CN111523206A - Gas turbine speed regulating system model improvement method considering' air hammer effect - Google Patents
Gas turbine speed regulating system model improvement method considering' air hammer effect Download PDFInfo
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Abstract
A gas turbine speed regulating system model improvement method considering 'air hammer effect' belongs to the technical field of electric power. The improved method comprises the steps of firstly establishing a gas turbine speed regulating system model considering the air hammer effect; secondly, analyzing and analyzing the frequency response characteristics through reasonable simplification; and finally, verifying the improved gas turbine speed regulating system model. The invention improves the combustion chamber link of the original gas turbine model by analyzing the formation reason of the 'air hammer effect' of the gas turbine, and adds a combustion chamber time constant T for assisting the adjustment of the air-fuel ratio of the combustion chamber by reacting a bypass system of the combustion chamberCRAnd then, a simplified dynamic model is provided, frequency response characteristic analysis is carried out, so that the follow-up further research on how to avoid the negative influence caused by the air hammer effect and give full play to the overall rapid frequency response advantage of the gas turbine is facilitated, and the method is used for ensuring the rapid frequency response in the power systemProvides a basis for the frequency quality of.
Description
Technical Field
The invention belongs to the technical field of electric power, and relates to a gas turbine speed regulating system model improvement method considering an air hammer effect.
Background
Under the vigorous development of extra-high voltage, the safety and stability of the system are seriously affected by the high-power loss, the addition of renewable energy occupies the internet space of a conventional rapid frequency response unit, and the fluctuation of the renewable energy such as wind power, photovoltaic and the like brings greater challenges to the frequency adjustment of the power system.
The gas turbine set has the advantages of being rapid in starting and stopping, rapid in load changing rate and the like, and becomes a good resource of the power grid in rapid frequency response resource allocation and calling at present. However, in the process of quick frequency response, the 'air hammer effect' exists in the initial stage of the variable output, and the 'reverse tuning' phenomenon that the output power is firstly reduced and then increased can be formed. The system urgently needs each power supply to rapidly provide power support in the initial stage of rapid frequency response so as to prevent the frequency from rapidly decreasing and avoid triggering low-frequency load shedding. The 'reverse tuning' caused by the 'air hammer effect' can seriously affect the frequency adjusting effect of the gas turbine at the initial response stage, reduce the quality of the system frequency and simultaneously have higher possibility of threatening the safety of the system frequency. And the existing gas turbine simulation model has less consideration to the dynamic process, and cannot reflect the dynamic change of the gas turbine output at the stage. Therefore, it is urgently needed to invent a gas turbine speed regulating system model improvement method considering the air hammer effect, which is convenient for reasonably compensating or controlling the action of the gas turbine speed regulating system model on the basis of the air hammer effect, so as to achieve the purpose of avoiding the negative influence caused by the air hammer effect and fully exerting the advantage of overall quick frequency response of the gas turbine.
Disclosure of Invention
The invention discovers that the 'air hammer effect' in the gas turbine has adverse effect on the frequency response capability of the gas turbine at the initial stage of primary frequency modulation by analyzing the reason of simulation error of the existing gas turbine simulation model, and based on the 'air hammer effect', the invention provides the gas turbine speed regulating system model improvement method considering the 'air hammer effect', wherein the 'air hammer effect' can form the 'reverse regulation' phenomenon that the output power is firstly reduced and then increased, and the system urgently needs each power supply to quickly provide power support at the initial stage of quick frequency response so as to prevent the frequency from quickly reducing and avoid triggering low-frequency load shedding. The 'reverse tuning' caused by the 'air hammer effect' can seriously affect the frequency adjusting effect of the gas turbine at the initial response stage, reduce the quality of the system frequency and simultaneously have higher possibility of threatening the safety of the system frequency.
In order to achieve the purpose, the technical scheme adopted by the invention is as follows:
a gas turbine speed regulating system model improvement method considering 'air hammer effect' is provided, the improvement method firstly establishes a gas turbine speed regulating system model considering 'air hammer effect'; secondly, analyzing and analyzing the frequency response characteristics through reasonable simplification; and finally, verifying the improved gas turbine speed regulating system model. The method comprises the following specific steps:
in the first step, a gas turbine governing system model considering the air hammer effect is established based on a traditional GAST model.
