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Analysis of Active Constrained Layer Dampingin composite sandwiched plates
Charles K. KimNASA-Goddard Space Flight Center, Code 542
Greenbelt, MD 20771
Chul H. ParkWilcoxon Labs
Wilcoxon Research Inc.Gaithersburg, MD 20878
Amr BazMechanical Engineering Department
University of MarylandCollege Park, MD 20742
FEMCI WorkshopMay 18, 2000
Abstract
This paper describes how a new class of composite sandwich platesis implemented to control vibration of the bending and torsional modes usingbuilt-in Active Constrained Layer Damping (ACLD). The paper also gives aninsight into the fundamentals governing the dynamics and active/passivecontrol of smart composite sandwiched plate structures to use as the potentialbasic building block of structures where effective vibration damping isessential to their successful operation.
To improve predictions of the dynamics and controlled vibration of thecomposite sandwiched plate/ACLD, a powerful assumed displacement field forthe finite element modeling is introduced. This assumed displacement fielddiffers from the classical laminated theory and offers a definite advantage infinite element modeling as it gives a displacement distribution along the wholethickness of the laminates and requires fewer degrees of freedoms torepresent the kinematical relationships for viscoelastic layers withpiezoelectric layers in ACLD. Also, the predictions of the finite element modelusing this assumed displacement field have been validated by comparing ofmodal frequencies and damping loss factors with experiment and are found tobe in close agreement.
Outline of Presentation
z Introduction
z Active Constrained Layer Damping (ACLD)
z Theoretical Development (Finite Element Modeling)
z Experimental Performance
z Comparison between Theory & Experiments
z Summary
Passive and active layer damping(a)-Passive: unconstrained(b)-Passive: constrained (c)-Active: constrained
Viscoelastic material
Variation of storage modulus, and loss factor, with temperature[Nashif et al. 1985]
Variation of storage modulus, and loss factor, with frequency [Nashif et al. 1985]
s
44
33
2210)( fafafafaafE ++++= 4
43
32
210)( fbfbfbfbbf ++++=η
Interaction processes between theelectrical, mechanical, and thermal system
[Ikeda Takuro; Fundamental of Piezoelectricity,1990]
Active constrained layer damping
• Combines active & passive damping control• Enhances energy dissipation characteristics
Operating principle of sandwichedplate/ACLD system.
Theoretical Development(Formulation)
z Displacement Field
z Displacement-Strain
z Stress-Strain
z Sensor & Actuator Equation
z Equation of Motion
Schematic drawing of six-layer cantileverplate/ACLD system
Composite sandwiched plate coordinate
Displacement field
),,()(),,(),,,(0
1
0
1 tyxztyxutzyxuNkj
jjN jN∑
−=
=± ±
+= φψ
),,()(),,(),,,(0
2
0
2 tyxztyxvtzyxuNkj
jjN jN∑
−=
=± ±
+= φψ
),,(),,(3 tyxwtyxu =
where the functions of the thicknessψ i z( ) and the in-planecoordinate φ 1i
( , , )x y t and φ 2i( , , )x y t are defined as follows:
ψ i z( ) = − −z z i , z z zi i− − −≥ ≥ 1
= z , z z z0 1≤ ≤ or z z z− ≤ ≤1 0
= −z zi , z z zi i≤ ≤ +1
xtyxw
atyxii ∂∂
φ),,(
),,( 11 −=
ytyxw
atyxii ∂∂
φ),,(
),,( 22 −=
where the al i's denotes adjustment coefficients which will be
determined later. Physically, awxi1
∂∂
and awyi2
∂∂
define the slopes of
the i th layer due to bending in the x and y directions, respectively
Displacement-Strain Relations
ε ε∂∂
∂∂
p
x x
p
x x
p
i
j
p
j
ii j j i
ux
ux
= = +12
( ) ( , , , )i j = 1 2 3 .
