A combined burner with adaptive exhaust gas calorific value

Abstract

This application provides an adaptive combined burner for exhaust gas calorific value, comprising a central assembly and peripheral assemblies. One end of the central assembly along the air intake direction is the combustion end, which delivers combustible gas and main combustion-supporting gas to the combustion end and ignites them to form the main flame. The peripheral assemblies surround the combustion end, and one end of the peripheral assemblies along the air intake direction has several combustion ends located downstream of the combustion end along the air intake direction. The peripheral assemblies include an exhaust gas duct for conveying exhaust gas and an exhaust gas-supporting combustion air duct for conveying exhaust gas and combustion-supporting gas. The exhaust gas-supporting combustion air duct is fitted around the exhaust gas duct, and both extend to the combustion ends, introducing the exhaust gas and exhaust gas-supporting gas into the combustion chamber. The peripheral assemblies also include a conical guide and a swirl vane assembly located at the combustion ends. The conical guide is located at the outlet of the exhaust gas duct with its tip facing the exhaust gas duct, and the swirl vane assembly is rotatably located at the outlet of the exhaust gas-supporting combustion air duct.

Description

Technical Field

[0001] This application relates to the field of chemical incineration, and in particular to a combined burner with adaptive calorific value of waste gas.

[0002] This application claims priority to Chinese patent application filed on January 16, 2025, with application number 202510065523.2 and entitled "An Adaptive Combined Burner for Exhaust Gas Calorific Value". Background Technology

[0003] During the incineration of chemical waste gas, changes in upstream production process parameters alter the composition of the waste gas, leading to fluctuations in its calorific value. Traditionally, this waste gas is delivered through a straight pipe into the furnace, with the angle controlled to direct it towards the burner root, without separate air distribution. When the calorific value is <500 kcal, the gas contains few combustible components and can be directly injected into the furnace for high-temperature pyrolysis, undergoing oxidation-reduction reactions in a flameless state. However, once the calorific value fluctuates to ≥500 kcal, or even reaches 1250 kcal or higher, the increased combustible content necessitates a greater oxygen demand, potentially leading to open flames within the furnace. Because separate air distribution for this waste gas is impossible, incomplete combustion can occur due to excessively high concentrations, resulting in substandard waste gas treatment or excessive carbon monoxide levels. If the exhaust gas is separately distributed in the furnace, the excessive air volume will directly affect the stability of the main flame. At the same time, it is impossible to set up a complex air distribution structure in the furnace. Even if separate air distribution is carried out, the mixing effect of high-concentration exhaust gas and combustion air is not ideal.

[0004] In related technologies, the method for treating chemical waste gas involves conveying it through a straight pipe in the furnace, controlling the angle of the waste gas and injecting it towards the root of the main flame of the burner, without separate air distribution. However, this works fine when the calorific value is low, but when the calorific value is high, the lack of air distribution leads to substandard waste gas treatment and excessive carbon monoxide levels.

[0005] How to solve the above problems and provide a burner with a stable air distribution structure is something that those skilled in the art need to consider. Summary of the Invention

[0006] To address the problems in the prior art, this application provides an adaptive combined burner for exhaust gas calorific value.

[0007] This application provides an adaptive combined burner for exhaust gas calorific value, including a central component and a peripheral component. One end of the central component along the air inlet direction is the combustion end, which is used to deliver combustible gas and main combustion-supporting gas to the combustion end and ignite them to form the main flame. The peripheral component surrounds the outside of the combustion end, and one end of the peripheral component along the air inlet direction has several combustion ends located downstream of the combustion end. The peripheral component includes an exhaust gas duct for conveying exhaust gas and an exhaust gas-supporting combustion air duct for conveying exhaust gas-supporting gas. The exhaust gas-supporting combustion air duct is sleeved around the exhaust gas duct and extends to the combustion end to introduce exhaust gas and exhaust gas-supporting gas into the combustion chamber. The peripheral component also includes a conical guide and a swirl blade assembly located at the combustion end. The conical guide is located at the outlet of the exhaust gas duct with its tip facing the exhaust gas duct, and the swirl blade assembly is rotatably located at the outlet of the exhaust gas-supporting combustion air duct.

[0008] Understandably, placing the peripheral components for transporting exhaust gas downstream of the combustion end of the central component ensures that the main flame formed by the central component is established stably first, unaffected by fluctuations in the composition, flow rate, or calorific value of the peripheral exhaust gas. The introduction and combustion of the peripheral exhaust gas occur downstream of the stable combustion zone of the main flame, fundamentally eliminating the impact of exhaust gas or its combustion-supporting air on the root of the main flame, thus ensuring the core stability of the entire combustion system. By setting up exhaust gas combustion-supporting air ducts surrounding the exhaust gas duct, a dedicated and independent combustion-supporting air channel is provided for the exhaust gas. This ensures that regardless of the calorific value of the exhaust gas, it can obtain sufficient oxygen for combustion or oxidation reactions. When the calorific value of the exhaust gas is high, independent air distribution ensures complete combustion and avoids excessive carbon monoxide. When the calorific value of the exhaust gas is low, it can still mix with the combustion-supporting air immediately, causing an early oxidation reaction and extending the effective residence time in the furnace. Meanwhile, conical guides and swirl blades are installed at the outlets of the exhaust gas and the exhaust gas combustion-supporting gas to achieve adaptive adjustment for exhaust gases with different calorific values. The conical guides disperse and evenly guide the exhaust gas jet, while the swirl blades create a strong rotating flow field for the exhaust gas combustion-supporting gas. The exhaust gas is entrained into this rotating flow field the moment it enters the combustion chamber, achieving efficient and rapid mixing. Furthermore, the low-pressure zone formed at the center of the rotating flow field is conducive to entraining high-temperature flue gas, providing conditions for establishing a stable flame for high-calorific-value exhaust gas.

[0009] In one embodiment, the flow velocity of the exhaust gas combustion-supporting gas at the outlet of the exhaust gas combustion-supporting air duct is not less than 15 m / s, and the flow velocity of the exhaust gas at the outlet of the exhaust gas duct is not less than 20 m / s.

