Improving the Stability of the Passenger Vehicle by Using an Active Stabilizer Bar Controlled by the Fuzzy Method

. The rollover phenomenon is a particularly dangerous problem. This phenomenon occurs when the driver travels at high speed and suddenly steers. Under the inﬂuence of centrifugal force, the body vehicle will be tilted and cause the wheels to lift oﬀ the road. To solve this problem, the method of using an active stabilizer bar has been proposed. The active stabilizer bar is controlled automatically by a previously designed controller. The performance of the active stabilizer bar depends on the selected control method. Previous research often only used a half-car dynamics model combined with a linear single-track dynamics model to simulate the vehicle’s oscillation. In addition, most of the research focuses only on the use of linear control methods for the active stabilizer bar. Therefore, the performance of the stabilizer bar is not guaranteed. This paper focuses on establishing the model of spatial dynamics combined with the nonlinear double-track dynamics model that fully describes the vehicle’s oscillation most accurately. Besides, the fuzzy control method is proposed to control the operation of the hydraulic stabilizer bar. This is a completely novel model, and it is suitable for the actual traveling conditions of the vehicle. Also, simulations are done based on diﬀerent scenarios. The results of the paper showed that the values of the roll angle, the diﬀerence in the vertical force at the wheels, and the displacement of the unsprung mass were signiﬁcantly reduced when the vehicle used the active stabilizer bar, which is controlled by an intelligent control method. Therefore, the stability and safety of the vehicle have been guaranteed. This result will be the basis for performing other more complex research in the future.


