Fire grate, burner and water heater

Abstract

The application discloses a fire grate, a burner and a water heater, and relates to the technical field of water heaters, wherein the fire grate comprises a fire grate body and a combustion head, the fire grate body is provided with a mixing cavity, a first air inlet channel and a second air inlet channel, the mixing cavity is provided with a fire opening, the exhaust end of the first air inlet channel is communicated with the mixing cavity, the air inlet end of the first air inlet channel forms an injection port, the injection port is used for conveying gas and air to the first air inlet channel, the exhaust end of the second air inlet channel is communicated with the first air inlet channel or the mixing cavity, and the second air inlet channel is used for conveying air to the mixing cavity, the combustion head is arranged at the fire opening, and the combustion head is provided with a plurality of fire holes communicated with the mixing cavity; the technical scheme provided by the application can reduce the generation of thermal nitrogen oxides during combustion.

Description

Technical Field

[0001] This invention relates to the field of water heater technology, and in particular to a burner, a burner, and a water heater. Background Technology

[0002] Traditional gas water heaters often suffer from insufficient primary air coefficient during air intake, resulting in high local flame temperatures and the generation of large amounts of thermal nitrogen oxides. Summary of the Invention

[0003] The main objective of this invention is to provide a burner, a combustor, and a water heater designed to reduce the generation of thermal nitrogen oxides during combustion.

[0004] To achieve the above objectives, the present invention provides a fire extinguisher comprising:

[0005] The burner body has a mixing chamber, a first air intake channel, and a second air intake channel. The mixing chamber has a burner port. The exhaust end of the first air intake channel is connected to the mixing chamber. The air intake end of the first air intake channel forms an ejector port for supplying fuel gas and air into the first air intake channel. The exhaust end of the second air intake channel is connected to either the first air intake channel or the mixing chamber. The second air intake channel is used to supply air into the mixing chamber.

[0006] A combustion head is disposed at the flame port, and the combustion head has multiple flame holes communicating with the mixing chamber.

[0007] In one embodiment, the first air intake channel has an ejector section, the ejector section including a tapering section and a expanding section arranged and connected from the ejector port toward the mixing cavity, the flow cross-sectional area of ​​the tapering section decreasing from the ejector port toward the expanding section, and the flow cross-sectional area of ​​the expanding section increasing from one end near the tapering section toward the mixing cavity.

[0008] In one embodiment, the exhaust end of the second intake air passage is connected to the diffuser section of the ejector section.

[0009] In one embodiment, there are multiple ejector segments, which are arranged sequentially and connected from the ejector port to the mixing chamber.

[0010] In one embodiment, the plurality of ejector sections include a first ejector section, a second ejector section, and a third ejector section, and the second air intake channel is connected to the second ejector section.

[0011] In one embodiment, the first ejector segment further includes a throat segment that connects the converging segment and the expanding segment.

[0012] In one embodiment, the burner body has a first side and a second side disposed opposite to each other along a first direction, and the first air intake channel and / or the second air intake channel extends from the first side to the second side, wherein the first direction is the length direction of the burner body.

[0013] In one embodiment, the combustion head includes a flame distribution plate and a metal mesh. The flame distribution plate has a plurality of flame holes spaced apart along a first direction. The metal mesh is stacked on top of the flame distribution plate and covers the plurality of flame holes.

[0014] In one embodiment, the metal mesh is stacked in three or four layers along its thickness direction.

[0015] In one embodiment, the mesh size of the metal mesh is not less than 0.55 mm and not more than 0.6 mm;

[0016] And / or, the wire diameter of the metal mesh is not less than 0.22 mm and not more than 0.25 mm;

[0017] And / or, the mesh count of the metal mesh is not less than 30 mesh and not more than 40 mesh;

[0018] And / or, the metal mesh is made of iron-chromium-aluminum.

[0019] In one embodiment, the combustion head is welded and fixed to the burner body;

[0020] And / or, the metal mesh is welded and fixed to the fire distribution plate.

[0021] In one embodiment, the fire distribution plate has a first plate surface disposed away from the mixing chamber, the sum of the total areas of the plurality of fire holes is defined as S1, the area of ​​the first plate surface is defined as S2, and the ratio of S1 to S2 is not less than 0.5 and not greater than 0.6.