[0010] Understandably, limiting the outlet velocities of the exhaust gas and the combustion-supporting gas further ensures and enhances the mixing effect. A higher exhaust gas / combustion-supporting gas velocity (not less than 15 m / s) creates a more powerful and stable swirling flow field, providing strong momentum and a stable macroscopic environment for subsequent mixing. Simultaneously, ensuring the exhaust gas has sufficiently high outlet momentum (velocity not less than 20 m / s) allows it to effectively "penetrate" and be entrained into the strong swirling combustion air, achieving more rapid and uniform mixing. This optimized velocity matching ensures that regardless of the exhaust gas's calorific value, optimal combustion or reaction conditions are reached in the shortest possible time, further improving combustion efficiency and the thoroughness of exhaust gas treatment.

[0011] In one embodiment, the tapered guide includes a tapered portion, which includes a top end and a bottom end, and a drainage surface extending from the top end to the bottom end. The outer diameter of the top end is smaller than the outer diameter of the bottom end, and the drainage surface is spaced apart from the exhaust gas pipe.

[0012] Understandably, the conical section evenly divides the concentrated single stream of exhaust gas into multiple streams circumferentially, avoiding excessively high local concentrations or uneven temperatures caused by single-point injection. The gap between the guide surface and the exhaust gas duct forms an annular injection channel, guiding the exhaust gas into the combustion chamber at a specific diffusion angle. This design not only promotes uniform radial distribution of the exhaust gas, creating a larger contact area and more uniform initial conditions for subsequent mixing with the swirling airflow, but also helps to evenly distribute the temperature field within the furnace, preventing the formation of localized high or low temperature zones.

[0013] In one embodiment, the conical guide further includes a protrusion connected to the top end, the protrusion extending into the exhaust gas pipe and being snapped into the exhaust gas pipe by a snap-fit ​​component, and the conical portion being located outside the exhaust gas pipe and spaced apart from the exhaust gas pipe.

[0014] Understandably, by adding a protrusion that connects to the top of the conical section and extends into the exhaust gas duct, and using a snap-fit ​​connector to achieve the connection with the exhaust gas duct, methods such as welding at the exhaust gas duct outlet that could cause material deformation or stress concentration are avoided. The snap-fit ​​structure is easy to install, provides precise positioning, and ensures a reliable connection, ensuring that the conical guide remains centered in the duct during long-term operation, thus guaranteeing the uniformity and symmetry of the circumferential distribution of exhaust gas. This improves the ease of manufacturing, installation reliability, and long-term operational stability of the device.

[0015] In one embodiment, the drainage surface is inclined relative to the air intake direction, and the angle between the drainage surface and the air intake direction ranges from 60° to 90°.

[0016] Understandably, by limiting the angle between the guide surface and the air intake direction to between 60° and 90°, an optimized design range is provided for the exhaust gas injection and diffusion angle. This angle range represents the best balance between mixing effect and flame stability; a larger angle (approaching 90°) allows the exhaust gas to diffuse more widely, increasing the contact area with the surrounding swirling airflow, which is suitable for scenarios requiring rapid mixing; a smaller angle (approaching 60°) allows the exhaust gas to be injected more directly, with stronger penetration, which is suitable for situations requiring a longer mixing path or avoiding the flame from getting too close to the burner wall.

[0017] In one embodiment, the swirl blade assembly is rotatably mounted on the outside of the exhaust gas duct and located inside the exhaust gas combustion air duct, and the swirl angle of the swirl blade assembly ranges from 30° to 60°.

[0018] Understandably, by limiting the swirl angle range of the swirl blade assembly to 30° to 60° and rotatably mounting it, the burner gains the ability to actively adjust the swirl intensity of the exhaust gas and combustion-supporting gas. The swirl angle is a key parameter determining swirl intensity: a smaller angle results in weaker swirl and a longer flame; a larger angle results in stronger swirl, a larger recirculation zone, a shorter and thicker flame, and more intense mixing. Setting the angle within this effective range of 30° to 60° allows for flexible adjustment of the combustion-supporting air swirl intensity based on actual operating conditions (such as changes in exhaust gas flow rate and calorific value), improving the burner's adaptability.

[0019] In one embodiment, the peripheral component has a first gas collecting chamber, a second gas collecting chamber, a third gas collecting chamber and a clearance chamber arranged sequentially along the air intake direction. The first gas collecting chamber and / or the second gas collecting chamber are respectively connected to the exhaust gas pipe, and the third gas collecting chamber is connected to the exhaust gas combustion air pipe. The exhaust gas pipe and the exhaust gas combustion air pipe extend along the air intake direction into the clearance chamber and extend to the incineration end.

[0020] Understandably, by creating a first, second, and third gas collection chamber, along with a clearance chamber, arranged sequentially along the air intake direction within the outer components, a highly integrated and modular internal fluid distribution system is constructed, transforming the chaotic external piping connections into a well-organized flow distribution within the burner. The first, second, and third gas collection chambers serve to buffer pressure and distribute flow evenly, ensuring that the exhaust gas or exhaust-fuel gas delivered to each annular channel is uniform in the circumferential direction; the clearance chamber provides space for the passage of the internal core piping. This design greatly simplifies the overall external structure of the burner and the on-site piping layout, making the entire system more compact and streamlined, and providing a structural foundation for handling multiple different exhaust gas flows.

[0021] In one embodiment, the peripheral components include a first exhaust gas inlet pipe and an exhaust gas combustion air inlet pipe. The exhaust gas pipeline includes a first exhaust gas inlet pipe. The first exhaust gas inlet pipe is connected to a first gas collection chamber. The first exhaust gas inlet pipe is connected to the first gas collection chamber and passes through a second gas collection chamber, a third gas collection chamber, and a clearance chamber in sequence along the gas inlet direction to the combustion end. The exhaust gas combustion air pipeline is connected to the third gas collection chamber and passes through the clearance chamber in the gas inlet direction to the combustion end.

[0022] Understandably, the first exhaust gas inlet pipe connects to the first gas collection chamber, and then passes through the first exhaust gas inlet pipe and subsequent chambers to the combustion end; the exhaust gas combustion air inlet pipe connects to the third gas collection chamber, and then passes through the exhaust gas combustion air duct to the combustion end. This achieves independent, interference-free delivery of different airflows within a compact structure of peripheral components. It ensures that the exhaust gas and exhaust gas combustion air are completely isolated before reaching the nozzle, mixing only at the designed combustion end, thereby achieving precise combustion control and guaranteeing combustion efficiency and stability.

