JPH11141811A - Burner for liquid fuel, and its mounting structure, and combustion method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a burner for liquid fuel suitable especially for a glass furnace utilizing the radiant heat conducted from flame, and its mounting structure and combustion method. SOLUTION: This is a burner for liquid fuel which has a coaxial combustion supporting gas passage around a fuel jet nozzle 15 where the tip of a fuel supply nozzle 16 for jetting liquid fuel is inserted into the center of one end in axial direction of a cylindrical mixing chamber 17 and an atomized flow passage 18 is made around the fuel supply nozzle 16 and an atomized fuel jet 19 is provided at the center of the other end of the mixing chamber 17, and the relation between the inside diameter Da and the length La of the mixing chamber 17 is put in the range of La/Da=0.75-1.75.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a liquid fuel burner particularly suitable for a glass melting furnace utilizing radiant heat transfer from a flame, a mounting structure thereof, and a combustion method.

[0002]

2. Description of the Related Art In a glass melting furnace, in order to uniformly heat and melt glass, a method of burning a liquid fuel such as heavy oil or kerosene with air is used without causing a flame to contact the glass.
A melting method mainly using radiant heat transfer is adopted.

However, if air is used as a supporting gas,
Since the nitrogen gas in the air does not contribute to the combustion, a large amount of exhaust gas is generated, and the loss of heat used for increasing the temperature of the nitrogen gas is inevitable.

However, when oxygen gas is used as the supporting gas, it is expected that the amount of exhaust gas is reduced and the thermal efficiency is improved, and harmful NOx can be reduced. Therefore, interest in oxyfuel combustion has increased, and there has been a demand for the use of an oxygen burner with substantially pure oxygen in a glass melting furnace.

However, in oxyfuel combustion, since the amount of gas after combustion is smaller than in air combustion and a high-temperature flame is obtained, the conventional oxygen burner for liquid fuel mainly heats a high-temperature flame having a short flame length. It was suitable for heating directly against objects.

On the other hand, in a glass melting furnace, as described above,
Since the radiant heat transfer is mainly used, a long flame length that can obtain a wide temperature distribution is desirable. To that end, we have:
Previously, as shown in FIG. 11, an oxygen burner for liquid fuel that forms a long flame by slow combustion was proposed (see Japanese Patent Application Laid-Open No. Hei 6-347008). This burner is a non-water-cooled, self-cooling type, and has excellent maintainability.
Suitable for glass melting furnace.

In the oxygen burner 1 for liquid fuel shown in FIG. 11, a fuel-supplying gas passage 4 is provided concentrically on the outer periphery of a fuel passage 3 having a fuel ejection hole 2 at the tip end, and is eccentric with the fuel ejection hole 2. A diaphragm member 6 having a diaphragm hole 5 formed at the designated position is continuously provided. Therefore, the liquid fuel is diffused into the gap portion 7 through the throttle hole 5 and then ejected from the fuel ejection hole 2. At this time, since the fuel ejection hole 2 and the throttle hole 5 are located at eccentric positions, the fuel ejection is performed. The liquid fuel from the hole 2 is ejected at a relatively small spray angle, and the flight distance is extended.

On the other hand, the supporting gas is ejected from the open end of the supporting gas passage 4 so as to surround the atomized liquid fuel.
By burning in this state, a flame having a long flame length and a large ratio of bright flame portions can be obtained. This is because in the burner 1, the mixing of the liquid fuel and the supporting gas becomes slow, and as a result, the burning of the liquid fuel becomes slow. However, the flame obtained by such a liquid fuel oxygen burner has a weak point of low propulsion.

[0009]

[0006] In the conventional mode of introducing an oxygen burner for liquid fuel into a glass melting furnace using air combustion, there is a case where a glass melting furnace dedicated to a liquid fuel oxygen burner is newly installed. In some cases, the oxygen burner for liquid fuel is partially replaced. There is no particular problem in the former case, but when the latter is partially replaced with a burner, an air combustion flame and an oxygen burner flame for liquid fuel coexist in the furnace. In this case, as described above, the oxygen burner flame for liquid fuel has a low propulsive force, so that the temperature of the furnace sidewall and the crown may be excessively increased by the air combustion flame. In particular, as shown in FIG. 12, in the glass melting furnace 8, the case where the oxygen burner flame Fo for liquid fuel is opposed to the air combustion flame Fa is remarkable.

