CN109899785A - Pressure-air burner and combustion method - Google Patents
Pressure-air burner and combustion method Download PDFInfo
- Publication number
- CN109899785A CN109899785A CN201910237540.4A CN201910237540A CN109899785A CN 109899785 A CN109899785 A CN 109899785A CN 201910237540 A CN201910237540 A CN 201910237540A CN 109899785 A CN109899785 A CN 109899785A
- Authority
- CN
- China
- Prior art keywords
- air
- combustion
- fuel
- burner
- fuel gas
- 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
Abstract
The present invention provides a kind of pressure-air burner and combustion method, the combustion method is strengthened air-fuel including the use of pressure-air and is blended, and makes fuel conflagration and generates flue gas, which is N*105The air of Pa rank.It is conducive to pressure-air intense impact fuel in the present invention, quickly break up fuel stream, air and fuel conflagration, the length of flame is obviously shortened, and furnace volume can reduce, and the high-temperature flue gas high speed ejection burner quickly formed, interior energy-kinetic energy the conversion of the high-temperature flue gas quickly formed can strengthen convective heat transfer, the heat exchange amount of unit heat exchange area is high, and the volume of heat exchanger can also reduce, conducive to the miniaturization of boiler and the raising of heat exchange efficiency；And further the multiple spot of fuel and air arranges the mode of disperses combustion, the thickness of flame front is thinned, in the case where burning load is constant, flammule face shortens the residence time of oxygen, nitrogen in flame front i.e. high-temperature region, so that NOx emission meets low emission requirement.
Description
Technical field
The invention belongs to industrial burning devices and field of boilers, and in particular to pressure-air burner and combustion method,
It is mainly used for industrial burning device and boiler.
Background technique
Burner is classified by air supply modes, there is injection type and blowing-type burner；It is (pre- by primary air ratio
The ratio between theoretical air requirement needed for first and combustion gas mixing combustion-supporting air quantity and combustion gas completely burned) classification, there are diffusion type, atmosphere
Formula and flameless burning device.
Diffusion type burner realizes combustion gas and the mixing of air simultaneously by combustion gas from the diffusion after fire hole evolution
Stablize the burner of burning.Diffusion type burner structure is simple, easy to use, flame stabilization.But its burning velocity is relatively slow,
Flame is longer, needs more excess air to reach completely burned, therefore ignition temperature is lower, the coefficient of heat transfer is smaller.
Atmospheric burning type device is pre-mixed the burner of partial air.Primary air ratio usually takes 0.4~0.7.
Combustion gas is sprayed from nozzle with certain pressure and sprays the negative pressure formed by means of high speed into mixing tube (i.e. injector) for surrounding a part
Air sucking, escapes from burner head fire hole after mixing in mixing tube and is burnt.The burning of atmospheric burning type device is compared
Completely, easy to use, but structure is more bulky and hulking when load is larger.
Blowing-type burner, the burner of whole air needed for air blower supply burning, is mainly used for various works
Industry furnace and large-sized boiler.The combustion chamber volume calorific intensity of blowing-type burner is usually smaller than fully premixed burner, flame
It is longer, it is therefore desirable to which that biggish combustion chamber volume, corresponding boiler volume and occupied area are also larger.Such burner burning
It is considered that chemical reaction rate is much larger than mixing rate (Da > > 1) in reaction mechanism, combustion velocity depends on each group
The mixing velocity divided.Therefore for overheavy firing, blowing-type burner has bushing type, swirl vane formula, snail again in structure
The various structures pattern such as shell-type and flat flow, purpose, which is adopted various measures, as far as possible accelerates combustion gas and air mixing velocity.
When air pressure is within the scope of 1-20KPa, the variation in traditional blowing-type burner structure cannot be in air fuel
Mixing the aspect become better has more promotions.Whole air needed for burner flameless combustion apparatus, combustion gas and burning are preparatory
Mixing, combustion process flame is very short or even does not see the burner of flame completely.Air is generally sucked using injector, with combustion
Gas sufficiently premixes, and moment completes burning in high temperature quirk.Flame generally oneself serves as igniter after lighting, to flowing into
Row igniting.This needs sufficiently high flame temperature just to reach minimum ignition energy, and high flame temperature makes NOx generate increasing
Add.Flameless combustion apparatus is in industry heating and stoving process using very extensively.Need the flameless combustion preheated to air
Generally require device or the measure of special preheated air.
