Gas control method for a burner and multi-ring fire burner

Abstract

The application discloses a gas control method of a burner and a multi-ring fire burner. The burner has a first combustion part and a second combustion part. The fire holes of the first combustion part and the fire holes of the second combustion part are arranged in the radial direction of the burner from inside to outside in sequence. The gas control method of the burner comprises the following steps: after receiving an instruction of closing the gas supply of the first combustion part and the second combustion part, first, the gas supply of the second combustion part is closed, and then the gas supply of the first combustion part is closed; or, after receiving an instruction of opening the gas supply of the second combustion part, the first combustion part is not in the gear with the largest gas supply amount, and then the second combustion part is opened. The control method of the burner can avoid causing the explosion of the first combustion part, or can avoid the deflagration at the second combustion part.

Description

Technical Field

[0001] This invention relates to the field of stove technology, and in particular to a gas control method for a burner and a multi-ring burner. Background Technology

[0002] Currently, multi-channel, multi-ring burners are gradually becoming an important branch of household gas stoves due to their advantages such as strong flame control and diverse flame layout types.

[0003] However, because these multi-channel, multi-ring burners have a larger number of flame rings (combustion sections), and each flame ring can have its gas flow controlled separately to achieve flame on / off, the gas control process is more complex than that of dual-ring burners, with a variety of on / off combinations. Therefore, during the flame-off process of some flame rings, they are easily affected by the flame rings of adjacent flame rings, leading to popping or abnormal noises during the shutdown process, thus impacting the user experience. Summary of the Invention

[0004] The technical problem to be solved by the present invention is to overcome the defects of existing multi-ring burners that are prone to knocking and abnormal noises, and to provide a gas control method for burners and a multi-ring burner.

[0005] The present invention solves the above-mentioned technical problems through the following technical solution:

[0006] A gas control method for a burner, the burner having a first combustion section and a second combustion section disposed on a burner cap, wherein the flame holes of the first combustion section and the second combustion section are arranged sequentially from the inside to the outside along the radial direction of the burner, and the gas control method for the burner includes:

[0007] Upon receiving an instruction to shut off the gas supply to the first and second combustion sections, the gas supply to the second combustion section is shut off first, followed by the gas supply to the first combustion section.

[0008] And / or, upon receiving an instruction to activate the gas supply to the second combustion chamber, the first combustion chamber is deactivated from its maximum gas supply position before the second combustion chamber is activated.

[0009] The burner's control method, when requiring shut-off, first shuts off the gas supply to the outermost second combustion chamber, then shuts off the gas supply to the innermost first combustion chamber. This avoids the sudden pressure drop in the first combustion chamber when it is shut off first, which would cause the lean gas to recede into the chamber due to pressure. Simultaneously, the adjacent second combustion chamber remains burning, effectively creating a high-temperature ignition source outside the first combustion chamber, continuously heating the area near the burner holes and igniting unburned gas, resulting in explosive backfire, producing knocking and abnormal noises, and affecting the user experience. Conversely, if the outermost second combustion chamber is shut off first, the flame from the first combustion chamber cannot heat the burner holes, failing to ignite unburned gas and preventing knocking.

[0010] Meanwhile, the burner control method ensures that when the second combustion section needs to be ignited, the first combustion section is not in the position with the maximum gas supply before the second combustion section is opened, so as to prevent the unignited gas in the second combustion section from being ignited by the flame of the first combustion section located relatively inside, thus avoiding deflagration in the second combustion section.

[0011] Preferably, the step of first shutting off the gas supply to the second combustion section and then shutting off the gas supply to the first combustion section after receiving the instruction to shut off the gas supply to the first combustion section specifically includes:

[0012] Upon receiving an instruction to shut off the gas supply to the first combustion chamber, the system first obtains the status of the second combustion chamber. If the second combustion chamber is in a combustion state, the instruction to shut off the gas supply to the first combustion chamber is terminated.

[0013] Before the first combustion section, which is relatively close to the inside, needs to be shut down, it is first identified whether the second combustion section is in a combustion state. The decision on whether to shut down the first combustion section is based on the combustion state of the second combustion section, which effectively avoids the situation where unburned gas in the first combustion section is ignited by the flame of the second combustion section, resulting in a detonation.

[0014] Specifically, if the gas supply to the first combustion chamber is shut off, the gas pressure in the first combustion chamber drops suddenly, causing the lean gas to recede into the cavity due to the pressure. At the same time, if the adjacent and lower second combustion chamber is still burning, it is equivalent to having a high-temperature ignition source next to and below the first combustion chamber. The flame of the second combustion chamber is located below the flame hole of the first combustion chamber, continuously heating the flame hole of the first combustion chamber, which will cause an explosive backfire, producing popping and abnormal noises, affecting the user experience.

[0015] Preferably, after terminating the instruction to shut off the gas supply to the first combustion chamber, the gas supply to the first combustion chamber is reduced.

[0016] After detecting that the second combustion section is in combustion mode, by reducing the gas supply to the first combustion section, it can effectively avoid the popping sound caused by turning off the first combustion section when the second combustion section is burning, and also reduce the firepower of the first combustion section to meet the user's firepower adjustment needs.

[0017] Preferably, after terminating the instruction to shut off the gas supply to the first combustion chamber, the gas supply to the second combustion chamber is shut off first, and then the gas supply to the first combustion chamber is shut off.

[0018] After detecting that the second combustion chamber is in combustion mode, the gas supply to the second combustion chamber is shut off first, and then the gas supply to the first combustion chamber is shut off, so as to meet the user's firepower adjustment needs while avoiding popping and abnormal noises at the first combustion chamber.

[0019] Preferably, the step of first reducing the gas supply to the first combustion unit to a level sufficient to maintain combustion, and then activating the second combustion unit after receiving the instruction to start the gas supply to the second combustion unit, specifically includes:

[0020] After the second combustion section is turned on, the gas supply of the first combustion section is controlled so that the gas supply of the first combustion section decreases as the gas supply of the second combustion section increases.

[0021] Since there are extreme requirements for the total load of the burner, when the gas supply of the second combustion section located on the outer side increases, the gas supply of the first combustion section located on the inner side is reduced accordingly. This allows the heat load of the second combustion section located on the outer side to be relatively larger, provided that the total load of the burner does not exceed the limit, thus meeting the cooking needs of the burner for a large area and high heat.

[0022] Preferably, the burner is a multi-ring burner, the first combustion section is a middle ring combustion section, the second combustion section is an outer ring combustion section, and the multi-ring burner also has an inner ring combustion section. The multi-ring burner, along the ignition direction of the gas knob, sequentially includes a concentrated heating zone and a large-area heating zone starting from 0°. The gas control method for the burner further includes:

[0023] When the gas knob is rotated from 0° to the centralized heating zone, the inner ring combustion section and the middle ring combustion section are turned on, while the outer ring combustion section is turned off. As the gas knob continues to rotate, the gas supply of the inner ring combustion section and the middle ring combustion section gradually increases.

[0024] When the gas knob is rotated from the centralized heating zone to the large-area heating zone, the outer ring combustion section is turned on and switched to the maximum gas supply, while the gas supply of the middle ring combustion section is reduced.

[0025] By setting a concentrated heating zone and a large-area heating zone on the gas knob of the multi-ring burner, the user's needs for both concentrated high heat and large-area high heat cooking can be met simultaneously. The so-called "reduced gas supply to the central ring combustion zone" means reducing the gas supply while ensuring combustion in the central ring combustion zone, not reducing the gas supply to the point where the flame cannot burn.

[0026] Specifically, as the user rotates the gas control knob within the concentrated heating zone, the gas supply to both the inner ring combustion section and the middle ring combustion section gradually increases to meet the user's demand for concentrated high-power cooking.

[0027] As the user rotates the gas control knob from the concentrated heating zone to the large-area heating zone, the outer ring combustion section is activated while the gas supply to the middle ring combustion section decreases. This allows the system to switch to a large-area, high-power state without exceeding the total load of the burner, thus meeting the user's cooking needs.

[0028] Preferably, the gas control method for the burner further includes:

[0029] As the gas knob rotates from the concentrated heating zone to the large-area heating zone, the gas supply to the outer ring combustion zone gradually decreases and eventually shuts off as the gas knob continues to rotate, keeping the middle ring combustion section open.

[0030] As the gas knob continues to rotate, the gas supply to the outer and middle ring combustion chambers gradually decreases and eventually shuts off, thus adjusting the heat output of the outer and middle ring combustion chambers to meet the user's different cooking needs. Simultaneously, the middle ring combustion chamber remains open until the gas supply to the outer ring combustion chamber reaches zero to prevent popping or other unusual noises from occurring there.

[0031] In this system, after the gas supply in the outer ring combustion chamber gradually decreases and eventually shuts off, the gas supply scheme in the middle ring combustion chamber can be set as needed. For example, the gas supply can be gradually increased, gradually decreased, or increased or decreased as needed.

[0032] Preferably, the gas control method for the burner further includes:

[0033] After the gas supply in the middle ring combustion section reaches zero, the gas supply in the inner ring combustion section gradually decreases.

[0034] As the gas knob continues to rotate, the user's cooking needs for different heat levels can be met by adjusting the heat of the middle and inner ring combustion sections.

[0035] Preferably, the maximum heat load of the middle ring combustion section is greater than the maximum heat load of the outer ring combustion section.

[0036] By setting the heat load of the outer ring combustion section at a relatively low level, the total load of the burner will not fluctuate significantly as the outer ring combustion section is turned on during the process of rotating from the concentrated heating zone to the large area heating zone. At the same time, deflagration is avoided during the opening of the outer ring combustion section.

[0037] Preferably, the burner cap has an annular first surface, and along the radial direction of the burner, the inner annular edge of the first surface is higher than the outer annular edge of the first surface, and the flame holes of the first combustion section and / or the flame holes of the second combustion section are formed on the first surface.

[0038] By configuring the first surface of the burner cap with a higher inner surface and a lower outer surface to accommodate the flame holes of either the first or second combustion section, the influence of the burner cap's surface shape on the secondary air supply at the flame holes of the first or second combustion section can be reduced. Furthermore, when the second combustion section is closed, the rate at which residual combustion gas at the flame holes of the second combustion section dilutes and diffuses to the outer periphery of the burner cap can be increased. Therefore, when the second combustion section is closed, by reducing the concentration of combustion gas at that location, the risk of residual combustion gas being ignited by the flame of the first combustion section and causing a detonation can be mitigated and reduced.

[0039] Preferably, the flame holes of the first combustion section and the flame holes of the second combustion section are both formed on the first surface, and the inclination angle of the first surface of the flame cap relative to the horizontal plane is in the range of 30° to 40°.

[0040] By positioning the first surface of the burner cap within the aforementioned inclined range, the second combustion section located on the outer side can supplement the flame holes of the first combustion section located on the inner side with air that flows radially inward and is preheated by the flame holes of the second combustion section, thereby making the combustion of the first combustion section more complete.

[0041] Preferably, the aperture of the flame hole in the first combustion section is defined as D;

[0042] Along the radial direction of the burner, the minimum distance between the center of the flame hole of the first combustion section and the center of the flame hole of the second combustion section is defined as L1, and the value of L1 ranges from 5D to 7.5D.

[0043] Along the axial direction of the burner, the minimum distance between the center of the flame hole of the first combustion section and the center of the flame hole of the second combustion section is defined as L2, and the value of L2 ranges from 2.5D to 3.5D.

