JP2000074371A - Burner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To safely and completely combust fuel gas irrespective of a supply flow rate of the fuel gas. SOLUTION: An internal cylinder 10 for defining a first flow passage 45 is provided outside a nozzle 20 including a main nozzle hole, and an introduction flow passage is defined between the nozzle 20 and the internal cylinder 10. A gas introduction hole is formed in a peripheral wall of the internal cylinder 10, opposing the main nozzle hole and putting the introduction flow passage therebetween. An external cylinder 12 is provided outside the internal cylinder 10 for defining an external flow passage, and the external flow passage is defined into second and third flow passages 55, 56 by a partition cylinder 54. When a supply flow rate is low, the fuel gas enters the first flow passage 45 through the introduction flow passage, entrained on an air stream flowing through the introduction flow passage, while, when the supply flow rate is increased, the fuel gas surpasses the air stream flowing through the introduction flow passage and further flows into a second flow passage 55 and a third flow passage 56 through the gas introduction hole in this order.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a burner device for burning a fuel gas suitably used in a gas turbine, a heating furnace, and the like.

[0002]

2. Description of the Related Art Various cogeneration systems have been proposed and put to practical use for performing district power generation, district heating and the like. One typical system of such a cogeneration system includes a burner device for burning fuel gas, and a gas turbine that is rotationally driven by the combustion gas burned by the burner device. Electricity is generated by utilizing it.

[0003] A burner device in such a cogeneration system has a primary nozzle means to which fuel gas is supplied from a first gas supply means and a secondary nozzle means to which fuel gas is supplied from a second gas supply means. Some include nozzle means. The primary nozzle means defines a first flow path;
Fuel gas from the first gas supply means is jetted into the air flow flowing through the first flow path, thereby generating a combustible mixed gas. Further, the secondary nozzle means defines a second flow path, and the fuel gas from the second gas supply means is jetted into the air flow flowing through the second flow path, whereby the mixed gas of the primary nozzle means is discharged. A combustible mixed gas having a low gas concentration is generated. In such a burner device, since the gas concentration of the mixed gas of the primary nozzle means is higher than the gas concentration of the mixed gas of the secondary nozzle means, the mixed gas of the primary nozzle means is burned, and this primary nozzle means The mixed gas of the secondary nozzle means is burned by using the combustion gas of (1). By burning the fuel gas in this manner, lean combustion can be performed, and the combustion temperature of the combustion gas can be lowered, thereby enabling highly efficient combustion in which generation of nitrogen oxides (NOx) is suppressed. .

[0004]

In such a burner device, the combustion output of the burner device is controlled by controlling the amount of fuel gas injected into the second flow path. If the amount of fuel gas jetting is reduced in order to reduce the combustion output, the air becomes excessive with respect to the fuel gas, so that the combustion flame from the secondary nozzle means disappears or the fuel gas jetting control cannot be followed. Therefore, when the load is low, there is a problem that the combustion state of the secondary nozzle means becomes unstable and incomplete combustion easily occurs.

Further, when the combustion flame from the secondary nozzle means is extinguished or ignited while burning the fuel gas from the primary nozzle means, the temperature of the combustion gas fluctuates, and in the gas turbine to which the combustion gas is fed, It causes load fluctuation.

An object of the present invention is to provide a burner device that can stably burn fuel gas regardless of the supply flow rate of fuel gas and can completely burn fuel gas.

[0007]

According to the present invention, there is provided a nozzle body having a main nozzle hole and a pilot nozzle hole for ejecting fuel gas, and an inner cylinder body provided around the nozzle body and defining an internal flow path. An introduction flow path extending from the nozzle body to the inner cylindrical body is defined between the nozzle body and the inner cylindrical body. Further, a gas introduction hole is provided on the peripheral wall of the inner cylindrical body so as to face the main nozzle hole. An inner cylindrical body formed with the inner cylindrical body and the outer cylindrical body that is provided at an interval radially outward of the inner cylindrical body and that defines an outer flow path, and is provided between the inner cylindrical body and the outer cylindrical body. A burner device comprising: a partitioning cylinder that radially partitions an outer flow path; a gas supply unit that supplies fuel gas to a nozzle body; and an air supply unit that supplies air to an introduction flow path and an outer flow path. It is.

According to the present invention, the inner cylinder defining the inner flow path is provided so as to surround the nozzle body, and an introduction flow path extending from the inner cylinder to the nozzle body is formed between the inner cylinder and the nozzle body. The air is supplied to the introduction channel and the outer channel. Since the introduction flow path is formed in the gap between the inner cylinder and the nozzle body, the cross-sectional area is smaller than that of the outer flow path, and the flow rate of air flowing into the inner flow path through the introduction flow path is smaller than that of the outer flow path. . Further, since the main nozzle hole and the gas introduction hole are provided to face each other with the introduction flow path interposed therebetween, the fuel gas is ejected from the main nozzle hole toward the gas introduction hole via the introduction flow path. With this, when the amount of fuel gas ejected from the main nozzle hole is small, that is, when the fuel gas ejection speed is low, the fuel gas from the main nozzle hole is affected by the air flow flowing through the introduction flow path and together with the air flow. It flows toward the inner flow path on the downstream side in the gas flow direction.
When the amount of fuel gas jetted from the main nozzle hole increases, that is, when the jetting speed of the fuel gas increases, the fuel gas from the main nozzle hole overcomes the airflow flowing through the introduction flow path and crosses the introduction flow path. The gas flows into the gas inlet and flows toward the outer flow path. The fuel gas that has flowed into the outer flow path mainly flows into the inner flow path partitioned by the partition cylinder when the flow rate is small, and mainly flows into the outer flow path when the flow rate increases. As described above, when the amount of fuel gas ejected from the main nozzle hole is small, the fuel gas mainly flows into the inner flow passage having a small amount of air inflow, so that the equivalence ratio of the mixed gas (reciprocal of the air ratio)
Is prevented from becoming smaller than the combustible range, and the combustion flame can continue burning stably without extinction. Further, as the flow rate of the fuel gas flowing into the outer flow path increases or decreases, the flow path through which the fuel gas mainly flows is switched, so that the cross-sectional area of each flow path can be obtained so that the air supply amount corresponding to the flow rate of the fuel gas can be obtained. If the value is set to, the equivalent ratio of the mixed gas is appropriately maintained. Thus, even when the flow rate of the fuel gas flowing into the outer flow path is small, the equivalent ratio is prevented from being smaller than the combustible range, so that the quenching of the combustion flame in the outer flow path is prevented. Therefore, the burner device of the present invention can burn in a stable combustion state regardless of the supply flow rate of the fuel gas, and can prevent incomplete combustion of the fuel gas.

