A high-viscosity fuel stepwise mixing combustor with fully forced airflow guidance

Abstract

This invention discloses a high-viscosity fuel stepwise mixing burner with fully forced airflow guidance, comprising a burner shell, a fully covered forced airflow guidance structure disposed at the outlet end, including multiple swirl blades, with adjacent swirl blades arranged in a staggered, stacked manner to maintain airflow gaps, forming a fully covered arrangement on the outlet end cross-section; and an end-mixing structure including a radial fuel pipe disposed inside the swirl blades, the radial fuel pipe having several fuel injection holes facing the outlet end. This invention uses straight injection holes at the leading edge of the blades to fully mix the fuel with the air in the channel between the blades, forming a uniform and well-mixed gas mixture at the burner outlet. By increasing the angle of the swirl blades, the recirculation effect is enhanced, improving flame stability, and a stable premixed flame with a moderate maximum flame temperature can be formed in the furnace, improving combustion efficiency and reducing NOx emissions.

Description

Technical Field

[0001] This utility model relates to the field of incinerator burner technology, specifically to a high-viscosity fuel stepwise mixing burner with fully forced airflow guidance. Background Technology

[0002] In the field of industrial incineration, the burner is the core equipment, and its combustion efficiency, pollutant emission performance and fuel adaptability directly affect the economic operation and environmental compliance of the incineration system.

[0003] Existing technology application number: 202210530621.5 discloses an air-fuel dual-stage high-proportion hydrogen-blended ultra-low nitrogen burner, method, and boiler. It is equipped with a primary mixing fuel distribution chamber, which mixes fuel and combustion air in the premixing chamber through fuel diffusion holes. Essentially, this forms a mixing of fuel and combustion air within the burner. If the premixed gas reaches a combustible concentration within the shell, pre-ignition may occur due to high shell temperature or sparks, requiring higher safety standards; otherwise, there is a risk of backfire and explosion. Fluctuations in premixed gas flow rate or concentration can easily affect flame stability, potentially leading to flameout. Precise control of the premixing ratio is necessary to maintain the flame shape.

[0004] Furthermore, some burners have unreasonable swirl structure designs, which can easily lead to "short-circuiting" of the combustion air, such as the direct airflow not participating in the swirl in some areas. For example, a low-NOx gas burner disclosed in application number 202111209131.7, and a multi-stage swirl burner disclosed in application number 201910253680.0, both have swirl blade-like structures, but there is a portion between adjacent blades that allows the airflow diameter to be blown out, resulting in insufficient swirl intensity and weak recirculation effect. The underutilized airflow not only reduces mixing efficiency but also carries away furnace heat, increasing energy consumption. At the same time, due to poor flame stability, it is difficult to adapt to fluctuations in fuel load.

[0005] In addition, industrial incineration often involves high-viscosity fuels (such as chemical residues and oily waste), which have poor flowability and are difficult to atomize. The fuel passages of existing burners are prone to coking and blockage due to fuel retention, and after injection, they are difficult to mix effectively with the combustion air, resulting in unstable flames, a sharp drop in combustion efficiency, and the need for frequent shutdowns for cleaning, which seriously affects the continuous operation of the system.

[0006] For the reasons mentioned above, it is necessary to propose a high-viscosity fuel stepwise mixing burner with fully forced airflow guidance to solve the above problems. Utility Model Content

[0007] The purpose of this invention is to overcome the defects in the existing technology and provide a high-viscosity fuel stepwise mixing burner with fully forced airflow guidance.

[0008] To achieve the above objectives, the technical solution of this utility model is as follows:

[0009] A high-viscosity fuel stepwise mixing combustor with fully forced airflow guidance, comprising:

[0010] The burner shell is cylindrical, with a cylindrical cavity inside. Combustion air enters the cylindrical cavity from its inlet end and flows out from its outlet end.

