Combustor

Abstract

The utility model discloses a combustor, and relates to the technical field of combustion equipment. The burner block is at least partially located in a hearth of a combustion furnace, the first-stage combustion assembly is arranged on the peripheral side of the burner block, the burner block is provided with a mixing groove, and a groove opening of the mixing groove is communicated with the interior of the hearth; the first gas channel penetrates through the burner block in the first direction and is used for introducing combustion-supporting gas into the hearth; the second gas channel comprises a first end and a second end; the first end is communicated with the first gas channel, and the second end is communicated with the mixing tank; the third gas channel comprises a third end and a fourth end; the third end penetrates through the outer side wall of the burner block, and the fourth end is communicated with the mixing tank; the first-stage combustion assembly comprises a first-stage gas nozzle; the first-stage gas nozzle is arranged opposite to the third end, and a gap is formed between the first-stage gas nozzle and the third end; and the gas injection direction of the first-stage gas nozzle is parallel to the extension direction of the third gas channel. The burner is used for reducing environmental pollution and prolonging the service life of equipment.

Description

Technical Field

[0001] This utility model relates to the field of combustion equipment technology, and in particular to a burner. Background Technology

[0002] Nitrogen oxides (NO) X Pollution mainly consists of nitric oxide (NO) and nitrogen dioxide (NO2). When their concentration and duration in the atmosphere reach a level that has a harmful effect on humans, animals, plants, and other substances, it constitutes pollution.

[0003] During the combustion process in petrochemical industrial furnaces, NO... X There are three ways in which it is generated: one is through the oxidation of nitrogen in the air at high temperatures, known as thermal NO. X Secondly, the CH radicals generated from the high-temperature decomposition of carbon and nitrogen compounds in fuel volatiles react with nitrogen in the air to produce HCN and N, which then react with oxygen at an extremely rapid rate to produce NO. X This is called instantaneous NO. X Thirdly, NO is generated from the oxidation of nitrogen-containing compounds in fuel during combustion. X It is called fuel-type NO X Among them, thermal NO X The formation rate of NO is related to the combustion temperature; if the combustion temperature is too high, it will cause thermal NO to form. X Uncontrolled emissions increase environmental pollution and can also cause local overheating, affecting equipment lifespan.

[0004] In existing technologies, to control combustion temperature, either an additional bellows is installed to control the oxygen content introduced into the furnace, or an additional recirculation combustion component (such as a cyclone separator) is installed. These methods complicate the overall structure of the burner and the temperature control process, thus reducing the efficiency of thermal NOx production. X The emission reduction effect is not good. Therefore, there is an urgent need for a burner to solve the above-mentioned technical problems. Utility Model Content

[0005] The purpose of this invention is to provide a burner that reduces environmental pollution and extends equipment lifespan.

[0006] To achieve this objective, the present invention adopts the following technical solution:

[0007] This invention provides a burner for providing heat to a combustion furnace. The burner includes a burner brick located at least partially inside the furnace chamber of the combustion furnace. The burner brick is provided with: a mixing groove, the opening of which communicates with the interior of the furnace chamber; a first gas passage penetrating the burner brick along a first direction for introducing combustion-supporting gas into the furnace chamber; a second gas passage including a first end and a second end; the first end communicating with the first gas passage and the second end communicating with the mixing groove; and a third gas passage including a third end and a fourth end; the third end penetrating the outer wall of the burner brick and the fourth end communicating with the mixing groove. The burner also includes a primary combustion assembly disposed on the outer periphery of the burner brick; the primary combustion assembly includes a primary gas nozzle; the primary gas nozzle is directly opposite the third end and has a gap between them; the jet direction of the primary gas nozzle is parallel to the extension direction of the third gas passage.

[0008] In some embodiments, the burner brick is further provided with a mounting hole; the mounting hole penetrates the burner brick along the first direction; an ignition component is installed in the mounting hole, the ignition component is used to ignite the fuel gas inside the furnace; the mixing groove is an annular mixing groove, the mixing groove is arranged around the mounting hole.

[0009] In some embodiments, the second end and the fourth end are tangential to the outer wall of the mixing tank in the same clockwise direction.

[0010] In some embodiments, the number of the first gas channels is multiple, and the multiple first gas channels are evenly spaced around the mixing tank.

[0011] In some embodiments, the first gas channel includes a conical sub-channel and a cylindrical sub-channel; the conical sub-channel includes a fifth end and a sixth end, the cross-sectional area of ​​the fifth end being smaller than the cross-sectional area of ​​the sixth end; the fifth end is connected to the interior of the furnace, and the sixth end is connected to the cylindrical sub-channel; the first end is connected to the end of the cylindrical sub-channel near the sixth end.

[0012] In some embodiments, the burner further includes: a secondary combustion assembly disposed on the outer periphery of the burner brick; the secondary combustion assembly includes a secondary gas nozzle, the jet direction of the secondary gas nozzle being set at an angle to the jet direction of the primary gas nozzle; the secondary gas nozzle and the primary gas nozzle are capable of jetting simultaneously.

[0013] In some embodiments, the bottom of the mixing tank is inclined, and there is a first angle between the plane of the bottom and the second direction; the second direction is at an angle to the first direction; the second end is connected to the bottom of the mixing tank; there is a second angle between the centerline of the second end and the second direction; the angle of the second angle is the same as the angle of the first angle, and both are acute angles.

[0014] In some embodiments, the fourth end is connected to the tank body of the mixing tank; there is a third angle between the centerline of the fourth end and the second direction; the angle of the third angle is smaller than the angle of the second angle.

