CN105157062A - Low-emission combustion chamber with double-layer axial hydrocyclone adopted at precombustion stage - Google Patents

Low-emission combustion chamber with double-layer axial hydrocyclone adopted at precombustion stage Download PDF

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CN105157062A
CN105157062A CN201510679691.7A CN201510679691A CN105157062A CN 105157062 A CN105157062 A CN 105157062A CN 201510679691 A CN201510679691 A CN 201510679691A CN 105157062 A CN105157062 A CN 105157062A
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combustion
combustion grade
grade
stage
combustion chamber
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林宇震
韩啸
张弛
王波
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Beihang University
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Beihang University
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Abstract

The invention discloses a low-emission combustion chamber with a double-layer axial hydrocyclone at a precombustion stage. The combustion chamber is of a single annular cavity structure and structurally comprises a pressure expander, a combustion chamber exterior casing, a combustion chamber interior casing, a flame tube and a combustion chamber head; all combustion-used air enters the flame tube through the combustion chamber head, a staged combustion scheme is adopted, and the combustion is divided into into the precombustion stage and a primary combustion stage; a premixed combustion mode is adopted at the primary combustion stage, and a diffusive combustion mode serves as the main mode of the precombustion stage; the double-layer axial hydrocyclone is adopted at the precombustion stage, two blasts of rotational flow can maintain individual flowing through a partition plate, and momentum loss due to the fact that the two blasts of rotational flow make contact with each other too early is avoided; the two blasts of rotational flow are utilized for reinforcing fuel oil atomization and mixing, meanwhile, reasonable recirculating zone distribution is generated, efficient and stable combustion under small working conditions is guaranteed, and meanwhile pollutant emission is lowered; the combustion chamber is simple in structure at the precombustion stage and easy to machine and install, combustion chamber emission under small working conditions can be lowered, and thereby the low emission performance of a total landing and taking-off cycle of the combustion chamber is improved.

Description

A kind of pre-combustion grade adopts the low emission combustor of double-deck axial swirler
Technical field
The present invention relates to a kind of low emission combustor, particularly a kind of pre-combustion grade adopts the low emission combustor of double-deck axial swirler.
Background technology
Aero-engine is a kind of high complexity and accurate thermal machine, for airborne vehicle provides the engine of flight required drive.As the heart of aircraft, be described as " flower of industry ", it directly affects the performance of aircraft, reliability and economy.Aero-engine can be categorized as civil engine and military aero-engine simply by purposes.For military aero-engine, civil engine has more strict requirement in low oil consumption, low emission, low noise.Wherein low emission mainly needs still Optimizing Combustion room design to realize.
The main pollutant effulent of modern civil engine comprises: nitrogen oxide (NOx), carbon monoxide (CO), unburned carbon hydrogen (UHC) and smolder (Smoke) etc., its Drainage feature is the region concentrated on centered by airport, affect the personnel health to airport and near zone thereof, even may cause the harm such as visibility reduction.In four kinds of main emissions, carbon monoxide (CO), unburned carbon hydrogen (UHC) and smolder (Smoke) mainly affect by completeness of combustion reaction, and burn more abundant, combustion zone temperature is higher, and its discharge capacity is lower; And nitrogen oxide (NOx) is primarily of thermal NO x mechanism, the too high meeting of combustion zone temperature makes NOx emission sharply increase.Therefore this two classes emission exists conflicting, is difficult to the problem balanced.Research finds, when head of combustion chamber equivalent proportion is 0.6 ~ 0.8 time, can take into account two kinds of emissions preferably, therefore now aeroengine combustor buring room mainly towards poor oil firing's future development; Arrange while equivalent proportion at reduction head, the uniformity coefficient improving fuel oil blending is most important, otherwise the hot spot region close to appropriate ratio easily appears in combustion zone, from but NOx emission is difficult to control.In sum, the core technology of modern low emission combustor is exactly, and while maintenance head poor oil firing, strengthens the atomization and vaporization of fuel oil, thus provides more uniform gas mixture for burner inner liner.
For large operating mode (take off, cruise), intake air flow is large, speed is high, pressure and temperature is all high than little operating mode (slow train), this brings very large benefit to the atomization and vaporization of fuel oil, and therefore the low emission problem of combustion chamber under large operating mode relatively easily solves.And when little operating mode, generally only have pre-combustion grade to work independently.Now there is fuel oil blending problem and there is lot of challenges: nozzle flow is little on the one hand, and fuel pressure is low, the mist of oil that nozzle produces inherently also exists atomization situation poor, pockety; On the other hand, air mass flow is little, speed is low, and the ratio of momentum of air and fuel oil is little, pre-combustion grade rotational flow air for the fragmentation of mist of oil and mixing capacity more weak.Therefore the atomization and vaporization of fuel oil and the blending of liquid mist and air are the keys that little operating mode bends down emission problem.