Summary of the invention
In order to solve the problems, such as burner blowing-type burner optimization mixing situation, overheavy firing, occupied area, together
When also for guaranteeing under underload, low excess air factor, NOx emission also meets low emission requirement, present inventor has performed
Sharp study, provide it is a kind of using pressure-air strengthen air-fuel blend, formed conflagration generate flue gas burning side
Method.Speed is higher when the air of high static pressure sprays, and penetration power, shearing, injection, the effect of reversion whirlpool body are stronger, is more advantageous to
The mixing of fuel and air, air and fuel conflagration, the length of flame are obviously shortened, and furnace volume can reduce, and quickly
Interior energy-kinetic energy the conversion of the high-temperature flue gas high speed ejection burner of formation, the high-temperature flue gas quickly formed can strengthen convection current
Heat transfer shortens (exchange thermal medium) heating time, improves the convective heat-transfer coefficient of furnace gas, the heat exchange amount of unit heat exchange area
The volume of height, heat exchanger tube (heat convection position) can also reduce, conducive to the miniaturization of boiler and the raising of heat exchange efficiency；And
The further mode of the multiple spot arrangement disperses combustion of fuel and air, is thinned the thickness of flame front, constant in burning load
In the case where, flammule face shortens the residence time of oxygen, nitrogen in flame front i.e. high-temperature region, so that NOx emission meets low row
Put requirement；Above-mentioned combustion system solves at least one technical problem existing for blowing-type burner in the prior art, thus
Complete the present invention.
The purpose of the present invention is to provide following technical schemes:
(1) a kind of combustion method, the combustion method are strengthened air-fuel including the use of pressure-air and are blended, and keep fuel fast
Quick burning burns and generates flue gas；
Preferably, pressure-air N*105The air of Pa rank, wherein N >=0.1, it is highly preferred that pressure-air is 0.1
~1.0*105The air of Pa.
(2) a kind of burner, for implementing combustion method described in above-mentioned (1).
The pressure-air burner and combustion method provided according to the present invention, has the advantages that
(1) combustion method in the present invention is n*10 using pressure5The air of Pa rank is sprayed by spout, intense impact by
The fuel that fuel nozzle ports spray, quickly breaks up fuel stream, and fuel is broken up once spraying and mixed with air rapidly, air and
Fuel conflagration, the length of flame are obviously shortened, and furnace volume can reduce, and the high-temperature flue gas high speed ejection combustion quickly formed
Device is burnt, the interior energy-kinetic energy conversion of high-temperature flue gas can strengthen convective heat transfer, shorten (exchange thermal medium) heating time, mention
The high convective heat-transfer coefficient of furnace gas, the heat exchange amount of unit heat exchange area is high, and the volume of heat exchanger tube (corresponding heat exchanger) also can
It is enough to reduce, conducive to the miniaturization of boiler and the raising of heat exchange efficiency.
(2) combustion method in the present invention avoids calorific intensity concentration of local in such a way that multiple spot arranges disperses combustion,
The disperse nucleus of flame of high-temperature region, flame region more uniform temperature, conducive to the inhibition generated to NOx.
(3) burner in the preferred embodiment for the present invention, air duct are sandwich, can be efficiently used in mixing chamber
The preliminary preheating of air in interlayer is realized in the heat transfer of high-temperature flue gas, reduces the heat loss of flue gas, and be conducive to mentioning for efficiency of combustion
It is high.
(4) classification of the burner in the preferred embodiment for the present invention, air hose and combustion tube is arranged and combustion gas at different levels
The arrangement shape of pipe and/or air hose at different levels, periphery fuel gas conduit and/or periphery air hose is set with what the cross sectional shape of mixing chamber matched
It sets, is conducive to improve combustion uniformity and stability.
(5) burner in the preferred embodiment for the present invention, by the arrangement of air hose and combustion tube, conducive to control is passed through
The different injection diameter of different zones realizes air feed and combustion gas different ratio, to form disperses combustion combustion, further decreases nitrogen
The discharge of oxide.
Detailed description of the invention
Fig. 1 shows a kind of structural schematic diagram of the burner of preferred embodiment according to the present invention；
Fig. 2 shows a kind of structural schematic diagrams of the burner of preferred embodiment according to the present invention；
Fig. 3 shows a kind of structural schematic diagram of the burner of preferred embodiment according to the present invention；
Fig. 4 shows a kind of side sectional view of the burner of preferred embodiment according to the present invention；
Fig. 5 shows a kind of side sectional view of the burner periphery air hose of preferred embodiment according to the present invention；
Fig. 6 shows a kind of side sectional view of the burner level-one air hose of preferred embodiment according to the present invention.
Drawing reference numeral explanation:
1- air duct；
2- side plate；
3- fuel gas conduit；
The center 31- fuel gas conduit；
The periphery 32- fuel gas conduit；
4- air hose；
41- level-one air hose；
The periphery 42- air hose；
5- gas manifold.
Specific embodiment
Below by drawings and examples, the present invention is described in more detail.Illustrated by these, the features of the present invention
It will be become more apparent from advantage clear.
Dedicated word " exemplary " means " being used as example, embodiment or illustrative " herein.Here as " exemplary "
Illustrated any embodiment should not necessarily be construed as preferred or advantageous over other embodiments.
Based on blowing-type burner, the present inventor studies combustion process.Fuel combustion
Burning can be divided into three root phases: the mixture of the mixing of fuel and combustion air, fuel and air is warming up to ignition temperature, with
And combustion reaction process.Oxidation process in combustion reaction process i.e. fuel and air between oxygen, this stage is actually
It is to complete moment, and the first two stage then takes a long time, therefore it is entire burned to organize mixed process to determine
The feature of journey and flame, and the adaptedness that decide the Temperature Distribution in burner hearth and technique is required.For this purpose, the present inventor will
Research emphasis concentrates on the process of tissue mixing, and obtains research achievement outstanding.It is specifically described as follows.
