阅读说明：本技术 燃气轮机燃烧器 (Gas turbine combustor ) 是由 浅井智广 吉田正平 平田义隆 林明典 穐山恭大 于 2020-09-27 设计创作，主要内容包括：本发明提供一种燃气轮机燃烧器,在稀薄燃烧方式的燃气轮机燃烧器中抑制伴随燃烧的煤尘向燃烧嘴的附着而提高结构可靠性。燃气轮机燃烧器具备形成燃烧室的筒状的内衬以及具备配置于上述内衬的入口且具备向上述燃烧室引导压缩空气的多个空气孔的空气孔板以及隔着上述空气孔板配置于与上述燃烧室相反侧且分别向对应的空气孔喷射燃料的多个燃料喷嘴的燃烧嘴,上述空气孔和上述燃料喷嘴构成同心圆状的多个环状列,以位于最内周的空气孔的环状列的内侧区域的方式在上述空气孔板上设置开口直径比上述空气孔小的多个小孔。(The invention provides a gas turbine combustor, which restrains coal dust attaching to a combustion nozzle and improves structure reliability in a gas turbine combustor of a lean combustion mode. The gas turbine combustor includes a tubular liner forming a combustion chamber, and a combustion nozzle including an air hole plate disposed at an inlet of the liner and including a plurality of air holes for guiding compressed air to the combustion chamber, and a plurality of fuel nozzles disposed on an opposite side of the liner from the combustion chamber with the air hole plate interposed therebetween and injecting fuel into the corresponding air holes, wherein the air holes and the fuel nozzles form a plurality of concentric annular rows, and the air hole plate is provided with a plurality of small holes having a smaller opening diameter than the air holes so as to be located in an inner region of the annular row of the innermost air holes.)

1. A gas turbine combustor is provided with:

a cylindrical liner forming a combustion chamber; and

a burner tip, comprising: an air hole plate disposed at an inlet of the liner and having a plurality of air holes for guiding compressed air to the combustion chamber; and a plurality of fuel nozzles disposed on the opposite side of the combustion chamber with the air hole plate interposed therebetween and injecting fuel into the respective corresponding air holes,

the air holes and the fuel nozzles form a plurality of concentric annular rows,

the gas turbine combustor is characterized in that,

the air hole plate is provided with a plurality of small holes having a smaller opening diameter than the air holes so as to be located in an inner region of the annular row of the innermost air holes.

2. The gas turbine combustor of claim 1,

an air flow path connected to the plurality of small holes is provided.

3. The gas turbine combustor of claim 1,

the fuel supply device is provided with a fuel flow path connected to the plurality of small holes.

4. The gas turbine combustor of claim 3,

and an air flow path connected to the plurality of small holes.

5. The gas turbine combustor of claim 4,

the plurality of small holes are connected to bypass holes branched from the air holes.

6. The gas turbine combustor of claim 1,

the burner is provided as a pilot burner, and a main burner is disposed so as to surround the pilot burner.

7. The gas turbine combustor of claim 6,

the burner includes a plurality of the burners as pilot burners and a plurality of main burners arranged so as to surround the pilot burners.

Technical Field

The present invention relates to gas turbine combustors.

Background

In a thermal power generator, carbon dioxide (CO) causing global warming is reduced₂) The displacement of (2) requires an improvement in the power generation efficiency. The high temperature of the combustion gas generated in the gas turbine combustor is effective for improving the power generation efficiency of the gas turbine generator. However, the high temperature of the combustion gas is accompanied by a technical problem of suppressing the emission of nitrogen oxides (NOx), which are environmental pollutants.

Combustion systems of gas turbine combustors are generally classified into diffusion combustion systems and premixed combustion systems.

The diffusion combustion method is a method of directly injecting fuel into a combustion chamber and mixing the fuel with air in the combustion chamber, and has excellent combustion stability because a flame is hardly generated by a reverse flow to the upstream side of the combustion chamber and self-ignition in a fuel supply flow path. On the contrary, a flame is formed in a region where the air ratio (quantitative mixing ratio) necessary for complete combustion of the fuel is mixed, and the flame locally becomes a high temperature. Since NOx is generated in a large amount in a local high-temperature region, it is necessary to reduce the NOx emission amount by injecting an inert medium such as water, steam, and nitrogen. As a result, auxiliary power for supplying the inert medium is required, and the power generation efficiency is lowered.

