CN222578231U - A low-nitrogen combustion head with segmented combustion - Google Patents

Abstract

The utility model discloses a segmented combustion low-nitrogen burner head, comprising a central burner head, a flame tube and a secondary gas nozzle, wherein the flame tube is sleeved on the periphery of the central burner head; the central burner head comprises a central gas distributor, a plurality of premixing nozzles and a central gas connecting pipe; an annular gap is provided between the flame tube wall and the outer wall of the central gas distributor, combustion air is introduced into the flame tube, a part of the combustion air meets and mixes with the gas inside the straight tube of the premixing nozzle, and is ignited when flowing out of the straight tube to form a plurality of independent combustion flames, and another part of the combustion air flows out through the annular gap. The utility model controls combustion in segments, wherein the initial stage adopts oxygen-rich lean combustion to control the generation of nitrogen oxides, and the secondary stage utilizes the smoke and heat generated by the initial stage combustion, so that the secondary stage combustion is diffused to a larger space, and is carried out in a flameless combustion manner, so that the combustion is more uniform, local high temperature is avoided, and overall low-nitrogen combustion is achieved.

Description

Low-nitrogen combustion head for sectional combustion

Technical Field

The utility model belongs to the technical field of combustors and related air-gas-flue gas mixing devices thereof, and particularly relates to a low-nitrogen combustion head capable of performing sectional combustion and staged premixing oxygen-enriched lean combustion. The present utility model relates to an associated industrial burner of the type comprising a burner head mounted on a combustion chamber, the fuel being natural gas for systems without external fume circulation.

Background

Nitrogen oxides (NOx) are known to be toxic and harmful gases, wherein the combustion process mainly comprises thermal nitrogen oxides, and the method is characterized in that as the temperature of flame and combustion area increases, the emission of pollutant nitrogen oxides also increases exponentially, and how to control the flame temperature for reducing combustion becomes the main technical means for reducing thermal nitrogen oxides.

The flue gas circulation technology is widely used in boiler systems, and mainly comprises carbon dioxide, water vapor and nitrogen, wherein the main components of the flue gas generated by combustion are carbon dioxide, and the non-combustible flue gas is conveyed into a combustion area again in a circulation mode, so that combustible substances and oxidants are diluted by the flue gas and then burnt in the chemical reaction process of combustion, the intensity of the combustion reaction is reduced, the flame temperature is reduced, the temperature of the combustion area is also reduced, the condition that oxygen and nitrogen generate thermal nitrogen oxides is effectively weakened, and the generation of the nitrogen oxides is reduced.

The flue gas circulation technology is basically divided into two types of flue gas circulation technology, namely flue gas external circulation and flue gas internal circulation. The external circulation of the flue gas is to extract a part of flue gas at a flue gas outlet at the tail part of the boiler, send the flue gas into combustion air, mix the flue gas with the combustion air and then enter a combustion area together, and the internal circulation of the flue gas is to directly circulate the flue gas into the combustion area in the combustion chamber through a swirl airflow formed in the combustion chamber of the boiler. The difference between the internal and external flue gas circulation means whether the circulation of the flue gas occurs inside or outside the combustion chamber. In many cases, the internal and external circulation are combined, the internal circulation technology of NOx less than or equal to 80mg/m < 3 > is mature, and NOx less than or equal to 30mg/m < 3 > can be achieved by combining the external circulation.

The widely used machine type in the market is a diffusion type burner with an additional flue gas external circulation technology, so as to reduce the emission of nitrogen oxides. The burner head of this type of burner is relatively simple in construction and reliable in operation. Because the working principle is to circularly burn the smoke by using a fan, the power of the fan is required to be increased or the smoke circulating fan is used, which causes the increase of investment cost.

In addition, the flue gas return pipes of most field installation are connected to the combustor air-blower air inlet side, and flue gas temperature is higher, and combustion-supporting air temperature is lower, and vapor in the flue gas can condense when two meet cold and become water when crossing, causes the corruption of junction, and the comdenstion water gets into the combustor when serious and leads to flame detector sensing part and ignition element to break down, produces the potential safety hazard. In addition, condensed water enters the shell of the burner, and the inner parts of the burner and the shell of the shell are corroded by the impeller of the blower, so that the service life of the burner is influenced.

In order to meet the effect of reducing nitrogen oxides, the flue gas internal circulation machine type used in the market generally requires that the diameter of a boiler combustion chamber is large enough and the backflow space of the internal circulation is sufficient, so that the internal circulation effect of sufficient flue gas quantity can be ensured. The size of the combustion chamber is increased, resulting in a substantial increase in the cost of the boiler.

