# Patent

## Title
System and method for operating a gas turbine

## Abstract

A system and method for operating a gas turbine include a controller that determines, for at least one combustion instability, a frequency; a quantification of the frequency or a quantification of the frequency through time; and, optionally, a phase and/or an amplitude. The logic also causes the controller to compare the frequency, the quantification of the frequency or the quantification of the frequency through time, the phase, and/or the amplitude of the at least one combustion instability to an associated predetermined limit. When the frequency is actionable relative to its predetermined limit and one of the quantification of the frequency or the quantification of the frequency through time is actionable relative to its respective predetermined limit, at least one parameter of the gas turbine is adjusted. The quantification of the frequency is one of the standard deviation, the coefficient of variation, the index of dispersion, and the variance.

## Background
TECHNICAL FIELD
The present invention generally involves a system and method for operating a gas turbine. In particular embodiments, the system and method may be incorporated into the gas turbine or other turbomachine to detect and/or reduce unwanted vibrations in hot gas path components downstream from a combustion system, which may result from in-phase, coherent combustion tones.
BACKGROUND
Combustors are commonly used in industrial and commercial operations to ignite fuel to produce combustion gases having a high temperature and pressure. For example, gas turbines and other turbomachines typically include one or more combustors to generate power or thrust. A typical gas turbine used to generate electrical power includes an axial compressor at the front, multiple combustors around the middle, and a turbine at the rear. Ambient air enters the compressor as a working fluid, and the compressor progressively imparts kinetic energy to the working fluid to produce a compressed working fluid at a highly energized state. The compressed working fluid exits the compressor and flows through one or more fuel injectors in the combustors where the compressed working fluid mixes with fuel before igniting to generate combustion gases having a high temperature and pressure. The combustion gases flow to the turbine where they expand to produce work. For example, expansion of the combustion gases in the turbine may rotate a shaft connected to a generator to produce electricity.
At particular operating conditions, combustion dynamics at specific frequencies and with sufficient amplitudes, which are in phase and coherent, may produce undesirable sympathetic vibrations in the turbine and/or other downstream components. In the context of this invention, coherence refers to the strength of the linear relationship between two (or more) dynamic signals, which is strongly influenced by the degree of frequency overlap between them. Coherence provides a measure of the degree of modal coupling of the combustion dynamics.
An alternate quantification for modal coupling is the standard deviation of the combustion dynamics frequency, either from combustor to combustor or through time. The standard deviation of the combustion dynamics frequency from combustor to combustor, herein referred to as the “standard deviation of the frequency” provides a measure of the variation in combustion dynamics frequency from combustor to combustor, which correlates with the coherence of the combustion instability. The standard deviation of the combustion dynamics frequency through time, herein referred to as the “standard deviation of the frequency through time” provides a measure of the variation of the combustion dynamics frequency through time, which also correlates with the coherence of the combustion instability. As the variation in frequency, either from combustor to combustor or through time, increases, the coherence decreases. Therefore, standard deviation of the frequency of the combustion dynamics, either from combustor to combustor or through time, can be used in the place of coherence to detect modal coupling of the combustion dynamics. Although not as robust, the standard deviation of amplitude, either from combustor to combustor or through time, herein referred to as “standard deviation of amplitude” and “standard deviation of amplitude through time,” respectively, can also be used in place of coherence to detect modal coupling of the combustion dynamics.
Alternative quantities, which are variations of standard deviation, can also be used in place of coherence to detect modal coupling. These include the variance (the square of the standard deviation of the frequency), the variance through time (the square of the standard deviation of the frequency through time), the coefficient of variation of frequency (the standard deviation of the frequency normalized by the mean of the frequency), the coefficient of variation of frequency through time (the standard deviation of the frequency through time normalized by the mean of the frequency through time), the index of dispersion of the frequency (the variance of the frequency normalized by the mean of the frequency) and the index of dispersion of the frequency through time (the variance of the frequency through time normalized by the mean of the frequency through time).
Typically, the problem of combustion-driven responses of downstream components is managed by combustor tuning which limits the amplitude of the combustion dynamics in a particular frequency band. However, combustor tuning may unnecessarily limit the operating range of the combustor. An alternative approach to reducing unwanted combustion-driven responses of downstream components is to alter the frequency, phase, amplitude, standard deviation of frequency, standard deviation of frequency through time, coefficient of variation of frequency, coefficient of variation of frequency through time, index of dispersion of frequency, index of dispersion of frequency through time, variance of frequency, and/or variance of frequency through time of the combustion dynamics.
For instance, as the combustion instability frequency in one or more, but not all, combustors is driven away from that of the other combustors, coherence and, therefore, modal coupling of combustion dynamics is reduced, which thereby reduces the ability of the combustor tone to cause a vibratory response in downstream components. Alternatively, shifting the combustion dynamics frequency of each of the combustors away from the natural frequency of the downstream components may also reduce unwanted vibrations of downstream components.
Therefore, a system and method for operating a gas turbine that detects and/or reduces the unwanted vibrations in downstream components by altering the frequency, phase, amplitude, standard deviation of the frequency, standard deviation of the frequency through time, coefficient of variation of the frequency, coefficient of variation of the frequency through time, index of dispersion of the frequency, index of dispersion of the frequency through time, variance of the frequency, and/or variance of the frequency through time of the combustors would be useful for enhancing the thermodynamic efficiency of the combustors, protecting against accelerated wear, promoting flame stability, and/or reducing undesirable emissions over a wide range of operating levels, without detrimentally impacting the life of the downstream hot gas path components.
SUMMARY
Aspects and advantages of the invention are set forth below in the following description, or may be obvious from the description, or may be learned through practice of the invention.
One embodiment of the present invention is a system for operating a gas turbine, which includes: a compressor section configured to receiving a working fluid and to produce a compressed working fluid; and a plurality of combustors downstream from the compressor section, wherein each combustor includes a fuel injector that receives fuel at a fuel temperature and a fuel flow rate. A controller is configured to execute logic stored in a memory that causes the controller: to determine a frequency of a combustion instability and at least quantification of the frequency of a combustion instability; to compare the frequency of the combustion instability to a predetermined frequency limit and the at least one quantification of the frequency of the combustion instability to a respective predetermined quantification limit; and to adjust at least one parameter of the gas turbine if the frequency of the combustion instability is actionable relative to the predetermined frequency limit and the at least one quantification of the frequency of the combustion instability is actionable relative to its respective predetermined quantification limit.
A method for operating a gas turbine includes: determining a frequency of a combustion instability, and comparing the frequency of the combustion instability to a predetermined frequency limit. The method further includes: determining at least one quantification of the frequency of a combustion instability, and comparing the at least one quantification of the frequency of the combustion instability to a respective predetermined quantification limit. If the frequency of the combustion instability is actionable relative to the predetermined frequency limit, and the at least one quantification of the frequency of the combustion instability is actionable relative to its respective predetermined quantification limit, the method adjusts at least one parameter of the gas turbine.
Quantifications of frequency may include: a standard deviation of frequency, a coefficient of variation of frequency, an index of dispersion of frequency, a variance of frequency, a standard deviation of frequency through time, a coefficient of variation of frequency through time, an index of dispersion of frequency through time, and a variance of frequency through time.
According to other embodiments, the system or method may further include comparing at least one of the frequency and the quantification of the frequency of the combustion instability to a predetermined time limit. In this or other embodiments, the system or method may further be employed to determine the amplitude and/or the phase of the combustion instability; to compare the amplitude to a predetermined amplitude limit and/or to compare the phase to a predetermined phase limit, and to adjust at least one parameter of the gas turbine is at least one of the amplitude and the phase of the combustion instability is actionable relative to a predetermined limit.
The parameters being adjusted by the system or through the practice of the method may include one or more of: a temperature of the compressed working fluid; a flow rate of the working fluid; a flow rate of the compressed working fluid recirculated through the compressor section; the fuel flow rate of the fuel to at least one injector; and the fuel temperature of the fuel to at least one injector.
Those of ordinary skill in the art will better appreciate the features and aspects of such embodiments, and others, upon review of the specification.