Summary of the invention
The technical problem to be solved in the present invention is: poor for the fuel-oil atmozation when little operating mode of existing low emission combustor, efficiency of combustion and low emission are difficult to the problem balanced, adopt the pattern of fractional combustion, main combustion stage adopts premixed combustion, pre-combustion grade adopts double-deck axial swirler, strengthens to combustion oil atomization and blending under little operating mode, thus when ensureing smooth combustion, improve the combustibility of combustion chamber under little operating mode, reduce disposal of pollutants.
The technical solution adopted for the present invention to solve the technical problems is: a kind of pre-combustion grade adopts the low emission combustor of double-deck axial swirler, it is characterized in that: adopt monocycle cavity configuration, primary structure comprises casing, burner inner liner and head of combustion chamber in diffuser, outer combustion case, combustion chamber; Combustion air all enters burner inner liner by head of combustion chamber, and tempering air enters from the Cooling Holes burner inner liner; Head of combustion chamber is connected with burner inner liner, and is fixed on combustion box, and main combustion stage is installed on pre-combustion grade periphery, and with pre-combustion grade and swirl atomizer coaxial; Combustion chamber adopts fractional combustion scheme, and be divided into pre-combustion grade and main combustion stage, main combustion stage is premixed combustion, and fuel oil forms main combustion stage mist of oil by main combustion stage fuel oil supply road ejection, and completes blending in main combustion stage passage; Described pre-combustion grade can have two kinds of versions, is respectively to shrink expansion type pre-combustion grade or shrinkage expansion type pre-combustion grade; Described contraction expansion type pre-combustion grade is made up of pre-combustion grade inward eddy device, pre-combustion grade contour stealth device, pre-combustion grade demarcation strip, inter-stage section; Described shrinkage expansion type pre-combustion grade is made up of pre-combustion grade inward eddy device, pre-combustion grade contour stealth device, pre-combustion grade demarcation strip, pre-combustion grade contraction section, pre-combustion grade expansion segment; Fuel oil sprays from swirl atomizer, and form pre-combustion grade mist of oil, air enters pre-combustion grade from inside and outside two-stage cyclones, and form inward eddy and contour stealth, eddy flow accelerates in pre-combustion grade constricted channel, and at pre-combustion grade venturi, place reaches maximal rate; Demarcation strip makes the two bursts of more enough maintenances of eddy flow flowings separately, avoids premature contact and loss momentum; Under the impact and shear action of two strands of eddy flows, fuel oil is fully atomized, and forms homogeneous mixture enter combustion chamber with rotational flow air; The eddy flow that pre-combustion grade produces produces rational recirculating zone with smooth combustion in pre-combustion grade downstream.
Wherein, the pre-combustion grade inward eddy device blade angle of described contraction expansion type pre-combustion grade is 10 ~ 70 °, pre-combustion grade contour stealth device blade angle is 10 ~ 70 °, the ratio of the air mass flow of inside and outside two-stage cyclones is 0.05 ~ 0.8, demarcation strip diameter is 0.3 ~ 0.9 with the ratio of pre-combustion grade throat diameter, pre-combustion grade throat diameter is 0.3 ~ 0.9 with the ratio of main combustion stage internal diameter, and nozzle is 0.1 ~ 1 to pre-combustion grade end wall distance and the ratio of pre-combustion grade throat diameter; Inter-stage section has the Cooling Holes of circumference distribution, and diameter is 0.3 ~ 2mm, and quantity is 15 ~ 70.
Wherein, the pre-combustion grade inward eddy device blade angle of described shrinkage expansion type pre-combustion grade is 10 ~ 70 °, pre-combustion grade contour stealth device blade angle is 10 ~ 70 °, the ratio of the air mass flow of inside and outside two-stage cyclones is 0.05 ~ 0.8, pre-combustion grade throat diameter is 0.3 ~ 0.9 with the ratio of main combustion stage internal diameter, pre-combustion grade flat segments length and pre-combustion grade expansion segment length ratio are 0 ~ 0.5, and the ratio of pre-combustion grade expansion segment length and expansion segment outlet diameter is 0.15 ~ 0.6, and expansion segment angle is 30 ° ~ 120 °; Pre-combustion grade expansion segment has the Cooling Holes of circumference distribution, and diameter is 0.3 ~ 2mm, and quantity is 15 ~ 70.
