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. The fire grate comprises a fire grate body and a spoiler. The fire grate body is provided with an air inlet channel and a mixing chamber. The mixing chamber is provided with an air outlet. The mixing chamber is in communication with the air outlet end of the air inlet channel. The air inlet end of the air inlet channel is provided with an air inlet. The spoiler is arranged in the air inlet channel. The spoiler comprises a spoiler body and a flow guide part. The spoiler body is provided with a through spoiler groove. The flow guide part is arranged corresponding to the spoiler groove. The spoiler groove is used for dispersing and disturbing the airflow flowing through the spoiler body. The flow guide part is used for guiding the airflow to flow from the spoiler groove to the mixing chamber. The technical scheme provided by the application can enhance the mixing uniformity of the gas and air in the fire grate, reduce the chemical equivalent ratio of the gas at the outlet of the fire grate, avoid the local high-temperature phenomenon, and further reduce the flue gas emission of pollutants such as CO and NOx.

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] In traditional gas water heaters, the gas and air flow in the same direction in the burner, relying solely on natural mixing during the flow process. This results in insufficient mixing of gas and air inside the burner, leading to uneven distribution of combustion equivalence ratio at the burner outlet, poor flame uniformity, and mediocre emission performance. Summary of the Invention

[0003] The main objective of this invention is to provide a burner, a burner, and a water heater that enhances the uniformity of gas and air mixing within the burner, reduces the chemical stoichiometry of gas at the burner outlet, avoids localized high-temperature phenomena, and thereby reduces the emission of pollutants such as CO and NOx.

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

[0005] The burner body has an air intake channel and a mixing chamber. The mixing chamber has an air outlet and is connected to the exhaust end of the air intake channel. The air intake end of the air intake channel has an air inlet.

[0006] A flow disruptor is disposed within the air intake channel. The flow disruptor includes a flow disruptor body and a flow guide. The flow disruptor body is provided with a flow disruptor groove that is arranged in a through manner. The flow guide is provided corresponding to the flow disruptor groove. The flow disruptor groove is used to disperse and disturb the airflow flowing through the flow disruptor body. The flow guide is used to guide the airflow from the flow disruptor groove toward the mixing chamber.

[0007] In one embodiment, the turbulence body includes a first turbulence portion and a second turbulence portion, wherein the first turbulence portion and the second turbulence portion form a first included angle that expands toward the side away from the air inlet, and the turbulence groove includes a first turbulence groove disposed in the first turbulence portion and / or a second turbulence groove disposed in the second turbulence portion.

[0008] In one embodiment, the air inlet is located on one side of the burner body along the length direction, the air inlet and the baffle are arranged opposite to each other along the length direction of the burner body, the air outlet is located on one side of the burner body along the height direction, the first baffle is inclined towards the side closer to the air outlet along the air intake direction of the air intake channel, and the second baffle is inclined towards the side farther from the air outlet along the air intake direction of the air intake channel.

[0009] In one embodiment, the first included angle is not less than 30 degrees and not greater than 45 degrees.

[0010] In one embodiment, the turbulence-disrupting body has a constricted end and an expanded end disposed opposite to each other along the length direction of the burner body, the first turbulence-disrupting groove has a first edge on the side near the constricted end, the flow-guiding part includes a first flow-guiding part, the first flow-guiding part includes a first flow-guiding section and a second flow-guiding section that are bent and connected, the first flow-guiding section is inclined from the first edge toward the side away from the air outlet, and the second flow-guiding section is disposed opposite to the first turbulence-disrupting groove.

[0011] In one embodiment, the turbulence-disrupting body has a constricted end and an expanded end disposed opposite to each other along the length direction of the burner body, the second turbulence-disrupting groove has a second edge on the side near the constricted end, the flow-guiding portion includes a second flow-guiding portion, the second flow-guiding portion includes a third flow-guiding section and a fourth flow-guiding section that are bent and connected, the third flow-guiding section is inclined from the second edge toward the side near the air outlet, and the fourth flow-guiding section is disposed opposite to the second turbulence-disrupting groove.

[0012] In one embodiment, the first turbulence portion and / or the second turbulence portion are provided with a plurality of turbulence protrusions at the end away from the air inlet, and the plurality of turbulence protrusions are arranged at intervals along the width direction of the burner body.

[0013] In one embodiment, the turbulence-disrupting body is disposed around the periphery of the flow-guiding portion, and the turbulence-disrupting groove is located between the peripheral wall of the turbulence-disrupting body and the flow-guiding portion;

[0014] In the air intake direction of the air intake channel, the peripheral wall of the turbulence body is constricted toward the side away from the air intake; and / or, the peripheral wall of the guide portion is expanded toward the side away from the air intake.

[0015] In one embodiment, in the axial cross-section of the turbulence-disrupting body, a second included angle is formed between the two side edges of the turbulence-disrupting body, the second included angle being not less than 25 degrees and not greater than 35 degrees;

[0016] And / or, in the axial section of the guide portion, a third included angle is formed between the two side edges of the guide portion, the third included angle being not less than 25 degrees and not greater than 35 degrees;

[0017] And / or, the flow-dispersing grooves are provided in multiple ways, and the multiple flow-dispersing grooves are arranged circumferentially along the guide portion.

[0018] In one embodiment, the air intake channel has an ejector section extending from the air inlet toward the mixing chamber. The ejector section has a tapering section and a diffusing section arranged and connected along the air intake direction of the air intake channel, and the turbulence element is disposed in the diffusing section.

[0019] In one embodiment, the burner further includes a combustion head disposed on the burner body. The combustion head includes a flame distribution plate and a flow equalization plate. The flame distribution plate covers the gas outlet. The flow equalization plate is disposed on the side of the flame distribution plate facing the mixing chamber. The flame distribution plate has a plurality of flame holes, and the flow equalization plate has a plurality of flow equalization holes.

[0020] In one embodiment, the plurality of flow equalization holes includes a first flow equalization hole and a second flow equalization hole; the flow equalization plate has two first flow equalization zones opposite each other along the length direction, and a second flow equalization zone located between the two first flow equalization zones, the first flow equalization zone is provided with a plurality of first flow equalization holes, the second flow equalization zone is provided with a plurality of second flow equalization holes, and the opening area of ​​the second flow equalization hole is larger than the opening area of ​​the first flow equalization hole.

[0021] In one embodiment, the plurality of first flow equalization holes include a plurality of first flow equalization sub-holes and a plurality of second flow equalization sub-holes. The plurality of first flow equalization sub-holes and the plurality of second flow equalization sub-holes are alternately arranged along the length direction of the flow equalization plate, and the plurality of second flow equalization sub-holes are arranged in multiple rows along the width direction of the flow equalization plate. Each row has a plurality of second flow equalization sub-holes, and the opening area of ​​the first flow equalization sub-holes is larger than the opening area of ​​the second flow equalization sub-holes.

[0022] And / or, a plurality of the second flow equalization holes are arranged along the length direction of the flow equalization plate.

[0023] In one embodiment, the combustion head further includes two side plates respectively disposed on both sides of the width direction of the flow equalization plate. Each side plate is provided with a plurality of flow diversion holes. A side air outlet channel is formed between the side of each side plate away from the other side plate and the burner body. The plurality of side air outlet channels are connected one-to-one with the plurality of flow diversion holes. The side of the side air outlet channel away from the mixing chamber is open to form a flame stabilizing port.

[0024] In one embodiment, the cross-sectional area of ​​the side outlet air passage gradually expands from the side away from the flame stabilizer towards the flame stabilizer.

[0025] In one embodiment, the burner body has a plurality of lateral protrusions spaced apart along its length at the portion opposite to each of the side plates. Each lateral protrusion forms a side air outlet channel with the adjacent side plate. Each lateral protrusion includes a main body disposed opposite to the side plate and bent plates disposed on opposite sides of the main body. Each bent plate is bent relative to the main body toward the side plate.

[0026] In one embodiment, the bent plate and the main plate are set at an obtuse angle;

[0027] And / or, the bent plate body forms a fourth included angle with the adjacent side plate, the fourth included angle being not less than 10 degrees and not greater than 15 degrees;

[0028] And / or, in the direction toward the flame stabilizing port, the main body is inclined outward relative to the adjacent side plate.

[0029] In one embodiment, each of the side plates has a first plate surface, the first plate surface of each of the side plates is disposed opposite to the other side plate, the sum of the total area of ​​the plurality of diversion holes of the two side plates is defined as S1, the sum of the total area of ​​the two first plate surfaces is defined as S2, and the ratio of S1 to S2 is not less than 0.2 and not greater than 0.3.

