1. Introduction
Clean, renewable energy generation, such as water, wind, and solar energy, is an effective means to cope with energy problems and environmental management issues. The proportion of clean, renewable energy in energy consumption will continue to increase. The development and full use of clean, efficient renewable energy and renewable energy generation are increasingly widely concerned by the international community [
1,
2]. At the same time, in some areas, there are hydroelectric power and wind power access to the same line because the wind speed is unstable; even if the wind turbine controller itself can reduce the impact of wind speed instability on the power, the wind power still has instability, causing some disturbance to the system frequency. Frequency is an important indicator of power quality and it is an essential requirement for power system operation to ensure that the system frequency is up to standard. Frequency is closely related to the rotational speed of the generator and in hydropower plants, the hydraulic turbine governing system (HTGS) is used to regulate the rotational speed of the unit. The HTGS is a complex control system integrating hydraulic, mechanical, and electrical components [
3,
4,
5]. Its primary task is to regulate the active power output of the hydro-generator set according to the constant change of the load of the power system, minimize the influence of environmental disturbance and load disturbance, and maintain the frequency of the set within the specified range, which plays an indispensable role in maintaining the safe, stable, and economic operation of the hydropower plant. However, the inertia of the flowing water in the penstock, the nonlinear characteristics of the hydro-generator set, and the load disturbance of the power system that occurs at any time make the control of the HTGS very difficult [
6,
7].
The problem of nonlinear modeling and control of the HTGS has been a topic of interest and has been studied in various aspects by related scholars. In the nonlinear modeling of the HTGS, a multi-machine differential equation model suitable for control design and stability analysis is established in [
8]. Under different operating conditions of the HTGS, a non-linear mathematical model of the HTGS, considering the fractional derivative and time delay and during load rejection using non-linear dynamic transfer coefficients, is established respectively [
9,
10]. In the nonlinear control of the HTGS, proportional-integral-derivative (PID) control is the main controller of this system because of its simple structure and easy implementation. Some scholars have used different intelligent optimization algorithms to optimally adjust the parameters of the system controller under multiple objectives to improve the performance of the PID controller [
11,
12,
13]. However, inevitably, the PID control method is not very adaptable to different working conditions nor resistant to disturbances. Therefore, many researchers have adopted some advanced intelligent control theories to optimize the control effect on the HTGS [
14,
15,
16,
17]. Nonlinear PID control, sliding mode control, model predictive control, Hamilton energy function method, and other nonlinear control applications have been applied to HTGS control problems, and all have achieved positive control results [
18,
19,
20,
21]. However, the above nonlinear modeling and control methods require a more in-depth mathematical foundation that is not easily mastered by most engineers and technicians.
In the field of control, Takagi–Sugeno (T-S) fuzzy control is a classical method that is easy to master [
22]. It has been empirically and theoretically proven that T-S fuzzy models can approximate nonlinear systems with arbitrary accuracy by local state information and fuzzy rules [
23]. In the literature [
24], a robust analysis of a T-S fuzzy controller for the nonlinear system was carried out, showing that the robust fuzzy controller works well under the influence of model uncertainty, time lag, and large perturbations. The literature [
25] shows the effectiveness of T-S fuzzy controllers based on the Lyapunov function and linear matrix inequality (LMI) for suppressing system disturbances. A systematic procedure of fuzzy control system design that consists of fuzzy model construction, rule reduction, and robust compensation for nonlinear systems was proposed in the literature [
26], which can provide a reference for solving the fuzzy control design problem of nonlinear systems. Scholars can linearize the nonlinear HTGS mathematical model and combine it with appropriate fuzzy rules to construct a T-S fuzzy model based on which the controller is designed. A T-S fuzzy controller based on the fractional-order system robust theory [
16] and finite-time stability theory was designed, respectively [
27]. As we all know, the nonlinear term in the HTGS is mainly the power angle of the generator. However, the establishment of the T-S fuzzy model in [
16,
27,
28] was based on the rotational speed as a prerequisite and the physical meaning of the fuzzy model established in this way is not clear. In the process of system response, the way that the T-S fuzzy system fits the original nonlinear system is not discussed in detail and in-depth in these papers.
