Fire grate, burner and gas water heating equipment

Abstract

The invention belongs to the technical field of fuel gas equipment, and particularly discloses a fire grate, a burner and fuel gas water heating equipment. The fire grate comprises an injection part with an injection channel, the injection channel comprises a contraction channel section and a main channel section, a turbulent flow convex hull set is arranged on the inner wall face of the main channel section, the turbulent flow convex hull set comprises two turbulent flow convex hulls, and the two turbulent flow convex hulls are arranged in a staggered mode in the airflow flowing direction. And the projections of the two turbulent flow convex hulls in the airflow flowing direction are at least partially staggered. According to the invention, the retention time of fuel gas and air in the injection channel can be prolonged, so that the combustion sufficiency and the combustion stability are improved.

Description

Technical Field

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

[0002] The burner is the core component of gas water heaters, gas wall-hung boilers and other gas water heating equipment. Its combustion stability and completeness directly affect the performance of the gas water heating equipment.

[0003] Existing burners used in gas-fired water heaters typically consist of multiple burners arranged side-by-side. Each burner contains a connected ejector channel and a gas passage. A flame hole is located at the upper end of the gas passage, igniting the gas flowing through the passage and flame hole to form a flame. With the increasing demand for thinner gas-fired water heaters, the width of the burners is becoming narrower, resulting in a smaller cross-sectional area for the gas passage. This leads to an increased velocity of the gas-air mixture flowing out of the passage, and a shorter residence time of the gas within the burner. This can easily cause uneven mixing of gas and air, resulting in unstable combustion and negatively impacting the user experience of the burner and the gas-fired water heater.

[0004] Therefore, there is an urgent need for a firebox, burner, and gas-fired hot water equipment to solve the above-mentioned technical problems. Summary of the Invention

[0005] The first technical problem solved by the present invention is to provide a burner that can effectively improve the uniformity of gas-air mixing.

[0006] The second technical problem solved by the present invention is to provide a burner that can effectively improve the uniformity of gas-air mixing.

[0007] The third technical problem solved by this invention is to provide a gas-fired device that can effectively improve the performance of gas-fired water heaters.

[0008] The first technical problem mentioned above is solved by the following technical solution:

[0009] A fire vent includes an ejector section with an ejector channel, the ejector channel including a converging channel section and a main channel section connected along the airflow direction, the inner wall surface of the main channel section is provided with a turbulence protrusion group, the turbulence protrusion group including two turbulence protrusions, the two turbulence protrusions are staggered along the airflow direction, and the projections of the two turbulence protrusions along the airflow direction are at least partially staggered.

[0010] Compared with the prior art, the firebox described in this invention has the following advantages: When the nozzle supplies gas into the firebox, the gas is injected into the converging channel section through the nozzle. The gas is concentrated in the central area of ​​the converging channel section and can draw in surrounding air. The surrounding air is distributed around the gas, so that the air entering the drawing channel can flow in the axial direction of the drawing channel under the guidance and collision of the wall of the converging channel section, and mix with the gas concentrated in the central area of ​​the converging channel section, thereby improving the mixing effect of air and gas. As the gas and air continue to flow into the main channel section, the airflow flowing near the wall will collide with the turbulence protrusion located on the upstream side, and the airflow direction will be changed to a different direction, thus mixing better with the airflow located in the central area, further improving the mixing effect of air and gas. Moreover, since the two turbulence protrusions are staggered along the airflow direction and the projections of the two turbulence protrusions along the airflow direction are at least partially misaligned, more airflow will collide with the upstream turbulence protrusion and then deflect towards the downstream turbulence protrusion and collide with it, further enhancing the disturbance to the airflow. This improves the uniformity of air and gas mixing, reduces harmful substances produced during combustion, and enhances the combustion stability and reliability of the burner, which is beneficial for the thinning design of the burner.

[0011] In one embodiment, along the airflow direction, of the two turbulence bulges, the turbulence bulge located on the upstream side is the first turbulence bulge, and the turbulence bulge located on the downstream side is the second turbulence bulge, and the turbulence bulges extend circumferentially along the main channel segment.

