# Design, Modeling, and Analysis of a Novel Hydraulic Energy-Regenerative Shock Absorber for Vehicle Suspension

Authors: Junyi Zou; Xuexun Guo; Lin Xu; Gangfeng Tan; Chengcai Zhang; Jie Zhang
Journal: Shock and Vibration
 (2017)

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## Abstract

To reduce energy consumption or improve energy efficiency, the regenerative devices recently have drawn the public’s eyes. In this paper, a novel hydraulic energy-regenerative shock absorber (HERSA) is developed for vehicle suspension to regenerate the vibration energy which is dissipated by conventional viscous dampers into heat waste. At first, the schematic of HERSA is presented and a mathematic model is developed to describe the characteristic of HERSA. Then the parametric sensitivity analysis of the vibration energy is expounded, and the ranking of their influences isk1≫m2>m1>k2≈cs. Besides, a parametric study of HERSA is adopted to research the influences of the key parameters on the characteristic of HERSA. Moreover, an optimization of HERSA is carried out to regenerate more power as far as possible without devitalizing the damping characteristic. To make the optimization results more close to the actual condition, the displacement data of the shock absorber in the road test is selected as the excitation in the optimization. The results show that the RMS of regenerated energy is up to 107.94 W under the actual excitation. Moreover it indicates that the HERSA can improve its performance through the damping control.


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## Body

## 1. Introduction

With the energy consumption rising rapidly, the energy crisis is being more and more urgent. The proportion of transportation energy consumption increases year by year, and the percent of which will come up to 26%. In general, the transportation of people and goods accounts for about 25% of total world energy consumption. Passenger transportation, in particular, light-duty vehicles, accounts for most transportation energy consumption, with light-duty vehicles consuming more energy than all modes of freight transportation, including heavy trucks, marine, and rail combined [1]. So a great number of countries have initiated the development of renewable power. Among this, the vibration energy of vehicle is one of the sources that can be harvested. In Figure 1 [2], the vehicle energy flows of a 2.5 L 2005 Camry are demonstrated. And Figure 1 shows that most fuel energy is wasted. Therefore the energy regeneration can be considered as a new technology of energy saving, such as regenerative braking and regenerative suspension.Figure 1
Vehicle energy flows of a 2.5 L 2005 Camry.As to energy harvesting, it can be traced back to many years ago. Okada and Harada [3] demonstrated an electrodynamic regenerative damper, and the power was harvested by a linear motor in the system. Suda and Shiiba [4] designed a multiple suspension which could realize the active control and energy regeneration. The active control strategy of energy-regenerative shock absorber was improved. Roshani et al. [5] conducted an experimental program to evaluate the potential of harvesting energy from roadways using piezoelectric materials, and it showed that the quantity and arrangement of the piezoelectric sensors alter the applied stresses, which leaded to variations in the generated output power. Zuo et al. [6] developed an electromagnetic energy harvester which could regenerate 16~64 W power at 0.25~0.5 m/s root mean square (RMS) suspension velocity. This study focused on the finite element method which carried out the analysis of magnetic field and optimization design. Li et al. [7] developed a shock absorber based on a permanent magnetic generator and a rack-pinion mechanism for energy harvesting and vibration damping. A peak power of 68 W and average power of 19 W could be attained at 48 km/h on a campus road. Singh and Satpute [8] designed an electromagnetic energy harvesting shock absorber, and a simulation with actual road excitation data indicated that the system could harvest 15 W of the average power from each wheel. Tang and Zuo [9] proposed a vibration energy harvester which composed of a spring-mass system. Comparison among the characteristics of dual-mass and single-mass was analyzed. The results also indicated that the harvesting power from vehicle suspension was proportional to tire stiffness and road vertical excitation spectrum. Montazeri-Gh and Soleymani [10] researched an energy storage system (ESS) in hybrid electric vehicles, and the simulation results revealed that the use of hybrid ESS could improve the efficiency of the batteries, and it could increase their working life as the active suspension (AS) load fluctuations were transferred from the batteries to the capacitors. Xie and Wang [11] proposed a dual-mass piezoelectric bar harvester which composed of a spring-mass system connected by a piezoelectric bar transducer which is equivalent to a spring and a damper in a mathematics model. And a power up to 738 W could be realized for a practical design of the harvester with a width and height of the piezoelectric bar of 0.015 m and 0.1 m, respectively. Wang et al. [12] designed a regenerative hydraulic shock absorber system which converted oscillatory motion of a vehicle suspension into unidirectional rotary motion of a generator. The power of 260 W and the efficiency of 40% were achieved by a shock absorber with piston rod dimensions of 50/30 mm under sinusoidal excitation of 1 Hz frequency and 25 mm amplitude when the accumulator capacity is set to 0.32 L with the load resistance 20 Ω. The appropriate damping characteristics could be realized by using variable load resistances and accumulator capacities. Guo et al. [13] developed an evaluation of energy harvesting shock absorbers on various vehicles, including passenger cars, buses, and trucks. An optimal analysis was developed to improve performance of ride comfort and road holding. Galluzzi et al. [14] applied a motion rectifier to improve energy recovery by constraining the motion of the electric motor to a single sense of rotation. This strategy can potentially reduce inertial issues related to zero-speed crossing and motion inversion; thus it could lead to the better conversion efficiency. Zuo and Zhang [15] investigated the performance of suspension with electromagnetic harvester. The tradeoff among energy harvesting, ride comfort, and road handling was analyzed. The study suggested that the road roughness, tire stiffness, and vehicle speed were greatly related to energy regenerating. 100~400 W average power was available at 60 mph on good and average roads. Fang et al. [16, 17] developed an electromagnetic shock absorber which could recover energy 200 W at the sinusoidal excitation of 10 Hz-3 mm. The energy harvesting efficiency decreased with the excitation frequency increase. And an optimal algorithm was proposed to achieve active control and power maximization. Kammer and Olgac [18] conducted a concept study of a delayed-feedback vibration absorber to enhance energy harvesting, in which the delayed resonator theory was used for the energy harvesting purpose. Gong et al. [19] investigated the characteristic of a hydraulic-electricity energy-regenerative suspension. The optimization based on ride comfort and energy regeneration was obtained. Huang et al. [20] proposed a systematic methodology for predicting and optimizing the performance of an energy regeneration suspension system to efficiently capture the vibratory energy induced by the road irregularities. The method provided a graphic design guideline for the selection of stiffness and damping coefficients aimed at either best ride comfort or maximum energy harvesting.The current article proposed a hydraulic electromagnetic shock absorber system. The modeling, analysis, simulation, and optimization of it are developed. And the analysis of the vibration energy is demonstrated to indicate that the potential of energy regeneration is immense. Thereafter, a parameter study and an optimization of HERSA are designed to improve the performance of it.


## 2. Schematic and Modeling of HERSA

### 2.1. System Configuration

The schematic of HERSA is described in Figure1. The structure contains three components: a mechanical part which consists of a cylinder and a piston rod part; a hydraulic rectifier part which consists of accumulator, a hydraulic motor and pipelines; an energy-regenerative part which consists of a generator and a charging circuit including capacitances, inductances, and external loads. The piston in cylinder is distinguished from traditional shock absorber. The rebound valve and compression valve are removed, and only the by-pass valve and compensation valve are kept in the piston valve and bottom valve, respectively. In addition, the piston rod is hollow so that the fluid can flow to external parts.As shown in Figure2, the structure of HERSA is designed based on the conventional one. It has three tubes which include recovery tube, compression tube, and reservoir tube. However, in HERSA, the piston rod is hollow, so the fluid can flow through it to energy harvesting device. The rebound valve in piston and the compression valve in base valve system are wiped off. The hydraulic motor is connected with a generator via a shaft coupler. The energy-regenerative part has a common rotating mechanism which can be founded in some references.Figure 2
Schematic of HERSA. (a) The assembly diagram of HERSA. (b) The equivalent diagram of HERSA.
(a)
(b)When in the extension stroke, the fluid flows from rebound chamber to hollow piston rod, then flows through the hollow channel in piston rod, along the pipeline to the hydraulic pump, flows through the hydraulic motor to the reservoir tube, and passes the replenishing valve back to the compression chamber at last. In this stroke, most energy can be harvested, and the external load can be adjusted to achieve semiactive suspension.When in the compression stroke, the process is a little more complicated and the flow process can be divided into two parts:(1)
At first, because of the small cracking pressure, most of the fluid flows through the by-pass valve from compression chamber to replenishing chamber;(2)
After step (1), the upper chamber will be filled with oil. There is a volumetric difference between the upper and lower chamber because of the existence of piston rod. Just because of the volume difference, the residual oil in lower chamber will flow through the hollow piston to the regenerative part. As the volume of piston rod is small, so the volume of oil which flows into hydraulic motor is small too, and finally the harvested energy is little.


### 2.2. Mathematic Model of HERSA

Based on the working principle of HERSA shown in the Figure2, a mathematic model is proposed to demonstrate the system dynamics, such as the damping characteristic. In the system, the hydraulic flow and generator circuit are important to the characteristic.In the shock absorber, the damping force can be defined below:(1)Fc=PfSf-PySy,where Pf and Py are, respectively, pressure of upper and inferior chamber and Sf and Sy are the ring area and surface area of piston.While taking into account internal leakage in the system, it is understood that the fluid should flow through the check valve, the pipeline, and the hydraulic motor-generator circuit. The damping force is dependent on the three parts above. To describe the damping characteristic in detail, the two aspects, the hydraulic and the circuit system, are described, respectively.


#### 2.2.1. Modeling of the Hydraulic System

In the extension stroke, the fluid firstly flows through the elbow in the hollow piston rod. This elbow can lead to the pressure partial loss, so the pressure drop can be presented by(2)ΔPjc=ερvjc2,where ΔPjc is the pressure drop of elbows in the hydraulic system; ε is the local resistance coefficient; ρ is the density of hydraulic oil; vjc is the flow velocity of the oil in this area.Then the fluid flows through the hollow piston rod; the hollow channel can be simplified as a pipeline of short length. Assuming the fluid is in laminar flow state, so the pressure drop can be presented by(3)ΔPl=λρllvl22.In the rubber hose, there are the common equations(4)λ=80Re(5)Re=2rlvluv.Combining (4) with (5), (3) can be presented by(6)ΔPl=10uvρllvlrl2,where ΔPl is the pressure drop in pipeline; λ is the coefficient of tube friction; ll is the length of pipeline; vl is the flow velocity of oil; rl is the radius of pipeline; Re is the Reynolds number; uv is the kinematic viscosity of oil.The valves in piston valve or base valve can lead to flow pressure drop; the check valves above are regarded as thin-wall holes, so the pressure drop can be presented by(7)Qi=CdSi2ΔPiρ(8)ΔPi=Qi2ρ2CdSi2,where ΔPi is the pressure drop of the check valve i; Qi is the flow rate of the check valve i; Cd is the flow coefficient; Si is the cross area of the check valve i.The reservoir tube in Figure1 can be treated as an accumulator in the system; the gas is assumed to be ideal gas. According to Boyle’s law, the gas pressure can be presented by(9)P0V0n=PgVgnPg=P0V0V0-Sy-Sf∫vtdtn,where P0 is the initial charge pressure of gas in reservoir tube; V0 is the initial charge volume; Pg and Vg are, respectively, the gas pressure and volume after the fluid flows into reservoir tube; n is the gas polytropic index; v(t) is the velocity of piston.


#### 2.2.2. Modeling of the Hydraulic System

The electric circuit consists of a motor, a DC generator, and an energy recovery circuit, where the circuit includes the inductances and the external resistances.In the extension stroke, the high pressure oil drives the hydraulic motor; then the motor drives the generator by a coupler. According to their connection, the rotational speed and the output torque of hydraulic motor can be presented by(10)nhm=QhmqηvThm=ΔPmq2πηm,where nhm and Thm are, respectively, the rotational speed and output torque of the hydraulic motor; q is the motor displacement; Qhm is the flow rate through the hydraulic motor; ΔPm is the pressure drop between the inlet and outlet of hydraulic motor; ηv and ηm are, respectively, the volumetric efficiency and mechanical efficiency of the hydraulic motor.The hydraulic motor drives the generator. According to the moment equilibrium principle and the law of electromagnetic induction, the electromotive force (EMF) voltage, the electromagnetic torque, and the input torque of generator can be presented by(11)TGi=Jmω˙+TeTe=ktIUe=kvω=IR,where TGi is the input torque of generator; Jm is the total rotational inertia of motor-generator unit; ω is the rotational speed of generator; Te is the electromagnetic torque of generator in power regenerated status; kt and kv are the torque constant and EMF constant of generator, respectively; Ue is the EMF voltage; I is the electric current in the circuit; R is the resistance in the circuit.Ignoring the rotational inertia of the rotor in generator [21], the pressure drop of hydraulic motor can be presented by(12)ΔPm=4π2Qhmktkvηvq2Rηm.As to the compression stroke, the volumetric difference can lead to fluids flow through the hydraulic motor, so the pressure drop can be presented by(13)ΔPvm=4π2Qvmktkvηvq2Rηm(14)Qvm=Svv=πrv2v,where ΔPvm is the pressure drop of the hydraulic motor in compression stroke; Qvm is the flow rate through the hydraulic motor; Sv is the cross area of the hollow piston rod wall; rv is the equivalent radius of the cross area.Ignoring the internal leakage in hydraulic cylinder, the flow rate in all parts of the hydraulic system is the same, so it can be presented by(15)Qc=Sfv=Sivi=πrl2vl=πrl2vjc.According to the pressure equation, the pressure in the system can be presented by(16)Pf=Py+ΔPjc+ΔPl+ΔPi+ΔPm.Therefore, based on the above inference, the damping force can be presented by(17)Fcy=PgSy-Sf+ρSy3vt22CdS22+4π2Qvmktkvq2Rηm+10uvρllSy2πrl4vt+ερSy32π2rl4vt2Fce=PgSf-Sy+ρSy3vt22CdS12+4π2Qhmktkvq2Rηm+10uvρllSySfπrl4vt+∑ερSySf22πrl4vt2.In the equation,Fcy and Fce are the damping force in compression stroke and extension stroke, respectively.


### 2.3. Prototype of the Cylinder in HERSA

As shown in Figure3, the prototype of the cylinder in HERSA is fabricated on the basis of a traditional shock absorber according to the conceptual design in Figure 2. In consideration of the worse road excitation of SUVs or heavy trucks, this design target is commercial vehicle. The primary components in the system are a hydraulic cylinder, a motor, oil tubes, and a DC generator.Figure 3
The prototype of the cylinder. (a) The drawing of the cylinder. (b) The fabrication of the cylinder.
(a)
(b)


## 2.1. System Configuration

The schematic of HERSA is described in Figure1. The structure contains three components: a mechanical part which consists of a cylinder and a piston rod part; a hydraulic rectifier part which consists of accumulator, a hydraulic motor and pipelines; an energy-regenerative part which consists of a generator and a charging circuit including capacitances, inductances, and external loads. The piston in cylinder is distinguished from traditional shock absorber. The rebound valve and compression valve are removed, and only the by-pass valve and compensation valve are kept in the piston valve and bottom valve, respectively. In addition, the piston rod is hollow so that the fluid can flow to external parts.As shown in Figure2, the structure of HERSA is designed based on the conventional one. It has three tubes which include recovery tube, compression tube, and reservoir tube. However, in HERSA, the piston rod is hollow, so the fluid can flow through it to energy harvesting device. The rebound valve in piston and the compression valve in base valve system are wiped off. The hydraulic motor is connected with a generator via a shaft coupler. The energy-regenerative part has a common rotating mechanism which can be founded in some references.Figure 2
Schematic of HERSA. (a) The assembly diagram of HERSA. (b) The equivalent diagram of HERSA.
(a)
(b)When in the extension stroke, the fluid flows from rebound chamber to hollow piston rod, then flows through the hollow channel in piston rod, along the pipeline to the hydraulic pump, flows through the hydraulic motor to the reservoir tube, and passes the replenishing valve back to the compression chamber at last. In this stroke, most energy can be harvested, and the external load can be adjusted to achieve semiactive suspension.When in the compression stroke, the process is a little more complicated and the flow process can be divided into two parts:(1)
At first, because of the small cracking pressure, most of the fluid flows through the by-pass valve from compression chamber to replenishing chamber;(2)
After step (1), the upper chamber will be filled with oil. There is a volumetric difference between the upper and lower chamber because of the existence of piston rod. Just because of the volume difference, the residual oil in lower chamber will flow through the hollow piston to the regenerative part. As the volume of piston rod is small, so the volume of oil which flows into hydraulic motor is small too, and finally the harvested energy is little.


## 2.2. Mathematic Model of HERSA

Based on the working principle of HERSA shown in the Figure2, a mathematic model is proposed to demonstrate the system dynamics, such as the damping characteristic. In the system, the hydraulic flow and generator circuit are important to the characteristic.In the shock absorber, the damping force can be defined below:(1)Fc=PfSf-PySy,where Pf and Py are, respectively, pressure of upper and inferior chamber and Sf and Sy are the ring area and surface area of piston.While taking into account internal leakage in the system, it is understood that the fluid should flow through the check valve, the pipeline, and the hydraulic motor-generator circuit. The damping force is dependent on the three parts above. To describe the damping characteristic in detail, the two aspects, the hydraulic and the circuit system, are described, respectively.


### 2.2.1. Modeling of the Hydraulic System

In the extension stroke, the fluid firstly flows through the elbow in the hollow piston rod. This elbow can lead to the pressure partial loss, so the pressure drop can be presented by(2)ΔPjc=ερvjc2,where ΔPjc is the pressure drop of elbows in the hydraulic system; ε is the local resistance coefficient; ρ is the density of hydraulic oil; vjc is the flow velocity of the oil in this area.Then the fluid flows through the hollow piston rod; the hollow channel can be simplified as a pipeline of short length. Assuming the fluid is in laminar flow state, so the pressure drop can be presented by(3)ΔPl=λρllvl22.In the rubber hose, there are the common equations(4)λ=80Re(5)Re=2rlvluv.Combining (4) with (5), (3) can be presented by(6)ΔPl=10uvρllvlrl2,where ΔPl is the pressure drop in pipeline; λ is the coefficient of tube friction; ll is the length of pipeline; vl is the flow velocity of oil; rl is the radius of pipeline; Re is the Reynolds number; uv is the kinematic viscosity of oil.The valves in piston valve or base valve can lead to flow pressure drop; the check valves above are regarded as thin-wall holes, so the pressure drop can be presented by(7)Qi=CdSi2ΔPiρ(8)ΔPi=Qi2ρ2CdSi2,where ΔPi is the pressure drop of the check valve i; Qi is the flow rate of the check valve i; Cd is the flow coefficient; Si is the cross area of the check valve i.The reservoir tube in Figure1 can be treated as an accumulator in the system; the gas is assumed to be ideal gas. According to Boyle’s law, the gas pressure can be presented by(9)P0V0n=PgVgnPg=P0V0V0-Sy-Sf∫vtdtn,where P0 is the initial charge pressure of gas in reservoir tube; V0 is the initial charge volume; Pg and Vg are, respectively, the gas pressure and volume after the fluid flows into reservoir tube; n is the gas polytropic index; v(t) is the velocity of piston.


### 2.2.2. Modeling of the Hydraulic System

The electric circuit consists of a motor, a DC generator, and an energy recovery circuit, where the circuit includes the inductances and the external resistances.In the extension stroke, the high pressure oil drives the hydraulic motor; then the motor drives the generator by a coupler. According to their connection, the rotational speed and the output torque of hydraulic motor can be presented by(10)nhm=QhmqηvThm=ΔPmq2πηm,where nhm and Thm are, respectively, the rotational speed and output torque of the hydraulic motor; q is the motor displacement; Qhm is the flow rate through the hydraulic motor; ΔPm is the pressure drop between the inlet and outlet of hydraulic motor; ηv and ηm are, respectively, the volumetric efficiency and mechanical efficiency of the hydraulic motor.The hydraulic motor drives the generator. According to the moment equilibrium principle and the law of electromagnetic induction, the electromotive force (EMF) voltage, the electromagnetic torque, and the input torque of generator can be presented by(11)TGi=Jmω˙+TeTe=ktIUe=kvω=IR,where TGi is the input torque of generator; Jm is the total rotational inertia of motor-generator unit; ω is the rotational speed of generator; Te is the electromagnetic torque of generator in power regenerated status; kt and kv are the torque constant and EMF constant of generator, respectively; Ue is the EMF voltage; I is the electric current in the circuit; R is the resistance in the circuit.Ignoring the rotational inertia of the rotor in generator [21], the pressure drop of hydraulic motor can be presented by(12)ΔPm=4π2Qhmktkvηvq2Rηm.As to the compression stroke, the volumetric difference can lead to fluids flow through the hydraulic motor, so the pressure drop can be presented by(13)ΔPvm=4π2Qvmktkvηvq2Rηm(14)Qvm=Svv=πrv2v,where ΔPvm is the pressure drop of the hydraulic motor in compression stroke; Qvm is the flow rate through the hydraulic motor; Sv is the cross area of the hollow piston rod wall; rv is the equivalent radius of the cross area.Ignoring the internal leakage in hydraulic cylinder, the flow rate in all parts of the hydraulic system is the same, so it can be presented by(15)Qc=Sfv=Sivi=πrl2vl=πrl2vjc.According to the pressure equation, the pressure in the system can be presented by(16)Pf=Py+ΔPjc+ΔPl+ΔPi+ΔPm.Therefore, based on the above inference, the damping force can be presented by(17)Fcy=PgSy-Sf+ρSy3vt22CdS22+4π2Qvmktkvq2Rηm+10uvρllSy2πrl4vt+ερSy32π2rl4vt2Fce=PgSf-Sy+ρSy3vt22CdS12+4π2Qhmktkvq2Rηm+10uvρllSySfπrl4vt+∑ερSySf22πrl4vt2.In the equation,Fcy and Fce are the damping force in compression stroke and extension stroke, respectively.


## 2.2.1. Modeling of the Hydraulic System

In the extension stroke, the fluid firstly flows through the elbow in the hollow piston rod. This elbow can lead to the pressure partial loss, so the pressure drop can be presented by(2)ΔPjc=ερvjc2,where ΔPjc is the pressure drop of elbows in the hydraulic system; ε is the local resistance coefficient; ρ is the density of hydraulic oil; vjc is the flow velocity of the oil in this area.Then the fluid flows through the hollow piston rod; the hollow channel can be simplified as a pipeline of short length. Assuming the fluid is in laminar flow state, so the pressure drop can be presented by(3)ΔPl=λρllvl22.In the rubber hose, there are the common equations(4)λ=80Re(5)Re=2rlvluv.Combining (4) with (5), (3) can be presented by(6)ΔPl=10uvρllvlrl2,where ΔPl is the pressure drop in pipeline; λ is the coefficient of tube friction; ll is the length of pipeline; vl is the flow velocity of oil; rl is the radius of pipeline; Re is the Reynolds number; uv is the kinematic viscosity of oil.The valves in piston valve or base valve can lead to flow pressure drop; the check valves above are regarded as thin-wall holes, so the pressure drop can be presented by(7)Qi=CdSi2ΔPiρ(8)ΔPi=Qi2ρ2CdSi2,where ΔPi is the pressure drop of the check valve i; Qi is the flow rate of the check valve i; Cd is the flow coefficient; Si is the cross area of the check valve i.The reservoir tube in Figure1 can be treated as an accumulator in the system; the gas is assumed to be ideal gas. According to Boyle’s law, the gas pressure can be presented by(9)P0V0n=PgVgnPg=P0V0V0-Sy-Sf∫vtdtn,where P0 is the initial charge pressure of gas in reservoir tube; V0 is the initial charge volume; Pg and Vg are, respectively, the gas pressure and volume after the fluid flows into reservoir tube; n is the gas polytropic index; v(t) is the velocity of piston.


## 2.2.2. Modeling of the Hydraulic System

The electric circuit consists of a motor, a DC generator, and an energy recovery circuit, where the circuit includes the inductances and the external resistances.In the extension stroke, the high pressure oil drives the hydraulic motor; then the motor drives the generator by a coupler. According to their connection, the rotational speed and the output torque of hydraulic motor can be presented by(10)nhm=QhmqηvThm=ΔPmq2πηm,where nhm and Thm are, respectively, the rotational speed and output torque of the hydraulic motor; q is the motor displacement; Qhm is the flow rate through the hydraulic motor; ΔPm is the pressure drop between the inlet and outlet of hydraulic motor; ηv and ηm are, respectively, the volumetric efficiency and mechanical efficiency of the hydraulic motor.The hydraulic motor drives the generator. According to the moment equilibrium principle and the law of electromagnetic induction, the electromotive force (EMF) voltage, the electromagnetic torque, and the input torque of generator can be presented by(11)TGi=Jmω˙+TeTe=ktIUe=kvω=IR,where TGi is the input torque of generator; Jm is the total rotational inertia of motor-generator unit; ω is the rotational speed of generator; Te is the electromagnetic torque of generator in power regenerated status; kt and kv are the torque constant and EMF constant of generator, respectively; Ue is the EMF voltage; I is the electric current in the circuit; R is the resistance in the circuit.Ignoring the rotational inertia of the rotor in generator [21], the pressure drop of hydraulic motor can be presented by(12)ΔPm=4π2Qhmktkvηvq2Rηm.As to the compression stroke, the volumetric difference can lead to fluids flow through the hydraulic motor, so the pressure drop can be presented by(13)ΔPvm=4π2Qvmktkvηvq2Rηm(14)Qvm=Svv=πrv2v,where ΔPvm is the pressure drop of the hydraulic motor in compression stroke; Qvm is the flow rate through the hydraulic motor; Sv is the cross area of the hollow piston rod wall; rv is the equivalent radius of the cross area.Ignoring the internal leakage in hydraulic cylinder, the flow rate in all parts of the hydraulic system is the same, so it can be presented by(15)Qc=Sfv=Sivi=πrl2vl=πrl2vjc.According to the pressure equation, the pressure in the system can be presented by(16)Pf=Py+ΔPjc+ΔPl+ΔPi+ΔPm.Therefore, based on the above inference, the damping force can be presented by(17)Fcy=PgSy-Sf+ρSy3vt22CdS22+4π2Qvmktkvq2Rηm+10uvρllSy2πrl4vt+ερSy32π2rl4vt2Fce=PgSf-Sy+ρSy3vt22CdS12+4π2Qhmktkvq2Rηm+10uvρllSySfπrl4vt+∑ερSySf22πrl4vt2.In the equation,Fcy and Fce are the damping force in compression stroke and extension stroke, respectively.


## 2.3. Prototype of the Cylinder in HERSA

As shown in Figure3, the prototype of the cylinder in HERSA is fabricated on the basis of a traditional shock absorber according to the conceptual design in Figure 2. In consideration of the worse road excitation of SUVs or heavy trucks, this design target is commercial vehicle. The primary components in the system are a hydraulic cylinder, a motor, oil tubes, and a DC generator.Figure 3
The prototype of the cylinder. (a) The drawing of the cylinder. (b) The fabrication of the cylinder.
(a)
(b)


## 3. Analysis of Suspension Vibration Energy

### 3.1. Suspension Vibration Energy

The road roughness can lead to the vibration of the vehicle suspension. The vibration energy is transformed into thermal energy by the traditional shock absorber. To analyze the vibration energy, the suspension vibration equation is given in Figure4.(18)m2z¨2+csz˙2-z˙1+k2z2-z1=0m1z¨1+csz˙1-z˙2+k2z1-z2+k1z1-qroad=0,where m2 and m1 are, respectively, the sprung and unsprung mass; z¨2 and z¨1 are, respectively, the acceleration of sprung and unsprung mass; k2 and k1 are, respectively, the stiffness of spring and tire; qroad is the road roughness.Figure 4
Dynamic model of 2-DOF suspension.The instantaneous dissipation power of suspension can be presented by(19)Ps=csz˙2-z˙12Pt=∫TPstdt,where Ps is the dissipation power of suspension; cs is the damping coefficient of the system; z˙2 and z˙1 are, respectively, the velocity of sprung mass and unsprung mass; T is the vibration period of suspension; Ps(t) is the dissipation power of suspension at t moment.The vibration energy is transformed into thermal energy in conventional suspension. But in the HERSA, the special structure determines the vibration power conversion; one part is converted into heat energy and the other part is converted into electric energy which can be regenerated. For the HERSA system, the power flow can be demonstrated in Figure5.Figure 5
Power flow chart of suspension vibration energy.As shown in Figure5, the vibration energy includes two parts: thermal Pth and electric Pel power; the thermal power Pth consists of the mechanical friction power Pm1, the check valve damping power Pc, the pipeline and elbow damping power Pp, the power stored in reservoir tube Pr, the mechanical and volumetric power dissipated in motor-generator Pm2, and power dissipated on internal resistance Prin. The power flow equation can be presented by(20)Pt=Pth+Pel=Pm1+Pc+Pp+Pr+Pm2+Prin+Pel.


### 3.2. Sensitivity Analysis of Suspension Vibration Energy

The vibration energy is related to suspension system and the road, so the parameter study is carried out to analyze the sensitivity. A model of quarter vehicle is established to analyze the influences of vehicle parameters on vibration energy. The values of the parameters are demonstrated in Table1.Table 1
Parameters of the quarter vehicle model.
Parameter of vehicle
Valve
Sprung mass/m2
350/kg
Unsprung mass/m1
40/kg
Spring stiffness/k2
20000/(N⋅m−1)
Tire stiffness/k1
180000/(N⋅m−1)
Damping rate/cs
1500/(N⋅s⋅m−1)Based on the parameters in the Table1, a simulation model is carried out to evaluate the influences of the vehicle parameters and different grade roads on suspension vibration energy.In Figure6(a), one parameter changes while the others are kept at nominal value. The N represents the nominal value of the parameters, and the parameters change in same proportion of 0.15N. The influences of the parameters on vibration energy are as follows:(1)
The RMS power is proportional tok1, m2, and m1, and the increasing rate ranking is k1≫m2>m1;(2)
Thek2 and cs almost have no influences on vibration energy, and the RMS power decreases at first and gradually tends to a constant value as cs increases;(3)
In Figure6(b), the road grade is according to the ISO standard [21]. The RMS power increases with the road grade increases from A to D, and the increasing rate gets bigger and bigger from A to D. The results are coincident with the results in Galluzzi et al. [14].Figure 6
Parameter analysis of suspension vibration energy. (a) The influence of the parameters on RMS dissipation power, on the B grade road. (b) The influence of different roads on RMS dissipation power.
(a)
(b)


## 3.1. Suspension Vibration Energy

The road roughness can lead to the vibration of the vehicle suspension. The vibration energy is transformed into thermal energy by the traditional shock absorber. To analyze the vibration energy, the suspension vibration equation is given in Figure4.(18)m2z¨2+csz˙2-z˙1+k2z2-z1=0m1z¨1+csz˙1-z˙2+k2z1-z2+k1z1-qroad=0,where m2 and m1 are, respectively, the sprung and unsprung mass; z¨2 and z¨1 are, respectively, the acceleration of sprung and unsprung mass; k2 and k1 are, respectively, the stiffness of spring and tire; qroad is the road roughness.Figure 4
Dynamic model of 2-DOF suspension.The instantaneous dissipation power of suspension can be presented by(19)Ps=csz˙2-z˙12Pt=∫TPstdt,where Ps is the dissipation power of suspension; cs is the damping coefficient of the system; z˙2 and z˙1 are, respectively, the velocity of sprung mass and unsprung mass; T is the vibration period of suspension; Ps(t) is the dissipation power of suspension at t moment.The vibration energy is transformed into thermal energy in conventional suspension. But in the HERSA, the special structure determines the vibration power conversion; one part is converted into heat energy and the other part is converted into electric energy which can be regenerated. For the HERSA system, the power flow can be demonstrated in Figure5.Figure 5
Power flow chart of suspension vibration energy.As shown in Figure5, the vibration energy includes two parts: thermal Pth and electric Pel power; the thermal power Pth consists of the mechanical friction power Pm1, the check valve damping power Pc, the pipeline and elbow damping power Pp, the power stored in reservoir tube Pr, the mechanical and volumetric power dissipated in motor-generator Pm2, and power dissipated on internal resistance Prin. The power flow equation can be presented by(20)Pt=Pth+Pel=Pm1+Pc+Pp+Pr+Pm2+Prin+Pel.


## 3.2. Sensitivity Analysis of Suspension Vibration Energy

The vibration energy is related to suspension system and the road, so the parameter study is carried out to analyze the sensitivity. A model of quarter vehicle is established to analyze the influences of vehicle parameters on vibration energy. The values of the parameters are demonstrated in Table1.Table 1
Parameters of the quarter vehicle model.
Parameter of vehicle
Valve
Sprung mass/m2
350/kg
Unsprung mass/m1
40/kg
Spring stiffness/k2
20000/(N⋅m−1)
Tire stiffness/k1
180000/(N⋅m−1)
Damping rate/cs
1500/(N⋅s⋅m−1)Based on the parameters in the Table1, a simulation model is carried out to evaluate the influences of the vehicle parameters and different grade roads on suspension vibration energy.In Figure6(a), one parameter changes while the others are kept at nominal value. The N represents the nominal value of the parameters, and the parameters change in same proportion of 0.15N. The influences of the parameters on vibration energy are as follows:(1)
The RMS power is proportional tok1, m2, and m1, and the increasing rate ranking is k1≫m2>m1;(2)
Thek2 and cs almost have no influences on vibration energy, and the RMS power decreases at first and gradually tends to a constant value as cs increases;(3)
In Figure6(b), the road grade is according to the ISO standard [21]. The RMS power increases with the road grade increases from A to D, and the increasing rate gets bigger and bigger from A to D. The results are coincident with the results in Galluzzi et al. [14].Figure 6
Parameter analysis of suspension vibration energy. (a) The influence of the parameters on RMS dissipation power, on the B grade road. (b) The influence of different roads on RMS dissipation power.
(a)
(b)


## 4. Parametric Analysis of HERSA

In the HERSA, there are many components in the system, such as the hydraulic cylinder, the piston, the pipeline, the check valve, the reservoir tube, the motor, the generator, and the electric elements. The parameter is enormous. The initial parameter valve of HERSA is shown in Table2.Table 2
Parameters of the HERSA.
Parameter
Valve
D
65 mm
d
26 mm
ρ
850 (kg/m3)
P
0
15 bar
V
0
0.5 L
q
10 (mL/r)
η
v
0.9
n
1.2
J
m
10−7 (kg⋅m2)
P
crack-valve
1
0.2 bar
l
l
500 mm
r
l
25 mm
c
d
0.6
k
t
0.25 (N⋅m/A)
k
v
0.25 (V⋅s/rad)
ε
1.34
η
m
0.9
R
i
n
0.6Ω
R
o
u
15Ω
P
crack-valve
2
0.2 barIn this paper, the parameters are various and shown in Table2; the effects of them on the damping characteristics of HERSA and regenerated energy are demonstrated in the following analysis. A sinusoidal excitation is set as the road roughness, and it can be presented by(21)qroad=Asin⁡2πft.A and f are, respectively, the amplitude and frequency of the sinusoidal excitation, and the initial valves of A and f are 50 mm and 1.67 Hz respectively.


### 4.1. Parameter Study

#### 4.1.1. Check Valve

In the system, there are by-pass valve and replenishing valve. The by-pass valve mainly works in the compression stroke, and the replenishing valve mainly works in the extension stroke. And the key parameter of valves is the cracking pressure. It affects greatly the damping force, and the influence diagram is presented in Figure7.Figure 7
The influence of check valve in HERSA. (a) The influence of by-pass valve on damping characteristics. (b) The influence of replenishing valve on damping characteristics.
(a)
(b)As shown in Figure7, the by-pass valve works in the compression stroke, so, in Figure 7(a), the damping force in extension stroke almost has no changes, whereas the damping force in compression stroke increases with the increase of cracking pressure. For the by-pass valve, the increase of ΔP leads to the damping force increasing according to (8). As to Figure 7(b), the damping force in the extension stroke increases with the increase of cracking pressure, and the influence is tiny.


#### 4.1.2. Hydraulic Motor

The hydraulic motor is the energy conversion part, and the vibration energy is put into the DC generator to generate electricity, in which the displacement of motor plays an important role in the influence on the flow characteristic of the fluid, which results in the change of pressure difference between import and export in motor. Damping and energy-regenerative characteristic can change with it.It can be seen from Figure8 that the motor hydraulic displacement has a negative correlation with damping force in extension stroke and regenerative power. In Figure 8(a), the influence of motor displacement on rebound force is unobvious. The motor speed decreases with motor displacement increases. The pressure drop in motor decreases too. So the damping force decreases according to (12). The motor with high speed can drive the generator to revolve faster and acquires more power.Figure 8
The influence of hydraulic motor on HERSA. (a) The indicator diagram of HERSA. (b) The influence on energy-regenerative characteristics.
(a)
(b)


#### 4.1.3. The External LoadRou

The external load is a significant element for the damping force and the regenerative power. The indicator diagram and the regenerative power under different external loads are demonstrated in Figure9, respectively.Figure 9
The influence of external load on HERSA. (a) The indicator diagram of HERSA. (b) The influence on energy-regenerative characteristics.
(a)
(b)The influences of the external load on the characteristic of HERSA are shown in Figure9. According to (12), the pressure drop of the hydraulic motor decreases with the external load increases. So in Figure 9(a), the damping force of extension decreases with the increase of external load; and in Figure 9(b), the peak regenerative power in the extension stroke decreases with the increase of external load.When HERSA is in compression stroke, the volumetric difference can lead to fluids flow through the hydraulic motor. But the amount of the fluids is very small because the wall thickness of piston rod is small. According to (13), the small Qvm can cause tiny influence on the damping force. So the influence in extension stroke is put forward in the Figure 9.


## 4.1. Parameter Study

### 4.1.1. Check Valve

In the system, there are by-pass valve and replenishing valve. The by-pass valve mainly works in the compression stroke, and the replenishing valve mainly works in the extension stroke. And the key parameter of valves is the cracking pressure. It affects greatly the damping force, and the influence diagram is presented in Figure7.Figure 7
The influence of check valve in HERSA. (a) The influence of by-pass valve on damping characteristics. (b) The influence of replenishing valve on damping characteristics.
(a)
(b)As shown in Figure7, the by-pass valve works in the compression stroke, so, in Figure 7(a), the damping force in extension stroke almost has no changes, whereas the damping force in compression stroke increases with the increase of cracking pressure. For the by-pass valve, the increase of ΔP leads to the damping force increasing according to (8). As to Figure 7(b), the damping force in the extension stroke increases with the increase of cracking pressure, and the influence is tiny.


### 4.1.2. Hydraulic Motor

The hydraulic motor is the energy conversion part, and the vibration energy is put into the DC generator to generate electricity, in which the displacement of motor plays an important role in the influence on the flow characteristic of the fluid, which results in the change of pressure difference between import and export in motor. Damping and energy-regenerative characteristic can change with it.It can be seen from Figure8 that the motor hydraulic displacement has a negative correlation with damping force in extension stroke and regenerative power. In Figure 8(a), the influence of motor displacement on rebound force is unobvious. The motor speed decreases with motor displacement increases. The pressure drop in motor decreases too. So the damping force decreases according to (12). The motor with high speed can drive the generator to revolve faster and acquires more power.Figure 8
The influence of hydraulic motor on HERSA. (a) The indicator diagram of HERSA. (b) The influence on energy-regenerative characteristics.
(a)
(b)


### 4.1.3. The External LoadRou

The external load is a significant element for the damping force and the regenerative power. The indicator diagram and the regenerative power under different external loads are demonstrated in Figure9, respectively.Figure 9
The influence of external load on HERSA. (a) The indicator diagram of HERSA. (b) The influence on energy-regenerative characteristics.
(a)
(b)The influences of the external load on the characteristic of HERSA are shown in Figure9. According to (12), the pressure drop of the hydraulic motor decreases with the external load increases. So in Figure 9(a), the damping force of extension decreases with the increase of external load; and in Figure 9(b), the peak regenerative power in the extension stroke decreases with the increase of external load.When HERSA is in compression stroke, the volumetric difference can lead to fluids flow through the hydraulic motor. But the amount of the fluids is very small because the wall thickness of piston rod is small. According to (13), the small Qvm can cause tiny influence on the damping force. So the influence in extension stroke is put forward in the Figure 9.


## 4.1.1. Check Valve

In the system, there are by-pass valve and replenishing valve. The by-pass valve mainly works in the compression stroke, and the replenishing valve mainly works in the extension stroke. And the key parameter of valves is the cracking pressure. It affects greatly the damping force, and the influence diagram is presented in Figure7.Figure 7
The influence of check valve in HERSA. (a) The influence of by-pass valve on damping characteristics. (b) The influence of replenishing valve on damping characteristics.
(a)
(b)As shown in Figure7, the by-pass valve works in the compression stroke, so, in Figure 7(a), the damping force in extension stroke almost has no changes, whereas the damping force in compression stroke increases with the increase of cracking pressure. For the by-pass valve, the increase of ΔP leads to the damping force increasing according to (8). As to Figure 7(b), the damping force in the extension stroke increases with the increase of cracking pressure, and the influence is tiny.


## 4.1.2. Hydraulic Motor

The hydraulic motor is the energy conversion part, and the vibration energy is put into the DC generator to generate electricity, in which the displacement of motor plays an important role in the influence on the flow characteristic of the fluid, which results in the change of pressure difference between import and export in motor. Damping and energy-regenerative characteristic can change with it.It can be seen from Figure8 that the motor hydraulic displacement has a negative correlation with damping force in extension stroke and regenerative power. In Figure 8(a), the influence of motor displacement on rebound force is unobvious. The motor speed decreases with motor displacement increases. The pressure drop in motor decreases too. So the damping force decreases according to (12). The motor with high speed can drive the generator to revolve faster and acquires more power.Figure 8
The influence of hydraulic motor on HERSA. (a) The indicator diagram of HERSA. (b) The influence on energy-regenerative characteristics.
(a)
(b)


## 4.1.3. The External LoadRou

The external load is a significant element for the damping force and the regenerative power. The indicator diagram and the regenerative power under different external loads are demonstrated in Figure9, respectively.Figure 9
The influence of external load on HERSA. (a) The indicator diagram of HERSA. (b) The influence on energy-regenerative characteristics.
(a)
(b)The influences of the external load on the characteristic of HERSA are shown in Figure9. According to (12), the pressure drop of the hydraulic motor decreases with the external load increases. So in Figure 9(a), the damping force of extension decreases with the increase of external load; and in Figure 9(b), the peak regenerative power in the extension stroke decreases with the increase of external load.When HERSA is in compression stroke, the volumetric difference can lead to fluids flow through the hydraulic motor. But the amount of the fluids is very small because the wall thickness of piston rod is small. According to (13), the small Qvm can cause tiny influence on the damping force. So the influence in extension stroke is put forward in the Figure 9.


## 5. Optimization of HERSA

For the HERSA, the design goal is to regenerate more power as far as possible without devitalizing the damping characteristic. In order to achieve this goal, an optimization is carried out to get the optimalq and Rou. In the optimization, there is one object and two constraints, whose object is the maximum of the RMS power. The procedure diagram of optimization is shown in Figure 10.Figure 10
The optimization procedure diagram.As shown in Figure10, the first step is to determine the design variables, which include motor displacement and external load. The reason is that such two parameters have great influences on damping and energy-regenerative characteristics as shown in Section 4. Moreover, the external load is a controllable variable for the semiactive control of suspension. So the design variables and constraint are shown in the Table 3.Table 3
Parameter determination of the optimization.
Parameter determination
Range
Variable determination
Hydraulic motor displacement/Dis
5~40/(mL/r)
External load/R
5–40/Ω
Constraint condition
F
c
e
8000~12000/(N)
F
c
y
−6000~−3000/(N)


### 5.1. Vibration Input

In Sections3 and 4, the simulation is based on the test standard of shock absorber, so the excitations should be sinusoidal excitation. But in practical road condition, the pavements are random. The sinusoidal excitation cannot demonstrate the real excitation input. In this paper, to make the optimization more close to the practical condition, the excitation input of shock absorber is collected through a road test.As shown in Figure11(a), the chosen vehicle in the test is a heavy truck which conforms to the design requirements. The reason is that the road conditions of commercial vehicles such as SUV and trucks are worse than which of ordinary passenger cars, and according to the relative analysis in Section 3, the commercial vehicles on worse road have bigger energy-regenerative potential. So a light truck is selected for this test. Figures 11(c) and 11(d) are displacement sensor and data collection equipment, respectively. The suspension working states can be obtained through the test above.Figure 11
The vehicle test for road roughness. (a) The vehicle in the test; (b) the location of sensor on the shock absorber; (c) the displacement sensor; (d) data collection equipment.
(a)
(b)
(c)
(d)To analyze the effects of different parameters on HERSA, several special road pavements are selected to compare the performance of HERSA. And Figure12 is physical image of these roads.Figure 12
The road surface.In the test, the sensor is fixed on the front suspension of a truck with half loads at 50 km/h. Through the test, the motion state of shock absorber can be obtained, and it is presented in Figure13.Figure 13
The typical road roughness.


### 5.2. Optimization and Results

In the optimization, an algorithm named Multi-Island Genetic Algorithm (MIGA) was adopted to perform the process. Considering that the constraint condition should be prioritized, so weight factors ofFce and Fcy are 0.5 and 0.5, respectively. The block diagram is shown in Figure 14.Figure 14
The block diagram in software.The optimization results are shown in Figure15. In Figure 15, the relationship between RmsPower and Dis, R is presented. And Table 4 showed the RMS value of energy and the corresponding damping force. After optimization, the regenerated energy increased greatly within the constraint condition. In summary, through an overall consideration, the optimization could improve the performance of HERSA, and it showed the semiactive control of HERSA was feasible.Table 4
The optimal results.
Variable
RmsPower
Optimal parameter
Dis: 14R: 18
107.94
Constraint condition
F
c
e
11298/(N)
F
c
y
−5725/(N)Figure 15
The optimized results. (a) The relationship between RmsPower and Dis,R; (b) the history of optimization.
(a)
(b)


## 5.1. Vibration Input

In Sections3 and 4, the simulation is based on the test standard of shock absorber, so the excitations should be sinusoidal excitation. But in practical road condition, the pavements are random. The sinusoidal excitation cannot demonstrate the real excitation input. In this paper, to make the optimization more close to the practical condition, the excitation input of shock absorber is collected through a road test.As shown in Figure11(a), the chosen vehicle in the test is a heavy truck which conforms to the design requirements. The reason is that the road conditions of commercial vehicles such as SUV and trucks are worse than which of ordinary passenger cars, and according to the relative analysis in Section 3, the commercial vehicles on worse road have bigger energy-regenerative potential. So a light truck is selected for this test. Figures 11(c) and 11(d) are displacement sensor and data collection equipment, respectively. The suspension working states can be obtained through the test above.Figure 11
The vehicle test for road roughness. (a) The vehicle in the test; (b) the location of sensor on the shock absorber; (c) the displacement sensor; (d) data collection equipment.
(a)
(b)
(c)
(d)To analyze the effects of different parameters on HERSA, several special road pavements are selected to compare the performance of HERSA. And Figure12 is physical image of these roads.Figure 12
The road surface.In the test, the sensor is fixed on the front suspension of a truck with half loads at 50 km/h. Through the test, the motion state of shock absorber can be obtained, and it is presented in Figure13.Figure 13
The typical road roughness.


## 5.2. Optimization and Results

In the optimization, an algorithm named Multi-Island Genetic Algorithm (MIGA) was adopted to perform the process. Considering that the constraint condition should be prioritized, so weight factors ofFce and Fcy are 0.5 and 0.5, respectively. The block diagram is shown in Figure 14.Figure 14
The block diagram in software.The optimization results are shown in Figure15. In Figure 15, the relationship between RmsPower and Dis, R is presented. And Table 4 showed the RMS value of energy and the corresponding damping force. After optimization, the regenerated energy increased greatly within the constraint condition. In summary, through an overall consideration, the optimization could improve the performance of HERSA, and it showed the semiactive control of HERSA was feasible.Table 4
The optimal results.
Variable
RmsPower
Optimal parameter
Dis: 14R: 18
107.94
Constraint condition
F
c
e
11298/(N)
F
c
y
−5725/(N)Figure 15
The optimized results. (a) The relationship between RmsPower and Dis,R; (b) the history of optimization.
(a)
(b)


## 6. Conclusions

This paper presented a novel hydraulic energy-regenerative shock absorber based on the traditional telescopic shock absorber. The design, modeling, and analysis of the HERSA are demonstrated. An accurate mathematical model is proposed based on the hydromechanics theory. The suspension vibration energy is analyzed to evaluate the potential of the power which could be regenerated. In the analysis, the sensitivity of vehicle parameters is researched with the constraints of different road surfaces, and it shows that the tire stiffness had the most influences on the regenerated energy, and it is a positive correlation. Through the theoretical calculation, the maximum energy can be obtained on the road D.To study the characteristics of HERSA, the parametric analysis of the system is demonstrated in this paper. The crack pressure of check valve, displacement of hydraulic motor, and external load are considered as the variables in the simulation. And the analysis indicated that the displacement of hydraulic motor and external load have large effects on the regenerated energy. To maximize the regenerated energy, an optimization based on the MIGA is carried out. In the optimization process, the displacement data obtained from the road test is regarded as the excitation input in the simulation; the purpose of it is to make the optimization more close to the actual situation. The results indicate that the optimal meets the requirements. In a word, a novel hydraulic energy-regenerative shock absorber was put forward, and the research in this paper could be as a foundation for the late-stage study.



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*Source: 3186584-2017-08-08.xml*