JPH1038226A - Combustion apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact combustion apparatus by improving a mixing method of fuel gas and air. SOLUTION: In a combustion apparatus 1 which utilizes a thick and thin fuel burner 1 which is constructed with a plurality of burner units 10, combustion primary air is sucked and mixed from a first suction hole by injecting fuel gas from a nozzle 11 to a thin side burner, and distributing mixture air to a thin side flame hole and a thick side flame hole whereby fuel gas sucked from the second suction inlet is injected to the thick side flame hole of the thick side burner. Thus, the mixed air is injected from the thin side flame hole and the thick side flame hole, and secondary air is supplied from the periphery of the thick side flame hole and is simultaneously combusted.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to suppress the generation of excess fuel mixture (rich mixture) and the excess air mixture (pale mixture) and was allowed simultaneous burning of nitrogen oxides (NO _X), the so-called gray It relates to a combustion device.

[0002]

Heretofore, thick and thin fuel combustion apparatus is known as one of the combustion device to reduce the NO _X. This device simultaneously ejects a rich mixture with a low air ratio (the ratio of the actual air amount to the theoretical air amount) from some of the multiple outlets, and a lean mixture with a high air ratio from the other outlets. And burn it.

For example, Japanese Patent Application Laid-Open No. Hei 6-3470013 discloses an integrated burner 60 on one side and a light mixing unit 70 on the other side with a central partition plate 75 interposed therebetween, as shown in FIG. Are disclosed in which burner units 80 formed side by side are arranged in parallel at intervals. The rich burner 60 sucks and mixes the fuel gas and the combustion air to blow out a rich air / fuel mixture having a low air ratio from the rich flame 63, and the light mixing unit 70 is provided adjacent to the rich flame 63. A light air-fuel mixture having a higher air ratio than the rich air-fuel mixture is ejected from the light-side flame port 73 thus obtained. As a result, a rich air-fuel mixture is blown out from the deep-side burner port 63 of each deep-side burner 60, and at the same time, a light-fuel mixture is blown out from the light-side burner port 73 between the deep-side burners 60 to perform rich-light combustion. Then, it is lack of oxygen at the base of the flame from the dark side flame hole 63, upward becomes oxygen-deficient by the exhaust gas of the flame from the light side flame hole 73 is produced of the NO _X is suppressed. On the other hand, in the light flame 76 from the light side flame port 73, since the fuel gas is lean, the flame temperature is lowered and the generation of NO _X is suppressed, and the low NO _X as a whole is achieved by a synergistic effect of these.
Moreover, since the light mixing unit 70 is formed integrally with the dark side burner 60, there is no need to individually arrange the light mixing units 70 between the dark side burners 60, and the arrangement interval of the dark side burners 60 is reduced. It was an excellent thing that it could be narrowed. Also, JP-A-7-42917 discloses that
As shown in FIG. 14, on both sides of the first burner port 6 of the first burner 5, a second burner 7 forming a second burner port 8 sandwiching the first burner port 6 is provided. Independent of one burner 5,
A gas inlet burner 100 provided above the inlet 3 of the first burner is provided with a common inlet 9 for sucking fuel gas and primary air and supplying the same to second burners 8 provided on both sides of the first burner 6. It is shown. The gas appliance burner 100 has a first flame port 6.
A leaner air-fuel mixture is ejected from the second flame port 8, and secondary air is supplied from around the second flame port 8 to perform rich-lean combustion.

[0004]

However, in the apparatus disclosed in Japanese Patent Application Laid-Open No. Hei 6-347003, the contact between each burner unit 80 and the secondary air is small. (Hereinafter referred to as λ _L )
Unavoidably had to be set to a higher value, and the good combustion range with respect to the fluctuation of the primary air ratio was narrow. For example, as shown in FIG.
C in flue gas against change in primary air ratio of lean mixture
When the change in O / CO ₂ is tested and graphed, the good combustion range is λ _L = 1.2 to 2.2 (CO / CO ₂ <0.00
5). Considering NO _X , λ _L > 1.8 (NO _X
<50 ppm). From these, λ _{L is set} to 18
The setting was set to 0% or more (1.8 <λ _L , λ _L = about 1.9). Therefore, λ _L was close to the combustion limit, and stable combustion could not be ensured due to slight fluctuations in the fuel gas composition, fuel gas amount, or combustion air amount. In the device disclosed in Japanese Patent Application Laid-Open No. 7-42917, secondary air is supplied to the second flame opening 8 to ensure stable combustion and easily adjust the air-fuel ratio of each burner. Since two inlets are provided, and the fuel gas and the primary air for combustion are supplied from the two inlets while being mixed, the mixing distance for sufficiently mixing has always been long. Therefore, the entire size (particularly, the width L shown in FIG. 14) cannot be made compact. An object of the present invention is to provide a compact combustion device which solves the above-mentioned problems, changes the setting of the primary air ratio to widen a good combustion range, and improves the method of mixing fuel gas and air to improve the combustion method. I do.

