CN112856416A - Semi-premixing internal circulation low-nitrogen combustor - Google Patents
Semi-premixing internal circulation low-nitrogen combustor Download PDFInfo
- Publication number
- CN112856416A CN112856416A CN202110224750.7A CN202110224750A CN112856416A CN 112856416 A CN112856416 A CN 112856416A CN 202110224750 A CN202110224750 A CN 202110224750A CN 112856416 A CN112856416 A CN 112856416A
- Authority
- CN
- China
- Prior art keywords
- gas
- channel
- layer
- layer gas
- air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
- F23D14/04—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone induction type, e.g. Bunsen burner
-
- 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
- F23D14/26—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid with provision for a retention flame
-
- 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
-
- 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
- F23D14/48—Nozzles
- F23D14/58—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
- F23D2900/14—Special features of gas burners
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
Abstract
本发明提供一种半预混内循环低氮燃烧器，包括：耐火浇注料环形台，耐火浇注料环形台内侧形成有空气通道；内燃气通道；内燃气空气混合通道；中层燃气通道；中层燃气环；中层燃气喷口；外层燃气通道；外层燃气环；外层燃气喷口。内燃气通道及内燃气空气混合通道的设置，使燃气与空气起到预混的作用。中层燃气环及外层燃气环上设置有细密的燃气喷口，燃气以高速从燃气喷口喷出，喷出的高速的燃气具有较高的动能，可卷吸周围烟气，在燃气与空气混合燃烧之前，该喷口所处区域未设置助燃空气，燃气就在缺氧环境下分解成还原性物质CO、H+等，且燃气的浓度得到一定程度的降低，从而降低燃料热值，由此燃气与空气相结合进行燃烧时，燃烧峰值温度较低。
The invention provides a semi-premixed inner-circulation low-nitrogen burner, comprising: a refractory castable annular platform, an air channel is formed inside the refractory castable annular platform; an inner gas channel; an inner gas-air mixing channel; a middle-layer gas channel; a middle-layer gas channel ring; middle layer gas nozzle; outer layer gas channel; outer layer gas ring; outer layer gas nozzle. The setting of the inner gas channel and the inner gas-air mixing channel makes the gas and air play a role of premixing. There are fine gas nozzles on the middle gas ring and the outer gas ring. The gas is ejected from the gas nozzle at a high speed. The high-speed gas ejected has high kinetic energy, which can entrain the surrounding smoke and burn when the gas and air are mixed. Before, there was no combustion air in the area where the nozzle was located, and the gas was decomposed into reducing substances CO, H+, etc. in an oxygen-deficient environment, and the concentration of the gas was reduced to a certain extent, thereby reducing the calorific value of the fuel. When combined for combustion, the combustion peak temperature is lower.
Description
Technical Field
The invention relates to the technical field of emission reduction of boilers and industrial furnaces, in particular to a semi-premixed internal circulation low-nitrogen combustor.
Background
Nitrogen oxides, as a pollutant with great harm, are an important pushing hand for causing acid rain and haze. The existing nitrogen reduction means in the field of industrial boilers can be wholly divided into combustion method nitrogen reduction and flue gas post-treatment nitrogen reduction. The combustion method is used for reducing nitrogen, namely the generation amount of nitrogen oxides is reduced in the combustion process, and the flue gas after-treatment is used for reducing nitrogen, namely the flue gas after combustion is treated to reduce the emission of the nitrogen oxides. Compared with the nitrogen reduction by flue gas post-treatment, the combustion method has the advantages of small investment, almost no need of extra operation cost, no secondary pollution and the like.
The nitrogen oxide emission of natural gas boilers required by a plurality of provinces and cities in China is as low as 30mg/Nm3. For the fuel with relatively clean high heat value like natural gas, the generated nitrogen oxide during combustion is mostly thermal nitrogen oxide, and the common and effective means for reducing nitrogen by the fuel combustion method are diffusion combustion and the cooperation of a flue gas recirculation technology and a full-premix surface combustion technology. The existing flue gas recirculation technology has the problem of condensate water in the application process, the existing flue gas recirculation has certain influence on the thermal efficiency of the boiler, and the vibration problem of the boiler is easily caused by uneven mixing of the added external circulation flue gas; the full-premixing surface combustion technology is that fuel and combustion-supporting air are premixed and then combusted, the requirement on air distribution is strict, too much oxygen can influence the combustion stability, and even safety accidents occur.