Accordingly, the present invention provides a burner for liquid fuel which can obtain a flame with strong propulsion while maintaining a long high-intensity flame, and which forms a flame which is not lifted by an air combustion flame in a glass melting furnace. It is another object of the present invention to provide an optimal mounting structure for mounting the liquid fuel burner on a glass melting furnace and an optimum combustion method at that time.

[0011]

In order to achieve the above object, a liquid fuel burner according to the present invention has a fuel supply nozzle for ejecting liquid fuel, the tip of which is inserted into the center of one axial end of a cylindrical mixing chamber. A fuel fluid passage is formed by the outer circumference of the tip of the fuel supply nozzle and the inner circumference of the mixing chamber, and around a fuel ejection nozzle provided with a spray fuel outlet at the center of the other axial end of the mixing chamber. A liquid fuel burner provided with a passage of a supporting gas provided concentrically with the fuel ejection nozzle, wherein the relationship between the inner diameter Da and the length La of the mixing chamber is La / Da = 0.75. -1.75.

The liquid fuel burner mounting structure of the present invention is characterized in that the liquid fuel burner having the above structure is mounted on a wall surface of a glass melting furnace through a burner tile surrounding the liquid fuel burner. The relationship between the inner diameter Db of the burner tile and the distance Lb between the tip of the burner tile and the tip of the burner for liquid fuel which is mounted retreated from the tip of the burner tile is Lb / Db = 1.5 to
It is characterized by being in the range of 3.0.

Further, in the method for burning a liquid fuel burner according to the present invention, when burning the liquid fuel burner mounted on the wall of the glass melting furnace by the steam mounting structure, oxygen gas is added to the spray fluid and the supporting gas. The liquid fuel ejected from the fuel supply nozzle into the mixing chamber was jetted at a velocity of 5 to 20 m / s, and the mass flow ratio Rs of the mass flow rate S1 of the spray fluid and the mass flow rate S2 of the liquid fuel was S1 / S2 = 0.
The flow rate ratio Rv between the average flow velocity V1 in the passage of the spray fluid and the average flow velocity V2 in the nozzle of the liquid fuel is set in the range of V1 / V2 = 12 to 30, and the mass The momentum ratio M, which is the product of the flow rate ratio Rs and the flow rate ratio Rv, is set to be in the range of 2 to 7.5, and the flow rate of the supporting gas is 15 to 30 m / sec. .

[0014]

1 and 2 show an embodiment of a liquid fuel burner according to the present invention. FIG. 1 is a sectional view of a main part showing a fuel jet nozzle portion, and FIG. It is sectional drawing which shows the state which mounted the burner for fuels on the wall surface of the glass melting furnace via the burner tile.

The liquid fuel burner 11 has a multi-tube structure in which a liquid fuel channel 12, a spray fluid channel 13, and a supporting gas channel 14 are provided concentrically. 1
2 and a fuel jet nozzle 15
Is provided. The fuel ejection nozzle 15 is such that the tip of a fuel supply nozzle 16 communicating with the liquid fuel flow path 12 is inserted into the center of one axial end of a cylindrical mixing chamber 17 having a larger diameter than the nozzle 16. A spray fluid passage 18 communicating with the spray fluid flow path 13 is formed by the outer circumference of the tip of the nozzle and the inner circumference of the mixing chamber 17.
The fuel injection port 19 is provided at the center of the other end in the axial direction. In addition, around the fuel ejection nozzle 15,
A supporting gas passage 20 communicating with the supporting gas passage 14 is provided concentrically.

The burner for liquid fuel 1 thus formed
1, a liquid fuel such as heavy oil or kerosene is supplied to the liquid fuel passage 12, an appropriate gas such as air or oxygen gas is supplied to the spray fluid passage 13, and a gas having a combustion supporting property is provided to the combustion supporting gas passage 14. For example, when a predetermined amount of air or oxygen gas is supplied, respectively, the liquid fuel supplied from the fuel supply nozzle 16 to the mixing chamber 17 is mixed with the spray fluid from the spray fluid passage 18 to form droplets having an appropriate diameter. Combustion flame is generated by mixing with the supporting gas ejected from the fuel spray outlet 19 and ejected from the supporting gas passage 20.

