Multi-Objective Optimization Study of Regenerative Braking Control Strategy for Range-Extended Electric Vehicle

: Currently, the researches on the regenerative braking system (RBS) of the range-extended electric vehicle (R-EEV) are inadequate, especially on the comparison and analysis of the multi-objective optimization (MOO) problem. Actually, the results of the MOO problem should be mutually independent and balanced. With the aim of guaranteeing comprehensive regenerative braking performance (CRBP), a revised regenerative braking control strategy (RRBCS) is introduced, and a method of the MOO algorithm for RRBCS is proposed to balance the braking performance (BP), regenerative braking loss e ﬃ ciency (RBLE), and battery capacity loss rate (BCLR). Firstly, the models of the main components related to the RBS of the R-EEV for the calculation of optimization objectives are built in MATLAB / Simulink and AVL / Cruise. The BP, RBLE, and BCLR are selected as the optimization objectives. The non-dominated sorting genetic algorithm (NSGA-II) is applied in RRBCS to solve the MOO problem, and a group of the non-inferior Pareto solution sets are obtained. The simulation results show a clear conﬂict that three optimization objectives cannot be optimal at the same time. Then, we evaluate the performance of the proposed method by taking the individual with the optimal CRBP as the ﬁnal optimal solution. The comparation among BP, RBLE, BCLR, and CRBP before and after optimization are analyzed and discussed. The results illustrate that characteristic parameters of RRBCS is crucial to optimization objectives. After parameters optimization, regenerative braking torque works early to increase braking energy recovery on low tire-road adhesion condition, and to reduce the battery capacity loss rate at the expense of small braking energy recovery on the medium tire-road adhesion condition. In addition, the results of the sensitivity analysis show that after parameter optimization, RRBCS is proved to perform better road adaptability regarding the distribution of solutions. These results thoroughly validate the proposed approach for multi-objective optimization of RRBCS and have a strong directive to optimize the control strategy parameters of RBS.


Introduction
The range-extended electric vehicle (R-EEV) can greatly improve its driving range through the auxiliary power unit, so as to solve the range anxiety from consumers. As one of the main working modes, the energy recovered with regenerative braking system (RBS) provides an effective approach so as to greatly improve energy efficiency of R-EEV. Research shows that about 20%-50% or more of the driving energy is lost during the braking process [1][2][3][4]. The characteristic parameters of regenerative braking control strategy (RBCS) are crucial to optimization objectives. Thereby, the parameters optimization study on RBCS and the comprehensive regenerative braking performance (CRBP) analysis have gotten a lot of attention and deserve to be studied. Present research mainly focuses on the balance and optimization between braking performance and braking energy recovery of RBS. Literature [5] focuses on the control algorithm of the braking energy regeneration system of an electric bus in a safety-critical driving situation. A sliding-mode controller based on the exponential reaching law for the antilock braking system is developed in the literature [6]. With the aims of regeneration efficiency and braking safety, three different control strategies are studied in [7,8]. Similar studies are available in the literature [9][10][11][12], which develop the braking torque allocating method to improve braking performance and energy regeneration. In the literature [13], a hierarchical control strategy is proposed, taking battery aging into consideration to ensure vehicle braking safety, recover more energy, and protect components from aging. Cooperative regenerative braking control is proposed in the literature [14] to recover optimal braking energy while guaranteeing the vehicle lateral stability. The longitudinal friction between the road and the tires is estimated and controlled while optimizing regenerative braking in the literature [15]. Moreover, battery is the most sensitive component in the powertrain of R-EEV, so a large regenerative charging current (RCC) can cause damage to the battery and reduce its service life [13].
However, current control strategies pay less attention to the impaction of regenerative braking current (RCC) on the battery state of health and rarely follow this essential characteristic of the multi-objective problem. How to optimize the control parameters of RBCS is mostly derived from the developer's experience. In addition, how to realize a better balance among the braking performance (BP), regenerative braking loss efficiency (RBLE), and battery capacity loss rate (BCLR) is also studied inadequately. The objective of the regenerative braking control strategy for an R-EEV is to guarantee the comprehensive performance of the R-EEV during operation, and this comprehensive performance includes braking performance and regenerative braking efficiency. Meanwhile, the strategy ensures RCC is always within the controllable range and battery state of charge (SoC) is close to the pre-set value, which not only protects the battery pack, but also gets the ideal braking comprehensive performance.
In this paper, a revised regenerative braking control strategy (RRBCS) based on the optimal slip ratio (OSR) with the rate and shape of battery RCC considerations is introduced. In addition, a multi-objective parameters optimization method (MOOM) for RRBCS is proposed to match the BP, RBLE, and BCLR in the power system of R-EEV. The major contribution and innovations of this work are mainly reflected in the following three aspects: (1) It adds the analysis of RCC's impact on battery health, and the adverse effects of RCC on battery health are reduced by the designed "conservative braking mode" in RRBCS. (2) The conflict among BP, RBLE, and BCLR are revealed and analyzed through the proposed MOOM, and the control parameters' optimal solution of RBCS is obtained based on the global optimization algorithm instead of deriving from the developer's experience to get a better balance among three objectives. (3) The sensitivity analysis of the optimal solution on various tire-road adhesion conditions is carried out to validate the effectiveness and feasibility of the proposed MOOM.
The rest of this paper is organized as follows: In Section 2, the RRBCS is given and revised allocation logic of the regenerative braking work-point is introduced. Section 3 describes the MOO problem, and the non-dominated sorting genetic algorithm (NSGA-II) is selected to solve the MOO problem and simulation model is built. In addition, the simulation test and non-inferior Pareto solution sets are given. In Section 4, a series of simulation tests on various tire-road adhesion conditions are carried out to validate the effectiveness and feasibility of the proposed MOOM. This is followed by the conclusion in the final section.

Process of the Regenerative Braking Control Strategy
A medium R-EEV driven by the front axle was used in this study to design RBCS. As shown in Figure 1, the RBS consists of two systems: the hydraulic braking system and electric braking system. In the hydraulic braking system, the pressure adjustment at the wheel master cylinder can be achieved Appl. Sci. 2020, 10, 1789 3 of 20 by modulating valves. Every wheel is equipped with the modulating valves so that each wheel can be controlled by the hydraulic braking controller independently.
Appl. Sci. 2020, 10, x FOR PEER REVIEW 3 of 19 In the hydraulic braking system, the pressure adjustment at the wheel master cylinder can be achieved by modulating valves. Every wheel is equipped with the modulating valves so that each wheel can be controlled by the hydraulic braking controller independently. The RRBCS studied in this paper was divided into three levels: the highest level (coordinate regenerative braking controller), the second level (fuzzy controller), and the third level (actuator), as shown in Figure 2. The highest level contains the hydraulic braking controller and the electric controller in RBS, whose main task is to coordinate regenerative braking torque and hydraulic braking torque. The second level contains the double fuzzy logic controller (DFLC), which is different from the fuzzy controller in [16][17][18][19]. Additionally, it can adjust the braking torque in real time to control the slip ratio of the front and rear wheels to achieve a good follow-up of the target slip ratio. The regenerative and hydraulic braking system without a controller is included in the third level, whose task is to realize the braking process under the controller's supervision. The RRBCS studied in this paper was divided into three levels: the highest level (coordinate regenerative braking controller), the second level (fuzzy controller), and the third level (actuator), as shown in Figure 2.

