Patent Application
20250052420
The present disclosure relates to a burner that uses gas fuel as auxiliary fuel, and a combustion furnace including the burner.
According to the current trend regarding the reduction of carbon dioxide (CO2), the use of CO2-free fuel which does not generate carbon dioxide in a thermal power boiler is required. Examples of such fuel include hydrogen (H2) and ammonia (NH3) as hydrogen-rich gas fuel. For example, PTL 1 discloses a burner that can perform multi-fuel combustion of solid fuel and ammonia.
The burner of PTL 1 includes: a fuel supply nozzle that discharges a fuel-air mixture containing solid fuel, such as pulverized coal, and a carrier gas for the solid fuel; an air nozzle that is located outside the fuel supply nozzle and discharges combustion air so as to separate the combustion air from the fuel-air mixture outward in a radial direction; and an ammonia supply nozzle that discharges an ammonia gas from a downstream side of an outlet of the fuel supply nozzle. The ammonia supply nozzle supplies the ammonia gas toward a reduction region (primary combustion region) where an oxygen concentration is low since oxygen is consumed by the combustion of the fuel at an immediately downstream side of the outlet of the fuel supply nozzle.
According to the structure of the burner disclosed in PTL 1, the strongest high-temperature reduction region is generated in front of a portion between the outlet of the fuel supply nozzle and the outlet of the air nozzle. At this position, a circulating vortex is generated by the flow of the fuel-air mixture and the flows of secondary air and tertiary air located at an outer peripheral side of the fuel-air mixture. Since combustible components and heat are kept in this circulating vortex, a condition for easily causing combustion is maintained, and the circulating vortex becomes an origin of ignition. In addition, the high-temperature reduction region is generated in the circulating vortex and at a downstream side of the circulating vortex. Therefore, it is thought that from the viewpoint of the improvement of combustion efficiency, discharging gas fuel such as ammonia toward the circulating vortex is more advantageous than discharging the ammonia toward the primary combustion region as in PTL 1. On the other hand, when the flow rate of the gas fuel discharged toward the circulating vortex increases, there are concerns that: the flow of the circulating vortex is disturbed by the jet flow of the gas fuel; and the combustion reaction in the circulating vortex is suppressed since the temperature of the circulating vortex is reduced by the inflow of unreacted gas fuel.
The present disclosure was made under these circumstances, and an object of the present disclosure is to propose the structure of a burner which uses gas fuel as auxiliary fuel and may improve combustion efficiency of the gas fuel while preventing a circulating vortex from being disturbed and preventing a combustion reaction in the circulating vortex from being deteriorated.
In order to solve the above problems, a burner according to one aspect of the present disclosure includes:
Moreover, a combustion furnace according to one aspect of the present disclosure includes:
The present disclosure can propose the structure of the burner which uses the gas fuel as the auxiliary fuel and may improve the combustion efficiency of the gas fuel while preventing the circulating vortex from being disturbed and preventing the combustion reaction in the circulating vortex from being deteriorated.
Hereinafter, an embodiment of the present disclosure will be described with reference to the drawings. First, the schematic configuration of a boiler 10 including burners 5 according to one embodiment of the present disclosure will be described.
A vertical combustion chamber 20 is located in the combustion furnace 2. The combustion furnace 2 according to the present embodiment is an inverted vertical furnace. A high-temperature reduction zone 21 is located at an upper portion of the combustion chamber 20, and a low-temperature oxidation zone 22 is located at a lower portion of the combustion chamber 20. A throat 23 is located between the high-temperature reduction zone 21 and the low-temperature oxidation zone 22. However, the combustion furnace 2 may be a vertical furnace in which: the high-temperature reduction zone 21 is located at the lower portion of the combustion chamber 20; and the low-temperature oxidation zone 22 is located at the upper portion of the combustion chamber 20. Or, the combustion furnace 2 to which the burners 5 according to the present disclosure are applied may be a combustion furnace other than the vertical furnace.