Further, the axes of the main nozzle hole and the gas introduction hole of the present invention are on a common straight line, and the inner diameter of the gas introduction hole is larger than the inner diameter of the main nozzle hole. The angle θ formed with the axis of the cylinder is 10 degrees ≦ θ ≦ 9
It is characterized in that the value is in a range of 0 degrees.

According to the present invention, the axes of the main nozzle hole and the gas introduction hole are on a common straight line, and the inside diameter of the gas introduction hole is larger than the inside diameter of the main nozzle hole. Since the angle formed with the axis of the cylinder is properly set, the fuel gas ejected from the main nozzle hole is reliably guided to the gas introduction hole when the discharge amount is large, and can flow into the external flow passage. .

Further, one end of the partition cylinder of the present invention on the upstream side in the fuel gas flow direction is mounted so as to be shifted downstream from the axis of the main nozzle hole, and the partition cylinder having the size of the deviation is provided. Is a value in the range of 0 ≦ R ≦ 80%.

According to the present invention, the one end of the partition cylinder is attached to be shifted downstream from the axis of the main nozzle hole, and the magnitude of the deviation is appropriately set.
The fuel gas flowing into the outer flow path can be reliably guided to a desired flow path according to the flow rate.

[0013] Further, the present invention is characterized in that the outer diameter of one end of the partition cylinder is smaller than the outer diameter of the other part.

According to the present invention, since the outer diameter of one end of the partitioning cylinder is narrowed to be smaller than the outer diameter of the other part, the entrance cross-sectional area in the flow path inside the outer flow path is reduced. The amount of air flowing into the flow path inside the outer flow path can be reduced. Also, when the amount of fuel gas flowing into the outer flow path is small, the flowing fuel gas flows into the flow path inside the outer flow path due to the action of the air flow. The amount and the air amount are commensurate, and the equivalent ratio of the mixed gas is prevented from becoming smaller than the combustible range.

Further, the flow velocity of the air in the outer flow path of the present invention is:
It is characterized by being faster than the flow velocity of the air in the inner flow path.

According to the present invention, since the air flowing into the inner flow path is supplied through the introduction flow path, the air flow rate of the inner flow path is determined by the cross-sectional area of the inlet of the introduction flow path. Since the introduction flow path is formed between the nozzle body and the inner cylinder, the cross-sectional area of the inlet portion is small and smaller than the cross-sectional area of the inlet portion of the outer flow path. Therefore, the flow rate of air flowing into the inner flow path is smaller than the flow rate of air flowing into the outer flow path. In the inner flow path, air flows from the introduction flow path having a smaller cross-sectional area into the inner flow path having a relatively larger cross-sectional area. It will be slower than the air velocity. As described above, since the flow velocity and the flow rate of the air in the inner flow path are lower than those in the outer flow path and the flow rate is smaller, even when the flow rate of the fuel gas flowing into the inner flow path is small, the flow rate of the fuel gas and the air is small. The equivalent ratio of the mixed gas is prevented from becoming smaller than the combustible range, and the extinction of the combustion flame in the inner flow passage is prevented.

Further, according to the present invention, the plurality of partitioning cylinders are provided coaxially at intervals in the radial direction, and the cross-sectional area of each flow path partitioned by the plurality of partitioning cylinders is so large that it becomes radially outward. It is characterized by.

According to the present invention, since a plurality of partitioning cylinders are provided coaxially at intervals in the radial direction, the fuel gas flowing into the external flow passage via the gas introduction holes is not air-flowing when the inflow amount is small. Mainly flows into the innermost flow path, and sequentially flows mainly into the outer flow path as the inflow amount increases. Further, since the cross-sectional area of each flow path partitioned by the plurality of partitioning cylinders is set to be larger as it becomes radially outward, the air flow rate supplied to the outer flow path is supplied to the inner flow path. Air flow rate. As a result, the main inflow passage can be switched finely, and the fuel gas corresponding to the flow rate of the air supplied to each passage can be caused to flow. Therefore, the equivalent ratio of the mixed gas in each flow path is reliably prevented from being smaller than the combustible range, and the extinction of the combustion flame is prevented.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a sectional view showing a simplified structure of a main part of a burner device according to an embodiment of the present invention, and FIG. 2 is a simplified schematic diagram of the burner device shown in FIG. FIG. Burner device 1 is diffuser 2
And a cylindrical holding case 4 is attached to the diffuser 2 via a flange 5. A combustion case 6 is provided in the holding case 4, and one end of the combustion case 6 is attached to the diffuser 2. An air passage 8 is formed in the diffuser 2, and combustion air is supplied to one end of the combustion case 6 via the air passage 8.
Combustion air (hereinafter abbreviated as air) is supplied to an air compressor 9.
Is sent in a compressed state.

The diffuser 2 has a mounting support block 1
6 is attached, and the external gas supply pipe 1 is attached to the mounting support block 16.
8 is mounted at one end. A nozzle body 20 is attached to the other end of the outer gas supply pipe 18. Nozzle body 20
Has a space 22 formed therein, and a partition sleeve 24 is mounted through the inner space 22 in the axial direction. The inner space 22 is divided into a first space 22a inside by a partition sleeve 24 and a second space 22 outside the first space 22a.
b. The other end of the outer gas supply pipe 18 is
It is communicated with the second space 22b of the injection nozzle body 20.
An inner gas supply pipe 26 is disposed inside the outer gas supply pipe 18, one end of which is mounted on the mounting support block 16, and the other end of which is mounted on the nozzle body 20. The inner gas supply pipe 26 is communicated with the first space 22 a of the nozzle body 20.

The inner gas supply pipe 26 and the outer gas supply pipe 18
Is connected to a gas supply device 27 which is a gas supply means for supplying a fuel gas. Gas supply device 27
A gas supply source 25 in which fuel gas is stored, first and second gas supply pipes 28 and 30 for individually guiding fuel gas from the gas supply source 25 to internal gas and external gas supply pipes 26 and 18, and gas Flow rate control valves 29a and 29b for controlling the flow rate of the gas supplied from the supply source 25 are included. As the fuel gas, for example, city gas can be suitably used.