[0023] In one embodiment, the peripheral component further includes a second exhaust gas inlet pipe, the exhaust gas pipeline including a second exhaust gas inlet pipe; the second exhaust gas inlet pipe is connected to a second gas collection chamber, the second exhaust gas inlet pipe is connected to the second gas collection chamber and passes through a third gas collection chamber and a clearance chamber in sequence along the gas inlet direction to the combustion end; the second exhaust gas inlet pipe is sleeved on the outside of the first exhaust gas inlet pipe, and the exhaust gas combustion air pipeline is sleeved on the outside of the second exhaust gas inlet pipe.

[0024] Understandably, by adding a second exhaust gas inlet pipe, a second gas collection chamber, and a second exhaust gas inlet pipe sleeved outside the first exhaust gas inlet pipe, integrated treatment of multiple (two) exhaust gases is achieved, enabling the burner to simultaneously process two types of exhaust gases that cannot be premixed at the front end. The concentric sleeve structure integrates different exhaust gas flow paths, greatly simplifying the on-site piping layout and the number of furnace openings, demonstrating the advantages of high integration.

[0025] In one embodiment, the swirl blade assembly is rotatably sleeved on the outside of the second exhaust gas inlet pipe, and the tip of the conical guide is positioned toward the first exhaust gas inlet pipe.

[0026] Understandably, the swirl vane assembly is mounted on the outermost exhaust duct (second exhaust inlet pipe), while the conical guide acts on the outlet of the innermost exhaust duct (first exhaust inlet pipe). The strong swirling combustion air at the periphery can simultaneously entrain and mix the two exhaust gases ejected from the inner and middle layers, while the injection pattern of the central exhaust gas remains precisely controlled by the conical guide. This ensures efficient and stable mixing and combustion even under complex conditions involving multiple different exhaust gases.

[0027] In one embodiment, the axial distance between the incineration end and the combustion end along the air intake direction is greater than 400 mm.

[0028] Furthermore, this application has at least the following beneficial effects:

[0029] The exhaust gas calorific value adaptive combined burner provided in this application embodiment has excellent adaptability to exhaust gases with different calorific values. When high-calorific-value exhaust gas is ejected from the central pipe, the conical guide evenly disperses it, and this exhaust gas is entrained by the strong swirling flow field formed by the high-speed rotating combustion air (generated by the swirl blade assembly) on the periphery. The center of the swirling flow field is a low-pressure zone, which can effectively entrain high-temperature flue gas and "anchor" the flame, establishing an extremely stable flame root for the high-calorific-value exhaust gas. At the same time, the strong turbulent mixing allows the exhaust gas and combustion air to be mixed instantly, ensuring full and efficient combustion and avoiding incomplete combustion and excessive carbon monoxide caused by lack of oxygen. When low-calorific-value exhaust gas enters, although it is not strong enough to form a stable flame, it will still be drawn into this oxygen-rich, strong swirling flow field. This allows the small amount of combustible components and other components that need to be oxidized in the exhaust gas to come into contact with and mix with oxygen in the most efficient way at the first moment. This greatly promotes the early occurrence and progress of its oxidation-reduction reaction, which is equivalent to extending the effective residence and reaction time of the exhaust gas in the furnace, thereby ensuring thorough harmless treatment.

[0030] The adaptive combined burner for waste gas calorific value provided in this application embodiment achieves adaptive effects for waste gases with different calorific values ​​while maintaining relatively simple control logic, making it highly practical. This application structurally separates the central component forming the main flame from the peripheral components treating the waste gas. Furthermore, the waste gas inlet is significantly downstream of the main flame inlet in the axial direction. Combined with the front-end cast refractory layer protecting the main flame, this minimizes the transmission of fluctuations in the peripheral waste gas (whether in calorific value, composition, or flow rate) to the central main flame, thus preventing any impact on its stability. Key process indicators such as the overall temperature of the incinerator or the steam output of the downstream waste heat boiler can have their control loops completely simplified, requiring only the adjustment of the central main fuel gas flow rate for precise control. Since the burner itself possesses adaptive capabilities to the calorific value of the waste gas, the waste gas treatment effect no longer depends on complex real-time adjustments. Therefore, in actual operation, the supply of waste gas combustion air can be set to a constant value without change, and the waste gas can be directly introduced within the treatment range without any pre-adjustment. This completely eliminates the need to write complex control programs that require real-time adjustment of air volume based on the calorific value of the exhaust gas, greatly reducing the complexity of system control and the risk of malfunctions, and improving the stability and reliability of the entire incineration system. Attached Figure Description

[0031] Figure 1 This is a three-dimensional schematic diagram of an adaptive combined burner for exhaust gas calorific value provided in an embodiment of this application.

[0032] Figure 2 This is a three-dimensional schematic diagram of the exhaust gas calorific value adaptive combined burner provided in the embodiments of this application from another angle.

[0033] Figure 3 This is a plan view of the exhaust gas calorific value adaptive combined burner provided in the embodiments of this application.

[0034] Figure 4 yes Figure 3 A cross-sectional view along the IV-IV direction.

[0035] Figure 5 yes Figure 4 A magnified view of the corresponding V region.

[0036] Figure 6 yes Figure 4 A magnified view of the corresponding VI area.

[0037] Figure 7 yes Figure 4 A magnified view of the corresponding region VII.

[0038] Figure 8 yes Figure 4 A magnified view of the corresponding VIII region.

[0039] Figure 9 yes Figure 4 A magnified view of the corresponding IX region.

[0040] Explanation of reference numerals in the attached drawings: 11. Central assembly; 110. Combustion end; 111. Central shell; 1111. Combustible gas collection chamber; 1112. Main and auxiliary gas collection chamber; 112. Combustible gas inlet pipe; 113. Main and auxiliary gas inlet pipe; 114. Combustible gas transmission pipe; 115. Main and auxiliary gas transmission pipe; 116. Igniter; 117. Flame observer; 118. Blade; 12. Peripheral assembly; 120. Combustion end; 121. Peripheral shell; 1211. First gas collection chamber; 1212. Second gas collection chamber; 1213. Third gas collection chamber ; 1214, clearance cavity; 1215, partition; 122, refractory layer; 123, exhaust gas duct; 1231, first exhaust gas inlet pipe; 1232, second exhaust gas inlet pipe; 124, exhaust gas combustion air duct; 125, first exhaust gas inlet pipe; 126, second exhaust gas inlet pipe; 127, exhaust gas combustion air inlet pipe; 128, conical guide; 1280, conical part; 1281, top end; 1282, bottom end; 1283, flow guide surface; 1284, protrusion; 1285, snap-fit ​​component; 129, swirl blade assembly; 101, air intake direction. Detailed Implementation

[0041] The following is in conjunction with the appendix Figure 1 To be continued Figure 9 This application will be described in further detail below.