[0022] In one embodiment, the flame distribution plate includes a plurality of combustion units spaced apart along the length of the flame plate body. Each combustion unit has a plurality of flame holes, and the plurality of flame holes of each combustion unit includes a first flame hole and a plurality of second flame holes. The first flame hole extends along the width of the flame plate body, and a plurality of second flame holes are respectively provided on both sides of the first flame hole along the length of the flame plate body. The plurality of second flame holes are spaced apart along the width of the flame plate body.

[0023] The present invention also proposes a burner comprising the fire bar as described above.

[0024] The present invention also proposes a water heater, including the burner described above.

[0025] The technical solution of the present invention provides a burner including a burner body and a combustion head. The burner body has a mixing chamber, a first air intake channel and a second air intake channel. Combustion and air are supplied to the first air intake channel through the ejector port. The second air intake channel connects to the first air intake channel or the mixing chamber and supplies air to the mixing chamber. This increases the proportion of air in the mixing chamber through the second air intake channel, improves the primary air coefficient of the burner intake, and reduces the combustion temperature, thereby reducing the formation of thermal nitrogen oxides. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0027] Figure 1 A schematic diagram of the structure of an embodiment of the fire briquette provided by the present invention;

[0028] Figure 2 for Figure 1 A partial sectional view of the center burner body;

[0029] Figure 3 for Figure 1 A schematic diagram of the structure of an embodiment of the combustion head;

[0030] Figure 4 for Figure 3 A schematic diagram of the combustion head from another angle;

[0031] Figure 5 for Figure 4 A magnified view of a portion of point A in the middle.

[0032] Explanation of icon numbers:

[0033] 100. Burner; 10. Burner body; 101. Mixing chamber; 101a. Flame outlet; 1011. First chamber section; 1012. Second chamber section; 102. First air intake channel; 102a. Injector port; 1021. Injector section; 1021a. Converging section; 1021b. Diverging section; 1021c. Throat section; 10211. First ejector section; 10212. Second ejector section; 10213. Third ejector section; 103. Second air intake channel; 11. First side; 12. Second side; 20. Combustion head; 20a. Combustion unit; 21. Flame distribution plate; 21a. First plate surface; 211. Flame hole; 211a. First flame hole; 211b. Second flame hole; 22. Metal mesh.

[0034] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0035] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0036] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0037] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0038] Traditional gas water heaters typically use bottom-mounted fans and burners. When the burner is taking in air, there is often insufficient primary air coefficient. In addition, the flame orifice area of ​​the burner is small, and the flame tends to concentrate during combustion, forming a continuous flame state. This ultimately leads to high local flame temperature and causes a large amount of thermal nitrogen oxides to be generated.

[0039] This invention proposes a fire grill 100.

[0040] Please see Figures 1 to 5In one embodiment of the present invention, the burner 100 includes a burner body 10 and a combustion head 20. The burner body 10 has a mixing chamber 101, a first air intake channel 102 and a second air intake channel 103. The mixing chamber 101 has a burner port 101a. The exhaust end of the first air intake channel 102 is connected to the mixing chamber 101. The air intake end of the first air intake channel 102 forms an ejector port 102a. The ejector port 102a is used to supply fuel gas and air to the first air intake channel 102. The exhaust end of the second air intake channel 103 is connected to the first air intake channel 102 or the mixing chamber 101. The second air intake channel 103 is used to supply air to the mixing chamber 101. The combustion head 20 is disposed at the burner port 101a. The combustion head 20 has a plurality of burner holes 211 that communicate with the mixing chamber 101.

[0041] The burner 100 of this invention can be used in the burner of a gas water heater. The burner may further include a main fan, the outlet of which is connected to an injector 102a. The main fan can supply gas and air to the injector 102a. Alternatively, the first air intake duct 102 may be a Venturi channel, with a gas pipeline supplying gas to the first air intake duct 102. The high-speed flow of gas within the first air intake duct 102 creates a local low-pressure zone. The suction generated by this local low-pressure zone draws air from the outside through the injector 102a, thus enabling the first air intake duct 102 to supply gas and air. The burner may also include an auxiliary fan, the inlet of which is connected to the outlet of the auxiliary fan. The auxiliary fan can directly supply air to the second air intake duct 103. In addition, when the exhaust end of the second intake air passage 103 is directly connected to the first intake air passage 102, the intake end of the second intake air passage 103 can be directly connected to the external environment. The second intake air passage 103 can use the suction generated by the local low-pressure area in the first intake air passage 102 to draw air from the external environment. In this way, there is no need to set up an additional auxiliary fan, and the first intake air passage 102 can be used to transport air.