[0015] In some embodiments, the ratio of the cross-sectional area of ​​the first gas channel to the cross-sectional area of ​​the second gas channel ranges from 7:3 to 8:2.

[0016] In some embodiments, a combustion-supporting gas distribution pipeline is further included, which is connected to the first gas channel.

[0017] The beneficial effects of this utility model are:

[0018] This utility model provides a burner that includes a mixing groove on the burner brick that communicates with the interior of the furnace; a first gas channel that penetrates the burner brick along a first direction to introduce combustion-supporting gas into the furnace; a second gas channel with its first end connected to the first gas channel and its second end connected to the mixing groove; and a third gas channel with its third end penetrating the outer wall of the burner brick and its fourth end connected to the mixing groove. Simultaneously, a primary combustion assembly is provided on the outer periphery of the burner brick, with the primary gas nozzle of the primary combustion assembly facing the third end of the third gas channel, with a gap between them. The jet direction of the primary gas nozzle is parallel to the extension direction of the third gas channel. This arrangement ensures that, during the process of the combustion-supporting gas entering the furnace through the first gas channel, most of the combustion-supporting gas enters the furnace directly through the first gas channel, while a small portion flows into the second gas channel, which is connected to the first gas channel, and then into the mixing tank. Simultaneously, when the primary gas nozzle injects fuel gas into the third gas channel, the high velocity of the fuel gas due to the injection action of the primary gas nozzle causes a decrease in pressure at the opening of the third end of the third gas channel and inside the third gas channel. This draws the flue gas from the furnace to the opening of the third end of the third gas channel, where it enters the mixing tank along with the fuel gas injected by the primary gas nozzle. At this point, the mixing tank simultaneously contains a small portion of the combustion-supporting gas from the second gas channel, the fuel gas from the third gas channel, and the furnace flue gas, all of which mix within the mixing tank. When the mixed gas in the ignition mixing tank forms the primary combustion zone, the overall oxygen concentration of the mixed gas decreases due to the mixing of flue gas from the furnace. At this time, the combustion type in the primary combustion zone is oxygen-deficient combustion. Under oxygen-deficient conditions, the fuel gas cannot be completely oxidized, and the heat released by the combustion of a unit of fuel gas is reduced, thus lowering the combustion temperature. This lower combustion temperature reduces the reaction rate of the Zeldovich chain reaction, while simultaneously increasing the reaction rate of CH radicals and NO. X Precursors (such as HCN and NH3) combine to form N2, inhibiting NO. X The formation of NO, that is, the reduction of NO as the combustion temperature decreases. X Reduce NO generation rate X This reduces emissions and environmental pollution, while also preventing localized overheating and extending equipment lifespan. Furthermore, the aforementioned burner only requires modification to the burner brick structure, eliminating the need for additional oxygen supply or recirculation combustion components. Its simple structure and straightforward temperature control process ensure reduced thermal NOx emissions. X The effect of emissions. Attached Figure Description

[0019] Figure 1 This is a structural diagram of a burner provided in a specific embodiment of this utility model;

[0020] Figure 2 This is a structural diagram of a burner from another perspective, provided in a specific embodiment of this utility model;

[0021] Figure 3 yes Figure 1 An enlarged structural diagram of region A in the structure shown;

[0022] Figure 4 yes Figure 1 An enlarged structural diagram of region B in the structure shown.

[0023] In the picture:

[0024] 1. Combustion furnace; 11. Furnace chamber; 2. Burner brick; 21. Mixing tank; 22. First gas passage; 221. Conical sub-passage; 2211. Fifth end; 2212. Sixth end; 222. Cylindrical sub-passage; 23. Second gas passage; 231. First end; 232. Second end; 24. Third gas passage; 241. Third end; 242. Fourth end; 25. Mounting hole; 26. First mounting slot; 27. Second mounting slot; 3. Primary combustion assembly; 31. Primary gas nozzle; 4. Ignition assembly; 5. Secondary combustion assembly; 51. Secondary gas nozzle; 6. Combustion-supporting gas distribution pipeline; 61. Main pipeline; 62. Branch pipeline;

[0025] a1, first included angle; a2, second included angle; a3, third included angle; S1, primary combustion zone; S2, secondary combustion zone; X1, first direction; X2, second direction. Detailed Implementation

[0026] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, and not the entire structure.

[0027] In the description of this utility model, unless otherwise explicitly specified and limited, the terms "connected", "linked", and "fixed" should be interpreted broadly. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0028] In this invention, unless otherwise expressly specified and limited, the first feature being "above" or "below" the second feature may include direct contact between the first and second features, or contact between the first and second features not being in direct contact but through another feature between them.

[0029] In the description of this embodiment, the terms "upper," "lower," "left," and "right," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. In addition, the terms "first" and "second" are only used for distinction in description and have no special meaning.

[0030] In the combustion process of petrochemical industrial furnaces, thermal NO... X The formation of [a substance] follows the Zeldovich chain reaction mechanism, with the core steps being: 1. Dissociation of oxygen atoms: O₂ → 2O at high temperature, with an activation energy of 498 kJ / mol; 2. N₂ + O → NO + N, with an activation energy of 315 kJ / mol; 3. Oxidation of nitrogen atoms: N + O₂ → NO + O, with an activation energy of 26 kJ / mol. Meanwhile, the exponential effect of temperature on the reaction rate is reflected in the Arrhenius equation: In the formula, for every 100K (approximately 100℃) increase in temperature T, the reaction rate constant k increases by approximately 6 to 7 times. Therefore, it is evident that lowering the combustion temperature has a significant effect on reducing NO levels. X The generation rate is crucial.

