Optimization of Vehicle Braking Distance Using a Fuzzy Controller

Abstract

The paper presents the study of an anti-lock braking system (ABS) that has been complemented by a fuzzy controller. The fuzzy controller was used to improve the braking performance of the vehicle, particularly in critical situations, for example, when braking a vehicle on wet road. The controller for the ABS was designed in the MATLAB/Simulink program. The designed controller was simulated on a medium-size vehicle model. During testing, three braking systems were simulated on the vehicle model. We compared the performance of a braking system without an ABS, a system with a threshold-based conventional ABS, and a braking system with the proposed ABS with a fuzzy controller. These three braking systems were simulation tested during braking the vehicle on a dry straight road and on a road with combined road adhesion. A maneuverability test was conducted, where the vehicle had to avoid an obstacle while braking. The results of each test are provided at the end of the paper.

1. Introduction

The increasing number of cars on the roads and the related rising accident rate have brought the concept of road safety to the forefront. The primary safety objective is to protect the health and lives of passengers and minimize the consequences of an accident. In order to achieve this goal, various security features are being applied in vehicles. They can be divided into two groups:

(1)

Active safety features.

(2)

Passive safety features.

One of the most important active safety features includes the braking system of the vehicle, which is considered to be the most important system in the vehicle, as safe stopping or slowing down of the vehicle is one of the ways of accident prevention. Since its introduction, the braking system has undergone numerous improvements, one of them being the application of the ABS. The anti-lock braking system (ABS), which has been developed and implemented from the late 1970s, prevents the wheels from locking during braking of the vehicle, and thereby, allows the driver to maintain control over steering [1]. Although this vehicle safety system has been used for decades, it is constantly being improved using either conventional or intelligent control methods [2].

Several studies have been published that focus on optimizing the vehicle’s braking system using various strategies, both for vehicles with internal combustion engines and electric vehicles. For electric vehicles, the most commonly applied method is regenerative braking control. The authors of paper [3] present regenerative braking control strategy intended to improve braking performance while maximizing braking energy recovery. Application of fuzzy logic rules enables the optimization of regenerative braking in order to achieve better braking performance. This issue is addressed in paper [4], where the rules of fuzzy logic were used to optimize the slip parameter of a sliding mode controller and to thereby achieve a shortening of the vehicle’s braking distance and an increase in the energy efficiency of regenerative braking.

As shown in several studies [5,6,7,8,9,10,11,12], the use of fuzzy logic rules in different ways of controlling the ABS has improved the braking performance of the vehicle in simulations on different road surfaces. Another possible approach to optimizing the braking performance of a vehicle is to use fuzzy logic to optimize the parameters of conventional methods of controlling ABSs. In paper [13], the authors present the achievement of optimal slip rate parameters using fuzzy logic. The presented simulation results prove the improved maneuverability and stability of the vehicle. In paper [14], the authors deal with the optimization of braking properties and shortening of vehicle braking distance using a PID-fuzzy controller with parameter adaptation.

Using fuzzy logic is not the only way to improve the vehicle ABS. The application of artificial neural networks to optimize the rules of the fuzzy controller [15], or as observers, or the implementation of neuro-controllers as such, seem to be suitable alternatives. Comparison of various strategies [16] and selection of the most appropriate method or combination of methods can result in optimization of the ABS performance, and thus, in the improvement of vehicle safety.

Mathematical modeling and simulation are powerful tools in the initial stages of research and in the verification of hypotheses, which is sometimes not possible to implement in practice, be it for safety, for physical or other reasons [17,18]. Therefore, in our design, we used a combination of two simulation tools, MATLAB/Simulink and CarSim, which allowed detailed setting of the vehicle parameters and simulation in different environments. Suitable setting and interlinking with other software, such as MATLAB/Simulink, provides the opportunity of testing vehicle performance in real time. Using the CarSim simulation software enables the verification of vehicle performance in situations where failure could have destructive consequences or even result in loss of life.

2. ABS—Anti-Lock Braking System

In terms of control, the ABS represents a feedback control system that controls brake pressure based on measuring wheel deceleration, and thereby, maintaining wheel slip at optimum value. The basic idea is the use of friction properties of tires on the road surface. As a result of the transmitted longitudinal friction force during braking, deformation and slipping of the individual parts of the tire tread on the road will occur. The result is that during braking, the wheel rotates more slowly than would correspond to the vehicle speed, so it rotates with specific slips. The maximum braking force that a tire is able to transfer onto the concrete road surface is highly dependent on this very specific slip of the wheel. The braking force reaches maximum at the specific value of slip and a further increase in slip reduces the braking force. At maximum value of brake force on normal road surfaces, using normal tires, the specific slip is in the range of 15–20%.

