Author :

Posted On :
Abstract: Impulsive force is a force of large magnitude that acts over a short time interval. In practice, vehicles and cranes are subjected to impulsive loads. In this chapter, the response of the single-degree-of-freedom system with or without damping subjected to impulsive loads is considered. The concept of response spectrum, which is a very useful tool in the design, is also illustrated.

**Response
of structures to impulsive loads**

**Abstract: **Impulsive
force is a force of large magnitude that acts over a** **short time
interval. In practice, vehicles and cranes are subjected to impulsive loads. In
this chapter, the response of the single-degree-of-freedom system with or
without damping subjected to impulsive loads is considered. The concept of
response spectrum, which is a very useful tool in the design, is also
illustrated.

**Key words: **impulsive loads, dynamic
magnification factor, shear frame,** **Duhamel integral, ramp, response
spectrum, Laplace transform.

**Introduction **

An impulsive load consists of a
single principal impulse as illustrated in Fig. 6.1. Such a load is generally
of short duration. Vehicles and cranes, etc., are subjected to impulsive loads.
The maximum response is reached due to impulsive loads within a short period of
time before damping forces absorb much energy. Hence for this reason only, an
undamped response to impulsive loads will be considered, and for completeness
an under-damped system subjected to impulsive load will also be discussed.

**Impulsive loading – sine
wave **

Consider a sine wave impulse as
shown in Fig. 6.2 with the duration of sine pulse as *t*_{1}.

1.Phase I

During this phase, the structure is subjected to harmonic
loading starting from rest. The undamped response including transient and
steady state may be obtained as

where *β* is the frequency ratio, *ω** _{n}* is the
natural frequency of the system and

2.Phase II

In this phase, there is no impulsive load but at the start of
the second phase, i.e. *t*′ = *t*–*t*_{1}
= 0, there will be velocity and displacement present at the end of phase I that
is, at the end of Phase I and at the beginning of Phase II

We have seen in 4th previous pages the
response of undamped system due to initial velocity and initial displacement is
given by

To find the maximum response velocity must be equated to zero.
Usually this occurs in Phase I.

Hence maximum displacement can be obtained by substituting *ω* *t* in Eq. 6.6 in Eq. 6.4c.
The result is valid only if *ω* *t*
< 1 or *β* < 1,
i.e. *ω** _{n}* <

3. Case
1 When *t*_{1}/*T _{n}* ≠
½

*Forced vibration phase*

Free vibration phase

4.Case 2 When *t*_{1}/*T _{n}*
= 1/2

*Forced vibration phase*

Free vibration phase

The above equation implies that the displacement in the forced
vibration phase reaches a maximum at the end of the phase.

The displacement response for
sine pulse with duration of pulse *t*_{1} = 1s is shown in Fig.
6.3.

*Maximum response*

The maximum values of response
over each of the two phases, forced vibration and free vibration, are
determined separately. The larger of the two values is the overall maximum
response.

A program in MATLAB to obtain the maximum response for various
values of *t*_{1}/*T _{n}* is given below.

**Program 6.1: MATLAB program
to obtain maximum response for half sine cycle pulse **

%Program to obtain maximum
response for half cycle pulse force %For various values of t1/Tn- Tn assumed as
1 rad/sec

for j=1:97 c(j)=(j-1)*0.0625
d=1/c(j); t1=c(j);

% time increment dt=0.002;

if c(j)==0.50 for i=1:2000 t(i)=dt*(i-1); if
t(i)<t1

y(i)=abs(0.5*(sin(2*pi*t(i))-2*pi*t(i)*cos(2*pi*t(i)))); else

y(i)=abs(0.5*pi*cos(2*pi*(t(i)-0.5))); end

end else

t1=c(j);

for i=1:2000 t(i)=dt*(i-1); if t(i)<t1

y(i)=((sin(pi*t(i)/t1)-d/2*sin(2*pi*t(i)))/(1-.25*d^2)); else
y(i)=(d*cos(pi*c(j))*sin(2*pi*(t(i)-c(j)/2))/((.25*d^2)-1)); end

end end

%DMF calculated for various
values of t1/Tn w(j)=max(y);

end w(1)=0; figure(1)
plot(c,w,‘k’)

xlabel(‘ t1/Tn’) ylabel(‘ DMF’)

title(‘ DMF for undamped system for various values of t1/Tn’)

Figure 6.4 shows the shock spectrum (the relationship between
maximum response (DMF) and *t*_{1}/*T _{n}*. DMF and
response ratio have the same meaning.

