CN110274227A - A kind of burning air feed plectane and its buner system - Google Patents
A kind of burning air feed plectane and its buner system Download PDFInfo
- Publication number
- CN110274227A CN110274227A CN201910433531.2A CN201910433531A CN110274227A CN 110274227 A CN110274227 A CN 110274227A CN 201910433531 A CN201910433531 A CN 201910433531A CN 110274227 A CN110274227 A CN 110274227A
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- Prior art keywords
- air
- heat exchange
- ventilation hole
- burning
- cylinder
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
- F23D11/101—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet
- F23D11/102—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet in an internal mixing chamber
- F23D11/103—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet in an internal mixing chamber with means creating a swirl inside the mixing chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
- F23D11/101—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet
- F23D11/105—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet at least one of the fluids being submitted to a swirling motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/36—Details, e.g. burner cooling means, noise reduction means
- F23D11/40—Mixing tubes or chambers; Burner heads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
- F23D11/36—Details, e.g. burner cooling means, noise reduction means
- F23D11/40—Mixing tubes or chambers; Burner heads
- F23D11/408—Flow influencing devices in the air tube
Abstract
The present invention provides a kind of burning air feed plectane and its buner system, the burning air feed plectane includes center vent and circumferential ventilation hole, circumferential ventilation hole, for using center vent center as the sector structure in the center of circle；Circumferential ventilation hole asymmetric distribution.The setting that the present invention passes through the shape of above-mentioned center vent and circumferential ventilation hole, position and its angle, fuel oil and air can be promoted just to be sufficiently mixed in premixing ignition room, increase the contact area of air and fuel oil at atomized fuel movement initial stage, improve the burning velocity of fuel oil, reduce the pressure in diffusion combustion stage, be conducive to reduce burner axial length demand, reduce burner volume.
Description
Technical field
The invention belongs to field of combustion technology, and in particular to a kind of actuating unit assistant starting warmer burning
Device.
Background technique
China has a vast territory, and weather and terrain environment are complicated, and Engines Used In Special Vehicle transmission system faces rubs under extremely cold environment
The unfavorable factors such as engine ignition difficulties under the secondary locking of wiping, insufficient lubrication, the decline of storage battery power supply ability and hypobaric, greatly
The reliability of vehicle is reduced greatly.Warmer transmits heat as a kind of combustion heat-exchange device, by coolant liquid, can be extreme
The cooling system of vehicle, lubricating system, transmission system, dynamical system etc. are heated under environment, each system is made to reach best
Working condition eliminates the unfavorable factor that vehicle launch faces.Meanwhile the lightweight of vehicle and the adaptation of a variety of extreme environmental conditions
Property proposes high power density to warmer, highly integrated, efficient low-consume, the requirement of high adaptivity.
Existing warmer generally faces the problem that efficiency of combustion is low with power density, carbon distribution is serious, and warmer technology is most
The key link is burner stable with satisfaction, efficient, conflagration.Warmer burning is a complicated physics
And chemical process, influence factor includes the geometric dimension of combustion chamber and shape, the turbulence intensity of Combustion Flow Field and scale, whether there is or not whirlpools
The distribution of air-fuel ratio, turbulent diffusion blending speed etc. in stream countercurrent zone, oil atomizing position and taper, flow field.Based on the above back
Scape technology and experimental study, the present invention propose a kind of premixing ignition, diffusion burner system.
Summary of the invention
The invention proposes a kind of premixing ignition, diffusion burner mounting seat and its burners, are applied to atomized fuel
In high-tension ignition formula warmer, with efficiency of combustion and summation watt rating are high, igniting is reliable, are suitable for a variety of extreme environments, hot benefit
With the high feature of rate.
Technical solution: a kind of diffusion burner, the diffusion burner include transitional cylinder, secondary air cylinder, enter the wind three times
Transition is entered the wind in the other end connection of transition rings, one end of the transition tube rear end connection secondary air cylinder, secondary air cylinder three times
Air inlet hole is arranged on the transitional cylinder for the first end of ring, and air inlet hole is arranged in the secondary air cylinder, described to enter the wind transition rings three times
Air inlet is set.
Preferably, diffusion burner transitional cylinder is conical ring, transitional cylinder is circumferentially uniformly distributed several circular holes, is used as diffusion
Burn main air supply channel.
Preferably, diffusion burner secondary air cylinder both ends are opening design, one end is connect with transitional cylinder bigger diameter end,
Diffusion combustion space is formed, the other end is connect with air inlet transition rings bigger diameter end three times, is used as diffusion combustion exhaust passage.
Preferably, diffusion burner secondary air cylinder outer wall is evenly distributed with several diversion pipes, it is secondary for diffusion burner
Air inlet.
Preferably, multiple rows of air inlet hole is arranged in secondary air cylinder, the length of secondary air cylinder is L, apart from it is secondary into
The distance of wind drum inlet is X, and the internal diameter of air inlet hole is D, D=F1(X), meet following require:
D '>0,0≤X<L/2；
D ' < 0, L/2≤X≤L.
D ' is the first order derivative of D.
Preferably, along transitional cylinder to entering the wind transition rings direction three times, the internal diameter of air inlet hole along entering the wind transition three times
Increased amplitude is increasing among ring entrance to air inlet transition rings three times, from being entered the wind among transition rings three times to entering the wind three times
It is increasing to cross the ever-reduced amplitude in ring outlet, meets following require:
D ">0,0≤X<L/2；
D " > 0, L/2≤X≤L.
D " is the second derivative of D.
Preferably, diffusion burner is entered the wind three times is uniformly provided with several circles on transition rings minor diameter band of column intermediate altitude
Hole, major diameter transition thin plate are circumferentially provided with several through-holes, are respectively used to diffusion combustion end and do not exhaust fuel burning and diffusion combustion
Burn the tissue and fuel burning in chamber interior flow field.
A kind of buner system, including burner outer cylinder, air feed mounting seat, premixing ignition room and diffusion burner, institute
It states premixing ignition room and diffusion burner is arranged in burner outer cylinder, air feed mounting seat, premixing ignition room and diffusion combustion
Room is successively linked in sequence, and burner outer cylinder first end is connected on the outer wall of mounting bracket in the connection of premixing ignition room one end
Heart ventilation opening, the other end connect diffusion burner, and diffusion burner tail end connects exhaust gas flue, and the diffusion burner is front
The diffusion burner.
Preferably, heat exchange core body is arranged in exhaust gas flue, the heat exchange core body includes round tube and flat tube, the round tube
Round tube all is sequentially distributed along the flow direction of exhaust gas perpendicular to the flow direction of exhaust gas with the flow direction of flat liquid in pipe
And flat tube.
Preferably, the multiple dispersion heat exchange structures of subsection setup in the round tube, the dispersion heat exchange structure includes core
And shell, in the shell, the shell is connected and fixed with heat transfer tube wall, and the core includes by several numbers for the core setting
The grid sheet of amount is arranged in a combination, and connection forms lattice and deletes hole between grid sheet；Along the flow direction of circle tube fluid, round tube
The interior multiple dispersion heat exchange structures of setting, from the entrance of round tube to the outlet of round tube, dispersion heat exchange structure length is increasingly longer；
From the entrance of round tube to the outlet of round tube, the increasingly longer amplitude of dispersion heat exchange structure length is continuously increased.
Compared with prior art, of the invention to have the advantage that
1) the invention proposes a kind of premixing ignition, diffusion burner, it include air feed mounting seat, premixing ignition room,
Diffusion burner, burner outer cylinder, four component parts, which connect to weld with one heart, forms burner entirety.Atomized fuel outlet with it is pre-
Mixed combustion chamber eddy flow generating plate is parallel, and partial air enters premixing ignition room, the air of rotational flow and atomization through swirl channel
Fuel oil is sufficiently mixed near atomizer and is formed flammable oil-gas gaseous mixture, as the fire source of burner ignition burning, ensure that
Reliable ignition.The air of lean premixed combustor is entered to oil-gas mixed Daqu retardation by part flow arrangement lower layer ventilation hole, and
Form oil-gas gaseous mixture with fuel oil as much as possible is while occurring fray-out of flame phenomenon after avoiding ignition process
The diffusion combustion stage provides premix gaseous mixture, reduces diffusion combustion stage work pressure, forms the stable flame source of burner,
Be conducive to flame transmission and the raising of efficiency of combustion.