[0042] The technical solutions in the embodiments of this application will be further described in detail below with reference to the accompanying drawings. The described embodiments are only possible technical implementations of this application, but are not limited thereto. Other embodiments obtained by those skilled in the art in conjunction with the embodiments of this application without creative effort are also within the protection scope of this application.

[0043] like Figure 1 and Figure 2 As shown in the figure, this application provides an adaptive combined burner for exhaust gas calorific value, including a central component 11 and a peripheral component 12. The central component 11 mainly integrates the functions of transmitting combustible gas and main combustion gas, igniting the main flame, and observing the combustion chamber. The peripheral component 12 mainly integrates the functions of transmitting exhaust gas and exhaust gas combustion gas, as well as constructing a stable combustion space and heat insulation structure around the main flame.

[0044] Further integration Figures 3 to 5 As shown, in one embodiment, one end of the central component 11 along the air intake direction 101 is a combustion end 110. The central component 11 is used to deliver combustible gas and main combustion-supporting gas to the combustion end 110, and ignite them to form a main flame. The peripheral component 12 is arranged around the outside of the combustion end 110. One end of the peripheral component 12 along the air intake direction 101 is provided with a plurality of combustion ends 120, which are located downstream of the combustion end 110 along the air intake direction 101. The peripheral component 12 includes an exhaust gas pipe 123 for conveying exhaust gas and an exhaust gas combustion-supporting air pipe 124 for conveying exhaust gas combustion-supporting gas. The exhaust gas combustion-supporting air pipe 124 is sleeved around the exhaust gas pipe 123. The exhaust gas pipe 123 and the exhaust gas combustion-supporting air pipe 124 Extending to the incineration end 120, it is used to introduce exhaust gas and exhaust gas combustion-supporting gas into the combustion chamber (not shown, located downstream of the exhaust gas calorific value adaptive combined burner); the peripheral component 12 also includes a conical guide 128 and a swirl blade assembly 129 disposed at the incineration end 120, the conical guide 128 is disposed at the outlet of the exhaust gas duct 123 and the tip of the conical guide 128 is disposed facing the exhaust gas duct 123, and the swirl blade assembly 129 is rotatably disposed at the outlet of the exhaust gas combustion-supporting air duct 124.

[0045] Understandably, placing the peripheral component 12 for conveying exhaust gas downstream of the combustion end 110 of the central component 11 ensures that the main flame formed by the central component 11 is established stably first, unaffected by fluctuations in the composition, flow rate, or calorific value of the peripheral exhaust gas. The introduction and combustion of the peripheral exhaust gas occur downstream of the stable combustion zone of the main flame, fundamentally eliminating the impact of exhaust gas or its combustion-supporting air on the root of the main flame, thus ensuring the core stability of the entire combustion system. By setting an exhaust gas combustion-supporting air duct 124 surrounding the exhaust gas duct 123, a dedicated and independent combustion-supporting air channel is provided for the exhaust gas. This ensures that regardless of the calorific value of the exhaust gas, sufficient oxygen can be obtained for combustion or oxidation reactions. When the calorific value of the exhaust gas is high, independent air distribution ensures complete combustion and avoids excessive carbon monoxide. When the calorific value of the exhaust gas is low, it can also mix with the combustion-supporting air immediately, causing an early oxidation reaction and extending the effective residence time in the furnace. Meanwhile, a conical guide 128 and a swirl blade assembly 129 are installed at the outlets of the exhaust gas and the exhaust gas combustion-supporting gas to achieve adaptive adjustment for exhaust gases with different calorific values. The conical guide 128 disperses the exhaust gas jet and guides it evenly, while the swirl blade assembly 129 makes the exhaust gas combustion-supporting gas form a strong rotating flow field. The exhaust gas is drawn into this rotating flow field the moment it enters the combustion chamber, achieving efficient and rapid mixing. Furthermore, the low-pressure zone formed at the center of the rotating flow field is also conducive to the entrainment of high-temperature flue gas, providing conditions for the establishment of a stable flame for high-calorific-value exhaust gas.

[0046] In this embodiment, the combustion end 110 is approximately located on the central axis of the exhaust gas calorific value adaptive combined burner (approximately the same direction as the air intake direction 101), and multiple combustion ends 120 are spaced apart around the combustion end 110 along the direction surrounding the central axis. The combustion end 110 and the combustion end 120 are staggered along the air intake direction 101, with the combustion end 120 located downstream of the combustion end 110 along the air intake direction 101. The axial distance between the combustion end 110 and the combustion end 120 along the air intake direction 101 should be greater than 400 mm.

[0047] Understandably, the exhaust gas and its combustion-supporting gas are not positioned directly towards the main flame to avoid affecting the combustion of the main flame and to help establish a stable incineration system.

[0048] It should be explained that the main air intake direction 101 of the exhaust gas calorific value adaptive combined burner provided in this application embodiment is basically extended in the same direction.

[0049] Further integration Figure 1 , 2As shown in Figure 9, in one embodiment, the central assembly 11 includes a central housing 111, a combustible gas intake pipe 112, a main and auxiliary gas intake pipe 113, a combustible gas transmission pipe 114, a main and auxiliary gas transmission pipe 115, an igniter 116, a flame observer 117, and blades 118. The central housing 111 is generally cylindrical and extends generally along the intake direction 101. The igniter 116 is inserted into the central housing 111 along the intake direction 101, and is generally located in the central region of the housing. The ignition end of the igniter 116 extends along the intake direction 101 to a position adjacent to the combustion end 110. The flame observer 117 is inserted into the central housing 111 along the intake direction 101 and is capable of observing the flame combustion within the combustion chamber.

[0050] In one embodiment, a combustible gas inlet pipe 112 is located outside the central housing 111 and communicates with the gas collection chamber 1111 inside the central housing 111. Multiple combustible gas transmission pipes 114 are located inside the housing and extend along the gas inlet direction 101. The multiple combustible gas transmission pipes 114 are arranged around the igniter 116. One end of the combustible gas transmission pipe 114 is communicated with the gas collection chamber 1111, and the other end of the combustible gas transmission pipe 114 extends out of the central housing 111 and is adjacent to the combustion end 110.