Disclosure of Invention
To achieve the above and other related objects, the present invention provides a semi-premixed internal circulation low nitrogen combustor, comprising: a refractory castable annular table including opposing first and second surfaces, an air channel formed inside the refractory castable annular table, the air channel extending from the first surface to the second surface; an inner air passage within the air passage extending from the first surface into the air passage; an inner gas-air mixing passage located in the air passage, one end of the inner gas-air mixing passage being connected to the inner gas passage, and the other end of the inner gas-air mixing passage extending downstream of the second surface; the middle-layer gas channel is positioned in the refractory castable annular table and extends from the first surface to the second surface; the middle layer gas ring is positioned on the second surface, surrounds the periphery of the air channel, is communicated with the middle layer gas channel and corresponds to the middle layer gas channel one to one; the middle layer gas nozzle is positioned on the middle layer gas ring and communicated with the middle layer gas ring; an outer layer gas channel located within the refractory castable annular table, the outer layer gas channel extending from the first surface to the second surface; the outer layer gas ring is positioned on the second surface, surrounds the periphery of the middle layer gas ring, is communicated with the outer layer gas channel and corresponds to the outer layer gas channel one by one; and the outer layer gas nozzle is positioned on the outer layer gas ring and communicated with the outer layer gas ring.
Optionally, the internal combustion air channel and the internal combustion air mixing channel are both multiple, and the internal combustion air channel and the internal combustion air mixing channel are arranged in a one-to-one correspondence manner; the plurality of internal combustion air channels and the plurality of internal combustion air mixing channels are arranged at intervals by taking the central line of the semi-premixed internal circulation low-nitrogen combustor as an axis.
Optionally, the inner combustion air passage is a tapered passage, and a flow area of an end of the inner combustion air passage communicating with the inner combustion air mixing passage is smallest.
Optionally, an outlet of the internal combustion air mixing channel is a bent portion, and the bent portion is bent towards the direction of the annular refractory castable platform; the included angle between the bending part and the central line of the semi-premixing inner circulation low-nitrogen combustor is 30-90 degrees.
Optionally, the middle layer gas nozzles and the outer layer gas nozzles are multiple, the middle layer gas nozzles are arranged along the circumferential direction of the middle layer gas ring, and the outer layer gas nozzles are arranged along the circumferential direction of the outer layer gas ring.
Optionally, the angle between the injection direction of the outer layer gas nozzle and the central line of the semi-premixed inner circulation low-nitrogen combustor is-10 to 60 degrees; the angle between the injection direction of the middle layer gas nozzle and the central line of the semi-premixed low-nitrogen burner is 10-70 degrees.
Optionally, the refractory castable annular table comprises a first refractory castable annular table layer, a second refractory castable annular table layer and a third refractory castable annular table layer which are sequentially stacked from outside to inside; the outer layer gas channel and the middle layer gas channel are both positioned in the first layer of the refractory castable annular table; and the spraying direction of the outer layer gas nozzle and the spraying direction of the middle layer gas nozzle face the second layer of the refractory castable annular table.
Optionally, the second surface of the second layer of refractory castable annular table includes an inclined surface and a horizontal surface, the inclined surface extending from the first layer of refractory castable annular table to the horizontal surface of the second layer of refractory castable annular table; the inclination angle of the inclined plane is 30-60 degrees; the second surface of the second layer of the refractory castable annular table is provided with a first annular groove, the second surface of the third layer of the refractory castable annular table is provided with a second annular groove, the second annular groove surrounds the periphery of the air channel, and the first annular groove surrounds the periphery of the second annular groove.
Optionally, the inner wall of the refractory castable annular table comprises a sloped inner wall such that the diameter of the opening of the air channel at the second surface is greater than the diameter of the opening at the first surface.
Optionally, the flame stabilizing device further comprises a flame stabilizing disc, wherein the flame stabilizing disc is positioned at the downstream of the air channel, the flame stabilizing disc is provided with swirl vanes and through holes, the through holes are communicated with the air channel, and the swirl vanes are positioned at the periphery of the through holes; the inner gas-air mixing channel is positioned on the outer side of the flame stabilizing disc.
As mentioned above, the semi-premixing internal circulation low-nitrogen combustor has the following beneficial effects:
the arrangement of the internal gas channel and the internal gas-air mixing channel leads the gas and the air to play a role of premixing.
The middle-layer gas ring and the outer-layer gas ring are provided with fine gas nozzles, gas is sprayed out from the gas nozzles at high speed, the sprayed high-speed gas has high kinetic energy and can entrain surrounding smoke, combustion-supporting air is not arranged in the area where the nozzles are located before the gas and air are mixed and combusted, the gas is decomposed into reducing substances such as CO and H + in an oxygen-deficient environment, the concentration of the gas is reduced to a certain degree, and therefore the heat value of the fuel is reduced, when the gas and the air are combined to combust, the combustion peak temperature is low, and the generation of nitrogen oxides can be effectively reduced through the above mode.