[0031] Combination Figure 1 , Figure 2 As shown, this embodiment provides a burner for providing heat to a combustion furnace 1. The burner includes a burner brick 2 located at least partially inside the furnace chamber 11 of the combustion furnace 1, and a primary combustion assembly 3 disposed on the outer periphery of the burner brick 2. The burner brick 2 is made of corundum material. The upper half of the burner brick 2 has a frustum-shaped structure, and the lower half has a cylindrical structure. The cross-sectional area of ​​the upper half of the burner brick 2 (the bottom surface area of ​​the frustum-shaped structure) is smaller than the cross-sectional area of ​​the lower half of the burner brick 2 (the top surface area of ​​the cylindrical structure). By setting the upper half of the burner brick 2 to a frustum-shaped structure, a gradually expanding gas flow space can be formed, which can effectively reduce the flow resistance of high-speed gas. Since the resistance to high-speed gas flow is proportional to the square of its velocity, the conical design (i.e., the frustum-shaped structure) allows the airflow to diffuse gradually, reducing local pressure loss and thus improving combustion efficiency. Furthermore, the frustum-shaped structure helps guide the mixing process of fuel gas and combustion-supporting gas, facilitating the formation of specific flame shapes (such as disc-shaped flames, which can make heat radiation more uniform and avoid localized high-temperature concentration). By setting the lower half of the burner brick 2 to a cylindrical structure, it is easier for the lower half of the burner brick 2 to fit tightly with the sidewalls or other refractory structures of the furnace chamber 11 of the combustion furnace 1, avoiding stress concentration problems caused by abrupt shape changes.

[0032] It is easy to understand that the "combustion-supporting gas" mentioned above can be pure oxygen, air (including conventional air and preheated air), or oxygen-enriched air (oxygen concentration of 25% to 95%). Those skilled in the art can make flexible choices according to the actual use scenario, and no further restrictions are imposed here.

[0033] Combination Figure 1 , Figure 2 As shown, the burner brick 2 is provided with a mixing groove 21, a first gas channel 22, a second gas channel 23, and a third gas channel 24. The mixing groove 21 is used to mix the combustion-supporting gas and the fuel gas. The mixing groove 21 is, for example, a cylindrical groove or an annular deep groove, as long as it can provide mixing space for the combustion-supporting gas and the fuel gas. The shape of the mixing groove 21 is not limited here. The opening of the mixing groove 21 is connected to the inside of the furnace chamber 11 of the combustion furnace 1, so that the mixed gas (combustion-supporting gas and fuel gas) can enter the furnace chamber 11.

[0034] like Figure 1 As shown, the first gas channel 22 extends through the burner brick 2 along the first direction X1. This first gas channel 22 is used to introduce combustion-supporting gas (e.g., pure oxygen) into the furnace chamber 11 of the combustion furnace 1. It is understood that, in order to introduce combustion-supporting gas into the furnace chamber 11, the burner may also include a combustion-supporting gas distribution pipe 6, which is connected to the first gas channel 22, supplying combustion-supporting gas from a gas source (e.g., a gas cylinder) into the furnace chamber 11 of the combustion furnace 1. Figure 1 Taking the perspective shown as an example, the first gas channel 22 connects the inside and outside of the furnace 11 from top to bottom, and the combustion-supporting gas distribution pipeline 6 is located below the first gas channel 22 and is connected to the first gas channel 22.

[0035] Combination Figure 1 , Figure 2 As shown, the second gas channel 23 includes a first end 231 and a second end 232. The second gas channel 23 is, for example, a cylindrical channel. The first end 231 of the second gas channel 23 is connected to the first gas channel 22, and the second end 232 of the second gas channel 23 is connected to the mixing tank 21.

[0036] Combination Figure 1 , Figure 2 As shown, the third gas channel 24 includes a third end 241 and a fourth end 242. The third gas channel 24 is, for example, a cylindrical channel. The third end 241 of the third gas channel 24 penetrates the outer wall of the burner brick 2, and the fourth end 242 of the third gas channel 24 communicates with the mixing tank 21.

[0037] like Figure 2As shown, the primary combustion assembly 3 is disposed on the outer periphery of the burner brick 2. The method for disposing the primary combustion assembly 3 on the outer periphery of the burner brick 2 is as follows: a first mounting groove 26 is provided on the outer wall of the burner brick 2, and the primary combustion assembly 3 is installed in the first mounting groove 26 by means of fasteners (e.g., bolts) or supports (e.g., support tubes). It is easy to understand that the inner wall of the first mounting groove 26 should be adapted to the shape of the primary combustion assembly 3, so that the primary combustion assembly 3 can be installed precisely within the first mounting groove 26 without protruding from the outer wall of the burner brick 2.

[0038] Combination Figure 1 , Figure 2 As shown, the primary combustion assembly 3 includes a primary gas injector 31, which is positioned directly opposite the third end 241 of the third gas passage 24, with a gap between them. The jet direction of the primary gas injector 31 is parallel to the extension direction of the third gas passage 24. In other words, the primary gas injector 31 has a first jet hole for injecting fuel gas, the centerline of which coincides with the centerline of the third gas passage 24, and a gap exists between the first jet hole and the opening of the third end 241 of the third gas passage 24. Furthermore, it is easy to understand that, in order to synchronously inject fuel gas into the furnace 11 of the combustion furnace 11, the primary gas injector 31 may also have a second jet port, the second jet port injecting fuel gas in a direction pointing into the furnace 11 of the combustion furnace 1.

