Patent Application
20130133329
This application claims the benefit of Chinese Patent Application No. 201110380006.2 filed on Nov. 25, 2011 in the State Intellectual Property Office of China, the whole disclosure of which is incorporated herein by reference.
1. Field of Invention
The present invention relates to gas turbines and, in particular, to a fuel-air premixer for a combustor of a gas turbine which uniformly mixes fuel and air so as to reduce Nitrogen Oxide (NOx) formed by the combustion progress.
2. Description of the Related Art
The worldwide concerns of air pollution have led to stricter emission standards requiring significant reduction in gas turbine pollution emission. NOx, which is an inducement to atmospheric pollution, is generally formed in the high temperature regions of the gas turbine combustor by direct oxidation of atmospheric nitrogen with oxygen. Thus reducing the emission of NOx can be achieved by decreasing the temperature of the reaction zone. And one preferred method is to premix fuel and air into a lean mixture prior to combustion. The thermal mass of the excess air absorbs heat and decreases the temperature of the reaction products.
There are several problems associated with dry low emissions combustors operating with lean premixing of fuel and air. Specifically, there is a tendency for flammable mixture of fuel and air within the premixing section of the combustor to combust due to flashback, which occurs when flame propagates from the combustor reaction zone into the premixing section, or auto-ignition, which occurs when the dwell time and temperature of the fuel-air mixture in the premixing section are sufficient for combustion to be initiated without an igniter. The combustion in the premixing section results in degradating of emission performance, and overheating and damaging of the premixing section. Therefore, a problem to be solved is to prevent flashback and auto-ignition within the premixer.
In addition, the fuel and air must be uniformly mixed in the premixer and the reaction zone of the combustor so as to achieve a desired emission performance. In regions in the flow field in which the fuel concentration of the mixture is significantly greater than an average, the temperature of the reaction products in these regions will be higher than an average, and thus a large quantity of thermal NOx will be produced, which makes the combustor fail to meet NOx emission requirements. In regions in the flow field in which the fuel concentration of the mixture is significantly leaner than the average, quenching may occur and oxidizing progress of the hydrocarbons or carbon monoxide may be terminated before reaching equilibrium levels, this can result in failure to meet carbon monoxide (CO) or unburned hydrocarbon (UHC) emission requirements. Thus, another problem to be solved is to mix the fuel and the air with significant uniform concentration distribution in the premixer to meet the emission performance requirements.
Still further, in order to meet emission performance requirements imposed upon the gas turbine in many applications, it is necessary to reduce the fuel concentration of the mixture to a level that is close to the lean flammability limit for most fuels. This results in a reduction in flame propagation speed as well as emissions. As a consequence, lean premixing combustors tend to be less stable than the conventional diffusion flame combustors, and often result in high level combustion driven dynamic pressure activities which often lead to hardware damage, flashback or blowoff. Thus, yet another problem to be solved is to control the combustion driven dynamic pressure activity to an acceptable low level.
Lean, premixing fuel injectors for emission abatement are commonly used in heavy duty industrial gas turbines. A representative example of such a device is described in U.S. Pat. No. 5,259,184. Such devices have achieved great progress in the gas turbine exhaust emission abatement by reducing the NOx emissions by an order of magnitude or more relative to the diffusion flame burners without using diluent injection. The advantages in emission performance, however, have been obtained at the expense of incurring several problems. In particular, flash back and flame holding within the premixer result in degradation of emission performance and hardware damage due to overheating. In addition, the high level combustion driven dynamic pressure activity results in the problems such as flashback, blowoff, and the reduction in the useful life of the combustor hardware.
An example of a method for reducing the combustion driven dynamic pressure activity in lean premixed dry low emissions combustors can be found in U.S. Pat. No. 6,438,961, which proposed an inlet flow conditioner upstream of the premixer inlet to improve the air flow velocity distribution through the premixer and the uniformity of the fuel-air mixture in the premixer, which successfully reduces the premixing flow sensitivity to the air flow mal-distribution in the flow field approaching the premixer.