2) diffusion burner transitional cylinder is designed as outer cone ring, and diameter gradually increases, and is to cooperate big cone angle atomizer
And the tissue of Combustion Flow Field, increase the contact area of fuel oil and air, reduce the probability of fuel oil attachment wall surface, while utilizing transition
Several circular holes that cylinder is circumferentially arranged, guidance air-flow increase near the unburned fuel oil of flame inside to burning chamber central zone flowing
Air content improves the burn rate of fuel oil.
3) 1/2 axial height of diffusion burner secondary air cylinder is nearby circumferentially with several cylindrical diversion pipes, enters
The partial air of diffusion combustion air intake passage enters combustion chamber through diversion pipe high speed, and the fuel oil ejected and flame are lifted in upper
Portion space reduces axial movement speed, increases its residence time in the combustion chamber, be conducive to the full combustion of fuel oil.
4) diffusion burner enters the wind transition rings major diameter transition thin plate three times and is circumferentially provided with several backflow through hole, into diffusion
The partial air via through holes of burning air intake passage flow up, and form gas together between the fuel oil and chamber wall ejected
Barrier, avoids fuel oil from being attached on chamber wall and forms carbon distribution, while being guided in air-flow uphill process by conical ring transitional cylinder, with mistake
The air collective effect of cylinder circumferential direction air inlet entrance is crossed, tumble flow is formed in heart district domain in a combustion chamber, increases the mixing journey of oil-gas
Degree improves fuel combustion efficiency and burning velocity, is conducive to axial length needed for reducing fuel oil full combustion, shortens burner
Highly.
5) diffusion burner enters the wind be uniformly provided with several circular holes on transition rings minor diameter band of column intermediate altitude three times, into expansion
The partial air for dissipating burning air intake passage enters burner ends through this hole, reduces flame movement velocity, not yet fires with flame
Most small part fuel oil is mixed and burned, and improves the efficiency of combustion of fuel oil.
6) residual heat heat-exchanging device is arranged in exhaust gas flue in the present invention, and the heat exchange core body is round tube-flat tube combined type heat exchange
Structure, heat exchange core body front end use the tubular heat exchange structure of thin-wall circular, are exchanged heat in heat exchange core body rear end using multiple rows of thin-walled flat pipe type
Structure is effectively reduced the film boiling phenomenon of water side using different heat exchange structures according to caloric receptivity is different in different location, drops
The low thermic load of heat exchange core body, improves heat exchange efficiency.
7) heat-exchanger rig of the present invention, heat exchange core body use tubular heat exchanger tube, and the heat exchanger tube diameter is along cigarette
Flow of air direction gradually becomes smaller, and can effectively reduce the film boiling phenomenon of water side, increases water side convection heat transfer intensity, reduces
The thermic load of heat exchange core body, improves heat exchange efficiency.
8) heat-exchanger rig of the present invention, the spacing of the dispersion heat exchange structure in round tube with apart from round tube entrance away from
Reduce from continuous, can effectively reduce the film boiling phenomenon of water side, increase water side convection heat transfer intensity, reduce heat exchange core
The thermic load of body, improves heat exchange efficiency.
9) heat-exchanger rig of the present invention, the length of the dispersion heat exchange structure in round tube with apart from round tube entrance away from
Reduce from continuous, can effectively reduce the film boiling phenomenon of water side, increase water side convection heat transfer intensity, reduce heat exchange core
The thermic load of body, improves heat exchange efficiency.
10) heat-exchanger rig of the present invention is arranged grating type in heat exchanger tube and disperses heat exchange structure, exchanges in heat pipe
Steam water interface is separated, and the film boiling phenomenon of water side is effectively reduced, and is increased water side convection heat transfer intensity, is reduced and change
The thermic load of hot core, improves heat exchange efficiency.
Detailed description of the invention
Fig. 1 is a kind of main view of embodiment of premixing ignition of the invention, diffusion burner；
Fig. 2 is the left view of the premixing ignition of Fig. 1, diffusion burner；
Fig. 3 is the main view of premixing ignition room whirlwind generating plate of the invention；
Fig. 4 is the cross-sectional view of premixing ignition room whirlwind generating plate of the invention；
Fig. 5 is the main view of three layers of diffusion burner air inlet transition rings of the invention.
Fig. 6 is the top view of three layers of diffusion burner air inlet transition rings of the invention.
Fig. 7 is air feed mounting seat schematic diagram of internal structure of the invention；
Fig. 8 is air feed mounting seat external structure schematic diagram of the invention；
Fig. 9 is a kind of main view of embodiment of UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig of the invention；
Figure 10 is the heat exchange core body water side structure figure of UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig；
Figure 11 is the heat exchange core body gas side structure chart of UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig；
Figure 12 is the dispersion heat exchange structure cross-sectional structure schematic diagram of UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig；
Figure 13 be UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig dispersion heat exchange structure in heat exchanger tube arrangement schematic diagram；
Figure 14 is another schematic diagram that the bright dispersion heat exchange structure of UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig is arranged in heat exchanger tube.
In figure: 1. mounting brackets；Positioning convex platform 1-1；Flange 1-2；2. burn air feed plectane；2-1 center vent；2-2
Circumferential ventilation hole；3. eddy flow generating plate；3-1 centre bore；3-2 swirl channel；Raised 3-3；4. part flow arrangement；5. sleeve；6. mistake
Cross cylinder；7. secondary air cylinder；8. entering the wind transition rings three times；9. muff；10. premixing exhaust vent；11. premix air inlet
Hole；12. main air supply hole；13. diversion pipe；14. return port；15. three layers of air inlet hole；16. flow manifold；17 flues, 18 heat exchange cores
Body, 19 front supports, 20 rear supports, 21 upper cover plates, 22 lower cover plates, 23 import headers, 24 outlet headers, 25 intermediate members,
26 round tubes, 27 outlet pipes, 28 separate heat exchange structure, 29 shells, 30 grid sheets, 31 grate openings, 32 flat tubes, 33 fins, 34 exhausts
Mouthful, 35 exhaust outlets, 36 inner fins.
Specific embodiment
Specific embodiments of the present invention will be described in detail with reference to the accompanying drawing.
As shown in Figure 1, a kind of premixing ignition, diffusion burner, the burner includes burner outer cylinder, air feed installation bottom
Seat, premixing ignition room and diffusion burner, the air feed mounting seat, premixing ignition room and diffusion burner are sequentially connected in series company
It connects, the premixing ignition room and diffusion burner are arranged in burner outer cylinder.