[0005]

According to a first aspect of the present invention, there is provided a combustion apparatus for sucking and mixing a fuel gas and a primary air for combustion to lean a lean air-fuel mixture having a stoichiometric air ratio or more. A light-side burner spouting from the side flame outlet, and a dense-side burner spouting a rich air-fuel mixture having a theoretical air ratio or less from the side flame outlet on both sides are integrally provided. In the combustion device for simultaneously burning the light side burner and the rich side burner while supplying the secondary air, the light side burner includes a first inlet for sucking the primary air for combustion and the fuel gas, A second suction port for inhaling only the primary air for combustion and a fuel gas from the first suction port to mix and distribute the air-fuel mixture to the light-side flame port and the rich-side flame port. While supplying the fuel gas, the fuel gas is sucked from the second suction port and ejected to the supply path to the rich side flame port. The gist of the door.

According to a second aspect of the present invention, in the combustion apparatus according to the first aspect, the total fuel gas amount (the sum of the fuel gas amount of the rich burner and the fuel gas amount of the light burner) is reduced. The fuel gas ratio of the rich side burner is 30 to
The ratio of the primary air amount of the rich burner to the theoretical air amount is set to 50 to 80%, the ratio of the primary air amount of the light burner to the theoretical air amount is set to 140 to 170%, and the theoretical air amount is set to 40%. The gist is that the ratio of the total amount of secondary air to the amount is set to 30 to 50%.

[0007] In the combustion apparatus according to the first aspect of the present invention having the above-described structure, rich burners are integrally formed on both sides of the light burners, and the air-fuel mixture having different air ratios from the burner opening of each burner. And ignite simultaneously. The light-side burner sucks and mixes the primary air for combustion and the fuel gas from the first suction port and distributes and supplies the air-fuel mixture to the light-side flame port and the rich-side flame port. The fuel gas is sucked from the mouth and is ejected to the supply path to the rich side flame outlet. The section from the second suction port to the supply path to the rich side flame port only needs to pass the fuel gas, and does not need to be mixed with air or the like. In other words, in the rich burner, fuel for increasing the concentration from the second suction port of the light burner is added to the air-fuel mixture mixed to some extent, so that the fuel passage section can be made as short as possible, and the whole can be made compact. .

In the combustion apparatus according to the second aspect of the present invention, the ratio of the fuel gas, the ratio of the primary air amount, and the ratio of the secondary air amount of the rich burner and the lean burner are set and adjusted in appropriate ranges. The combustion is stable, and the generation of harmful substances in the combustion exhaust gas is small.

[0009]

BEST MODE FOR CARRYING OUT THE INVENTION In order to further clarify the configuration and operation of the present invention described above, a preferred embodiment of a combustion apparatus of the present invention will be described below. FIG. 1 shows a schematic configuration of a burner 1 using a combustion device as one embodiment. In the burner 1, a plurality of burner units 10 as a combustion device are arranged in a line at a predetermined interval, and fuel gas is supplied from nozzles 11 and 12 provided behind the burner units 10, respectively. The primary air is also sucked into the burner unit 10, and the air-fuel mixture is blown out from the upper flame port to form a flame, and the flame is supplied with the secondary air rising between the burner units 10. ing.
The nozzles 11 and the nozzles 12 are arranged in two rows at predetermined intervals corresponding to each burner unit 10.

