Double-air-regulation pure hydrogen turbulent burner and burner combustion control method

Abstract

The invention provides a double-air-regulation pure hydrogen turbulent burner and a burner combustion control method, and belongs to the field of burners. The combustor comprises a combustion body and a mixing part, the mixing part comprises a first cylindrical channel and a second cylindrical channel which are coaxially arranged, a first opening is formed in the side wall of the first cylindrical channel, a second opening is formed in the side wall of the second cylindrical channel, and a third opening is formed in the outer side wall of the combustor. The position of the third opening in the vertical direction is lower than that of the first opening and the second opening; and the rotating blade is arranged in the first cylindrical channel, and in the vertical direction, the rotating blade is arranged between the outlet of the second air inlet channel and the first opening. According to the double-air-regulation pure hydrogen turbulent burner and the burner combustion control method, efficient mixing of hydrogen and air can be achieved, dependence on an external power source is reduced, and the energy utilization efficiency is improved.

Description

Technical Field

[0001] The present application relates to the technical field of burners, and in particular to a dual-air-adjusted pure hydrogen swirl burner and a burner combustion control method. Background Art

[0002] With the adjustment of energy structures and increasing environmental protection requirements, hydrogen has attracted widespread attention as a clean and efficient energy source. In the field of burners, achieving efficient hydrogen combustion and solving its power supply issues have become research hotspots. Traditional burners suffer from poor mixing, low combustion efficiency, and the inability to generate their own power when burning hydrogen, making them unable to meet the energy utilization needs of modern industry and life. For example, some burners fail to fully mix hydrogen and air, resulting in incomplete combustion, wasted energy, and the generation of pollutants. Furthermore, their reliance on external power sources increases cost and complexity. Summary of the Invention

[0003] In view of this, the present application provides a dual-air-adjusted pure hydrogen swirl burner and a burner combustion control method, which can achieve efficient mixing of hydrogen and air, reduce dependence on external power supplies, and improve energy utilization efficiency.

[0004] Specifically, this application is implemented through the following technical solutions: In a first aspect, the present application provides a dual-air-adjusted pure hydrogen swirl burner, the burner comprising a combustion body and a mixing portion, the mixing portion comprising a first cylindrical channel and a second cylindrical channel arranged coaxially, the first cylindrical channel having a smaller diameter than the second cylindrical channel, the second cylindrical channel being located above the first cylindrical channel and fixedly connected via an annular connecting plate; A first opening is provided on the side wall of the first cylindrical channel, and a second opening is provided on the side wall of the second cylindrical channel. The first opening is connected to the hydrogen intake channel, and the second opening is connected to the first air intake channel. A third opening is provided on the outer side wall of the burner. The third opening is located lower than the first opening and the second opening in the vertical direction. The second air intake channel passes through the third opening. The inlet of the second air intake channel is located on the outside of the burner, and the outlet of the second air intake channel is located at the center of the circle at the inlet of the first cylindrical channel. a rotating blade, the rotating blade being disposed in the first cylindrical passage, and being disposed vertically between the outlet of the second air intake passage and the first opening; The rotating blades drive the hydrogen entering the first cylindrical channel from the first opening to rotate at a first speed in the first cylindrical channel to form a first vortex; the first vortex forms a suction force at the center of the vortex, attracting the air at the outlet of the second air intake channel to rise to the center position of the first vortex, and forming a first direct current at the center position at a second speed; the first mixed flow after the first vortex and the first direct current are mixed rises into the second cylindrical channel, driving the air entering the first air intake channel from the second opening to rotate along the inner wall of the second cylindrical channel at a third speed to form a second vortex; the second mixed flow after the first mixed flow and the second vortex are mixed rises to the combustion body, wherein the first speed, the second speed and the third speed are calculated according to the required degree of mixing of hydrogen and air.

[0005] A second aspect of the present application provides a combustion control method for a dual-air-regulated pure hydrogen swirl burner, the method comprising: Pure hydrogen is introduced into the first opening of the side wall of the first cylindrical channel through the hydrogen inlet channel; The rotating blades are started to drive the pure hydrogen gas flowing from the hydrogen inlet channel into the first cylindrical channel to rotate to form a first vortex flow; Air is introduced into the first cylindrical channel through the second air inlet channel to form a first direct flow at the center of the first swirl flow. The first swirl flow and the first direct flow are mixed to form a first mixed flow that rises to the second cylindrical channel. Air is introduced into the second cylindrical channel through the first air intake channel, and a second vortex is formed under the drive of the first mixed flow. The first mixed flow and the second vortex are mixed to form a second mixed flow that rises to the combustion body for combustion.

[0006] The double-adjusted air pure hydrogen swirl burner and burner combustion control method provided by the present application are characterized by openings at different positions on the first cylindrical channel and the second cylindrical channel, which respectively form air swirls inside and outside the rotating pure hydrogen, wrapping the rotating hydrogen so that the hydrogen and air can be fully mixed to a safe mixing ratio, thereby improving the combustion effect. At the same time, the mixing part and the combustion body are adjacent components in a device, and the mixed hydrogen and air can be quickly and short-distance transferred to the combustion area, ensuring the safe transmission of the mixed gas and improving the safety of the burner. Specifically, through the coaxial arrangement of the first and second cylindrical channels and the reasonable layout of each air inlet channel, multi-stage swirl mixing is achieved, so that hydrogen and air reach a highly uniform mixing state before entering the combustion body, and the fully mixed hydrogen and air can achieve more complete combustion in the combustion body, thereby improving combustion efficiency. By controlling the speed and air intake of each swirl, the rate and intensity of the combustion reaction can be accurately adjusted to ensure that the combustion process is always in a stable state. The stable airflow and good mixing effect ensure the stability of combustion. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] Figure 1 This is a schematic diagram of the structure of the dual-air-adjusted pure hydrogen swirl burner provided in this application; Figure 2 Exploded diagram of the dual-air-adjusted pure hydrogen swirl burner provided for this application; Figure 3 A cross-sectional view of the mixing portion shown in this application; Figure 4 This is a cross-sectional view of the dual-air-adjusted pure hydrogen swirl burner shown in this application; Figure 5 Another cross-sectional view of the mixing portion shown in this application; Figure 6 This is a structural diagram of the water cooling head shown in this application; Figure 7 This is a flow chart of Example 2 of the combustion control method for a dual-air-adjusted pure hydrogen swirl burner provided in this application; Description of reference numerals: 1-first cylindrical channel; 2-second cylindrical channel; 3-first opening; 4-second opening; 5-hydrogen inlet channel; 6-first air inlet channel; 7-third opening; 8-second air inlet channel; 9-bottom cover plate; 10-top cover plate; 11-first temperature end; 12-second temperature end. DETAILED DESCRIPTION