[0051] In one embodiment, the main auxiliary gas intake pipe 113 is located outside the central housing 111 and communicates with the main auxiliary gas collection chamber 1112 inside the central housing 111. The other end of the main auxiliary gas collection chamber 1112 extends to a position adjacent to the combustion end 110, and the blade 118 is rotatably located at the other end of the main auxiliary gas collection chamber 1112.

[0052] like Figure 1 and Figure 2 As shown, in one embodiment, the peripheral component 12 is generally hollow and annular, and the central component 11 extends into the peripheral component 12 along the air intake direction 101. The rear end of the central component 11, which is provided with a combustible gas intake pipe 112 and a main auxiliary gas intake pipe 113, is located outside the peripheral component 12. The front end of the central component 11, which is provided with a combustion end 110, extends approximately to the middle section of the peripheral component 12 along the air intake direction 101 and does not extend beyond the peripheral component 12.

[0053] In one embodiment, the peripheral component 12 further includes a peripheral shell 121 and a refractory layer 122. A portion of the refractory layer 122 is generally annular, with its inner edge connected to the front end of the central component 11 and its outer edge abutting against the shell of the peripheral component 12. Another portion of the refractory layer 122 surrounds the area of ​​the peripheral shell 121 that is offset from the central component 11. The refractory layer 122 is used to construct the combustion space and provide necessary heat insulation; the thickness of the refractory layer 122 should be not less than 250 mm. In this embodiment, the material of the refractory layer 122 can be refractory brick; in other embodiments, the refractory layer 122 can also be made of other known refractory materials, which will not be elaborated here.

[0054] Further integration Figures 4 to 8 As shown, in one embodiment, the peripheral component 12 has a first gas collecting chamber 1211, a second gas collecting chamber 1212, a third gas collecting chamber 1213 and a clearance chamber 1214 arranged sequentially along the air intake direction 101. The first gas collecting chamber 1211 and / or the second gas collecting chamber 1212 are respectively connected to the exhaust gas pipe 123, and the third gas collecting chamber 1213 is connected to the exhaust gas combustion air pipe 124. The exhaust gas pipe 123 and the exhaust gas combustion air pipe 124 extend along the air intake direction 101 into the clearance chamber 1214 and extend to the combustion end 120.

[0055] In this embodiment, the peripheral component 12 further includes a partition 1215. The first gas collecting chamber 1211, the second gas collecting chamber 1212, the third gas collecting chamber 1213 and the clearance chamber 1214 are located inside the peripheral housing 121. The first gas collecting chamber 1211, the second gas collecting chamber 1212, the third gas collecting chamber 1213 and the clearance chamber 1214 are separated from each other by the partition 1215.

[0056] Understandably, by creating a first gas collecting chamber 1211, a second gas collecting chamber 1212, a third gas collecting chamber 1213, and a clearance chamber 1214 sequentially arranged along the air intake direction 101 inside the outer component 12, a highly integrated and modular internal fluid distribution system is constructed, transforming the chaotic external pipe connections into a regular flow channel distribution inside the burner. The first gas collecting chamber 1211, the second gas collecting chamber 1212, and the third gas collecting chamber 1213 serve to buffer pressure and distribute flow evenly, ensuring that the exhaust gas or exhaust gas combustion-supporting gas delivered to each annular channel is uniform in the circumferential direction; the clearance chamber 1214 provides space for the passage of the internal core pipes. This design greatly simplifies the overall external structure of the burner and the on-site pipe layout, making the entire system more compact and neat, and providing a structural basis for handling multiple different exhaust gas flows.

[0057] Further integration Figure 5 and Figure 6As shown, in one embodiment, the peripheral component 12 includes a first exhaust gas inlet pipe 125 and an exhaust gas combustion air inlet pipe 127, and the exhaust gas pipe 123 includes a first exhaust gas inlet pipe 1231. The first exhaust gas inlet pipe 125 is connected to the first gas collecting chamber 1211, and the first exhaust gas inlet pipe 1231 is connected to the first gas collecting chamber 1211 and passes through the second gas collecting chamber 1212, the third gas collecting chamber 1213, and the clearance chamber 1214 in sequence along the air intake direction 101 to the combustion end 120. The exhaust gas combustion air pipe 124 is connected to the third gas collecting chamber 1213 and passes through the clearance chamber 1214 in the air intake direction 101 to the combustion end 120.

[0058] In this embodiment, the first exhaust gas inlet pipe 125 is located outside the outer casing 121 and communicates with the first gas collection chamber 1211 via an opening on the outer casing 121. The other end of the first exhaust gas inlet pipe 125 is connected to a set of external exhaust gas transmission pipelines for introducing exhaust gas into the first gas collection chamber 1211. The first exhaust gas inlet pipe 1231 is connected to the partition 1215 between the first gas collection chamber 1211 and the second gas collection chamber 1212, and communicates with the first gas collection chamber 1211 through an opening on the partition 1215. The first exhaust gas inlet pipe 1231 further passes through the second gas collection chamber 1212, the third gas collection chamber 1213, and the clearance chamber 1214, but does not communicate with them.

[0059] In this embodiment, the exhaust gas combustion air inlet pipe 127 is located outside the outer casing 121 and communicates with the third gas collection chamber 1213 via an opening on the outer casing 121. The other end of the exhaust gas combustion air inlet pipe 127 is connected to an external exhaust gas combustion air transmission pipeline for introducing exhaust gas combustion air into the third gas collection chamber 1213. The exhaust gas combustion air duct 124 is connected to the partition 1215 between the third gas collection chamber 1213 and the clearance chamber 1214, and communicates with the third gas collection chamber 1213 via an opening on the partition 1215. The first exhaust gas inlet pipe 1231 further passes through the clearance chamber 1214 but does not communicate with it. The exhaust gas combustion air duct 124 is sleeved on the outside of the portion of the first exhaust gas inlet pipe 125 located in the clearance chamber 1214.

[0060] Understandably, the first exhaust gas inlet pipe 125 connects to the first gas collection chamber 1211, and then passes through the first exhaust gas inlet pipe 1231 and subsequent chambers to the combustion end 120; the exhaust gas combustion air inlet pipe 127 connects to the third gas collection chamber 1213, and then passes through the exhaust gas combustion air duct 124 to the combustion end 120. Independent, interference-free delivery of different airflows is achieved within the compact structure of the peripheral component 12. This ensures that the exhaust gas and exhaust gas combustion air are completely isolated before reaching the nozzle and mixed at the designed combustion end 120, thereby achieving precise combustion control and ensuring combustion efficiency and stability.