The ABS ensures that even at maximum braking (maximum pressure of the driver on the brake pedal), the specific slip of the wheel does not exceed the said range of 15–20%. This ensures that the vehicle is braked with maximum efficiency, i.e., on the shortest path, plus the transferable lateral forces are in the area of specific slip and are even large enough to allow the correction of direction during braking, in case the vehicle has to get round an obstacle [19,20,21].

2.1. Tire Slip Characteristics

Tire slip characteristics are described by curves that characterize the longitudinal and lateral forces that are transmitted onto the road by the tire at various slips of the tire. The tire slip characteristic shown in Figure 1 presents a typical course of the longitudinal and lateral forces.

The longitudinal forces Fx are the braking and driving forces that a tire can transfer onto the road under various slip values. The lateral forces Fy are forces that a tire transfers onto the road when the vehicle is changing direction. Figure 1 demonstrates the size of the braking (driving) force and the lateral force that a tire can transfer onto the road at various slips [22,23].

Slip λ is calculated according to the equation:

$$\lambda =\frac{v-\omega \times R_{\omega }}{v}=1-\frac{\omega \times R_{\omega }}{v}$$

(1)

where:

v 

is vehicle velocity,

ω 

is angular velocity of tire,

R_ω 

is tire radius.

2.2. Vehicle Braking System

The principle scheme of the braking system used for simulation is shown in Figure 2.

The input variable for the vehicle braking system is the force exerted on the brake pedal by the driver—the pedal force. The force that enters the master cylinder is multiplied by the mechanical transmission brake pedal—ratio.

$$F_{in}=F_{pedal}\times ratio$$

(2)

where:

F_pedal 

is the pedal force,

ratio 

is the mechanical transmission brake pedal,

F_in 

is the force entering the brake booster.

The pressure of the master cylinder is calculated according to the equation:

$$P_{MC}=\frac{F_{MC}}{D_{MC}^2\times \frac{\pi }{4}}$$

(3)

where:

F_MC 

is the master cylinder output force,

D 

is the diameter.

The braking torque depends on the pressure in the brake cylinders and the temperature of the brake disc. The calculation of brake disc temperature uses the input energy from the braking torque, the rotational speed and the energy loss due to cooling. Input energy is dependent on brake torque and wheel speed. Output energy loss due to cooling is dependent on the cooling coefficient as a function of vehicle speed, brake disc weight, specific heat of the wheel as a function of the temperature of the wheel, brake disc temperature and air temperature.

The output heat change (ΔT) is calculated according to:

$$\Delta T=\frac{\left(E_{in}-E_{out}\right)}{M_d\times C_p\left(T_d\right)}$$

(4)

where:

∆T 

is output heat change,

E_in 

is input energy,

E_out 

is output energy,

M_d 

is brake disc weight,

C_p(T_d)

is specific heat of the wheel as a function of the temperature of the wheel.

First order delay is applied to the brake booster. It is a specific time constant that depends on whether the brake pedal is pressed or released. Consequently, the brake pressure is transferred through proportioning valves to the brake cylinders of the wheels as the supply pressure, which together with other parameters generates the mechanical braking torque, as demonstrated in Figure 3. This type of brake system was used for simulation in the CarSim program.

2.3. Basic Model of ABS Control

The input to the ABS controller is the vehicle speed and the equivalent speeds of the individual wheels. These speeds are processed in the controller and slip is evaluated on their basis. The output of the controller are then values from −1 to 1 depending on the speed and slip. This dependence of the output values is shown in

Table 1. ABS controller logic.

Output Values	−1	0	1
Slip	>0.2	0.05–0.2	<0.05
Vehicle speed (km/h)	>5	>5	>5

.

The basic block diagram of the ABS control model used in the CarSim program is shown in Figure 4.

3. Fuzzy Control of ABS

The fuzzy control of the ABS is based on a conventional ABS complemented by a fuzzy controller. The design and the subsequent verification by simulation were carried out in CarSim and MATLAB/Simulink. The designed fuzzy ABS control system consists of three parts:

(1)

Speed controller.