[0012] In one embodiment, the distance between the upstream end of the second turbulence convex hull and the upstream end of the first turbulence convex hull is L1, and the length of the first turbulence convex hull along the airflow direction is L2, where 0.5≤L1:L2≤2.

[0013] In one embodiment, the minimum flow cross-sectional area of ​​the main channel segment corresponding to the first turbulence convex hull is S1, and the minimum flow cross-sectional area of ​​the main channel segment corresponding to the second turbulence convex hull is S2, where S1:S2=0.9-1.1.

[0014] In one embodiment, the maximum flow cross-sectional area of ​​the main channel segment corresponding to the first turbulence convex hump is S3, and the minimum flow cross-sectional area of ​​the main channel segment corresponding to the first turbulence convex hump is S1, where S1:S3 = 0.4-0.8.

[0015] And / or,

[0016] The maximum flow cross-sectional area of ​​the main channel segment corresponding to the second turbulence convex hull is S4, and the minimum flow cross-sectional area of ​​the main channel segment corresponding to the second turbulence convex hull is S2, where S2:S4=0.4-0.8.

[0017] In one embodiment, the fire bar includes a first fire bar piece and a second fire bar piece disposed opposite to each other along the thickness direction of the fire bar. The first fire bar piece and the second fire bar piece together form the ejector channel. A first turbulence protrusion is disposed on the first fire bar piece and extends circumferentially along the main channel segment. A second turbulence protrusion is disposed on the second fire bar piece and extends circumferentially along the main channel segment. The two ends of the first turbulence protrusion abut against the second fire bar piece along the length direction, and the two ends of the second turbulence protrusion abut against the first fire bar piece along the length direction.

[0018] In one embodiment, the turbulence bump group further includes a third turbulence bump and a fourth turbulence bump. The third turbulence bump and the fourth turbulence bump are both located downstream of the second turbulence bump. The third turbulence bump and the fourth turbulence bump are at the same height of the fire bar. The third turbulence bump and the fourth turbulence bump extend circumferentially along the main channel section, and the two ends of the third turbulence bump along the length direction and the two ends of the fourth turbulence bump along the length direction abut against each other.

[0019] In one embodiment, a plurality of turbulence bump groups are provided on the main channel section, and the plurality of turbulence bump groups are spaced apart along the height direction of the fire bar.

[0020] In one embodiment, the turbulence bulge includes a contraction portion and an expansion portion arranged sequentially along the airflow direction. The contraction portion approaches the axis of the main channel section along the airflow direction, and the expansion portion moves away from the axis of the main channel section along the airflow direction.

[0021] In one embodiment, the turbulence bulge further includes a connecting portion that connects the contraction portion and the expansion portion.

[0022] In one embodiment, the angle between the contraction portion and the axis of the main channel segment is α, where 30°≤α≤80°;

[0023] And / or,

[0024] The angle between the expansion section and the axis of the main channel section is β, where 30°≤β≤80°.

[0025] The second technical problem mentioned above is solved by the following technical solution:

[0026] A burner comprising a fire bar as described above.

[0027] Compared with the prior art, the burner described in this invention has the following advantages: by adopting the above-mentioned burner, the uniformity of mixing of gas and air in the burner can be improved, thereby improving combustion stability and reliability, enhancing the user experience of the burner, and facilitating the thinning design of the burner.

[0028] The third technical problem mentioned above is solved by the following technical solution:

[0029] A gas-fired hot water appliance includes a burner as described above.

[0030] Compared with the prior art, the burner described in this invention has the following advantages: by adopting the above-mentioned burner, the stability and reliability of the gas-fired water heater can be improved, and the performance of the gas-fired water heater can be enhanced. Attached Figure Description

[0031] Figure 1 This is a three-dimensional structural diagram of a fire briquette provided in an embodiment of the present invention;

[0032] Figure 2 for Figure 1 The main view of the firebox provided in the image;

[0033] Figure 3 For along Figure 2 Cross-sectional view along the AA direction;

[0034] Figure 4 for Figure 3 A magnified view of a section at point I;

[0035] Figure 5 This is a schematic diagram of the structure of a fire bar provided in another embodiment of the present invention;

[0036] Figure 6 for Figure 5 The side view of the firebox provided in the image;

[0037] Figure 7 This is a schematic diagram of the structure of a fire bar provided in another embodiment of the present invention;

[0038] Figure 8 for Figure 7 The side view of the firebox provided in the image.