The existing gas turbine simulation model has little consideration on the change of parameters such as temperature, air pressure and the like in the operation process of a system, and cannot reflect the dynamic change of the active power output of the gas turbine in the initial response stage. Wherein the combustor force function is shown in equation (1).
Wherein, PcFor combustion chamber output, Δ μ is combustion chamber intake variation, T2Is the combustion chamber fuel time constant.
During actual operation, the gas turbine system calculates a corresponding fuel set command to control the main fuel nozzle opening by measuring the deviation of its actual rotational speed from a set value, and changes the power load of the gas turbine by changing the amount of fuel entering the combustor. Meanwhile, the opening of the Inlet Guide Vanes (IGV) of the gas turbine is also changed. If the output force is required to be increased, the IGV opening is increased, and due to the air hammer effect, the gas in the pipeline is pumped back, so that the ratio of the air and the fuel in the combustion chamber is changed, and the optimal air-fuel ratio cannot be maintained. Then the gas turbine adjusts the air flow in the combustion chamber through a bypass system, so that the air-fuel ratio is recovered to the optimal value, and the stable combustion reaction is maintained, therefore, the 'air hammer effect' can form the 'reverse regulation' phenomenon that the output power is firstly reduced and then increased.
Therefore, the method for controlling the speed of the gas turbine includes the step of adding a response time constant T containing a combustion chamber into the combustion chamber of the original gas turbine speed control system modelCRAnd the first-order differential link is used for reflecting the process of adjusting and correcting the air-fuel ratio in the combustion chamber by the gas turbine bypass system, and the output function of the improved combustion chamber is shown as a formula (2).
In the formula, PcFor combustion chamber output, Δ μ is combustion chamber intake variation, T2Is the combustion chamber fuel time constant, TCRIs the combustion chamber response time constant.
Therefore, an improved model of the gas turbine speed regulating system, which is called a dynamic improved model for short, is obtained by considering the air hammer effect, and the transfer function of the improved model is shown as the formula (3).
In the formula, vrefRated speed of the speed regulator, K power gain factor, R generator set regulation constant, △ omega generator set speed deviation, T1Is the IGV opening positioner constant, T2Is the time constant of the fuel, TCRIs the combustion chamber response time constant, PeH represents an inertia time constant and D represents a load damping coefficient for the electromagnetic power of the generator set.
And secondly, carrying out frequency response characteristic analysis on the improved model of the gas turbine speed regulating system considering the air hammer effect through reasonable simplification.
Because the improved model of the gas turbine speed regulating system considering the 'air hammer effect' has more related parameters and higher order, the actual frequency response analytic analysis and calculation process is too complex, and an analytic solution is difficult to obtain, the analytic analysis is carried out after reasonable simplification of the analytic solution is considered. The specific simplification steps include:
(1) in the quick frequency response, the actual process of the opening change of the gas turbine is that the gas turbine is fast first and then slow, and when the opening reaches the upper limit, the maximum opening is kept unchanged. When the frequency is seriously decreased, the opening degree mu is rapidly increased within 0.5s and is maintained at the upper limit mu0. Due to the fact that the change time is very short, the IGV opening degree change process can be linearized and approximately equivalent to a slope form, and the functional expression of the IGV opening degree change process is shown in the formula (4).
Where k is the IGV opening degree change speed, t0For the disturbance start time, t1Is the time at which the IGV opening degree increases to the upper limit.
(2) In the process of quick frequency response, because the change of the operating temperature of the unit is not obvious, the gas turbine can be assumed to be capable of keeping normal operation in the process, and therefore a temperature control loop in the step 1 can be omitted.
Thus, a simplified dynamic model of the gas turbine (abbreviated as a simplified dynamic model) for analytical analysis is obtained by the above simplification, and a specific transfer function thereof is shown in formula (5).
In the formula, tdThe moment at which the IGV opening reaches a steady state value, v0For the rate of change of IGV opening, TCRRepresenting the combustion chamber response time constant, TFRepresenting the fuel time constant.
