Patent Application
20150300648
The present invention relates to a premixed-combustion gas turbine combustor and a gas turbine including the gas turbine combustor.
There are conventionally known premixed-combustion gas turbine combustors that previously mix the fuel with combustion air and then burn the premixed gas (for example, see Patent Literature 1). The gas turbine combustor includes a main burner in which the premixed gas passes. The main burner includes a burner external cylinder and an extension pipe placed downstream of the burner external cylinder. Burning the premixed gas from the main burner generates flashback that is a phenomenon of a backfire (combustion) in the main burner. In light of the foregoing, to prevent the generation of flashback, an air formed into a film shape (the film air) flows from the gap between the burner external cylinder and the extension pipe and along the inner wall surface of the extension pipe.
Patent Literature 1: Japanese Patent No. 4070758
By the way, the air taken in the gas turbine combustor is distributed as the cooling air in addition to as the combustion air and the film air described above. At that time, the amount of air to be taken in the gas turbine combustor is prescribed in accordance with the output performance of the gas turbine. Thus, using a large amount of the air as the film air and the cooling air reduces the amount of air to be used as the combustion air. Meanwhile, the fuel component in the premixed gas increases. This makes it difficult to reduce the NOx generated in the combustion.
In light of the foregoing, an objective of the present invention is to provide a gas turbine combustor and a gas turbine that can reduce NOx generated in the combustion while preventing flashback.
According to an aspect of the present invention, a gas turbine combustor that forms therein a combustion region by burning a premixed gas obtained by mixing a fuel and combustion air in advance, comprises: a premixed gas supply passage in which the premixed gas passes; a film air supply port that is provided on the premixed gas supply passage and that supplies a film air formed into a film shape along an inner wall surface of the premixed gas supply passage; and a cooling passage in which a cooling air passes to cool the inner wall surface facing the combustion region formed. An outlet side of the cooling passage is connected to the film air supply port.
The configuration can use the cooling air as the film air, and thus can reduce the amount of air to be used in comparison with the case in which separate airs are used for the cooling air and the film air. The reduction can increase the amount of air to be used as the fuel air. The increase can decrease the concentration of the fuel component in the premixed gas. This can cool the inner wall surface in the combustion chamber while preventing the flashback, and can reduce NOx generated by the combustion of the premixed gas.
Advantageously, in the gas turbine combustor, the cooling passage is formed along an inner surface opposing to the combustion region across the inner wall surface.
The configuration enables the cooling air to pass along the inner surface, and thus can cool the inner wall surface preferably.
Advantageously, in the gas turbine combustor, an impingement member is inserted in the cooling passage and the impingement member includes an impingement hole penetrating the impingement member such that the cooling air is injected onto the inner surface.
This configuration enables the cooling air passing through the cooling passage to jet from the impingement member and hit the inner surface by causing the cooling air to pass through the impingement member. Thus, the configuration can cool the inner wall surface facing the combustion region preferably. Meanwhile, the configuration can accelerate the flow rate of air after the air passes through the impingement hole, and thus can improve the efficiency of cooling the inner surface. This can reduce the amount of air to be used as the cooling air.
Advantageously, in the gas turbine combustor, the film air supply port is an opening formed between the inner wall surface on an upstream side of the premixed gas supply passage and the inner wall surface on a downstream side provided outside the inner wall surface on the upstream side.
The configuration enables the film air supplied from the film air supply port to pass along the inner wall surface of the premixed gas supply passage preferably.
Advantageously, in the gas turbine combustor, the film air supply port is a slit opening formed on the inner wall surface of the premixed gas supply passage.
The configuration can supply the film air supplied from the film air supply port from the inner wall surface of the premixed gas supply passage, thus can use the inner wall surface as a plane.
According to another aspect of the present invention, a gas turbine comprises: any one of the above gas turbine combustors; and a turbine that rotates by a combustion gas generated by combustion of the premixed gas in the gas turbine combustor.
The configuration can rotate the turbine in low NOx combustion while preventing flashback.
The embodiments according to the present invention will be described in detail hereinafter with reference to the appended drawings. Note that the present invention is not limited to the embodiments. Furthermore, the components in the embodiments include things that a person skilled in the art can replace and that are simple, or things that are substantially the same as the components.