Preferably, the air feed mounting seat includes mounting bracket 1 and burning air feed plectane 2, the mounting bracket 1 the
Open at one end, second end setting burning air feed plectane 2,2 center of burning air feed plectane is arranged center vent 2-1, surrounds
Center vent 2-1 is circumferentially arranged circumferential ventilation hole 2-2, and premixing ignition room first end connects center vent 2-1, and second
End connection diffusion burner, the premixing ignition room includes eddy flow generating plate 3, part flow arrangement 4 and sleeve 5, the part flow arrangement 4
It is arranged in concentric circles with sleeve 5, eddy flow generating plate 3 is set in the part flow arrangement 4, is formed and is divided between part flow arrangement 4 and sleeve 3
Runner 16 is flowed, the sleeve 3 extends to the center vent 2-1 of burning air feed plectane 2, and close with the periphery center vent 2-1
Envelope connects, setting premix air outlet 10 and premix air inlet 11, the premix air outlet 10 on the tube wall of the flow manifold 16
It is arranged between eddy flow generating plate 3 and center vent (front end that eddy flow generating plate 3 is set), the premix air inlet 11
It is arranged between eddy flow generating plate 3 and diffusion burner；The diffusion burner includes transitional cylinder 6, secondary air cylinder 7, three times
Air inlet transition rings 8, the outer wall of 6 one end of transitional cylinder connection part flow arrangement 4, one end of other end connection secondary air cylinder 7, two
The other end of secondary air inlet cylinder 7 connects the first end for entering the wind transition rings 8 three times, setting air inlet hole 12 on the transitional cylinder 6, and described two
Air inlet hole 13 is arranged in secondary air inlet cylinder 7, and air inlet 15 is arranged in the transition rings 8 of air inlet three times, and 9 first end of burner outer cylinder connects
It connects on the outer wall of mounting bracket 1, second end is connected to the second end for entering the wind transition rings 8 three times.
The invention proposes a kind of premixing ignitions, diffusion burner, it includes air feed mounting seat, premixing ignition room, expands
Combustion chamber, burner outer cylinder are dissipated, four component parts, which connect to weld with one heart, forms burner entirety.Atomized fuel outlet and premix
Combustion chamber eddy flow generating plate is parallel, and partial air enters premixing ignition room through swirl channel, and the air of rotational flow and atomization are fired
Oil is sufficiently mixed near atomizer and is formed flammable oil-gas gaseous mixture, and as the fire source of burner ignition burning, ensure that can
By igniting.The air of lean premixed combustor is entered to oil-gas mixed Daqu retardation by part flow arrangement lower layer ventilation hole, and with
Fuel oil as much as possible forms oil-gas gaseous mixture, while occurring fray-out of flame phenomenon after avoiding ignition process, to expand
It dissipates combustion phases and premix gaseous mixture is provided, reduce diffusion combustion stage work pressure, form the stable flame source of burner, have
Conducive to flame transmission and the raising of efficiency of combustion.
Preferably, the mounting bracket 1 is equipped with burner positioning convex platform 1-1, the installation positioning of burner is realized.
Preferably, mounting bracket 1 is the stairstepping cylinder of Diameter Gradual Change, first end face is provided with mounting flange 1-2, uses
In burner axially position, lateral surface is provided with installation fixing lug boss 1-1, circumferentially positioned for carrying out to burner.
Preferably, being stepped on the inside of mounting bracket 1, gradually tapered up from first end to second end.It is efficient to be formed
Quick air inlet effect.
Preferably, mounting bracket 1 have three-level ladder, be respectively from first end to second end the first order, the second level and
The third level is tapering transition between three-level ladder, and the internal diameter of three-level ladder is successively are as follows: 180-190mm, 160-170mm, 135-
145mm
Further preferably, the internal diameter of three-level ladder is successively are as follows: 186mm, 163mm, 138mm.
By above-mentioned preferred size, air inlet effect is further increased.
Preferably, fixing lug boss 1-1 is mounted on the step of the second level.
The present invention by setting three-level ladder and three-level step dimension it is preferred, can effectively improve into burner
The flowing velocity of air enhances exercise intensity of the air in premixing ignition room and diffusion combustion room, increases air and burning
Contact area.
Preferably, center vent and circumferential ventilation hole gross area ratio are (3.5-4.5): 1；Preferably, 3.7:1.
Preferably, the 2 circumferential direction ventilation hole 2-2 of burning air feed plectane is using the center center vent 2-1 as the center of circle
Sector structure.
Preferably, circumferential ventilation hole 2-2 asymmetric distribution.
Preferably, circumferential direction ventilation hole 2-2 is provided with 8.8 circumferential direction ventilation hole 2-2 are asymmetric distribution, specifically
Distribution are as follows: the area of the circumferential ventilation hole 2-2 of lowest part is greater than the circumferential ventilation hole 2-2 of other positions.
Preferably, the central angle of other positions 7 fan rings is identical, angular interval corresponding to other 7 adjacent fan ring sides
It is identical.
Further preferably, angular interval corresponding to the central angles of adjacent 7 fans ring and adjacent fan ring side is identical, respectively
19 °, 26 °, another fan ring central angle is 23.5 °, and the angular interval with adjacent fan ring is 17 °, 30.5 °.
By the setting of the shape of above-mentioned center vent and circumferential ventilation hole, position and its angle, fuel oil can be promoted
It is just sufficiently mixed in premixing ignition room with air, increases the contact area of air and fuel oil at atomized fuel movement initial stage, mention
The burning velocity of high fuel oil reduces the pressure in diffusion combustion stage, is conducive to reduce burner axial length demand, reduces burning
Body product.
Preferably, 3 center of eddy flow generating plate is equipped with circular hole 3-1, it is used as atomized fuel entrance, is circumferentially with eddy flow
Channel 3-2, the entrance as combustion air.
Preferably, the swirl channel 3-2 is that the 3-2 that cracks in eddy flow generating plate is formed.The seam extends to circular hole
3-1.Further preferably, the side 3-3 for stitching 3-2 is tilted outward (the first extreme direction of premixing ignition room), so that it is logical to form eddy flow
Road.Further preferably, the side 3-3 of the tilting is bending structure, and the bending angle of bending structure is preferably obtuse angle.Preferably
100-120 °, preferably 109 °.Preferably, outer diameter of the inflection point 3-4 closer to eddy flow generating plate.Preferably, inflection point
3-4 is 8-10 times with outer diameter distance at a distance from 3 internal diameter of eddy flow generating plate, preferably 9 times.
Preferably, interplanar spacing where the eddy flow generating plate front end face and the upper layer premix air outlet center of circle is 6mm.
Preferably, the side 3-3 of seam 3-2 and the other side 3-5 of seam form triangle.Swirl channel section triangle pair
Answering interior angle is 6 °, 65 °.The side 3-3 and eddy flow generating plate angle of tilting are 17 °.
Preferably, the premix air inlet hole 11 on part flow arrangement 4 is column structure, to 4 internal stretch of part flow arrangement.
Preferably, the height of column structure is 3mm.
Preferably, circumferentially have the swirl channel 3-2 of several protrusions on the basis of 3 centre bore of eddy flow generating plate,
Channel cross-section is triangle, and depth of section is gradually increased along far from spiral board center position.
Premixing ignition room of the present invention by using Novel structure, atomized fuel entrance and lean premixed combustor eddy flow generating plate
In parallel, partial air enters premixing ignition room through swirl channel, and the air and atomized fuel of rotational flow fill near atomizer
Divide and mix and formed flammable oil-gas gaseous mixture, as the fire source of burner ignition burning, ensure that reliable ignition.
Preferably, diffusion burner transitional cylinder 6 is conical ring, miner diameter end and the outlet of premixing ignition room connect, are used as pre-
Mixed combustion flame and diffusion combustion fuel filler.
Preferably, transitional cylinder 6 is circumferential to be uniformly distributed several circular holes 12, it is used as the main air supply channel of diffusion combustion.
Diffusion burner transitional cylinder is designed as outer cone ring, and diameter gradually increases, be in order to cooperate big cone angle atomizer and
The tissue of Combustion Flow Field increases the contact area of fuel oil and air, reduces the probability of fuel oil attachment wall surface, while utilizing transitional cylinder
Several circular holes being circumferentially arranged, guidance air-flow increase the sky near the unburned fuel oil of flame inside to burning chamber central zone flowing
Gas content improves the burn rate of fuel oil.
Preferably, 7 both ends of diffusion burner secondary air cylinder are opening design, one end and 6 bigger diameter end of transitional cylinder connect
It connects, forms diffusion combustion space, the other end is connect with air inlet 8 bigger diameter end of transition rings three times, is used as diffusion combustion exhaust passage.
