JP2008045836A - Burner tip, burner device and boiler apparatus including it - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a burner tip, effectively restraining burning vibration. <P>SOLUTION: In this boiler apparatus, a plurality of fuel injection main holes 21 and a plurality of fuel injection sub-holes 22 are alternately disposed in the peripheral direction of the burner tip 11, the ratio of the total opening area of the fuel injection main holes 21 to the total opening area of the fuel injection sub-holes 22 is set to 80:20 - 90:10, and the fuel injection angle θ3 of the fuel injection sub-holes 22 is larger than that θ2 of the fuel injection main holes 21. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a burner device, and more particularly to a burner tip that is attached to a burner main end of a burner device and injects a fuel fluid.

  Low NOx combustion technology for boiler equipment includes exhaust gas recirculation method and two-stage combustion method, but the two-stage combustion method is not applied when fuel with a small amount of N in the fuel, for example, LNG, is used. In both cases, since NOx reduction can be achieved, a single-stage combustion method in which all combustion air is introduced from the burner throat is often employed.

FIG. 6 is a partial schematic configuration diagram of a boiler apparatus equipped with a center gas nozzle type burner apparatus. A furnace 2 is defined by being surrounded by a furnace wall 1, and a number of burner devices 3 are provided in a plurality of stages in a vertical direction in a wind box (not shown) installed outside the furnace wall 1. ing.

In the burner device 3, a primary air supply pipe 5 that forms a primary air supply path 4 is installed on the inner side toward the furnace 2, and a predetermined interval is provided outside the primary air supply pipe 5. The secondary air supply pipe 6 is installed concentrically, and a secondary air supply path 7 is formed between the primary air supply pipe 5 and the secondary air supply pipe 6.

The primary air supply pipe 5 is provided with a primary air inlet damper 8 for adjusting the primary air supply amount. The secondary air supply pipe 6 is provided with a secondary air register 9 for applying a turning force to the secondary air. Since the primary air supply pipe 5 is not provided with a register, the primary air is supplied to the furnace 2 as a straight flow.

A burner main pipe 10 is inserted and installed in the inner central part of the primary air supply pipe 5. A burner tip 11 is attached to the front end of the burner main 10 on the furnace 2 side, and a swirler 12 is installed immediately behind the burner tip 11. A diameter-expanded portion 13 that gradually expands toward the tip side is formed at a portion facing the swirler 12 at the tip side of the furnace side of the primary air supply pipe 5.

Connected to the rear end side of the burner main pipe 10 are a liquid fuel supply pipe 14 for supplying a liquid fuel such as dimethyl ether and a atomization medium supply pipe 15 for supplying a atomization medium made of vapor or compressed air. ing. This burner device is characterized by its simple structure and low manufacturing cost.

FIG. 7 is a front view of a conventional burner tip 11, and FIG. 8 is a cross-sectional view of the burner tip 11.

As shown in FIG. 8, a plurality of liquid fuel supply holes 17 for supplying the liquid fuel 16 and a plurality of atomization medium supply holes 19 for supplying the atomization medium 18 are provided at the rear part of the burner chip 11. The tips of the supply holes 17 and 19 communicate with the atomization chamber 20. A plurality of fuel injection main holes 21 are provided in the circumferential direction further from the atomization chamber 20 toward the tip, and all the fuel injection main holes 21 have a gas injection angle θ1 (for example, 90 °) about the burner main axis X. Are inclined to each other.

As shown in FIG. 6, the liquid fuel 16 supplied from the liquid fuel supply pipe 14 and the atomization medium 18 supplied from the atomization medium supply pipe 15 pass through the burner main pipe 10 and are liquid in the burner tip 11. The fuel is supplied to the fuel supply hole 17 and the atomization medium supply hole 19, respectively. Although not shown, the burner main pipe 10 has a double pipe structure. For example, the liquid fuel 16 circulates in the inner pipe, and the atomization medium 18 circulates between the inner pipe and the outer pipe. The two do not mix.

Both the liquid fuel 16 and the atomization medium 18 are supplied to the atomization chamber 20 in the center of the burner chip, atomized (gasified) by mixing, and then ejected from each fuel injection main hole 21 into the furnace 2 for combustion. To do.