As shown in FIGS. 2 and 3, the burner unit 10 is a light-side burner in which a single stainless steel plate having a symmetrical concave portion formed by a press is bent at the center to form an overlapping room. 20, a dark side burner 30 in which a similar stainless steel plate is further laminated on both sides of the light side burner 20 to form a room, and a flame port plate 50 inserted into the flame port 25 of the light side burner 20. Consists of The light side burner 20 includes a light mixing unit right plate 21R as shown in FIG.
The left plate 21L of the light mixing unit is bent at the center and superposed symmetrically on the left and right to form a mixed gas flow path and a fuel gas flow path (an intake 22, a throat portion 23, a mixing chamber 24, a light flame port 2).
5) is formed integrally, but the right plate 21R of the light mixing unit will be described because it is symmetric. Also, for easy understanding, the superposed flat plate portions are indicated by hatching. The light mixing unit right plate 21R that forms the side surface of the light side burner 20 is formed with a concave portion by pressing, leaving the flat plate portion right 29R, and is provided at the lower left as viewed from the side surface, and sucks the fuel gas and the primary air for combustion. A funnel-shaped intake right 22R, a throat right 23R that narrows the flow path downstream thereof, an L-shaped bent right intake chamber 24R for mixing fuel gas and combustion primary air from the intake, and an upper part 24R. And a right flare opening 25R for discharging the mixture. In the vicinity of the downstream of the throat portion 23R, there are provided a plurality of air-fuel mixture ejection holes 28R on the right of the small holes. In addition, a fuel opening right 26R formed by a groove opened to the left end is provided above the intake right 22R, and several small gas ejection holes 27R pass through the side surface of the fuel opening right 26R. . The left plate 21L of the light mixing unit leaves the flat plate portion 29L, and these concave portions (the intake left 22L, the throat left 23L, the mixing chamber left 24L, the light flame left 25L, and the fuel left 26L) are mixed with the light mixing unit. It is formed in a shape symmetrical with the right plate 23R, and a left-side air-fuel mixture outlet 28L and a left-side gas outlet 27L are also provided. As shown in FIG. 6, the flame plate 50 has two ears 50b projecting left and right and three projections 5 formed at equal intervals therebetween.
Two plates having 0a and two plates having grooves corresponding to the protrusions 50a are created by overlapping the protrusions 50a and the grooves.

The dark side burner 30 is integrally connected to the left and right symmetrical right and left mixing plates 31R and 31L by three connecting plates 32 at the center, as shown in FIG. After being bent into a U-shape at the bottom, the chambers are superposed on both side surfaces of the light-side burner 20 to form chambers serving as air-fuel mixture flow paths. In order to make the description easy to understand, similarly to the description of the light-side burner 20, first, the shape of the rich mixing unit right plate 31R configuring the side surface shape of the room will be described. The dense mixing unit right plate 31R forms a concave portion leaving a flat plate portion right 39R (indicated by hatching in the figure),
Air-fuel mixture introduction chamber right 35R that forms a passage for air-fuel mixture ejected from the air-fuel mixture ejection hole right 28R of the light mixing unit right plate 21R.
And a gas introduction chamber right 36R through which gas ejected from the gas ejection hole right 27R of the light mixing unit right plate 21R and an air-fuel mixture from below pass therethrough, and a gap is similarly opened to open the upper part to allow the air-fuel mixture to pass therethrough. It has a thick flame outlet 37R to the right.
On the other hand, the left rich mixing unit plate 31L is symmetrical to the right rich mixing unit right plate 31R, and has a concave portion formed by leaving a flat plate portion left 39L (indicated by hatching in the figure). 35L, gas introduction chamber left 36L,
37L of deep flame outlet left.

The burner unit 10 (FIGS. 2, 3 and 4)
First, the light mixing unit right plate 21R and the light mixing unit left plate 21L are bent at the center, and the flat plate portion right 29R and the flat plate portion left 29L are spot-welded to form the light-side burner 20. The flame port plate 50 is inserted into the part 25 from the upper opening. Furthermore, with the connecting plate 32 as the bottom,
The dark side burner 30 bent in the shape of "" is superposed from the outside, and the flat plate portion 39R and the flat plate portion 39L are spot welded. Thus, the intake 22, the throat 23, the mixing chamber 24, the light flame port 25, and the fuel port 26 are formed in the light burner 20, leaving the flat plate portion 29. Room right 35R, mixture gas introduction room left 35L, gas introduction room right 36R, gas introduction room left 36L, rich flame outlet right 3
7R and 37L of rich flame mouth left are formed. Light side burner 20
In the assembly of the burner 30 and the dark side, since one plate is bent from the center and then spot-welded, the right and left light mixing unit right plates 21R and the left and right light mixing unit left plates 21
The positioning of the right mixing unit right plate 31R and the deep mixing unit left plate 31L is simple and easy to manufacture.