An inner cylindrical body 10 is mounted outside the nozzle body 20. The inner cylindrical body 10 is a substantially cylindrical member made of stainless steel, and its internal space defines an inner flow path 45 (hereinafter, referred to as a first flow path). An outward projection 11 is formed at one end of the inner cylindrical body 10, and the outward projection 11 makes it easier for air to flow into the inner flow path 10. On the inner peripheral surface of the peripheral wall at one end of the inner cylindrical body 10, there are integrally provided inner projections 34 protruding radially inward at intervals in the circumferential direction. The inner cylinder body 10 is coaxially supported by the nozzle body 20 via a plurality of (eight in this embodiment) inner projections 34.

FIG. 3 is an enlarged sectional view showing a main part of the burner device shown in FIG. 1, and FIG.
FIG. 5 is a cross-sectional view as viewed from IV, and FIG. 5 is a cross-sectional view in a state where a nozzle body is removed from FIG. 4 for convenience of illustration. The nozzle body 20 has a large-diameter portion 31 having a large outer diameter, an intermediate taper portion 33 extending in a radially inward tapered shape, a small-diameter portion 35 having a small outer diameter, and a tip taper portion 37. It is provided in this order towards the side. Nozzle body 20
Is mounted with its tip facing downstream in the gas flow direction (hereinafter referred to as downstream). Also in this connection,
Each of the inner protrusions 34 of the inner cylindrical body 10 has a support portion 34a having a distal end surface extending in the axial direction, and an inclined portion 34b extending from the support portion 34a in a radially inward direction.
The large diameter portion 31 of the nozzle body 20 is attached to the nozzle body 20. In such a mounted state, the inclined portion 34b of the inner projection 34 is located opposite the intermediate tapered portion 33 of the nozzle body 20, and a slight distance exists between the intermediate tapered portion 33 and the inclined portion 34b of the inner projection 34. A gap 39 exists. 4 and 5, a substantially annular region is formed over a predetermined range in the circumferential direction, in other words, in a region excluding a region where the support portion 34a of the inner protrusion 34 exists, as shown in FIGS. Gap 38 exists. The gap 38 and the gap 39 between the intermediate tapered portion 33 and the inclined portion 34b form an introduction flow path. The air from the air flow path 8 flows in from the inlet of the introduction flow path, passes through the introduction flow path, and is guided to the first flow path 45 in the inner cylinder 10.

An inner swirler 36 is provided between the small diameter portion 35 of the nozzle body 20 and one end of the inner cylinder 10. As shown in FIG. 6, a plurality of inner swirlers 36 (eight in the present embodiment) are arranged at intervals in the circumferential direction.
In the present embodiment, it is integrally provided on the inner peripheral surface of the inner cylindrical body 10 adjacent to the downstream side of the inclined portion 34 b of the inner projection 34. Therefore, the air flowing through the gap 38 between the nozzle body 20 and the inner cylindrical body 10 serving as the introduction flow path is formed into a swirling flow by the inner swirler 36, and flows in the first flow path 45 in a swirling flow state as shown in FIG. And it flows downstream in FIG. The inner swirler 36 may be formed separately from the inner cylindrical body 10 and interposed between them.

Referring again to FIG. 1 and FIG.
The outer cylinders 12 are mounted on the outer side in the radial direction of 0 at an interval. The outer cylinder 12 is a substantially cylindrical member made of stainless steel, and defines an outer flow path 47 between the outer cylinder 12 and the inner cylinder 10.
An outer swirler 40 is integrally provided on the inner peripheral surface at one end of the outer cylindrical body 12, that is, at an inlet portion of the outer flow path 47, and the outer cylindrical body 12 is connected to the inner cylindrical body 10 through the outer swirler 40.
Is mounted coaxially on the outer peripheral surface of. Outtaswara 40
Is composed of a plurality (12 in the present embodiment) of revolving blades arranged at intervals in the circumferential direction similarly to the inner swirler 36. Since the outer swirler 40 is provided in this manner, the air introduced from the inlet of the outer flow path 47 forms a swirling flow by the action of the outer swirler 40,
In the state of the swirling flow, it flows to the downstream side in FIG. 1 and FIG. The outer swirler 40 may be formed separately from the outer cylinder 12 and may be interposed between the inner cylinder 10 and the outer cylinder 12.

An annular flange 42 protruding outward in the radial direction is integrally provided at one end of the outer cylinder 12, and one end of the combustion cylinder 14 is attached to a distal end of the annular flange 42 by an attachment screw. ing. The combustion cylinder 14 includes the inner cylinder 1
A substantially annular space 51 is provided coaxially with the outer case 12 and the combustion case 6. A substantially straight cylindrical tubular portion 41 is provided at the center in the length direction of the outer tubular body 12, and the other end of the outer tubular body 12 is provided with a ring-shaped outer portion via a curved portion 43. An orientation protrusion 44 is formed.

In the present embodiment, as shown in FIGS. 3 and 4, a plurality of (eight in the present embodiment) pilot nozzle holes are provided at the tip tapered portion 37 of the nozzle body 20 at circumferential intervals. 46 are formed, and these pilot nozzle holes 46 communicate with the first space 22 a of the nozzle body 20. In the intermediate tapered portion 33 of the nozzle body 20, a plurality of (eight in the present embodiment) main nozzle holes 48 extending in a substantially radial direction are formed at intervals in a circumferential direction. These main nozzle holes 48 communicate with the second space 22 b of the nozzle body 20. Furthermore, corresponding to each of the main nozzle holes 48,
A gas introduction hole 50 is formed in the inclined portion 34 b of the inner projection 34 of the inner cylinder 10 so as to penetrate the peripheral wall of the inner cylinder 10, and the main nozzle hole 48 and the gas introduction hole 50 are mutually interposed with a gap 39 interposed therebetween. They are arranged facing each other.

The axes of the main nozzle hole 48 and the gas introduction hole 50 are present in an imaginary plane including the axis 10a of the inner cylinder 10, and are present on a common straight line in the imaginary plane. The common axis 49 extends away from the axis 10a of the inner cylindrical body 10 toward the downstream side, and an angle θ between the axis 49 and the axis 10a (hereinafter, referred to as a main nozzle hole ejection angle) is 10 degrees. It is set to a value in the range of ≦ θ ≦ 90 degrees. The upper limit value of the main nozzle hole ejection angle θ is limited to 90 degrees.
And the gas introduction hole 50 is formed in the intermediate tapered portion 3 of the nozzle body 20.
This is because it is physically difficult to form the inner projection 3 and the inclined portion 34b of the inner projection 34. The reason for limiting the lower limit value of the main nozzle hole ejection angle θ will be described later. It is desirable that the inner diameter D1 of the gas introduction hole 50 is set substantially equal to or larger than the inner diameter D2 of the main nozzle hole 48 of the nozzle body 20. This makes it easier for the fuel gas ejected from the main nozzle hole 48 to flow into the gas introduction hole 50.