The compressor 11 includes an air inlet 15 for taking air in, and a compressor casing 16 in which a plurality of compressor vanes 17 and turbine blades 18 are alternately arranged. The combustor 12 can burn the air compressed in the compressor 11 (the combustion air) by supplying the fuel to the air and then igniting the air with the burner. The turbine 13 includes a plurality of turbine vanes 21 and turbine blades 22 that are alternately arranged in a turbine casing 20. The exhaust chamber 14 includes a exhaust diffuser 23 continuously connected to the turbine 13. A rotor (turbine shaft) 24 penetrates the central portions of the compressor 11, the combustor 12, the turbine 13, and the exhaust chamber 14. The end of the rotor 24 on the side of the compressor 11 is rotatably supported at a bearing portion 25 while the end of the rotor 24 on the side of the exhaust chamber 14 is rotatably supported at a bearing portion 26. Furthermore, a plurality of disk plates are fixed on the rotor 24 so as to connect each of the turbine blades 18 and 22 to the disk plate. A driving shaft of an electric generator (not illustrated) is connected to the end of the rotor 24 on the side of the exhaust chamber 14.
The air taken from the air inlet 15 of the compressor 11 is compressed and becomes a compressed air with a high temperature and a high pressure while passing through the compressor vanes 21 and the turbine blades 22. Then, the compressed air burns with a predetermined fuel supplied thereto in the combustor 12. Combustion gas with a high temperature and a high pressure is generated in the combustor 12 as a working fluid. Subsequently, the combustion gas drives and rotates the rotor 24 by passing through the turbine vanes 21 and turbine blades 22 included in the turbine 13. This rotation drives the electric generator connected to the rotor 24. On the other hand, the exhausted gas that is the combustion gas after driving and rotating the rotor 24 is discharged to the air after the pressure of the exhausted gas is transformed into a static pressure in the exhaust diffuser 23 of the exhaust chamber 14.
The external cylinder 31 is fastened to the casing housing 27 forming a casing 34 to which the compressed air flows from the compressor 11. The base end portion of the inner cylinder 32 is supported with the external cylinder 31. The inner cylinder 32 is placed inside the external cylinder 31, leaving a predetermined space from the external cylinder 31. A pilot burner 40 is provided along the central axis S at the central portion of the inner cylinder 32. A plurality of main burners 50 are arranged at regular intervals around the pilot burner 40, surrounding the pilot burner 40 and being parallel to the pilot burner 40. The base end of the transition piece 33 is formed into a cylindrical shape and is connected to the top end of the inner cylinder 32. The transition piece 33 is formed into a curved shape while the cross-sectional area decreases toward the top end of the transition piece 33. The transition piece 33 includes an opening that opens toward a first turbine vane 21 in the turbine 13. The transition piece 33 includes a combustion chamber therein.
As illustrated in
In other words, the compressed air that has flown into the inner cylinder 32 is mixed with the fuel ejected from the main nozzle 52. The mixed air forms a swirling flow of the premixed gas and flows into the transition piece 33 from the burner cylinder 51. Thus, the burner cylinder 51 functions as a premixed gas supply passage for supplying the premixed gas toward the transition piece 33. Separately from the premixed gas, the compressed air that has flown into the inner cylinder 32 is swirled with the pilot swirler 43 and then is mixed with the fuel ejected from the pilot nozzle 42 and becomes a premixed gas. The premixed gas flows into the transition piece 33. The premixed gas from the pilot nozzle 42 is ignited with a pilot light (not illustrated) and burns. After that, the premixed gas becomes the combustion gas and jets into the transition piece 33. At that time, a part of the combustion gas jets with flame in the transition piece 33 while diffusing. This ignites and burns the premixed gas that has flown in the transition piece 33 from the burner cylinder 51 in each of the main burners 50.
As described above, the diffusion flame with the fuel ejected from the pilot nozzle 42 can stabilize the flame for stably burning the lean premixed fuel from the main nozzle 52. The premix of the fuel from the main nozzle 52 and the compressed air in the main burner 50 equalizes the concentration of the fuel. This equalization can reduce NOx.