Regarding the burner device, the following patent documents can be cited.
Japanese Utility Model Publication No. 2-54006 JP 58-75613 A JP 2003-172505 A Japanese Utility Model Publication No. 61-13128 JP 58-64420 A

In order to reduce NOx and SOx emissions in boiler equipment that burns oil-based fuels such as heavy oil with a high concentration ratio of N and S as environmental regulations become stricter, a part of the burner equipment is divided into N More and more cases are being replaced with fuels having a low concentration ratio of S.

One such fuel is dimethyl ether (DME). This fuel has a feature that soot is hardly generated because C / H is low and oxygen is present in the fuel. Since the concentration ratio of N and S is overwhelmingly lower than that of oil-based fuels such as C heavy oil, it is highly effective in reducing NOx concentration, SOx concentration, and dust concentration in boiler exhaust gas.

  In an oil-based fuel fired boiler device such as heavy oil, when the burner device is modified for DME combustion, there are the following problems.

  Oil-based fuels such as heavy oil take a long time to spray and evaporate and do not match the frequency of occurrence of combustion vibration, so that combustion vibration hardly occurs. However, DME is easy to vaporize, and the combustion speed is overwhelmingly faster than LNG and heavy oil, so that an environment in which combustion vibration is likely to occur is obtained. This is because a coupled system in which the amount of heat generated in the vicinity of the burner device fluctuates due to pressure pulsation in the furnace, and pressure fluctuations occur due to the fluctuation, is likely to be established.

When combustion vibration occurs, troubles such as noise, damage to the boiler device structure, and failure to achieve boiler load (steam generation amount) occur.

An object of the present invention is to provide a burner tip, a burner device, and a boiler device equipped with the burner tip that can eliminate the above-mentioned drawbacks of the prior art and effectively suppress combustion vibration.

  To achieve the above object, the present invention provides a fuel supply path for supplying a fuel such as DME, a atomization medium supply path for supplying a atomization medium such as steam and compressed air, and the fuel supply path. For a burner chip having a atomization chamber for atomizing fuel supplied from the atomization medium supply path from the atomization medium supply path and a fuel injection hole for injecting the atomized fuel It is.

According to a first means of the present invention, the fuel injection hole comprises a plurality of fuel injection main holes having a large hole diameter and a plurality of fuel injection sub-holes having a hole diameter smaller than the fuel injection main hole. Main holes and fuel injection sub-holes are provided alternately in the circumferential direction of the burner tip,
The ratio of the total opening area of the fuel injection main hole and the total opening area of the fuel injection sub-hole is set in a range of 80:20 to 90:10,
In addition, the fuel injection angle of the fuel injection sub-hole is larger than the fuel injection angle of the fuel injection main hole.

  According to a second means of the present invention, in the first means, the fuel injection angle of the fuel injection main hole is set to 60 to 90 °, and the fuel injection angle of the fuel injection sub-hole is set to 80 to 120 °. It is characterized by being set in between.

  According to a third means of the present invention, in the first or second means, the number of the fuel injection sub-holes is larger than the number of the fuel injection main holes.

  According to a fourth means of the present invention, in the first to third means, the fuel is dimethyl ether.

  According to a fifth means of the present invention, there is provided a burner main pipe for individually supplying the fuel and the atomizing medium, a flame holder provided at the tip side of the burner main pipe, and a tip side of the flame holder. In the burner apparatus provided with the provided burner chip, the burner chip is the first to fourth burner chips.

  According to a sixth means of the present invention, in the fifth means, the burner main pipe is inserted and disposed in a central portion of a primary air supply path for supplying primary air into the furnace as a straight flow, and the primary air supply A secondary air supply path for supplying secondary air into the furnace as a swirling flow is provided on the outer peripheral side of the path.

  According to a seventh aspect of the present invention, in the boiler apparatus in which the burner apparatus is installed on the furnace wall that defines the furnace, the burner apparatus is the burner apparatus of the fifth or sixth means. is there.

  The present invention is configured as described above, and combustion vibration can be effectively suppressed by making both the stabilization of the flame and the lengthening of the flame compatible.

Conventionally, since the center gas nozzle type burner has a gas nozzle inside the flame holder, there has been no concept of flame holding fuel (sub fuel) and main fuel involved in boiler load.

Since the combustion vibration is generated in the coupled system of the burner and the boiler furnace, the combustion vibration is generated if the matching between the burner and the furnace is poor.

This combustion vibration is an acoustic resonance phenomenon (air column resonance phenomenon) with the furnace, and the air amount or fuel amount of the burner changes due to the sound pressure, heat generation fluctuation occurs, and the sound pressure fluctuation develops in a chain. Since these are feedback loops, combustion oscillation does not occur if any factor forming the loop is removed.

The main cause of fluctuating heat generation is poor ignition. If the flame holding is strengthened, even if the sound pressure fluctuation from the inside of the furnace is received, it does not lead to a large fluctuation in heat generation, so that combustion vibration does not occur.

In order to reduce the potential of combustion vibration, it is important to realize uniform combustion, that is, slow combustion, from the vicinity of the burner to the entire furnace, and it is important to achieve both stable flame holding and slow combustion.

Since the conventional center nozzle type burner tip has only a fuel injection main hole as shown in FIGS. 7 and 8, in order to achieve stable flame holding, the gas injection direction (gas injection angle θ1) must be widened. However, if so, slow combustion is not possible, and combustion vibrations are likely to occur.

  Next, an embodiment of the present invention will be described with reference to the drawings. 1 is a front view of a tip portion of a burner tip according to an embodiment of the present invention, FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1, and FIG. 3 is an enlarged cross-sectional view of the tip portion of the burner tip.

As shown in FIG. 2, at the rear part of the burner chip 11, a liquid fuel supply hole 17 for supplying a liquid fuel 16 made of dimethyl ether (DME) and a atomizing medium 18 made of vapor or compressed air are used. A plurality of medium supply holes 19 are provided, and the tips of the supply holes 17 and 19 communicate with the atomization chamber 20. A plurality of fuel injection main holes 21 and fuel injection sub-holes 22 are provided in the circumferential direction from the atomization chamber 20 toward the tip.

In the case of this embodiment, as shown in FIG. 1, four fuel injection main holes 1 are provided at equal intervals of 90 degrees in the circumferential direction of the burner tip 11, and the injection of the fuel injection main holes 1 as shown in FIG. The angle θ2 is set to 70 ° (elevation angle 35 °). In addition, two fuel injection sub-holes 22 and 22 are provided in parallel at the intermediate position between the fuel injection main hole 21 and the fuel injection main hole 21 in the circumferential direction of the burner tip 11. A total of eight are provided. The injection angle θ3 of the fuel injection sub-hole 2 is set to 110 ° (elevation angle 55 °). Therefore, there is a relationship of θ2 <θ3.

As shown in FIG. 3, the front inclined surface 23 that forms the fuel injection main hole 21 and the fuel injection sub-hole 22 and defines the atomization chamber 22 has an equal inclination angle α with respect to the burner main axis X. Although inclined, an angle β1 (about 90 °) formed by the front inclined surface 23 and the axis 24 of the fuel injection main hole 21 is an angle β2 formed by the front inclined surface 23 and the axis 25 of the fuel injection sub-hole 22. (Β1> β2), and the fuel injection sub-hole 22 is drilled with respect to the front inclined surface 23 in a state tilted with respect to the fuel injection main hole 21.

As shown in the figure, the intersection Y between the axis 24 of the fuel injection main hole 21 and the burner main axis X and the intersection Z between the axis 25 of the fuel injection sub-hole 22 and the burner main axis X are both burner of the atomization chamber 22. Although present on the main axis X, the intersection Z is located closer to the front inclined surface 23 than the intersection Y.

As shown in FIG. 1, two fuel injection sub-holes 22 are formed in pairs along the circumferential direction of the burner tip 11, but the fuel injection sub-holes 22 a close to the outer peripheral side of the burner tip 11 The fuel injection sub-hole 22b that opens to a position on the outer peripheral side of the burner tip 11 with respect to the virtual circle 26 that connects the center points of the fuel injection main holes 21 and is closer to the inner side of the burner tip 11 is located on the burner tip 11 than the virtual circle 26. Open to the inner position.

In this embodiment, the fuel injection sub-hole 22 is opened by dividing the virtual circle 26 between the outside and the inside as described above. However, the fuel injection sub-hole 22 may be opened side by side in the circumferential direction of the burner tip 11. it can.

The inner diameter d2 of the fuel injection sub-hole 22 is designed to be smaller than the inner diameter d1 of the fuel injection main hole 21 (inner diameter d1> inner diameter d2), and the fuel flow rate injected from the fuel injection main hole 21 is 80% of the total fuel flow rate. The fuel flow rate injected from the fuel injection sub-hole 22 ranges from 10% to 20% by volume (20% by volume in the present embodiment) of the total fuel flow rate. The total opening area ratio between the fuel injection main hole 21 and the fuel injection sub hole 22 is set.