The supply of the fuel gas and the combustion air to the burner unit 10 is performed as follows (FIGS. 2, 3 and 3).
(See FIG. 4). First, in the light-side burner 20, fuel gas is jetted from the nozzle 11 toward the intake 22. The jetted fuel gas passes through the throat portion 23, which is narrowed on the way, and enters the mixing chamber 24. At this time, the primary air for combustion is simultaneously sucked from the gap between the nozzle 11 and the intake port 22,
The mixture enters the mixing chamber 24 through the throat section 23. An air-fuel mixture of fuel gas and primary air for combustion (hereinafter, referred to as a lean air-fuel mixture) is sufficiently mixed in the mixing chamber 24 and jets upward through the flame port plate 50 of the light flame port 25. Also, part of the light mixture
28 R of the air-fuel mixture ejection hole, 35 R of the air-fuel mixture introduction chamber of the burner 30 on the dense side from the 28 L of the air-fuel mixture ejection hole left, 3 left of the air-fuel mixture introduction chamber
Enter 5L. Fuel gas from the nozzle 10 is also supplied to the rich burner 30 (see also FIG. 5). Nozzle 10
First, the fuel gas is ejected to the fuel port 26 of the light-side burner 20, and passes through the gas ejection hole right 27R and the gas ejection hole left 27L, and enters the gas introduction chamber right 36R and the gas introduction chamber left 36L of the dark side burner 30. No gap is provided between the nozzle 10 and the fuel port 26, and no primary air is sucked. In the rich-side burner 30, the mixture from the light-side burner 20 is supplied to the mixture-introducing chamber right 3R from the mixture-air ejection hole right 28R and the mixture-air ejection hole left 28L.
5R, left 35L of the gas mixture introduction chamber, 36 right of the gas introduction chamber
R, after passing through 36 L of gas introduction chamber left, 37
R, spouts upwards from 37L of the deep flame outlet. At this time, the fuel gas from the nozzle 10 is additionally supplied to the right gas introduction chamber 36R and the left gas introduction chamber 36L. In other words, the fuel gas is ejected from the nozzle 10 to the fuel port 26 of the light-side burner 20, and the gas ejection hole right 27R and the gas ejection hole left 2
After passing through 7L, the gas enters the gas introduction chamber right 36R and the gas introduction chamber left 36L of the dark side burner 30. Since the primary air is not sucked from the fuel port 26, the air-fuel mixture (hereinafter, referred to as a rich air-fuel mixture) ejected from the rich flame outlet 37R and the rich flame left 37L is
The fuel gas concentration is increased by the amount of the fuel gas added to the lean mixture. Further, the fuel port 26 and the right gas injection hole 27R,
Since only the fuel gas passes between the gas ejection hole 27L and the left, and nothing is mixed, the distance can be reduced as much as possible.

[0014] Next, a description will be given of the relationship generation amount and the air ratio of nitrogen oxides when burned with the combustion device 1 (NO _X) and carbon monoxide (CO). 9 and 10, the horizontal axis represents the air ratio, the vertical axis represents the NO _X, CO / CO _2, is a graph showing a generation amount changes in both with respect to the change of the air ratio. When the air ratio of the rich mixture is 0.6, the burner gas amount on the rich side is:
FIG. 9 shows that only the air ratio (λ _L ) of the lean air-fuel mixture is changed, and FIG. 10 shows the overall air ratio (λ _T). 7) is a graph in which only the graphs are changed. When the air ratio λ _L of the lean mixture is changed, as shown in FIG. 9, the section where λ _L is extremely small (λ _L = 0.
7) and an extremely large λ _L section (λ _L = 2.2 or more), CO / CO ₂ increases (CO / CO ₂ =
0.005 or more) and CO / CO ₂ around λ _L = 1.4.
Is minimum and stable. NO _X gradually increases as λ _L is decreased, and exceeds 50 ppm when λ _L = 1.4 or less. When the overall air ratio λ _T is changed, as shown in FIG.
In the section where λ _T is extremely small (λ _T = 1.4 or less) and in the section where λ _T is extremely large (λ _T = 3.0 or more), CO
/ CO ₂ increases (CO / CO ₂ = 0.005 or more),
CO / CO ₂ is minimum around λ _T = 2.25 (CO / CO 2
₂ = 0.001). NO _X gradually increases as λ _T is reduced, and exceeds 50 ppm when λ _T = 1.8 or less. By the way, when the same test is performed in a conventional combustion apparatus (a combustion apparatus having a configuration shown in FIG. 13 disclosed in Japanese Patent Application Laid-Open No. 6-347013), graphs shown in FIGS. 11 and 12 are obtained. When the air ratio λ _L of the lean mixture is changed, as shown in FIG. 11, a section where λ _L is small (λ _L = 1.2 or less) and a section where λ _L is large (λ _L = 2.
2 or more), CO / CO ₂ increases (CO / CO ₂
= 0.005 or more) and CO / CO around λ _L = 1.7
₂ is the minimum. There is no stable section. NO _X is λ
_It gradually increases with the decrease of _L , and 5 when λ _L = 1.8 or less.
Exceeds 0 ppm. When the overall air ratio λ _T is changed,
As shown in FIG. 12, the section where λ _T is small (λ _T = 1.4
Below) and lambda _T is large interval (λ _T = 2.2 or higher), CO / CO ₂ is increased (CO / CO ₂ = 0.005 or more), lambda _T = 1.8 around at CO / CO ₂ Is the smallest (CO
/ CO ₂ = 0.002). There is no stable section. NO _X gradually increases as λ _T is decreased, and λ _T
= 50 ppm or less at 1.8 or less.