In these flue gas recirculation type burners, although the purpose of reducing nitrogen oxides is achieved by feeding flue gas into the combustion area by a circulation method, when a lower emission index is pursued, the circulation amount of flue gas must be increased to further reduce the intensity of combustion flame, and these methods cause a decrease in combustion stability, and combustion surge, flame instability and an increase in the failure rate accompanying the operation of the burner are likely to occur.

In the patent document DE 3811477 A1, it is described that for a gas burner, gas is mixed with air at the inlet of the combustion chamber, the gas being admitted through some mixing tubes. Wherein the fuel gas is directly sent into the inlet of the combustion chamber through the gas mixing pipe and the nozzle thereof, and is mixed with the combustion air to enter the combustion chamber. The outlets of the gas pipes are distributed in different tangential planes in the mixing cavity of the burner according to the divergent direction.

In DE 195 09 219, a burner is described for a burner head for a burner which is designed to reduce nitrogen oxides by means of inert gas while burning fuel gas, wherein the fuel gas is divided into two stages, one stage is superimposed behind the other stage, the combustion air is blown in from the root of the flame in the flow direction of the combustion air, the combustion air with a first stage super-chemical reaction ratio and the fuel gas mixture flow to the flame, the supplementary fuel gas is added in the tangential direction of the second stage, the flue gas circulated back where is added as inert gas to the second stage, a part of the combustion gas is injected into the second stage and the circulated flue gas to form a mixture gas with a lower chemical reaction ratio, and the mixture gas is mixed before reaching the flame.

Patent EP 0 635 676 describes a low NOx burner for liquid or gaseous fuels, with a burner projecting into the combustion chamber of a boiler, with at least one fuel nozzle in the burner cartridge for supplying fuel and adjacent to the burner plate, which delivers a large quantity of fuel gas from the burner plate outwards to the inner wall area of the cartridge, and the rapid gas flow through the gap between the cartridge and the burner plate creates a negative pressure at the front edge of the cartridge, to which the flue gases generated in the combustion chamber are delivered by internal circulation, with a plurality of flow guide corners extending into the negative pressure area.

Chinese patent CN112178626B describes an internal circulation low-nitrogen gas burner, a cyclone is sleeved at one end of a first gas pipe, an annular gas pipe is sleeved at the outer side of the cyclone and in clearance fit with the cyclone, a second gas pipe conveys gas to the annular gas pipe, a splitter pipe is sleeved at the outer side of the annular gas pipe, and a flow separation member is sleeved at the outer side of a splitter pipe and forms a flue gas channel with the splitter pipe. The gas components of the inner rings are positioned in the flue gas channel, and the gas components of the outer rings are arranged on the periphery of the flow separation piece. The shunt tubes are used for shunting air to form air for mixing cigarettes and air for mixing combustion, negative pressure is generated at a smoke inlet when the air for mixing cigarettes flows through a smoke channel, so that smoke in a combustion chamber is sucked, and the air for mixing cigarettes participates in combustion again. Because of the way of directly recycling the smoke by utilizing vacuum, not only is a smoke channel omitted and the potential safety hazard eliminated, but also the use cost is reduced.

Chinese patent CN107120652 describes a staged gas low nitrogen burner, which relates to the burner technical field. The staged gas low nitrogen burner includes a distributor, a baffle plate, an ignition electrode, an ignition fuel tube and a combustion can. The distributor is used for providing a flow path for fuel gas and air and comprises a body, a plurality of fuel gas spray pipes, a fuel gas distribution ring and a plurality of air distribution pipes. The body is a cylinder with a first interlayer, and the fuel gas is sprayed out from the fuel gas distribution ring after entering the fuel gas pipe through the body. The air flows through the hollow part of the body, the air distribution pipe and the outer side of the distributor to form an air flow path for providing combustion-supporting gas for the fuel gas. The distribution ring of CN107120652 is thinner, not larger than 4 times the diameter of the gas distribution hole, just the gas is distributed as the inner and outer rings, and there is no function of separating air. The flow guiding disc of CN107120652 guides the air led in by a plurality of air distributing pipes to form a rotating air flow, the main body is air, and no gas distributing device is arranged.

The above-mentioned known methods and structures are not adequate to achieve the increasing demands for reduction of pollutant emissions from combustion plants, especially when the emissions levels of nitrogen oxides are further reduced as required by legal regulations, which are limited or have problems with excessive levels of nitrogen oxides or unstable combustion, which are difficult to meet environmental emission standards.

The utility model uses the concept of staged combustion to control the combustion in a staged manner, the primary stage adopts the principle of oxygen-enriched lean combustion to control the generation of nitrogen oxides, the secondary stage uses the flue gas and heat generated by the primary stage combustion to create one for the secondary stage combustion, and satisfies the conditions that the combustion-supporting air required by the secondary combustion is diluted and preheated and the fuel is diluted and preheated, so that the secondary stage combustion is diffused to a larger space to be carried out in a manner similar to flameless combustion, after the diffusion, the combustion is more uniform, the occurrence of local high temperature is avoided, the generation of nitrogen oxides is restrained, and the integral low-nitrogen combustion is realized.