Preferably, 7 outer wall of diffusion burner secondary air cylinder is evenly distributed with several diversion pipes 13, it to be used for diffusion burner two
Secondary air inlet.
Preferably, diversion pipe 13 is arranged at 1/2 axial height plane of secondary air cylinder 7.
1/2 axial height of diffusion burner secondary air cylinder is nearby circumferentially with several air inlet holes, into diffusion combustion
The partial air of air intake passage enters combustion chamber through diversion pipe high speed, and the fuel oil ejected and flame are lifted in upper space,
Axial movement speed is reduced, increases its residence time in the combustion chamber, is conducive to the full combustion of fuel oil.
Preferably, multiple rows of air inlet hole 13 is arranged in secondary air cylinder 7.The internal diameter of air inlet hole is along transitional cylinder 6 to three times
Air inlet 8 direction of transition rings first increases to be reduced afterwards.
The length of secondary air cylinder 7 is L, and the distance apart from 7 entrance of secondary air cylinder is X, and the internal diameter of air inlet hole is
D, D=F1(X), meet following require:
D '>0,0≤X<L/2；
D ' < 0, L/2≤X≤L.
D ' is the first order derivative of D.
By the variation of the internal diameter of above-mentioned air inlet 13, according to 7 fuel combustion situation of secondary air cylinder, so that combustion-supporting
The flow of wind axially rule variation, so that burner combustion reaches optimal efficiency of combustion.
It is found through experiments that, by so set, efficiency of combustion can be further increased.
Further preferably, along transitional cylinder 6 to entering the wind 8 direction of transition rings three times, the internal diameter of air inlet hole along entering the wind three times
Increased amplitude is increasing among 8 entrance of transition rings to air inlet transition rings 8 three times, from being entered the wind among transition rings 8 three times to three
It is increasing that secondary air inlet transition rings 8 export ever-reduced amplitude, meets following require:
D ">0,0≤X<L/2；
D " > 0, L/2≤X≤L.
D " is the second derivative of D.
It is found through experiments that, by so set, 10% or so efficiency of combustion can be further increased.
The air inlet hole is cylindrical diversion pipe 13, and diversion pipe 13 penetrates cylinder outer wall face and diffusion combustion intake adit connects
It is logical.Preferably, diversion pipe 13 stretches out wall face height 3mm, internal diameter is 10mm.
Preferably, diffusion burner is entered the wind three times is uniformly provided with several circles on 8 minor diameter band of column intermediate altitude of transition rings
Hole 15, major diameter transition thin plate are circumferentially provided with several through-holes 14, are respectively used to diffusion combustion end and do not exhaust fuel burning and expansion
Dissipate the tissue and fuel burning in combustion chamber flow field.
The air inlet 8 second end of transition rings (i.e. tail portion, the outlet air position of Fig. 1) three times connects exhaust gas flue 17, exhaust gas cigarette
UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig is set in road, and the UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig includes heat exchange core body 18, heat exchange core body front supports
19 and heat exchange core body rear supports 20, the heat exchange core body 18, front supports 19 and rear supports 20 are arranged in exhaust gas flue 17
Interior, the heat exchange core body 18 includes upper cover plate 21, lower cover plate 22 and Duo Gen heat exchanger tube, and heat exchanger tube connection is through upper cover plate 21 under
Cover board 22, the front supports 19 and rear supports 20 are located at 18 both ends of heat exchange core body, are collectively formed with heat exchange core body 18
The gas side channel of heat-exchanger rig；The front supports 1 connect heat exchange core body upper cover plate 21,17 tube wall of lower cover plate 22 and flue, institute
It states rear supports 19 and connects heat exchange core body upper cover plate 21,17 tube wall of lower cover plate 22 and flue, the front supports 19, rear supports
20, the liquid-inlet header 23 and outlet header 24 of heat-exchanger rig is collectively formed in heat exchange core body cover board and 17 tube wall of flue.
Heat-exchanger rig of the present invention, using tube wall as a portion of the import header of heat-exchanger rig and outlet header
Part is formed the import header and outlet header of heat-exchanger rig using flue tube wall, heat-exchanger rig is integrally all disposed within to exhaust gas cigarette
In road, avoid that import header and outlet header is separately provided so that heat-exchanger rig take up space it is few, reduce heat exchange core body volume with
Weight, it is compact-sized.
Preferably, the front supports 19 and rear supports 20 are tubular structure, the 19 tube wall both ends of front supports
Connect lower cover plate 21,22 and flue tube wall, the tube wall both ends connection lower cover plate 21,22 and flue tube wall of rear supports 20.
By so set, the exhaust gas for making front supports 19 and rear supports 20 be respectively formed heat-exchanger rig exhaust gas side enters
Mouth and waste gas outlet, further such that compact-sized.
It is managed preferably, the tube wall of the front supports 19, rear supports 20 connects flue 17 by intermediate member 25
Wall, the intermediate member 25 are curved plate structure, as shown in Figure 1.
Preferably, the water inlet pipe (not shown) and outlet pipe 27 of the heat-exchanger rig are separately positioned on 17 tube wall of flue
And it is respectively communicated with import header and outlet header.
Preferably, import header is located at the lower part of flue, outlet header is located at the top of flue.
Preferably, the heat exchanger tube includes round tube 26, the round tube 26 is arranged perpendicular to exhaust gas flow direction, along useless
The diameter in flow of air direction, round tube 26 is smaller and smaller.If the distance apart from exhaust gas entrance is S, then the internal diameter of round tube is D, if D=
F (S), then F ' (S) < 0, F ' (S) is the first order derivative of F (S).
Because the waste air temperature at inlet of UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig is very high, so that the liquid in heat exchanger tube forms carbonated drink
Mixture, and along the flow direction of flue gas, the vapour phase ratio formed in steam water interface is lower and lower, and liquid phase ratio is more next
It is higher.Because the vapour phase ratio of front end is high, the space occupied is necessarily big, therefore passes through the variation of round tube diameter, so that changing
The round tube cross-sectional area of the front end of thermal is big, so that inner space is sufficient for the distribution of liquid phase and meets heat exchanger tube
The requirement of pressure avoids front heat exchange pipe pressure excessive, so that integrally all heat exchange overpressures are uniform for heat exchange core body, keeps away
Exempt from excessive with pressure, extends the service life of heat-exchanger rig.
Preferably, then F " (S) > 0, F " (S) are the second derivatives of F (S).I.e. along exhaust gas flow direction, round tube it is straight
The smaller and smaller amplitude of diameter is continuously increased.
It is found through experiments that, it, can be with the pressure in further satisfaction different location round tube point by the setting of upper F " (S) > 0
Cloth is further ensured that heat exchange overpressure is evenly distributed.
Preferably, as shown in Figure 10, along the flow direction of flue gas, round tube 26 is set as multiple rows of, and the round tube 26 is
Shifted structure, the spacing between the center of circle of adjacent round tube 26 are 1.1-1.3 times of 26 outer diameter of round tube.26 outer diameter of round tube is adjacent two
The average value of root heat exchange pipe outside diameter.
Preferably, the diameter of latter row's round tube 26 is the 0.93- of adjacent front-seat round tube diameter along exhaust gas flow direction
0.98 times.
Above-mentioned proportionate relationship is optimal proportionate relationship through a large number of experiments.Pass through above-mentioned caliber and spacing
The setting of size enables to pressure distribution to be optimal.
Preferably, front supports 19 form the intake channel of gas side, rear supports 20 form the exit passageway of gas side.
Preferably, the heat exchanger tube includes round tube 26, the multiple separation heat exchange structures 28 of subsection setup in the round tube 26,
The separation heat exchange structure 28 includes core and shell 29, and the core is arranged in shell 29, the shell 29 and round tube 26
Inner wall is connected and fixed, and the core includes by a number of grid sheet 30, and connection forms grate opening 31 between grid sheet 30.