[0042] It is understandable that since the exhaust end of the second intake channel 103 is directly connected to the mixing chamber 101, or indirectly connected to the mixing chamber 101 through the first intake channel 102, the second intake channel 103 can deliver additional air to the mixing chamber 101, thereby increasing the proportion of air in the mixed gas in the mixing chamber 101 and increasing the primary air coefficient. With this setting, on the one hand, by increasing the external air, excess cold air can enter the combustion zone, thereby reducing the flame temperature by diluting the combustion reaction and absorbing heat. When the flame temperature is reduced to below the nitrogen chemical reaction threshold, the generation of thermal nitrogen oxides can be significantly reduced.

[0043] The technical solution of the present invention provides a burner 100 comprising a burner body 10 and a combustion head 20. The burner body 10 has a mixing chamber 101, a first air intake channel 102, and a second air intake channel 103. Gas and air are supplied to the first air intake channel 102 through the ejector port 102a. The second air intake channel 103 connects the first air intake channel 102 or the mixing chamber 101, and supplies air to the mixing chamber 101 through the second air intake channel 103. This increases the proportion of air in the mixing chamber 101 through the second air intake channel 103, improves the primary air coefficient of the burner 100, reduces the combustion temperature, and thus reduces the generation of thermal nitrogen oxides.

[0044] Understandably, when the fuel gas and air in the mixing chamber 101 are not fully mixed, there will be localized areas with excessively high fuel gas content, localized areas with excessively low fuel gas content, and localized areas with near-optimal fuel gas content. This leads to excessively high temperatures, rapid combustion rates, and intense chemical reactions in these areas, resulting in a concentrated release of energy within a short period. This creates localized high-temperature points. When these localized high-temperature points reach the threshold temperature for the formation of thermal nitrogen oxides, the formation rate of nitrogen oxides increases rapidly. Thus, insufficient mixing of fuel gas and air leads to the formation of large quantities of thermal nitrogen oxides.

[0045] To avoid the above situation, this invention further improves the mixing method of gas and air by increasing the primary air coefficient. The relevant improvements are as follows.

[0046] like Figure 2 As shown, in one embodiment, the first air intake channel 102 has an ejector section 1021, which includes a tapering section 1021a and a expanding section 1021b arranged and connected from the ejector port 102a toward the mixing chamber 101. The flow cross-sectional area of ​​the tapering section 1021a decreases from the ejector port 102a toward the expanding section 1021b, and the flow cross-sectional area of ​​the expanding section 1021b increases from the end near the tapering section 1021a toward the mixing chamber 101.

[0047] The ejector section 1021 may also have a throat connecting the tapering section 1021a and the expanding section 1021b. The throat may be a connection port connecting the tapering section 1021a and the expanding section 1021b, or it may be a flow section connecting the tapering section 1021a and the expanding section 1021b.

[0048] It is understandable that when the flow cross-sectional area of ​​the converging section 1021a of the ejector section 1021 decreases from the ejector port 102a to the expanding section 1021b, a local negative pressure zone can gradually form near the end of the converging section 1021a as air and gas pass through it. This negative pressure actively draws the gas and air from the ejector port 102a, achieving efficient ejection and initial mixing. In addition, when the flow cross-sectional area of ​​the expanding section 1021b of the ejector section 1021 increases from the end near the converging section 1021a towards the mixing chamber 101, the flow velocity of the gas and air gradually decreases and the pressure gradually recovers as they pass through the expanding section 1021b. During this process, strong turbulence is formed, allowing the gas and air to fully penetrate and mix, further improving the mixing uniformity. In this way, when the first intake channel 102 delivers gas and air, the gas and air can be fully mixed, thereby improving the uniformity of the gas-air mixture when the first intake channel 102 is inlet.

[0049] Furthermore, since the second inlet air passage 103 supplies air into the mixing chamber 101, it increases the overall primary air coefficient of the mixed gas within the mixing chamber 101. To further mix the air supplied by the second inlet air passage 103 with the fuel gas and air supplied by the first inlet air passage 102, thereby improving the overall uniformity of the fuel gas and air mixing within the mixing chamber 101, the present invention further improves the connection position of the second inlet air passage 103, such as... Figure 2 As shown, in one embodiment, the exhaust end of the second intake air passage 103 is connected to the expanding section 1021b of the ejector section 1021.