[0061] Further integration Figure 7 and Figure 8 As shown, in one embodiment, the peripheral component 12 further includes a second exhaust gas inlet pipe 126, and the exhaust gas pipe 123 includes a second exhaust gas inlet pipe 1232; the second exhaust gas inlet pipe 126 is connected to the second gas collection chamber 1212, the second exhaust gas inlet pipe 1232 is connected to the second gas collection chamber 1212 and passes through the third gas collection chamber 1213 and the clearance chamber 1214 in sequence along the gas inlet direction 101 to the combustion end 120; the second exhaust gas inlet pipe 1232 is sleeved on the outside of the first exhaust gas inlet pipe 1231, and the exhaust gas combustion air pipe 124 is sleeved on the outside of the second exhaust gas inlet pipe 1232.

[0062] In this embodiment, the first exhaust gas inlet pipe 125 and the second exhaust gas inlet pipe 126 are spaced apart. The second exhaust gas inlet pipe 126 is located outside the outer casing 121 and communicates with the second gas collection chamber 1212 through an opening on the outer casing 121. The other end of the second exhaust gas inlet pipe 126 is connected to another set of external exhaust gas transmission pipelines for introducing exhaust gas into the second gas collection chamber 1212. The second exhaust gas inlet pipe 1232 is connected to the partition 1215 between the second gas collection chamber 1212 and the third gas collection chamber 1213, and communicates with the second gas collection chamber 1212 through an opening on the partition 1215. The second exhaust gas inlet pipe 1232 further passes through the third gas collection chamber 1213 and the clearance chamber 1214 but does not communicate with them.

[0063] In this embodiment, the second exhaust gas inlet pipe 1232 is sleeved on the outer side of the portion of the first exhaust gas inlet pipe 1231 located in the third gas collection chamber 1213 and the clearance chamber 1214, and the exhaust gas combustion air pipe 124 is sleeved on the outer side of the portion of the second exhaust gas inlet pipe 1232 located in the clearance chamber 1214.

[0064] Understandably, by adding a second exhaust gas inlet pipe 126, a second gas collecting chamber 1212, and a second exhaust gas inlet pipe 1232 sleeved outside the first exhaust gas inlet pipe 1231, integrated treatment of multiple (two) exhaust gases is achieved, enabling the burner to simultaneously process two types of exhaust gases that cannot be premixed at the front end. The concentric sleeve structure integrates different exhaust gas flow paths, greatly simplifying the on-site piping layout and the number of furnace openings, demonstrating the advantages of high integration.

[0065] It should be noted that arrow A corresponds to the flow direction of exhaust gas in the first exhaust gas inlet pipe 1231, arrow B corresponds to the flow direction of exhaust gas in the second exhaust gas inlet pipe 1232, and arrow C corresponds to the flow direction of exhaust gas combustion-supporting gas in the exhaust gas combustion-supporting air duct 124.

[0066] Further integration Figure 5 and Figure 7As shown, in one embodiment, the tapered guide 128 includes a tapered portion 1280, the tapered portion 1280 includes a top end 1281 and a bottom end 1282 and a drainage surface 1283 extending from the top end 1281 to the bottom end 1282, the outer diameter of the top end 1281 is smaller than the outer diameter of the bottom end 1282, and the drainage surface 1283 is spaced apart from the exhaust gas pipe 123.

[0067] In this embodiment, the cone portion 1280 is located downstream of the exhaust gas pipe 123 along the air intake direction 101 and is spaced apart from the exhaust gas pipe 123, and is used to divert and guide the ejected exhaust gas at the outlet of the exhaust gas pipe 123. The guide surface 1283 is the inclined cone surface of the cone portion 1280.

[0068] Understandably, the conical section 1280 evenly divides the concentrated single stream of exhaust gas into multiple streams circumferentially, avoiding excessively high local concentrations or uneven temperatures caused by single-point injection. The gap between the guide surface 1283 and the exhaust gas duct 123 forms an annular injection channel, guiding the exhaust gas into the combustion chamber at a specific diffusion angle. This design not only promotes uniform radial distribution of the exhaust gas, creating a larger contact area and more uniform initial conditions for subsequent mixing with the swirling air, but also helps to evenly distribute the temperature field within the furnace, avoiding the formation of localized high or low temperature zones.

[0069] In one embodiment, the drainage surface 1283 is inclined relative to the air intake direction 101, and the angle between the drainage surface 1283 and the air intake direction 101 ranges from 60° to 90°.

[0070] In this embodiment, the angle between the guide surface 1283 and the intake direction 101 can be 60°, 75°, or 90°. Specifically, the range of the angle between the guide surface 1283 and the intake direction 101 can also be 60°, 61°, 62°, 63°, 64°, 65°, 66°, 67°, 68°, 69°, 70°, 71°, 72°, 73°, 74°, 75°, 76°, 77°, 78°, 79°, 80°, 81°, 82°, 83°, 84°, 85°, 86°, 87°, 88°, 89°, or 90°. When the estimated calorific value of the incoming exhaust gas is higher, a larger angle can be preset, and it also needs to be selected in conjunction with the design shape of the combustion chamber.

[0071] Understandably, by limiting the angle between the guide surface 1283 and the intake direction 101 to between 60° and 90°, an optimized design range is provided for the exhaust gas injection diffusion angle. This angle range represents the best balance between mixing effect and flame stability; a larger angle (approaching 90°) allows the exhaust gas to diffuse more widely, increasing the contact area with the surrounding swirling airflow, which is suitable for scenarios requiring rapid mixing; a smaller angle (approaching 60°) allows the exhaust gas to be injected more directly, with stronger penetration, which is suitable for situations requiring a longer mixing path or avoiding the flame from getting too close to the burner wall.

[0072] In one embodiment, the tapered guide 128 further includes a protrusion 1284. The protrusion 1284 is connected to the top end 1281, extends into the exhaust gas duct 123 and is engaged with the exhaust gas duct 123 by a snap-fit ​​member 1285, and the tapered portion 1280 is located outside the exhaust gas duct 123 and is spaced apart from the exhaust gas duct 123.