Realization of Braking Torque Based on OSR
Appl. Sci. 2020, 10, x FOR PEER REVIEW 3 of 19 In the hydraulic braking system, the pressure adjustment at the wheel master cylinder can be achieved by modulating valves. Every wheel is equipped with the modulating valves so that each wheel can be controlled by the hydraulic braking controller independently. The RRBCS studied in this paper was divided into three levels: the highest level (coordinate regenerative braking controller), the second level (fuzzy controller), and the third level (actuator), as shown in Figure 2. The highest level contains the hydraulic braking controller and the electric controller in RBS, whose main task is to coordinate regenerative braking torque and hydraulic braking torque. The second level contains the double fuzzy logic controller (DFLC), which is different from the fuzzy controller in [16][17][18][19]. Additionally, it can adjust the braking torque in real time to control the slip ratio of the front and rear wheels to achieve a good follow-up of the target slip ratio. The regenerative and hydraulic braking system without a controller is included in the third level, whose task is to realize the braking process under the controller's supervision. The highest level contains the hydraulic braking controller and the electric controller in RBS, whose main task is to coordinate regenerative braking torque and hydraulic braking torque. The second level contains the double fuzzy logic controller (DFLC), which is different from the fuzzy controller in [16][17][18][19]. Additionally, it can adjust the braking torque in real time to control the slip ratio of the front and rear wheels to achieve a good follow-up of the target slip ratio. The regenerative and hydraulic braking system without a controller is included in the third level, whose task is to realize the braking process under the controller's supervision.

Realization of Braking Torque Based on OSR
As shown in Figure 3a, the motor reaches the allowable braking force upper limit T mot_max at point A. The braking strength corresponding to point A is defined as the threshold value of low brake strength Z a_l , and the braking strength corresponding to point B is defined as the threshold value of high brake strength Z b_h . The braking force distribution should follow the ideal braking force distribution curve (I curve), so that the front and rear wheels are locked at the same time to fully use the road surface adhesion. The I curve is related to the vehicle's actual mass and static axle load, which are variable in daily driving. The ideal braking force distribution is obtained by adjusting the slip ratio of the front and rear wheels. To realize the braking torque control, the relationship between the front and rear axle braking force and the slip ratio is derived as shown in Figure 3b. According to the ECE R13-H braking regulations, the rear wheels must have a certain braking force to maintain vehicle's stability and braking efficiency when the front and rear wheels are locked. The relationship between the rear wheels' minimum braking force and the front wheels' braking force is the M curve, as shown in the Figure 3a.
Appl. Sci. 2020, 10, x FOR PEER REVIEW 4 of 19 As shown in Figure 3a, the motor reaches the allowable braking force upper limit Tmot_max at point A. The braking strength corresponding to point A is defined as the threshold value of low brake strength Za_l, and the braking strength corresponding to point B is defined as the threshold value of high brake strength Zb_h. The braking force distribution should follow the ideal braking force distribution curve (I curve), so that the front and rear wheels are locked at the same time to fully use the road surface adhesion. The I curve is related to the vehicle's actual mass and static axle load, which are variable in daily driving. The ideal braking force distribution is obtained by adjusting the slip ratio of the front and rear wheels. To realize the braking torque control, the relationship between the front and rear axle braking force and the slip ratio is derived as shown in Figure 3b. According to the ECE R13-H braking regulations, the rear wheels must have a certain braking force to maintain vehicle's stability and braking efficiency when the front and rear wheels are locked. The relationship between the rear wheels' minimum braking force and the front wheels' braking force is the M curve, as shown in the Figure 3a. W is the correction factor with the tire-road adhesion condition consideration. Together with Za_l and Zb_h, they can be calculated as follows: where Tmot_max is the motor allowable braking force upper limit; m is the total mass of vehicle; R is the wheelbase; i is the transmission ratio; μmax is the peak tire-road adhesion coefficient (PTAC); μw_l is the threshold value of the low tire-road adhesion coefficient (TAC); μw_h is the threshold value of the high TAC; mf is the front axle mass distribution coefficient; l is the front and rear axle wheelbase; and hg is the centroid height.
The distribution values of the slip ratio in three braking stages are described as follows: (1) Full regenerative braking of the "OA" stage W is the correction factor with the tire-road adhesion condition consideration. Together with Z a_l and Z b_h , they can be calculated as follows: where T mot_max is the motor allowable braking force upper limit; m is the total mass of vehicle; R is the wheelbase; i is the transmission ratio; µ max is the peak tire-road adhesion coefficient (PTAC); µ w_l is the threshold value of the low tire-road adhesion coefficient (TAC); µ w_h is the threshold value of the high TAC; m f is the front axle mass distribution coefficient; l is the front and rear axle wheelbase; and h g is the centroid height.
The distribution values of the slip ratio in three braking stages are described as follows: (1) Full regenerative braking of the "OA" stage (2) Hydraulic braking compensation of the "AB" stage (3) Regenerative braking and hydraulic braking coordination of the "BC" stage Considering the difference of the braking torque between the front and rear wheels, the DFLC for the front and rear wheels is designed to ensure OSR tracking control target values effectively. As shown in Figure 4, the demand slip ratio s req (t) of the front and rear wheels can be obtained from the demand braking strength calculation and s osr (t) can be output in real time. If s req (t) < s osr (t), the OSR control target s csr (t) is defined as s csr (t) = s req (t). Otherwise, s csr (t) is defined as s csr (t) = s osr (t), and it generally occurs on the low tire-road adhesion condition or the braking strength demand is too large.
Considering the difference of the braking torque between the front and rear wheels, the DFLC for the front and rear wheels is designed to ensure OSR tracking control target values effectively. As shown in Figure 4, the demand slip ratio sreq(t) of the front and rear wheels can be obtained from the demand braking strength calculation and sosr(t) can be output in real time. If sreq(t) < sosr(t), the OSR control target scsr(t) is defined as scsr(t) = sreq(t). Otherwise, scsr(t) is defined as scsr(t) = sosr(t), and it generally occurs on the low tire-road adhesion condition or the braking strength demand is too large. There are two inputs in the fuzzy logic controller of the front wheels and the two inputs are the difference between the real slip ratio and the target slip ratio ef(t), and the slip rate change rate s f(t), respectively. The output is the regenerative braking force adjustment value of the front wheel ΔTf _e(t), the hydraulic braking force adjustment value of the front wheel ΔTf_m (t), respectively. There are two inputs in the fuzzy logic controller of the rear wheels and the two inputs are the difference between the real slip ratio and the target slip ratio er(t), and the slip rate change rate s ŕ(t), respectively. The output is the hydraulic braking force adjustment value of the rear wheel ΔTr_m(t). There are two inputs in the fuzzy logic controller of the front wheels and the two inputs are the difference between the real slip ratio and the target slip ratio e f (t), and the slip rate change rateś f (t), respectively. The output is the regenerative braking force adjustment value of the front wheel ∆T f _e (t), the hydraulic braking force adjustment value of the front wheel ∆T f_m (t), respectively. There are two inputs in the fuzzy logic controller of the rear wheels and the two inputs are the difference between the real slip ratio and the target slip ratio e r (t), and the slip rate change rateś r (t), respectively. The output is the hydraulic braking force adjustment value of the rear wheel ∆T r_m (t).

