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Introduction
The last decades have seen a growing interest for design and construction of tall buildings. In order to accurately estimate the dynamic response to environmental loads of such complex constructions, structural models are usually characterized by a large number of degrees of freedom; as a consequence, structural optimization algorithms, used to reduce the cost and the energy required to construct such buildings while maintaining appropriate safety levels, might be time consuming and even not feasible given the large dimension of the problem. As far as the global response is concerned, it is of interest to develop reduced models that are capable of giving approximate optimal solutions by significantly reducing the computation time. Therefore, a reduced model based on a Timoshenko beam will be presented in this paper which can be used to estimate the response of tall buildings subjected to environmental loads, such those induced by earthquakes.
Flexural Beam Models
In the present section, the main beam models are recalled, focusing mainly on the Timoshenko model, which is able to describe the flexural behavior of the beam taking into account, besides the flexural stiffness and inertia due to deflections, also the shear deformability and the rotational inertia. Nevertheless, before introducing the Timoshenko beam model, the two models that can considered to be the ones on which it is based, the Euler-Bernoulli and the simple shear models, will be briefly recalled.
The Cartesian reference system consists of the principal axes of the section, x and y, and the axis of the beam (the line where centroids of the sections lie), z. The beam is loaded with a distributed load q(z), acting in the direction y, and a distributed moment m(z) whose axis is in x direction (see Fig. 1). The analysis is limited to the plane y-z, and the only displacements of interest are those in y direction, the deflection v(z). In the following, since the dependence on z is obvious, it will be dropped.
In what follows, the balance equations, which relate the loads q and m to the bending moment M and shear force V, will be used:
The Euler-Bernoulli Beam
It is assumed that the deflection of the beam is due to the moment only, and therefore this behavior is known as “pure bending.” The constitutive equation which relate the bending moment M to the slope of deflection curve is
where EI is the bending stiffness, the product of the Elastic (Young’s) modulus, E, and the second moment of area (or moment of inertia) for rotation around x, I. The previous relation takes into account the fact that the sections of the beam remain plane in the deformed configuration and normal to the axis.
Using Eqs. 3 and 1, the following equation is obtained:
Assuming m = 0, differentiating again, and using Eq. 2, the Euler-Bernoulli equation for the beam is obtained:
Moreover, the following are also valid:
The Euler-Bernoulli model can be extended to the dynamic case using the D’Alembert principle and adding to the external load q the load equivalent to inertia forces associated with deflections, q i :
where ρ is the density of mass and A is the area of the section. Assuming ρ and A constant along the axis, the equation that rules the problem is
The free motion equation is
with solution that can be written through separation of variables as
where
and
The parameters D1, D2, D3, and D4 can be obtained using the boundary conditions and determining ω to avoid the trivial solution. For example, in the case of cantilever beam clamped at z = 0 and free at z = L, the following boundary conditions hold
and the values of ω are given by the following
which has solutions
with
The Simple Shear Beam
The simple shear beam model is based on the assumption that the beam undergoes only shear deformation. In this case, the constitutive equation which relates V to the slope of deflection curve is
where GK is the shear stiffness, the product of the tangential modulus, G, and shear area K. Moreover, the shear area is related to A by means of a shear factor κ, K = κA, which depends on the shape of the section and is determined by means of energetic equivalence.
Using the preceding and Eq. 2, the following equation is obtained:
In dynamics, by means of D’Alembert principle, the following equation of motion is obtained:
and in free motion
Adopting the separation of variables Eq. 4, the following expression for deflection is obtained:
and
The parameters D1, D2 can be obtained using the boundary conditions and determining ω to avoid the trivial solution. For example, in the case of cantilever beam clamped at z = 0 and free at z = L, the boundary conditions are
and therefore
The Timoshenko Beam Model
In the Timoshenko beam model (Timoshenko 1921, 1922), it is assumed that the slope of the deflection curve is the sum of those due to bending moment and those given by shear deformation, each one assumed to act alone
The first part of both Eqs. 3 and 5 is unchanged, while the second parts are modified according to Eq. 6, and therefore
Assuming EI and GK constant along the axis, the following equations are obtained:
In dynamics the D’Alembert principle is used again. Moreover, in the Timoshenko beam model, the inertial forces associated to rotations θ are also taken into account
and the equations of motion are therefore
In free motion the following equations hold:
and considering that
the following equation can be obtained:
The solution is given by
where
where ωc is a cut-off frequency given by
As usual, ω is found by imposing the suitable boundary conditions.
