Pure hydrogen micro-mixing combustor with special throat

Abstract

The application provides a pure hydrogen micro-mixing combustor with a special throat, and belongs to the field of micro-mixing combustors. The application solves the problems of uneven air intake, insufficient mixing of fuel and air, poor combustion stability and poor cooling effect of the existing pure hydrogen micro-mixing combustor. The application comprises a micro-mixing combustor cylinder, which is provided with a windward surface and a leeward surface along the air inlet direction; a plurality of micro-mixing units are arranged, and the two ends of the micro-mixing units are connected with the windward surface and the leeward surface, respectively; wherein, a partition plate is arranged in the micro-mixing combustor cylinder, and the partition plate divides the cavity formed by the micro-mixing combustor cylinder and the plurality of micro-mixing units.

Description

Technical Field

[0001] This invention belongs to the field of micro-mixed burners, and in particular relates to a pure hydrogen micro-mixed burner with a special throat. Background Technology

[0002] Driven by global "dual carbon" goals, green and low-carbon low-emission combustion technologies have become a core development direction in the energy and industrial sectors. Hydrogen fuel, with its combustion products consisting only of water and no carbon oxide emissions, is considered a key clean energy source to replace traditional fossil fuels. Micro-mixing combustion technology, with its advantages of uniform gas-fuel mixing and high combustion efficiency, has become an important technological path adapted to hydrogen fuel, and is widely used in industrial boilers, gas turbines, and fuel cell heating equipment. However, current micro-mixing burners for pure hydrogen fuel still face multiple technical bottlenecks in practical applications, making it difficult to meet the requirements for high efficiency, stability, and low emissions.

[0003] First, uneven air intake is a significant problem. Traditional micro-hybrid burners often employ a planar design for their windward side. As air flows through, boundary layer separation can easily create localized vortices or velocity differences. Micro-hybrid units near the edge of the burner are prone to excessive air intake, while units in the central area may experience insufficient air intake, resulting in significant variations in air supply to different micro-hybrid units. This air intake imbalance directly affects the basis of subsequent fuel-air mixing, creating a potential for combustion instability. Furthermore, while some burners attempt to optimize their windward side shape, they fail to integrate this with the array layout of the micro-hybrid units, thus failing to achieve uniform air coverage across the entire area.

[0004] Secondly, the problem of insufficient fuel-air mixing is widespread. The molecular diffusion coefficient of hydrogen fuel is much higher than that of conventional natural gas (approximately 3.8 times that of methane). If the turbulence intensity is insufficient during mixing, "local fuel-rich" or "local fuel-lean" phenomena are likely to occur: fuel-rich areas lead to incomplete combustion, wasting energy and potentially generating localized high temperatures; fuel-lean areas, due to excessively low fuel concentration, result in large fluctuations in the heat released during combustion. Traditional micro-mixing units mostly adopt a straight-tube structure with no special design at the throat. The airflow is mainly laminar, with a turbulence intensity of only 0.1 to 0.2. The momentum exchange between air and fuel is weak, resulting in poor mixing uniformity. Ultimately, this leads to a difference of more than 8% in the equivalence ratio of the mixture at the outlet of different micro-mixing units, seriously affecting combustion consistency.

[0005] Furthermore, the unique challenges posed by the characteristics of hydrogen fuel urgently need to be addressed. On the one hand, hydrogen burns extremely quickly (about three times faster than methane, reaching 2.8 m / s), which can easily cause thermoacoustic oscillations under lean combustion conditions—pressure and temperature fluctuate periodically during combustion, with amplitudes reaching hundreds of Pascals. This can not only lead to flameout and severe equipment vibration, but also potentially cause ablation at the tail end of the micro-hybrid unit. On the other hand, hydrogen has a high risk of backfire. The cooling structure of traditional micro-hybrid burners is mostly a simple airflow chamber, and the cooling airflow cannot accurately cover the tail end and leeward side of the micro-hybrid unit. The local temperature can easily exceed the ignition temperature of hydrogen, causing the flame to enter the micro-hybrid unit in reverse, burning the unit structure and shortening the equipment's service life.