Another premixed combustion method is a method in which fuel and air are mixed in advance and supplied to a combustion chamber, and since fuel can be burned lean, the NOx emission amount is small. On the other hand, when the combustion gas is heated to a high temperature, if the combustion air temperature is increased and the fuel temperature in the premixer is increased, the risk of the flame flowing back to the upstream side of the combustion chamber increases. Therefore, there is a fear of burning of the burner structural member.

Therefore, a lean combustion type combustor is known in which the dispersibility of fuel is improved to prevent the formation of local high-temperature flames and thereby reduce the NOx emission and prevent the reverse flow of the flames (patent document 1 and the like).

Documents of the prior art

Patent document 1: japanese patent laid-open publication No. 2003-148734

The burner disclosed in patent document 1 includes a plurality of pairs of fuel nozzles and air holes. The air holes are concentrically arranged in the air hole plate. On the surface of the air hole plate facing the combustion chamber, the center of a concentric circle formed by the air holes is referred to as a wall surface without the air holes, and soot associated with combustion adheres to the wall surface. If coal dust attached to the air hole plate catches fire, there is a possibility that the burner will be overheated, and if coal dust falls off, there is a possibility that the downstream structural member will be damaged.

Disclosure of Invention

The purpose of the present invention is to provide a gas turbine combustor of a lean combustion system that can improve structural reliability by suppressing the adhesion of soot and dust to a burner tip during combustion.

In order to achieve the above object, a gas turbine combustor according to the present invention includes a tubular liner forming a combustion chamber, an air hole plate disposed at an inlet of the liner and including a plurality of air holes for guiding compressed air to the combustion chamber, and a burner including a plurality of fuel nozzles disposed on an opposite side of the liner from the combustion chamber with the air hole plate interposed therebetween and injecting fuel into the corresponding air holes, wherein the air holes and the fuel nozzles form a plurality of concentric annular rows, and the air hole plate is provided with a plurality of small holes having a smaller opening diameter than the air holes so as to be located in an inner peripheral region of the annular row of innermost air holes.

The effects of the present invention are as follows.

According to the present invention, in a gas turbine combustor of a lean combustion system, adhesion of soot and dust accompanying combustion to a burner tip is suppressed, and structural reliability is improved.

Drawings

Fig. 1 is a schematic configuration diagram of a gas turbine generator including a gas turbine combustor according to a first embodiment of the present invention.

Fig. 2 is a view showing a main structure of a burner included in a gas turbine combustor according to a first embodiment of the present invention, and is a cross-sectional view including a central axis of the burner.

Fig. 3 is a view of a combustion nozzle provided in a gas turbine combustor according to a first embodiment of the present invention, as viewed from a combustion chamber.

Fig. 4 is a sectional view of a central shaft including a conventional burner tip.

Fig. 5 is a view of a conventional burner tip as viewed from a combustion chamber.

Fig. 6 is a structural diagram of an apparatus in which soot generated by combustion is attached to an inner zone Z in a conventional burner.

Fig. 7 is an explanatory view of an apparatus for suppressing the adhesion of soot to a burner in the present invention.

Fig. 8 is a view showing a main structure of a burner included in a gas turbine combustor according to a second embodiment of the present invention, and is a cross-sectional view including a central axis of the burner.

Fig. 9 is a view showing a main structure of a burner included in a gas turbine burner according to a third embodiment of the present invention, and is a cross-sectional view including a central axis of the burner.

Fig. 10 is a view showing a main structure of a burner included in a gas turbine combustor according to a fourth embodiment of the present invention, and is a cross-sectional view including a central axis of the burner.

Fig. 11 is a view showing a main structure of a burner tip provided in a gas turbine burner according to a fifth embodiment of the present invention, and is a cross-sectional view including a central axis of the burner tip.

Fig. 12 is a schematic configuration diagram of a gas turbine generator including a gas turbine combustor according to a sixth embodiment of the present invention.

Fig. 13 is a schematic configuration diagram of a gas turbine generator including a gas turbine combustor according to a seventh embodiment of the present invention.

Fig. 14 is a view of a burner tip provided in a gas turbine combustor according to a seventh embodiment of the present invention, as viewed from a combustion chamber.

