CN206281000U - Pre-combustion grade uses the low emission combustor of double-deck axial swirler - Google Patents
Pre-combustion grade uses the low emission combustor of double-deck axial swirler Download PDFInfo
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- CN206281000U CN206281000U CN201621089424.0U CN201621089424U CN206281000U CN 206281000 U CN206281000 U CN 206281000U CN 201621089424 U CN201621089424 U CN 201621089424U CN 206281000 U CN206281000 U CN 206281000U
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Abstract
A kind of pre-combustion grade uses the low emission combustor of double-deck axial swirler, is monocyclic cavity configuration, and head of combustion chamber main combustion stage is installed on pre-combustion grade periphery, and main combustion stage is premixed combustion structure, and pre-combustion grade is to shrink expansion type pre-combustion grade or shrinkage expansion type pre-combustion grade；Shrinking expansion type pre-combustion grade includes inside and outside cyclone, demarcation strip and interstage section；Shrinkage expansion type pre-combustion grade includes inside and outside cyclone, demarcation strip, contraction section and expansion segment, and expansion segment is configured in the downstream of contraction section；Fuel oil sprays from swirl atomizer, forms pre-combustion grade mist of oil, and air enters pre-combustion grade from inner swirler, outer swirler, forms inward eddy and contour stealth, and two strands of eddy flows accelerate in contraction section, and maximal rate is reached at the venturi of contraction section end；Demarcation strip makes inward eddy and contour stealth keeps respective flowing, and fuel oil is atomized in two spiral-flow impacts and shearing, and forming homogeneous mixture with rotational flow air enters burner inner liner.
Description
Technical field
The utility model is related to the combustion chamber of gas turbine, more particularly to aero-engine low emission combustor.
Background technology
The discharge standard (CAEP2~CAEP8) that International Civil Aviation Organization promulgates is improved constantly, and low emissions combustion technology turns into the people
With one of most important research contents in aeroengine combustor buring room, rely primarily on optimization Combustion chamber design to realize low emission.
The main pollutant effulent of modern civil engine includes：Nitrogen oxides (NOx), carbon monoxide (CO), not
Fire and hydrocarbon (UHC) and smolder (Smoke) etc., its Drainage feature is to concentrate on the region centered on airport, influence to airport and
The personnel health of its near zone, in some instances it may even be possible to cause the harm such as visibility reduction.In four kinds of main emissions, carbon monoxide
(CO), unburned hydrocarbon (UHC) and smolder (Smoke) mainly influenceed by the completeness of combustion reaction, burn more abundant, combustion zone
Temperature is higher, and its discharge capacity is lower；And nitrogen oxides (NOx) is main by thermal NO x mechanisms, the too high meeting of combustion zone temperature
Sharply increase NOx emission.Therefore this two classes emission exists conflicting, it is difficult to the problem of balance.Research discovery, works as burning
Chamber-head portion equivalent proportion can preferably take into account two class emissions, therefore aeroengine combustor buring room master now at 0.6~0.8
To develop towards poor oil firing direction；While head entirety equivalent proportion is reduced, the uniformity coefficient for improving fuel oil blending is extremely closed
Important, otherwise combustion zone easily occurs close to the hot spot region of appropriate ratio, so that NOx emission is difficult to control to.
In sum, the core technology of modern low emission combustor is exactly while head poor oil firing is kept, to strengthen
The atomization and vaporization of fuel oil, so that for burner inner liner provides more uniform gas mixture.
For big operating mode (take off, cruise), intake air flow is big, speed is high, pressure and temperature is than small operating mode
(slow train) is high, and this brings very big benefit, therefore low emission problem of the combustion chamber under big operating mode to the atomization and vaporization of fuel oil
Relatively easily solve.And in small operating mode, typically only pre-combustion grade works independently.Now there are problems that fuel oil blending etc. is all
Many challenges：One side nozzle flow is small, and fuel pressure is low, and the mist of oil that nozzle is produced inherently is existed and is atomized poor, distribution not
Uniform situation；On the other hand, air mass flow is small, speed is low, and the ratio of momentum of air and fuel oil is small, pre-combustion grade rotational flow air for
The broken and mixing capacity of mist of oil is weaker.Therefore the blending of the atomization and vaporization and liquid mist and air of fuel oil is low row under small operating mode
Put the key of problem.