[0073] In this embodiment, the protrusion 1284 is generally cylindrical, extending along the air intake direction 101. The diameter of the protrusion 1284 is designed to be small to avoid blocking the outlet of the exhaust pipe 123. The protrusion 1284 is inserted into the middle of the snap-fit ​​member 1285. The snap-fit ​​member 1285 can be a plate with a hollow structure or a structure of multiple interconnected rods. The snap-fit ​​member 1285 is disposed inside the exhaust pipe 123 and abuts against the inner surface of the exhaust pipe 123. The tapered guide member 128 is fixedly connected to the exhaust pipe 123 through the snap-fit ​​member 1285.

[0074] Understandably, by adding a protrusion 1284 that connects to the top 1281 of the conical section 1280 and extends into the exhaust gas pipe 123, and using a snap-fit ​​component 1285 to achieve connection with the exhaust gas pipe 123, the fixing methods that may cause material deformation or stress concentration, such as welding at the outlet of the exhaust gas pipe 123, are avoided. The snap-fit ​​structure is easy to install, accurately positioned, and reliably connected, ensuring that the conical guide component 128 remains in the center position of the pipe during long-term operation, thereby guaranteeing the uniformity and symmetry of the circumferential distribution of exhaust gas. This improves the ease of manufacturing, installation reliability, and long-term operational stability of the device.

[0075] In one embodiment, the swirl blade assembly 129 is rotatably mounted on the outside of the exhaust gas duct 123 and located inside the exhaust gas combustion air duct 124, and the swirl angle of the swirl blade assembly 129 is in the range of 30° to 60°.

[0076] In this embodiment, the swirl angle of the swirl blade assembly 129 can be 30°, 31°, 32°, 33°, 34°, 35°, 36°, 37°, 38°, 39°, 40°, 41°, 42°, 43°, 44°, 45°, 46°, 47°, 48°, 49°, 50°, 51°, 52°, 53°, 54°, 55°, 56°, 57°, 58°, 59°, or 60°.

[0077] Understandably, by limiting the swirl angle range of the swirl blade assembly 129 to 30° to 60° and rotatably mounting it, the burner is given the ability to actively adjust the swirl intensity of the exhaust gas and combustion-supporting gas. The swirl angle is a key parameter determining the swirl intensity: a small angle results in a weak swirl and a longer flame; a large angle results in a strong swirl, a large recirculation zone, a short and thick flame, and more intense mixing. Setting the angle within the effective range of 30° to 60° allows for flexible adjustment of the swirl intensity of the combustion-supporting air according to actual operating conditions (such as changes in exhaust gas flow rate and calorific value), improving the burner's adaptability.

[0078] In one embodiment, when the exhaust gas combustion air duct 124 is in a state of only cooperating with the first exhaust gas inlet pipe 1231, the swirl blade assembly 129 is rotatably sleeved on the outside of the first exhaust gas inlet pipe 1231, and the tip of the conical guide 128 is set towards the first exhaust gas inlet pipe 1231.

[0079] In one embodiment, when the exhaust gas combustion air duct 124 is simultaneously engaged with the first exhaust gas inlet pipe 1231 and the second exhaust gas inlet pipe 1232, the swirl vane assembly 129 is rotatably sleeved on the outside of the second exhaust gas inlet pipe 1232, and the tip of the conical guide 128 is positioned toward the first exhaust gas inlet pipe 1231.

[0080] Understandably, the swirl vane assembly 129 is mounted on the outermost exhaust gas duct 123 (second exhaust gas inlet duct 1232), while the conical guide 128 acts on the outlet of the innermost exhaust gas duct 123 (first exhaust gas inlet duct 1231). The strong swirling combustion air on the periphery can simultaneously entrain and mix the two exhaust gases ejected from the inner and middle layers, while the ejection pattern of the central exhaust gas is still precisely controlled by the conical guide 128. This ensures efficient and stable mixing and combustion even under complex operating conditions involving multiple different exhaust gases.

[0081] In one embodiment, the flow velocity of the exhaust gas combustion-supporting gas at the outlet of the exhaust gas combustion-supporting air duct 124 is not less than 15 m / s, and the flow velocity of the exhaust gas at the outlet of the exhaust gas duct 123 is not less than 20 m / s.

[0082] Understandably, limiting the outlet velocities of the exhaust gas and the combustion-supporting gas further ensures and enhances the mixing effect. A higher exhaust gas / combustion-supporting gas velocity (not less than 15 m / s) creates a more powerful and stable swirling flow field, providing strong momentum and a stable macroscopic environment for subsequent mixing. Simultaneously, ensuring the exhaust gas has sufficiently high outlet momentum (velocity not less than 20 m / s) allows it to effectively "penetrate" and be entrained into the strong swirling combustion air, achieving more rapid and uniform mixing. This optimized velocity matching ensures that regardless of the exhaust gas's calorific value, optimal combustion or reaction conditions are reached in the shortest possible time, further improving combustion efficiency and the thoroughness of exhaust gas treatment.

[0083] Furthermore, this application has at least the following beneficial effects:

[0084] The exhaust gas calorific value adaptive combined burner provided in this application embodiment has excellent adaptability to exhaust gases with different calorific values. When high-calorific-value exhaust gas is ejected from the central pipe, the conical guide 128 evenly disperses it, and this exhaust gas is entrained by the strong swirling flow field formed by the high-speed rotating combustion air (generated by the swirl blade assembly 129) on the periphery; the center of the swirling flow field is a low-pressure zone, which can effectively entrain high-temperature flue gas and "anchor" the flame, establishing an extremely stable flame root for the high-calorific-value exhaust gas; at the same time, the strong turbulent mixing allows the exhaust gas and combustion air to be mixed instantly, ensuring full and efficient combustion and avoiding incomplete combustion and excessive carbon monoxide caused by lack of oxygen. When low-calorific-value exhaust gas enters, although it is not strong enough to form a stable flame, it will still be drawn into this oxygen-rich, strong swirling flow field. This allows the small amount of combustible components and other components that need to be oxidized in the exhaust gas to come into contact with and mix with oxygen in the most efficient way at the first moment. This greatly promotes the early occurrence and progress of its oxidation-reduction reaction, which is equivalent to extending the effective residence and reaction time of the exhaust gas in the furnace, thereby ensuring thorough harmless treatment.