[0050] Understandably, when the second inlet channel 103 is connected at the throat or converging section 1021a where the gas flow velocity is extremely high, the high-speed main airflow at the throat or converging section 1021a acts like a wall, pushing away or enveloping the newly injected air from the second inlet channel 103. The air injected from the second inlet channel 103 has difficulty penetrating into the mixed gas transported by the first inlet channel 102, and the two easily form stratification, resulting in insufficient mixing. When the second inlet channel 103 is connected to the expanding section 1021b, the air input from the second inlet channel is injected at the slower-flowing converging section 1021a. The initial momentum of the new airflow is smaller than the inertia of the main airflow in the first inlet channel 102, making it easier to be entrained and pulled into the main airflow, achieving fusion from the smooth edge to the center.

[0051] Furthermore, the increased flow cross-sectional area of ​​the diffuser section 1021b generates significant turbulence within the fluid, forming numerous tiny vortices. When the air injected into the second intake channel 103 enters this turbulent region, it is instantly sheared and stretched, breaking into even smaller airflow streams. This allows for rapid mixing with the main airflow, thereby improving the mixing uniformity between the air input into the second intake channel 103 and the main airflow in the first intake channel 102. This ensures that the combustion gas and air are fully and uniformly mixed within the mixing chamber 101. This prevents excessively high local combustion temperatures in the burner 100.

[0052] Continue reading Figure 2 Optionally, multiple ejector segments 1021 are provided, and the multiple ejector segments 1021 are arranged and connected sequentially from the ejector port 102a to the mixing chamber 101.

[0053] It is understandable that, since the ejector section 1021 can accelerate the flow and decelerate the mixing of gas when conveying gas, when the first inlet flow channel 102 has multiple ejector sections 1021 arranged in sequence and connected, the airflow can undergo multiple acceleration-deceleration processes through the first inlet flow channel 102, so that the gas and air in the first inlet flow channel 102 can be mixed multiple times, thereby further improving the uniformity of gas and air mixing in the first inlet flow channel 102.

[0054] Furthermore, the plurality of ejector sections 1021 include a first ejector section 10211, a second ejector section 10212 and a third ejector section 10213, and the second air intake channel 103 is connected to the second ejector section 10212.

[0055] Understandably, when the second intake duct 103 is connected to the second ejector section 10212, especially to the expanding section 1021b of the second ejector section 10212, the expanding section 1021b of the second ejector section 10212 gradually recovers its internal pressure and its flow velocity gradually decreases, resulting in lower flow inertia. Air introduced into the second intake duct 103 at this point is more easily entrained by the main airflow and penetrates into the gas, thus achieving deep mixing. Furthermore, after mixing with the main airflow of the second ejector section 10212, the air entering from the second intake duct 103 will further pass through the third ejector section 10213, undergoing another acceleration-deceleration process and secondary mixing with the main airflow. This ensures a more uniform and thorough mixing of the air introduced into the second intake duct 103 with the mixed gas delivered by the first intake duct 102, thereby preventing excessively high local combustion temperatures in the burner 100.

[0056] Understandably, since the first ejector section 10211 is directly connected to the ejector port 102a, it will directly draw in external air from the ejector port 102a and perform preliminary mixing with the combustion gas entering the first ejector section 10211. If the second intake channel 103 is connected to the expanding section 1021b of the first ejector section 10211, it may affect the air ejected from the first intake channel 102 and the preliminary mixing of air and combustion gas within the first intake channel 102. Furthermore, the third ejector section 10213 is directly connected to the mixing chamber 101 and is closer to the combustion head 20. If the second intake channel 103 is connected to the expanding section 1021b of the third ejector section 10213, the air entering from the second intake channel 103 can only mix with the main airflow through this section and then directly enter the mixing chamber 101, which may result in poor mixing. Therefore, connecting the second intake channel 103 with the expanding section 1021b of the second ejector section 10212 can avoid affecting the air ejected by the first intake channel 102 and the initial mixing of the gas. At the same time, it can ensure that the air supplemented by the second intake channel 103 can be mixed again, ensuring that both the first intake channel 102 and the second intake channel 103 can work in an orderly manner.