[0044] If the horizontal distance (minimum spacing L1) between the first and second combustion sections is less than 5 times the aperture D of the first combustion section's burner orifice, and the vertical distance (minimum spacing L2) is less than 2.5 times the aperture D of the first combustion section's burner orifice, the distance between the first and second combustion sections is too close. This will cause the first and second combustion sections to interfere with each other during ignition switching and shut-off, resulting in popping sounds. Furthermore, their proximity will also cause the flame of the second combustion section to affect the shape of the flame of the first combustion section, leading to incomplete combustion and excessively blurred flames.

[0045] If the horizontal distance (minimum spacing L1) between the first and second combustion sections is greater than 7.5 times the aperture D of the first combustion section's orifice, and the vertical distance (minimum spacing L2) is greater than 3.5 times the aperture D of the first combustion section's orifice, the flame from the first combustion section cannot be effectively transmitted to the second combustion section. As the flow rate of the second combustion section gradually increases, it cannot ignite under a small exhaust pressure, resulting in exhaust from the second combustion section without ignition, posing a safety hazard. The "center of the orifice" refers to the centerline of the orifice. If the orifice is irregularly shaped, the "center of the orifice" is the center of its radial width.

[0046] Preferably, the flame holes of the first combustion section are positioned higher than the flame holes of the second combustion section.

[0047] By setting the height difference between the flame holes of the first combustion section and the second combustion section, so that the flame holes of the first combustion section are higher than those of the second combustion section, the concentration of unburned gas diffused from the second combustion section to the flame holes of the first combustion section can be reduced during the ignition process. This is to prevent the concentration of unburned gas diffused from the second combustion section to the first combustion section from reaching a critical value and causing deflagration.

[0048] At the same time, during the flame-off process, the flame in the second combustion section can be prevented from igniting the remaining gas in the first combustion section, thus solving the problem of explosions that easily occur when the flame is switched off.

[0049] Preferably, the burner is a multi-ring burner, and the second combustion section is the outermost combustion section of the multi-ring burner.

[0050] Preferably, the structural arrangement of the first combustion section and the second combustion section relative to the flame cap is one of the following:

[0051] (1) The flame holes of the first combustion part and the flame holes of the second combustion part are both provided on the same flame cap, and the flame holes of the first combustion part and the flame holes of the second combustion part have the same orientation and are both outward;

[0052] (2) The flame cap includes a first flame cap and a second flame cap that are respectively separated. The flame hole of the first combustion part is disposed on the first flame cap, and the flame hole of the second combustion part is disposed on the second flame cap. The flame holes of the first combustion part and the flame holes of the second combustion part have the same orientation and both face outward.

[0053] (3) The flame cap includes a first flame cap and a second flame cap that are arranged separately from each other. The flame hole of the first combustion part is arranged on the first flame cap, and the flame hole of the second combustion part is arranged on the second flame cap. The flame holes of the first combustion part and the flame holes of the second combustion part have different orientations and are arranged opposite to each other.

[0054] A multi-ring burner employs the gas control method for burners as described above, characterized in that the flame holes of the first combustion section and the flame holes of the second combustion section of the multi-ring burner have the same orientation and are both arranged outwards.

[0055] The flame holes of the first combustion section of this multi-ring burner are positioned further outwards when they are located at a relatively high position, which can easily cause detonation problems when the second combustion section is switched off or shut off.

[0056] By employing this burner's gas control method, when flameout is required, the gas supply to the second combustion section is shut off first, followed by the gas supply to the first combustion section. This prevents unburned gas in the first combustion section from flowing downwards to the second combustion section and being ignited by the flame there, thus avoiding a detonation. Furthermore, the second combustion section, being shut off first, is located at a relatively low position, so even if unburned gas diffuses into the flame zone of the first combustion section after shutdown, its concentration is relatively low and will not cause a detonation.

[0057] Meanwhile, when it is necessary to ignite the second combustion chamber, first reduce the gas supply of the first combustion chamber to a level that can maintain combustion, and then turn on the second combustion chamber to avoid the unignited gas in the second combustion chamber being ignited by the relatively high flame of the first combustion chamber, which would cause a popping sound in the second combustion chamber.

[0058] Preferably, the flame cap of the multi-ring burner has an annular first surface. Along the radial direction of the multi-ring burner, the inner ring edge of the first surface is higher than the outer ring edge of the first surface. The flame holes of the first combustion section and the flame holes of the second combustion section are sequentially formed on the first surface from the inside to the outside along the radial direction of the multi-ring burner.

[0059] The multi-ring burner arranges flame holes for the first combustion section and the second combustion section on the inner high and outer low flame cap surface, in order from the inside to the outside along the radial direction of the multi-ring burner, so as to use the flame holes of the second combustion section to adjust the flame temperature at the flame holes of the first combustion section.

[0060] Specifically, when the first combustion section located on the inner side is open and the second combustion section is closed, because the flame holes of the first combustion section are arranged on the surface of the flame cap, which is higher on the inside and lower on the outside, the air (secondary air) flowing from the outside of the multi-ring burner inward is not blocked by the flame cap surface and can flow smoothly to the flame holes of the first combustion section, especially to the flame root of the first combustion section, for effective air replenishment, thereby improving the replenishment capacity of the first combustion section and thus increasing the flame temperature of the first combustion section. At the same time, when the second combustion section is not open, the flame holes of the second combustion section can also serve as air replenishment holes for the first combustion section, which can increase the secondary air acquisition pathways of the first combustion section.

[0061] When the first combustion section and the second combustion section are turned on at the same time, the flame at the burner hole of the second combustion section, which is located on the outer side, will consume some of the air flowing inward, thereby reducing the amount of secondary air available to the first combustion section and thus reducing the flame temperature of the first combustion section.

[0062] Therefore, through this structural improvement, the flame temperature of the first combustion section can change depending on whether the second combustion section is open or closed. When the second combustion section is closed, the flame temperature of the first combustion section is relatively high to meet the user's demand for concentrated high heat in cooking. When the second combustion section is open, the flame temperature of the first combustion section is reduced due to the influence of the second combustion section. This ensures that even when the heat load of the first combustion section is high, further opening the second combustion section will not cause the total load of the multi-ring burner to exceed the limit. This can simultaneously meet the user's demand for concentrated high heat and large-area high heat in cooking, expanding the application scenarios of the multi-ring burner.

[0063] Preferably, the multi-ring burner further has an inner ring combustion section, and the flame cover includes an inner flame cover and an outer flame cover arranged concentrically. The flame holes of the inner ring combustion section are disposed on the inner flame cover, and the flame holes of the first combustion section and the flame holes of the second combustion section are disposed on the first surface of the outer flame cover.

[0064] By arranging the first and second combustion sections outside the inner ring combustion section, the burner can better meet the cooking needs of concentrated high heat and large-area high heat.

[0065] Preferably, the flame cap of the multi-ring burner includes a first flame cap and a second flame cap arranged concentrically.

[0066] The first flame cap has an annular first surface. Along the radial direction of the multi-ring burner, the inner ring edge of the first surface is higher than the outer ring edge of the first surface, and the flame holes of the first combustion section are formed on the first surface.

[0067] The second burner cap has an annular second surface. Along the radial direction of the multi-ring burner, the inner ring edge of the second surface is higher than the outer ring edge of the second surface, and the flame holes of the second combustion section are formed on the second surface.

[0068] Preferably, the multi-ring burner further has an inner ring combustion section, and the flame cover includes an inner flame cover, a middle flame cover and an outer flame cover arranged concentrically. The flame holes of the inner ring combustion section are disposed on the inner flame cover, the flame holes of the first combustion section are disposed on the first surface of the middle flame cover, and the flame holes of the second combustion section are disposed on the second surface of the outer flame cover.

[0069] Preferably, the multi-ring burner has a secondary air supply channel, the end of which extends upward to the outer periphery of the inner burner cap, and the flame hole of the first combustion part is positioned below the inner ring edge of the burner cap where the flame hole of the first combustion part is located.

[0070] By setting up a secondary air channel, secondary air replenishment can be better achieved. Specifically, while the secondary air channel extends to the outer periphery of the inner burner cap to replenish the area, the burner holes of the first combustion chamber are further positioned below the inner circumference edge of the burner cap. This prevents secondary air flowing from the secondary air channel from replenishing the burner holes of the first combustion chamber. Consequently, the secondary air source for the first combustion chamber relies solely on air flowing from the outside to the inside of the burner cap surface. This increases the impact of whether the second combustion chamber is open or closed on the amount of secondary air flowing to the first combustion chamber, thereby increasing the influence of the second combustion chamber's opening or closing on the flame temperature of the first combustion chamber. This better meets users' needs for concentrated high heat and large-area high-heat cooking.

[0071] Preferably, a flame transmission channel is provided on the outer flame cover, and the flame transmission channel penetrates the outer flame cover radially along the multi-ring burner.

[0072] When the flame hole of the first combustion section is positioned lower than the inner ring edge of the first surface, flame transmission between the flame hole of the inner ring combustion section and the flame hole of the first combustion section is difficult due to the obstruction of the inner ring edge of the outer flame cap. Therefore, a flame transmission channel is provided to solve the problem of flame transmission from the inner ring combustion section to the first combustion section.

[0073] Furthermore, choosing to set up a flame transmission channel for flame transmission, compared to the solution of opening a flame transmission groove, can reduce the impact of the surface shape of the first surface of the outer flame cap, so that the shape of the first surface being higher inside and lower outside can better prevent secondary air from being supplied to the first combustion section at the secondary air channel.

[0074] Preferably, the opening of the ignition channel on the first surface is located between the flame holes of the first combustion section and the flame holes of the second combustion section.

[0075] By setting the opening of the ignition channel on the first surface between the flame holes of the first combustion section and the second combustion section, the ignition of the inner ring combustion section can ensure that the first combustion section is ignited no later than the second combustion section, thereby avoiding the explosion caused by the first combustion section being ignited too late.

[0076] Preferably, the angle at which the flame holes of the second combustion section are positioned covers the flame holes of the first combustion section on the circumference centered on the axis of the multi-ring burner.

[0077] On the circumference centered on the axis of the multi-ring burner, the setting angle of the flame holes of the first combustion section falls within the setting angle range of the flame holes of the second combustion section. This improves the ability of the second combustion section to consume the secondary air flowing toward the flame holes of the first combustion section when it is turned on, making fuller use of the secondary air and better controlling the flame temperature of the first combustion section by turning on the second combustion section.

[0078] And / or, along the circumferential direction of the multi-ring burner, the flame holes of the first combustion section are evenly distributed on the first surface;

[0079] And / or, along the circumferential direction of the multi-ring burner, the flame holes of the second combustion section are evenly distributed on the first surface.

[0080] Preferably, the angle between the flame hole of the first combustion section and the horizontal plane is defined as α1, and the value of α1 ranges from 25° to 40°.

[0081] By setting this angle range, the flame of the first combustion section is directed upwards and outwards. Specifically, by controlling the angle α1 between the flame holes of the first combustion section and the horizontal plane, the lower limit of α1 is set to 25°. This prevents the flame holes of the first combustion section from tilting too far towards the second combustion section, which would cause the flames of the first and second combustion sections to interfere with each other, resulting in incomplete combustion and low energy efficiency.

[0082] By controlling the angle α1 between the flame holes of the first combustion section and the horizontal plane, the upper limit of α1 is set to 40°, thus preventing the flame of the first combustion section from being too vertical and failing to effectively heat the bottom of the pot.

[0083] Preferably, the angle between the flame hole of the first combustion section and the first surface is defined as α2, and the value of α2 ranges from 55° to 80°.