By the way, in such a premix combustor 12, the flow rate of the premixed gas flowing in the burner cylinder 51 decreases downstream of the main nozzle 52 and on the side of the inner wall surface of the burner cylinder 51. The combustion in the combustion region R1 expands toward the premixed gas at the decreasing speed. This expansion facilitates backfire (flashback) from the combustion region R1 to the unburned gas region R2. In light of the foregoing, to prevent the flashback from the combustion region R1 to the unburned gas region R2, a film air is supplied to the burner cylinder 51 of the main burner 50 along the inner wall surface of the burner cylinder 51.
Additionally, the combustion increases the temperature in the combustion region R1. Thus, the inner wall surface facing the combustion region R1 needs to be cooled. Specifically, the inner wall surface facing the combustion region R1 includes the inner wall surface of the pilot cone 41 and a back-step surface 65 to be described below. To cool the inner wall surface of the pilot cone 41 and the back-step surface 65, the cooling air is supplied in the pilot cone 41.
As described above, the air taken from the air inlet 15 in the compressor 11 is used as the combustion air, the film air, and the cooling air. In such a case, the amount of air to be taken in is prescribed in accordance with the output performance of the gas turbine 1. Thus, using a large amount of the air as the film air and the cooling air reduces the amount of air to be used as the combustion air. In light of the foregoing, the first embodiment includes the configuration to be described below in order to prevent the decrease in the amount of air to be used as the combustion air. The configuration around the pilot cone 41 and the burner cylinder 51 will be described hereinafter with reference to
As illustrated in
The top end portion 41a on the inner circumferential surface (the inner wall surface) of the pilot cone 41 is connected to the top end portion 57b on the inner circumferential surface of the second burner cylinder 57 (the burner cylinder 51) through the back-step surface 65. The back-step surface 65 is perpendicular to the central axis S and faces the combustion region R1.
The pilot cone 41 includes a cooling passage 71 in which the cooling air flows. The cooling passage 71 is formed between the outer circumferential surface of the pilot cone 41 and the outer circumferential surface of the burner cylinder 51. A first end of the cooling passage 71 is connected to the casing 34 in which the compressed air flows. A second end of the cooling passage 71 is connected to the film air supply port 61. The cooling passage 71 includes an upstream cooling passage 71a, a midstream cooling passage 71b, a downstream cooling passage 71c, and a film air supply passage 71d.
The upstream cooling passage 71a lies along the outer circumferential surface of the pilot cone 41 such that the cooling air flows therein from the base end to top end of the pilot cone 41. The midstream cooling passage 71b lies along the surface (inner surface) of the inside (the opposite side) of the back-step surface 65 such that the cooling air flows therein from the pilot cone 41 to each of the second burner cylinders 57. The downstream cooling passage 71c lies along the outer circumferential surface of the second burner cylinder 57 such that the cooling air flows from the top end to base end of the second burner cylinder 57. The film air supply passage 71d is a cooling passage that lies between the outer circumferential surface of the first burner cylinder 56 and the inner circumferential surface of the second burner cylinder 57 such that the cooling air flows therein from the base end to top end of the second burner cylinder 57 and then the cooling air is discharged from the film air supply port 61.
A part of the compressed air in the casing 34 flows as the cooling air into the cooling passage 71 having the configuration described above. The cooling air flows along the outer circumferential surface of the pilot cone 41 by flowing in the upstream cooling passage 71a. The flow cools the inner circumferential surface of the pilot cone 41. After that, the cooling air flows along the inner surface of the back-step surface 65 by flowing in the midstream cooling passage 71b. The flow cools the back-step surface 65. Then, the cooling air flows along the outer circumferential surface of the second burner cylinder 57 by flowing in the downstream cooling passage 71c. The flow cools the inner circumferential surface of the second burner cylinder 57. Thus, the cooling air flows in the upstream cooling passage 71a in the opposite direction to the direction in which the cooling air flows in the downstream cooling passage 71c. Subsequently, the cooling air flows along the inner circumferential surface of the second burner cylinder 57 by flowing in the film air supply passage 71d. This flow discharges the cooling air as the film air from the film air supply port 61.
After being discharged from the film air supply port 61, the film air flows along the inner circumferential surface of the second burner cylinder 57 and joins the premixed gas flowing in the second burner cylinder 57 downstream of the film air supply port 61.