BRIEF DESCRIPTION OF THE DRAWINGS
A full and enabling disclosure of the present invention, including the best mode thereof, is set forth more particularly in the remainder of the specification, including reference to the accompanying figures, in which:
FIG. 1 is a simplified side cross-sectional view of an exemplary gas turbine, according to various embodiments of the present disclosure;
FIG. 2 is a simplified side cross-sectional view of an exemplary combustor, according to various embodiments of the present disclosure;
FIG. 3 is an upstream plan view of the cap assembly shown in FIG. 2, according to an embodiment of the present disclosure;
FIG. 4 is an upstream plan view of the cap assembly shown in FIG. 2, according to an alternate embodiment of the present disclosure;
FIG. 5A is an exemplary graph of the standard deviation of a selected frequency over time versus coherence, according to an alternate embodiment of the present disclosure;
FIG. 5B is an exemplary graph of the coefficient of variation of a selected frequency over time versus coherence, according to an alternate embodiment of the present disclosure;
FIG. 5C is an exemplary graph of the index of dispersion of a selected frequency over time versus coherence, according to an alternate embodiment of the present disclosure;
FIG. 5D is an exemplary graph of the variance of a selected frequency over time versus coherence, according to an alternate embodiment of the present disclosure;
FIG. 6 is a simplified side cross-sectional view of a system, according to various embodiments of the present disclosure;
FIG. 7 is a diagram of a system, according to alternate embodiments of the present disclosure; and
FIG. 8 is an exemplary flow diagram of a method for operating a gas turbine, according to various embodiments of the present disclosure.