In obtaining a combustion flame as described above, the relationship between the inner diameter Da and the length La of the cylindrical mixing chamber 17 is an important factor, and the relationship between the two is La / Da = 0.7.
By setting to fall within the range of 5 to 1.75,
Good flame is obtained. If the length La is shorter than the inner diameter Da beyond this range, the flame will blow off and stable combustion will not be obtained. Conversely, if the length La is long, the brightness of the flame will be reduced due to rapid combustion, The heat load on the system also increases.

As shown in FIG. 2, when the liquid fuel burner 11 is mounted on the wall surface of the glass melting furnace 22 via a burner tile 21 formed in a cylindrical shape, the tip of the liquid fuel burner 11 is Position is an important factor. That is, the relationship between the inner diameter Db of the burner tile 21 and the distance Lb between the tip of the liquid fuel burner 11 mounted retreated from the tip of the burner tile 21 and the tip of the burner tile 21 is Lb / Db = 1. It is preferable to set so as to fall within a range of 0.5 to 3.0. By setting it in this range, the jetting angle of the flame jetting from the burner tile 21 into the furnace can be set to 10 to 15 degrees, and the inertial force in the axial direction becomes sufficient. When the distance Lb becomes shorter than the inner diameter Db beyond this range, the tip of the burner becomes overheated due to heat radiation from the furnace, and conversely, the distance Lb
When the length is longer, the burner flame collides violently with the inner peripheral surface of the burner tile 21, so that the burner tile 21 is thermally damaged and the flame is disturbed.

In the burner 11 for liquid fuel, it is preferable to use pure oxygen industrially as a combustion supporting gas for the purpose of thermal efficiency and suppression of NOx. Also, the spray fluid is
Since the liquid fuel may be formed into liquid droplets having an appropriate diameter, steam or air is also possible.However, when steam is used, not only the flame temperature is lowered, but also it is intentionally generated to obtain a suitable brightness. It is not preferable because the generation of soot is suppressed, and air is not preferable from the viewpoint of thermal efficiency and suppression of NOx. Therefore, it is preferable to use oxygen as the spray fluid.

The burner 1 for liquid fuel having the above structure
In 1, the ejection speed of the liquid fuel from the fuel supply nozzle 16 is 5 to 20 m / s per second, and the mass flow ratio Rs between the mass flow rate S1 of the spray fluid and the mass flow rate S2 of the liquid fuel is:
S1 / S2 = 0.12 to 0.24, and the flow velocity ratio R between the average flow velocity V1 of the spray fluid in the spray fluid passage 18 and the average flow velocity V2 of the liquid fuel in the fuel supply nozzle 16
Let v be in the range of V1 / V2 = 12 to 30, and the momentum ratio M, which is the product of the mass flow rate ratio Rs and the flow rate ratio Rv, be in the range of Rs × Rv = 2 to 7.5. And the flow rate of the supporting gas is 15 to
It is preferably 30 m.

By burning under such conditions,
The inertia of the flame in the glass melting furnace is sufficient, and the flame is not affected by the air flame, and a flame having a long brightness and a favorable state can be obtained. In particular, oxygen gas, which is a combustion supporting gas, is supplied at a rate of 1
By flowing the liquid fuel at a flow rate of 5 to 30 m, the periphery of the liquid fuel sprayed in the form of droplets is wrapped concentrically and gradually burns from the periphery to form a flame. The flow rate of oxygen gas is 1 per second
If it is less than 5 m, the propulsive power of the flame is weak, and the unburned portion remains downstream of the flame without sufficiently burning. On the other hand, if the speed exceeds 30 m / s, the combustion speed increases, the heat load on the nozzle increases, and a favorable result cannot be obtained.

[0022]

As shown in FIG. 3, as a test furnace 31, a cylindrical furnace body 31a having an inner diameter of 1000 mm and an inner length of 4000 mm was used.
At one end, a burner for liquid fuel 11 having an outer diameter of 145 mm is installed via a burner tile 21 having an inner diameter of 150 mm, and at the other end, an exhaust port 32 having an inner diameter of 600 mm is provided. A device provided with a thermocouple so as to be able to measure in (h) to (h) was manufactured. Fuel C is supplied to the burner 11 at a flow rate of 200 liters / hour as fuel.
Oxygen gas was supplied in total of 400 Nm ³ / h as a combustion supporting gas and a spray fluid. The C heavy oil was supplied after being preheated to 110 ° C. (viscosity 15 cP) in order to lower the viscosity.