As described above, the configuration enables the first embodiment to use the cooling air as the film air. The usage can reduce the amount of air to be used in comparison with the case in which separate airs are used for the cooling air and the film air. The reduction can increase the amount of air to be used as the fuel air. The increase can decrease the concentration of the fuel component in the premixed gas. This can cool the surface facing the combustion region R1, namely, the back-step surface 65 and the like while preventing the flashback and can reduce NOx generated by the combustion of the premixed gas.
A gas turbine combustor 100 according to the second embodiment will be described next with reference to
As illustrated in
A cooling passage 71 that cools a pilot cone 41 of a pilot burner 40 is connected to the inside film air supply port 61a. On the other hand, the outside film air supply port 61b is connected to the casing 34. Thus, the cooling passage 71 includes an upstream cooling passage 71a, a midstream cooling passage 71b, and a downstream cooling passage 71c. Note that the upstream cooling passage 71a, the midstream cooling passage 71b, and the downstream cooling passage 71c are similar to those in the first embodiment. At that time, the inside film air supply port 61a is connected to the downstream cooling passage 71c.
A part of the compressed air in the casing 34 flows as the cooling air into the cooling passage 71 having the configuration described above. The cooling air flows along the outer circumferential surface of the pilot cone 41 by flowing in the upstream cooling passage 71a. The flow cools the inner circumferential surface of the pilot cone 41. After that, the cooling air flows along the inner surface of the back-step surface 65 by flowing in the midstream cooling passage 71b. The flow cools the back-step surface 65. Then, the cooling air flows along the inside of the burner cylinder 106 by flowing in the downstream cooling passage 71c. This flow cools the inside inner circumferential surface of the burner cylinder 106. Thus, the cooling air flows in the upstream cooling passage 71a and the downstream cooling passage 71c in the opposite direction to the direction in which the cooling air flows in the upstream cooling passage 71a. Subsequently, the cooling air is discharged as the film air from the inside film air supply port 61a connected to the downstream cooling passage 71c.
The film air discharged from the inside film air supply port 61a flows along the inside inner circumferential surface of the burner cylinder 106 and joins the premixed gas flowing in the burner cylinder 106 downstream the inside film air supply port 61a.
As described above, the configuration in the second embodiment can use the cooling air as the film air even in an annular combustor. The usage can reduce the amount of air to be used in comparison with the case in which separate airs are used for the cooling air and the film air. The reduction can increase the amount of air to be used as the fuel air. The increase can decrease the concentration of the fuel component in the premixed gas. This can cool the surface facing the combustion region R1, namely, the back-step surface 65 and the like while preventing the flashback and can reduce NOx generated by the combustion of the premixed gas.
A gas turbine combustor 110 according to the third embodiment will be described next with reference to
As illustrated in
The compressed air flows into the inside cylinder 114 of the inside burner 111. After flowing in the inside cylinder 114, the compressed air is mixed with the fuel ejected from the inside fuel nozzle 115, and then flows as the swirling flow of the premixed gas into the transition piece 33 from the inside cylinder 114. Thus, the inside cylinder 114 functions as a premixed gas supply passage for supplying the premixed gas toward the transition piece 33. Separately from the compressed air, the compressed air flows into the outside cylinder 116 of the outside burner 112. After flowing in the outside cylinder 116, the compressed air is mixed with the fuel ejected from the outside fuel nozzle 117, and flows as the swirling flow of the premixed gas from the outside cylinder 116 into the transition piece 33. Thus, the outside cylinder 116 also functions as a premixed gas supply passage for supplying the premixed gas toward the transition piece 33. The premixed gas from the inside cylinder 114 of the inside burner 111 is ignited with a pilot light (not illustrated) and burns. Then, the premixed gas becomes the combustion gas and jets into a transition piece 33. At that time, a part of the combustion gas jets with flame in the transition piece 33 while diffusing. This ignites and burns the premixed gas flown in the transition piece 33 from the outside cylinder 116 of the outside burner 112.