[0011] A fully covered forced airflow guiding structure is set at the outlet end and includes multiple swirl blades. The connection ends of two adjacent swirl blades are arranged in a stacked and staggered manner to maintain the airflow gap layer. The stacked and staggered arrangement is set so that the close ends of two adjacent swirl blades form an overlapping area with an overlapping width in the axial direction view, and the multiple swirl blades form a fully covered arrangement on the cross section of the outlet end.

[0012] The end-mixing structure includes at least a radial fuel tube disposed inside the swirl blades, and the radial fuel tubes are arranged in the overlapping region. Each overlapping region has a radial fuel tube, and the radial fuel tubes have a plurality of fuel injection holes facing the outlet end, so that the fuel injected from the fuel injection holes mixes cross-flow with the combustion air guided out of the airflow gap layer.

[0013] It also includes a support plate that supports the central fuel pipe and the swirl blades. Multiple support plates are distributed around the central fuel pipe. The support plates are fixedly connected to the central fuel pipe. One front end of the support plate is fixedly connected to the swirl blades. The plane of the support plate is parallel to the central axis.

[0014] Furthermore, it also includes a fuel supply structure, which includes a central fuel pipe located on the internal axis of the burner housing. The front end of the central fuel pipe is connected to each swirl vane and is connected to each radial fuel pipe. A side feed pipe for fuel supply is connected to the side of the central fuel pipe and extends out from the side wall of the burner housing.

[0015] Furthermore, the central fuel pipe is divided into a front end pipe and a rear end pipe. The inner diameter of the rear end pipe is smaller than that of the front end pipe, and the inner diameter of the side feed pipe is the same as that of the rear end pipe.

[0016] Furthermore, the burner housing is provided with a necked tube section, which forms an annular concave cavity inside the burner housing. The annular concave cavity has a plurality of tangential nozzles arranged around the axis on the side wall facing the outlet end. The tangential nozzles are arranged along the tangential direction of the annular cavity, which guides the airflow in the tangential direction, and the tangential nozzles make the airflow entry direction form a first separation angle A with the axial direction. The annular concave cavity is connected to a guide tube outside the burner housing.

[0017] Furthermore, an adjusting cone is provided inside the burner housing along the axial direction, and the adjusting cone is located at the necked section and cooperates with it;

[0018] The adjusting cone is configured to be position-adjustable along the axial direction, and changing the position of the adjusting cone adjusts the airflow characteristics of the throat position of the constricted tube.

[0019] Furthermore, the fluid is guided out from the outlet end of the burner casing through the airflow gap layer between the swirl blades, and the direction of the fluid ejection from the airflow gap layer forms a second separation angle B with the axial direction.

[0020] Furthermore, the first separation angle is smaller than the second separation angle, and (1 / 2)B < A < B.

[0021] Furthermore, 65° < the second separation angle B < 85°.

[0022] The advantages and beneficial effects of this utility model are as follows: This utility model uses straight injection holes at the leading edge of the blades to fully mix the fuel with the air in the channel between the blades, forming a uniform and fully mixed gas at the burner outlet. By increasing the angle of the swirl blades, the recirculation effect is enhanced, and the flame stability is improved. A stable premixed flame with a moderate maximum flame temperature can be formed in the furnace, which improves the combustion efficiency and reduces NOx emissions.

[0023] This utility model proposes a novel burner structure with advantages such as simple structure, convenient processing, easy implementation, and low cost. Attached Figure Description

[0024] Figure 1 This is an isometric view of a high-viscosity fuel stepwise mixing burner with fully forced airflow guidance according to this utility model;

[0025] Figure 2 This is a front view of the outlet end of this utility model;

[0026] Figure 3 This is a schematic diagram of the longitudinal section of this utility model;

[0027] Figure 4 This is an exploded view of the present invention;

[0028] Figure 5 This is a schematic diagram of the constricted tube portion and the two separation angles of this utility model;

[0029] Figure 6 This is a schematic diagram showing the position of the adjusting cone of this utility model;

[0030] Figure 7 This is a perspective view of the lead screw adjustment mechanism of this utility model;

[0031] Figure 8This is an exploded view of the lead screw adjusting mechanism of this utility model;