With the large-scale grid connection of wind power and photovoltaic power generation, more and more factors affect the stable operation of the hydro-generator set. When the hydro-generator set is disturbed by random load, the state trajectory, in terms of power angle and rotational speed, exhibits instability, affecting the unit’s stable operation. The system’s stability is inseparable from the control parameters, which places high demands on the HTGS control parameters. Various parameter optimization algorithms currently have their advantages and disadvantages. Genetic algorithm (GA) has an excellent global search capability but poor local search capability and is prone to local minima [
29]. Particle swarm optimization (PSO) has favorable searchability in the early iteration stage but poor searchability in the late stage [
30]. Gravitational search algorithm (GSA) has a strong global search capability, but its local search capability is insufficient and it is prone to the phenomenon of oscillation of optimal values. Therefore, there is an urgent need to study the parameter optimization techniques applicable to an HTGS controller.
From the above discussion, we were motivated to propose an optimal T-S fuzzy controller based on a suitable parameter optimization algorithm and study the control strategy for a nonlinear HTGS. The main contributions of this paper are reflected in the following: (1) the T-S fuzzy model of the HTGS was established with generator power angle as the precondition; (2) the mixed controllers were integrated into T-S fuzzy control under the parallel distributed compensation (PDC); (3) these mixed controllers were optimized using the modified hybrid particle swarm optimization and gravitational search algorithm integrated with chaotic maps (CPSOGSA) optimization algorithms to improve the performance of T-S fuzzy control; (4) the fuzzy control obtained by the optimization solution was applied to the HTGS.
The rest of this paper is organized as follows:
Section 2 provides models of each component of the HTGS in incremental form, including the model of hydraulic turbine, penstock, actuator, and the nonlinear model of generator, which together form the nonlinear model of the HTGS.
Section 3 demonstrates the T-S fuzzy local linearization of the nonlinear model of the HTGS through which three local linear models were obtained, and introduces three fuzzy control rules, which are linked together with fuzzy membership functions to form a T-S fuzzy controller. In
Section 4, using the LMI toolbox in MATLAB, we propose our design of the mixed
controller for the fuzzy linear model introduced in
Section 3.
Section 5 presents a chaotic map-based PSOGSA optimization algorithm (CPSOGSA) as it was applied to parameter optimization of the mixed
controller. A simulation study was conducted and is shown in
Section 6 to demonstrate the advantages of the new approach. Finally, concluding remarks are presented in
Section 7.
2. System Description
An HTGS is a non-linear, multi-input, multi-output complex control system integrating hydraulic, mechanical, and electrical components, consisting of a hydraulic turbine, penstock, generator, and governor [
10,
31,
32,
33]. It has an important feature: its characteristics are related to the steady-state operating point. The structural diagram of the HTGS studied in this paper is shown in
Figure 1. The upper part of
Figure 1 is the general physical structure of the hydropower plant, which consists of upper and downstream reservoirs, hydrogenerator set, and penstock. The generator in it is driven by a hydroturbine. In order to maintain the power quality, it is necessary to keep the rotational speed of the generator stable. This part of the task is accomplished by adjusting the opening of the guide vanes by the actuator controlled by the governor. The lower part of
Figure 1 is a block diagram of the HTGS that this paper focuses on, where the control quantity is the actual value, the power angle is the incremental value, and the remaining quantities are the relative values of the increments. To study the control strategy of the controller, each component of the HTGS needs to be modeled separately [
20,
23].
2.1. Hydraulic Turbine Model
For Francis turbines, five parameters are usually used to describe them: torque
, flow rate
, water head
, rotational speed
, and guide vane opening
. The torque and flow rate of the turbine are related to the water head, rotational speed, and guide vane opening [
34]. Assuming an approximately linear relationship between the guide vane opening and the actuator stroke
, the steady-state characteristics of the hydraulic turbine are now widely used to approximate the dynamic processes of the HTGS.
is the torque rating,
is the flow rating,
is the rotational speed rating,
is the water head rating, and
is the maximum value of the actuator stroke. For the steady-state operating point (
), the nonlinear model of the hydraulic turbine in incremental form is obtained as shown in Equation (1) [
35]:
where
is the relative value of torque increment,
is the relative value of flow increment,
is the relative value of speed increment,
(subscript * indicates per unit value),
is the relative value of actuator stroke increment, and
is the relative value of head increment.