Most of the fuel gas is sprayed out from the middle layer fuel gas nozzles and the outer layer fuel gas nozzles, little premixed fuel gas is sprayed in the central area of the burner, the flame is hollow due to the structure, namely no flame is generated at the root and the center of the whole flame, and therefore the temperature of the central area of the burning can be effectively controlled, and the generation of thermal nitrogen oxides is reduced.
In the embodiment, the internal gas channel is arranged in the air channel, the rear end of the internal gas channel is connected with the internal gas-air mixing device, and the rear end of the internal gas channel is provided with a section of tapered opening and a section of straight section. Because venturi effect, the gas velocity of flow is high including gas channel throat department, forms the environment of relative negative pressure, makes the air in the air passage get into in the gas-air mixture channel more easily, and including gas-air mixture channel carries out premixed combustion partly gas and air. The premixed combustion temperature is more uniform, the combustion peak temperature is lower, and the generation of thermal nitrogen oxides can be effectively reduced. The premixing gun can also play a role in stabilizing the main flame and provide a heat source for the outer layer fuel.
The middle layer gas nozzle and the outer layer gas nozzle respectively spray fuel to the combustion area at a certain angle, so that the structure avoids the over concentration of the fuel spraying area, the combustion space can be effectively utilized, the combustion temperature is more average, and the generation of thermal nitrogen oxide is reduced.
The arrangement of the plurality of gas nozzles realizes multi-stage combustion, and the injection of the plurality of gas nozzles makes the fuel injection more uniform; and the fuel and the flue gas can be better mixed by injecting the fuel gas through the plurality of nozzles, the heat value of the fuel is reduced as much as possible, the combustion speed is further effectively controlled, and the generation of thermal nitrogen oxides is reduced.
The air channel is a flaring device, and the structure can enable air to diffuse and enter a combustion area, so that the combustion space is fully utilized, the fullness of the hearth is better, and the combustion temperature is more average.
A flame stabilizing disc is arranged at the downstream of the air channel, negative pressure is formed at the rear end of the flame stabilizing disc due to the flame stabilizing disc, high-temperature flue gas can be sucked by the negative pressure, and internal circulation of the flue gas is realized. The internal circulation of the flue gas can reduce the temperature and the oxygen content of a combustion area, thereby reducing the combustion peak value and further reducing the generation of thermal nitrogen oxides. The flame stabilizing disc is also provided with swirl blades which can increase the kinetic energy of air in the radial direction and enhance the mixing of the air and the fuel gas.
The refractory castable annular table is divided into three layers, and the refractory castable of the three-layer protruding part has the functions of heat storage and stable combustion, so that flame can be stably combusted under the oxygen content of 0-3%. And annular grooves are formed in the second layer and the third layer of the refractory castable annular table, the annular grooves can effectively increase the rotational flow of the flue gas, can increase the mixing time and effect of the fuel gas and the flue gas, further reduce the heat value of the fuel gas and control the generation of thermal nitrogen oxides.
Drawings
FIG. 1 is a top view of a semi-premixed internal circulation low NOx combustor provided by the present invention.
FIG. 2 is a cross-sectional view along AA in FIG. 1 of a semi-premixed internal circulation low NOx burner provided by the present invention.
FIG. 3 is a gas flow directed graph of a semi-premixed inner cycle low nitrogen combustor provided by the present invention.
FIG. 4 is an enlarged schematic view of the middle layer gas ring and the middle layer gas nozzle in the semi-premixed inner circulation low-NOx burner provided by the invention.
FIG. 5 is a schematic structural diagram of an inner gas passage and an inner gas-air mixing passage in a semi-premixed inner circulation low-nitrogen combustor provided by the invention.
FIG. 6 is an enlarged schematic view of an outer layer gas ring and an outer layer gas nozzle in the semi-premixed inner circulation low-nitrogen combustor provided by the invention.
FIG. 7 is a partial cross-sectional view of a castable annular table in a semi-premixed inner circulation low-nitrogen combustor provided by the present invention.
Element number description: 1. 101, a first layer and 102 of a refractory castable annular table, a second layer of the refractory castable annular table, 1021 a first annular groove, 103, a third layer of the refractory castable annular table, 1031, a second annular groove, 2, an outer layer gas ring, 3, an outer layer gas nozzle, 4, a middle layer gas ring, 5, a middle layer gas nozzle, 6, an inner gas channel, 7, an inner gas-air mixing channel, 8, an air channel, 9, a flame stabilizing disc, 10, an inner gas-air mixing channel wall, 11, an outer layer gas channel and 12 a middle layer gas channel.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The preferred embodiments in the following description are given by way of example only, and other obvious variations will occur to those skilled in the art. The basic principles of the invention, as defined in the following description, may be applied to other embodiments, variations, modifications, equivalents, and other technical solutions without departing from the spirit and scope of the invention.