Braking Work-Point Switching Logic of RRBCS
The objective of the regenerative braking control strategy for R-EEV is to guarantee the comprehensive regenerative braking performance during operation. The allocation logic of the Appl. Sci. 2020, 10, 1789 6 of 20 braking work-point is crucial to the efficiency of RRBCS [20]. In this paper, the braking work-point in RRBCS was divided into five types, as shown in Figure 5a,b.
Appl. Sci. 2020, 10, x FOR PEER REVIEW 6 of 19 The objective of the regenerative braking control strategy for R-EEV is to guarantee the comprehensive regenerative braking performance during operation. The allocation logic of the braking work-point is crucial to the efficiency of RRBCS [20]. In this paper, the braking work-point in RRBCS was divided into five types, as shown in Figure 5a,b. Allocation logic of the braking work-point in RRBCS is as follows: (1) If Zreq_l < Za_l and μmax < μμ_l, the braking work-point should follow the I curve on work-point 1 (WC1) to protect the wheel from locking and slipping. (2) If Zreq_l < Za_l and μmax > μμ_l, the braking work-point should follow the "OA" curve on work-point 2 (WC2) to protect the wheel from locking and slipping. Regenerative braking torque provides sufficient braking torque at the front wheel and the rear wheel hydraulic force is 0.
(3) If Zb_h > Zreq_m > Za_l and μmax < μμ_h, the braking work-point should follow the I curve on work-point 3 (WC3) to protect the wheel from locking and slipping due to the fact that larger Zreq_m exists. (4) If Zb_h > Zreq_m > Za_l and μmax > μμ_h, the braking work-point should follow the "AB" curve on work-point 4 (WC4). The motor will provide its maximum regenerative torque applied at the front wheels, and the insufficient part of the driving braking torque would be compensated by the hydraulic braking system. (5) If Zreq_h > Zb_h, the braking work-point should follow the I curve on work-point 5 (WC5).
In order to control the fluctuation range of the battery SoC and prevent the RCC from being too large to affect the battery life, the regenerative charging work-point of the control logic is referenced in the battery SoC characteristics for conservative adjustments. The strategy makes the SoC close to the pre-set value, which not only protects the battery state of health, but also fully uses the battery pack power. The "conservative braking mode" is a conservative adjustment of the original braking work-point of RBCS. In order to meet the above performance requirements, the braking work-point switching logic needs to be adjusted in real time according to the vehicle status. With SoC characteristics as the switching limit, the braking work-point switching logic is shown in Figure 6. The battery SoC value at the k instant SoC (k) and the k + 1 instant SoC (k+1) were detected, respectively. The SoC change rate kSoC and change rate discrimination value kcr were calculated as follows: Allocation logic of the braking work-point in RRBCS is as follows: (1) If Z req_l < Z a_l and µ max < µ µ_l , the braking work-point should follow the I curve on work-point 1 (W C1 ) to protect the wheel from locking and slipping. (2) If Z req_l < Z a_l and µ max > µ µ_l , the braking work-point should follow the "OA" curve on work-point 2 (W C2 ) to protect the wheel from locking and slipping. Regenerative braking torque provides sufficient braking torque at the front wheel and the rear wheel hydraulic force is 0. (3) If Z b_h > Z req_m > Z a_l and µ max < µ µ_h , the braking work-point should follow the I curve on work-point 3 (W C3 ) to protect the wheel from locking and slipping due to the fact that larger Z req_m exists. (4) If Z b_h > Z req_m > Z a_l and µ max > µ µ_h , the braking work-point should follow the "AB" curve on work-point 4 (W C4 ). The motor will provide its maximum regenerative torque applied at the front wheels, and the insufficient part of the driving braking torque would be compensated by the hydraulic braking system. (5) If Z req_h > Z b_h , the braking work-point should follow the I curve on work-point 5 (W C5 ).
In order to control the fluctuation range of the battery SoC and prevent the RCC from being too large to affect the battery life, the regenerative charging work-point of the control logic is referenced in the battery SoC characteristics for conservative adjustments. The strategy makes the SoC close to the pre-set value, which not only protects the battery state of health, but also fully uses the battery pack power. The "conservative braking mode" is a conservative adjustment of the original braking work-point of RBCS. In order to meet the above performance requirements, the braking work-point switching logic needs to be adjusted in real time according to the vehicle status. With SoC characteristics as the switching limit, the braking work-point switching logic is shown in Figure 6.
Appl. Sci. 2020, 10, x FOR PEER REVIEW 6 of 19 The objective of the regenerative braking control strategy for R-EEV is to guarantee the comprehensive regenerative braking performance during operation. The allocation logic of the braking work-point is crucial to the efficiency of RRBCS [20]. In this paper, the braking work-point in RRBCS was divided into five types, as shown in Figure 5a,b. Allocation logic of the braking work-point in RRBCS is as follows: (1) If Zreq_l < Za_l and μmax < μμ_l, the braking work-point should follow the I curve on work-point 1 (WC1) to protect the wheel from locking and slipping. (2) If Zreq_l < Za_l and μmax > μμ_l, the braking work-point should follow the "OA" curve on work-point 2 (WC2) to protect the wheel from locking and slipping. Regenerative braking torque provides sufficient braking torque at the front wheel and the rear wheel hydraulic force is 0.
(3) If Zb_h > Zreq_m > Za_l and μmax < μμ_h, the braking work-point should follow the I curve on work-point 3 (WC3) to protect the wheel from locking and slipping due to the fact that larger Zreq_m exists. (4) If Zb_h > Zreq_m > Za_l and μmax > μμ_h, the braking work-point should follow the "AB" curve on work-point 4 (WC4). The motor will provide its maximum regenerative torque applied at the front wheels, and the insufficient part of the driving braking torque would be compensated by the hydraulic braking system. (5) If Zreq_h > Zb_h, the braking work-point should follow the I curve on work-point 5 (WC5).
In order to control the fluctuation range of the battery SoC and prevent the RCC from being too large to affect the battery life, the regenerative charging work-point of the control logic is referenced in the battery SoC characteristics for conservative adjustments. The strategy makes the SoC close to the pre-set value, which not only protects the battery state of health, but also fully uses the battery pack power. The "conservative braking mode" is a conservative adjustment of the original braking work-point of RBCS. In order to meet the above performance requirements, the braking work-point switching logic needs to be adjusted in real time according to the vehicle status. With SoC characteristics as the switching limit, the braking work-point switching logic is shown in Figure 6. The battery SoC value at the k instant SoC (k) and the k + 1 instant SoC (k+1) were detected, respectively. The SoC change rate kSoC and change rate discrimination value kcr were calculated as follows: The battery SoC value at the k instant SoC (k) and the k + 1 instant SoC (k+1) were detected, respectively. The SoC change rate k SoC and change rate discrimination value k cr were calculated as follows: where SoC 0 is the SoC control target value; k 0 is the SoC control target change rate on drop stage; the k 0_CD is a preset value in charge depletion; the k 0_CS = 0 in charge sustaining; and ζ 0 is a correction coefficient with a value of 0.5. As depicted in Figures 5c and 6, the braking work-point is changed to follow the I curve, that is, W C1 is switched to W C2 , and the W C4 is switched to the W C3 . The "conservative braking mode" is realized in three cases and the details are explained as follows: (1) In CD, if k soc > |k cr | > 0, the "conservative braking mode" should be used to prevent SoC from deviating too much from SoC 0 , which can reduce the adverse impact of RCC on the battery. (2) If 0 > k SoC > -|k cr |, the "conservative braking mode" should be adopted to reduce the positive deviation of the SoC 0 , because SoC is approaching SoC 0 at a smaller rate. (3) In CS, the SoC is positively deviating from the SoC 0 and the RCC makes the SoC deviation larger. When SoC > 0, the "conservative braking method" should be adopted.