[0039] Therefore, the burner provided in this embodiment has a mixing groove 21 on the burner brick 2 that communicates with the inside of the furnace 11, a first gas channel 22 that penetrates the burner brick 2 along a first direction X1 for introducing combustion-supporting gas into the furnace 11, a second gas channel 23 that has a first end 231 communicating with the first gas channel 22 and a second end 232 communicating with the mixing groove 21, and a third gas channel 24 that has a third end 241 penetrating the outer wall of the burner brick 2 and a fourth end 242 communicating with the mixing groove 21. At the same time, a primary combustion assembly 3 is also provided on the outer wall of the burner brick 2, and the primary gas nozzle 31 of the primary combustion assembly 3 is positioned directly opposite the third end 241 of the third gas channel 24 with a gap between them, and the jet direction of the primary gas nozzle 31 is parallel to the extension direction of the third gas channel 24. This ensures that, during the process of the combustion-supporting gas being introduced into the furnace 11 of the combustion furnace 1 through the first gas channel 22, most of the combustion-supporting gas will directly enter the furnace 11 through the first gas channel 22, while a small portion will flow into the second gas channel 23, which is connected to the first gas channel 22, and then into the mixing tank 21. Simultaneously, when the primary gas nozzle 31 injects fuel gas into the third gas channel 24, the fuel gas has a high flow velocity due to the injection action of the primary gas nozzle 31. This causes a decrease in pressure at the opening of the third end 241 of the third gas channel 24 and inside the third gas channel 24. The flue gas in the furnace 11 is then drawn to the opening of the third end 241 of the third gas channel 24, and the fuel gas injected by the primary gas nozzle 31 enters the mixing tank 21 through the third gas channel 24. At this time, the mixing tank 21 simultaneously contains a small portion of the combustion-supporting gas from the second gas channel 23, the fuel gas from the third gas channel 24, and the furnace flue gas, and these three gases mix within the mixing tank 21. When the mixed gas in the ignition mixing tank 21 forms the primary combustion zone S1, the overall oxygen concentration of the mixed gas decreases due to the mixing of flue gas from the furnace. At this time, the combustion type in the primary combustion zone S1 is oxygen-deficient combustion. Under oxygen-deficient conditions, the fuel gas cannot be completely oxidized, and the heat released by the combustion of a unit of fuel gas is reduced, thus lowering the combustion temperature. This decrease in combustion temperature reduces the reaction rate of the Zeldovich chain reaction, while simultaneously increasing the reaction rate of CH radicals and NO. X Precursors (such as HCN and NH3) combine to form N2, inhibiting NO. X The formation of NO, that is, the reduction of NO as the combustion temperature decreases. X Reduce NO generation rate X This reduces emissions and environmental pollution, while also preventing localized overheating and extending equipment lifespan. Furthermore, the aforementioned burner only requires structural modifications to the burner brick 2, eliminating the need for additional oxygen supply or recirculation combustion components. Its simple structure and straightforward temperature control process ensure effective reduction of thermal NOx emissions.X The effect of emissions.

[0040] In some embodiments, such as Figure 1 As shown, the burner brick 2 is also provided with a mounting hole 25. The mounting hole 25 penetrates the burner brick 2 along the first direction X1. An ignition assembly 4 is installed inside the mounting hole 25, and the ignition assembly 4 is installed in the mounting hole 25 by means of mechanical connection such as a flange or bolts. The ignition assembly 4 is used to ignite the fuel gas inside the furnace 11. Exemplarily, the ignition assembly 4 is a continuous lamp, which includes a combustion head assembly, an ignition and flame transmission assembly, a detection and feedback assembly, etc. The combustion head assembly includes structures such as an ejector (e.g., a Venturi ejector) and a nozzle; the ignition and flame transmission assembly includes an igniter (e.g., a piezoelectric ceramic), a flame transmission cylinder, a return flame structure, etc.; the detection and feedback assembly includes a flame detection module (e.g., an ion probe) and a temperature field monitoring module (e.g., using a multimode optical fiber to analyze the temperature field distribution in real time through Raman scattering), etc.

[0041] It is readily understood that the aforementioned ignition component 4 can also be configured in other forms or ignited using other methods. For example, an independent pre-combustion chamber can be set before the burner; or an auxiliary ignition method can be used (using liquid fuel or solid igniter for ignition); or laser-induced ignition can be used; or even manual torch ignition can be used. Those skilled in the art can flexibly choose the configuration according to actual usage requirements, and no further limitations are made here.

[0042] Combination Figure 1 , Figure 2 As shown, the mixing groove 21 is an annular mixing groove 21. The mixing groove 21 is arranged around the mounting hole 25, that is, the center of the inner circle of the annular mixing groove 21 coincides with the center line of the mounting hole 25.

[0043] In the aforementioned burner, by providing mounting holes 25 on the burner brick 2 and installing the ignition assembly 4 within the mounting holes 25, the ignition of the fuel gas in the furnace 11 of the combustion furnace 1 is facilitated. Simultaneously, the mixing tank 21 is configured as an annular mixing tank surrounding the mounting holes 25, allowing the combustion-supporting gas, fuel gas, and furnace flue gas to spiral upwards along the sidewall of the annular mixing tank 21 after entering it. This ensures sufficient contact between the combustion-supporting gas, fuel gas, and furnace flue gas, improving the uniformity of the mixing of the three gases.