When the burner 1 of the embodiment is compared with this conventional example, the burner 1 is supplied with secondary air from around the rich-side flame and burns simultaneously in the rich-side burner 30 and the light-side burner 20 because the burner 1 burns simultaneously. In particular, in a light air-fuel mixture, it is not necessary to make the primary air ratio extremely high, and good combustion can be performed together with the secondary air. Therefore, especially in the light-side burner 20, the range of the air ratio width in the good combustion area is expanded to the lower air ratio side as compared with the conventional case where the ratio of the primary air is extremely high, and the secondary air is also reduced. In addition to providing a margin for changing the mixing ratio of the entire air including the air, the good combustion range is expanded.
For example, the good combustion width Δ in the change of the total air ratio λ _T
Where λ _T is Δλ _T = 1.6 in burner 1,
_T = 0.8, which is narrow, and CO / CO ₂ is as large as CO / CO ₂ = 0.002 in the conventional example, whereas CO / CO ₂ = 0.001 in the embodiment. Air ratio of light mixture λ
There is a similar difference for _L. Moreover, lambda in the _L configuration, and select a point NO _X and CO / CO ₂ is small, the conventional example in lambda _L = 1.9, sets the lambda _L = 1.4 in the burner 1. However, the setting of λ _L = 1.9 in the conventional example is close to the upper limit of the flammable air ratio λ _L = 2.2, so that the flame lifts up with a slight change in the air ratio, or the flame exceeds the combustion limit and CO / CO ₂ will increase rapidly. On the other hand, the setting of λ _L = 1.4 for the burner 1 is at the center of the change width of the flammable air ratio, and it is difficult to lift even with the change of the air ratio, so that the combustion state does not deteriorate. Also, the overall air ratio λ _T
Λ _T can be increased and the dew point can be increased, especially when burning with a small amount of gas. Therefore, generation of drain adhering to the heat exchanger is reduced and durability is improved.

Also, when compared with the combustion apparatus disclosed in Japanese Patent Application Laid-Open No. 7-42917, the combustion apparatus has a longer distance from the fuel port to the flame port. The rich air-fuel mixture ejected from the side flame opening is mixed with the air-fuel mixture supplied from the light mixing unit 21 by further adding a fuel gas from the fuel port 26 and supplied with an increased fuel gas concentration. The length of the fuel gas passage can be reduced (because there is no need to mix), and the whole becomes compact.
As a result, in particular, the overall width L shown in FIG. 1 can be reduced. In comparison with the conventional example, in the embodiment, the air ratio of the rich mixture is set to 0.6, the burner gas amount of the rich side: the burner gas amount of the light side = 3: 7, and the secondary air ratio is set to 0.45. Although the explanation was made using a graph in which only the air ratio (λ _L ) of the lean air-fuel mixture or the total air ratio (λ _T ) was changed, various tests were performed without being limited thereto, and a good combustion range was determined. Was. It gas amount ratio I _R (fuel gas amount / total amount of the fuel gas of concentrated side burner) = 30-40% the amount of fuel gas / overall gas amount ratio I _L (light side burner pale side burner dark side burners Fuel gas amount) = 60-70% Air ratio λ _{R of} rich burner (primary air ratio of rich burner / theoretical air amount) = 50-80% Air ratio λ _{L of} light burner (light burner Primary air ratio / theoretical air amount) = 140-170% Secondary air ratio λ ₂ (total secondary air amount / theoretical air amount) = 3
0 to 50%. However the whole of the fuel gas amount = the amount of fuel gas + amount of fuel gas pale side burner _{λ T = λ R × I R} + λ L × I L + λ 2 This range of dark side burners, CO / CO ₂ ≦ 0.005 ( Safety standards in our company). Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments at all, and it is needless to say that the present invention can be implemented in various modes without departing from the gist of the present invention. For example, in the embodiment, in assembling the light-side burner 20 and the dark-side burner 30, one plate is bent from the center and then spot-welded, but the right and left light mixing unit right plates 21R and the light mixing unit left plate 21L, the rich mixing unit right plate 31R, and the rich mixing unit left plate 31L may be formed separately, and spot welding may be performed while positioning. In this case, the press die is not large and the die cost is low. The slit plate 50 has substantially the same shape when viewed from the top, as shown in FIGS. 2 and 6, but has a small size as shown in FIG. 7 or FIG. A combination of different slits or a corrugated flame outlet may be formed.