Utility model content
For existing low emission combustor, in small operating mode, fuel-oil atmozation is poor, and efficiency of combustion and low emission are difficult to what is balanced
Problem, the utility model provides a kind of low emission combustor of pre-combustion grade using double-deck axial swirler.
The utility model uses the pattern of fractional combustion, main combustion stage to use premixed combustion, and pre-combustion grade is using double-deck axially rotation
Stream device, atomization and blending under the small operating mode of reinforcement to fuel oil, so as in the case where stabilization burning is ensured, raising combustion chamber is small
Combustibility under operating mode, reduces disposal of pollutants.
Based on this, a kind of pre-combustion grade uses the low emission combustor of double-deck axial swirler, it is characterised in that：Using monocyclic
Cavity configuration, primary structure includes casing, burner inner liner and head of combustion chamber in diffuser, outer combustion case, combustion chamber；Burning is used
Air all enters burner inner liner by head of combustion chamber, and Cooling Holes of the tempering air from burner inner liner enter；Head of combustion chamber with
Burner inner liner is connected, and is fixed on combustion box, and main combustion stage is installed on pre-combustion grade periphery, and common with pre-combustion grade and swirl atomizer
Axle；Combustion chamber uses fractional combustion scheme, is divided into pre-combustion grade and main combustion stage, and main combustion stage is premixed combustion, and fuel oil passes through main combustion stage
Fuel oil supply road is sprayed to form main combustion stage mist of oil, and blending is completed in main combustion stage passage；The pre-combustion grade can have two kinds of knots
Configuration formula, is respectively to shrink expansion type pre-combustion grade or shrinkage expansion type pre-combustion grade；The contraction expansion type pre-combustion grade is by pre-combustion grade
Inner swirler, pre-combustion grade outer swirler, pre-combustion grade demarcation strip, interstage section composition；The shrinkage expansion type pre-combustion grade is by pre-combustion grade
Inner swirler, pre-combustion grade outer swirler, pre-combustion grade demarcation strip, pre-combustion grade contraction section, pre-combustion grade expansion segment composition；Fuel oil is from centrifugation
Nozzle sprays, and forms pre-combustion grade mist of oil, and air enters pre-combustion grade from inside and outside two-stage cyclones, forms inward eddy and contour stealth, rotation
Stream accelerates in pre-combustion grade shrinks passage, and maximal rate is reached at pre-combustion grade venturi；Demarcation strip enables two strands of eddy flows to keep
Respective flowing, it is to avoid premature contact and momentum is lost；Under two bursts of impacts and shear action of eddy flow, fuel oil is obtained fully
Atomization, forms homogeneous mixture and enters combustion chamber with rotational flow air；It is reasonable that the eddy flow that pre-combustion grade is produced is produced in pre-combustion grade downstream
Recirculating zone with stabilization burn.
Wherein, the pre-combustion grade inner swirler blade angle for shrinking expansion type pre-combustion grade is 10~70 °, pre-combustion grade outward turning
Stream device blade angle is 10~70 °, and the ratio between air mass flow of inside and outside two-stage cyclones is 0.05~0.8, separate board diameter with it is pre-
The ratio between combustion level throat diameter is 0.3~0.9, and the ratio between pre-combustion grade throat diameter and main combustion stage internal diameter are 0.3~0.9, and nozzle is in advance
The ratio between combustion level end wall distance and pre-combustion grade throat diameter are 0.1~1；Circumferentially distributed Cooling Holes, diameter are provided with interstage section
It is 0.3~2mm, quantity is 15~70.
Wherein, the pre-combustion grade inner swirler blade angle of the shrinkage expansion type pre-combustion grade is 10~70 °, pre-combustion grade outward turning
Stream device blade angle is 10~70 °, and the ratio between air mass flow of inside and outside two-stage cyclones is 0.05~0.8, pre-combustion grade throat diameter
It is 0.3~0.9 with the ratio between main combustion stage internal diameter, segment length that pre-combustion grade is straight is 0-0.5, pre-burning with pre-combustion grade expansion segment length ratio
Level expansion segment length is 0.15~0.6 with the ratio of expansion segment outlet diameter, and expansion segment angle is 30 °~120 °；In pre-combustion grade
Circumferentially distributed Cooling Holes, a diameter of 0.3~2mm are provided with expansion segment, quantity is 15~70.
