JP3848801B2 - Liquid fuel burner - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a liquid fuel-fired burner applied to a liquid fuel-fired boiler that generates steam for power generation or factory use.
[0002]
[Prior art]
FIG. 10 is a system diagram showing an example of a boiler for explaining the prior art, FIG. 11 is a longitudinal sectional view of a conventional liquid fuel burning burner (main burner), and FIG. 12 is a view taken in the direction of arrow a in FIG.
As shown in FIGS. 10 to 12, the combustion air 20 is sent to the burner wind box 1 by a forced air blower 17 (FDF). In the middle of the combustion air 20, Heat exchange is performed and the temperature is raised. Further, the combustion air 20 is mixed with a part of the recirculation exhaust gas 23 (GR) branched from the combustion exhaust gas 22a by the recirculation exhaust gas ventilator 24 (GRF) as the air mixing recirculation exhaust gas 25 (GM). It becomes mixed combustion air 27.
[0003]
The GM-mixed combustion air 27 is divided into burner combustion air 28 and additional air 29 (AA) before being sent to the burner wind box 1. The burner combustion air 28 is sent to the burner wind box 1 and blown from the burner body 2 into the furnace 16a for combustion. The burner body 2 is provided with a circular primary air flow path 6 at the center of the burner, and a burner gun 12 is mounted at the center of the primary air flow path 6. An atomizer 12a is attached to the tip of the burner gun 12, and a flame stabilizer 13 is provided so as to surround the atomizer 12a.
[0004]
In the burner body 2, a secondary air cylinder 4 is disposed so as to surround a primary air cylinder 3 that forms the primary air flow path 6 therein, and a tertiary air cylinder 5 is further enclosed so as to surround the secondary air cylinder 4. Is arranged. An annular secondary air flow path 7 is formed between the primary air cylinder 3 and the secondary air cylinder 4, and an annular tertiary air flow path 8 is formed between the secondary air cylinder 4 and the tertiary air cylinder 5. Is formed. A primary air damper 9, a secondary air damper 10, and a tertiary air damper 11 are provided at the inlets of the flow paths 6, 7, and 8 for adjusting the air flow rates. The tip end side of the burner body 2 is attached to the furnace body 16 by a burner mounting plate 2a fixed to the tip of the outermost tertiary air cylinder 5. The burner combustion air 28 sent to the burner wind box 1 is divided into primary air 28a, secondary air 28b, and tertiary air 28c, and passes through the dampers 9, 10, 11 to the primary air flow path 6, After being sent to the secondary air flow path 7 and the tertiary air flow path 8, respectively, it is blown into the furnace interior 16a, and is used for combustion of liquid fuel separately blown into the furnace interior 16a. In addition, the code | symbol 26 in FIG. 10 has shown the furnace bottom recirculation waste gas (BGR) injected into the bottom part of the furnace inside 16a.
[0005]
The liquid fuel 21 is pumped from the liquid fuel supply device (not shown) to the burner gun 12 and sprayed from the atomizer 12a to the furnace interior 16a, and ignited by an ignition source (not shown) to form a flame 31. The spread angle of the flame 31 is determined by the fuel spray angle of the atomizer 12a and the flow pattern of the secondary air 28b. In the case of the burner that performs the swirl combustion in the furnace 16a, it is approximately 70 ° to 90 ° (with respect to the burner axis). Is an angle of ejection of 35 ° to 45 °.
[0006]
The flame 31 is a circulating flow formed on the back surface of the flame holder 13 provided at the outlet of the primary air passage 6 when the primary air 28a is blown from the primary air passage 6 into the furnace 16a. This stabilizes the ignition point. The primary air 28a is consumed for combustion in the vicinity of the ignition point of the flame 31, and the secondary air 28b and the tertiary air 28c are consumed for combustion in the combustion zone of the burner body 2 while being diffusely mixed with the entire flame 31. Normally, the burner combustion air 28 is sent in an amount smaller than the theoretical combustion air amount relative to the amount of liquid fuel 21 sent separately, and a reducing atmosphere is formed in the combustion zone below the AA port 15 from the burner body 2. Then, nitrogen oxides (hereinafter abbreviated as NOx) in the combustion gas 22 generated by the combustion of the liquid fuel 21 are reduced. Further, combustibles remain in the combustion gas 22 generated by the combustion of the liquid fuel 21 due to air shortage.