[0017]

As described in detail above, claim 1 of the present invention
According to the combustion device described above, the rich burner is supplied with the air-fuel mixture mixed to some extent from the light burner, and further adds a fuel for increasing the concentration from the fuel port to the air-fuel mixture and mixes the fuel. The distance of the fuel passage section in the light burner can be made as short as possible. Therefore, the whole can be made compact.

According to the combustion apparatus of the second aspect, since the combustion conditions are set and adjusted within an appropriate range, the combustion is stabilized and the generation of harmful substances in the combustion exhaust gas is small.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a combustion device as one embodiment.

2 is a top view and a side view of the burner unit 10. FIG.

3 is a sectional view and a rear view of the burner unit 10. FIG.

FIG. 4 is a component diagram of the light-side burner 20.

FIG. 5 is a component diagram of the dark side burner 30.

FIG. 6 is a perspective view of a flame port plate 50.

FIG. 7 is a top view of the burner unit.

FIG. 8 is a top view of the burner unit.

FIG. 9 is a graph showing a change in the generation amount of NO _X and CO / CO ₂ with respect to a change in the air ratio in the example.

FIG. 10 shows the relationship between the change in the air ratio and the NO _X in the embodiment.
4 is a graph showing a change in the generation amount of CO / CO ₂ and CO / CO ₂ .

FIG. 11 is a graph showing the relationship between the change in the air ratio and the NO _x in the conventional example.
4 is a graph showing a change in the generation amount of CO / CO ₂ and CO / CO ₂ .

FIG. 12 is a graph showing the relationship between the change in the air ratio and the NO _x in the conventional example.
4 is a graph showing a change in the generation amount of CO / CO ₂ and CO / CO ₂ .

FIG. 13 is a schematic configuration diagram of a combustion device as a conventional example.

FIG. 14 is a schematic configuration diagram of a combustion device as a conventional example.

[Explanation of symbols]

 Reference Signs List 1 burner 10 burner unit 11, 12 nozzle 20 light side burner 21R light mixing unit right plate 21L light mixing unit left plate 22 intake port 23 throat section 24 mixing chamber 25 light flame port section 26 fuel port 29, 39 flat plate section 30 dark side Burner 31R Rich mixing unit right plate 31L Rich mixing unit left plate 32 Connecting plate 35 Gas mixture introduction chamber 36 Gas introduction chamber 37 Rich flame outlet

Claims (2)

[Claims] 1. A light-side burner that inhales and mixes fuel gas and primary air for combustion to eject a light air-fuel mixture having a stoichiometric air ratio or more from a light-side flame opening, and a rich mixture having a stoichiometric air ratio on both sides thereof. Combustion in which an integrated burner is provided integrally with a rich burner that blows air from the rich burner, and the light burner and the rich burner are simultaneously burned while supplying secondary air for combustion from around the rich burner. In the apparatus, the light-side burner includes a first suction port for sucking primary air for combustion and fuel gas, and a second suction port for sucking only fuel gas. The air and the fuel gas are sucked and mixed, and the air-fuel mixture is distributed and supplied to the light-side flame port and the rich-side flame port, and the fuel gas is sucked from the second suction port to the rich-side flame port. A combustion device characterized by being ejected to a supply path. 2. The ratio of the fuel gas amount of the rich side burner to the total fuel gas amount (the sum of the fuel gas amount of the rich side burner and the fuel gas amount of the light side burner) is set to 30 to 40%. The ratio of the primary air amount of the dense side burner to the amount of air is 50 to 80%, the ratio of the primary air amount of the light side burner to the theoretical air amount is 140 to 170%, and the overall secondary amount to the theoretical air amount. Air volume ratio 30-50
2. The combustion apparatus according to claim 1, wherein the temperature is set to%.