[0006] Furthermore, balancing low emissions with adaptability to different operating conditions is difficult. Although hydrogen combustion produces no carbon, NOx is still generated at high temperatures (mainly from the oxidation of nitrogen in the air at high temperatures). Traditional micro-hybrid burners often control combustion temperature by reducing the mixture concentration to achieve lean combustion and low emissions, but this further exacerbates thermoacoustic oscillations and easily leads to insufficient flame stability under low load conditions. Some burners attempt to adopt a staged fuel supply design, but unreasonable fuel distribution ratios and airflow organization between the main combustion stage and the shift stage result in the shift stage being unable to stabilize the flame at low loads and uneven mixing in the main combustion stage at high loads. The operating condition adaptability range can only cover 30% to 80%, which is insufficient to meet the needs of frequent load fluctuations in practical applications.

[0007] In summary, existing pure hydrogen micro-hybrid burners suffer from technical deficiencies in areas such as intake uniformity, adequate mixing, hydrogen fuel compatibility, and the balance between low emissions and stability, which hinder the efficient application of hydrogen fuel. Therefore, developing a high-efficiency micro-hybrid burner that can solve these problems and is compatible with pure hydrogen fuel has become a key requirement for promoting the development of low-emission combustion technologies. Summary of the Invention

[0008] In view of this, the present invention aims to propose a pure hydrogen micro-hybrid burner with a special throat, which solves the problems of uneven air intake, insufficient mixing of fuel and air, poor combustion stability and poor cooling effect of existing pure hydrogen micro-hybrid burners.

[0009] To achieve the above objectives, the present invention adopts the following technical solution to provide a pure hydrogen micro-mixing burner with a special throat, comprising: The micro-hybrid burner cylinder has a windward side and a leeward side along the air inlet direction; The micro-mixing unit is provided in multiple units, with its two ends connected to the windward side and the leeward side, respectively. The micro-mixer burner cylinder is equipped with a baffle plate inside, which divides the cavity consisting of the micro-mixer burner cylinder and multiple micro-mixing units into a fuel cavity and a cooling air cavity. The fuel conduit is connected to the fuel cavity.

[0010] Furthermore, the micro-mixing unit has a tubular structure with a radially constricted throat, including an air inlet connected to the windward side and a mixed gas outlet connected to the leeward side; the throat is provided with a fuel inlet.

[0011] Furthermore, the windward surface is conical.

[0012] Furthermore, the top of the cone is connected to one end of the inner cylinder wall, and the other end of the inner cylinder wall passes through the partition and is connected to the leeward side. The fuel conduit is inserted into the inner cylinder wall and communicates with the fuel chamber through the fuel pipe connection hole provided on the inner cylinder wall.

[0013] Furthermore, the inner cylinder wall has a venturi tube structure at the end closest to the leeward side.

[0014] Furthermore, the fuel pipe connection hole is provided with an annular baffle on one side of the fuel chamber.

[0015] Furthermore, an airflow channel is provided between the fuel conduit and the inner cylinder wall, which is used to guide air from the windward side to the leeward side.

[0016] Furthermore, swirl vanes are provided between the fuel conduit and the inner cylinder wall.

[0017] Furthermore, the fuel conduit has a double-layer structure, with the inner layer supplying duty fuel and the outer layer supplying main fuel. The outer layer is connected to the fuel pipe connection hole through a fuel pipe provided on the outer wall of the fuel conduit.

[0018] Furthermore, the lower end of the outer wall of the micro-mixer burner cylinder has a cooling air inlet connected to a cooling air cavity, and a cooling air outlet is located on the leeward side.