A partition cylinder 54 is provided between the inner cylinder 10 and the outer cylinder 12. The partitioning cylinder 54 is a substantially cylindrical member made of stainless steel, and partitions the outer channel 47 in the radial direction. Inner flow path 5 partitioned by partition cylinder 54
5 (hereinafter referred to as a second flow path) has a cross-sectional area of the outer flow path 5.
6 (hereinafter, referred to as a third flow path). The reason will be described later. Partition cylinder 54
The one end on the upstream side in the gas flow direction is mounted so as to be shifted downstream from the axis 49 as shown in FIG. The magnitude of the deviation is represented by a distance L2 from the intersection K to one end of the partition cylinder, where K is the intersection of the axis 49 and the extension of the partition cylinder 54. In the present embodiment, the ratio R to the total length L1 of the partition cylinder 54 having the displacement L2 is described.
(= L2 / L1 × 100) is preferably set to a value in the range of 0 ≦ R ≦ 80%. The reason for this will be described later.

With such a configuration, the fuel gas supplied through the gas supply pipe 28 is supplied to the inner gas supply pipe 2.
6 to the first space 22a of the nozzle body 20,
It is ejected through the pilot nozzle hole 46. Inner cylinder 1
0 defines a first flow path 45 as shown in FIGS. 1 and 2, and one end of the first flow path 45, that is, the upstream side, extends between the nozzle body 20 and the inner cylindrical body 10. The introduction channel is formed. Part of the air flowing through the air flow path 8 passes through the introduction flow path and flows into the downstream first flow path 45. The fuel gas jetted from the pilot nozzle hole 46 is jetted by the inner swirler 36 toward the airflow forming the swirling flow, and is substantially uniformly mixed by the action of the swirling flow to become a lean mixed gas. The amount of fuel gas ejected from the pilot nozzle hole 46 can be controlled by operating the flow control valve 29a of the gas supply device 27.

The fuel gas supplied via the gas supply pipe 30 is supplied to the first space 22b of the nozzle body 20 via the external gas supply pipe 18 and is ejected from the main nozzle hole 48.
As shown in FIGS. 1 to 3, the outer cylindrical body 12 and the partition cylindrical body 54 define substantially annular second and third flow paths 55 and 56. 40
Flows into the second and third flow paths 55 and 56 through the flow path and flows downstream. The fuel gas ejected from the main nozzle hole 48 passes through the gap 39 as described later and passes through the first flow path 45.
The gas is ejected to the outer channel 47 through the gas introduction hole 50 across the gap 39. The fuel gas ejected to the outer flow path 47 is ejected by the outer swirler 40 toward the airflow forming the swirling flow, and is uniformly mixed by the action of the swirling flow to become a lean mixed gas. The amount of fuel gas ejected from the main nozzle hole 48 can be controlled by operating the flow control valve 29b of the gas supply device 27.

The remainder of the air flowing through the air passage 8 is:
It flows through a space 51 between the combustion tube 14 and the combustion case 6. In the present embodiment, a plurality of air holes 52 are formed in the combustion cylinder 14 at intervals in the circumferential direction and the axial direction, and the air flowing through the space 51 passes through the air holes 52 and burns. It is introduced into the cylinder 14. Air hole 52
Forms an air layer flowing along the inner peripheral surface of the combustion tube 14, and the air layer cools the combustion tube 14. Further, the combustion cylinder 14 is provided with a dilution hole 53, so that air flowing through the space 51 passes through the dilution hole 53 and is introduced into the combustion cylinder 14, so that the temperature of the combustion gas is not abnormally increased by the introduced air. Is reduced to

Inner cylinder 10, partition cylinder 54 and outer cylinder 1
2 (hereinafter, may be referred to as a tip portion)
As shown in FIG. 2 and extending to substantially the same position or substantially the same position downstream, the other end of the combustion cylinder 14 extends further downstream therefrom. Therefore, the combustion flame due to the mixed gas flowing through the first flow path 45 is generated in the inside of the inner cylindrical body 10 or on the downstream side from the distal end, and the second combustion flame is generated.
The combustion flame due to the mixed gas flowing through the third flow paths 55 and 56 is generated downstream from the distal ends of the partition cylinder 54 and the outer cylinder 12.

In this embodiment, the gas concentration of the mixed gas flowing through the first flow path 45 is set to be higher than the gas concentration of the mixed gas flowing through the second and third flow paths 55 and 56. In connection with this, an ignition plug 58 for igniting the mixed gas is provided to protrude into the first flow path 45. The ignition plug 58 has a base mounted on the holding case 4 and a front end penetrated through the combustion case 6, the combustion cylinder 14, the outer cylinder 12, the partition cylinder 54 and the inner cylinder 10, and a first flow passage 45. It protrudes into. Spark plug 58
Generates a spark toward the mixed gas flowing through the first flow path 45, and the mixed gas in the first flow path 45 is ignited and burned by the spark. Further, the flame of the combustion gas generated in the first flow path 45 is supplied to the second and third flow paths 55 and 56.
The mixed gas flowing through the second and third flow paths 55 and 56 is combusted by the propagation of the flame.

The gap between the nozzle body 20 and the inner cylinder 10 that defines the introduction flow path is larger than the gap between the inner cylinder 10 and the partition cylinder 54 and the gap between the partition cylinder 54 and the outer cylinder 12. It is set small. As a result, the cross-sectional area of the inlet portion of the introduction flow channel becomes smaller than the cross-sectional area of the inlet portion of the outer flow channel 47.
Is smaller than the air flow rate flowing into the outer flow path 47. Further, the air that has flowed in from the inlet portion of the introduction flow path, after passing through the narrow gap of the introduction flow path, flows into the first flow path 45 having a relatively large cross-sectional area on the downstream side. The flow rate of the airflow flowing through 45 becomes relatively slow. On the other hand, the flow velocity of the airflow flowing through the second and third flow paths 55 and 56 forming the outer flow path 47 is relatively high. That is, in the present embodiment, the flow velocity of the air in the outer flow path 47 is configured to be higher than the flow velocity of the air in the first flow path 45. As described above, since the flow velocity and the flow rate of the air in the first flow path 45 are lower than those in the outer flow path 47 and are smaller, the first flow rate is lower.
Even when the flow rate of the fuel gas flowing into the flow passage 45 is small,
It is prevented that the equivalent ratio of the mixed gas of the fuel gas and the air becomes smaller than the combustible range. Therefore, the extinction of the combustion flame in the first flow passage 45 is prevented, and the mixed gas can be stably burned.