As illustrated in
In the combustor 110 described above, the film air flows along the inner circumferential surface inside the inside cylinder 114 of the inside burner 111, and the inner circumferential surface inside the outside cylinder 116 of the outside burner 112. Thus, an inside film air supply port 125 is provided on the inner circumferential surface inside the inside cylinder 114, and an outside film air supply port 126 is provided on the inner circumferential surface inside the outside cylinder 116. The inside film air supply port 125 is a slit opening that opens on the inner circumferential surface inside the circular inside cylinder 114 and is formed into a slit shape. The outside film air supply port 126 is also a slit opening that opens on the inner circumferential surface inside the circular outside cylinder 116 and is formed into a slit shape.
An inside cooling passage 121 that cools the back-step surface 65 inside the inside cylinder 114 is connected to the inside film air supply port 125. An outside cooling passage 122 that cools the back-step surface 65 between the inside cylinder 114 and the outside cylinder 116 is connected to the outside film air supply port 126.
The inside cooling passage 121 includes an upstream inside cooling passage 121a, and a downstream inside cooling passage 121b. The upstream inside cooling passage 121a lies along the surface (inner surface) of the inside (the opposite side) of the back-step surface 65 inside the inside cylinder 114 such that the cooling air flows therein from the central axis S to the inside cylinder 114. The downstream inside cooling passage 121b lies along the surface (inner surface) of the inside (the opposite side) of the inner circumferential surface inside the inside cylinder 114 such that the cooling air flows therein from the top end to base end of the inside cylinder 114. In that case, the inside film air supply port 125 is connected to the downstream inside cooling passage 121b.
The outside cooling passage 122 includes an upstream outside cooling passage 122a and a downstream outside cooling passage 122b. The upstream outside cooling passage 122a lies along the surface (inner surface) of the inside (the opposite side) of the back-step surface 65 between the inside cylinder 114 and the outside cylinder 116 such that the cooling air flows therein from the inside cylinder 114 to the outside cylinder 116. The downstream outside cooling passage 122b lies along the surface (inner surface) of the inside (the opposite side) of the inner circumferential surface inside the outside cylinder 116 such that the cooling air flows therein from the top end to base end of the outside cylinder 116. In that case, the outside film air supply port 126 is connected to the downstream outside cooling passage 122b.
A part of the compressed air in the casing 34 flows as the cooling air into the inside cooling passage 121 and the outside cooling passage 122 described above. In the inside cooling passage 121, the cooling air flows along the inner surface of the back-step surface 65 inside the inside cylinder 114 by flowing in the upstream inside cooling passage 121a. The flow cools the back-step surface 65. The cooling air flows along the inner surface of the inside cylinder 114 by flowing in the downstream inside cooling passage 121b. The flow cools the inner circumferential surface inside the inside cylinder 114. Subsequently, the cooling air is discharged as the film air from the inside film air supply port 125 connected to the downstream inside cooling passage 121b. Similarly, in the outside cooling passage 122, the cooling air flows along the inner surface of the back-step surface 65 between the inside cylinder 114 and the outside cylinder 116 by flowing in the upstream outside cooling passage 122a. The flow cools the back-step surface 65. The cooling air flows along the inner surface of the outside cylinder 116 by flowing in the downstream outside cooling passage 122b. The flow cools the inner circumferential surface inside the outside cylinder 116. Subsequently, the cooling air is discharged as the film air from the outside film air supply port 126 connected to the downstream outside cooling passage 122b.
After being discharged from the inside film air supply port 125, the film air flows along the inner circumferential surface inside the inside cylinder 114, and joins the premixed gas flowing in the inside cylinder 114 downstream of the inside film air supply port 125. After being discharged from the outside film air supply port 126, the film air flows along the inner circumferential surface inside the outside cylinder 116, and joins the premixed gas flowing in the outside cylinder 116 downstream of the outside film air supply port 126.
As described above, the gas turbine combustor 110 having the configuration according to the third embodiment can also use the cooling air as the film air. The usage can reduce the amount of air to be used in comparison with the case in which separate airs are used for the cooling air and the film air. The reduction can increase the amount of air to be used as the fuel air. The increase can decrease the concentration of the fuel component in the premixed gas. This can cool the surface facing the combustion region R1, namely, the back-step surface 65 and the like while preventing the flashback and can reduce NOx generated by the combustion of the premixed gas.