[0019] The present invention has the following beneficial effects: 1. Significantly Improved Air Intake Uniformity: Traditional micro-hybrid burners often employ a planar windward structure. When air flows through this structure, boundary layer separation can easily create local dead zones or velocity differences, leading to excessive air intake in some micro-hybrid units and insufficient air intake in others, directly affecting the subsequent blending quality. This invention designs the windward surface as a conical structure that can convex or concave. The generatrix of the cone forms a specific angle with the horizontal plane, guiding air along the cone surface in a "gradient split" state—the airflow diffuses uniformly from the edge of the cone towards the center, covering the air inlets of all micro-hybrid units in the micro-hybrid cluster, avoiding localized airflow congestion or gaps. Simultaneously, the conical structure expands the effective cross-sectional area for airflow, reducing airflow resistance and ensuring that the airflow deviation entering each layer of micro-hybrid units is controlled within a small limit, laying a stable intake foundation for the uniform blending of fuel and air.

[0020] 2. Sufficient and uniform mixing of fuel and air: Insufficient mixing is a major drawback of traditional hydrogen micro-mixing burners, mainly due to poor fuel injection dispersion and insufficient airflow turbulence intensity. This invention solves this problem through "dual-structure synergy." On the one hand, the micro-mixing unit adopts a tubular design with a concave throat. The concave area generates strong vortices in the flowing air, significantly increasing the turbulence intensity compared to traditional straight-tube micro-mixing units, thereby greatly increasing the contact area and momentum exchange frequency between air and fuel. On the other hand, the baffle plate on the outer side of the inner cylinder wall intercepts the high-pressure fuel ejected from the fuel pipe. Through a "deceleration-diffusion-uniform distribution" process, the fuel is transformed from a "direct jet" into a "area diffusion flow," uniformly covering the fuel inlet of the micro-mixing unit and avoiding excessive or insufficient fuel in a single micro-mixing unit.

[0021] 3. Strong combustion stability and suppression of thermoacoustic oscillations: During lean combustion of hydrogen fuel, the low fuel concentration and large fluctuations in heat release during combustion easily lead to thermoacoustic oscillations, which can severely cause flameout or equipment vibration damage. This invention enhances combustion stability through a "dual recirculation mechanism": First, the Venturi tube structure at the lower end of the inner cylinder wall utilizes the "contraction-expansion" flow channel characteristics to reduce the outlet air pressure, creating a pressure gradient between the high-temperature region of the combustion chamber and the outlet of the micro-mixing unit, naturally forming an "internal recirculation zone." This recirculates the high-temperature gas after combustion back to the initial combustion zone, providing a continuous heat source for the newly entering mixture and preventing "cold start" flameout. Second, the swirl vanes between the outer wall of the fuel duct and the inner cylinder wall generate a rotating airflow for the combustion process, forming an "external recirculation zone," further stabilizing the flame shape. The synergistic effect of the dual recirculation zones significantly reduces the amplitude of thermoacoustic oscillations.

[0022] 4. Achieving Zero-Carbon and Low-NOx Emission Combustion: Nitrogen oxides are the main pollutants in combustion equipment, and their generation is positively correlated with the peak combustion temperature. This invention achieves low-emission combustion through staged combustion and low-peak temperature control: First, it employs centrally staged combustion technology, where the standby fuel undergoes gentle combustion in the recirculation zone, while the main combustion fuel achieves complete combustion in subsequent zones, avoiding localized high temperatures caused by concentrated fuel combustion; second, the rotating airflow formed by the swirl blades ensures more uniform mixing of fuel and air, resulting in a more complete combustion reaction and reducing the formation of localized oxygen-rich high-temperature zones. Simultaneously, hydrogen itself is a clean energy source, and the combustion product is only water, with no carbon oxide emissions.