It will be understood by those skilled in the art that in the present disclosure, the terms "longitudinal," "lateral," "up," "down," "front," "back," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "upstream," "downstream," and the like are used in a generic and descriptive sense only and not for purposes of limitation, as the terms are used to indicate or imply that the referenced devices or components must be in a particular orientation, construction and operation, and are not necessarily to be limiting.
As mentioned above, the nitrogen reduction means in the field of industrial boilers can be generally divided into combustion method nitrogen reduction and flue gas post-treatment nitrogen reduction. The combustion method is used for reducing nitrogen, namely the generation amount of nitrogen oxides is reduced in the combustion process, and the flue gas after-treatment is used for reducing nitrogen, namely the flue gas after combustion is treated to reduce the emission of the nitrogen oxides. Compared with the nitrogen reduction by flue gas post-treatment, the combustion method has the advantages of small investment, almost no need of extra operation cost, no secondary pollution and the like. For the fuel with relatively clean high heat value like natural gas, the generated nitrogen oxide during combustion is mostly thermal nitrogen oxide, and the common and effective means for reducing nitrogen by the fuel combustion method are diffusion combustion and the cooperation of a flue gas recirculation technology and a full-premix surface combustion technology. The flue gas recirculation technology has the condensate water problem in the application process, the flue gas recirculation has certain influence on the thermal efficiency of the boiler, and the added external circulation flue gas is easy to cause the vibration problem of the boiler due to uneven mixing; the full-premixing surface combustion technology is that fuel and combustion-supporting air are premixed and then combusted, the requirement on air distribution is strict, too much oxygen can influence the combustion stability, and even safety accidents occur.
Example one
Referring to fig. 1 to 2, the present invention provides a semi-premixed internal circulation low-nitrogen combustor, comprising: the refractory castable annular table 1 comprises a first surface and a second surface which are opposite, wherein the first surface is a front end upstream surface, the second surface is a rear end downstream surface, an air channel 8 is formed on the inner side of the refractory castable annular table 1, and the air channel 8 extends from the first surface to the second surface; an inner air passage 6 located within the air passage 8, extending from the first surface into the air passage 8; an inner combustion air-air mixing passage 7 located in the air passage 8, one end of which is connected with the inner combustion air passage 6, and the other end of which extends to the downstream of the second surface; the middle-layer gas channel 12 is positioned in the refractory castable annular table 1, and the middle-layer gas channel 12 extends from the first surface to the second surface; the middle layer gas ring 4 is positioned on the second surface, surrounds the periphery of the air channel 8, is communicated with the middle layer gas channel 12 and corresponds to the middle layer gas channel 12 one by one; the middle-layer gas nozzle 5 is positioned on the middle-layer gas ring 4 and communicated with the middle-layer gas ring 4; the outer layer gas channel 11 is positioned in the refractory castable annular table 1, and the outer layer gas channel 11 extends from the first surface to the second surface; the outer layer gas ring 2 is positioned on the second surface, surrounds the periphery of the middle layer gas ring 4, is communicated with the outer layer gas channel 11, and corresponds to the outer layer gas channel 11 one by one; and the outer layer gas nozzle 3 is positioned on the outer layer gas ring 2 and communicated with the outer layer gas ring 2.
Through the setting of interior gas passageway 6 and interior gas-air mixture passageway 7 in the semi-premix inner loop low NOx burner in this application, make gas and air play the effect of premixing. The middle layer gas ring 4 and the outer layer gas ring 2 are provided with fine gas nozzles, gas is sprayed out from the gas nozzles at high speed, the sprayed high-speed gas has high kinetic energy and can entrain surrounding smoke, combustion-supporting air is not arranged in the area where the nozzles are located before the gas and air are mixed and combusted, the gas is decomposed into reducing substances such as CO and H + in an oxygen-deficient environment, the concentration of the gas is reduced to a certain degree, and therefore the heat value of the fuel is reduced, when the gas and the air are combined to combust, the combustion peak temperature is low, and therefore the generation of nitrogen oxides can be reduced. Most of the fuel gas is sprayed out from the middle layer fuel gas nozzles and the outer layer fuel gas nozzles, little premixed fuel gas is sprayed in the central area of the burner, the flame is hollow due to the structure, namely no flame is generated at the root and the center of the whole flame, and therefore the temperature of the central area of the burning can be effectively controlled, and the generation of thermal nitrogen oxides is reduced. Flue gas is not needed to be circulated externally, the condition of uneven mixing of flue gas and air is avoided, and the problem of boiler vibration is avoided; the premixing combustion of the non-metal net in the traditional mode has no strict requirement on air distribution, and the combustion stability cannot be influenced due to too much and too little oxygen, so that safety accidents are avoided.