After obtaining the simplified dynamic model, the method for analyzing the frequency response characteristic of the model specifically comprises the following steps:
assuming that the fault occurs at a time t equal to 0s, the IGV opening degree remains unchanged to μ after the IGV opening degree reaches the steady-state value0And obtaining the variation quantity delta mu of the IGV opening degree according to the IGV linear variation curve in the formula (4) as follows:
Δμ＝v0t-v0(t-td)(t-td) (6)
in the formula, tdAt the time when the IGV opening reaches the steady state value, (t) represents a unit step function, v0Indicating the IGV opening degree change speed.
By applying laplace transform to equation (5), we can obtain:
in the formula, s is a complex parameter variable in the Laplace transformation.
From this, the transfer function of the simplified dynamic model of the gas turbine is shown in equation (5).
The equation of motion of the rotor of a synchronous generator used in a gas turbine is as follows:
in the formula, delta omega represents the rotating speed deviation of the generator set, H represents the inertia time constant, D represents the load damping coefficient, and delta PmRepresenting gas turbine mechanical power, Δ PeRepresenting the gas turbine electromagnetic power.
Laplace transform of formula (8) and converting Δ PmThe substitution of(s) solves for Δ ω to obtain
In the formula,. DELTA.omega1The free response of the system during the non-rotation standby and low-frequency load shedding control is reflected; Δ ω2Reflecting the influence of the release of the spinning reserve caused by the continuous opening of the IGV on the frequency; Δ ω3Reflecting the effect of the back-up constraint on frequency, wherein:
when the active power of the load in the system generates step disturbance with the disturbance amplitude value of delta PeWhen the temperature of the water is higher than the set temperature,
ΔPe(s)＝ΔPe/s (11)
substituting equation (10) into equation (9) and performing inverse Rayleigh transform can obtain:
thus by observing Δ ω2Time domain solution of Δ ω2(t) the output characteristics of the gas turbine can be analyzed when the system has a frequency modulation requirement. When the system is disturbed, the method is shown in formula (12)
The term is always a negative value and is consistent with the expression of the water hammer effect in the water turbine, so that the frequency of the power grid is deteriorated, and the phenomenon of 'reverse regulation' that the output power of the gas turbine is increased after being reduced at the initial stage of the quick frequency response is expressed, so that the frequency response characteristic of the dynamic improved model and the analytic description of the 'air hammer effect' under the quick frequency response are obtained.
And thirdly, carrying out simulation verification on the improved gas turbine speed regulating system model.
Taking an E-class gas turbine with rated power of 100MW as an example, by reasonable parameter setting and simulation calculation based on an MATLAB/SIMULINK platform, the improved simulation result of the gas turbine speed regulating system model considering the air hammer effect and the traditional GAST model is compared with the actual measurement data. And (3) finding out errors of data and actually measured data of the dynamic improved model and the traditional GAST model in each stage (including initial power drop, rising stage, minimum output active power value, transient stability value and the like) in the whole frequency response process from the simulation result, and verifying the actual feasibility of the improved gas turbine speed regulating system model and the simulation accuracy of the traditional model.
The invention has the advantages ofComprises the following steps: the invention provides a gas turbine speed regulating system model improvement method considering 'air hammer effect', which deeply analyzes the basic structure and the working mechanism of a gas turbine to obtain the reason of simulation error of the existing gas turbine simulation model, namely: the 'air hammer effect' is provided, and the improvement measure is pertinently provided, namely, the combustion chamber link of the original gas turbine model is improved, and the combustion chamber time constant T which reflects the bypass system to perform auxiliary adjustment on the air-fuel ratio of the combustion chamber is addedCRAnd then, a simplified dynamic model is provided, frequency response characteristic analysis is carried out, so that the follow-up further research on how to avoid the negative influence caused by the 'air hammer effect' and give full play to the overall rapid frequency response advantage of the gas turbine is facilitated, and a basis is provided for guaranteeing the frequency quality in the rapid frequency response in the power system.
Drawings
FIG. 1 is a GAST model simulation result versus actual measurement data comparison curve;
FIG. 2 is a gas turbine governor system improvement model taking into account the "air hammer effect";
FIG. 3 is a graph illustrating IGV opening variation of a gas turbine;
FIG. 4 is a simplified dynamic model of a gas turbine governing system that takes into account the "air hammer effect";
FIG. 5 is a graph of simulated versus measured data for the improved model and the GAST model.
