# Energy Consumption of an Active Vehicle Suspension with an Optimal Controller in the Presence of Sinusoidal Excitations

Authors: Jarosław Konieczny; Waldemar Rączka; Marek Sibielak; Janusz Kowal
Journal: Shock and Vibration
 (2020)

---

## Abstract

Control of vibration is a significant problem in the design and construction of vehicle suspensions. The usage of controlled suspensions is important due to ride comfort, driving safety, and vehicle road holding. The control law for such systems is usually determined as a solution of an optimisation problem with a quality indicator. The effectiveness of vibration reduction is possible to be improved in the entire useful frequency range of a system operation, but usually increasing external energy consumption is observed. An additional problem in the case of vehicle suspensions includes the necessity for increased vibration reduction at selected frequencies. This is related to the natural frequencies of the driver’s internal organs or to other reasons. The goal of this work is to find a compromise between efficiency of the suspension in terms of the aforementioned indicators and energy consumption in the presence of sinusoidal excitations. This paper presents a synthesis of a weighted multitone optimal controller (WMOC) for an active vibration reduction system. Energy limitation is taken into account by selection coefficients of the weighting matrix associated with the control signal vector. The control signal in this case is determined on the basis of the parameter estimation of the sinusoidal disturbances vector (PESDV). The vibration transmissibility function and the energetic indicators for the active suspension were determined while taking note of nonlinearities occurring in the actual vehicle. The analysis of energy indicators is presented, depending on the level of vibration reduction efficiency. The results were compared with referencing to LQR control strategy.


---

## Body

## 1. Introduction

Taking into account the nature of external disturbances caused by road irregularities is an important problem in the design of vehicle suspension structures [1–6]. In general, these disturbances are of a random character [7–10] or of a random character with specified power spectral density (PSD) characteristics depending on the class of the road (ISO 8608) being driven on. From the point of view of the synthesis of the active control system, this spectrum can be broken down into individual enforcing signals with sinusoidal character [11]. Considerations related to the active as well as semiactive reduction of external excitation can be found in many publications [12–20]. The highest vibration reduction efficiency is achieved using the active methods [21–23], but their practical use is limited due to the high energy consumption from the external power source [24–27]. When designing active suspensions [28], it is always necessary to seek a compromise between their effectiveness and energy consumption. This compromise can be achieved by determining the control law as a solution for the optimisation problem [29]. Energy limitation is taken into account when selecting the matrix weighting factors in the adopted quality indicator [21]. By selecting these factors, the efficiency of vibration reduction can be improved in the entire useful frequency range of the system operation. This generally results in an increase in the demand for external energy. In the case of active vehicle suspensions, the necessity for increased vibration reduction at selected frequencies is an additional issue. This applies, for example, to the individual natural frequencies of the driver’s and passengers’ internal organs or to the need for special vibration reduction for arbitrarily selected frequencies, such as those related to vehicle engine harmonic frequencies or resonant frequencies of the suspension or other car body parts. The method enabling a solution of this problem is presented in the article [19].The motivation for presented research was the initial numerical research presented at the IMAC-XXXVI Conference and Exposition on Structural Dynamics in 2018 [30]. This work presents the study of the suspension controlled by a weighted multitone optimal controller (WMOC), with particular emphasis on energy issues. The main goal of the conducted research was improvement of active vehicle suspension efficiency by using the WMOC. The main limitation of active suspensions application is high demand for energy required from the external power source. Limitation of energy consumption, maximal force, and power used by the actuator is the most important challenge put before designers of these suspensions. It is high challenge for those who want to simultaneously assure the high comfort of operator work and sufficient vehicle road holding. Determination of a controller for an active vibration reduction system as a solution of the optimisation task makes it possible to take into account indicators mentioned above.Because of vibration reduction, the efficiency increase is mainly connected with an increase in energy consumption; therefore, in this paper, optimal control was considered. The objective function takes into account the opposed criteria such as efficiency of vibration reduction and external energy demand. The WMOC satisfies above assumption and additionally allows improving efficiency of vibration reduction for chosen frequencies.Control synthesis was performed using the WMOC for a parallel active vibration reduction system. A WMOC is determined as a solution of the optimisation problem. Indicators for evaluating the energy properties of active suspensions are suggested. The results of the WMOC tests were compared with the LQR-controlled active suspension test results. In addition to the numerical tests that allow for assessing the suspension comfort, the authors present quality indicators enabling assessment of the demand for external energy necessary to power the active system. The proposed energy indicators for active suspensions are necessary to assess the energy efficiency of the applied controller’s operation.