The utility model is most important and different, innovatively invents a central multistage premix burner, and utilizes the uniform distribution of a plurality of premix nozzles to divide combustion flame into a plurality of independent flames, so that the effect of oxygen enrichment and lean combustion on nitrogen reduction is fully exerted, and meanwhile, because air and fuel gas are mixed in each premix nozzle, the possible backfire and deflagration risks caused by the need of premixing and redistributing combustion of most premix burners are avoided.

Disclosure of utility model

The utility model aims to solve the problems, and aims to provide a stable, safe, compact, efficient and environment-friendly staged combustion low-nitrogen gas burner.

The technical scheme of the utility model is that the low-nitrogen combustion head for sectional combustion comprises a primary combustion which utilizes a multi-stage premixing structure in a primary stage and combines an oxygen-enriched lean combustion low-nitrogen principle, and a secondary combustion which utilizes a secondary combustion principle of primary combustion flue gas, residual air and fuel gas which are mixed and then combusted in a secondary stage, wherein the secondary combustion is performed by the flue gas internal circulation low-nitrogen principle.

The utility model relates to a sectional type low-nitrogen combustion head, which comprises a central combustion head, flame tubes and secondary gas nozzles distributed around the flame tubes, wherein the flame tubes are coaxially sleeved on the periphery of the central combustion head; the central combustion head comprises a central gas distributor, a plurality of premixing nozzles and a central gas connecting pipe, wherein the central gas distributor is in a cylindrical shape with a hollow inside, the central gas connecting pipe is communicated to the inside of the central gas distributor, each premixing nozzle is a straight pipe penetrating through the inside of the central gas distributor, the inner wall of each straight pipe is provided with a gas hole, the inside of the central gas distributor is communicated through the gas holes, the plurality of straight pipe-shaped premixing nozzles are uniformly distributed on the central gas distributor, the gas introduced by the central gas connecting pipe is introduced into the premixing nozzles through the inside of the central gas distributor and then passes through the gas holes, an annular gap is reserved between the wall of a flame tube and the outer wall of the central gas distributor, combustion air is introduced into the flame tube, part of combustion air and the gas meet and are mixed in the straight pipe of the premixing nozzles and are ignited when flowing out of the straight pipe, a plurality of independent combustion flames are formed on one side of the central gas distributor, and the other part of combustion air flows out through a gap between the flame tube and the central gas distributor.

Further, the hollow cylindrical central gas distributor is composed of a cylinder body and a front end cover and a rear end cover, the front end cover and the rear end cover enclose a hollow cylindrical space with the cylinder body, through holes corresponding to the positions are formed in the front end cover and the rear end cover, straight pipe-shaped premixing nozzles are embedded in and penetrate through the through holes of the front end cover and the rear end cover, a gas outlet end of the central gas connecting pipe is communicated with the front end cover, straight pipes of the premixing nozzles extend out of the rear end cover, an interval is formed between each straight pipe-shaped premixing nozzle, mutually independent flames are formed at the root parts of each premixing nozzle during combustion, and accordingly primary combustion classification flames with the same quantity as the premixing nozzles are formed.

Further, the flame tube is of a conical closing-in structure, and the distance between the central gas distributor and the conical opening of the flame tube can be adjusted in the axial direction, so that the size of the annular gap between the flame tube and the central gas distributor can be changed.

Further, the gas inlet end of the central gas connection pipe is connected with the main gas pipe through the central gas regulating valve, so that the central gas regulating valve can regulate the gas amount of the central gas distributor.

Further, the other end opposite to the conical closing-in of the flame tube is connected with a secondary gas distributor, the secondary gas distributor is a cylindrical annular cavity, the diameter of the annular cavity is larger than that of the flame tube, a plurality of communicated secondary gas nozzles are uniformly arranged on the end face of the annular cavity facing one end of the combustion chamber,

Further, the connecting end of the annular cavity and the flame tube is provided with a connecting flange which is used for being connected with the front wall of the boiler, the other end of the annular cavity and the flame tube is provided with a connecting flange which is connected with a blower, the flame tube is connected and installed on one side of the connecting flange surface of the boiler of the annular cavity, and a plurality of connecting holes of gas nozzles are arranged on the connecting flange surface and are used for being connected with the secondary gas nozzles.

Further, the secondary gas nozzle is a straight pipe, and the length of the straight pipe of the secondary gas nozzle extends beyond the air outlet of the flame tube and stretches into the combustion chamber.