Wherein, the hydrocyclone structure that described main combustion stage adopts is axial swirler, or radial swirler, or tangential cyclones, and the ratio of main combustion stage external diameter and main combustion stage internal diameter is 0.5 ~ 1.5, and main combustion stage external diameter and burner inner liner diameter ratio are 0.4 ~ 0.9.
Wherein, the air capacity of described head of combustion chamber accounts for 20% ~ 80% of combustion chamber total air, cold gas air capacity accounts for 10% ~ 30% of combustion chamber total air, can also retain 10 ~ 30% of combustion chamber total air in addition for blending, distribute to regulate combustor exit temperature; Wherein main combustion stage accounts for 60% ~ 90% of head of combustion chamber air capacity, and pre-combustion grade accounts for 10% ~ 40% of head of combustion chamber air capacity.
Wherein, described burner inner liner adopts gaseous film control, disperses cooling, the cooling of impinging cooling, effusion wall or Compound cooling mode, to improve cooling effectiveness, and reduction flame tube wall surface temperature, thus prolonging combustion room life-span.
Operation principle of the present invention: the air for burning accounts for the major part of combustion chamber total air, and all enters burner inner liner from head, thus reduce head equivalent proportion, be conducive to the generation that control combustion district temperature reduces NOx.Burning tissues adopts center hierarchical approaches, and pre-combustion grade is at center, and the mode adopting diffusion combustion and premixed combustion to combine, provides stable Central backflow area with main combustion stage of igniting; Main combustion stage, in periphery, adopts the mode of premixed combustion, and fuel oil in the atomization evaporation of main combustion stage passage, thus forms uniform mixture and enters burner inner liner and participate in burning.Especially, pre-combustion grade of the present invention adopts double-deck axial swirler, and rotational flow air accelerates in constricted channel, and reaches maximal rate at pre-combustion grade venturi place; Demarcation strip makes the two bursts of more enough maintenances of eddy flow flowings separately, avoids premature contact and loss momentum; Under the impact and shear action of two strands of eddy flows, fuel oil is fully atomized, and forms homogeneous mixture enter burner inner liner with rotational flow air; Meanwhile, the eddy flow that pre-combustion grade produces produces rational Central backflow area in order to smooth combustion in downstream.Thus when ensureing smooth combustion, improve the combustibility of combustion chamber under little operating mode, reduce disposal of pollutants.
The advantage that the present invention compared with prior art has is as follows:
(1) combustion chamber of the present invention adopts pre-combustion grade to adopt double-deck axial swirler, and demarcation strip makes the two bursts of more enough maintenances of eddy flow flowings separately, avoids premature contact and loss momentum.Under the impact and shear action of two strands of eddy flows, fuel oil is fully atomized, thus when ensureing smooth combustion, improves the combustibility of combustion chamber under little operating mode, reduces disposal of pollutants;
(2) combustion chamber of the present invention can select pre-combustion grade to adopt contraction expansion type or shrinkage expansion type according to actual conditions, can be suitable for different chamber structure, thus have better adaptability;
(3) the present invention adopts center fractional combustion enterprise schema, and the air needed for burning all enters from head, thus reduces the overall equivalent proportion of head, is conducive to control combustion district temperature, reduces disposal of pollutants.
Accompanying drawing explanation
Fig. 1 is engine structure schematic diagram;
Fig. 2 is chamber structure schematic diagram of the present invention;
Fig. 3 is head of combustion chamber structure sectional view figure of the present invention;
Fig. 4 is contraction expansion type pre-combustion grade structural representation of the present invention;
Fig. 5 is shrinkage expansion type pre-combustion grade structural representation of the present invention;
Fig. 6 is contraction expansion type pre-combustion grade of the present invention assembling schematic diagram;
Fig. 7 is shrinkage expansion type pre-combustion grade of the present invention assembling schematic diagram.