[0007]
On the other hand, AA 29 diverted from the GM-mixed combustion air 27 upstream of the burner wind box 1 is blown from the AA port 15 into the furnace 16a to be used for combustion of the remaining combustibles in the combustion gas 22 to complete the combustion. To do. After the combustion is completed, the combustion gas 22 is sent to the evaporation tube group 30 to heat the steam, and then, as the combustion exhaust gas 22, it is attracted by the induction fan 18 (IDF) through the air heater 19 and discharged from the boiler.
[0008]
FIG. 13 shows the case where the burner body 2 is provided at the corner of the furnace body 16. Can It is a plane sectional view in burner body 2 center height for explaining an example of swirl combustion. In FIG. 13, the burner body 2 provided at each corner portion blows liquid fuel 21 and burner combustion air 28 in a tangential direction with respect to a virtual circle 32 set in the center portion of the furnace 16a to form a flame 31. Let The formed flame 31 interferes with each other and swirls while forming a flame vortex, and ascends in the furnace 16a. Burner combustion air 28 blown from the burner body 2 is blown at a high flow rate in order to enhance the diffusion effect with the liquid fuel 21. A negative pressure is generated between the wall surfaces of the furnace interior 16a by the flow of burner combustion air 28 blown at this high flow velocity, and the flame 31 is drawn toward the wall surface side of the furnace interior 16a (a kind of Coanda effect). As a result, the wall surface of the furnace interior 16a in the vicinity of the burner body 2 is exposed to the high-temperature reducing combustion gas.
[0009]
It is generally known that when oxygen sulfide is low and hydrogen sulfide (H2S) is generated due to incomplete combustion, it reacts with iron at a high temperature to produce sulfide (sulfidation corrosion). If reduction combustion is continued in this state, the wall surface in the vicinity of the burner body 2 always has a risk of hot corrosion.
[0010]
[Problems to be solved by the invention]
As described above, a reducing atmosphere is formed in the combustion zone of the burner body 2 as a NOx reduction measure for the swirl combustion type boiler, NOx generated by the combustion of the liquid fuel 21 is reduced, and additional air 29 (AA) is injected. A combustion method that completes combustion is employed. However, in conventional liquid fuel-fired burners, it is inevitable that high-temperature combustion gas is exposed to the furnace inner wall composed of steel pipes, and in the combustion performed in a high-temperature reducing atmosphere zone, hydrogen sulfide and the like are generated in the high-temperature gas. Thus, there is a problem that the inner wall surface of the furnace is damaged by high temperature corrosion.
[0011]
The present invention has been made in view of the above-described problems of the prior art, and an object thereof is to provide a liquid fuel-burning burner that can prevent high-temperature corrosion of the furnace inner wall.
[0012]
[Means for Solving the Problems]
In order to achieve the above object, according to the present invention, a primary air flow path is formed at the center of the burner body, and at least one annular air flow path is formed surrounding the primary air flow path. Furthermore, a flame holder and a burner gun penetrating the flame holder are provided at the center tip of the primary air flow path, and are mounted on a corner portion or a wall surface of the boiler furnace, and liquid fuel and combustion air are supplied into the boiler furnace. In a liquid fuel-fired burner that performs tangential injection with respect to the virtual circle set to Side air outlets are provided at an ejection angle of 45 ° to 75 ° with respect to the burner axis. The burner body is provided with a side air flow path for introducing side air into the side air outlet, and burner combustion air is branched and introduced into the side air intake of the side air flow path. The side air intake port of the side air flow path is provided with a side air damper for flow rate adjustment. It is characterized by this.