(2)

Fuzzy controller.

(3)

Brake pressure control device.

The block model of the proposed fuzzy control is shown in Figure 5.

The basic parameters for speed controller input were the values of vehicle speed and the speed values of individual wheels. As shown in Figure 6, the output of the speed controller is the value of the vehicle speed multiplied by a constant that modifies the speed value, and this then, becomes the input value to the fuzzy controller. Constant 1/200 was selected on the basis of the defined maximum speed 200 km/h. For tests involving a higher speed, this constant has to be modified. The second output is the ratio of the wheel speed and the vehicle speed. The ratio of vehicle speed and wheel speed can be in the range of values between 0 and 1, where value 0 represents an unblocked wheel (slip 0), and value 1 represents a blocked wheel (slip 1).

The input for the fuzzy controller, shown in Figure 7, is the modified vehicle speed and speeds of the individual wheels.

The range of values for the first input is from 0 to 1. Zero value represents zero vehicle speed and 1 is the highest speed. The range of values for the second input can also be from 0 to 1. In this case, the 0 value represents zero slip and value 1 represents maximum slip value.

The fuzzy controller output value is in the range −1 to 1. Value 1 represents full brake pressure applied to the wheels and −1 represents the application of negative pressure, which means that the wheel is released. The constant output pressure ratio is 20/8 for the front/rear wheels. The constant ratio in favor of the front wheels was chosen in view of the fact that during braking, the vehicle weight is transferred forward and the rear wheels are relieved, which at full braking force would cause blocking of the wheels and subsequent loss of control over the vehicle. This ratio value has been taken as ideal from the CarSim brake pressure control actuator model. Since a fuzzy controller is used to control the braking force, a ratio of 20/8 was chosen as ideal for achieving the largest possible parameter of relative deceleration. The maximum pressure for the simulation was limited to 10 MPa.

Table 2. Table of rules for the fuzzy controller.

Fuzzy Rules		Speed
		VS	S	M	H	VH
Ws/Vs	VS	VN	VN	VN	VN	VN
	S	N	N	N	N	VN
	M	Z	Z	Z	Z	Z
	H	P	P	P	P	P
	VH	VP	VP	VP	VP	VP

VS—very small, S—small, M—middle, H—high, VH—very high, VN—very negative, N—negative, Z—zero, P—positive, VP—very positive.

shows the decision rules for the fuzzy controller setting.

Values of the individual variables for the FIS matrix shown in Figure 8 were selected on the basis of tire slip, which was set at 20%. At such slip, the vehicle is still operable even under heavy braking. A graph showing the dependence between vehicle speed, ratio of vehicle and wheel speed and the resulting pressure is presented in Figure 9.

4. Braking Systems Comparison by Simulation

In order to verify the properties of the proposed ABS with the fuzzy controller, simulation tests were performed in the CarSim and MATLAB/Simulink programs. The simulation tests were performed on a medium-size category vehicle model with independent front and rear suspension. The vehicle had a 7-speed automatic transmission and the maximum engine torque was 534 Nm. During the simulation, the vehicle had 225/60/R18 radial tires.

The tests were performed for a given vehicle in three different combinations. A comparison was made of the vehicle’s braking behavior with a conventional threshold-based ABS, with the proposed ABS with a fuzzy controller designed to slip around 0.2, and with braking without an ABS, where the wheels were locked during braking.

The tests of these systems were carried out for the following operating states:

(1)

Dry road;

(2)

Road with combined adhesion;

(3)

Avoiding an obstacle on the road.

The results of each simulation test are presented below.

4.1. Vehicle Braking Systems Test on Dry Road

In this test, we observed the performance of individual braking systems when the vehicle was braking on a straight dry road. The test was performed for the initial vehicle speeds of 100 and 140 km/h. The results of the braking test for the individual braking systems from speed 100 km/h are shown in Figure 10 and

Table 3. Test results on dry road at speed 100 km/h.

Monitored Value	Without ABS	ABS	Fuzzy ABS
Braking time (s)	6.53	6.73	6.35
Braking distance (m)	103.66	104.80	100.7
Max. rotation in z-axis (deg.)	0.124	0.088	−0.067

.

Figure 11 and

Table 4. Test results on dry road at speed 140 km/h.

