A top-inlet burner

Abstract

An upward-intake burner includes a base (3) having an upward-opening mixing chamber (32); a first flame cap (1) covering the mixing chamber (32), with flame outlet holes (110) spaced apart to connect the mixing chamber (32) to the external environment; an ejector tube (4) horizontally placed at the bottom of the base (3), its air inlet end located in the external environment and correspondingly fitted with a nozzle, and its air outlet end connected to the mixing chamber (32); the flame outlet hole (110) has a flame heat intensity of 4 to 5.5 kW / mm². 2 Compared with existing technologies, this invention can ensure the replenishment of secondary air and improve combustion efficiency.

Description

Technical Field

[0001] This invention belongs to the field of household stove technology, specifically relating to an upward-intake burner. Background Technology

[0002] To avoid nozzle clogging caused by overflow, the top-inlet burner adopts a nozzle-top design. The ejector tube is placed horizontally at the bottom of the burner, and its length is limited by the outer diameter of the burner, making it shorter than the length of a conventional ejector tube. Therefore, the ejector performance of the ejector structure is weaker than that of a conventional bottom-inlet structure.

[0003] To compensate for the insufficient primary air in the top-intake burner, the applicant adopted a multi-hole sheet metal structure on the top wall of the outer ring burner, as shown in the invention patent application "A Fully Top-Intake Burner" (application publication number CN112240548A) with application number 201910647362.2. The flame holes formed by its thin sheet metal structure have the advantage of low air outlet resistance. In addition, the multi-hole burner has the advantages of small individual flame hole diameter and large total flame area, thus alleviating the problem of insufficient primary air in the top-intake burner.

[0004] However, existing burner caps, especially for high-load top-intake burners, still suffer from insufficient secondary air supply and excessively fast combustion speed due to the thin top wall of the burner cap, resulting in flame lift-off and backfire.

[0005] In addition, the heat intensity of the flame holes in the flame cap refers to 1 mm. 2 The heat released by the flame hole per unit time, i.e., the flame hole thermal intensity = heat load / total flame area, is expressed in kW / mm². 2 According to Chapter 7, Section 2, "Atmospheric Burners," in the book "Gas Combustion and Application (Fourth Edition)" compiled by Tongji University, the standard burner hole heat intensity of existing burner caps is: 5.8–8.7 kW / mm² for natural gas. 2 ; Liquefied petroleum gas 7~9.3kW / mm 2 In burner design, the heat load is first determined, and then the total flame area of ​​the flame holes is calculated based on the recommended flame hole heat intensity.

[0006] The above-mentioned standard burner hole heat intensity is applicable to bottom-inlet burners. If used in top-inlet burners, due to the short primary air injection path, combustion mainly relies on secondary air replenishment around the burner hole. When using the existing standard burner hole heat intensity, the following technical problems exist: the flame outlet area of ​​the burner hole is relatively small, resulting in a small outer surface area of ​​the burner hole, which limits the replenishment of secondary air around the burner hole. This leads to insufficient air, incomplete combustion, and low combustion efficiency, which is especially serious in high-load, high-efficiency top-inlet burners. Summary of the Invention

[0007] The first technical problem to be solved by the present invention is to provide an upward-intake burner that can improve combustion efficiency, in light of the current state of the prior art.

[0008] The second technical problem to be solved by the present invention is to provide an upper air intake burner to reduce the risk of flame detachment and backfire.

[0009] The technical solution adopted by the present invention to solve the first technical problem mentioned above is: an upper air intake burner, comprising:

[0010] The base has an upward-facing mixing chamber;

[0011] The first flame cap is placed on the gas mixing chamber, and flame holes are distributed at intervals on the first flame cap to connect the gas mixing chamber with the external environment.

[0012] An ejector tube is placed horizontally at the bottom of the base, with its air inlet located in the external environment and correspondingly fitted with a nozzle, and its air outlet connected to the mixing chamber.

[0013] Its features are:

[0014] The heat intensity of the flame outlet is 4–5.5 kW / mm². 2 .

[0015] Thus, by designing the heat intensity of the flame hole to be 4–5.5 kW / mm² 2 The heat intensity of the flame holes is lower than that of existing flame caps, thereby increasing the total flame area of ​​the flame holes. The large flame area of ​​the flame holes is conducive to the replenishment of secondary air, making up for the problem of insufficient primary air in the top-intake burner, so that the top-intake burner of the present invention can burn more completely and improve combustion efficiency.