[0030] In one embodiment, the flow equalization plate has a second plate surface facing the fire distribution plate, the sum of the total areas of the plurality of flow equalization holes is defined as S3, the area of ​​the second plate surface is defined as S4, and the ratio of S3 to S4 is not less than 0.25 and not greater than 0.35.

[0031] The present invention also proposes a burner comprising the fire bar as described above.

[0032] The present invention also proposes a water heater, including the burner described above.

[0033] The technical solution of the present invention provides a baffle in the air intake channel of the burner. The baffle includes a baffle body with a through baffle groove and a guide part corresponding to the baffle groove. The baffle groove disperses and disturbs the airflow flowing through the baffle body, and the guide part guides the dispersed airflow toward the mixing chamber, so that the combustion gas and air are more fully mixed before entering the mixing chamber. This reduces the uneven distribution of the combustion equivalence ratio at the burner outlet, improves flame uniformity, and helps to reduce the emission levels of pollutants such as carbon monoxide and nitrogen oxides. Attached Figure Description

[0034] 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.

[0035] Figure 1 A schematic diagram of the structure of an embodiment of the fire briquette provided by the present invention;

[0036] Figure 2 for Figure 1 A cross-sectional view of an embodiment;

[0037] Figure 3 for Figure 1 A cross-sectional view of another embodiment;

[0038] Figure 4 for Figure 2 A schematic diagram of the structure of one embodiment of the central spoiler;

[0039] Figure 5 for Figure 4 A front view of an embodiment;

[0040] Figure 6 for Figure 3 A schematic diagram of another embodiment of the central spoiler;

[0041] Figure 7 for Figure 6 A cross-sectional view of an embodiment;

[0042] Figure 8 for Figure 1 A cross-sectional view of yet another embodiment;

[0043] Figure 9 for Figure 1 A schematic diagram of the structure of an embodiment of the combustion head;

[0044] Figure 10 for Figure 1 A top view of an embodiment of the combustion head.

[0045] Explanation of icon numbers:

[0046] 100. Flame duct; 10. Flame duct body; 101. Inlet air passage; 1011. Ejector section; 10111. Converging section; 10112. Expanding section; 102. Mixing chamber; 103. Air outlet; 104. Air inlet; 20. Baffle; 21. Baffle body; 2101. Converging end; 2102. Expanding end; 211. First baffle section; 212. Second baffle section; 213. Baffle protrusion; 22. Guide section; 221. First guide section; 2211. First guide section; 2212. Second guide section; 222. Second guide section; 2221. Third guide section; 2222. Fourth guide section; 201. Baffle groove; 2011. First baffle groove; 20111. First edge; 2012, Second turbulence groove; 20121, Second edge; 23, Connecting part; 30, Combustion head; 31, Flame distribution plate; 32, Flow equalization plate; 321, Second plate surface; 3211, First flow equalization zone; 3212, Second flow equalization zone; 33, Side plate; 331, First plate surface; 301, Flame hole; 302, Flow equalization hole; 3021, First flow equalization hole; 30211, First flow equalization sub-hole; 30212, Second flow equalization sub-hole; 3022, Second flow equalization hole; 303, Flow splitting hole; 304, Side air outlet channel; 305, Flame stabilizer; 40, Lateral protrusion; 41, Main body; 42, Bending plate body; α1, First included angle; α2, Second included angle; α3, Third included angle; α4, Fourth included angle.

[0047] 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

[0048] 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.

[0049] In traditional gas water heaters, the gas and air flow in the same direction in the burner, relying solely on natural mixing during the flow process. This results in insufficient mixing of gas and air inside the burner, leading to uneven distribution of combustion equivalence ratio at the burner outlet, poor flame uniformity, and mediocre emission performance.

[0050] This invention proposes a fire grill 100.

[0051] Please see Figures 1 to 3In one embodiment of the present invention, the burner 100 includes a burner body 10 and a baffle 20. The burner body 10 has an air intake channel 101 and a mixing chamber 102. The mixing chamber 102 is provided with an air outlet 103 and is connected to the exhaust end of the air intake channel 101. The air intake end of the air intake channel 101 is provided with an air inlet 104. The baffle 20 is disposed in the air intake channel 101 and includes a baffle body 21 and a guide portion 22. The baffle body 21 is provided with a through baffle groove 201, and the guide portion 22 is provided corresponding to the baffle groove 201. The baffle groove 201 is used to disperse and agitate the airflow flowing through the baffle body 21, and the guide portion 22 is used to guide the airflow from the baffle groove 201 toward the mixing chamber 102.

[0052] The burner body 10 constitutes the main structure of the burner 100. The burner body 10 is hollow, forming an air intake channel 101, a mixing chamber 102, an air outlet 103, and an air inlet 104. For ease of manufacturing, the burner body 10 can be constructed by joining two sheet metal parts together and fixing them by welding or riveting to improve the sealing reliability of the air intake channel 101 and the mixing chamber 102. The air inlet 104 can be located on the bottom side of the burner body 10 to correspond with the air outlet of the fan below the burner. The air outlet 103 of the mixing chamber 102 can be located on the top of the burner body 10, so that the flame holes 301 on the combustion head 30 of the burner 100 face upwards. The air inlet 104 of the burner body 10 connects to the mixing chamber 102 via the air intake channel 101, and then the mixing chamber 102 connects to the flame holes 301 of the combustion head 30. The air inlet 104 is used to supply air and fuel gas to the air intake channel 101. The air and fuel gas are then transported to the mixing chamber 102 for mixing, and then transported from the mixing chamber 102 to the burner port 301 for ignition to produce a flame. In practical applications, the nozzle of the burner's gas distribution device can be used to inject fuel gas into the air inlet 104 so that the fuel gas enters the air intake channel 101. At the same time, external air can also enter the air intake channel 101 through the air inlet 104 by self-priming or forced air blowing. The fuel gas and air initially come into contact in the air intake channel 101 and gradually mix with the flow. Then, they enter the mixing chamber 102 for further mixing and are discharged from the air outlet 103 to the burner port 301 for combustion.

[0053] It is understandable that the gas and air flow in the same direction in the intake channel 101, relying solely on natural mixing during the flow process, results in insufficient mixing of gas and air within the intake channel 101, thus affecting the stability of the combustion process. Due to the inadequate premixing of gas and air, localized areas of the intake channel 101 may experience excessively high or low gas concentrations, leading to differences in the ratio of gas to air participating in the combustion reaction at the burner holes 301, i.e., uneven distribution of the stoichiometric ratio. The stoichiometric ratio refers to the ratio between the actual molar ratio of gas to air participating in combustion and the stoichiometric ratio required for theoretical complete combustion. Uneven distribution of this ratio directly causes inconsistencies in the flame temperature field; some areas are rich in fuel and therefore have higher temperatures, while others are lean in fuel and therefore experience incomplete combustion, resulting in poor flame uniformity and increased emissions of pollutants such as carbon monoxide and nitrogen oxides.