[0084] By setting this angle range, the flame of the first combustion section is directed upwards and outwards. Specifically, by controlling the angle α2 between the flame hole of the first combustion section and the first surface of the flame cap to be within the range of 55° to 80°, the air, after being preheated on the surface of the flame cap, can be supplied to the root region of the flame in the first combustion section. If the angle α2 is too small, the planar airflow will not be able to flow, making it difficult for secondary air to supply the root of the flame, resulting in incomplete combustion. If the angle α2 is too large, the preheating effect on the air will be poor.

[0085] Preferably, the angle between the flame hole of the second combustion section and the horizontal plane is defined as β1, and the value of β1 ranges from 20° to 30°.

[0086] By setting this angle range, the flame of the second combustion section is directed upwards and outwards. Specifically, by controlling the angle β1 between the flame holes of the second combustion section and the horizontal plane, the lower limit of β1 is set to 20°. This prevents the flame holes of the second combustion section from being too close to the horizontal plane, which would affect the normal combustion of the flame and lead to incomplete combustion and low energy efficiency.

[0087] By controlling the angle β1 between the flame holes of the second combustion section and the horizontal plane, and setting the upper limit of β1 to 30°, the excessive elevation angle of the flame holes of the second combustion section is avoided from interfering with the flame of the first combustion section, which would lead to incomplete combustion and low energy efficiency.

[0088] Preferably, the angle between the flame hole of the second combustion section and the first surface is defined as β2, and the value of β2 ranges from 55° to 75°.

[0089] By setting this angle range, the flame of the second combustion section is directed upwards and outwards. Specifically, by controlling the angle β2 between the flame hole of the second combustion section and the first surface of the flame cap to be within the range of 55° to 75°, the air, after being preheated on the surface of the flame cap, can be supplied to the flame root region of the second combustion section. If the angle β2 is too small, the planar airflow will not be able to flow, while if the angle β2 is too large, the preheating effect on the air will be poor.

[0090] A multi-ring burner employs the gas control method for burners described above, wherein the flame holes of the first combustion section and the flame holes of the second combustion section of the multi-ring burner have different orientations and are arranged opposite each other.

[0091] Preferably, the flame cap of the multi-ring burner includes a first flame cap and a second flame cap arranged concentrically.

[0092] The first flame cap has an annular first surface. Along the radial direction of the multi-ring burner, the inner ring edge of the first surface is higher than the outer ring edge of the first surface, and the flame holes of the first combustion section are formed on the first surface.

[0093] The second burner cap has an annular second surface. Along the radial direction of the multi-ring burner, the inner ring edge of the second surface is lower than the outer ring edge of the second surface, and the flame holes of the second combustion section are formed on the second surface.

[0094] Preferably, the multi-ring burner further has an inner ring combustion section, and the flame cover includes an inner flame cover, a middle flame cover and an outer flame cover arranged concentrically. The flame holes of the inner ring combustion section are disposed on the inner flame cover, the flame holes of the first combustion section are disposed on the first surface of the middle flame cover, and the flame holes of the second combustion section are disposed on the second surface of the outer flame cover.

[0095] The positive and progressive effects of this invention are as follows:

[0096] The burner control method, when it is necessary to shut off the flame, first shuts off the gas supply to the second combustion section located on the outer side, and then shuts off the gas supply to the first combustion section located on the inner side, so as to avoid causing the first combustion section to explode.

[0097] The control method of this burner is to reduce the gas supply of the first combustion section to a level that can maintain combustion before igniting the second combustion section when the second combustion section needs to be opened, so as to avoid deflagration at the second combustion section. Attached Figure Description

[0098] Figure 1 This is a schematic diagram of the burner structure of Embodiment 1 of the present invention.

[0099] Figure 2 This is a top view of the burner structure of Embodiment 1 of the present invention.

[0100] Figure 3 This is a schematic diagram of the gas valve in Embodiment 1 of the present invention.

[0101] Figure 4 This is a schematic diagram of the outer flame cap of the burner in Embodiment 1 of the present invention.

[0102] Figure 5 This is a schematic diagram (a) of the secondary air replenishment of the burner in Embodiment 1 of the present invention.

[0103] Figure 6 This is a schematic diagram (II) of the secondary air replenishment of the burner in Embodiment 1 of the present invention.

[0104] Figure 7 This is a schematic diagram (III) of the secondary air replenishment of the burner in Embodiment 1 of the present invention.

[0105] Figure 8 This is a schematic diagram (a) showing the external dimensions of the burner's outer flame cap according to Embodiment 1 of the present invention.

[0106] Figure 9 This is a schematic diagram (II) showing the external dimensions of the burner's outer flame cap according to Embodiment 1 of the present invention.

[0107] Figure 10 This is a schematic diagram (III) showing the external dimensions of the burner's outer flame cap according to Embodiment 1 of the present invention.

[0108] Figure 11 This is a schematic flowchart (I) of the gas control method for the burner in Embodiment 1 of the present invention.

[0109] Figure 12 This is a schematic flowchart (II) of the gas control method for the burner in Embodiment 1 of the present invention.

[0110] Figure 13 This is a schematic flowchart (III) of the gas control method for the burner in Embodiment 1 of the present invention.

[0111] Figure 14 This is a schematic diagram of the burner in another embodiment of the present invention (I).

[0112] Figure 15 This is a schematic diagram (II) of the burner in another embodiment of the present invention.

[0113] Figure 16 This is a schematic diagram of the burner in another embodiment two of the present invention.

[0114] Figure 17 This is a schematic diagram showing the rotation angle distribution of the gas valve's gas knob in Embodiment 2 of the present invention.

[0115] Figure 18 This is a schematic diagram of the heat load of the burner in each section according to Embodiment 2 of the present invention.

[0116] Figure 19 This is a schematic diagram of the heat load of the burner in each section of Embodiment 3 of the present invention.

[0117] Explanation of reference numerals in the attached figures:

[0118] Burner 100, circumferential direction X, radial direction Y, axial direction Z

[0119] Inner ring combustion section 1, flame hole 1a

[0120] Central ring combustion section 2, ignition port 2a, flame 2b

[0121] Outer ring combustion section 3, flame hole 3a, flame 3b

[0122] Inner flame cap 41

[0123] Outer flame cap 42, first surface 42a, inner ring edge 421, outer ring edge 422, flame transmission channel 423, and middle flame cap 43

[0124] Gas distribution plate 5

[0125] Base 6, secondary air channel 61

[0126] Inner ring ejector tube 71

[0127] 72-ring ejector tube

[0128] Outer ring ejector tube 73

[0129] Gas valve 8

[0130] Valve stem 81

[0131] Inner ring gas outlet 82

[0132] Central Ring Gas Exit 83

[0133] Outer ring gas outlet 84 Detailed Implementation

[0134] The present invention will be further illustrated by way of embodiments below, but the present invention is not limited to the scope of the embodiments described herein.

[0135] Example 1

[0136] like Figure 1 As shown, this embodiment provides a multi-ring burner 100, specifically a three-channel three-ring burner, which is applied in a gas stove. The combustion and extinguishing of the three ring flames (inner ring, middle ring, and outer ring) are controlled by three sets of gas channels to achieve different flame combinations and meet different heating and cooking needs of users. For example, Figure 1 As shown, the circumferential direction of the burner 100 is defined as X, the radial direction as Y, and the axial direction as Z. Figure 1 and Figure 2As can be seen, the burner 100 has three rings of combustion sections arranged from the inside to the outside along its radial direction Y: an inner ring combustion section 1, a middle ring combustion section 2 (equivalent to the first combustion section), and an outer ring combustion section 3 (equivalent to the second combustion section). The inner ring combustion section 1 is formed separately on the inner flame cap 41, while the middle ring combustion section 2 and the outer ring combustion section 3 are formed on the same flame cap, i.e., simultaneously on the outer flame cap 42. However, the gas passages between the two combustion sections are separated to allow for independent opening and closing. The inner ring combustion section 1 is connected to the middle inner ring ejector tube 71 and is supplied with gas through the gas nozzle at the inner ring ejector tube 71. The middle ring combustion section 2 is connected to the right middle ring ejector tube 72 and is supplied with gas through the gas nozzle at the middle ring ejector tube 72. The outer ring combustion section 3 is connected to the left outer ring ejector tube 73 and is supplied with gas through the gas nozzle at the outer ring ejector tube 73. The gas from each ejector tube flows through the base 6 and the gas distribution plate 5, and after being distributed by the gas flow direction of the base 6 and the gas distribution plate 5, it flows to the corresponding combustion section.

[0137] like Figure 3 The diagram shows the structure of the gas valve 8 connected to the burner 100 in this embodiment. By rotating the valve stem 81, the valve spool (not shown in the figure) inside the gas valve 8 is driven to rotate synchronously. Different sized connecting holes are opened on the surface of the valve spool at the corresponding rotation angle, so as to change the gas supply quantity and ratio through the cooperation between the valve spool and the valve body. The inner ring gas outlet 82 of the gas valve 8 is connected to the gas nozzle of the inner ring injector 71 through a pipe, the middle ring gas outlet 83 is connected to the gas nozzle of the middle ring injector 72 through a pipe, and the outer ring gas outlet 84 is connected to the gas nozzle of the outer ring injector 73 through a pipe, so as to form three independent gas channels and realize three independent control of the three-channel three-ring burner 100.

[0138] Specifically, in order to address the problem that current multi-ring burners cannot simultaneously meet the cooking needs of concentrated high heat and large-area high heat, such as... Figure 4 As shown, the outer flame cap 42 has an annular first surface 42a. Along the radial direction Y of the multi-ring burner 100, the inner ring edge 421 of the first surface 42a is higher than the outer ring edge 422, so that the entire outer flame cap 42 has a surface shape that is higher on the inside and lower on the outside at the first surface 42a. The flame holes 2a of the middle ring combustion section 2 and the flame holes 3a of the outer ring combustion section 3 are formed sequentially from the inside to the outside along the radial direction Y on the first surface 42a.

[0139] By making the outer flame cap 42 form a surface that is higher on the inside and lower on the outside, and arranging the flame holes 2a of the middle ring combustion section 2 and the flame holes 3a of the outer ring combustion section 3 in the order from the inside to the outside along the radial direction Y, the temperature of the flame 2b at the flame hole 2a of the middle ring combustion section 2 can be adjusted by using the flame holes 3a of the outer ring combustion section 3.

[0140] Specifically, such as Figure 5 As shown, when the inner ring combustion section 2 is open and the outer ring combustion section 3 is closed, because the flame holes 2a of the inner ring combustion section 2 are arranged on the flame cap surface which is higher on the inside and lower on the outside, the air A (secondary air) flowing from the outside of the burner 100 to the inside is not blocked by the flame cap surface and can flow smoothly to the flame holes 2a of the inner ring combustion section 2, especially to the root of the flame 2b of the inner ring combustion section 2, to effectively replenish air, thereby improving the replenishment capacity of the inner ring combustion section 2 and thus increasing the flame temperature of the inner ring combustion section 2. At the same time, when the outer ring combustion section 3 is not open, the flame holes of the outer ring combustion section 3 can also serve as air replenishment holes for the inner ring combustion section 2, which can increase the secondary air acquisition pathways of the inner ring combustion section 2.

[0141] When the middle ring combustion section 2 and the outer ring combustion section 3 are opened simultaneously, such as Figure 6 As shown, the flame 3b at the burner hole 3a of the outer ring combustion section 3, which is located on the outer side, consumes part of the air A (secondary air) flowing inward, which reduces the amount of secondary air A available in the middle ring combustion section 2, thereby reducing the flame temperature of the middle ring combustion section 2.