Because exhaust gas temperature is very high, so that the process in round tube will form stream-liquid two-phase flow, the present invention is arranged in round tube
Grid heat exchange dispersion heat exchange structure is separated the liquid and gas in two-phase fluid by dispersion heat exchange structure, by liquid phase
It is dispersed into small liquid group, by gas phase dispersion at minute bubbles, inhibits the reflux of liquid phase, promotes gas phase smooth outflow, play regime flow
Effect, have the effect of vibration and noise reducing.Meanwhile the present invention disperses heat exchange structure by setting grid, is equivalent in heat exchanger tube
Inner fin is inside increased, heat exchange is enhanced, improves heat transfer effect.
The present invention is because all cross-section locations by gas-liquid two-phase in all heat exchanger tubes are dispersed, thus entire
The dispersion of gas-liquid interface and gas phase boundary and the contact area of cooling wall are realized on heat exchange tube section and enhances disturbance, greatly
Big reduces noise and vibration, enhances heat transfer.
Preferably, the core for separating heat exchange structure 28 is to be integrally formed.
Preferably, the core for separating heat exchange structure 28 is welded by grid sheet 30.
Preferably, preferably, intercommunicating pore is arranged on the grid sheet 30.It is realized between grate opening 31 by intercommunicating pore
Connection.
Pass through setting intercommunicating pore, it is ensured that it is interconnected between adjacent grate opening, it can be between homogeneous lattice gate hole
Pressure, so that the fluid of high pressure runner flows to low pressure, while it is gentle further to separate liquid phase while fluid flows
Phase is conducive to further stablize two-phase flow.
Preferably, setting is more in round tube 26 along the flow direction (i.e. the short transverse of Figure 13) of fluid in round tube 26
A dispersion heat exchange structure 28, from the entrance of round tube to the outlet of round tube, the distance between adjacent dispersion heat exchange structure is shorter and shorter.
If the distance apart from round tube entrance is H, the distance between adjacent dispersion heat exchange structure is L, L=F1(H), i.e. L is to be with height H
The function of variable, L ' are the first order derivatives of L, meet following require:
L'<0；
Main cause is because the steam in round tube understands carrier's liquid, in uphill process, round tube in uphill process
It is continuous heated, cause the steam in biphase gas and liquid flow more and more, because the vapour phase in stream-liquid two-phase flow is more and more, round tube
Interior exchange capability of heat can increase with vapour phase and weaken relatively, and vibration and its noise also can constantly increase as vapour phase increases
Add.Therefore the distance between the adjacent dispersion heat exchange structure for needing to be arranged is shorter and shorter.
In addition, exporting to this section of upper header from round tube, because the space of this section becomes larger suddenly, the variation in space can be led
Cause quickly flowing upwards out and assemble for gas, thus spatial variations will lead to the vapour phase (vapour group) of aggregation enter from round tube position it is cold
Agglutination pipe, due to gas (vapour) liquid density contrast, air mass leaves adapter tube position and will move rapidly upward, and air mass original spatial position is by gas
Group pushes away the liquid of wall surface while will also spring back and hit wall surface rapidly, forms impingement phenomenon.Gas (vapour) liquid phase is more discontinuous, gas
Reuniting, collection is bigger, and water hammer energy is bigger.Impingement phenomenon will cause biggish noise vibration and mechanical shock, cause brokenly to equipment
It is bad.Therefore in order to avoid the generation of this phenomenon, the distance between adjacent dispersion heat exchange structure being arranged at this time is shorter and shorter, from
And constantly separate gas phase and liquid phase in fluid delivery process, to reduce vibration and noise to the full extent.
It is found through experiments that, by above-mentioned setting, can both reduce vibration and noise to the full extent, while can mention
High heat transfer effect.
Further preferably, from the entrance of round tube 26 to the outlet of round tube 26, the distance between adjacent dispersion heat exchange structure is more
It is continuously increased come shorter amplitude.That is S " is the second derivative of S, meets following require:
L">0；
It is found through experiments that, by being improved simultaneously so set, 10% or so vibration and noise can be further decreased
11% or so heat transfer effect.
Preferably, the length of each dispersion heat exchange structure 28 remains unchanged.
Preferably, dispersing heat exchange structure others parameter other than the distance between adjacent dispersion heat exchange structure 28
(such as length, caliber etc.) remains unchanged.
Preferably, along the short transverse of round tube 26, the multiple dispersion heat exchange structures 28 of setting in round tube 26, from round tube 26
Entrance to the outlet of round tube 26, the length for dispersing heat exchange structure 28 is increasingly longer.The length for dispersing heat exchange structure is C, C=
F2(X), C ' is the first order derivative of C, meets following require:
C'>0；
Further preferably, disperse the increasingly longer amplitude of the length of heat exchange structure to the outlet of round tube from the entrance of round tube
It is continuously increased.That is C " is the second derivative of C, meets following require:
C">0；
The variation of the distance between for example adjacent dispersion heat exchange structure of specific reason is identical.
Preferably, the distance between adjacent dispersion heat exchange structure remains unchanged.
Preferably, in addition to dispersion heat exchange structure length be outside one's consideration, dispersion heat exchange structure others parameter (such as it is adjacent between
Away from, caliber etc.) it remains unchanged.
Preferably, along the short transverse of round tube 26, the multiple dispersion heat exchange structures of setting in round tube 26, from round tube 26
For entrance to the outlet of round tube 26, the hydraulic diameter that difference disperses the grate opening 41 in heat exchange structure 28 is smaller and smaller.I.e. dispersion is changed
The grate opening hydraulic diameter of heat structure is Z, Z=F3(X), Z ' is the first order derivative of Z, meets following require:
Z'<0；
Preferably, dispersing the grate opening hydraulic diameter of heat exchange structure increasingly from the entrance of round tube to the outlet of round tube
Small amplitude is continuously increased.I.e.
Z " is the second derivative of Z, meets following require:
Z”>0。
The variation of the distance between for example adjacent dispersion heat exchange structure of specific reason is identical.
Preferably, the length of dispersion heat exchange structure and the distance of adjacent dispersion heat exchange structure remain unchanged.
Preferably, dispersing heat exchange structure others parameter (example other than the grate opening hydraulic diameter of dispersion heat exchange structure
The distance between such as length, adjacent dispersion heat exchange structure) it remains unchanged.
Further preferably, as shown in figure 13, groove, the shell of the dispersion heat exchange structure 28 are set inside the round tube 26
29 are arranged in groove.
Preferably, the aligning inner of the inner wall of shell 29 and round tube 26.By alignment, so that on the surface of round tube inner wall face
Reach in the same plane, guarantees the smooth of surface.
Preferably, the thickness of shell 29 is less than the depth of groove, round tube inner wall face can be made to form groove in this way, from
And carry out augmentation of heat transfer.
Further preferably, as shown in figure 14, round tube 26 is welded for multi-segment structure, the junction setting point of multi-segment structure
Dissipate heat exchange structure 28.This mode makes being simple to manufacture for the round tube of setting dispersion heat exchange structure, and cost reduces.
It is learnt by analyzing and testing, the spacing dispersed between heat exchange structure cannot be excessive, leads to damping if excessive
The effect of noise reduction is bad, while can not be too small, causes resistance excessive if too small, and similarly, the outer diameter of grate opening can not mistake
The big perhaps too small effect for also resulting in damping noise reduction is bad or resistance is excessive, therefore the present invention is through a large number of experiments,
Preferentially meet normal flow resistance (total pressure-bearing be 2.5Mpa hereinafter, single round tube on-way resistance be less than or equal to 5Pa/
M in the case where), so that being optimal of damping noise reduction, has arranged the optimal relationship of parameters.