Wherein, the partition shape between the shrinkage expansion type pre-combustion grade two-stage, can be the tapered straight line of single hop, under dividing plate
Trip end face is located at pre-combustion grade venturi upstream；Or the tapered broken line of multistage, broken line number is 2~5, and dividing plate downstream end face is located at
Pre-combustion grade venturi upstream；Or straight line connects SPL, straightway is located at pre-combustion grade venturi upstream, SPL downstream end face position
At pre-combustion grade venturi upstream or venturi or expansion segment.
Wherein, the hydrocyclone structure that the main combustion stage is used is axial swirler, or radial swirler, or tangential rotation
Stream device, the ratio between main combustion stage external diameter and main combustion stage internal diameter are 0.5~1.5, main combustion stage external diameter and burner inner liner diameter ratio be 0.4~
0.9。
Wherein, the air capacity of the head of combustion chamber accounts for the 20%~80% of combustion chamber total air, cools down gas air capacity
Account for the 10%~30% of combustion chamber total air.
Wherein, can also retain the 10%~30% of combustion chamber total air is used to blend, to adjust combustor exit temperature
Degree distribution；
Wherein main combustion stage accounts for the 60%~90% of head of combustion chamber air capacity, and pre-combustion grade accounts for head of combustion chamber air capacity
10%~40%.
Wherein, the burner inner liner is using gaseous film control, diverging cooling, impinging cooling, effusion wall cooling or Compound cooling side
Formula, to improve cooling effectiveness, reduces burner inner liner wall surface temperature, so as to extend the combustion chamber life-span.
The beneficial effects of the utility model are：
Air for combustion accounts for the major part of combustion chamber total air, and all from head enters burner inner liner, so that
Head equivalent proportion is reduced, is conducive to the generation for controlling combustion zone temperature to reduce NOx.Burning tissues use center hierarchical approaches,
Pre-combustion grade at center, by the way of diffusion combustion and premixed combustion are combined, there is provided the Central backflow area of stabilization is with main combustion of igniting
Level；, in periphery, by the way of premixed combustion, fuel oil is in the atomization evaporation of main combustion stage passage, so as to form uniform for main combustion stage
Mixture enters burner inner liner and participates in burning.Especially, using double-deck axial swirler, rotational flow air exists the utility model pre-combustion grade
Shrink in passage and accelerate, and maximal rate is reached at pre-combustion grade venturi；Demarcation strip enables two strands of eddy flows to keep respective stream
It is dynamic, it is to avoid premature contact and momentum is lost；Under two bursts of impacts and shear action of eddy flow, fuel oil is sufficiently atomized, with
Rotational flow air forms homogeneous mixture and enters burner inner liner；Meanwhile, the eddy flow that pre-combustion grade is produced produces rational center to return in downstream
Stream area is used to stabilization burning.So as in the case where stabilization burning is ensured, improve combustibility of the combustion chamber under small operating mode, drop
Low pollution emission.
Brief description of the drawings
The above and other feature of the present utility model, property and advantage will be by with reference to the accompanying drawings and examples
Description and become readily apparent from, wherein：
Fig. 1 is engine structure schematic diagram；
Fig. 2 is chamber structure schematic diagram of the present utility model；
Fig. 3 is head of combustion chamber structure sectional view of the present utility model；
Fig. 4 is contraction expansion type pre-combustion grade structural representation of the present utility model；
Fig. 5 is shrinkage expansion type pre-combustion grade structural representation of the present utility model；
Fig. 6 is band broken line type demarcation strip shrinkage expansion type pre-combustion grade structural representation of the present utility model；
Fig. 7 is contraction expansion type pre-combustion grade assembling schematic diagram of the present utility model；
Fig. 8 is shrinkage expansion type pre-combustion grade assembling schematic diagram of the present utility model.