Introduction
Today, the automotive industry is developing very strongly.Compared to before, the quantity and quality of the vehicles have also been greatly improved.When the vehicle is on the road, many unexpected situations happen.ese situations can cause instability and be unsafe for the driver.In particular, the phenomenon of rollover is extremely dangerous, and it can directly affect life and cargo.
Usually, there are two types of accidents that are mentioned, including turnover and rollover.A turnover occurs when the vehicle travels at a high speed and impacts an obstacle.At that time, the roof of the vehicle will be in contact with the road surface, and the wheels will point up.Actually, the turnover phenomenon rarely occurs in practice.In contrast, the phenomenon of rollover often occurs with great frequency.e vehicle is rolled over, which means that the side of the vehicle will be in contact with the road, the wheels facing the same direction.When the driver is traveling at high speed and suddenly steers, the rollover phenomenon may occur [1].e main cause of this phenomenon is the appearance of the centrifugal force, which is proportional to the square of the vehicle's velocity.In addition, vehicles that are bulky in size are also very easy to fall into this situation when traveling at high speeds.Besides, some other factors, such as lateral wind, and external force, can also affect this problem [2].
Because of the danger of the rollover phenomenon, automotive manufacturers are always trying to improve this situation.
ere are several solutions to limit this phenomenon, such as using the active suspension system, integrated air suspension system, and hydraulic antiroll system, in which the method of using the stabilizer bar is more appropriate [3].e passive stabilizer bar is used on most vehicles today.Its structure is quite simple, with high durability and low cost [4].erefore, its performance is not good.In many dangerous situations, the passive stabilizer bar is not able to meet the requirements set in terms of vehicle stability and safety.To improve this problem, the active stabilizer bar is equipped to replace the conventional passive stabilizer bar.
e active stabilizer bar is controlled automatically by a predesigned controller based on signals received from sensors around the body of the vehicle.e structure of the active stabilizer bar (using a hydraulic motor) is introduced as shown in Figure 1.
e two arms of the bar (1) are connected to the wheel hub.e back of the bar can be rotated flexibly based on two rubber bearings (2) that are attached to the chassis (3).When the body of the vehicle is tilted and other parameters of the vehicle also change, the sensor will record this change and send it to the ECU.en, the ECU will send a current signal to the actuator of the stabilizer bar to control the opening and closing of the internal valves.At this time, high-pressure hydraulic oil is supplied to the actuator (5) through the pipeline (4).e actuator of the stabilizer bar is a hydraulic motor, the operation of which is based on the opening and closing of the valves, which are controlled by an electric current signal.When the hydraulic motor rotates, the impact force F S is generated at the ends of the lever arm, which is attached to the wheel hub.ese two force values are opposite and act on the unsprung mass to bring the vehicle body back to a stable position.e performance of the active stabilizer bar depends entirely on the controller, which is designed.
erefore, the choice of the control method for the active stabilizer bar is extremely important.
Recently, there has been quite a bit of research on the problem of rollover and methods to improve this situation.According to [5], the rollover phenomenon occurs when the vehicle changes direction suddenly at high speed.e centrifugal force that is produced by the lateral acceleration will cause the vehicle body to tilt [6].At this time, the wheels tend to separate from the road surface [7].If the vertical force at the wheel reaction approaches zero, the vehicle can roll over at any time.is has been demonstrated by Anh in his research [8].To evaluate the rollover phenomenon, Phanomchoeng and Rajamani introduced the concept of the rollover index R [9].However, this is only true when both wheels on the same side are lifted off the road, which means that the value of the roll index R will approach "1."In general, rollover problems are extremely complex and dangerous.
In order to improve this situation, the option of using an active suspension system was proposed by Yim et al. [10].Besides, Nguyen and Hoang also proposed equipping the stabilizer bar on the vehicle in their research [11].e stabilizer bar can be fitted on other family cars, buses, or large vehicles.Its effect is positive [12].In addition, the stabilizer bar can be combined with several other mechatronic systems to support the vehicle's stability.is idea was proposed by Yim et al. [13].Passive stabilizer bars are widely used on many vehicles.It is made up of an elastic steel bar with a circular, hollow inside [14].In [15], Nguyen proposed a new method for calculating the impact force of the passive stabilizer bar on the unsprung mass.However, the effect of the passive stabilizer bar is still not very good.In some dangerous cases, the vehicle can still roll over.erefore, the active stabilizer bar is recommended for use.
It is very important to control the operation of the active stabilizer bar.Zulkarnain et al. designed a linear controller LQG for the stabilizer bar [16].In this paper, Zulkarnain only uses the half-car dynamics model combined with the conventional linear single-track dynamics model.Similarly, Vu et al. also introduced the linear parameter varying control law (LPV) for their stable bar model [17].However, the actuator that is described in [17] is the hydraulic piston.Besides, the active stabilizer bar that uses a hydraulic motorshaped actuator has also been researched and introduced.In  [19].In which, the influence of the parameters has been described more clearly.Recently, Nguyen introduced the PID control rules for hydraulic stabilizer bars [20].For this paper, Nguyen used the model of spatial dynamics, which fully describes the effect of oscillations when a vehicle is traveling on the road.Because the vehicle is a very complex mechanical system, if conventional linear control methods are used, the performance of the stabilizer bar is not guaranteed.erefore, more complex control methods are needed to control the operation of the hydraulic stabilizer bar.
Instead of just using the conventional linear control method, Zulkarnain et al. proposed the use of the composite nonlinear feedback control method (CNF) to improve the efficiency of the system.According to [21], the CNF controller is designed to increase the damping ratio when the system output approaches the desired threshold and avoids overshoot.Based on the idea of minimizing the error of the control signal to the lowest threshold, Konieczny et al. proposed a sliding mode control algorithm (SMC) to control the operation of the antiroll system [22].
e hydraulic actuator of the system is located on both sides of the wheel.Its efficiency is very high.Besides, intelligent control methods also bring stable effects to the vehicle's antiroll system.In [23], Muniandy et al. introduced the fuzzy PI-PD law for the controller.e parameters of the PID controller will be self-tuned by the fuzzy controller based on the error of the output signals.e results of the study have been 2 Complexity proven through the simulation and experiment process, which is mentioned in the paper.Again, this content is expressed more specifically through [24].Obviously, the vehicle's stability can be further improved by using intelligent control methods.Based on this idea, Marzbanrad et al. also proposed a fuzzy control algorithm using two modes [25].However, this research has not addressed the effect of actuators on overall system performance.Recognizing the shortcomings of previous studies, Dawei et al. published a paper with the content towards controlling the operation of hydraulic actuators [26].In this paper, the characteristics of the active stabilizer bar are shown.Besides, experiments were also conducted to prove the results of the paper.Recently, some research on controlling the active antiroll system has also been carried out and published [27,28].
Overall, the results of these researches are very positive.
Intending to improve the stability and safety of the vehicle when steering, this paper focuses on calculating and simulating the oscillation of a vehicle equipped with a hydraulic stabilizer bar in dangerous situations. is is different from previous studies that used only half-car dynamics models integrated with the linear single-track dynamics model.
is paper establishes a spatial dynamics model that describes the vehicle oscillations fully.Besides, the tire influence is also shown through the Pacejka tire model.en, the control model of the actuator is given with fuzzy control algorithms.
e contents of the paper are presented below.