Description of MOO Problem for RRBCS
Compared with the general optimization problem, any decision variable of the MOO problem may influence any optimization target. Obviously, the essential MOO problem is to solve the mapping relationship of the function. The mapping relationship between the decision space and objective space belongs to a complex many-to-many relationship [21,22]. As we know, the solution set of the multi-objective problem belongs to vector optimization in nature. Among the solution sets, such as the absolute optimal solution, strong efficient solution, fuzzy efficient solution, Pareto optimal solutions, and others, the Pareto optimal solution is the best solution of the multi-objective mapping relation. The Pareto optimal solutions are a set of optimal solutions (Pareto front), among which one cannot be claimed to be better than the other without more information [23,24].
There are many parameters that affect the efficiency of the RRBCS. It is difficult to optimize all parameters due to its complexity and diversity. The vehicle's structural parameters cannot be changed, but the control parameters of RRBCS can be optimized and changed in reality. From the previous section, the allocation rules of work-point are decided by the four shutdown threshold parameters, namely, µ ϕ_l , µ ϕ_h , Z a-1 , and Z b-h . The tire-road adhesion factor W is a function of µ w_l and µ w_h , which determines the value of Z a-1 and Z b-h .
The problem described in this section is optimization with the objective of I bp_cyc , I rble_cyc , I bclr_cyc , and I crbp_cyc under multidimensional constraints. Therefore, the overall expression of the objective is expressed as follows: In the expression, J min represents the minimum total evaluation indicator of control system, and µ ϕ_l , µ ϕ_h , µ w_l , and µ w_h represent a set of optimization variables that make the objective function obtain its minimum I bp_cyc , I rbe_cyc , and I bclr_cyc , respectively. I bp_cyc represents the evaluation indicator of braking performance, I rble_cyc represents the evaluation indicator of regenerative braking loss efficiency, and I bclr_cyc represents the battery capacity loss rate.

Braking Performance (BP)
The evaluation indicator of the braking performance I bp_cyc characterizes the agreement between the actual braking strength and the target value, which is a calculation of the mean square error value of the braking strength. I bp_cyc is calculated as follows: where Z act is the actual braking strength and Z req is the required braking strength.

Regenerative Braking Loss Efficiency (RBLE)
The MOO problems are described as cost-type optimization problems. It is expected that the objective function values are as small as possible. The evaluation indicator of the regenerative braking efficiency optimization problem is a revenue-type optimization problem. It is expected that the I rbe_cyc is as large as possible.
where E regen_on and E regen_off are the energy consumed with and without RBC under a driving cycle, respectively. I rbe_cyc can be represented as the contribution made by regenerative braking to energy consumption reduction.
In order to construct a cost optimization problem uniformly, the evaluation indicator of regenerative braking loss efficiency I rble_cyc is calculated as follows: I rble_cyc essentially represents the proportion of regenerative braking energy that is not recovered during the braking process.

Battery Capacity Loss Rate (BCLR)
Charging current profiles can be changed and controlled to obtain the optimal charging capacity without affecting the battery service life [25]. The battery is subjected to repeated operations of charging and discharging profiles, and the rate and shape of the charging current undoubtedly affect the BCLR. Battery current I(t) and life cycles N cyc are selected as model reference variables in the battery capacity loss model (BCLM) referred to [26,27]. According to the measurements of battery capacity fading in [25], battery capacity loss rate I bclr_cyc and the capacity attenuation coefficient α 1 can be calculated as follows: where DOD is the depth of discharge; Ah cell is the cumulative capacity of the battery; C n is the charging rate; and I(t) is the battery current. B 1 and B 2 is the fitting parameter, which can be calculated through the least squares method. Under comprehensive driving cycle conditions, the BCLM can be obtained as follows: where T cyc is the total cycle time.
Considering that the focus of this research is on the application of the BCLM and article length limitation, a reference can be made in [25][26][27][28] for the experimental details of the battery life cycle. By fitting the experimental data, the following can be acquired: B 1 = 0.0018 and B 2 = 0.3785.

Optimization Decision Based on the Comprehensive Regenerative Braking Performance (CRBP)
A well-distributed Pareto optimal solution set is found through the optimization algorithm. In engineering practice, only one final solution is needed. So, just finding the Pareto optimal solution set does not completely solve the MOO problem. The multi-objective normalization optimization discussed in this paper adopts the linear normalization method, which is simple, practical, and efficient to deal with the frontier of non-convex problems. Additionally, it can reflect the weights of optimization goals clearly. Since the above four optimization variables represent different physical meanings, it is necessary to unify the cost functions in each dimension by normalizing the normalization method. After transformation, it becomes a dimensionless expression.
Normalization of linear functions (Min-Max scaling) converts the original data linearization method to the range of [0, 1]. The normalization formula is as follows: where X (nor) is the normalized data; X p is the original data in Pareto optimal solution sets; and X p (nax) and X p (min) are the maximum and minimum values of the original data sets respectively.
The evaluation indicator of comprehensive regenerative braking performance I crbp_cyc is calculated as follows: where λ is the weighting coefficients of normalized data. Different weighting results are obtained when different weighting coefficients are selected. Designers can choose a reasonable weight coefficient allocation based on design performance requirements. In this paper, the weight parameter selection is as follows:

Non-Dominated Sorting Genetic Algorithm (NSGA-II)
For the MOO problem, it is difficult to directly judge the merits and demerits of the individual. It needs a comprehensive index to evaluate all objectives. NSGA-II is a kind of multi-objective evolutionary algorithm based on Pareto-optimal solutions to solve the MOO problem, which has conflicting objectives. NSGA-II can build solution sets with fast non-dominated sorting and the crowd distance computing method, which is an adaptive global optimization algorithm and has better performance such as a faster convergence speed, better convergence effect, better robustness, and adaptive ability. It assures a good convergence towards the Pareto-optimal front without losing the solution diversity [29]. A detailed explanation and steps of NSGA-II can be found in [30]. In this study, the population size of the algorithm was set to be 200, and the number of generations was set to be 100. The flowchart for implementing the algorithm in solving the MOO problem is shown in Figure 7. In the present work, according to the characteristics of optimization variables, binary cross mutations are simulated by real number encoding. The algorithm mutation can be adjusted adaptively to improve the global search ability in the early stage and local search ability in the later stage. Meanwhile, in order to increase the convergence speed and ensure the global optimality of the Pareto solution set, the process of simulating the binary cross mutation of the algorithm is as follows: where xi (k+1) and xi+1 (k+1) are the individuals before crossing; xi (k) and xi+1 (k) are the individuals after crossing; k is the evolutionary algebra; ci(λ) is the cross coefficient, using the dynamic state adjustment mechanism; xj (k) is the individual to be mutated; and cj(λ) is the coefficient of variation.
It is necessary to make corresponding changes in ci(λ) and cj(λ) to maximize the performance of the algorithm according to the change of the solution set. The algorithm is further improved so that ci(λ) and cj(λ) can adapt to the changes of the solution set. The adaptive change model is expressed as: where λ is the adaptive coefficient of variation; N is the number of populations; and Np is the optimal number of solutions. In the present work, according to the characteristics of optimization variables, binary cross mutations are simulated by real number encoding. The algorithm mutation can be adjusted adaptively to improve the global search ability in the early stage and local search ability in the later stage. Meanwhile, in order to increase the convergence speed and ensure the global optimality of the Pareto solution set, the process of simulating the binary cross mutation of the algorithm is as follows: where x i (k+1) and x i+1 (k+1) are the individuals before crossing; x i (k) and x i+1 (k) are the individuals after crossing; k is the evolutionary algebra; c i (λ) is the cross coefficient, using the dynamic state adjustment mechanism; x j (k) is the individual to be mutated; and c j (λ) is the coefficient of variation.
It is necessary to make corresponding changes in c i (λ) and c j (λ) to maximize the performance of the algorithm according to the change of the solution set. The algorithm is further improved so that c i (λ) and c j (λ) can adapt to the changes of the solution set. The adaptive change model is expressed as: where λ is the adaptive coefficient of variation; N is the number of populations; and N p is the optimal number of solutions.

MOO Simulation Model
In order to guarantee the Pareto solution sets and evaluate the control effect of the strategies during deceleration braking, several simulations experiments were carried out to verify the feasibility and effectiveness of the system in MATLAB/Simulink and AVL-Cruise software. The main parameters used in the simulations are shown in Table 1. The API function provided by the Cruise software was used to develop vehicle control strategy on Simulink, while vehicle model development and the simulation calculation for vehicle performance were conducted on the Cruise. The vehicle control strategy was developed by the means of Simulink and the API function was provided by the Cruise. Vehicle model development and simulation calculations of vehicle performance are carried out on Cruise. The signals data such as traction and breaking, battery SoC, and V veh were transferred via the interface of Cruise to Simulink. The analysis results were sent back to Cruise via the interface. Simulation on the power system was conducted in the Cruise model.
In the model, the values of the output form a vector by a multiplexer. After completing the simulation step successfully, the output vector was transferred into the Matlab Workspace by the Matlab object "Block Parameters: To Workspace," and Cruise could access it. The output values of the model had to be combined to a vector. Cruise got this vector and put its elements onto the data bus where they could be used by other components. The vehicle's dynamic model and regenerative braking control system were established in Cruise and Simulink, respectively, using a co-simulation model as seen in Figure 8.

MOO Simulation Model
In order to guarantee the Pareto solution sets and evaluate the control effect of the strategies during deceleration braking, several simulations experiments were carried out to verify the feasibility and effectiveness of the system in MATLAB/Simulink and AVL-Cruise software. The main parameters used in the simulations are shown in Table 1. The API function provided by the Cruise software was used to develop vehicle control strategy on Simulink, while vehicle model development and the simulation calculation for vehicle performance were conducted on the Cruise. The vehicle control strategy was developed by the means of Simulink and the API function was provided by the Cruise. Vehicle model development and simulation calculations of vehicle performance are carried out on Cruise. The signals data such as traction and breaking, battery SoC, and Vveh were transferred via the interface of Cruise to Simulink. The analysis results were sent back to Cruise via the interface. Simulation on the power system was conducted in the Cruise model.
In the model, the values of the output form a vector by a multiplexer. After completing the simulation step successfully, the output vector was transferred into the Matlab Workspace by the Matlab object "Block Parameters: To Workspace," and Cruise could access it. The output values of the model had to be combined to a vector. Cruise got this vector and put its elements onto the data bus where they could be used by other components. The vehicle's dynamic model and regenerative braking control system were established in Cruise and Simulink, respectively, using a co-simulation model as seen in Figure 8. In order to verify the effectiveness of MOO algorithm, a co-simulation test was carried out based on the braking system model of R-EEV in the simulation environment. A customized typical In order to verify the effectiveness of MOO algorithm, a co-simulation test was carried out based on the braking system model of R-EEV in the simulation environment. A customized typical deceleration braking (CTDB) was defined, as shown in Figure 9a. In simulations, the initial braking speed was set at 80 km/h. The braking strength increased slowly from 0 to 0.2 in 2 s and then increased quickly to 0.7 to simulate emergency braking conditions, and finally it stabilized at 0.5 until the vehicle speed was 0. A comprehensive driving cycle consisting of the CTDB, New European Drive Cycle (NEDC), China Light-duty Vehicle Test Cycle (CLTC), and World Light vehicle Test Procedure (WLTP) was set up, as shown in Figure 9b.
Appl. Sci. 2020, 10, x FOR PEER REVIEW 12 of 19 deceleration braking (CTDB) was defined, as shown in Figure 9a. In simulations, the initial braking speed was set at 80 km/h. The braking strength increased slowly from 0 to 0.2 in 2 s and then increased quickly to 0.7 to simulate emergency braking conditions, and finally it stabilized at 0.5 until the vehicle speed was 0. A comprehensive driving cycle consisting of the CTDB, New European Drive Cycle (NEDC), China Light-duty Vehicle Test Cycle (CLTC), and World Light vehicle Test Procedure (WLTP) was set up, as shown in Figure 9b. Three different roads were assumed, namely, a dry asphalt surface with a high PTAC (μmax_h = 0.9), dry cement surface with a medium PTAC (μmax_m = 0.6), and wet cobblestone surface with a low PTAC (μmax_l = 0.3), respectively.

Results Analysis Based on Pareto Solution Sets
As we know, the theory of Pareto optimality can reflect the essential characteristic of the MOO problem better. Therefore, the evolutionary algorithm based on the Pareto principle is proposed to solve the MOO problem. The existence of the optimal solution sets was further studied, and a group of non-inferior Pareto solution sets was obtained. The conflicting relationship among the three objectives is shown in Figure 10. The four evaluation indexes of BP, RBLE, BCLR, and CRBP were comparatively analyzed.  Three different roads were assumed, namely, a dry asphalt surface with a high PTAC (µ max _ h = 0.9), dry cement surface with a medium PTAC (µ max _ m = 0.6), and wet cobblestone surface with a low PTAC (µ max _ l = 0.3), respectively.

