Deflection 2

16.21 Techniques of Structural Analysis and

Design

Spring 2005

Unit #1

Ra´l Radovitzky
u
February 2, 2005

In this course we are going to focus on energy and variational methods
for structural analysis. To understand the overall approach we start by con
trasting it with the alternative vector mechanics approach:

Example of Vector mechanics formulation:
Consider a simply supported beam subjected to a uniformlydistributed load
q0 , (see Fig.1). To analyze the equilibrium of the beam we consider the free
body diagram of an element of length Δx as shown in the ﬁgure and apply
Newton’s second law:
�
Fy = 0 : V − q0 Δx − (V + ΔV ) = 0 (1)

� Δx
MB = 0 : −V Δx − M + (M + ΔM ) + (q0 Δx) =0 (2)
2

Dividing by Δx and taking the limit Δx → 0:

dV
= −q0 (3)
dx

dM
=V (4)
dx

1

z

q0

x
A B
L
q0

M M+dM
V V+dV
x A dx B

Figure 1: Equilibrium of a simply supported beam

Eliminating V , we obtain:

d2 M
+ q0 = 0 (5)
dx2
Recall from Uniﬁed Engineering or 16.20 (we’ll cover this later in the
course also) that the bending moment is related to the deﬂection of the
beam w(x) by the equation:
d2 w
M = EI (6)
dx2
where E is the Young’s modulus and I is the moment of inertia of the beam.
Combining 5 and 6, we obtain:
d2 d2 w
� �
EI 2 + q0 = 0, 0 < x < L (7)
dx2 dx
The boundary conditions of the beam are:
w(0) = w(L) = 0, M (0) = M (L) = 0 (8)
The solution of equations 7 and 8 is given by:
q0
x (L − x) L2 + Lx − x2
� �
w(x) = − (9)
24EI

2

Corresponding variational formulation
The same problem can be formulated in variational form by introducing the
potential energy of the beam system:
� L� �2 �
EI d2 w
�
Π(w) = + q0 w dx (10)
0 2 dx2

and requiring that the solution w(x) be the function minimizing it that also
satisfies the displacement boundary conditions:
w(0) = w(L) = 0 (11)
A particularly attractive use of the variational formulation lies in the
determination of approximate solutions. Let’s seek an approximate solution
to the previous beam example of the form:

w1 (x) = c1 x(L − x) (12)
which has a continuous second derivative and satisfies the boundary condi
tions 11. Substituting w1 (x) in 10 we obtain:
� L� �
EI
Π(c1 ) = (−2c1 )2 + q0 c1 (Lx − x2 ) dx
0 2
(13)
L3
= 2EILc2 + q0 c1
1
6
Note that our functional Π now depends on c1 only. w1 (x) is an ap
proximate solution to our problem if c1 minimizes Π = Π(c1 ). A necessary
condition for this is:
dΠ L3
= 4EILc1 + q0 =0
dc1 6
2
q0 L
or c1 = − 24EI , and the approximate solution becomes:
q0 L2
w1 (x) = − x(L − x)
24EI
In order to assess the accuracy of our approximate solution, let’s compute
the approximate deflection of the beam at the midpoint δ1 = w1 ( L ):
2

q0 L 2 � L � 2 q0 L4
δ=− =−
24EI 2 96EI
3

The exact value δ = w( L ) is obtained from eqn.9 as:
2

5 q0 L 4
� �
q0 L L � 2 L � L �2 �
δ=− L− L +L − =−
24EI 2 2 2 2 384 EI

We observe that:
1
δ1 4
= 96 = = 0.8
δ 5 5
384
i.e. the approximate solution underpredicts the maximum deflection by 20%.
However, if we consider the following approximation with 3 degrees of
freedom (note it also satisfies the essential boundary conditions, eqn.11):

w3 (x) = c1 x(L − x) + c2 x2 (L − x) + c3 x3 (L − x) (14)
and require that Π(c1 , c2 , c3 ) be a minimum:

∂Π ∂Π ∂Π
= 0, = 0, = 0,
∂c1 ∂c2 ∂c3
i.e.:
L3 q0
4 c1 EI L + 2 c2 EI L2 + 2 c3 EI L3 + =0
6
L4 q0
2 c1 EI L2 + 4 c2 EI L3 + 4 c3 EI L4 + =0
12
24 c3 EI L5 L5 q0
2 c1 EI L3 + 4 c2 EI L4 + + =0
5 20
whose solution is:

− (L2 q0) − (L q0) q0
c1 → , c2 → , c3 →
24 EI 24 EI 24 EI

If you replace this values in eqn. 14 and evaluate the deflection at the
midpoint of the beam you obtain the exact solution !!!

4

Deflection 2

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