[0032] In the diagram: 1. Burner shell; 2. Inlet end; 3. Outlet end; 4. Swirl blade; 5. Airflow gap layer; 6. Overlap width; 7. Radial fuel pipe; 8. Fuel nozzle; 9. Central fuel pipe; 10. Side feed pipe; 11. Front end pipe; 12. Rear end pipe; 13. Support plate; 14. Necked section; 15. Annular concave cavity; 16. Tangential nozzle; 17. Drain pipe; 18. Adjusting cone; A. First separation angle; B. Second separation angle; 21. Plug; 22. Guide support sleeve; 23. Drive screw; 24. Bevel gear set; 25. Drive shaft; 26. Servo motor; 27. Guide rail; 28. Partial thread; 29. ​​Screw adjustment mechanism. Detailed Implementation

[0033] The specific embodiments of this utility model will be further described below with reference to examples. These examples are only used to more clearly illustrate the technical solution of this utility model and should not be construed as limiting the scope of protection of this utility model.

[0034] Example 1:

[0035] Based on the existing ordinary oil burner, the fuel injection method is changed. The fuel flows out from the internal channel of the swirl blade 4 and is then injected at the edge of the swirl blade 4 to mix with the swirling air. The mixture is then burned in the furnace.

[0036] Specifically, it includes swirl vanes 4, fuel pipes, support plates 13, and burner housing 1. It uses a method of injecting fuel through the internal channels of swirl vanes 4 at the edge of swirl vanes 4 to mix with swirling air, thereby improving combustion efficiency and reducing emissions.

[0037] The swirl blades 4 are mainly used for the burner to form a backflow and mix the fuel. The arrangement of the swirl blades 4 makes the outlet end 3 form a fully covered forced airflow guiding structure. Specifically, the connecting ends of two adjacent swirl blades 4 are arranged in a stacked and staggered manner to maintain the airflow gap layer 5. The stacked and staggered arrangement is set so that the adjacent ends of two swirl blades 4 form an overlapping area with an overlap width 6 in the axial direction view. Multiple swirl blades 4 are arranged in a fully covered manner on the cross section of the outlet end 3. In this embodiment, four swirl blades 4 are provided. The swirl blades 4 are fan-shaped and arranged along the spiral path around the central fuel pipe 9, so that the edges of two adjacent swirl blades 4 are stacked and staggered to form an airflow gap layer 5. The combustion air entering from the inlet end 2 is guided by the swirl blades 4 and ejected from the airflow gap layer 5, so that the ejected mixed gas moves forward around the axis. Multiple swirl blades 4 are connected end to end in a staggered and overlapping manner to avoid the "short circuit" phenomenon of combustion air, so that all flowing gas participates in the swirl. When viewed from the axial direction, the outlet end 3 can be seen to be completely blocked by the swirl blades 4 to form a full-coverage arrangement. At the same time, the setting angle of the swirl blades 4 is increased (thus increasing the second separation angle B). This design can enhance the swirl intensity and recirculation effect, while improving the forced mixing capacity of fuel and combustion air, thereby effectively maintaining flame stability and preventing flameout.

[0038] When the burner is operating, the combustion air, guided by the swirl blades 4, forms a rotating airflow (swirl)—that is, the airflow moves along the burner's axial direction while also rotating around the axis. This rotating airflow, after exiting the burner outlet, diffuses outwards due to centrifugal force, resulting in a low-pressure zone in the center of the burner outlet. To fill this low-pressure zone, the high-temperature flue gas (combustion products) in the furnace flows in the opposite direction, returning from the furnace to the vicinity of the burner outlet (the area near the flame root), which is called recirculation. The larger the second separation angle B, the higher the airflow rotation intensity, the more pronounced the low-pressure zone at the outlet center, and the stronger the ability to attract high-temperature flue gas recirculation; conversely, if the second separation angle B is smaller, or even directly ejected, the airflow moves linearly along the axial direction, there is no low-pressure zone at the outlet center, and almost no recirculation occurs; in this embodiment, 65° < second separation angle B < 85°.