[0142] Therefore, through this structural improvement, the flame temperature of the middle ring combustion section 2 can change depending on whether the outer ring combustion section 3 is open or closed. When the outer ring combustion section 3 is closed, the flame temperature of the middle ring combustion section 2 is relatively high to meet the user's demand for concentrated high heat. When the outer ring combustion section 3 is open, the flame temperature of the middle ring combustion section 2 is reduced due to the influence of the outer ring combustion section 3. This ensures that even when the heat load of the middle ring combustion section 2 is high, further opening the outer ring combustion section 3 will not cause the total load of the multi-ring burner 100 to exceed the limit. This can simultaneously meet the user's demand for concentrated high heat and large-area high heat, expanding the application scenarios of the multi-ring burner.

[0143] Of course, in other embodiments, this burner surface structure and the arrangement of the flame holes in the two combustion sections can also be applied to the non-middle and outer ring combustion sections 3. For example, in the three-ring burner 100 as in this embodiment, the flame holes of the inner ring combustion section 1 and the middle ring combustion section 2 are arranged sequentially on the burner cap, which is higher on the outside and lower on the inside. This allows the air flowing inward to be consumed by opening the middle ring combustion section 2, thereby relatively reducing the amount of usable secondary air A in the inner ring combustion section 1 and thus lowering the flame temperature of the inner ring combustion section 1. In this embodiment, this structural improvement is applied to the relatively outer middle ring combustion section 2 and the outer ring combustion section 3, so that the three-ring burner 100 can better meet the cooking needs of concentrated high heat and large-area high heat.

[0144] Alternatively, in other embodiments, it can also be applied to other multi-ring burners such as four-ring burners. By applying the above structure to any two adjacent combustion sections, the air flowing inward is consumed by the opening of the relatively outer combustion section, thereby relatively reducing the amount of available secondary air A in the relatively inner combustion section, and thus reducing the flame temperature of the relatively inner combustion section.

[0145] Furthermore, the first surface 42a of the outer burner cap 42 is configured with an inner higher surface and an outer lower surface, and the middle ring combustion section 2 and the outer ring combustion section 3 are arranged sequentially, such that the flame hole 3a of the outer ring combustion section 3 is relatively lower than the flame hole 2a of the middle ring combustion section 2. During the ignition transfer and ignition cutting process, the concentration of unburned residual gas located in the outer ring combustion section 3 can diffuse to the flame hole 2a of the middle ring combustion section 2, thereby improving and reducing the risk of residual unburned gas being ignited by the flame 2b of the middle ring combustion section 2 and causing a detonation.

[0146] like Figure 1 As shown, in this embodiment, the burner 100 is further provided with a secondary air passage 61 to guide air into the area between the inner burner cap 41 and the outer burner cap 42, thereby replenishing the air supply to the inner ring combustion section 1. Specifically, the secondary air supply passage is formed in the base 6 below the outer burner cap 42, and extends radially inward through the base 6, connecting the area between the inner burner cap 41 and the outer burner cap 42. Figure 7 As shown, secondary air B enters the area between the inner burner cap 41 and the outer burner cap 42 via the secondary air replenishment channel to replenish the inner ring combustion section 1. In this case, the burner hole 2a of the middle ring combustion section 2 is positioned on the first surface 42a as the inner ring edge 421 lower than the first surface 42a, so as to prevent the secondary air B flowing out of the secondary air channel 61 from replenishing the burner hole 2a of the middle ring combustion section 2. This makes the secondary air source of the middle ring combustion section 2 rely solely on the air flowing from the outside to the inside on the surface of the outer burner cap 42, thereby increasing the impact of whether the outer ring combustion section 3 is open or not on the amount of secondary air flowing to the middle ring combustion section 2, and better meeting the user's cooking needs for concentrated high heat and large area high heat.

[0147] Meanwhile, in order to better replenish the secondary air B flowing in the secondary air passage 61 to the burner holes of the inner ring combustion section 1, such as Figure 7 As shown, some of the flame holes 1a in the inner ring combustion section 1 are set below the inner ring edge 421 of the first surface 42a. The reason for not setting all the flame holes 1a of the inner ring combustion section 1 below the inner ring edge 421 of the first surface 42a is mainly to avoid affecting the heating efficiency of the pot bottom if the flame holes are set too low.

[0148] When the flame hole 2a of the middle ring combustion section 2 is positioned lower than the inner ring edge 421 of the first surface 42a, the flame transfer between the flame hole 1a of the inner ring combustion section 1 and the flame hole 2a of the middle ring combustion section 2 is difficult due to the obstruction of the inner ring edge 421 of the outer flame cap 42. Therefore, if... Figure 4 As shown, a flame transmission channel 423 is provided on the outer burner cap 42. The flame transmission channel 423 passes through the outer burner cap 42 along the radial direction of the burner 100. The flame transmission channel 423 is provided to solve the problem of flame transmission from the inner ring combustion section 1 to the middle ring combustion section 2.

[0149] Specifically, such as Figure 4 As shown, in this embodiment, the opening of the ignition channel 423 on the first surface 42a is located between the flame hole 2a of the middle ring combustion section 2 and the flame hole 3a of the outer ring combustion section 3. This allows the ignition of the inner ring combustion section 1 to simultaneously ignite the middle ring combustion section 2 and the outer ring combustion section 3, while preventing the gas in the outer ring combustion section 3 from igniting first, while the gas in the middle ring combustion section 2 remains ignited. In this situation, a large amount of unignited gas accumulates in the middle ring combustion section 2, while the flame in the outer ring combustion section 3 has already begun to burn. The large-scale flame of the outer ring combustion section 3 can easily ignite the gas in the middle ring combustion section 2, leading to deflagration.

[0150] like Figure 4 As shown, in order to improve the consumption capacity of secondary air A at the flame hole 2a of the middle ring combustion section 2 when the outer ring combustion section 3 is opened, and to better utilize the opening of the outer ring combustion section 3 to control the flame temperature of the middle ring combustion section 2, the setting angle of the flame hole 2a of the middle ring combustion section 2 falls within the range of the setting angle of the flame hole 3a of the outer ring combustion section 3 on the circumference centered on the axis of the multi-ring burner 100. This ensures that the secondary air flowing radially Y toward the flame hole 2a of the middle ring combustion section 2 can be covered by the flame hole 3a of the outer ring combustion section 3, so that the secondary air is consumed by the flame 3b of the outer ring combustion section 3.

[0151] Along the circumferential direction X of the burner 100, the flame holes 2a of the middle ring combustion section 2 and the flame holes 3a of the outer ring combustion section 3 are evenly distributed on the first surface 42a. Specifically, in this embodiment, the flame holes 3a of the outer ring combustion section 3 are in the form of annular grooves, which can cover a larger circumferential area compared to other single-hole flame holes, so as to better consume the secondary air flowing towards the middle ring combustion section 2 and achieve effective control of the flame temperature of the middle ring combustion section 2. At the same time, the groove-shaped flame holes have a faster ignition speed than circular flame holes, so that the flame holes of the outer ring combustion section 3 can still achieve rapid ignition even when the circumference of the arrangement of the flame holes is relatively longer than that of the middle ring combustion section 2.

[0152] In addition, choosing an annular groove as the flame hole form of the outer ring combustion section 3 has better combustion stability compared to other single-hole flame holes, due to the relatively large opening area, the initial velocity of the gas flow is lower, the amount of air entrained is limited.

[0153] In addition, such as Figure 6 As shown, in order for the flame 3b of the outer ring combustion section 3 to better cover the secondary air A flowing radially Y toward the flame hole 2a of the middle ring combustion section 2, the tip of the flame 3b of the flame hole 3a of the outer ring combustion section 3 should be higher than the flame hole 2a of the middle ring combustion section 2. Taking this embodiment as an example, the flame hole 3a of the outer ring combustion section 3 includes two annular grooves, wherein the tip of the flame 3b of the relatively higher annular groove should be higher than the flame hole 2a of the middle ring combustion section 2, so as to consume the secondary air A more effectively.

[0154] The specific methods to ensure that the tip of the flame 3b of the outer ring combustion section 3 is higher than the flame hole 2a of the middle ring combustion section 2 are varied. For example, the angle of the flame hole 3a of the outer ring combustion section 3 can be changed and adjusted so that the flame hole 3a is positioned as high as possible. Alternatively, the gas supply of the outer ring combustion section 3 can be changed and adjusted to increase the length of the flame 3b. Or, the position of the flame hole 3a of the outer ring combustion section 3 on the first surface 42a can be changed and adjusted so that the flame hole 3a of the outer ring combustion section 3 is relatively close to the flame hole 2a of the middle ring combustion section 2, so that the tip of the flame 3b of the outer ring combustion section 3 is higher than the flame hole 2a of the middle ring combustion section 2. This allows for better consumption of air flowing towards the root of the flame 2b of the middle ring combustion section 2, thus achieving effective control of the flame temperature of the middle ring combustion section 2.

[0155] like Figure 8 As shown, in this embodiment, the diameter of the flame hole 2a of the middle ring combustion section 2 is D. Along the radial direction Y of the burner 100, the minimum distance between the center of the flame hole 2a of the middle ring combustion section 2 and the center of the flame hole 3a of the outer ring combustion section 3 is L1, and the value of L1 ranges from 5D to 7.5D. Simultaneously, along the axial direction Z of the burner 100, the minimum distance between the flame hole 2a of the middle ring combustion section 2 and the flame hole 3a of the outer ring combustion section 3 is L2, and the value of L2 ranges from 2.5D to 3.5D.

[0156] By controlling the spacing L1 and L2 between the flame holes 2a of the middle ring combustion section 2 and the flame holes 3a of the outer ring combustion section 3 along the radial direction Y and axial direction Z of the burner 100, the problem of poor flame transmission between the flame holes 2a of the middle ring combustion section 2 and the flame holes 3a of the outer ring combustion section 3 caused by excessive spacing is avoided. Also, the problem of insufficient flame 3b of the outer ring combustion section 3 failing to effectively consume the secondary air A flowing to the middle ring combustion section 2 due to excessive spacing, and thus failing to effectively reduce the flame temperature of the middle ring combustion section 2 through combustion in the outer ring combustion section 3 is avoided.

[0157] At the same time, the spacing L1 and L2 are controlled to avoid the flame 2b of the middle ring combustion section 2 and the flame 3b of the outer ring combustion section 3 from interfering with each other due to the spacing being too small.

[0158] like Figure 9 As shown, the angle α1 between the flame hole 2a of the middle ring combustion section 2 and the horizontal plane is α1, and the value of α1 ranges from 25° to 40°. This angle range ensures that the flame 2b of the middle ring combustion section 2 faces upwards and outwards. Specifically, by controlling the angle α1 between the flame hole 2a of the middle ring combustion section 2 and the horizontal plane, the lower limit of α1 is set to 25° to prevent the flame hole 2a of the middle ring combustion section 2 from tilting too far towards the outer ring combustion section 3, which would cause interference between the flames of the middle ring combustion section 2 and the outer ring combustion section 3, resulting in incomplete combustion and low energy efficiency. Simultaneously, by controlling the angle α1 between the flame hole 2a of the middle ring combustion section 2 and the horizontal plane, the upper limit of α1 is set to 40° to prevent the flame 2b of the middle ring combustion section 2 from being too vertical and unable to effectively heat the bottom of the pot.