DETAILED DESCRIPTION
Reference will now be made in detail to present embodiments of the invention, one or more examples of which are illustrated in the accompanying drawings. The detailed description uses numerical and letter designations to refer to features in the drawings. Like or similar designations in the drawings and description have been used to refer to like or similar parts of the invention.
As used herein, the terms “first,” “second,” and “third” may be used interchangeably to distinguish one component from another and are not intended to signify location or importance of the individual components. The terms “upstream,” “downstream,” “radially,” and “axially” refer to the relative direction with respect to fluid flow in a fluid pathway. For example, “upstream” refers to the direction from which the fluid flows, and “downstream” refers to the direction to which the fluid flows. Similarly, “radially” refers to the relative direction substantially perpendicular to the fluid flow, and “axially” refers to the relative direction substantially parallel to the fluid flow.
Each example is provided by way of explanation of the invention, not limitation of the invention. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in the present invention without departing from the scope or spirit thereof. For instance, features illustrated or described as part of one embodiment may be used on another embodiment to yield a still further embodiment. Thus, it is intended that the present invention covers such modifications and variations as come within the scope of the appended claims and their equivalents.
Various embodiments of the present invention include a system and method for operating a gas turbine to detect and/or reduce unwanted vibrations in hot gas path components downstream from the combustion system, which may result from in-phase, coherent combustion tones. The system and method may be implemented in a gas turbine having multiple combustors, and each combustor may include one or more fuel injectors for mixing fuel with a compressed working fluid prior to combustion. The system and method may further include a controller configured to execute logic stored in a memory that causes the controller to determine, for one or more combustion instabilities, a frequency and one or more quantifications of modal coupling, including: a standard deviation of the frequency, a standard deviation of the frequency over time, a coefficient of variation of the frequency, a coefficient of variation of the frequency over time, an index of dispersion of the frequency, an index of dispersion of the frequency over time, a variance of the frequency, and/or a variance of the frequency through time, and, optionally, a phase and/or an amplitude of the one or more combustion instabilities.
The logic causes the controller to compare one or more of the frequency, the standard deviation of the frequency, the standard deviation of the frequency over time, the coefficient of variation of the frequency, the coefficient of variation of the frequency over time, the index of dispersion of the frequency, the index of dispersion of the frequency over time, the a variance of the frequency, and/or the variance of the frequency through time, and, optionally, the phase and/or the amplitude of the one or more combustion instabilities, to a predetermined limit for each quantification of the modal coupling.
The logic may further cause the controller to adjust at least one parameter of the gas turbine if the frequency and one or more quantifications of the modal coupling is actionable relative to a predetermined limit, the quantification of the modal coupling being one or more of the standard deviation of the frequency over time, the coefficient of variation of the frequency, the coefficient of variation of the frequency over time, the index of dispersion of the frequency, the index of dispersion of the frequency over time, the a variance of the frequency, and/or the variance of the frequency through time, and, optionally, the phase and/or the amplitude of the one or more combustion instabilities.
As used herein, the phrase “actionable relative to a predetermined limit” depends on the particular parameter being compared and means that the parameter is either within a designated range (e.g., for frequency), less than a lower predetermined limit (e.g., for phase, standard deviation of frequency, standard deviation of frequency through time, coefficient of variation of frequency, coefficient of variation of frequency through time, index of dispersion of frequency, index of dispersion of frequency through time, variance of frequency, or variance of frequency through time), or greater than an upper predetermined limit (e.g., for amplitude).
For example, the system and method may adjust a temperature, pressure, and/or flow rate of a compressed working fluid produced by a compressor section of the gas turbine. Alternately, or in addition, the system and method may adjust a fuel flow and/or fuel temperature to one or more fuel circuits in one or more of the combustors. As a result, various embodiments of the present disclosure may reduce the ability of the combustor tone to cause a vibratory response in downstream components. Although exemplary embodiments of the present invention will be described generally in the context of the combustion dynamics in a gas turbine for purposes of illustration, one of ordinary skill in the art will readily appreciate that embodiments of the present invention may be applied to any combustion dynamics and are not limited to a gas turbine unless specifically recited in the claims.
Referring now to the drawings, FIG. 1 provides a simplified side cross-sectional view of an exemplary gas turbine 10 that may incorporate various embodiments of the present disclosure. As shown, the gas turbine 10 may generally include an inlet section 12, a compressor section 14, a combustion section 16, a turbine section 18, and an exhaust section 20. The inlet section 12 may include a series of filters 22 and one or more fluid conditioning devices 24 to clean, heat, cool, moisturize, demoisturize, and/or otherwise condition a working fluid 28 (e.g., air) entering the gas turbine 10. The cleaned and conditioned working fluid 28 flows to a compressor 30 in the compressor section 14. A compressor casing 32 contains the working fluid 28, as alternating stages of rotating blades 34 and stationary vanes 36 progressively accelerate and redirect the working fluid 28 to produce a continuous flow of compressed working fluid 38 at a higher temperature and pressure.
The majority of the compressed working fluid 38 flows through a compressor discharge plenum 40 to one or more combustors 42 in the combustion section 16. A fuel supply 44 in fluid communication with each combustor 42 supplies a fuel to each combustor 42. Possible fuels may include, for example, blast furnace gas, coke oven gas, natural gas, methane, vaporized liquefied natural gas (LNG), hydrogen, syngas, butane, propane, olefins, diesel, petroleum distillates, and combinations thereof. The compressed working fluid 38 mixes with the fuel and ignites to generate combustion gases 46 having a high temperature and pressure.
The combustion gases 46 flow along a hot gas path through a turbine 48 in the turbine section 18 where they expand to produce work. Specifically, the combustion gases 46 may flow across alternating stages of stationary nozzles 50 and rotating buckets 52 in the turbine 48. The stationary nozzles 50 redirect the combustion gases 46 onto the next stage of rotating buckets 52, and the combustion gases 46 expand as they pass over the rotating buckets 52, causing the rotating buckets 52 to rotate. The rotating buckets 52 may connect to a shaft 54 that is coupled to the compressor 30 so that rotation of the shaft 54 drives the compressor 30 to produce the compressed working fluid 38. Alternately, or in addition, the shaft 54 may connect to a generator 56 for producing electricity. Exhaust gases 58 from the turbine section 18 flow through the exhaust section 20 prior to release to the environment.
FIG. 2 provides a simplified side cross-section view of an exemplary combustor 42 according to various embodiments of the present invention. The combustors 42 may be any type of combustor known in the art, and the present invention is not limited to any particular combustor design unless specifically recited in the claims.
As shown in FIG. 2, a combustor casing 60 and an end cover 62 may combine to contain the compressed working fluid 38 flowing to the combustor 42. A cap assembly 64 may extend radially across at least a portion of the combustor 42, and one or more fuel injectors 66, 68 may be radially arranged across the cap assembly 64 to supply fuel to a combustion chamber 70 downstream from the cap assembly 64. The fuel being directed to the fuel injectors 66, 68 is supplied at a fuel flow rate and a fuel temperature.
A liner 72 may circumferentially surround at least a portion of the combustion chamber 70, and a transition duct 74 downstream from the liner 72 may connect the combustion chamber 70 to the inlet of the turbine 48. An impingement sleeve 76 with flow holes 78 may circumferentially surround the transition duct 74, and a flow sleeve 88 may circumferentially surround the liner 72. In this manner, the compressed working fluid 38 may pass through the flow holes 78 in the impingement sleeve 76 to flow through an annular passage 80 outside of the transition duct 74 and liner 72. When the compressed working fluid 38 reaches the end cover 62, the compressed working fluid 38 reverses direction to flow through the fuel injectors 66, 68 and into the combustion chamber 70.
Although generally shown as cylindrical, the radial cross-section of the fuel injectors 66, 68 may be any geometric shape, and the present disclosure is not limited to any particular radial cross-section unless specifically recited in the claims. In addition, various embodiments of the combustor 42 may include different numbers and arrangements of fuel injectors 66, 68 in the cap assembly 64.
FIGS. 3 and 4 provide upstream plan views of exemplary arrangements of the fuel injectors 66, 68 in the cap assembly 64 within the scope of the present disclosure. As shown in FIG. 3, for example, multiple fuel injectors 66, 68 may be radially arranged around a single fuel injector 66. Alternatively, a plurality of non-circular truncated pie-shaped fuel injectors 68 may circumferentially surround a single circular fuel injector 66, as shown in FIG. 4. One of ordinary skill in the art will readily appreciate multiple other shapes and arrangements for the fuel injectors 66, 68 from the teachings herein, and the particular shape and arrangement of the fuel injectors 66, 68 are not limitations of the present disclosure, unless specifically recited in the claims.