Monitored Value	Without ABS	ABS	Fuzzy ABS
Braking time (s)	8.65	8.73	8.30
Braking distance (m)	185.04	182.83	177.08
Max. rotation in z-axis (deg.)	−0.063	−0.052	−0.045

show the results of braking test runs at the speed of 140 km/h.

As seen from the test results, all vehicles were kept in their lane and the vehicle with the fuzzy ABS in both cases had the shortest braking distance.

4.2. Vehicle Braking Systems Test on Road with Combined Adhesion

This test was performed on a straight road with different adhesion values for the right and left sides. The left side of the vehicle was on the road with adhesion value 0.2, and the right side of the vehicle on the road with adhesion value 0.5. In general, such combination of surface adhesion represents an icy road. The test was performed for the initial vehicle speeds of 100 and 140 km/h. The results of the braking test for the individual braking systems for speed 100 km/h are shown in Figure 12 and

Table 5. Test results on road with combined adhesion at speed 100 km/h.

Monitored Value	Without ABS	ABS	Fuzzy ABS
Braking time (s)	10.5	9.73	9.6
Braking distance (m)	150.52	143.23	141.78
Max. rotation in z-axis (deg.)	−873.24	−3.21	−2.14

.

Figure 13 and

Table 6. Test results on road with combined adhesion at speed 140 km/h.

Monitored Value	Without ABS	ABS	Fuzzy ABS
Braking time (s)	13.23	15.55	12.43
Braking distance (m)	272.21	263.83	247.56
Max. rotation in z-axis (deg.)	−1372.30	−141.29	−2.83

show the results of braking test runs at speed 140 km/h.

As demonstrated by the test results, a vehicle without an ABS slipped into skidding on the icy road and at both speeds ended off the road. The vehicle with a conventional ABS also skidded at the speed of 140 km/h and finished off turned in the opposite direction. The vehicle with the fuzzy ABS was the only one able to remain on the road and had the shortest braking distance at both speeds.

4.3. Vehicle Braking Systems Test When Avoiding an Obstacle on the Road

In this test, we observed the ability of the vehicle to maneuver on a dry road during braking, employing the individual braking systems. During this test, the vehicle was avoiding an obstacle during braking. The obstacle was simulated by delimiting the route using cones, as illustrated in Figure 14.

The test was performed for the initial vehicle speeds of 100 and 130 km/h. Because it was important to avoid an obstacle in this test, instead of vehicle rotation in z-axis, the shift of the vehicle from the defined route was under observation. The results of this test for individual braking systems at speed 100 km/h are shown in Figure 15 and

Table 7. Maneuverability test on dry road at speed 100 km/h.

Monitored Value	Without ABS	ABS	Fuzzy ABS
Braking time (s)	6.78	6.95	6.58
Braking distance (m)	105.10	107.52	103.03
Max. deviation of the vehicle (m)	3.76	0.2	0.01

.

As seen from the vehicle maneuverability tests during braking at speed 100 km/h, the vehicle with the fuzzy ABS was able to copy the desired trajectory with most accuracy. A vehicle without an ABS would not be able to maneuver when braking, it would just move straight forward with locked wheels and would hit the obstacle.

Figure 16 and

Table 8. Maneuverability test on dry road at speed 130 km/h.

Monitored Value	Without ABS	ABS	Fuzzy ABS
Braking time (s)	8.15	8.8	8.58
Braking distance (m)	162.93	172.66	172.43
Max. deviation of the vehicle (m)	3.52	0.34	0.19

show the results of test runs at a speed of 130 km/h.

As demonstrated in the vehicles’ maneuverability test during braking at speed 130 km/h, the vehicle with the fuzzy ABS was able to copy the desired trajectory most accurately of all the vehicles. The vehicle with the conventional ABS showed problems in copying the desired trajectory at this speed. The vehicle without an ABS would not be able to maneuver when braking, it would just move straight forward with locked wheels and would hit the obstacle the same as before.

5. Discussion

The CarSim and MATLAB/Simulink programs were used to verify the design of the vehicle’s fuzzy ABS controller. The main goal of this work was to improve the braking properties of the vehicle by using fuzzy logic for the brake pressure regulator. We have chosen three types of operating states for testing the fuzzy ABS. The first was to test the vehicle’s braking behavior on dry roads at speeds of 100 and 140 km/h.

In this test, the shortest braking distance was the main criterion for assessing the quality of the proposed fuzzy ABS controller. The value of the braking distance of a vehicle with a classic ABS was taken as a reference value for comparison, as we wanted to improve the properties of this ABS by using a fuzzy logic.