At the tip of the combustion cylinder 14, a cylindrical lead-out cylinder 60 is further provided. The lead-out cylinder 60 extends to the downstream side, and its tip is tapered. The leading end of the lead-out cylinder 60 is supported by a support plate 64 attached to the leading end of the combustion case 6. The combustion gas guided from the combustion tube 14 to one end of the discharge tube 60 is collected at a tapered tip portion through the discharge tube 60 and flows downstream. A gas turbine 62 is provided at the tip end of the lead-out tube 60, and the combustion gas burned in the combustion tube 14 passes through the lead-out tube 60 and is supplied to the gas turbine 62. As shown in FIG. 7, a plurality of, for example, six such burner devices 1 are arranged at intervals in the circumferential direction of the virtual circle 63 with respect to the blades of the gas turbine 62. The gas turbine 62 is rotationally driven by the combustion gas from each burner device 1.

In such a burner device 1, the fuel gas from the ignition gas supply device 27 is supplied to the first space 22a of the nozzle body 20 through the internal gas supply pipe 28, and the pilot gas is supplied from the first space 22a to the pilot space. Fuel gas is jetted through the nozzle holes 46. Therefore, the fuel gas is jetted toward the airflow flowing through the first flow passage 45, and the mixed gas having a relatively high concentration flows through the first flow passage 45. When a spark is generated from the spark plug 58 toward the mixed gas flow, the mixed gas is burned by the spark, and the mixed gas flowing through the first flow path 45 is burned to become a combustion gas.

After the ignition, the fuel gas from the gas supply device 27 is supplied to the second space 2 of the nozzle body 20 through the external gas supply pipe 18.
2b, and the fuel gas is ejected from the second space 22b through the main nozzle hole 48. The amount of fuel gas ejected is, for example, that the fuel gas traverses the gap 39 between the intermediate tapered portion 33 of the nozzle body 20 and the inclined portion 34 b of the inner projection 34 of the inner cylinder 10, 55. Thereby, the fuel gas is jetted toward the airflow flowing through the second flow path 55, and the first flow path 45
The mixed gas having a concentration lower than that of the mixed gas flowing through the second flow path 55 flows through the second flow path 55. The mixed gas flowing through the second flow path 55 is burned by the flame from the first flow path 45 propagating to the second flow path 55 to become a combustion gas.

As described above, when the mixed gas flowing through the second flow path 55 starts burning, the supply of the fuel gas supplied from the gas supply device 27 to the pilot nozzle hole 46 via the internal gas supply pipe 26 is stopped. Is done. In such a combustion state, if the supply amount of the fuel gas from the gas supply device 27 is reduced in order to reduce the combustion output of the burner device 1, the ejection amount of the fuel gas ejected from the main nozzle hole 48 of the nozzle body 20 becomes smaller. The jetting speed decreases as the number decreases. When the jetting speed decreases, as is apparent from FIG.
The fuel gas ejected from the nozzle 8 has a large diameter 3
1 and the inner cylindrical body 10, the air flow flowing through the gap 39 between the intermediate tapered portion 33 and the inclined portion 34 b of the inner protrusion 34 greatly receives the effect of the air flow, and flows toward the first flow passage 45 together with the air flow. become. As a result, most of the fuel gas ejected from the main nozzle hole 48 flows through the first flow passage 45, and the amount of fuel gas ejected to the second flow passage 55 through the gas introduction hole 50 is reduced. Therefore, the gas concentration of the mixed gas generated in the first flow passage 45 in which the flow of air is relatively slow and the air flow rate is small is high, and the supply flow of the fuel gas is small in the first flow passage 45 despite the small supply amount of fuel gas. The mixed gas burns stably.

On the other hand, if the supply amount of the fuel gas from the gas supply device 27 is increased in order to increase the combustion output of the burner device 1, the ejection amount of the fuel gas ejected from the main nozzle hole 48 of the nozzle body 20 is increased. And the ejection speed increases. As the ejection speed of the fuel gas increases, the fuel gas ejected from the main nozzle hole 48 flows through the gap 39 between the intermediate tapered portion 33 of the nozzle body 20 and the inclined portion 34b of the inner projection 34, as is apparent from FIG. By overcoming the action of the flow, the gas flows across the gap 39 into the gas introduction hole 50 of the inclined portion 34 b of the inner cylinder 10. In addition, gas introduction hole 50
The supply amount supplied via the fuel gas increases as the supply amount of the fuel gas increases.

In the present embodiment, the fuel gas flowing into the outer flow path 47 through the gas introduction hole 50 is configured such that the main flow path is switched according to the flow rate. That is, when the inflow amount of the fuel gas is small and the inflow speed is low, the fuel gas mainly flows into the second flow path 55 by the action of the air flow from the outer swirler 40, and when the inflow amount of the fuel gas is large and the inflow speed is high. , Fuel gas is Outtaswara 4
It overcomes the airflow from zero and makes it mainly flow into the third flow path 56. Thereby, the fuel gas mainly flows into the third flow path 56 having a large cross-sectional area and a large air flow rate when the inflow amount of the fuel gas is large, and has a small cross-sectional area and a small air amount when the flow rate of the fuel gas is small. Since the fuel gas mainly flows into the second flow path 55, the equivalent ratio of the mixed gas is prevented from being excessively small, and the extinction of the combustion flame at the outlet side of each flow path is prevented. Therefore, a stable combustion state can be maintained, and the occurrence of incomplete combustion due to extinction can be prevented. As described above, it is for this reason that the cross-sectional area of the third flow path 56 is formed larger than the cross-sectional area of the second flow path 55.

In order to smoothly switch the inflow channel in the outer channel 47, it is necessary to set the main nozzle hole ejection angle θ to a value in the range of 10 degrees ≦ θ ≦ 90 degrees as described above. preferable. The lower limit of the main nozzle hole ejection angle θ is 10
The reason is that the fuel gas flowing into the outer flow path 47 flows downstream along the outer peripheral surface of the inner cylindrical body 10 at an angle smaller than the lower limit value, so that most of the fuel gas flows into the second flow path 55. This is because, even if the inflow flow rate increases, it becomes difficult to flow into the third flow path 56. Therefore, the main inflow channel cannot be switched smoothly in accordance with the flow rate of the fuel gas. The main nozzle hole ejection angle θ is more preferably 30 degrees ≦ θ ≦ 60 degrees, and most preferably θ = 45 degrees.