[0023] 5. Wide adaptability and high combustion efficiency: Traditional micro-hybrid burners have a fixed structure and can only adapt to a single operating condition, resulting in strong limitations. This invention improves versatility through "flexible design + intelligent adaptation": Structurally, the micro-hybrid units in the micro-hybrid cluster can adopt different array patterns to adapt to combustion chambers of different sizes; in terms of fuel control, the fuel ratio between the main combustion stage and the shift stage can be flexibly adjusted through flow regulating valves to meet the stable combustion requirements under different loads. In addition, uniform mixing and stable combustion patterns can improve the combustion efficiency of hydrogen, reduce fuel waste, and lower operating costs, making it widely applicable in industrial boilers, gas turbines, fuel cell heating equipment, and other scenarios. Attached Figure Description

[0024] Figure 1 This is a front cross-sectional view of a pure hydrogen micro-mixed burner with a special throat. Figure 2 This is a structural diagram of a pure hydrogen micro-mixed burner with a special throat. Figure 3 It is the cylinder of a pure hydrogen micro-mixed burner with a special throat; Figure 4 This is a structural diagram of a micro-mixing unit in a pure hydrogen micro-mixing burner with a special throat. Figure 5 It is a fuel system and duty structure for a pure hydrogen micro-mixed burner with a special throat and a pure hydrogen micro-mixed burner siphon pipe; Figure 6 yes Figure 5 Enlarged view of section A in the middle; Figure 7 It is a fuel system and cylinder of a pure hydrogen micro-mixed combustor cyclone with a special throat; Figure 8 This is a diagram showing the distribution of cooling holes in a pure hydrogen micro-mixed burner with a special throat. Figure 9 Overall structural diagram of a pure hydrogen micro-mixer burner with a special throat. Figure 10 This is a cross-sectional view of the annular combustion chamber where this micro-hybrid burner is installed.

[0025] In the diagram: 1. Micro-mixer burner shell, 1-1 windward side, 1-2 inner shell wall, 1-3 outer shell wall, 1-4 cooling air inlet, 1-5 cooling air outlet, 1-6 micro-mixing unit connection hole, 1-7 fuel chamber, 1-8 baffle, 1-9 cooling air chamber, 1-10 baffle, 1-11 leeward side, 1-12 venturi structure; 2. Micro-mixer cluster, 2-1 micro-mixing unit, 2-2 air inlet, 2-3 fuel inlet, 2-4 mixed gas outlet; 3. Fuel duct, 3-1 fuel duct inner wall, 3-2 fuel duct outer wall, 3-3 main combustion stage fuel inlet, 3-4 shift fuel inlet, 3-5 fuel pipe, 3-6 swirl vane, 3-7 shift fuel outlet. Detailed Implementation

[0026] Referring to the accompanying drawings, this embodiment provides a pure hydrogen micro-mixing burner with a special throat, comprising: a micro-mixing burner body 1, a micro-mixing cluster 2, and a fuel conduit 3. The micro-mixing units 2-1 in the micro-mixing cluster 2 are connected to the micro-mixing burner body 1 via micro-mixing unit connection holes 1-6 located on the windward side 1-1, the leeward side 1-11, and the baffle 1-10. The fuel conduit 3 is connected to the micro-mixing burner body 1 via a fuel pipe 3-5 and swirl vanes 3-6.

[0027] The micro-mixer burner body 1 is composed of an air-facing surface 1-1, an inner cylinder wall 1-2, an outer cylinder wall 1-3, a leeward surface 1-11, and a baffle plate 1-10. The air-facing surface 1-1 is at an angle to the horizontal plane and is a cone. This cone can protrude outward or be recessed inward to ensure the uniformity of air intake. Micro-mixing unit connection holes 1-6 are opened on the air-facing surface 1-1, the leeward surface 1-11, and the baffle plate 1-10 for connecting with the micro-mixing unit 2-1. A fuel pipe connection hole 1-13 is opened on the inner cylinder wall 1-2, which connects to the fuel pipe 3-5. Near the fuel pipe connection hole 1-13 on the outer side of the inner cylinder wall 1-2, a baffle plate 1-8 is connected. The baffle plate 1-8 can block the fuel ejected from the fuel pipe, slowing down and reducing pressure, thus allowing the fuel to enter the micro-mixing unit 2-1 evenly from the fuel inlet 2-3 on the micro-mixing unit 2-1. A protrusion at the lower end of the inner cylinder wall 1-2 forms a Venturi structure 1-12, which can reduce the pressure of the outlet air, thus making it easier to form a recirculation zone. A cooling air inlet 1-4 is opened at the lower end of the outer cylinder wall 1-3. A cooling air outlet 1-5 is opened on the leeward side 1-11, allowing air to enter the cooling air cavity and exit from the leeward side, thus cooling the leeward side and preventing backfire of the jet flame in the micro-mixing unit. A baffle plate 1-10 divides the cylinder into two chambers: the upper part is the fuel chamber 1-7, and the lower part is the cooling air chamber 1-9.