The fuel injectors 66, 68 may be divided into various groups or circuits to facilitate multiple fueling regimes over the range of operations. For example, as shown in FIGS. 3 and 4, the center fuel injector 66 and/or one of the outer fuel injectors 66, 68 may receive fuel from a first fuel circuit 82, while one or more of the surrounding fuel injectors 66, 68 may be grouped to receive the same or a different fuel from a second and/or third fuel circuit 84, 86. During base load operations, fuel may be supplied to each fuel injector 66, 68 through one of the three fuel circuits 82, 84, 86, while fuel flow may be reduced or completely eliminated from one or more of the fuel injectors 66, 68 during reduced or turndown operations. Altering the fuel split to each fuel circuit 82, 84, 86 in one or more combustors 42 may alter the frequency, the phase, the amplitude, the standard deviation of frequency, the standard deviation of frequency through time, the coefficient of variation of frequency, the coefficient of variation of frequency through time, the index of dispersion of frequency, the index of dispersion of frequency through time, the variance of frequency, and/or the variance of frequency through time of one or more combustion instabilities.
An overlap between the frequency of the combustion dynamics and the downstream component resonant frequency may result in unwanted vibration of the downstream components when an in-phase and coherent relationship between the frequencies of two or more combustors 42 exists. Various embodiments of the present disclosure seek to detect and/or reduce unwanted vibrations in hot gas path components downstream from the combustion system by determining a frequency, a standard deviation of a frequency, a standard deviation of a frequency through time, a coefficient of variation of a frequency, a coefficient of variation of a frequency through time, an index of dispersion of a frequency, an index of dispersion of a frequency through time, a variance of a frequency, and/or a variance of a frequency through time, and, optionally, a phase and/or an amplitude, of one or more combustion instabilities. The frequency, the standard deviation of the frequency, the standard deviation of the frequency through time, the coefficient of variation of the frequency, the coefficient of variation of the frequency through time, the index of dispersion of the frequency, the index of dispersion of the frequency through time, the variance of the frequency, and/or the variance of the frequency through time, and optionally, a phase and/or an amplitude, are compared to a predetermined limit. When one or more of the frequency, the standard deviation of the frequency through time, the coefficient of variation of the frequency, the coefficient of variation of the frequency through time, the index of dispersion of the frequency, the index of dispersion of the frequency through time, the variance of the frequency, and/or the variance of the frequency through time, and optionally, the phase and/or the amplitude are actionable relative to its respective predetermined limit, the present system and method adjust at least one parameter of the gas turbine. In this manner, the embodiments of the present disclosure may detect and/or reduce unwanted vibrations in hot gas path components downstream from the combustion system over a wide range of operating levels.
Specifically, one or more various quantifications may be employed to provide a measure of the degree of frequency overlap of the combustors 42 and, therefore, an indication of the degree of modal coupling of the combustion dynamics. Quantifications that have been found useful include the standard deviation of frequency, the coefficient of variation of frequency, the index of dispersion of frequency, and the variance of frequency. Such quantifications may be calculated for two or more combustors 42 and for one or more combustion instabilities. It has been found that a decrease in any of these quantifications indicates that the degree of modal coupling of the combustion dynamics has increased.
Alternately, or in addition, any of the above quantifications when calculated over time—that is, the standard deviation of the frequency through time, the coefficient of variation of frequency through time, the index of dispersion of frequency through time, and the variance of frequency through time—for one or more combustion instabilities of the individual combustors 42, and/or for the mean or median of one or more combustion instabilities of the combustors 42, provides a measure of the variability of the combustion dynamics frequency through time. Therefore, such quantifications are indicative of the degree of modal coupling of the combustion dynamics.
FIG. 5A provides an exemplary graph of coherence as a function of the standard deviation of a mean or median frequency through time, according to one embodiment of the present disclosure. For example, the standard deviation of the frequency over time may be calculated from the mean or median frequency for two or more combustors 42; for one or more individual combustors 42 for a pre-defined time period (e.g., for 10 seconds); or for a pre-defined number of scans (e.g., for 32 scans of individual spectra). It should be noted that the optimal time period or number of scans may vary with the capability of the combustion dynamics measurement system, and possibly also the specific characteristics of the combustion instability. As the graph of FIG. 5A shows, coherence in the combustion dynamics increases noticeably as the standard deviation of the mean frequency over time decreases below a predetermined standard deviation of mean frequency over time threshold 94.
FIG. 5B provides an exemplary graph of coherence as a function of the coefficient of variation of a mean or median frequency through time, according to another embodiment of the present disclosure. For example, the coefficient of variation of the frequency over time may be calculated from the mean or median frequency for two or more combustors 42; for one or more individual combustors 42 for a pre-defined time period (e.g., for 10 seconds); or for a pre-defined number of scans (e.g., for 32 scans of individual spectra). It should be noted that the optimal time period or number of scans may vary with the capability of the combustion dynamics measurement system, and possibly also the specific characteristics of the combustion instability. As the graph of FIG. 5B shows, coherence in the combustion dynamics increases noticeably as the coefficient of variation of the mean frequency over time decreases below a predetermined coefficient of variation of mean frequency over time threshold 94.
FIG. 5C provides an exemplary graph of coherence as a function of the index of dispersion of a mean or median frequency through time, according to yet another embodiment of the present disclosure. For example, the index of dispersion of the frequency over time may be calculated from the mean or median frequency for two or more combustors 42; for one or more individual combustors 42 for a pre-defined time period (e.g., for 10 seconds); or for a pre-defined number of scans (e.g., for 32 scans of individual spectra). It should be noted that the optimal time period or number of scans may vary with the capability of the combustion dynamics measurement system, and possibly also the specific characteristics of the combustion instability. As the graph of FIG. 5C shows, coherence in the combustion dynamics increases noticeably as the index of dispersion of the mean frequency over time decreases below a predetermined index of dispersion of mean frequency over time threshold 94.
FIG. 5D provides an exemplary graph of coherence as a function of the variance of a mean or median frequency through time, according to a further embodiment of the present disclosure. For example, the variance of the frequency over time may be calculated from the mean or median frequency for two or more combustors 42; for one or more individual combustors 42 for a pre-defined time period (e.g., for 10 seconds); or for a pre-defined number of scans (e.g., for 32 scans of individual spectra). It should be noted that the optimal time period or number of scans may vary with the capability of the combustion dynamics measurement system, and possibly also the specific characteristics of the combustion instability. As the graph of FIG. 5D shows, coherence in the combustion dynamics increases noticeably as the variance of the mean frequency over time decreases below a predetermined variance of mean frequency over time threshold 94.
Thus, various embodiments of the present disclosure may determine the frequency, the coefficient of variation of the frequency, the index of dispersion of the frequency, the variance of the frequency, and/or any of the above through time and optionally, the phase and/or the amplitude of one or more combustion instabilities. The determined quantifications are compared to a predetermined limit for that quantification. At least one parameter of the gas turbine 10 is adjusted if the frequency, one or more of the quantifications of frequency, and, optionally, the phase and/or the amplitude is actionable relative to its predetermined limit. In this manner, the embodiments of the present disclosure may detect and/or reduce unwanted vibrations in hot gas path components downstream from the combustion system over a wide range of operating levels.
FIG. 6 provides a simplified cross-section view of a system 100 for reducing unwanted vibrations in hot gas path components downstream from the combustion section 16, according to the present disclosure. As shown in FIG. 6, the system 100 may be incorporated into the gas turbine 10 (previously described with respect to FIG. 1) and may include a controller 102 configured to execute logic 104 stored in a memory 106.
The controller 102 may generally be any suitable processing device known in the art, and the memory 106 may generally be any suitable computer-readable medium or media, including, but not limited to, RAM, ROM, hard drives, flash drives, or other memory devices. As is generally understood, the memory 106 may be configured to store information accessible by the controller 102, including instructions or logic 104 that can be executed by the controller 102. The instructions or logic 104 may be any set of instructions that when executed by the controller 102 cause the controller 102 to provide the desired functionality.
For instance, the instructions or logic 104 can be software instructions rendered in a computer-readable form. When software is used, any suitable programming, scripting, or other type of language or combinations of languages may be used to implement the teachings contained herein. Alternatively, the instructions can be implemented by hard-wired logic or other circuitry, including, but not limited to application-specific circuits.