Example two
Referring to fig. 2 to 7 in conjunction with fig. 1, the present embodiment further provides a semi-premixed inner circulation low-nitrogen burner, and the semi-premixed inner circulation low-nitrogen burner in the present embodiment further includes the following structure compared to the semi-premixed inner circulation low-nitrogen burner in the first embodiment:
as an example, the internal combustion gas channel 6 and the internal combustion air mixing channel 7 are both multiple, and the internal combustion gas channel 6 and the internal combustion air mixing channel 7 are arranged in a one-to-one correspondence manner; the plurality of internal combustion air channels 6 and the plurality of internal combustion air mixing channels 7 are circumferentially arranged by taking the center line of the semi-premixed internal circulation low-nitrogen combustor as an axis.
As an example, the internal combustion air passage 6 is a tapered passage, and a flow area of an end of the internal combustion air passage 6 that communicates with the internal combustion air mixing passage 7 is smallest. Namely, the rear end of the inner gas channel 6 is provided with a section of tapered mouth and a section of straight section. Because of the Venturi effect, the gas flow rate is high at the necking part of the inner gas channel 6, and an environment with relative negative pressure is formed, so that air with higher pressure in the air channel 8 easily flows into the negative pressure area, the air in the air channel 8 more easily enters the inner gas-air mixing channel 7, and partial gas and air are premixed and combusted in the inner gas-air mixing channel 7, and a partial premixing effect is formed. The premixed combustion temperature is more uniform, the formation of a local high-temperature area is avoided, the combustion peak temperature is lower, and the generation of thermal nitrogen oxides can be effectively reduced. The premixing gun can also play a role in stabilizing the main flame and provide a heat source for the outer layer fuel. And the air outside the inner gas-air mixing channel 7 has a certain cooling effect on the inner gas-air mixing channel wall 10, so that the burning out of the inner gas-air mixing channel wall can be avoided.
By way of example, the inner combustion air channel 6 and the inner combustion air mixing channel 7 constitute a premix assembly.
As an example, as shown in fig. 5, the outlet of the internal combustion air mixing channel 7 is a bent portion, and the bent portion is bent toward the direction of the annular refractory castable platform 1; the included angle alpha between the bending part and the central line of the semi-premixing inner circulation low-nitrogen combustor is 30-90 degrees.
As an example, the middle layer gas nozzles 5 and the outer layer gas nozzles 3 are both multiple, the multiple middle layer gas nozzles 5 are arranged along the circumferential direction of the middle layer gas ring 4, and the multiple outer layer gas nozzles 3 are arranged along the circumferential direction of the outer layer gas ring 2. Specifically, the fuel is sprayed to a combustion area through the outer layer gas nozzles 3 and the middle layer gas nozzles 5, so that the fuel is sprayed in multiple stages, multi-stage combustion is realized, the fuel and flue gas can be better mixed, the combustion reaction speed is effectively controlled, the combustion peak temperature is reduced, and the combustion temperature is more average; and the fuel passes through the jet direction difference of outer layer gas spout 3 and middle level gas spout 5, has effectually used the combustion space, can make flame fill up the furnace, makes the oven fully absorb the heat, can reduce the burning peak temperature and then reduce the formation of nitrogen oxide, has improved the thermal efficiency again. The arrangement of the plurality of gas nozzles realizes multi-stage combustion, and the injection of the plurality of gas nozzles makes the fuel injection more uniform; and the fuel and the flue gas can be better mixed by injecting the fuel gas through the plurality of nozzles, the heat value of the fuel is reduced as much as possible, the combustion speed is further effectively controlled, and the generation of thermal nitrogen oxides is reduced.
As an example, the angle γ between the injection direction of the outer layer gas nozzle 3 and the central line of the semi-premixed inner circulation low-nitrogen burner is-10 ° to 60 °, as shown in fig. 6; the angle beta between the injection direction of the middle layer gas nozzle 5 and the central line of the semi-premixed low-nitrogen burner is 10-70 degrees, as shown in fig. 4. The middle layer gas nozzle 5 and the outer layer gas nozzle 3 respectively spray fuel to the combustion area at a certain angle, so that the structure avoids the over concentration of the fuel spraying area, the combustion space can be effectively utilized, the combustion temperature is more average, and the generation of thermal nitrogen oxide is reduced.