It can be interesting to plot the values of ω in terms of variation of slenderness λ = L/r where \( \mathrm{r}=\sqrt{\mathrm{I}/\mathrm{A}} \), as in Fig. 2 (the values have been obtained assuming κ = 0.85 and E/G = 2.6). It can be noted that as λ increases, the values ω of the Euler-Bernoulli model are achieved
while as λ decreases the values of the simple shear model are recovered
It is worth noting that the convergence to the Euler-Bernoulli or simple shear beam tends to slow down as mode number increases. For intermediate values of slenderness, the natural frequencies ω depend on both the bending stiffness EI and the shear stiffness GK.
Example
The case of a cantilever beam with the following characteristics:
is considered in what follows.
The first 12 modal shapes are shown in Fig. 3, and the parameters of Eq. 8 are shown in Tables 1 and 2. In the tables also the phase velocity, defined as the ratio between the angular frequency, ω, and the wavenumber, k1, is reported: as well known, the phase velocity is unbounded for the Euler-Bernoulli beam, while in the case of Timoshenko beam the two different families of waves present when ω > ωc, with wavenumbers k1 and k2, tend to the following values (Hagedorn and DasGupta 2007):
where j is the mode number.
Deterministic Excitation-Response Relations
The unit impulse applied at the section z = zo at the instant t = to is considered:
Assuming that prior of the unit impulse application the beam is at rest with zero displacement, the response can be expressed by (Robson et al. 1971; Crandal 1979; Lin 1967; Elishakoff 1988)
where h(z, t − to; zo) is the impulse response function or Green’s function. A f(z, t) arbitrary space-time action can be regarded as a superposition of unit impulses at the time τ in generic section \( 0\le \upxi \le \mathrm{L} \)
If the impulse response function is known, then the response at the time t in the generic section \( 0\le \upxi \le \mathrm{L} \) can be obtained by the following convolution integral or superposition integral:
The unit complex sinusoidal action with the fixed frequency ω applied at the section z = zo is
Given the complex frequency response function H (z, ω; zo), the response is given by
Let F (z, ω) be the Fourier transform of the action f (z, t) which is assumed to be an integrable function, so that
and
The complex frequency response function is the Fourier transform of the impulse response function
Introduced the Fourier transform of the response
and
the excitation-response relation for Fourier transform is
so that
and
Statistical Characteristics of the Excitation
Let f(z, t) be a random space-time processes. In order to describe this processes, it is introduced the ensemble average or expected value
the space-time correlation
and the space-time covariance
It is assumed that the previous characteristics are sufficient to describe the excitation.
Considering the case of weak stationary process, the mean is independent on t, and the space-time correlation depends on τ = t2 − t1 so that
If z1 = z2 = z, the autocovariance function is obtained
that for τ = 0 reduces to the variance
where \( {\left.{\mathrm{R}}_{\mathrm{f}}\left(\mathrm{z},\uptau \right)\right|}_{\tau =0}=\mathrm{E}\left[{\mathrm{f}}^2\left(\mathrm{z}\right)\right] \) is the mean-square value.
Let Sf(z1, z2, ω) be the space-time cross-spectral density function; this function is connected to the cross-correlation function by the Wiener-Khintchine relations:
If z1 = z2 = z and τ = 0, the mean-square value can be expressed by the cross-spectral density function
and for excitation with zero mean
It is worth noting that earthquake-induced base accelerations are samples of non-stationary random process. Anyway, there is an interval, called strong motion phase, where the base accelerations can be considered samples of stationary random process. The length of strong motion phase is TS. It is commonly assumed that, if TS is much greater than the period of the elementary oscillator, both the base accelerations and the response can be considered samples of stationary random process with zero mean.
Statistical Characteristics of the Response
The statistical characteristics of the response can be obtained from corresponding characteristics of the excitation by taking the averages of the previously introduced relations. The expected value of the response can be obtained by equation
and interchanging the integral operators and mean operator, the following equation is obtained:
where E[f(z, t)] is the mean of the excitation. If the excitation is a stationary processes, its mean value is constant, E[f(z, t)] = mf(z), and also the mean value of the response is constant, E[v(z, t)] = mv(z), where
If in addition mf(z) = 0, as for the seismic excitation, then mv(z) = 0.