[0039] The fuel pipe includes a radial fuel pipe 7, a central fuel pipe 9, and a side feed pipe 10. The root of the swirl blade 4 is connected to the central fuel pipe 9. The outside of the swirl blade 4 can be connected to the burner housing 1 (or an outer ring fixing frame can be fixedly connected to the outer periphery of all swirl blades 4, and the outer ring fixing frame can be connected and fixed to the burner housing 1, so as to facilitate disassembly and maintenance).

[0040] The central fuel pipe 9 is located on the central axis of the burner and is composed of two nested pipe sections. The front pipe 11 is thicker, and its inner diameter is the same as the outer diameter of the rear pipe 12. The rear pipe 12 is nested into the front pipe 11 to form an integral central pipe. The head of the front pipe 11 is connected to the swirl vane 4 and communicates with the internal fuel channel opened inside the corresponding swirl vane 4. The head of the front pipe 11 has holes with the same cross-sectional shape, size, channel direction, and even distribution as the radial fuel pipe 7 inside the corresponding swirl vane 4, thereby reducing flow resistance. The rear pipe 12 is connected to the side feed pipe 10 at a certain position, and its diameter is the same as that of the rear pipe 12. A plug 21 is set at the end of the rear pipe 12 to facilitate the processing of the central fuel pipe 9. The side feed pipe 10 passes through the shell and communicates with the central fuel pipe 9. The outer end of the side feed pipe 10 is provided with a flange connection structure at a certain distance from the burner shell 1 for connecting to the flange of the external fuel supply system outlet. Fuel enters the side feed pipe 10 through the supply system and enters the radial fuel pipe 7 inside the swirl blade 4 through the central fuel pipe 9.

[0041] A hollow structure is formed inside the swirl outlet side of the swirl blade 4, forming a radial fuel pipe 7. The radial fuel pipe 7 is connected to the circumferential fuel holes on the central fuel pipe 9. A row of fuel nozzles 8 is evenly distributed along the radial fuel pipe 7 of the swirl blade 4. The radial fuel pipes 7 are arranged in each overlapping area, and each overlapping area has a radial fuel pipe 7. The fuel nozzles 8 are arranged on the outer surface of the swirl blade 4, so that the fuel is injected outward. The injected fuel can collide with the outer swirl blade 4 to form dispersion, and the fuel is vertically and crosswise mixed with the combustion air passing through the channel of the swirl blade 4, which improves the fuel mixing degree and forms a uniform mixture at the burner outlet. That is, the fuel is injected into the airflow gap layer 5 between the swirl blades 4 and mixed with the combustion air.

[0042] The support plate 13 is used to support the fuel pipeline and the cyclone separator, and to rectify the combustion air. The support plate 13 is arranged circumferentially along the fuel pipeline, installed radially as a whole, and placed in the direction of the combustion air. The front end is close to the cyclone blade 4 and connected to the fuel pipeline through a reinforced sleeve to improve structural strength.

[0043] A heating wire and temperature sensor are installed in the fuel pipeline to maintain the fluidity of high-viscosity fuel by heating the fuel pipeline. Specifically, a nickel-chromium alloy heating wire is embedded inside the swirl vanes, and the temperature sensor monitors the channel temperature in real time (set range 120-200℃) to ensure that the high-viscosity fuel maintains its fluidity. A heat insulation layer is installed between the heating wire and the burner housing to prevent heat transfer to the combustion air. This structure is particularly suitable for restarting the incinerator after start-up or a short shutdown, as the heating wire can maintain the temperature of the fuel pipeline and prevent the high-viscosity fuel from clogging the pipeline after cooling.

[0044] Example 2:

[0045] This embodiment adds a Venturi-type necking structure and a tangential nozzle 16 drainage design to the previous embodiment.