[0159] The angle between the flame hole 2a of the middle ring combustion section 2 and the first surface 42a is α2, with α2 ranging from 55° to 80°. This angle range ensures that the flame 2b of the middle ring combustion section 2 faces upwards and outwards. Specifically, by controlling the angle α2 between the flame hole 2a of the middle ring combustion section 2 and the first surface 42a of the flame cap to be within the range of 55° to 80°, air preheated on the flame cap surface can replenish the root region of the flame 2b in the middle ring combustion section 2. If the angle α2 is too small, the planar airflow will not flow smoothly to the flame root, resulting in insufficient secondary air supply at that location. Conversely, if the angle α2 is too large, the preheating effect on the air will be poor.

[0160] like Figure 10 As shown, the angle between the flame hole 3a of the outer ring combustion section 3 and the horizontal plane is β1, and the value of β1 ranges from 20° to 30°. This angle range ensures that the flame 3b of the outer ring combustion section 3 faces upwards and outwards. Specifically, by controlling the angle β1 between the flame hole 3a of the outer ring combustion section 3 and the horizontal plane, the lower limit of β1 is set to 20° to prevent the flame hole 3a of the outer ring combustion section 3 from tilting too far towards the middle ring combustion section 2, which would cause interference between the flames of the middle ring combustion section 2 and the outer ring combustion section 3, resulting in incomplete combustion and low energy efficiency. Simultaneously, by controlling the angle β1 between the flame hole 3a of the outer ring combustion section 3 and the horizontal plane, the upper limit of β1 is set to 30° to prevent the flame hole 3a of the outer ring combustion section 3 from having an excessively large elevation angle, which would interfere with the flames of the middle ring combustion section 2, leading to incomplete combustion and low energy efficiency.

[0161] The angle between the flame hole 3a of the outer ring combustion section 3 and the first surface 42a is β2, and the value of β2 ranges from 55° to 75°. By setting this angle range, the flame 3b of the outer ring combustion section 3 is directed upward and outward. Specifically, by controlling the angle β2 between the flame hole 3a of the outer ring combustion section 3 and the first surface 42a of the flame cap to be within the range of 55° to 75°, the air, after being preheated on the surface of the flame cap, can be replenished to the root region of the flame 3b of the outer ring combustion section 3. If the angle β2 is too small, the planar airflow will not be able to flow, while if the angle β2 is too large, the preheating effect on the air will be poor.

[0162] Based on this, the first surface 42a of the outer burner cap 42 has an inclination angle of 30° to 40° relative to the horizontal plane. This inclination range allows the flame holes 3a of the outer ring combustion section 3, located on the outer side, to supplement the flame holes 2a of the middle ring combustion section 2, which are located on the inner side, with air flowing radially inward and preheated by the flame holes 3a. This results in more complete combustion in the middle ring combustion section 2. Specifically, by controlling the range of the inclination angle to prevent it from being too small, a certain height difference exists between the middle ring combustion section 2 and the outer ring combustion section 3 on the first surface 42a. This prolongs the preheating time of the secondary air by the outer ring combustion section 3, improving combustion efficiency. Simultaneously, it increases the vertical spacing between the middle ring combustion section 2 and the outer ring combustion section 3, reducing the mutual influence between them while maintaining the overall diameter of the burner head.

[0163] This embodiment also provides a gas control method for a burner to avoid the problems of knocking or deflagration during use for various multi-ring burners, including the burner 100 described above. Specifically, the gas control method addresses the problem of deflagration during use from two dimensions: ignition control of the outer ring combustion section 3 (transferring flame to the outer ring combustion section 3 to ignite it), and ignition control of the middle ring combustion section 2 and the outer ring combustion section 3 (shutting off the flame).

[0164] Specifically, addressing the issue of knocking noises that easily occur when the middle ring combustion section 2 and the outer ring combustion section 3 are shut off, the gas control method of this burner includes the following steps: Upon receiving an instruction to shut off the gas supply to the middle ring combustion section 2 and the outer ring combustion section 3, the gas supply to the outer ring combustion section 3 is shut off first, followed by the gas supply to the middle ring combustion section 2. This avoids a sudden drop in gas pressure in the middle ring combustion section 2 after it is shut off first, causing the lean gas to recede into the cavity due to pressure. Simultaneously, the adjacent outer ring combustion section 3 remains in combustion, meaning a high-temperature ignition source exists outside the middle ring combustion section 2, continuously heating the area near the burner holes of the middle ring combustion section 2, igniting unburned gas, causing explosive backfire, and producing knocking noises and abnormal sounds, affecting the user experience. However, if the outer ring combustion section 3 is shut off first as in this solution, the flame of the middle ring combustion section 2 cannot heat the burner holes of the outer ring combustion section 3, failing to ignite the unburned gas and preventing knocking noises.

[0165] Specifically, to address the issue of deflagration that easily occurs when the outer ring combustion section 3 is switched on (the flame is transferred to the outer ring combustion section 3 to ignite it), the gas control method of this burner includes the following steps: Before the outer ring combustion section 3 is turned on, the middle ring combustion section 2 is not at the maximum gas supply position. That is, the gas supply of the middle ring combustion section 2 can be reduced first, but not too much. It needs to be enough to keep the middle ring combustion section 2 in a burning state. Then, the outer ring combustion section 3 is turned on, so that the flame of the middle ring combustion section 2 is difficult to heat the flame hole of the outer ring combustion section 3, so as to avoid the unignited gas in the outer ring combustion section 3 being ignited by the flame of the relatively high-positioned middle ring combustion section 2, resulting in deflagration at the outer ring combustion section 3.

[0166] Furthermore, such as Figure 11 As shown, the gas control method for this burner specifically includes the following steps:

[0167] Regarding the step of first shutting off the gas supply to the outer ring combustion unit 3 and then shutting off the gas supply to the middle ring combustion unit 2 after receiving the instruction to shut off the gas supply to the middle ring combustion unit 2, upon receiving the instruction to shut off the gas supply to the middle ring combustion unit 2, the status of the outer ring combustion unit 3 is obtained. If the outer ring combustion unit 3 is in a combustion state, the instruction to shut off the gas supply to the middle ring combustion unit 2 is terminated. If the outer ring combustion unit 3 is not in a combustion state, the instruction to shut off the gas supply to the middle ring combustion unit 2 is executed.

[0168] This solution identifies whether the outer ring combustion section 3 is in a combustion state before shutting down the middle ring combustion section 2, and determines whether to shut down the middle ring combustion section 2 based on the combustion state of the outer ring combustion section 3, effectively avoiding the occurrence of knocking sounds at the middle ring combustion section 2.

[0169] Specifically, if the gas supply to the middle ring combustion chamber 2 is shut off, the gas pressure in the middle ring combustion chamber 2 will suddenly drop, causing the lean gas to retract into the cavity due to the pressure. At the same time, if the adjacent and lower outer ring combustion chamber 3 is still burning, it is equivalent to having a high-temperature ignition source below and to the side of the middle ring combustion chamber 2. The flame 3b of the outer ring combustion chamber 3 is located below the flame hole 2a of the middle ring combustion chamber 2, and continuously heats the flame hole 2a of the middle ring combustion chamber 2, which will cause an explosive backfire, producing popping and abnormal noises, affecting the user experience.

[0170] The determination of whether to close the middle ring combustion section 2 based on the combustion state of the outer ring combustion section 3 can be implemented in various ways on the burner 100. For example, the combustion state of the outer ring combustion section 3 can be detected by setting a sensor (such as a temperature sensor or thermocouple) and sent to the control module. The control module controls the gas valve 8 to maintain or cut off the gas supply to the middle ring combustion section 2 based on the data obtained by the sensor. In this case, the control module inside the gas stove receives and processes the command to close the gas supply to the middle ring combustion section 2. Alternatively, it can be achieved by adjusting the internal closing structure of the gas valve 8 through purely mechanical means. In this case, the gas valve 8 inside the gas stove receives and processes the command to close the gas supply to the middle ring combustion section 2. Specific implementation methods can be existing technologies, and therefore will not be elaborated here.

[0171] A preferred control scheme, such as Figure 12 As shown, the gas control method of this burner can reduce the gas supply to the middle ring combustion section 2 after terminating the command to shut off the gas supply to the middle ring combustion section 2. Specifically, upon receiving the command to shut off the gas supply to the middle ring combustion section 2, the state of the outer ring combustion section 3 is obtained. If the outer ring combustion section 3 is in combustion, the gas supply to the middle ring combustion section 2 is reduced. Compared to not adjusting the gas supply to the middle ring combustion section 2, reducing the gas supply to the middle ring combustion section 2 based on the condition that the outer ring combustion section 3 remains in combustion after receiving the command to shut off the gas supply to the middle ring combustion section 2 effectively avoids the popping sound caused by shutting off the middle ring combustion section 2 while the outer ring combustion section 3 is burning, and also meets the user's firepower adjustment needs by reducing the flame of the middle ring combustion section 2.

[0172] Another preferred control scheme, such as Figure 13As shown, the gas control method of this burner, after terminating the command to shut off the gas supply to the middle ring combustion section 2, first shuts off the gas supply to the outer ring combustion section 3, and then shuts off the gas supply to the middle ring combustion section 2. That is, upon receiving the command to shut off the gas supply to the middle ring combustion section 2, the state of the outer ring combustion section 3 is obtained. If the outer ring combustion section 3 is in combustion, its gas supply is shut off first, and then the gas supply to the middle ring combustion section 2 is shut off. Compared to not adjusting the gas supply to the middle ring combustion section 2, shutting off the outer ring combustion section 3 first, based on the assumption that the outer ring combustion section 3 is still in combustion, after receiving the command to shut off the gas supply to the middle ring combustion section 2, satisfies the user's adjustment needs for shutting off the middle ring combustion section 2, and avoids producing popping and abnormal noises at the middle ring combustion section 2.

[0173] Of course, in other embodiments, this gas control scheme for the middle ring combustion section 2 and the outer ring combustion section 3 can also be implemented for other multi-ring burners. For example, for a four-ring burner, the gas control method can be applied to the outermost third and fourth ring combustion sections to effectively avoid popping and abnormal noises caused by the fourth ring combustion section still burning when the third ring combustion section is turned off.

[0174] In addition, the dimensions of the distance between the flame holes 2a of the middle ring combustion section 2 and the flame holes 3a of the outer ring combustion section 3 (i.e., the minimum distance L1 and L2) are also further limited. For example Figure 8 As shown, the diameter of the fire hole 2a of the middle ring combustion section 2 is D, the minimum spacing L1 along the radial direction Y ranges from 5D to 7.5D, and the minimum spacing L2 along the axial direction Z ranges from 2.5D to 3.5D.

[0175] If the horizontal distance (minimum spacing L1) between the middle ring combustion section 2 and the outer ring combustion section 3 is less than 5 times the aperture D of the burner hole 2a of the middle ring combustion section 2, and the vertical distance (minimum spacing L2) is less than 2.5 times the aperture D of the burner hole 2a of the middle ring combustion section 2, the aforementioned interference problem will occur. Simultaneously, the flame of the outer ring combustion section 3 will affect the shape of the flame of the middle ring combustion section 2, resulting in insufficient combustion and excessively blurred flame. If the horizontal distance (minimum spacing L1) between the middle ring combustion section 2 and the outer ring combustion section 3 is greater than 7.5 times the aperture D of the burner hole 2a of the middle ring combustion section 2, and the vertical distance (minimum spacing L2) is greater than 3.5 times the aperture D of the burner hole 2a of the middle ring combustion section 2, the flame of the middle ring combustion section 2 cannot be effectively transmitted to the outer ring combustion section 3. As the supply to the outer ring combustion section 3 gradually increases, it cannot ignite under a small gas output, resulting in a situation where the outer ring combustion section 3 outputs gas but does not ignite, posing a safety hazard.

