:
Fig. 1 is the sectional view of burner according to a preferred embodiment of the present invention;
In the drawings, identical member is indicated by identical Reference numeral.Accompanying drawing is not according to actual scale.
The specific embodiment
Below in conjunction with accompanying drawing, the present invention will be further described.
As shown in Figure 1, the burner that the present invention proposes comprises primary combustion section 10 and second-time burning section 20, first fuel and primary air carry out primary combustion after the interior mixing of primary combustion section 10, and then enter into second-time burning section 20 and carry out second-time burning, secondary combustion-supporting air is directed in second-time burning section 20 and participates in second-time burning simultaneously.To describe burner of the present invention and each several part thereof below in detail.
It should be noted that, fuel of the present invention is gaseous fuel, and such as natural gas or coal gas etc. all can.In addition, the quantity delivered of primary air and secondary combustion-supporting air be less than respectively given fuel can the required combustion air total amount of completing combustion.As preferred example, primary air amount is about 50～60% of combustion air total amount, and secondary combustion-supporting air capacity is about 40～50% of combustion air total amount.
As shown in Figure 1, primary combustion section 10 is configured to the pipeline section of hollow, and primary combustion section 10 comprises mixed zone 11 and the primary combustion zone 12 that fluid is communicated with, and mixed zone 11 is near the outside of primary combustion section 10.The arranged outside of mixed zone 11 has fuel inlet and primary air entrance, and mixed zone 11 is for the mixing of fuel and primary air, and the direction of the arrow in figure in mixed zone 11 is the flow direction of fuel and primary air.Preferably, as shown in the figure, fuel inlet is gas nozzle 13.And primary air entrance 14 is arranged at gas nozzle 13 around, be convenient to thus fully mixing of combustion gas and primary air.Further, in figure, primary air entrance 14 places are provided with cyclone, and stronger eddy flow wind can be provided, and are beneficial to mixing of combustion gas and primary air.
As shown in Figure 1, second-time burning section 20 is configured to the pipeline section of hollow equally, and second-time burning section 20 is connected in the inner end of primary combustion section 10.Preferably, primary combustion section 10 and second-time burning section 20 can form as one.As shown in the figure, second-time burning section 20 comprises intermediate zone 21, and intermediate zone 21 is communicated with primary combustion zone 12 fluids.Fuel can not fully burn after completing primary combustion thus, enters into intermediate zone 21 from primary combustion zone 12, carries out second-time burning in intermediate zone 21.It should be noted that, the outside (namely near primary combustion zone) of intermediate zone 21 is provided with secondary combustion-supporting air intake 22, and in order to secondary combustion-supporting air to be provided, secondary combustion-supporting air participates in the second-time burning in intermediate zone.
While adopting burner of the present invention to produce, fuel is respectively at the interior burn incompletely in primary combustion zone 12 and intermediate zone 21, cause ignition temperature lower than theoretical temperature combustion, particularly in primary combustion zone 12, fuel overrich, primary combustion excess air coefficient is less than 1, cause ignition temperature lower than theoretical temperature combustion, the oxygen concentration that participates in addition burning is low, also has the reduction reaction of NO simultaneously, thereby reduced to a certain extent the generation of NOx in flame.
As shown in Figure 1, as preferred embodiment, burner hearth exhaust gases passes 23 is set on the sidewall of second-time burning section 20, burner hearth exhaust gases passes 23 fluids are communicated with inner side and the intermediate zone 21 of second-time burning section 20.As can be seen from the figure, the inner end of intermediate zone 21 opens wide, and sprays in burner hearth for flame and the high-temperature flue gas of fuel second-time burning.And the burner hearth flue gas that can entrainment combustion furnace by burner hearth exhaust gases passes 23 that arranges can burn in intermediate zone time of burner hearth exhaust gases passes 23 enters into intermediate zone 21, therefore the oxygen concentration of sneaking into while making second-time burning of burner hearth flue gas reduces, thereby the flame temperature that has suppressed fuel second-time burning, has therefore reduced the generation of NOx effectively.