The response spectrum concept is
useful in design. A response spectrum is a plot of maximum peak response of the
single-degree-of-freedom (SDOF) system oscillator. Different types of shock
excitation result in different response spectra which will be discussed in
later in this page.

**Response to other arbitrary
dynamic excitation **

1.Rectangular pulse force

Next let us consider the case of a load *F*_{0}
applied instantly to a structure. The force is suddenly removed after a finite
time *t*_{1} as shown in Fig. 6.5. Such ais known as force is
commonly denoted as rectangular pulse force and t1 *duration. *When* t*_{1}*
*tends to infinity then the load is a suddenly applied load.* *The
rectangular pulse force is a representative example of an impulsive or shock
loading of short duration. Consequently, the response is not significantly
affected by the presence of damping in the system. Hence the effect of damping
is neglected in the following discussion. The forcing function of the
rectangular pulse is defined as

The equation of motion for undamped forced vibration can be
written as

*Phase I*

A plot of *R*(*t*) vs *t*/*T*_{n}
is presented in Fig. 6.6 for several values of *t*_{1}/*T*_{n}.
It is obvious from these plots that during the forced vibration phase, the
system oscillates about the static displacement position at its natural period *T*_{n}.
In the transient phase *t* tending to *t*_{1}, the system
oscillates about its original equilibrium position. Examining Fig. 6.5 reveals
that maximum displacement for the forced vibration phase = *R*_{max}
= 2. This can occur when cos(*ω* *t*) = – 1 or *ω* *t* = *π* or 2*π*/*T _{n}*

2.Triangular pulse force

A triangular pulse force as shown
in Fig. 6.7 is usually employed to simulate a blast. The load *F*_{0}
is instantly applied to the structure and decreased linearly over the time
duration *t*_{1}.

*Phase I*

Example 6.1

The shear frame (moment of inertia of the beam is very high)
shown in Fig. 6.9 is constructed of a rigid girder and flexible column. The
frame supports uniformly distributed load having a total weight of 2.5kN. The
frame is

subjected to an impulsive load of
triangular pulse as shown in Fig. 6.9 at girder level. Determine the shear in
the column.

**Duhamel integral **

In previous page, it was shown
that for any periodic function represented by a trigonometric series, the analysis
can be extended by using the principle of superposition to include the solution
for a general periodic forcing function.

6.5.1 Physical
approach

Figure 6.10 shows an arbitrary forcing function in which
exciting force is applied at *t* = 0. The forcing function can be
considered as made up of thin strips like *F*(*τ*) d*τ* summed up.

Consider a small strip alone as shown in Fig. 6.11. According
to Newton’s second law

*F*(*τ*) d*τ** *is called
the linear impulse and* m *∆*x***˙*** *is the
momentum. The impulse* *produces a velocity of ∆*x***˙** without
any displacement. Hence ∆*x* when *t*
> *τ* can be written as

The above integral is known as the Duhamel integral or the
convolution integral. For a viscously under-damped system

2.Formal approach

Steps: The differential equation of motion for an undamped system
with an exerting force *F*(*τ*) is

Multiplying both sides by sin *ω** _{n}*(

Substituting the limits of integration we get,

If initial displacement and velocity are zero then the
response becomes

**Response to arbitrary
dynamic excitation **

To illustrate the application of
the *Duhamel integral* in evaluating the response of an SDOF system to
arbitrary excitation, several classical load functions are considered.

1. Ideal step force

Consider a suddenly applied force of the *F*_{0}
that remains constant at all times as shown in Fig. 6.12. For an undamped
system

A plot of DMF(*t*) versus *t*/*T*_{n}
is presented in Fig. 6.13 for several levels of damping. DMF(*t*) = 1 on
the response ratio plot corresponds to static displacement position and DMF(*t*)
>1 represents displacement beyond the static displacement position or *overshoot*.
For an undamped system subjected to step force, the resulting response is
oscillating motion about the static displacement position with maximum values
of DMF_{max} = 2. In a damped system, the response ratio gradually
approaches static values of 1 after a number of cycles of damped oscillation.
The maximum overshoot in a damped system as well as the rate of decay of the
oscillation about static equilibrium position depends on the damping factor as
illustrated in Fig. 6.13.

