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A comparison study of steady-state vibrations with single fractional-order and distributed-order derivatives

  • Jun-Sheng Duan EMAIL logo , Cui-Ping Cheng and Lian Chen
Published/Copyright: December 29, 2017
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Open Physics
From the journal Open Physics Volume 15 Issue 1

Abstract

We conduct a detailed study and comparison for the one-degree-of-freedom steady-state vibrations under harmonic driving with a single fractional-order derivative and a distributed-order derivative. For each of the two vibration systems, we consider the stiffness contribution factor and damping contribution factor of the term of fractional derivatives, the amplitude and the phase difference for the response. The effects of driving frequency on these response quantities are discussed. Also the influences of the order α of the fractional derivative and the parameter γ parameterizing the weight function in the distributed-order derivative are analyzed. Two cases display similar response behaviors, but the stiffness contribution factor and damping contribution factor of the distributed-order derivative are almost monotonic change with the parameter γ, not exactly like the case of single fractional-order derivative for the order α. The case of the distributed-order derivative provides us more options for the weight function and parameters.

Keywords: fractional calculus; vibration; distributed-order derivative; excitation; response
PACS: 02.30.Hq; 46.40.-f; 83.60.Bc

1 Introduction

In recent decades, fractional calculus has been applied to describe memory phenomena and hereditary properties of various materials and processes in different fields of science and engineering. These areas of application cover viscoelasticity theory, non-Newtonian flow, anomalous diffusion, control theory, image processing, capacitor theory, fitting of experimental data, and so on [1, 2, 3, 4]. In recent years, even fractional-order models of happiness [5] and love [6] have been developed, and they are claimed to give a better representation than the integer-order dynamical systems approach.

Viscoelasticity theory is one of the earliest and most active application areas of fractional calculus. The wide use of polymers in fields of engineering has promoted the development of this subject.

In fact, the introducing of the fractional calculus to viscoelastic theory is very natural [7]. Scott-Blair [8, 9, 10] suggested a fractional constitutive relation for a viscoelastic body, which reflects mechanical properties between elastic solids and viscous fluids. Such fractional model was called as the Scott-Blair model [3, 11]. In [12], the terminology “spring-pot” was introduced for the Scott-Blair model.

Fractional oscillator and related models and equations were presented and investigated by Caputo [13], Bagley and Torvik [14], Beyer and Kempfle [15], Mainardi [16], Gorenflo and Mainardi [17], and others [18, 19, 20, 21, 22, 23, 24, 25]. Achar et al. [18] considered response feature for fractional oscillator. Lim et al. [19] considered the relationship between fractional vibration and fractional Brownian movement. Lim and Teo [20] proposed fractional process by using a stochastic differential equation of fractional-order. Li et al. [21] investigated impulse response and system stability for a type of fractional oscillation. Shen et al. [22, 23], Huang and Duan [24] and Duan et al. [25] deliberated the dynamics and resonance phenomenon for fractional-order vibration. A fractional dynamical system and its stability problem and chaotic behaviors were analyzed by Li et al. [26], Zhang et al. [27], Wang and Hu [28], Huang et al. [29] and Wu et al. [30]. Li and Ma [31] presented a linearization and stability theorem for nonlinear fractional system.

Let us recall the basic definitions of fractional calculus. Suppose f(t) is piecewise continuous on (b, +∞) and integrable on any subinterval (b, t). The Riemann-Liouville fractional integral of f(t) of order α is defined as [1, 2, 3, 4]:

bJtαf(t):=∫bt(t−s)α−1Γ(α)f(s)ds,α>0,(1)

where Γ(.) is the Euler’s gamma function and is defined as the infinite integral

Γ(z)=∫0+∞e−xxz−1dx,z>0.(2)

Next we write down the expression for the Riemann-Liouville fractional derivative of f(t) of order α,

bRLDtαf(t):=dndtnbJtn−αf(t),n−1<α<n,(3)

Let f(n)(t) be piecewise continuous on (b, +∞) and integrable on any subinterval (b, t). The Caputo fractional derivative of f(t) of order α is defined as

bCDtαf(t):=bJtn−αf(n)(t),n−1<α<n,(4)

We note that existence of solution of a fractional differential equation was investigated by Podlubny [1], Baleanu et al. [32] and Baleanu and Mustafa [33]. Analytical and numerical methods for solving fractional differential equations were presented in references [1, 2, 4, 16, 17, 34, 35, 36].