Results Analysis Based on Pareto Solution Sets
As we know, the theory of Pareto optimality can reflect the essential characteristic of the MOO problem better. Therefore, the evolutionary algorithm based on the Pareto principle is proposed to solve the MOO problem. The existence of the optimal solution sets was further studied, and a group of non-inferior Pareto solution sets was obtained. The conflicting relationship among the three objectives is shown in Figure 10. The four evaluation indexes of BP, RBLE, BCLR, and CRBP were comparatively analyzed.
The optimization results are summarized in Table 2. As we know, the theory of Pareto optimality can reflect the essential characteristic of the MOO problem better. Therefore, the evolutionary algorithm based on the Pareto principle is proposed to solve the MOO problem. The existence of the optimal solution sets was further studied, and a group of non-inferior Pareto solution sets was obtained. The conflicting relationship among the three objectives is shown in Figure 10. The four evaluation indexes of BP, RBLE, BCLR, and CRBP were comparatively analyzed.  The results of the experiment on the high tire-road adhesion condition were taken as an example for discussion and analysis. As shown in Table 3 and Figure 10, the conflict was reflected as the following aspects: (1) Under the best BP (S1), I bp_cyc = 0.0407 with a best braking performance, I bclr_cyc = 2.9 with a better battery state of health (SOH). However, I rble_cyc = 0.76 with the worst braking recovery efficiency. The worse I crbp_cyc = 0.61 was caused by the worst indicator I rble_cyc . A similar situation manifested under the lowest BCLR (S3). (2) Under the lowest RBLE (S2), I rble_cyc = 0.68 with the best braking recovery efficiency. However, I bp_cyc = 0.0473 with the worst braking performance and I bclr_cyc = 11.7 with the worst battery SOH, which caused the worst I crbp_cyc . (3) Under the best CRBP (S4), although none of the three indicators were optimal, they were suboptimal and made the best I crbp_cyc. The performance optimization of one single target may inevitably damage the other targets. The optimization results should be multiple sets of solutions rather than a single optimal solution. Each point represents a set of alternatives. BP, RBLE, and BCLR present a clear conflict, and three optimization objectives cannot be optimal at the same time. Since reducing regenerative braking efficiency tends to extend the battery life, the battery RCC is limited to the maximum. The braking work-point on high regenerative braking will switch to low regenerative braking on the I curve to ensure braking performance better, which means the high braking performance reduces the regenerative braking efficiency to a certain extent and causes the conflict. The above obtained Pareto optimal solution sets consist of a series of discrete points. It needs only one index to show optimal values and evaluation index more clearly. Therefore, averaging method is adopted to fit the discrete optimal points into optimal value. The averaging Pareto optimal solution set is calculated as follows: where x n (k) is the optimal solution set in the k-th generation; X (k) is the averaging value of optimal solution set in the k-th generation; y n (k) is the evaluation indicator in the k-th generation; and Y (k) is the averaging value of evaluation indicator in the k-th generation. When the optimization range contains all regions, all solution sets can be represented by their respective averages. It should be emphasized that the results of average values were not the real optimal solution under CRBP. However, we could understand and observe the optimal solution set through the trend during each iteration. The optimization calculation results are shown in Figure 11 and Table 3.  (21) where xn (k) is the optimal solution set in the k-th generation; X (k) is the averaging value of optimal solution set in the k-th generation; yn (k) is the evaluation indicator in the k-th generation; and Y (k) is the averaging value of evaluation indicator in the k-th generation.
When the optimization range contains all regions, all solution sets can be represented by their respective averages. It should be emphasized that the results of average values were not the real optimal solution under CRBP. However, we could understand and observe the optimal solution set through the trend during each iteration. The optimization calculation results are shown in Figure 11 and Table 3.  It can be seen clearly that optimization variables converged to a stable value after about 60 optimization iterations eventually. Additionally, the convergence trajectories of optimization variables during iteration show some difference. Four optimization variables could converge to the stable Pareto solution sets, which reflect that the MOOM for RRBCS proposed in this paper could achieve the Pareto solution sets "regional convergence" of the MOO problem. "Regional convergence" can be understood as a process, which refers that optimal individual in the Pareto solution sets flows to the Pareto front during the iteration. In addition, four evaluation indexes converged towards the optimization direction. Ibp_cyc reduced from the initial value of 0.443-0.428, a decrease of about 3.4%. Irble_cyc reduced from the initial value of 79.4%-75.1%, a decrease of about 5.4%. Ibclr_cyc reduced from the initial value of 16.1%-11.2%, a decrease of about 30.4%. Ibp_cyc increased from the initial value of 0.32-0.71, an increase of 0.39. The results prove the effectiveness and feasibility of the MOOM. It can be seen clearly that optimization variables converged to a stable value after about 60 optimization iterations eventually. Additionally, the convergence trajectories of optimization variables during iteration show some difference. Four optimization variables could converge to the stable Pareto solution sets, which reflect that the MOOM for RRBCS proposed in this paper could achieve the Pareto solution sets "regional convergence" of the MOO problem. "Regional convergence" can be understood as a process, which refers that optimal individual in the Pareto solution sets flows to the Pareto front during the iteration. In addition, four evaluation indexes converged towards the optimization direction. I bp_cyc reduced from the initial value of 0.443-0.428, a decrease of about 3.4%. I rble_cyc reduced from the initial value of 79.4%-75.1%, a decrease of about 5.4%. I bclr_cyc reduced from the initial value of 16.1%-11.2%, a decrease of about 30.4%. I bp_cyc increased from the initial value of 0.32-0.71, an increase of 0.39. The results prove the effectiveness and feasibility of the MOOM.