Further, wherein the inner cavity radial thickness of the annular cavity is greater than the diameter of the secondary gas nozzle, the secondary gas nozzle being in communication with the annular cavity through a nozzle orifice.

Further, the outer wall of the annular cavity is provided with a hole, a connecting flange is arranged at the hole, a secondary gas regulating valve is connected with the main gas pipe through the connecting flange, and the secondary gas regulating valve is used for regulating secondary stage gas quantity.

Further, the inner cylinder of the secondary gas distributor is hollow, the central combustion head is installed and fixed in the inner cylinder of the gas distributor through a bracket arranged in the inner cylinder space, and the blower conveys combustion air from the inner cylinder of the secondary gas distributor into the flame tube, and then enters the combustion chamber through a premixing nozzle on the central gas distributor and an annular gap with the flame tube.

In summary, the beneficial effects of the utility model are as follows:

The utility model relates to a sectional type low-nitrogen combustion head, which comprises a primary combustion part and a secondary gas distribution part, wherein the primary combustion part utilizes an oxygen-enriched lean combustion low-nitrogen principle in the primary stage, and the secondary gas distribution part utilizes a flue gas circulation low-nitrogen principle in the secondary stage, wherein the surplus air except air required by the primary stage combustion is mixed, secondary gas is mixed and flows back to the flue gas after the primary combustion flue gas is mixed, and the secondary gas is mixed and combusted with each other. The utility model relates to a low-nitrogen combustion head for the primary-stage oxygen-enriched lean combustion, wherein air and fuel gas flowing out of a premixing nozzle of a central fuel gas distributor are subjected to oxygen-enriched lean combustion and low-nitrogen air-fuel ratio with high excess air coefficient. The air which meets the requirement of the primary stage combustion is other than the air, the rest air flows out of the combustion head through an annular gap formed by the central gas distributor and the flame tube, the rest air surrounds the multi-stage flame in the primary center, like an annular sleeve, flows in the same axial direction with the multi-stage combustion flame in the primary stage in a laminar flow mode, and is mutually diffused and mixed with the combustion tail gas in the middle and rear stages of the primary stage combustion. The secondary gas nozzles are uniformly arranged around the flame tube, the secondary gas nozzle outlets extend into the combustion chamber beyond the air outlet end of the flame tube, a space is reserved between the secondary gas nozzles and the flame tube outlets in the axial direction, the gas injection direction is the same as the central main gas flow, the back flow flue gas is generally distributed in the space, and the secondary gas is not immediately contacted with the surplus air flow after being sprayed out, so that the secondary gas cannot be combusted immediately, but is mutually diffused and mixed with the back flow flue gas and the surplus air along with the accompanying vortex formed by the central main gas flow at the middle and rear sections, and then combusted. The primary combustion output power needs to meet the requirement that the generated heat and the gas quantity are large enough, the temperature of the surplus air is not lower than the self-ignition temperature of the fuel gas after the surplus air is mixed with the primary flue gas after being heated and diluted, the surplus air is diluted by the mixed flue gas, the fuel gas molecules and the oxygen molecules are diffused into a larger space, the secondary combustion is a chemical reaction which occurs in the environment meeting the temperature above the self-ignition temperature of the fuel gas, and no obvious stagnation flame phenomenon exists.

According to the utility model, through the ratio of the primary multi-stage premixing structure and the oxygen-enriched lean combustion, the primary low-nitrogen combustion is realized, and conditions are created for the secondary stage, so that combustion air and fuel gas are mixed and combusted again under the condition of mixing the flue gas and preheating, the secondary stage combustion is performed in a fully-diffused space, the local high temperature is avoided, and the generation of nitrogen oxides is limited. The staged combustion technology can realize low nitrogen oxide emission under the condition of smaller diameter of the combustion chamber. As the secondary combustion occurs under the condition that the fuel gas and the air are fully diffused, the temperature in the whole hearth is uniform, the heat exchange efficiency of the boiler is improved, and the heat utilization equipment is more efficient and environment-friendly.

Drawings

FIG. 1 is a cross-sectional view of a sectional combustion low nitrogen burner head of the present utility model mounted to a combustion chamber.

FIG. 2 is a schematic flow diagram of the gas and combustion air and flue gas in a combustion chamber of a staged combustion low nitrogen burner according to the present utility model.

FIG. 3 is a schematic view of the center burner of a staged combustion low nitrogen burner of the present utility model.

FIG. 4 is a cross-sectional view of a staged combustion low nitrogen burner head of the present utility model.