[0016] Meanwhile, due to the limited area of ​​the burner cap on household gas stoves, if the heat intensity of the burner holes is less than 4kW / mm², 2 If the flame area is too large, the outer surface area of ​​the flame holes will be too large, resulting in an overly dense arrangement of flame holes on the burner cap. Since the space between adjacent flame holes on the burner cap is used for secondary air circulation, if the flame holes are too densely arranged, the distance between adjacent flame holes will be too small, failing to form a smooth supplementary channel for secondary air circulation. This makes it difficult for the flame holes, especially the inner flame holes, to receive sufficient secondary air, thus reducing combustion efficiency. Conversely, if the burner cap area is enlarged, the flame holes will be too sparse, resulting in greater heat loss, decreased thermal efficiency, and poor overall flame stability, making backfire more likely.

[0017] If the flame hole strength is greater than 5.5 kW / mm 2 If the flame area is small and the outer surface area of ​​the flame hole is small, it will be difficult to provide enough secondary air during combustion, resulting in incomplete combustion.

[0018] The first flame cap can be circular or annular in shape to match the opening shape of the gas mixing chamber. Preferably, the first flame cap is annular in shape to match the opening shape of the gas mixing chamber and has an annular top wall with flame outlet holes spaced circumferentially. Alternatively, the flame outlet holes can also be located on the side peripheral wall of the flame cap.

[0019] When the heat intensity of the burner orifice is low and the ejector capability is weak, the exhaust resistance of the burner cap needs to be reduced to ensure smooth gas output. Therefore, the burner cap needs to be designed as a thin plate structure with low exhaust resistance. The thinner the burner cap and the shallower the burner orifice, the faster the combustion speed. When the combustion speed exceeds the exhaust speed, backfire is likely to occur. To solve the backfire problem, the thin plate burner cap needs to ensure that the exhaust resistance matches the ejector performance. The principle is that when the heat load is constant, when the heat intensity of the burner orifice increases, i.e., the exhaust area decreases, the gas pressure inside the burner increases. Therefore, the gas flow rate per unit burner orifice area per unit time increases. Since the ejector capability of the top-intake burner is weak, the air required for combustion cannot match the increased gas flow rate. Therefore, the increased heat intensity of the burner orifice will slow down the combustion speed, thereby matching the combustion speed and exhaust speed and reducing the occurrence of backfire. However, excessive heat intensity in the burner holes increases the resistance to gas exhaust, hindering primary air intake. Therefore, to further address the second technical problem, the ratio of the thickness of the annular top wall to the heat intensity of the burner holes is preferably 0.15–0.62. This ensures primary and secondary air intake while reducing the risk of backfire. When the ratio is less than 0.15, the thickness of the annular top wall is too thin, making backfire likely even with increased burner hole heat intensity. When the ratio is greater than 0.62, the thickness is too thick, resulting in excessive exhaust resistance, making it difficult to ensure smooth gas exhaust from the burner holes and achieve stable combustion.

[0020] Preferably, the flaming holes are distributed circumferentially to form a group of flaming zones, with at least two groups, and are distributed radially at intervals along the annular top wall.

[0021] The secondary air located inside the outer ring flame cap needs to simultaneously replenish the oxygen required by both the inner and outer ring flame caps. To further ensure the replenishment of secondary air to the flame outlets located on the inner side of the outer ring flame cap, within the interval defined by two circumferentially arranged and radially extended radial lines on the annular top wall, two radially adjacent flame outlet areas are denoted as the first flame outlet area and the second flame outlet area, with the second flame outlet area located outside the first flame outlet area.

[0022] And within this interval, the sum of the flame areas of each flame hole in the first flame area is V1, and the sum of the flame areas of each flame hole in the second flame area is V2.

[0023] And let the inner arc line of each fire hole in the first fire zone be the first baseline, the outer arc line of each fire hole in the second fire zone be the second baseline, and the arc line located at the center of the first baseline and the second baseline be the third baseline. Let the area of ​​the interval enclosed by the first baseline, the third baseline and the two radial lines be S1, and the area of ​​the interval enclosed by the third baseline, the second baseline and the two radial lines be S2, satisfying: (V1 / S1):(V2 / S2)≤1.1;

[0024] Furthermore, the centers of the circles corresponding to the first baseline, the second baseline, and the third baseline coincide with the center of the circle corresponding to the annular top wall.