It is an aspect of the invention to provide a kind of combustion method for boiler, this method is including the use of pressure-air
Strengthen air-fuel blending, makes fuel conflagration and generate the combustion method of flue gas.
In the present invention, burner, be make fuel and air spray in a certain way mixed firinor fuel burning device general designation, be
A kind of equipment that substance is converted to thermal energy by this chemical reaction mode of burning.
Burner hearth in the present invention refers to the radiation heat affected zone of boiler, is thermal energy or other heat using fuel combustion release
Water or a kind of power conversion region of other working medium can be heated, the energy inputted to boiler has chemical energy, electric energy in fuel, pot
Furnace output has steam, high-temperature water or the organic heat carrier of certain thermal energy.The energy inputted in the present invention is the chemical energy of fuel.
Special boiler (such as cyclone furnace) and specific fuel (such as coal dust), combustion chamber are to separate with burner hearth, and stable burning is only played in combustion chamber
Effect, and burner hearth mainly plays heat transfer effect.Fuel is fuel gas in the present invention, without individual combustion chamber.
In the present invention, speed is higher when the air of high static pressure sprays, penetration power, shearing, injection, the effect for inverting whirlpool body
It is stronger, it is more advantageous to the mixing of fuel and air, fuel conflagration, the length of flame is obviously shortened, and flame temperature is high, and then fast
Speed forms high-temperature flue gas, high speed ejection burner.The flue gas of high speed ejection strengthens convective heat transfer, shortens adding for exchange thermal medium
The hot time.High velocity smoke has biggish kinetic energy, plays the role of strong stirring and volume to gas opposing stationary in furnace and inhales, can
To drive the furnace gas for being equivalent to several times to tens times of flue gas of ejection to move together, heat exchange area is (as exchanged heat in furnace
In pipe) form strong circulating current.When high-speed flow washes away heating surface, the wake boundary on heat-transfer surface surface can be thinned
Layer improves convective heat transfer amount, and when burner, which sprays velocity of flue gas, reaches 200-300m/s, convective heat-transfer coefficient is up to 800-
1250kj/(m2.h.℃)。
In addition, for external force to air work, mechanical energy is converted into interior energy during air pressurized, air themperature is increased, according to
Arrhenius equation chemical reaction rate is related to temperature, and the raising of air themperature is conducive to mentioning for combustion chemistry reaction speed
Height is conducive to improve flue-gas temperature.In calculation of radiation heat transferring, can generally be approximately considered the biquadratic of radiant force and absolute temperature at
Direct ratio, flue-gas temperature raising (high-temp combustion causes) are conducive to radiant heat transfer.
Cigarette journey back segment, after high-temperature flue gas completes basic convection current radiation heat transfer, remaining energy is within the condenser with thermal energy
Pattern absorb again.
The above pressure-air accelerates the high velocity smoke that combustion velocity generates rapidly, improves convective heat transfer, high pressure
The raising of air themperature improves radiant heat transfer.The method that pressure-air promotes burning, also has change to the structure of boiler
Meaning is conducive to the miniaturization of boiler and the raising of heat exchange efficiency.
In a kind of preferred embodiment of the present invention, pressure-air N*105The air of Pa rank, wherein N >=0.1,
Preferably, pressure-air is 0.1~1.0*105The air of Pa, more preferably 0.1~0.6*105The air of Pa.Selection 0.1~
0.6*105The embodiment of the air of Pa more preferably is because air pressure is more advantageous to the type selecting of Fan Equipment thus.It adopts
Original 50% can be narrowed down to the volume of preferred embodiment, boiler convection heat exchange part (such as heat exchanger tube)；Boiler Furnace
The volume of thorax position can narrow down to original 75%.The miniaturization of boiler in the present invention, solve heat exchange efficiency and use at
Originally it is difficult to the problem of taking into account, under the premise of high heat exchange efficiency, boiler volume reduces, and manufacture material is few, and manufacturing cost reduces, pot
Occupied area/space contraction of furnace, use cost reduce again.
In a kind of preferred embodiment of the present invention, combustion gas is sprayed by multiple combustion gas spouts, and air passes through multiple skies
Gas blowout mouth sprays, and improves the mixing of air and fuel, conducive to the conflagration of air and fuel.The setting of multiple fuel jet orifices,
One flame is divided into several flammules, the thickness of flame front is thinned once again, in the case where burning load is constant, flammule face
Shorten the residence time of oxygen, nitrogen in flame front i.e. high-temperature region.In addition, the mode of multiple spot arrangement disperses combustion, avoids
Calorific intensity concentration of local, the disperse nucleus of flame of high-temperature region, flame region more uniform temperature.It is obvious that the above favorable factor
There is apparent inhibiting effect to " thermal NO x " and " fuel type NOx ".