2. Program
6.2: MATLAB program to find the response for step force

%program for finding max dynamic response factor for given
loading

%define damping ratios for which
response is required rho=[0 0.02 0.05 0.1 0.2]

for jj=1:5 zeta=rho(jj);

%assume natural period 1 wn=2*pi;

%assume
mass =1

m=1;

% find natural frequency of
damped system wd=wn*sqrt(1-zeta^2);

ts=0.002; %sampling period N=1000
% sampling points

%force is defined for ideal step
force for n=1:N

t(n)=ts*(n-1); f(n)=1;

end figure(1) plot(t,f)

xlabel(‘ time in secs’) ylabel(‘ force ‘)

title(‘ force definition’)
n=[1:N]

g=ts*exp(-(n-1)*zeta*wn*ts).*sin((n-1)*wd*ts)/(m*wd);
c0=conv(f,g);

for i=1:N tt(i)=(i-1)*ts;

c1(i)=abs(c0(i)*wn^2); end

figure(2)

plot(tt,c1,‘k’) hold on

end gtext(‘rho=0’)
gtext(‘rho=2%’) gtext(‘rho=5%’) gtext(‘rho=10%’) gtext(‘rho=20%’) xlabel(‘
t/Tn’); ylabel(‘ R(t)’)

title(‘ Response of SDOF to ideal step force’)

3 Rectangular pulse force

Let us consider the case of load *F*_{0} applied
instantly to a structure for a finite time duration of *t*_{1}
known as rectangular pulse.

*Undamped system*

For an under-damped system similar to Eq. 6.47, the response
can be derived.

Several plots of DMF(*t*) as
a function of *t*/*T _{n}* for several values of

4 Step
force with ramp

Consider a force which is applied
over a finite time *t*_{1}. Such a forcing function is called a
ramp function and is shown in Fig. 6.15. The dynamic response is significantly
affected by *t*_{1}/*T _{n}*.

The Duhamel integral for the loading in the time interval 0 ≤ *t* ≤
*t*_{1}

Figure 6.16 shows the plot of
response ratio values versus *t*/*T _{n}* for several ratios
of

6.6.5 Triangular pulse force

A load function often employed to simulate blast is the
triangular pulse shown in Fig. 6.17. The load *F*_{0} is instantly
applied to the structure and decreases linearly over the time duration *t*_{1}.

Once the Duhamel integral has been evaluated for a specific
forcing function, the result may be used to evaluate response of any SDOF
system to that particular type of loading. Figure 6.18 depicts the plot of
response ratio versus *t*/*T _{n}* for triangular loading for
several values of

Example 6.2

The shear frame shown in Fig. 6.21 is constructed of rigid
girder and flexible columns. The frame supports uniformly distributed load of
total weight of 120kN and the frame is subjected to step force with a ramp as
shown in Fig. 6.21 at the girder level. Determine the horizontal displacement
at *t* = 0.75s. *E *= 200 GPa and damping can be assumed as zero.
Moment of inertia of end columns and centre column are 3.4465e^{–5}mm^{4}
and 7.07e^{–5}mm^{4} respectively.

The Duhamel method is a closed form procedure for calculating
a system response to arbitrary dynamic excitation. But evaluation of the
integral is cumbersome as evidenced in previous sections. But with the MATLAB
and MATHEMATICA packages these convolution integrals may be evaluated quite
easily. It is not possible to apply a closed form procedure for earthquake
ground motion since ground motion recordings are in digitized form. In such
cases a numerical procedure is resorted to.

**Response spectrum**

A shock represents a sudden
application of force or other form of disruption which results in a transient
response of a system. The maximum value of the response is a good measure of
the severity of the shock and is of course dependent upon dynamic
characteristics of the system. In order to categorize all types of shock
excitation an SDOF system oscillator is chosen as the standard.