[0054] To improve the uniformity of the mixing of fuel gas and air in the intake duct 101 and reduce the emission of pollutants such as carbon monoxide and nitrogen oxides, the present invention also provides a flow-dispersing element 20 within the intake duct 101. The flow-dispersing element 20 can be located on the side of the intake duct 101 near the air inlet 104, or it can be located on the side of the intake duct 101 away from the air inlet 104, i.e., near the mixing chamber 102. For example, to enhance the disturbance effect of fuel gas and air before entering the mixing chamber 102, the flow-dispersing element 20 can be located on the side of the intake duct 101 away from the air inlet 104. In this way, the airflow can still be effectively disturbed by the flow-dispersing element 20 after passing through a relatively long intake duct 101, avoiding the early disturbance from attenuating due to the excessive length of the subsequent flow path. The flow-dispersing element 20 includes a flow-dispersing body 21 and a flow-guiding part 22. The flow-dispersing body 21 is provided with a flow-dispersing groove 201, which is through-flow. The mixed gas flow of gas and air enters the intake duct 101 through the intake port 104. When it flows through the turbulence body 21, it is dispersed and disturbed into multiple small airflows by the turbulence groove 201. Some of the small airflows pass through the turbulence groove 201 and flow towards the mixing chamber 102, while other small airflows flow along the outer wall of the turbulence body 21 towards the mixing chamber 102. The small airflows that pass through the turbulence groove 201 are guided to the mixing chamber 102 by the guide part 22 provided in the corresponding turbulence groove 201, while the small airflows that flow along the outer wall of the turbulence body 21 are guided to the mixing chamber 102 by the turbulence body 21 itself. The turbulence channel 201 divides and disturbs the airflow entering the inlet channel 101, splitting the originally concentrated and laminar airflow into several smaller airflows with different velocities and paths. These smaller airflows interweave spatially, increasing the relative motion frequency between gas and air molecules and expanding their contact interface per unit volume. This enhances the turbulence intensity and contact area of ​​the gas and air within the inlet channel 101, helping to improve the initial mixing effect before entering the mixing chamber 102. The guide section 22, through its structural guiding function, ensures that the disturbed smaller airflows flow more orderly into the mixing chamber 102, avoiding adverse effects on the subsequent mixing process caused by flow turbulence. Furthermore, the shape of the turbulence channel 201 can be rectangular, circular, elliptical, etc., and is not limited here. The number of turbulence channels 201 can be multiple, and is not limited here. By setting multiple turbulence slots 201, a multi-point turbulence area can be formed in the intake air passage 101, so that the gas and air are divided by the turbulence body 21 and guided by the flow guide 22 at different cross-sectional positions, thereby improving the mixing uniformity of the overall mixing path, strengthening the control capability of the turbulence component 20 on the airflow, and further optimizing the airflow state before entering the mixing chamber 102.

[0055] In summary, the technical solution of the present invention provides a baffle 20 in the air intake channel 101 of the burner 100. The baffle 20 includes a baffle body 21 with a through baffle groove 201 and a guide part 22 corresponding to the baffle groove 201. The baffle groove 201 disperses and agitates the airflow flowing through the baffle body 21, and the guide part 22 guides the dispersed airflow toward the mixing chamber 102, so that the combustion gas and air are more fully mixed before entering the mixing chamber 102. This reduces the uneven distribution of the combustion equivalence ratio at the outlet of the burner 100, improves the flame uniformity, and helps to reduce the emission levels of pollutants such as carbon monoxide and nitrogen oxides.

[0056] like Figure 4 and Figure 5 As shown, in one embodiment, the turbulence body 21 includes a first turbulence portion 211 and a second turbulence portion 212. A first included angle α1 is formed between the first turbulence portion 211 and the second turbulence portion 212, which expands toward the side away from the air inlet 104. The turbulence groove 201 includes a first turbulence groove 2011 disposed in the first turbulence portion 211 and / or a second turbulence groove 2012 disposed in the second turbulence portion 212.

[0057] In this embodiment, the first baffle 211 and the second baffle 212 are arranged to gradually open along the direction of airflow from the air inlet 104 to the mixing chamber 102. The first included angle α1 between them gives the baffle body 21 a larger expansion span at the end near the mixing chamber 102. The direction of this expansion span can be an extension in the width or height direction of the firebox body 10. The expansion structure formed by the first baffle 211 and the second baffle 212 helps guide the airflow to diffuse into the mixing chamber 102 when passing through the baffle body 21, thereby alleviating the airflow concentration phenomenon to a certain extent.

[0058] Since the first turbulence section 211 and the second turbulence section 212 are arranged in an expanding manner, the airflow flowing along the intake direction first contacts the outer walls of the first turbulence section 211 and the second turbulence section 212, and expands towards the mixing chamber 102 under their guidance. Subsequently, a portion of the airflow continues to flow towards the mixing chamber 102 along the outer walls of the first turbulence section 211 and the second turbulence section 212, while another portion of the airflow enters the first turbulence groove 2011 and / or the second turbulence groove 2012 respectively. The airflow entering the first turbulence groove 2011 and / or the second turbulence groove 2012 is further divided and disturbed into multiple small airflows, which are guided to the mixing chamber 102 by the guide sections 22 correspondingly provided at the first turbulence groove 2011 and / or the second turbulence groove 2012. Through the diversion and disturbance effects of the above-mentioned path, the gas and air undergo multiple directional adjustments and interface reorganizations within the disturbance body 21, which helps to improve their mixing uniformity and provides more favorable initial conditions for full mixing in the mixing chamber 102.

[0059] like Figure 4 and Figure 5 As shown, in one embodiment, the air inlet 104 is located on one side of the burner body 10 along the length direction. The air inlet 104 and the baffle 20 are arranged opposite each other along the length direction of the burner body 10. The air outlet 103 is located on one side of the burner body 10 along the height direction. The first baffle 211 is inclined along the air intake direction of the air intake channel 101 towards the side closer to the air outlet 103. The second baffle 212 is inclined along the air intake direction of the air intake channel 101 towards the side farther from the air outlet 103.

[0060] In this embodiment, since the air inlet 104 is located on one side of the burner body 10 along its length, and the baffle 20 is arranged opposite to the air inlet 104 along the length of the burner body 10, the airflow entering from the air inlet 104 needs to flow a certain distance along the length of the burner body 10 before reaching the location of the baffle 20. Thus, the airflow can gain a certain development length during its journey, which helps to reduce the local velocity and concentration gradients in the area of ​​the air inlet 104 caused by gas injection or air intake. This allows the gas and air to form a relatively uniform initial distribution before reaching the baffle 20, thereby improving the effectiveness of the baffle 20 in dividing and guiding the airflow. The air outlet 103 is located on one side of the burner body 10 along its height, indicating that the airflow needs to change its flow direction after mixing to be discharged towards the air outlet 103.

[0061] In this configuration, the first baffle 211 is tilted towards the side closer to the air outlet 103, which helps to guide part of the airflow upward, allowing it to flow more smoothly towards the air outlet 103; the second baffle 212 is tilted towards the side farther from the air outlet 103, which can cause another part of the airflow to deflect downward, thus forming a vertically differentiated flow path. The formation of this vertically differentiated flow path is closely related to the fact that the air outlet 103 is located on one side of the burner body 10 along the height direction. Since the air outlet 103 is located in the height direction, the airflow needs to turn upward after passing through the baffle 20 in order to effectively merge into the air outlet 103. If all the airflow is concentrated in the same height area and turns, it is easy to cause excessively high local flow velocity or flow blockage. The first turbulence section 211 is inclined towards the side closer to the outlet 103, conforming to the overall trend of airflow converging towards the outlet 103. This provides pre-deflection guidance for some airflow, reducing the angle change required for subsequent turning and thus reducing flow losses. The second turbulence section 212 is inclined away from the outlet 103, intentionally guiding another part of the airflow in the opposite direction, delaying its upward turning process, allowing this part of the airflow to occupy a lower area in space and gradually migrate upward in subsequent flow. The symmetrical guiding structure constructed by the different inclination directions of the first turbulence section 211 and the second turbulence section 212 can form staggered flow layers downstream of the turbulence member 20, avoiding excessive concentration of airflow in a single height area, while promoting lateral mixing between different height layers. The first turbulence section 211 and the second turbulence section 212 are arranged at an angle to cooperate with the first turbulence groove 2011 and the second turbulence groove 2012 to divide the flow. This causes the gas and air to be disturbed when passing through the turbulence member 20. Furthermore, due to the guidance of different tilt directions, they generate more complex flow trajectories in space, which is beneficial to enhance the mixing effect between the two and provide a more uniformly distributed premixed airflow for subsequent entry into the mixing chamber 102.

[0062] like Figure 4 and Figure 5 As shown, in one embodiment, the first included angle α1 is not less than 30 degrees and not greater than 45 degrees.

[0063] In this embodiment, the range of the first included angle α1 can create a suitable airflow diffusion space and path differentiation effect within the turbulence body 21. If the first included angle α1 is less than 30 degrees, the opening between the first turbulence part 211 and the second turbulence part 212 may not be sufficient to effectively guide airflow diffusion, causing the airflow to remain concentrated and weakening the turbulence effect; if the first included angle α1 is greater than 45 degrees, the expansion is too large, which may cause local flow separation or backflow, which is not conducive to the stable delivery and uniform distribution of airflow. Controlling the first included angle α1 within the range of 30 to 45 degrees helps to maintain the continuity of airflow while allowing the combustion gas and air to achieve reasonable longitudinal expansion and path differentiation when passing through the turbulence body 21, thereby improving the mixing uniformity and supporting the stability of the subsequent combustion process without excessively increasing the flow resistance.