In studying the small disturbance problem, it can be linearized near the steady-state operating point. Expanding Equation (1) to Taylor series at the steady-state operating point and omitting the higher-order terms above the second order, a linearized model expressed in six transfer coefficients is obtained as Equation (2) [
36]:
where,
,
, and
are the transmission coefficients of turbine torque to rotational speed, stroke, and water head under steady-state conditions, respectively;
,
, and
are the transmission coefficients of turbine flow rate to rotational speed, stroke, and water head under steady-state conditions, respectively.
According to Equation (2), the linearized model of the hydraulic turbine is plotted in the form of the block diagram shown in
Figure 2, where
is the transfer function of the penstock.
2.2. Penstock Model
When the rotational speed changes in unstable conditions, the hydraulic turbine guide vane opening changes automatically under the action of the governor.
Water strike is a common phenomenon in this process, which is caused by the inertia of flowing water, compressibility, and the elasticity of the penstock. When the guide vane opening is increased, the increase in flow rate causes the working water pressure of the turbine to decrease. In the case of a large water hammer, the amount of torque decrease caused by the water pressure decrease exceeds the amount of torque increase caused by the flow increase, and the torque temporarily decreases. This counter-conditioning effect has a very negative impact on the dynamic characteristics of the HTGS. Thus, it is essential to analyze the dynamic characteristics of the penstock [
37].
For the HTGS in minor fluctuation conditions, when the penstock length is less than 800 m, the compressibility of the flowing water and the elasticity of the penstock wall can be ignored. The penstock can be represented by the transfer function shown as Equation (3) [
3]:
where
is the flowing water inertia time constant.
The corresponding differential equation model of the penstock is given as:
2.3. Generator Model
In this paper, the second-order model of the generator is shown as Equation (5), including the equation of rotor rotational motion and the equation characterizing the relation between power angle and rotational speed [
16]:
where
is the inertia time constant (s) of the unit,
is the electrical angular velocity p.u.) of the generator,
is the mechanical torque (p.u.) of the turbine,
is the electromagnetic torque (p.u.) of the generator,
is the damping coefficient,
is the power angle of the generator, and
is taken to be 30° under steady-state conditions, i.e.,
, and
changes when disturbance occurs;
is the synchronous electrical angular velocity.
The relationship between the generator’s output power and the power angle is also considered. Assuming that the generator q-axis transient electromotive force
remains constant during the disturbance and ignoring the stator winding losses, the electromagnetic power
(p.u.) supplied to the grid by the convex-pole synchronous generator is obtained as Equation (6) [
38]:
where
is the bus voltage (p.u.);
,
are the sum of reactances (p.u.) in the d- axes and q-axes, respectively.
The generator model is now transformed into incremental form and the relationship between the correlated variables is as follows:
Because the electrical angular velocity is generally considered to vary little during the analysis of minor disturbances under grid-connected operation conditions,
is taken so that:
Substituting Equations (7)–(10) into Equation (5) yields the second-order model of the generator in incremental form, as shown in Equation (11) [
38]:
where
is the per unit of the electromagnetic power increment, which is derived as follows:
2.4. Actuator Model
The actuator of the HTGS generally adopts the electro-hydraulic follower system, whose function is to amplify the control signal and provide the execution power to convert the weak electrical control signal from the controller into a mechanical displacement signal that can drive the hydraulic turbine guide vane. When the nonlinear factors are ignored, the actuator can be simplified to a first-order inertial element [
14], whose transfer function [
39] can be expressed as:
where
is the actuator response time constant.
The corresponding differential equation model of the actuator [
36] is given as:
To avoid the system scattering phenomenon caused by the actuator saturation, we designed the actuator with anti-integration saturation in the simulation. The integration stops when the actuator’s output reaches saturation and the sign of the control quantity is the same as the sign of the actuator’s output.
2.5. HTGS Model
The transfer function from
to
which derived from
Figure 2, is shown as Equation (15):
Substituting Equation (3) into Equation (17) yields:
The inverse Laplace transform of Equation (18) yields:
Substituting Equation (14) into Equation (19) yields:
Equations (11), (14) and (20) constitute the model of the HTGS, which is shown as Equation (21):
where
is a nonlinear term on the variable
, whose expression is shown in Equation (12).
3. T-S Fuzzy Local Linearization and Controller Proposal
The T-S fuzzy model has a wide range of applications in control design and analysis of nonlinear systems [
40], which is easy to understand, convenient, and flexible for engineering applications. Its main feature is described by some If-Then fuzzy inference rules; each inference rule represents the dynamics of the local area linear model and then the individual local linear models are linked with fuzzy membership functions to obtain the overall fuzzy nonlinear model, which in turn achieves the purpose of control design for nonlinear uncertain systems [
28]. In this section, the T-S fuzzy local linearization of the nonlinear model of the HTGS is carried out to obtain three local linear models and the three fuzzy control rules are proposed. They are linked together with fuzzy membership functions to form a T-S fuzzy controller.