[0057] like Figure 2 As shown, in one embodiment, the first ejector segment 10211 further includes a throat segment 1021c that connects the tapering segment 1021a and the expanding segment 1021b.

[0058] Understandably, compared to connecting the tapered section 1021a and the expanding section 1021b via a connector, connecting the tapered section 1021a and the expanding section 1021b via a throat section 1021c increases the length of the throat. Since the gas velocity is highest at the throat, it provides a longer forced mixing time for the air and fuel gas. Within the extended high-speed flow channel, the intense turbulence effect allows sufficient time for shearing and stretching of the gas microparticles, thus achieving a deeper mixing of the fuel gas and air. When the throat of the first ejector section 10211 is set to a longer throat section 1021c, it ensures that the first inlet flow channel 102 can better initially mix the air and fuel gas in the first ejector section 10211, thereby ensuring that the air supplemented in the second ejector section 10212 can better integrate with the already initially mixed gas, guaranteeing more uniform gas mixing in subsequent stages.

[0059] like Figure 2 As shown, the mixing chamber 101 includes a first chamber section 1011 and a second chamber section 1012. The first chamber section 1011 and the second chamber section 1012 are arranged sequentially from the first air intake channel 102 to the flame port 101a. The flow cross-sectional area of ​​the first chamber section 1011 decreases from the first air intake channel 102 to the second chamber section 1012, and the flow cross-sectional area of ​​the second chamber section 1012 increases from the second chamber section 1012 to the flame port 211.

[0060] This configuration allows the gas and air input from the first intake channel 102 to mix after passing through multiple ejector sections 1021, and the air input from the second intake channel 103 to mix with the gas input from the first intake channel 102 within the first intake channel 102. The gases input from both channels can then be accelerated through the first section 1011 of the mixing chamber 101 and decelerated through the second section 1012 of the mixing chamber 101, resulting in further mixing. This not only increases the air intake volume but also further enhances the uniformity of the air-gas mixture.

[0061] The volume of the mixing chamber 101 can be greater than the sum of the volumes of the first flow channel and the second flow channel, and the volume of the second chamber section 1012 can be further set to be greater than the volume of the first chamber section 1011. The mixed gas after secondary mixing in the mixing chamber 101 has sufficient diffusion space, and the gas flow rate can be reduced, thereby making the gas flow rate distribution delivered from the second chamber section 1012 to the vent 101a more uniform.

[0062] like Figure 1 , Figure 2 As shown, in one embodiment, the burner body 10 has a first side 11 and a second side 12 disposed opposite to each other along a first direction, and the first air intake channel 102 and / or the second air intake channel 103 extend from the first side 11 to the second side 12, wherein the first direction is the length direction of the burner body 10.

[0063] This configuration allows the first intake air passage 102 to intake air from the length direction of the burner body 10. Since the burner body 10 is relatively long, the overall length of the first intake air passage 102 can be increased, which makes it easier to set multiple ejector sections 1021 for the first intake air passage 102 to improve the uniformity of air and gas mixing.

[0064] Alternatively, the second air intake channel 103 can be configured to extend in the same direction as the first air intake channel 102, so that the air flow direction of the second air intake channel 103 into the first air intake channel 102 is approximately the same as the flow direction of the mixed gas in the first air intake channel 102. This facilitates the use of the negative pressure generated by the first air intake channel 102 to eject air from the second air intake channel 103.

[0065] The structure of the combustion head 20 is described below, such as... Figure 1 , Figure 3 As shown, in one embodiment, the combustion head 20 includes a flame distribution plate 21 and a metal mesh 22. The flame distribution plate 21 has a plurality of flame holes 211 spaced apart along a first direction. The metal mesh 22 is stacked on top of the flame distribution plate 21 and covers the plurality of flame holes 211.

[0066] It is understandable that when the metal mesh 22 covers multiple flame holes 211, the dense mesh structure of the metal mesh 22 can play the role of flame division. When the mixed gas is sprayed out from the multiple flame holes 211 on the flame distribution plate 21 and ignited, the flame spreads upward. The dense mesh of the metal mesh 22 divides the relatively concentrated flame into countless uniform and stable micro flames, thereby avoiding the flame from merging and forming local high temperature areas.