The gas burner comprises the following components of 1, a combustion chamber, 2, a combustion head, 3, a central combustion head, 4, a secondary gas distributor, 5, a main gas pipe, 11, a combustion chamber front wall, 12, a combustion chamber wall, 13, a heating medium, 21, a flame tube, 31, a central gas distributor, 32, a premixing nozzle, 33, a gas hole, 34, a central gas connecting pipe, 35, a central gas regulating valve, 36, a central regulating valve actuator, 41, an annular cavity, 42, a boiler connecting flange, 43, a blower connecting flange, 44, a secondary gas nozzle, 45, a secondary gas connecting pipe, 46, a secondary gas regulating valve, 47, a secondary regulating valve actuator, 48, a central combustion head fixing bracket, A, combustion-supporting air, B1, central gas, B2, secondary gas, C1, primary stage combustion flue gas, C2, backflow flue gas, D, accompanying vortex, C3, circulating flue gas, F and flame.

Detailed Description

In order to make the technical means, technical features, achieving the object and technical effects of the present utility model easy to understand, the present utility model is specifically described below with reference to the embodiments and the accompanying drawings.

As shown in fig. 1 to 4, which illustrate the specific principle and specific structure of the staged combustion low nitrogen burner head of the present utility model.

As shown in fig. 1, a staged combustion low nitrogen burner 2 of the present utility model, the burner 2 comprises a central burner 3, a flame tube 21 and secondary gas nozzles 44 distributed around the flame tube 21, wherein the flame tube 21 is coaxially sleeved on the periphery of the central burner 3. The burner head 2 is mounted on the front wall 11 of the burner 1 by means of the boiler connection flange 42 of the secondary gas distributor 4, the outside of the burner wall 12 is the heating medium 13, the central burner head 3 of the burner head 2, the burner tube 21 and the secondary gas nozzles 44 uniformly arranged around the burner tube extend beyond the front wall plane 11 of the burner to the inside of the burner 1, and the burner head 2 is connected to the burner blower by means of the blower connection flange 43 of the secondary gas distributor 4.

As shown in fig. 1 to 4, the burner head of the present utility model comprises a central burner head 3 positioned at the center of the burner head 2 and adopting a multi-stage premixed combustion mode, the central burner head 3 comprises a central gas distributor 31, a plurality of premixed nozzles 32 and a central gas connecting pipe 34, the central gas distributor 31 is in a hollow cylinder shape, a hollow cylinder shape space is surrounded by a cylinder body and a front disc-shaped end cover and a rear disc-shaped end cover, the central gas connecting pipe 34 is connected with the front end cover and communicated with the cylinder body inner space, a plurality of through holes are uniformly arranged at corresponding positions on the front end cover and the rear end cover, the positions and the sizes of the through holes of the front end cover and the rear end cover are the same, the premixed nozzles 32 are in a straight pipe structure, the straight pipes are embedded and penetrate through the through holes on the front end cover and the rear end cover, and the straight pipes of the premixed nozzles 32 extend and protrude from the rear end cover, and the lengths of the straight pipes meet the requirement of uniform mixing of gas and air. Each straight pipe-shaped premixing nozzle 32 is provided with a space, each straight pipe of the premixing nozzle 32 is provided with a gas hole 33, and the gas holes 33 are communicated with the inner wall and the outer wall of the straight pipe, namely, the inside of the central gas distributor 31. During operation, combustion air is introduced into the flame tube 21, a part of combustion air passes through the disc surface of the gas distributor 31 through the inner wall of the straight tube of the premixing nozzle 32, and enters the combustion chamber 1, gas enters the center gas distributor 31 through the center gas connecting tube 34, then enters the straight tube of the premixing nozzle 32 through the gas holes 33 on the straight tubes, the combustion air and the gas meet and mix in the straight tube of the premixing nozzle 32, are ignited when flowing out of the straight tube, and mutually independent flames are formed at the root part between each premixing nozzle when the center gas distributor 31 is positioned on one side of the combustion chamber 1, so that primary combustion classification flames with the same quantity as the premixing nozzles are formed.

During combustion operation, combustion air required for primary stage combustion flows out of the premixing nozzle 32 on the central gas distributor 31, other surplus air flows out of the combustion head through an annular gap formed by the central gas distributor 31 and the flame tube 21, a plurality of secondary gas nozzles 44 are uniformly arranged around the flame tube 21, the length of each secondary gas nozzle 44 is longer than that of the flame tube 21, so that the outlet of each secondary gas nozzle 44 exceeds the air outlet end of the flame tube 21 and extends into the combustion chamber 1, the secondary gas nozzles 44 and the air outlet of the flame tube 21 are provided with a spacing space which is not smaller than the conical closing-in axial direction, and the gas injection direction is the same as the central main gas flow.

