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2
t
2
where
p
is a vector of applied loadings. The inertia force would be
−
ρ(∂
w/∂
)
=−
ρ
w
¨
,
where
is the deflection, so that the principle of virtual
work for a beam model with no shear deformation becomes
ρ
is the mass per unit length and
w
x
δwρ
x
δw
2
EI
2
x
]
a
=
−
δ
W
=
x
δw
x
∂
∂
w
dx
+
w
¨
dx
−
p
z
dx
−
[
M
δθ
+
V
δw
0
(10.7)
Introduce the shape functions for the static response of a beam [Chapter 4, Eq. (4.47)]
w
=
Nv
i
,
where
v
i
θ
b
]
T
=
[
w
a
θ
a
w
b
and
T
2
3
1
−
3
ξ
+
2
ξ
2
3
(
−
ξ
+
2
ξ
−
ξ
)
N
=
(10.8)
2
3
3
ξ
−
2
ξ
2
3
(ξ
−
ξ
)
giving the principle of virtual work of Eq. (10.7) for
M
elements in the form
v
iT
N
T
p
z
dx
M
N
,xx
EI
N
,xx
dx
v
i
N
T
N
dx
v
i
−
δ
W
=
1
δ
+
x
ρ
−
=
0
(10.9)
x
x
i
=
k
i
v
i
m
i
v
i
p
i
+
−
=
0
x
N
2
N
x
2
,
and the boundary terms have been ignored. Substitute
N
where
N
,xx
=
∂
=
∂
/∂
=
x
ρ
of Eq. (10.8) into
m
i
N
T
N
dx
and carry out the integration. Then, the consistent mass
matrix for the beam element of Fig. 10.1 becomes
−
156
22
54
13
0
ρ
−
2
−
−
2
=
ρ
420
22
4
13
3
m
i
N
T
N
dx
=
(10.10a)
54
−
13
156
22
13
−
3
2
22
4
2
Note that this consistent mass matrix is a full symmetric matrix.
If axial motion of the beam element is considered, the nodal displacement vector is
b
]
T
and the shape function is developed in Chapter 4, Example 4.1.
The consistent mass matrix is
v
=
[
u
a
w
θ
a
u
b
w
θ
a
b
140
0
0
70
0
0
0
156
−
22
0
54
13
0
ρ
2
2
0
−
22
4
0
−
13
−
3
=
ρ
420
m
i
N
T
N
dx
=
(10.10b)
70
0
0
140
0
0
0
54
−
13
0
156
22
2
2
0 3
−
3
0 2
4
FIGURE 10.1
A uniform beam segment with in-plane bending about the
y
axis. Sign Convention 2.
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