In figure：1 low-pressure compressor, 2 high-pressure compressors, 3 combustion chambers, 4 high-pressure turbines, 5 low-pressure turbines, 6 diffusers, 7 masters
Combustion level fuel oil supply road, 8 pre-combustion grade fuel oils supply road, 9 outer combustion cases, casing in 10 combustion chambers, 11 head of combustion chamber, 12
Burner inner liner, 13 swirl atomizers, 14 main combustion stages, 15 main combustion stage mist of oils, 16 head installing plates, 17 splash pans, 18 pre-combustion grade mist of oils, 19
Pre-combustion grade, 20 main combustion stage internal diameters, 21 main combustion stage external diameters, 22 burner inner liner diameters, 23 pre-combustion grade inner swirlers, 24 pre-combustion grade contour stealths
Device, 25 interstage sections, 26 interstage section screw threads, 27 Cooling Holes, 28 demarcation strips, 29 pre-combustion grade venturis, 30 contour stealths, 31 inward eddies, 32
To pre-combustion grade end wall distance, 33 separate board diameter to nozzle, and 34 pre-combustion grade throat diameters, 35 pre-combustion grade contraction sections, 36 pre-combustion grades expand
Open section, 37 pre-combustion grade throat lengths, 38 pre-combustion grades expansion segment length, 39 expansion segment angles, 40 pre-combustion grade throat diameters, 41 expansions
Section outlet diameter, 42 shrink expansion type pre-combustion grade, 43 shrinkage expansion type pre-combustion grades, 44 demarcation strip extensions.
Specific embodiment
Fig. 1 is engine structure schematic diagram, including low-pressure compressor 1, high-pressure compressor 2, low emission combustor 3, high pressure
Turbine 4 and low-pressure turbine 5.When engine works, air enters burning after low-pressure compressor 1 and high-pressure compressor 2 compress
Room 3, by spraying into fuel oil and organizing burning, forms the combustion gas of HTHP, impulse high voltage turbine 4 and low-pressure turbine 5, so as to drive
Dynamic low-pressure compressor 1 and high-pressure compressor 2 do work, and export power.
As shown in Fig. 2 low emission combustor 3 uses monocyclic cavity configuration, its primary structure includes diffuser 6, outdoor of burning
Casing 10, burner inner liner 12 and head of combustion chamber 11 in casing 9, combustion chamber；Combustion air is all entered by head of combustion chamber 11
Burner inner liner 12, Cooling Holes of the tempering air from burner inner liner 12 enter；Head of combustion chamber 11 is connected with burner inner liner 12, and fixed
On the combustion box that casing 10 is constituted in by outer combustion case 9, combustion chamber.Fuel oil is supplied by main combustion stage fuel oil respectively
Road 7 and pre-combustion grade fuel oil supply road 8 enter head of combustion chamber 11, blend to form uniform mixture and enter flame with rotational flow air
Cylinder simultaneously participates in burning.High-temperature fuel gas after burning are discharged from combustor exit.
As shown in figure 3, head of combustion chamber 11 is connected by head installing plate 16 with burner inner liner 12.Opened on head installing plate 16
There are Cooling Holes, and be connected with splash pan 17, so that cooling down splash pan 17 avoids structural failure.Low emission combustor 3 is using classification
Combustion scheme, is divided into pre-combustion grade 19 and main combustion stage 14, and main combustion stage 14 is installed on the periphery of pre-combustion grade 19, and with pre-combustion grade 19 and centrifugation
Nozzle 13 is coaxial.Fuel oil supplies the ejection of road 7 and forms main combustion stage mist of oil 15 by main combustion stage fuel oil, and real in the passage of main combustion stage 14
Existing atomization and vaporization, forms uniform combustible gas and enters burner inner liner participation burning.The hydrocyclone structure that main combustion stage 14 is used is axially
Cyclone, or radial swirler, or tangential cyclones, the ratio between main combustion stage external diameter 21 and main combustion stage internal diameter 20 be 0.5~
1.5, the ratio between main combustion stage external diameter 21 and burner inner liner diameter 22 are 0.4~0.9.Fuel oil is sprayed by swirl atomizer 13, forms pre-burning
Level mist of oil 18, under the shear action of the eddy flow that pre-combustion grade 19 is produced, enhances fuel oil blending, so as to form uniform mixture
Into burner inner liner.The eddy flow that the cyclone of pre-combustion grade 19 is produced forms suitable Central backflow area in burner inner liner, plays stabilization
The effect of flame and the main combustion stage mixture that ignites.