[0008] Exemplary embodiments are described in detail herein, with examples illustrated in the accompanying drawings. When the following description refers to the drawings, identical numerals in different drawings represent identical or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments are not intended to represent all embodiments consistent with this application.

[0009] The terms used in this application are for the purpose of describing specific embodiments only and are not intended to limit this application. The singular forms "a," "the," and "the" used in this application are also intended to include the plural forms unless the context clearly indicates otherwise. It should also be understood that the term "and / or" as used herein refers to and includes any or all possible combinations of one or more of the associated listed items.

[0010] It should be understood that although the terms first, second, third, etc. may be used in this application to describe various information, such information should not be limited to these terms. These terms are only used to distinguish information of the same type from each other. For example, without departing from the scope of this application, first information may also be referred to as second information, and similarly, second information may also be referred to as first information. Depending on the context, the word "if" as used herein may be interpreted as "at the time of" or "when" or "in response to determining".

[0011] Specific embodiments are given below to introduce the technical solutions of the present application in detail.

[0012] Example 1:

[0013] Figure 1 This is a schematic diagram of the structure of the dual-air-adjusted pure hydrogen swirl burner provided in this application. Figure 2 The exploded diagram of the double-air-adjusted pure hydrogen swirl burner provided in this application is Figure 3 This is a cross-sectional view of the mixing portion shown in this application. Please also refer to Figure 1 、 Figure 2 and Figure 3 The burner provided in this embodiment includes a combustion body and a mixing part. The mixing part includes a first cylindrical channel 1 and a second cylindrical channel 2 arranged coaxially. The diameter of the first cylindrical channel is smaller than the diameter of the second cylindrical channel. The second cylindrical channel is located above the first cylindrical channel and is fixedly connected by an annular connecting plate. A first opening 3 is provided on the side wall of the first cylindrical channel, and a second opening 4 is provided on the side wall of the second cylindrical channel. The first opening 3 is connected to the hydrogen intake channel 5, and the second opening 4 is connected to the first air intake channel 6. A third opening 7 is provided on the outer side wall of the burner. The third opening 7 is located lower than the first opening 3 and the second opening 4 in the vertical direction. A second air intake channel 8 passes through the third opening 7. The inlet of the second air intake channel 8 is located on the outside of the burner, and the outlet of the second air intake channel 8 is located at the center of the inlet of the first cylindrical channel 1. a rotating blade (not shown in the figure), which is provided in the first cylindrical channel 1 and is vertically located between the outlet of the second air intake channel 8 and the first opening 3; The rotating blades drive the hydrogen entering the first cylindrical channel 1 from the first opening 3 to rotate at a first speed in the first cylindrical channel 1 to form a first vortex; the first vortex forms a suction force at the center of the vortex, attracting the air at the outlet of the second air inlet channel to rise to the center position of the first vortex, and forming a first straight flow at a second speed at the center position; the first mixed flow after the first vortex and the air at the outlet of the second air inlet channel are mixed rises into the second cylindrical channel 2, driving the air entering the first air inlet channel 6 from the second opening 4 to rotate along the inner wall of the second cylindrical channel 2 at a third speed to form a second vortex, wherein the first speed, the second speed and the third speed are calculated according to the required degree of mixing of hydrogen and air; the second mixed flow after the first mixed flow and the second vortex are mixed rises to the combustion body.

[0014] Specifically, the calculation process for the first, second, and third speeds includes: determining the transmission distance between the gas outlet of the mixing section and the combustion body; calculating the target mixing parameter at the gas outlet of the mixing section based on the transmission distance and the optimal mixed gas parameters of the combustion body. Specifically, the gas continuously mixes during the transmission process, increasing the degree of mixing harmony. In this case, the gas transmission process and the transmission distance can be used to calculate the mixing ratio of the gas at the outlet after the transmission distance, and the target mixing parameter can be calculated by reverse calculation based on the optimal mixed gas parameters; determining the gas mixing distance at the mixing section, and calculating the first speed based on the gas mixing distance and the target mixing parameter. Similarly, based on the gas mixing distance and the gas transmission process, the speed required to achieve the target mixing parameter can be calculated, and this speed is used as the first speed. An adjustment coefficient is determined based on the law of gas movement, and the second speed is calculated based on the product of the adjustment coefficient and the first speed. The gas mixing degree at the entrance of the second cylindrical channel is calculated based on the first and second speeds, and the third speed is calculated based on the difference between the gas mixing degree and the target mixing parameter.

[0015] It should be noted that the mixing area of ​​the burner includes first and second cylindrical channels arranged coaxially. The first cylindrical channel 1 has a smaller diameter and is located at the bottom, while the second cylindrical channel 2 is located at the top. The two are fixedly connected by an annular connecting plate. This structural design makes the flow of gas in the channel more stable and orderly. In addition, the coaxial arrangement ensures that the gas can be smoothly transmitted along the central axis during the flow process, reducing airflow turbulence and energy loss. The annular connecting plate not only connects the two channels, but also enhances the stability and sealing of the entire structure, preventing gas leakage.

[0016] In this embodiment, the layout of the burner air inlet passage is very critical. The following is an introduction to each air inlet passage.

[0017] Hydrogen inlet channel 5: The first opening 3 on the side wall of the first cylindrical channel 1 is connected to the hydrogen inlet channel 5. After hydrogen enters from the opening, it can fully diffuse in the first cylindrical channel 1, creating conditions for forming a stable vortex.