[0025] This ensures secondary air supply to the inner flame outlet on the outer ring burner, thereby reducing the amount of smoke generated during combustion and improving combustion efficiency.

[0026] To further ensure the supply of secondary air to the inner flame outlets on the outer ring flame cap, preferably, there are at least three sets of flame outlet areas, radially spaced along the annular top wall, with the radial distance between adjacent sets of flame outlet areas gradually decreasing from the inside to the outside. This increases the distance between adjacent inner sets of flame outlet areas, allowing for more thorough contact between the secondary air and the flame in the flame outlets.

[0027] Preferably, the flame outlets are arranged radially staggered. This allows for more efficient use of secondary air and enables the arrangement of more flame outlets.

[0028] Furthermore, the flame area of ​​a single flame outlet in the outermost flame outlet region is smaller than or equal to the flame area of ​​a single flame outlet in other flame outlet regions. Flame outlets in the outermost flame outlet regions on the outer ring burner cap are prone to cold-face flame lift-off (Note: cold-face flame lift-off refers to the lower temperature and shallower flame outlet depth at the outermost flame outlet, thus making flame lift-off more likely). This invention improves flame stabilization performance and combustion efficiency by using flame outlets with smaller flame areas.

[0029] Preferably, the innermost flame zone is positioned adjacent to the inner edge of the annular top wall. This allows secondary air located in the inner ring of the outer flame cap to directly replenish the flame root.

[0030] In the above scheme, preferably, the annular top wall slopes downwards from the inside to the outside. The sloped annular top wall has the following technical effects: First, with a fixed burner cap diameter, the sloped annular top wall can accommodate more flame outlets compared to a planar annular top wall, ensuring a sufficiently large flame outlet area; Second, the outer edge of the annular top wall is at a lower height, reducing the overall height of the burner; Third, as heated air flows upwards, the sloped annular top wall facilitates the flow of secondary air from the outside to the inside, making the replenishment of secondary air at the flame outlets on the inner ring of the outer burner cap and the flame outlets on the inner burner cap smoother, resulting in higher combustion efficiency.

[0031] Preferably, the number of flame outlets is 400 to 800. A densely arranged array of flame outlets enables self-stabilizing flames and ensures uniform heating.

[0032] Each flame outlet is circular with an inner diameter of 1–1.6 mm. This flame outlet size design enables self-stabilizing flames and increases the number of flame outlets, improving the heating area and heating uniformity. It also ensures firepower while providing easy cleaning.

[0033] To increase the contact area between the flame and the secondary air, preferably, the axis of the flame outlet is perpendicular to the annular top wall.

[0034] Furthermore, the angle between the axis of the fire outlet and the horizontal plane is 45° to 70°.

[0035] Preferably, the flame outlet is located radially on the inner side of the annular top wall, while the outer side of the annular top wall forms a flame-free zone without flame outlets. When secondary air flows through the flame-free zone to the flame zone, it receives better airflow guidance and preheating.

[0036] In the above solutions, to further ensure secondary air supply, preferably, the spacing of the flame outlet holes meets the following requirements:

[0037] At least two adjacent flare holes have a spacing greater than or equal to the diameter of the single flare hole that forms that spacing.

[0038] Furthermore, the ratio of the number of flare holes that meet the above requirements to the total number of flare holes is ≥90%.

[0039] Preferably, the base further has an inner annular mixing chamber with an upward-facing opening, located within the inner periphery of the mixing chamber;

[0040] The upper air intake burner also has an inner ring flame cap located inside the first flame cap. The inner ring flame cap has a vertically extending peripheral wall opposite to the first flame cap and is provided with inner ring main flame holes at intervals along the circumference. The diameter of the inner ring main flame holes is greater than or equal to 1.8 mm, and the upper limit of the diameter value of the inner ring main flame holes is 3 mm.