EXPERIMENTAL EXAMPLE 1 In setting a burner on a burner tile, Lb in FIG. 2 was set to 300 mm (Lb / Db = 2.0), and the shape of a cylindrical mixing chamber was examined. That is, the inner diameter Da of the mixing chamber in FIG.
Was changed to produce seven types of burners having a La / Da value of 0.5 to 2.0. Then, the flow rate of the oxygen gas for spray from the spray fluid passage was set to 23.4 Nm ³ / h, and the spray characteristics were examined without burning. At this time, the mass flow ratio R
s is 0.18, flow velocity ratio Rv is 26.5, momentum ratio M is 4.8, and the flow velocity of combustion oxygen, which is a supporting gas, is 25 m.
/ S. In each burner, a photograph of the jet flow from the burner tile was taken and the result of measuring the jet angle was shown in Table 1.
Shown in A Sauter average particle diameter and a flow velocity of a fuel droplet were measured at a position 500 mm from the tip of the burner (Ae, USA).
2D-PA / RSA system manufactured by metrics)
FIG. 4 shows the results of the measurement.

[0024]

[Table 1]

From Table 1, it can be seen that when the value of La / Da is small, the ejection angle is small, and the value of La / Da is large and the ejection angle is large. Also, from FIG.
When the value of a / Da is small, the droplet is large and its speed is small. It can be seen that as the value of La / Da increases, the diameter of the droplet decreases, and the speed increases.

Experimental Example 2 Based on the results of Experimental Example 1, the value of La / Da was 0.5,
As shown in FIG. 3, three types of 1.0 and 2.0 were selected, and assuming a co-firing with an air flame in an actual glass melting furnace,
400 Nm ³ / h of air was sent from the exhaust port 32 by the blower 33 to examine how the flame was affected. FIG. 5 shows the result of the temperature measurement of the furnace inner wall.

From FIG. 5, when La / Da = 1.0,
A good temperature distribution can be obtained. However, when La / Da = 0.5, the flame is disturbed because the air is blown by the blower and the flame is disturbed, and the temperature of the furnace inner wall sometimes exceeds 1600 ° C. Poor, incomplete combustion and high unburned content were observed. When La / Da = 2.0, combustion is rapid and flame luminance is also reduced, the flame is short, and the temperature of the inner surface of the wall does not reach far. Further, the same experiment was performed with each burner of Experimental Example 1. As a result, it was found that a good flame could be obtained if the value of La / Da was in the range of 0.75 to 1.75.

From the results of Experimental Examples 1 and 2, it is considered that when the value of La / Da is 0.5, the ejection angle is too small as 5 degrees, the flame is not sufficiently dispersed, and poor combustion occurs. When the value of La / Da is 2.0, the ejection angle is 1
It was observed that the temperature increased to 7.5 degrees, the combustion was fast, the brightness of the flame decreased, and the flame length was short, and the heat load on the nozzles and the like was large and inappropriate. Therefore, the ejection angle is preferably in the range of 10 to 15 degrees.

EXPERIMENTAL EXAMPLE 3 The same test was carried out with the value of La / Da fixed at 1.0 and the conditions (Lb / Db) for setting the burner on the burner tile were variously changed. As a result, the value of Lb / Db becomes 1.5 to
When it was in the range of 3.0, a good flame was obtained, but Lb /
If the value of Db is less than 1.5, the burner tip is overheated, and if it exceeds 3.0, heat damage to the burner tile and disturbance of the flame occur.

Experimental Example 4 Next, the effect of the ejection speed of the liquid fuel into the mixing chamber was examined. The value of La / Da is set to 1.0, and the fuel ejection speed is changed to 5, 10, 15, 2 per second by changing the diameter of the fuel supply nozzle.
Four types of nozzles of 0 m were prepared, and oxygen for spraying was supplied at 27 Nm ³ / s, and the same test as in Experimental Example 2 was performed. In this range, there was no particular difference in the state of the flame and the like, and good results were obtained. At this time, the mass flow ratio Rs was 0.21, and the flow rate of the combustion oxygen was 25.0 m / s.