[0064] like Figure 4 and Figure 5 As shown, in one embodiment, the turbulence-disrupting body 21 has a constricted end 2101 and an expanded end 2102 disposed opposite to each other along the length direction of the burner body 10. The first turbulence-disrupting groove 2011 has a first edge 20111 on the side near the constricted end 2101. The flow guide 22 includes a first flow guide 221, which includes a first flow guide section 2211 and a second flow guide section 2212 that are bent and connected. The first flow guide section 2211 is inclined from the first edge 20111 toward the side away from the air outlet 103. The second flow guide section 2212 is disposed opposite to the first turbulence-disrupting groove 2011.

[0065] In this embodiment, the turbulence-disrupting body 21 gradually expands from the contraction end 2101 to the expansion end 2102 along the length of the burner body 10, causing the airflow to experience a channel change from narrow to wide when passing through the turbulence-disrupting body 21, which helps to promote the longitudinal expansion and uniform distribution of the airflow. The first turbulence-disrupting groove 2011 has a first edge 20111 on the side near the contraction end 2101, which constitutes the initial boundary for the airflow to enter the first turbulence-disrupting groove 2011. The first guide section 221 is located near the first turbulence-disrupting groove 2011, and its first guide section 2211 extends obliquely from the first edge 20111 toward the side away from the air outlet 103. It can initially guide the flow direction of the small airflows after the airflow is divided into small airflows through the first turbulence-disrupting groove 2011, so that the small airflows deflect toward the central region of the turbulence-disrupting body 21, thereby avoiding the small airflows from flowing straight along the air intake direction and causing local concentration. Subsequently, the second guide section 2212 is positioned opposite to the first turbulence channel 2011, receiving the small airflow deflected by the first guide section 2211 and guiding it to flow along the inner wall of the first turbulence section 211 toward the mixing chamber 102. This further disperses the segmented small airflow in space and allows it to flow into the mixing chamber 102 in an orderly manner. Since the first guide section 2211 and the second guide section 2212 are connected by a bend, they together form a continuous guide structure with a steering function. This structure can apply an orderly path constraint to the small airflow segmented by the first turbulence channel 2011 without significantly increasing flow resistance, allowing it to flow into the mixing chamber 102 more effectively. This improves the spatial distribution uniformity and mixing efficiency of the fuel gas and air before entering the mixing chamber 102.

[0066] like Figure 4 and Figure 5 As shown, in one embodiment, the turbulence-disrupting body 21 has a constricted end 2101 and an expanded end 2102 disposed opposite to each other along the length direction of the burner body 10. The second turbulence-disrupting groove 2012 has a second edge 20121 on the side near the constricted end 2101. The flow guide 22 includes a second flow guide 222, which includes a third flow guide section 2221 and a fourth flow guide section 2222 that are bent and connected. The third flow guide section 2221 is inclined from the second edge 20121 toward the side near the air outlet 103, and the fourth flow guide section 2222 is disposed opposite to the second turbulence-disrupting groove 2012.

[0067] In this embodiment, the turbulence-disrupting body 21 gradually expands from the contraction end 2101 to the expansion end 2102 along the length of the burner body 10, causing the airflow to experience a channel change from narrow to wide when passing through the turbulence-disrupting body 21, which helps to promote the longitudinal expansion and uniform distribution of the airflow. The second turbulence-disrupting groove 2012 has a second edge 20121 on the side near the contraction end 2101, which constitutes the initial boundary for the airflow to enter the second turbulence-disrupting groove 2012. The second guide section 222 is located near the second turbulence-disrupting groove 2012, and its third guide section 2221 extends obliquely from the second edge 20121 toward the side near the air outlet 103. It can initially guide the flow direction of the small airflows after the airflow is divided into small airflows through the second turbulence-disrupting groove 2012, causing the small airflows to deflect toward the central region of the turbulence-disrupting body 21, thereby avoiding the small airflows from flowing straight along the air intake direction and causing local concentration. Subsequently, the fourth guide section 2222 is positioned opposite to the second turbulence channel 2012, receiving the small airflow deflected by the third guide section 2221 and guiding it to flow along the inner wall of the second turbulence section 212 toward the mixing chamber 102. This further disperses the segmented small airflow in space and allows it to flow into the mixing chamber 102 in an orderly manner. Since the third guide section 2221 and the fourth guide section 2222 are connected by a bend, they together form a continuous guide structure with a steering function. This structure can apply an orderly path constraint to the small airflow segmented by the second turbulence channel 2012 without significantly increasing flow resistance, allowing it to flow into the mixing chamber 102 more effectively. This improves the spatial distribution uniformity and mixing efficiency of the fuel gas and air before entering the mixing chamber 102.

[0068] like Figure 4 and Figure 5 As shown, in one embodiment, the first turbulence portion 211 and / or the second turbulence portion 212 are provided with a plurality of turbulence protrusions 213 at the end away from the air inlet 104, and the plurality of turbulence protrusions 213 are arranged at intervals along the width direction of the burner body 10.

[0069] In this embodiment, the first turbulence section 211 has a turbulence protrusion 213 at the end away from the air inlet 104. The turbulence protrusion 213 is used to apply local turbulence to the airflow about to enter the mixing chamber 102, further dispersing any possible concentration or velocity concentration areas, and enhancing the mixing effect of the fuel gas and air near the inlet of the mixing chamber 102. Multiple turbulence protrusions 213 are provided, and these protrusions are arranged at intervals along the width direction of the burner body 10. By providing multiple turbulence protrusions 213, a multi-point distributed turbulence effect can be formed in the width direction of the burner body 10, causing the airflow to experience turbulence at different lateral positions. This helps improve the uniformity of airflow distribution in the width direction and reduces the occurrence of localized rich or lean combustion phenomena.

[0070] Similarly, the end of the second turbulence section 212 furthest from the air inlet 104 is provided with a turbulence protrusion 213. The turbulence protrusion 213 is used to locally turbulent the airflow flowing through the end of the second turbulence section 212, refine the airflow distribution structure in the width direction of the combustor body 10, and improve the mixing efficiency at the microscale. Multiple turbulence protrusions 213 are provided, and these protrusions are arranged at intervals along the width direction of the combustor body 10. By providing multiple turbulence protrusions 213, a continuous and dispersed turbulence effect can be constructed within the width range covered by the second turbulence section 212, preventing the airflow from excessively adhering to the second turbulence section 212 due to inertia, thereby promoting the lateral diffusion and homogenization of the airflow in the width direction.

[0071] Furthermore, the number of turbulence protrusions 213 provided on the first turbulence section 211 and the second turbulence section 212 can be two, three, or even more. For example, the first turbulence section 211 and the second turbulence section 212 each have seven turbulence protrusions 213 at the end away from the air inlet 104. This configuration can achieve a relatively dense and balanced turbulence coverage in the width direction of the burner body 10, effectively improving the airflow control capability of the turbulence protrusions 213 while maintaining low flow resistance, thereby optimizing the premixed airflow state before entering the mixing chamber 102.

[0072] like Figure 6 and Figure 7 As shown, in one embodiment, the turbulence-disrupting body 21 surrounds the flow-guiding portion 22, and the turbulence-disrupting groove 201 is located between the peripheral wall of the turbulence-disrupting body 21 and the flow-guiding portion 22.

[0073] In this embodiment, the turbulence-inducing body 21 is arranged to surround the flow guide 22, so that the flow guide 22 is contained within the internal space enclosed by the turbulence-inducing body 21. The turbulence-inducing groove 201 is formed in the annular channel between the peripheral wall of the turbulence-inducing body 21 and the flow guide 22. When the airflow enters the intake air passage 101 and flows through the turbulence-inducing member 20, part of the airflow flows along the outer peripheral wall of the turbulence-inducing body 21, while the other part of the airflow passes through the turbulence-inducing groove 201 and enters the annular channel between the turbulence-inducing body 21 and the flow guide 22. Since the turbulence-inducing groove 201 is located between the peripheral wall of the turbulence-inducing body 21 and the flow guide 22, it provides a path for the airflow to transition from the outside of the turbulence-inducing body 21 to the internal flow guide 22 region, while simultaneously dividing and turbulentizing the airflow during the passage. The flow guide 22 is located inside the turbulence-inducing groove 201 and can directionally guide the airflow entering through the turbulence-inducing groove 201, causing it to flow orderly towards the mixing chamber 102 along the intake direction. This layout enables the turbulence-dispersing body 21 and the flow guide 22 to work together in space. The turbulence-dispersing groove 201 achieves initial dispersion of airflow, while the flow guide 22 maintains the continuity of airflow along the intake direction after disturbance. This improves the mixing effect while avoiding flow turbulence or local backflow caused by excessive disturbance.