The liquid fuel 16 is supplied to the atomization chamber 20 in the center of the burner together with the atomization medium 18, atomized by mixing, and then ejected from the fuel injection main holes 21 and the fuel injection sub-holes 22 into the boiler furnace 2. Burn. As described above, since the fuel injection main holes 21 and the fuel injection sub-holes 22 are provided alternately and equally, combustion of the gasified fuel is performed in a balanced manner in the circumferential direction of the burner main shaft X.

  As shown in FIG. 6, the structure of the boiler device is provided with a swirler 4 having a large number of swirl vanes on the tip side of the burner main pipe 10, and a burner tip 11 on the tip side. The burner main pipe 10 is installed at the center of the primary air supply pipe 5, and the secondary air supply pipe 6 is provided on the outer periphery of the primary air supply pipe 5. As a result, a center gas nozzle type triple structure is formed. It has become.

  The DME that is the liquid fuel 16 is supplied to the burner main pipe 10 together with the vapor or compressed air that is the atomizing medium 18. The liquid fuel 16 and the atomizing medium 18 are conveyed to the burner tip 11 at the tip of the burner main pipe 10 without joining in the burner main pipe 10.

  Both the liquid fuel 16 and the atomization medium 18 supplied to the burner chip 11 are injected into the atomization chamber 20 in the burner chip 11, and the liquid fuel 16 is subjected to a strong shearing force by the atomization medium 18 and atomized. The fuel is injected into the furnace 2 from the fuel injection main holes 21 and the fuel injection sub-holes 22. Since DME which is the liquid fuel 16 is vaporized at a normal temperature of 0.6 MPa, when released into the furnace 2, the pressure is reduced and the gas is instantly gasified and burned.

  The primary air supplied to the center of the burner device is a straight flow, but a strong swirl force is given to a part of the primary air by a swirler (swivel unit) 12 provided at the nozzle outlet portion, and FIG. As shown, a combustion air circulation region 27 is formed on the downstream side of the swirler 12. By supplying the gas fuel from the burner tip 18 to the combustion air circulation area 27, the flame can be stably maintained. On the other hand, the secondary air is jetted into the furnace 2 with a turning force applied by the register 9 (see FIG. 6).

  Since the gas burner has a very high fuel combustibility, that is, a combustion speed, compared with a burner that burns coal or oil, the gas burner is often operated under a condition in which excess air in the boiler apparatus is reduced. When operating under such conditions, combustion vibrations are likely to occur. This is because combustion vibrations tend to occur when the amount of heat generated near the burner is maximized.

  Next, the combustion vibration test of the conventional burner device and the burner device according to the embodiment of the present invention will be described. The specifications of the burner tip subjected to the test are as follows.

Type A (equivalent to the prior art shown in FIG. 8):
Six holes with the same hole diameter are provided at equal intervals in the circumferential direction, and the gas injection angle of each hole is 90 °.

Type B (comparative example of the present invention):
Four main holes in the circumferential direction are provided at intervals of 90 °, and four sub-holes having a diameter smaller than the main hole are provided at a midpoint between the main holes and the main hole / sub-hole fuel flow ratio is 80/20. In any of the holes, the gas injection angle is 90 °, and the gas injection angle difference between the main hole and the sub hole = 0 °.

Type C (Example 1 of the present invention):
A total of eight sub-holes with a diameter smaller than that of the four main holes at intervals of 90 ° in the circumferential direction and two main holes smaller than the main hole are provided in the middle position between the main hole and the main hole / sub-hole fuel flow ratio 90 / 10, the gas injection angle of the main hole is 80 °, the gas injection angle of the sub hole is 110 °, and the gas injection angle difference between the main hole and the sub hole = 30 °.

Type D (Example 2 of the present invention):
A total of eight sub-holes with a diameter smaller than that of the four main holes at intervals of 90 ° in the circumferential direction and two main holes smaller than the main hole are provided in the middle position between the main hole and the main hole / sub-hole fuel flow ratio 90 / 10, the gas injection angle of the main hole is 70 °, the gas injection angle of the sub hole is 110 °, and the gas injection angle difference between the main hole and the sub hole = 40 °.