A portion of an inner wall of the combustion furnace 2 which defines the high-temperature reduction zone 21 is covered with a fire-resistant material 25. The burners 5 that discharge the fuel and first-stage combustion air to the high-temperature reduction zone 21 are located on a furnace wall of an upper portion of the combustion furnace 2. A fuel-air mixture containing the fuel and the air is discharged from the burners 5 into the combustion chamber 20, and flame is generated. The burners 5 are located on a pair of opposing furnace walls. At least one burner stage in an upper-lower direction is located on each furnace wall, and each burner stage includes the burners 5 lined up in a horizontal direction. The burners 5 located so as to be opposed to each other as above are located in zigzag so as to be opposed to each other such that burner axes of the burners 5 do not intersect with each other.
An outlet of the high-temperature reduction zone 21 is connected to an inlet of the low-temperature oxidation zone 22 through the throat 23. A smallest horizontal sectional area of the throat 23 is about 20 to 50% of a horizontal sectional area of the high-temperature reduction zone 21.
Air nozzles 26 are located on a furnace wall of a lower portion of the combustion furnace 2. Second-stage combustion air is discharged from the air nozzles 26 to the low-temperature oxidation zone 22. In the present embodiment, air nozzle stages are located so as to be lined up in the upper-lower direction, and each air nozzle stage includes the air nozzles 26 lined up in the horizontal direction. In the low-temperature oxidation zone 22, a cooling portion 24 is located between the throat 23 and the air nozzles 26. The furnace wall of the cooling portion 24 is a water-cooled wall at which a water pipe (not shown) of the boiler main body 40 is located.
An outlet 11 of the low-temperature oxidation zone 22 is connected to an inlet of a flue 28. A heat transfer pipe 43 of the boiler main body 40 is located at the flue 28. An exhaust gas processing system 30 is connected to an outlet of the flue 28.
In the boiler 10 configured as above, an air ratio of the fuel and the first-stage combustion air which are supplied to the high-temperature reduction zone 21 is maintained to be less than one (for example, about 0.7). In addition, a furnace internal temperature of the high-temperature reduction zone 21 surrounded by the fire-resistant material 25 hardly decreases compared to the temperature of the other furnace portion. Therefore, the atmosphere of the high-temperature reduction zone 21 is a high-temperature reduction atmosphere (atmosphere where the amount of air is smaller than the theoretical amount of air, i.e., the amount of air is inadequate) where the average temperature is about 1,500° C. In the high-temperature reduction zone 21, the gasification of the fuel is promoted.
In the high-temperature reduction zone 21, a combustion gas is generated by the gasification of the fuel. The generated combustion gas flows into the low-temperature oxidation zone 22 through the throat 23. The air ratio in the low-temperature oxidation zone 22 is maintained to be one or more (for example, about 1.1) by the second-stage combustion air supplied from the air nozzles 26 to the low-temperature oxidation zone 22. Therefore, the atmosphere of the low-temperature oxidation zone 22 is the oxidizing atmosphere, and thus, the combustion of the combustion gas is promoted in the low-temperature oxidation zone 22.
In the low-temperature oxidation zone 22, the combustion of an unburned portion of the combustion gas is completed. A flue gas from the low-temperature oxidation zone 22 flows out to the exhaust gas processing system 30 through the flue 28. The heat of the flue gas is recovered by the heat transfer pipe 43 located at the flue 28 and the furnace wall, and the steam is generated by the boiler main body 40. The generated steam is utilized by, for example, a steam turbine of a power generation facility.
Burner 5 The burner 5 included in the boiler 10 configured as above is a multi-fuel combustion burner that uses the solid fuel as the main fuel and utilizes hydrogen-containing gas fuel as auxiliary fuel. The solid fuel is, for example, pulverized fossil fuel or particulate fossil fuel, such as pulverized coal. In the present embodiment, an ammonia gas containing hydrogen and nitrogen is adopted as the gas fuel. However, a hydrogen gas or a by-product gas generated at a plant may be used as the gas fuel.
The first nozzle 71 is supplied with powdered solid fuel and carrier air that carries the solid fuel. The carrier air is primary air (primary combustion air). A first flame holding plate 77 that is continuous in a circumferential direction is located at a downstream end of the first nozzle 71. The first flame holding plate 77 increases in diameter toward the downstream end of the first nozzle 71 in a trumpet shape. A main fuel outlet 71a is defined by the first flame holding plate 77 at the downstream end of the first nozzle 71. A fuel-air mixture 51 containing the solid fuel and the carrier air is discharged from the main fuel outlet 71a.