[0028] The micro-mixing cluster 2 is composed of micro-mixing units 2-1 arrayed together, and different array configurations can be selected to meet the needs of different situations. Because the windward side 1-1 is a cone, the lengths of the micro-mixing units 2-1 in different layers are different. The micro-mixing unit 2-1 is a tubular structure with a concave throat. This design can greatly increase the turbulence in the throat, making the momentum exchange between air and fuel more intense, thereby improving the uniformity of mixing. Its head is the air inlet 2-2, which has a certain slope due to the windward side, and the tail is the mixed gas outlet 2-4. There are four fuel inlets 2-3 arrayed around the central position of the concave throat.

[0029] The fuel conduit 3 consists of an inner wall 3-1 and an outer wall 3-2. The head of the inner wall 3-1 forms a standby fuel inlet 3-4, while the annular channel between the inner and outer walls forms the main combustion stage fuel inlet 3-3. The tail of the outer wall 3-2 forms a frustum-shaped seal with an opening on its surface connecting to the fuel pipe 3-5. An opening at the head of the frustum forms a standby fuel outlet 3-7. Below the fuel pipe 3-5, an annular channel is formed between the outer wall 3-2 and the inner wall 1-2, allowing air to enter. This air is the air required for standby combustion. Simultaneously, swirl vanes 3-6 are present inside the channel, creating a recirculation zone at the bottom of the standby area. Studies have shown that this recirculation zone helps reduce NOx emissions.

[0030] Example According to the appendix Figure 1 , 2 As shown in Figure 3, the windward side 1-1, inner wall 1-2, outer wall 1-3, leeward side 1-11, and baffle 1-10 of the micro-mixer burner cylinder 1 are assembled into a whole, ensuring that the baffle 1-10 accurately separates the upper fuel chamber 1-7 and the lower cooling air chamber 1-9, and the lower end of the inner wall 1-2 protrudes to form a Venturi structure 1-12; the micro-mixing units 2-1 are fixed in a circular array through the micro-mixing unit connection holes 1-6 on the windward side 1-1, leeward side 1-11, and baffle 1-10, so that the slope of the air inlet 2-2 of the micro-mixing unit matches the cone angle of the windward side 1-1, and the mixed gas outlet 2-4 faces the combustion area; according to the appendix Figure 5 , 6 Connect the fuel pipe 3-5 of the fuel conduit 3 to the fuel pipe connection hole 1-13 of the inner cylinder wall 1-2. Fix the outer wall 3-2 of the fuel conduit to the inner cylinder wall 1-2 by the swirl vane 3-6, and install the baffle 1-8 on the outside of the fuel pipe connection hole 1-13. Finally, confirm that there is no blockage between the cooling air inlet 1-4 at the lower end of the outer cylinder wall 1-3 and the cooling air outlet 1-5 on the leeward side 1-11, so as to ensure that the air, fuel and cooling system form a complete passage. Based on the burner's design power requirements, determine the number of array layers and the number of units per layer for the micro-mixing unit 2-1; accordingly, adjust the number of fuel pipes 3-5 so that each micro-mixing unit layer is matched with one set of fuel pipes. The fuel pipes 3-5 are evenly distributed circumferentially along the inner cylinder wall 1-2 and connect with the fuel pipe connection holes 1-13, ensuring that the fuel injected from each set of fuel pipes, after being decelerated by the baffle 1-8, can evenly cover the fuel inlet 2-3 of the corresponding micro-mixing unit layer. During this process, maintain the throat recessed structure of the micro-mixing unit 2-1, the slope of the air inlet 2-2, and the array pattern of the four fuel inlets 2-3, and the attached... Figure 1 Or 2 is the same.