[0013]
As described above, the flame of the burner main body provided at, for example, four corners in the furnace is formed to spread to the inner wall surface side of the furnace by swirling combustion, so that the inner wall surface of the furnace is easily exposed to high-temperature combustion gas. Moreover, the combustion zone of the burner body is in a reducing atmosphere and is in an air-deficient state, which may cause high temperature corrosion. Therefore, in the present invention, side air (for example, even if the burner combustion air is branched) is introduced into the side air intake port, and the side air passes through the side air flow path from the side air outlet to the flame and the furnace inner wall surface. It is possible to increase the oxygen concentration of the combustion gas that is blown in between and is in contact with the furnace inner wall surface.
[0014]
Here, in the plan view of the burner body, the furnace inner wall surface on the opposite side to the flame turning direction, that is, the furnace inner wall surface on the downstream side of the flame has a wide reach of high-temperature combustion gas, compared with other parts. It is necessary to blow a large amount of side air.
Therefore, by providing a side air damper for adjusting the flow rate at the side air intake port of the side air flow path, the side air damper is adjusted so that the side air outlet near the furnace inner wall surface on the downstream side of the flame. The blowing flow rate is increased by setting the opening area larger than the opening area of the other side air outlet. Here, the side air blowing flow rate and the flow velocity to the downstream side of the flame are set to such a size that the side air reaches a range sufficiently wider than the reach range of the downstream side wall surface of the high-temperature combustion gas.
[0015]
Claim 2 In the described invention, in the plan view of the burner body, the opening area of the side air outlet close to the furnace inner wall opposite to the flame turning direction is set larger than the opening area of the other side air outlets. It is what.
That is, if the flame is swirl combustion in the left direction, the arrival ratio of the high temperature reducing combustion gas to the wall surface side opposite to the swirl direction of the flame, that is, on the right side (downstream of the flame) increases. The area of the side air outlet is set so that the air blowing flow rate also increases particularly on the downstream side of the flame. The upstream side wall surface of the flame is expanded by the combustion gas from the flame, but at the same time there is side air blowing, and the side air is blown away from the upstream side wall surface. Set the amount to a small amount. The amount of side air blown into the vertical wall surface of the flame is set to a small amount because the distance between the burners provided in the upper and lower stages is short.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Next, embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
1 is a longitudinal sectional view of a liquid fuel burning burner (main burner) according to the present invention, FIG. 2 (a) is a sectional view taken along line BB in FIG. 1, and FIG. 1 (b) is a sectional view taken along line CC in FIG. .
[0017]
A primary air flow path 6 having a circular cross section is formed at the burner center of the burner body 102, and an annular secondary air flow path 7 is formed so as to surround the primary air flow path 6. An annular side air flow path 108 so as to surround the air flow path 7 But Is formed. The primary air damper 9, the secondary air damper 10 and the side air damper 111 for adjusting the flow rate are respectively provided at the inlets of the primary air passage 6, the secondary air passage 7 and the side air passage 108. It has been. A burner gun 12 is attached to the center of the primary air flow path 6. An atomizer 12a is attached to the tip of the burner gun 12, and a flame stabilizer 13 is provided so as to surround the atomizer 12a.
[0018]
The side air flow path 108 is formed between the secondary air cylinder 4 and the side air cylinder 105, and the ends of the secondary air cylinder 4 and the side air cylinder 105 are fixed to the burner mounting plate 102a. A side air chamber 109 is formed at the tip of the flow path 108. The front end side of the burner body 102 is attached to the furnace body 16 by a burner attachment plate 102a. The burner mounting plate 102 a is provided with a plurality of side air ejection pipes 109 a that pass through the burner mounting plate 102 a and communicate with the side air chamber 109. The end of the side air ejection pipe 109a penetrates the burner tile (refractory material) 14 forming the burner throat 14a of the burner body 102, and is provided with a side air ejection port that ejects the side air 128 toward the furnace 16a side. 109b. The side air outlet 109b can blow the side air 128 at a high flow velocity of about 60 m / s or more along the wall surface in the vertical and horizontal directions at a position that does not contact the flame 31 at an early stage on the outer periphery of the burner throat 14a. It is arranged.