[0074] like Figure 6 and Figure 7 As shown, in one embodiment, in the air intake direction of the air intake channel 101, the peripheral wall of the turbulence body 21 is constricted toward the side away from the air intake port 104.

[0075] In this embodiment, in the intake direction of the intake channel 101, the peripheral wall of the turbulence body 21 is tapered away from the intake port 104, causing the cross-sectional area of ​​the turbulence body 21 to gradually decrease along the intake direction. This structure causes the annular channel formed by the turbulence groove 201 to narrow accordingly in the intake direction, thereby producing a local acceleration and convergence effect on the airflow entering the turbulence groove 201. Since the turbulence groove 201 is located between the peripheral wall of the turbulence body 21 and the guide portion 22, the change in the size of its annular channel can enhance the shearing and segmentation effect on the airflow, promoting more sufficient contact and mixing of the combustion gas and air when passing through the turbulence groove 201. At the same time, the tapering shape of the turbulence body 21 along the intake direction helps to constrain the distribution range of the disturbed airflow, keeping it in a relatively concentrated spatial shape near the inlet area of ​​the mixing chamber 102, avoiding an increase in concentration gradient or energy loss due to excessive diffusion, thereby providing more uniform and controllable initial conditions for the subsequent mixing process.

[0076] like Figure 6 and Figure 7 As shown, in one embodiment, the peripheral wall of the guide portion 22 is extended toward the side away from the air inlet 104.

[0077] In this embodiment, the peripheral wall of the guide section 22 expands away from the air inlet 104, causing the cross-sectional area of ​​the guide section 22 to gradually increase along the air intake direction. This expansion structure, together with the turbulence body 21, creates a flow cross-section change from narrow to wide within the annular channel formed by the turbulence groove 201, which helps to reduce the velocity gradient of the airflow entering through the turbulence groove 201 in the region near the mixing chamber 102. At the same time, the expansion shape of the guide section 22 can provide a wider guiding space for the airflow output from the turbulence groove 201, allowing it to achieve appropriate radial expansion during its journey along the air intake direction. This, combined with the constraint effect of the turbulence body 21, optimizes the spatial distribution of the mixed airflow at the annular channel outlet.

[0078] More importantly, the turbulence-inducing body 21 surrounds the flow guide 22, and the turbulence-inducing groove 201 is located between the peripheral wall of the turbulence-inducing body 21 and the flow guide 22. The peripheral wall of the flow guide 22 expands away from the air inlet 104, while the peripheral wall of the turbulence-inducing body 21 contracts away from the air inlet 104 in the air intake direction of the air intake channel 101. In this structure, the airflow entering the annular channel through the turbulence-inducing groove 201 is divided into two parts: one part flows along the inner peripheral wall of the turbulence-inducing body 21 toward the mixing chamber 102, and the other part flows along the outer peripheral wall of the flow guide 22 toward the mixing chamber 102. Because the inner peripheral wall of the turbulence-inducing body 21 contracts inward while the outer peripheral wall of the flow guide 22 expands outward, the two airflows gradually approach each other as they advance in the air intake direction, and converge and overlap in the inlet area of ​​the mixing chamber 102, forming a spatial cross-mixing effect. This cross-mixing effect helps to break the unevenness of local concentration or velocity, improve the mixing quality of gas and air before entering the mixing chamber 102, and provide more uniform premixed airflow conditions for the subsequent combustion process.

[0079] like Figure 6 and Figure 7 As shown, in one embodiment, in the axial cross section of the turbulence body 21, a second included angle α2 is formed between the two side edges of the turbulence body 21, the second included angle α2 being not less than 25 degrees and not greater than 35 degrees.

[0080] In this embodiment, the turbulence-disrupting body 21 surrounds the flow guide 22, and the turbulence-disrupting groove 201 is located between the peripheral wall of the turbulence-disrupting body 21 and the flow guide 22. In the air intake direction of the air intake channel 101, the peripheral wall of the turbulence-disrupting body 21 is constricted towards the side away from the air intake 104. This constriction shape is manifested in the axial cross section as the two side edges of the turbulence-disrupting body 21 moving inward, thereby forming a second included angle α2. By controlling the second included angle α2 between 25 degrees and 35 degrees, a reasonable convergence rate of the annular channel can be maintained during the constriction of the turbulence-disrupting body 21 along the air intake direction. This avoids weakening the convergence effect of the airflow due to the channel narrowing too slowly due to an excessively small angle, or inducing flow blockage or separation due to a sudden reduction in the local flow cross section caused by an excessively large angle. Within this angular range, the turbulence body 21 can effectively constrain the distribution range of the airflow entering through the turbulence groove 201 along the air intake direction, and can also work with the guide section 22 to maintain the continuity and stability of the airflow in the annular channel, providing a more concentrated and uniform airflow for the inlet area of ​​the mixing chamber 102.

[0081] like Figure 6 and Figure 7 As shown, in one embodiment, in the axial section of the guide portion 22, a third included angle α3 is formed between the two side edges of the guide portion 22, the third included angle α3 being not less than 25 degrees and not greater than 35 degrees.

[0082] In this embodiment, the turbulence-inducing body 21 surrounds the flow guide 22, and the turbulence-inducing groove 201 is located between the peripheral wall of the turbulence-inducing body 21 and the flow guide 22. The peripheral wall of the flow guide 22 expands away from the air inlet 104. This expansion shape is manifested in the axial cross-section as the two side edges of the flow guide 22 opening outward, thereby forming a third included angle α3. By controlling the third included angle α3 between 25 degrees and 35 degrees, the cross-sectional change of the annular channel can maintain a moderate gradual expansion rate during the expansion of the flow guide 22 along the air intake direction, avoiding insufficient expansion due to an excessively small angle that would limit the radial expansion capability of the airflow, or a sudden increase in local flow space due to an excessively large angle that would cause flow stagnation or backflow. Within this angular range, the guide section 22 can provide a stable and gradually expanding guiding area for the airflow entering through the turbulence channel 201, so that it can obtain reasonable spatial distribution adjustment when it advances along the air intake direction. At the same time, it works in conjunction with the contraction profile of the turbulence body 21 to optimize the uniformity and continuity of the airflow at the outlet of the annular channel, laying a good premixing foundation for subsequent entry into the mixing chamber 102.

[0083] like Figure 6 and Figure 7 As shown, in one embodiment, multiple turbulence channels 201 are provided, and the multiple turbulence channels 201 are arranged circumferentially along the guide portion 22.

[0084] In this embodiment, the turbulence-inducing body 21 surrounds the flow guide 22, and the turbulence-inducing groove 201 is located between the peripheral wall of the turbulence-inducing body 21 and the flow guide 22. Multiple turbulence-inducing grooves 201 are arranged circumferentially along the flow guide 22, dividing the annular channel between the turbulence-inducing body 21 and the flow guide 22 into multiple circumferentially distributed local channels. This arrangement can form multiple point and multiple region turbulence inlets in the air intake direction, causing the airflow entering the turbulence-inducing component 20 to undergo segmentation and turbulence at different circumferential positions. Because the turbulence-inducing grooves 201 are evenly or intermittently distributed around the flow guide 22, the airflow entering through each turbulence-inducing groove 201 can cover a wider circumferential range during its subsequent propagation along the air intake direction, helping to improve the circumferential uniformity of the airflow within the annular channel. Meanwhile, the arrangement of multiple turbulence channels 201 enhances the ability of the turbulence body 21 and the guide section 22 to coordinate and regulate the airflow, providing a more spatially balanced and fully mixed premixed airflow to the inlet area of ​​the mixing chamber 102 without increasing the overall flow resistance.

[0085] like Figures 1 to 3 As shown, in one embodiment, the air intake channel 101 has an ejector section 1011 extending from the air intake port 104 toward the mixing chamber 102. The ejector section 1011 has a tapered section 10111 and a diffusing section 10112 arranged and connected along the air intake direction of the air intake channel 101. The turbulence member 20 is disposed in the diffusing section 10112.