[0018] First air intake channel 6: Second opening 4 on the sidewall of second cylindrical channel 2 connects to first air intake channel 6. When the first mixed airflow rises into second cylindrical channel 2, it drives the incoming air through this channel to rotate, forming a second vortex flow and further mixing. Positioning first air intake channel 6 within second cylindrical channel 2 aligns with the overall gas mixing process and helps improve mixing efficiency.

[0019] Second air intake channel 8: The third opening 7 on the outer wall of the burner is lower than the first and second openings. The second air intake channel 8 passes through the third opening 7, with the entrance outside the burner and the exit located at the center of the entrance of the first cylindrical channel 1. This layout is designed to allow the air from the second intake channel to accurately enter the center area of ​​the first vortex, forming a strong mixing effect with the hydrogen. Introducing air from the outside can take advantage of the external pressure difference to allow air to enter the burner more smoothly, and setting the exit at the center of the entrance of the first cylindrical channel 1 can maximize the suction force of the first vortex center to promote the mixing of air and hydrogen.

[0020] In addition to the aforementioned structure, rotating blades are also provided. Specifically, these are located within the first cylindrical channel 1, between the outlet of the second air inlet channel 8 and the first opening 3. These blades provide rotational force to the hydrogen, prompting it to form a first vortex. By designing the shape, angle, and mounting position of the rotating blades, the hydrogen achieves an appropriate rotational speed and direction, thereby enabling the subsequent mixing process.

[0021] The formation of the first swirl flow, the first straight flow and the second swirl flow, as well as the final mixing and combustion process and principle are introduced below.

[0022] It should be noted that the rotating blades drive the hydrogen entering through the first opening to rotate clockwise at a first speed within the first cylindrical channel 1, forming a first vortex. According to the principles of fluid mechanics, the rotating fluid forms a central low-pressure area within the channel, which is the source of the central suction force of the first vortex. This rotational flow increases the kinetic energy and turbulence of the hydrogen, enabling it to better mix with the subsequently entering air.

[0023] Furthermore, the suction at the center of the first vortex draws the air at the outlet of the second air inlet channel 8 upward to the center of the first vortex, forming a first direct current at the second speed. At this point, the direct current air mixes with the hydrogen from the first vortex to form a first mixed flow. The first speed is greater than the second speed. This mixing method utilizes the shear force and suction of the vortex. Under the influence of the suction at the center of the first vortex, the air at the outlet of the second air inlet channel cooperates with the first vortex, promoting contact between hydrogen and air from both the inside and outside, thereby fully mixing the two gases and improving mixing uniformity.

[0024] After forming the first mixed airflow, it rises to the second cylindrical channel 2, driving the air entering through the second opening 4 to rotate along the inner wall of the second cylindrical channel 2 at a third speed, forming a second vortex. Because the second cylindrical channel has a larger diameter and the first mixed airflow has a certain amount of energy and rotational momentum, it can effectively drive the newly entering air to rotate, further enhancing the mixing effect. The third speed is lower than the first speed because the second cylindrical channel has a larger space, which reduces the airflow speed somewhat, but still ensures sufficient mixing of the air and the first mixed airflow.

[0025] Finally, the first mixed flow and the second swirl flow combine to form a second mixed flow, which rises to the combustion body for combustion. After multiple stages of mixing, the hydrogen and air are fully and evenly mixed, achieving efficient and stable combustion in the combustion body.

[0026] It should be noted that the burner provided in this embodiment also includes a cover plate. Figure 4 This is a cross-sectional view of the double-adjusted air pure hydrogen swirl burner shown in this application, please refer to Figure 4 and continue to refer to Figure 2 Specifically, a cover plate is provided at the top and bottom of the second cylindrical channel. The bottom cover plate 9 is provided at the bottom of the second cylindrical channel, and a guide hole is provided at the center of the bottom cover plate 9. The guide hole is coaxial with the first cylindrical channel 1, and the inner ring diameter of the guide hole is equal to the diameter of the first cylindrical channel; the top cover plate 10 is provided at the top of the second cylindrical channel 2, and a guide port is provided at the center of the top cover plate 10. The inner ring diameter of the guide port is larger than the diameter of the first cylindrical channel and smaller than the diameter of the second cylindrical channel, and the inner ring diameter of the top cover plate 10 is larger than the inner ring diameter of the bottom cover plate 9.

[0027] Among them, since the bottom cover plate guide hole is coaxial with the first cylindrical channel and the inner ring diameter is equal, the resistance and turbulence during the rising process of the airflow are reduced, so that the first mixed airflow rising from the first cylindrical channel enters the second cylindrical channel stably and orderly.

[0028] The top cover plate 10 is installed on the top of the second cylindrical channel 2, and the inner ring diameter of the guide port at the center thereof is larger than the diameter of the first cylindrical channel and smaller than the diameter of the second cylindrical channel. On the one hand, it limits the flow range of the second mixed airflow in the second cylindrical channel, so that it can be fully mixed with the second vortex during the rising process, thereby improving the uniformity of the mixing; on the other hand, the guide port of appropriate size can control the speed and direction of the second mixed airflow entering the combustion body, ensuring that it enters the combustion body for combustion in the best state, thereby improving combustion efficiency and stability.

[0029] In addition, it should be noted that Figure 5 For another cross-sectional view of the mixing portion shown in this application, please refer to Figure 5 , the upper surface of the first cylindrical channel and the lower surface of the bottom cover of the second cylindrical channel are serrated structures; Specifically, when the hydrogen rotates clockwise at a first speed under the drive of the rotating blades to form a first vortex and rises, the first vortex is divided and guided by the serrated structure, and the airflow is disturbed; when the air at the outlet of the second air inlet channel rises to the center of the first vortex under the action of the suction force of the first vortex center, the air in the first direct current mixes with the disturbed hydrogen to form a first mixed airflow; the first mixed airflow rises to the second cylindrical channel, passes through the serrated structure on the lower surface of the bottom cover of the second cylindrical channel, and reaches the second cylindrical channel, so that the hydrogen and air in the first mixed airflow are further mixed.