Optimization Decisions and Results Discussion
Taking the individual with comprehensive regenerative braking performance as the final optimization solution, the optimal variable solution was [µ ϕ_l , µ ϕ_h , µ w_l , µ w_h ] T = [0.11, 0.53, 0.28, 0.65] T . The results of the brake strength thresholds Z a-l and Z b-h after optimization are summarized in Table 4. As shown in Figure 12, the points with "*" represent the regenerative braking work-point after optimization, and the points without "*" represent the regenerative braking work-point before optimization. It can be seen that Z a-l and Z b-h at points A and B remain unchanged before and after optimization on high TAC. After optimization, points A and B move forward to A* and B* on medium TAC and points A and B move backward to A* and B* on low TAC.
In addition, changes of the W function before and after optimization is shown in Figure 13.
Appl. Sci. 2020, 10, x FOR PEER REVIEW 15 of 19 Taking the individual with comprehensive regenerative braking performance as the final optimization solution, the optimal variable solution was [μφ_l, μφ_h, μw_l, μw_h] T = [0.11, 0.53, 0.28, 0.65] T . The results of the brake strength thresholds Za-l and Zb-h after optimization are summarized in Table  4. As shown in Figure 12, the points with " ⃰ " represent the regenerative braking work-point after optimization, and the points without " ⃰ " represent the regenerative braking work-point before optimization. It can be seen that Za-l and Zb-h at points A and B remain unchanged before and after optimization on high TAC. After optimization, points A and B move forward to A⃰ and B⃰ on medium TAC and points A and B move backward to A⃰ and B⃰ on low TAC. In addition, changes of the W function before and after optimization is shown in Figure 13. The analysis of the simulation results is described as follows: (1) In the case of μmax ∈ (0, μ⃰ w_l] = (0, 0.28], the wheel had a risk of slipping due to the poor TAC. The control parameters and W function did not change after optimization (W⃰ = W = 0), the braking work-points were on the I curve to ensure the braking safety, and the front and rear wheel braking torques were provided by hydraulic torque.
(2) In the case of μmax ∈ (μ⃰ w_l, μw_l] = (0.28, 0.4], the threshold value μw_l "drill down" after optimization (W⃰ > W), which made the regenerative braking torque "enter ahead" to increase the regenerative braking energy. As shown in Figure 12a, under the conditions of low PTAC, the braking work-points C(Wc5) and D(Wc5) on the I curve before optimization would switch to C*(Wc1) and D*(Wc3) after optimization. (3) In the case of μmax ∈ (μw_l, μw_cr] = (0.4, 0.54], threshold switching points A and B moved backward after optimization, and the regenerative braking ratio did not change or Taking the individual with comprehensive regenerative braking performance as the final optimization solution, the optimal variable solution was [μφ_l, μφ_h, μw_l, μw_h] T = [0.11, 0.53, 0.28, 0.65] T . The results of the brake strength thresholds Za-l and Zb-h after optimization are summarized in Table  4. As shown in Figure 12, the points with " ⃰ " represent the regenerative braking work-point after optimization, and the points without " ⃰ " represent the regenerative braking work-point before optimization. It can be seen that Za-l and Zb-h at points A and B remain unchanged before and after optimization on high TAC. After optimization, points A and B move forward to A⃰ and B⃰ on medium TAC and points A and B move backward to A⃰ and B⃰ on low TAC. In addition, changes of the W function before and after optimization is shown in Figure 13. The analysis of the simulation results is described as follows: (1) In the case of μmax ∈ (0, μ⃰ w_l] = (0, 0.28], the wheel had a risk of slipping due to the poor TAC. The control parameters and W function did not change after optimization (W⃰ = W = 0), the braking work-points were on the I curve to ensure the braking safety, and the front and rear wheel braking torques were provided by hydraulic torque.
(2) In the case of μmax ∈ (μ⃰ w_l, μw_l] = (0.28, 0.4], the threshold value μw_l "drill down" after optimization (W⃰ > W), which made the regenerative braking torque "enter ahead" to increase the regenerative braking energy. As shown in Figure 12a, under the conditions of low PTAC, the braking work-points C(Wc5) and D(Wc5) on the I curve before optimization would switch to C*(Wc1) and D*(Wc3) after optimization. (3) In the case of μmax ∈ (μw_l, μw_cr] = (0.4, 0.54], threshold switching points A and B moved backward after optimization, and the regenerative braking ratio did not change or The analysis of the simulation results is described as follows: (1) In the case of µ max ∈ (0, µ * w_h ] = (0, 0.28], the wheel had a risk of slipping due to the poor TAC. The control parameters and W function did not change after optimization (W* = W = 0), the braking work-points were on the I curve to ensure the braking safety, and the front and rear wheel braking torques were provided by hydraulic torque. (2) In the case of µ max ∈ (µ * w_h , µ w_l ] = (0.28, 0.4], the threshold value µ w_l "drill down" after optimization (W > W), which made the regenerative braking torque "enter ahead" to increase the regenerative braking energy. As shown in Figure 12a, under the conditions of low PTAC, the braking work-points C(W c5 ) and D(W c5 ) on the I curve before optimization would switch to C*(W c1 ) and D*(W c3 ) after optimization. (3) In the case of µ max ∈ (µ * w_h , µ w_cr ] = (0.4, 0.54], threshold switching points A and B moved backward after optimization, and the regenerative braking ratio did not change or became larger at the same braking strength. (4) In the case of µ max ∈ (µ w_cr , µ w_h ] = (0.54, 0.65], the threshold value µ w_h "goes up" after optimization (W* < W), which accompanied by the threshold switching points A and B moved forward after optimization. Under the demand of high braking strength, the risk of locking and slipping was prone to occur. It can "sacrifice" smaller braking energy in exchange for better braking performance to ensure braking safety after parameter optimization. As shown in Figure 12b, under the demand of low braking strength, the braking work-points E(W c1 ) before optimization would switch to E*(W c4 ) after optimization, and under the demand of medium braking strength, the braking work-points G(W c4 ) and I(W c4 ) before optimization would switch to G*(W c4 ) and I*(W c5 ) after optimization. (5) In the case of µ max ∈ (µ * w_h , 1) = (0.65, 1), the threshold switching points A and B remained unchanged after optimization (W* = W = 1), as shown in Figure 12c.
In summary, in the case of low TAC, the parameters could be optimized to make the regenerative braking starting threshold "drill down"; in the case of medium TAC, the optimization direction focused more on energy recovery while ensuring braking safety; in the case of high TAC and high-strength braking, RRRBCS would "sacrifice" smaller regenerative braking energy in exchange for better braking performance.

Discussion and Sensitivity Analysis of RRBCS Based on the Optimization Results
From the above discussion, it could be seen clearly that on the three different tire-road adhesion condition, the influence of control parameters on the performance of RRBCS was different. Therefore, simulation tests were designed to analyze the sensitivity of the different tire-road condition to optimization objective functions. The simulation results of three driving cycles were statistically analyzed, as shown in Figures 14-16.
Appl. Sci. 2020, 10, x FOR PEER REVIEW 16 of 19 became larger at the same braking strength. (4) In the case of μmax ∈ (μw_cr, μ⃰ w_h] = (0.54, 0.65], the threshold value μw_h "goes up" after optimization (W⃰ < W), which accompanied by the threshold switching points A and B moved forward after optimization. Under the demand of high braking strength, the risk of locking and slipping was prone to occur. It can "sacrifice" smaller braking energy in exchange for better braking performance to ensure braking safety after parameter optimization. As shown in Figure 12b, under the demand of low braking strength, the braking work-points E(Wc1) before optimization would switch to E*(Wc4) after optimization, and under the demand of medium braking strength, the braking work-points G(Wc4) and I(Wc4) before optimization would switch to G*(Wc4) and I*(Wc5) after optimization. (5) In the case of μmax ∈ (μ⃰ w_h, 1) = (0.65, 1), the threshold switching points A and B remained unchanged after optimization (W⃰ = W = 1), as shown in Figure  12c.
In summary, in the case of low TAC, the parameters could be optimized to make the regenerative braking starting threshold "drill down"; in the case of medium TAC, the optimization direction focused more on energy recovery while ensuring braking safety; in the case of high TAC and highstrength braking, RRRBCS would "sacrifice" smaller regenerative braking energy in exchange for better braking performance.