In most of the above-mentioned articles, the lower limit b of integration in fractional integral and derivative was taken as zero. So the initial conditions are necessary for solving of fractional-order differential equations. In general, this kind of problem does not admit any periodic solution [16, 17, 37, 38, 39, 40].

Distributed-order derivatives, which are defined by means of integration with respect to the order of fractional derivatives, were presented and discussed in terms of filtering by Caputo [41]. In [42], distributed-order differential equations were introduced to constitutive relations of dielectric media and to a diffusion model. In [43, 44], distributed-order differential equations were solved by introducing a generalized Taylor series representation of solutions. In [45, 46], the relations of viscoelastic bodies were discussed by using distributed-order derivatives.

For the sake of convenient reference, we recall the classic integer-order one-degree-of-freedom vibration subject to a harmonic excitation,

x¨+kx+cx˙=Feiωt,(5)

where k,c,F,ω are positive constants and i is the imaginary unit. The steady response is

x(t)=Feiωtk−ω2+iωc=Fei(ωt−φ)(k−ω2)2+(ωc)2,(6)

where φ is the phase difference between the excitation and the response and is determined by the following equation,

φ=arctan⁡ωck−ω2,k−ω2>0,π/2,k−ω2=0,π+arctan⁡ωck−ω2,k−ω2<0.(7)

For vibration responses, we are usually more interested in the steady-state response. We remark that if the lower limits b in the two definitions of fractional derivatives are taken as −∞, then (3) and (4) are identical. We denote them as−∞Dtαf(t)uniformly.

In this work, we conduct a comparative study for fractional vibration systems with single fractional-order derivative and distributed-order derivative. We consider the steady-state responses to the harmonic excitation by using the fractional-order derivative operator −∞Dtα. In Section 2, we consider the steady-state vibration of a system with single fractional-order derivative. In Section 3, the system with distributed-order derivative is taken into account. In Section 4, two special cases belonging to two different systems in Section 2 and Section 3, respectively, are compared.

2 Steady-state vibration with single fractional-order derivative

Suppose a mass block m slides on a frictionless surface. It is attached to a spring of stiffness factor k in parallel with a dashpot of damping coefficient c and a viscoelastic rod of length l, whose constitutive relation obeys Scott-Blair law. We consider the steady-state vibration of the block under the harmonic driving Feiωt.

The one-degree-of-freedom vibration system is written as

mx¨+kx+cx˙+Gτα⋅−∞Dtαx=Feiωt,(8)

where m,k,c,G,τ,F,ω are positive real constants and 0 ≤ α ≤ 1. If α = 0 or 1, −∞Dtαx denotes x or χ̇, respectively.

Introducing the dimensionless variables and parameters

tτ→t,xl→x,τ2km→k,τcm→c,τ2Gm→G,τ2Fml→F,τω→ω,

we derive the dimensionless form for the vibration system

x¨+kx+cx˙+G⋅−∞Dtαx=Feiωt.(9)

We look for the steady-state same frequency response of the system as

x(t)=Xeiωt,(10)

where X is independent of t and is called as the complex amplitude.

Substituting the first- and second-order derivatives of x(t) and the fractional derivative

−∞Dtαxt=Xiωαeiωt,(11)

into Eq.(9), we achieve the equation

Xk−ω2+iωc+G(iω)α=F.(12)

By the identity iα=cosπα2+isinπα2,Eq. (12) is written as

Xk+Gωαcosπα2−ω2+iωc+Gωα−1sinπα2=F.(13)

Inserting Eq. (10) results in the steady-state response

x(t)=Feiωt/k+Gωαcosπα2−ω2+iωc+Gωα−1sinπα2.(14)

By comparison with the results of the integer-order case in Eq. (6), we derive the equivalent stiffness coefficient and the equivalent damping coefficient and denote them as

k~=k+Gωαcos⁡πα2,c~=c+Gωα−1sin⁡πα2.(15)

So the steady-state response is expressed as

x(t)=Feiωtk~−ω2+iωc~.(16)

Making use of the exponential representation of complex number, we rewrite the steady-state response as

xt=Feiωt−φ(k~−ω2)2+(ωc~)2,(17)

where φ is the phase difference between the excitation and the response and is determined by the following

φ=arctan⁡ωc~k~−ω2,k~−ω2>0,π/2,k~−ω2=0,π+arctan⁡ωc~k~−ω2,k~−ω2<0.(18)

2.1 The stiffness contribution factor and damping contribution factor

The equivalent stiffness factor and damping factor in Eq. (15) mean that the steady-state response of the fractional vibration system (9) is equivalent to that of the integer-order system

x¨+k~x+c~x˙=Feiωt.(19)

We call

k~−k=Gωαcos⁡(πα2),c~−c=Gωα−1sin⁡(πα2),(20)

as the stiffness contribution factor and damping contribution factor of the fractional derivative term G−∞Dtαx, respectively. They are all positive. The stiffness contribution factor k̃ − k is an increasing function of the driving frequency ω, while the damping contribution factor c̃− c is an decreasing function of the driving frequency ω.

