Patent Application
20100281872
The embodiments described herein relate generally to integrated gasification combined-cycle (IGCC) power generation systems and, more particularly, to fuel nozzles for use with an IGCC power generation system.
At least some known gasifiers convert a mixture of fluids, including air and/or oxygen, liquid water and/or steam, fuel, and/or a slag additive, into a partially oxidized gas that is often referred to as “syngas.” Controlling the mixing of fluids delivered to a gas turbine engine may be critical to the engine's performance and/or emissions.
For example, improper and/or inadequate mixing may cause a flame to attach proximate to a fuel nozzle tip and/or within the nozzle, thereby increasing a temperature of the fuel nozzle tip and/or the nozzle. Moreover, improper and/or inadequate mixing may or may not create a separation zone in a center of a flow, thereby increasing or decreasing a probability of a vortex breakdown. Further, improper and/or inadequate mixing may cause the recirculation stability zone defined within the combustor to shift downstream, thereby detaching the flame and increasing the generation of carbon monoxide emissions.
In one embodiment, a method of assembling a fuel nozzle tip for use with a combustor is provided. The method includes providing a fuel tube and coupling an air collar to the fuel tube. The fuel tube is formed with a first plurality of circumferentially-spaced fuel openings and a second plurality of circumferentially-spaced fuel openings. The fuel tube is oriented such that fuel may be discharged into a mixing zone through the first and second pluralities of fuel openings. The air collar is formed with a plurality of circumferentially-spaced air openings. At least one of the plurality of air openings is oriented to facilitate generating a swirl number of greater than 0.6 within the mixing zone. The air collar is oriented such that air may be discharged into the mixing zone through the plurality of air openings.
In another embodiment, a fuel nozzle tip for use with a combustor is provided. The fuel nozzle tip includes a fuel tube and an air collar coupled to the fuel tube. The fuel tube includes a first plurality of circumferentially-spaced fuel openings and a second plurality of circumferentially-spaced fuel openings. The fuel tube is configured to channel fuel into a mixing zone defined within the combustor. The air collar includes a plurality of circumferentially-spaced air openings configured to discharge air into the mixing zone. At least one of the plurality of air openings is oriented to facilitate generating a swirl number of greater than 0.6 within the mixing zone.
In yet another embodiment, a gas turbine engine for use in an integrated gasification combined-cycle (IGCC) power generation system is provided. The gas turbine engine includes a combustor and a fuel nozzle tip that includes a fuel tube and an air collar coupled to the fuel tube. The fuel tube includes a first plurality of circumferentially-spaced fuel openings and a second plurality of circumferentially-spaced fuel openings. The fuel tube is configured to channel fuel into a mixing zone defined within the combustor. The air collar includes a plurality of circumferentially-spaced air openings configured to discharge air into the mixing zone. At least one of the plurality of air openings is oriented to facilitate generating a swirl number of greater than 0.6 within the mixing zone.
The systems and methods described herein facilitate discharging a fuel-air mixture from a fuel nozzle that enables a first swirl number for the fuel and a second swirl number for the air. The swirl number, as used in the present application, is defined as an axial flux of angular momentum relative to axial thrust.
During operation, air flows through main air compressor 52, which discharges compressed air to air separation unit 53. In the exemplary embodiment, additional compressed air is supplied to air separation unit 53 from gas turbine engine compressor 12.
Air separation unit 53 separates the compressed air into an oxygen flow O2 and a gas by-product flow NPG, also referred to as a process gas flow. In the exemplary embodiment, air separation unit 53 channels oxygen flow O2 to gasifier 56, at least some of process gas flow NPG to gas turbine engine combustor 16 via a compressor 60, and at least some of process gas flow NPG to the atmosphere. In the exemplary embodiment, process gas flow NPG includes nitrogen. For example, in one embodiment, process gas flow NPG includes between about 95% and 100% nitrogen. Process gas flow NPG may also include other gases such as, but not limited to, oxygen and/or argon. Alternatively, the process gas flow includes (H2O) steam in lieu of nitrogen, wherein the process gas flow includes between about 90% and 100% (H2O) steam.