The space-time correlation function of the response is obtained by average of the product of v(z1, t) and v(z2, t + τ), which are given by the impulse response function
and interchanging the integral operators and mean operator
If the excitation is stationary, then its space-time correlation is independent of t and so is the response space-time correlation
Applying the Wiener-Khintchine relations, the space-time cross-spectral density of the response can be obtained by the following:
Introducing in the previous integrals the unity products \( {\mathrm{e}}^{-{\mathrm{i}\upomega \uptheta}_1}{\mathrm{e}}^{{\mathrm{i}\upomega \uptheta}_1} \) and \( {\mathrm{e}}^{-{\mathrm{i}\upomega \uptheta}_2}{\mathrm{e}}^{{\mathrm{i}\upomega \uptheta}_2} \), by the frequency response function
and introducing the space-time cross-spectral density of the excitation,
the following expression to determine Sv(z1, z2, ω) is obtained:
Natural Modes and Frequencies
The dynamic proprieties of the systems can be described in terms of natural modes, ṽ, and corresponding natural frequencies, ω. In what follows, the natural modes will be expressed in terms of both deflection, \( {v}_{\mathrm{j}}\left(\mathrm{z}\right)=\tilde{v}\left(\mathrm{z}\right) \), and rotation, θj(z), where j is the mode number. Once the natural modes have been found, the equations of motion Eq. 7 can be reduced to
where mj, kj, and fj are, respectively, the generalized mass, stiffness, and force corresponding to mode j, given by
and gj is the jth principal coordinate. In the preceding, the following orthogonality properties of the modes have been used (Bishop and Price 1977):
Once the gj are known, the values of displacements are given by
If a modal damping vj is assumed, the equations of motion are
that can also be written as
Let hj(t) be the single degree of freedom unit impulse response function. With initial conditions gi = 0 and dgj/dt = 0, and assuming distributed load q = δ (z – z0) δ(t) and distributed moments m = 0, the solution is
where
so that
and using the Fourier transform relation, the complex frequency response is
where the single degree of freedom unit complex frequency response function is given by
Inserting in the previous equations, the following expressions for space-time correlation and space-time cross-spectral density are obtained:
Application to the Beam Under Seismic Load
The concepts illustrated in the previous sections are applied to the case of the cantilever beam seen previously in the example, subjected to a seismic load. The seismic load is modeled by means of an elastic response spectrum according to the European standard for seismic actions (Eurocode 8 2004). It has been assumed a type 1 elastic response spectrum with a ground type C, with parameters:
A 5 % damping, ν = 0.05, was adopted. The response spectrum in terms of pseudo-accelerations (RSA) is shown in Fig. 4a.
In order to apply what presented in previous sections, the power spectral density function, \( {\mathrm{G}}_{{\ddot{\mathrm{u}}}_{\mathrm{g}}} \), corresponding to the assumed response spectrum is needed. The method proposed in (Cacciola et al. 2004) is used. The time observing window (coincident with the strong motion phase) TS has been set to 10s, while the cut-off frequency is ωu = 150 rad/s and the frequency step is Δω = 2π/TS = 0.63 rad/s. An iterative scheme has been used as suggested in (Cacciola 2010), and the power spectral density function obtained is shown in Fig. 4b.
The generation of a time history of base acceleration is achieved by means of superposition of Na harmonics with random phases Φi as follows:
where φ(t) is the modulating function (which changes the total energy but not its distribution among the frequencies; see Fig. 4b) (Cacciola 2010):
with t2 = t1 + TS. In the present case, it was assumed t1 = 10s and β = 0.3 s−1. An example of the generated üg(t) is shown in Fig. 5.
The problem of the beam subjected to the base acceleration given by üg(t) can be solved by means of modal analysis, as formulated in Eq. 9.
In the case of seismic action represented by base accelerations üg(t), the external loads are
and therefore:
Once the time histories of gj have been determinated, the solution is given by
where Np is the number of modes considered in the solution. For example, the displacement at the free end, ν(L), for the base acceleration shown in Fig. 5 and assuming Np = 10 (the modal contribution tends to be negligible quite rapidly) is shown in Fig. 6.
The power spectral density function of the displacement at free end, Sν(L, L, ω) is shown in Fig. 7, compared to that evaluated by mean of Eq. 11. As can be appreciated, the same results are obtained using both procedures.
References
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Cacciola P, Colajanni P, Muscolino G (2004) Combination of modal responses consistent with seismic input representation. J Struct Eng 130:47–55
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Gusella, V., Cluni, F. (2015). Vibrations of Beams for Seismic Response Estimation. In: Beer, M., Kougioumtzoglou, I.A., Patelli, E., Au, SK. (eds) Encyclopedia of Earthquake Engineering. Springer, Berlin, Heidelberg. https://doi.org/10.1007/978-3-642-35344-4_331
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