Discussion and Sensitivity Analysis of RRBCS Based on the Optimization Results
From the above discussion, it could be seen clearly that on the three different tire-road adhesion condition, the influence of control parameters on the performance of RRBCS was different. Therefore, simulation tests were designed to analyze the sensitivity of the different tire-road condition to optimization objective functions. The simulation results of three driving cycles were statistically analyzed, as shown in Figures 14-16. As depicted in Figure 14, when the PTAC was in the range of 0-0.35 and 0.55-1.0, Ibp_cyc were similar and close before and after parameters optimization. There was a significant difference before and after optimization when the PTAC was in the range of 0.35-0.55. Compared with the braking process controlled by RRBCS before parameters optimization, Ibp_cyc decreased significantly and ∆Ibp_cyc was up to about 7% when μmax = 0.38. In addition, the performance result of recovery energy was similar to BP. As depicted in Figure 15, when the adhesion coefficient was in the range of 0.35-0.5, the recovery braking energy controlled by the proposed control strategy after parameters optimization was about 26.71%. Compared with the braking process controlled by RRBCS before parameters optimization, the recovery braking energy could improve 19.3% after parameters optimization, which denotes that the RRBCS was effective to improve the regenerative energy after parameters optimization. As depicted in Figure 16, when the tire-road adhesion coefficient was in the range of 0.2-0.5, after parameters optimization, Ibclr_cyc reduced slightly and ∆Ibclr_cyc was up to about 1.2% when μmax = 0.52. When the adhesion coefficient was in the range of 0.55-0.75, ∆Ibclr_cyc decreased significantly and ∆Ibclr_cyc was up to about 5.3% when μmax = 0.63, which denotes that the RRBCS was effective to reduce the battery capacity loss rate after parameters optimization. As depicted in Figure 16, when the tire-road adhesion coefficient was in the range of 0.2-0.5, after parameters optimization, Ibclr_cyc reduced slightly and ∆Ibclr_cyc was up to about 1.2% when μmax = 0.52. When the adhesion coefficient was in the range of 0.55-0.75, ∆Ibclr_cyc decreased significantly and ∆Ibclr_cyc was up to about 5.3% when μmax = 0.63, which denotes that the RRBCS was effective to reduce the battery capacity loss rate after parameters optimization. The optimization calculation results are shown in Table 5. As shown in Table 6, after parameters optimization, Ibp_cyc reduced about 4.7%-7.1% when μmax = 0.38, Irble_cyc reduced about 16.1%-19.3% when μmax = 0.42, and Ibclr_cyc reduced about 4.8% when μmax = 0.62. As a comparison, the results of this optimal response to different tire-road conditions reflected different performances, which means that the sensitivity of optimization parameters to different road conditions was different. This is due to three main reasons: first, the vehicle's safety is the main factor in the emergency situation, and the optimization direction is more focused on ensuring braking safety, especially on low and medium tire-road adhesion conditions; second, the regenerative braking torque will "enter ahead" to increase the regenerative braking energy while ensuring braking safety; and third, regenerative braking torque participates in energy recovery in advance, which causes increased recovery current from zero. Overall RRBCS was robust to change on the road conditions and the effectiveness of the proposed strategy could be verified by tests. As depicted in Figure 14, when the PTAC was in the range of 0-0.35 and 0.55-1.0, I bp_cyc were similar and close before and after parameters optimization. There was a significant difference before and after optimization when the PTAC was in the range of 0.35-0.55. Compared with the braking process controlled by RRBCS before parameters optimization, I bp_cyc decreased significantly and ∆I bp_cyc was up to about 7% when µ max = 0.38. In addition, the performance result of recovery energy was similar to BP. As depicted in Figure 15, when the adhesion coefficient was in the range of 0.35-0.5, the recovery braking energy controlled by the proposed control strategy after parameters optimization was about 26.71%. Compared with the braking process controlled by RRBCS before parameters optimization, the recovery braking energy could improve 19.3% after parameters optimization, which denotes that the RRBCS was effective to improve the regenerative energy after parameters optimization.
As depicted in Figure 16, when the tire-road adhesion coefficient was in the range of 0.2-0.5, after parameters optimization, I bclr_cyc reduced slightly and ∆I bclr_cyc was up to about 1.2% when µ max = 0.52. When the adhesion coefficient was in the range of 0.55-0.75, ∆I bclr_cyc decreased significantly and ∆I bclr_cyc was up to about 5.3% when µ max = 0.63, which denotes that the RRBCS was effective to reduce the battery capacity loss rate after parameters optimization.
The optimization calculation results are shown in Table 5. As shown in Table 5, after parameters optimization, I bp_cyc reduced about 4.7%-7.1% when µ max = 0.38, I rble_cyc reduced about 16.1%-19.3% when µ max = 0.42, and I bclr_cyc reduced about 4.8% when µ max = 0.62. As a comparison, the results of this optimal response to different tire-road conditions reflected different performances, which means that the sensitivity of optimization parameters to different road conditions was different. This is due to three main reasons: first, the vehicle's safety is the main factor in the emergency situation, and the optimization direction is more focused on ensuring braking safety, especially on low and medium tire-road adhesion conditions; second, the regenerative braking torque will "enter ahead" to increase the regenerative braking energy while ensuring braking safety; and third, regenerative braking torque participates in energy recovery in advance, which causes increased recovery current from zero. Overall RRBCS was robust to change on the road conditions and the effectiveness of the proposed strategy could be verified by tests.

Conclusions
In this paper, a multi-objective optimization system with various conflicting objectives and a parameters optimization method of RRBCS were proposed to design an optimal RBCS for R-EEV. The method consists of the following steps: (1) A RRBCS was proposed and used in simulation to balance BP, RBLE, and BCLR. (2) The MOO model was established to calculate the objective functions by using simulation results of RRBCS on three different tire-road adhesion conditions. (3) The individual with optimal CRBP was selected as the final optimization solution to evaluate the performance of the proposed methodology, and control parameters decision and optimization results were analyzed and discussed. (4) A study on the sensitivity of the different PTAC to three optimization objectives was conducted through a series of simulation tests.
The reasonable parameter optimization of RRBCS enabled the RBS work to become more efficient and to balance the BP, RBLE, and BCLR. The results analysis based on Pareto solution sets show that BP, RBLE, and BCLR presented a clear conflict, and three optimization objectives could not reach the optimal at the same time. The "regional convergence" of variables could also prove the effectiveness and feasibility of MOOM by statistical analysis. Under the final optimization solution [µ ϕ_l , µ ϕ_h , µ w_l , µ w_h ] T = [0.11, 0.53, 0.28, 0.65] T , optimized threshold parameters µ w_l and µ w_h show a bipolar expansion to make regenerative braking torque work early to increase regenerative braking efficiency on low tire-road adhesion condition, and reduce the battery capacity loss rate at the expense of small braking energy recovery on medium tire-road adhesion condition. The influence of final optimization control parameters on evaluation indexes on different tire-road adhesion condition was discussed and analyzed, and a more detailed discussion was in the subsequent sensitivity analysis. RRBCS was proved to perform better road adaptability regarding the distribution of solutions. Under the medium and low tire-road adhesion condition, the improvement obtained by optimization was the most significant. This study could provide more references for the optimal control strategy and laid a foundation for multi-objective regenerative braking energy control of the actual vehicle.
Author Contributions: Y.L. and Y.F. managed the project and conceptualized scheme; H.L. conceived the control method, completed the modeling and performed the simulation experiments, and finished the manuscript; X.L. collected the data and reviewed the paper. All authors have read and agreed to the published version of the manuscript.