Gasifier 56 converts oxygen flow O2 supplied by air separation unit 53, liquid water and/or steam, a mixture of fuel, a carbonaceous substance, and/or a slag additive into a partially oxidized gas that is often referred to as “syngas.” Although gasifier 56 may use any fuel, in some embodiments, gasifier 56 uses coal, petroleum coke, residual oil, oil emulsions, tar sands, and/or other similar fuels. In the exemplary embodiment, gasifier 56 channels the syngas to gas turbine engine combustor 16 via a clean-up device 62. More specifically, in the exemplary embodiment, gasifier 56 generates a syngas that includes carbon dioxide CO2, and clean-up device 62 separates carbon dioxide CO2 from the syngas. Carbon dioxide CO2 separated from the syngas by clean-up device 62 may be vented to the atmosphere, recycled to an injection nozzle 70 for use by gasifier 56, compressed and sequestered for geological storage (not shown), and/or processed for industrial use gases (not shown).
During operation, compressor 12 compresses air, and the compressed air is channeled to combustor 16. Combustor 16 mixes the compressed air from compressor 12, compressed process gas from air separation unit 53 (shown in
More specifically, in the exemplary embodiment, engine 10 also includes at least one fuel nozzle (not shown in
In the exemplary embodiment, fuel nozzle tip 30 is positioned at a downstream end 44 of an associated fuel nozzle (not shown). Moreover, in the exemplary embodiment, fuel nozzle tip 30 includes an air collar 34, a pilot fuel tube 36, and a primary fuel tube 40. More specifically, in the exemplary embodiment, primary fuel tube 40 is radially outward from, and extends circumferentially about, pilot fuel tube 36. In the exemplary embodiment, air collar 34 is coupled to a fuel tube face 42 at downstream end 44.
Air collar 34 is formed with a first outer diameter 112 adjacent to fuel tube face 42. In the exemplary embodiment, first outer diameter 112 is approximately the same size as an outer diameter 200 of primary fuel tube 40. In the exemplary embodiment, air collar 34 is also formed with, downstream from first outer diameter 112, a second outer diameter 122 that is smaller than first outer diameter 112. As such, second outer diameter 122 enables air collar 34 to slide axially proximate to combustor mixing zone 32.
Fuel tube face 42 of primary fuel tube 40 includes at least a first plurality of circumferentially-spaced primary fuel openings 52. In the exemplary embodiment, fuel tube face 42 also includes a second plurality of circumferentially-spaced primary fuel openings 54 to enable primary fuel tube 40 to discharge a larger volume of fluid into combustor mixing zone 32. In the exemplary embodiment, primary fuel openings 52 and 54 are substantially circular. Alternatively, openings 52 and/or 54 may be formed with any cross-sectional shape that enables primary fuel tube 40 to function as described herein. In the exemplary embodiment, primary fuel openings 52 and 54 are spaced substantially concentrically and circumferentially about a centerline 210 of fuel nozzle tip 30. More specifically, in the exemplary embodiment, primary fuel openings 52 are spaced at a first radial distance 252 outward from centerline 210, and primary fuel openings 54 are spaced at a second radial distance 254 outward from centerline 210. In the exemplary embodiment, first radial distance 252 is shorter than second radial distance 254.
In the exemplary embodiment, primary fuel openings 52 and 54 discharge a fluid (not shown) into combustor mixing zone 32. More specifically, in the exemplary embodiment, primary fuel openings 52 and 54 discharge a primary fuel (not shown), such as an air blown gasifier syngas, into combustor mixing zone 32. More specifically, primary fuel openings 52 and 54 discharge primary fuel at a predefined discharge angle θ1 that is obliquely oriented with respect to centerline 210. In the exemplary embodiment, discharge angle θ1 is between about 10° to about 30°. In one embodiment, discharge angle θ1 of at least one fuel opening 54 is different from discharge angle θ1 of at least one fuel opening 52.