[0041] Preferably, the first flame cap further has an inner annular wall extending downward from the inner edge of the annular top wall. At least the upper part of the inner annular wall slopes inward from top to bottom to form a guide wall, and the upper edge of the guide wall engages with the inner edge of the annular top wall. The guide wall can guide the secondary air located in the inner ring of the outer annular flame cap, allowing the secondary air to flow more smoothly to the flame outlet; at the same time, it can prevent the flame at the inner ring main flame outlet from burning the guide wall.

[0042] To further prevent the flame at the inner ring main flame hole from burning the guide wall, preferably, the lower edge of the inner ring main flame hole is at a higher height than the lower edge of the guide wall.

[0043] The angle between the axis of the inner ring main flame hole and the horizontal plane is greater than the angle between the guide wall and the horizontal plane. This further prevents the flame at the inner ring main flame hole from burning the guide wall.

[0044] In the above scheme, preferably, the upper air intake burner is used in a stove.

[0045] Compared with the prior art, the advantages of the present invention are: by designing the heat intensity of the flame hole to be 4-5.5 kW / mm 2 The heat intensity of the flame holes is lower than that of existing flame caps, thereby increasing the total flame area of ​​the flame holes. The large flame area of ​​the flame holes is conducive to the replenishment of secondary air, making up for the problem of insufficient primary air in the top-intake burner, so that the top-intake burner of the present invention can burn more completely and improve combustion efficiency. Attached Figure Description

[0046] Figure 1 This is a schematic diagram of the burner structure in an embodiment of the present invention;

[0047] Figure 2 This is a cross-sectional view of the burner in an embodiment of the present invention;

[0048] Figure 3 This is a top view of the outer ring fire cover in an embodiment of the present invention;

[0049] Figure 4 This is a cross-sectional view of the outer ring fire cover in an embodiment of the present invention;

[0050] Figure 5 This is a partial structural diagram of the outer ring flame cap in an embodiment of the present invention. Detailed Implementation

[0051] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0052] like Figures 1-5 As shown, this is a preferred embodiment of an upward-intake burner of the present invention. The burner is for use in stoves and includes a base 3, an outer ring burner cap, an inner ring burner cap 2, and an injector tube 4.

[0053] The base 3 is a prior art technology, having an inner ring mixing chamber 31 with its opening facing upwards and a mixing cavity 32 located circumferentially around the inner ring mixing chamber 31.

[0054] There are at least two ejector tubes 4, which are placed horizontally at the bottom of the base 3. The air inlet of the first ejector tube is located in the external environment and is equipped with a nozzle accordingly. The air outlet of the first ejector tube is connected to the mixing chamber 32. The air inlet of the second ejector tube is located in the external environment and is equipped with a nozzle accordingly. The air outlet of the second ejector tube is connected to the inner ring mixing chamber 31.

[0055] The inner ring burner cap 2 is installed on the inner ring mixing chamber 31 and has a vertically extending peripheral wall 21. The peripheral wall 21 is provided with inner ring main burner holes 210 at intervals along the circumference. The diameter of a single inner ring main burner hole 210 is 1.8 to 3 mm (the diameter of a single inner ring main burner hole 210 can be any value of 1.8 to 3 mm, such as 1.8 mm, 2 mm or 3 mm).

[0056] The outer ring flame cap, which is the first flame cap 1 of the present invention, is mounted on the gas mixing chamber 32. It has an annular top wall 11, an inner annular wall 12 extending downward from the inner edge of the annular top wall 11, and an outer annular wall 13 extending downward from the outer edge of the annular top wall 11. An annular gas mixing chamber 10 with a downward opening is formed between the annular top wall 11, the inner annular wall 12, and the outer annular wall 13. In this embodiment, the annular top wall 11 of the outer ring flame cap is inclined downward from the inside to the outside, and the angle between the annular top wall 11 and the horizontal plane is 20 to 45° (the angle can be any value between 20 and 45°, such as 20°, 30°, or 45°).

[0057] The inner ring wall 12 of the outer ring burner is located outside the peripheral wall 21 of the inner ring burner 2 and is spaced apart from the peripheral wall 21. The upper part of the inner ring wall 12 slopes inward from top to bottom to form a guide wall 121, and the angle between the guide wall 121 and the horizontal plane is smaller than the angle between the axis of the inner ring main burner hole 210 and the horizontal plane. Simultaneously, the upper edge of the guide wall 121 engages with the inner edge of the annular top wall 11. The lower edge of the guide wall 121 is at a lower height than the lower edge of the inner ring main burner hole 210. This prevents the flame at the inner ring main burner hole 210 from burning the guide wall 121.