[0176] Furthermore, the gas control scheme provided in this embodiment can also be applied to burners in which the middle ring combustion section 2 and the outer ring combustion section 3 are respectively set in different burner caps, so as to avoid combustion explosion when the outer ring combustion section 3 is ignited, and to avoid explosion during the ignition-off process of the middle ring combustion section 2 and the outer ring combustion section 3.

[0177] Specifically, when the middle and outer ring combustion sections are located under different burner caps, if the burner holes of the middle ring combustion section are relatively higher than those of the outer ring combustion section, and there is space for gas flow along the shortest path connecting the burner holes of the middle ring combustion section and the outer ring combustion section, then the middle and outer ring combustion sections may affect each other, and the remaining gas at the burner holes of the middle ring combustion section may flow obliquely downwards to the outer ring combustion section. The gas control scheme provided in this solution effectively avoids mutual interference between the two combustion sections and prevents detonation or knocking by controlling the opening and closing sequence or flame intensity of the middle and outer ring combustion sections respectively during the flameout stages of the outer ring combustion section 3 and the flameout stages of the middle and outer ring combustion sections 2 and 3.

[0178] For example, in other implementation schemes, such as Figure 14 and Figure 15 As shown, the burner cap may include an inner burner cap 41, a middle burner cap 43, and an outer burner cap 42. The middle ring combustion section 2 and the outer ring combustion section 3 are respectively disposed on the middle burner cap 43 and the outer burner cap 42, rather than being integrated on the same burner cap as in this embodiment. Specifically, in this case, the flame holes 2a of the middle ring combustion section 2 are disposed on the relatively outwardly inclined surface of the middle burner cap 43, and the flame holes 3a of the outer ring combustion section 3 are disposed on the relatively outwardly inclined surface of the outer burner cap 42. The flame holes 2a of the middle ring combustion section 2 are relatively higher than the flame holes 3a of the outer ring combustion section 3, so that when the outer ring combustion section 3 is ignited, it is easily ignited by the flame of the middle ring combustion section 2, resulting in detonation. Furthermore, when the middle ring combustion section 2 is turned off, the remaining gas in the middle ring combustion section 2 is easily ignited by the flame of the outer ring combustion section 3, resulting in detonation. The gas control scheme provided in this embodiment effectively avoids mutual interference between the two separately set combustion sections by controlling the opening and closing sequence or fire intensity of the middle ring combustion section and the outer ring combustion section respectively during the flame-off and flame-out stages, thus preventing deflagration or knocking.

[0179] For another example, in other implementation schemes, the flame holes of the middle ring combustion section 2 and the outer ring combustion section 3 can also have different orientations; specifically, they can be arranged facing each other. For example... Figure 16As shown, the flame holes 2a of the middle ring combustion section 2 on the middle burner cap 43 are obliquely outward, while the flame holes 3a of the outer ring combustion section 3 on the outer burner cap 42 are obliquely inward, meaning the flame holes of the two burners are facing each other. In this arrangement, the flame holes and flames of the two burners can influence each other, leading to deflagration or knocking during operation. Specifically, because the flame holes 2a of the middle ring combustion section 2 are relatively higher than the flame holes 3a of the outer ring combustion section 3, the outer ring combustion section 3 is easily affected by the flame of the middle ring combustion section 2 during ignition, resulting in deflagration. Furthermore, when the middle ring combustion section 2 is turned off, the remaining gas in the middle ring combustion section 2 is easily ignited by the flame of the outer ring combustion section 3, producing knocking. The gas control scheme provided in this embodiment effectively avoids mutual influence between the two separately arranged combustion sections and prevents deflagration or knocking by controlling the opening and closing sequence or flame intensity of the middle ring combustion section and the outer ring combustion section respectively during the ignition-cutting and ignition-off stages.

[0180] Example 2

[0181] This embodiment further optimizes the gas supply process based on the gas control method of the burner provided in Embodiment 1, and controls the gas supply to meet diverse cooking needs such as concentrated high heat and large area high heat for multi-ring burners.

[0182] Specifically, taking the three-ring burner 100 provided in Example 1 as an example, the gas control method of this burner specifically includes:

[0183] After the outer ring combustion section 3 is turned on, the gas supply of the middle ring combustion section 2 is controlled so that the gas supply of the middle ring combustion section 2 decreases as the gas supply of the outer ring combustion section 3 increases.

[0184] This gas control method can meet diverse cooking needs, such as concentrated high heat and large-area high heat, of multi-ring burners. Specifically, because the total load of the burner has an extreme value requirement, when the gas supply to the outer ring combustion section 3 (located relatively on the outside) increases, the gas supply to the middle ring combustion section 2 (located on the inside) is correspondingly reduced. This ensures that, without exceeding the total load limit of the burner, the heat load of the outer ring combustion section 3 can be relatively larger, meeting the cooking needs for large-area high heat. Simultaneously, after the outer ring combustion section 3 is closed, the sum of the heat loads of the middle ring combustion section 2 and the inner ring combustion section 1 is less than the extreme value requirement of the burner's total load. This ensures that the three-ring burner 100 maintains a large heat range regardless of whether the inner ring combustion section 1 and the middle ring combustion section 2 are on, or whether all three are on, thus meeting cooking requirements.

[0185] The scheme of adjusting the gas supply of the middle ring combustion section 2 based on the gas supply of the outer ring combustion section 3 can be implemented in various ways on the burner. For example, a sensor (e.g., a flow sensor) can be installed inside the gas valve 8 to detect the gas supply of the outer ring combustion section 3 and send it to the control module. The control module then controls the gas valve 8 to adjust the gas supply of the middle ring combustion section 2 based on the data obtained from the sensor. In this case, the control module inside the gas stove is the object that adjusts the gas supply of the middle ring combustion section 2 based on the condition of the outer ring combustion section 3. Alternatively, it can be achieved through purely mechanical structural adjustments, such as setting the closing structure inside the gas valve 8. Specifically, the supply can be adjusted by changing the size of the opening / slot of the closing element inside the gas valve 8. This allows the gas supply of the middle ring combustion section 2 to decrease when the outer ring combustion section 3 is opened by rotating the closing element, or the gas supply of the middle ring combustion section 2 to decrease continuously as the gas supply of the outer ring combustion section 3 increases by rotating the closing element. This achieves reasonable gas distribution, enabling high firepower while avoiding overloading the total load of the burner. At this point, the adjustment of the gas supply to the middle ring combustion unit 2 based on the condition of the outer ring combustion unit 3 is made to the gas valve 8 inside the gas stove, specifically the shut-off valve 8. Since the specific means of implementation can be found in existing technology, they will not be elaborated upon here.

[0186] Specifically, this embodiment provides a preferred gas control scheme, which controls the gas flow in the inner ring combustion section 1, the middle ring combustion section 2 and the outer ring combustion section 3 of the three-ring burner 100, so that the burner 100 can achieve concentrated high heat and large area high heat cooking states respectively, to meet the diverse cooking needs of users.

[0187] Specifically, taking the heat load of a household gas stove burner as an example, the maximum firepower required by national standards should be less than or equal to 5.23KW. For a three-ring burner, in the current technology, in order to avoid the heat load exceeding the national standard when all three rings are fully open, the gas supply distribution of the gas valve supplying gas to the burner is designed according to the principle that the maximum supply of the inner ring burner + the maximum supply of the middle ring burner + the maximum supply of the outer ring burner should be less than or equal to 5.23KW. This results in insufficient heat load provided by the burner when the inner and middle ring burners are open, which cannot meet the demand for stir-frying.

[0188] When the inner, middle, and outer ring combustion sections are activated simultaneously, although the total load can meet the requirements for stir-frying, the flame from the outer ring combustion section cannot effectively transfer heat to the food in the center of the pan, resulting in wasted heat. Furthermore, heating a large frying pan can lead to uneven heating, causing localized overheating in the central area.

[0189] To address the aforementioned issues, specifically, the rotation angle distribution of the gas valve 8's gas knob in this embodiment is as follows: Figure 17 As shown, the gas valve 8 used in this embodiment is a segment valve, which can stop at 0°, 45°, 65°, 90°, 135°, 175°, 210°, 235°, 260° and 285° respectively, so as to divide the gas knob into nine segments based on the rotation angle, so as to facilitate the user's precise gas control operation.

[0190] The 0°–135° range is the concentrated heating zone, while the 135°–175° range is the large-area heating zone. After 175°, the outer ring combustion section 3 and the middle ring combustion section 2 are closed sequentially to meet the heating requirements of the small flame. The gas supply of each combustion section at each stage is shown in the table below:

[0191]

[0192]

[0193] Specifically, when the user rotates the gas knob, the gas valve 8, driven by the gas knob, moves from the zero point ( Figure 17 The oscillator begins to rotate from 0° to 0°, and then rotates into the concentrated heating zone. Figure 17 At 0°~135°, the inner ring combustion section 1 and the middle ring combustion section 2 are in section 1 ( Figure 17 The gas knob is turned on at 45° (in the middle), and the outer ring combustion section 3 is not turned on. As the gas knob continues to rotate, it will turn to position 2 in sequence. Figure 17 (65°) and 3 segments ( Figure 17 At 90° (in the middle), the gas supply to both the inner ring combustion section 1 and the middle ring combustion section 2 gradually increases from a small gas flow to a large gas flow. Specifically, when the gas knob is rotated to position 3 (…),… Figure 17 When the flame is at 90°, the inner ring combustion section 1 and the middle ring combustion section 2 are both high-volume combustion sections. The gas supply of both rings reaches its maximum value. Users can stir-fry with both rings on, which meets the user's need for concentrated high heat and avoids the situation in the current technology where the burner must be in the state of three rings on for stir-frying, and the heat provided by the outer ring is wasted.

[0194] When the gas knob is rotated to position 4, it moves from the concentrated heating zone to the large-area heating zone. Figure 17When the temperature reaches 135°C, the outer ring combustion section 3 activates and directly switches to its maximum gas supply. Simultaneously, the gas supply to the middle ring combustion section 2 decreases, becoming a medium gas flow. With the three-ring burner activated, users can cook with large-sized pans, satisfying the need for large-area heating without causing localized overheating due to excessive heat load at the inner ring combustion section 1 and the middle ring combustion section 2. Therefore, this gas control method can achieve both concentrated high heat (3 levels) and large-area high heat (4 levels) states, while ensuring the total load does not exceed the limit, to adapt to the user's actual cooking needs.

[0195] In other words, when the gas knob is rotated to position 3, the sum of the high airflow in the inner ring combustion section 1 and the high airflow in the middle ring combustion section 2 does not exceed the total load of the burner 100 (i.e., Figure 18 (The dotted line in the diagram). Simultaneously, when the gas knob is rotated to position 4, the combined airflow of the inner ring combustion section 1 (high airflow), the middle ring combustion section 2 (medium airflow), and the outer ring combustion section 3 (high airflow) does not exceed the total load of the burner 100. In this situation, by reducing the gas supply to the middle ring combustion section 2 when switching to position 4, the heat load of the middle ring combustion section 2 is reduced, ensuring that the burner 100's total load approaches but does not exceed it in both positions 3 and 4. This solves the problem in the current technology where the burner's heat load is insufficient when only the inner ring combustion section 1 and the middle ring combustion section 2 (i.e., position 3) are activated, failing to meet the demands of stir-frying. This allows the burner to achieve its "high-fire" state when the gas valve 8 is switched to positions 3 and 4. By achieving a "dual-stage fire" state, the heat load when the inner and middle rings of the three-ring burner 100 are open, as well as when the inner, middle, and outer rings are open, can approach but not exceed the total load of the burner 100, thus meeting the user's needs for concentrated high heat and large-area high-heat cooking.