A pilot fuel tube face 46 includes a plurality of pilot fuel openings 48. In the exemplary embodiment, pilot fuel openings 48 are substantially circular. Alternatively, pilot fuel openings 48 may be formed with any cross-sectional shape that enables pilot fuel tube 36 to function as described herein. In the exemplary embodiment, pilot fuel openings 48 discharge a fluid into combustor mixing zone 32. More specifically, in the exemplary embodiment, pilot fuel openings 48 discharge a pilot fuel (not shown) or a startup fuel into combustor mixing zone 32. More specifically, pilot fuel openings 48 discharge pilot fuel at a predefined discharge angle (not shown) that is obliquely oriented with respect to centerline 210.
Air collar 34 includes a plurality of circumferentially-spaced air openings 58. In the exemplary embodiment, discharging air through openings in air collar 34, rather than openings in fuel tube face 42, enables discharging a larger volume of primary fuel through primary fuel openings 52 and/or 54. In the exemplary embodiment, air openings 58 are substantially circular. Alternatively, air openings 58 may be formed with any cross-sectional shape that enables air openings 58 to function as described herein. In the exemplary embodiment, air openings 58 are spaced substantially circumferentially about centerline 210. More specifically, in the exemplary embodiment, air openings 58 are spaced at a radial distance 258 outward from centerline 210. In the exemplary embodiment, radial distance 258 is greater than radial distances 252 and 254.
In the exemplary embodiment, air openings 58 discharge fluid into combustor mixing zone 32. More specifically, in the exemplary embodiment, air openings 58 discharge air into combustor mixing zone 32. More specifically, air openings 58 discharge air at a predefined discharge angle θ2 that is obliquely oriented with respect to centerline 210. In the exemplary embodiment, discharge angle θ2 is between about 40° to about 50°. A thickness 158 of air collar 34 enables air to be discharged at discharge angle θ2 while defining a separation 68 circumferentially adjacent between air openings 58. In the exemplary embodiment, discharge angle θ1 and discharge angle θ2 are approximately equal. Alternatively, discharge angles θ1 and θ2 may be at any angle that enables a fuel-air mixture as described herein.
During operation, pilot fuel tube 36 discharges pilot fuel or startup fuel to combustor mixing zone 32 during start-up and idle operations of engine 10. In the exemplary embodiment, the startup fuel is natural gas. When additional power is demanded, pilot fuel tube 36 discontinues discharging pilot fuel to combustor mixing zone 32, and primary fuel tube 40 and air collar 34 discharge primary fuel and air, respectively, to combustor mixing zone 32. Primary fuel openings 52 and 54 discharge fuel at discharge angle θ1, and air openings 58 discharge air at discharge angle θ2. More specifically, the swirling and mixing of primary fuel and air discharged from primary fuel openings 52 and 54 and air openings 58 facilitate the generation of a swirl number below a tipping point within combustor mixing zone 32. In the exemplary embodiment, the swirl number of the discharged fuel is less than about 0.4, and the swirl number of the discharged air is greater than about 0.6. The relatively high swirl of the discharged air facilitates creating a vortex breakdown downstream. Moreover, the relatively high swirl of the discharged air also enhances a fuel flexibility of the fuel nozzle. Moreover, the circular shape of each air opening 58 enables a rich flame to be created such that a probability of flame-holding is reduced.
The methods and systems described herein facilitate discharging a fuel-air mixture with a first swirl number for the discharged fuel and a second swirl number for the discharged air. In the exemplary embodiment, the airblown syngas fuel nozzles are used in a refinery or a coal gasification plant. The methods and systems described herein illustrate the disclosure by way of example and not by way of limitation. The description clearly enables one skilled in the art to make and use the disclosure, describes several embodiments, adaptations, variations, alternatives, and uses of the disclosure, including what is presently believed to be the best mode of carrying out the disclosure.
Exemplary embodiments of the airblown syngas fuel nozzle with circular diluent air openings and a method of assembling the same are described above in detail. The methods and systems are not limited to the specific embodiments described herein, but rather, components of the methods and systems may be utilized independently and separately from other components described herein. For example, the methods and systems described herein may have other industrial and/or consumer applications and are not limited to practice with refineries or coal gasification plants as described herein. Rather, the present invention can be implemented and utilized in connection with many other industries.
While the invention has been described in terms of various specific embodiments, those skilled in the art will recognize that the invention can be practiced with modification within the spirit and scope of the claims.