Experimental Example 5 In order to investigate the effect of the mass flow ratio Rs, the diameter Da of the mixing chamber was adjusted to 5.0, 6.0, 6.8, 7.5, 8.2 mm.
5 types of nozzles were prepared. Using these nozzles, the mass flow ratio Rs was 0.06, 0.1, respectively.
The amount of oxygen gas for spraying was adjusted to be 2,0.18,0.24,0.3. At this time, the flow velocity ratio Rv is 26.
It was 5. The flow rate of combustion oxygen was fixed at 25 m / s. In the same manner as in Experimental Examples 1 and 2, the ejection angle, spray characteristics (droplets and speed), and furnace wall temperature were measured. The results are shown in Table 2 and FIGS. Further, a thermocouple was attached to the tapered end of the fuel ejection nozzle to measure the temperature. FIG. 8 shows the result.

[0032]

[Table 2]

From these results, it was found that the mass flow ratio Rs was 0.06
In the case of, the droplets are insufficiently refined, the flow velocity is slow, and the flame becomes unstable, and it is easy to be agitated.The agitated flame contacts the furnace wall and raises the temperature of the furnace wall locally. . on the other hand,
When the mass flow ratio Rs is 0.3, the flow velocity of the droplet is high and the thrust of the flame is high, but the droplet is small and burns rapidly (the temperature of the nozzle is abnormally high in FIG. 8), so that the long flame And the temperature of the furnace wall decreases rapidly with distance.

Experimental Example 6 Next, the influence of the flow velocity ratio Rv was examined. La in the mixing chamber
Assuming that the value of / Da is 1, 10.9, 9.6,
Five types of nozzles having the sizes of 7.5, 6.8, and 6.0 mm were prepared. Using these nozzles, the flow velocity ratio Rv is
The flow rate of the oxygen for spraying was adjusted to 9.3, 12.5, 23.2, 30.9, and 44.2. At this time, the mass flow ratio Rs is 0.21, and the momentum ratio M is 1.9, 2.6, 4.9, 6.5, 9.3, respectively. The fuel flow rate was 10 m / s, and the combustion oxygen flow rate was 2 m / s.
5 m / s. As in Experimental Example 1, the ejection angle and the spray characteristics (droplets and speed) were measured. The results are shown in Table 3 and FIG. FIG. 10 shows the result of measuring the wall surface temperature in the same manner as in Experimental Example 2.

[0035]

[Table 3]

From these results, when the flow velocity ratio Rv was 9.3, although the jetting angle was 11.2 degrees, the flame was violently heated and contacted the ceiling, causing thermal damage. When the flow velocity ratio Rv was 44.2, the flame was short and was not heated to a long distance because the droplet diameter was small.

Experimental Example 7 Next, the flow rate of combustion oxygen was examined. Da and La
Used a burner of 7.1 mm (La / Da = 1.0) and inserted a ring-shaped sleeve into the combustion support gas passage to adjust the cross-sectional area, and adjusted the flow rate of combustion oxygen to 8.7, 15,
It was changed to 25, 30, and 45 m / s, and the effect was examined. At this time, the mass flow ratio Rs is 0.21, the flow velocity ratio R
v is 26.5 and the fuel flow rate is 10 m / s. When the flow rate of oxygen for combustion was 8.7 m / s, the propulsion of the flame was small, and it was flooded by the opposite gas. On the other hand, the combustion oxygen flow rate is 45 m
In the case of / s, combustion was promoted too much and the heat load of the burner was large, which was not suitable for practical use. The oxygen flow rate for combustion is 1
At 5, 25, 30 m / s, a good flame was obtained.

Examples and Comparative Examples Based on the results of the above experimental examples, a burner was attached to an actual glass melting furnace shown in FIG. 12 and operation was observed under the following five conditions A to E to observe the results. The air flame Fa is shown in FIG.
In the above, since the gas is blown out alternately from the jet ports (9a, 9b) on both sides of the furnace, the gas becomes parallel to or opposed to the oxygen flame. The inner diameter D of the burner tile was 150 mm, and Lb / Db = 2.0. Table 4 shows the results.