[0085] The adaptive combined burner for waste gas calorific value provided in this application embodiment achieves adaptive effects for waste gases with different calorific values ​​while maintaining relatively simple control logic, making it highly practical. This application structurally separates the central component 11 forming the main flame from the peripheral component 12 that treats the waste gas. Furthermore, the waste gas inlet is significantly downstream of the main flame inlet in the axial direction. Combined with the front-end cast refractory layer 122 protecting the main flame, this minimizes the transmission of fluctuations in the peripheral waste gas (whether in calorific value, composition, or flow rate) to the central main flame, thus preventing any impact on its stability. Key process indicators such as the overall temperature of the incinerator or the steam output of the downstream waste heat boiler can have their control loops completely simplified, requiring only the adjustment of the central main fuel gas flow rate for precise control. Since the burner itself possesses adaptive capabilities for the calorific value of the waste gas, the waste gas treatment effect no longer depends on complex real-time adjustments. Therefore, in actual operation, the supply of waste gas combustion air can be set to a constant value without change, and the waste gas can be directly introduced within the treatment range without any pre-adjustment. This completely eliminates the need to write complex control programs that require real-time adjustment of air volume based on the calorific value of the exhaust gas, greatly reducing the complexity of system control and the risk of malfunctions, and improving the stability and reliability of the entire incineration system.

[0086] The embodiments described in this specific implementation are preferred embodiments of this application and are not intended to limit the scope of protection of this application. Identical components are represented by the same reference numerals. Therefore, all equivalent changes made to the structure, shape, and principle of this application should be included within the scope of protection of this application.

Claims

1. A combined waste heat value self-adaptive burner, characterized in that, The application relates to a gas turbine, which comprises: a central component (11) having a combustion end (110) at one end along an air intake direction (101), the central component (11) being used for conveying combustible gas and main combustion-supporting gas to the combustion end (110) and igniting the combustible gas and the main combustion-supporting gas at the combustion end (110) to form a main flame; a peripheral component (12) arranged outside the combustion end (110), the peripheral component (12) being provided with a plurality of incineration ends (120) at one end along the air intake direction (101), the incineration ends (120) being located downstream of the combustion end (110) along the air intake direction (101), and the incineration ends (120) being axially spaced apart from the combustion end (110) along the air intake direction (101) by a distance greater than 400 mm; the peripheral component (12) comprises a waste gas pipeline (123) for conveying waste gas and a waste gas combustion-supporting air pipeline (124) for conveying waste gas combustion-supporting gas, the waste gas combustion-supporting air pipeline (124) being arranged outside the waste gas pipeline (123), and the waste gas pipeline (123) and the waste gas combustion-supporting air pipeline (124) extending to the incineration ends (120) for introducing waste gas and waste gas combustion-supporting gas into a combustion chamber, the flow rate of the waste gas combustion-supporting gas at the outlet of the waste gas combustion-supporting air pipeline (124) being not less than 15 m / s, and the flow rate of the waste gas at the outlet of the waste gas pipeline (123) being not less than 20 m / s; the peripheral component (12) further comprises a conical guide (128) arranged at the incineration ends (120) and a swirl vane group (129) rotatably arranged at the outlet of the waste gas combustion-supporting air pipeline (124); wherein the peripheral component (12) comprises a first waste gas introduction pipeline (125), a second waste gas introduction pipeline (126) and a waste gas combustion-supporting air introduction pipeline (127), the waste gas pipeline (123) comprises a first waste gas intake pipeline (1231) and a second waste gas intake pipeline (1232), and the peripheral component (12) is internally provided with a first gas collecting cavity (1211), a second gas collecting cavity (1212), a third gas collecting cavity (1213) and an avoiding cavity (1214) arranged in sequence along the air intake direction (101); the third gas collecting cavity (1213) is in communication with the waste gas combustion-supporting air pipeline (124), the waste gas pipeline (123) and the waste gas combustion-supporting air pipeline (124) extend along the air intake direction (101) to the avoiding cavity (1214) and to the incineration ends (120). The first exhaust gas introduction pipe (125) is in communication with the first gas collecting cavity (1211), and the first exhaust gas inlet pipe (1231) is in communication with the first gas collecting cavity (1211) and sequentially passes through the second gas collecting cavity (1212), the third gas collecting cavity (1213) and the avoiding cavity (1214) to the incineration end portion (120) along the air inlet direction (101); the exhaust gas combustion-supporting air pipe (124) is in communication with the third gas collecting cavity (1213) and passes through the avoiding cavity (1214) to the incineration end portion (120) along the air inlet direction (101); The second exhaust gas introduction pipe (126) is in communication with the second gas collecting cavity (1212), and the second exhaust gas inlet pipe (1232) is in communication with the second gas collecting cavity (1212) and sequentially passes through the third gas collecting cavity (1213) and the avoiding cavity (1214) to the incineration end portion (120) along the air inlet direction (101); the second exhaust gas inlet pipe (1232) is sleeved outside the first exhaust gas inlet pipe (1231), and the exhaust gas combustion-supporting air pipe (124) is sleeved outside the second exhaust gas inlet pipe (1232); The swirl vane group (129) is rotatably sleeved outside the second exhaust gas inlet pipe (1232), and the tip of the conical guide (128) is arranged towards the first exhaust gas inlet pipe (1231).

2. The waste heat value self-adaptive combined burner according to claim 1, characterized in that: The conical guide (128) comprises a conical portion (1280), the conical portion (1280) comprises a top end (1281) and a bottom end (1282) and a flow guide surface (1283) extending from the top end (1281) to the bottom end (1282), the outer diameter of the top end (1281) is smaller than the outer diameter of the bottom end (1282), and the flow guide surface (1283) is arranged in spaced manner with the exhaust gas pipe (123).

3. The waste heat value self-adapting combined burner according to claim 2, characterized in that: The conical guide (128) further comprises a protruding portion (1284) connected with the top end (1281), the protruding portion (1284) extends into the exhaust gas pipe (123) and is clamped with the exhaust gas pipe (123) through a clamping piece (1285), and the conical portion (1280) is arranged outside the exhaust gas pipe (123) in spaced manner.

4. The waste heat value self-adapting combined burner according to claim 2, characterized in that: The flow guide surface (1283) is arranged in inclined manner compared with the air inlet direction (101), and the included angle between the flow guide surface (1283) and the air inlet direction (101) ranges from 60° to 90°.

5. The waste heat value self-adapting combined burner according to claim 1, characterized in that: The swirl vane group (129) is rotatably sleeved outside the exhaust gas pipe (123) and located in the exhaust gas combustion-supporting air pipe (124), and the swirl angle of the swirl vane group (129) ranges from 30° to 60°.

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