In figure: 1 low-pressure compressor, 2 high-pressure compressors, 3 combustion chambers, 4 high-pressure turbines, 5 low-pressure turbines, 6 diffusers, 7 main combustion stage fuel oil supply roads, 8 pre-combustion grade fuel oil supply roads, 9 outer combustion cases, casing in 10 combustion chambers, 11 head of combustion chamber, 12 burner inner liners, 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 inward eddy devices, 24 pre-combustion grade contour stealth devices, 25 inter-stage sections, 26 inter-stage section screw threads, 27 Cooling Holes, 28 demarcation strips, 29 pre-combustion grade venturis, 30 contour stealth, 31 inward eddies, 32 nozzles are to pre-combustion grade end wall distance, 33 demarcation strip diameters, 34 pre-combustion grade throat diameter, 35 pre-combustion grade contraction sections, 36 pre-combustion grade expansion segments, 37 pre-combustion grade flat segments length, 38 pre-combustion grade expansion segment length, 39 expansion segment angles, 40 pre-combustion grade throat diameter, 41 expansion segment outlet diameters, 42 shrink expansion type pre-combustion grade, 43 shrinkage expansion type pre-combustion grade.
Detailed description of the invention
The present invention is further illustrated below in conjunction with the drawings and specific embodiments.
Fig. 1 is engine structure schematic diagram, comprises low-pressure compressor 1, high-pressure compressor 2, combustion chamber 3, high-pressure turbine 4 and low-pressure turbine 5.During engine operation, air enters combustion chamber 3, by spraying into fuel oil and organizing burning after low-pressure compressor 1 and high-pressure compressor 2 compress, form the combustion gas of HTHP, impulse high voltage turbine 4 and low-pressure turbine 5, thus drive low-pressure compressor 1 and high-pressure compressor 2 to do work, and outputting power.
As shown in Figure 2, adopt monocycle cavity configuration, primary structure comprises casing 10, burner inner liner 12 and head of combustion chamber 11 in diffuser 6, outer combustion case 9, combustion chamber; Combustion air all enters burner inner liner 12 by head of combustion chamber 11, and tempering air enters from the Cooling Holes burner inner liner 12; Head of combustion chamber 11 is connected with burner inner liner 12, and is fixed on combustion box.Fuel oil enters head of combustion chamber 11 respectively by main combustion stage fuel oil supply road 7 and pre-combustion grade fuel oil supply road 8, forms uniform mixture enter burner inner liner and participate in burning with rotational flow air blending.High-temperature fuel gas after burning is discharged from combustor exit.
As shown in Figure 3, head of combustion chamber 11 is connected with burner inner liner 12 by head installing plate 16.Head installing plate 16 has Cooling Holes, and is connected with splash pan 17, thus cooling splash pan 17 avoids structural failure.Combustion chamber adopts fractional combustion scheme, is divided into pre-combustion grade 19 and main combustion stage 14, and it is peripheral that main combustion stage 14 is installed on pre-combustion grade 19, and with pre-combustion grade 19 and swirl atomizer 13 coaxial.Fuel oil is sprayed by main combustion stage fuel oil supply road 7 and forms main combustion stage mist of oil 15, and realizes atomization and vaporization in main combustion stage 14 passage, forms uniform combustible gas and enters burner inner liner participation burning.The hydrocyclone structure that main combustion stage 14 adopts is axial swirler, or radial swirler, or tangential cyclones, and the ratio of main combustion stage external diameter 21 and main combustion stage internal diameter 20 is 0.5 ~ 1.5, and main combustion stage external diameter 21 is 0.4 ~ 0.9 with the ratio of burner inner liner diameter 22.Fuel oil is sprayed by swirl atomizer 13, forms pre-combustion grade mist of oil 18, under the shear action of the eddy flow produced in pre-combustion grade 19, enhances fuel oil blending, thus forms uniform mixture and enter burner inner liner.The eddy flow that pre-combustion grade 19 produces forms suitable Central backflow area in burner inner liner, plays and stabilizes the flame and the effect of the main combustion stage mixture that ignites.
As shown in Figure 4, shrink expansion type pre-combustion grade 42 and be made up of pre-combustion grade inward eddy device 23, pre-combustion grade contour stealth device 24, pre-combustion grade demarcation strip 28, inter-stage section 25, can adopt between them and be welded to connect, tight fit or other fixed forms can be adopted.Shrink expansion type pre-combustion grade 42 to be connected with main combustion stage by 26 inter-stage section screw threads.Air enters from two-stage cyclones, and rotational flow air accelerates in constricted channel, and reaches maximal rate at pre-combustion grade venturi 29 place.Demarcation strip 28 makes the two bursts of more enough maintenances of eddy flow flowings separately, avoids premature contact and loss momentum.Under the impact and shear action of two strands of eddy flows, fuel oil is fully atomized.Pre-combustion grade inward eddy device 23 blade angle shrinking expansion type pre-combustion grade 42 is 10 ~ 70 °, pre-combustion grade contour stealth device 24 blade angle is 10 ~ 70 °, the ratio of the air mass flow of inside and outside two-stage cyclones is 0.05 ~ 0.8, demarcation strip diameter 33 is 0.3 ~ 0.9 with the ratio of pre-combustion grade throat diameter 34, pre-combustion grade throat diameter 34 is 0.3 ~ 0.9 with the ratio of main combustion stage internal diameter 20, and nozzle is 0.1 ~ 1 to pre-combustion grade end wall distance 32 with the ratio of pre-combustion grade throat diameter 34; Inter-stage section 25 has the Cooling Holes 27 of circumference distribution, and diameter is 0.3 ~ 2mm, and quantity is 15 ~ 70.