[0030] It should be noted that when the hydrogen, driven by the rotating blades, rotates clockwise at a first speed, forming a first vortex and moving upward, the serrated structure on the upper surface of the first cylindrical channel comes into play. The serrated structure disrupts the originally regular airflow pattern, dividing the first vortex into multiple smaller streams and changing the direction of the airflow, causing strong disturbances in the airflow. This disturbance increases the contact area and contact opportunities between the hydrogen and the surrounding air.

[0031] At this point, under the suction of the first vortex center, the direct current air at the outlet of the second air inlet channel rises to the center of the first vortex. Because the first vortex has been disturbed by the sawtooth structure, its mixing with the first direct current air is no longer a simple regular mixing, but rather a more thorough and rapid interpenetration and blending. This greatly improves the mixing efficiency of hydrogen and air and helps form a more uniform first mixed flow.

[0032] Furthermore, after the first mixed airflow rises to the second cylindrical channel, it will pass through the serrated structure on the lower surface of the bottom cover of the second cylindrical channel. This serrated structure acts on the airflow again, further disrupting the flow state of the first mixed airflow, causing the hydrogen and air therein to be disturbed again. This secondary disturbance promotes a deeper mixing of the hydrogen and air in the first mixed airflow. Originally, there may be areas of uneven mixing during the initial mixing process, but after passing through the action of this serrated structure, they can be further mixed and adjusted, so that the hydrogen and air of the first mixed airflow are more fully mixed before entering the subsequent combustion stage, providing a strong guarantee for efficient and stable combustion.

[0033] It should also be noted that the burner provided in this embodiment also includes a thermoelectric power generation module, which includes a first temperature end 11 and a second temperature end 12, wherein the first temperature is higher than the second temperature. The first temperature end is described below as a high-temperature end, and the second temperature end as a low-temperature end. Specifically, the high-temperature end is attached to the outer side of the combustion body, and the heat generated by the combustion body during the combustion process provides a heat source for the high-temperature end of the thermoelectric power generation module; the low-temperature end is connected to a water-cooled head, which surrounds the outer wall of the high-temperature end. Coolant circulates inside the water-cooled head, and the coolant absorbs the heat of the first cylindrical channel to provide a cold source for the low-temperature end of the thermoelectric power generation module; the electricity generated by the thermoelectric power generation module is connected to the two micro-blowers of the burner through wires, which drive the intake of the central wind and the swirl air respectively.

[0034] The thermoelectric power generation module operates on the Seebeck effect, which states that when two different conductors or semiconductor materials form a closed circuit with a temperature difference between the two ends, an electromotive force is generated in the circuit, thereby converting thermal energy into electrical energy. In this burner, the thermoelectric power generation module cleverly utilizes the heat generated by the combustion body and the heat in the first cylindrical channel, achieving effective energy recovery and reuse.

[0035] It should be noted that the high-temperature end is tightly bonded to the outside of the combustion body, allowing the large amount of heat released by the combustion body during combustion to be efficiently transferred to the high-temperature end of the thermoelectric power generation module. The combustion reaction in the combustion body is a highly exothermic process. This direct bonding provides a stable and sufficient heat source for the thermoelectric power generation module, ensuring that the temperature of the high-temperature end is maintained at a high level, thereby creating a sufficient temperature difference between the two ends of the thermoelectric power generation module. The low-temperature end is connected to a water-cooled head arranged around the outer wall of the high-temperature end, within which coolant circulates. During this circulation, the coolant absorbs heat from the first cylindrical channel, thereby providing a cooling source for the low-temperature end of the thermoelectric power generation module. The gas in the first cylindrical channel carries a certain amount of heat during mixing and flow. This heat is removed by the heat exchange action of the water-cooled head, reducing the temperature of the low-temperature end, further increasing the temperature difference between the two ends of the thermoelectric power generation module, and improving power generation efficiency.

[0036] It should also be noted that the water-cooling head is connected to the aluminum radiator, cooling fan, expansion water tank and circulating water pump in sequence through a circulation pipeline; among them, the circulating water pump drives the coolant to flow in a closed loop, absorbs heat and then cools it down through the aluminum radiator and cooling fan, and the expansion water tank compensates for the thermal expansion and contraction of the liquid.

[0037] Figure 6This is a structural diagram of the water-cooled head portion shown in this application. Specifically, a circulating water pump is installed near the inlet of the water-cooled head. It generates pressure through mechanical operation and drives the coolant to flow continuously in a closed loop. During the circulation process, the coolant continuously removes heat from the water-cooled head and then circulates throughout the system to ensure that the water-cooled head can always absorb heat from the first cylindrical channel and maintain the cold source supply at the low-temperature end of the thermoelectric power generation module. The working efficiency and stability of the circulating water pump directly affect the circulation speed and heat dissipation effect of the coolant. If the circulating water pump power is insufficient and the coolant circulates slowly, the temperature of the water-cooled head will rise, reducing the power generation efficiency of the thermoelectric power generation module. If the circulating water pump fails and the coolant stops flowing, the entire system will lose its heat dissipation capacity, which may cause equipment damage.

[0038] After the coolant absorbs heat, it flows through the aluminum radiator, which is installed in the circulation line after the circulating water pump. Aluminum radiators are usually placed in well-ventilated locations to facilitate heat dissipation. They have excellent thermal conductivity and can quickly transfer heat from the coolant to their surface, increasing the heat dissipation area. A cooling fan is installed near the aluminum radiator, with the fan facing the aluminum radiator. Its high-speed rotation generates strong winds, accelerating air flow and removing heat from the aluminum radiator's surface, thereby rapidly cooling the coolant. The two work together to significantly improve heat dissipation efficiency.