[0019]
Further, the ejection angle θ (see FIG. 1) of the side air 128 from the side air ejection port 109b with respect to the burner axis is 45 ° or more, which is the spread angle of the flame 31 (from 35 ° to the burner axis). 45 °) or more, the side air 128 does not contribute to combustion almost at an early stage and reaches the furnace inner wall surface in a sufficiently oxygen-containing state. Furthermore, in order to reliably reach the side air 128 to the furnace inner wall surface and increase the combustion gas oxygen concentration in contact with the wall surface, the jet angle θ (see FIG. 1) of the side air 128 with respect to the burner axis is 45 ° to 75 °. The range of is preferable.
[0020]
FIG. 3 is a plan sectional view of the furnace interior 16 a at the center height of the burner body 102 when the burner body 102 is provided at the corner of the furnace body 16. In plan view, the side air outlet 109b near the wall surface 16a in the furnace opposite to the turning direction of the flame 31 (in this example, the counterclockwise direction) with respect to the burner body 102 (in FIG. 2A, the left side air jet) The opening area of the outlet) is set to be larger than the opening area of the other side air outlet 109b. That is, if the flame 31 is swirling in the left direction, the arrival rate of the high temperature reducing combustion gas to the wall surface side (flame downstream side) located on the right side (flame downstream) of the flame 31 is increased. The area of the side air outlet 109b is set so that the blow flow rate is particularly greater on the flame downstream side 128a than on the flame upstream side 128b.
[0021]
Next, the operation will be described.
The burner combustion air 28 that has been sent to the burner wind box 1 is blown from the burner body 102 into the furnace interior 16a for combustion. That is, the burner combustion air 28 sent to the burner wind box 1 is adjusted to have a predetermined air amount by the dampers 109, 110, 111 provided at the inlets of the flow paths 6, 7, 108. Thereafter, the air is sent to the primary air flow path 6, the secondary air flow path 7, and the side air flow path 108, respectively. The primary air 28a and the secondary air 28b are used for combustion of the liquid fuel 21 that has been separately fed by the same action as in the case of the conventional liquid fuel-burning burner described above, and air shortage occurs in the combustion zone of the furnace interior 16a. Swirl combustion is performed.
[0022]
As shown in FIG. 3, the flame 31 of the burner main body 102 provided at the four corners of the furnace interior 16a is formed so as to spread to the wall surface side of the furnace interior 16a by swirl combustion. Therefore, the wall surface of the furnace interior 16a is hot and reducing. Exposed to combustion gas. On the other hand, the side air 128 branched in the burner wind box 1 passes through the side air damper 111 and is sent from the annular side air flow path 108 to the side air chamber 109.
[0023]
The side air 128 sent into the side air chamber 109 is connected to the flame 31 and the furnace from the side air ejection pipe 109a provided on the burner mounting plate 102a and the side air ejection port 109b provided through the burner tile 14 on the side. The oxygen concentration of the combustion gas blown between the inner 16a wall surfaces and in contact with the furnace inner 16a wall surface is increased. That is, side air (for example, burner combustion air 28 is branched to the side air intake port. The The side air is blown from the side air outlet 109b between the flame 31 and the wall surface of the furnace 16a through the side air passage 108, and the oxygen concentration of the combustion gas in contact with the wall surface of the furnace 16a is increased. Can do. Therefore, even in the combustion method performed in the high-temperature reducing atmosphere zone, hydrogen sulfide or the like is hardly generated in the high-temperature gas, the furnace inner wall surface is hardly damaged by high-temperature corrosion, and the life is extended. Since the side air 128 is ejected along the wall surface of the furnace 16a, it hardly contributes to combustion.