Detailed Description
In order to make the technical solutions and advantages of the present invention clearer, the following describes the technical solutions in the embodiments of the present invention clearly and completely with reference to the drawings in the embodiments of the present invention:
1-5, a method for improving a gas turbine governor system that takes into account the "air hammer effect" includes: 1) establishing a gas turbine speed regulating system model considering the air hammer effect; 2) through reasonable simplification, the gas turbine speed regulator system considering the air hammer effect is analyzed and analyzed in frequency response characteristic; 3) and carrying out simulation verification on the improved gas turbine speed regulating system model. The method comprises the following specific steps:
firstly, establishing a gas turbine speed regulating system model considering the air hammer effect.
The existing gas turbine simulation model has less consideration to the change of parameters such as temperature, air pressure and the like in the system operation process, taking a GAST model as an example, a comparison curve of the simulation result and measured data is shown in FIG. 1. As can be seen from the figure, the simulation result of the existing gas turbine simulation model has a certain error with the actually measured data, and the dynamic change of the active power output of the gas turbine at the initial response stage cannot be reflected.
During actual operation, the gas turbine system calculates a corresponding fuel set command to control the main fuel nozzle opening by measuring the deviation of its actual rotational speed from a set value, and changes the power load of the gas turbine by changing the amount of fuel entering the combustor. Meanwhile, the opening of the Inlet Guide Vanes (IGV) of the gas turbine is also changed. If the output force is required to be increased, the IGV opening is increased, and due to the air hammer effect, the gas in the pipeline is pumped back, so that the ratio of the air and the fuel in the combustion chamber is changed, and the optimal air-fuel ratio cannot be maintained. Then the gas turbine adjusts the air flow in the combustion chamber through a bypass system, so that the air-fuel ratio is recovered to the optimal value, and the stable combustion reaction is maintained, therefore, the 'air hammer effect' can form the 'reverse regulation' phenomenon that the output power is firstly reduced and then increased.
Therefore, the method for controlling the speed of the gas turbine includes the step of adding a response time constant T containing a combustion chamber into the combustion chamber of the original gas turbine speed control system modelCRAnd a first-order differential link of the system is used for reflecting the process of adjusting and correcting the air-fuel ratio in the combustion chamber by a gas turbine bypass system, and then an improved model of the gas turbine speed regulating system considering the air hammer effect is established as shown in fig. 2, wherein an improved post-combustion chamber model is arranged in a dashed frame.
And secondly, analyzing and analyzing the frequency response characteristics of the gas turbine speed regulator system considering the air hammer effect through reasonable simplification.
Because the improved model of the gas turbine speed regulating system considering the 'air hammer effect' has more related parameters and higher order, the actual frequency response analytic analysis and calculation process is too complex, and an analytic solution is difficult to obtain, the analytic analysis is carried out after reasonable simplification of the analytic solution is considered. The specific simplification steps include:
(1) in the fast frequency response, the actual process of the gas turbine opening degree change is that the gas turbine opening degree is fast first and then slow, and when the opening degree reaches the upper limit, the maximum opening degree is kept unchanged, as shown in fig. 3 (a). When the frequency is seriously decreased, the opening degree mu is rapidly increased within 0.5s and is maintained at the upper limit mu0. Since the change time is very short, the IGV opening degree change process can be linearized, and is approximately equivalent to a ramp form, as shown in fig. 3 (b).
(2) In the process of quick frequency response, because the variation of the unit operation temperature is not obvious, the gas turbine can be assumed to keep normal operation in the process, and therefore, a temperature control loop in the model in the step one can be omitted.