Type E (Example 3 of the present invention):
A total of eight sub-holes with a diameter smaller than that of the four main holes at intervals of 90 ° in the circumferential direction and two main holes smaller than the main hole are provided in the middle position between the main hole and the main hole / sub-hole fuel flow ratio 90 / 10, the gas injection angle of the main hole is 90 °, the gas injection angle of the sub hole is 120 °, and the gas injection angle difference between the main hole and the sub hole = 30 °.

Type F (Example 4 of the present invention):
A total of eight sub-holes with a diameter smaller than the main hole are provided in the middle position between the four main holes at intervals of 90 ° in the circumferential direction and two main holes smaller than the main hole. / 20, the gas injection angle of the main hole is 70 °, the gas injection angle of the sub hole is 110 °, and the gas injection angle difference between the main hole and the sub hole = 40 °.

The combustion vibration level was measured using a burner apparatus equipped with each type of burner tip. Here, the combustion vibration level is measured by installing a number of pressure detection elements at predetermined intervals in the combustion vibration level measuring furnace, measuring pressure fluctuations accompanying combustion in real time, and determining the amplitude (mmAg) of the resonance frequency of the furnace. The following table shows the amplitude ratio of each burner apparatus when the conventional type A amplitude is set to 100. It can be evaluated that the lower this value is, the lower vibration the burner device is. This combustion vibration test was conducted using a burner apparatus having a 13A city gas flow rate of 200 m ³ N / h.

table
Type A (conventional technology) 100
Type B (Comparative example) 52
Type C (Example 1) 31
Type D (Example 2) 20
Type E (Example 3) 16
Type F (Example 4) 14

As is apparent from this combustion vibration test, the type B as a comparative example was able to lower the combustion vibration level to about half compared to the conventional type A. However, according to the present invention, the vibration level is further reduced to about 1/3. We were able to lower it to the following.

  The reason for this will be described with reference to FIG. 4 showing the gas flow state in the downstream portion of the swirler 12. Gas fuel is injected at an angle from the nozzle tip. The conventional type A or the type B of the comparative example is injected and burned at a uniform elevation angle as indicated by an arrow 28 in the figure. On the other hand, in types C to F, gas fuel is injected from the main hole in the direction of arrow 29, gas fuel is injected from the sub hole in the direction of arrow 30, and is injected at the respective elevation angles of the main hole and the sub hole. Burned.

  Next, the mixed diffusion state of air and fuel will be described. As shown in FIG. 4, a recirculation region 27 is formed in the wake of the swirler 12. In the conventional type A, as shown by the arrow 28, the injected fuel gas penetrates the recirculation gas, and thus is partially taken into the recirculation region 27, but the fuel concentration in this region 27 is low and stable combustion is achieved. It cannot be continued.

  On the other hand, in types C to F, it is possible to suppress the momentum by increasing the flow rate of fuel injected from the sub-holes to 10 to 20% by volume and increasing the number of sub-holes from the number of main holes. The fuel injected from the auxiliary hole is successfully taken in without passing through the recirculation region 27. That is, in comparison with the case where the main hole alone injects and burns uniformly, the fuel from the main hole burns slowly (heat generation) inside the furnace, and the fuel from the sub hole is the main hole. It is possible to stably burn in the swirler 27, that is, the downstream portion of the flame holder, without being affected by the injection angle. It has been proved that these mutual effects are effective in suppressing combustion vibration.

  Figure 5 shows various experiments on the effects of the fuel injection angle of the main and sub-holes and the fuel injection ratio of the sub-hole and the fuel flow ratio (sub-hole fuel flow / total fuel flow) on the combustion state. The results of evaluating them were summarized.

  An appropriate injection angle range with respect to the main hole is 60 to 90 °, preferably 60 to 70 °. If the angle is smaller than that, the flame becomes long as a phenomenon, and troubles such as soot and unburned content occur. On the other hand, when the angle is larger than the above-mentioned range, the phenomenon becomes a short flame and combustion vibration is generated as a trouble.

  An appropriate injection angle range for the sub-hole is 80 to 120 °, and even if the angle is smaller or larger than that, flame holding failure occurs as a phenomenon, and combustion vibration occurs as a problem.