[0031] According to the appendix Figure 3 , 7The cooling air chamber 1-9 shown allows cooling air to enter the chamber from the cooling air inlet 1-4 at the lower end of the outer cylinder wall 1-3, and flow naturally over the outer side of the inner cylinder wall 1-2, the inner side of the outer cylinder wall 1-3, and the lower surface of the partition 1-10. During this process, the airflow is guided by the physical space of the chamber, and finally discharged from the cooling air outlet 1-5 distributed around the leeward side 1-11. This process dissipates heat from the leeward side 1-11, the tail of the micro-mixing unit 2-1, and the cylinder wall, preventing local overheating that could lead to flame backfire or equipment damage.

[0032] According to the appendix Figure 5 , 6 The structure of fuel conduit 3 shown in section 7 supplies standby fuel through standby fuel inlet 3-4 at the head of the inner wall 3-1 of the fuel conduit, and main combustion stage fuel through the annular channel between the inner wall 3-1 and the outer wall 3-2 of the fuel conduit and the main combustion stage fuel inlet 3-3; the main combustion stage fuel enters the fuel pipe 3-5 through the opening on the outer wall 3-2 of the fuel conduit, and then enters the fuel inlet 2-3 of the micro-mixing unit 2-1 after being decelerated and diffused by the baffle 1-8 through the connection hole 1-13 of the fuel pipe 3-5 and the inner cylinder wall 1-2; the standby fuel is directly sprayed out from the standby fuel outlet 3-7 at the head of the frustum at the tail of the outer wall 3-2 of the fuel conduit, meeting the fuel requirements of different combustion stages.

[0033] According to the appendix Figure 7 At the position shown, the swirl vane 3-6 is fixed between the outer wall 3-2 of the fuel conduit and the inner cylinder wall 1-2, while retaining the venturi structure 1-12 at the lower end of the inner cylinder wall 1-2. After assembly, the swirl vane can guide the air required for combustion to form a rotating airflow, while the venturi structure reduces the outlet air pressure through its convex shape. The two work together to form a stable recirculation zone in the combustion area, providing a continuous heat source for the mixture injected by the micro-mixing unit 2-1, ensuring stable combustion and reducing pollutant emissions.

[0034] Working principle: Air enters the burner from the windward side 1-1 and is divided into two paths: one path enters the air inlet 2-2 of each micro-mixing unit 2-1; the other path enters the annular airflow channel between the fuel duct 3 and the inner cylinder wall 1-2, and generates a rotating airflow through the swirl vanes 3-6.

[0035] The main combustion stage fuel enters the annular channel of the fuel conduit 3 through the main combustion stage fuel inlet 3-3, and enters the fuel chamber 1-7 through the fuel pipe 3-5. Under the deceleration and diffusion effect of the annular baffle 1-8, it is evenly distributed to the fuel inlet 2-3 of each micro-mixing unit 2-1.

[0036] The throat of the micro-mixing unit 2-1 adopts a radially contracting structure. When air flows through this contracting throat, the flow velocity increases and the static pressure decreases, forming a local low-pressure zone in the throat region. This low-pressure zone exerts a strong ejector suction effect on the fuel inlet 2-3 located circumferentially in the throat, causing the fuel to be automatically drawn into the throat and mixed with the high-speed air.

[0037] The duty fuel enters the inner wall 3-1 of the fuel conduit through the duty fuel inlet 3-4 and is ejected from the duty fuel outlet 3-7. It burns stably in the recirculation zone formed by the swirl blades, providing a continuous ignition source for the main combustion stage.