As shown in FIG. 2, the gas of the present utility model, The flow direction of the combustion air and the flue gas is schematically shown, wherein after the combustion air A enters the combustion head 2, the combustion air A is initially combusted in the center of the stage and enters the space of the combustion chamber 1 behind the surface of the center gas distributor 31 through a straight-through pipe of a premixing nozzle 32 on the end cover of the center gas distributor 31, the surplus air except the air required by the initial stage center combustion is satisfied, then enters the combustion chamber 1 through an annular gap formed between the center gas distributor 31 and the flame tube 21, the center gas B1 enters the inner space of the center gas distributor 31 through a center gas connecting pipe 34, then enters the inside of a straight-through pipe of the premixing nozzle 32 through a gas hole 33 on the premixing nozzle 32, is ignited when flowing out of the premixing nozzle 32 after being mixed with the initial stage combustion air, forms a multi-stage independent combustion flame F, enters the combustion chamber 1, the secondary gas B2 enters the inside of an annular cavity 41 of the secondary gas distributor 4 through a secondary gas connecting pipe 45, and enters the combustion chamber 1 through a secondary nozzle 44 which is arranged and connected around the flame tube. The central gas quantity can be controlled through the central gas regulating valve 35, so that the low-nitrogen combustion of the oxygen-enriched lean air-fuel ratio of the primary-stage multi-stage flame is realized. The surplus air which meets the requirement of the primary stage center combustion except the air flows out of the combustion head through the annular gap between the center gas distributor 31 and the flame tube 21, the surplus air surrounds the primary center multi-stage flame, like an annular sleeve, flows coaxially with the primary stage combustion multi-stage flame in a laminar flow mode, and is mutually diffused and mixed with the primary stage combustion flue gas C1 in the middle and rear stages of the primary stage combustion. The flow directions of the air flowing out from the center of the premixing nozzle, the surplus air and the smoke generated by the central multi-stage flame combustion are consistent in the axial direction, the middle and rear sections of the primary stage combustion are mixed into a converging airflow, the airflow generally generates an accompanying vortex D, particularly, in the case of adopting a conical closing structure of the flame tube 21, the air outlet of the flame tube 21 surrounds the outer edge of the conical closing to form a negative pressure area, the existence of the negative pressure can guide the reflux smoke C2 of the accompanying vortex D to flow back to the position of the negative pressure area of the combustion head to form smoke internal circulation, the secondary gas nozzle 44 and the air outlet of the flame tube 21 are provided with an interval space which is not smaller than the conical closing in the radial direction, the gas spraying direction is the same as the central airflow, the circulating smoke C3 is normally distributed in the interval space, the part of the secondary gas is not contacted with the surplus air flow immediately after being sprayed out, so that the secondary gas is not burnt immediately, and the circulating vortex D formed at the middle and the surplus air and the smoke C1 are mutually diffused and combusted with the primary stage combustion smoke. The primary stage combustion output power is adjustable, heating and dilution of surplus air can be met after adjustment, after the surplus air is mixed with primary stage flue gas, the temperature is not lower than the self-ignition temperature of fuel gas, the surplus air is diluted by the mixed flue gas, fuel gas molecules and oxygen molecules are diffused into a larger space, the secondary stage combustion is a chemical reaction which occurs in an environment meeting the temperature above the self-ignition temperature of the fuel gas, the reaction area is enlarged, no obvious standing point flame phenomenon exists, the temperature is average, and the generation of nitrogen oxides is limited. Meanwhile, the secondary stage combustion consumes the surplus air of the primary stage, and the conditions of high air excess coefficient and low combustion efficiency are prevented.

As shown in fig. 1 and 4, the present utility model shows a staged combustion low nitrogen burner, wherein the flame tube 21 has a tapered closing structure, and the size of the annular gap can be changed by adjusting the distance between the central gas distributor 31 and the tapered opening of the flame tube 21 in the axial direction, so that the air amount ratio of primary combustion and secondary combustion and the total power of combustion output can be changed. When the gap is reduced, the wind pressure is increased, the total wind quantity is reduced, the total power is reduced, the central primary wind quantity is increased due to the increase of the wind pressure, the combustion power of the initial stage is also increased, the gap is increased, and the effect is opposite.

On the other hand, when air flows through the outlet rapidly, due to the effect of the conical closing-in, a negative pressure area is formed around the outer edge of the air outlet of the flame tube 21 on one side of the combustion chamber, the suction force of the negative pressure guides the flue gas in the combustion chamber to flow back, so that the flue gas internal circulation effect is formed, the backflow flue gas effectively isolates the secondary fuel gas from the surplus air flow in the initial section after being sprayed out, and meanwhile, the part of the backflow flue gas effectively heats and dilutes the secondary fuel gas.