As shown in Figure 5, shrinkage expansion type pre-combustion grade 43 is made up of pre-combustion grade inward eddy device 23, pre-combustion grade contour stealth device 24, pre-combustion grade demarcation strip 28, pre-combustion grade contraction section 35, pre-combustion grade expansion segment 36.Pre-combustion grade inward eddy device 23 blade angle is 10 ~ 70 °, pre-combustion grade contour stealth device 24 blade angle is 10 ~ 70 °, the ratio of the air mass flow of inside and outside two-stage cyclones is 0.05 ~ 0.8, pre-combustion grade throat diameter 40 is 0.3 ~ 0.9 with the ratio of main combustion stage internal diameter 20, pre-combustion grade flat segments length 37 is 0 ~ 0.5 with the ratio of pre-combustion grade expansion segment length 38, pre-combustion grade expansion segment length 38 is 0.15 ~ 0.6 with the ratio of expansion segment outlet diameter 41, and expansion segment angle 39 is 30 ° ~ 120 °; Pre-combustion grade expansion segment 36 has the Cooling Holes 27 of circumference distribution, and diameter is 0.3 ~ 2mm, and quantity is 15 ~ 70.Rotational flow air accelerates in constricted channel, demarcation strip 28 avoids two strands of eddy flow premature contact and loss momentum, thus in venturi place and fuel oil blending, then mix further in pre-combustion grade expansion segment 36, part fuel particles evaporates in this course, thus realizes the burning tissues form of part premix and pre-evaporation.Pre-combustion grade expansion segment 36 contributes to improving the fuel oil blending uniformity further, avoids recirculating zone temperature too high; Also be conducive to flame stabilization simultaneously.In general, should select to adopt contraction expansion type pre-combustion grade 42 or shrinkage expansion type pre-combustion grade 43 according to combustion chamber practical structures and demand.
Shrink the assembling mode of expansion type pre-combustion grade 42 as shown in Figure 6.
The assembling mode of shrinkage expansion type pre-combustion grade 43 as shown in Figure 7.
The above is only the preferred embodiment of the present invention; it should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.

Claims (6)

1. a pre-combustion grade adopts the low emission combustor of double-deck axial swirler, it is characterized in that: adopt monocycle cavity configuration, primary structure comprises casing (10), burner inner liner (12) and head of combustion chamber (11) in diffuser (6), outer combustion case (9), combustion chamber; Combustion air all enters burner inner liner (12) by head of combustion chamber (11), and tempering air enters from the Cooling Holes burner inner liner (12); Head of combustion chamber (11) is connected with burner inner liner (12), and be fixed on combustion box, it is peripheral that main combustion stage (14) is installed on pre-combustion grade (19), and with pre-combustion grade (19) and swirl atomizer (13) coaxial; Combustion chamber adopts fractional combustion scheme, be divided into pre-combustion grade (19) and main combustion stage (14), main combustion stage (14) is premixed combustion, fuel oil forms main combustion stage mist of oil (15) by main combustion stage fuel oil supply road (7) ejection, and completes blending in main combustion stage (14) passage; Described pre-combustion grade (19) can have two kinds of versions, is respectively to shrink expansion type pre-combustion grade (42) or shrinkage expansion type pre-combustion grade (43); Described contraction expansion type pre-combustion grade (42) is made up of pre-combustion grade inward eddy device (23), pre-combustion grade contour stealth device (24), pre-combustion grade demarcation strip (28), inter-stage section (25); Described shrinkage expansion type pre-combustion grade (43) is made up of pre-combustion grade inward eddy device (23), pre-combustion grade contour stealth device (24), pre-combustion grade demarcation strip (28), pre-combustion grade contraction section (35), pre-combustion grade expansion segment (36); Fuel oil sprays from swirl atomizer (13), form pre-combustion grade mist of oil (18), air enters pre-combustion grade from inside and outside two-stage cyclones, form inward eddy (31) and contour stealth (30), eddy flow accelerates in pre-combustion grade constricted channel, reaches maximal rate at pre-combustion grade venturi (29) place; Demarcation strip (28) makes the two bursts of more enough maintenances of eddy flow flowings separately, avoids premature contact and loss momentum; Under the impact and shear action of two strands of eddy flows, fuel oil is fully atomized, and forms homogeneous mixture enter combustion chamber with rotational flow air; The eddy flow that pre-combustion grade (19) produces produces rational recirculating zone with smooth combustion in pre-combustion grade downstream.