Dynamic Model.
To evaluate the vehicle body oscillation accurately, a spatial dynamics model that includes 7 degrees of freedom was used in this research (Figure 2).Separating the sprung mass (m) and the unsprung mass (m ij ), the equations describing the oscillation of each part are shown below: where a y is the lateral acceleration in global coordinates, Lateral acceleration (a y ) is what causes the vehicle's body to be tilt, which leads to a rollover phenomenon. is value is determined based on a nonlinear double-track dynamics model as shown in Figure 3.
where v x � v cos β and v y � v sin β.
In this research, the influence of external force (wind force) is not considered.erefore, the value of F i can be ignored.
To be able to determine equations ( 1) and ( 2), the forces and moments at the wheel need to be calculated specifically.
ere are many methods used to calculate longitudinal force (F x ), lateral force (F y ), and moment (M z ). is paper uses the Complexity Pacejka tire model to calculate the above values [29].e parameters of slip ratio and slip angle at the wheel are shown in the following equations: where D x,y,z ; C x,y,z ; B x,y,z ; E x,y,z ; S vx,vy,vz ; and S hx,hy,hz are coefficients of the tire model.Also, s x is the slip ratio, and α is the slip angle of the tire.

Hydraulic Motor Model.
e schematic diagram of the hydraulic actuator is shown in Figure 4. e hydraulic actuator consists of a rotating motor that is controlled by valves, which are widely used in engineering fields.In particular, the changes in the volume of liquid inside the motor are not constant; they vary in a discontinuous depending on the rotational speed of the motor shaft.
e hydraulic actuator is controlled by the current signal i(t) [30].When current is supplied, the valve inside the hydraulic motor will travel.e displacement of the servo valve X v depends on current signal i(t).It is shown in the following equation: e linearization equation describes the flow of fluid ΔQ through the valve as follows: Assuming that V 1 � V 2 � 0.5V t and ΔP � P 1 − P 2 , the flow of the liquid can be calculated as follows: where θ m is the rotation angle of the motor shaft.
From equations ( 5) and ( 6), where e torque balance equation at the output of the motor shaft is as follows: After the actuator's dynamics model has been established, the controller needs to be designed to be able to control the actuator's operation appropriately.

Designing the Controller.
As discussed in the previous section, there are many methods used to control the operation of the hydraulic motor.Each method has its advantages and disadvantages.In this paper, the intelligent control method with fuzzy law is used to control the process of generating force F S for the hydraulic actuator.Unlike traditional linear or nonlinear control methods, the fuzzy control law is an intelligent control method.is method makes it possible to achieve a high level of system performance.In particular, complex systems like in this research can use the fuzzy control method.Besides, the fuzzy control method helps ensure the efficiency of the system, while the uncertainty factors change continuously.
e fuzzy controller consists of three main stages: fuzzification, rules, and defuzzification.e fuzzification stage helps convert the explicit values (the signal received from the Signal A ′ � fuzz(x ′ ). (9) e second stage of the controller is the rules.At this time, the linguistic value of the fuzzy set will be converted to an explicit value based on the defined basis set.e algorithm diagram for this stage is given as shown in Figure 5.According to this figure, positions from A 1 to A 9 are the limits of the controller's input parameter.
e third stage of the controller is the defuzzification process. is process is performed based on the control rules that have been established for the controller.For each limit position, the output parameter will be set specifically.
erefore, if the input value is not at the limit position, this controller can easily interpolate its position.From there, the corresponding output value can be reasonably calculated.