[0058] Meanwhile, the inner radial side of the annular top wall 11 is provided with flame outlets 110 that are circumferentially spaced and connected to the annular mixing chamber 10, forming a flame zone. The axis of each flame outlet 110 in the flame zone is perpendicular to the annular top wall 11. The outer side of the annular top wall 11 forms a ring of flameless zones without flame outlets. During use, the entire flame cap is at a high temperature, and the temperature of the outer flameless zone is very high. When secondary air flows from the flameless zone to the flame zone, it can be well guided and preheated. If the size of the no-flame zone is too large, too much gas will remain below the outer ring of the burner cap when the flame is turned off, resulting in a popping sound during flameout. Furthermore, if the no-flame zone is too large, the temperature of the outermost area of ​​the burner cap will be relatively low, leading to poor combustion stability and making the flame outlets on the outer ring prone to flame lift-off. If the no-flame zone is too small, the secondary air cannot be properly preheated. Therefore, to solve these technical problems, the radial width of the no-flame zone projected onto the horizontal plane is 12% to 62% of the radial width of the annular top wall 11 projected onto the horizontal plane (the width percentage of the no-flame zone can be any value from 12% to 62%, such as 12%, 20%, 40%, 50%, or 62%). This achieves two goals: First, it avoids excessive gas retention below the no-flame zone due to its large size, which could cause a popping sound during flameout. Second, it prevents... First, it allows secondary air to flow radially along the non-flame zone during replenishment, resulting in better airflow guidance and preheating. If the non-flame zone is too small, it cannot achieve good preheating and airflow guidance during secondary air replenishment. Second, for top-inlet burners, the outlet end of the injector generally extends horizontally into the mixing chamber below the outer ring burner cap. To ensure uniform mixing, the outlet end of the injector is not opposite to the flame outlet, so that the fuel gas output from the injector can be uniformly mixed with the air in the mixing chamber. The non-flame zone design in this invention provides space for the mixing of fuel gas and air, thereby improving the uniformity of mixing. Furthermore, the size design of the non-flame zone allows for an increase in the length of the portion of the injector extending into the mixing chamber (i.e., the non-flame zone can block the top of the injector), thereby extending the overall length of the injector. Third, it ensures a high overall temperature of the burner cap and prevents flame lift-off.

[0059] In this embodiment, the number of flame outlet holes 110 is 400 to 800; each flame outlet hole 110 is circular with an inner diameter of 1 to 1.6 mm. Furthermore, the heat intensity of the flame outlet holes on the outer ring flame cap is 4 to 5.5 kW / mm². 2 The ratio of the wall thickness of the annular top wall 11 to the thermal intensity of the flame holes is 0.15 to 0.62. In this embodiment, the number of flame holes 110 can be any value from 400 to 800, such as 400, 500, 700, or 800; the inner diameter of a single flame hole 110 can be any value from 1 to 1.6 mm, such as 1 mm, 1.2 mm, 1.5 mm, or 1.6 mm; and the thermal intensity of the flame holes can be 4 to 5.5 kW / mm². 2Any value, such as the heat intensity of the fire hole, can be 4kW / mm. 2 5kW / mm 2 Or 5.5kW / mm 2 The ratio of the wall thickness of the annular top wall 11 to the thermal intensity of the fire hole can be any value from 0.15 to 0.62, such as 0.15, 0.3, 0.5 or 0.62.

[0060] Specifically, 4 to 7 groups of flame outlets 110 are arranged at intervals along the circumferential direction, forming a flame outlet region. These groups are radially spaced along the annular top wall 11, with the radial distance between adjacent groups gradually decreasing from the inside to the outside. This increases the distance between adjacent groups of flame outlets on the inner side, allowing for more thorough contact between the secondary air and the flame from the flame outlets. Furthermore, the flame outlets 110 are radially staggered. The flame outlet area of ​​a single flame outlet 110 in the outermost flame outlet region is smaller than or equal to the flame outlet area of ​​a single flame outlet 110 in other flame outlet regions. The innermost flame outlet region is located adjacent to the inner edge of the annular top wall 11.