The technical effect of the controller 102 is to execute the logic 104 stored in the memory 106 to cause the controller 102 to determine a frequency, a quantification of frequency and/or a quantification of frequency through time, and optionally, a phase and/or an amplitude of one or more combustion instabilities. As provided above, the quantifications of frequency include a standard deviation of frequency, a coefficient of variation of frequency, an index of dispersion of frequency, and a variance of frequency.
The controller 102 may receive a dynamic pressure signal 108 from each combustor 42, and the logic 104 may enable the controller 102 to calculate the frequency, the quantification of frequency, and/or the quantification of the frequency through time, and, optionally, a phase and/or an amplitude of one or more combustors 42 for one or more combustion instabilities. Additionally, the logic 104 may enable the controller 102 to calculate the mean or median frequency, quantification of frequency through time, phase, and/or amplitude of two or more of the combustors 42.
The method by which average or median values are determined may vary for different combustion instabilities and for different types of combustors 42. For example, the mean or median phase may be determined as the mean or median of the absolute value of the phase measured (a) for one or more of the combustion instabilities, (b) between one or more pairs of adjacent combustors 42, (c) between one or more pairs of combustors 42, and/or (d) for each combustor 42 with respect to a predetermined reference combustor 42. Similarly, the mean or median frequency and/or amplitude may be determined from two or more of the combustors 42 in the gas turbine 10.
The quantification of frequency through time may be determined similarly, by determining the quantification of the frequency of one or more cans through time, followed by determination of the mean or median of the quantification of frequency through time for the one or more cans. Alternately, the quantification of frequency through time may be determined by first determining the mean or median for two or more combustors, followed by the quantification of the frequency through time for the mean or median of two or more combustors 42. In addition, quantification of frequency may be determined as the quantification of the frequency for one or more instabilities of two or more combustors 42. The particular quantifications contemplated herein include the standard deviation, the coefficient of variation, the index of dispersion, and the variance.
It is important to note that a dynamic pressure signal is not required for all combustors 42. Certainly, it is beneficial to have a dynamic pressure signal from each combustor 42. However, in the event that the dynamic pressure signal is identified as faulty or unavailable for one or more combustors 42, the dynamic pressure signal may be excluded from the determination of average or median phase, quantification of frequency, and/or quantification of frequency through time.
The logic 104 may further cause the controller 102 to compare the frequency, the quantification of frequency, and/or the quantification of frequency through time, and, optionally, the phase and/or amplitude of the one or more combustion instabilities to a predetermined limit; and to adjust at least one parameter of the gas turbine 10 if the frequency, the quantification of the frequency, the quantification of the frequency through time, and, optionally, the phase and/or the amplitude, of the one or more combustion instabilities is actionable relative to the predetermined limit.
As used herein, the phrase “actionable relative to the predetermined limit” depends on the particular parameter being compared and means that the parameter is either within a designated range (e.g., for frequency), less than a lower predetermined limit (e.g., for phase, standard deviation of frequency, coefficient of variation of frequency, index of dispersion of frequency, variance of frequency, or any of the above quantifications of frequency through time), or greater than an upper predetermined limit (e.g., for amplitude). It is to be understood that, in various embodiments, two, three, or four characteristics may be determined to be actionable relative to their predetermined limits before the system (or method) performs an action. The predetermined limits may vary for different combustion instabilities and may vary for different combustor 42 and gas turbine 10 configurations. Therefore, it should be understood that the predetermined limits for frequency, phase, amplitude, and quantification(s) of frequency may be set to any value.
In an exemplary embodiment, if the frequency is actionable relative to the predetermined frequency limit by being within the designated frequency range, the phase is actionable relative to the predetermined phase limit by being less than the predetermined phase limit, the amplitude is actionable relative to the predetermined amplitude limit by being greater than the predetermined amplitude limit, the quantification of the frequency is actionable relative to the predetermined quantification of frequency limit by being less than the predetermined quantification of frequency limit, and/or the quantification of the frequency through time exceeds the predetermined quantification of frequency through time limit 94 by being less than the predetermined quantification of frequency through time limit 94, then the system 100 may take corrective action to reduce unwanted combustion-driven vibrations in hot gas path components downstream from the combustion section 16.
One particular method contemplated herein includes the determination of each of the frequency, amplitude, phase, and one quantification of frequency and/or quantification of frequency through time, prior to adjusting any parameter of the gas turbine, since a determination of these four characteristics provides the most information with respect to the behavior of the combustion dynamics of the combustors 42. However, for some configurations, such as those of a mature fleet with significant operating experience, it may be possible to adjust a parameter of the gas turbine based only on a determination of frequency and one quantification of frequency or quantification of frequency through time. In this instance, the additional operating experience may provide pre-existing knowledge of the phase, such that the phase characteristics can be assumed, as opposed to being determined as part of the present method.
The system 100 may include various means for adjusting at least one parameter of the gas turbine 10 if the frequency, the quantification of the frequency, and/or the quantification of the frequency through time, and, optionally, the phase and/or the amplitude of the one or more combustion instabilities is actionable relative to the predetermined limit. For example, a change in the temperature, pressure, and/or flow rate of the compressed working fluid 38 produced by the compressor section 14 directly affects the frequency and/or amplitude of each combustor 42. In turn, a change in the frequency and/or amplitude may change the phase, the quantifications of frequency, and/or the quantifications of frequency through time of one or more combustion instabilities of the combustion system. The system 100 may include various mechanisms for changing the temperature, pressure, and/or flow rate of the compressed working fluid 38 produced by the compressor section 14.
The temperature of the working fluid 28 entering the compressor section 14 may be changed using evaporative cooling, heat exchangers, chillers, or other temperature-altering devices known in the art. In one particular embodiment shown in FIG. 6, a valve 110 (such as a control valve, a throttle valve, a thermostatic expansion valve, or other suitable flow control device) is operably connected to the one or more temperature-altering devices 24 in the inlet section 12. The controller 102 may reposition the valve 110 to either increase or decrease heating or cooling provided to the working fluid 28 flowing through the inlet section 12. In this manner, the temperature of the working fluid 28 entering the compressor section 14 may be varied, which in turn varies the temperature, pressure, and/or flow rate of the compressed working fluid 38 produced by the compressor section 14.
In a second embodiment shown in FIG. 6, the flow rate of the compressed working fluid 38 produced by the compressor section 14 may be changed by changing a flow rate of the working fluid 28 entering the compressor section 14. As shown in FIG. 6, the system 100 includes an actuator 112 or other operator operably connected to one or more inlet guide vanes 114 installed in the compressor 30. The controller 102 may reposition the actuator 112 to either open or close the inlet guide vanes 114, thereby increasing or decreasing (respectively) the flow rate of the working fluid 28 entering the compressor section 14.
In alternate embodiments, one or more sets of stationary vanes 36 having variable positions, also known as variable stator vanes (not shown), may be used to vary the flow rate of the working fluid 28 through the compressor 30. In this configuration, the flow rate of the working fluid 28 through the compressor 30 may be varied or altered, which consequently changes the temperature, pressure, and/or flow rate of the compressed working fluid 38 produced by the compressor section 14.
FIG. 6 provides a third example of a suitable structure for changing the temperature, pressure, and/or flow rate of the compressed working fluid 38 produced by the compressor section 14. In this example, the system 100 includes a conduit 116 (or pipe or other fluid connection) positioned between a downstream portion of the compressor 30 and an inlet of the compressor 30. The controller 102 may reposition a valve 118 (such as a control valve, throttle valve, thermostatic expansion valve, or other suitable flow control device) to either increase or decrease the flow rate of the compressed working fluid 38 diverted through the conduit 116 to recirculate through the compressor section 14. In alternate embodiments, the system 100 may include an additional heat exchanger (not shown) operably connected to the conduit 116 to either heat or cool the compressed working fluid 38 recirculated through the compressor section 14. In this manner, the flow rate and/or temperature of the compressed working fluid 38 recirculated through the compressor section 14 may be varied, which therefore varies the temperature, pressure, and/or flow rate of the compressed working fluid 38 produced by the compressor section 14.