Simulation Conditions.
e process of simulating the vehicle's oscillations when traveling is performed based on two types of dangerous steering, including J-turn steering and fishhook steering (Figure 6) [20].For each type of steering, the vehicle's speed will be shown in two cases, including case 1: v 1 � 60 km/h and case 2: v 2 � 90 km/h.In these situations, the vehicle can use the passive stabilizer bar (Pa), the active stabilizer bar controlled by the linear controller (PC), the active stabilizer bar controlled by the fuzzy controller (FC), or not use the stabilizer bar (none).
e technical parameters of the vehicle and the hydraulic actuator are given in Table 1 [31].

J-Turn
Steering.With the J-turn steering type, the results of two simulation processes are given below.
(1) Case 1: v 1 � 60 km/h.In this case, the car travels at a steady speed: v 1 � 60 km/h. is is the actual speed value, suitable for most traveling conditions on the road.Figure 7 shows the change in the roll angle of the sprung mass over time.e maximum value of the roll angle can reach φ max � 5.77 °when the vehicle does not use the stabilizer bar.If the passive stabilizer bar is used, this value will decrease slightly, reaching 5.35 °. is change is not much.However, when the hydraulic stabilizer bar is equipped instead of the passive stabilizer bar, the change is significant.e maximum value of the roll angle of the sprung mass decreased sharply, to only 4.90 °and 4.59 °, respectively, in the situation of using the PID controller and the fuzzy controller for the stabilizer bar.
is change is dependent on the impact force, which is generated by the stabilizer bar.e graph in Figure 8 shows the impact force values of the stabilizer bar.According to this result, the value of the impact force of the stabilizer bar at the front axle will be larger than that of the rear axle.However, this difference is small.e value of the impact force when the vehicle uses the hydraulic stabilizer bar controlled by the fuzzy controller is the largest.It can be up to 2,569.7 N and 2,486.9N, respectively, for each axle.For the situation of a vehicle using the hydraulic stabilizer bar controlled by the conventional linear controller, the value of the impact force will be smaller.It only reaches 2,036.9N and 1,951.7 N, respectively.e value of the impact force in the other case (mechanical stabilizer bar) is the smallest.It is only about 30% more than in the first case.Obviously, if the value of the impact force F S is too small, the vehicle's stability support effect is not guaranteed.erefore, the use of the fuzzy controller in this research has brought very positive results.
e peak of the impact force value appears at different times corresponding to the situations.Firstly, the delay of the control process can cause this situation.Secondly, because the actuator's inertia force is large, it will continue to operate for a short time afterward.However, this does not affect the safety of the vehicle.
e vertical force at the wheel is a value that characterizes the stability of the vehicle.If this value is too small or it even tends to approach zero, the rollover phenomenon may occur.Figure 9 shows the change in the value of the vertical force in this simulation case.According to the results obtained from these graphs, the value of the vertical force of the wheel at position (21) tends to decrease the most. is is completely consistent with reality.eir minimum value is 3,486.9N, 3,044.3N, 2,508.2N, and 1,715.0N, respectively.When the vehicle uses the hydraulic stabilizer bar, the difference in the vertical reaction of the two wheels at each ΔF zi bridge will be controlled stably.For the vehicle using the hydraulic stabilizer bar that is controlled by a PID controller, the difference value of ΔF zi will be smaller than that of the conventional passive stabilizer bar.If the fuzzy controller is used to replace the PID controller, this change occurs much more strongly.Because the force generated by the actuator is quite large, the difference between ΔF zi will tend to be opposite to that of the other three cases.
e change in the vertical force's value at the wheel ΔF zij has a direct effect on the displacement of the unsprung mass e ij (Figure 10).When the value of F zij approaches zero, that is, the value of e ij approaches the maximum limit, lateral instability will occur.