Note that the inside cooling passage 121 and outside cooling passage 122 in the third embodiment may be provided as illustrated in
The configuration enables the cooling air that passes in the inside cooling passage 121 and the outside cooling passage 122 to jet and hit the inner surface of the back-step surface 65 by causing the cooling air to pass through the impingement member 131. Thus, the configuration can preferably cool the back-step surface 65. The configuration can accelerate the cooling air after the cooling air has passed through the impingement hole 132 and can improve the efficiency of cooling the back-step surface 65. Thus, the configuration can reduce the amount of air to be used as the cooling air.
A gas turbine combustor 140 according to the fourth embodiment will be described next with reference to
As illustrated in
The compressed air flows into the burner cylinder 142 of the burner 141. After flowing in the burner cylinder 142, the compressed air is mixed with the fuel ejected from the fuel nozzle 143, and then flows as the swirling flow of the premixed gas from the burner cylinder 142 into the transition piece 33. Thus, the burner cylinder 142 functions as a premixed gas supply passage for supplying the premixed gas toward the transition piece 33. The premixed gas from the burner cylinders 142 of the burners 141 is ignited with a pilot light (not illustrated) and burns, and then jets as the combustion gas into the transition piece 33.
As illustrated in
In the combustor 140 described above, the film air flows along the inner circumferential surface of the burner cylinder 142. Thus, a film air supply port 146 is provided on the inner circumferential surface of the burner cylinder 142. The film air supply port 146 is a slit opening that opens on the inner circumferential surface and is formed into a slit shape. A cooling passage 145 that cools the back-step surface 65 is connected to the film air supply port 146.
The cooling passage 145 includes an upstream cooling passage 145a and a downstream cooling passage 145b. The upstream cooling passage 145a includes a cooling passage lies along the surface (inner surface) of the inside (the opposite side) of the back-step surface 65 on the inner circumferential side of the central axis S, and a cooling passage lies along the surface (inner surface) of the inside (the opposite side) of the back-step surface 65 on the outer circumferential side of the central axis S. Thus, in the upstream cooling passage 145a, the cooling air flows from the central side of the central axis S toward the burner cylinder 142, and flows from the outer circumferential side of the central axis S toward the burner cylinder 142. The downstream cooling passage 145b lies along the outer circumferential surface of the burner cylinder 142 such that the cooling air flows therein from the top end toward base end of the burner cylinder 142. In that case, the film air supply port 146 is connected to the downstream cooling passage 145b.
A part of the compressed air in the casing 34 flows as the cooling air into the cooling passage 145 described above. The cooling air flows along the inner surface of the back-step surface 65 on the inner and outer circumferential sides of the central axis S by flowing in the upstream cooling passage 145a. The flow cools the back-step surface 65. Then, the cooling air flows along the outer circumferential surface of the burner cylinder 142 by flowing in the downstream cooling passage 145b. The flow cools the inner circumferential surface of the burner cylinder 142. Subsequently, the cooling air is discharged as the film air from the film air supply port 146 connected to the downstream cooling passage 145b.
After being discharged from the film air supply port 146, the film air flows along the inner circumferential surface of the burner cylinder 142, and joins the premixed gas flowing in the burner cylinder 142 downstream of the film air supply port 146.
As described above, the gas turbine combustor 140 having the configuration according to the fourth embodiment can also use the cooling air as the film air. The usage can reduce the amount of air to be used in comparison with the case in which separate airs are used for the cooling air and the film air. The reduction can increase the amount of air to be used as the fuel air. The increase can decrease the concentration of the fuel component in the premixed gas. This can cool the surface facing the combustion region R1, namely, the back-step surface 65 and the like while preventing the flashback and can reduce NOx generated by the combustion of the premixed gas.
Note that the cooling passage 145 provided in the fourth embodiment may be provided as illustrated in
The configuration enables the cooling air that flows in the cooling passage 145 to jet and hit the inner surface of the back-step surface 65 by causing the cooling air to pass through the impingement member 151. Thus, the configuration can preferably cool the back-step surface 65. The configuration can accelerate the cooling air after the cooling air has passed through the impingement hole 152 and can improve the efficiency of cooling the back-step surface 65. The configuration can reduce the amount of air to be used as the cooling air.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2012-240829 | Oct 2012 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2013/078618 | 10/22/2013 | WO | 00 |