Another way to change the frequency, phase, amplitude, quantification of frequency, and/or quantification of frequency through time of one or more combustion instabilities of the combustors 42 is to change the fuel flow and/or fuel temperature to one or more of the fuel circuits 82, 84, 86 in one or more combustors 42. FIG. 7 provides a diagram of such a system 120 for changing the combustion instability frequency and/or amplitude of one or more combustors 42 by changing the fuel flow and/or fuel temperature in one or more fuel circuits 82, 84, 86 in one or more of the combustors 42, according to alternate embodiments of the present disclosure.
Specifically, a change in the fuel pressure ratio (i.e., combustor pressure-to-fuel pressure) and/or equivalence ratio resulting from differences in the fuel flow rate and/or fuel temperature may directly affect the combustion instability frequency and/or amplitude in each combustor 42. As the frequency of the combustion dynamics in one or more, but not all, combustors 42 is driven away from that of the other combustors 42, the quantification of frequency and/or quantification of frequency through time is reduced. Accordingly, the modal coupling of the combustion dynamics is reduced, which thereby reduces the ability of the combustor tone to cause a vibratory response in downstream components. In addition, shifting the combustion dynamics frequency of each of the combustors 42 away from the natural frequency of the downstream components may also reduce unwanted vibrations of downstream components.
As shown in FIG. 7, the system 120 may be incorporated into the gas turbine 10 previously described with respect to FIG. 1 and may include various mechanisms for changing the combustion instability frequency in one or more combustors 42 by changing the fuel flow and/or fuel temperature to one or more of the fuel circuits 82, 84, 86 in one or more combustors 42. Although only three combustors 42 are shown in FIG. 7, the present invention is not limited to any specific number of combustors 42, unless specifically recited in the claims.
In one particular embodiment shown in FIG. 7, the fuel flow to one or more of the combustors 42 may be changed using a valve 122 (such as a control valve, a throttle valve, or other suitable flow control device) operably connected to one or more of the fuel circuits 82, 84, 86 that supply fuel to one or more of the combustors 42. The controller 102 may reposition each valve 122 in the respective fuel circuits 82, 84, 86 to increase or decrease the fuel flow into one or more of the fuel circuits 82, 84, 86.
In other particular embodiments, the fuel flow from the one or more fuel circuits 82, 84, 86 to one or more individual combustors 42 may be changed. In this embodiment, individual valves 124 (such as control valves, throttle valves, or other suitable flow control devices) are operably connected in one or more of the fuel circuits 82, 84, 86 upstream from individual combustors 42. The controller 102 may reposition each individual control valve 124 to change the fuel flow through one or more fuel circuits 82, 84, 86 to one or more combustors 42, thus changing the fuel flow to the fuel injectors 66, 68 in one or more individual combustors 42.
One of ordinary skill in the art will readily appreciate from the teachings herein that the individual valves 124 in one or more fuel circuits 82, 84, 86 may be present in addition to, or instead of, the valves 122 in the respective fuel circuits 82, 84, 86 previously described. According to this aspect of the present disclosure, the fuel flow from one or more fuel circuits 82, 84, 86 may be varied to one or more fuel injectors 66, 68 and/or combustors 42 to change the frequency, phase, amplitude, one or more of the quantifications of frequency, and/or one or more of the quantifications of frequency through time of one or more combustors 42.
In yet another particular embodiment shown in FIG. 7, the combustion instability frequency in one or more combustors 42 may be changed by changing the fuel temperature to one or more of the fuel circuits 82, 84, 86 in one or more combustors 42. As shown in FIG. 7, the system 120 may include a valve 126 (such as a control valve, a throttle valve, a thermostatic expansion valve, or other suitable flow control device) operably connected to one or more heat exchangers 128, which are used to adjust the temperature of the fuel to one or more of the fuel circuits 82, 84, 86.
Alternately, or in addition, a separate control valve 130 and a heat exchanger 132 may be connected in one or more of the fuel circuits 82, 84, 86 upstream from individual combustors 42 to similarly change the fuel temperature through one or more fuel circuits 82, 84, 86 to one or more combustors 42. In this manner, the temperature of the fuel being directed to the fuel injectors 66, 68 in one or more individual combustors 42 may be changed. Thus, the fuel temperature through one or more fuel circuits 82, 84, 86 and/or to one or more fuel injectors 66, 68 and/or combustors 42 may be varied to change the frequency, phase, amplitude, one or more of the quantifications of frequency, and/or one or more of the quantifications of frequency through time of one or more combustion instabilities of one or more combustors 42.
One of ordinary skill in the art will readily appreciate from the teachings herein that the systems 100, 120 described and illustrated with respect to FIGS. 6 and 7 may provide various methods for the gas turbine 10 to detect and/or reduce unwanted vibrations in hot gas path components downstream from the combustion system. FIG. 8 provides an exemplary flow diagram of suitable methods according to various embodiments of the present invention.
In FIG. 8, at block 134, the method may determine the frequency, one or more of the quantifications of the frequency, and/or one or more of the quantifications of the frequency through time of one or more combustion instabilities of one or more combustors 42. Optionally, the phase and/or amplitude of one or more combustion instabilities of one or more combustors 42 may also be determined. The quantifications of frequency include the standard deviation (δd) of frequency, the coefficient of variation (COV) of frequency, the index of dispersion (IOD) of frequency, and the variance of frequency. The quantifications of frequency through time include the standard deviation of frequency through time, the coefficient of variation of frequency through time, the index of dispersion of frequency through time, and the variance of frequency through time.
According to a first aspect of the present disclosure, the method may determine the frequency and at least one of the quantifications of frequency (and/or at least one of the quantifications of frequency through time) of one or more combustion instabilities. In another aspect of the present disclosure, the method may determine the frequency, at least one of the quantifications of frequency (and/or at least one of the quantifications of frequency through time), and the phase of one or more combustion instabilities. In yet another aspect of the present disclosure, the method may determine the frequency, at least one of the quantification of frequency (and/or at least one of the quantifications of frequency through time), and the amplitude of one or more combustion instabilities. In a still further aspect of the present disclosure, the method may determine, the frequency, at least one of the quantification of frequency (and/or at least one of the quantifications of frequency through time), the phase, and the amplitude of one or more combustion instabilities.
At block 136, the method may compare the frequency, one or more of the quantifications of the frequency and/or one or more of the quantifications of the frequency through time, and, optionally, the phase and/or amplitude to the associated predetermined limits to determine if there is a likelihood of unwanted vibrations in downstream components. Such unwanted vibrations may result from coherent, in-phase combustion instabilities. In particular embodiments, the method may determine two, three, four, or more of the frequency, quantifications of frequency, quantifications of frequency through time, phase, and amplitude of the one or more combustion instabilities and compare each to a separate predetermined limit to determine if the characteristics are actionable.
If one or more of the measured characteristics are actionable relative to their respective predetermined limit, the method may adjust at least one parameter of the gas turbine 10 (as previously described with respect to FIGS. 6 and 7) to reduce unwanted vibrations in hot gas path components downstream from the combustion system, as indicated by block 138. Otherwise, the method returns to block 134, and the process repeats. As described above, parameters of the gas turbine 10 that may be adjusted include: the temperature of the compressed working fluid produced by the compressor section; the flow rate of the working fluid entering the compressor section; the flow rate of the compressed working fluid recirculated through the compressor section; the flow rate of the fuel directed to at least one fuel injector; and the fuel temperature of the fuel directed to at least one fuel injector.
As discussed above, the comparisons performed in block 136 may also incorporate a predetermined time limit into the comparison to increase reliability and to reduce false indications of modal coupling conditions. For example, the comparisons performed in block 136 may include a comparison of a quantification of the frequency of the one or more combustion instabilities through time with a predetermined quantification limit through time. The method may be configured such that, when two or more of the frequency, the quantification of the frequency through time, the amplitude, and the phase are determined actionable relative to their respective predetermined limit for a predetermined time interval, an adjustment of one or more of the gas turbine parameters is triggered to reduce unwanted vibrations of downstream components.
The various embodiments described and illustrated with respect to FIGS. 1-8 may provide one or more of the following advantages over existing systems and methods for operating gas turbines 10. Specifically, changing the temperature, pressure, and/or flow rate of the compressed working fluid 38 and/or the flow rate or temperature of the fuel directed to the combustors 42, alone or in various combinations, may decouple the combustion dynamics and/or reduce modal coupling of the combustors 42, thereby reducing unwanted vibrations in hot gas path components downstream from the combustion system. As a result, the various embodiments described herein may enhance thermodynamic efficiency, promote flame stability, and/or reduce undesirable emissions over a wide range of operating levels, without detrimentally impacting the life of the downstream hot gas path components.
This written description uses examples to disclose the invention, including the best mode, and to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they include structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims.