εεγ
ε
ε
γ
ψ1
2
6
1
0
2
0
6
0 1
1
2
6
31 3
32 3
0
=
+
+
=
=
∑ ii
i k
i
d x yd x y
ΚΚΚ
Ε ΛΕ Λ
( , )( , )
γγ
∂∂∂∂
5
4
1
2
31 3
31 3
1
1
=
−
−
+
∫
∫k
l
vem
w
vem
awx
awy
d x y dx
hd x y dy
h
k
k
( )
( )
( , )
( , )
Ε Λ
Ε Λ
Stress-Strain Relation
σσσ
εεγ
1
2
6
11 12 16
12 22 26
16 26 66
1
2
6
=
k k k
Q Q QQ Q QQ Q Q
σσ
γγ
5
4
55 45
45 44
5
4
=
k k k
Q QQ Q
.
Sensor & Actuator Equation
∫
=A
T
dAdd
tq
6
2
1032
031
0)(
σσσ
VC
q tC
dd dAs
T
A
= =
∫1 1
0
310
320
1
2
6
( )σσσ
V K i K VC p d S= − +( )ω
Equation of Motion & Eigenvalue Analysis
[ ] [ ]{ } { } { }GGGGG
G FFKt
M ~2
2
+=∆+
∆
∂∂
[ ] [ ]{ }{ } 02* =Φ− GG MK ω
where ω *2 are complex eigenvalues.
The n th eigenvalue is written as follows:
)1(22*nnn iηωω +=
Experimental setup for compositesandwiched plate/ACLD
Response to random excitationsfor bending control
0 5 10 15 20 25 30 35
Frequency (Hz)
-0.05
0
0.05
0.1
0.15
0.2
0.25
0.3
0.35
0.4
Am
plit
ud
e (m
m)
PCLDACLD, Gain AACLD, Gain BACLD, Gain C
Response to random excitationsfor torsion control
0 5 10 15 20 25 30 35
Frequency (Hz)
-0.05
0
0.05
0.1
0.15
0.2
0.25
0.3A
mp
litu
de
(mm
) PCLDACLD, Gain DACLD, Gain EACLD, Gain F
Comparison between theory &experiments for first bending mode
with different control gains
4.00 4.20 4.40 4.60 4.80 5.00
Theoretical Natural Frequency (Hz)
4.00
4.20
4.40
4.60
4.80
5.00
Exp
erim
enta
l Nat
ural
Fre
quen
cy (H
z) PCLDACLD, Gain AACLD, Gain BACLD, Gain C
(a)
0.00 0.02 0.04 0.06 0.08 0.10 0.12
Theoretical Loss Factor
0.00
0.02
0.04
0.06
0.08
0.10
0.12
Exp
erim
enta
l Los
s Fa
ctor
PCLDACLD, Gain AACLD, Gain BACLD, Gain C
(b)
Comparison between theory &experiments for second bending mode
with different control gains
30.00 31.00 32.00 33.00 34.00 35.00
Theoretical Natural Frequency (Hz)
30.00
31.00
32.00
33.00
34.00
35.00
Exp
erim
enta
l Nat
ural
Fre
quen
cy (H
z) PCLDACLD, Gain AACLD, Gain BACLD, Gain C
(a)
0.00 0.02 0.04 0.06 0.08 0.10
Theoretical Loss Factor
0.00
0.02
0.04
0.06
0.08
0.10
Exp
erim
enta
l Los
s Fa
ctor
PCLDACLD, Gain AACLD, Gain BACLD, Gain C
(b)
Comparison between theory &experiments for torsional mode
with different control gains
15.00 20.00 25.00
Theoretical Natural Frequency (Hz)
15.00
20.00
25.00
Exp
erim
enta
l Nat
ural
Fre
quen
cy (H
z) PCLDACLD, Gain DACLD, GainEACLD, GainF
(a)
0.00 0.05 0.10 0.15 0.20
Theoretical Loss Factor
0.00
0.05
0.10
0.15
0.20
Exp
erim
enta
l Los
s Fa
ctor
PCLDACLD, Gain DACLD, Gain EACLD, Gain F
(b)
Summary
z Introduced a a new class of composite sandwiched plates
z Developed the theoretical analysis of a composite plate/ACLD
z Theoretical Analysis was validated experimentally
z The ACLD is found to be effective in controlling the vibration of the plates