,
,
, and
are selected as state variables and Equation (21) is transformed into the matrix form of the HTGS model as follows:
where
where
is the coefficient matrix of the control input.
. Considering the boundedness of (, taking d = ), the T-S fuzzy model of the system is established. When , then , , ; when , then , ; when , then , and . This leads to the following three T-S fuzzy rules.
3.1. Fuzzy Local Linearization
Fuzzy rule 1: If
is about 0, then fuzzy model 1 is shown as Equation (27):
where
at this point,
Fuzzy rule 2: If
is about
, then fuzzy model 2 is shown as Equation (32):
where
at this point,
Fuzzy rule 3: If
is about
, then fuzzy model 3 is shown as Equation (37):
where
at this point,
3.2. T-S Fuzzy Controller
Design the following three fuzzy control rules:
where
,
, and
are the feedback gain matrices of the three locally stabilized controllers:
The T-S fuzzy state feedback controller of the design governor according to the parallel distribution compensation (PDC) algorithm is shown as Equation (44):
where
,
, and
are the membership degrees of
to the first, second, and third fuzzy rules, respectively, and
. The degree of membership functions are shown as follows:
The degree of membership functions are shown schematically in
Figure 3:
4. Design of the Mixed H2/H∞ Controller
For the fuzzy linear model
in
Section 3, designing a state feedback controller
is the problem to be solved in this section.
Equation (48) is the linear model corresponding to the fuzzy rule
:
where
is the disturbance signal, including the disturbance caused by the disturbance torque and the modeling error; take
as the disturbance signal coefficient matrix;
and
are the defined dynamic performance evaluation signals; and
,
,
,
,
, and
are the dimensionally appropriate weighting matrices. Optimizing the weighting matrix is the difficult part of the mixed
control. There is no well-established theory on how to select the weighting matrix. Generally, the main diagonal element has more influence on the controller and several attempts are needed to choose the optimal weighting matrix.
Define the correlation coefficient matrix in this paper as follows:
where
are the weighting coefficients and the intelligent optimization algorithm will be used in
Section 5 to find the optimal weighting coefficients several times and select the combination of weighting coefficients with optimal performance.
The system in Equation (48) can be represented as the control system in
Figure 4. We aimed to design a controller with a feedback coefficient
such that the closed-loop system is asymptotically stable and the
norm of the closed-loop transfer function
from
to
does not exceed a given upper bound
, ensuring that the closed-loop system is robust to the uncertainty perturbations entering the system from
, and such that the
norm of the closed-loop transfer function
from
to
does not exceed a given upper bound
, ensuring that the system performance measured with the
norm is at a good level [
41].
From Equation (48), the augmented controlled object based on the mixed
control theory can be obtained as Equation (55):
The linear matrix inequality (LMI) toolbox in MATLAB provides a solution for the mixed
control problem, which can solve the feedback coefficient
of the mixed
state feedback controller
shown in
Figure 3. The closed-loop system can be made stable for all parameter perturbation and external disturbances and the following performance specifications can be achieved.
That is the
norm minimization, which is the peak minimization of the maximum singular value of the system frequency response. Then, the LMI is used to complete the design objective set in Equation (56), i.e., if and only if there exists a symmetric matrix
, such that:
That is the
norm minimization. Similarly, to accomplish the design goal shown in Equation (58), the inequality shown in Equation (59) is satisfied if and only if there exist symmetric matrices
and
.
- 3.
Mixed -optimal design.
Every state feedback controller in the T-S fuzzy system of the HTGS makes the closed-loop poles of the system lie in the left half-open complex plane and minimizes
[
42]. Then, the above two sets of conditions add up to the nonconvex optimization problem with variables
,
,
, and
. For tractability in the LMI framework, we sought a single matrix
that enforces all two objectives. The change of variable
allows the following suboptimal LMI problem for multi-objective state feedback control to be solved.
Minimize
by
,
,
, and
satisfying Equation (60):
From the optimal solution
,
,
,
, the corresponding every state feedback gain
is given by Equation (61):