## 2. Control System with a Weighted Multitone Optimal Controller

### 2.1. Synthesis Method for a Weighted Multitone Optimal Controller

The weighted multitone optimal controller (WMOC) is determined by solving the optimisation task. The advantage of this approach is the possibility to take note of the energy limitation concerning the controlling signal in the quality indicator. Object condition equations (1) contain a component that takes into account the disturbance being the sum of sinusoidal components wt (2). For the correct synthesis of the WMOC controller, it is important to assume that the system with open feedback loop is stable. If this is not the case in the first phase described below, the object-stabilising coupling is implemented.(1)x˙t=Asxt+Buut+Bwwt,x0=x0,(2)wt=α1sinω1t+φ1,…,αjsinωjt+φj,…,αnwsinωnwt+φnwT,where AsandB are matrices describing the dynamics of the object, As is the matrix for which all real parts of the eigenvalues assume negative values, and αj,ωj,andφj are the amplitude, frequency, and phase of the jth disturbance signal, respectively.The model of the object described by equations (1) and (2) is nonstationary; it is due to the fact that harmonic disturbances for chosen frequencies ωj are taken into account. During modelling of the disturbing signal existing in vector wt, the model of the object could be transformed to its autonomous form which is time-independent. The harmonic disturbances existing in vector wt were modelled by equation (3).(3)x˙d,2j−1t=ωjxd,2jt,x˙d,2jt=−ωjxd,2j−1t,wjt=xd,2j−1t,j=1,…,nw.Taking into consideration equation (3), the model of the object described by equations (1) and (2) can be rewritten in the autonomous form with extended state vector x^t.(4)x˙t=Asxt+Buut+BwCdxdt,x˙dt=Adxdt,x0=x0,xd0=xd,0,x^=xT,xdTT.On the basis of formula (3), coefficients of matrices Ad∈R2nw×2nw and Cd∈Rnw×2nw (5) were determined.(5)ad,l,j=ωk,l=2k−1,j=2k,k=1,…,nw,−ωk,l=2k,j=2k−1,k=1,…,nw,0,in other  cases,cd,l,j=1,l=2k−1,j=2k−1,k=1,…,nw,0,in other  cases.The model of the object described by state equations (4) is time-independent. Amplitudes and phases of disturbing harmonic signal frequencies wt are the result of initial conditions xd,0 and vector xdt. Compound frequencies ωj of disturbing signal wt are the assumed object model parameters. For the considerations presented below, in particular for these frequencies, an improvement of vibration reduction efficiency with minimal energy consumption is required. To design a controller, a WMOC method was used. The method is described in detail in the literature [31].In the WMOC synthesis method, a weighted multitone quality indicator is used to evaluate feasible solutions. It allows for the inclusion of energy limitations, independently for each component of the control signal.During WMOC design, an optimal solution is searched for in a set of control signalsU˜ consisting of continuous and bounded functions for which limits (6) and (7) exist for any ω.(6)uα=2limTd⟶∞1Td∫0Tdutsinωtdt,(7)uβ=2limTd⟶∞1Td∫0Tdutcosωtdt.In particular, from equations (6) and (7), it results that limits exist for frequency ωj.(8)uαj=2limTd⟶∞1Td∫0Tdutsinωjtdt,(9)uβj=2limTd⟶∞1Td∫0Tdutcosωjtdt.Taking into account equations (8) and (9), functions from set U˜ could be written as formulas (10) and (11):(10)ut=∑j=1nwujt+uˇt,(11)ujt=uαjsinωjt+uβjcosωjt.This indicator is based on the distribution of control signalut on sinusoidal components ujt, related to the frequency of disturbing signals ωj.Taking into account the foregoing, weighted multitone quality indicator [31] is defined using the following equation:(12)Jωx,u=limsupTd⟶∞1Td∫0TdxTtQxt+∑j=1nwujtTRjujtdt.MatricesRj (positively defined Rj>0) are associated with individual sinusoidal components of the control signal and allow for the inclusion of energy limitations independently for each component. The optimum WMOC is determined by solving the dynamic optimisation task with quality indicator (12) and limitations (1) and (2). The set of control signals U˜ contains limited continuous functions for which there is a decomposition defined by formulas (8) to (10). Quality indicator Jω is determined correctly for a set of control signals defined as such. The solution of the optimisation task described by formulas (1), (2), and (12) is determined based on formulas (13) to (16).(13)u∗t=∑j=1nwu∗jt,(14)u∗jt=ReKjwjt+ImKjwω,jt,(15)Kj=−BuT−iωjIn−AsT−1QiωjIn−As−1Bu+Rj−1⋅BuT−iωjIn−AsT−1QiωjIn−As−1Bwj,(16)wωt=α1sinω1t+φ1+π2,…,αnwsinωnwt+φnw+π2T,where Bwj is the jth column of the Bw matrix, wjt is the jth coordinate of vector wt, and i=−1.The solution of the optimisation problem denoted by (1), (2), and (12) is described by (13) to (16). The proof of it is shown in the literature [31].The solution of the optimisation problem described by formulas (1), (2), and (12) is ambiguous, e.g., by adding any limited signal tending to zero to the optimal control, optimal control is obtained as well. The solution given in formulas (13) to (16) was selected in a manner allowing it to be independent of the initial conditions and of state vector xt describing the state of the object without taking into account harmonic disturbances. It is a function of disturbing signals wt and the signals offset by π/2 with respect to the wt vector.Taking into account the model of the object in formulas (4) and (5) independent of time, signal vector wωt was formulated in the form(17)wωt=Cd,ωxdt.Matrix coefficientsCd,ω were determined based on (3).(18)cd,ω,l,j=1,l=2k,j=2k,k=1,…,nw,0,in other cases.The WMOC determines optimal control. The control signal is optimal only for sinusoidal components with frequenciesω1,…,ωnw. For other frequencies, the amplitude characteristics of the closed system remain unchanged. For this reason, the synthesis of the controller is divided into two phases.


#### 2.1.1. Phase One

It allows shaping of the frequency characteristics over the entire frequency range. The control signal is determined by solving the classical optimisation problem with the linear quadratic controller (LQR) defined by formulas (19) and (20):(19)Jx,u=∫0∞xTtQxt+uTtR0utdt,(20)x˙t=Axt+Buut,x0=x0.TheK0 controller is determined by solving the Riccati equation:(21)PA+ATP−PBuR0−1BuTP+Q=0,K0=BuTP.


#### 2.1.2. Phase Two

The frequency characteristics are modified for the selected disturbance signal frequencies. The controllers, as mentioned previously, are determined based on the solution of the optimisation task from (1) to (12). Matrix As occurring in object state equations (1) is derived from the following formula:(22)As=A−BuK0.ControllersKj for each frequency are determined based on formula (15).The WMOC structure is presented in Figure1.Figure 1
Block diagram of the WMOC.