[0067] Meanwhile, the mesh openings of the metal mesh 22 can generate a certain flow resistance to the ejected airflow. The uniformly distributed resistance formed by the metal mesh 22 helps to balance the airflow velocity across the entire combustion surface, preventing the gas from being excessively concentrated in certain burner holes 211, thus avoiding excessively high local flame temperatures and allowing the flame to spread evenly on the surface of the metal mesh 22. This avoids concentrated flames and excessively high local flame temperatures during combustion, which would lead to the formation of large amounts of thermal nitrogen oxides.

[0068] Optionally, the metal mesh 22 is stacked in three or four layers along its thickness direction.

[0069] Understandably, if too many layers of metal mesh 22 are stacked, it will result in greater gas flow resistance. When the gas flows out of the burner holes 211, it will encounter significant flow resistance, affecting combustion. If fewer layers of metal mesh 22 are stacked, such as only one layer, the gas flow resistance will be too high, making it difficult to evenly distribute the gas from the burner holes 211. Therefore, three or four layers of metal mesh 22 are used to ensure moderate gas flow resistance and even distribution of the gas to each burner hole 211, thus ensuring a more uniform flame distribution during combustion.

[0070] Optionally, the mesh size of the metal mesh 22 is not less than 0.55 mm and not more than 0.6 mm. The mesh size of the metal mesh 22 can be square, and the mesh size can be the width of the mesh opening. This design avoids the mesh size being too small, which would affect the smooth flow of the gas, and also avoids the mesh size being too large, which would prevent the metal mesh 22 from uniformly dividing the flame. For example, the mesh size can be 0.55 mm, 0.56 mm, 0.57 mm, 0.58 mm, 0.59 mm, 0.6 mm, or any value within the range [0.55, 0.6].

[0071] Optionally, the wire diameter of the metal mesh 22 is not less than 0.22 mm and not more than 0.25 mm. This setting ensures that the metal mesh 22 has sufficient wire diameter, thereby providing sufficient structural strength and durability in the high-temperature environment of the crater 101a, and preventing damage or deformation due to prolonged heating. Simultaneously, sufficient metal content allows the metal mesh 22 to have better thermal conductivity, which is beneficial for uniform temperature distribution. For example, the wire diameter of the metal mesh 22 can be 0.22 mm, 0.23 mm, 0.24 mm, 0.25 mm, or any value within the range [0.22, 0.25].

[0072] Optionally, the mesh count of the metal mesh 22 is not less than 30 mesh and not more than 40 mesh. It is understood that a mesh count between 30 and 40 meshes means there are 30 to 40 holes per inch of length. This roughly corresponds to a mesh aperture of approximately 0.425 mm to 0.595 mm. This sufficiently dense mesh of the metal mesh 22 effectively divides the flame into uniform micro-flames, avoiding localized high temperatures, while also allowing sufficient airflow without causing excessive resistance to the flow of the mixed gas. This ensures that the firebox 100 has sufficient heat load output and prevents the flame from concentrating on a few larger fire holes 211, which could lead to excessively high combustion temperatures. For example, the mesh count of the metal mesh 22 can be 30, 32, 34, 36, 38, or 40 meshes.

[0073] Optionally, the metal mesh 22 is made of iron-chromium-aluminum alloy. It is understood that iron-chromium-aluminum alloy has better high-temperature resistance, can withstand the high temperatures generated by combustion, and can prevent deformation under high-temperature combustion conditions, thus extending the service life of the metal mesh 22.

[0074] Optionally, the combustion head 20 is welded and fixed to the burner body 10. In this invention, the combustion head 20 may further include a connecting edge circumferentially disposed around the burner plate 21. The connecting edge may be integrally formed with the burner plate 21. The combustion head 20 and the burner body 10 can be welded to the inner peripheral wall of the mixing chamber 101 through the connecting edge, specifically through energy storage welding.

[0075] Optionally, the metal mesh 22 is welded to the flame distribution plate 21. Specifically, the metal mesh 22 and the flame distribution plate 21 can be fixed by welding, such as by spot welding. Of course, other welding methods can also be used to fix the metal mesh 22 and the flame distribution plate 21, and this is not limited here.