[0039]

[Table 4]

Under the condition A, poor combustion occurs, the flame is violently heated, and there is a local temperature rise on the furnace ceiling and the burner installation wall, which is not suitable for practical use. This is the mass flow ratio R
This is because s is as small as 0.06. Conditions B, C, and D are
It was confirmed that the flame length, brightness, and stability were good, heat transfer to the glass was effective, and the practicability was high. In condition E, combustion was performed rapidly, the combustion noise was loud, short flame, low brightness, and poor heat transfer to the glass. In this case, erosion was observed inside the furnace of the burner tile. This is because the combustion oxygen is as fast as 45 m / s.

[0041]

As described above, according to the present invention,
A flame burner for liquid fuel which has good flame length, brightness and stability, and is particularly suitable for application to a glass melting furnace can be obtained.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a main part showing one embodiment of a fuel ejection nozzle portion.

FIG. 2 is a cross-sectional view showing a state in which a liquid fuel burner is mounted on a wall surface of a glass melting furnace via a burner tile.

FIG. 3 is a sectional view of a test furnace manufactured in an example.

FIG. 4 is a diagram showing a relationship between a particle size and a flow rate in Experimental Example 1.

FIG. 5 shows measurement positions and La / Da in Experimental Example 2.
FIG. 4 is a diagram showing a relationship between the value of the temperature and the furnace wall temperature.

FIG. 6 is a diagram showing the relationship between the particle size and the flow rate in Experimental Example 5.

FIG. 7 shows measurement positions and La / Da in Experimental Example 5.
FIG. 4 is a diagram showing a relationship between the value of the temperature and the furnace wall temperature.

FIG. 8 is a diagram showing a relationship between a mass flow ratio and a nozzle temperature.

FIG. 9 is a diagram showing the relationship between the particle size and the flow rate in Experimental Example 6.

FIG. 10 shows measurement positions and La / D in Experimental Example 6.
It is a figure which shows the relationship between the value of a and furnace wall temperature.

FIG. 11 is a sectional view showing an example of a conventional liquid fuel oxygen burner.

FIG. 12 is a sectional plan view showing an example of a glass melting furnace.

[Explanation of symbols]

11 ... burner for liquid fuel, 12 ... liquid fuel passage, 13
… Spray fluid flow path, 14… support gas path, 15… fuel ejection nozzle, 16… fuel supply nozzle, 17… mixing chamber, 18…
Atomizing fluid passage, 19: atomized fuel jet, 20: supporting gas passage, 21: burner tile, 22: glass melting furnace, 3
1 ... test furnace, 32 ... exhaust port

Claims (3)

[Claims] 1. A tip of a fuel supply nozzle for ejecting liquid fuel is inserted into the center of one end in the axial direction of a cylindrical mixing chamber, and a spray fluid is formed by an outer circumference of the tip of the fuel supply nozzle and an inner circumference of the mixing chamber. Around the fuel ejection nozzle provided with a spray fuel ejection port at the center of the other end of the mixing chamber in the axial direction, and a support gas passage provided concentrically with the fuel ejection nozzle. A burner for a liquid fuel, wherein the relationship between the inner diameter Da and the length La of the mixing chamber is La / Da = 0.7.
A burner for a liquid fuel, which is in the range of 5 to 1.75. 2. The liquid fuel burner according to claim 1,
When mounting the burner tile on the wall surface of the glass melting furnace through a burner tile surrounding the burner for liquid fuel, the inner diameter Db of the burner tile, the tip of the burner for liquid fuel mounted by being retracted from the tip of the burner tile, and the burner tile Lb / Db = Lb / Db =
A mounting structure for a burner for a liquid fuel, characterized in that the range is 1.5 to 3.0. 3. When burning the liquid fuel burner mounted on the wall of the glass melting furnace by the mounting structure according to claim 2, an oxygen gas is used as the spray fluid and the supporting gas, and a mixing chamber is provided from a fuel supply nozzle. And the mass flow ratio Rs between the mass flow rate S1 of the spray fluid and the mass flow rate S2 of the liquid fuel is set to 5 to 20 m per second.
S1 / S2 = 0.12 to 0.24, and the flow velocity ratio Rv between the average flow velocity V1 in the passage of the spray fluid and the average flow velocity V2 in the nozzle of the liquid fuel is V1 / V2 = 12 to 30. And the momentum ratio M, which is the product of the mass flow ratio Rs and the flow velocity ratio Rv, is set to be in the range of 2 to 7.5, and the flow rate of the supporting gas is set to 1 / sec.
A method for burning a liquid fuel burner, comprising 5 to 30 m.