Preferably, the distance between adjacent dispersion heat exchange structure is L, the length for dispersing heat exchange structure is C, heat exchanger tube
Diameter is D, and the fluid flow area of grate opening is A, and the Zhou Changwei Z of the fluid circulation of grate opening meets following require:
L/C=a-b*LN (D/E)；
E=4*A/Z；
Wherein LN is logarithmic function, and a, b are parameters, wherein 4.9 < a < 6.1,1.3 <b < 2.1；
10<D<18mm；
8<C<15mm；
25<L<35mm。
Preferably, 5.4 < a < 5.8,1.6 <b < 1.9；
Preferably, a=5.52, b=1.93.
The interval S for wherein dispersing heat exchange structure is the both ends the distance between opposite with adjacent dispersion heat exchange structure；Before i.e.
Face disperses the tail end of heat exchange structure and the distance between the front end for dispersing heat exchange structure below.Referring specifically to the mark of Figure 13.
The diameter D of heat exchanger tube refers to the average value of internal diameter and outer diameter.
Preferably, round tube length S is between 140-200mm.Further preferably, between 160-180mm.
By the preferred of the optimal geometric scale of above-mentioned formula, can be realized under the conditions of meeting normal flow resistance,
Damping noise reduction reaches optimum efficiency.
Further preferably, as the increase of D/E, a constantly reduce, b constantly increases.
For parameters such as other parameters, such as tube wall, shell wall thickness according to normal standard setting.
Preferably, grate opening 34 extends in the whole length direction of dispersion heat exchange structure 28.That is the length of grate opening 34
Equal to the length of dispersion heat exchange structure 28.
By above-mentioned setting, can further augmentation of heat transfer, can be improved heat exchange efficiency.
Preferably, groove is arranged in the heat transfer tube wall, the shell of the dispersion heat exchange structure is arranged in groove, institute
State the inner wall of shell and the aligning inner of round tube.
Preferably, in addition to the grate opening that shell 29 is formed, remaining grate opening is square.
Preferably, the heat exchanger tube includes round tube 26 and flat tube 32, the round tube 26 is distributed in the front end of flat tube 32.
I.e. along the flow direction of exhaust gas, it is sequentially distributed round tube 26 and flat tube 32.
Main reason is that exhaust gas entrance side temperature is high, therefore liquid is easy boiling, so that stream-liquid two-phase flow is formed, because
The shape of round tube is circle, even if round tube circulation area is big in identical heat exchange area, so that bearing capacity ability is strong, and
With the heat exchange of flue gas, the flue-gas temperature of rear end is relatively low, therefore flat tube can be used, flat tube because shape be prolate shape,
Free air space is small, and liquid will not boil in rear end, therefore does not need big channel and can satisfy pressure requirements, and flat tube heat-transfer surface
Product is big, so that augmentation of heat transfer.Therefore pass through the distribution of flat tube and round tube, so that pressure distribution is opposite on the whole for heat-exchanger rig
Uniformly, it is excessive to avoid the occurrence of pressure, and exchange capability of heat relative increase.
Preferably, the fluid flow area of single round tube is greater than single flat tube.
Preferably, the fluid flow area of single round tube is 2-3 times of single flat tube circulation area.
Preferably, the round tube 26 is placed on front side of heat exchange core body, round tube 26 has multiple rows of, and every row contains multiple round tubes
26, adjacent two rows round tube 26 is interspersed.The flat tube 32 divide it is multiple rows of be arranged in heat exchange core body close to round tube heat exchange structure after
Side, every row contain multiple flat tubes 32, and the adjacent forward and backward one-to-one correspondence of two rows of flat pipes.
The extending direction of flat tube 32 is parallel to the flow direction of flue gas.
Preferably, the flow direction of liquid is all perpendicular to the flow direction of exhaust gas in the round tube 26 and flat tube 32.
Preferably, fin 36 is arranged inside flat tube, flow channel for liquids in flat tube is divided into multiple small flow channels.Preferably,
Along the direction that exhaust gas flows, the small flow channels hydraulic diameter in different flat tubes constantly becomes smaller.If the distance apart from exhaust gas entrance is
S, then the hydraulic diameter of flat tube small flow channels is d, if d=F (S), then F ' (S) < 0, F ' (S) is the first order derivative of F (S).
Main cause is the flow direction along exhaust gas, and the pressure for needing to bear in flat tube is smaller and smaller, therefore can be incited somebody to action
Hydraulic diameter becomes smaller, and by the way that hydraulic radius becomes smaller, and can increase heat exchange area, improves exchange capability of heat.Therefore by upper
The setting for stating feature not only can satisfy pressure requirements, but also augmentation of heat transfer may be implemented.
Preferably, the amplitude that the hydraulic diameter of flat tube small flow channels is d is continuously increased along exhaust gas flow direction.That is F "
(S) > 0, F " (S) is the second derivative of F (S).
For F " (S) > 0, heat transfer effect can be significantly improved, and realize pressure balance.It is above-mentioned the result is that by big
The conclusion that the numerical simulation of amount and experiment obtain.
Preferably, preferably, the small flow channels hydraulic radius in same flat tube constantly becomes along the direction that liquid flows
It is small.If distance apart from exhaust gas entrance is S, then the hydraulic diameter of flat tube small flow channels is d, if d=F (S), then F ' (S) < 0, F '
It (S) is the first order derivative of F (S).
Preferably, the amplitude that the hydraulic diameter of same flat tube small flow channels is d is continuously increased along exhaust gas flow direction.
Then F " (S) > 0, F " (S) are the second derivatives of F (S).Concrete reason is such as front.
Preferably, the small flow channels cross section in flat tube is rectangle, having a size of 2x4mm.
Preferably, the small flow channels cross section between flat tube is triangle.
Preferably, front supports and rear supports are hollow side-circle transition structure, a side end face is rectangular, side
End face is circle, wherein the square end surface of front supports is connected and is fixed with one side end face of heat exchange core body round tube, sealed, round
It fixes, seal at end face and front combustion chamber mounting cylinder rear end face air outlet；The square end surface of rear supports and heat exchange core body are flat
One side end face of pipe is connected and fixes, seals, and fixes, seals at circular end face and aft flange device air outlet.
Preferably, the UTILIZATION OF VESIDUAL HEAT IN heat-exchanger rig is arranged in the exhaust gas flue of burner, preferably warmer
Flue.
Preferably, the exhaust gas flue 17 is combustion chamber mounting cylinder.
Preferably, the exhaust gas entrance temperature of heat-exchanger rig is 1200-1400 degrees Celsius, preferably 1300 degrees Celsius.Make
To be preferred, front-seat round tube is high temperature resistant stainless steel.
Preferably, exhaust outlet 34,35 is arranged in the heat-exchanger rig, the exhaust gas cigarette of upper collecting chamber is arranged in the exhaust outlet 34
On the tube wall in road 17, the exhaust outlet 35 is arranged on outlet pipe.Preferably, exhaust outlet 34,35 is automatic according to pressure condition
Exhaust.
Preferred embodiment is illustrated with reference to the accompanying drawing.