Wherein, " thermal NO x " generates the nitrogen mainly in burning, in combustion air under thermal-flame, through aoxidizing
It generates, temperature, excess air coefficient and high-temperature region residence time can all influence the generation of thermal NO x.Wherein temperature is heat
The most important influence factor of power type, Actual combustion process cause NOx since temperature distributing disproportionation is likely to result in high-temperature area
It generates and increases.
" fuel type NOx " is that the nitrogen as contained in fuel is formed in fuel combustion.Its formation mechanism is main
It is related with fuel itself and excess air coefficient.Nitrogen in fuel be converted to the conversion ratio of NOx increase with excess air coefficient and
Increase；As excess air coefficient a > 1, fuel NO_x production quantity is held essentially constant；As excess air coefficient a < 1, conversion ratio
It can decline quickly.
In a kind of preferred embodiment of the present invention, gas jet orifice and air jet orifices are oppositely arranged, and make combustion gas and high pressure
Air moves toward one another.
In a kind of preferred embodiment of the present invention, when burning, excess air factor is between 1-1.1；
It is 60-120m/s that air, which is passed through speed, and it is 1.5-3 times that air is passed through speed that combustion gas, which is passed through speed,；
The burning load of burner is 0.56-2.8MW；
Ignition temperature is between 1200-1500 DEG C in burner；Fire box temperature is between 800-1000 DEG C；
Speed when flue gas ejection burner is 200-300m/s, and convective heat-transfer coefficient is up to 800-1250kj/
(m2.h.℃)；
The volume of boiler convection heat exchange part can achieve original 50%；The volume at boiler furnace position can achieve original
75% come.
In the present invention, which can be suitable for existing burner, do not have to or only need to existing
Burner carries out small technological transformation.
The present inventor further studies combustion system, provides one kind and is used to/is conducive to implement above-mentioned burning
The burner of method.Combustion gas is sprayed by multiple combustion gas spouts in the burner, and air is sprayed by multiple air ports,
To improve the mixing of air and fuel.
In a kind of preferred embodiment of the present invention, as shown in Figure 1, the burner includes blowing unit and combustion gas list
Member, blowing unit include the air duct 1 for participating in surrounding mixing chamber, and combustion unit includes protruding into the fuel gas conduit being axially distributed in mixing chamber
3；
Air duct 1 is sandwich, is connected with pressure-air in interlayer, outer layer wall surface not apertured, the internal layer in mixing chamber
Air jet orifices I is set on wall surface, and pressure-air spurts into mixing chamber by the air jet orifices I on 1 internal layer wall surface of air duct；
Fuel gas conduit 3 is one or more, is distributed multiple gas jet orifices on the tube wall of fuel gas conduit 3 to be passed through combustion into mixing chamber
Gas.
Mixing chamber is the generation air-gas that side plate 2 and air duct 1 surround or air-gas-flue gas mixing and combustion gas
The place of burning.The fuel gas conduit 3 passes through side plate 2 and enters mixing chamber, and side plate 2 plays a supporting role to fuel gas conduit 3.
In further preferred embodiment of the present invention, as shown in Fig. 2, blowing unit further includes protruding into mixing chamber inner shaft
To one or more air hoses 4 of distribution, multiple air jet orifices II are distributed on the tube wall of air hose 4 to be passed through high pressure sky into mixing chamber
Gas.
In the present invention, air duct 1 can be cylinder, square tube, section be regular polygon cylinder, section is irregular polygon
Cylinder etc. can be divided into along its axially symmetric structure cylinder or along its axial unsymmetric structure cylinder, preferably axially and symmetrically along it
Structure cylinder, more preferably cylinder, axial direction are its length direction.
In the present invention, fuel gas conduit 3 and air hose 4 can be round tube, section be the pipe of regular polygon, section is irregular
The pipe etc. of polygon can be divided into along its axially symmetric pipe or along its axial asymmetrical pipe, preferably axially and symmetrically along it
Pipe, more preferably round tube.
As shown in Figure 3 and Figure 4, as a preferred embodiment, air hose 4 and fuel gas conduit 3 are multiple, 4 He of air hose
Fuel gas conduit 3 is layered staggered.In this way, passing through more nozzle hole number and biggish jet surface product, combustion gas and pressure-air
Mixing is more effective.
As further preferred embodiment, fuel gas conduit 3 includes the center fuel gas conduit 31, close positioned at mixing chamber center
The periphery fuel gas conduit 32 of 1 inner wall of air duct and the combustions at different levels optionally between center fuel gas conduit 31 and periphery fuel gas conduit 32
Tracheae.In center fuel gas conduit 31 to the direction of periphery fuel gas conduit 32, fuel gas conduit is named as level-one fuel gas conduit, second gas burning
Pipe ..., N grades of fuel gas conduits, N is positive integer, with level-one combustion gas distance center fuel gas conduit 31 be equidistant or it is extremely close.
Air hose 4 include the level-one air hose 41 for surrounding center fuel gas conduit 31, close to 1 inner wall of air duct periphery air hose 42 and
Other air hoses at different levels optionally between level-one air hose 41 and periphery air hose 42.At center, fuel gas conduit 31 is to periphery air hose 42
Direction on, air hose be named as level-one air hose 41, second level air hose ..., N grades of air hoses, N is positive integer, with level-one air hose distance
Center fuel gas conduit 31 be equidistant or it is extremely close.