[0039] As the coolant circulates, it expands and contracts due to temperature fluctuations. The expansion tank compensates for this volume change. It's installed relatively high in the circulation piping (between the aluminum radiator and the circulating water pump). This allows excess fluid to flow into the tank as the coolant expands due to heat, preventing damage to the piping and other components due to excessive pressure. As the coolant contracts due to cooling, the fluid in the tank is replenished back into the circulation piping, ensuring proper circulation of the coolant within the system. The expansion tank also stabilizes system pressure, ensuring safe and reliable operation of the entire water cooling system. For example, during system startup and shutdown, when temperatures fluctuate dramatically, the expansion tank effectively buffers pressure fluctuations caused by changes in coolant volume, protecting system components.

[0040] It should be noted that the output of the thermoelectric power generation module is connected to two micro-blowers. One micro-blower delivers central air, i.e., it delivers air to the center of the first cylindrical channel entrance through the second air inlet channel. The other micro-blower delivers swirl air, i.e., it delivers air to the second cylindrical channel through the first air inlet channel. Furthermore, the power generated by the thermoelectric power generation module is equal to or greater than the power required for external power supply. After deducting the power consumption of the cooling system (i.e., the cooling water pump and cooling fan connected to the water-cooled head), the remaining power can drive the two micro-blowers, thus achieving self-powered operation of the burner. For example, assuming a power generation of over 15W, after deducting the total power consumption of the cooling water pump and cooling fan (8.3W), over 6W of external power can still be supplied. If two micro-blowers with power outputs of 1.45W and 1.2W, respectively, are installed, the self-generated power supply (6W) exceeds the power required by the blowers (2.65W), maintaining self-power supply. This reduces reliance on external power sources, lowering operating costs while also improving the burner's independence and adaptability. By converting the heat that would otherwise be wasted during the combustion process into electrical energy, power is provided for the normal operation of the burner, forming a closed-loop system for energy recycling and reflecting the design concept of energy conservation and environmental protection.

[0041] Example 2:

[0042] Figure 7 This is a flow chart of Example 2 of the dual-air-adjusted pure hydrogen swirl burner combustion control method provided by this application. Figure 7 , based on the above structural embodiment, the method includes: S701 , introducing pure hydrogen into the first opening of the side wall of the first cylindrical channel through the hydrogen inlet channel.

[0043] It should be noted that the above operations can be performed according to preset ventilation time and flow rate to ensure that the gases in the burner are mixed and burned under optimal conditions. The preset ventilation time and flow rate are accurately calculated based on factors such as the burner design parameters, the stoichiometric ratio of hydrogen to air, and the desired combustion effect.

[0044] It should be noted that, in order to avoid problems such as uneven gas mixing and incomplete combustion, the following operations may be performed before pure hydrogen is introduced into the first opening of the side wall of the first cylindrical channel through the hydrogen inlet channel: (1) Obtain the total amount of mixed gas that needs to be burned by the burner.

[0045] Obtaining the total amount of mixed gas required for burner combustion is fundamental to all preparations. This total amount is typically determined by the burner's application scenario and actual needs. For example, in industrial production, the amount of mixed gas used may be determined by the production process's heat requirements; in civilian equipment, the amount is determined based on factors such as the equipment's power requirements.

[0046] (2) Conduct multiple sets of combustion tests, record the combustion effects at different hydrogen-air mixture ratios, and determine the optimal mixture ratio; calculate the amount of hydrogen and air required for each combustion based on the total amount of the mixed gas and the optimal mixture ratio.

[0047] The hydrogen-air mixture ratio significantly impacts combustion performance. Different ratios can lead to variations in combustion performance indicators, such as combustion temperature, combustion efficiency, and pollutant emissions. For example, a hydrogen ratio that is too high can lead to unstable combustion and even create the risk of explosion; a low hydrogen ratio can result in low combustion efficiency and significant energy waste. By conducting combustion tests at different ratios, recording various combustion performance indicators, and then comprehensively analyzing this data, we can identify the hydrogen-air mixture ratio that optimizes combustion performance and ensure that the burner operates under optimal conditions.

[0048] (3) Based on the calculated hydrogen amount and air amount, the intake amount of the hydrogen intake passage, the first air intake passage, and the second air intake passage is controlled.

[0049] Specifically, controlling the intake amounts of the hydrogen intake channel, the first air intake channel, and the second air intake channel according to the calculated hydrogen amount and air amount includes: (31) Measure the volume of the mixing portion and the air flow velocity at the outlet of the mixing portion.

[0050] It should be noted that the mixing area is the key region for the initial mixing of hydrogen and air, and its volume directly affects the space and effect of gas mixing. The airflow velocity at the outlet of the mixing area reflects how quickly the mixed gas leaves the area.

[0051] (32) Set a safe mixing ratio range based on the stoichiometric ratio of hydrogen to air.

[0052] The stoichiometric ratio of hydrogen to air refers to the ratio of hydrogen and air required for complete reaction. In practical applications, a safe mixing ratio range is necessary to ensure the safety and stability of the combustion process. This is because hydrogen is a flammable and explosive gas. When the hydrogen-air mixture falls within a certain range, it may explode when exposed to a fire source. By studying the chemical properties and reaction characteristics of hydrogen and air, combined with relevant safety standards and experience, a safe mixing ratio range has been determined that ensures complete combustion while avoiding the risk of explosion.

[0053] (33) Calculate the mixing time required to achieve a safe mixing ratio based on the volume and outlet air flow velocity.

[0054] Based on the measured mixing area volume and outlet airflow velocity, the gas residence time within the mixing area can be calculated. The mixing time required to achieve a safe mixing ratio is the time required to ensure that hydrogen and air are fully mixed within the mixing area and within a safe mixing range. Through fluid dynamics analysis and experimental research of the mixing process, a corresponding mathematical model can be established. This, combined with the mixing area volume and outlet airflow velocity, can be used to calculate the mixing time required to achieve a safe mixing ratio.

[0055] (34) Obtaining the air flow rate of the second air intake channel, the hydrogen flow rate of the hydrogen intake channel, and the air flow rate of the first air intake channel, and calculating the intake air volume in combination with the mixing time.