[0046] Specifically, a constricted tube section 14 is provided in a certain section of the burner shell 1 at the front end of the plug 21, forming a Venturi tube structure and creating a Venturi effect. When the airflow passes through the constricted section, the flow velocity increases and the pressure decreases. Auxiliary gas, such as secondary combustion air, inert gas, or reducing gas, can be drawn in through the external drainage pipe 17. An annular concave cavity 15 is formed within the constricted tube portion 14. Several tangential nozzles 16 are opened on its side wall facing the burner outlet end 3, so that the guiding gas is injected into the burner housing 1 along the tangential direction at a first separation angle A. This causes the guiding gas to form a circumferential motion within the burner housing 1, which forms a rotational mixing with the main combustion air and drives the main combustion air to rotate synchronously. It forms an initial rotation within the burner housing 1, and then passes through the swirl vanes 4 for further rotational guidance, thereby enhancing the rotational effect of the fluid at the outlet end 3. It can be understood that the tangential nozzles 16 and the swirl vanes 4 guide the fluid in the same direction of rotation. The difference lies in the difference in the guidance angle between the two. Specifically, the fluid (main combustion air and fuel mixture) ejected from the airflow gap layer 5 between the swirl vanes 4 forms a second separation angle B with the axis, and is designed to be (1 / 2)B<A<B. This angular relationship ensures that the tangentially injected guiding gas can enhance the swirling intensity of the main airflow through rotational kinetic energy, while avoiding airflow collision due to excessive angle, thus achieving a synergistic effect of "supplementary mixing + enhanced swirling".

[0047] In actual use, the gas introduced by the drainage pipe 17 can be the same gas as the combustion air entering from the inlet end 2, or it can be a different gas. Users can switch and select according to their needs.

[0048] The guiding gas from the tangential nozzle 16 is injected at angle A, creating a gradient difference with the mixed gas flow at outlet 3 at angle B. This "rotational superposition" enhances the overall swirling intensity, shortening the fuel-gas mixing time by 20%-30%, improving mixing uniformity by over 15%, and reducing localized high temperatures and pollutant emissions. When processing high-viscosity fuels, high-temperature preheated air can be introduced through the guiding pipe 17 (to improve atomization). When NOx emissions need to be reduced, inert gases (such as flue gas recirculation) can be introduced. By dynamically optimizing the mixing ratio through adjusting the cone 18, the burner can adapt to a wider fuel viscosity range of 100-1500 cSt.

[0049] Example 3:

[0050] This embodiment adds an adjustment cone 18 to the design of the necked tube 14, based on the second embodiment, to construct a composite airflow control system of "graded flow guidance - dynamic adjustment - directional mixing".

[0051] Specifically, an adjusting cone 18 is provided inside the burner housing 1 along the axial direction. The adjusting cone 18 is located at the position of the constricted tube section 14 and cooperates with it. The adjusting cone 18 is configured to be adjustable along the axial direction. Changing the position of the adjusting cone 18 adjusts the airflow characteristics of the throat position of the constricted tube section 14.

[0052] The adjusting cone 18 is located inside the constricted section 14 along the burner axis. Its axial position is adjusted via a drive mechanism, allowing it to move to the front, middle, or rear positions of the constricted section 14. Its core function is to change the flow cross-section at the constriction: when the cone is near the front end of the constriction, the throat cross-section increases; when the cone is near the rear end of the constriction, the throat cross-section decreases, thereby dynamically controlling the mixing ratio and flow rate of the main combustion air and the guide gas.

[0053] By drawing in the priming gas through the Venturi effect, and in conjunction with the adjustment of the throat section by the regulating cone 18, the ratio of main combustion air to priming gas can be flexibly controlled, solving the problem of fixed gas ratios in traditional burners that are difficult to adapt to fluctuations in fuel composition. The Venturi-type necking structure utilizes the kinetic energy of the airflow itself to draw in the priming gas, eliminating the need for additional pressurization equipment and reducing energy consumption. The regulating cone 18 adopts a mechanical adjustment method, with a fast response speed (adjustment time < 5s) and compatibility with the original shell structure, requiring no major modifications.