In the present invention, the distribution density of the caliber, gas jet orifice of fuel gas conduit at the same level is identical with pore size.Center combustion gas
Gas jet orifice in pipe 31, periphery fuel gas conduit 32 and fuel gas conduit at different levels annular spread in the axial direction.
Each fuel gas conduit is supplied by corresponding gas manifold 5,5 caliber of gas manifold and distance phase of fuel gas conduit preferably at the same level
Deng.
In the present invention, one end that each air hose is located at outside mixing chamber is connected to air duct 1, by the unified air feed of air duct 1.
In a preferred embodiment, the caliber of air hose at the same level, the distribution density of air jet orifices and pore size phase
Together.Air jet orifices on level-one air hose 41, periphery air hose 42 and air hose at different levels annular spread in the axial direction.
In another preferred embodiment of the present invention, as shown in figure 5, point of the caliber of air hose at the same level, air jet orifices
Cloth density is identical with pore size.Air hose 42 unilateral side in periphery opens up air jet orifices II, and opening direction is towards center fuel gas conduit 31, i.e.,
Air jet orifices II is not opened up towards 42 side of periphery air hose of 1 internal layer wall surface of air duct.The unilateral side aperture mode, so that periphery air hose 42
It is consistent with the direction of air jet orifices on air duct 1, it avoids influencing the air inflow of air duct 1, drop due to the multi-faceted aperture of periphery air hose 42
The timely mixing of the low combustion gas that periphery fuel gas conduit 32 is sprayed.
As shown in fig. 6, level-one air hose 41 or other air hoses at different levels are full wall surface aperture, which can be with its week
The combustion gas for enclosing the fuel gas conduit ejection of distribution moves toward one another, and the air-flow of generation is conducive to quickly break up combustion gas, forms the burning of disperse formula, fires
Seedless heart district and high-temperature region are burnt, " thermal NO x " is reduced and generates.
In a kind of preferred embodiment of the present invention, fuel gas conduits at different levels and/or air hose at different levels and periphery fuel gas conduit 32
And/or the arrangement shape of periphery air hose 42 matches with the cross sectional shape of mixing chamber, with improve mixing efficiency, combustion uniformity and
Stability.
As shown in Figure 3, side plate 2 is circle, and air duct 1 is cylinder, i.e., the cross section of its mixing chamber surrounded is circle, combustion
Tracheae 3 and air hose 4 are staggered with annular shape layering in air duct 1.Fuel gas conduit 3 includes the center combustion gas positioned at mixing chamber center
Pipe 31 and periphery fuel gas conduit 32, air hose 4 include 32 periphery of level-one air hose 41 and periphery fuel gas conduit for surrounding center fuel gas conduit 31
Periphery air hose 42.
In a kind of preferred embodiment of the present invention, the diameter of the gas jet orifice of center fuel gas conduit 31 is greater than combustion gas at different levels
The diameter of pipe or periphery fuel gas conduit 32, preferably in center fuel gas conduit 31 to the direction of periphery fuel gas conduit 32, the combustion gas of fuel gas conduit
Injection diameter is on a declining curve, is conducive to realize that air feed and combustion gas different ratio further decrease nitrogen oxygen to form disperses combustion
The discharge of compound.Generally, fuel gas conduit 31 surrounding air excess coefficient in center is less than 1, and the air excess system of periphery fuel gas conduit
Number is greater than 1, realizes fractional combustion.
In the present invention, using above-mentioned burner, the internal layer wall surface of air duct 1 forms the condition of high temperature because heated, in air duct 1
Pressure-air tentatively preheated.Pressure-air after ejection is able to further heat temperature raising, this benefit because of volume suction high-temperature flue gas
In the raising of ignition temperature.The mode of the air smoke mixture of high temperature, the air-flow of high speed and multiple spot arrangement disperses combustion, disperse
The nucleus of flame of high-temperature region compared to low pressure/minute-pressure air further shortens oxygen, nitrogen in flame front i.e. high-temperature region
Residence time equally plays effective control action to the generation of NOx during high temperature conflagration.
Embodiment
Embodiment 1
A kind of combustion method for boiler, using burner as shown in Figure 3 and Figure 4, air duct 1 and side plate 2 are surrounded
Cylindric mixing chamber, fuel gas conduit 3 and air hose 4 protrude into staggered with annular shape layering in mixing chamber.Fuel gas conduit is by being located at mixing
1 center fuel gas conduit 31 and 6 periphery fuel gas conduit 32 at chamber center forms, and air hose is by 6 level-ones around center fuel gas conduit 31
6 periphery air hoses 42 composition of 32 periphery of air hose 41 and periphery fuel gas conduit.