[0056] For the second air inlet channel, the volume of air required to enter the mixing area within that time, i.e., the intake volume, can be calculated based on the air flow rate and mixing time. Similarly, for the hydrogen inlet channel and the first air inlet channel, the intake volume can be calculated based on the corresponding flow rates and mixing times. This approach allows for precise control of the intake volume for each inlet channel, ensuring that hydrogen and air are fully mixed at a safe mixing ratio within the mixing area. This operation improves the combustion efficiency and safety of the dual-air-adjusted pure hydrogen swirl burner.

[0057] S702 , starting the rotating blades, which drive the pure hydrogen entering the first cylindrical channel from the hydrogen inlet channel to rotate to form a first vortex.

[0058] It should be noted that when hydrogen enters the first cylindrical channel through the hydrogen inlet channel, the rotating blades begin to work. The design and installation of the rotating blades enable it to exert a tangential force on the hydrogen during rotation, thereby driving the hydrogen to rotate clockwise at a first speed. This rotational motion causes the hydrogen to form a stable vortex in the first cylindrical channel, namely the first vortex. Among them, the vortex motion of the first vortex increases the disturbance of the hydrogen, making the hydrogen more evenly distributed in the first cylindrical channel, and the rotating fluid forms a low-pressure area in the center, generating suction.

[0059] S703 , air is introduced into the first cylindrical channel through the second air inlet channel to form a first direct flow at the center of the first vortex flow. The first vortex flow and the first direct flow are mixed to form a first mixed flow that rises to the second cylindrical channel.

[0060] It should be noted that due to the suction generated by the center of the first vortex, the air at the outlet of the second air inlet channel is attracted and rises to the center of the first vortex. When the air enters the center of the first vortex, it interacts with the surrounding hydrogen, forming a first direct current at a second speed. The second speed is lower than the first speed because the initial driving force on the air when entering the center of the first vortex is relatively small, and it encounters a certain amount of resistance during the mixing process with the hydrogen. The formation of the first direct current further promotes the mixing of hydrogen and air, allowing the two gases to more fully contact and blend.

[0061] The first swirling flow and the first direct flow interact and mix within the first cylindrical channel, forming a first mixed flow. This mixing process is dynamic, with the hydrogen and air constantly exchanging positions and interpenetrating under the influence of the swirling flow, resulting in a more uniform mixing. The resulting first mixed flow possesses a certain amount of energy and upward momentum, naturally rising to the second cylindrical channel. During this ascent, the first mixed flow maintains a certain degree of rotation.

[0062] S704. Air is introduced into the second cylindrical channel through the first air intake channel to form a second vortex driven by the first mixed flow. The first mixed flow and the second vortex are mixed to form a second mixed flow that rises to the combustion body for combustion.

[0063] It should be noted that the first mixed airflow maintains a rotating state during its ascent, and the fluid dynamic field generated by this rotation exerts a force on the air entering through the first air intake channel. Driven by this force, the air rotates at a third speed along the inner wall of the second cylindrical channel, forming a second vortex. The formation of this second vortex further promotes gas mixing, allowing the first mixed airflow to blend more fully with the newly entering air.

[0064] In addition, it should be noted that before the air is introduced into the second cylindrical channel through the first air intake channel, the following steps are also included: The speed at which the hydrogen is driven to rotate by the rotating blades in the first cylindrical channel is obtained, and the speed is used as the rotational speed of the hydrogen. Based on the ideal state of mixing and combustion of hydrogen and air in the burner, a proportional relationship between the hydrogen rotational speed and the rotational speed of the air when a second vortex is formed under the drive of the first mixed flow after air is introduced into the first air inlet channel is preset. The rotational speed of the air in the second vortex is calculated based on the hydrogen rotational speed and the proportional relationship.

[0065] It should be noted that the mixing effect of hydrogen and air directly determines combustion efficiency and stability. The speed of the hydrogen driven by the rotating blades affects the intensity and characteristics of the first swirl, which in turn affects the formation of the first direct flow and the subsequent second swirl. The preset ratio between the hydrogen speed and the air rotation speed in the second swirl is based on in-depth research on the ideal state of hydrogen-air mixing and combustion in the burner. Through experimental testing and theoretical analysis, the rotation speed ratio of hydrogen and air for optimal mixing under different operating conditions was determined.

[0066] Reasonable control of the rotation speed of the gas in each swirl can ensure a stable and efficient combustion process. When the hydrogen rotation speed reaches an ideal match with the air rotation speed in the second swirl, the first mixed flow and the second swirl will mix more evenly and smoothly in the second cylindrical channel. After this uniform second mixed flow enters the combustion body, it can make the combustion reaction closer to the stoichiometric ratio, burn more completely, release more heat, improve combustion efficiency, and reduce energy waste and environmental pollution caused by incomplete combustion of hydrogen. In addition, the burner may face a variety of working conditions in actual applications, such as different combustion power requirements, ambient temperature and pressure changes, etc. Obtaining the hydrogen rotation speed and presetting the proportional relationship to calculate the air rotation speed in the second swirl can enable the burner to flexibly adapt to these changes.

[0067] In steps S701-S704, the first and third speeds correspond to the rotational speeds of the first and second swirls, respectively, while the second speed represents the speed at which the first straight stream forms. These speeds have a crucial impact on the mixing and combustion performance of the gases within the burner. A suitable speed combination ensures that hydrogen and air are fully mixed at all stages, improving combustion efficiency and reducing pollutant emissions. For example, if the first speed is too fast, it may prevent the first swirl from forming stably, affecting the uniformity of gas mixing; if the speed is too slow, it may not provide sufficient power to fully mix and promote gas rise.

[0068] It should be noted that the rotating blades are the key components that drive the hydrogen to form the first vortex. Their shape and angle directly affect the magnitude and direction of the tangential force applied to the hydrogen. By changing the shape of the rotating blades, such as their curvature and thickness, the contact area between the blades and the hydrogen and the force applied can be adjusted, thereby changing the rotational speed of the hydrogen, i.e., the first speed. At the same time, adjusting the angle of the rotating blades can change the direction and force of the blades' push on the hydrogen, further precisely controlling the first speed. Changes in the first speed, in turn, influence the formation and speed of the first direct current through factors such as the suction force at the center of the first vortex.