[0024]
Here, by adjusting the side air damper 111 for flow rate adjustment corresponding to each side air outlet 109b, the opening area of the side air outlet near the wall surface 16a in the furnace on the downstream side of the flame 31 is changed to other side air. By setting it larger than the opening area of the spout, the blowing flow rate is increased. Of course, the side air blowing flow rate and the flow velocity to the downstream side of the flame 31 are set to such a size that the side air can reach a range sufficiently wider than the reach range of the downstream side wall surface of the high-temperature combustion gas. Further, as described above, if the flame 31 is swirling in the left direction, the arrival rate of the high temperature reducing combustion gas to the wall surface side (flame downstream side) located on the right side (flame downstream) of the flame 31 is increased. The opening area of the side air outlet 109b is set so that the flow rate of the side air is also increased particularly on the downstream side of the flame. It should be noted that the furnace inner wall 16a on the upstream side of the flame 31 has combustion gas from the flame 31 extending, but at the same time there is side air blowing, and the flame 31 is away from the upstream furnace inner wall 16a. The amount of side air blowing is set to a small amount due to the slightness, and the amount of side air blowing with respect to the vertical wall surface of the flame 31 is the distance between the burners provided in the upper and lower stages (see FIG. 10). Since it is short, it may be set to a small amount.
[0025]
The total amount of combustion air blown from the burner body 102 and the side air 128 into the furnace 16a is adjusted so that the air ratio in the combustion zone of the burner body 102 does not become 1 or more. However, if the reducing atmosphere in the combustion zone of the burner body 102 cannot be maintained due to a decrease in boiler load, the air ratio may be> 1, but the amount of side air 128 blown in is as much as possible. Maintain the same state as at 100% load.
[0026]
The NOx in the combustion gas 22 generated by the combustion of the liquid fuel 21 is not reduced by the reduction combustion in the combustion zone of the burner body 102, but instead, intermediate products such as NH3 and HCN are generated. In addition, combustibles remain in the combustion gas 22 due to combustion with insufficient air. The combustion gas 22 discharged from the combustion zone of the burner body 102 is oxidized and burned by the AA 29 that is blown from the additional air (AA) port 15. The oxidation combustion by the AA 29 is performed while completely burning the remaining combustible material in the combustion gas 22 and suppressing the regeneration of NOx caused by the combustion of the remaining combustible material and the oxidation of the intermediate product as low as possible. However, even in that case, it is necessary to secure a particularly large amount of the side air 128 blown into the downstream side wall surface of the flame 31 as described above. Side air is moved along the furnace inner wall in the vertical and horizontal directions of the furnace inner wall. Infuse Not limited to this, side air outlets may be arranged evenly on the circumference, and side air may be blown along the furnace inner wall surface in the entire circumferential direction of the furnace inner wall surface.
[0027]
(Second Embodiment)
4 is a longitudinal sectional view of a liquid fuel burning burner according to a second embodiment of the present invention, FIG. 5 is a sectional view taken along the line BB in FIG. 4, and FIG. 4B is a sectional view taken along the line CC in FIG. It is.
[0028]
An annular side air inlet header 133 is provided on the outer periphery of the secondary air cylinder 4 of the burner body 102, and a side air damper 111 for taking in side air 128 and adjusting the flow rate is provided at the inlet of the side air inlet header 133. Is provided. A plurality of side air passage pipes 134 extending in the axial direction of the burner body 102 are attached to the outlet side of the side air inlet header 133, and the downstream end of the side air passage pipe 134 is connected to the side air chamber 109. By attaching to the side air passage pipe 134, the inside of the side air passage tube 134 is used as the side air passage 108. With such a configuration, the side air 128 is sent to the side air inlet header 133 through the side damper 111 and reaches the side air chamber 109 from the side air flow path 108 in the plurality of side air flow path pipes 134. As described above, the second embodiment is different from the first embodiment in that the side air inlet header 133 is provided in the shape of the side air flow path 108 and the intake portion of the side air 128.