Wherein, the diameter of gas jet orifice is 2mm in center fuel gas conduit 31, the distribution density of gas jet orifice is 580/it is flat
Rice；
The diameter of gas jet orifice is 2mm in 6 periphery fuel gas conduits 32, and the distribution density of gas jet orifice is 780/square meter；
The diameter of air jet orifices II is 8mm on 6 level-one air hoses 41, the distribution density of air jet orifices II is 590/it is flat
Rice；
The diameter of air jet orifices II is 8mm on 6 periphery air hoses 42, the distribution density of air jet orifices II is 440/it is flat
Rice；
The diameter of air jet orifices I is 2mm on air duct 1, and the distribution density of air jet orifices I is 2000/square meter；
The pressure of the pressure-air of feeding is 0.6*105Pa, velocity of liquid assets 120m/s；The velocity of liquid assets of combustion gas is
180m/s；Excess air factor is 1-1.1；
The burning load of burner is 0.56-2.8MW, and ignition temperature is between 1200-1500 DEG C in burner；
Fire box temperature is between 800-1000 DEG C；
Speed when flue gas ejection burner is 200-300m/s, and convective heat-transfer coefficient is up to 800-1250kj/
(m2.h.℃)；
The volume of boiler convection heat exchange part can achieve original 50%；The volume at boiler furnace position can achieve original
75% come.
Embodiment 2
A kind of combustion method for boiler, using burner as shown in Figure 2, the structure and embodiment of burner
1 is consistent, and difference is only that, combustion unit is made of 1 center fuel gas conduit 31 for being located at mixing chamber center, includes in blowing unit
Level-one air hose 41 does not include periphery fuel gas conduit 32 and second level air hose 42.
Wherein, the diameter of gas jet orifice is 2mm in center fuel gas conduit 31, the distribution density of gas jet orifice is 680/it is flat
Rice；
The diameter of air jet orifices II is 8mm on 6 air hoses 4, and the distribution density of air jet orifices is 590/square meter；
The diameter of air jet orifices is 2mm on air duct 1, and the distribution density of air jet orifices is 2000/square meter；
The pressure of the pressure-air of feeding is 0.6*105Pa, velocity of liquid assets 120m/s；The velocity of liquid assets of combustion gas is
180m/s；Excess air factor is 1-1.1；The burning load of burner is 0.56-2.8MW, ignition temperature in burner
Between 1200-1500 DEG C；Fire box temperature is between 800-1000 DEG C；
Speed when flue gas ejection burner is 200-300m/s, and convective heat-transfer coefficient is up to 800-1250kj/
(m2.h.℃)；
The volume of boiler convection heat exchange part can achieve original 50%；The volume at boiler furnace position can achieve original
85% come.
Embodiment 3
A kind of combustion method for boiler " is divided using 08 month 2017 patent of invention filed in 09 day of the applicant
Grade nonflame low nitrogen burning head " implements mechanism as burner.Using burner as shown in Figure 1, the structure of burner
Consistent with embodiment 1, difference is only that, combustion unit is made of 1 center fuel gas conduit 31 for being located at mixing chamber center, does not include
Periphery fuel gas conduit 32 does not include level-one air hose 41, second level air hose 42 in blowing unit.
Wherein, the diameter of gas jet orifice is 2mm in center fuel gas conduit 31, the distribution density of gas jet orifice is 680/it is flat
Rice；
The diameter of air jet orifices is 4mm on air duct 1, and the distribution density of air jet orifices is 2000/square meter；
The pressure of the pressure-air of feeding is 0.6*105Pa, velocity of liquid assets 120m/s；The velocity of liquid assets of combustion gas is
180m/s；Excess air factor is 1-1.1；
Ignition temperature is between 1200-1500 DEG C in burner；Fire box temperature is between 800-1000 DEG C；
Speed when flue gas ejection burner is 200-300m/s, and convective heat-transfer coefficient is up to 800-1250kj/
(m2.h.℃)；
The volume of boiler convection heat exchange part can achieve original 50%；The volume at boiler furnace position can achieve original
95% come.
Comparative example 1
Comparative example 1
A kind of combustion method for boiler, using burner as shown in Figure 3 and Figure 4, difference is only that, feeding
Air is minute-pressure air, and pressure is between 0.06*105Pa。
Combustion parameter is as follows:
The burning load of burner is 0.56-2.8MW, and ignition temperature is between 1200-1500 DEG C in burner；
Fire box temperature is between 800-1000 DEG C；
Speed when flue gas sprays burner is 60m/s, convective heat-transfer coefficient 400-600kj/ (m2.h.℃)；
The volume of boiler convection heat exchange part is 100%；The volume at boiler furnace position is 100%.
Experimental example
Burner and boiler are equipped, adjust different load, to CO, NOx content and exhaust gas temperature in final tail gas into
Row monitoring, determines combustion case.Wherein, load refers to the percentage for reaching burner rated condition in table；O2(%) is
Refer to O in final tail gas2Percentage by volume.CO (%) refers to the percentage by volume of CO in final tail gas.
