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2
l
( ) (
)
+
( ) (
)
ψ
d
e
d
e
H
d
2
2
∫
−
F t
( )
=
χ
x p x t
,
φ
x p x t
,
a
=
χ
2
+ +
φ
2
A
+
κ
A
ψχ
1
y
z
0
11
3
2
+
( )
(
)
ψ
x m x t
,
e dx
(36)
A
x
The linearized interaction forces determined
by Eq.(34) together with Eq.(33) render
d
e
B
e
a
= − +
χκ
ψκ
+
A
ψκ
12
1
2
d
e
=
F
'
≈
m
χ
−
A
ψ
Y
−
κ
u
d
e
B
e
y
f
a
= − +
χκ
ψκ
+
A
ψκ
(39)
21
1
2
x
ξ
If the bridge is modeled as an MDOF system
using a finite series Ritz approximation, and
multiple TLCGD are installed, Eq.(37) still holds
in a hypermatrix notation, Reiterer et al. (2006).
In case of a low order bridge model, the equa-
tions of motion of a TMD and a TLCGD can be
compared to get the optimal tuning values. For
dominating lateral vibrations the vertical and
torsional mode shapes
φ
and
ψ
are set to zero in
Eq.(38), and the mass ratio
µ
*
of the equivalent
TMD results
F
m Y
'
=
φ
z
f
x
=
ξ
κ
B
u
H
e
2
M
≈
m
κ
ψ
Y
+
1
2
+
g u
κ
(37)
Ax
f
3
Neglecting the TLCGD parametric excitation,
(
)
wu H d H
A
, in Eq.(32)
renders, together with the bridge dynamics (rep-
resented by a generalized SDOF system), a linear
coupled matrix equation of motion of the two
DOF isolated system
−
κ
+
κ
−
κ ϑ
2
1
1
2
m
M
2
µχ κκ
µχ
f
*
µ
=
,
µ
=
(40)
(
)
1
+
2
1
−
κκ
Y
Y
Y
u
M
1
x
=
ξ
( )
M
+
C
+
K
=
F t
u
S
S
u
S
0
According to the optimal Den Hartog tuning,
see Eq. (9), the optimal frequency tuning becomes
+
µ
a
µ
a
1
=
M
S
=
11
21
a
1
*
ω
δ
12
x
ξ
A opt
,
opt
δ
=
=
,
opt
Ω
(
)
1
2
1
+
µχ
−
κκ
x
=
ξ
ζ
Ω
2
0
*
ζ
=
ζ
(41)
C
S
=
A opt
,
A opt
,
ζ ω
0
2
A A
The active TLCGD absorber mass is defined
by
m
*
=
m
f
κκχ
2
and thus determines the
Ω
2
µψκ
g e
=
x
=
ξ
K
S
=
(38)
optimal absorber placement at the position of
maximum horizontal modal displacement
χ
. The
possible parametric excitation from vertical bend-
ing remains ineffective for sufficiently large
damping, because the cut-off value
ζ
A
,
2
ψκ
g e
ω
A
x
ξ
with constant coefficients, position
ξ
, see Eqs.
(32) and (33) for the geometry factors,
(
0
for time
)
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