In the figure: 3-gas turbine combustor, 5-combustion chamber, 8-burner, 12-liner, 20-air hole plate, 21, 22-fuel nozzle, 31-pilot burner (burner), 32-main burner (burner), 51, 52-air hole, 72, 73-air flow path, 75-small hole, 76, 77-fuel flow path, 79-bypass hole, a 2-compressed air.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(first embodiment)

Gas turbine generator

Fig. 1 is a schematic configuration diagram of a gas turbine generator including a gas turbine combustor according to a first embodiment of the present invention. Fig. 2 is a view showing a main structure of a burner included in a gas turbine combustor according to a first embodiment of the present invention, and is a cross-sectional view including a central axis of the burner. Fig. 3 is a view of a combustion nozzle provided in a gas turbine combustor according to a first embodiment of the present invention, as viewed from a combustion chamber.

The gas turbine generator 1 includes an air compressor 2, a gas turbine combustor (hereinafter simply referred to as a combustor) 3, a turbine 4, and a generator 6. The air compressor 2 takes in and compresses air a1, and supplies compressed air a2 to the combustor 3. The combustor 3 mixes and combusts the compressed air a2 with the gas fuel F to generate combustion gas G1. The turbine 4 is driven by the combustion gas G1 generated in the combustor 3, and the combustion gas G1 that drives the turbine 4 is discharged as exhaust gas G2. The generator 6 is driven by the rotational power of the turbine 4 to generate electric power. The gas turbine is driven by the starter motor 7 only at the start of starting.

Gas turbine combustor

The combustor 3 is mounted on a casing (not shown) of a gas turbine, and includes a liner (inner tube) 12, a sleeve (outer tube) 10, a burner 8, and a fuel system 200. The liner 12 is a cylindrical member and forms the combustion chamber 5 therein. The sleeve 20 is a cylindrical member having an inner diameter larger than that of the liner 12 and surrounding the outer periphery of the liner 12, and forms a cylindrical air flow path 9 with the liner 12. The end of the sleeve 10 opposite the turbine 4 (left side in fig. 1) is closed by an end shield 13. The compressed air a2 from the air compressor 2 flows through the sleeve 10 in the air flow path 9 formed on the outer periphery of the liner 12 in a direction away from the turbine 4, and the compressed air a2 flowing through the air flow path 9 convectively cools the outer peripheral surface of the liner 12. Further, a plurality of holes are formed in the wall surface of the liner 12, and a part A3 of the compressed air a2 flowing through the air flow path 9 flows into the combustion chamber 5 through the holes, thereby film-cooling the inner peripheral surface of the liner 12. The compressed air a2 that has reached the burner tip 8 through the air flow path 9 is discharged into the combustion chamber 5 together with the gaseous fuel F supplied from the combustion system 200 to the burner tip 8 and is combusted. The combustion chamber 5 combusts a mixture of the compressed air a2 and the gas fuel F to generate combustion gas G1, and supplies the combustion gas G to the turbine 4 through a combustor transition piece (not shown).

As shown in fig. 1, the burner 8 is provided with only one air hole plate 20, fuel nozzles 21 and 22, and a fuel distributor (fuel head) 23, which are disposed at an inlet (an end opening on the opposite side of the turbine 4) of the liner 12.

The air hole plate 20 is a circular plate coaxial with the liner 12, is disposed at an inlet (an end opening on the opposite side to the turbine 4) of the liner 12, and is supported by the fuel distributor 23 via a plate support 70 as shown in fig. 1 in the present embodiment. The air hole plate 20 is provided with a plurality of air holes 51, 52 through which the compressed air a2 is introduced into the combustion chamber 5. The plurality of air holes 51 and 52 form a plurality of (2 in this example) annular rows concentric with the center axis O of the liner 12. The annular row belonging to the first row (innermost circumference) is an air hole 51, and the annular row belonging to the second row (outermost circumference) is an air hole 52. In the present embodiment, the air holes 51 and 52 are provided with a rotation angle, and the outlet of each hole is offset to one side in the circumferential direction with respect to the inlet.

The fuel nozzles 21 and 22 are supported by a fuel distributor 23, and are disposed on the opposite side of the combustion chamber 5 across the air hole plate 20. The number and positions of the fuel nozzles 21 and 22 correspond to the air holes 51 and 52 (one fuel nozzle corresponds to one air hole), and a plurality of concentric (2 rows in this example) annular rows centered on the central axis O of the liner 12 are formed together with the air holes 51 and 52. The fuel nozzles 21 belong to the annular row of the first row (innermost circumference), and the fuel nozzles 22 belong to the annular row of the second row (outermost circumference). The fuel nozzles 21 and 22 inject the gaseous fuel F toward the inlets of the corresponding air holes toward the injection ports and toward the corresponding air holes. By injecting fuel from the plurality of fuel nozzles into the corresponding air holes, the fuel and the coaxial jet of air covering the periphery of the fuel flow with the air flow are dispersed and injected from each air hole into the combustion chamber 5.