In order to smoothly switch the inflow channel, as described above, the ratio R of the displacement L2 with respect to the partition cylinder 54 to the total length L1 of the partition cylinder 54 is determined.
(= L2 / L1 × 100) is preferably set to a value in the range of 0 ≦ R ≦ 80%. The reason why the lower limit value of the ratio R is limited to zero is that at a ratio R lower than the lower limit value, one end of the partition cylinder 54 is located upstream of the intersection K, in other words, the main nozzle hole 4.
This is because the fuel gas ejected from the main nozzle hole 48 along the axis 49 is less likely to flow into the third flow path 56. The reason why the upper limit of the ratio R is limited to 80% is that the fuel gas flowing into the outer flow path 47 is uniformly mixed with the air at the ratio R exceeding the upper limit because the position of the partitioning cylinder 54 is farther downstream. After that, the liquid is supplied to the second and third flow paths, and the partitioning effect of the partitioning cylinder 54 cannot be exhibited. It is particularly preferable that the ratio R has a value in the range of 5% ≦ R ≦ 50%.

As described above, in the present embodiment, when the supply amount of the fuel gas is increased to increase the combustion output, the fuel gas flows into the second and third flow paths 55 and 56 of the outer flow path 47. When the combustion output is reduced by reducing the supply amount of the fuel gas, the fuel gas flows into the first flow passage 45. The flow rate of the air supplied to the outer flow path 47 is configured to be larger than the flow rate of the air supplied to the first flow path 45 that is the inner flow path. Therefore, fuel gas corresponding to the air flow rate is supplied in each flow path,
The mixed gas can be stably burned without causing a problem such as extinction of the combustion flame.

As described above, the main nozzle hole 4 of the nozzle body 20
In order to allow the fuel gas ejected from the nozzle 8 to flow into the first flow passage 45 and the outer flow passage 47 in accordance with the ejection amount, the flow rate of the air flowing through the first flow passage 45 and the size of the main nozzle hole 48 And the intermediate tapered portion 33 of the nozzle body 20 and the inner cylindrical body 1
It is necessary to properly set the gap 39 between the zero inclined portion 34b. These are set based on the combustion output required for the burner device 1.
It can be set to about 1.0 mm. In order to sufficiently eject the fuel gas ejected from the main nozzle hole 48 of the nozzle body 20 into the outer flow path 47 by overcoming the airflow flowing through the gap 39, the maximum ejection speed of the fuel gas from the main nozzle hole 48 is required. Is preferably in the range of 1 to 1000 m / s.

As described above, in the burner device 1 of this embodiment, as shown in Table 1, when the supply amount of the fuel gas is small, the fuel gas becomes a relatively rich mixed gas and is mainly combusted in the first passage 45. When the supply amount of the fuel gas is medium, the mixed gas becomes a relatively thin gas and mainly the second gas.
When the fuel gas is burned on the outlet side of the flow path 55 and the supply amount of the fuel gas is large, it becomes a relatively thin mixed gas and is mainly burned on the outlet side of the third flow path 56. As a result, even if the amount of fuel gas supplied from the gas supply device 27 changes greatly, the fuel gas can be stably burned. The circles in Table 1 represent flow paths to which fuel gas is mainly supplied.

[0047]

[Table 1]

In the present embodiment, although the supply of fuel gas to the pilot nozzle hole 46 is stopped after ignition,
The present invention is not limited to this, and the fuel gas may always be supplied to the pilot nozzle hole 46 and burned even after ignition. Although the gas introduction hole 50 for guiding the fuel gas to the outer flow path 47 is formed in the inner projection 34 of the inner cylinder 10, the tubular body may be provided on the inner peripheral surface of the inner cylinder 10. . The main nozzle hole 48 and the gas introduction hole 50
Are the same, and are configured to exist in an imaginary plane including the axis 10a of the inner cylindrical body 10,
It may be inclined so as to intersect the virtual plane along the swirling flow of the air from the outer swirler 40.

FIG. 8 is a sectional view showing a simplified structure of a main part of a burner apparatus according to another embodiment of the present invention. The configuration of the burner device 65 of the present embodiment is shown in FIGS.
Are similar to the configuration of the burner device 1 shown in FIG. It should be noted that the outer diameter of one end on the upstream side of the partitioning cylinder 66 is narrowed, and is formed so as to be smaller than the outer diameters of the other portions. As a result, the flow rate of the air flowing into the second flow path 55 decreases, so that when the flow rate of the fuel gas flowing into the outer flow path 47 through the gas introduction hole 50 is small, the second flow path 55 serving as the main flow path of the fuel gas is provided. Within the fuel gas and a correspondingly reduced amount of air. Therefore, it is possible to prevent the equivalent ratio of the mixed gas from becoming smaller than the combustible range, and to prevent the extinction of the combustion flame. As a result, the mixed gas can be stably burned, and the fuel gas can be completely burned.

FIG. 9 is a sectional view showing a simplified structure of a main part of a burner apparatus according to still another embodiment of the present invention. The configuration of the burner device 68 of the present embodiment is similar to the configuration of the burner device 1, and the corresponding parts are denoted by the same reference numerals and description thereof will be omitted. It should be noted that in the present embodiment, three partition cylinders are provided.
The first to third partitioning cylinders 69, 70, 71 are provided in this order from the inside between the inner cylinder 10 and the outer cylinder 12, and partition the outer flow path 47 into four to form the second to fifth partitioning cylinders. Channels 55, 56, 7
3, 74 are defined in this order from the inside. The cross-sectional area of each flow path is formed so as to increase toward the outside, and the cross-sectional area of the fifth flow path 74 is the largest. For this reason,
The flow rate of the supplied air increases as the position of the flow path increases.

One end of the third partitioning cylinder 71 is mounted to be shifted downstream from the axis 49 of the main nozzle hole 48. The magnitude of the deviation is represented by a distance L3 from the intersection P to one end of the third partition cylinder 71, where P is the intersection of the axis 49 and the extension of the third partition cylinder 71. The ratio R1 (= L3 / L4 × 100) of the deviation L3 to the entire length L4 of the third partitioning cylinder 71 is a value in the range of 0 ≦ R1 ≦ 80% as in the case of the burner device 1. It is particularly preferable that the range of 5% ≦ R1 ≦ 50% is satisfied. First and second partition cylinders 69, 70
The installation position and the overall length of the third partitioning cylinder 71
Is the same as

The fuel gas that has flowed into the outer flow path 47 through the gas introduction hole 50 has a lower flow rate when the flow rate is small.
Mainly flows into the outer flow path as the inflow amount increases. Thus, in the present embodiment, the main inflow passage can be switched more finely than in the burner device 1, so that the fuel gas corresponding to the flow rate of the air supplied to each passage can be flowed. The equivalent ratio of the mixed gas in the road is more reliably prevented from being smaller than the combustible range.