A swirling adjustment plate 711 is located inside the downstream end of the first nozzle 71 and upstream of the first flame holding plate 77. A dispersion blade 713 is located inside the first nozzle 71 and upstream of the swirling adjustment plate 711.
A heavy oil burner 79 through which the burner axis 70 extends is inserted into a center axis portion of the first nozzle 71. A downstream end of the heavy oil burner 79 is located in the vicinity of the downstream end of the first nozzle 71. Therefore, a passage section of the downstream end of the first nozzle 71 has an annular shape about the burner axis 70.
The second nozzle 72 is located at an outer peripheral side of the first nozzle 71. A second passage 72f having an annular passage section is defined between the first nozzle 71 and the second nozzle 72. The second passage 72f is supplied with secondary air 52 (secondary combustion air) from a wind box. A secondary air outlet 72a that is a downstream end of the second passage 72f is located at an outer peripheral side of the main fuel outlet 71a and emits the secondary air 52 to an outer peripheral side of the flow of the fuel-air mixture 51 discharged from the main fuel outlet 71a.
The third nozzle 73 is located at an outer peripheral side of the second nozzle 72. A third passage 73f having an annular passage section is defined between the third nozzle 73 and the second nozzle 72. The third passage 73f is supplied with tertiary air 53 (tertiary combustion air) from a wind box. A tertiary air outlet 73a that is a downstream end of the third passage 73f is located at an outer peripheral side of the secondary air outlet 72a and emits the tertiary air 53 at an outer peripheral side of the secondary air 52 discharged from the secondary air outlet 72a.
A second flame holding plate 72b that increases in diameter toward the downstream side in a trumpet shape is located at a downstream end of the second nozzle 72. Moreover, an outer guide 73b that increases in diameter toward the downstream side in a trumpet shape is located at an opening edge of a downstream end of the third nozzle 73. The secondary air 52 discharged from the secondary air outlet 72a is guided by the first flame holding plate 77 and the second flame holding plate 72b so as to flow away from the fuel-air mixture 51 discharged from the first nozzle 71, i.e., flow outward. Moreover, the tertiary air 53 discharged from the third nozzle 73 is guided by the second flame holding plate 72b and the outer guide 73b so as to flow away from the secondary air 52 discharged from the second nozzle 72, i.e., flow outward.
First passages 91f in the auxiliary fuel injection nozzles 91 are supplied with gas fuel 90 from a gas fuel source. The gas fuel 90 is discharged from auxiliary fuel outlets 91a that are downstream ends of the auxiliary fuel injection nozzles 91. Moreover, the first passages 91f may be supplied with combustion air in addition to the gas fuel 90. In this case, a gas discharged from the auxiliary fuel outlets 91a may be switchable among the gas fuel 90, the combustion air, and a fuel-air mixture containing the gas fuel 90 and the combustion air.
The auxiliary fuel outlets 91a are located between the main fuel outlet 71a and the secondary air outlet 72a. The auxiliary fuel outlets 91a are lined up in the circumferential direction along an outer peripheral edge of the first flame holding plate 77 located at the downstream end of the first nozzle 71. It is desirable that the auxiliary fuel outlets 91a be lined up uniformly in the circumferential direction. In the example shown in
In the burner 5 configured as above, the fuel-air mixture 51 containing the solid fuel and the primary air which have been supplied to the first nozzle 71 is discharged as swirling flow from the main fuel outlet 71a by the actions of the dispersion blade 713 and the swirling adjustment plate 711. Moreover, at an outer peripheral side of the main fuel outlet 71a, the secondary air 52 is emitted from the secondary air outlet 72a, and the tertiary air 53 is emitted from the tertiary air outlet 73a. The secondary air 52 is emitted so as to spread outward in a radial direction about the burner axis 70 by the actions of the first flame holding plate 77 and the second flame holding plate 72b. Similarly, the tertiary air 53 is emitted so as to spread outward in the radial direction by the actions of the second flame holding plate 72b and the outer guide 73b.