1 embodiment of table, 1 correlation test data
2 embodiment of table, 2 correlation test data
3 embodiment of table, 3 correlation test data
4 comparative example correlation test data of table
By the analysis of above embodiments, using the burner of pressure-air, the volume of boiler convection heat exchange part can
To narrow down to original 50%；The volume at boiler furnace position can narrow down to original 75-95%, increase air pressure and solve
Heat exchange efficiency and use cost are difficult to the problem of taking into account, and under the premise of high heat exchange efficiency, realize the miniaturization of boiler, boiler
Volume-diminished, manufacture material is few, and manufacturing cost reduces, and occupied area/space contraction of boiler, use cost reduces again.
Combining preferred embodiment above, the present invention is described, but these embodiments are only exemplary
, only play the role of illustrative.On this basis, a variety of replacements and improvement can be carried out to the present invention, these each fall within this
In the protection scope of invention.
Claims (10)
1. a kind of combustion method, which is characterized in that the combustion method is strengthened air-fuel including the use of pressure-air and blended, and makes
Fuel conflagration simultaneously generates flue gas.
2. combustion method according to claim 1, which is characterized in that pressure-air N*105The air of Pa rank, wherein N
>=0.1, it is preferable that pressure-air is 0.1~1.0*105The air of Pa.
3. combustion method according to claim 1, which is characterized in that combustion gas is sprayed by multiple combustion gas spouts, and air is logical
It crosses multiple air ports to spray, combustion gas is moved toward one another with pressure-air.
4. combustion method according to claim 1, which is characterized in that when burning, excess air factor between 1-1.1 it
Between；
It is 60-120m/s that air, which is passed through speed, and it is 1.5-3 times that air is passed through speed that combustion gas, which is passed through speed,；
The burning load of burner is 0.56-2.8MW；
Ignition temperature is between 1200-1500 DEG C in burner；Fire box temperature is between 800-1000 DEG C；
Speed when flue gas ejection burner is 200-300m/s, and convective heat-transfer coefficient is up to 800-1250kj/ (m2.h.℃)；
The volume of boiler convection heat exchange part can achieve original 50%；The volume at boiler furnace position can achieve original
75%.
5. combustion method according to claim 1, which is characterized in that the burner for implementing the combustion method includes
Blowing unit and combustion unit, blowing unit include the air duct (1) for participating in surrounding mixing chamber, and combustion unit includes protruding into mixing chamber
The fuel gas conduit (3) being inside axially distributed；
Air duct (1) is sandwich, is connected with pressure-air in interlayer, outer layer wall surface not apertured, the inner layer wall in mixing chamber
Air jet orifices I is set on face, pressure-air spurts into mixing chamber by the air jet orifices I on air duct (1) internal layer wall surface,
Fuel gas conduit (3) is one or more, is distributed multiple gas jet orifices on the tube wall of fuel gas conduit (3) to be passed through combustion into mixing chamber
Gas.
6. combustion method according to claim 5, which is characterized in that blowing unit further includes protruding into mixing chamber axially to divide
One or more air hoses (4) of cloth are distributed multiple air jet orifices II on the tube wall of air hose (4) to be passed through high pressure sky into mixing chamber
Gas.
7. combustion method according to claim 6, which is characterized in that air hose (4) and fuel gas conduit (3) are multiple, air hose
(4) and fuel gas conduit (3) layering is staggered.
8. combustion method according to claim 7, which is characterized in that the arrangement shape of combustion gas (3) and/or air hose (4) with
The cross sectional shape of mixing chamber matches.
9. combustion method according to claim 8, which is characterized in that air duct (1) is cylinder, fuel gas conduit (3) and air hose (4)
It is staggered with annular shape layering in air duct (1)；
Fuel gas conduit (3) includes the center fuel gas conduit (31) and six periphery fuel gas conduits (32) positioned at mixing chamber center, air hose
(4) include around center fuel gas conduit (31) six level-one air hoses (41) and periphery fuel gas conduit (32) periphery six periphery air hoses
(42)。
10. a kind of burner, for implementing combustion method described in one of the claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910237540.4A CN109899785B (en) | 2019-03-27 | 2019-03-27 | High-pressure air combustion device and combustion method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910237540.4A CN109899785B (en) | 2019-03-27 | 2019-03-27 | High-pressure air combustion device and combustion method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109899785A true CN109899785A (en) | 2019-06-18 |
| CN109899785B CN109899785B (en) | 2020-10-09 |