[0086] In this embodiment, the ejector section 1011 is part of the intake airflow channel 101. Its tapering section 10111 gradually reduces the flow cross-section along the intake direction, which helps to increase the flow velocity of the combustion gas and air and enhance the initial mixing effect. The subsequent expanding section 10112 gradually increases the flow cross-section along the intake direction, which can reduce the velocity gradient to a certain extent and provide a suitable working environment for the turbulence-dispersing component 20. The turbulence-dispersing component 20 is located in the expanding section 10112, so that the turbulence-dispersing body 21 and the guide section 22 can divide and guide the airflow in a region with a relatively stable flow field and a certain development length. This arrangement allows the turbulence-dispersing channel 201 to fully exert its dispersing and disturbing effect on the airflow, while enabling the guide section 22 to more effectively guide the disturbed airflow to the mixing chamber 102 in an orderly manner, thereby synergistically improving the premixing uniformity and combustion stability of the overall structure.

[0087] like Figures 8 to 10 As shown, in one embodiment, the burner 100 further includes a combustion head 30 disposed on the burner body 10. The combustion head 30 includes a flame distribution plate 31 and a flow equalization plate 32. The flame distribution plate 31 covers the gas outlet 103. The flow equalization plate 32 is disposed on the side of the flame distribution plate 31 facing the mixing chamber 102. The flame distribution plate 31 is provided with a plurality of flame holes 301, and the flow equalization plate 32 is provided with a plurality of flow equalization holes 302.

[0088] In this embodiment, after the airflow in the mixing chamber 102 enters the combustion head 30 region through the outlet 103, it first passes through multiple flow equalization holes 302 on the flow equalization plate 32, allowing the airflow to undergo further distribution adjustment and velocity equalization before entering the flame holes 301. Subsequently, the airflow passes through multiple flame holes 301 on the flame distribution plate 31 and is ignited at the flame holes 301 to form a flame. The flow equalization plate 32 helps to alleviate local flow unevenness caused by the upstream turbulence member 20 or the mixing chamber 102, improves the consistency of air supply to each flame hole 301, and thus improves the uniformity and stability of the flame.

[0089] like Figures 8 to 10 As shown, in one embodiment, the plurality of flow equalization holes 302 include a first flow equalization hole 3021 and a second flow equalization hole 3022; the flow equalization plate 32 has two first flow equalization regions 3211 opposite to each other along the length direction, and a second flow equalization region 3212 located between the two first flow equalization regions 3211. The first flow equalization region 3211 is provided with a plurality of first flow equalization holes 3021, and the second flow equalization region 3212 is provided with a plurality of second flow equalization holes 3022. The opening area of ​​the second flow equalization hole 3022 is larger than the opening area of ​​the first flow equalization hole 3021.

[0090] In this embodiment, the mixing chamber 102 includes a first chamber segment and a second chamber segment, which are sequentially arranged from the inlet air passage 101 to the outlet air outlet 103. The flow cross-sectional area of ​​the first chamber segment decreases from the inlet air passage 101 to the second chamber segment, while the flow cross-sectional area of ​​the second chamber segment increases from the second chamber segment to the outlet air outlet 103. This results in the mixing chamber 102 forming a flow structure that first contracts and then expands. The airflow accelerates as it passes through the first chamber segment due to the reduced flow area, and then decelerates and diffuses as it enters the second chamber segment due to the increased flow area. This leads to a distribution trend of lower flow rate in the middle and higher flow rate on both sides in the outlet region of the mixing chamber 102. To compensate for this distribution difference, the flow equalization plate 32 is configured with a second flow equalization hole 3022 with a larger opening area in the middle second flow equalization zone 3212 to improve the flow capacity in the middle region; while the first flow equalization zones 3211 on both sides use first flow equalization holes 3021 with smaller opening areas to moderately limit their flow capacity. By setting a first flow equalization hole 3021 and a second flow equalization hole 3022 with different opening areas, the flow equalization plate 32 can differentiate the airflow in different flow equalization zones, so that the flow rate of the mixed gas entering each flame hole 301 tends to be balanced, thereby improving the uniformity and stability of the overall flame of the combustion head 30.

[0091] like Figures 8 to 10 As shown, in one embodiment, the plurality of first flow equalization holes 3021 include a plurality of first flow equalization sub-holes 30211 and a plurality of second flow equalization sub-holes 30212. The plurality of first flow equalization sub-holes 30211 and the plurality of second flow equalization sub-holes 30212 are alternately arranged along the length direction of the flow equalization plate 32. The plurality of second flow equalization sub-holes 30212 are arranged in multiple rows along the width direction of the flow equalization plate 32. Each row has a plurality of second flow equalization sub-holes 30212. The opening area of ​​the first flow equalization sub-holes 30211 is larger than the opening area of ​​the second flow equalization sub-holes 30212.

[0092] In this embodiment, the multiple first flow equalization holes 3021 within the first flow equalization zone 3211 are arranged alternately with the second flow equalization sub-holes 30211 along the length of the flow equalization plate 32, forming a periodically changing flow structure. The first flow equalization sub-holes 30211 with larger opening areas provide relatively high local flow capacity, while the second flow equalization sub-holes 30212 with smaller opening areas play a moderate throttling role. The multiple second flow equalization sub-holes 30212 are further arranged in multiple rows along the width direction of the flow equalization plate 32, with each row containing multiple second flow equalization sub-holes 30212, resulting in a dense and orderly distributed throttling array in the width direction. This structure enables fine-tuning of flow along the length direction and precise distribution control along the width direction within the first flow equalization zone 3211. This helps alleviate the gas supply differences caused by the non-uniformity of the opening area and spatial arrangement of the first flow equalization sub-hole 30211 and the second flow equalization sub-hole 30212, thereby improving the consistency of the gas and air mixture supply in the flame hole 301 area and enhancing combustion stability.

[0093] like Figures 8 to 10 As shown, in one embodiment, a plurality of second flow equalization holes 3022 are arranged along the length direction of the flow equalization plate 32.

[0094] In this embodiment, multiple second flow equalization holes 3022 are arranged along the length of the flow equalization plate 32, so that the second flow equalization zone 3212 forms a continuous and orderly flow structure along the length. This arrangement can provide a relatively uniform flow cross section in the middle region of the flow equalization plate 32 along the length, which helps to alleviate the local flow concentration or attenuation caused by the geometry of the upstream mixing chamber 102. By regularly arranging the second flow equalization holes 3022 with large opening areas along the length, the overall flow capacity of the middle region can be improved without introducing additional flow disturbances, so that the mixed airflow entering the corresponding burner hole 301 is more evenly distributed in space, thereby providing more consistent gas supply conditions for the combustion head 30 and improving flame stability and uniformity.

[0095] like Figures 8 to 10 As shown, in one embodiment, the combustion head 30 further includes two side plates 33 respectively disposed on both sides of the width direction of the flow equalization plate 32. Each side plate 33 is provided with a plurality of flow diversion holes 303. A side air outlet channel 304 is formed between the side of each side plate 33 away from the other side plate 33 and the burner body 10. The plurality of side air outlet channels 304 are connected one-to-one with the plurality of flow diversion holes 303. The side of the side air outlet channel 304 away from the mixing chamber 102 is open to form a flame stabilizer 305.

[0096] In this embodiment, two side plates 33 are located on both sides of the width direction of the flow equalization plate 32, and multiple diversion holes 303 provided on them form independent and one-to-one flow paths with their respective side exhaust channels 304. Part of the premixed airflow in the mixing chamber 102 enters the side exhaust channel 304 through the diversion holes 303 and is discharged through the flame stabilizer 305 open on the side of the side exhaust channel 304 away from the mixing chamber 102. This structure allows the combustion head 30 to form additional auxiliary exhaust areas on both sides in the width direction outside the area of ​​the flame hole 301. The airflow released by the flame stabilizer 305 can form a low-speed, continuous flow at the outer edge of the main flame, which helps to stabilize the flame root, suppress flame detachment or flashing, and form a local backflow zone to maintain the continuity of ignition and combustion. By configuring the side air outlet channel 304 and the diversion hole 303 one-to-one, and combining them with the open structure of the flame stabilizer 305, the edge flame stabilization function can be provided to the combustion head 30 without interfering with the gas supply of the flame hole 301, thereby improving the overall combustion reliability and anti-disturbance capability.

[0097] like Figures 8 to 10 As shown, in one embodiment, the cross-sectional area of ​​the side outlet passage 304 gradually expands from the side away from the flame stabilizer 305 toward the flame stabilizer 305.

[0098] In this embodiment, the cross-sectional area of ​​the side outlet passage 304 gradually expands from the side away from the flame stabilizer 305 towards the flame stabilizer 305, causing the flow cross-section of the airflow passing through the side outlet passage 304 to gradually increase as it approaches the flame stabilizer 305. This gradually expanding structure helps to reduce the airflow velocity near the flame stabilizer 305, preventing the flame from being blown away from the flame stabilizer 305 or causing unstable combustion due to excessively high flow velocity. At the same time, as the cross-sectional area gradually expands, the airflow pressure is moderately restored, which is conducive to forming a stable, continuous, and uniformly distributed low-speed airflow at the flame stabilizer 305, providing a reliable flame stabilizing gas source for the edge flame.

[0099] like Figures 8 to 10 As shown, in one embodiment, the portion of the burner body 10 opposite to each side plate 33 is provided with a plurality of lateral protrusions 40 at intervals along its length direction. Each lateral protrusion 40 forms a side air outlet channel 304 with the adjacent side plate 33. Each lateral protrusion 40 includes a main body 41 disposed opposite to the side plate 33, and bent plates 42 disposed on opposite sides of the main body 41. Each bent plate 42 is bent relative to the main body 41 toward the side closer to the side plate 33.

[0100] In this embodiment, the burner body 10 has multiple lateral protrusions 40 spaced apart along its length at the location opposite to the side plate 33, which, together with the side plate 33, form multiple independent side air outlet channels 304. Each lateral protrusion 40 consists of a main body 41 and bent plates 42 located on opposite sides thereof. The bent plates 42 are bent towards the side closer to the side plate 33, thereby structurally forming a barrier around the two sides of the side air outlet channel 304. This structure not only limits the flow space of the side air outlet channel 304, but also enhances the assembly stability between the burner body 10 and the side plate 33, while preventing airflow from leaking through unexpected gaps between the lateral protrusions 40 and the side plate 33. Since the lateral protrusions 40 are spaced apart along the length of the burner body 10, the resulting multiple side air outlet channels 304 are discretely distributed along their length, allowing for multi-point, segmented supply of flame-stabilizing airflow to the edge region of the combustion head 30. This helps maintain local flame stability at different locations and improves the overall combustion uniformity and anti-disturbance capability.

[0101] like Figures 8 to 10 As shown, in one embodiment, the bent plate 42 and the main plate 41 are set at an obtuse angle.

[0102] In this embodiment, the bent plate 42 and the main plate 41 are set at an obtuse angle, so that the lateral protrusion 40 forms a gently transitioning bent area in the structure. This obtuse angle configuration helps to reduce the flow resistance of the airflow when it flows through the connection between the bent plate 42 and the main plate 41, and reduces local eddies or flow separation caused by abrupt changes in direction. At the same time, the obtuse angle arrangement allows the bent plate 42 to extend more stably toward the side plate 33, reducing gap fluctuations between the bent plate 42 and the side plate 33 caused by assembly deviations or thermal deformation, thereby ensuring that the airflow is smoothly delivered to the flame stabilizer 305 along the side outlet channel 304.

[0103] like Figures 8 to 10 As shown, in one embodiment, a fourth included angle α4 is formed between the bent plate 42 and the adjacent side plate 33, the fourth included angle α4 being not less than 10 degrees and not greater than 15 degrees.

[0104] In this embodiment, a fourth angle α4 is formed between the bent plate 42 and the adjacent side plate 33. This fourth angle α4 is limited to the range of 10 to 15 degrees, so that the side exhaust channel 304 maintains a relatively gentle flow gap in the area near the flame stabilizer 305. This angle range helps to avoid the gap between the bent plate 42 and the side plate 33 being too narrow due to an excessively small angle, thereby reducing flow resistance and preventing abnormal increases in local flow velocity; at the same time, it also avoids the gap in the outlet area of ​​the side exhaust channel 304 being too wide due to an excessively large angle, which would cause the airflow to diffuse too early or lose direction control near the flame stabilizer 305. By controlling the fourth angle α4 within this range, while maintaining structural compactness, the airflow can achieve a relatively uniform lateral distribution and stable discharge state at the flame stabilizer 305. This is beneficial for forming a continuous, low-disturbance auxiliary airflow at the edge of the combustion head 30, providing effective flame stabilization support for the flame root, and improving the adhesion and operational stability of combustion.

[0105] like Figures 8 to 10 As shown, in one embodiment, the main body 41 is inclined outward relative to the adjacent side plate 33 in the direction toward the flame stabilizing port 305.

[0106] In this embodiment, the main body 41 is inclined outward relative to the adjacent side plate 33 in the direction towards the flame stabilizer 305, so that the side exhaust channel 304 formed between the lateral protrusion 40 and the side plate 33 gradually widens along this direction. This inclined arrangement helps to provide a moderately increased flow cross-section in the area near the flame stabilizer 305, thereby reducing the velocity gradient of the airflow near the flame stabilizer 305 and avoiding the impact of excessive velocity on flame stability. At the same time, the outward inclination of the main body 41 can cooperate with the structural layout of the bent plate 42 to form a gently transitioning geometry in the length direction of the side exhaust channel 304, reducing the generation of flow separation or local vortices. In addition, this inclined structure can also optimize the volume distribution of the side exhaust channel 304 in a limited space, improve the uniformity and continuity of the airflow in the flame stabilizer 305, and provide a more reliable flame stabilizing gas source for the edge area of ​​the combustion head 30.

[0107] like Figures 8 to 10 As shown, in one embodiment, each side plate 33 has a first plate surface 331, and the first plate surface 331 of each side plate 33 is disposed away from the other side plate 33. The sum of the total area of ​​the plurality of diversion holes 303 of the two side plates 33 is defined as S1, and the sum of the total area of ​​the two first plate surfaces 331 is defined as S2. The ratio of S1 to S2 is not less than 0.2 and not greater than 0.3.

[0108] In this embodiment, the first surface 331 of each side plate 33 faces the outside of the flame arrestor body 10. The sum of the areas of the two first surfaces 331, S2, reflects the overall structural dimensions of the two side plates 33, while the sum of the areas of all the diversion holes 303 on the two side plates 33, S1, characterizes the total flow capacity of the flame stabilizing airflow. Limiting the ratio of S1 to S2 to between 0.2 and 0.3 provides an appropriate area of ​​diversion holes 303 to meet the flame stabilizing requirements while ensuring the structural strength of the side plates 33. If the ratio is too small, the total area of ​​the diversion holes 303 will be insufficient, which may lead to insufficient airflow supply to the flame stabilizing port 305 and affect the stability of the edge flame. If the ratio is too large, the effective support area of ​​the side plates 33 will be reduced, which may weaken its mechanical strength and lead to excessively concentrated airflow distribution or local velocity imbalance. By controlling S1 / S2 within this range, a balance can be achieved between structural reliability and flame stabilizing performance, allowing the flame stabilizing port 305 to obtain a continuous, uniform, and controllable auxiliary airflow, thereby effectively supporting the overall combustion stability of the combustion head 30.

[0109] like Figures 8 to 10 As shown, in one embodiment, the flow equalization plate 32 has a second plate surface 321 facing the fire distribution plate 31. The sum of the total areas of the plurality of flow equalization holes 302 is defined as S3, and the area of ​​the second plate surface 321 is defined as S4. The ratio of S3 to S4 is not less than 0.25 and not greater than 0.35.

[0110] In this embodiment, the second surface 321 of the flow equalization plate 32 faces the flame distribution plate 31, and its area S4 represents the effective coverage range of the flow equalization plate 32 in the combustion head 30. The sum of the areas S3 of the multiple flow equalization holes 302 reflects the total flow capacity of the mixed airflow entering the flame hole 301 region through the flow equalization plate 32. Limiting the ratio of S3 to S4 to between 0.25 and 0.35 ensures that the flow equalization plate 32 has sufficient structural strength while providing an appropriate opening ratio to achieve effective distribution of the mixed airflow. If the ratio is lower than 0.25, the total area of ​​the flow equalization holes 302 is relatively insufficient, which may lead to increased airflow resistance and affect the uniformity of air supply to each flame hole 301. If the ratio is higher than 0.35, the opening density is too large, which may weaken the mechanical stability of the flow equalization plate 32 and reduce its ability to regulate airflow distribution. By controlling S3 / S4 within this range, it is helpful to optimize the velocity and concentration field distribution of the mixed airflow before entering the flame hole 301 while maintaining the structural integrity of the flow equalization plate 32, thereby improving the uniformity of the flame and the combustion stability.

[0111] The present invention also proposes a burner including a burner 100. The specific structure of the burner 100 is as described in the above embodiments. Since the burner adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0112] The present invention also proposes a water heater, which includes a burner. The specific structure of the burner is as described in the above embodiments. Since the water heater adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0113] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A fire grill, characterized in that, include: The burner body has an air intake channel and a mixing chamber. The mixing chamber is provided with an air outlet. The mixing chamber is connected to the exhaust end of the air intake channel. The air intake end of the air intake channel is provided with an air inlet. as well as A flow deflector is disposed within the air intake channel. The flow deflector includes a flow deflector body and a flow guide. The flow deflector body has a through-flow deflector groove, and the flow guide is disposed corresponding to the flow deflector groove. The flow deflector groove is used to disperse and agitate the airflow flowing through the flow deflector body, and the flow guide is used to guide the airflow from the flow deflector groove toward the mixing chamber. The flow deflector body includes a first flow deflector and a second flow deflector. A first angle is formed between the first flow deflector and the second flow deflector, which expands toward the side away from the air intake. The flow deflector groove includes a first flow deflector groove disposed in the first flow deflector and / or a second flow deflector groove disposed in the second flow deflector.

2. The fire grill as described in claim 1, characterized in that, The air inlet is located on one side of the burner body along the length direction. The air inlet and the baffle are arranged opposite to each other along the length direction of the burner body. The air outlet is located on one side of the burner body along the height direction. The first baffle is inclined towards the side closer to the air outlet along the air intake direction of the air intake channel. The second baffle is inclined away from the air outlet along the air intake direction of the air intake channel.

3. The fire grill as described in claim 1, characterized in that, The first included angle is not less than 30 degrees and not more than 45 degrees.

4. The fire grill as described in claim 1, characterized in that, The turbulence-disrupting body has a constricted end and an expanded end that are arranged opposite to each other along the length direction of the burner body. The first turbulence-disrupting groove has a first edge on the side near the constricted end. The flow-guiding part includes a first flow-guiding part, which includes a first flow-guiding section and a second flow-guiding section that are bent and connected. The first flow-guiding section is inclined from the first edge toward the side away from the air outlet. The second flow-guiding section is arranged opposite to the first turbulence-disrupting groove.

5. The fire grill as described in claim 1, characterized in that, The turbulence-disrupting body has a constricted end and an expanded end that are arranged opposite to each other along the length direction of the burner body. The second turbulence-disrupting groove has a second edge on the side near the constricted end. The flow-guiding part includes a second flow-guiding part, which includes a third flow-guiding section and a fourth flow-guiding section that are bent and connected. The third flow-guiding section is inclined from the second edge toward the side near the air outlet, and the fourth flow-guiding section is arranged opposite to the second turbulence-disrupting groove.

6. The fire grill as described in claim 1, characterized in that, The first and / or the second turbulence section has a plurality of turbulence protrusions at the end away from the air inlet, and the plurality of turbulence protrusions are arranged at intervals along the width direction of the burner body.

7. A fire grill, characterized in that, include: The burner body has an air intake channel and a mixing chamber. The mixing chamber is provided with an air outlet. The mixing chamber is connected to the exhaust end of the air intake channel. The air intake end of the air intake channel is provided with an air inlet. as well as A flow disruptor is disposed within the air intake channel. The flow disruptor includes a flow disruptor body and a flow guide. The flow disruptor body has a through-flow groove, and the flow guide is disposed corresponding to the flow disruptor groove. The flow disruptor groove is used to disperse and disturb the airflow flowing through the flow disruptor body, and the flow guide is used to guide the airflow from the flow disruptor groove toward the mixing chamber. The flow disruptor body surrounds the periphery of the flow guide, and the flow disruptor groove is located between the peripheral wall of the flow disruptor body and the flow guide. In the air intake direction of the air intake channel, the peripheral wall of the flow disruptor body is constricted toward the side away from the air intake.

8. The fire briquette as described in claim 7, characterized in that, The peripheral wall of the guide section is expanded toward the side away from the air inlet.

9. The fire grill as described in claim 8, characterized in that, In the axial cross-section of the turbulence-disrupting body, a second included angle is formed between the two side edges of the turbulence-disrupting body, and the second included angle is not less than 25 degrees and not greater than 35 degrees; And / or, in the axial section of the guide portion, a third included angle is formed between the two side edges of the guide portion, the third included angle being not less than 25 degrees and not greater than 35 degrees; And / or, the flow-dispersing grooves are provided in multiple ways, and the multiple flow-dispersing grooves are arranged circumferentially along the guide portion.

10. The fire rack according to any one of claims 1 to 9, characterized in that, The air intake channel has an ejector section extending from the air inlet toward the mixing chamber. The ejector section has a tapering section and a dipping section arranged and connected along the air intake direction of the air intake channel. The turbulence element is disposed in the dipping section.

11. The fire rack according to any one of claims 1 to 9, characterized in that, The burner also includes a combustion head disposed on the burner body. The combustion head includes a flame distribution plate and a flow equalization plate. The flame distribution plate covers the gas outlet. The flow equalization plate is disposed on the side of the flame distribution plate facing the mixing chamber. The flame distribution plate has multiple flame holes, and the flow equalization plate has multiple flow equalization holes.

12. The fire briquette as described in claim 11, characterized in that, The plurality of flow equalization holes include a first flow equalization hole and a second flow equalization hole; the flow equalization plate has two first flow equalization zones opposite each other along the length direction, and a second flow equalization zone located between the two first flow equalization zones. The first flow equalization zone is provided with a plurality of first flow equalization holes, and the second flow equalization zone is provided with a plurality of second flow equalization holes. The opening area of ​​the second flow equalization hole is larger than the opening area of ​​the first flow equalization hole.

13. The fire grill as described in claim 12, characterized in that, The plurality of first flow equalization holes include a plurality of first flow equalization sub-holes and a plurality of second flow equalization sub-holes. The plurality of first flow equalization sub-holes and the plurality of second flow equalization sub-holes are alternately arranged along the length direction of the flow equalization plate. The plurality of second flow equalization sub-holes are arranged in multiple rows along the width direction of the flow equalization plate. Each row has a plurality of second flow equalization sub-holes. The opening area of ​​the first flow equalization sub-hole is larger than the opening area of ​​the second flow equalization sub-hole. And / or, a plurality of the second flow equalization holes are arranged along the length direction of the flow equalization plate.

14. The fire grill as described in claim 11, characterized in that, The combustion head also includes two side plates respectively disposed on both sides of the width direction of the flow equalization plate. Each side plate is provided with multiple flow diversion holes. A side air outlet channel is formed between the side of each side plate away from the other side plate and the burner body. The multiple side air outlet channels are connected one-to-one with the multiple flow diversion holes. The side of the side air outlet channel away from the mixing chamber is open to form a flame stabilizing port.

15. The fire rack as described in claim 14, characterized in that, The cross-sectional area of ​​the side outlet channel gradually expands from the side away from the flame stabilizer towards the flame stabilizer.

16. The fire grill as described in claim 14, characterized in that, The burner body has multiple lateral protrusions spaced along its length at the portion opposite to each of the side plates. Each lateral protrusion forms a side air outlet channel with the adjacent side plate. Each lateral protrusion includes a main body disposed opposite to the side plate and bent plates disposed on opposite sides of the main body. Each bent plate is bent relative to the main body toward the side plate.

17. The fire grill as described in claim 16, characterized in that, The bent plate and the main plate are set at an obtuse angle; And / or, the bent plate body forms a fourth included angle with the adjacent side plate, the fourth included angle being not less than 10 degrees and not greater than 15 degrees; And / or, in the direction toward the flame stabilizing port, the main body is inclined outward relative to the adjacent side plate.

18. The fire rack as described in claim 14, characterized in that, Each of the side plates has a first plate surface, and the first plate surface of each of the side plates is disposed opposite to the other side plate. The sum of the total area of ​​the multiple diversion holes of the two side plates is defined as S1, and the sum of the total area of ​​the two first plate surfaces is defined as S2. The ratio of S1 to S2 is not less than 0.2 and not greater than 0.

3.

19. The fire rack as described in claim 11, characterized in that, The flow equalization plate has a second plate surface facing the fire distribution plate. The sum of the total areas of the plurality of flow equalization holes is defined as S3, and the area of ​​the second plate surface is defined as S4. The ratio of S3 to S4 is not less than 0.25 and not greater than 0.

35.

20. A burner, characterized in that, Includes the fire rack as described in any one of claims 1 to 19.

21. A water heater, characterized in that, Includes the burner as described in claim 20.

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