As shown in figure 4, shrinking expansion type pre-combustion grade 42 by pre-combustion grade inner swirler 23, pre-combustion grade outer swirler 24, pre-burning
Fraction dividing plate 28, interstage section 25 are constituted, and tight fit or other fixation sides can be used using being welded to connect between them
Formula.Expansion type pre-combustion grade 42 is shunk to be connected with main combustion stage 14 by interstage section screw thread 26.Air enters from two-stage cyclones 23,24
Enter, rotational flow air accelerates in contraction passage, and reaches maximal rate at pre-combustion grade venturi 29.Demarcation strip 28 makes two strands of eddy flows
Respective flowing can be kept, it is to avoid premature contact and momentum is lost, under two bursts of impacts and shear action of eddy flow, fuel oil
It is sufficiently atomized.The blade angle of pre-combustion grade inner swirler 23 for shrinking expansion type pre-combustion grade 42 is 10~70 °, pre-combustion grade outward turning
Stream device 24 blade angle is 10~70 °, and the ratio between air mass flow of inside and outside two-stage cyclones 23,24 is 0.05~0.8, demarcation strip
The ratio between diameter 33 and pre-combustion grade throat diameter 34 are 0.3~0.9, and the ratio between pre-combustion grade throat diameter 34 and main combustion stage internal diameter 20 are
0.3~0.9, the ratio between nozzle to pre-combustion grade end wall distance 32 and pre-combustion grade throat diameter 34 are 0.1~1；Opened in interstage section 25
There are circumferentially distributed Cooling Holes 27, a diameter of 0.3~2mm, quantity is 15~70.
As shown in figure 5, shrinkage expansion type pre-combustion grade 43 is by pre-combustion grade inner swirler 23, pre-combustion grade outer swirler 24, pre-burning
Fraction dividing plate 28, pre-combustion grade contraction section 35, pre-combustion grade expansion segment 36 are constituted.The blade angle of pre-combustion grade inner swirler 23 be 10~
70 °, the blade angle of pre-combustion grade outer swirler 24 be 10~70 °, the ratio between air mass flow of inside and outside two-stage cyclones be 0.05~
0.8, the ratio between pre-combustion grade throat diameter 40 and main combustion stage internal diameter 20 are 0.3~0.9, and pre-combustion grade throat length 37 is expanded with pre-combustion grade
The ratio between segment length 38 is 0~0.5, and pre-combustion grade expansion segment length 38 is 0.15~0.6 with the ratio of expansion segment outlet diameter 41, is expanded
It is 30 °~120 ° to open section angle 39；It is provided with circumferentially distributed Cooling Holes 27 on pre-combustion grade expansion segment 36, a diameter of 0.3~
2mm, quantity is 15~70.Rotational flow air accelerates shrinking in passage, demarcation strip 28 avoid two strands of eddy flow premature contacts and
Loss momentum, so as to be blended with fuel oil at venturi, may also operate as pre- film and is atomized using the dividing plate in appropriate type face as shown in Figure 6
Effect, strengthen fuel-oil atmozation, be then further well mixed in the pre-combustion grade expansion segment 36, a part of fuel particles are at this
During evaporate, so as to realize the burning tissues form of part premix and pre-evaporation.Pre-combustion grade expansion segment 36 helps further to carry
Fuel oil high blends the uniformity, it is to avoid recirculating zone temperature is too high；It is also beneficial to flame stabilization simultaneously.In general, should be according to burning
Room practical structures and demand selection are using contraction expansion type pre-combustion grade 42 or shrinkage expansion type pre-combustion grade 43.
As shown in fig. 6, having carried out certain extension, i.e. demarcation strip to demarcation strip 28 from unlike pre-combustion grade shown in Fig. 5
Extension 44.The type face of demarcation strip extension is that broken line is tapering type, or SPL is tapering type, or the tapered gradual-enlargement type of broken line, or
The tapered gradual-enlargement type of SPL.The downstream end face axial position range of demarcation strip extension 44 for demarcation strip 28 downstream end face extremely
At the 2/5 of expansion segment, the footpath of demarcation strip extension downstream end face inner ring radial direction radius and pre-combustion grade second cyclone annulus channel
It is 0.1~0.5 to the ratio between radius.In general, dividing plate extension shape should be used according to combustion chamber practical structures and demand selection
Shape.