Figures 1 and 2 show, respectively, the stiffness contribution factor k̃− k and damping contribution factor c̃− c versus ω for G = 1 and α = 0.25, 0.5, 0.75.

Figure 1 The stiffness contribution factor k̃−k versus α for different values of ω: 0.25 (solid line), 0.5 (dot line), 0.75 (dash line)
Figure 1

The stiffness contribution factor k̃−k versus α for different values of ω: 0.25 (solid line), 0.5 (dot line), 0.75 (dash line)

Figure 2 The damping contribution factor c̃− c versus α for different values of ω: 0.25 (solid line), 0.5 (dot line), 0.75 (dash line)
Figure 2

The damping contribution factor c̃− c versus α for different values of ω: 0.25 (solid line), 0.5 (dot line), 0.75 (dash line)

In order to investigate the dependence of k̃−k and c̃− c on the order α, we calculate the derivatives

d(k~−k)dα=Gωαcos⁡(πα2)ln⁡(ω)−π2tan⁡(πα2),(21)

and

d(c~−c)dα=Gωα−1sin⁡(πα2)ln⁡(ω)+π2cot⁡(πα2).(22)

It follows from Eq. (21) that when 0 < ω ≤ 1, k̃−k monotonically decreases as α increases, while when ω > 1, k̃ − k firstly increases then decreases on the interval 0 ≤ α < 1; see Figure 3, where the curves of k̃ − k versus α are shown for G = 1 and different values of ω. From Eq. (22) we deduce that if 0 < ω < 1, c̃ − c increases followed by decreasing on the interval 0 ≤ α ≤ 1, while if ω ≥ 1, c̃ − c is a monotonically increasing function of α; see Figure 4, where the curves of c̃ − c versus α are shown for G = 1 and different values of ω.

Figure 3 The stiffness contribution factor k̃ − k versus α for different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 3 (dot-dash-line) and 6 (dot-dot-dash line)
Figure 3

The stiffness contribution factor k̃ − k versus α for different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 3 (dot-dash-line) and 6 (dot-dot-dash line)

Figure 4 The damping contribution factor c̃ − c versus α for different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line)and 3 (dotdash line) and 6 (dot-dot-dash line)
Figure 4

The damping contribution factor c̃ − c versus α for different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line)and 3 (dotdash line) and 6 (dot-dot-dash line)

2.2 Amplitude and phase difference

The amplitude of the response is obtained from Eqs. (15) and (17) as

xt=F/k+Gωαcosπα2−ω22+ωc+Gωαsinπα221/2.(23)

We take k = 1.2, c = 0.1, F = G = 1, the curves of amplitudes |x (t)| versus the driving frequency ω are shown in Figure 5 for different values of the order α. The curves of amplitude |x (t)| versus the order α are shown in Figure 6 for different values of the driving frequency ω. We observe that as α increases, resonance peaks and resonance frequencies decrease. Increasing and decreasing of the amplitude with the order α depend on the frequency region.

Figure 5 The amplitude |x (t)| versus α for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.1 (solid line), 0.2 (dot line), 0.4 (dash line), 0.6 (dot-dash line), 0.8 (dot-dot-dash line) and 1 (dot-dot-dash-dash line)
Figure 5

The amplitude |x (t)| versus α for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.1 (solid line), 0.2 (dot line), 0.4 (dash line), 0.6 (dot-dash line), 0.8 (dot-dot-dash line) and 1 (dot-dot-dash-dash line)

Figure 6 The amplitude |x (t)| versus α for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)
Figure 6

The amplitude |x (t)| versus α for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)

In Figures 7 and 8, the curves of phase-difference φ in Eq. (18) versus the frequency ω and versus the order α are shown for the same parameter values as in Figures 5 and 6, respectively. As the driving frequency ω increases, the phase-difference φ increases from 0 to π, and the variation is more abrupt for small α. The changing of the phase-difference with the order α relies on the frequency region.