Thus, a simplified dynamic model is obtained, as shown in fig. 4, frequency response characteristic analysis of the model is performed according to formula (6) -formula (11), and finally, a system frequency change Δ ω expression is obtained as shown in formula (12), where physical meanings of the parts are respectively: Δ ω1The free response of the system during the non-rotation standby and low-frequency load shedding control is reflected; Δ ω2Reflecting the influence of the release of the spinning reserve caused by the continuous opening of the IGV on the frequency; Δ ω3Reflecting the effect of the back-up constraint on frequency. Thus by observing Δ ω2Time domain solution of Δ ω2(t) the output characteristics of the gas turbine can be analyzed when the system has a frequency modulation requirement. When the system is disturbed, in equation (12)
The term is always a negative value and is consistent with the expression of the water hammer effect in the water turbine, so that the frequency of the power grid is deteriorated, and the phenomenon of 'reverse regulation' that the output power of the gas turbine is increased after being reduced at the initial stage of the quick frequency response is expressed, so that the frequency response characteristic of the dynamic improved model and the analytic description of the 'air hammer effect' under the quick frequency response are obtained.
And thirdly, carrying out simulation verification on the improved gas turbine speed regulating system model.
Take an E-class gas turbine with a rated power of 100MW as an exampleCarrying out simulation calculation based on MATLAB/SIMULINK platform, wherein the disturbance load delta P is 15MW, and the turbine damping coefficient DturbIs 0.3, the temperature limiter gain KTIs 1.0, valve positioner constant T11.0s, fuel system time constant T2The value was 0.2 s; turbine time constant T3The value was 0.2 s; combustion chamber response time constant TCRThe value was 0.28 s. The simulation results of the improved gas turbine speed regulating system model considering the air hammer effect and the traditional GAST model are compared with the measured data. The variation curve of the output power of the unit in each model is shown in figure 5, and the specific data is compared with that in table 1.
TABLE 2 errors between simulation results of different gas turbine model output powers and actual data
The simulation result shows that the simulation result of the dynamic improvement model can reflect the condition of 'reverse regulation' that the output power generated by the influence of the 'air hammer effect' of the gas turbine at the initial stage of frequency regulation is reduced firstly and then increased. And each stage (including initial power falling, rising stage, minimum value of output active power, transient stability value and the like) in the whole frequency response process is basically superposed with the measured data curve, the simulation error is far lower than that of the GAST model, and the dynamic improved model established by the method can better simulate the actual dynamic process of active power change of the gas turbine in the rapid frequency response process.
The method discovers that the 'air hammer effect' in the gas turbine has adverse effect on the frequency response capability of the gas turbine at the initial stage of primary frequency modulation by analyzing the reason of simulation errors of the existing gas turbine simulation model, deeply analyzes the basic structure and the working mechanism of the gas turbine to obtain the reason for forming the 'air hammer effect' of the gas turbine, and provides an improvement measure in a targeted way, namely, the method improves the link of a combustion chamber of the original gas turbine model, and adds a combustion chamber time constant T which reacts the bypass system of the gas turbine to perform auxiliary regulation on the air-fuel ratio of the combustion chamber into the linkCRFurther, a simplified dynamic model is proposed and frequency is performedThe rate response characteristic analysis is convenient for further research on how to avoid the negative influence caused by the 'air hammer effect' and give full play to the overall rapid frequency response advantage of the gas turbine, and provides a basis for guaranteeing the frequency quality in the rapid frequency response in the power system.
Finally, it should be noted that: the above-mentioned embodiments only express the embodiments of the present invention, but not should be understood as the limitation of the scope of the invention patent, it should be noted that, for those skilled in the art, many variations and modifications can be made without departing from the concept of the present invention, and these all fall into the protection scope of the present invention.