[0044] In some embodiments, combined with Figure 1 , Figure 3As shown, the bottom of the mixing tank 21 is inclined, and there is a first angle a1 between the plane of the bottom of the mixing tank 21 and the second direction X2. The second end 232 of the second gas channel 23 is connected to the bottom of the mixing tank 21. At the same time, there is a second angle a2 between the centerline of the second end 232 of the second gas channel 23 and the second direction X2. The angle of the second angle a2 is the same as the angle of the first angle a1, and both are acute angles, for example, both are 45° or 30°.

[0045] In the aforementioned burner, by connecting the second gas channel 23 to the bottom of the mixing tank 21, when the combustion-supporting gas is introduced into the mixing tank 21 through the second gas channel 23, the combustion-supporting gas flows from the bottom to the opening of the mixing tank 21. During this upward flow, the combustion-supporting gas inevitably comes into contact with the fuel gas and furnace flue gas within the mixing tank 21, ensuring complete mixing of the three gases. Simultaneously, the second gas channel 23 is inclined relative to the second direction X2, giving the combustion-supporting gas an upward flow tendency after entering the mixing tank 21. This ensures that the mixed gas can be quickly introduced into the furnace 11 from the mixing tank 21, preventing the mixed gas from remaining in the mixing tank 21 for too long, which could lead to backfire and ensure the safety of the combustion process.

[0046] In some embodiments, combined with Figure 1 , Figure 4 The fourth end 242 of the third gas channel 24 is connected to the tank body of the mixing tank 21. A third angle a3 exists between the centerline of the fourth end 242 of the third gas channel 24 and the second direction X2. This third angle a3 is also an acute angle, and its angle is smaller than the angle of the second angle a2. For example, when the angle of the second angle a2 is 45°, the angle of the third angle a3 is 30°; or, when the angle of the second angle a2 is 30°, the angle of the third angle a3 is 20°. This configuration ensures that the fuel gas and furnace flue gas have an upward flow tendency after entering the mixing tank 21, further guaranteeing that the mixed gas can be quickly introduced into the furnace 11 from the mixing tank 21. This prevents the mixed gas from remaining in the mixing tank 21 for too long, which could lead to backfire and further ensure the safety of the combustion process.

[0047] In some embodiments, the ratio of the cross-sectional area of ​​the first gas channel 22 to the cross-sectional area of ​​the second gas channel 23 ranges from 7:3 to 8:2. It is readily understood that the "cross-sectional area of ​​the first gas channel 22" refers to the area of ​​the cross-section perpendicular to the axis of the first gas channel 22, and the same applies to the "cross-sectional area of ​​the second gas channel 23." Furthermore, the cross-sectional area of ​​the gas channel is positively correlated with the amount of combustion-supporting gas introduced into the gas channel; that is, the larger the cross-sectional area of ​​the gas channel, the more combustion-supporting gas is introduced into the gas channel, and the smaller the cross-sectional area of ​​the gas channel, the less combustion-supporting gas is introduced into the gas channel.

[0048] For example, if the ratio is 7:3, then the amount of combustion-supporting gas entering the first gas channel 22 accounts for 70% of the total combustion-supporting gas, and the amount entering the second gas channel 23 accounts for 30% of the total combustion-supporting gas. As another example, if the ratio is 7.25:2.75, then the amount of combustion-supporting gas entering the first gas channel 22 accounts for 72.5% of the total combustion-supporting gas, and the amount entering the second gas channel 23 accounts for 27.5% of the total combustion-supporting gas. As yet another example, if the ratio is 7.5:2.5, then the amount of combustion-supporting gas entering the first gas channel 22 accounts for 75% of the total combustion-supporting gas, and the amount entering the second gas channel 23 accounts for 25% of the total combustion-supporting gas. As yet another example, if the ratio is 7.75:2.25, then the amount of combustion-supporting gas entering the first gas channel 22 accounts for 77.5% of the total combustion-supporting gas, and the amount entering the second gas channel 23 accounts for 22.5% of the total combustion-supporting gas. For example, if the ratio is 8:2, then the amount of combustion-supporting gas introduced into the first gas channel 22 accounts for 80% of the total combustion-supporting gas, and the amount of combustion-supporting gas introduced into the second gas channel 23 accounts for 20% of the total combustion-supporting gas.

[0049] By setting the cross-sectional area of ​​the first gas channel 22 and the cross-sectional area of ​​the second gas channel 23 as described above, the combustion-supporting gas introduced into the first gas channel 22 and the combustion-supporting gas introduced into the second gas channel 23 are both in suitable quantities, which can ensure that both primary premixed combustion (i.e., the combustion-supporting gas introduced into the second gas channel 23 is mixed in the mixing tank 21 and then ignited) and secondary diffusion combustion (i.e., the combustion-supporting gas introduced into the first gas channel 22 is directly ignited after entering the furnace chamber 11 of the combustion furnace 1) have good combustion effects.

[0050] It is easy to understand that the angles of the first included angle a1, the second included angle a2, the third included angle a3, and the height of the mixing tank 21 in the first direction X1 can all affect the residence time of the mixed gas in the mixing tank 21. Therefore, those skilled in the art can obtain the optimal angles of the first included angle a1, the second included angle a2, the third included angle a3, and the height of the mixing tank 21 in the first direction X1 through CFD (Computational Fluid Dynamics) numerical simulation according to different application scenarios, thereby obtaining a safe and stable primary combustion zone S1.