[0038] The Venturi structure 1-12 at the lower end of the inner cylinder wall 1-2 reduces the outlet air pressure, promotes the recirculation of high-temperature flue gas, and suppresses thermoacoustic oscillations. Cooling air enters the cooling air cavity 1-9 from the cooling air inlet 1-4 at the lower end of the outer cylinder wall 1-3 and exits from the cooling air outlet 1-5 on the leeward side 1-11, cooling the tail end and leeward side of the micro-mixing unit to prevent backfire.

[0039] The embodiments of the present invention disclosed above are merely illustrative of the invention. These embodiments do not exhaustively describe all details, nor do they limit the invention to the specific implementations described. Many modifications and variations can be made based on the content of this specification. This specification selects and specifically describes these embodiments to better explain the principles and practical applications of the invention, thereby enabling those skilled in the art to better understand and utilize the invention.

Claims

1. A pure hydrogen micro-mixing burner with a special throat, characterized in that, include: The micro-hybrid burner cylinder (1) has a windward side (1-1) and a leeward side (1-11) along the air inlet direction. Multiple micro-mixing units (2-1) are provided, with their two ends connected to the windward side (1-1) and the leeward side (1-11) respectively; The micro-mixed burner cylinder (1) is provided with a baffle (1-10) inside. The baffle (1-10) divides the cavity composed of the micro-mixed burner cylinder (1) and multiple micro-mixing units (2-1) into a fuel cavity (1-7) and a cooling air cavity (1-9). The fuel conduit (3) is connected to the fuel cavity (1-7).

2. The pure hydrogen micro-mixing burner with a special throat according to claim 1, characterized in that: The micro-mixing unit (2-1) is a tubular structure with a radially constricted throat, including an air inlet (2-2) connected to the windward side (1-1) and a mixed gas outlet (2-4) connected to the leeward side (1-11); the throat is provided with a fuel inlet (2-3).

3. A pure hydrogen micro-mixing burner with a special throat according to claim 2, characterized in that: The windward side (1-1) is conical.

4. A pure hydrogen micro-mixing burner with a special throat according to claim 3, characterized in that: The top of the cone is connected to one end of the inner cylinder wall (1-2), and the other end of the inner cylinder wall (1-2) passes through the partition (1-10) and is connected to the leeward side (1-11). The fuel conduit (3) is inserted into the inner cylinder wall (1-2) and communicates with the fuel chamber (1-7) through the fuel pipe connection hole (1-13) provided on the inner cylinder wall (1-2).

5. A pure hydrogen micro-mixing burner with a special throat according to claim 4, characterized in that: The inner cylinder wall (1-2) has a Venturi tube structure (1-12) at the end near the leeward side (1-11).

6. A pure hydrogen micro-mixing burner with a special throat according to claim 4, characterized in that: The fuel pipe connection hole (1-13) is located on one side of the fuel chamber (1-7) and is provided with an annular baffle (1-8).

7. A pure hydrogen micro-mixing burner with a special throat according to claim 4, characterized in that: An air passage is provided between the fuel conduit (3) and the inner cylinder wall (1-2), and the air passage is used to guide air from the windward side (1-1) to the leeward side (1-11).

8. A pure hydrogen micro-mixing burner with a special throat according to claim 7, characterized in that: Swirl blades (3-6) are provided between the fuel conduit (3) and the inner cylinder wall (1-2).

9. A pure hydrogen micro-mixing burner with a special throat according to claim 8, characterized in that: The fuel conduit (3) has a double-layer structure. The inner layer supplies fuel for duty personnel, and the outer layer supplies main fuel. The outer layer is connected to the fuel pipe connection hole (1-13) through the fuel pipe (3-5) provided on the outer wall (3-2) of the fuel conduit.

10. A pure hydrogen micro-mixing burner with a special throat according to any one of claims 1-9, characterized in that: The lower end of the outer wall (1-3) of the micro-mixed burner cylinder (1) has a cooling air inlet (1-4) connected to the cooling air cavity (1-9), and a cooling air outlet (1-5) is opened on the leeward side (1-11).

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