Further, the number of fuel nozzles and air holes increases in the outer annular row due to the difference in the circumference of the annular row. That is, the number of the fuel nozzles 21 and the air holes 51 (6 each in the example of fig. 3) in the first row (innermost circumference) is smaller than the number of the fuel nozzles 22 and the air holes 52 (12 each in the example of fig. 3) in the second row (outermost circumference).

The fuel distributor 23 is a member that distributes and supplies fuel to the fuel nozzles 21 and 22, and includes a plurality of fuel chambers 25 and 26 inside. The fuel chambers 25 and 26 are spaces that function to distribute and supply the gaseous fuel F to the plurality of fuel nozzles belonging to the corresponding annular rows. The fuel chamber 25 is formed in a columnar shape on the central axis O of the liner 12, and the fuel chamber 26 is formed in a cylindrical shape surrounding the outer periphery of the fuel chamber 25. In the present embodiment, each fuel nozzle 21 is connected to the fuel chamber 25, and each fuel nozzle 22 is connected to the fuel chamber 26. When the gas fuel F is supplied to the fuel chamber 25, the gas fuel F is distributed and discharged to the fuel nozzles 21 arranged in the annular row on the inner periphery, and the gas fuel F is discharged from the air holes 51 to the combustion chamber 5 together with the compressed air a 2. When the gas fuel F is supplied to the fuel chamber 26, the gas fuel F is distributed and discharged to the fuel nozzles 22 arranged in the annular row on the outer periphery, and is discharged from the air holes 52 to the combustion chamber 5 together with the compressed air a 2.

Here, the burner 8 of the present embodiment includes a chamber 74, a plurality of small holes 75, and air passages 72 and 73. The chamber 74 is a space formed inside the air orifice plate 20 to distribute and supply the compressed air a2 to the plurality (a plurality) of small orifices 75, and is formed in a columnar shape in the center portion of the annular row of the air orifices 51, 52 (on the center axis O of the air orifice plate 20 in the present embodiment).

The plurality of small holes 75 are gas injection holes connecting the chamber 74 and the combustion chamber 5, and open to the surface of the air orifice plate 20 (the surface facing the combustion chamber 5). In the present embodiment, the number of the small holes 75 is larger than the total number of the air holes 51, 52, and the opening diameter of each small hole 75 is much smaller than the opening diameter of the air holes 51, 52. These small holes 75 are densely provided in the inner region 71 of the annular row of innermost air holes (i.e., air holes 51). In the present embodiment, as shown in fig. 1 to 3, the inner region 71 on the surface of the air hole plate 20 is formed by a lid-like circular plate that closes the chamber 74, and the entire small holes 75 pass through the circular plate. These small holes 75 are preferably formed with a rotation angle in the same manner as the air holes 51 and 52, but are not preferably formed with a rotation angle, and in the present embodiment, all the small holes 75 are formed parallel to the central axis O of the liner 12.

The air flow paths 72 and 73 are passages for guiding a gas (compressed air a2 in the present embodiment) to the small holes 75, and are connected to the small holes 75 through the chamber 74. Specifically, the air flow path 72 penetrates the plate holder 70 in a direction intersecting the center axis O of the liner 12, and opens into a space filled with compressed air a2 between the air orifice plate 20 and the fuel distributor 23. Air flow path 73 extends along center axis O inside plate holder 70 and air orifice plate 20, and connects air flow path 72 and chamber 74. Thereby, the compressed air a2 is guided to the chamber 74 through the air flow paths 72 and 73, and the compressed air a2 introduced into the chamber 74 is distributed and discharged from the respective orifices 75 to the combustion chamber 5. In the present embodiment, only the air flow path 73 is connected to the chamber 74 except for the orifice 75, and only the compressed air a2 is discharged from the orifice 75 to the combustion chamber 5.