### 2.2. Control System with the WMOC

The WMOC generates a control signal based on the state variables and of course on disturbing signal (14). For calculating u∗jt of the control signal components, it is required to determine the sinusoidal component vectors wt and the wωt vector (16) in real time. In the presented control system, these vectors are determined basing on disturbing signal ξt. But if disturbance ξt measurement is impossible, the extended state vector x^t estimator could be used.In the method which is used in this case, parameters (wαj and wβj) of signals wjt are estimated on the basis of formulas (23). The time interval equals t−TIj,t, where TIj is the estimation time and t is the current moment of time.(23)wαjt=1TIj∫t−TIjtξτsinωjτ−t+TIjdτ,wβjt=1TIj∫t−TIjtξτcosωjτ−t+TIjdτ,wjτ=wαjtsinωjτ+wβjtcosωjτfor,τ∈t−TIj,t.Estimation timesTIj can be chosen independently for each jth component. It is good practice to determine it as the multiple of the estimated wjt component period. Signals wjt,wω,jt are determined on the basis of formulas (24) (t is the present moment of time).(24)wjt=wαjtsinωjTIj+wβjtcosωjTIj,wω,jt=wαjtsinωjTIj+π2+wβjtcosωjTIj+π2.A short estimation time of componentswjt, wω,jt improves the quality of control in the case of variation of disturbance parameters. As a result, estimation times TIj should be assumed as being as short as possible. On the other hand, the shortening of these times aggravates the quality of harmonic component estimation. From the numerical analysis, it is clear that a good compromise is to assume estimation time TIj at the level equal to 10 periods of the estimated sinusoidal component. In the tests carried out later in this study, estimation times TIj were used at the level of 100 periods of the estimated sinusoidal component of the disturbing signal.Figure2 shows a diagram of a control system with the WMOC. The K0 controller closes the feedback loop and is determined in phase one using LQR synthesis. Controllers K1,…,Knw are derived from formula (15). Parameter estimation of sinusoidal disturbances vector (PESDV) blocks are used to determine sinusoidal component wjt when ωj is the frequency of the disturbing signal. These blocks additionally generate signals x˜d,2j−1 and x˜d,2j corresponding to wj and wω,j necessary for the correct operation of controllers Kj. Signals wjt, wω,jt are determined in the PESDV block from formula (24).Figure 2
The WMOC control system with the parameter estimation of sinusoidal disturbances.


## 2.1. Synthesis Method for a Weighted Multitone Optimal Controller

The weighted multitone optimal controller (WMOC) is determined by solving the optimisation task. The advantage of this approach is the possibility to take note of the energy limitation concerning the controlling signal in the quality indicator. Object condition equations (1) contain a component that takes into account the disturbance being the sum of sinusoidal components wt (2). For the correct synthesis of the WMOC controller, it is important to assume that the system with open feedback loop is stable. If this is not the case in the first phase described below, the object-stabilising coupling is implemented.(1)x˙t=Asxt+Buut+Bwwt,x0=x0,(2)wt=α1sinω1t+φ1,…,αjsinωjt+φj,…,αnwsinωnwt+φnwT,where AsandB are matrices describing the dynamics of the object, As is the matrix for which all real parts of the eigenvalues assume negative values, and αj,ωj,andφj are the amplitude, frequency, and phase of the jth disturbance signal, respectively.The model of the object described by equations (1) and (2) is nonstationary; it is due to the fact that harmonic disturbances for chosen frequencies ωj are taken into account. During modelling of the disturbing signal existing in vector wt, the model of the object could be transformed to its autonomous form which is time-independent. The harmonic disturbances existing in vector wt were modelled by equation (3).(3)x˙d,2j−1t=ωjxd,2jt,x˙d,2jt=−ωjxd,2j−1t,wjt=xd,2j−1t,j=1,…,nw.Taking into consideration equation (3), the model of the object described by equations (1) and (2) can be rewritten in the autonomous form with extended state vector x^t.(4)x˙t=Asxt+Buut+BwCdxdt,x˙dt=Adxdt,x0=x0,xd0=xd,0,x^=xT,xdTT.On the basis of formula (3), coefficients of matrices Ad∈R2nw×2nw and Cd∈Rnw×2nw (5) were determined.(5)ad,l,j=ωk,l=2k−1,j=2k,k=1,…,nw,−ωk,l=2k,j=2k−1,k=1,…,nw,0,in other  cases,cd,l,j=1,l=2k−1,j=2k−1,k=1,…,nw,0,in other  cases.The model of the object described by state equations (4) is time-independent. Amplitudes and phases of disturbing harmonic signal frequencies wt are the result of initial conditions xd,0 and vector xdt. Compound frequencies ωj of disturbing signal wt are the assumed object model parameters. For the considerations presented below, in particular for these frequencies, an improvement of vibration reduction efficiency with minimal energy consumption is required. To design a controller, a WMOC method was used. The method is described in detail in the literature [31].In the WMOC synthesis method, a weighted multitone quality indicator is used to evaluate feasible solutions. It allows for the inclusion of energy limitations, independently for each component of the control signal.During WMOC design, an optimal solution is searched for in a set of control signalsU˜ consisting of continuous and bounded functions for which limits (6) and (7) exist for any ω.(6)uα=2limTd⟶∞1Td∫0Tdutsinωtdt,(7)uβ=2limTd⟶∞1Td∫0Tdutcosωtdt.In particular, from equations (6) and (7), it results that limits exist for frequency ωj.(8)uαj=2limTd⟶∞1Td∫0Tdutsinωjtdt,(9)uβj=2limTd⟶∞1Td∫0Tdutcosωjtdt.Taking into account equations (8) and (9), functions from set U˜ could be written as formulas (10) and (11):(10)ut=∑j=1nwujt+uˇt,(11)ujt=uαjsinωjt+uβjcosωjt.This indicator is based on the distribution of control signalut on sinusoidal components ujt, related to the frequency of disturbing signals ωj.Taking into account the foregoing, weighted multitone quality indicator [31] is defined using the following equation:(12)Jωx,u=limsupTd⟶∞1Td∫0TdxTtQxt+∑j=1nwujtTRjujtdt.MatricesRj (positively defined Rj>0) are associated with individual sinusoidal components of the control signal and allow for the inclusion of energy limitations independently for each component. The optimum WMOC is determined by solving the dynamic optimisation task with quality indicator (12) and limitations (1) and (2). The set of control signals U˜ contains limited continuous functions for which there is a decomposition defined by formulas (8) to (10). Quality indicator Jω is determined correctly for a set of control signals defined as such. The solution of the optimisation task described by formulas (1), (2), and (12) is determined based on formulas (13) to (16).(13)u∗t=∑j=1nwu∗jt,(14)u∗jt=ReKjwjt+ImKjwω,jt,(15)Kj=−BuT−iωjIn−AsT−1QiωjIn−As−1Bu+Rj−1⋅BuT−iωjIn−AsT−1QiωjIn−As−1Bwj,(16)wωt=α1sinω1t+φ1+π2,…,αnwsinωnwt+φnw+π2T,where Bwj is the jth column of the Bw matrix, wjt is the jth coordinate of vector wt, and i=−1.The solution of the optimisation problem denoted by (1), (2), and (12) is described by (13) to (16). The proof of it is shown in the literature [31].The solution of the optimisation problem described by formulas (1), (2), and (12) is ambiguous, e.g., by adding any limited signal tending to zero to the optimal control, optimal control is obtained as well. The solution given in formulas (13) to (16) was selected in a manner allowing it to be independent of the initial conditions and of state vector xt describing the state of the object without taking into account harmonic disturbances. It is a function of disturbing signals wt and the signals offset by π/2 with respect to the wt vector.Taking into account the model of the object in formulas (4) and (5) independent of time, signal vector wωt was formulated in the form(17)wωt=Cd,ωxdt.Matrix coefficientsCd,ω were determined based on (3).(18)cd,ω,l,j=1,l=2k,j=2k,k=1,…,nw,0,in other cases.The WMOC determines optimal control. The control signal is optimal only for sinusoidal components with frequenciesω1,…,ωnw. For other frequencies, the amplitude characteristics of the closed system remain unchanged. For this reason, the synthesis of the controller is divided into two phases.