As shown in fig. 4, the present utility model shows a staged combustion low nitrogen burner in which the central gas distributor 31 is connected to and communicates with the main gas pipe 5 through a central gas regulating valve 35 by a central gas connecting pipe 34, and the central gas regulating valve 35 is regulated by a central regulating valve actuator 36, so that the amount of gas introduced into the primary stage combustion central burner can be regulated.

As shown in fig. 1 and 4, the present utility model shows a sectional type low-nitrogen burner, a secondary gas distributor 4 is connected to the other end opposite to the conical closing of a burner 21, the secondary gas distributor 4 is a cylindrical annular cavity, the diameter of the annular cavity is larger than that of the burner 21, a plurality of secondary gas nozzles 44 communicated with each other are uniformly arranged on the end face of the annular cavity facing one end of the burner, the plurality of secondary gas nozzles 44 are uniformly arranged around the burner 21, the connecting end of the annular cavity and the burner 21 is provided with a boiler connecting flange 42 for connecting with a boiler front wall, the other end is provided with a blower connecting flange 43 connected with a blower, the burner 21 is connected and mounted on the boiler connecting flange face of the annular cavity close to one side of the boiler, and a plurality of gas nozzle connecting holes are arranged on the flange face for connecting the secondary gas nozzles 44. The secondary gas nozzle 44 is of a straight tube structure, and the straight tube length of the secondary gas nozzle 44 extends beyond the air outlet of the flame tube 21 and into the combustion chamber 1. And wherein the inner cavity radial thickness of the annular cavity is greater than the diameter of the secondary gas nozzle 44, the secondary gas nozzle 44 communicating with the interior of the annular cavity through a nozzle orifice.

The outer wall of the annular cavity is provided with a hole, a connecting flange is arranged at the hole, the connecting flange is connected with the main gas pipe 5 through a secondary gas regulating valve 46, and the secondary gas regulating valve 46 is regulated through a secondary regulating valve actuator 47, so that the gas quantity of secondary stage combustion is regulated.

As shown in fig. 1 and 4, the inner cylinder of the secondary gas distributor 4 is hollow and transparent, the central burner 3 is mounted and fixed in the inner cylinder of the secondary gas distributor 4 by a bracket 48 arranged in the inner cylinder space, and the blower delivers combustion air from the inner cylinder of the secondary gas distributor 4 into the flame tube 21 and then into the combustion chamber through the premixing nozzle 32 on the central gas distributor 31 and the annular gap with the flame tube 21.

The utility model discloses a sectional type low-nitrogen combustion head which adopts a primary combustion by utilizing a multi-stage premixing structure in a primary stage and combining an oxygen-enriched lean combustion low-nitrogen principle, and a secondary combustion by utilizing a secondary stage of secondary combustion by utilizing a principle that primary combustion flue gas is mixed with residual air and fuel gas and then combusted, wherein the flue gas is internally circulated. The structure of the combustion head comprises a primary center combustion head which is positioned in the center of the combustion head and adopts a multistage premixed combustion mode, a flame tube and a secondary gas nozzle which surrounds the flame tube. The central combustion head consists of a central gas distributor, a plurality of premixing nozzles and a gas connecting pipe, wherein the premixing nozzles are of straight pipe structures and are embedded on the disc surface of the gas distributor, combustion air required by primary stage combustion passes through the disc surface of the central gas distributor through the inner wall of the straight pipe of the premixing nozzle and enters a combustion chamber, a plurality of small holes are formed in the straight pipe of the premixing nozzle and communicated with the inner wall and the outer wall of the straight pipe, gas enters the central gas distributor through the small holes after entering the central gas distributor through the gas connecting pipe, combustion air and gas meet and are mixed in the straight pipe of the premixing nozzle and are ignited when flowing out of the straight pipe, a plurality of independent combustion flames are formed on the disc surface of the combustion chamber finally, the primary stage low-nitrogen combustion effect of premixing, oxygen enrichment and lean combustion is achieved through the air-fuel ratio regulation, the consumption of the primary stage low-nitrogen combustion is not more than 50%, and the rich air can flow out of the combustion head through an annular clearance formed by the straight pipe of the premixing gas distributor and the flame tube under the condition of the primary stage combustion of meeting the lean combustion ratio, the primary stage combustion condition of the rich air is in a laminar flow and the primary stage combustion mode, and the rich air flows like a laminar flow and the primary stage combustion sleeve, and the primary stage combustion air flows like the primary stage combustion and the primary stage combustion flame is mixed with the primary stage combustion flame in a coaxial mode. The secondary gas nozzles are uniformly arranged around the flame tube, the gas nozzle outlets exceed the air outlet end of the flame tube and extend into the combustion chamber, a space is reserved between the secondary gas nozzles and the residual air flow of central combustion in the axial direction, the gas injection direction is also in the laminar flow direction, and as backflow flue gas is distributed in the space, the secondary gas is not immediately contacted with air after being sprayed out, so that the secondary gas cannot be immediately combusted, and is mutually diffused and mixed along with vortex flow formed by the main gas flow at the middle and rear sections.