[0061] Meanwhile, the spacing of the flaming holes 110 in each group of flaming areas meets the following requirements: the interval between adjacent (either circumferential or radial) flaming holes 110 is greater than or equal to the aperture of a single flaming hole 110 in the two adjacent flaming holes 110 that form the interval; and the ratio of the number of flaming holes 110 that meet the above requirements to the total number of flaming holes 110 is ≥90%.

[0062] Furthermore, within the interval defined by two circumferentially arranged and radially extended radial lines on the annular top wall 11, two radially adjacent sets of fire-emitting areas are denoted as the first fire-emitting area 11a and the second fire-emitting area 11b, with the second fire-emitting area 11b located outside the first fire-emitting area 11a; and within this interval, the sum of the fire-emitting areas of each fire-emitting hole 110 in the first fire-emitting area 11a is denoted as V1, and the sum of the fire-emitting areas of each fire-emitting hole 110 in the second fire-emitting area 11b is denoted as V2; and within this interval, the inner arc-shaped line of each fire-emitting hole 110 in the first fire-emitting area 11a is denoted as the first baseline 101, the second baseline 102, the third baseline 103, the fourth baseline 104, the fifth baseline 105, the sixth baseline 106, the sixth baseline 107, the sixth baseline 108, the sixth baseline 109, the sixth baseline 10 ... In the two-fire-outlet zone 11b, the outer arc of each fire outlet 110 is the second baseline 102, and the arc located at the center of the first baseline 101 and the second baseline 102 is the third baseline 103. The area enclosed by the first baseline 101, the third baseline 103, and the two radial lines is S1, and the area enclosed by the third baseline 103, the second baseline 102, and the two radial lines is S2, satisfying: V1 / S1:V2 / S2≤1.1, and the centers of the circles corresponding to the first baseline 101, the second baseline 102, and the third baseline 103 coincide with the center of the circle corresponding to the annular top wall 11. This ensures sufficient secondary air around the fire outlets, especially those in the inner ring, thereby reducing the smoke generated during combustion and improving combustion efficiency.

[0063] The specification and claims of this invention use terms indicating direction, such as "front," "rear," "upper," "lower," "left," "right," "side," "top," and "bottom," to describe various exemplary structural parts and elements of the invention. However, these terms are used herein merely for ease of explanation and are determined based on the exemplary orientations shown in the accompanying drawings. Since the embodiments disclosed in this invention can be arranged in different orientations, these terms indicating direction are for illustrative purposes only and should not be considered as limitations. For example, "upper" and "lower" are not necessarily limited to directions opposite to or consistent with the direction of gravity.

[0064] The term "vertical" is also used in the specification and claims of this invention, meaning basically along the up and down direction, and is not limited to just the vertical direction, but can also be slightly deviated from the vertical direction.

[0065] The term "radial" is also used in the specification and claims of this invention, meaning essentially along the inside-out direction, and is not limited to the radial direction that passes through the center of the circle, but can also be slightly deviated from the radial direction.

Claims

1. A top-inlet burner, comprising: The base (3) has an upward-facing mixing chamber (32); The first flame cap (1) is placed on the gas mixing chamber (32), and flame holes (110) are distributed at intervals on the first flame cap (1) to connect the gas mixing chamber (32) with the external environment. The ejector tube (4) is placed horizontally at the bottom of the base (3), with its air inlet located in the external environment and correspondingly equipped with a nozzle, and its air outlet connected to the mixing chamber (32). Its features are: The heat intensity of the flame outlet (110) is 4~5.5 kW / mm. 2 This increases the total flame area of ​​the flame outlet.

2. The top-inlet burner according to claim 1, characterized in that: The first flame cap (1) is annular in shape that matches the opening shape of the gas mixing chamber (32), and has an annular top wall (11) with the flame outlet holes (110) spaced apart along the circumference.

3. The top-inlet burner according to claim 2, characterized in that: The ratio of the wall thickness of the annular top wall (11) to the thermal intensity of the fire hole is 0.15~0.

62.

4. The top-inlet burner according to claim 3, characterized in that: There are at least two groups of flaming zones, with flaming holes (110) spaced apart in the circumferential direction, and they are distributed radially along the annular top wall (11).