### 2.1.1. Phase One

It allows shaping of the frequency characteristics over the entire frequency range. The control signal is determined by solving the classical optimisation problem with the linear quadratic controller (LQR) defined by formulas (19) and (20):(19)Jx,u=∫0∞xTtQxt+uTtR0utdt,(20)x˙t=Axt+Buut,x0=x0.TheK0 controller is determined by solving the Riccati equation:(21)PA+ATP−PBuR0−1BuTP+Q=0,K0=BuTP.


### 2.1.2. Phase Two

The frequency characteristics are modified for the selected disturbance signal frequencies. The controllers, as mentioned previously, are determined based on the solution of the optimisation task from (1) to (12). Matrix As occurring in object state equations (1) is derived from the following formula:(22)As=A−BuK0.ControllersKj for each frequency are determined based on formula (15).The WMOC structure is presented in Figure1.Figure 1
Block diagram of the WMOC.


## 2.1.1. Phase One

It allows shaping of the frequency characteristics over the entire frequency range. The control signal is determined by solving the classical optimisation problem with the linear quadratic controller (LQR) defined by formulas (19) and (20):(19)Jx,u=∫0∞xTtQxt+uTtR0utdt,(20)x˙t=Axt+Buut,x0=x0.TheK0 controller is determined by solving the Riccati equation:(21)PA+ATP−PBuR0−1BuTP+Q=0,K0=BuTP.


## 2.1.2. Phase Two

The frequency characteristics are modified for the selected disturbance signal frequencies. The controllers, as mentioned previously, are determined based on the solution of the optimisation task from (1) to (12). Matrix As occurring in object state equations (1) is derived from the following formula:(22)As=A−BuK0.ControllersKj for each frequency are determined based on formula (15).The WMOC structure is presented in Figure1.Figure 1
Block diagram of the WMOC.


## 2.2. Control System with the WMOC

The WMOC generates a control signal based on the state variables and of course on disturbing signal (14). For calculating u∗jt of the control signal components, it is required to determine the sinusoidal component vectors wt and the wωt vector (16) in real time. In the presented control system, these vectors are determined basing on disturbing signal ξt. But if disturbance ξt measurement is impossible, the extended state vector x^t estimator could be used.In the method which is used in this case, parameters (wαj and wβj) of signals wjt are estimated on the basis of formulas (23). The time interval equals t−TIj,t, where TIj is the estimation time and t is the current moment of time.(23)wαjt=1TIj∫t−TIjtξτsinωjτ−t+TIjdτ,wβjt=1TIj∫t−TIjtξτcosωjτ−t+TIjdτ,wjτ=wαjtsinωjτ+wβjtcosωjτfor,τ∈t−TIj,t.Estimation timesTIj can be chosen independently for each jth component. It is good practice to determine it as the multiple of the estimated wjt component period. Signals wjt,wω,jt are determined on the basis of formulas (24) (t is the present moment of time).(24)wjt=wαjtsinωjTIj+wβjtcosωjTIj,wω,jt=wαjtsinωjTIj+π2+wβjtcosωjTIj+π2.A short estimation time of componentswjt, wω,jt improves the quality of control in the case of variation of disturbance parameters. As a result, estimation times TIj should be assumed as being as short as possible. On the other hand, the shortening of these times aggravates the quality of harmonic component estimation. From the numerical analysis, it is clear that a good compromise is to assume estimation time TIj at the level equal to 10 periods of the estimated sinusoidal component. In the tests carried out later in this study, estimation times TIj were used at the level of 100 periods of the estimated sinusoidal component of the disturbing signal.Figure2 shows a diagram of a control system with the WMOC. The K0 controller closes the feedback loop and is determined in phase one using LQR synthesis. Controllers K1,…,Knw are derived from formula (15). Parameter estimation of sinusoidal disturbances vector (PESDV) blocks are used to determine sinusoidal component wjt when ωj is the frequency of the disturbing signal. These blocks additionally generate signals x˜d,2j−1 and x˜d,2j corresponding to wj and wω,j necessary for the correct operation of controllers Kj. Signals wjt, wω,jt are determined in the PESDV block from formula (24).Figure 2
The WMOC control system with the parameter estimation of sinusoidal disturbances.


## 3. Synthesis of Active Suspension Based on a WMOC

### 3.1. Criteria for Assessing the Active Suspension of a Vehicle

The basic criterion for evaluating the suspension system is the vibration transmissibility function. In the case of active suspensions, the energy indicators are important criteria for evaluating suspension work. These criteria were formulated for the quarter suspension of a wheeled vehicle, the scheme of which is shown in Figure3. The primary function of the suspension system is to reduce the vibrations of mass m2. The displacement coordinate of sprung mass m2 is denoted by z2. The suspension elements were modelled using a parallel connection of spring k2 and viscous damping b2. The tyre was modelled using spring k1 and unsprung mass m1 (the wheel weight and reduced weight of the suspension arm and suspension components associated with it).Figure 3
Schematic diagram of the quarter vehicle suspension.Ideal force-generating elementFs was adopted as the actuator. The disturbance signal from the road is denoted by w. The vibration transmissibility function for the shown suspension in Figure 3 is defined by the following formula:(25)Tz2,wf=z2skfwskf,zxskf=1To∫0Tozxt−z¯x2dt,z¯x=1To∫0Tozxtdt,where zx∈z2,w.Active suspension was assessed with regard to energy based on the average energy transferred from or to the power source and instantaneous power analysis on the actuator.The instantaneous power generated by the actuator is presented by the following formula:(26)Pst=Fstz˙2t−z˙1t.One of the basic indicators used in the selection of the actuators is power demandPs,max (27). This indicator allows for the selection of the power supply unit. The actuators must be selected so that when the control system is operating, the maximum power specified for a given component is not exceeded. Power Ps,max takes positive values. If the Ps,max values for the analysed frequency range were negative, then a controlled energy dissipation element (e.g., based on intelligent materials) should be used as the actuator. Then, the suspension of the vehicle would be a type of semiactive suspensions.(27)Ps,max=maxtPst.Similarly, for the control system, minimum instantaneous powerPs,min can be defined (28). Power Ps,min may generally assume negative values. This means that in a given control, there is the possibility for energy recovery.(28)Ps,min=mintPst.The energy demand of the vibration reduction system can be estimated from theEs,mod index (29). In this indicator, the modulus of instantaneous power is averaged. Adoption of this definition implies that there is no energy recovery system in the suspension.(29)Es,mod=1To∫0ToPstdt.The average energy dissipated in active suspensionEs,avg is determined by formula (30). This energy corresponds to the demand for energy from an external power source in the case of using an ideal energy recovery system.(30)Es,avg=1To∫0ToPstdt.The evaluation criteria defined by formulas (27) to (30) were used to compare the energy properties of the WMOC and the reference controller designed using the LQR method.


### 3.2. Synthesis of a WMOC for Quarter Active Vehicle Suspension

The mathematical model of the active suspension is established from the calculation scheme shown in Figure3. The equations of force equilibrium are presented by the following formula:(31)m2z¨2+b2z˙2−z˙1+k2z2−z1=Fs,m1z¨1−b2z˙2−z˙1−k2z2−z1+k1z1−w=−Fs.The state vector and input vector are assumed in the following formula:(32)x=z2,z˙2,z1,z˙1T,u=Fs.Displacementw was assumed as the disturbance signal. Force Fs is the control signal. The state equations are derived from equilibrium force equations (31). State matrix As and input matrix Bu needed to determine equation (1) are defined by the following formula:(33)A=0100−k2m2−b2m2k2m2b2m20001k2m1b2m1−k2+k1m1−b2m1,Bu=0,1m2,0,−1m1T.MatrixBw is defined by the following formula:(34)Bw=Bw1,…,Bwnw,Bw1=Bw2=⋯Bwnw=0,0,0,k1m1T.All theBw matrix columns are equal because disturbing signal w is scalar. The following suspension parameters were assumed:(35)m1=35.5kg,m2=365kg,k1=175500N/m,k2=20000N/m,b2=1290Ns/m.The adopted parameters correspond to the parameters of a light SUV vehicle suspension.


## 3.1. Criteria for Assessing the Active Suspension of a Vehicle

The basic criterion for evaluating the suspension system is the vibration transmissibility function. In the case of active suspensions, the energy indicators are important criteria for evaluating suspension work. These criteria were formulated for the quarter suspension of a wheeled vehicle, the scheme of which is shown in Figure3. The primary function of the suspension system is to reduce the vibrations of mass m2. The displacement coordinate of sprung mass m2 is denoted by z2. The suspension elements were modelled using a parallel connection of spring k2 and viscous damping b2. The tyre was modelled using spring k1 and unsprung mass m1 (the wheel weight and reduced weight of the suspension arm and suspension components associated with it).Figure 3
Schematic diagram of the quarter vehicle suspension.Ideal force-generating elementFs was adopted as the actuator. The disturbance signal from the road is denoted by w. The vibration transmissibility function for the shown suspension in Figure 3 is defined by the following formula:(25)Tz2,wf=z2skfwskf,zxskf=1To∫0Tozxt−z¯x2dt,z¯x=1To∫0Tozxtdt,where zx∈z2,w.Active suspension was assessed with regard to energy based on the average energy transferred from or to the power source and instantaneous power analysis on the actuator.The instantaneous power generated by the actuator is presented by the following formula:(26)Pst=Fstz˙2t−z˙1t.One of the basic indicators used in the selection of the actuators is power demandPs,max (27). This indicator allows for the selection of the power supply unit. The actuators must be selected so that when the control system is operating, the maximum power specified for a given component is not exceeded. Power Ps,max takes positive values. If the Ps,max values for the analysed frequency range were negative, then a controlled energy dissipation element (e.g., based on intelligent materials) should be used as the actuator. Then, the suspension of the vehicle would be a type of semiactive suspensions.(27)Ps,max=maxtPst.Similarly, for the control system, minimum instantaneous powerPs,min can be defined (28). Power Ps,min may generally assume negative values. This means that in a given control, there is the possibility for energy recovery.(28)Ps,min=mintPst.The energy demand of the vibration reduction system can be estimated from theEs,mod index (29). In this indicator, the modulus of instantaneous power is averaged. Adoption of this definition implies that there is no energy recovery system in the suspension.(29)Es,mod=1To∫0ToPstdt.The average energy dissipated in active suspensionEs,avg is determined by formula (30). This energy corresponds to the demand for energy from an external power source in the case of using an ideal energy recovery system.(30)Es,avg=1To∫0ToPstdt.The evaluation criteria defined by formulas (27) to (30) were used to compare the energy properties of the WMOC and the reference controller designed using the LQR method.


## 3.2. Synthesis of a WMOC for Quarter Active Vehicle Suspension

The mathematical model of the active suspension is established from the calculation scheme shown in Figure3. The equations of force equilibrium are presented by the following formula:(31)m2z¨2+b2z˙2−z˙1+k2z2−z1=Fs,m1z¨1−b2z˙2−z˙1−k2z2−z1+k1z1−w=−Fs.The state vector and input vector are assumed in the following formula:(32)x=z2,z˙2,z1,z˙1T,u=Fs.Displacementw was assumed as the disturbance signal. Force Fs is the control signal. The state equations are derived from equilibrium force equations (31). State matrix As and input matrix Bu needed to determine equation (1) are defined by the following formula:(33)A=0100−k2m2−b2m2k2m2b2m20001k2m1b2m1−k2+k1m1−b2m1,Bu=0,1m2,0,−1m1T.MatrixBw is defined by the following formula:(34)Bw=Bw1,…,Bwnw,Bw1=Bw2=⋯Bwnw=0,0,0,k1m1T.All theBw matrix columns are equal because disturbing signal w is scalar. The following suspension parameters were assumed:(35)m1=35.5kg,m2=365kg,k1=175500N/m,k2=20000N/m,b2=1290Ns/m.The adopted parameters correspond to the parameters of a light SUV vehicle suspension.


## 4. Tests of Active Suspension with a WMOC

### 4.1. Active Suspension with a WMOC

The tests of the WMOC were carried out for the active parallel suspension. The diagram of the quadratic model of this suspension is shown in Figure3. The parameters taken in the tests correspond to the quarter SUV-type suspension. The reference controller (REF) was designed using the LQR method. It was assumed that the active system guarantees vibration reduction below −10dB over the entire frequency range, and for arbitrarily selected frequencies (1Hz,2Hz,3Hz,4Hz,and5Hz), the vibration reduction should be greater and be at a level of at least −20dB. These frequencies are selected, for example, from the control band. In a real object, they should be associated with specific frequencies that are relevant to the control goal. The vibration transmissibility functions for the designed controllers (REF and WMOC) are shown in Figure 4.Figure 4
Vibration transmissibility functions for the suspension with the reference controller (REF) and WMOC.In the case of REF, the need to provide vibration reduction of−20dB for some frequencies resulted in a necessity to increase the efficiency of vibration reduction over the entire frequency range to the level of −20dB or even less.


### 4.2. Analysis of WMOC Properties

The controllers developed using the LQR method generate the optimum control signal for an object with nonzero initial conditions. In the case of the harmonic disturbing signal, the control signal generated by such a controller is not optimal. On the other hand, the control law in the case of the WMOC is optimal for the harmonic disturbance signals that were assumed during the design phase. In Figure5, it is shown that for the WMOC at frequencies of 2Hz,3Hz,4Hz, and 5Hz, the force generated by the actuator decreased. At the same time, the vibration reduction for these frequencies is less than −20dB (Figure 4). This results from the aforementioned fact that in the case of 1Hz,2Hz,3Hz,4Hz, and 5Hz frequencies, the WMOC generates an optimal controlling signal.Figure 5
The force generated by the suspension actuator with the WMOC and the reference (REF) controller for 0.05 m induction amplitude.
(a)
(b)Figure5 shows the comparison between the forces generated by the actuator in the case of the WMOC (green line) and REF (red line). The maximum output force generated in the case of the WMOC is 1600N, whereas in respect of the REF, it is 4250N. In the frequency range below 2.5Hz, the forces generated by actuators are similar. In the case of frequencies above 2.5Hz, the WMOC is characterised by much lower generated force values compared to the reference controller. The use of the WMOC allowed for reducing the requirements concerning the maximum force generated by the actuator—from 4250N to 1600N.


### 4.3. Analysis of Energy Properties

As mentioned earlier, one of the basic indicators used in the selection of actuators includes power demandPs,max (27). Figure 6 shows the comparison between the power demand for an active suspension controlled with the WMOC and the REF reference one. In the case of the WMOC, maximum power Ps,max for the entire frequency range was 2,831kW, while for REF, it was 32,22kW. Limiting the power requirement from the external power supply allows for limiting its size and price. The Ps,max values are higher for REF over the entire frequency range compared to the values for the WMOC. For the 1Hz frequency, the Ps,max value for the WMOC and the reference controllers were equal. Above the 3Hz frequency, the value of Ps,max for the WMOC is much lower than that for the reference controller.Figure 6
Maximum power generated by the active suspension actuator with the WMOC and the reference one (REF) for 0.05 m induction amplitude.
(a)
(b)Figure7 shows minimum power Ps,min (28) emitted at the actuator for the WMOC and the reference one (REF). In the case of both WMOC and REF controllers, power values Ps,min are negative over the entire frequency range. Based on this result, there is a possibility to retrieve energy in both systems.Figure 7
Minimum values of output power at the actuator of the active suspension with the WMOC and the reference controller (REF) for 0.05 m induction amplitude.For frequencies lower than1.5Hz, power Ps,min assumes the values which are practically equal, regardless of the controller. In the frequency range between 1.5Hz and 5.5Hz, the value of Ps,min is lower for the WMOC, except for the selected frequencies: 1Hz,2Hz,3Hz,4Hz, and 5Hz. In the case of the latter frequencies, the Ps,min values are higher for the WMOC than for the reference controller. Based on this result, the possibility to retrieve energy decreases for optimal control of the active suspension. For frequencies ranging from 5.9Hz to 13.1Hz, the Ps,min values are much higher for the WMOC. Above the 13.1Hz frequency, the Ps,min values are similar for both controllers.The analysis of the WMOC’s demand for energy from the external power supply was conducted using criterionEs,mod defined by formula (29). Figures 8 and 9 show the comparison of the Es,mod values for the WMOC and the reference controller.Figure 8
Average energy taken from the external energy source by the actuator with the WMOC and the reference (REF) controllers. Excitation amplitudeA = 0.05 m.Figure 9
Average energy taken from the external energy source by the actuator with the WMOC and the reference (REF) controllers. The most interesting part (frequency range 0 to 5.5 Hz) of Figure8 was enlarged.
(a)
(b)Figure8 shows that over the entire frequency range, the values of Es,mod are lower for the WMOC than the values achieved by the reference controller. The maximum power consumption for the WMOC was 1400J/s at 11.5Hz, while for the reference controller, it was 15230J/s at 11.1Hz.Figure9 shows the graphs of the Es,mod function in the frequency range up to 5.5Hz. It can be seen that at 1Hz and 2Hz for the WMOC, there was a slight increase in power demand from the external power source. In the case of 3Hz, 4Hz, and 5Hz, the Es,mod values decreased while obtaining the vibration transmissibility function values below −20dB.Figure10 shows the comparison of average energy Es,avg (30) taken from the external power source by the WMOC and the REF controllers.Figure 10
Average energy consumed by or returned from the actuator with the WMOC and the reference (REF) controllers. Excitation amplitudeA = 0.05 m.For the WMOC,Es,avg takes negative values in the frequency range between 1.9Hz and 10.6Hz, except for the specific previously chosen frequencies of 3Hz,4Hz, and 5Hz. Taking this fact into account, the usage of an efficient energy recovery system would allow the reduction of vibrations at −10dB level without an external power supply. The vibration transmissibility function for frequencies of 1Hz,2Hz,3Hz,4Hz, and 5Hz is below −20dB; therefore, Es,avg values for these specific frequencies are greater than zero.Estimating the energy consumption in the active suspension would require using theEs,mod index. Analysis of Es,avg indicates the possibility of a significant reduction in energy use, if an active suspension is equipped with an energy recovery system.


## 4.1. Active Suspension with a WMOC

The tests of the WMOC were carried out for the active parallel suspension. The diagram of the quadratic model of this suspension is shown in Figure3. The parameters taken in the tests correspond to the quarter SUV-type suspension. The reference controller (REF) was designed using the LQR method. It was assumed that the active system guarantees vibration reduction below −10dB over the entire frequency range, and for arbitrarily selected frequencies (1Hz,2Hz,3Hz,4Hz,and5Hz), the vibration reduction should be greater and be at a level of at least −20dB. These frequencies are selected, for example, from the control band. In a real object, they should be associated with specific frequencies that are relevant to the control goal. The vibration transmissibility functions for the designed controllers (REF and WMOC) are shown in Figure 4.Figure 4
Vibration transmissibility functions for the suspension with the reference controller (REF) and WMOC.In the case of REF, the need to provide vibration reduction of−20dB for some frequencies resulted in a necessity to increase the efficiency of vibration reduction over the entire frequency range to the level of −20dB or even less.


## 4.2. Analysis of WMOC Properties

The controllers developed using the LQR method generate the optimum control signal for an object with nonzero initial conditions. In the case of the harmonic disturbing signal, the control signal generated by such a controller is not optimal. On the other hand, the control law in the case of the WMOC is optimal for the harmonic disturbance signals that were assumed during the design phase. In Figure5, it is shown that for the WMOC at frequencies of 2Hz,3Hz,4Hz, and 5Hz, the force generated by the actuator decreased. At the same time, the vibration reduction for these frequencies is less than −20dB (Figure 4). This results from the aforementioned fact that in the case of 1Hz,2Hz,3Hz,4Hz, and 5Hz frequencies, the WMOC generates an optimal controlling signal.Figure 5
The force generated by the suspension actuator with the WMOC and the reference (REF) controller for 0.05 m induction amplitude.
(a)
(b)Figure5 shows the comparison between the forces generated by the actuator in the case of the WMOC (green line) and REF (red line). The maximum output force generated in the case of the WMOC is 1600N, whereas in respect of the REF, it is 4250N. In the frequency range below 2.5Hz, the forces generated by actuators are similar. In the case of frequencies above 2.5Hz, the WMOC is characterised by much lower generated force values compared to the reference controller. The use of the WMOC allowed for reducing the requirements concerning the maximum force generated by the actuator—from 4250N to 1600N.


## 4.3. Analysis of Energy Properties

As mentioned earlier, one of the basic indicators used in the selection of actuators includes power demandPs,max (27). Figure 6 shows the comparison between the power demand for an active suspension controlled with the WMOC and the REF reference one. In the case of the WMOC, maximum power Ps,max for the entire frequency range was 2,831kW, while for REF, it was 32,22kW. Limiting the power requirement from the external power supply allows for limiting its size and price. The Ps,max values are higher for REF over the entire frequency range compared to the values for the WMOC. For the 1Hz frequency, the Ps,max value for the WMOC and the reference controllers were equal. Above the 3Hz frequency, the value of Ps,max for the WMOC is much lower than that for the reference controller.Figure 6
Maximum power generated by the active suspension actuator with the WMOC and the reference one (REF) for 0.05 m induction amplitude.
(a)
(b)Figure7 shows minimum power Ps,min (28) emitted at the actuator for the WMOC and the reference one (REF). In the case of both WMOC and REF controllers, power values Ps,min are negative over the entire frequency range. Based on this result, there is a possibility to retrieve energy in both systems.Figure 7
Minimum values of output power at the actuator of the active suspension with the WMOC and the reference controller (REF) for 0.05 m induction amplitude.For frequencies lower than1.5Hz, power Ps,min assumes the values which are practically equal, regardless of the controller. In the frequency range between 1.5Hz and 5.5Hz, the value of Ps,min is lower for the WMOC, except for the selected frequencies: 1Hz,2Hz,3Hz,4Hz, and 5Hz. In the case of the latter frequencies, the Ps,min values are higher for the WMOC than for the reference controller. Based on this result, the possibility to retrieve energy decreases for optimal control of the active suspension. For frequencies ranging from 5.9Hz to 13.1Hz, the Ps,min values are much higher for the WMOC. Above the 13.1Hz frequency, the Ps,min values are similar for both controllers.The analysis of the WMOC’s demand for energy from the external power supply was conducted using criterionEs,mod defined by formula (29). Figures 8 and 9 show the comparison of the Es,mod values for the WMOC and the reference controller.Figure 8
Average energy taken from the external energy source by the actuator with the WMOC and the reference (REF) controllers. Excitation amplitudeA = 0.05 m.Figure 9
Average energy taken from the external energy source by the actuator with the WMOC and the reference (REF) controllers. The most interesting part (frequency range 0 to 5.5 Hz) of Figure8 was enlarged.
(a)
(b)Figure8 shows that over the entire frequency range, the values of Es,mod are lower for the WMOC than the values achieved by the reference controller. The maximum power consumption for the WMOC was 1400J/s at 11.5Hz, while for the reference controller, it was 15230J/s at 11.1Hz.Figure9 shows the graphs of the Es,mod function in the frequency range up to 5.5Hz. It can be seen that at 1Hz and 2Hz for the WMOC, there was a slight increase in power demand from the external power source. In the case of 3Hz, 4Hz, and 5Hz, the Es,mod values decreased while obtaining the vibration transmissibility function values below −20dB.Figure10 shows the comparison of average energy Es,avg (30) taken from the external power source by the WMOC and the REF controllers.Figure 10
Average energy consumed by or returned from the actuator with the WMOC and the reference (REF) controllers. Excitation amplitudeA = 0.05 m.For the WMOC,Es,avg takes negative values in the frequency range between 1.9Hz and 10.6Hz, except for the specific previously chosen frequencies of 3Hz,4Hz, and 5Hz. Taking this fact into account, the usage of an efficient energy recovery system would allow the reduction of vibrations at −10dB level without an external power supply. The vibration transmissibility function for frequencies of 1Hz,2Hz,3Hz,4Hz, and 5Hz is below −20dB; therefore, Es,avg values for these specific frequencies are greater than zero.Estimating the energy consumption in the active suspension would require using theEs,mod index. Analysis of Es,avg indicates the possibility of a significant reduction in energy use, if an active suspension is equipped with an energy recovery system.


## 5. Conclusions

This work presents the study of the energy properties of the WMOC used to control the active suspension of a wheeled vehicle. The results of the study were compared with LQR-controlled suspension studies. It can be seen that the WMOC improves the vibration transmissibility function for selected frequencies while taking into account energy limitation. The control signal generated by the WMOC for these frequencies is optimal, and therefore, it is possible to improve the vibration transmissibility function while limiting the amplitude of the force generated by the actuator. When comparing WMOC and LQR controllers, the use of the WMOC allowed for reducing the requirements concerning the power generated by the actuator when the assumed requirements regarding the vibration transmissibility function were met. Another important parameter is the demand for power of the active vibration reduction system. The WMOC allowed for limiting the power consumption from external power supplies so they could be smaller and cheaper in terms of reduced dimensions and price. The conducted tests demonstrated that the use of the WMOC allows for a significant reduction of the energy requirements in the vibration reduction system. By analysing the criteria for the suspension evaluation, it was found that there was a possibility for improving the energy properties of the active suspension by using an energy recovery system.



---

*Source: 6414352-2020-02-12.xml*