Figure 7 Curves of φ versus ω for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.1 (solid line), 0.2 (dot line), 0.4 (dash line), 0.6 (dot-dash line), 0.8 (dot-dot-dash line) and 1 (dot-dot-dash-dash line)
Figure 7

Curves of φ versus ω for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.1 (solid line), 0.2 (dot line), 0.4 (dash line), 0.6 (dot-dash line), 0.8 (dot-dot-dash line) and 1 (dot-dot-dash-dash line)

Figure 8 Curves of φ versus ω for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)
Figure 8

Curves of φ versus ω for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)

3 Steady-state vibration with distributed-order derivative

We suppose the acting force of the viscoelastic rod in the vibration system (8) in Section 2 is expressed as an integration of the Scott-Blair model with respect to the order, i.e. a distributed-order derivative as

∫01p(λ)Gτλ⋅−∞Dtλxdλ,

where p(λ) is the weight distribution function of the order and satisfies the following identities,

p(λ)≥0,0≤λ≤1;∫01p(λ)dλ=1.(24)

Then the dimensionless vibration system in Eq. (9) is modified as

x¨+kx+cx˙+G∫01p(λ)⋅−∞Dtλxdλ=Feiωt.(25)

The weight distribution function of the order p(λ) can be given in infinitely many ways. Here we take it as an exponential function with the constant base μ as a parameter,

p(λ)=C(μ)μλ,0<μ<+∞,(26)

where the coefficient is given as

C(μ)=ln⁡μμ−1,μ≠1,1,μ=1.(27)

It is easy to check that p(λ) in Eq. (26) satisfies the conditions in (24). We remark that such selection of the weight distribution function is for the sake of calculation. Also we note that if we take the weight distribution function p (λ) as the Dirac delta distribution δ(λ−α), Eq. (25) is derived from the system with the distributed-order (25).

Similar to the last section, with the assumption

x(t)=Xeiωt,(28)

we derive the relation for the complex amplitude X as

Xk−ω2+iωc+GC(μ)∫01(iμω)λdλ=F.(29)

Calculating the integration yields

Xk+GC(μ)2πμω−4ln⁡(μω)4ln2⁡(μω)+π2−ω2+iωc+GC(μ)4μωln⁡(μω)+2π4ωln2⁡(μω)+π2ω=F.(30)

On substitution into Eq. (28) we obtain

x(t)=Feiωt/k+GC(μ)2πμω−4ln⁡(μω)4ln2⁡(μω)+π2−ω2+iωc+GC(μ)4μωln⁡(μω)+2π4ωln2⁡(μω)+π2ω.(31)

The equivalent stiffness factor and damping factor are derived as

k^=k+2GC(μ)πμω−2ln⁡(μω)4ln2⁡(μω)+π2,(32)

and

c^=c+2GC(μ)2μωln⁡(μω)+π4ωln2⁡(μω)+π2ω.(33)

Accordingly, the steady-state response of the system is

xt=Feiωtk^−ω2+iωc^=Feiωt−φ(k^−ω2)2+(ωc^)2,(34)

where the phase difference between the excitation and response is determined as

φ=arctan⁡ωc^k^−ω2,k^−ω2>0,π/2,k^−ω2=0,π+arctan⁡ωc^k^−ω2,k^−ω2<0.(35)

For the sake of comparison and valuation, we apply the replacement

μ=tan⁡πγ2.(36)

So we convert the infinite interval of μ: 0< μ < +∞ into the finite interval of γ: 0 < γ < 1. Since μ is a constant in the above derivation, such replacement is allowable.

We remark that there are an infinite number of ways to perform such replacement as in Eq. (36).

The weight function parameterized by γ is

p(λ)=p(λ;γ)=C(tan⁡πγ2)tan⁡πγ2γ,(37)

0< γ < 1. In Figure 9, the curves of the weight functions p(λ) are shown for different parameters γ.

Figure 9 The curves of p(λ) versus λ for different values of γ: 0.01 (solid line), 0.2 (dot line), 0.5 (dash line), 0.8 (dot-dash line) and 0.99 (dot-dot-dash line)
Figure 9

The curves of p(λ) versus λ for different values of γ: 0.01 (solid line), 0.2 (dot line), 0.5 (dash line), 0.8 (dot-dash line) and 0.99 (dot-dot-dash line)

3.1 The stiffness contribution factor and damping contribution factor

It follows from Eqs. (32) and (33) that the stiffness contribution factor and damping contribution factor of the distributed-order derivative term are

k^−k=2GC(μ)πμω−2ln⁡(μω)4ln2⁡(μω)+π2,(38)

and

c^−c=2GC(μ)2μωln⁡(μω)+π4ωln2⁡(μω)+π2ω,(39)

respectively.

It is easy to prove that

πy−2lny>0,2yln⁡y+π>0,fory>0.

So the stiffness contribution factor and damping contribution factor are all positive. By substituting μ → tan πγ2, we have

k^−k=2GC(tan⁡πγ2)πωtan⁡πγ2−2ln⁡(ωtan⁡πγ2)4ln2⁡(ωtan⁡πγ2)+π2,c^−c=2GC(tan⁡πγ2)2ωtan⁡πγ2ln⁡(ωtan⁡πγ2)+π4ωln2⁡(ωtan⁡πγ2)+π2ω.(40)

In Figures 10 and 11, the curves of the stiffness contribution factor k̃ − k and damping contribution factor c̃ − c versus ω are shown for G = 1 and γ = 0.1, 0.25, 0.5, 0.75, 0.9, respectively.

Figure 10 The stiffness contribution factork̃ − k versus ω for G = 1 and different values of γ: 0.1 (solid line), 0.25 (dot line), 0.5 (dash line), 0.75 (dot-dash line) and 0.9 (dot-dot-dash line)
Figure 10

The stiffness contribution factork̃ − k versus ω for G = 1 and different values of γ: 0.1 (solid line), 0.25 (dot line), 0.5 (dash line), 0.75 (dot-dash line) and 0.9 (dot-dot-dash line)

Figure 11 The damping contribution factor c̃ − c versus ω for G = 1 and different values of γ: 0.1 (solid line), 0.25 (dot line), 0.5 (dash line), 0.75 (dot-dash line) and 0.9 (dot-dot-dash line)
Figure 11

The damping contribution factor c̃ − c versus ω for G = 1 and different values of γ: 0.1 (solid line), 0.25 (dot line), 0.5 (dash line), 0.75 (dot-dash line) and 0.9 (dot-dot-dash line)

Figures 12 and 13 show, respectively, the stiffness contribution factor k̃ − k and damping contribution factor c̃ − c versus γ for G = 1 and ω = 0.3, 0.6, 1, 3, 6.

Figure 12 The stiffness contribution factork̃ − k versus γ for G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 3 (dot-dash line) and 6 (dot-dot-dash line)
Figure 12

The stiffness contribution factork̃ − k versus γ for G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 3 (dot-dash line) and 6 (dot-dot-dash line)

Figure 13 The damping contribution factor c̃ − c versus γ for G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 3 (dot-dash line) and 6 (dot-dot-dash line)
Figure 13

The damping contribution factor c̃ − c versus γ for G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 3 (dot-dash line) and 6 (dot-dot-dash line)

In contrast to Figures 3 and 4, the curves in Figure 12 are monotonic decreasing apart from a small part on the left in the case of ω = 6 , and the curves in Figure 13 are monotonic increasing.

3.2 Amplitude and phase difference

From Eq. (34), the amplitude of the response is

|xt|=F(k^−ω2)2+(ωc^)2.(41)

In Figure 14 and 15, the curves of the amplitudes |x (t)| versus ω and versus γ are shown for k = 1.2, c = 0.1, F = G = 1 and different values of γ and ω, respectively. The resonance peaks descend as the parameter γ increases. This implies that increasing of γ enhances the system damping. The increasing and decreasing of the amplitudes |x (t)| with the parameter γ rely on the driving frequency ω. In the low-frequency region, the amplitudes |x (t)| is an increasing function of γ, while {in} the high-frequency region, the amplitudes |x (t)| is an decreasing function of γ.

Figure 14 The amplitude |x (t)| versus ω for k = 1.2, c = 0.1, F = G = 1 and different values of γ: 0.01 (solid line), 0.1 (dot line), 0.4 (dash line), 0.7 (dot-dash line), 0.9 (dot-dot-dash line) and 0.99 (dot-dot-dash-dash line)
Figure 14

The amplitude |x (t)| versus ω for k = 1.2, c = 0.1, F = G = 1 and different values of γ: 0.01 (solid line), 0.1 (dot line), 0.4 (dash line), 0.7 (dot-dash line), 0.9 (dot-dot-dash line) and 0.99 (dot-dot-dash-dash line)

Figure 15 The amplitude |x (t)| versus γ for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)
Figure 15

The amplitude |x (t)| versus γ for k = 1.2, c = 0.1, F = G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)

In Figures 16 and 17, the curves of phase difference φ in Eq. (35) versus ω and versus γ are shown for k = 1.2, c = 0.1, G = 1 and different values of γ and ω, respectively. Similar behaviors to Figures 7 and 8 are displayed.

Figure 16 Curves of φ versus ω for k = 1.2, c = 0.1, G = 1 and different values of γ: 0.01 (solid line), 0.1 (dot line), 0.4 (dash line), 0.7 (dot-dash line), 0.9 (dot-dot-dash line) and 0.99 (dot-dot-dashdash line)
Figure 16

Curves of φ versus ω for k = 1.2, c = 0.1, G = 1 and different values of γ: 0.01 (solid line), 0.1 (dot line), 0.4 (dash line), 0.7 (dot-dash line), 0.9 (dot-dot-dash line) and 0.99 (dot-dot-dashdash line)

Figure 17 Curves of φ versus γ for k = 1.2, c = 0.1, G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)
Figure 17

Curves of φ versus γ for k = 1.2, c = 0.1, G = 1 and different values of ω: 0.3 (solid line), 0.6 (dot line), 1 (dash line), 1.3 (dot-dash line), 1.6 (dot-dot-dash line) and 2 (dot-dot-dash-dash line)

4 A comparison of single half order and uniform distributed-order

We consider two special cases, one with the single half order derivative,

x¨+kx+cx˙+G⋅−∞Dt1/2x=Feiωt,(42)

and another with the uniform distributed-order derivative,

x¨+kx+cx˙+G∫01−∞Dtλxdλ=Feiωt.(43)

For the system (42), the equivalent stiffness and damping factors are

k~=k+Gω2,c~=c+G12ω.(44)

We denote the response amplitude and the phase difference as A(ω) and φ(ω).

For the system (43), the equivalent stiffness and damping factors are

k^=k+2Gπω−2ln⁡(ω)4ln2⁡(ω)+π2,c^=c+2G2ωln⁡(ω)+π4ωln2⁡(ω)+π2ω.(45)

We denote the response amplitude and the phase difference as B(ω) and θ(ω).

We take F = G = k = 1, c = 0.1 and 1, respectively, the amplitudes A(ω) and B(ω) are plotted in Figure 18, and the phase difference φ(ω) and θ(ω) are plotted in Figure 19. The two cases display similar variation trend and dependence on the driving frequency. When c = 0.1 the case of uniform distributed-order shows a higher resonance peak than the case of single half order.

Figure 18 The amplitude A (solid line and dash line) and the amplitude B (dot line and dot-dash line) (F = G = 1)
Figure 18

The amplitude A (solid line and dash line) and the amplitude B (dot line and dot-dash line) (F = G = 1)

Figure 19 The phase difference φ (solid line and dash line) and θ (dot line and dot-dash line) (G = 1)
Figure 19

The phase difference φ (solid line and dash line) and θ (dot line and dot-dash line) (G = 1)

5 Conclusions

We considered the steady-state response to harmonic driving for two types of fractional one-degree-of-freedom systems, one with a single fractional-order derivative and another with a distributed-order derivative. The first case was examined in Section 2, where the stiffness contribution factor and damping contribution factor of the fractional derivatives, the response amplitude and phase difference were explored, especially for their relevance to the driving frequency and the order α of the fractional derivative. In Section 3, such problems were investigated for the system with a distributed-order derivative, where the weight function is parameterized by μ or γ. In Section 4, we displayed the results of systems with single half order derivative and uniform distributed-order derivative in the same figures.

The two types of systems display similar response behaviors, but the stiffness contribution factor and damping contribution factor of the distributed-order derivative are almost monotonic varying with the parameter γ on the interval (0, 1) in the weight function p(λ), not exactly like the case of single fractional-order derivative with the order α on the interval [0, 1]. The case of the distributed-order derivative provides us more options for the weight function and involved parameters.

Acknowledgements

This work was supported by the National Natural Science Foundation of China (No.11772203) and the Natural Science Foundation of Shanghai (No.17ZR1430000).

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Received: 2017-9-6
Accepted: 2017-11-9
Published Online: 2017-12-29

© 2017 J.-S. Duan et al.

This work is licensed under the Creative Commons Attribution-NonCommercial-NoDerivatives 4.0 License.

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https://doi.org/10.1515/phys-2017-0095
Keywords for this article
fractional calculus; vibration; distributed-order derivative; excitation; response
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