The fuel system 200 includes a fuel supply source 56, a main flow pipe 57, branch pipes 58 and 59, a fuel shutoff valve 60, and fuel flow rate adjustment valves 61 and 62. A main pipe 57 extends from the fuel supply source 56, and the main pipe 57 branches into two branch pipes 58 and 59. The branch pipe 58 is connected to the fuel chamber 25, and the branch pipe 59 is connected to the fuel chamber 26. The fuel shutoff valve 60 is provided in the main flow pipe 57, the fuel flow rate adjustment valve 61 is provided in the branch pipe 58, and the fuel flow rate adjustment valve 62 is provided in the branch pipe 59. The fuel shut-off valve 60 is opened to supply the gaseous fuel F to the branch pipes 58, 59, and the fuel shut-off valve 60 is closed to shut off the supply of the gaseous fuel F to the branch pipes 58, 59. The fuel flow rate adjustment valves 61 and 62 function to adjust the flow rate of the fuel flowing through the branch pipes 58 and 59 according to the opening degree, and can shut off the flow of the fuel in the branch pipes 58 and 59 even when the branch pipes are fully closed. For example, the fuel cut valve 60 is opened and the opening degree of the fuel flow rate adjustment valve 61 is increased from the fully closed state to increase the supply flow rate of the fuel to the fuel chamber 25, thereby increasing the fuel injection amount from the fuel nozzle 21 or the fuel-air ratio of the coaxial jet flow ejected from the air hole 51. Similarly, the opening degree of the fuel flow rate adjustment valve 62 is increased from the fully closed state to increase the supply flow rate of the fuel to the fuel chamber 26, thereby increasing the fuel injection amount from the fuel nozzle 22 or the fuel-air ratio of the coaxial jet flow ejected from the air hole 52.

The gas fuel F supplied from the fuel supply source 56 may be a gas containing hydrogen and carbon monoxide, such as an oil gas, a coke oven gas, a refinery off gas, or a coal gas, in addition to natural gas, which is a standard gas turbine fuel.

Comparative example-

For comparison, fig. 4 shows a cross-sectional view of a central axis including a conventional burner tip, and fig. 5 shows a view seen from a combustion chamber. In these drawings, a burner in which a plurality of air holes and fuel nozzles are arranged in two concentric annular rows is shown as in the present embodiment, and the conventional burner does not include elements corresponding to the orifice 75, the air flow passages 72, 73, and the chamber 74 of the present embodiment. The inner zone Z of the annular row of innermost air holes in the air hole plate constitutes a wall surface facing the combustion chamber.

An apparatus in which coal dust generated by combustion adheres to the inner zone Z in a conventional burner is described with reference to fig. 6. The flame X formed by the burner tip and the recirculation flow Y are schematically shown in this figure. The combustion gas returns upstream by forming the recirculation flow Y in the center portion downstream of the burner tip, and the mixed gas of the gas fuel and the air is burned by the heat of the combustion gas to form the stable flame X. The coal dust is generated by thermal decomposition of the fuel under fuel rich conditions and high temperature conditions, using carbon components of hydrocarbons such as methane and propane contained in the fuel as sources. The soot returns to the center of the burner along with the recirculation flow Y and adheres to the inner region Z of the annular row of air holes in the innermost periphery of the air hole plate. When the attached soot burns, the burner may be overheated, and when the soot falls off, the downstream structural member may be damaged.

Effects-

(1) In this embodiment, an apparatus for suppressing the adhesion of soot to a burner tip will be described with reference to fig. 7. In the present embodiment, as shown in the drawing, the compressed air a2 flows in from the air flow path 72 provided in the plate holder 70, and the compressed air a2 is ejected from the plurality of small holes 75 to the combustion chamber 5 through the air flow path 73 and the chamber 74. The jet 82 formed by the compressed air a2 blows up the flying soot along with the recirculation flow 80, and suppresses the adhesion of the soot to the inner area 71. By suppressing the adhesion of soot to the burner 8, the possibility of overheating of the burner 8 due to the combustion of soot and the possibility of damage to the downstream components due to the dropping of soot can be reduced. As described above, according to the present embodiment, in the gas turbine combustor of the lean combustion system, adhesion of soot and dust accompanying combustion to the burner 8 can be suppressed, and structural reliability can be improved.

(2) In the present embodiment, the structure is simple in which a part of the compressed air a2 is branched and discharged from the small hole 75, and the energy efficiency is high because fuel is not used in forming the nozzle 82.

(3) Assuming that the small holes 75 have a rotation angle, the jet flow 82 has a rotation component to form a circulation flow, and in the present embodiment, the small holes 75 extend parallel to the central axis O of the liner 12, and the jet flow 82 actively flows downstream, so that the soot and dust can be effectively moved downstream.

(second embodiment)

-structure-

Fig. 8 is a view showing a configuration of a main part of a burner tip provided in a gas turbine burner according to a second embodiment of the present invention, and is a sectional view including a central axis of the burner tip. Fig. 8 corresponds to fig. 2 of the first embodiment. In fig. 8, the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 2, and description thereof is omitted.