[0196] In other words, as the user rotates the gas control knob within the concentrated heating zone, the gas supply to both the inner ring combustion section 1 and the middle ring combustion section 2 gradually increases to meet the user's demand for concentrated high-heat cooking. Conversely, as the user rotates the gas control knob from the concentrated heating zone to the large-area heating zone, the outer ring combustion section 3 activates while the gas supply to the middle ring combustion section 2 decreases. This allows the system to switch to a large-area, high-heat state without exceeding the burner's total load, thus satisfying the user's cooking needs.

[0197] Specifically, this embodiment further provides a preferred gas control scheme, such as... Figure 18 As shown, by adjusting the position of the orifice of the gas valve 8, the maximum gas supply of the gas valve 8 to the three-ring burner in the dual-ring opening mode (i.e., the inner ring combustion section 1 and the middle ring combustion section 2 are open, and the outer ring combustion section 3 is closed) is actually greater than that in the three-ring opening mode (i.e., the inner ring combustion section 1 and the middle ring combustion section 2 are open, and the outer ring combustion section 3 is closed). With both the outer ring combustion section 2 and the outer ring combustion section 3 open, the maximum gas supply is achieved, enabling the three-ring combustion chamber to reach its maximum capacity. The burner can achieve a "dual-stage fire" mode, simultaneously When the three-ring burner is in dual-ring mode, the heat load meets the high heat demand for concentrated stir-frying. In triple-ring mode, the total heat load will not be too large, thus meeting the user's temperature uniformity requirements when using large-sized cookware for large-area heating.

[0198] Meanwhile, in the gas rotation direction of gas valve 8, the maximum gas supply corresponding to the dual-ring opening mode of the burner is located at position 3, and the maximum gas supply corresponding to the triple-ring opening mode is located at position 4. These two gas positions are arranged adjacently to avoid the separation of the two maximum gas supply positions as in other designs, which could cause large fluctuations in gas flow when switching positions, leading to problems such as deflagration. Furthermore, the two extreme flame positions are adjacent, and the high and medium flames in each combustion section also gradually transition adjacently, making it more convenient for users to switch positions and adjust the flame intensity.

[0199] Furthermore, after the gas knob is rotated from the centralized heating zone to position 4 ( Figure 17 After 135°, as the gas knob continues to rotate, the middle ring combustion chamber 2 remains open, and the gas supply to the outer ring combustion chamber 3 gradually decreases. Specifically, the outer ring combustion chamber 3 at position 5 ( Figure 17 At 175°, the airflow becomes moderate, and at stage 7, it becomes zero. It can be seen that in the outer ring combustion section 3, from stage 5 to stage 6... Figure 17 During the process of the gas supply (210°) gradually decreasing and eventually reaching zero, the middle ring combustion chamber 2 remains open to avoid knocking or abnormal noises at the middle ring combustion chamber 2. Specifically, at stage 5, the middle ring combustion chamber 2 has a small airflow, while at stage 6, it has a medium airflow.

[0200] After that, at stage 6, that is, after the gas supply to the outer ring combustion section 3 is zero, the middle ring combustion section 2 at stage 7 ( Figure 17 (235°) to 9th position ( Figure 17 The gas supply at 285° gradually decreases to meet users' cooking needs for different heat levels by reducing the heat output of the middle ring combustion section 2. Simultaneously, from level 7 to level 9, the gas supply to the inner ring combustion section 1 gradually decreases, changing from a medium airflow to a low airflow. Finally, at level 9, both the outer ring combustion section 3 and the middle ring combustion section 2 are closed, with only the inner ring combustion section 1 open and maintaining a low airflow. Specifically, the level angle of the gas valve 8 provided in this embodiment, the gas outlet logic of each combustion section, and the total heat output are shown in the table below:

[0201] 1 45° Inner Ring Road + Middle Ring Road 2 65° Inner Ring Road + Middle Ring Road 3 90° Fire: Inner Ring Road + Middle Ring Road 4 135° Fire: Inner Ring Road + Middle Ring Road + Outer Ring Road 5 175° Medium fire: Inner ring + Middle ring + Outer ring 6 210° Medium Fire: Inner Ring + Middle Ring 7 235° Inner Ring Road, Middle Ring Road 8 260° Inner Ring Road 9 285° Inner Ring Road

[0202] Furthermore, the relationship between the position angle of the gas valve 8 in this embodiment, the number of ventilation rings of the three-ring burner 100, and the gas supply to each combustion section is shown in the following table:

[0203]

[0204]

[0205] Among them, the gas valve 8 supplies the maximum gas to the three-ring burner 100 at 90°, resulting in a total load of approximately 5000W for the three-ring burner. However, at this time, only the inner ring combustion section 1 and the middle ring combustion section 2 are open. Figure 15 As shown, during the process of turning the gas knob of gas valve 8 from 90° to 135°, the gas supply to the middle ring combustion section 2 decreases rapidly, with B3 > B4. This ensures that even at 135°, the outer ring combustion section 3 is also open, and the total gas supply to the three rings is less than the total gas supply to the two rings at 90°. At 135°, the total burner load is around 4500W. By reducing the gas supply to the middle ring combustion section 2 when switching to 135°, it is possible to prevent unignited gas from being ignited by the flame of the middle ring combustion section 2 during the flameout process of the outer ring combustion section 3, thus avoiding deflagration.

[0206] In addition, in this embodiment, in order to ensure that the gas supply of the gas valve 8 to the burner can be in the maximum gas supply state in the dual ring fire mode, it is necessary to strictly control the orifice size of the shut-off valve 8 at B3 and B4, so that the orifice size of the shut-off valve at B4 is much smaller than the orifice size at B3.

[0207] It should be noted that the degree of change in gas supply in each combustion section of the gas valve 8 provided in this embodiment from section 1 to section 9, and the so-called "small airflow," "medium airflow," and "large airflow" are only relative relationships of the gas supply changes in the gas passage of each individual combustion section. The values ​​of "small airflow," "medium airflow," and "large airflow" are not the same between the gas passages of different combustion sections.

[0208] Taking this embodiment as an example, in the case of a three-channel three-ring burner 100, the gas supply of the middle ring combustion section 2, i.e., the middle ring channel, is usually larger than that of the inner ring combustion section 1 and the outer ring combustion section 3. Specifically, the "high airflow" of the middle ring channel of the middle ring combustion section 2 is greater than that of the inner ring combustion section 1 and the outer ring combustion section 3; the "medium airflow" of the middle ring channel of the middle ring combustion section 2 is greater than that of the inner ring combustion section 1 and the outer ring combustion section 3; and the "low airflow" of the middle ring channel of the middle ring combustion section 2 is greater than that of the inner ring combustion section 1 and the outer ring combustion section 3. This is because the heating area of ​​the middle ring combustion section 2 is larger than that of the inner ring combustion section 1, and its usage frequency is higher than that of the outer ring combustion section 3. Of course, this is only one gas distribution scheme in this embodiment. In other embodiments, especially in multi-ring burners different from three-ring burners, other gas distribution schemes can also be adopted to simultaneously meet the different cooking needs of users for concentrated high heat and large-area high heat.

[0209] During the rotation of the gas knob, the gas is distributed according to the aforementioned gas supply scheme. This can be achieved in various ways on the burner. It can be implemented using a traditional mechanical structure by adjusting the opening position of the gas valve 8's gate. Alternatively, a control module can be used to electrically control the opening of the solenoid valves in each gas channel based on the rotation angle of the gas knob, thereby adjusting the gas supply. Specific implementation methods can utilize existing technologies, and therefore will not be elaborated upon here.

[0210] Example 3

[0211] This embodiment also provides a gas control method for a burner, which is also used to realize the gas distribution of different combustion sections of the burner. The main difference between this method and the gas control method for the burner provided in Embodiment 2 is the difference in the gas supply at different angles of the gas knob.

[0212] Similar to Example 2, the gas knob operates in a concentrated heating range of 0°–135°, while the range of 135°–175° is a large-area heating range. Unlike Example 2, as shown in… Figure 19 As shown in the table below, the gas supply amount for each combustion chamber's corresponding gas passage at each stage is as follows:

[0213]

[0214] Among them, corresponding to the table, Figure 19The circles at each endpoint of the broken line represent the opening status of each combustion section at the current angle. The central point corresponds to the inner ring combustion section 1, with sizes ranging from smallest to largest corresponding to the "small airflow," "medium airflow," and "large airflow" of the inner ring channel, respectively. The circles outside the central point correspond to the middle ring combustion section 2, with sizes ranging from smallest to largest corresponding to the "small airflow," "medium airflow," and "large airflow" of the middle ring channel, respectively. If this circle is not displayed, it corresponds to "no airflow" in the middle ring channel of the middle ring combustion section 2. The outermost circle corresponds to the outer ring combustion section 3, with sizes ranging from smallest to largest corresponding to the "medium airflow" and "large airflow" of the outer ring channel, respectively. If this circle is not displayed, it corresponds to "no airflow" in the outer ring channel of the outer ring combustion section 3.

[0215] From the table above and Figure 19 As can be seen, the gas control method of the burner in this embodiment can also form large flame 1 (concentrated high firepower) and large flame 2 (large area high firepower) at the 3rd stage (90°) and 4th stage (135°). The main difference is that in this embodiment, at the 4th stage, the gas supply of the inner ring combustion section 1 is switched to medium airflow, while the gas supply of the middle ring combustion section 2 is switched to low airflow, so that the total load of the burner at the 3rd stage is slightly higher than the total load at the 4th stage.

[0216] Taking specific values ​​as an example: In this embodiment, the total load of the burner is limited to 5000W. When the gas knob is rotated to position 3 at 90°, the heat load of the inner ring combustion section 1 under the large airflow condition is 1700W, and the heat load of the middle ring combustion section 2 under the large airflow condition is 3300W. The total heat load is 5000W, thus limiting the total load of the burner.

[0217] Within the 90°–110° range, the airflow in the middle ring combustion section 2 decreases sharply to a low airflow state. Within the 110°–35° range, the airflow in the middle ring combustion section 2 remains relatively stable, maintaining a low airflow state. As for the outer ring combustion section 3, within the 90°–110° range, the outer ring combustion section 3 maintains a no-airflow state. Within the 110°–125° range, the airflow in the outer ring combustion section 3 increases sharply to a high airflow state, and remains in a high airflow state within the 125°–135° range.

[0218] Therefore, when the gas knob is rotated to position 4 (135°), the heat load of the inner ring combustion section 1 under medium airflow conditions is 1600W, the heat load of the middle ring combustion section 2 under low airflow conditions is 1400W, and the heat load of the outer ring combustion section 3 under high airflow conditions is 1100W. The total load is 4100W, lower than the 5000W when the dual-ring is turned on at 90°, which meets the needs of users when using large-sized cookware. Even cooking Heat requirements should be considered to prevent localized overheating of the cookware.