Claims (10)

1. A low-nitrogen combustion head for sectional combustion is characterized by comprising a central combustion head, flame tubes and secondary gas nozzles distributed around the flame tubes, wherein the flame tubes are coaxially sleeved on the periphery of the central combustion head, the central combustion head comprises a central gas distributor, a plurality of premixing nozzles and a central gas connecting tube, the central gas distributor is in a cylindrical shape with hollow inside, the central gas connecting tube is communicated to the inside of the central gas distributor, each premixing nozzle is a straight tube penetrating through the inside of the central gas distributor, gas holes are formed in the inner wall of each straight tube and are communicated with the inside of the central gas distributor through the gas holes, the plurality of straight tube-shaped premixing nozzles are uniformly distributed on the central gas distributor, gas introduced by the central gas connecting tube is introduced into the premixing nozzles through the inside of the central gas distributor, an annular gap is reserved between the wall of the flame tube and the outer wall of the central gas distributor, air is introduced into the flame tubes for supporting combustion, a part of the supporting air and the gas meet each other in the inside of the premixing nozzles, the supporting combustion air is ignited when the gas flows out, and the gas flows out of the straight tube is ignited and is positioned between the flame tubes and the flame tube through the other flame distributor.

2. The low-nitrogen combustion head of sectional type combustion as claimed in claim 1, wherein the hollow cylindrical central gas distributor is composed of a cylinder body and a front end cover and a rear end cover, the front end cover and the rear end cover enclose a hollow cylindrical space, through holes corresponding to the positions are formed in the front end cover and the rear end cover, straight pipe-shaped premixing nozzles are embedded in and penetrate through the through holes of the front end cover and the rear end cover, a gas outlet end of the central gas connecting pipe is communicated with the front end cover, straight pipes of the premixing nozzles extend and protrude from the rear end cover, a space is reserved between each straight pipe-shaped premixing nozzle, mutually independent flames are formed at roots between each premixing nozzle during combustion, and accordingly primary combustion staged flames with the same number as that of the premixing nozzles are formed.

3. The low nitrogen burner head of claim 1, wherein the flame tube is of a tapered neck configuration, and the distance of the central gas distributor relative to the cone of the flame tube is adjustable in an axial direction, thereby changing the size of the annular gap between the flame tube and the central gas distributor.

4. A staged combustion low nitrogen burner according to claim 1 wherein the gas inlet end of the central gas connection tube is connected to the main gas pipe via a central gas regulator valve whereby the central gas regulator valve is capable of regulating the gas flow of the central gas distributor.

5. The low-nitrogen burner head of claim 1, wherein a secondary gas distributor is connected to the other end of the burner tube opposite to the conical mouth of the burner tube, the secondary gas distributor is a cylindrical annular cavity with a diameter larger than that of the burner tube, and a plurality of secondary gas nozzles are uniformly arranged on the end face of the annular cavity facing one end of the burner tube.

6. The low-nitrogen burner head for staged combustion according to claim 5, wherein the connection end of the annular cavity and the flame tube is provided with a boiler connection flange for connecting with a boiler front wall, the other end is provided with a blower connection flange for connecting with a blower, the flame tube is connected and installed on one side of the boiler connection flange surface of the annular cavity, and a plurality of connection holes of gas nozzles are arranged on the flange surface for connecting with the secondary gas nozzles.

7. A staged combustion low nitrogen burner head as defined in claim 6, wherein the secondary gas nozzle is a straight tube and the straight tube length of the secondary gas nozzle extends beyond the liner air outlet and into the combustion chamber.

8. The staged combustion low nitrogen burner head of claim 7, wherein the annular cavity has an inner cavity radial thickness greater than the diameter of the secondary gas nozzle, the secondary gas nozzle being in communication with the interior of the annular cavity through a nozzle orifice.

9. The low-nitrogen burner head of claim 8, wherein a connecting flange is arranged at the opening of the outer wall of the annular cavity, a secondary gas regulating valve is connected with the main gas pipe through the connecting flange, and the secondary gas regulating valve is used for regulating secondary stage gas quantity.

10. The staged combustion low nitrogen burner of claim 7 wherein the inner barrel of the secondary gas distributor is hollow and the central burner is mounted and secured within the inner barrel of the gas distributor by brackets spatially disposed within the inner barrel, and the blower delivers combustion air from the inner barrel of the secondary gas distributor into the flame tube and then through premix nozzles on the central gas distributor and annular gaps with the flame tube into the combustion chamber.