As can be seen from the comparison in

Table 9. Comparison of parameters when braking on dry road.

Test on Dry Road	Max. Rotation in Z-Axis (deg.)	Braking Time (s)	Braking Distance (m)
100 km/h
ABS	0.088	6.730	104.800
Fuzzy ABS	0.067	6.350	100.700
Without ABS	0.124	6.530	103.660
140 km/h
ABS	0.052	8.730	182.830
Fuzzy ABS	0.045	8.300	177.080
Without ABS	0.063	8.650	185.040

 reference value,  better value,  worse value.

and Figure 17, the ABS with the fuzzy controller achieved better properties with all monitored parameters, i.e., directional stability, braking time and braking distance than when using ABS without a fuzzy controller.

In the second test, we observed the braking behavior of the vehicle on the road with different adhesion on the right and left side. In this test, in addition to monitoring the shortest braking distance, the ABS’s ability to maintain the vehicle in a straight line when braking was also monitored. Again, as in the previous test, the reference values were obtained by simulating a conventional ABS. As can be seen from the comparison shown in

Table 10. Comparison of parameters when braking on road with combined adhesion.

Test on Dry Road	Max. Rotation in Z-Axis (deg.)	Braking Time (s)	Braking Distance (m)
100 km/h
ABS	3.210	9.730	143.230
Fuzzy ABS	2.140	9.600	141.780
Without ABS	873.240	10.500	150.520
140 km/h
ABS	141.290	15.550	263.830
Fuzzy ABS	2.830	12.430	247.560
Without ABS	1372.300	13.230	272.210

 reference value,  better value,  worse value.

and Figure 18, the ABS with the fuzzy controller achieved better results also in this case.

In the last test, we observed the behavior of the vehicle during braking and simultaneously avoiding an obstacle in the roadway. In this test, we monitored the vehicle’s ability to maintain within the prescribed path, and the reference value in this test was the value of the maximum deviation from the prescribed path for a vehicle with a conventional ABS. As

Table 11. Comparison of parameters during avoiding an obstacle on the road.

Test on Dry Road	Max. Deviation of the Vehicle (m)	Braking Time (s)	Braking Distance (m)
100 km/h
ABS	0.200	6.950	107.520
Fuzzy ABS	0.010	6.580	103.030
Without ABS	3.760	6.780	105.100
140 km/h
ABS	0.340	8.800	172.660
Fuzzy ABS	0.190	8.580	172.430
Without ABS	3.520	8.150	162.930

 reference value,  better value,  worse value.

and Figure 19 demonstrates, although the vehicle without ABS had the shortest braking distance at speed 130 km/h, this vehicle was not able to avoid the obstacle and continued straight on, which would eventually cause the vehicle to collide with the obstacle.

Based on the previous results, we made a percentage comparison of the improvement in the performance of the ABS with the fuzzy controller compared to the classic ABS. The result of this comparison is shown in

Table 12. Percentage comparison of the improvement of key indicators.

Monitored Value	Improvement of the Measured Parameter (%)
	100 km/h	140 km/h (130 km/h)
Test on dry road—Braking distance	3.91	3.14
Test on road with combined adhesion—Braking distance	1.01	6.17
Test on road with combined adhesion—Max. rotation in z-axis	33.33	98.00
Maneuverability test on dry road—Max. deviation of the vehicle	95.00	44.12

.

It is shown in Table 11 that by using a fuzzy controller for the vehicle’s ABS, we can achieve up to a 6% reduction in braking distance when braking on a road with combined adhesion. In the simulations, however, we achieved much more significant results in the directional stability of the vehicle or when avoiding an obstacle.

6. Conclusions

In this paper, we presented the design of an ABS with a fuzzy controller. Integrating fuzzy control into a conventional ABS has resulted in achieving improved maneuverability of the vehicle when braking on different surfaces and in different situations at high speed. As can be seen from the simulation results presented in the discussion, in all tests, the ABS with a fuzzy controller achieved better results than the conventional ABS. Comparing the key parameters in Table 12, we can see that by using a fuzzy controller, we achieved a reduction in the braking distance compared to the conventional ABS by 6% in the test on the road with combined adhesion. We achieved significantly better results mainly in the directional stability of the vehicle during the test on a road with a combined surface and the test of maneuverability.