The *response spectrum*
concept is useful in design. A *response spectrum* is a plot of maximum
peak response of the SDOF system oscillator. Different types of shock
excitation result in different response spectra. It is possible to have similar
response spectra for two different shock excitation. In spite of this
limitation, the response spectrum is a useful concept that is extensively used.

Consider the excited force function as *F*(*τ*) = *F*_{0}*f*
(*τ*) and the response for SDOF of an
undamped system as given by

The inner product given in the
integral is *f*(*τ*) sin *ω*_{n}(*t*
– *τ*) and the integral is known as
the convolution integral. MATLAB can calculate a convolution integral very
easily.

**Program 6.3: MATLAB
program to find the response spectrum for any load pulse **

%program for finding max dynamic response factor for given
loading

%define damping ratios for which
response is required rho=[0 0.02 0.05 0.1 0.2]

for jj=1:5 zeta=rho(jj);

%define the fac=td/Tn= duration
of loading / natural period for ii=1:193

fac(ii)=0.03125*(ii-1);

td=0.1; %period of forcing
function

%natual
frequency of the system

wn=fac(ii)*2*pi/td;

%assume mass =1 m=1;

%find natural frequency of damped
system wd=wn*sqrt(1-zeta^2);

ts=0.002; %sampling period N=1000
% sampling points load=1

%force is defined for rectangular pulse

for n=1:N t(n)=ts*(n-1); if n>td/ts+1

f(n)=0;

else

f(n)=1;

end end %load=2

%force is defined for triangular
load %for n=1:N

%t(n)=ts*(n-1);

%if
n>td/ts+1

%f(n)=0;

%else

%f(n)=1-t(n)/td;

%end

%end

%load=3

%force is
defined for sinusoidal loading

%defining
force

%for n=1:N

%t(n)=ts*(n-1);

%if
n>td/ts+1

%f(n)=0;

%else

%f(n)=sin(pi*t(n)/td);

%end

%end

%load=4;

%force is defined for double triangular load

%for n=1:N

%t(n)=ts*(n-1);

%if
n<=(td/2)/ts+1

%f(n)=2.0*(n-1)*ts/td;

%else

%f(n)=2.0*(1-(n-1)*ts/td);

%end

%if
n>td/ts+1;

%f(n)=0;
end

%end

%load=5

force is defined as ramp loading

%for n=1:N

%t(n)=ts*(n-1);

%if
n>td/ts+1

%f(n)=1;

%else

%f(n)=t(n)/td;

%end

%end

figure(1)

plot(t,f)

xlabel(‘ time in secs’) ylabel(‘
force ’)

title(‘ force definition’)
n=[1:N]

g=ts*exp(-(n-1)*zeta*wn*ts).*sin((n-1)*wd*ts)/(m*wd);
c0=conv(f,g);

for i=1:N tt(i)=(i-1)*ts; c1(i)=c0(i)*wn^2;

end dmf(ii)=max(abs(c1)); end

if load<4 dmf(1)=0

else end

figure(2)

plot(fac,dmf,‘k’) hold on

end gtext(‘rho=0’)
gtext(‘rho=2%’) gtext(‘rho=5%’) gtext(‘rho=10%’) gtext(‘rho=20%’) xlabel(‘
td/Tn’); ylabel(‘ DMF’)

title(‘ Response spectrum for the given loading’)

The responses spectrum for (a) rectangular pulse, (b)
triangular pulse, (c) sine pulse, (d) double triangle pulse and (e) step ramp
loadings are shown in Fig. 6.22.

Example 6.3

Determine the maximum horizontal displacement of structural
frame when subjected to ramp loading as given in Example 6.2.

DMF_{max}
= 1.5

*x*_{max}* *= 1.5* *×* *0.096 = 0.144m

The construction of response
spectrum can be greatly facilitated through numerical evaluation techniques.
The construction of a response spectrum by numerical integration is addressed
in later chapters. Once constructed, the response spectrum offers the design
engineer an opportunity to evaluate the response of a wide frequency range of
structures to a specific input.

**Laplace transform**

The *Laplace transform* method of solving the
differential equation provides a complete solution, yielding both transient and
forced vibrations. Here in we give a brief introduction of the theory and
illustrate with some examples.

If *f* (*t*) is a function of *t* for *t*
> 0 its Laplace transform *f* (*s*) is defined as

where ‘*s*’ is a complex variable. For the real part of *s*
> 0 the integral exists provided *f* (*t*) is absolutely
integrable function in the time interval 0 to infinity.

For Laplace transform of simpler
expressions, the reader may consult any mathematics handbook or one can use the
MATHEMATICA package to obtain both Laplace transform and inverse Laplace
transform.

Example 6.4

Write a MATHEMATICA program to obtain the motion of the mass
subjected to initial conditions. There is no external forcing function. The
SDOF system is shown in Fig. 6.23; *m* = 4kg, *K* = 10N/m; *c* =
6Ns/m and at *t* = 0 *x *(0)* *=* *0.1m and*
x***˙*** *(0)* *=* *0.16m/s.

Taking inverse transform of the
above equation, we get *x*(*t*) which is given in the MATHEMATICA
program.

Example 6.5

For the same problem, when 20N force (step input) is applied
and the system is at rest initially.

Taking inverse transform we get *x*(*t*) which is
given in MATHEMATICA program.

Example 6.6

When *F*(*t*) = 20e^{–2t}.

Solution

**Program 6.4:
MATHEMATICA program for Laplace transform method **

f=InverseLaplaceTransform[(.1 *s+0.31)/

(s^2+1.5*s+2.5),s,t]

E^((-0.75 -
1.3919410907075054*I)*t)* (0.05000000000000001 + 0.08441449195258423*I + (0.05
-0.08441449195258421*I)* E^(2.7838821814150108*I*t)) f

E^((-0.75 - 1.3919410907075054*I)*t) *(0.05000000000000001 +
0.08441449195258423*I + (0.05 -
0.08441449195258421*I)*E^(2.7838821814150108*I*t)) Plot[f,{t,0,5},AxesLabel→{“time in sec”,
“displacement”},PlotStyle→{Thickness[0.008]}]

g=InverseLaplaceTransform[(20)/(s*(4*s^2+6*s+10)),s,t]

2/31*(31 -
(31*Cos[(Sqrt[31]*t)/4])/E^((3*t)/4) -
(3*Sqrt[31]*Sin[(Sqrt[31]*t)/4])/E^((3*t)/4))

Plot[g,{t,0,5},AxesLabelÆ{“time in sec”,
“displacement”},PlotStyleÆ{Thickness[0.008]}]

h=InverseLaplaceTransform[(20)/

((s+3)*(4*s^2+6*s+10)),s,t]

(5/217*(31 - 31*E^((9*t)/4)*Cos[(Sqrt[31]*t)/4] +

9*Sqrt[31]*E^((9*t)/4)*Sin[(Sqrt[31]*t)/4]))/E^(3*t)

Plot[h,{t,0,5},AxesLabel→{“time in sec”, “displacement”},PlotStyle→{Thickness[0.008]}]

**Summary **

In this chapter, the response spectrum is constructed only for
certain loads such as rectangular, triangular, double triangle, sine and ramp
pulses. For any other general pulses, the numerical technique as addressed in
Chapter 7 should be used. Once constructed, the response spectrum offers the
design engineer the opportunity to evaluate the maximum response of a wide
frequency range of structures to a specific input. Application of the response
spectrum will follow in later chapters for earthquake loading.

Tags : Civil - Structural dynamics of earthquake engineering

Last 30 days 283 views
Related words : ### What is Response of structures to impulsive loads Define Response of structures to impulsive loads Definition of Response of structures to impulsive loads where how
meaning of Response of structures to impulsive loads
lecturing notes for Response of structures to impulsive loads lecture notes question and answer for Response of structures to impulsive loads answer
Response of structures to impulsive loads study material Response of structures to impulsive loads assignment Response of structures to impulsive loads reference description of Response of structures to impulsive loads
explanation of Response of structures to impulsive loads brief detail of Response of structures to impulsive loads easy explanation solution Response of structures to impulsive loads wiki
Response of structures to impulsive loads wikipedia how why is who were when is when did where did Response of structures to impulsive loads list of Response of structures to impulsive loads school assignment college assignment
Response of structures to impulsive loads college notes school notes kids with diagram or figure or image difference between Response of structures to impulsive loads www.readorrefer.in - Read Or Refer

Recent New Topics :