[0219] Regarding the selection of the heat load for the outer ring combustion section 3, the current embodiment provides a heat load of 1100W under high airflow conditions, which is significantly lower than the heat load selection for the middle ring combustion section 2 (3300W under high airflow conditions). This is because if the heat load of the outer ring combustion section 3 is too high, during the process of rotating from the concentrated heating zone to the large-area heating zone, even if the gas supply of the middle ring combustion section is reduced, the total load of the burner may fluctuate with the opening of the outer ring combustion section 3, making it impossible to change relatively smoothly. At the same time, it is also prone to detonation. Of course, the heat load of the outer ring combustion section 3 cannot be too low either, to avoid flame transmission problems, that is, the outer ring combustion section 3 is open and gas is being produced but not ignited.

[0220] It should be clearly stated that the gas control method of the burner provided in Embodiments 2 and 3 is only for illustrative purposes. In other embodiments, this scheme can also be applied to other non-triple-ring burners. At the same time, this scheme can also be implemented in the gas valve 8 in the form of a non-stage valve to achieve the same cooking requirements of both concentrated high heat and large area high heat.

[0221] While specific embodiments of the present invention have been described above, those skilled in the art should understand that these are merely illustrative examples, and the scope of protection of the present invention is defined by the appended claims. Those skilled in the art can make various changes or modifications to these embodiments without departing from the principles and essence of the present invention, but all such changes and modifications fall within the scope of protection of the present invention.

Claims

1. A method for controlling the gas flow of a burner, characterized in that, The burner has a first combustion section and a second combustion section disposed on a flame cap, wherein the flame holes of the first combustion section and the second combustion section are arranged sequentially from the inside to the outside along the radial direction of the burner, and the gas control method of the burner includes: Upon receiving an instruction to shut off the gas supply to both the first and second combustion sections, the gas supply to the second combustion section is shut off first, followed by the gas supply to the first combustion section. Furthermore, upon receiving the instruction to activate the gas supply to the second combustion chamber, the first combustion chamber is not in the position of maximum gas supply before the second combustion chamber is activated.

2. The gas control method for the burner as described in claim 1, characterized in that, The step of first shutting off the gas supply to the second combustion unit and then shutting off the gas supply to the first combustion unit after receiving the instruction to shut off the gas supply to the first combustion unit specifically includes: Upon receiving an instruction to shut off the gas supply to the first combustion chamber, the system first obtains the status of the second combustion chamber. If the second combustion chamber is in a combustion state, the instruction to shut off the gas supply to the first combustion chamber is terminated.

3. The gas control method for the burner as described in claim 2, characterized in that, After terminating the instruction to shut off the gas supply to the first combustion chamber, reduce the gas supply to the first combustion chamber; Alternatively, after terminating the instruction to shut off the gas supply to the first combustion chamber, the gas supply to the second combustion chamber may be shut off first, followed by the shutdown of the gas supply to the first combustion chamber.

4. The gas control method for a burner as described in claim 1, characterized in that, The step of first reducing the gas supply of the first combustion unit to a level sufficient to maintain combustion after receiving the instruction to start the gas supply of the second combustion unit specifically includes: after the second combustion unit is started, controlling the gas supply of the first combustion unit so that the gas supply of the first combustion unit decreases as the gas supply of the second combustion unit increases.

5. The gas control method for a burner as described in claim 1, characterized in that, The burner is a multi-ring burner, the first combustion section is a middle ring combustion section, the second combustion section is an outer ring combustion section, and the multi-ring burner also has an inner ring combustion section. The multi-ring burner, along the ignition direction of the gas knob, sequentially includes a concentrated heating zone and a large-area heating zone starting from 0°. The gas control method for the burner further includes: When the gas knob is rotated from 0° to the centralized heating zone, the inner ring combustion section and the middle ring combustion section are turned on, while the outer ring combustion section is turned off. As the gas knob continues to rotate, the gas supply of the inner ring combustion section and the middle ring combustion section gradually increases. When the gas knob is rotated from the centralized heating zone to the large-area heating zone, the outer ring combustion section is turned on and switched to the maximum gas supply, while the gas supply of the middle ring combustion section is reduced.

6. The gas control method for a burner as described in claim 5, characterized in that, The gas control method for the burner also includes: As the gas knob rotates from the concentrated heating zone to the large-area heating zone, the gas supply to the outer ring combustion zone gradually decreases and eventually shuts off as the gas knob continues to rotate, keeping the middle ring combustion section open.

7. The gas control method for a burner as described in claim 6, characterized in that, The gas control method for the burner also includes: After the gas supply in the middle ring combustion section reaches zero, the gas supply in the inner ring combustion section gradually decreases.

8. The gas control method for the burner as described in claim 5, characterized in that, The maximum heat load of the middle ring combustion section is greater than the maximum heat load of the outer ring combustion section.

9. The gas control method for a burner as described in claim 1, characterized in that, The burner cap has an annular first surface. Along the radial direction of the burner, the inner annular edge of the first surface is higher than the outer annular edge of the first surface, and the flame holes of the first combustion section and / or the flame holes of the second combustion section are formed on the first surface.

10. The gas control method for a burner as described in claim 9, characterized in that, The flame holes of the first combustion section and the second combustion section are both formed on the first surface, and the inclination angle of the first surface of the flame cap relative to the horizontal plane is in the range of 30°~40°.

11. The gas control method for a burner according to any one of claims 1-10, characterized in that, The diameter of the flame hole in the first combustion section is defined as D; Along the radial direction of the burner, the minimum distance between the center of the flame hole of the first combustion section and the center of the flame hole of the second combustion section is defined as L1, and the value of L1 ranges from 5D to 7.5D. Along the axial direction of the burner, the minimum distance between the center of the flame hole of the first combustion section and the center of the flame hole of the second combustion section is defined as L2, and the value of L2 is in the range of 2.5D~3.5D.

12. The gas control method for a burner according to any one of claims 1-10, characterized in that, The flame holes of the first combustion section are positioned higher than those of the second combustion section; And / or, the burner is a multi-ring burner, and the second combustion section is the outermost combustion section of the multi-ring burner.

13. The gas control method for a burner according to any one of claims 1-8, characterized in that, The structural arrangement of the first combustion section and the second combustion section relative to the flame cap is one of the following: (1) The flame holes of the first combustion part and the flame holes of the second combustion part are both provided on the same flame cap, and the flame holes of the first combustion part and the flame holes of the second combustion part have the same orientation and are both outward; (2) The flame cap includes a first flame cap and a second flame cap that are respectively separated. The flame hole of the first combustion part is disposed on the first flame cap, and the flame hole of the second combustion part is disposed on the second flame cap. The flame holes of the first combustion part and the flame holes of the second combustion part have the same orientation and both face outward. (3) The flame cap includes a first flame cap and a second flame cap that are arranged separately from each other. The flame hole of the first combustion part is arranged on the first flame cap, and the flame hole of the second combustion part is arranged on the second flame cap. The flame holes of the first combustion part and the flame holes of the second combustion part have different orientations and are arranged opposite to each other.

14. A multi-ring burner, characterized in that, It employs the gas control method for a burner as described in any one of claims 1-12, wherein the flame holes of the first combustion section and the flame holes of the second combustion section of the multi-ring burner have the same orientation and are both arranged outwards.

15. The multi-ring burner as described in claim 14, characterized in that, The flame cap of the multi-ring burner has an annular first surface. Along the radial direction of the multi-ring burner, the inner ring edge of the first surface is higher than the outer ring edge of the first surface. The flame holes of the first combustion part and the flame holes of the second combustion part are formed sequentially from the inside to the outside along the radial direction of the multi-ring burner on the first surface.

16. The multi-ring burner as described in claim 15, characterized in that, The multi-ring burner also has an inner ring combustion section, and the flame cover includes an inner flame cover and an outer flame cover arranged concentrically. The flame holes of the inner ring combustion section are disposed on the inner flame cover, and the flame holes of the first combustion section and the flame holes of the second combustion section are disposed on the first surface of the outer flame cover.

17. The multi-ring burner as described in claim 14, characterized in that, The flame cap of the multi-ring burner includes a first flame cap and a second flame cap arranged concentrically. The first flame cap has an annular first surface. Along the radial direction of the multi-ring burner, the inner ring edge of the first surface is higher than the outer ring edge of the first surface, and the flame holes of the first combustion section are formed on the first surface. The second burner cap has an annular second surface. Along the radial direction of the multi-ring burner, the inner ring edge of the second surface is higher than the outer ring edge of the second surface, and the flame holes of the second combustion section are formed on the second surface.

18. The multi-ring burner as described in claim 17, characterized in that, The multi-ring burner also has an inner ring combustion section. The flame cover includes an inner flame cover, a middle flame cover, and an outer flame cover arranged concentrically. The flame holes of the inner ring combustion section are disposed on the inner flame cover. The flame holes of the first combustion section are disposed on the first surface of the middle flame cover. The flame holes of the second combustion section are disposed on the second surface of the outer flame cover.

19. The multi-ring burner as described in claim 16 or 18, characterized in that, The multi-ring burner has a secondary air supply channel, the end of which extends upward to the outer periphery of the inner burner cap. The flame hole of the first combustion part is positioned below the inner ring edge of the burner cap where the flame hole of the first combustion part is located.

20. The multi-ring burner as described in claim 16, characterized in that, A flame transmission channel is provided on the flame cap, and the flame transmission channel penetrates the outer flame cap radially along the multi-ring burner.

21. The multi-ring burner as described in claim 20, characterized in that, The opening of the ignition channel on the first surface is located between the flame holes of the first combustion section and the flame holes of the second combustion section.

22. The multi-ring burner according to any one of claims 15-18, characterized in that, On the circumference centered on the axis of the multi-ring burner, the setting angle of the flame holes of the second combustion section covers the flame holes of the first combustion section; And / or, along the circumferential direction of the multi-ring burner, the flame holes of the first combustion section are evenly distributed on the first surface; And / or, along the circumferential direction of the multi-ring burner, the flame holes of the second combustion section are evenly distributed on the first surface.

23. The multi-ring burner according to any one of claims 15-18, characterized in that, The angle between the flame hole of the first combustion section and the horizontal plane is defined as α1, and the value of α1 ranges from 25° to 40°. And / or, define the angle between the flame hole of the first combustion part and the first surface as α2, where the value of α2 ranges from 55° to 80°; And / or, define the angle between the flame hole of the second combustion section and the horizontal plane as β1, where the value of β1 ranges from 20° to 30°; And / or, define the angle between the flame hole of the second combustion section and the first surface as β2, where β2 ranges from 55° to 75°.

24. A multi-ring burner, characterized in that, It employs the gas control method for a burner as described in any one of claims 1-13, wherein the flame holes of the first combustion section and the flame holes of the second combustion section of the multi-ring burner have different orientations and are arranged opposite to each other.

25. The multi-ring burner as described in claim 24, characterized in that, The flame cap of the multi-ring burner includes a first flame cap and a second flame cap arranged concentrically. The first flame cap has an annular first surface. Along the radial direction of the multi-ring burner, the inner ring edge of the first surface is higher than the outer ring edge of the first surface, and the flame holes of the first combustion section are formed on the first surface. The second burner cap has an annular second surface. Along the radial direction of the multi-ring burner, the inner ring edge of the second surface is lower than the outer ring edge of the second surface, and the flame holes of the second combustion section are formed on the second surface.

26. The multi-ring burner as described in claim 25, characterized in that, The multi-ring burner also has an inner ring combustion section. The flame cover includes an inner flame cover, a middle flame cover, and an outer flame cover arranged concentrically. The flame holes of the inner ring combustion section are disposed on the inner flame cover. The flame holes of the first combustion section are disposed on the first surface of the middle flame cover. The flame holes of the second combustion section are disposed on the second surface of the outer flame cover.

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