As an example, the refractory castable annular table 1 comprises a first refractory castable annular table layer 101, a second refractory castable annular table layer 102 and a third refractory castable annular table layer 103 which are sequentially stacked from outside to inside; the outer layer gas channel 11 and the middle layer gas channel 12 are both positioned in the first layer 101 of the refractory castable annular table; the spraying direction of the outer layer gas nozzle 3 and the spraying direction of the middle layer gas nozzle 5 both face the second layer 102 of the refractory castable annular table.
Specifically, the refractory castable annular table 1 is divided into a first refractory castable annular table layer 101, a second refractory castable annular table layer 102 and a third refractory castable annular table layer 103, and the refractory castable has heat storage capacity, so that heat around the refractory castable annular table 1 is sufficient, sufficient ignition heat can be provided for fuel, and a strong combustion stabilizing effect is achieved. The first layer 101, the second layer 102 and the third layer 103 of the castable refractory annular table 1 are protruded to increase the heat storage area, so that the heat storage capacity of the castable refractory annular table 1 is enhanced. The stable combustion structure enables the flame to be stably combusted under the condition of 0-3% of oxygen content.
By way of example, the second surface of the second layer 102 of refractory castable annular table includes an inclined surface and a horizontal surface, the inclined surface extending from the first layer of refractory castable annular table to the horizontal surface of the second layer of refractory castable annular table; the inclination angle delta of the inclined plane is 30-60 degrees, as shown in figure 7; a first annular groove 1021 is formed in the second surface of the second layer 102 of the castable refractory annular table, a second annular groove 1031 is formed in the second surface of the third layer 103 of the castable refractory annular table, the second annular groove 1031 surrounds the periphery of the air passage 8, and the first annular groove 1021 surrounds the periphery of the second annular groove 1031.
Specifically, as shown in fig. 3, there is no air radially outside the refractory castable annular table 1, so there is only flue gas around the gas ejected from the outer layer gas nozzles 3 and the middle layer gas nozzles 5, and the fuel is in an oxygen-deficient environment after being ejected. The outer layer gas nozzle 3 and the middle layer gas nozzle 5 are small in size, the speed of gas passing through the outer layer gas nozzle 3 and the middle layer gas nozzle 5 is large, the kinetic energy of gas flow is large, surrounding smoke can be sucked into the gas flow, the first annular groove 1021 and the second annular groove 1031 can enhance the vortex of the gas flow, and the gas is further enhanced to be mixed with the smoke and simultaneously cracked into reducing substances such as CO and H +. The structure can effectively dilute the fuel gas to a certain degree, further reduce the combustion peak temperature and reduce the generation of thermal nitrogen oxides.
By way of example, the inner wall of the refractory castable annular table 1 comprises an inclined inner wall such that the diameter of the opening of the air channel 8 at the second surface is greater than the diameter of the opening at the first surface.
Specifically, air passageway 8 is the flaring structure, and flow area is bigger and bigger in the gas flow direction, and this structure can make the air diffusion get into the combustion area, make full use of combustion space, and furnace flame fullness is better, makes combustion temperature more even, not only reduces the formation of nitrogen oxide and can also improve the thermal efficiency of stove.
As an example, the flame stabilizing device further comprises a flame stabilizing disc 9, wherein the flame stabilizing disc 9 is located at the downstream of the air channel 8, a rotational flow blade and a through hole are arranged on the flame stabilizing disc 9, the through hole is communicated with the air channel 8, and the rotational flow blade is located at the periphery of the through hole; the inner gas-air mixing channel 7 is positioned on the outer side of the flame stabilizing disc 9.
Specifically, the flame stabilizing disc 9 is arranged at the rear end of the air channel 8, and the center line of the flame stabilizing disc 9 is superposed with the center line of the semi-premixing internal circulation low-nitrogen combustor. The flame stabilizing disc 9 blocks airflow, so that negative pressure is formed at the rear end of the flame stabilizing disc, and the smoke can be sucked by the negative pressure, so that the internal circulation of the smoke is realized. The internal circulation of the flue gas can reduce the temperature and the oxygen content of a combustion area, thereby reducing the combustion peak value and further reducing the generation of thermal nitrogen oxides. The flame stabilizing disc 9 is also provided with swirl blades which can increase the kinetic energy of air in the radial direction, enhance the mixing of air and fuel gas, realize uniform combustion, and can form central negative pressure for further smoking.
The invention combines the technical means of flue gas internal circulation, staged combustion, semi-premixing, heat storage and stable combustion and the like, and the hollow design of flame can effectively reduce the combustion temperature, and can realize that the emission of nitrogen oxides at 30mg/Nm can be realized without using flue gas external circulation and flameless combustion when high heat value of combustion is relatively clean fuel3The following. The low-nitrogen burner has low-nitrogen combustion characteristic, the flame in the hearth is full, and the heat efficiency of the furnace can be improved.