## Claims

1. A system for operating a gas turbine (10), the system comprising:
a. a compressor section (14) configured to receive a working fluid (28) and to produce a compressed working fluid (38), wherein the compressor section (14) comprises a conduit (116) for recirculating the compressed working fluid (38) from a downstream portion of the compressor section (14) to an upstream portion of the compressor section (14);
b. a plurality of combustors (42) downstream from the compressor section (14), each combustor (42) comprising a fuel injector (66, 68), the fuel injector (66, 68) receiving fuel at a fuel temperature and a fuel flow rate; and
c. a controller (102) configured to execute logic (104) stored in a memory (106), the logic (104) causing the controller (102):
i. to determine (step 134, FIG. 8) a frequency of a combustion instability and at least one quantification of the frequency of the combustion instability;
ii. to compare (step 136, FIG. 8) the frequency of the combustion instability to a predetermined frequency limit and the at least one quantification of the frequency of the combustion instability to a respective predetermined quantification limit (e.g., 94, FIGS. 5A-5D); and
iii. to adjust (step 138, FIG. 8) at least one parameter of the gas turbine (10) if the frequency of the combustion instability is actionable relative to the predetermined frequency limit and the at least one quantification of the frequency of the combustion instability is actionable relative to its respective predetermined quantification limit (e.g., 94, FIGS. 5A-5D);
wherein the at least one parameter adjusted (step 138, FIG. 8) by the controller (102) is one of a temperature of the compressed working fluid (38) produced by the compressor section (14) of the gas turbine (10); a flow rate of the working fluid (28) entering the compressor section (14) of the gas turbine (10); a flow rate of the compressed working fluid (38) recirculated through the compressor section (14) of the gas turbine (10); the fuel flow rate of the fuel to at least one injector (66, 68); and the fuel temperature of the fuel to at least one injector (66, 68).