Preferably, as shown in the figure, burner hearth exhaust gases passes 23 extends to the outer end of second-time burning section 20.The direction of arrow in figure in burner hearth exhaust gases passes 23 is the flow direction of burner hearth flue gas, make thus the mist that enters into intermediate zone 21 from primary combustion zone 12 be mixed by secondary combustion-supporting air and burner hearth flue gas, thereby effectively reduce combustion flame oxygen concentration around simultaneously.Further, burner hearth exhaust gases passes 23 is enlarging shape with the connectivity part 24 of intermediate zone 21 towards intermediate zone 21.In figure, the direction of arrow of connectivity part 24 is the flow direction of burner hearth flue gas, thereby accelerates the diffusion of burner hearth flue gas in intermediate zone 21, is beneficial to the reduction of intermediate zone 21 interior oxygen concentrations.
As preferred embodiment, on the sidewall of primary combustion section 10, be provided with along axis direction the secondary combustion-supporting air duct 16 being communicated with secondary combustion-supporting air intake 22.The direction of arrow in figure in secondary combustion-supporting air duct 16 is the flow direction of secondary combustion-supporting air, can supply with in the outside of primary combustion section 10 thus primary air and secondary combustion-supporting air simultaneously, improves the convenience that combustion air is supplied with.
Preferably, the aperture of mixed zone 11 is not more than the aperture of primary combustion zone 12, and can guarantee to burn in primary combustion zone time, primary combustion section 10 can not born excessive pressure.In addition, mixed zone 11 is configured to be from inside to outside enlarging shape.Guarantee that fuel can fully mix in mixed zone with primary air.In addition, mixed zone 11 makes the root (near the position of primary combustion zone) of primary combustion zone form a smoke backflow district 15 with the gap in the aperture of primary combustion zone 12, is beneficial to the flame stabilization of primary combustion.In the case of adopting the primary air of eddy flow wind, burning regulates than being improved.
Be understandable that, as shown in Figure 1, the aperture of primary combustion zone 12 is less than the aperture of intermediate zone 21.Due to intermediate zone 21 interior importing secondary combustion-supporting air, even burner hearth flue gas also can enter into wherein, and the aperture that the aperture of primary combustion zone 12 is less than intermediate zone 21 can guarantee that second-time burning section 20 can not bear excessive pressure.In addition, as shown in the figure, form secondary flue gas recirculating zone 25 because the gap in the aperture of primary combustion zone 12 and intermediate zone 21 makes the root (by the position of mixed zone only) of intermediate zone, thereby be beneficial to the flame stabilization of second-time burning, be beneficial to the adjusting of burning.
Further, gas nozzle 13 is silicon nitride combined silicon carbide material.Burner block is high temperature mould material.Improve thus the heat-resisting ability of burner.For example, maximum operation (service) temperature can reach 1700 ℃.
According to a second aspect of the invention, also provide a kind of combustion system, this combustion system comprises combustion furnace and according to burner mentioned above, the burner hearth of combustion furnace is arranged at the inner side of second-time burning section.In the time adopting such combustion system to produce, the combustion flame and the high-temperature flue gas that in intermediate zone, produce spray in burner hearth.Contrast prior art, in order to make the fire box temperature of combustion furnace reach 1200 ℃, while adopting burner of the present invention to carry out high-temp combustion in the situation that of air pre-mixing coefficient a=1, NOx discharge capacity is low to moderate 500ppm, and the discharge capacity of NOx reduces by 90%.
Although invention has been described with reference to preferred embodiment, without departing from the scope of the invention, can carry out various improvement and can replace parts wherein with equivalent it.The present invention is not limited to disclosed specific embodiment in literary composition, but comprises all technical schemes in the scope that falls into claim.
Claims (10)
1. a burner, is characterized in that, comprising:
Primary combustion section, it is configured to the pipeline section of hollow, and comprises mixed zone and primary combustion zone that fluid is communicated with, and described mixed zone is near the outside of described primary combustion section;
Second-time burning section, the inner end that it is configured to the pipeline section of hollow and is connected in described primary combustion section, it comprises intermediate zone, described intermediate zone is communicated with described primary combustion zone fluid;
Wherein, the arranged outside of described mixed zone has fuel inlet and primary air entrance, and the arranged outside of described intermediate zone has secondary combustion-supporting air intake.
2. burner according to claim 1, is characterized in that, is provided with the burner hearth exhaust gases passes that fluid is communicated with inner side and the described intermediate zone of described second-time burning section on the sidewall of described second-time burning section.
3. burner according to claim 2, is characterized in that, described burner hearth exhaust gases passes extends to the outer end of described second-time burning section.
4. burner according to claim 3, is characterized in that, the connectivity part of described burner hearth exhaust gases passes and described intermediate zone is enlarging shape towards described intermediate zone.