It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be combined as appropriate to form other embodiments understood by those skilled in the art.
Claims (10)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110224750.7A CN112856416B (en) | 2021-03-01 | 2021-03-01 | Semi-premixed internal circulation low nitrogen burner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110224750.7A CN112856416B (en) | 2021-03-01 | 2021-03-01 | Semi-premixed internal circulation low nitrogen burner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112856416A true CN112856416A (en) | 2021-05-28 |
| CN112856416B CN112856416B (en) | 2025-09-30 |
Family
ID=75990698
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110224750.7A Active CN112856416B (en) | 2021-03-01 | 2021-03-01 | Semi-premixed internal circulation low nitrogen burner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112856416B (en) |
Citations (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0488481A1 (en) * | 1990-11-30 | 1992-06-03 | Remeha Fabrieken B.V. | Low NOx gas burner |
| EP1391657A2 (en) * | 2002-08-22 | 2004-02-25 | Hitachi, Ltd. | Gas turbine combustor, combustion method of the gas turbine combustor, and method of remodeling a gas turbine combustor |
| KR20040040577A (en) * | 2002-11-07 | 2004-05-13 | 한국에너지기술연구원 | premix type knitted metal fiber mat gas burner |
| CN101349425A (en) * | 2007-07-16 | 2009-01-21 | 通用电气公司 | Apparatus/method for cooling the combustion chamber/venturi in a low NOx burner |
| CN101603687A (en) * | 2008-06-11 | 2009-12-16 | 钱志鸿 | A low nitrogen oxide burner for gas combustion |
| CN103123115A (en) * | 2012-12-26 | 2013-05-29 | 内蒙古科技大学 | Auto-ignition stable-flame-type total oxygen combustor |
| CN103742911A (en) * | 2014-01-07 | 2014-04-23 | 天津城建大学 | Fully premixed fuel gas burner |
| CN105509049A (en) * | 2016-01-13 | 2016-04-20 | 哈尔滨工业大学 | High-speed injection and combustion device adapting to various fuels |
| CN105953219A (en) * | 2016-06-21 | 2016-09-21 | 上海齐耀热能工程有限公司 | Flameless combustion device |
| CN107620961A (en) * | 2017-11-02 | 2018-01-23 | 上海华之邦科技股份有限公司 | A new type of ultra-low nitrogen combustion device combining non-premixed combustion and premixed combustion |
| CN109611847A (en) * | 2018-12-30 | 2019-04-12 | 上海华之邦科技股份有限公司 | A Gas Combustion System Suitable for Fire Tube Boilers |
| CN110145737A (en) * | 2019-04-19 | 2019-08-20 | 王晓峰 | A kind of rotational-flow stable-flame radial spray low NO |
| CN110220190A (en) * | 2019-06-18 | 2019-09-10 | 上海华之邦科技股份有限公司 | One kind partly premixing low NOx gas burner |
| CN209484602U (en) * | 2018-10-22 | 2019-10-11 | 北京泷涛环境科技有限公司 | A flue gas internal circulation ultra-low nitrogen burner |
| WO2020140383A1 (en) * | 2019-01-02 | 2020-07-09 | 刘维 | Two-stage fuel burning row burner |
| CN212005662U (en) * | 2020-01-10 | 2020-11-24 | 清华大学 | Fuel side flue gas recirculation low-nitrogen combustor |
| CN112413590A (en) * | 2020-12-11 | 2021-02-26 | 深圳市佳运通电子有限公司 | Flue gas inner loop low NOx burner |
-
2021
- 2021-03-01 CN CN202110224750.7A patent/CN112856416B/en active Active
Patent Citations (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0488481A1 (en) * | 1990-11-30 | 1992-06-03 | Remeha Fabrieken B.V. | Low NOx gas burner |
| EP1391657A2 (en) * | 2002-08-22 | 2004-02-25 | Hitachi, Ltd. | Gas turbine combustor, combustion method of the gas turbine combustor, and method of remodeling a gas turbine combustor |
| KR20040040577A (en) * | 2002-11-07 | 2004-05-13 | 한국에너지기술연구원 | premix type knitted metal fiber mat gas burner |
| CN101349425A (en) * | 2007-07-16 | 2009-01-21 | 通用电气公司 | Apparatus/method for cooling the combustion chamber/venturi in a low NOx burner |
| CN101603687A (en) * | 2008-06-11 | 2009-12-16 | 钱志鸿 | A low nitrogen oxide burner for gas combustion |
| CN103123115A (en) * | 2012-12-26 | 2013-05-29 | 内蒙古科技大学 | Auto-ignition stable-flame-type total oxygen combustor |
| CN103742911A (en) * | 2014-01-07 | 2014-04-23 | 天津城建大学 | Fully premixed fuel gas burner |