[0029]
(Third embodiment)
FIG. 6 is a longitudinal sectional view of a third embodiment of the liquid fuel burning burner of the present invention, and FIG. 6 BB line sectional view, (b) is a figure 6 CC sectional view taken on the line, (c) is the figure 6 It is the DD sectional view taken on the line.
[0030]
The side air flow path 108 provided on the outer periphery of the secondary air cylinder 4 is divided into at least two or more in the circumferential direction by a side air dividing plate 108a extending along the side air flow path 108 (four divisions in this example). A side air damper 111 is provided at the inlet of each divided side air flow path 108. The side air chambers 109 are also divided into the same number as the side air flow paths 108 by the side air chamber dividing plates 109c, and the tips of the corresponding side air flow path dividing plates 108a and the side air chamber dividing plates 109c are connected. That is, the inside of the side air chamber 109 is divided by the side air chamber dividing plate 109c into the same number as the side air flow passage 108, and the side air flow dividing plate 108c and the side air chamber dividing plate 109c are connected to each other. A plurality of independent (four in this example) flow paths including a damper 111, a side air flow path 108, and a side air chamber 109 are provided, and a side air jet port penetrating from the divided side air chamber 109 to the furnace interior 16a. The flow rate of the side air 128 blown by 109b can be arbitrarily adjusted.
[0031]
As described above, in the third embodiment, the side air flow path 108 and the side air chamber 109 are divided in the burner body 102 of the first embodiment, and the desired side air flow path 108 is closed by the side air damper 111. Thus, the side air 128 is blown from an arbitrary side air outlet 109b, and the flow distribution can be arbitrarily adjusted. As a result, it is possible to arbitrarily adjust the flow rate of the side air 128 blown from the divided side air chamber 109 through the side air outlet 109b penetrating into the furnace 16a.
[0032]
(Fourth embodiment)
8 is a longitudinal sectional view of a fourth embodiment of the liquid fuel burning burner of the present invention, FIG. 9A is a sectional view taken along line BB in FIG. 8, and FIG. 8B is a sectional view taken along line CC in FIG. is there.
An annular side air inlet header 133 is provided on the outer periphery of the secondary air cylinder 4, and the inside of this side air inlet header 133 is divided into at least two or more (four in this example) by the side air inlet header dividing plate 133a. Side air dampers 111 are provided at the inlets of the inlet headers 133 formed. The side air chamber 109 is also divided into the same number as the side air inlet header 133 by the same method as in the third embodiment, that is, the side air chamber dividing plate 109c, and the side air inlet header 133 and the side air chamber 109 are divided between the side air chambers. The air channel pipe 134 communicates. As a result, it is possible to arbitrarily adjust the flow rate of the side air 128 blown from the divided side air chamber 109 through the side air outlet 109b penetrating into the furnace 16a. As described above, in the fourth embodiment, the side air inlet header 133 and the side air chamber 109 of the burner main body 102 of the second embodiment are divided and the corresponding compartments are connected by the side air flow channel pipe 134. The air 128 can be blown only from an arbitrary arbitrary side air outlet 109b to an arbitrary wall surface, or the flow distribution can be adjusted arbitrarily.
[0033]
【The invention's effect】
Since the present invention is configured as described above, an arbitrary amount of combustion air can be blown into the arbitrary wall surface between the flame and the furnace inner wall surface from the side air outlet as side air. Therefore, the oxygen concentration of the combustion gas in contact with the inner wall surface of the furnace is increased, and high temperature corrosion can be prevented.
[0034]
In particular, the inner wall of the furnace on the downstream side of the flame has a wide reach of high-temperature combustion gas, so a large amount of side air is required compared to the others, so the side air blowing flow rate and flow velocity to the downstream side of the flame are adjusted. It is preferable to do.
The flow rate and flow rate can be easily adjusted by opening / closing the damper and the opening area of the side air outlet.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a first embodiment of a liquid fuel burning burner according to the present invention.