[0039] Label Explanation:

[0040] 100. Flame rack body; 110. First flame rack plate; 120. Second flame rack plate; 200. Flame stabilizer plate; 300. Flame stabilizer channel;

[0041] 10. Ejector section; 101. Ejector channel; 20. Flow equalization section; 201. Flow equalization cavity; 30. Head; 301. Main flame channel; 40. Flame orifice plate; 401. Main flame orifice;

[0042] 1. Contraction channel segment;

[0043] 2. Main channel section; 21. Turbulence bulge; 211. Contraction section; 212. Expansion section; 213. Connecting section; 21a. First turbulence bulge; 21b. Second turbulence bulge; 21c. Third turbulence bulge; 21d. Fourth turbulence bulge;

[0044] 3. Intake section. Detailed Implementation

[0045] 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 some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0046] In the description of this invention, it should be understood that the terms "center", "upper", "lower", "vertical", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0047] The terms "first," "second," "third," and "fourth" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0048] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0049] This invention provides a burner that can be applied in a burner, which can improve the uniformity of gas and air mixing, enhance the combustion stability of the burner and the burner, and facilitate the thinning of the burner.

[0050] Example 1

[0051] like Figures 1 to 4As shown, the fire grate includes a fire grate body 100. The fire grate body 100 includes an ejector section 10, a flow equalization section 20, and a head 30 connected sequentially from bottom to top along the height direction of the fire grate. The ejector section 10 has an ejector channel 101, the head 30 has a main flame channel 301, and the flow equalization section 20 has a flow equalization cavity 201 connecting the ejector channel 101 and the main flame channel 301. The ejector channel 101 has a constriction channel section 1 and a main channel section 2 connected along the airflow direction. The flow cross-sectional area of ​​the constriction channel section 1 gradually decreases along the airflow direction. A set of turbulence protrusions is provided on the inner wall of the main channel section 2. The turbulence protrusions include two turbulence protrusions 21, which are connected along the airflow direction ( Figure 3 The direction of the dashed arrow in the middle is misaligned, and the projections of the two turbulence convex hulls 21 along the airflow direction are at least partially misaligned.

[0052] When the nozzle supplies gas into the firebox, the gas is injected into the converging channel section 1 through the nozzle. The gas is concentrated in the central area of ​​the converging channel section 1 and can draw in the surrounding air. The surrounding air is distributed around the gas, so that the air entering the ejector channel 101 can flow in the axial direction of the ejector channel 101 under the guidance and collision of the wall of the converging channel section 1, and mix with the gas concentrated in the central area of ​​the converging channel section 1, improving the mixing effect of air and gas. As the gas and air continue to flow into the main channel section 2, the airflow (mainly air) flowing near the wall will collide with the turbulence protrusion located on the upstream side, and the airflow direction will be changed to a different direction, so that it mixes better with the airflow (mainly gas) located in the central area, further improving the mixing effect of air and gas. Furthermore, since the two turbulence protrusions 21 are staggered along the airflow direction and their projections along the airflow direction are at least partially misaligned, more airflow, after colliding with the upstream turbulence protrusion 21, will deflect towards the downstream turbulence protrusion 21 and collide with it, further enhancing the disturbance to the airflow. This improves the uniformity of air-fuel mixing, reduces harmful substances produced during combustion, and enhances the combustion stability and reliability of the burner, facilitating the thinning design of the burner. In other words, the burner provided in this embodiment, through the configuration of the contraction channel section 1 and the turbulence protrusion group, allows the airflow to undergo multiple directional changes within the ejector channel 101, effectively enhancing the mixing effect of air and fuel, improving the uniformity of air-fuel mixing, thereby increasing the uniformity of mixing, reducing harmful substances produced during combustion, and enhancing the combustion stability and reliability of the burner, facilitating the thinning design of the burner.

[0053] For ease of description, along the airflow direction, the turbulence convex 21 located on the upstream side is defined as the first turbulence convex 21a, and the turbulence convex 21 located on the downstream side is defined as the second turbulence convex 21b. Specifically, both the first turbulence convex 21a and the second turbulence convex 21b extend circumferentially along the main channel segment 2 to increase the possibility that the airflow changes direction after contacting the first turbulence convex 21a and then impacts the second turbulence convex 21b, thereby further improving the turbulence effect.

[0054] In one embodiment, the burner body 100 includes a first burner plate 110 and a second burner plate 120 disposed opposite to each other along the thickness direction of the burner. The ejector channel 101 is formed by pressing the first burner plate 110 and the second burner plate 120. On this basis, a first turbulence protrusion 21a is disposed on the first burner plate 110 and a second turbulence protrusion 21b is disposed on the second burner plate 120. That is, the first turbulence protrusion 21a and the second turbulence protrusion 21b are respectively located on both sides of the main channel section 2 disposed opposite to each other along the thickness direction of the burner. Specifically, the ejector channel 101 is formed by stamping the first flame plate 110 and the second flame plate 120. The first turbulence protrusion 21a and the second turbulence protrusion 21b are formed by partial secondary pressing of the first flame plate 110 and the second flame plate 120, respectively. The two ends of the first turbulence protrusion 21a along the length direction abut against the second flame plate 120 where the second turbulence protrusion 21b is located, and the two ends of the second turbulence protrusion 21b along the length direction abut against the first flame plate 110 where the first turbulence protrusion 21a is located, so as to increase the contact area between the airflow and the first turbulence protrusion 21a and the second turbulence protrusion 21b, and further improve the turbulence effect.

[0055] refer to Figure 4 As shown, let L1 be the distance between the upstream end of the second turbulence convex 21b and the upstream end of the first turbulence convex 21a, and let L2 be the length of the first turbulence convex 21a along the airflow direction, where 0.5 ≤ L1:L2 ≤ 2. When L1:L2 is too large, the airflow velocity slows down after passing through the first turbulence convex 21a, the deflection effect weakens, and the velocity of the airflow when it hits the second turbulence convex 21b decreases, resulting in poor turbulence effect of the second turbulence convex 21b on the airflow. Conversely, when L1:L2 is too small, the airflow hitting the first turbulence convex 21a easily passes over the second turbulence convex 21b, causing the second turbulence convex 21b to lose its function of changing the airflow direction again. Specifically, L1:L2 can be, but is not limited to, 0.5, 0.6, 1, 1.5, or 2.

[0056] Understandably, the flow cross-sectional area of ​​the main channel section 2 decreases at both the first turbulence protrusion 21a and the second turbulence protrusion 21b. Let the minimum flow cross-sectional area of ​​the main channel section 2 at the first turbulence protrusion 21a be S1, and the minimum flow cross-sectional area of ​​the main channel section 2 at the second turbulence protrusion 21b be S2, where S1:S2 = 0.9-1.1. That is, the heights of the first turbulence protrusion 21a and the second turbulence protrusion 21b are similar, in order to improve the uniformity of gas distribution after the gas flows out of the ejector channel 101. Specifically, S1:S2 can be, but is not limited to, 0.9, 1, or 1.1. Preferably, S1:S2 = 1.

[0057] Meanwhile, let the maximum flow cross-section of the main channel section 2 at the first turbulence protrusion 21a be S3 (the main channel section 2 corresponds to the upstream end or the downstream end of the first turbulence protrusion 21a), and S1:S3=0.4-0.8. Under the premise that S3 is constant, when the ratio of S1 to S3 is too small, it means that S1 is too small, the first turbulence protrusion 21a fluctuates significantly, the flow resistance loss when the airflow passes through the first turbulence protrusion 21a is large, the minimum flow cross-sectional area of ​​the ejector channel 101 is too small, resulting in an increase in the ejection resistance of the ejector channel 101, thereby reducing the ejection performance of the ejector channel 101, resulting in insufficient primary air introduction, which in turn leads to a low primary air coefficient of the mixed gas, resulting in problems such as high flue gas and increased pollutants during combustion. In addition, the first turbulence protrusion 21a is difficult to press and the structure strength of the burner is low. On the other hand, if S1 is too large, the first turbulence protrusion 21a will not fluctuate significantly, thus affecting the gas mixing effect. Specifically, S1:S3 can be, but is not limited to, 0.4, 0.5, 0.6, 0.7, or 0.8.

[0058] Similarly, let the maximum flow cross-sectional area of ​​the main channel section 2 at the second turbulence protrusion 21b be S4 (the main channel section 2 corresponds to the upstream end or the downstream end of the second turbulence protrusion 21b), and S2:S4 = 0.4-0.8. Given a fixed S4, if the ratio of S2:S4 is too small, it indicates that S2 is too small, the second turbulence protrusion 21b fluctuates significantly, the flow resistance loss when the airflow passes through the second turbulence protrusion 21b is large, the minimum flow cross-sectional area of ​​the ejector channel 101 is too small, resulting in increased ejection resistance of the ejector channel 101, thus reducing the ejection performance of the ejector channel 101. This leads to insufficient primary air intake, resulting in a low primary air coefficient in the mixed gas, which in turn causes problems such as high flue gas volume and increased pollutants during combustion. Furthermore, the second turbulence protrusion 21b is difficult to mold, and the burner structure has low strength. Conversely, if S2 is too large, the less pronounced fluctuations of the second turbulence protrusion 21b will affect the gas mixing effect. Specifically, S2:S4 can be, but is not limited to, 0.4, 0.5, 0.6, 0.7, or 0.8.

[0059] In one embodiment, the main channel section 2 expands along the airflow direction, thereby decelerating and diffuses the mixed airflow flowing out of the contraction channel section 1, reducing kinetic energy loss.

[0060] It is worth noting that the expansion of the main channel section 2 along the airflow direction specifically means: when the channel wall of the main channel section 2 is a smooth channel wall, the flow cross-sectional area of ​​the main channel section 2 gradually increases along the airflow direction; when the channel wall of the expansion channel section is provided with turbulence structures such as grooves and protrusions, the flow cross-sectional area of ​​the part of the main channel section 2 without turbulence structures gradually increases along the airflow direction. That is, the main body of the main channel section 2 without the first turbulence protrusion 21a and the second turbulence protrusion 21b gradually increases in cross-sectional area along the airflow direction.

[0061] Specifically, such as Figure 2 As shown, along the airflow direction, without considering the first turbulence convex 21a and the second turbulence convex 21b of abrupt changes, the size of the main channel section 2 gradually increases along the width direction of the fire bar, while the size along the thickness direction of the fire bar remains unchanged, so as to reduce the processing difficulty of the main channel section 2.

[0062] In one embodiment, the turbulence protrusion 21 includes a contraction portion 211 and an expansion portion 212 arranged sequentially along the airflow direction. The contraction portion 211 moves closer to the axis of the main channel section 2 along the airflow direction, while the expansion portion 212 moves further away from the axis of the main channel section 2 along the airflow direction. The cross-sectional area of ​​the portion of the main channel section 2 corresponding to the turbulence protrusion 21 first decreases and then increases along the airflow direction. During the process of decreasing the cross-sectional area, the airflow velocity increases, thereby enhancing the side impact between airflows and increasing the mixing effect of the airflow. As the cross-sectional area of ​​the main channel section 2 increases, part of the static pressure becomes dynamic pressure, the airflow forms vortices, and the airflow (mainly air) is disturbed again, further mixing the fuel gas and air, effectively improving the mixing fullness of the fuel gas and air.

[0063] In another embodiment, the turbulence protrusion 21 further includes a connecting portion 213, which connects the contraction portion 211 and the expansion portion 212. By providing the connecting portion 213, the overall size of the turbulence protrusion 21 along the height direction of the flame bar can be increased, thereby reducing the demolding difficulty of the turbulence protrusion 21 during molding and reducing the processing difficulty of the flame bar. Specifically, the connecting portion 213 can be parallel to the axis of the main channel section 2.

[0064] In one embodiment, the contraction section 211 is inclined relative to the axis of the main channel section 2, and the angle between the contraction section 211 and the axis of the main channel section 2 is α, where α ≥ 30°. Generally speaking, the larger α is, the faster the cross-section of the main channel section 2 changes, that is, the greater the rate of change of the flow cross-sectional area, the better the disturbance effect on the airflow, and the better the mixing effect of the gas and air. Therefore, setting α to be greater than 30° can more effectively ensure the disturbance effect on the airflow, thereby improving the mixing effect.

[0065] Furthermore, α ≤ 80° can avoid the problem that if α is too large, the contraction section 211 will be nearly perpendicular to the axis of the main channel section 2, which would lead to a significant increase in the backward flow resistance of the airflow. It also avoids the problem that if α is too large, the length of the contraction section 211 will be too small, which would increase the processing difficulty of the contraction section 211. Specifically, α is not limited to 30°, 40°, 45°, 60°, or 80°.

[0066] In one embodiment, the expansion section 212 is inclined relative to the axis of the main channel section 2, and the angle between the expansion section 212 and the axis of the main channel section 2 is β, where β ≥ 30°. Generally speaking, the larger β is, the faster the cross-section of the main channel section 2 changes, that is, the greater the rate of change of the flow cross-sectional area, the better the disturbance effect on the airflow, and the better the mixing effect of the gas and air. Therefore, setting β to be greater than 30° can more effectively ensure the airflow disturbance effect. At the same time, compared with a larger β, the length of the expansion section 212 can be shortened, so that the pressure of the mixed airflow can be quickly restored, avoiding the problem of insufficient ejection capacity of the ejector channel 101 due to the excessive length of the expansion section 212.

[0067] Furthermore, β ≤ 80° to avoid β being too large, causing the expansion portion 212 to be nearly perpendicular to the axis of the main channel segment 2, thereby avoiding the problem that a large β would result in a small length of the expansion portion 212, which would increase the processing difficulty of the expansion portion 212. Specifically, β is not limited to 30°, 40°, 45°, 60°, or 80°.

[0068] In one embodiment, the ejector channel 101 further includes an air intake section 3 connected to the upstream end of the contraction channel section 1. The flow cross-sectional area of ​​the air intake section 3 is equal everywhere along the airflow direction and is equal to the maximum flow cross-sectional area of ​​the contraction channel section 1. By providing the air intake section 3, it is beneficial to achieve the cooperation between the burner and the external structure.

[0069] It is worth noting that the specific parameter settings for the intake section 3 and the contraction channel section 1 can be set with reference to existing technologies. This is not the focus of this invention, and this invention will not limit or elaborate on it.

[0070] In one embodiment, the ejector channel 101 is vertically arranged, that is, the airflow direction is vertically upward. The lower end of the ejector channel 101 forms the air inlet of the ejector channel 101, and the upper end of the ejector channel 101 forms the air outlet of the ejector channel 101. The burner is a T-shaped burner. There may be only one ejector channel 101, or there may be two or more ejector channels spaced apart along the width of the burner.

[0071] In another embodiment, the ejector channel 101 is L-shaped, meaning that the air inlet of the ejector channel 101 faces one side of the burner along the width direction, and the burner is a C-shaped burner. There may be only one ejector channel 101, or two may be spaced apart along the width direction of the burner, with the air inlets of the two ejector channels 101 facing each other and spaced apart.

[0072] like Figure 1 and Figure 3 As shown, in one embodiment, the fire rack also includes a flame stabilizing plate 200. Flame stabilizing plates 200 are provided on both sides of the head 30 along the thickness direction of the fire rack. Each flame stabilizing plate 200 and the fire rack body 100 form a flame stabilizing channel 300. Ventilation holes are provided on both sides of the head 30. The ventilation holes connect the main flame channel 301 and the flame stabilizing channel 300.

[0073] A vent is provided to connect the flame stabilizing channel 300 and the main flame channel 301, allowing some of the gas in the main flame channel 301 to flow through the vent to the flame stabilizing channel 300. This forms a stable flame at the upper end of the flame stabilizing channel 300, thereby reducing the gas flow velocity at the main burner hole 401. This avoids the situation where the gas flow velocity is too high due to the thinning of the water heater while maintaining the same gas flow rate, which would affect combustion stability. At the same time, the gas in the flame stabilizing channel 300 is diverted away from the main flame channel 301, so the gas flow velocity in the flame stabilizing channel 300 is lower than that in the main flame channel 301. This allows the stable flame at the upper end of the flame stabilizing channel 300 to effectively stabilize the main flame at the main burner hole 401, further improving combustion stability.

[0074] It is worth noting that other structures of the fire duct can be set with reference to existing technology, which is not the focus of this invention and will not be described in detail in this embodiment.

[0075] This embodiment also provides a burner including multiple burners arranged side-by-side as described above, with the multiple burners arranged side-by-side along the thickness direction of the burners. The burner provided in this embodiment, by employing the aforementioned burners, can improve the uniformity of mixing of fuel gas and air within the burners, thereby improving combustion stability and reliability, and enhancing the user experience of the burners.

[0076] This embodiment also provides a gas-fired water heater, including the burner described above. By employing the burner described above, the gas-fired water heater provided in this embodiment can improve the stability and reliability of its operation, thereby enhancing its performance.

[0077] Example 2

[0078] This embodiment provides a fire rack. The fire rack provided in this embodiment has the same basic structure as the fire rack provided in the above embodiment, except that the number of turbulence bump groups is different. Multiple turbulence bump groups are provided on the main channel section 2. The turbulence bump groups are spaced apart along the height direction of the fire rack. Each turbulence bump group includes a first turbulence bump 21a and a second turbulence bump 21b.

[0079] For example, two turbulence convex hull groups are set on the main channel segment 2, such as... Figure 5 and Figure 6 As shown, two turbulence convex assemblies are provided on the main channel section 2. The two first turbulence convex convex assemblies 21a of the two turbulence convex assemblies are spaced apart on the first flame plate 110 along the airflow direction, and the two second turbulence convex convex assemblies 21b of the two turbulence convex assemblies are spaced apart on the second flame plate 120 along the airflow direction. The arrangement of the first turbulence convex convex 21a and the second turbulence convex convex 21b can continuously change the flow cross-sectional area of ​​the main channel section 2. The gas continuously impacts the wall surface, and the flow direction and pressure are continuously changed, enhancing the turbulence and making the gas and air mix more fully.

[0080] Example 3

[0081] like Figure 7 and Figure 8 As shown, this embodiment provides a fire grid. The fire grid provided in this example has the same basic structure as the fire grid provided in Embodiment 1. The only difference is that there are four turbulence protrusions 21 in the turbulence protrusion group. In addition to the first turbulence protrusion 21a and the second turbulence protrusion 21b, there are also a third turbulence protrusion 21c and a fourth turbulence protrusion 21d. The third turbulence protrusion 21c and the fourth turbulence protrusion 21d are both located downstream of the second turbulence protrusion 21b. The third turbulence protrusion 21c and the fourth turbulence protrusion 21d are at the same height of the fire grid. The third turbulence protrusion 21c and the fourth turbulence protrusion 21d both extend circumferentially along the main channel section 2. The two ends of the third turbulence protrusion 21c along the length direction and the two ends of the fourth turbulence protrusion 21d along the length direction abut against each other.

[0082] The third turbulence protrusion 21c can change the gas flow direction again and improve the mixing effect. Since the third turbulence protrusion 21c and the fourth turbulence protrusion 21d are at the same height of the burner, and the head and tail of the third turbulence protrusion 21c and the fourth turbulence protrusion 21d abut each other, the air surrounding the gas can come into contact with the third turbulence protrusion 21c and the fourth turbulence protrusion 21d, thereby changing its direction and mixing with the gas again, and then flowing to the main burner hole 401, resulting in a more uniform gas distribution.

[0083] Specifically, both the third turbulence convex 21c and the fourth turbulence convex 21d are formed by the partial contraction of the channel wall of the main channel segment 2. It is worth noting that the third turbulence convex 21c may also include a contraction portion 211, a connecting portion 213, and an expansion portion 212, which will not be described in detail here.

[0084] In the specific embodiments described above, the technical features can be combined in any non-contradictory way. For the sake of brevity, not all possible combinations of the technical features are described. However, as long as the combinations of these technical features are not contradictory, they should be considered within the scope of this specification. The specific embodiments described above only illustrate several implementations of the present invention, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the present invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this patent should be determined by the appended claims.

Claims

1. A fire briquette, comprising an ejector section (10) having an ejector channel (101), said ejector channel (101) comprising a converging channel section (1) and a main channel section (2) connected along the airflow direction, characterized in that, The inner wall of the main channel section (2) is provided with a turbulence convex group, which includes two turbulence convex ...

2. The fire grill according to claim 1, characterized in that, Along the airflow direction, of the two turbulence convex humps (21), the turbulence convex hump (21) located on the upstream side is the first turbulence convex hump (21a), and the turbulence convex hump (21) located on the downstream side is the second turbulence convex hump (21b). Both the first turbulence convex hump (21a) and the second turbulence convex hump (21b) extend circumferentially along the main channel segment (2).

3. The fire grill according to claim 2, characterized in that, The distance between the upstream end of the second turbulence convex hull (21b) and the upstream end of the first turbulence convex hull (21a) is L1, and the length of the first turbulence convex hull (21a) along the airflow direction is L2, 0.5≤L1:L2≤2.

4. The fire grill according to claim 2, characterized in that, The minimum flow cross-sectional area of ​​the main channel segment (2) at the location of the first turbulence convex hull (21a) is S1, and the minimum flow cross-sectional area of ​​the main channel segment (2) at the location of the second turbulence convex hull (21b) is S2, where S1:S2=0.9-1.

1.

5. The fire grill according to claim 2, characterized in that, The maximum flow cross-sectional area of ​​the main channel section (2) at the first turbulence protrusion (21a) is S3, and the minimum flow cross-sectional area of ​​the main channel section (2) at the location of the first turbulence protrusion (21a) is S1, where S1:S3=0.4-0.8; And / or, The maximum flow cross-sectional area of ​​the main channel section (2) at the location where the second turbulence convex hull (21b) is set is S4, and the minimum flow cross-sectional area of ​​the main channel section (2) at the location where the second turbulence convex hull (21b) is set is S2, where S2:S4=0.4-0.

8.

6. The fire grill according to claim 2, characterized in that, The fire bar includes a first fire bar piece (110) and a second fire bar piece (120) arranged opposite to each other along the thickness direction of the fire bar. The first fire bar piece (110) and the second fire bar piece (120) together form the ejector channel (101). The first turbulence protrusion (21a) is disposed on the first fire bar piece (110), and the second turbulence protrusion (21b) is disposed on the second fire bar piece (120). The two ends of the first turbulence protrusion (21a) in the length direction abut against the second fire bar piece (120), and the two ends of the second turbulence protrusion (21b) in the length direction abut against the first fire bar piece (110).

7. The fire grill according to claim 2, characterized in that, The turbulence convex ...

8. The fire grill according to claim 2, characterized in that, Multiple turbulence convex hulls are provided on the main channel section (2), and the multiple turbulence convex hulls are spaced apart along the airflow direction.

9. The fire rack according to any one of claims 1-5, characterized in that, The turbulence bulge (21) includes a contraction portion (211) and an expansion portion (212) arranged sequentially along the airflow direction. The contraction portion (211) approaches the axis of the main channel section (2) along the airflow direction, and the expansion portion (212) moves away from the axis of the main channel section (2) along the airflow direction.

10. The fire grill according to claim 9, characterized in that, The turbulence bulge (21) also includes a connecting part (213) that connects the contraction part (211) and the expansion part (212).

11. The fire grill according to claim 9, characterized in that, The angle between the axis of the contraction section (211) and the axis of the main channel section (2) is α, where 30°≤α≤80°; And / or, The angle between the expansion section (212) and the axis of the main channel section (2) is β, where 30°≤β≤80°.

12. A burner, characterized in that, Including the fire rack as described in any one of claims 1-11.

13. A gas-fired hot water device, characterized in that, Includes the burner as described in claim 12.

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