| CN105509049A (en) * | 2016-01-13 | 2016-04-20 | 哈尔滨工业大学 | High-speed injection and combustion device adapting to various fuels |
| CN105953219A (en) * | 2016-06-21 | 2016-09-21 | 上海齐耀热能工程有限公司 | Flameless combustion device |
| CN107620961A (en) * | 2017-11-02 | 2018-01-23 | 上海华之邦科技股份有限公司 | A new type of ultra-low nitrogen combustion device combining non-premixed combustion and premixed combustion |
| CN209484602U (en) * | 2018-10-22 | 2019-10-11 | 北京泷涛环境科技有限公司 | A flue gas internal circulation ultra-low nitrogen burner |
| CN109611847A (en) * | 2018-12-30 | 2019-04-12 | 上海华之邦科技股份有限公司 | A Gas Combustion System Suitable for Fire Tube Boilers |
| WO2020140383A1 (en) * | 2019-01-02 | 2020-07-09 | 刘维 | Two-stage fuel burning row burner |
| CN110145737A (en) * | 2019-04-19 | 2019-08-20 | 王晓峰 | A kind of rotational-flow stable-flame radial spray low NO |
| CN110220190A (en) * | 2019-06-18 | 2019-09-10 | 上海华之邦科技股份有限公司 | One kind partly premixing low NOx gas burner |
| CN212005662U (en) * | 2020-01-10 | 2020-11-24 | 清华大学 | Fuel side flue gas recirculation low-nitrogen combustor |
| CN112413590A (en) * | 2020-12-11 | 2021-02-26 | 深圳市佳运通电子有限公司 | Flue gas inner loop low NOx burner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112856416B (en) | 2025-09-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN205504983U (en) | Gas recirculation low NOx burner in combustion -supporting wind injection type stove | |
| CN111121023A (en) | Fuel side flue gas recirculation nitrogen combustor and combustion method thereof | |
| CN110822423B (en) | A kind of multi-purpose burner with fins and different diameter gas spin premixing | |
| CN104613473B (en) | A kind of porous gas jet burner | |
| CN111442271A (en) | Flue gas inner loop low NOx burner | |
| CN205137451U (en) | Force to draw low NOx gas combustion ware of penetrating flue gas backward flow | |
| CN110836383A (en) | A kind of high temperature flue gas generator and control method thereof | |
| CN107606613A (en) | The low nitrogen rotational flow gas-fired combustor of flue gas recirculation built in gas-air Accurate Classification | |
| CN106016362A (en) | Gas turbine engine mild combustor and control method thereof | |
| CN111023091A (en) | High-temperature flue gas multi-stage backflow low-nitrogen combustor and combustion method thereof | |
| CN105737152A (en) | Combusting device for low nitrogen combustion of classification pre-mixed swirling flow | |
| CN115614748A (en) | A ring-cavity injection low-nitrogen burner | |
| CN115143459A (en) | A low-nitrogen burner with internal circulation of ejected premixed flue gas | |
| CN1333199C (en) | W-shape flame furnace with gradation coal burner | |
| CN118794016A (en) | A low-nitrogen combustion head with segmented combustion | |
| CN116624872A (en) | A flue gas internal circulation low-nitrogen combustion head | |
| CN107461742B (en) | Graded flameless low-nitrogen combustion head | |
| CN215411868U (en) | Cyclone flue gas recirculation gas burner | |
| CN204460213U (en) | A kind of porous gas jet burner | |
| CN107543160A (en) | A kind of ultralow nitrogen gas burner | |
| CN116006970A (en) | Combustor and combustion method for realizing circumferential swirl injection and axial flameless combustion | |
| CN215675303U (en) | Premixing fuel nozzle of gas turbine | |
| CN113405095A (en) | Cyclone flue gas recirculation gas burner | |
| CN110056864A (en) | A kind of gaseous fuel low NO | |
| CN201688400U (en) | Powdered coal burner and powdered coal boiler comprising the same |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20211213 Address after: 200433 room 13002-3, No. 188, Wudong Road, Yangpu District, Shanghai Applicant after: SHANGHAI SIFANG BOILER GROUP ENGINEERING SYSTEM Co.,Ltd. Applicant after: Shanghai bonasen Environmental Technology Co.,Ltd. Address before: 201901 room b1541, building 11, no.358, Meilin Road, Baoshan District, Shanghai Applicant before: Shanghai bonasen Environmental Technology Co.,Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |