JP7100963B2 - Stove - Google Patents

Description

The present invention relates to a control burner that mixes fuel gas and combustion air in a mixing passage and burns the generated mixed gas.

A stove burner that burns a mixed gas of fuel gas and combustion air is widely used. This burner is directed toward the burner head in which multiple flame ports for burning the mixed gas are formed, the burner body on which the burner head is placed, the mixing passage connected to the burner body, and the opening end of the mixing passage. It is equipped with a gas injection nozzle that injects fuel gas. The inside of the mixing passage has a Venturi shape in which the cross-sectional area gradually decreases from the opening end toward the burner body and then gradually increases, and the fuel gas is formed from the gas injection nozzle toward the opening end of the mixing passage. When the fuel gas is injected, the fuel gas flows into the mixing passage from the open end while entraining the surrounding air. Then, the fuel gas and the combustion air are mixed in the mixing passage to generate a mixed gas. As described above, since the inside of the mixing passage is formed in a ventilated shape, the flow velocity of the fuel gas and the combustion air increases once when passing through the mixing passage and then decreases, so that the fuel gas and the combustion air are used. Mixing with air is promoted. The mixed gas thus generated in the mixing passage is supplied to the burner head via the burner body and flows out from a plurality of flame openings provided in the burner head. By igniting the mixed gas, a flame is formed around the burner head and the mixed gas is burned.

Further, in recent years, it has been required to increase the combustion thermal power without increasing the size of the stove burner. In order to increase the combustion thermal power, it is necessary to increase the maximum flow rate of the fuel gas injected from the gas injection nozzle and also increase the flow rate of the combustion air flowing into the mixing passage together with the fuel gas. Therefore, by making various measures such as enlarging the inflow port of the damper plate attached to the open end of the mixing passage and securing a space around the gas injection nozzle, the fuel ejected from the gas injection nozzle is used. A conroburner has been proposed in which the gas can efficiently entrain the surrounding air (Patent Document 1, Patent Document 2, etc.).

Japanese Unexamined Patent Publication No. 2013-120020 Japanese Unexamined Patent Publication No. 2016-023817

However, if the size of the stove burner remains the same, even if the maximum flow rate of the fuel gas and the maximum flow rate of the combustion air are increased, the flame formed around the burner head becomes uneven at the maximum thermal power. was there.

The present invention has been made in response to the above-mentioned problems of the prior art, and it is possible to increase the maximum thermal power without increasing the size of the stove burner, and it is possible to increase the maximum thermal power around the burner head. It is an object of the present invention to provide a stove burner in which a uniform flame is formed.

In order to solve the above-mentioned problems, the stove burner of the present invention adopts the following configuration. That is,
In a conroburner in which a mixed gas, which is a mixture of fuel gas and combustion air, is guided to a burner head having multiple flame openings and burned.
A mixing passage that mixes the fuel gas and the combustion air to generate the mixed gas,
A damper plate attached to the open end of the mixing passage and having an inlet smaller than the open end.
A gas injection nozzle that injects the fuel gas from the outside of the inflow port toward the inside of the mixing passage,
Along with the connection of the mixing passage, the burner head is mounted and provided with a burner body for supplying the mixed gas flowing from the mixing passage to the burner head.
The mixing passage includes a straight pipe portion in which the inner diameter of the passage is maintained within a predetermined distance range from the opening end, a reduced diameter portion in which the inner diameter of the passage is reduced from the straight pipe portion toward the burner body, and the reduced diameter portion. It is formed in a venturi shape having an enlarged diameter portion whose inner diameter of the passage is expanded from the portion toward the burner body.
The damper plate is
A portion around the inflow port is formed in a tapered shape whose diameter is reduced toward the mixing passage side, and the end of the tapered shape is the inflow port.
The end of the tapered shape is attached to the mixing passage in a state where it enters the mixing passage from the opening end within a distance shorter than half the length of the straight pipe portion. It is characterized by that.

In the stove burner of the present invention, the mixing passage is formed in the following Venturi shape. First, a predetermined distance range from the opening end is a straight pipe portion in which the inner diameter of the passage is maintained, and from the straight pipe portion, the inner diameter of the passage is reduced toward the burner body. The diameter-reduced portion has a Venturi shape in which an enlarged diameter portion is formed in which the inner diameter of the passage is expanded toward the burner body. Further, a damper plate is attached to the open end of the mixing passage, and the damper plate is provided with an inflow port smaller than the open end. The portion around the inflow port is formed in a tapered shape that reduces in diameter toward the mixing passage side, and the end of the tapered shape is the inflow port. Then, the damper plate is in a state where the end of the tapered shape (that is, the inflow port) enters the mixing passage from the open end within a distance shorter than half the length of the straight pipe portion. It is attached to the open end of the mixing passage.

By doing so, the flow of air that tries to flow into the mixing passage from the inflow port becomes smooth, so that the flow rate of the air flowing into the mixing passage can be increased without increasing the inflow port. In addition, the damper plate is in a position where the tapered end (ie, the inlet) is within a distance shorter than half the length of the straight pipe and enters the mixing passage from the open end. It is attached to the open end of the mixing passage. Further, since the straight pipe portion at the open end is formed larger than the inflow port at the end of the tapered shape, the tapered portion protrudes into the wide space inside the straight pipe portion at the open end. become. As a result, the flow of air and fuel gas toward the inflow port is accelerated at the tapered portion of the damper plate, and then when it flows out from the inflow port, it flows out into a wide space inside the straight pipe portion, and the air And as a result of the rapid expansion of the fuel gas flow in the radial direction, it decelerates sharply. After the fuel gas and combustion air are mixed to some extent by the acceleration in this tapered part and the rapid deceleration after flowing out from the inflow port, the fuel gas and the combustion air pass through the reduced diameter part from the straight pipe part in the mixing passage. Further, the mixing is further promoted by increasing the speed again when the speed is increased and then decelerating again when passing from the reduced diameter portion to the enlarged diameter portion. As a result, even if the flow rates of the fuel gas and combustion air flowing in from the inflow port increase, they can be sufficiently mixed in the mixing passage, so that a uniform flame is formed around the burner head. It is possible to increase the maximum firepower of the stove burner while maintaining the condition.

Further, as described above, in the stove burner of the present invention in which the periphery of the inflow port is formed in a tapered shape, the tapered shape around the inflow port may be changed to the following shape with respect to the Venturi shape of the mixing passage. good. First, the venturi shape of the mixed passage is such that the inner diameter of the passage is reduced from the opening end side toward the burner body side, and then the inner diameter of the passage is expanded with a smaller inclination than the inner diameter of the passage is reduced. The tapered portion formed around the inlet of the damper plate has the same inclination as the inclination of the venturi shape of the mixing passage toward the burner body side from the end end side, or a large inclination. You may do so.

The smaller the inclination of the tapered shape formed around the inlet of the damper plate, the larger the inlet becomes into the mixing passage, and the distance from the inlet to the Venturi-shaped part in the mixing passage. Cannot be secured. On the other hand, if the inclination of the taper shape is the same as or larger than the inclination of the part where the inner diameter of the passage is reduced from the opening end side to the burner body side in the Venturi shape, the slope from the inflow port to the Venturi shape is set. The distance can be secured. Therefore, the fuel gas and combustion air flowing in from the inflow port can be mixed to some extent until they reach the venturi-shaped portion of the mixing passage. Therefore, in the venturi-shaped portion of the mixing passage, the fuel gas and combustion are used. It is possible to mix well with air.

It is a vertical sectional view which shows the structure of the stove burner 10 of this Example. It is a perspective view which shows the mode that the damper plate 16 is attached to the stove burner 10 of this Example. It is sectional drawing which shows the appearance that the inner diameter of the inlet of a damper plate 16 was enlarged in order to increase the maximum thermal power of a stove burner 10. It is explanatory drawing of the reason why the mixing of fuel gas and combustion air in a mixing passage 11 becomes insufficient when the inflow port 26o is enlarged by the conventional damper plate 26. It is explanatory drawing which showed the cross-sectional shape of the damper plate 16 of this Example. In the damper plate 16 of this embodiment, it is explanatory drawing which showed the reason why the mixing of a mixed gas does not deteriorate even if the maximum thermal power of a stove burner 10 is increased. It is explanatory drawing which showed the cross-sectional shape of the damper plate 16 of the 1st modification. It is explanatory drawing which showed the cross-sectional shape of the damper plate 16 of the 2nd modification.

FIG. 1 is a cross-sectional view showing the structure of a gas stove 1 equipped with the temperature detection device 100 of this embodiment. The gas stove 1 is provided by covering the upper surface of the stove body (not shown) and facing the top plate 3 having the burner opening 3a and the burner opening 3a, and burning the fuel gas. It is equipped with a stove burner 10 that heats a cooking container, and a trivet 5 on which a cooking container such as a pot is placed. Further, the gap between the stove burner 10 and the burner opening 3a is closed by the annular burner ring 4.

The stove burner 10 includes a burner body 12 formed in an annular shape, a mixing passage 11 connected to the burner body 12, an annular burner head 13 mounted on the upper surface of the burner body 12, and the like. There is. The burner head 13 is formed by forging or die casting with an aluminum alloy, brass, or the like, and a plurality of grooves (flame mouth grooves) are formed on the lower surface side of the outer peripheral portion. Then, when the burner head 13 is placed on the burner body 12, a plurality of flame openings 13a are formed between the plurality of flame opening grooves formed in the burner head 13 and the upper surface of the burner body 12. Further, a sheet metal burner cap 14 formed in an annular shape is attached to the upper portion of the burner body 12, and a temperature sensor 15 is projected from the center of the burner cap 14. The temperature sensor 15 is urged upward by a spring (not shown), and when the cooking container is placed on the trivet 5, it comes into contact with the bottom surface of the cooking container and detects the temperature of the cooking container.

One end of the mixing passage 11 is connected to the burner body 12, but the other end is an open end 11o. The shape of the mixing passage 11 is a Venturi shape in which the inner diameter of the passage is maintained up to a predetermined distance from the opening end 11o toward the burner body 12, but after that, the inner diameter of the passage is reduced and then the diameter is expanded. .. The venturi shape has an inclination in which the inner diameter of the passage expands (that is, an increase in the inner diameter of the passage per unit length) rather than an inclination in which the inner diameter of the passage decreases (that is, a decrease in the inner diameter of the passage per unit length). The amount) is formed in a smaller shape. In the following, the portion where the inner diameter of the passage is maintained within a predetermined range from the opening end 11o of the mixing passage 11 is referred to as a straight pipe portion 11a, and the inner diameter of the passage is reduced from the opening end 11o toward the burner body 12. The portion where the diameter is increased may be referred to as a reduced diameter portion 11b, and the portion where the inner diameter of the passage is expanded may be referred to as a diameter expanded portion 11c. Further, the reduced diameter portion 11b and the expanded diameter portion 11c of the mixing passage 11 may be collectively referred to as a Venturi-shaped portion.

Further, a damper plate 16 having an inflow port 16o formed in the center is attached to the open end 11o of the mixing passage 11. A gas injection nozzle 18 for injecting fuel gas toward the inflow port 16o of the damper plate 16 is provided on the outside of the damper plate 16. The fuel gas injected from the gas injection nozzle 18 flows into the mixing passage 11 from the inflow port 16o of the damper plate 16 while entraining the surrounding air. Then, when passing through the venturi-shaped portions (diameter-reduced portion 11b and diameter-expanded portion 11c) of the mixing passage 11, the fuel gas and air are mixed to generate a mixed gas, which flows into the burner body 12 and then flows into the burner body 12. It flows out from the flame port 13a of the burner head 13. Combustion of the stove burner 10 is started by igniting this mixed gas with a spark plug (not shown).

FIG. 2 is a perspective view showing the shape of the damper plate 16 attached to the open end 11o of the mixing passage 11. As shown, the damper plate 16 comprises a short cylindrical body portion 16a and an annular flange portion 16b formed by bending one end side of the body portion 16a inward. An inflow port 16o is formed in the center of the flange portion 16b. Further, a reduced diameter portion 16c having a tapered shape toward the body portion 16a is formed in the peripheral portion of the inflow port 16o. The damper plate 16 having such a shape is attached to the open end 11o of the mixing passage 11 so that the body portion 16a of the damper plate 16 covers the straight pipe portion 11a of the mixing passage 11.

As shown in FIG. 2, the damper plate 16 of the present embodiment is provided at a position where the inflow port 16o has entered the body portion 16a side, and a reduced diameter portion 16c is provided around the inflow port 16o. It is formed. The reason why the damper plate 16 of this embodiment has such a shape is that it is becoming difficult to increase the maximum thermal power of the stove burner 10 by the method of increasing the inflow port 16o of the damper plate 16, and it is no longer the limit. This is because it is. The reason for this will be described in detail below.

As shown in FIG. 3, in the stove burner 10 provided with the conventional damper plate 26, it is generally practiced to increase the maximum thermal power by increasing the inflow port 26o formed in the center of the damper plate 26. It has been broken. FIG. 3A shows the cross-sectional shape of the conventional damper plate 26. As shown in the figure, the conventional damper plate 26 also has a cylindrical body portion 26a and an annular flange portion 26b, like the damper plate 16 of the present embodiment, and has a center of the flange portion 26b. An inflow port 26o is formed in the port. However, unlike the damper plate 16 of the present embodiment shown in FIG. 2, the inflow port 26o is provided at the surface position of the flange portion 26b, and the reduced diameter portion 16c is provided around the inflow port 26o. do not have.

Further, FIG. 3A conceptually shows how the fuel gas and the combustion air are mixed to generate the mixed gas in the mixing passage 11 to which the conventional damper plate 26 is attached. Has been done. First, the fuel gas is injected from the gas injection nozzle 18 provided on the outside of the damper plate 26 toward the inflow port 26o, as shown by the solid arrow in the figure. Then, the surrounding air also flows in from the inflow port 26o so as to be involved in the flow of the fuel gas. The dashed arrow shown in the figure represents the flow of air. Further, the fuel gas and air that have flowed in from the inflow port 26o are mixed by speeding up once at the diameter-reduced portion 11b of the mixing passage 11 and then decelerating at the diameter-expanding portion 11c (see FIG. 1). ) Is supplied. The dashed line arrow shown in the figure represents the flow of fuel gas and air flowing in the mixing passage 11.

As shown by the broken line arrow in FIG. 3A, the flow rate of the air flowing into the mixing passage 11 is limited by the inflow port 26o of the damper plate 26. Therefore, even if the flow rate of the fuel gas injected from the gas injection nozzle 18 is increased in an attempt to increase the maximum thermal power of the stove burner 10, the flow rate of air cannot be increased by the amount corresponding to the increase. Therefore, conventionally, the flow rate of air has been increased by increasing the inner diameter D0 of the inflow port 26o of the damper plate 26. As shown in FIG. 3B, if the damper plate 26 is changed to one having an inner diameter D0 of the inlet 26o having a larger inner diameter D1, the air flowing in from the inlet 26o can be increased, so that the fuel gas can be increased. The flow rate of air can be increased as the flow rate of the air increases. However, as a result of repeatedly increasing the maximum thermal power using such a method, in recent years, when trying to increase the maximum thermal power, the flame formed on the burner head 13 becomes non-uniform. There was a limit to increasing the maximum firepower. It has been considered that the reason why such a limit occurs is that the following unavoidable phenomenon occurs.

First, if the mixing passage 11 is the same, the flow rate in the mixing passage 11 increases as the flow rates of the fuel gas and air are increased. Then, the time until the fuel gas and air flowing in from the inflow port 26o pass through the mixing passage 11 and reach the burner body 12 (see FIG. 1) is shortened. As a result, the time required for the fuel gas and the combustion air to be mixed in the mixing passage 11 cannot be secured, and the fuel gas flows into the burner body 12 with insufficient mixing, and the burner head 13 is charged. The concentration of the mixed gas flowing out varies among the plurality of flame openings 13a formed. Therefore, it has been considered that the flame formed on the burner head 13 becomes non-uniform. Of course, if the inner diameter of the mixing passage 11 is increased, the flow velocity in the mixing passage 11 decreases, so that it is possible to secure the time required for mixing even at the maximum thermal power, but this time, at the time of medium thermal power. Alternatively, the flow velocity at the time of low thermal power becomes too low, and it becomes difficult to mix the fuel gas and the combustion air in the mixing passage 11. Therefore, the maximum thermal power of the stove burner 10 is limited to some extent by the length of the mixing passage 11, and the maximum thermal power of the stove burner 10 may be increased by a method such as increasing the inflow port 26o of the damper plate 26. However, it has been considered that there is a limit.

However, the inventors of the present application have found that the reason why the mixing becomes insufficient when the inflow port 26o of the damper plate 26 is increased is not because the time required for mixing cannot be secured, but for another reason. .. The damper plate 16 of this embodiment has been completed based on such new findings. By using the damper plate 16 of this embodiment, it is possible to increase the flow rates of the fuel gas and the combustion air without deteriorating the mixing in the mixing passage 11, and further increase the maximum thermal power of the stove burner 10. Will be. Therefore, first, a new finding found by the inventors of the present application, that is, the reason why the mixing becomes insufficient when the inflow port 26o of the damper plate 26 is increased, and then the damper plate of the present embodiment will be described. The reason why it is possible to increase the flow rate of the fuel gas and the combustion air without deteriorating the mixing in the mixing passage 11 will be described by using 16.

FIG. 4 is an explanatory diagram showing a mechanism in which the mixture of the fuel gas and the combustion air becomes insufficient when the inflow port 26o is enlarged by the conventional damper plate 26. FIG. 4A shows the flow of air flowing in from the inflow port 26o when the inflow port 26o is enlarged. Further, as a reference, FIG. 4B shows the flow of air flowing in from the inflow port 26o before the inflow port 26o is enlarged.

As is clear from a comparison between FIGS. 4 (a) and 4 (b), when the inflow port 26o is increased, a large difference occurs in the air flow after flowing in from the inflow port 26o. That is, in the state of FIG. 4B before the inflow port 26o is enlarged, the air flowing in from the inflow port 26o has a flow that spreads in the radial direction at the straight pipe portion 11a of the mixing passage 11. On the other hand, in the state of FIG. 4A after enlarging the inflow port 26o, the air flowing in from the inflow port 26o flows along the straight pipe portion 11a of the mixing passage 11 in the radial direction. There is no flow that spreads to the air.

Here, focusing on the air flow in FIG. 4B, the air flowing in from the inflow port 26o is once throttled at the inflow port 26o to increase the flow velocity, and then in the radial direction at the straight pipe portion 11a of the mixing passage 11. It spreads and the flow velocity decreases. This movement in which the flow velocity increases or decreases is just a movement in which the fuel gas and the combustion air accelerate and then decelerate in the venturi-shaped portion (that is, the diameter reduction portion 11b and the diameter expansion portion 11c) of the mixing passage 11 to mix. Is the same as. From this, it is considered that in the state of FIG. 4B before the inflow port 26o is enlarged, the fuel gas and the combustion air are mixed even in the straight pipe portion 11a of the mixing passage 11.

On the other hand, in the state of FIG. 4A after increasing the inflow port 26o, the flow velocity when passing through the inflow port 26o does not increase due to the increase in the inflow port 26o, and further passes through the inflow port 26o. Since the flow that spreads in the radial direction does not occur even after this, the flow does not slow down. As a result, it is considered that the fuel gas and the combustion air are not mixed in the straight pipe portion 11a of the mixing passage 11. From this, the real reason why the mixture of the fuel gas and the combustion air was insufficient by increasing the inflow port 26o was not because the time passing through the mixing passage 11 was shortened, but the flow. It is considered that this is because the mixing in the straight pipe portion 11a of the mixing passage 11 does not proceed due to the enlargement of the inlet 26o. Conversely, if the amount of air flowing in from the inflow port 26o can be increased without obstructing the mixing in the straight pipe portion 11a of the mixing passage 11, even if the time passing through the mixing passage 11 is shortened. It is considered possible to sufficiently mix the fuel gas and the combustion air in the mixing passage 11. The damper plate 16 of this embodiment is completed by devising various methods based on such an idea.

FIG. 5A is an explanatory view showing a detailed cross-sectional shape of the damper plate 16 of this embodiment. Further, FIG. 5B also shows, for reference, the cross-sectional shape of the conventional damper plate 26 before the inflow port 26o is enlarged. As is clear from comparing FIGS. 5 (a) and 5 (b), in the damper plate 16 of this embodiment, the inflow port 16o is a mixing passage from the opening end 11o with respect to the conventional damper plate 26. It is formed at a position that enters the 11th side. A diameter-reduced portion 16c formed in a tapered shape toward the mixing passage 11 side is formed around the inflow port 16o. However, the size of the inflow port 16o is the same as the size of the inflow port 26o of the conventional damper plate 26. By doing so, the flow of air passing through the inflow port 16o becomes smooth, and it is considered possible to increase the flow rate of the air flowing in from the inflow port 16o without increasing the inflow port 16o. Further, since the size of the inflow port 16o is the same as the size of the inflow port 26o, it is considered possible to mix the fuel gas and the combustion air in the straight pipe portion 11a of the mixing passage 11.

FIG. 6 shows the damper plate 16 of the present embodiment shown in FIG. 5 (a) and the conventional damper plate 26 shown in FIG. 5 (b) (that is, the damper plate before increasing the size of the inflow port 26o). 26) is an explanatory diagram comparing the flow of air passing through the inflow port 16o or the inflow port 26o. Further, in FIGS. 6A and 6B, the flow of air passing through the inlet 16o and the inlet 26o is indicated by a broken line arrow, respectively. As shown in FIG. 6A, in the damper plate 16 of the present embodiment, since the tapered diameter-reduced portion 16c is formed around the inflow port 16o, the air flowing into the inflow port 16o is formed. The flow becomes smooth. As a result, the flow rate of the inflowing air can be increased as compared with the damper plate 26 before increasing the size of the inflow port 26o shown in FIG. 6 (b).

On the other hand, the size of the inflow port 16o is the same as the size of the inflow port 26o of the conventional damper plate 26 shown in FIG. 6 (b). Similar to the case of the damper plate 26, a flow spreading in the radial direction is generated in the straight pipe portion 11a of the mixing passage 11. That is, even in the damper plate 16 of this embodiment, the fuel gas and the combustion air are being mixed in the straight pipe portion 11a of the mixing passage 11. Furthermore, in the damper plate 16 of the present embodiment, although the size of the inflow port 16o is not larger than that of the conventional damper plate 26, the air flow rate increases, so that the air flow rate passes through the inflow port 16o. The flow velocity of the air is higher than that of the conventional damper plate 26. As a result, when passing through the inflow port 16o, the speed is greatly increased as compared with the case of the conventional damper plate 26, and even after passing, the speed is greatly reduced as compared with the case of the conventional damper plate 26. Mixing in the straight pipe portion 11a will be further promoted. As described above, when the damper plate 16 of the present embodiment is used, the fuel gas and the combustion air are mixed in the straight pipe portion 11a of the mixing passage 11 while increasing the flow rate of the air flowing in from the inflow port 16o. Can be promoted. As a result, it is possible to form a uniform flame around the burner head while increasing the maximum thermal power of the stove burner 10.

Further, as described above, the damper plate 16 of the present embodiment is a straight pipe by decelerating the increased air flow when passing through the inflow port 16o at the straight pipe portion 11a of the mixing passage 11. In part 11a, the fuel gas and the combustion air are mixed. Therefore, in order to mix the fuel gas and the combustion air, it is desirable that the length of the straight pipe portion 11a after flowing in from the inflow port 16o has a certain length. From this point of view, it is desirable that the damper plate 16 has the following shape.

First, as shown in FIG. 5A, the damper plate 16 of the present embodiment is provided at a position where the inflow port 16o has entered the inside of the mixing passage 11, but from the opening end 11o of the mixing passage 11. It is desirable that the distance LI at which the inflow port 16o enters the inside of the mixing passage 11 is shorter than half the length L of the straight pipe portion 11a of the mixing passage 11. Further, in FIG. 5A, it is assumed that a tapered diameter reduced portion 16c is formed around the inflow port 16o, but the inclination of this tapered shape (that is, the reduced diameter amount per unit length). The smaller the inclination, the more the inflow port 16o enters the inside of the mixing passage 11. Therefore, it is desirable that the inclination of the tapered shape of the reduced diameter portion 16c is about the same as the inclination of the reduced diameter portion 11b of the mixing passage 11 or larger than the inclination of the reduced diameter portion 11b.

The damper plate 16 of the present embodiment described above has some modifications. Hereinafter, these modified examples will be briefly described with a focus on the differences from the present embodiment.

In the above-described embodiment, the reduced diameter portion 16c formed around the inflow port 16o has been described as having a tapered shape. However, the shape of the reduced diameter portion 16c does not necessarily have to be a tapered shape as long as the diameter is reduced toward the mixing passage 11. For example, it is possible to use a rounded diameter-reduced portion 16c as shown in FIG. 7 (a) or an inverted round-shaped reduced diameter portion 16c as shown in FIG. 7 (b). Even in these cases, the flow of the inflowing air from the inflow port 16o becomes smooth, so that the flow rate of the inflowing air can be increased, and yet, after the inflow, a flow that spreads in the radial direction also occurs, so that the mixing passage is used. Mixing of fuel gas and combustion air can also be promoted in the straight pipe portion 11a of 11.

Further, in the above-described embodiment, it has been described that the inflow port 16o is provided at a position where the inflow port 16o has entered the inside of the mixing passage 11. However, if a diameter-reduced portion 16c whose diameter is reduced toward the mixing passage 11 can be provided around the inflow port 16o, the inflow port 16o is not necessarily provided at a position where the diameter is reduced to the inside of the mixing passage 11. There is no need. For example, as shown in FIG. 8 (a), the damper plate 16 may be such that the inflow port 16o is outside the mixing passage 11, or as shown in FIG. 8 (b), the above-mentioned. The damper plate 16 of the present embodiment may be attached so as to be slightly separated from the opening end 11o of the mixing passage 11 so that the inflow port 16o does not enter the inside of the mixing passage 11. Even in these cases, since the flow of the inflowing air from the inflow port 16o becomes smooth, the flow rate of the inflowing air can be increased, and yet the fuel gas and combustion are performed in the straight pipe portion 11a of the mixing passage 11. It is also possible to promote mixing with air.

Although the stove burner 10 of the present embodiment and the modified example has been described above, the present invention is not limited to the above-mentioned embodiment, and can be carried out in various embodiments without departing from the gist thereof.

1 ... Gas stove, 10 ... Stove burner, 11 ... Mixing passage,
11a ... straight pipe part, 11b ... reduced diameter part, 11c ... enlarged diameter part,
11o ... open end, 12 ... burner body, 13 ... burner head,
13a ... Flame mouth, 14 ... Burner cap, 15 ... Temperature sensor,
16 ... Damper plate, 16a ... Body, 16b ... Flange,
16c ... reduced diameter part, 16o ... inlet, 18 ... gas injection nozzle,
100 ... Temperature detector.

Claims (2)

In a conroburner in which a mixed gas, which is a mixture of fuel gas and combustion air, is guided to a burner head having multiple flame openings and burned.
A mixing passage that mixes the fuel gas and the combustion air to generate the mixed gas,
A damper plate attached to the open end of the mixing passage and having an inlet smaller than the open end.
A gas injection nozzle that injects the fuel gas from the outside of the inflow port toward the inside of the mixing passage,
Along with the connection of the mixing passage, the burner head is mounted and provided with a burner body for supplying the mixed gas flowing from the mixing passage to the burner head.
The mixing passage includes a straight pipe portion in which the inner diameter of the passage is maintained within a predetermined distance range from the opening end, a reduced diameter portion in which the inner diameter of the passage is reduced from the straight pipe portion toward the burner body, and the reduced diameter portion. It is formed in a venturi shape having an enlarged diameter portion whose inner diameter of the passage is expanded from the portion toward the burner body.
The damper plate is
A portion around the inflow port is formed in a tapered shape whose diameter is reduced toward the mixing passage side, and the end of the tapered shape is the inflow port.
The end of the tapered shape is attached to the mixing passage in a state where it enters the mixing passage from the opening end within a distance shorter than half the length of the straight pipe portion. A stove that features that. In the stove burner according to claim 1,
The venturi shape of the mixed passage has a shape in which the inner diameter of the passage is reduced from the opening end side toward the burner body side, and then the inner diameter of the passage is expanded with a smaller inclination than the inclination of the inner diameter of the passage. It has become
The inclination of the tapered portion of the damper plate around the inflow port is the same as or larger than the inclination of the venturi shape of the mixing passage to be reduced in diameter from the opening end side toward the burner body side. A stove burner characterized by being.

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