Fig. 1 show a kind of structural schematic diagram of the embodiment of premixing ignition, diffusion burner.In the example, point is premixed
Fire, diffusion burner use heat-resisting alloy Steel material, and burner is from front to back by air feed mounting seat, premixing ignition room, diffusion
Combustion chamber, muff are sequentially connected end to end fixation and form.Air feed mounting seat is by mounting bracket 1,2 groups of air feed plectane of burning
At mounting bracket 1 is the stairstepping gradually to close up, and burning air feed plectane 2 is embedded at 1 lower end surface circular hole of mounting bracket, under two
End face is coplanar.2 center of air feed plectane burn equipped with circular vent, is circumferentially with the fan loop vent of several non-uniform Distributions
Hole.Premixing ignition room is made of eddy flow generating plate 3, part flow arrangement 4, sleeve 5, if part flow arrangement 4 is provided with for two layers along axial direction point
Dry ventilation hole, upper layer are premix air outlet 10, and lower layer is premix air inlet 11, and eddy flow generating plate 3 is coaxially installed on part flow arrangement
Between two layers of ventilation hole and close to premix air outlet, the part flow arrangement 4 for being equipped with eddy flow generating plate 3 is coaxially fixed in sleeve 5,
Bottom surface is coplanar with 5 bottom surface of sleeve and junction seals, and part flow arrangement upper surface is lower than sleeve upper surface, part flow arrangement 4 and sleeve 5
Between formed split channel 16.Combined premixing ignition room front penetrates fixed in the centre bore of burning air feed plectane 2.Diffusion combustion
It burns room and forms 8 by transitional cylinder 6, two floor air inlet cylinder 7, three floor air inlet transition rings, transitional cylinder 6 is conical ring, if being circumferentially provided with
The dry central axis circular hole vertical with the conical surface, two layers of air inlet cylinder 7 are the cylinder of both ends open, two layers of 7 diameter of air inlet cylinder and
6 major diameter of transitional cylinder is identical, and front end face is aligned fixation with 6 rear end face of transitional cylinder, is fixed at two layers of air inlet 7 intermediate altitude of cylinder
Circumferentially distributed hollow flow-guiding pipe 13, and with cylinder outer surface penetrate through, three layers of air inlet transition rings 8 by with two layers of air inlet cylinder 7
Transition thin plate with diameter is fixed with two layers of 7 lower end surface of air inlet cylinder, is provided with return port 14 and three layers of air inlet hole 15.Group
The diffusion burner upper surface of conjunction is fixed with lean premixed combustor lower end surface co-axially align.Muff 9 is placed on the confession after combination
Fixed after the aligned coplanar of lower end surface outside wind mounting seat, lean premixed combustor and diffusion combustion room, bearing keeps sealing.Burning
Diffusion air intake passage 17 is formed between outdoor cylinder and air feed mounting seat, premixing ignition room, diffusion burner.
Specifically, seeing Fig. 1 and Fig. 2, mounting bracket 1 is the stairstepping cylinder of Diameter Gradual Change, and it is convex that upper surface is provided with installation
Edge is used for burner axially position, and lateral surface is provided with installation fixing lug boss, circumferentially positioned for carrying out to burner.Installation
Bracket 1 is flowed for installing warmer control system and ignition system, guidance air-flow to entry of combustion chamber, increases its flowing speed
Degree, while being also the carrier that burning air feed plectane 2 and muff 8 are installed.In the present embodiment, mounting bracket internal diameter is successively
Are as follows: 186mm, 163mm, 138mm, mounting flange diameter are 198mm.
The distribution of required air specifically, burning air feed plectane 2 is used to burn, the air for flowing through circular vent enter in advance
Mixed combustion chamber, participates in premixing ignition room ignition phase and the burning in diffusion combustion stage, flows through the sky of fan annular, peripheral ventilation hole
Gas enters diffusion burner, participates in the burning in diffusion combustion stage, it is preferred that circular vent is with ring vent area ratio is fanned
3.7:1.Burning 2 circular ventilation hole peripheral of air feed plectane shown in Fig. 2 is equipped with guide groove in the present embodiment, facilitates premixing ignition room
Installation is fixed, the identical fan looping pit non-uniform Distribution of 8 radial dimensions, it is preferred that 7 adjacent fan ring central angles and interval
Central angle is identical, respectively 19 °, 26 °, another fan ring central angle is 23.5 °, be 17 ° with the adjacent angular interval for fanning ring,
30.5°。
Specifically, premixing ignition room part flow arrangement 4 is axial to be provided with two layers of forward and backward corresponding ventilation hole, every layer of ventilation hole
Quantity is 6, and upper layer premix air outlet 10 is used to shunt the air entered by 2 circular vent of burning air feed plectane, shunts air
Enter lower layer through split channel 16 and premix air inlet 11, fuel oil downlink is mixed and blocked with atomized fuel, increases Fuel Air
Incorporation time improves diffusion combustion stability.Eddy flow generating plate 3, eddy flow generating plate front end face are provided between two layers of ventilation hole
It is 6mm with the preferred spacing of plane where the premix air outlet center of circle of upper layer, center is equipped with circular hole, is used as atomized fuel entrance, circumferential
It is triangle and its normal direction and the swirl channel of eddy flow generating plate plane at an angle equipped with section, for the shape in igniting chamber
At eddy flow, Fig. 3 is seen, it is preferred that it is 6 °, 65 ° that swirl channel section triangle, which corresponds to interior angle, and section normal direction and eddy flow generating plate are pressed from both sides
Angle is 17 °.By 2 circular vent of burning air feed plectane enter air a part through the swirl channel in eddy flow generating plate 3 into
Enter rear portion combustion space, combustion mixture needed for igniting is thoroughly mixed to form with the atomized fuel entered through center hole.
Specifically, diffusion burner transitional cylinder 6 is conical ring, it is preferred that diameter ratio in front and rear end is 9:13, circumferential circle
Hole number is 16, and diameter 8mm is uniformly distributed.Two layers are entered the wind cylinders 7 for the cylinder of both ends open, after diameter and transitional cylinder
End face diameter is equal, it is preferred that the diversion pipe of contour distribution is equipped at axial 1/2 height of cylinder, diversion pipe quantity is 10, water conservancy diversion
Pipe is penetrated through and is aligned with cylinder outer end face.See Fig. 4, three layers of air inlet transition rings 8 are equipped with return port 14 and three layers of air inlet hole 15, use
In connection diffusion air intake passage and diffusion combustion chamber interior, it is preferred that return port 14 and three layers of 15 quantity of air inlet hole be respectively 8 with
36, diameter is respectively 10mm and 2mm.Air needed for burning enters diffusion air intake passage by the circumferential fan annular distance of fuel oil air feed plectane 2
17, and respectively by the reflux in 13, three layers of diversion pipe air inlet transition rings 8 on the circumferential circular hole of transitional cylinder 6, secondary air cylinder 7
Hole 14 and three layers of air inlet hole 15 enter diffusion combustion chamber interior and participate in burning, it is preferred that each layer incoming air area of diffusion burner accounts for
The ratio of diffusion combustion incoming air area are as follows: 44%, 15%, 35%, 6%.Wherein, the circumferential circular hole of transitional cylinder 6 is diffusion combustion
Main air supply channel, the air thus entered enter flame inside along conical surface normal direction, increase the sky on the unburned fuel oil periphery of flame inside
Gas content improves efficiency of combustion.Portion is formed the high-speed air entered by the diversion pipe 13 on secondary air cylinder 7 in a combustion chamber
Airbond reduces flame and moves axially speed while mixed firinor fuel burning with atomized fuel, increase fuel oil in the residence time of combustion chamber,
Guarantee is sufficiently mixed and burns, this measure advantageously reduces axial length needed for fuel burning.It is recoiled by return port 14 and enters combustion
The air for burning room, atomized fuel and Inner Wall of Combustion Chamber are separated, and reduce fuel oil in the attachment probability of wall surface, are conducive to eliminate product
Carbon, meanwhile, air depends on the transitional cylinder conical surface during uplink and changes flow direction, the air phase circumferentially entered with transitional cylinder 6
Interaction forms tumble flow on 7 top of secondary air cylinder, promotes the mixing and burning of air and unburned fuel oil.By entering the wind three times
The air that hole 15 enters is in burner ends sluggishness flame movement velocity, it is ensured that the burning of a small amount of uncombusted fuel oil improves burning
The efficiency of combustion of device reduces burning wake flame length, reduces postposition heat exchanger thermic load.
