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Mathematical Problems in Engineering

Volume 2013 (2013), Article ID 598489, 12 pages

http://dx.doi.org/10.1155/2013/598489

## Finite Frequency Vibration Control for Polytopic Active Suspensions via Dynamic Output Feedback

^{1}Research Institute of Intelligent Control and Systems, Harbin Institute of Technology, Harbin 150001, China^{2}School of Astronautics, Harbin Institute of Technology, Harbin 150001, China^{3}Department of Engineering, Faculty of Engineering and Science, University of Agder, N-4898 Grimstad, Norway

Received 18 June 2013; Accepted 25 July 2013

Academic Editor: Hui Zhang

Copyright © 2013 Yifu Zhang et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

#### Abstract

This paper presents a disturbance attenuation strategy for active suspension systems with frequency band constraints, where dynamic output feedback control is employed in consideration that not all the state variables can be measured on-line. In view of the fact that human are sensitive to the virbation between 4–8 Hz in vertical direction, the control based on generalized Kalman-Yakubovich-Popov (KYP) lemma is developed in this specific frequency, in order to achieve the targeted disturbance attenuation. Moreover, practical constraints required in active suspension design are guaranteed in the whole time domain. At the end of the paper, the outstanding performance of the system using finite frequency approach is confirmed by simulation.

#### 1. Introduction

By reason of rough road conditions, passengers in the car are often in a vibration environment which negatively impacts the comfort, mental, and physical health of them, and suspensions are crucial to attenuate the disturbance transferred to passengers [1–3]. Hence, various approaches various approaches have been developed that aim to enhance suspensions’ performance such as adaptive control [4], robust control [5, 6], and fuzzy control [7]. Generally speaking, there are three types of suspensions: passive, semiactive, and active suspensions. Compared with the other two kinds of suspensions, active suspensions have a greater potential to improve ride comfort and to guarantee the ride safety due to the existence of active actuator.

There are three performance requirements for active suspension systems. One is the ride comfort, which requires isolation of vibration from road; another one is handling performance mainly described by road holding, which restricts the hop of wheel in order to ensure continuous contact of wheels to road; the last one is the sprung displacement which limits the suspension stroke within an allowable band.

However, these requirements are usually conflicting. For instance, a large suspension displacement may exist if a better rider comfort performance is required. A variety of control strategies have been applied to cope with this conflict [8–12]. In particular, because the norm index can measure the vibration attenuation performance of system appropriately [13], many suspension problems are considered by control theory [14–22]. In this paper, the handling performance and the suspension stroke are regarded as constraints, and the ride comfort is deemed as the main index to optimize.

Although various control strategies have been applied to promote ride comfort performance of suspension systems, few of them notice the fact that due to the human body structure and other factors people are more sensitive to disturbances in 4–8 Hz than other frequency in vertical direction (ISO2361). Therefore, it is considerable to develop a finite frequency strategy to reduce the negative effect caused by disturbances in 4–8 Hz. The generalized Kalman-Yakubovich-Popov (KYP) lemma, which has been used to solve practical problems [23, 24], is applied to achieve the finite frequency control to active suspensions.

It should be mentioned that the parameters of passengers including model for suspension system could vary due to the mass change of passengers, so how to guarantee the performance of suspension with varying parameters is worth discussing. Meanwhile, considering that the mass of passengers can be accessed on line, in this paper, the suspension model is described as a polytope, and then a parameter-dependent control law is proposed to assure the above performance requirements, which can also reach a lower conservativeness than control law based on quadratic stability and constant parameter feedback at the same time. In addition, though state feedback may attain a superior performance compared with static output feedback, measuring some states may bring burden to the systems. Thusly, constructing dynamic output feedback is desirable, which can achieve a relative enhanced performance and meanwhile reduce state-measuring sensors.

The paper is organized as follows. In Section 2 the state-space model for quarter car suspension is presented. In Section 3 the theorems which can be used to design the dynamic feedback controller are illustrated. The simulation is presented in Section 4, and the conclusion is in Section 5.

*Notation*. For a matrix , , , , , and stand for its transpose, conjugate transpose, inverse, transposed inverse, and orthogonal complement, respectively; denotes . means that matrix is positive (negative) definite. For a matrix, stands for the th line of the matrix. stands for the norm of transfer function matrix . For matrices and , means the Kronecker product. In symmetric block matrices or complex matrix expressions, we use an asterisk () to represent a term that is induced by symmetry.