The assembling mode of expansion type pre-combustion grade 42 is shunk as shown in Figure 7.
The assembling mode of shrinkage expansion type pre-combustion grade 43 as shown in Figure 8.
The above is only preferred embodiment of the present utility model, it is noted that for the common skill of the art
For art personnel, on the premise of the utility model principle is not departed from, some improvements and modifications can also be made, these improve and
Retouching also should be regarded as protection domain of the present utility model.
Claims (9)
1. a kind of pre-combustion grade uses the low emission combustor of double-deck axial swirler, it is characterised in that：The low emission combustor is
Monocyclic cavity configuration, including diffuser, outer combustion case, casing, burner inner liner and head of combustion chamber in combustion chamber, and it is configured to combustion
Burning air all enters the burner inner liner by the head of combustion chamber, and Cooling Holes of the tempering air from the burner inner liner enter
Enter；The head of combustion chamber is connected with the burner inner liner, and is fixed on by the outer combustion case and the burning indoor set
On the combustion box that casket is surrounded；The head of combustion chamber includes main combustion stage and pre- right level, and the main combustion stage is installed on described pre-
Combustion level periphery, and with the pre-combustion grade and and the pre- right level configuration swirl atomizer it is coaxial；The main combustion stage is fired for premix
Sintering structure, including main combustion stage cyclone and main combustion stage fuel oil supply road, wherein, fuel oil supplies road and sprays shape by main combustion stage fuel oil
Into main combustion stage mist of oil, and blending is completed in the main combustion stage passage of concatenation main combustion stage cyclone；The pre-combustion grade is to shrink sudden expansion
Type pre-combustion grade or shrinkage expansion type pre-combustion grade；The contraction expansion type pre-combustion grade includes pre-combustion grade inner swirler, pre-combustion grade outward turning
Stream device, pre-combustion grade demarcation strip and interstage section；The shrinkage expansion type pre-combustion grade includes pre-combustion grade inner swirler, pre-combustion grade outward turning
Stream device, pre-combustion grade demarcation strip, pre-combustion grade contraction section and pre-combustion grade expansion segment, the pre- right level expansion segment configuration is described pre- right
The downstream of level contraction section；The pre-combustion grade is also configured with swirl atomizer, and the fuel flow path of the pre- right level is configured to：Fuel oil from
Swirl atomizer sprays, and forms pre-combustion grade mist of oil, and air enters described pre- from the pre-combustion grade inner swirler, pre-combustion grade outer swirler
Combustion level, forms inward eddy and contour stealth, and inward eddy and contour stealth accelerate in the pre-combustion grade contraction section, is received in the pre-combustion grade
Maximal rate is reached at the pre-combustion grade venturi of contracting section end；And the pre- right fraction dividing plate is configured to make inward eddy and contour stealth
Respective flowing is kept so that fuel oil is sufficiently atomized under the impact of inward eddy and contour stealth and shear action, with eddy flow
Air forms homogeneous mixture and enters the burner inner liner.
2. low emission combustor as claimed in claim 1, it is characterised in that the pre-burning of the contraction expansion type pre-combustion grade
The blade angle of level inner swirler is 10~70 °, and the blade angle of the pre-combustion grade outer swirler is 10~70 °, the pre-burning
Level inner swirler, the ratio between air mass flow of the pre-combustion grade outer swirler are 0.05~0.8, the pre- right fire resisting division board diameter with
The ratio between described pre-combustion grade throat diameter is 0.3~0.9, and the ratio between the pre-combustion grade throat diameter and described main combustion stage internal diameter are 0.3
~0.9, the ratio between the end wall distance of the swirl atomizer to the pre-combustion grade and described pre-combustion grade throat diameter are 0.1~1；Institute
State and circumferentially distributed Cooling Holes are provided with interstage section.