The present embodiment differs from the first embodiment in that it includes a fuel flow path 76 connected to a plurality of small holes 75. In the present embodiment, the air passages 72 and 73 of the first embodiment do not exist, and the chamber 74 is connected to the fuel chamber 25 through the fuel passage 76. The fuel flow path 76 extends along the center axis O inside the plate holder 70 and the air orifice plate 20. Thereby, the gaseous fuel F is guided to the chamber 74 through the fuel flow path 76, and the gaseous fuel F introduced into the chamber 74 is distributed and discharged from the respective orifices 75 to the combustion chamber 5. In the present embodiment, only the fuel flow path 76 is connected to the chamber 74 except for the orifice 75, and only the gaseous fuel F is discharged from the orifice 75 to the combustion chamber 5.

The gas fuel F ejected from the orifice 75 is a part of the gas fuel F supplied to the fuel nozzle 21, and the flow rate distribution of the gas fuel F ejected from the fuel nozzle 21 and the orifice 75 can be adjusted by the ratio of the flow path area (for example, the hole diameter) of the fuel nozzle 21 and the orifice 75 (or the fuel flow path 76). However, the setting of the opening diameter of the orifice 75 is limited within the pressure variation range (design value) of the chamber 74 so that the gas fuel F jetted from the orifice 75 does not burn and so that the fuel-air ratio in the vicinity of the inner region 71 by the gas fuel F jetted from the orifice 75 does not reach the flammable range (flammable boundary). The opening diameter of the orifice 75 is preferably set to limit the fuel injection flow rate so that the fuel-air ratio does not reach the lower limit of the flammable limit (always smaller than the lower limit) even at the maximum pressure of the chamber 74, and a configuration that always exceeds the upper limit of the flammable range may be considered. Further, a configuration may be considered in which a dedicated branch pipe (fuel pipe) for supplying the gaseous fuel F to the fuel flow path 76, a fuel flow rate adjustment valve provided in the dedicated branch pipe, and the flow rate of the gaseous fuel F discharged from the orifice 75 can be adjusted independently of the amount of fuel supplied to the fuel nozzles 21 and 22.

Except for the above-described aspects, the present embodiment is the same as the first embodiment.

Effects-

In the present embodiment, the gaseous fuel F ejected from the small hole 75 to the combustion chamber 5 blows off coal dust, and the adhesion of the coal dust to the burner 8 is suppressed. Thus, the same effect (1) as in the first embodiment can be obtained also in the present embodiment. Further, since the configuration of the small hole 75 is the same as that of the first embodiment, the effect (3) can be obtained as well as the first embodiment.

(third embodiment)

-structure-

Fig. 9 is a view showing a configuration of a main part of a burner tip provided in a gas turbine burner according to a third embodiment of the present invention, and is a sectional view including a central axis of the burner tip. Fig. 9 corresponds to fig. 2 of the first embodiment. In fig. 9, the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 2, and description thereof is omitted.

The present embodiment differs from the first embodiment in that it includes a fuel flow path 77 connected to the orifice 75 in addition to the air flow paths 72 and 73 connected to the plurality of orifices 75. The fuel flow path 77 extends along the central axis O and opens in the middle of the air flow path 73 while opening inside the plate holder 70, and connects the fuel chamber 25 and the air flow path 73. Thereby, a part of the gas fuel F is introduced from the fuel chamber 25 into the air flow path 73 through the fuel flow path 77, and a mixture of the gas fuel F and the compressed air a2 is introduced into the chamber 74 through the air flow path 73. The air-fuel mixture introduced into the chamber 74 is distributed to the small holes 75 and is discharged into the combustion chamber 5 in a state where the air-fuel mixture of the gas fuel F and the compressed air a2 further progresses. As in the second embodiment, the flow rate distribution of the gas fuel F ejected from the fuel nozzle 21 and the orifice 75 can be adjusted by the ratio of the flow path area of the fuel nozzle 21 and the orifice 75 (or the fuel flow path 77). The second embodiment is also the same in that the fuel-air ratio of the air-fuel mixture jetted from the small holes 75 in the vicinity of the inner region 71 does not fall within the combustible range.

Except for the above-described aspects, the present embodiment is the same as the first embodiment.

Effects-

In the present embodiment, the mixture gas ejected from the small hole 75 to the combustion chamber 5 blows off coal dust, thereby suppressing the adhesion of the coal dust to the burner 8. Thus, the same effect (1) as in the first embodiment can be obtained also in the present embodiment. Further, since the configuration of the small hole 75 is the same as that of the first embodiment, the effect (3) can be obtained as in the first embodiment.