is can even lead to the rollover phenomenon.If the vehicle uses the hydraulic stabilizer bar controlled by a fuzzy controller, the maximum value of displacement of the unsprung mass is only 3.45 mm.Conversely, if the vehicle is not equipped with the stabilizer bar, this value can go up to 14.01 mm.Obviously, the hydraulic stabilizer bar that is controlled by the fuzzy controller works very well compared to other cases.
In this case, the vehicle only moves at an average speed of v 1 � 60 km/h.erefore, the instability of the vehicle is still not much.In order to demonstrate the performance of the fuzzy controller that controls the hydraulic stabilizer bar's operation, it is necessary to perform simulations in a more hazardous case.
(2) Case 2: v 2 � 90 km/h.In this case, the vehicle moves at very high speeds and may fall into dangerous situations.Similar to Case 1, the outputs include the roll angle, the impact force, the vertical force at the wheel, and the displacement of the unsprung mass.6 Complexity In Figure 11, the change in the roll angle over time is shown.Obviously, these values have increased a lot compared to Case 1.If the vehicle does not use the stabilizer bar, the maximum roll angle can reach φ max � 8.36 °.When the passive stabilizer bar is used, this value drops slightly, to only 7.78 °.If the hydraulic stabilizer bar that is controlled by the designed controller is fitted, the value of the roll angle of the vehicle body will be greatly reduced.At this moment, it is  Complexity only about 7.17 °and 6.73 °, respectively, with the PID controller and fuzzy controller.e difference in the roll angle between using the fuzzy controller and not using the stabilizer bar is quite large, φ max � 1.63 °. e value of the impact force of the stabilizer bar is shown in the graph in Figure 12.In fact, the value of the force generated from the hydraulic stabilizer bar that is controlled by the fuzzy controller is larger than the other two cases.Its maximum value can be up to 3,715.2N and 3,597.8N, respectively, for each axle.Meanwhile, the stabilizer bar controlled by the linear controller can only produce lower forces, 2,945.5 N and 2,824.8N, respectively.At the same time, the value of the passive stabilizer bar is very low, only about 1,232.5 N and 1,089.1 N If the F S impact force is too low, the vehicle's stability will not be improved.
e values for the vertical force at the wheel F zij are extremely important.It is an indication of possible lateral instability.In the case of the vehicle traveling at a high speed, v 2 � 90 km/h, this change is very large.If the vehicle does not have a stabilizer bar, the minimum value of the vertical force at the wheel is only about 649.0 N (Figure 13). is is a very small value, and it is close to the dangerous threshold.If the vehicle uses the passive stabilizer bar, this value has increased.It can reach 1,790.4N. Besides, the active stabilizer bar can improve this problem more optimally.When the vehicle is equipped with the hydraulic stabilizer bar controlled by the linear controller, this value increases to 2,586.4N. In addition, if the PID controller is replaced by a fuzzy controller, the minimum value of the vertical force at the wheel can reach 3,205.9N, which is the safety threshold of the vehicle when moving.
e hydraulic stabilizer bar generates a large impact force F S to ensure that the change in the vertical force at the wheel is minimal.erefore, the displacement of the unsprung mass e ij will also be improved.Figure 14 shows that the maximum value of the displacement of the unsprung Complexity mass is only 5.20 mm.To achieve this value, the vehicle needs to be equipped with a hydraulic stabilizer bar that is controlled by the fuzzy controller.If the linear controller is used for the hydraulic stabilizer bar, this value will be larger, about 8.52 mm.In the case of vehicles using only the conventional mechanical stabilizer bar, this value is quite large, up to 13.03 mm.Conversely, if the vehicle does not use the stabilizer bar, the maximum value of the displacement of the unsprung mass can be as high as 20.31 mm; lateral instability can occur at any time.