5. burner according to claim 1, is characterized in that, on the sidewall of described primary combustion section, is provided with along axis direction the secondary combustion-supporting air duct being communicated with described secondary combustion-supporting air intake.
6. burner according to claim 1, is characterized in that, the aperture of described mixed zone is not more than the aperture of described primary combustion zone, and described mixed zone is configured to be from inside to outside enlarging shape.
7. according to the burner described in any one in claim 1 to 6, it is characterized in that, the aperture of described primary combustion zone is less than the aperture of described intermediate zone.
8. burner according to claim 1, is characterized in that, described fuel inlet is gas nozzle, and described primary air entrance is arranged at described gas nozzle around.
9. burner according to claim 8, is characterized in that, described gas nozzle is silicon nitride combined silicon carbide material, and/or burner block is high temperature mould material.
10. a combustion system, is characterized in that, described combustion system comprises combustion furnace and according to the burner described in any one in claim 1 to 9, the burner hearth of described combustion furnace is arranged at the inner side of described second-time burning section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410135512.9A CN103868065B (en) | 2014-04-04 | 2014-04-04 | Combustor and combustion system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410135512.9A CN103868065B (en) | 2014-04-04 | 2014-04-04 | Combustor and combustion system |
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| Publication Number | Publication Date |
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| CN103868065A true CN103868065A (en) | 2014-06-18 |
| CN103868065B CN103868065B (en) | 2017-02-15 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410135512.9A Active CN103868065B (en) | 2014-04-04 | 2014-04-04 | Combustor and combustion system |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106838900A (en) * | 2017-02-20 | 2017-06-13 | 海湾环境科技（北京）股份有限公司 | Burner and fuel gas buring method |
| CN110242952A (en) * | 2019-05-30 | 2019-09-17 | 国电浙江北仑第一发电有限公司 | A kind of low cooling air quantity burner using composite material spout |
| CN106838900B (en) * | 2017-02-20 | 2024-05-24 | 海湾环境科技（北京）股份有限公司 | Burner and gas combustion method |
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| US5735681A (en) * | 1993-03-19 | 1998-04-07 | The Regents, University Of California | Ultralean low swirl burner |
| US5957682A (en) * | 1996-09-04 | 1999-09-28 | Gordon-Piatt Energy Group, Inc. | Low NOx burner assembly |
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| CN101315187A (en) * | 2008-06-26 | 2008-12-03 | 天时燃烧设备（苏州）有限责任公司 | Anti-flashback nozzle and combustion device with the same |
| CN202902281U (en) * | 2012-10-15 | 2013-04-24 | 江苏焱鑫科技股份有限公司 | Back-mixing type multi-level burning low nitric oxide (NOx) gas burner |
| CN103277795A (en) * | 2013-05-27 | 2013-09-04 | 中国科学院广州能源研究所 | Gas burner capable of adjusting gas to be self-recycling |
| CN203893179U (en) * | 2014-04-04 | 2014-10-22 | 湖南巴陵炉窑节能股份有限公司 | Combustor and combustion system |
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2014
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| Publication number | Priority date | Publication date | Assignee | Title |
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| EP0374423A2 (en) * | 1988-12-20 | 1990-06-27 | John Zink Gmbh | Atmospheric burner |
| US5735681A (en) * | 1993-03-19 | 1998-04-07 | The Regents, University Of California | Ultralean low swirl burner |
| US5957682A (en) * | 1996-09-04 | 1999-09-28 | Gordon-Piatt Energy Group, Inc. | Low NOx burner assembly |
| CN2743702Y (en) * | 2004-10-22 | 2005-11-30 | 中国石化集团洛阳石油化工工程公司 | High temperature combustion supporting air top burning energy saving environmental protection burner |
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| CN203893179U (en) * | 2014-04-04 | 2014-10-22 | 湖南巴陵炉窑节能股份有限公司 | Combustor and combustion system |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106838900A (en) * | 2017-02-20 | 2017-06-13 | 海湾环境科技（北京）股份有限公司 | Burner and fuel gas buring method |
| CN106838900B (en) * | 2017-02-20 | 2024-05-24 | 海湾环境科技（北京）股份有限公司 | Burner and gas combustion method |
| CN110242952A (en) * | 2019-05-30 | 2019-09-17 | 国电浙江北仑第一发电有限公司 | A kind of low cooling air quantity burner using composite material spout |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103868065B (en) | 2017-02-15 |
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