Family
ID=66953048
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910237540.4A Active CN109899785B (en) | 2019-03-27 | 2019-03-27 | High-pressure air combustion device and combustion method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109899785B (en) |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2463693Y (en) * | 2001-02-03 | 2001-12-05 | 郭伟席 | Mixed gas burner nozzle |
| CN1372102A (en) * | 2001-02-26 | 2002-10-02 | 姜建纲 | Prepositioned mixing all closed type combustion method for gas combustion |
| US6619280B1 (en) * | 2002-05-30 | 2003-09-16 | Dongsheng Zhou | Converging flame burner |
| CN201121895Y (en) * | 2007-10-22 | 2008-09-24 | 张学凤 | High-efficiency combustor |
| CN202581331U (en) * | 2012-04-17 | 2012-12-05 | 宜宾天原集团股份有限公司 | Gas combustion burner |
| CN204042902U (en) * | 2014-09-04 | 2014-12-24 | 郑州鼎力新能源技术有限公司 | A kind of new type nozzle being applicable to gas generator |
| CN205746825U (en) * | 2016-05-19 | 2016-11-30 | 佛山市绿林陶瓷节能科技有限公司 | A kind of multilamellar Premixed fuel gas burner |
| CN107781814A (en) * | 2016-08-30 | 2018-03-09 | 天津征鑫热能设备制造有限公司 | The burner of novel energy-conserving |
| CN108019751A (en) * | 2017-11-08 | 2018-05-11 | 扬州高立达科技产业有限公司 | The low NO of ultralow discharged nitrous oxidesxBurner |
| CN108151020A (en) * | 2018-01-26 | 2018-06-12 | 北京水木星源环保科技有限公司 | Low NO |
| CN208295910U (en) * | 2018-05-23 | 2018-12-28 | 福建鼎元热能技术有限公司 | A kind of high-pressure hot wind burner |
-
2019
- 2019-03-27 CN CN201910237540.4A patent/CN109899785B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2463693Y (en) * | 2001-02-03 | 2001-12-05 | 郭伟席 | Mixed gas burner nozzle |
| CN1372102A (en) * | 2001-02-26 | 2002-10-02 | 姜建纲 | Prepositioned mixing all closed type combustion method for gas combustion |
| US6619280B1 (en) * | 2002-05-30 | 2003-09-16 | Dongsheng Zhou | Converging flame burner |
| CN201121895Y (en) * | 2007-10-22 | 2008-09-24 | 张学凤 | High-efficiency combustor |
| CN202581331U (en) * | 2012-04-17 | 2012-12-05 | 宜宾天原集团股份有限公司 | Gas combustion burner |
| CN204042902U (en) * | 2014-09-04 | 2014-12-24 | 郑州鼎力新能源技术有限公司 | A kind of new type nozzle being applicable to gas generator |
| CN205746825U (en) * | 2016-05-19 | 2016-11-30 | 佛山市绿林陶瓷节能科技有限公司 | A kind of multilamellar Premixed fuel gas burner |
| CN107781814A (en) * | 2016-08-30 | 2018-03-09 | 天津征鑫热能设备制造有限公司 | The burner of novel energy-conserving |
| CN108019751A (en) * | 2017-11-08 | 2018-05-11 | 扬州高立达科技产业有限公司 | The low NO of ultralow discharged nitrous oxidesxBurner |
| CN108151020A (en) * | 2018-01-26 | 2018-06-12 | 北京水木星源环保科技有限公司 | Low NO |
| CN208295910U (en) * | 2018-05-23 | 2018-12-28 | 福建鼎元热能技术有限公司 | A kind of high-pressure hot wind burner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109899785B (en) | 2020-10-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104508374B (en) | The gaseous fuel burners of high-energy high combustion rate low pollution emission and high thermal conductivity | |
| CN204063038U (en) | Low NO xflue gas is from return flow burner | |
| CN202012913U (en) | Novel flue gas self-reflux low-oxygen combustor | |
| CN112682780A (en) | Gas water heater | |
| CN207035119U (en) | A kind of low NOx self preheating burners of direct injection | |
| CN104266190B (en) | oxygen enrichment flameless gas burner and control method thereof | |
| CN102425793A (en) | Self-backheating swirling burner for fuel gas with low heat value | |
| CN105737152A (en) | Combusting device for low nitrogen combustion of classification pre-mixed swirling flow | |
| CN207539904U (en) | Ultralow nitrogen gas burner | |
| CN110469851A (en) | A kind of low nitrogen non-oxidation burner of self-preheating type flue gas self-circulation type | |
| CN109899786A (en) | Nonflame low NO and nonflame low nitrogen burning method | |
| CN205119061U (en) | Gas fractional combustion ware | |
| CN110822705B (en) | Combustion heat exchange device, gas wall-mounted furnace and gas water heater | |
| CN107893991B (en) | Loop swirl-flow premixed multiple rows of array jetstream whirl penetrates the burner of accumulation of heat sleeve | |
| CN207527582U (en) | The low nitrogen rotational flow gas-fired combustor of flue gas recirculation built in gas-air Accurate Classification | |
| CN205939147U (en) | Steady flame formula combustor | |
| CN107504487B (en) | Continuous dispersion type combustion device and method for forming continuous dispersion type combustion | |
| JPH0579614A (en) | Burner contstruction for low calorific gas and burning method therefor | |
| CN104132343A (en) | Radiant tube combustor | |
| CN205579544U (en) | Discharge pulverized coal combustion system a little | |
| CN203703982U (en) | Combustor and combustion furnace | |
| CN105531541B (en) | For burn gas fuel or fluid combustion device assembly and method | |
| CN109899785A (en) | Pressure-air burner and combustion method | |
| CN107461742B (en) | Graded flameless low-nitrogen combustion head | |
| CN201819218U (en) | Horizontal internal mixing type ceramics burner used for top combustion stove |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |