# Pressure Estimation and Pressure Control of Hydraulic Control Unit in Electric-Wheel Vehicle

Authors: Zhao Xiangyang; Xu Wen-bo; Gang Liu
Journal: Mathematical Problems in Engineering
 (2020)

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## Abstract

In order to improve the braking performance and safety performance of electric vehicles driven by a hub motor, the cylinder pressure estimation and pressure control of its hydraulic braking system are studied. In this paper, a mathematical model is established for the solenoid valve, a key component of the hydraulic actuator, and the hydraulic and electrical characteristics of the solenoid valve are studied. A state equation is established for the solenoid valve, and the square root volume Kalman filter (SRCKF) algorithm is used to estimate the solenoid valve spool position. The brake fluid flow and brake wheel cylinder pressure are calculated based on the spool position. Finally, a solenoid valve spool position control algorithm based on sliding mode variable structure algorithm is designed, and the brake pressure in the brake wheel cylinder is controlled by adjusting the spool position. Matlab/Simulink-AMESim software simulation and hardware-in-the-loop were used to verify the algorithm. Simulation results show that the brake cylinder pressure can be estimated accurately, and the pressure control algorithm can accurately follow the control target value.


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## Body

## 1. Introduction

Electric vehicles driven by in-wheel motors are highly competitive in the market. An important method to improve the energy utilization rate of electric vehicles is braking energy recovery technology. This technology has always been a hot research area for electric vehicles. While studying the braking energy regenerative technology, the research team designed a new type of hydraulic control unit. Based on the HCU, a series of regenerative braking energy coordinated control research is carried out [1–3]. During the research, it is found that accurate estimation of brake wheel cylinder pressure and pressure linear control are the basis of electric vehicle regenerative braking and ABS control [4–7].The target wheel cylinder pressure is calculated by the ABS control algorithm. Based on the target wheel cylinder pressure, the estimated value of the current pressure of the wheel cylinder, and the current solenoid valve working condition, the solenoid valve control command is calculated by the pressure control algorithm. The current actual pressure of the wheel cylinder and the target pressure are monitored in real time. The control command and working status of the solenoid valve are constantly adjusted by the pressure control algorithm so that the actual pressure of the wheel cylinder reaches the target pressure as soon as possible.Qu introduced the pressure control method based on program logic (if-else) [8]. The inlet and outlet valves of hydraulic control unit (HCU) are adjusted to achieve the control of the wheel cylinder pressure. The use of program logic (if-else) method will cause the actual pressure of the wheel cylinder to fluctuate greatly, and the highly reliable PID control algorithm [9, 10] is used to design the wheel cylinder pressure controller.Due to the increasingly higher requirements for control accuracy and speed of the wheel cylinder pressure control system, the PID algorithm has gradually failed to meet the demand. Aiming at the various defects of PID control algorithms, such as poor real-time control system, poor robustness, easy to generate oscillations in the integration link, susceptibility to external disturbances, and sensitivity to changes in system parameters, various advanced and effective control theories [11–13] were used to design the wheel cylinder pressure controller.The hydraulic pressure control unit (HCU) is the core unit of the hydraulic pressure control system. The solenoid valve is one of the main devices. The hydraulic pressure control of the wheel cylinder is closely related to the solenoid valve. At present, commonly used solenoid valves include on-off valves, high-speed on-off valves, and linear solenoid valves. Since the on-off valve only has two states of open and closed, it is very difficult to achieve continuous flow control. In [14], it was found that the wheel cylinder pressure fluctuated greatly during the braking process of ABS.The high-speed on-off valve has the same working principle as the traditional on-off valve. The on-off of the brake fluid is controlled by switching between the on and off states of the high-speed solenoid valve. The difference is that the operating frequency of the high-speed on-off valve is higher. In [15], the method of using PWM signal to control the solenoid valve is proposed, and it is verified in experiment that the brake fluid flow is proportional to the PWM signal. In [16], by effectively adjusting the PWM signal, the brake fluid flow is controlled approximately linearly.The proportional valve can continuously control the brake fluid flow. However, the cost of the proportional valve is relatively high, and it is not realistic to apply it to the automobile brake system. In [17], the pressure of the four wheel cylinders can be smoothly controlled by the solenoid valve. In the ABS control system, the proportional valve can ensure that the wheel cylinder pressure accurately follows the target pressure value.After analysis of references, in order to improve the braking performance and safety performance of the wheel motor-driven electric vehicle, a composite braking system was designed. In compound brake systems, high-speed on-off valves are used to control the brake fluid flow. The mathematical model of the high-speed on-off valve was established, the hydraulic characteristics and the electrical characteristics of the high-speed on-off valve were studied. The state equation of the high-speed switching valve is established, and the square root volume Kalman filter (SRCKF) algorithm [18, 19] is used to estimate the position of the solenoid valve spool. The current brake wheel cylinder pressure is calculated based on the spool position. According to the PV characteristics, a wheel cylinder pressure control algorithm based on the sliding mode variable structure algorithm is designed.This paper is structured as follows: in Section2, the HCU structure and working principle of the regenerative braking system designed by the project team are briefly introduced, and the method of pressure increase is also introduced; in Section 3, the dynamic model of the HCU is derived, and the electromagnetic characteristics and electrical characteristics of the solenoid valve required for pressure control are analyzed; in Section 4, the SRCKF-based estimation algorithm of spool position is designed, and the wheel cylinder pressure control algorithm is derived based on the spool position data; in Section 5, the method proposed in this paper is verified by software cosimulation; in Section 6, experiments are conducted to prove the performance of the entire control system; and conclusions are made in Section 7.


## 2. HCU Function Introduction

As shown in Figure1, the HCU mainly includes two parts: the solenoid valve and the high-pressure accumulator. The high-pressure accumulator has two main functions. First, in the pure motor braking mode, the brake fluid generated by the driver pressing the brake pedal is temporarily stored in the high-pressure accumulator. Second, when relying on pure motor braking, the braking force is insufficient, and the brake fluid in the accumulator can quickly replenish the braking pressure. The solenoid valve is responsible for adjusting the brake pressure in the brake wheel cylinder, which is the basic brake torque of the electric vehicle. Hydraulic braking torque is mainly used in combination with motor braking torque to achieve the vehicle’s deceleration function. The purpose of this paper is to design a method of controlling the position of the solenoid valve spool. The valve spool is used to adjust the increase rate of the brake fluid, and when the brake pressure reaches the target value, the solenoid valve is closed. With this linear pressure increase approach which is based on valve spool displacement regulation, accurate wheel cylinder pressure (WCP) control can be achieved.Figure 1
Architecture of proposed hydraulic control unit.


## 3. Modeling of the Solenoid Valve

The structure of the solenoid valve can be referred from Dr. Fan’s thesis [20]. When the current does not flow through the solenoid valve coil, the valve spool is affected by the spring force. At this time, the solenoid valve spool is fully opened. The brake fluid flows into the brake wheel cylinder through the solenoid valve and generates braking force. In contrast, when a current flows through the coil, the generated electromagnetic force overcomes the spring force. The opening of the solenoid valve core is gradually reduced, which will reduce the flow of brake fluid into the brake wheel cylinder and reduce the wheel cylinder pressure.During braking, the valve spool is mainly subjected to spring force, friction force between push rod and pipe wall, electromagnetic force, and hydraulic power of brake fluid. The structure of the on-off solenoid valve is shown in Figure2. 1 in the figure represents the working air gap. 2 represents the spool. 3 represents the valve seat. 4 in the figure represents the coil. 5 represents the outlet of valve. 6 represents the inlet of valve. 7 represents the secondary air gap.Figure 2
The structure of the on-off solenoid valve.The force analysis diagram of the solenoid valve is shown in Figure3. The force model of the spool can be expressed as follows:(1)mz¨ev=Fm−Fs−Fk−Cu⋅z˙ev,where zev denotes the spool position and its range from 0 mm to 0.22 mm, m denotes the total mass of the spool, Fm denotes the electromagnet force acting on the spool, Fs denotes the flow force acting on the spool, Fk denotes the force produced by return spring, and Cu is the coefficient of viscous friction.Figure 3
Force analysis diagram of valve.The model of electromagnetic forceFk can be expressed as(2)Fk=F0+Kk⋅zev,where F0 denotes the preload force and Kk denotes the stiffness coefficient of the return spring.


### 3.1. Electromagnetic Force Generated by the Solenoid Valve

According to Maxwell’ stress theory, the electromagnetic force acting on the spool can be expressed as(3)Fm=ψi,zev22μ0S0,where S0 denotes the area of the magnetic pole, μ0 denotes the permeability coefficient, and ψi,zev denotes the flux linkage through the main air gap, which is the model of coil current i and spool position zev:(4)ψ=i⋅nRm1+Rm2,where n denotes the number of coil turns, Rm1 denotes the magnetoresistance parameters of the working air gap, and Rm2 denotes the magnetoresistance parameters of secondary air gap. The mathematical models of Rm1 and Rm2 can be expressed as follows:(5)Rm1=0.4×10−3−zevπμ0S0,Rm2=ln2e+R/R2⋅π⋅μ0⋅ls,where 0.4×10−3−zev denotes the length of the working air gap, ls denotes the width of the secondary air gap, e denotes the length of the secondary air gap, and R denotes the radius of the spool. The parameters are marked in Figure 2.


### 3.2. Analysis of Electrical Characteristics of the Solenoid Valve Spool

Coil magnetic field strength is mainly determined by two factors: one is the magnitude of current, and the other is the back electromotive force. Therefore, the loop control valve coil circuit model is(6)ui=i⋅r+∂ψi,zev∂ii˙+∂ψi,zev∂sz˙ev,where r is the electric resistance of the solenoid coil, ∂ψi,zev/∂ii˙ denotes the back electromotive force (EMF) produced by the inductance of the coil, and ∂ψi,zev/∂sz˙ev denotes the back EMF produced by the motion of the spool.


### 3.3. Analysis of Hydraulic Characteristics of the Solenoid Valve Spool

When the valve spool is opened by electromagnetic force, the velocity and direction of brake fluid will change. In this paper, the space between the spool and the oil inlet of the solenoid valve is taken as the research object, as shown in Figure4. According to Leibniz Reynolds transmission theorem, the mathematical model of the object of study can be expressed as(7)ddt∫∫V∫v⇀ρdV=∮VFdS.Figure 4
Schematic diagram of hydrodynamic force.Dimensional parameters of the space consisting of the spool and seat are substituted into equation (7), and then, we can get(8)Fs=ρqevv0−ρqevvtcosα+pmA0+c1PtAtwsinα−PwAtcosα−PwA0+Atwsinα−Atcosα,where qev denotes the flow rate through the valve, ρ denotes the mass density of brake fluid, v0 denotes the flow velocity of brake fluid passing through inlet section of the valve orifice, A0 denotes the section area, vt is the average flow velocity at the throttle section, the section area is At, Pt denotes the average pressure at the throttle section, α denotes half of the cone angle corresponding to the valve seat, Pm denotes the average pressure at the inlet section of the valve orifice, the value of Pm can be acquired by main cylinder pressure sensor, Pw denotes the pressure of the brake cylinder, and Atw denotes the cone-shaped wall area surrounding the throttle section. Considering the uneven pressure distribution of brake fluid on the surface Atw, the compensation coefficient c1 is added.The flow rate of brake fluid through the valve seat is expressed as(9)qev=cdAt2Pm−Pwρ,where cd represents the flow parameters of brake fluid.According to Bernoulli equation in fluid mechanics,(10)Pt+12ρvt2=Pw+121−ζρvev2,(11)A0v0=Atvt=Aevvev,where vev denotes the average flow velocity at the outlet section of the valve and Aev denotes the section area of the valve. The brake fluid is affected by the friction of the pipe wall in the solenoid valve, so the mechanical energy loss coefficient of the brake fluid ζ is added.Combining equations (9)–(11), Pw can be expressed as(12)Pw=Pt+cd21+ζAt2Aev2−1Pm−Pw.Combining equations (8)–(12), steady state flow force on the spool can be expressed as(13)Fs=2cd2AtAtAev−cosα+Aev+c1cd21+ζAt2Aev2−1Atwsinα⋅Pm−Pw.When the solenoid valve is working, the spool will move up or down to change the wheel cylinder pressure. At this time, the transient flow force can be expressed as(14)Fst=ρLhcdW2ρPm−Pwz˙ev,where Lh represents the distance from A0 to At. According to [21], the transient flow force is affected by the speed of spool movement and the pressure difference. When the pressure difference of the solenoid valve is 20 MPa and the movement speed of the spool is 2 m/s, the transient hydrodynamic force is only 0.15 N. The value of the transient flow force is smaller than that of the steady state flow force and is not the main factor affecting the movement of the spool, so the transient hydrodynamic force can be ignored [21, 22].


## 3.1. Electromagnetic Force Generated by the Solenoid Valve

According to Maxwell’ stress theory, the electromagnetic force acting on the spool can be expressed as(3)Fm=ψi,zev22μ0S0,where S0 denotes the area of the magnetic pole, μ0 denotes the permeability coefficient, and ψi,zev denotes the flux linkage through the main air gap, which is the model of coil current i and spool position zev:(4)ψ=i⋅nRm1+Rm2,where n denotes the number of coil turns, Rm1 denotes the magnetoresistance parameters of the working air gap, and Rm2 denotes the magnetoresistance parameters of secondary air gap. The mathematical models of Rm1 and Rm2 can be expressed as follows:(5)Rm1=0.4×10−3−zevπμ0S0,Rm2=ln2e+R/R2⋅π⋅μ0⋅ls,where 0.4×10−3−zev denotes the length of the working air gap, ls denotes the width of the secondary air gap, e denotes the length of the secondary air gap, and R denotes the radius of the spool. The parameters are marked in Figure 2.


## 3.2. Analysis of Electrical Characteristics of the Solenoid Valve Spool

Coil magnetic field strength is mainly determined by two factors: one is the magnitude of current, and the other is the back electromotive force. Therefore, the loop control valve coil circuit model is(6)ui=i⋅r+∂ψi,zev∂ii˙+∂ψi,zev∂sz˙ev,where r is the electric resistance of the solenoid coil, ∂ψi,zev/∂ii˙ denotes the back electromotive force (EMF) produced by the inductance of the coil, and ∂ψi,zev/∂sz˙ev denotes the back EMF produced by the motion of the spool.


## 3.3. Analysis of Hydraulic Characteristics of the Solenoid Valve Spool

When the valve spool is opened by electromagnetic force, the velocity and direction of brake fluid will change. In this paper, the space between the spool and the oil inlet of the solenoid valve is taken as the research object, as shown in Figure4. According to Leibniz Reynolds transmission theorem, the mathematical model of the object of study can be expressed as(7)ddt∫∫V∫v⇀ρdV=∮VFdS.Figure 4
Schematic diagram of hydrodynamic force.Dimensional parameters of the space consisting of the spool and seat are substituted into equation (7), and then, we can get(8)Fs=ρqevv0−ρqevvtcosα+pmA0+c1PtAtwsinα−PwAtcosα−PwA0+Atwsinα−Atcosα,where qev denotes the flow rate through the valve, ρ denotes the mass density of brake fluid, v0 denotes the flow velocity of brake fluid passing through inlet section of the valve orifice, A0 denotes the section area, vt is the average flow velocity at the throttle section, the section area is At, Pt denotes the average pressure at the throttle section, α denotes half of the cone angle corresponding to the valve seat, Pm denotes the average pressure at the inlet section of the valve orifice, the value of Pm can be acquired by main cylinder pressure sensor, Pw denotes the pressure of the brake cylinder, and Atw denotes the cone-shaped wall area surrounding the throttle section. Considering the uneven pressure distribution of brake fluid on the surface Atw, the compensation coefficient c1 is added.The flow rate of brake fluid through the valve seat is expressed as(9)qev=cdAt2Pm−Pwρ,where cd represents the flow parameters of brake fluid.According to Bernoulli equation in fluid mechanics,(10)Pt+12ρvt2=Pw+121−ζρvev2,(11)A0v0=Atvt=Aevvev,where vev denotes the average flow velocity at the outlet section of the valve and Aev denotes the section area of the valve. The brake fluid is affected by the friction of the pipe wall in the solenoid valve, so the mechanical energy loss coefficient of the brake fluid ζ is added.Combining equations (9)–(11), Pw can be expressed as(12)Pw=Pt+cd21+ζAt2Aev2−1Pm−Pw.Combining equations (8)–(12), steady state flow force on the spool can be expressed as(13)Fs=2cd2AtAtAev−cosα+Aev+c1cd21+ζAt2Aev2−1Atwsinα⋅Pm−Pw.When the solenoid valve is working, the spool will move up or down to change the wheel cylinder pressure. At this time, the transient flow force can be expressed as(14)Fst=ρLhcdW2ρPm−Pwz˙ev,where Lh represents the distance from A0 to At. According to [21], the transient flow force is affected by the speed of spool movement and the pressure difference. When the pressure difference of the solenoid valve is 20 MPa and the movement speed of the spool is 2 m/s, the transient hydrodynamic force is only 0.15 N. The value of the transient flow force is smaller than that of the steady state flow force and is not the main factor affecting the movement of the spool, so the transient hydrodynamic force can be ignored [21, 22].


## 4. Pressure Estimation and Pressure Control Methods

The entire pressure estimation and pressure control system is shown in Figure5. The whole system is mainly composed of four parts: pressure estimation module, pressure control module, pressure PID, and current PID. In the pressure estimation module, the spool position is obtained using the SRCKF algorithm. The input of spool position estimation algorithm is ui, i, and Fs. Both ui and i are measured using sensors mounted on solenoid valves. Fs is calculated by equation (13). After the spool position is obtained, the wheel cylinder pressure can be calculated by the method described below.Figure 5
Overall structure diagram of the pressure estimation and pressure control system.In the pressure control algorithm, a spool position controller based on the sliding mode algorithm is adopted to adjust the WCP. The input of pressure control algorithm is spool positionzev and desired spool position znom. The relationship between nominal spool position znom and WCP is a nonlinear state equation, so it is necessary to convert WCP to znom through the PID algorithm. The output of pressure control algorithm is the desired coil current. But the solenoid valve is driven by PWM. Therefore, the PID algorithm is used to convert the current to PWM.


### 4.1. Introduction of Wheel Cylinder Pressure Estimation Method

The calculation method of the brake wheel cylinder pressure is mainly based on the P-V characteristic curve of the brake fluid. The volume increase of the brake fluid volume in each control cycle plus the original brake fluid volume can be used to obtain the total volume in the wheel cylinder. Then, the P-V characteristic curve check table can be used to obtain the pressure value in the brake wheel cylinder.


#### 4.1.1. Calculation of Wheel Cylinder Pressure during the Stage of Increasing Pressure

The brake fluid volume increment is determined by the opening of the valve. The volume increase of the brake fluid is as follows:(15)ΔV=∫qevdt,where qev denotes the brake fluid flow rate during pressurization.The calculation method of the wheel cylinder pressure in the pressurization stage is shown in Figure6. The brake fluid flow rate in the increasing pressure phase is determined by the displacement of the valve spool. The spool position is determined by the valve coil current. Therefore, the solution of the spool displacement is the key to the calculation of the wheel cylinder pressure.Figure 6
Schematic diagram of a method to calculate cylinder pressure.Combining equations (1) and (6), the equation of state for the displacement of solenoid valve spool and coil current can be obtained as follows:(16)x˙1x˙2x˙3=uiAi,zev−rAi,zevx1−i,zevx31mFmi,zev−FsΔP,zev−Fkzev−Cu⋅x3y=100x,,where the state variable is x=x1,x2,x3T=i,zev,z˙evT, A=∂ψi,zev/∂i, B=∂ψi,zev/∂zev, y=i00, and FsΔP,zev can be obtained by equation (13).For equation (16), the SRCKF algorithm is used to estimate the spool displacement and coil current. The SRCKF algorithm is shown in Figure 7.Figure 7
Schematic diagram of SRCKF.As can be seen from Figure4, the mathematical model of the spool displacement and the control valve orifice area is(17)At=πAoπ+zcosα2−Aoπ.Combining equations (17) and (9), the flow rate of the solenoid valve during the increase phase can be obtained:(18)qev=cdπAoπ+zcosα2−Aoπ2Pm−Pwρ.Combining equations (17) and (18), the pressure of the wheel cylinder can be obtained:(19)Pwe=cdKPw∫0tAtzsgnPm−Pw2Pm−Pwρdt.


#### 4.1.2. Calculation of Wheel Cylinder Pressure during the Stage of Pressure Reduction

During the phase, the brake fluid increment can be expressed as(20)ΔV=−∫qavdt,where qav denotes the flow rate of the brake fluid during decompression. Since the valve port is fully open during the depressurization phase, the brake fluid flow is available according to the Bernoulli equation:(21)qav=cdAav2Pwc−Paccuρ.Then, the flow rate is integrated, and the volume increase of the brake fluid during the decompression phase can be obtained:(22)ΔV=−∫cdAav2Pwc−Paccuρdt.Finally, by adding the original brake fluid volume and the current volume increment, the cylinder pressure in the brake wheel cylinder during the decompression stage can be obtained by using the PV characteristic curve look-up table method:(23)P=fpvVw+ΔV.


### 4.2. Wheel Cylinder Pressure Control Method

The pressure control of the valve is also divided into a pressure increasing phase and a pressure reducing phase. The two phases are controlled differently. During the decompression phase, the valve port is completely opened to achieve the purpose of rapid decompression. The control method in the pressure increasing phase is relatively more complicated than that in the pressure reducing phase. The pressure control strategy in the pressure increasing phase is shown in Figure5. The input parameters mainly include the estimated value of the wheel cylinder pressure, the target value of the wheel cylinder pressure, and the displacement of the solenoid valve spool. The control signal in the control strategy is the PWM duty cycle, which can be obtained by coil current conversion.The analysis in Section4.1.1 shows that the brake fluid flow rate is qev=cdAt2Pm−Pw/ρ, and the flow area At varies with the valve spool displacement in the pressure increasing phase. The valve spool displacement is determined by the coil current. Therefore, by adjusting the coil current, the increment of brake fluid can be controlled in the pressure increasing phase, and then the brake wheel cylinder pressure can be controlled.As shown in Figure8, the conversion between the target value of coil current and the target value of PWM signal depends on the PID algorithm:(24)Dpwm=Kp_dutyΔiet+Ki_duty∫Δiedt+Kd_dutyΔiet−Δiet−1,Δie=inom−i,where Dpwm denotes the target value of PWM signal, Kp_duty denotes the proportional coefficients of the PID algorithm, Ki_duty denotes the integral coefficients of the PID algorithm, Kd_duty denotes the differential coefficients of the PID algorithm, inom denotes the target value of coil current, and i denotes the actual value of solenoid valve coil.Figure 8
Schematic diagram of cylinder pressure control strategy.Similarly, the target value of the wheel-cylinder pressure and the target value of the spool distance are converted by the PID algorithm:(25)znom=Kp_pΔPet+Ki_p∫ΔPetdt+Kd_pΔPet−ΔPet−1,ΔPet=Pnom−Pwe,where znom denotes the target value of the valve spool distance, Kp_duty denotes the proportional coefficients of the PID algorithm, Ki_duty denotes the integral coefficients of the PID algorithm, Kd_duty denotes the differential coefficients of the PID algorithm, Pnom denotes the wheel cylinder pressure control target value, and Pwe denotes the current brake pressure of the brake wheel cylinder.Relying on the PID algorithm, the control of the brake wheel cylinder pressure is converted to the control of the valve spool displacement. Then, the sliding mode variable structure control algorithm is used to solve the nonlinear problem between the wheel cylinder pressure and the valve spool displacement.The sliding-mode surface is chosen as(26)s=z˙ev−z˙nom+kxzev−znom,where kx is the weight factor；when s is equal to 0，then z˙ev−z˙nom⟶0 and z−znom⟶0.By differentiatings, thus the following equation is derived：(27)s˙=z¨ev−z¨nom+kz.z˙ev−z˙nom.Exponential reaching law is chosen:(28)z¨ev−z¨nom+kxz˙ev−z˙nom=−εsgns−kss.According to equations (1)–(3), the following equation is derived:(29)z¨ev=i2n22μ0S00.4×10−3−zev/πμ0S0+ln2e+R/R/2⋅π⋅μ0⋅ls2+−Fs−Fk−Cu⋅z˙evm.According to equations (27) and (29), the following equation is derived:(30)i2Jzev+Lzev,z˙ev,ΔP−z¨nom+kxz˙ev−z˙nom=−εsgns−kss,Jx=n22μ0S00.4×10−3−zev/πμ0S0+ln2e+R/R/2×π×μ0×ls2,Lzev,z˙ev,ΔP=−Fs−Fk−Cu⋅z˙evm.The relationship between the target value of brake wheel cylinder pressure and the target value of solenoid valve coil current is as follows:(31)i=z¨nom−Lzev,z˙ev,ΔP−kzz˙ev−z˙nom−εsgns−kssJzev.


## 4.1. Introduction of Wheel Cylinder Pressure Estimation Method

The calculation method of the brake wheel cylinder pressure is mainly based on the P-V characteristic curve of the brake fluid. The volume increase of the brake fluid volume in each control cycle plus the original brake fluid volume can be used to obtain the total volume in the wheel cylinder. Then, the P-V characteristic curve check table can be used to obtain the pressure value in the brake wheel cylinder.


### 4.1.1. Calculation of Wheel Cylinder Pressure during the Stage of Increasing Pressure

The brake fluid volume increment is determined by the opening of the valve. The volume increase of the brake fluid is as follows:(15)ΔV=∫qevdt,where qev denotes the brake fluid flow rate during pressurization.The calculation method of the wheel cylinder pressure in the pressurization stage is shown in Figure6. The brake fluid flow rate in the increasing pressure phase is determined by the displacement of the valve spool. The spool position is determined by the valve coil current. Therefore, the solution of the spool displacement is the key to the calculation of the wheel cylinder pressure.Figure 6
Schematic diagram of a method to calculate cylinder pressure.Combining equations (1) and (6), the equation of state for the displacement of solenoid valve spool and coil current can be obtained as follows:(16)x˙1x˙2x˙3=uiAi,zev−rAi,zevx1−i,zevx31mFmi,zev−FsΔP,zev−Fkzev−Cu⋅x3y=100x,,where the state variable is x=x1,x2,x3T=i,zev,z˙evT, A=∂ψi,zev/∂i, B=∂ψi,zev/∂zev, y=i00, and FsΔP,zev can be obtained by equation (13).For equation (16), the SRCKF algorithm is used to estimate the spool displacement and coil current. The SRCKF algorithm is shown in Figure 7.Figure 7
Schematic diagram of SRCKF.As can be seen from Figure4, the mathematical model of the spool displacement and the control valve orifice area is(17)At=πAoπ+zcosα2−Aoπ.Combining equations (17) and (9), the flow rate of the solenoid valve during the increase phase can be obtained:(18)qev=cdπAoπ+zcosα2−Aoπ2Pm−Pwρ.Combining equations (17) and (18), the pressure of the wheel cylinder can be obtained:(19)Pwe=cdKPw∫0tAtzsgnPm−Pw2Pm−Pwρdt.


### 4.1.2. Calculation of Wheel Cylinder Pressure during the Stage of Pressure Reduction

During the phase, the brake fluid increment can be expressed as(20)ΔV=−∫qavdt,where qav denotes the flow rate of the brake fluid during decompression. Since the valve port is fully open during the depressurization phase, the brake fluid flow is available according to the Bernoulli equation:(21)qav=cdAav2Pwc−Paccuρ.Then, the flow rate is integrated, and the volume increase of the brake fluid during the decompression phase can be obtained:(22)ΔV=−∫cdAav2Pwc−Paccuρdt.Finally, by adding the original brake fluid volume and the current volume increment, the cylinder pressure in the brake wheel cylinder during the decompression stage can be obtained by using the PV characteristic curve look-up table method:(23)P=fpvVw+ΔV.


## 4.1.1. Calculation of Wheel Cylinder Pressure during the Stage of Increasing Pressure

The brake fluid volume increment is determined by the opening of the valve. The volume increase of the brake fluid is as follows:(15)ΔV=∫qevdt,where qev denotes the brake fluid flow rate during pressurization.The calculation method of the wheel cylinder pressure in the pressurization stage is shown in Figure6. The brake fluid flow rate in the increasing pressure phase is determined by the displacement of the valve spool. The spool position is determined by the valve coil current. Therefore, the solution of the spool displacement is the key to the calculation of the wheel cylinder pressure.Figure 6
Schematic diagram of a method to calculate cylinder pressure.Combining equations (1) and (6), the equation of state for the displacement of solenoid valve spool and coil current can be obtained as follows:(16)x˙1x˙2x˙3=uiAi,zev−rAi,zevx1−i,zevx31mFmi,zev−FsΔP,zev−Fkzev−Cu⋅x3y=100x,,where the state variable is x=x1,x2,x3T=i,zev,z˙evT, A=∂ψi,zev/∂i, B=∂ψi,zev/∂zev, y=i00, and FsΔP,zev can be obtained by equation (13).For equation (16), the SRCKF algorithm is used to estimate the spool displacement and coil current. The SRCKF algorithm is shown in Figure 7.Figure 7
Schematic diagram of SRCKF.As can be seen from Figure4, the mathematical model of the spool displacement and the control valve orifice area is(17)At=πAoπ+zcosα2−Aoπ.Combining equations (17) and (9), the flow rate of the solenoid valve during the increase phase can be obtained:(18)qev=cdπAoπ+zcosα2−Aoπ2Pm−Pwρ.Combining equations (17) and (18), the pressure of the wheel cylinder can be obtained:(19)Pwe=cdKPw∫0tAtzsgnPm−Pw2Pm−Pwρdt.


## 4.1.2. Calculation of Wheel Cylinder Pressure during the Stage of Pressure Reduction

During the phase, the brake fluid increment can be expressed as(20)ΔV=−∫qavdt,where qav denotes the flow rate of the brake fluid during decompression. Since the valve port is fully open during the depressurization phase, the brake fluid flow is available according to the Bernoulli equation:(21)qav=cdAav2Pwc−Paccuρ.Then, the flow rate is integrated, and the volume increase of the brake fluid during the decompression phase can be obtained:(22)ΔV=−∫cdAav2Pwc−Paccuρdt.Finally, by adding the original brake fluid volume and the current volume increment, the cylinder pressure in the brake wheel cylinder during the decompression stage can be obtained by using the PV characteristic curve look-up table method:(23)P=fpvVw+ΔV.


## 4.2. Wheel Cylinder Pressure Control Method

The pressure control of the valve is also divided into a pressure increasing phase and a pressure reducing phase. The two phases are controlled differently. During the decompression phase, the valve port is completely opened to achieve the purpose of rapid decompression. The control method in the pressure increasing phase is relatively more complicated than that in the pressure reducing phase. The pressure control strategy in the pressure increasing phase is shown in Figure5. The input parameters mainly include the estimated value of the wheel cylinder pressure, the target value of the wheel cylinder pressure, and the displacement of the solenoid valve spool. The control signal in the control strategy is the PWM duty cycle, which can be obtained by coil current conversion.The analysis in Section4.1.1 shows that the brake fluid flow rate is qev=cdAt2Pm−Pw/ρ, and the flow area At varies with the valve spool displacement in the pressure increasing phase. The valve spool displacement is determined by the coil current. Therefore, by adjusting the coil current, the increment of brake fluid can be controlled in the pressure increasing phase, and then the brake wheel cylinder pressure can be controlled.As shown in Figure8, the conversion between the target value of coil current and the target value of PWM signal depends on the PID algorithm:(24)Dpwm=Kp_dutyΔiet+Ki_duty∫Δiedt+Kd_dutyΔiet−Δiet−1,Δie=inom−i,where Dpwm denotes the target value of PWM signal, Kp_duty denotes the proportional coefficients of the PID algorithm, Ki_duty denotes the integral coefficients of the PID algorithm, Kd_duty denotes the differential coefficients of the PID algorithm, inom denotes the target value of coil current, and i denotes the actual value of solenoid valve coil.Figure 8
Schematic diagram of cylinder pressure control strategy.Similarly, the target value of the wheel-cylinder pressure and the target value of the spool distance are converted by the PID algorithm:(25)znom=Kp_pΔPet+Ki_p∫ΔPetdt+Kd_pΔPet−ΔPet−1,ΔPet=Pnom−Pwe,where znom denotes the target value of the valve spool distance, Kp_duty denotes the proportional coefficients of the PID algorithm, Ki_duty denotes the integral coefficients of the PID algorithm, Kd_duty denotes the differential coefficients of the PID algorithm, Pnom denotes the wheel cylinder pressure control target value, and Pwe denotes the current brake pressure of the brake wheel cylinder.Relying on the PID algorithm, the control of the brake wheel cylinder pressure is converted to the control of the valve spool displacement. Then, the sliding mode variable structure control algorithm is used to solve the nonlinear problem between the wheel cylinder pressure and the valve spool displacement.The sliding-mode surface is chosen as(26)s=z˙ev−z˙nom+kxzev−znom,where kx is the weight factor；when s is equal to 0，then z˙ev−z˙nom⟶0 and z−znom⟶0.By differentiatings, thus the following equation is derived：(27)s˙=z¨ev−z¨nom+kz.z˙ev−z˙nom.Exponential reaching law is chosen:(28)z¨ev−z¨nom+kxz˙ev−z˙nom=−εsgns−kss.According to equations (1)–(3), the following equation is derived:(29)z¨ev=i2n22μ0S00.4×10−3−zev/πμ0S0+ln2e+R/R/2⋅π⋅μ0⋅ls2+−Fs−Fk−Cu⋅z˙evm.According to equations (27) and (29), the following equation is derived:(30)i2Jzev+Lzev,z˙ev,ΔP−z¨nom+kxz˙ev−z˙nom=−εsgns−kss,Jx=n22μ0S00.4×10−3−zev/πμ0S0+ln2e+R/R/2×π×μ0×ls2,Lzev,z˙ev,ΔP=−Fs−Fk−Cu⋅z˙evm.The relationship between the target value of brake wheel cylinder pressure and the target value of solenoid valve coil current is as follows:(31)i=z¨nom−Lzev,z˙ev,ΔP−kzz˙ev−z˙nom−εsgns−kssJzev.