Burner operation after assembling is initial, and the atomizer being integrated on warmer pot head assembly ejects the combustion of atomization
Oil, fuel oil enter eddy flow generating plate back space through the center hole in eddy flow generating plate, while through circumferential in eddy flow generating plate
The swirl channel of arrangement enters the air of back space and atomized fuel is sufficiently mixed, and forms air-fuel mixture necessary to lighting a fire
Gas, and the igniter by being integrated on pot head assembly lights gaseous mixture, forms burner and continues working required nucleus of flame.
After lighting a fire successfully, igniter stops working, and atomizer continues to spray fuel oil, and enter with swirl channel and premix air inlet
Eddy flow generating plate back space forms stable fire source in premixing ignition room after air mixing, burns incompletely in premixing ignition room
Fuel oil continues to diffusion burner internal motion.At the same time, fan of the air needed for diffusion combustion through air feed plectane circumferential direction of burning
Shape hole enters split channel, and by transitional cylinder, secondary air cylinder, the air inlet hole of air inlet transition rings etc. enters diffusion burner three times,
In the process constantly with unburned fuel gauge face contact and burning, the exhaust gas of generation is discharged through muff small diameter bore
Burner.
Premixing ignition of the present invention, diffusion burner are suitable for the small fuel oils formula combustion heat-exchange devices such as warmer
In, have the characteristics that structure is simple, high combustion efficiency, the premixing ignition cell structure may insure burner various extreme
Reliable ignition and stable burning under environment, multilayer air inlet diffusion combustion structure are conducive to reduce combustion chamber axial length, improve
The summation watt rating of burner.
Although the present invention has been disclosed in the preferred embodiments as above, present invention is not limited to this.Any art technology
Personnel can make various changes or modifications, therefore protection scope of the present invention is answered without departing from the spirit and scope of the present invention
When being defined by the scope defined by the claims..
Claims (6)
1. a kind of burning air feed plectane, the burning air feed plectane includes center vent and circumferential ventilation hole, circumferential ventilation hole,
For using center vent center as the sector structure in the center of circle；Circumferential ventilation hole asymmetric distribution.
2. burning air feed plectane as described in claim 1, which is characterized in that circumferential ventilation hole is provided with 8,8 week
It is asymmetric distribution to ventilation hole, it is specific to be distributed are as follows: the circumferential direction that the area of the circumferential ventilation hole of lowest part is greater than other positions is logical
Air holes.
3. burning air feed plectane as described in claim 1, which is characterized in that center vent and circumferential ventilation hole gross area ratio
For (3.5-4.5): 1；Preferably, 3.7:1.
4. burning air feed plectane as claimed in claim 3, which is characterized in that the central angle of other positions 7 fan rings is identical,
Angular interval corresponding to his 7 adjacent fan ring sides is identical.Preferably, the 2 circumferential direction ventilation hole 2-2 of burning air feed plectane be with
The center center vent 2-1 is the sector structure in the center of circle.
5. a kind of buner system, including air feed mounting seat, the expansion air feed mounting seat includes one of claim 1-4 institute
The secondary air cylinder that the method three stated designs.
6. a kind of diffusion burner, the diffusion burner includes transitional cylinder, secondary air cylinder, enters the wind transition rings three times, described
Transition tube rear end connects one end of secondary air cylinder, and the first end of transition rings is entered the wind in the other end connection of secondary air cylinder three times,
Air inlet hole is set on the transitional cylinder, and air inlet hole is arranged in the secondary air cylinder, and air inlet is arranged in the transition rings of air inlet three times.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910433531.2A CN110274227B (en) | 2017-05-22 | 2017-05-22 | Combustion air supply circular plate and combustor system thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910433531.2A CN110274227B (en) | 2017-05-22 | 2017-05-22 | Combustion air supply circular plate and combustor system thereof |
| CN201710362241.4A CN107246610B (en) | 2017-05-22 | 2017-05-22 | Diffusion combustion chamber and combustor system comprising same |
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| CN201710362241.4A Division CN107246610B (en) | 2017-05-22 | 2017-05-22 | Diffusion combustion chamber and combustor system comprising same |
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| CN201910433531.2A Expired - Fee Related CN110274227B (en) | 2017-05-22 | 2017-05-22 | Combustion air supply circular plate and combustor system thereof |
| CN201910433533.1A Expired - Fee Related CN110260304B (en) | 2017-05-22 | 2017-05-22 | Design method of secondary air inlet cylinder and burner system thereof |
| CN201710362241.4A Expired - Fee Related CN107246610B (en) | 2017-05-22 | 2017-05-22 | Diffusion combustion chamber and combustor system comprising same |
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Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1528348A1 (en) * | 2003-10-20 | 2005-05-04 | Behr GmbH & Co. KG | Heat exchanger |
| CN202221145U (en) * | 2011-07-29 | 2012-05-16 | 北京北机机电工业有限责任公司 | Compact type original surface heat exchanger for fuel oil and fuel gas heater |
| CN103115354A (en) * | 2013-02-21 | 2013-05-22 | 北京北机机电工业有限责任公司 | Combined cyclone combustion chamber |
| CN203274557U (en) * | 2013-04-22 | 2013-11-06 | 南京金典制冷实业有限公司 | Wave-sheet diversion grid type spiral heat exchanger |
| CN203349267U (en) * | 2013-05-10 | 2013-12-18 | 彭玉延 | Novel double-high burner |
| CN104214774A (en) * | 2014-06-13 | 2014-12-17 | 浙江绍兴世纪能源有限公司 | Low-energy consumption environmental-protection burner |
| CN204329696U (en) * | 2014-12-08 | 2015-05-13 | 西安交通大学 | Wing thermoexcell in a kind of |
| CN104832920A (en) * | 2015-05-25 | 2015-08-12 | 珠海巴陆信息科技有限公司 | Fuel oil burner and steam boiler with same |
| CN106461219A (en) * | 2014-05-02 | 2017-02-22 | 西门子股份公司 | Combustor burner arrangement |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN206989194U (en) * | 2017-05-22 | 2018-02-09 | 中国北方车辆研究所 | A kind of diffusion burner and the buner system including combustion chamber |
-
2017
- 2017-05-22 CN CN201910433531.2A patent/CN110274227B/en not_active Expired - Fee Related
- 2017-05-22 CN CN201910433533.1A patent/CN110260304B/en not_active Expired - Fee Related
- 2017-05-22 CN CN201710362241.4A patent/CN107246610B/en not_active Expired - Fee Related
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1528348A1 (en) * | 2003-10-20 | 2005-05-04 | Behr GmbH & Co. KG | Heat exchanger |
| CN202221145U (en) * | 2011-07-29 | 2012-05-16 | 北京北机机电工业有限责任公司 | Compact type original surface heat exchanger for fuel oil and fuel gas heater |
| CN103115354A (en) * | 2013-02-21 | 2013-05-22 | 北京北机机电工业有限责任公司 | Combined cyclone combustion chamber |
| CN203274557U (en) * | 2013-04-22 | 2013-11-06 | 南京金典制冷实业有限公司 | Wave-sheet diversion grid type spiral heat exchanger |
| CN203349267U (en) * | 2013-05-10 | 2013-12-18 | 彭玉延 | Novel double-high burner |
| CN106461219A (en) * | 2014-05-02 | 2017-02-22 | 西门子股份公司 | Combustor burner arrangement |
| CN104214774A (en) * | 2014-06-13 | 2014-12-17 | 浙江绍兴世纪能源有限公司 | Low-energy consumption environmental-protection burner |
| CN204329696U (en) * | 2014-12-08 | 2015-05-13 | 西安交通大学 | Wing thermoexcell in a kind of |
| CN104832920A (en) * | 2015-05-25 | 2015-08-12 | 珠海巴陆信息科技有限公司 | Fuel oil burner and steam boiler with same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110274227B (en) | 2021-03-16 |
| CN107246610A (en) | 2017-10-13 |
| CN110260304B (en) | 2021-05-28 |
| CN107246610B (en) | 2020-05-12 |
| CN110260304A (en) | 2019-09-20 |
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