2. a kind of pre-combustion grade according to claim 1 adopts the low emission combustor of double-deck axial swirler, it is characterized in that: pre-combustion grade inward eddy device (23) blade angle of described contraction expansion type pre-combustion grade (42) is 10 ~ 70 °, pre-combustion grade contour stealth device (24) blade angle is 10 ~ 70 °, the ratio of the air mass flow of inside and outside two-stage cyclones is 0.05 ~ 0.8, demarcation strip diameter (33) is 0.3 ~ 0.9 with the ratio of pre-combustion grade throat diameter (34), pre-combustion grade throat diameter (34) is 0.3 ~ 0.9 with the ratio of main combustion stage internal diameter (20), nozzle is 0.1 ~ 1 to pre-combustion grade end wall distance (32) and the ratio of pre-combustion grade throat diameter (34), inter-stage section (25) has the Cooling Holes (27) of circumference distribution, and diameter is 0.3 ~ 2mm, and quantity is 15 ~ 70.
3. a kind of pre-combustion grade according to claim 1 adopts the low emission combustor of double-deck axial swirler, it is characterized in that: pre-combustion grade inward eddy device (23) blade angle of described shrinkage expansion type pre-combustion grade (43) is 10 ~ 70 °, pre-combustion grade contour stealth device (24) blade angle is 10 ~ 70 °, the ratio of the air mass flow of inside and outside two-stage cyclones is 0.05 ~ 0.8, pre-combustion grade throat diameter (40) is 0.3 ~ 0.9 with the ratio of main combustion stage internal diameter (20), pre-combustion grade flat segments length (37) is 0 ~ 0.5 with the ratio of pre-combustion grade expansion segment length (38), pre-combustion grade expansion segment length (38) is 0.15 ~ 0.6 with the ratio of expansion segment outlet diameter (41), expansion segment angle (39) is 30 ° ~ 120 °, pre-combustion grade expansion segment (36) has the Cooling Holes (27) of circumference distribution, and diameter is 0.3 ~ 2mm, and quantity is 15 ~ 70.
4. a kind of pre-combustion grade according to claim 1 adopts the low emission combustor of double-deck axial swirler, it is characterized in that: the hydrocyclone structure that described main combustion stage (14) adopts is axial swirler, or radial swirler, or tangential cyclones, the ratio of main combustion stage external diameter (21) and main combustion stage internal diameter (20) is 0.5 ~ 1.5, and main combustion stage external diameter (21) is 0.4 ~ 0.9 with the ratio of burner inner liner diameter (22).
5. a kind of pre-combustion grade according to claim 1 adopts the low emission combustor of double-deck axial swirler, it is characterized in that: the air capacity of described head of combustion chamber (11) accounts for 20% ~ 80% of combustion chamber total air, cold gas air capacity accounts for 10% ~ 30% of combustion chamber total air, 10 ~ 30% of combustion chamber total air can also be retained in addition for blending, distribute to regulate combustor exit temperature; Wherein main combustion stage (14) accounts for 60% ~ 90% of head of combustion chamber (11) air capacity, and pre-combustion grade (19) accounts for 10% ~ 40% of head of combustion chamber (11) air capacity.
6. a kind of pre-combustion grade according to claim 1 adopts the low emission combustor of double-deck axial swirler, it is characterized in that: described burner inner liner (12) adopt gaseous film control, disperse cooling, impinging cooling, effusion wall cool or Compound cooling mode, to improve cooling effectiveness, reduce burner inner liner (12) wall surface temperature, thus the prolonging combustion room life-span.
CN201510679691.7A 2015-10-19 2015-10-19 Low-emission combustion chamber with double-layer axial hydrocyclone adopted at precombustion stage Withdrawn CN105157062A (en)

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