## 5. Simulation Results

The brake wheel cylinder pressure estimation and control algorithms mentioned in this paper are verified by software cosimulation. Software cosimulation is shown in Figure9. Both pressure estimation and pressure control algorithms were modeled using Matlab/Simulink software. The solenoid valve in the simulation is modeled by Simulink, and the other hydraulic components are modeled by Amesim.Figure 9
Schematic diagram of software cosimulation.The execution period of pressure estimation algorithm and pressure control algorithm is 10 ms. The pressure estimation algorithm requires the solenoid valve opening time parameter, which is calculated by the pressure control algorithm. The pressure control algorithm section requires the wheel cylinder pressure target value and the pressure estimate difference. The coil current, voltage parameters, and master cylinder pressure are used as input parameters to the pressure estimation algorithm model and the control algorithm model, respectively.Parameters of the valve model are listed in Table1. Parameters can be referred from [23–25].Table 1
Parameters of the valve model.
VariableSymbolValueMass of the valve spoolm0.004kgNumber of valve coil windingsn300The area of the magnetic poleS010−4m2Preload force of springF01NStiffness coefficient of the return springKk1000N/mWidth of secondary air gapls6×10−4mRadius of the spoolR7×10−3mElectric resistance of the solenoid coilr6ΩMass density of brake fluidρ860kg/m3Inlet section area of valveA03.8×10−7m2Cone angle of valve seat2α120deg


### 5.1. Verification of Solenoid Valve Spool Position Estimation

The key to the accuracy of the pressure value lies in the spool displacement estimation. Therefore, the spool displacement estimation algorithm needs to be verified. In the simulation verification, the spool stroke of the solenoid valve is forced to make a cosine curve. The purpose of this is to verify the spool estimation algorithm based on SRCKF. During this process, the MCP is set to make a step change every 37.5 ms to see whether SRCKF is robust to MCP changes. The simulation curve is shown in Figures10–13.Figure 10
The curve of estimated spool position value and real value.Figure 11
The relative error between estimated spool position value and real value.Figure 12
The curve of MCP and WCP.Figure 13
The curve of estimated coil current value and real value.As shown in Figure10, despite the error, the observed curve still tracks the actual spool position well. The absolute error between the actual position of the spool and the estimated value is within 0.01 mm. The changes in MCP and WCP have little effect on the error of spool position estimation, which proves the robustness of SRCKF. It can be seen from Figure 10 that the estimated value of coil current is also consistent with the real value.


### 5.2. Verification of Pressure Estimation

Firstly, the wheel cylinder pressure estimation algorithm is verified. Figure14 shows the valve control command. The duty cycle of the PWM starts from 40%, and the cycle is boosted by 10% in 0.02 s. After reaching 100%, it is restored to 40%. As shown in Figure 15, the master cylinder pressure is set to vary between 30 bar and 80 bar. This setting is to simulate the driver’s emergency braking under dangerous driving conditions. As shown in Figure 15, the estimated value of the wheel cylinder pressure and the actual value substantially coincide. Figure 16 shows the deviation curve between the estimated value and the actual value. It can be seen that the deviation rate between the estimated value and the actual value is about +6%.Figure 14
Schematic diagram of solenoid valve control instruction.Figure 15
Curve of estimated pressure value.Figure 16
Curve of error value.


### 5.3. Verification of Pressure Control

The simulation verification results of the wheel cylinder pressure control algorithm are shown in Figures17–19. The master cylinder pressure is set in AMESim to reach 90 bar in about 0.05 seconds and is kept constant. Figure 17 shows the simulation verification effect of the pressure control. The actual value of the wheel cylinder pressure basically coincides with the target value. As shown in Figure 18, the error is relatively large at 0.1 s, 0.25 s, and 0.4 s. It is caused by the integral operation in the wheel cylinder pressure estimation algorithm. As can be seen from Figure 19, the actual value of the spool distance closely follows the target value. The actual value of the spool displacement closely follows the target value. At the initial stage of boosting, the spool is fully opened, and the brake wheel cylinder pressure is increased at the highest rate. When the actual value is gradually equal to the target value, the spool displacement is gradually zeroed to reduce the boost rate.Figure 17
Curve of estimated and actual cylinder pressure.Figure 18
Curve of error value.Figure 19
Curve of valve spool position.


## 5.1. Verification of Solenoid Valve Spool Position Estimation

The key to the accuracy of the pressure value lies in the spool displacement estimation. Therefore, the spool displacement estimation algorithm needs to be verified. In the simulation verification, the spool stroke of the solenoid valve is forced to make a cosine curve. The purpose of this is to verify the spool estimation algorithm based on SRCKF. During this process, the MCP is set to make a step change every 37.5 ms to see whether SRCKF is robust to MCP changes. The simulation curve is shown in Figures10–13.Figure 10
The curve of estimated spool position value and real value.Figure 11
The relative error between estimated spool position value and real value.Figure 12
The curve of MCP and WCP.Figure 13
The curve of estimated coil current value and real value.As shown in Figure10, despite the error, the observed curve still tracks the actual spool position well. The absolute error between the actual position of the spool and the estimated value is within 0.01 mm. The changes in MCP and WCP have little effect on the error of spool position estimation, which proves the robustness of SRCKF. It can be seen from Figure 10 that the estimated value of coil current is also consistent with the real value.


## 5.2. Verification of Pressure Estimation

Firstly, the wheel cylinder pressure estimation algorithm is verified. Figure14 shows the valve control command. The duty cycle of the PWM starts from 40%, and the cycle is boosted by 10% in 0.02 s. After reaching 100%, it is restored to 40%. As shown in Figure 15, the master cylinder pressure is set to vary between 30 bar and 80 bar. This setting is to simulate the driver’s emergency braking under dangerous driving conditions. As shown in Figure 15, the estimated value of the wheel cylinder pressure and the actual value substantially coincide. Figure 16 shows the deviation curve between the estimated value and the actual value. It can be seen that the deviation rate between the estimated value and the actual value is about +6%.Figure 14
Schematic diagram of solenoid valve control instruction.Figure 15
Curve of estimated pressure value.Figure 16
Curve of error value.