A circulating vortex 55 is generated at a boundary between the flow of the fuel-air mixture 51 and the flow of the secondary air 52 by a pressure decrease. A high-temperature combustion gas stays in the circulating vortex 55. In the present embodiment, as shown in
The burner 5 is switchable among single-fuel combustion of the solid fuel, single-fuel combustion of the gas fuel, and multi-fuel combustion of the solid fuel and the gas fuel. At the time of the single-fuel combustion of the solid fuel, the combustion air is supplied to the first passages 91f, or the supply of the gas fuel to the first passages 91f is stopped. At the time of the single-fuel combustion of the gas fuel, the combustion air is supplied to the first nozzle 71, and the gas fuel is supplied to the first passages 91f. At the time of the multi-fuel combustion of the solid fuel and the gas fuel, the solid fuel and the combustion air are supplied to the first nozzle 71, and the gas fuel 90 is supplied to the first passages 91f. The burner 5 can switch the single-fuel combustion and the multi-fuel combustion without stopping the operation of the boiler 10.
The flow of the gas fuel 90 emitted from the auxiliary fuel outlets 91a joins outermost flow of the circulating vortex 55, i.e., the forward flow flowing toward the downstream side. Thus, the gas fuel 90 is taken in the circulating vortex 55 that is the origin of the ignition. As a result, the gas fuel 90 can be efficiently combusted.
As described above, the burner 5, 5A, or 5B according to the present disclosure includes:
Then, the auxiliary fuel injection nozzles 91 include: the auxiliary fuel outlets 91a lined up along the outer peripheral edge of the flame holding plate 77; or the auxiliary fuel outlets 91a located inside the outer peripheral edge of the flame holding plate 77 and outside the inner peripheral edge of the flame holding plate 77. The auxiliary fuel outlets 91a discharge the gas fuel 90 as the auxiliary fuel toward a boundary between the flow of the fuel-air mixture 51 discharged from the main fuel outlet 71a and the flow of the secondary air 52 discharged from the secondary air outlet 72a.
According to the burners 5, 5A, and 5B configured as above, the gas fuel 90 discharged from the auxiliary fuel outlets 91a flows toward the circulating vortex 55 generated at the boundary between the flow of the fuel-air mixture 51 and the flow of the secondary air 52. Thus, the gas fuel 90 is taken in the circulating vortex 55 that is the origin of the ignition, and therefore, the gas fuel 90 can be efficiently combusted. Moreover, the gas fuel 90 is dispersedly discharged from the auxiliary fuel outlets 91a. Therefore, as compared to a case where the number of auxiliary fuel outlets 91a is one, an injection flow velocity for supplying the same amount of gas fuel 90 can be made low. Thus, it is possible to prevent a case where the circulating vortex 55 is disturbed by the discharged gas fuel 90 and a case where the combustion reaction in the circulating vortex 55 is deteriorated by the temperature decrease of the circulating vortex 55. In order to make the injection flow velocity low, the number of auxiliary fuel outlets 91a may be at least two, but is desirably large.
In the burners 5, 5A, and 5B configured as above, the auxiliary fuel injection nozzles 91 may be joined to the outer surface of the first nozzle 71.
Thus, the auxiliary fuel injection nozzles 91 and the first nozzle 71 can be handled integrally. Moreover, since the auxiliary fuel injection nozzles 91 extend along the outer surface of the first nozzle 71, the auxiliary fuel injection nozzles 91 can be prevented from influencing the flow field of the secondary air 52 in the second passage 72f.
In the burners 5A and 5B configured as above, the downstream ends of the auxiliary fuel injection nozzles 91 may extend through the flame holding plate 77.
Therefore, the auxiliary fuel outlets 91a can be located inside the outer peripheral edge of the flame holding plate 77.
In the burner 5A configured as above, the flame holding plate 77 may include cutouts at an outer peripheral edge thereof, and the downstream ends of the auxiliary fuel injection nozzles 91 extend through the cutouts.
Thus, the auxiliary fuel outlets 91a can be located inside the outer peripheral edge of the flame holding plate 77. Moreover, the unevenness at the outer peripheral edge of the flame holding plate 77 can be reduced.