(fourth embodiment)

-structure-

Fig. 10 is a view showing a configuration of a main part of a burner tip provided in a gas turbine burner according to a fourth embodiment of the present invention, and is a sectional view including a central axis of the burner tip. Fig. 10 corresponds to fig. 2 of the first embodiment. In fig. 10, the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 2, and description thereof is omitted.

The present embodiment is different from the first embodiment in that a bypass hole 79 branched from the innermost peripheral air hole 51 is connected to a plurality of small holes. The bypass hole 79 opens at the inner wall surface of the air hole 51, and is connected to the chamber 74 through the inside of the air hole plate 20. At least one bypass hole 79 is present, connecting at least one air hole 51 with the chamber 74. In the present embodiment, the air flow paths 72 and 73 of the first embodiment are not present, and only at least one bypass hole 79 is connected to the chamber 74 except for the small hole 75. Thereby, the air-fuel mixture is introduced from the air hole 51 into the chamber 74 through the bypass hole 79. The air-fuel mixture introduced into the cavity 74 is distributed to the respective small holes 75 and is discharged into the combustion chamber 5 in a state where the gas fuel F and the compressed air a2 are further mixed. Further, since the air-fuel mixture discharged from the small hole 75 is a part of the air-fuel mixture discharged from the air hole 51, the flow rate distribution of the air-fuel mixture discharged from the small hole 75 and the air hole 51 can be adjusted by the ratio of the flow path area of the air hole 51 to the bypass hole 79. The ratio of the flow path area is limited so that the fuel-air ratio generated by the air-fuel mixture jetted from the small holes 75 in the vicinity of the inner region 71 does not fall within the combustible range.

Except for the above-described aspects, the present embodiment is the same as the first embodiment.

Effects-

In the present embodiment, the mixture gas ejected from the small hole 75 to the combustion chamber 5 blows off coal dust, thereby suppressing the adhesion of the coal dust to the burner 8. Thus, the same effect (1) as in the first embodiment can be obtained also in the present embodiment. Further, since the configuration of the small hole 75 is the same as that of the first embodiment, the effect (3) can be obtained also in the same manner as that of the first embodiment.

(fifth embodiment)

-structure-

Fig. 11 is a view showing a main structure of a burner tip provided in a gas turbine burner according to a fifth embodiment of the present invention, and is a cross-sectional view including a central axis of the burner tip. Fig. 11 corresponds to fig. 2 of the first embodiment. In fig. 11, the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 2, and description thereof is omitted.

The present embodiment differs from the first embodiment in that a fuel flow path 77 of the third embodiment and a bypass hole 79 of the fourth embodiment are added. Therefore, in the present embodiment, a part of the gaseous fuel F is introduced from the fuel chamber 25 into the air flow path 73 through the fuel flow path 77, and a mixture of the gaseous fuel F and the compressed air a2 is introduced into the chamber 74 through the air flow path 73. In addition, the air-fuel mixture is introduced from the air hole 51 into the chamber 74 through the bypass hole 79. The air-fuel mixture introduced into the chamber 74 is distributed to the small holes 75 and is discharged into the combustion chamber 5 in a state where the air-fuel mixture of the gas fuel F and the compressed air a2 further progresses. The flow rate of the air-fuel mixture and the like can be adjusted in the same manner as in the third and fourth embodiments.

Except for the above-described aspects, the present embodiment is the same as the first embodiment. In the present embodiment, a case where the fuel flow path 77 and the bypass hole 79 are added to the structure of the first embodiment (a combination of the third embodiment and the fourth embodiment) will be described as an example. However, the combination of the embodiments is not limited to this, and for example, a configuration (combination of the first embodiment and the fourth embodiment) in which the fuel flow path 77 is omitted is also applicable in the present embodiment. Note that, in the present embodiment, a configuration in which the air flow paths 72 and 73 are omitted (a combination of the second embodiment and the fourth embodiment) is also established.

Effects-

In the present embodiment, the above-described effects (1) and (3) can be obtained.

(sixth embodiment)

-structure-

Fig. 12 is a schematic configuration diagram of a gas turbine generator provided in a gas turbine combustor according to a sixth embodiment of the present invention. Fig. 12 corresponds to fig. 1 of the first embodiment. In fig. 12, the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 1, and description thereof is omitted.