2. The system of claim 1, wherein the at least one quantification of frequency is selected from the group consisting of: a standard deviation of frequency, a coefficient of variation of frequency, an index of dispersion of frequency, a variance of frequency, a standard deviation of frequency through time (94, FIG. 5A), a coefficient of variation of frequency through time (94, FIG. 5B), an index of dispersion of frequency through time (94, FIG. 5C), and a variance of frequency through time (94, FIG. 5D).

3. The system of claim 1, wherein the controller (102) is further configured to compare (step 136, FIG. 8) at least one of the frequency and the quantification of the frequency of the combustion instability to a predetermined time limit (94, FIGS. 5A-5D).

4. The system of claim 1, wherein the controller (102) is further configured to determine (step 134, FIG. 8) an amplitude of the combustion instability; to compare (step 136, FIG. 8) the amplitude of the combustion instability to a predetermined amplitude limit; and to adjust (step 138, FIG. 8) at least one parameter of the gas turbine (10) if the amplitude of the combustion instability is actionable relative to the predetermined amplitude limit.

5. The system of claim 1, wherein the controller (102) is further configured to determine (step 134, FIG. 8) a phase of the combustion instability; to compare (step 136, FIG. 8) the phase of the combustion instability to a predetermined phase limit; and to adjust (step 138, FIG. 8) at least one parameter of the gas turbine (10) if the phase of the combustion instability is actionable relative to the predetermined phase limit.

6. The system of claim 1, wherein the controller (102) is further configured to determine (step 134, FIG. 8) an amplitude and a phase of the combustion instability; to compare (step 136, FIG. 8) the amplitude of the combustion instability to a predetermined amplitude limit and the phase of the combustion instability to a predetermined phase limit; and to adjust (step 138, FIG. 8) at least one parameter of the gas turbine (10) if at least one of the amplitude of the combustion instability is actionable relative to a predetermined amplitude limit and the phase of the combustion instability is actionable relative to a predetermined phase limit.

7. The system of claim 6, wherein the controller (102) is further configured to compare (step 136, FIG. 8) at least one of the frequency, the quantification of frequency, the amplitude, and the phase of the combustion instability to a predetermined time limit; and wherein the quantification of the frequency is selected from the group consisting of a standard deviation of frequency, a coefficient of variation of frequency, an index of dispersion of frequency, and a variance of frequency.

8. A method for operating a gas turbine (10), the gas turbine (10) comprising a compressor section (14) configured to receive a working fluid (28) and to produce a compressed working fluid (38), wherein the compressor section (14) comprises a conduit (116) for recirculating the compressed working fluid (38) from a downstream portion of the compressor section (14) to an upstream portion of the compressor section (14); and a plurality of combustors (42) downstream from the compressor section (14), each combustor (42) comprising a fuel injector (66, 68), the fuel injector (66, 68) receiving fuel at a fuel temperature and a fuel flow rate; and a controller (102) configured to execute logic (104) stored in a memory (106), the logic (104) causing the controller (102) to practice the method comprising:
a. determining (step 134, FIG. 8) a frequency of a combustion instability;
b. comparing (step 136, FIG. 8) the frequency of the combustion instability to a predetermined frequency limit;
c. determining at least one quantification (step 134, FIG. 8) of the frequency of the combustion instability;
d. comparing (step 136, FIG. 8) the at least one quantification of the frequency of the combustion instability to a respective predetermined quantification limit; and
e. adjusting (step 138, FIG. 8) at least one parameter of the gas turbine (10) if the frequency of the combustion instability is actionable relative to the predetermined frequency limit, and the quantification of the frequency of the combustion instability is actionable relative to its respective predetermined quantification limit;
wherein the at least one parameter adjusted (step 138, FIG. 8) by the controller (102) is one of a temperature of the compressed working fluid (38) produced by the compressor section (14) of the gas turbine (10); a flow rate of the working fluid (28) entering the compressor section (14) of the gas turbine (10); a flow rate of the compressed working fluid (38) recirculated through the compressor section (14) of the gas turbine (10); the fuel flow rate of the fuel to at least one injector (66, 68); and the fuel temperature of the fuel to at least one injector (66, 68).

9. The method of claim 8, wherein the at least one quantification of frequency is selected from the group consisting of: a standard deviation of frequency, a coefficient of variation of frequency, an index of dispersion of frequency, a variance of frequency, a standard deviation of frequency through time (94, FIG. 5A), a coefficient of variation of frequency through time (94, FIG. 5B), an index of dispersion of frequency through time (94, FIG. 5C), and a variance of frequency through time (94, FIG. 5D).

10. The method of claim 8, further comprising: comparing at least one of the frequency and the quantification of frequency of the combustion instability to a predetermined time limit (94, FIGS. 5A-5D).

11. The method of claim 8, further comprising: determining (step 134, FIG. 8) an amplitude of the combustion instability; comparing (step 136, FIG. 8) the amplitude of the combustion instability to a predetermined amplitude limit; and adjusting (step 138, FIG. 8) at least one parameter of the gas turbine (10) if the amplitude of the combustion instability is actionable relative to the predetermined amplitude limit.

12. The method of claim 8, further comprising:
determining (step 134, FIG. 8) a phase of the combustion instability; comparing (step 136, FIG. 8) the phase of the combustion instability to a predetermined phase limit; and adjusting (step 138, FIG. 8) at least one parameter of the gas turbine (10) if the phase of the combustion instability is actionable relative to the predetermined phase limit.

13. The method of claim 8, further comprising: determining (step 134, FIG. 8) an amplitude and a phase of the combustion instability; comparing (step 136, FIG. 8) the amplitude of the combustion instability to a predetermined amplitude limit and the phase of the combustion instability to a predetermined phase limit; and adjusting (step 138, FIG. 8) at least one parameter of the gas turbine (10) if at least one of the amplitude of the combustion instability is actionable relative to a predetermined amplitude limit and the phase of the combustion instability is actionable relative to a predetermined phase limit.

14. The method of claim 13, further comprising: comparing (step 136, FIG. 8) at least one of the frequency, the quantification of frequency, the amplitude, and the phase of the combustion instability to a predetermined time limit; wherein the quantification of frequency is selected from the group consisting of a standard deviation of frequency (94, FIG. 5A), a coefficient of variation of frequency (94, FIG. 5B), an index of dispersion of frequency (94, FIG. 5C), and a variance of frequency (94, FIG. 5D).