[0076] Optionally, the fire distribution plate 21 has a first plate surface 21a disposed away from the mixing chamber 101, the sum of the total areas of the plurality of fire holes 211 is defined as S1, the area of ​​the first plate surface 21a is defined as S2, and the ratio of S1 to S2 is not less than 0.5 and not greater than 0.6.

[0077] The first plate surface 21a can be defined as the combustion surface of the flame distribution plate 21. When the ratio of the total area of ​​multiple flame holes 211 to the combustion surface is between 0.5 and 0.6, it avoids the situation where the total area of ​​the flame holes 211 occupies too little of the combustion surface area, resulting in excessively fast gas output velocity from each flame hole 211, leading to an excessively long flame that concentrates in a few flame holes 211, causing localized high temperatures and the generation of high-temperature nitrogen oxides. Conversely, it avoids the situation where the total area of ​​the flame holes 211 occupies too much of the combustion surface area, resulting in insufficient structural strength of the flame distribution plate 21 and potentially excessively dispersed flames, leading to insufficient combustion intensity. Therefore, setting the ratio of the total area of ​​multiple flame holes 211 to the combustion surface between 0.5 and 0.6 ensures that the gas flow rate and combustion uniformity are balanced, guaranteeing combustion intensity while preventing the generation of nitrogen oxides from localized high temperatures. For example, the ratio of S1 to S2 can be 0.5, 0.52, 0.54, 0.56, 0.58, 0.6, or any point value within the interval [0.5, 0.6].

[0078] The arrangement of the flame holes 211 on the flame distribution plate 21 is described below, such as... Figure 4 , Figure 5 As shown, in one embodiment, the flame distribution plate 21 includes a plurality of combustion units 20a spaced apart along the length direction of the flame plate body 10. Each combustion unit 20a has a plurality of flame holes 211. The plurality of flame holes 211 of each combustion unit 20a includes a first flame hole 211a and a plurality of second flame holes 211b. The first flame hole 211a extends along the width direction of the flame plate body 10. A plurality of second flame holes 211b are respectively provided on both sides of the first flame hole 211a along the length direction of the flame plate body 10. The plurality of second flame holes 211b are spaced apart along the width direction of the flame plate body 10.

[0079] Each combustion unit 20a may include four second flame holes 211b. Two second flame holes 211b may be distributed on either side of the first flame hole 211a in each combustion unit 20a. The two second flame holes 211b are spaced apart along the width of the flame pack body 10. This arrangement ensures that each combustion unit 20a consists of a large strip-shaped flame hole and two shorter flame holes 211 on each side of the large strip-shaped flame hole. Within each combustion unit 20a, the first flame hole 211a serves as a central anchor point, establishing a stable and continuous reference flame band. The multiple second flame holes 211b on either side serve as distribution points, dispersing the flame energy and forming a small, stable flame group, preventing excessive flame concentration at any single point in a single combustion unit 20a.

[0080] Furthermore, by diverting the total gas flow within a combustion unit 20a through a large first burner 211a and multiple small auxiliary burners, the heat release is more dispersed and gradual compared to concentrating all the gas on a few points for combustion, thus fundamentally eliminating the conditions for generating localized high-temperature zones.

[0081] Furthermore, the larger flame formed by the first fire hole 211a and the smaller flame formed by the second fire hole 211b restrain each other. The adjacent flames can preheat each other through thermal radiation and thermal conduction, stabilize each other, and form a stable combustion field, making the combustion on the entire fire distribution plate 21 more stable.

[0082] In addition to setting multiple combustion units 20a, the number of flame holes 211 located on both sides of the burner body 10 along its length can be increased. For example, the number of second flame holes 211b on both sides of the combustion units 20a can be increased, doubling the number of second flame holes 211b on both sides of the burner body 10 along its length, from two to four. This raises the ignition point and prevents the combustion temperature on both sides of the burner 100 from being too low due to insufficient gas supply. It also makes the temperature distribution of the entire combustion area along the length of the burner 100 more uniform, preventing excessively high temperatures in local combustion areas and the generation of thermal nitrogen oxides.

[0083] This invention also proposes a burner comprising a burner 100. The specific structure of the burner 100 is as described in the above embodiments. Since this burner adopts all the technical solutions of all the above embodiments, it possesses at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be elaborated further here. The burner may further include a frame and a fan. The burner 100 is disposed within the frame, and multiple burners 100 can be arranged side-by-side. The fan can be mounted on the frame in a top-mounted manner to draw out the high-temperature flue gas generated during combustion.