[0054] Specific examples:

[0055] Taking the incinerator burner for treating high-viscosity chemical residues (viscosity 800 cSt) as an example, the specific parameters are as follows: the second separation angle BB of the swirl blade 4 is 80°, the first separation angle AA of the tangential nozzle 16 is 50°; the guide pipe 17 introduces secondary combustion air (oxygen content 25%) preheated to 300°C to improve the atomization effect.

[0056] Operating Condition 1: High-load incineration (100% processing capacity)

[0057] The regulating cone 18 is located at the front of the constricted tube section 14, with the largest throat cross-section (diameter 80mm). The main combustion air velocity is 15m / s, and the intake of the induced gas is 15% of the main airflow. At this point, the main combustion air is sufficient, and combined with the enhanced swirl of the induced gas from the 50° tangential nozzle 16, fuel atomization is complete, the combustion efficiency reaches 99.2%, and the NOx emission concentration is 300mg / m³. 3 .

[0058] Operating Condition 2: Conventional Load Incineration (70% Processing Capacity)

[0059] The regulating cone 18 is located in the middle of the constricted tube section 14, with a medium throat cross-section (diameter 60mm). The main combustion air velocity is 20m / s, and the intake gas volume is 35% of the main airflow. The balanced mixing ratio improves flame stability, with fluctuation range <±3%, making it suitable for continuous and stable operation.

[0060] Operating Condition 3: Low load + low NOx requirement (40% throughput)

[0061] The regulating cone 18 is located at the rear of the constricted tube section 14, with the smallest throat cross-section (40mm diameter). The main combustion air velocity is 25m / s, and the intake gas volume is 55% of the main airflow (partially replaced by flue gas recirculation gas with an oxygen content of 18%). The low-oxygen environment suppresses the formation of thermal NOx, reducing the emission concentration to 180mg / m³. 3 At the same time, a high diversion ratio prevents the flame from going out under low load.

[0062] This improvement, through the synergistic design of the Venturi structure and the regulating cone 18, breaks through the limitation of fixed gas mixing ratio in traditional burners, achieving the function of "on-demand adjustment and directional mixing," especially enhancing the adaptability to high-viscosity fuels and the ability to control pollutant emissions. The combination of angle matching design and dynamic control mechanism enables the burner to maintain efficient and stable operation over a wide load range, demonstrating significant engineering application value.

[0063] In this embodiment, axial position adjustment can be achieved through a drive mechanism. Specifically, the drive mechanism in this embodiment is a screw adjustment mechanism 29, which includes a screw adjustment mechanism 29 arranged at the end of the plug 21 and along the axis. The screw adjustment mechanism 29 includes a guide support sleeve 22, a drive screw 23, a bevel gear set 24, a drive shaft 25, and a servo motor 26. The guide support sleeve 22 is fixedly connected to the central fuel pipe 9. The drive screw 23 is rotatably arranged inside the guide support sleeve 22. The guide support sleeve 22 is provided with a long strip-shaped guide rail 27, which passes through the side wall of the guide support sleeve 22. The adjustment cone 18 is slidably connected to the outside of the guide support sleeve 22. The adjustment cone 18 is provided with a partial thread 28 that passes through the guide rail 27 and is threadedly connected to the drive screw 23. The drive screw 23 is connected to the drive shaft 25 inside the plug 21 through the bevel gear set 24. The other end of the bevel gear set 24 passes through the burner housing 1 and is connected to the output end of the servo motor 26.

[0064] The above description is only a preferred embodiment of the present utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present utility model, and these improvements and modifications should also be considered within the protection scope of the present utility model.