[0069] Furthermore, the gas flow rate of each intake channel directly affects the flow rate and energy of the corresponding gas. For example, increasing the gas flow rate of the hydrogen intake channel will increase the amount of hydrogen entering the first cylindrical channel, which, under the action of the rotating blades, may increase the speed of the first swirl. Increasing the gas flow rate of the second air intake channel will increase the amount of air entering the center of the first swirl. Increasing the gas flow rate of the first air intake channel will increase the amount of air entering the second cylindrical channel, thereby affecting the speed of the second swirl. By precisely adjusting the gas flow rate of each intake channel, effective control of the first, second, and third speeds can be achieved to achieve optimal gas mixing and combustion.

[0070] It should be noted that within the second cylindrical channel, the first mixed flow is initially formed by mixing hydrogen and some air within the first cylindrical channel, rising to this point with a certain degree of rotational momentum and mixing. The second swirl flow, on the other hand, is formed by the air entering through the first air intake channel, driven by the first mixed flow. When these two flows meet in the second cylindrical channel, their different speeds, directions, and rotational states lead to a strong interaction.

[0071] As the first mixed flow and the second swirling flow combine, entrainment, collision, and diffusion occur. Entrainment causes the two flows to entangle each other, increasing their contact area; collisions further break up gas clumps, bringing molecules closer together; and diffusion promotes the interpenetration of hydrogen and air molecules, achieving a more uniform mixing. As a result of these interactions, the two flows gradually merge to form the second mixed flow.

[0072] After the second mixed flow is formed, it rises to the main combustion chamber due to its upward kinetic energy and the pressure differential within the burner. There, the highly mixed hydrogen and air create favorable reaction conditions, enabling full and stable combustion. This thoroughly mixed gas ensures a closer combustion reaction to the stoichiometric ratio, resulting in more complete combustion and greater heat release, improving combustion efficiency and reducing energy waste and environmental pollution caused by incomplete hydrogen combustion.

[0073] It should also be noted that during the combustion process, it is necessary to monitor the air flow velocity at the outlet of the mixing part and the combustion state in the combustion body in real time; if the air flow velocity at the outlet of the mixing part is less than the hydrogen flame propagation speed or the combustion state is unstable, the air supply speed of the second air intake channel is increased, and the air intake volume of the hydrogen intake channel and the first air intake channel is adjusted.

[0074] The airflow velocity at the mixing zone outlet reflects the flow state of the mixed gas as it enters the subsequent combustion stage from the mixing zone. The hydrogen flame propagation velocity is a critical parameter. When the airflow velocity at the mixing zone outlet is less than the hydrogen flame propagation velocity, the flame may propagate back into the mixing zone, causing flashback. Flashback not only disrupts the normal operation of the burner but can also lead to serious safety accidents such as explosions. Therefore, real-time monitoring of the airflow velocity at the mixing zone outlet can promptly identify potential safety hazards.

[0075] The combustion state within the combustion engine is directly related to combustion efficiency and energy utilization. Unstable combustion may manifest as flickering flames, extinction, and incomplete combustion. This not only reduces combustion efficiency and wastes energy, but can also generate large amounts of pollutants such as carbon monoxide.

[0076] When the airflow velocity at the mixing zone outlet is slower than the hydrogen flame propagation speed or the combustion state is unstable, increasing the air supply velocity in the second air intake passage can increase the overall flow rate of the mixed gas. On the one hand, a higher flow rate allows the mixed gas to exit the mixing zone more quickly, preventing flame backpropagation and flashback. On the other hand, increasing the air supply helps provide more oxygen, promoting full combustion of the hydrogen and improving the combustion state.

[0077] By adjusting the intake volume of the hydrogen intake channel and the first air intake channel, the hydrogen-air mixture ratio can be altered. If combustion instability is caused by an improper mixture ratio, adjusting the intake volume appropriately can bring the mixture closer to the optimal combustion ratio. For example, if the hydrogen content is too high, this may lead to incomplete combustion. In this case, the hydrogen intake volume can be appropriately reduced or the intake volume of the first air intake channel can be increased. Conversely, if the air content is too high, this may lower the flame temperature and cause unstable combustion. In this case, the hydrogen intake volume can be appropriately increased or the intake volume of the first air intake channel can be reduced.

[0078] The method provided in this embodiment obtains the total amount of mixed gas and determines the optimal mixing ratio before ventilation. Based on this, the intake volume of each gas is calculated, ensuring that hydrogen and air enter the burner in the ideal ratio. During combustion, ventilation time and flow are precisely controlled to ensure orderly gas entry. Multi-swirl mixing ensures that hydrogen and air are fully blended, enabling full and stable combustion upon entering the combustion chamber. This releases more heat, improves combustion efficiency, and reduces energy waste and environmental pollution caused by incomplete hydrogen combustion.

[0079] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A dual-air regulating pure hydrogen swirl burner, characterized in that: The burner includes a combustion body and a mixing part, the mixing part includes a first cylindrical channel and a second cylindrical channel arranged coaxially, the diameter of the first cylindrical channel is smaller than the diameter of the second cylindrical channel, the second cylindrical channel is located above the first cylindrical channel and is fixedly connected by an annular connecting plate; A first opening is provided on the side wall of the first cylindrical channel, and a second opening is provided on the side wall of the second cylindrical channel. The first opening is connected to the hydrogen intake channel, and the second opening is connected to the first air intake channel. A third opening is provided on the outer side wall of the burner. The third opening is located lower than the first opening and the second opening in the vertical direction. The second air intake channel passes through the third opening. The inlet of the second air intake channel is located on the outside of the burner, and the outlet of the second air intake channel is located at the center of the circle at the inlet of the first cylindrical channel. a rotating blade, the rotating blade being disposed in the first cylindrical passage, and being disposed vertically between the outlet of the second air intake passage and the first opening; The rotating blades drive the hydrogen entering the first cylindrical channel from the first opening to rotate at a first speed in the first cylindrical channel to form a first vortex; the first vortex forms a suction force at the center of the vortex, attracting the air at the outlet of the second air intake channel to rise to the center position of the first vortex, and forming a first direct current at the center position at a second speed; the first mixed flow after the first vortex and the first direct current are mixed rises into the second cylindrical channel, driving the air entering the first air intake channel from the second opening to rotate along the inner wall of the second cylindrical channel at a third speed to form a second vortex; the second mixed flow after the first mixed flow and the second vortex are mixed rises to the combustion body, wherein the first speed, the second speed and the third speed are calculated according to the required degree of mixing of hydrogen and air.