[0084] This invention also proposes a water heater, including the burner described above. The burner may further include a heat exchanger, an inlet pipe, and an outlet pipe. The heat exchanger is connected to the burner, the inlet pipe is connected to the inlet end of the heat exchanger, and the outlet pipe is connected to the outlet end of the heat exchanger. During operation, the high-temperature flue gas generated by the burner passes through the heat exchanger and exchanges heat with the room-temperature water flowing into the heat exchanger through the inlet pipe. The heated room-temperature water then flows out through the outlet pipe, thus preparing hot water.

[0085] The above description is merely an exemplary embodiment of the present invention and does not limit the scope of protection of the present invention. Any equivalent structural transformations made based on the technical concept of the present invention and the contents of the specification and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present invention.

Claims

1. A fire grill, characterized in that, include: The burner body has a mixing chamber, a first air intake channel and a second air intake channel. The mixing chamber has a burner opening. The exhaust end of the first air intake channel is connected to the mixing chamber. The air intake end of the first air intake channel forms an ejector port, which is used to supply fuel gas and air to the first air intake channel. The exhaust end of the second air intake channel is connected to the first air intake channel, which is used to supply air to the mixing chamber. as well as A combustion head is disposed at the flame port, and the combustion head has multiple flame holes communicating with the mixing chamber; The first air intake channel has an ejector section, which includes a tapering section and a expanding section arranged and connected from the ejector port toward the mixing cavity. The flow cross-sectional area of ​​the tapering section decreases from the ejector port toward the expanding section, and the flow cross-sectional area of ​​the expanding section increases from the end near the tapering section toward the mixing cavity. The ejector section is provided in multiple ways, and the multiple ejector sections are arranged in sequence and connected from the ejector port to the mixing chamber; the multiple ejector sections include a first ejector section, a second ejector section and a third ejector section, and the second air intake channel is connected to the diffuser section of the second ejector section.

2. The fire grill as described in claim 1, characterized in that, The first ejector segment also includes a throat segment that connects the converging segment and the expanding segment.

3. The fire rack as described in claim 1 or 2, characterized in that, The fire vent body has a first side and a second side disposed opposite to each other along a first direction, and the first air intake channel and / or the second air intake channel extend from the first side to the second side, wherein the first direction is the length direction of the fire vent body.

4. The fire rack as described in claim 1 or 2, characterized in that, The combustion head includes a flame distribution plate and a metal mesh. The flame distribution plate has a plurality of flame holes spaced apart along a first direction. The metal mesh is stacked on top of the flame distribution plate and covers the plurality of flame holes.

5. The fire grill as described in claim 4, characterized in that, The metal mesh is stacked in three or four layers along its thickness direction.

6. The fire grill as described in claim 4, characterized in that, The mesh size of the metal mesh is not less than 0.55 mm and not more than 0.6 mm; And / or, the wire diameter of the metal mesh is not less than 0.22 mm and not more than 0.25 mm; And / or, the mesh count of the metal mesh is not less than 30 mesh and not more than 40 mesh; And / or, the metal mesh is made of iron-chromium-aluminum.

7. The fire grill as described in claim 4, characterized in that, The combustion head is welded and fixed to the fire bar body; And / or, the metal mesh is welded and fixed to the fire distribution plate.

8. The fire grill as described in claim 4, characterized in that, The fire distribution plate has a first plate surface disposed away from the mixing chamber. The total area of ​​the plurality of fire holes is defined as S1, and the area of ​​the first plate surface is defined as S2. The ratio of S1 to S2 is not less than 0.5 and not greater than 0.

6.

9. The fire grill as described in claim 4, characterized in that, The fire distribution plate includes a plurality of combustion units spaced apart along the length of the fire plate body. Each combustion unit has a plurality of fire holes. The plurality of fire holes in each combustion unit include a first fire hole and a plurality of second fire holes. The first fire hole extends along the width of the fire plate body. A plurality of second fire holes are respectively provided on both sides of the first fire hole along the length of the fire plate body. The plurality of second fire holes are spaced apart along the width of the fire plate body.

10. A burner, characterized in that, Includes the fire rack as described in any one of claims 1 to 9.

11. A water heater, characterized in that, Includes the burner as described in claim 10.

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