#### 2. Quarter Car Suspension Model

The model of a quarter car suspension is shown in Figure 1. and stand for sprung and unsprung mass, respectively. , , and denote the sprung, unsprung displacement, and disturbance displacement from the road, respectively. , , , and are the stiffnesses and dampings of the suspension system, respectively. The input of the controller is denoted by .

Based on the law of Newton, the motion equation of suspension can be denoted as

Define the following state variables and the disturbance input: Then (1) is equivalent to where Define which reflects the acceleration of that contains the body mass of passengers and seat. In the design of control law for suspension system, body acceleration is the main index that needs to be optimized.

The handling performance requires continuous contact of wheel to road, which means that the suspension system needs to guarantee that dynamic tire load is less than static load, namely,

The stroke of the suspension could not be so large that it may exceed the maximum, which can be formulated as

The state space expression is described integrally as where , , and are same with the definition in (4), and

reflects the acceleration output of ; represents for the relative (normalized) constraints output; stands for the output of measurable states.

The parameter-varying model is depicted as the following polytopic form: where and , stand for the maximum and minimum of , respectively.

The form of dynamic output feedback controller is described as Substituting (12) into (8), we get where Denote as the transfer function from to .

The norm of transfer function matrix is applied to depict the ride comfort performance of suspension system, which is defined as where

The control target is summarized as follows.

For a certain , design a dynamic output feedback in the form of (12) which satisfies(I) The closed loop system is asymptotically stable. (II) The finite frequency (from to ) norm from road disturbance to vehicle acceleration is less than . namely, (III) The relative constraint responses shown in the following can be satisfied as long as the disturbance energy is less than the maximum of the 2-norm of disturbance input denoted as . that is,

#### 3. Dynamic Output Feedback Controller Design for Polytopic Suspension System

In this section, we will derive three theorems for the design of output feedback controller that satisfies (19) and one theorem of full frequency controller used for comparison.

##### 3.1. Finite Frequency Design

Theorem 1. *For the given parameters , if there exist symmetric matrices , positive definite symmetric matrices , , and general matrix satisfying**where**then a dynamic output feedback controller exists, which satisfies the requirements of (I), (II) and (III) with .*

*Proof. *By using Schur complement, inequality (20) is equivalent to
where

Multiplying (24) by from the left side and by from the right side, respectively, we obtainwhere .

Applying reciprocal projection theorem (see Appendix A) and choosing , , inequality (26) is equivalent to

Multiplying the above inequality from both the left and the right sides by , we get
which guarantees
obviously. From the standard Lyapunov theory for continuous-time linear system, the closed-loop system (13) is asymptotically stable with .

By substitution, inequality (21) is equivalent to
where

Based on projection lemma (see Appendix A), inequality (30) is equivalent to

Noting that inequality (33) is eternal establishment, we just need to consider inequality (32), which is equivalent to
where

Rewrite inequality (34) as
and then we obtain

Applying generalized KYP lemma (see Appendix A), we get
where
namely,

Select
as the Lyapunov function, we obtain

Applying the following inequality
and (28) to (42), we get

Integrate (44) from to :

Substituting (41) into (45) with , we get
which is equivalent to
where .

Noting that
where stands for the maximum eigenvalue, we can therefore guarantee constraints mentioned in (19) as long as
which is equivalent to (22) by applying Schur complement.

Before giving a convex expression which can be solved by LMI Toolbox, we firstly perform transformation to inequalities (20), (21), and (22).

Decompose matrix for convenience in the following form:

According to the literature [25], we assume that both and are invertible without loss of generality.

Denote and perform the congruence transformation to inequalities (20), (21), and (22) by respectively.

Denotethen we get the following theorem.

Theorem 2. *For the given parameters , if there exist symmetric matrix , positive definite symmetric matrices , , and general matrices , , , , , , , satisfying**then a dynamic output feedback controller exists, which satisfies the requirements of (I), (II) and (III) with .**The corresponding controller in the form of (12) can be given by
*

Though a parameter-dependent controller can be designed via Theorem 2, it is difficult to obtain targeted matrices in real time as varies. Therefore, we give a tractable LMI-based theorem as follows.

Theorem 3. *For the given parameters , and , if there exist symmetric matrix , positive definite symmetric matrices , and general matrices (), satisfying
**
where
**
then a dynamic output feedback controller exists, which satisfies the requirements of (I), (II) and (III) with .**The corresponding controller in the form of (12) can be given by
**
where
**
and can be calculated by (11).*

*Proof. *we just prove that inequality (58) is sufficient to inequality (54) for simplicity.

Denotewhich stands for the left of inequality (54).

Inequality (58) is equivalent to
where
Assume that
and then we get
which is negative definite by inequality (65), that is,

*Remark 4. *, should be chosen to meet the definition, that is,

However, the value of and can be chosen variously for the given , , and . In this paper, we use the singular value decomposition approach.

*Remark 5. *Based on [26], for real matrices and , is equivalent to . Thusly, (59) can be converted into real matrix inequality by defining

*Remark 6. *The matrices of dynamic output feedback controller , , , , and Lyapunov matrix are dependent nonlinearly on parameter . For instance, as can be seen in the above deduction, matrix in Theorem 3 can be formulated as
where and are the corresponding matrix solutions of LMIs in Theorem 3, and the value of matrix may vary with the change of .

*Remark 7. *Inequalities from (58) to (60) can be simplified from 12 LMIs to 4 LMIs if the following matrix variables are chosen as , , , , , , , , , , and . However, this simplification will keep the matrices for the designed controller constant for all , and an invariant Lyapunov function, rather than a parameter-dependent one, has to be used for the whole domain, which will bring a larger conservativeness than Theorem 3.

##### 3.2. Full Frequency Design

Based on the theorem of [27], we formulate Theorem 8 without proof for simplicity.

Theorem 8. *For the given parameter , if there exist positive definite symmetric matrices and general matrices , (), satisfying
**
where
**
then a dynamic output feedback controller exists, which satisfies (I) and (III), and with .**The corresponding controller in the form of (12) can be given by
**
where
**
and can be calculated by (11). *

The same approach mentioned in Remark 4 is used to obtain the value of and , which should meet the following equation:

#### 4. A Design Example

In this section, we will show how to apply the above theorems to design finite frequency controller and full frequency controller for a specific suspension system. The parameter for the suspension is shown in Table 1.

We first choose the following parameters: , , , , and . Then, the matrices in (12) can be calculated by applying Theorem 3 and Remark 7 for finite frequency controller and Theorem 8 for full frequency controller (shown in Appendix B) with the least guaranteed performances for Theorem 3, for Remark 6, and for Theorem 8.

Then, the curves of maximum singular values of systems using open-loop, finite frequency (parameter-dependent), and full frequency controllers are shown in Figure 2. Compared with the other two curves (the open-loop system and the system with full frequency controller), the system with finite frequency controller has the least norm of the three systems in 4–8 Hz, which indicates that the finite frequency controller has a better effect on the attenuation of targeted frequency disturbance.

In order to examine the performance of finite frequency controller, we assume that the disturbance is in the form of where stand for the amplitude and the frequency of disturbance, respectively, and .

Suppose that is 0.4 m and is 5 Hz, and then the body acceleration and the relative constraints responses to this disturbance are shown in Figures 3, 4, and 5, respectively.

It is obvious that the body acceleration response for finite frequency controller decreases faster with respect to time than the other two controllers, and at the same time, both the relative dynamic tire load response and relative suspension stroke response are within the allowable range, which satisfy requirement (III), namely, , .

#### 5. Conclusion

In this paper, we manage to design a dynamic output feedback controller for active suspensions with practical constraints included. This controller particularly diminishes disturbance at 4–8 Hz, which is the frequency sensitive band for human. Besides, for the reason that the controller is a parameter-dependent one, it has a smaller conservativeness than controller designed on the basis of quadratic stability and constant parameter feedback. The excellent performance of the closed-loop system with finite frequency controller has been demonstrated by simulation.

#### Appendices

#### A. Related Lemmas

Lemma A.1 (generalized KYP lemma [28]). *Let matrices , , , and be given, Denote by the null space of , where . The inequality
**
holds, if and only if, there exist , such that
**
where
**
with .*

Lemma A.2 (projection lemma [25] ). *Let , , and be given, there exists a matrix satisfying
**
if and only if, the following two conditions hold:
*

Lemma A.3 (reciprocal projection lemma [25]). *Let be any given positive definite matrix. The following statements are equivalent.*(1)*.*(2)*The LMI problem
is feasible with respect to .*

#### B. Controller Matrices

The parameter matrices of the dynamic output feedback controller for Theorem 3:

The parameter matrices of the dynamic output feedback controller for Theorem 8:

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