2. The burner according to claim 1, characterized in that A cover plate is provided on the top and bottom of the second cylindrical channel. The bottom cover plate is provided at the bottom of the second cylindrical channel. A guide hole is provided at the center of the bottom cover plate. The guide hole is coaxial with the first cylindrical channel. The top cover plate is arranged on the top of the second cylindrical channel, and a guide port is opened at the center of the top cover plate. The inner ring diameter of the top cover plate is larger than the inner ring diameter of the bottom cover plate.

3. The burner according to claim 1, characterized in that The upper surface of the first cylindrical channel and the lower surface of the bottom cover of the second cylindrical channel are serrated structures; When the hydrogen gas rotates clockwise at a first speed under the drive of the rotating blades to form a first vortex and rises, the first vortex is divided and guided by the sawtooth structure, causing disturbance in the airflow; When the air at the outlet of the second air inlet channel rises to the first vortex center under the suction force of the first vortex center, the air is mixed with the disturbed hydrogen to form a first mixed airflow; The first mixed airflow rises to the second cylindrical channel, passes through the serrated structure on the lower surface of the bottom cover of the second cylindrical channel, and reaches the second cylindrical channel.

4. The burner according to claim 1, characterized in that The burner further includes a thermoelectric power generation module, the thermoelectric power generation module including a first temperature end and a second temperature end, the first temperature being higher than the second temperature; The first temperature end is in contact with the outer side of the combustion body, and the heat generated by the combustion body during the combustion process provides a heat source for the first temperature end of the thermoelectric power generation module; The second temperature end is connected to a water-cooling head, which surrounds the outer wall of the first temperature end. Cooling liquid circulates inside the water-cooling head. The cooling liquid absorbs heat from the first cylindrical channel and provides a cold source for the second temperature end of the thermoelectric power generation module. The electric energy generated by the temperature difference power generation module is connected to the two blowers of the burner through wires, driving the intake of central wind and swirl air respectively.

5. The burner according to claim 4, characterized in that The water cooling head is connected to the aluminum radiator, the cooling fan, the expansion water tank and the circulating water pump in sequence through a circulation pipeline; Among them, the circulating water pump drives the coolant to flow in a closed loop, and after absorbing heat, it is cooled by the aluminum radiator and cooling fan, and the expansion water tank compensates for the thermal expansion and contraction of the liquid.

6. A combustion control method for a dual-air-adjusted pure hydrogen swirl burner, characterized in that: The method is applied to the burner according to any one of claims 1 to 5, and the method comprises: Pure hydrogen is introduced into the first opening of the side wall of the first cylindrical channel through the hydrogen inlet channel; The rotating blades are started to drive the pure hydrogen gas flowing from the hydrogen inlet channel into the first cylindrical channel to rotate to form a first vortex flow; Air is introduced into the first cylindrical channel through the second air inlet channel to form a first direct flow at the center of the first swirl flow. The first swirl flow and the first direct flow are mixed to form a first mixed flow that rises to the second cylindrical channel. Air is introduced into the second cylindrical channel through the first air intake channel, and a second vortex is formed under the drive of the first mixed flow. The first mixed flow and the second vortex are mixed to form a second mixed flow that rises to the combustion body for combustion.

7. The method according to claim 6, characterized in that Before introducing pure hydrogen into the first opening of the side wall of the first cylindrical channel through the hydrogen inlet channel, the method further includes: Obtain the total amount of mixed gas that needs to be burned by the burner; Conduct multiple combustion tests, record the combustion effects at different hydrogen-air mixture ratios, and determine the optimal mixture ratio; Calculating the amount of hydrogen and air required for each combustion based on the total amount of the mixed gas and the optimal mixing ratio; The intake amounts of the hydrogen intake passage, the first air intake passage, and the second air intake passage are controlled according to the calculated hydrogen amount and air amount.

8. The method according to claim 6, characterized in that Before introducing air into the second cylindrical channel through the first air inlet channel, the method further includes: Obtaining a speed at which the hydrogen is driven to rotate by the rotating blades in the first cylindrical channel, and using the speed as a rotational speed of the hydrogen; Based on the ideal state of hydrogen and air mixing and combustion in the burner, a proportional relationship between the hydrogen rotation speed and the rotation speed of the air when the second swirl is formed under the drive of the first mixed flow after the air is introduced into the first air inlet channel is preset; The rotation speed of the air in the second vortex is calculated based on the rotation speed and the proportional relationship of the hydrogen.

9. The method according to claim 7, characterized in that The calculated hydrogen amount and air amount are used to control the intake amounts of the hydrogen intake channel, the first air intake channel, and the second air intake channel, including: measuring the volume of the mixing portion and the airflow velocity at the outlet of the mixing portion; Set the safe mixing ratio range according to the stoichiometric ratio of hydrogen to air; calculating the mixing time required to achieve a safe mixing ratio based on the volume and outlet air flow velocity; The air flow rate of the second air intake channel, the hydrogen flow rate of the hydrogen intake channel, and the air flow rate of the first air intake channel are obtained, and the intake air volume is calculated in combination with the mixing time.

10. The method according to claim 6, characterized in that During the combustion process, the air flow velocity at the outlet of the mixing part and the combustion state in the combustion body are monitored in real time; If the air flow velocity at the outlet of the mixing portion is less than the hydrogen flame propagation velocity, the air supply velocity of the second air intake passage is increased, and the air intake volume of the hydrogen intake passage and the first air intake passage is adjusted.

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