  An appropriate range of the sub-hole fuel flow ratio is 10 to 20% by volume. If the sub-hole fuel flow ratio is less than this range, flame holding failure occurs as a phenomenon, and combustion vibration occurs as a problem. On the other hand, it was found that when the sub-hole fuel flow ratio is larger than the above-mentioned range, the fuel becomes excessive as a phenomenon, and soot and unburned fuel are generated as a trouble.

  According to the present invention, since the stabilization of the flame and the lengthening of the flame are compatible, the combustion vibration can be suppressed, and the mixing of the combustion air and the gas fuel is slightly suppressed. As a result, Thermal-NOx can be suppressed, exhaust gas recirculation equipment and two-stage combustion equipment are not required, and the equipment cost can be greatly reduced.

  In the above embodiment, the plurality of fuel injection sub-holes are drilled in parallel. However, the fuel injection angles of the plurality of fuel injection sub-holes may be slightly different and drilled in parallel.

It is a front view of the burner chip concerning an embodiment of the present invention. It is sectional drawing on the II-II line of FIG. It is an expanded sectional view of the tip part of the burner tip. It is explanatory drawing which shows the flow of the gas of a swirler wake part. It is explanatory drawing which shows the appropriate range of the gas fuel injection angle of the main hole of the burner chip | tip which concerns on embodiment of this invention, and a subhole, and a subhole fuel flow ratio. It is a partial schematic block diagram of the boiler apparatus equipped with the burner apparatus. It is a front view of the conventional burner tip. It is sectional drawing of the burner tip.

Explanation of symbols

  1: furnace wall, 2: furnace, 3: burner device, 4: primary air supply path, 5: primary air supply pipe, 6: secondary air supply pipe, 7: secondary air supply path, 8: primary Air inlet damper, 9: secondary air register, 10: burner main pipe, 11: burner tip, 12: swirler, 13: enlarged diameter part, 14: liquid fuel supply pipe, 15: atomization medium supply pipe, 16: Liquid fuel, 17: Liquid fuel supply hole, 18: Atomization medium, 19: Atomization medium supply hole, 20: Atomization chamber, 21: Fuel injection main hole, 22: Fuel injection subhole, 23: Front side inclination 24, axis of main hole, 25: axis of sub hole, 26: virtual circle, 27: combustion air circulation region, X: burner main axis, θ2: gas injection angle of fuel injection main hole, θ3: sub fuel injection The gas injection angle of the hole.

Claims (7)

A fuel supply path for supplying fuel, a atomization medium supply path for supplying an atomization medium, and a fuel for atomization supplied from the fuel supply path by the atomization medium supply path. In a burner chip having a atomization chamber for atomizing and a fuel injection hole for injecting atomized fuel,
The fuel injection hole includes a plurality of fuel injection main holes having a large hole diameter and a plurality of fuel injection sub holes having a hole diameter smaller than the fuel injection main hole, and the fuel injection main hole and the fuel injection sub hole are burners. Provided alternately in the circumferential direction of the chip,
The ratio of the total opening area of the fuel injection main hole and the total opening area of the fuel injection sub-hole is set in a range of 80:20 to 90:10,
The burner tip is characterized in that the fuel injection angle of the fuel injection sub-hole is larger than the fuel injection angle of the fuel injection main hole. The burner tip according to claim 1, wherein a fuel injection angle of the fuel injection main hole is set between 60 and 90 °.
A burner tip, wherein a fuel injection angle of the fuel injection sub-hole is set between 80 and 120 °.   The burner tip according to claim 1 or 2, wherein the number of the fuel injection sub-holes is larger than the number of the fuel injection main holes.   The burner tip according to any one of claims 1 to 3, wherein the fuel is dimethyl ether. A burner main that individually supplies fuel and atomization medium, a flame holder provided on the tip side of the burner main, and a burner tip provided on the tip side of the flame holder In the burner device,
The burner device according to any one of claims 1 to 4, wherein the burner tip is the burner tip.   6. The burner apparatus according to claim 5, wherein the burner main is inserted and disposed in a central portion of a primary air supply path for supplying primary air into the furnace as a straight flow, and is disposed at an outer peripheral side of the primary air supply path. A burner device characterized in that a secondary air supply passage for supplying secondary air as a swirling flow into the furnace is provided.   The boiler apparatus which installed the burner apparatus in the furnace wall which divides and forms a furnace, The said burner apparatus is a burner apparatus of Claim 5 or 6. The boiler apparatus characterized by the above-mentioned.

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