In the burners 5, 5A, and 5B configured as above, the auxiliary fuel outlets 91a may discharge the gas fuel 90 to the forward flow of the circulating vortex 55 generated at the boundary between the flow of the fuel-air mixture 51 and the flow of the secondary air 52, the forward flow flowing toward the downstream side.
When the gas fuel 90 is emitted so as to contact the reverse flow of the circulating vortex 55 which flows toward the upstream side, the circulating vortex 55 may be disturbed by the flow of the gas fuel 90. However, in the burners 5, 5A, and 5B according to the present disclosure, the gas fuel 90 is discharged to the forward flow of the circulating vortex 55, the forward flow flowing toward the downstream side. Therefore, the gas fuel 90 is taken in the circulating vortex 55 without disturbing the flow of the circulating vortex 55.
In the burner 5B configured as above, the circulating vortex 55 may include the outer circulating vortex 55a and the inner circulating vortex 55b located closer to the burner axis 70 than the outer circulating vortex 55a. The auxiliary fuel outlets 91a may include the inner auxiliary fuel outlet 91a and the outer auxiliary fuel outlet 91a which are at a substantially same rotational position about the burner axis 70. The inner auxiliary fuel outlet 91a may discharge the gas fuel 90 toward the forward flow of the inner circulating vortex 55b, the forward flow flowing toward the downstream side. The outer auxiliary fuel outlet 91a may discharge the gas fuel 90 toward the forward flow of the outer circulating vortex 55a, the forward flow flowing toward the downstream side.
Thus, even when the flow rate of the gas fuel 90 is increased, the gas fuel 90 discharged from the auxiliary fuel outlets 91a is dispersedly supplied to the outer circulating vortex 55a and the inner circulating vortex 55b. Therefore, the discharging flow velocity of the gas fuel 90 flowing toward the circulating vortex 55 can be suppressed. Then, it is possible to prevent a case where the circulating vortex 55 is disturbed by the discharged gas fuel 90 and a case where the combustion reaction in the circulating vortex 55 is deteriorated by the temperature decrease of the circulating vortex 55.
In the burners 5, 5A, and 5B, the gas fuel outlets 91a may be switchable so as to emit the combustion air instead of the gas fuel 90.
Each of the burners 5, 5A, and 5B configured as above is switchable between the combustion of only the main fuel and the combustion of the main fuel and the auxiliary fuel. In the above embodiment, the solid fuel is used as the main fuel. However, the main fuel may be gas fuel or liquid fuel. Moreover, the main fuel and the auxiliary fuel may be the same type of fuel. Or, in the burners 5, 5A, and 5B configured as above, the gas fuel 90 may be an ammonia gas.
Moreover, the combustion furnace 2 according to the present disclosure includes: the high-temperature reduction zone 21 which has a reduction atmosphere and at which at least one burner 5, 5A, or 5B is located; and the low-temperature oxidation zone 22 which has an oxidizing atmosphere and is lower in temperature than the high-temperature reduction zone 21 and into which the combustion gas generated in the high-temperature reduction zone 21 flows.
According to the combustion furnace 2 configured as above, the multi-fuel combustion of the solid fuel and the gas fuel containing a large amount of nitrogen is performed in the high-temperature reduction zone 21. Thus, in-furnace NOx removal of NOx generated from the solid fuel and the nitrogen contained in the gas fuel is performed, and therefore, the discharge of the NOx can be suppressed. Moreover, a water gas shift reaction in which water generated from the solid fuel and/or the hydrogen contained in the gas fuel is converted into an activated gas is caused. Thus, the combustion efficiency can be improved. Herein, when the gas fuel is the ammonia gas, a large amount of water which is subjected to the water gas shift reaction is generated. Therefore, the combustion efficiency can be further improved.
The foregoing discussion of the disclosure has been presented for purposes of illustration and description. The foregoing is not intended to limit the disclosure to the form or forms disclosed herein. In the foregoing Detailed Description for example, various features of the disclosure are grouped together in one embodiment for the purpose of streamlining the disclosure. The features of the disclosure may be combined in alternate embodiments, configurations, or aspects other than those discussed above.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2021-212245 | Dec 2021 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2022/048396 | 12/27/2022 | WO |