Claims (1)
1. A gas turbine speed regulating system model improvement method considering 'air hammer effect' is characterized by comprising the following steps:
firstly, establishing a gas turbine speed regulating system model considering the air hammer effect based on a traditional GAST model;
the method is characterized in that a combustion chamber containing a combustion chamber response time constant T is added into a combustion chamber of an original gas turbine speed regulating system modelCRThe first-order differential link is used for reflecting the process of adjusting and correcting the air-fuel ratio in the combustion chamber by the gas turbine bypass system, and the output function of the improved combustion chamber is shown as a formula (2);
wherein, PcFor combustion chamber output, Δ μ is combustion chamber intake variation, T2Is the combustion chamber fuel time constant, TCRIs the combustor response time constant;
therefore, an improved model of the gas turbine speed regulating system considering the air hammer effect is obtained, and is called a dynamic improved model for short, and the transfer function of the improved model is shown as the formula (3):
in the formula (I), the compound is shown in the specification,vrefrated speed of the speed regulator, K power gain factor, R generator set regulation constant, △ omega generator set speed deviation, T1Is the IGV opening positioner constant, T2Is the time constant of the fuel, TCRIs the combustion chamber response time constant, PeThe method comprises the following steps that (1) the electromagnetic power of a generator set is represented by H, an inertia time constant is represented by D, and a load damping coefficient is represented by D;
secondly, carrying out frequency response characteristic analysis on the dynamic improved model obtained in the first step through reasonable simplification;
(1) in the quick frequency response, the IGV opening degree change process of the inlet guide vane of the gas turbine is subjected to linearization treatment, the approximate equivalence is a slope form, and the functional expression of the function is shown as a formula (4);
where k is the IGV opening degree change speed, t0For the disturbance start time, t1At the time when the IGV opening degree is increased to the upper limit, mu is the opening degree;
(2) in the process of quick frequency response, a temperature control loop in an original model is omitted, a simplified dynamic model of the gas turbine for analysis is obtained after simplification, the simplified dynamic model is called as a simplified dynamic model for short, and a transfer function of the simplified dynamic model is shown as a formula (5):
in the formula, tdThe moment at which the IGV opening reaches a steady state value, v0For the rate of change of IGV opening, TCRRepresenting the combustion chamber response time constant, TFRepresents a fuel time constant;
after obtaining the simplified dynamic model, the method for analyzing the frequency response characteristic of the model specifically comprises the following steps:
assuming that the fault occurs at a time t equal to 0s, the IGV opening degree remains unchanged to μ after the IGV opening degree reaches the steady-state value0And obtaining the variation quantity delta mu of the IGV opening degree according to the IGV linear variation curve in the formula (4) as follows:
Δμ＝v0t-v0(t-td)(t-td) (6)
in the formula, tdThe moment when the IGV opening reaches a steady-state value, (t) represents a unit step function;
the laplace transform is performed on equation (5) to obtain:
therefore, the transfer function of the simplified dynamic model of the gas turbine is shown as the formula (5);
the equation of motion of the rotor of a synchronous generator used in a gas turbine is as follows:
in the formula, delta omega represents the rotating speed deviation of the generator set, H represents the inertia time constant, D represents the load damping coefficient, and delta Pm
Representing gas turbine mechanical power, Δ PeRepresenting gas turbine electromagnetic power;
laplace transform of formula (8) and converting Δ PmSubstitution of(s) solving for Δ ω yields:
in the formula,. DELTA.omega1The free response of the system during the non-rotation standby and low-frequency load shedding control is reflected; Δ ω2Reflecting the influence of the release of the spinning reserve caused by the continuous opening of the IGV on the frequency; Δ ω3Reflecting the effect of the back-up constraint on frequency, wherein:
when the active power of the load in the system generates step disturbance with the disturbance amplitude value of delta PeWhen the temperature of the water is higher than the set temperature,
ΔPe(s)＝ΔPe/s (11)
substituting equation (10) into equation (9) and performing inverse Rayleigh transform can obtain:
in the formula, the physical meanings of each part are respectively as follows: Δ ω1The free response of the system during the non-rotation standby and low-frequency load shedding control is reflected; Δ ω2Reflecting the influence of the release of the spinning reserve caused by the continuous opening of the IGV on the frequency; Δ ω3Reflecting the effect of backup constraints on frequency;
thus by observing Δ ω2Time domain solution of Δ ω2(t) the output characteristics of the gas turbine can be analyzed when the system has frequency modulation requirements; when the system is disturbed, the method is shown in formula (12)
The term is always a negative value and is consistent with the expression of the water hammer effect in the water turbine, so that the frequency of the power grid is deteriorated, and the phenomenon of 'reverse regulation' that the output power of the gas turbine is increased after being reduced at the initial stage of the quick frequency response is expressed, so that the frequency response characteristic of the dynamic improved model and the analytic description of the 'air hammer effect' under the quick frequency response are obtained.
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