Fishhook Steering.
Compared to the normal J-turn steering type, the fishhook steering can cause many dangerous situations for the vehicle.In this section, two travel conditions will also be performed to simulate and evaluate the results of the research.
Vehicles often use the fishhook steering type when drivers want to change lanes or avoid obstacles.e value of the steering acceleration when the vehicle uses this type of steering is very high.erefore, the results obtained from this situation will be very different from the first situation.
(1) Case 1: v 1 � 60 km/h.When the vehicle travels at a speed of v 1 � 60 km/h and performs fishhook steering, the roll angle of the sprung mass will change as shown in Figure 15.In the first phase, the value of the roll angle is not large because the steering angle is quite small.In contrast, this value in the second phase is quite large.e maximum value of the roll angle φ max can reach 7.07 °if the vehicle does not use the stabilizer bar.Besides, if the hydraulic stabilizer  Complexity bar that is controlled by the fuzzy controller is equipped, this value is only 6.01 °.Compared to the above situation, this value has been considerably reduced.
e value of the impact force that is produced by the stabilizer bar F S also changes continuously.
e fuzzy controller that was established in this research enables the hydraulic stabilizer bar to generate a larger torque than the other two cases.Based on the results from Figure 16, this can reach 3,145.1 N and 3,056.0N for each axle, respectively.Meanwhile, the conventional linear controller can only produce smaller torque, only about 2,637.0N and 2,543.7 N.
e value of the vertical force at the wheel changes following the law of the fishhook steering angle.Figure 17 shows this change when the vehicle uses the hydraulic stabilizer bar, which is controlled by the fuzzy controller.In the first phase, when the impact force of the actuator is small, the change in the value of the vertical force is completely compatible with the roll angle of the sprung mass.In the second phase, when the impact force generated by the actuator is large, the change in the value of the vertical force at the wheel has the opposite direction to the roll angle of the vehicle body.e minimum value of the vertical force is 2,435.8N, which is obtained at the wheel position (22).Besides, the minimum value of the vertical force at the wheel when the vehicle uses the PID controller for the stabilizer bar is 2,036.3N. In the case of a vehicle equipped with only the passive stabilizer bar, the value of the force F zij is only about 2,151.1 N is value is slightly larger than the vehicle using the active stabilizer bar controlled by a linear controller.Obviously, in many special cases, the linear controller cannot be used to its full potential.If the vehicle does not have a stabilizer bar, the value of the vertical force at the wheel drops sharply.It is only 1,178.0N. A dangerous situation can occur.12 Complexity e displacement of the unsprung mass e ij varies depending on the value of the vertical force at the wheel F zij .
is value is too large, which also means that the vehicle falls into a state of lateral instability.Even so, the rollover phenomenon can happen.In the case of the vehicle using the fuzzy controller to control the hydraulic stabilizer bar operation, the displacement of the unsprung mass was significantly reduced.Its maximum value is only 9.37 mm (Figure 18).Meanwhile, if the vehicle uses the active stabilizer bar, which is controlled by a PID controller, or uses the passive stabilizer bar, their values are equivalent, 11.71 mm and 10.98 mm.erefore, the linear controller is completely ineffective in this case.In particular, the displacement of the unsprung mass is very large, reaching 17.18 mm if the vehicle does not have a stabilizer bar.In the case of danger, the value of the impact force generated by the stabilizer bar is also much larger than in other cases.According to Figure 20, the maximum value of the impact force generated by the fuzzy controller can be up  When the vehicle is traveling at high speed and using this type of steering, the wheels tend to separate from the road surface.At time t � 3.38 s, the value of F z22 will equal zero if the vehicle has no stabilizer bar.If the vehicle only uses the conventional mechanical stabilizer bar, this value is only about 1,162.6 N (Figure 21).When the vehicle is equipped with the hydraulic stabilizer bar controlled by a PID controller, this value decreases slightly, reaching 947.3 N. In fact, the PID controller cannot solve complex problems like this.
e efficiency of the stabilizer bar that uses a linear controller is only comparable to that of the passive stabilizer.However, the fuzzy controller that has been designed in this paper can assist the vehicle in this dangerous situation.e minimum value of the vertical force at the wheel can be reached at 1,693.8 N. us, the rollover phenomenon can be greatly improved.
Similar to the cases simulated above, the displacement of the unsprung mass will depend on the value of the vertical force at each wheel.rough the graphs in Figure 22, their maximum values are 13.58 mm, 17.93 mm, and 16.60 mm, respectively, corresponding to specific technical conditions.
With the above results obtained, the stabilizer bar has a noticeable effect when equipped on the vehicle.In addition, the fuzzy controller, which controls the hydraulic stabilizer bar operation, can help improve the stability and safety of the vehicle when traveling at high speed.