[0051] In some embodiments, such as Figure 2 As shown, the second end 232 of the second gas channel 23 and the fourth end 242 of the third gas channel 24 are tangent to the outer wall of the mixing tank 21 in the same clockwise direction. That is, the second end 232 of the second gas channel 23 and the fourth end 242 of the third gas channel 24 are both tangent to the outer wall of the mixing tank 21 in a clockwise direction, or the second end 232 of the second gas channel 23 and the fourth end 242 of the third gas channel 24 are both tangent to the outer wall of the mixing tank 21 in a counterclockwise direction.

[0052] With the above configuration, the airflow (i.e., combustion-supporting gas) entering the mixing tank 21 from the second end 232 of the second air intake channel and the airflow (i.e., fuel gas and furnace flue gas) entering the mixing tank 21 from the fourth end 242 of the third air intake channel can be injected into the mixing tank 21 in the same direction of rotation, forming a swirling flow. Under the action of the swirling flow, the movement trajectories of the fuel gas, combustion-supporting gas, and furnace flue gas are spiral-shaped, prolonging the mixing path and effective contact time of the three gases, making the mixing of the three gases more uniform. Under the action of the swirling flow, fuel clumps can be sheared and broken up, reducing the standard deviation of the equivalence ratio distribution, improving the spatial homogenization level of fuel-combustion gas mixing in the combustion system, and improving the completeness of combustion. Simultaneously, under the centrifugal force of the swirling flow, macroscopic pre-separation of fuel (fuel gas) and oxidant (combustion-supporting gas) can be achieved, forming a radial concentration gradient where heavy fuel adheres to the wall and light oxidant approaches the axis. This stratification is equivalent to "pre-arranging" the fuel and oxidant to the optimal reaction distance, avoiding local over-rich or over-lean regions caused by random collisions in direct injection mixing. Furthermore, between the concentration gradient layers formed by the stratification, the shear vortices generated by the swirling flow trigger turbulent mixing. The amplification of the concentration gradient at the vortex interface increases the molecular diffusion rate, and the internal recirculation zone formed within the swirling flow can repeatedly entrain fuel particles into the oxidant-rich zone, achieving cyclically enhanced combustion. In addition, the stratification process and the mixing reaction have different time scales. Centrifugal stratification is completed in milliseconds, while turbulent mixing and chemical reactions are on the order of 10ms to 100ms. This time difference allows the combustion system to first complete component positioning and then concentrate energy for efficient reaction, avoiding energy dissipation caused by simultaneous disordered collisions in traditional mixing, thus improving combustion efficiency.

[0053] In some embodiments, such as Figure 1 As shown, the first gas channel 22 includes a conical sub-channel 221 and a cylindrical sub-channel 222. The conical sub-channel 221 includes a fifth end 2211 and a sixth end 2212, with the cross-sectional area of ​​the fifth end 2211 being smaller than that of the sixth end 2212. The fifth end 2211 communicates with the interior of the furnace 11, and the sixth end 2212 communicates with the cylindrical sub-channel 222. The first end 231 of the second gas channel 23 is connected to the end of the cylindrical sub-channel 222 near the sixth end 2212.

[0054] Specifically, with Figure 1Taking the shown perspective as an example, the lower half of the first gas channel 22 is a cylindrical sub-channel 222, and the upper half is a conical sub-channel 221 (i.e., a tapered nozzle structure). The upper end of the conical sub-channel 221 is the fifth end 2211, and the lower end is the sixth end 2212. The cross-sectional area of ​​the fifth end 2211 is smaller than that of the sixth end 2212. In other words, the cross-sectional area of ​​the conical sub-channel 221 gradually decreases from bottom to top. The flow velocity of the combustion-supporting gas increases as the cross-sectional area of ​​the upper half of the first gas channel 22 (conical sub-channel 221) decreases. This arrangement increases the flow velocity of the combustion-supporting gas flowing through the first gas channel 22, creating a turbulence effect, promoting thorough mixing of the combustion-supporting gas and fuel gas, enhancing the disturbance effect of the combustion reaction, ensuring uniform contact between the combustion air and fuel gas, and thus improving combustion efficiency. Meanwhile, the first end 231 of the second gas channel 23 is connected to the upper end of the cylindrical sub-channel 222 (i.e., the end near the sixth end 2212 of the conical sub-channel 221). This allows the combustion-supporting gas introduced into the first gas channel 22 to flow from the cylindrical sub-channel 222 to the conical sub-channel 221. As the cross-sectional area of ​​the conical sub-channel 221 decreases, some of the combustion-supporting gas is forced to flow to the first end 231 near the sixth end 2212 of the conical sub-channel 221. This ensures that some of the combustion-supporting gas can flow smoothly into the second gas channel 23, thereby ensuring that the gas mixing process in the mixing tank 21 can proceed smoothly.

[0055] It is easy to understand that the structures of the second gas channel 23 and the third gas channel 24 can also be set with reference to the structure of the first gas channel 22. That is, the first end 231 of the second gas channel 23 is set as a cylindrical channel, and the second end 232 of the second gas channel 23 is set as a conical channel; the third end 241 of the third gas channel 24 is set as a cylindrical channel, and the fourth end 242 of the third gas channel 24 is set as a conical channel. With this setting, the flow velocity of the gas (combustion-supporting gas) flowing through the second gas channel 23 and the gas (fuel gas and furnace flue gas) flowing through the third gas channel 24 can be increased, forming a turbulence effect, further promoting the full mixing of the three gases, ensuring uniform contact of the three gases, and further improving combustion efficiency.