5. The top-inlet burner according to claim 4, characterized in that: Within the range defined by two radially arranged and radially extended radial lines on the annular top wall (11), two radially adjacent sets of fire-emitting areas are denoted as the first fire-emitting area (11a) and the second fire-emitting area (11b), with the second fire-emitting area (11b) located outside the first fire-emitting area (11a). And record the sum of the fire-emitting areas of each fire-emitting hole (110) in the first fire-emitting area (11a) as V1 and the sum of the fire-emitting areas of each fire-emitting hole (110) in the second fire-emitting area (11b) as V2. And let the inner arc line of each fire hole (110) in the first fire zone (11a) be the first baseline (101), the outer arc line of each fire hole (110) in the second fire zone (11b) be the second baseline (102), and the arc line located at the center of the first baseline (101) and the second baseline (102) be the third baseline (103). The area of ​​the interval enclosed by the first baseline (101), the third baseline (103) and the two radial lines is S1, and the area of ​​the interval enclosed by the third baseline (103), the second baseline (102) and the two radial lines is S2, satisfying: (V1 / S1):(V2 / S2)≤1.1; Furthermore, the centers of the circles corresponding to the first baseline (101), the second baseline (102), and the third baseline (103) coincide with the center of the circle corresponding to the annular top wall (11).

6. The top-inlet burner according to claim 4, characterized in that: There are at least three groups of fire zones, which are distributed radially at intervals along the annular top wall (11), and the interval between two adjacent groups of fire zones in the radial direction gradually decreases from the inside to the outside.

7. The top-inlet burner according to claim 4, characterized in that: Each fire hole (110) is arranged radially staggered.

8. The top-inlet burner according to claim 4, characterized in that: The fire area of ​​a single fire hole (110) in the outermost fire zone is less than or equal to the fire area of ​​a single fire hole (110) in other fire zones.

9. The top-inlet burner according to claim 4, characterized in that: The innermost fire zone is located adjacent to the inner edge of the annular top wall (11).

10. The top-inlet burner according to claim 2, characterized in that: The number of the fire outlet holes (110) is 400 to 800.

11. The top-inlet burner according to claim 2, characterized in that: Each flame outlet (110) is circular with an inner diameter of 1~1.6mm.

12. The top-inlet burner according to claim 2, characterized in that: The axis of the fire outlet (110) is perpendicular to the annular top wall (11).

13. The top-inlet burner according to claim 12, characterized in that: The angle between the axis of the fire outlet (110) and the horizontal plane is 45~70°.

14. The top-inlet burner according to claim 2, characterized in that: The flame outlet (110) is located on the inner side of the annular top wall (11) in the radial direction, and the outer side of the annular top wall (11) forms a flameless zone without the flame outlet (110).

15. The top-inlet burner according to any one of claims 1 to 14, characterized in that: The spacing of the flame outlet holes (110) meets the following requirements: At least two adjacent fire holes (110) have a spacing greater than or equal to the diameter of the single fire hole (110) that forms the spacing. Furthermore, the ratio of the number of flame outlet holes (110) that meet the above requirements to the total number of flame outlet holes (110) is ≥90%.

16. The top-inlet burner according to any one of claims 2 to 14, characterized in that: The base (3) also has an inner ring mixing chamber (31) with the opening facing upward, located in the inner periphery of the mixing chamber (32); The upper air intake burner also has an inner ring flame cap (2) located inside the first flame cap (1), and the inner ring flame cap (2) has a vertically extending peripheral wall (21). The peripheral wall (21) is opposite to the first flame cap (1) and is provided with inner ring main flame holes (210) at intervals along the circumference. The diameter of the inner ring main flame holes (210) is 1.8~3mm.

17. The top-inlet burner according to claim 16, characterized in that: The first flame cap (1) also has an inner ring wall (12) extending downward from the inner edge of the annular top wall (11), at least the upper part of the inner ring wall (12) is inclined inward from top to bottom to form a guide wall (121), and the upper edge of the guide wall (121) is engaged with the inner edge of the annular top wall (11).

18. The top-inlet burner according to claim 17, characterized in that: The lower edge of the inner ring main fire hole (210) is at a higher height than the lower edge of the guide wall (121); The angle between the axis of the inner ring main fire hole (210) and the horizontal plane is greater than the angle between the guide wall (121) and the horizontal plane.

19. The top-inlet burner according to any one of claims 1 to 14, characterized in that: The top-intake burner is used in stoves.

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