2A is a cross-sectional view taken along line BB in FIG. 1, and FIG. 2B is a cross-sectional view taken along line CC in FIG.
FIG. 3 is a cross-sectional view of a boiler furnace body according to the present invention cut along a horizontal plane.
FIG. 4 is a longitudinal sectional view of a second embodiment of the liquid fuel burning burner of the present invention.
5A is a cross-sectional view taken along line BB in FIG. 4, and FIG. 5B is a cross-sectional view taken along line CC in FIG.
FIG. 6 is a longitudinal sectional view of a third embodiment of the liquid fuel burning burner of the present invention.
7A is a cross-sectional view taken along line BB in FIG. 6, FIG. 7B is a cross-sectional view taken along line CC in FIG. 6, and FIG. 7C is a cross-sectional view taken along line DD in FIG.
FIG. 8 is a longitudinal sectional view of a fourth embodiment of the liquid fuel burning burner of the present invention.
9A is a cross-sectional view taken along line BB in FIG. 8, and FIG. 9B is a cross-sectional view taken along line CC in FIG.
FIG. 10 is a system diagram showing an example of a boiler for explaining the prior art.
FIG. 11 is a longitudinal sectional view of a conventional liquid fuel burning burner.
12 is a view on arrow a in FIG.
FIG. 13 is a cross-sectional view of a conventional boiler furnace body cut along a horizontal plane.
[Explanation of symbols]
1 Burner-style box
2 Burner body
3 Primary air cylinder
4 Secondary air cylinder
6 Primary air flow path
7 Secondary air flow path
9 Primary air damper
10 Secondary air damper
12 Burnagan
12a atomizer
13 Flame holder
14 Burner tile
14a Burner Throat
15 Additional Air (AA) Port
16 Furnace body
16a In the furnace
17 Forced blower (FDF)
18 Induction fan (IDF)
19 Air heater
20 Combustion air
21 Liquid fuel
22 Combustion gas
22a Combustion exhaust gas
23 Recirculated exhaust gas (GR)
24 Recirculation exhaust gas ventilator (GRF)
25 Recirculated exhaust gas (GM) for air mixing
26 Furnace bottom recirculation exhaust gas (BGR)
27 GM mixed combustion air
28 Burner combustion air
29 Primary air
28b Secondary air
29 Additional Air (AA)
30 Evaporation tube group
31 flame
32 virtual circles
102 Burner body
102a Main burner mounting plate
108 Side air flow path
108a Side air flow path dividing plate
109 Side air chamber
109a Side air jet pipe
109b Side air outlet
109c Side air chamber divider
111 Side air damper
128 side air
133 Side air inlet header
133a Side air inlet header dividing plate
134 Side air flow pipe

Claims (2)

A primary air flow path is formed at the center of the burner body, and at least a single or more annular air flow path is formed surrounding the primary air flow path, and the center of the primary air flow path is further formed. A flame holder and a burner gun that penetrates the flame holder are provided at the tip. The flame holder is attached to the corner or wall of the boiler furnace. Liquid fuel and combustion air are tangential to the virtual circle set in the boiler furnace. In a liquid fuel-fired burner that performs jet and swirl combustion, a side air outlet that blows side air along the wall surface in the vertical and horizontal directions or the entire circumferential direction of the inner wall surface of the furnace is provided outside the air passage. Is provided at an ejection angle of 45 ° to 75 ° ,
The burner body is provided with a side air flow path for introducing side air to the side air outlet,
It is configured to branch and introduce burner combustion air into the side air intake of the side air flow path,
A liquid fuel burning burner in which a side air damper for flow rate adjustment is provided at a side air intake port of the side air flow path . Opening area of the side air ejection port near the opposite furnace wall surface of the turning direction of the flame in a plan view of the burner body, in claim 1, which is larger than the opening area of the other side air jet port The liquid fuel-burning burner described.

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