As described above, the present invention can be suitably used as a burner device of a combustor of a gas turbine. However, the application of the present invention is not limited to only gas turbines, and can be suitably used for a wide range of applications such as a burner device of a heating furnace.

Example In order to confirm the effect of the burner device of the present invention, a combustion test of fuel gas was performed using the burner device 1 shown in FIGS. 1 to 3 as an example. The dimensions and the like of each member in the used burner device 1 are as shown in Table 2. The gap 39 between the inclined portion 34b of the inner projection 34 of the inner cylinder 10 and the intermediate tapered portion 33 of the nozzle body 20 was set to 0.5 mm. Deviation L between one end of the partition cylinder 54 and the axis 49 of the main nozzle hole 48
2 to the length L1 of the partitioning cylinder 54 (R = L2 /
L1 × 100) was set to 10%. On the other hand, as a comparative example, a fuel gas combustion experiment was performed using a burner device having the same configuration as that of the example except that the partition cylinder was omitted.

[0055]

[Table 2]

In a combustion experiment using such a burner device, air at a temperature of 350 ° C.
It was fed at 0 Nm ³ / h. The supplied air flowed downstream via the first flow path 45, the outer flow path 47, and the flow path 51 outside the combustion cylinder 14. The flow path 5 outside the combustion cylinder 14
1 flows into the combustion cylinder 14 through the air holes 52 of the combustion cylinder 14. Using methane as fuel gas,
At a flow rate of 1 Nm ³ / h, it was ejected from the pilot nozzle hole of the nozzle body 20 and at a flow rate of 24.7 Nm ³ / h, it was ejected from the main nozzle hole of the nozzle body 20. The supplied air and methane were mixed to form a mixed gas, and the mixture was ignited by an ignition plug 58 to burn the mixed gas to generate a combustion gas.
After the ignition, the ejection of methane from the pilot nozzle hole was stopped, and the ejection flow rate of methane ejected from the main nozzle hole 48 was set to 25.7 Nm ³ / h. At this time, the equivalent ratio of the mixed gas was 0.35. Thereafter, the methane supply was gradually reduced, in other words, the equivalent ratio was gradually reduced, and the change in the combustion state was examined. The evaluation of the combustion state is based on the combustion efficiency and the NOx in the exhaust gas.
The test was performed at the content rate. The results are shown in FIGS.

FIG. 10 is a graph showing the relationship between the equivalent ratio of the mixed gas and the combustion efficiency, and FIG. 11 is a graph showing the relationship between the equivalent ratio of the mixed gas and the NOx content in the exhaust gas.
The combustion efficiency is an index indicating the degree of complete combustion of the fuel gas in the mixed gas, and C is the incomplete combustion product in the exhaust gas.
It is calculated by measuring the content (%) of O and HC. These components indicate that incomplete combustion has occurred due to the extinction of the combustion flame or the like. Therefore, when CO and HC are not contained in the exhaust gas, the combustion efficiency is 1
00%. 10 and 11, the experimental result of the example is represented by reference numeral 75, and the experimental result of the comparative example is represented by reference numeral. Reference numeral 77 in FIG. 10 indicates an equivalent ratio range in which the fuel gas mainly flows into the first flow passage 45 of the embodiment, and reference numeral 78 indicates the second flow passage 55 of the embodiment.
The reference numeral 79 indicates an equivalent ratio range in which the fuel gas mainly flows into the third flow path 56 of the embodiment. Reference numeral 80 in FIG. 10 indicates an equivalent ratio range in which the fuel gas mainly flows into the first flow path of the comparative example, that is, the inner cylinder 10, and reference numeral 81 indicates the second flow path of the comparative example, It shows an equivalent ratio range in which the fuel gas mainly flows into the outer passage.

From FIG. 10, it can be seen that in the range of the equivalent ratio of 0.30 to 0.35, the combustion efficiency of both Example 75 and Comparative Example 76 is 1
When the equivalent ratio is less than 0.30, the combustion efficiency decreases as the equivalent ratio decreases in both the examples and the comparative examples. In Example 75, the combustion efficiency decreases with respect to the decrease in the equivalent ratio as compared with Comparative Example 76. Example 75 has a better combustion efficiency than Comparative Example 76 when compared at the same equivalence ratio, that is, the degree is small. It can be seen that this is remarkable when the fuel gas mainly flows into the second flow path 55 of the burner device 1. From FIG. 11, it can be seen that the NOx content in the exhaust gas is substantially the same as in Example 75 and Comparative Example 76, and that the NOx content in the exhaust gas is both low. Thus, the burner device 1 of the embodiment can maintain good combustion efficiency while maintaining low NOx properties even when the equivalent ratio is reduced, that is, even when the supply amount of methane is reduced.

[0059]

As described above, according to the first aspect of the present invention, when the amount of fuel gas ejected from the main nozzle hole is small, the fuel gas mainly flows into the inner flow passage having a small air inflow. Therefore, it is prevented that the equivalent ratio of the mixed gas becomes smaller than the combustible range, and the combustion flame can continue burning stably without extinction. In addition, since the flow path where fuel gas mainly flows in is switched as the flow rate of fuel gas flowing into the outer flow path increases and decreases, the equivalent ratio of the mixed gas in each flow path is appropriately maintained. As a result, even when the flow rate of the fuel gas flowing into the outer flow path is small, the equivalent ratio is prevented from being smaller than the combustible range, so that the quenching of the combustion flame in the outer flow path is prevented. Therefore, regardless of the supply flow rate of the fuel gas, the mixed gas can be stably burned, and incomplete combustion of the fuel gas can be prevented.

According to the present invention, the axes of the main nozzle hole and the gas introduction hole are on a common straight line, the inner diameter of the gas introduction hole is larger than the inner diameter of the main nozzle hole, and Since the angle between the axis of the main nozzle hole and the axis of the inner cylinder is properly set, the fuel gas ejected from the main nozzle hole is reliably guided to the gas introduction hole when the ejection amount is large, and Can flow into

According to the third aspect of the present invention, one end of the partitioning cylinder is attached to the downstream side with respect to the axis of the main nozzle hole, and the magnitude of the deviation is appropriately set. Therefore, the fuel gas flowing into the outer flow path can be reliably guided to a desired flow path according to the flow rate.