Conclusions
e rollover phenomenon is a very dangerous problem.It can happen at any time in many unexpected situations.To overcome this, the active stabilizer bar is recommended for use in vehicles.e active stabilizer bar that is simulated in this paper is a hydraulic actuator, which is controlled automatically through the previously established controller.
e performance of the stabilizer bar depends on the control method that has been designed and selected.
is paper proceeds to establish the model of the spatial dynamics of the vehicle combined with the nonlinear double-track dynamics model that fully describes the factors affecting the vehicle's oscillation.Besides, the dynamics model of the hydraulic actuator is also clearly shown.e fuzzy control law is proposed to control the operation of the hydraulic actuator.e control law is selected based on actual experience, through previous researches.
e results of the paper show that when the vehicle uses the active stabilizer bar, parameters such as the roll angle, the difference in vertical force at the wheel, the displacement of the unsprung mass, and so on are all reduced significantly.According to the results of the simulation process, if the active stabilizer bar is controlled by the fuzzy controller, the maximum roll angle of the vehicle can be reduced by more than 10% compared to using the passive stabilizer bar.Also, the value of impact force that is generated by the active stabilizer bar is 2.8 times that of the corresponding mechanical stabilizer bar.Besides, the fuzzy control law also shows outstanding advantages compared with other conventional control methods.As a result, the vehicle's stability and safety have been improved.Compared with other control algorithms, the fuzzy control algorithm is quite complex.e control process relies heavily on fuzzy rules, which are used for the controller.It is very difficult to establish the fuzzy rule correctly.
is depends on the experience of the expert as well as some experiments and simulations that have been done before.In some special cases, the fuzzy controller's performance is still not good.In the future, fuzzy control algorithms can be combined with some complex algorithms such as SMC, ANN, and so on to improve the efficiency of the system.Gravitational acceleration (m/s 2 ) h φ : Distance from the center of gravity to roll axis (m) h θ : Distance from the center of gravity to pitch axis (m) J x : Moment of inertia of the x-axis (kg m 2 ) J y : Moment of inertia of the y-axis (kg m 2 ) J z : Moment of inertia of the z-axis (kg m 2 ) l i : Distance from the center of gravity to front/rear axle (m) m: Sprung mass (kg) M: Total mass (kg) [18], Varga et al. presented the LQ control law for this model.Based on Varga's ideas, Tan also published research on active stabilizer bars that use hydraulic motors with linear control methods

( 2 )
Case 2: v 2 � 90 km/h.Fishhook steering at the high speed of v 2 � 90 km/h is extremely dangerous.en, the problem of rollover can happen at any time.e change of roll angle over time is shown in Figure 19.Indeed, the maximum roll angle φ max is very large.If the vehicle did not have the stabilizer bar, the vehicle would have rolled over at time t � 3.38 s.At the time the vehicle rollover phenomenon occurs, the maximum roll angle of the vehicle only reached φ max � 7.54 °.If the vehicle uses the stabilizer bar, this phenomenon can be improved.Besides, the threshold for the roll angle of the vehicle may be increased.

Complexity
Lateral acceleration (m/s 2 ) e ij :Displacement of the unsprung mass (m) F Cij : Force of the damper (N) F Kij : Force of the spring (N) F KTij : Force of the tire (N)F Si : Impact force (N) F xij : Longitudinal force (N) F yij : Lateral force (N) F i :External force (N) c i :Distance from the center of gravity to external force (m) g:

18
Complexity m ij : Unsprung mass (kg) t wi : Half of the track width front/rear axle (m) v x : Longitudinal velocity (m/s) v y : Lateral velocity (m/s) z: Displacement of the sprung mass (m) CNF: Composite nonlinear feedback ECU: Electronic control unit HSB: Hydraulic stabilizer bar LQR: Linear quadratic regulator LQG: Linear quadratic Gaussian LQ: Linear quadratic LPV: Linear parameter varying PID: Proportional integral derivative SMC: Sliding mode control.

Table 1 :
e technical parameters.