[0056] In some embodiments, such as Figure 2As shown, there are multiple first gas channels 22, which are evenly spaced around the mixing tank 21. For example, there are four first gas channels 22, which are evenly spaced around the mixing tank 21. In other words, the four first gas channels 22 are arranged in a circular array with a pitch angle of 90° around the axis of the burner brick 2. Alternatively, there are six first gas channels 22, which are evenly spaced around the mixing tank 21. That is, the six first gas channels 22 are arranged in a circular array with a pitch angle of 60° around the axis of the burner brick 2. By using multiple first gas inlet channels evenly spaced around the mixing tank 21, the fuel gas and combustion-supporting gas can be mixed more evenly. Simultaneously, the uniform gas inlet design can effectively control the stability of combustion and the shape of the flame, avoid excessively high local temperatures, and optimize heat transfer efficiency.

[0057] In some embodiments, such as Figure 2 As shown, multiple first mounting slots 26 are evenly spaced on the outer wall of the burner brick 2. Correspondingly, there are also multiple primary combustion components 3, for example, four primary combustion components 3. The number of primary combustion components 3 is equal to the number of first mounting slots 26. Multiple primary combustion components 3 are arranged one-to-one with multiple first mounting slots 26. During combustion, fuel gas is simultaneously introduced into the mixing tank 21 using multiple primary combustion components 3 evenly spaced on the outer wall of the burner brick 2, which accelerates the mixing speed of fuel gas and combustion-supporting gas and improves the uniformity of the mixture. Furthermore, the multiple first mounting slots 26 corresponding to the multiple primary combustion components 3 provide installation positions for each component, preventing the components from protruding from the outer wall of the burner brick 2 and facilitating the installation of the burner brick 2 inside the furnace chamber 11 of the combustion furnace 1.

[0058] In some embodiments, combined with Figure 1 , Figure 2 As shown, the burner also includes a secondary combustion assembly 5. This secondary combustion assembly 5 is located on the outer periphery of the burner brick 2. The secondary combustion assembly 5 includes a secondary gas nozzle 51, the jet direction of which is angled to the jet direction of the primary gas nozzle 31. Here, the angle between them is, for example, 45°, 60°, or 75°. In other words, from... Figure 1Taking the shown perspective as an example, the jet direction of the secondary gas nozzle 51 forms an angle with the first direction X1, or in other words, the jet direction of the secondary gas nozzle 51 is parallel to the outer peripheral wall of the upper half (i.e., the frustum-shaped structure) of the burner brick 2. The jet direction of the secondary gas nozzle 51 of the secondary combustion assembly 5 points towards the interior of the furnace 11 of the combustion furnace 1. This secondary gas nozzle 51 and the primary gas nozzle 31 of the primary combustion assembly 3 can perform jet injection simultaneously. For example, when the combustion-supporting gas is introduced through the first gas channel 22, a small portion of the combustion-supporting gas will enter the mixing tank 21 through the second gas channel 23, while most of the combustion-supporting gas will continue to enter the furnace 11 of the combustion furnace 1 along the first gas channel 22. When the combustion action begins, the first-stage gas nozzle 31 of the first-stage combustion component 3 injects fuel gas into the third gas channel 24. The fuel gas injected by the first-stage combustion component 3 enters the mixing tank 21 and mixes with the combustion-supporting gas. After being ignited by the ignition component 4, it forms the primary combustion zone S1. At the same time, the second-stage gas nozzle 51 of the second-stage combustion component 5 injects fuel gas into the furnace 11 of the combustion furnace 1. The fuel gas injected by the second-stage combustion component 5 mixes with the combustion-supporting gas introduced into the furnace 11 of the combustion furnace 1 through the first gas channel 22. After being ignited by the flame of the primary combustion zone S1, it forms the secondary combustion zone S2. With the above setup, a primary combustion zone S1 can be formed inside the furnace chamber 11 of the combustion furnace 1 using the primary combustion assembly 3, and a secondary combustion zone S2 can be formed inside the furnace chamber 11 of the combustion furnace 1 using the secondary combustion assembly 5. The combustion temperature of the primary combustion zone S1 is relatively low, which can directly reduce NO. X The secondary combustion zone S2 is formed at the tail of the flame in the primary combustion zone S1. Through the turbulent vortex at the flame tail, the fuel gas is dispersed into a larger volume within the furnace 11, which helps to ensure complete combustion of the fuel gas and avoids the formation of a high-temperature concentration zone. Reducing the formation of the high-temperature concentration zone can also reduce NO emissions. X Reduce NO generation rate X This reduces emissions while avoiding localized overheating, further reducing environmental pollution and extending equipment lifespan.

[0059] In some embodiments, such as Figure 2As shown, multiple second mounting slots 27 are evenly spaced on the outer wall of the burner brick 2. Correspondingly, there are also multiple secondary combustion components 5, for example, four secondary combustion components 5. The number of secondary combustion components 5 is equal to the number of second mounting slots 27. Each secondary combustion component 5 corresponds to one of the multiple second mounting slots 27. During combustion, fuel gas is simultaneously introduced into the furnace chamber 11 of the combustion furnace 1 using multiple secondary combustion components 5 evenly spaced on the outer wall of the burner brick 2. This accelerates the mixing speed of the fuel gas and the combustion-supporting gas and improves the uniformity of the mixture. Furthermore, the multiple second mounting slots 27 corresponding to the multiple secondary combustion components 5 provide installation positions for each component, preventing them from protruding from the outer wall of the burner brick 2 and facilitating the installation of the burner brick 2 inside the furnace chamber 11 of the combustion furnace 1.