3. low emission combustor as claimed in claim 1, it is characterised in that the pre-burning of the shrinkage expansion type pre-combustion grade
The blade angle of level inner swirler is 10~70 °, and the blade angle of the pre-combustion grade outer swirler is 10~70 °, the pre-burning
Level inner swirler, the ratio between air mass flow of the pre-combustion grade outer swirler are 0.05~0.8, the pre-combustion grade throat diameter and institute
It is 0.3~0.9 to state the ratio between main combustion stage internal diameter, and the pre-combustion grade throat length is 0- with the pre-combustion grade expansion segment length ratio
0.5, it is 0.15~0.6 that the pre-combustion grade expands segment length and the ratio of the pre- right level expansion segment outlet diameter, described pre- right
Level expansion segment angle is 30 °~120 °；Circumferentially distributed Cooling Holes are provided with the pre-combustion grade expansion segment.
4. low emission combustor as claimed in claim 1, it is characterised in that the pre-burning of the shrinkage expansion type pre-combustion grade
Level inner swirler, the described pre- right fraction partition shape of the pre-combustion grade outer swirler, are the tapered straight line of single hop, the pre- right level
The downstream end face of demarcation strip is located at pre-combustion grade venturi upstream；Or the tapered broken line of multistage, broken line number is 2~5, described pre-
The downstream end face of right fraction dividing plate is located at pre-combustion grade venturi upstream；Or straight line connects SPL, the straight line connects SPL
Straightway is located at the pre-combustion grade venturi upstream, and the downstream end face of SPL is located at the pre-combustion grade venturi upstream or described
At pre-combustion grade venturi or the pre- right level expansion segment.
5. low emission combustor as claimed in claim 1, it is characterised in that the cyclone of the main combustion stage is axial rotational flow
The ratio between internal diameter of device, or radial swirler, or tangential cyclones, the external diameter of the main combustion stage and the main combustion stage is 0.5
~1.5, the main combustion stage external diameter is 0.4~0.9 with the diameter ratio of the burner inner liner.
6. low emission combustor as claimed in claim 1, it is characterised in that the air capacity of the head of combustion chamber accounts for the low row
Put the 20%~80% of combustion chamber total air, the cooling gas air capacity account for the low emission combustor total air 10%~
30%.
7. low emission combustor as claimed in claim 6, it is characterised in that the 10% of the total air of the low emission combustor
~30% outlet blending for being arranged in the low emission combustor, to adjust the Exit temperature distribution of the low emission combustor.
8. low emission combustor as claimed in claim 6, it is characterised in that the main combustion stage accounts for the head of combustion chamber air
The 60%~90% of amount, the pre-combustion grade accounts for the 10%~40% of the head of combustion chamber air capacity.
9. low emission combustor as claimed in claim 1, it is characterised in that the burner inner liner be configured with gaseous film control device,
Diverging cooling device, impingement cooling device, effusion wall cooling device or composite cooling apparatus.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510679691.7A CN105157062A (en) | 2015-10-19 | 2015-10-19 | Low-emission combustion chamber with double-layer axial hydrocyclone adopted at precombustion stage |
| CN2015106796917 | 2015-10-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206281000U true CN206281000U (en) | 2017-06-27 |
Family
ID=54798021
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510679691.7A Withdrawn CN105157062A (en) | 2015-10-19 | 2015-10-19 | Low-emission combustion chamber with double-layer axial hydrocyclone adopted at precombustion stage |
| CN201621089424.0U Active CN206281000U (en) | 2015-10-19 | 2016-09-28 | Pre-combustion grade uses the low emission combustor of double-deck axial swirler |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510679691.7A Withdrawn CN105157062A (en) | 2015-10-19 | 2015-10-19 | Low-emission combustion chamber with double-layer axial hydrocyclone adopted at precombustion stage |
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| CN (2) | CN105157062A (en) |
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| CN107525095A (en) * | 2017-07-24 | 2017-12-29 | 西北工业大学 | A kind of axially staged can burner of gas turbine |
| CN107559882A (en) * | 2017-07-24 | 2018-01-09 | 西北工业大学 | A kind of axially staged low pollution combustor |
| CN107763666A (en) * | 2017-11-07 | 2018-03-06 | 中国科学院工程热物理研究所 | A kind of head of combustion chamber oil gas mixing machine and the engine with the structure |
| CN109424977A (en) * | 2017-08-23 | 2019-03-05 | 通用电气公司 | Buner system for high fuel/air rate and the kinetics of combustion of reduction |
| CN109737451A (en) * | 2019-01-23 | 2019-05-10 | 南方科技大学 | Gaseous fuel is low discharge combustion chamber of swirl injection in advance |
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2016
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