## 5.3. Verification of Pressure Control

The simulation verification results of the wheel cylinder pressure control algorithm are shown in Figures17–19. The master cylinder pressure is set in AMESim to reach 90 bar in about 0.05 seconds and is kept constant. Figure 17 shows the simulation verification effect of the pressure control. The actual value of the wheel cylinder pressure basically coincides with the target value. As shown in Figure 18, the error is relatively large at 0.1 s, 0.25 s, and 0.4 s. It is caused by the integral operation in the wheel cylinder pressure estimation algorithm. As can be seen from Figure 19, the actual value of the spool distance closely follows the target value. The actual value of the spool displacement closely follows the target value. At the initial stage of boosting, the spool is fully opened, and the brake wheel cylinder pressure is increased at the highest rate. When the actual value is gradually equal to the target value, the spool displacement is gradually zeroed to reduce the boost rate.Figure 17
Curve of estimated and actual cylinder pressure.Figure 18
Curve of error value.Figure 19
Curve of valve spool position.


## 6. Experiments

In this paper, the pressure estimation and wheel cylinder pressure control algorithm designed in this paper are verified by software simulation. Then, the hardware-in-loop experiment is used to further verify the algorithm. The bench is shown in Figure20, and the symbol 1 shows the brake and brake wheel cylinder of the rear axle of the car. The symbol 2 is the PXI chassis of National Instruments. The device numbered 3 is a controller that is responsible for running the pressure estimation and pressure control algorithm. The device numbered 4 is a computer workstation responsible for compiling and downloading the algorithm into the controller. The devices numbered 5 and 6 are, respectively, the automobile steering wheel and the brake pedal. The device numbered 7 is the accelerator pedal. The device numbered 8 is a brake caliper of the front axle, and the device shown by reference numeral 9 is a wheel cylinder pressure sensor for collecting wheel cylinder pressure data. The device shown at 10 is a solenoid valve driving circuit board. The numeral 11 is an HCU, and the numeral 12 is a main cylinder.Figure 20
Architecture diagram of HIL.As shown in Figure21, at the beginning of the experiment, the master cylinder pressure was stabilized at 80 bar by means of a motor pump. The wheel cylinder pressure increased from 5 seconds, and the wheel cylinder pressure reached 65.2 bar at 5.506 seconds. The supercharging rate reached 129 bar/s during the entire pressurization process, which was basically consistent with the target value. Figure 22 shows the valve coil current measurement data and the target value data curve. It can be seen that the coil current measurement value and the target value are basically consistent. Therefore, it can be determined that the position of the solenoid valve spool can be accurately controlled, and it can be determined that the algorithm can accurately control the brake fluid flow.Figure 21
Curve of data detail.Figure 22
Curve of coil current.Figure23 shows the measured data of the wheel cylinder pressure under the stepped boost condition. Under this condition, the master cylinder pressure data are always maintained at around 110 bar. At the start of the experiment for 3 seconds, the controller controls the solenoid valve to pressurize. After 40 ms, the brake wheel cylinder pressure reached the target value of 20 bar. After another 0.2 seconds, the pressure is again increased. As shown in Figure 23, SRCKF, extended Kalman filter (EKF), and unscented Kalman filter (UKF) are used to estimate the wheel cylinder pressure, respectively. The value estimated by other filter methods has more error than the value estimated by SRCKF. The SRCKF-based estimation algorithm shows more accuracy than other methods. There is a small difference between the actual value and the value estimated by SRCKF. Figure 24 shows the valve coil current data. At 3 seconds, 3.2 seconds, 3.4 seconds, and 3.6 seconds, the loop control valve coil current rapidly drops to zero and the spool position reaches a maximum. At this time, the brake fluid quickly flows into the brake wheel cylinder to ensure that the wheel cylinder pressurization rate reaches the maximum. This ensures that the wheel cylinder pressure closely follows the target value.Figure 23
Curve of stepped pressurization.Figure 24
Curve of coil current.In order to compare the pressure control effects of the proposed pressure control method and the on-off threshold control method, a slope WCP increase test was implemented. This method has been introduced in many references [26, 27]. The result of on-off threshold is shown in Figure 25. Unlike the linear controller, the solenoid valve current can only be switched on or off, so the spool position is fully opened or closed. The wheel cylinder pressure cannot accurately follow the target value, and the error is large. Figure 26 shows the coil current curve, and the coil current can only be fully opened or completely closed.Figure 25
The curve of WCP pressure used by on-off threshold control.Figure 26
The curve of coil current used by on-off threshold control.Figure27 shows the result of the slope WCP increase controlled by the proposed method. The filtered WCP can follow the desired WCP pressure well by the switching valve. The control effect of proposed method by the switch value is similar to the effect of using a proportional valve in [28]. Figure 28 shows the coil current curve controlled by the proposed method.Figure 27
The curve of WCP pressure used by the proposed control method.Figure 28
The curve of coil current used by the proposed control method.


## 7. Conclusion

Firstly, this paper studies the working mechanism and characteristics of the solenoid valve of HCU. Then, according to the PV characteristics, the pressure estimation algorithm and pressure control method of brake wheel cylinder are designed. Finally, the pressure estimation and pressure control algorithm are verified by HIL, and the following conclusions are obtained:(1)
The valve is an on-off switching solenoid valve. Electromagnetic force and hydraulic force together affect the position of the valve spool. The change in the position of the valve spool will affect the brake fluid flow into the brake wheel cylinder. Based on this, the state equation is established. Then, the position of the valve spool is calculated by the square root volume Kalman filter algorithm.(2)
The electromagnetic force can be effectively adjusted by changing the coil current of the valve. The sliding mode variable structure algorithm is used to adjust the position of the valve spool, so as to change the brake fluid flow into the wheel cylinder. Finally, the purpose of accurately adjusting the brake wheel cylinder pressure was achieved.



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*Source: 6576297-2020-07-14.xml*