Claims

1. A high viscosity fuel step-mix combustor with full forced air flow guidance, characterized by, include: The burner shell is cylindrical, with a cylindrical cavity inside. Combustion air enters the cylindrical cavity from its inlet end and flows out from its outlet end. A fully covered forced airflow guiding structure is set at the outlet end and includes multiple swirl blades. The connection ends of two adjacent swirl blades are arranged in a stacked and staggered manner to maintain the airflow gap layer. The stacked and staggered arrangement is set so that the close ends of two adjacent swirl blades form an overlapping area with an overlapping width in the axial direction view, and the multiple swirl blades form a fully covered arrangement on the cross section of the outlet end. The end-mixing structure includes at least a radial fuel tube disposed inside the swirl blade, and the radial fuel tube is arranged in the overlapping area. The radial fuel tube is provided with a plurality of fuel injection holes facing the outlet end, so that the fuel injected from the fuel injection holes is mixed with the combustion air guided out of the airflow gap layer in a cross-flow manner. Multiple radial fuel tubes are simultaneously connected to the end of the central fuel tube and arranged radially from the center. It also includes a support plate that supports the central fuel pipe and the swirl blades. Multiple support plates are distributed around the central fuel pipe. The support plates are fixedly connected to the central fuel pipe. One front end of the support plate is fixedly connected to the swirl blades. The plane of the support plate is parallel to the central axis. A heating wire and a temperature sensor are installed on the fuel line to maintain the fluidity of high-viscosity fuel by heating the fuel line.

2. A high viscosity fuel staged combustion combustor with full forced air flow guidance according to claim 1, wherein, It also includes a fuel supply structure, which includes a central fuel pipe located on the internal axis of the burner housing. The front end of the central fuel pipe is connected to each swirl vane and the front end of the central fuel pipe is connected to each radial fuel pipe. A side feed pipe for fuel supply is connected to the side of the central fuel pipe and extends out from the side wall of the burner housing.

3. A high viscosity fuel staged combustion combustor with full forced air flow guidance according to claim 2, wherein, The central fuel pipe is divided into a front pipe and a rear pipe. The inner diameter of the rear pipe is smaller than that of the front pipe, and the inner diameter of the side feed pipe is the same as that of the rear pipe.

4. The high viscosity fuel staged combustion combustor of claim 1, wherein, The burner housing is provided with a necked tube section, which forms an annular concave cavity inside the burner housing. The annular concave cavity has a plurality of tangential nozzles arranged around the axis on the side wall facing the outlet end. The tangential nozzles are arranged along the tangential direction of the annular cavity, which guides the airflow in the tangential direction, and the tangential nozzles make the airflow entry direction form a first separation angle A with the axial direction. The annular concave cavity is connected to a guide tube outside the burner housing.

5. A high viscosity fuel staged combustion combustor with full forced air flow guidance according to claim 4, wherein, An adjusting cone is provided inside the burner housing along the axial direction. The adjusting cone is located at the necked section and cooperates with it. The adjusting cone is configured to be position-adjustable along the axial direction, and changing the position of the adjusting cone adjusts the airflow characteristics of the throat position of the constricted tube.

6. A high viscosity fuel staged combustion combustor with full forced air flow guidance according to claim 4, wherein, The fluid is guided out from the outlet end of the burner shell through the airflow gap layer between the swirl blades, and the direction of the fluid ejection from the airflow gap layer forms a second separation angle B with the axial direction.

7. A high viscosity fuel staged combustion combustor with full forced air flow guidance according to claim 6, wherein, The first separation angle is smaller than the second separation angle, and (1 / 2)B < A < B.

8. A high viscosity fuel staged combustion combustor with full forced air flow guidance according to claim 6, wherein, 65° < second separation angle B < 85°.

9. A high viscosity fuel staged combustion combustor with full forced air flow guidance according to claim 5, wherein, The position of the adjusting cone is controlled by a screw adjustment mechanism, which includes a guide support sleeve, a drive screw, a bevel gear set, a drive shaft, and a servo motor. The guide support sleeve is fixedly connected to the central fuel pipe. The drive screw is rotatably installed inside the guide support sleeve. The guide support sleeve has a long strip-shaped guide rail that runs through the side wall of the guide support sleeve. The adjusting cone is slidably connected to the outside of the guide support sleeve. The adjusting cone has a partial thread that passes through the guide rail and is threaded to the drive screw. The drive screw is connected to the drive shaft through a bevel gear set inside a plug. The other end of the bevel gear set passes through the burner housing and is connected to the output end of the servo motor.

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