Fig. 12 shows a structure of a burner according to example 6. The present embodiment differs from the first embodiment in that it includes a composite burner configured such that the burner 3 includes a plurality of burners. The burner 3 of the present embodiment includes a single pilot burner 31 and a main burner 32 disposed so as to surround the pilot burner 31. The present embodiment is an example in which the invention is applied to the pilot burner 31, and fig. 12 illustrates a case in which a burner of the same type as the fifth embodiment (fig. 11) is applied to the pilot burner 31, and any of the burners of the first to fifth embodiments can be applied to the pilot burner 31. The compressed air a2 is supplied to the air holes 51, 52, and the small holes 75 of the pilot burner 31 through the pilot burner air introduction hole 30 provided in the nozzle holder of the main burner 32 and the pilot burner air passage 33 provided around the fuel distributor 23.

A variety of burners can be employed in the primary burner 32. The main burner 32 of the present embodiment is a premix burner, and includes a main burner fuel nozzle 34, a main burner premix passage 35, and an annular flame holder 36. The gas fuel F is supplied to the main burner fuel nozzle 34 through a branch pipe 59a that branches from the main flow pipe 57 downstream of the fuel cut valve 60. The branch pipe 59a is provided with a fuel flow rate adjustment valve 63, and the fuel supplied to the main burner fuel nozzle 34 can be shut off by adjusting the flow rate by the fuel flow rate adjustment valve 63. The gas fuel F injected from the main burner fuel nozzle 34 is mixed with the compressed air a2 in the main burner premixing passage 35 to become a premixed gas, and is discharged from the main burner premixing passage 35 into the combustion chamber 5 to form a flame. The annular flame holder 36 stabilizes the flame generated by the premixed gas jetted from the main burner premixing flow path 35.

As described above, the present embodiment is the same as the first embodiment except that the main burner 32 of another combustion type is disposed around the pilot burner 31.

Effects-

As described above, the burner tip of the present invention can be combined with various kinds of burner tips. As in the present embodiment, a lean combustion method having excellent combustion stability is applied to the pilot burner 31 located at the center of the combustor 3, and a premixed burner is used for the main burner 32, whereby a large-capacity gas turbine having excellent combustion stability and low NOx can be established. In this case, by applying the burner of any of the previous embodiments to the pilot burner 31, it is possible to suppress the adhesion of soot to the burner and to improve the structural reliability.

(seventh embodiment)

-structure-

Fig. 13 is a schematic configuration diagram of a gas turbine generator including a gas turbine combustor according to a seventh embodiment of the present invention, and fig. 14 is a view of a combustion nozzle provided in the gas turbine combustor according to the present embodiment as viewed from a combustion chamber. Fig. 13 and 14 correspond to fig. 1 and 3 of the first embodiment. In fig. 13 and 14, the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 1 and 3, and description thereof is omitted.

The present embodiment differs from the first embodiment in that the combustor 3 includes a composite burner including a plurality of burners, as in the sixth embodiment. However, in the present embodiment, the present invention is applicable not only to the pilot burner 31 but also to a plurality of (6 in the present example) main burners 32 arranged around the pilot burner 31. Any one of the burners of the first to fifth embodiments can be applied to the pilot burner 31 and the plurality of main burners 32. For example, the pilot burner 31 and the main burner 32 may be selected from the first to fifth embodiments, and may be unified with each other, or a mixture of a plurality of burners may be selected from the first to fifth embodiments. The pilot burner 31 may be shared by the air hole plate 20 and the plurality of main burners 32 (the air holes 51 and 52 of the respective burners are formed in one air hole plate 20).

In the combustion system 200, the branch pipes 58 and 59 branching from the main pipe 57 in the same number as the total number (7 in this example) of the pilot burner 31 and the main burner 32 are connected to the fuel chambers 25 and 26 of the corresponding burners. The main burner 32 may be configured such that the fuel system (the branch pipe 59 and the fuel flow rate adjustment valve 62) is shared by at least 2 burners. As in the first to sixth embodiments, the main flow pipe 57 and the branch pipes 58 and 59 are provided with a fuel shutoff valve 60 and fuel flow rate adjustment valves 61 and 62, respectively.

Except for the above-described aspects, the present embodiment is the same as the first embodiment.

Effects-

By configuring a composite burner by applying a burner configuration arbitrarily selected from the first to fifth embodiments to the pilot burner 31 and the main burner 32, the same effects as those of the selected embodiments can be obtained and the capacity of the gas turbine can be increased.