According to the fourth aspect of the present invention, since the outer diameter of one end of the partitioning cylinder is set smaller than the outer diameter of the other part, the inlet diameter of the partition inside the outer flow path is reduced. The side sectional area is reduced, and the amount of air flowing into the flow path inside the outer flow path can be reduced. Also, when the amount of fuel gas flowing into the outer flow path is small, the flowing fuel gas flows into the flow path inside the outer flow path, so that the flow rate of the fuel gas and the amount of air flow in the flow path inside the outer flow path. Accordingly, it is prevented that the equivalent ratio of the mixed gas becomes smaller than the combustible range.

According to the fifth aspect of the present invention, the flow velocity of the air in the inner flow path is lower than the flow velocity of the air in the outer flow path. The flow rate of the air flowing into the inner flow path is smaller than the flow rate of the air flowing into the outer flow path. Therefore, even when the flow rate of the fuel gas flowing into the inner flow passage is small, the equivalent ratio of the mixed gas is prevented from being smaller than the combustible range, and the quenching of the combustion flame in the inner flow passage is prevented.

According to the sixth aspect of the present invention, since a plurality of partitioning cylinders are provided coaxially at intervals in the radial direction, the amount of fuel gas flowing into the outer flow path through the gas introduction hole is reduced. When the flow rate is small, the gas mainly flows into the innermost flow path, and sequentially flows into the outer flow path as the flow rate increases. Further, since the cross-sectional area of each flow path partitioned by the plurality of partitioning cylinders is set to be larger as it becomes radially outward, the air flow rate supplied to the outer flow path is supplied to the inner flow path. Air flow path.
As a result, the main inflow passage can be switched finely, and the fuel gas corresponding to the flow rate of the air supplied to each passage can be caused to flow. Therefore, it is possible to reliably prevent the equivalent ratio of the mixed gas in each flow path from becoming smaller than the combustible range.

[Brief description of the drawings]

FIG. 1 is a simplified cross-sectional view showing a configuration of a main part of a burner device according to an embodiment of the present invention.

FIG. 2 is a simplified cross-sectional view showing the entire configuration of the burner device shown in FIG.

FIG. 3 is an enlarged sectional view showing a main part of the burner device shown in FIG. 1;

FIG. 4 is a cross-sectional view taken along the line IV-IV of FIG. 3;

FIG. 5 is a sectional view showing a state where a nozzle body is removed from FIG. 4;

FIG. 6 is a simplified perspective view showing a configuration of an inner straw.

FIG. 7 is a perspective view showing an arrangement state of a burner device with respect to the gas turbine.

FIG. 8 is a simplified cross-sectional view showing a configuration of a main part of a burner device according to another embodiment of the present invention.

FIG. 9 is a cross-sectional view showing a simplified configuration of a main part of a burner device according to still another embodiment of the present invention.

FIG. 10 is a graph showing a relationship between an equivalent ratio of a mixed gas and combustion efficiency.

FIG. 11 is a graph showing the relationship between the equivalent ratio of a mixed gas and the NOx content in exhaust gas.

[Explanation of symbols]

 1, 65, 68 Burner device 8 Air flow path 10 Inner cylinder 12 Outer cylinder 14 Combustion cylinder 20 Nozzle body 27 Gas supply device 29 Flow control valve 34 Inner projection 36 Inner straw 40 Outer straw 45 First passage 46 Pilot nozzle hole 47 Outer flow path 48 Main nozzle hole 50 Gas introduction hole 52 Air hole 54 Partition cylinder 55 Second flow path 56 Third flow path 58 Ignition plug 60 Outgoing cylinder

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kazuo Shimohira 7-44-1 Jindaiji Higashicho, Chofu City, Tokyo Inside the Aerospace Research Institute of Science and Technology Agency (72) Inventor Tsutomu Wakabayashi 4-chome Hiranocho, Chuo-ku, Osaka-shi, Osaka No. 1-2 in Osaka Gas Co., Ltd. (72) Koji Moriya Inventor Koji Morino 4-1-2 in Hirano-cho, Chuo-ku, Osaka-shi, Osaka (72) Inventor Yuji Nakamura Hirano-cho, Chuo-ku, Osaka-shi, Osaka 4-1-2, Osaka Gas Co., Ltd.

Claims (6)

[Claims] 1. A nozzle body having a main nozzle hole for ejecting fuel gas and a pilot nozzle hole, and an inner cylinder body provided around the nozzle body and defining an internal flow path, An introduction passage extending from the inner passage is defined between the inner passage and the cylinder, and a gas introduction hole is formed in a peripheral wall of the inner cylinder so as to face the main nozzle hole and sandwich the introduction passage. A cylindrical body, provided at an interval radially outward of the inner cylindrical body, and an outer cylindrical body that defines an outer flow path, and provided between the inner cylindrical body and the outer cylindrical body, radially extending the outer flow path. A burner device comprising: a partitioning cylinder for partitioning; gas supply means for supplying a fuel gas to a nozzle body; and air supply means for supplying air to an introduction flow path and an external flow path. 2. The axis of the main nozzle hole and the gas introduction hole are on a common straight line, the inner diameter of the gas introduction hole is larger than the inner diameter of the main nozzle hole, and the axis of the main nozzle hole and the inner cylindrical body. 2. The burner device according to claim 1, wherein the angle θ formed with the axis is within a range of 10 degrees ≦ θ ≦ 90 degrees. 3. An end of the partition cylinder on the upstream side in the fuel gas flow direction is mounted to be shifted downstream from the axis of the main nozzle hole, and the entire length of the partition cylinder having the size of the deviation is provided. The burner device according to claim 1 or 2, wherein the ratio R to R is a value in a range of 0 ≦ R ≦ 80%. 4. An outer diameter of one end of the partitioning cylinder is smaller than an outer diameter of the other part.
The burner device according to any one of claims 1 to 3. 5. The air flow rate in the outer flow path is higher than the flow rate of air in the inner flow path.
5. The burner device according to any one of 4. 6. A plurality of said partitioning cylinders are provided coaxially at intervals in the radial direction, and the cross-sectional area of each flow path partitioned by the plurality of partitioning cylinders is larger as it goes radially outward. The burner device according to claim 1.