Though those conventional premixers have achieved progress in premixing fuel and air without introducing some associated problems in premix combustion, much improvement is still needed. The first is to reduce the fuel-air mixing non-uniformity in the premixer which limits the combustors to achieve maximum emission reduction. The second is to resist or prevent the flashback and auto-ignition in the case of various operation conditions and different fuels. The third is to reduce the level of combustion driven dynamic pressure activity so as to obtain high combustion performance in the combustors.
In accordance with one aspect of the present invention, a fuel-air premixer for use in a combustor of a gas turbine includes an air inlet, a fuel inlet, a shroud, a central body and a cascade of vanes. The premixer mixes fuel and air in the annular mixing passage into a uniform mixture for injecting into a combustor reaction zone. The air from a compressor is injected into the mixer through an air inlet. The fuel is introduced into an air stream via fuel injection holes that pass through the walls of the vanes which contain internal fuel flow passages. The flow field inside the premixer is broken up by the arrayed vanes into a series of small regions each contains a small size mixing eddy which is steadily attached to the surface of the vanes. By premixing fuel and air in this manner, the concentration distribution of the mixture flow out of the premixer is perfectly uniform, the large scale turbulent of the air flow is absorbed and the problems of flashback and auto-ignition for the premixer are eliminated.
These and other aspects and advantages of the invention will become apparent from the following detailed description of the invention, with reference to the accompanying drawings, in which:
Preferred embodiments of the present invention will be described hereinafter in detail with reference to the attached drawings, wherein the like reference numerals refer to the like elements throughout the specification. These embodiments should not be construed as being limited to the embodiment set forth herein, rather for illustrative purpose.
The fuel-air premixer of the present invention for use in a combustor of a gas turbine includes an air inlet, a fuel inlet 11, a shroud 14, a central body 12 and a cascade of vanes 25,24,23. The premixer mixes fuel and air in an annular mixing passage 13 into a uniform mixture for injecting into a combustor reaction zone through the exhaust 22.
High pressure air discharged from a compressor enters the premixer through the air inlet, which is located at an upstream end of the annular mixing passage 13 confined by a solid cylindrical inner wall of the shroud 14 and a cylindrical outer wall of the central body 12. The fuel is introduced from the fuel inlet 11 into a fuel flow passage inside the central body 12, which is communicated with the internal fuel flow passages 21 inside the fuel nozzle vanes 25, and the fuel is then injected into an air stream via fuel injection holes 15 that pass through the walls of the fuel nozzle vanes 25.
In the present invention, the fuel and air mixture flows downstream inside the annular mixing passage 13 and the flow field is broken up by the arrayed vanes into a series of small regions to create a highly confined mixing flow which can successfully inhibit the generation of large scale turbulence in the mixing process. By using the mixing vane described above, each small flow region comprises a well designed mixing eddy which greatly enhances the mixing intensity of the flow field and effectively absorbs the turbulence in the air steam.
Adjusting the size and arrangement of the vanes can change the size and the spin velocity of the eddies, therefore the characteristics of the mixing and the turbulence absorbability will be effectively adjusted to adapt to a very wide range of operation conditions while keeping high premixing performance. The small size and high spin velocity of the eddies can achieve high intensity of heat and mass transfer rate through eddies' boundary with the main stream and eliminate the possibility of incurring auto-ignition and flashback because of lacking the flame holding mechanism.
Before reaching the exhaust of the premixer, swirl is imparted to the mixture of the fuel and air by airfoil shaped turning vanes 23, which are designed to minimize the disturbance to the flow field in this progress. Downstream the turning vanes, the fuel-air mixture flows into the reaction zone of the combustor, where the swirl causes a central vortex to form a flow recirculation stabilizing the flame front.
The present invention relates to a gas turbine combustor having a reaction zone in which a mixture of air and fuel is combusted, wherein the combustor comprises the above premixer, and the mixture is injected from the premixer into the reaction zone.
Although several exemplary embodiments have been shown and described, it would be appreciated by those skilled in the art that various changes or modifications may be made in these embodiments without departing from the principles and spirit of the disclosure, the scope of which is defined in the appended claims and their equivalents.
| Number | Date | Country | Kind |
|---|---|---|---|
| 201110380006.2 | Nov 2011 | CN | national |