[0060] In some embodiments, to facilitate the introduction of combustion-supporting gas into the first gas passage 22, the burner further includes a combustion-supporting gas distribution pipe 6. Figure 1 Taking the shown perspective as an example, the combustion-supporting gas distribution pipe 6 is located below the burner brick 2 of the burner and is connected to the aforementioned first gas channel 22. It is easy to understand that when there is only one first gas channel 22, the combustion-supporting gas distribution pipe 6 is directly connected to it. When there are multiple first gas channels 22, the combustion-supporting gas distribution pipe 6 includes a main pipe 61 and multiple branch pipes 62. The number of branch pipes 62 should be the same as the number of first gas channels 22, and each branch pipe 62 corresponds to one of the multiple first gas channels 22. The main pipe 61 is connected to the gas source, one end of each branch pipe 62 is connected to the main pipe 61, and the other end is connected to the first gas channel 22. Furthermore, the cross-sectional area of ​​each branch pipe 62 is the same, thus ensuring that the amount of combustion-supporting gas entering each first gas channel 22 is the same, achieving uniform distribution of the combustion-supporting gas. Furthermore, by implementing the above-mentioned settings, the combustion-supporting gas can be distributed into the first gas channel 22, which allows for convenient and flexible control of the combustion-supporting gas entering the first gas channel 22 (for example, an intelligent control component such as an electric regulating valve, flow monitoring module, or flow velocity monitoring module can be additionally installed on the combustion-supporting gas distribution pipeline 6), thereby improving the practicality of the burner.

[0061] Obviously, the above embodiments of this utility model are merely examples for clearly illustrating the present utility model, and are not intended to limit the implementation of the present utility model. Those skilled in the art can make various obvious changes, readjustments, and substitutions without departing from the protection scope of this utility model. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of the claims of this utility model.

Claims

1. A burner for providing heat to a combustion furnace (1), said burner comprising a burner tile (2) at least partly located inside a hearth (11) of the combustion furnace (1), characterized in that, The burner brick (2) is equipped with: A mixing tank (21), the opening of which is connected to the interior of the furnace (11); A first gas passage (22) extends through the burner brick (2) along a first direction (X1) and is used to introduce combustion-supporting gas into the furnace (11); The second gas channel (23) includes a first end (231) and a second end (232); the first end (231) is connected to the first gas channel (22), and the second end (232) is connected to the mixing tank (21); The third gas channel (24) includes a third end (241) and a fourth end (242); the third end (241) penetrates the outer wall of the burner brick (2), and the fourth end (242) is connected to the mixing tank (21); The burner also includes: A primary combustion assembly (3) is disposed on the outer periphery of the burner brick (2); the primary combustion assembly (3) includes a primary gas nozzle (31); the primary gas nozzle (31) is disposed opposite to the third end (241) and there is a gap between the primary gas nozzle (31) and the third end (241); the jet direction of the primary gas nozzle (31) is parallel to the extension direction of the third gas passage (24).

2. The burner of claim 1, wherein The burner brick (2) is also provided with a mounting hole (25); the mounting hole (25) penetrates the burner brick (2) along the first direction (X1); an ignition component (4) is installed in the mounting hole (25), and the ignition component (4) is used to ignite the fuel gas inside the furnace (11); The mixing groove (21) is an annular type and is arranged around the mounting hole (25).

3. The burner of claim 2, wherein The second end (232) and the fourth end (242) are tangential to the outer wall of the mixing tank (21) in the same clockwise direction.

4. The burner of claim 1, wherein The number of the first gas channels (22) is multiple, and the multiple first gas channels (22) are evenly spaced around the mixing tank (21).

5. The burner of claim 1, wherein The first gas channel (22) includes a conical sub-channel (221) and a cylindrical sub-channel (222); the conical sub-channel (221) includes a fifth end (2211) and a sixth end (2212), the cross-sectional area of ​​the fifth end (2211) is smaller than the cross-sectional area of ​​the sixth end (2212); the fifth end (2211) is connected to the interior of the furnace (11), and the sixth end (2212) is connected to the cylindrical sub-channel (222); The first end (231) is connected to the end of the cylindrical sub-channel (222) near the sixth end (2212).

6. The burner of claim 1, wherein Also includes: A secondary combustion assembly (5) is disposed on the outer periphery of the burner brick (2); the secondary combustion assembly (5) includes a secondary gas nozzle (51), the jet direction of the secondary gas nozzle (51) is set at an angle to the jet direction of the primary gas nozzle (31); the secondary gas nozzle (51) and the primary gas nozzle (31) can perform jet action simultaneously.

7. The burner of claim 1, wherein The bottom of the mixing tank (21) is inclined, and there is a first angle (a1) between the plane where the bottom of the tank is located and the second direction (X2); the second direction (X2) is set at an angle to the first direction (X1); The second end (232) is connected to the bottom of the mixing tank (21); there is a second included angle (a2) between the center line of the second end (232) and the second direction (X2); the angle of the second included angle (a2) is the same as the angle of the first included angle (a1), and both are acute angles.

8. The burner of claim 7, wherein The fourth end (242) is connected to the tank body of the mixing tank (21); there is a third included angle (a3) ​​between the center line of the fourth end (242) and the second direction (X2); the angle of the third included angle (a3) ​​is smaller than the angle of the second included angle (a2).

9. Burner according to any one of claims 1 to 8, characterized in that The ratio of the cross-sectional area of ​​the first gas channel (22) to the cross-sectional area of ​​the second gas channel (23) is in the range of 7:3 to 8:

2.

10. Burner according to any one of claims 1 to 8, characterized in that It also includes a combustion-supporting gas distribution pipeline (6), which is connected to the first gas channel (22).

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