Sloshing Suppression Control During Liquid Container Transfer.pdf
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Sloshing Suppression Control During Liquid Container TransferInvolving Dynamic Tilting using Wigner Distribution Analysis
Yoshiyuki Noda, Ken’ichi Yano, Satoshi Horihata, and Kazuhiko Terashima
Abstract— This paper addresses concerned with the ad-vanced control of the transfer of liquid in a container, with spe-cial consideration given to transfer involving liquid containerwith dynamic tilting as well as the suppression of sloshing(liquid vibration) while maintaining a high transfer speed forthe container. In the transfer with dynamic (continuous) tilting,the sloshing’s natural frequency is varied with the change oftilting angle. In order to suppress the sloshing caused by suchtransfer, a new controller design method is proposed. First,the varying natural frequency is estimated using the WignerDistribution. Then, in order to suppress the sloshing, theposition control is designed using the Hybrid Shape Approachutilizing a time-varying notch filter. The effectiveness of theproposed control system is shown experimentally in a liquidcontainer transfer system.
I. INTRODUCTION
Many industries utilize transfer systems with mechanisms
that induce vibration, for example, crane systems, robotic
manipulators, automatic pouring systems, liquid container
transfer systems, and so on. In these industrial plants, it
is required that vibration is damped, while motion control
is accomplished as the mechanism moves at high speeds.
Recently, in order to meet such requirements, advanced
control systems using various control theories have been
developed. In most of these control systems, vibration
dynamics is treated as a stationary vibration. However, there
exists a transfer system having non-stationary vibration, for
example, a crane system with a changing length of cable, a
liquid container transfer system whose tilting angle changes,
and so on. In the crane system, the vibration’s natural
frequency is varied in terms of the cable length. Therefore,
the natural frequency is estimated theoretically by using the
pendulum model with a varying length of cable, and the
control system is designed with the application of Gain-
Scheduled Control, and so on[1]. However, there exists a
case in which it is difficult to estimate the varying natural
frequency. In the self-transfer-type automatic pouring robot,
the ladle is transferred along the mold line while pouring
the molten metal into the mold by tilting the ladle. In such
a transfer system that involves the tilting of a container, the
natural frequency of sloshing in the container varies with the
tilting; however, it is difficult to theoretically estimate the
varying natural frequency based on the shape of container.
Y. Noda, S. Horihata, and K. Terashima are with Departmentof Production Systems Engineering, Toyohashi University of Tech-nology, 1-1 Hibarigaoka, Tempaku, Toyohashi, Aichi 441-8580 [email protected]
K. Yano is with Department of Mechanical and Systems Engineering,Gifu University, 1-1 Yanagido, Gifu, Gifu 501-1193 Japan
Previous studies have described the design of transfer
systems involving tilting motion in consideration of slosh-
ing suppression. For example, sloshing suppression in an
automatic pouring robot has been achieved by using a
Hybrid Shape Approach[2]. Although this robot had the
ability to suppress sloshing during transfer and pouring
motions, the tilting control of ladle was sequentially per-
formed after the transfer of the ladle. As well, sloshing
suppression during the pouring motion and during transfer
was achieved through the use of preview control[3]. These
studies have been performed under the assumption that the
natural frequency of sloshing is constant if the ladle is
slightly tilted, (about 5[deg]). However, in actual pouring
motion, because the tilting angle of ladle has a wide range,
the natural frequency of sloshing varies with the degree of
ladle tilt. No studies have focused on sloshing suppression
in consideration of the change of the natural frequency due
to the tilt of the liquid container.
Therefore, the purpose of this paper is to propose a design
method for sloshing suppression during liquid container
transfer involving the dynamic tilting of the container. First,
the natural frequency of sloshing caused by container trans-
fer involving tilting is estimated by using time-frequency
analysis, which is useful for analyzing non-stationary vi-
bration. In particular, the Wigner Distribution[4] has higher
resolution in time and frequency domain than other time-
frequency analyses (for example, Short Time Fourier Trans-
form and Wavelet Transform). Therefore, in the field of
signal processing, the Wigner Distribution is often applied
to the identification of multi-element structures, fault detec-
tion in rotating machinery, and so on[5]. On the other hand,
this analysis contains interference which does not exist in
real signals with more than two frequency bands. However,
in the present process of liquid container transfer, the first
mode sloshing is dominant, and the natural frequency of
sloshing varies with the change of the container’s liquid
level and tilting angle.
Next, a sloshing suppression system for container transfer
involving dynamic tilting is designed through the use of
the Hybrid Shape Approach with a time-varying notch
filter. The controller designed using the Hybrid Shape
Approach developed by the author’s group in previous
research allows the fastest possible transfer while meeting
the given control specifications for time and frequency
characteristics[2]. The Hybrid Shape Approach is a design
method aimed at starting control and vibration damping by
using real-time feedback of only liquid container position
data without on-line sloshing feedback. In the present paper,
43rd IEEE Conference on Decision and ControlDecember 14-17, 2004Atlantis, Paradise Island, Bahamas
0-7803-8682-5/04/$20.00 ©2004 IEEE
ThA09.3
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the Hybrid Shape Approach is improved, such that the anti-
resonant frequency of a notch-filter is adequately shifted
corresponding to the dynamic change of the sloshing’s
natural frequency as estimated by the Wigner Distribution.
The effectiveness of the proposed system is validated by
applying it to the transfer of liquid by a container involving
pouring motion.
II. EXPERIMENTAL APPARATUS
A schematic diagram of the experimental apparatus of a
liquid container transfer system is shown in Fig.1. In this
study, in order to pour the liquid, a cylindrical container
with nozzle is used. The radius of the three-dimensional
cylindrical container R is 0.12[m] and its height is 0.3[m].
The liquid used in the present experiments is water, whose
static liquid level hs is 0.16[m]. This paper addresses liquid
container transfer on a straight path and the rotation of the
liquid container. The liquid container is transferred using
an AC servo motor equipped with a ball screw, and tilted
by using an AC servo motor directly. The position and
angle are controlled by adjusting the voltage applied to each
motor. The maximum velocity and maximum acceleration
of the motor used for transfer are 0.8[m/s] and 2.0[m/s2],
respectively, and those of the motor used for tilting are
150[deg/s] and 1500[deg/s2]. The position and angle of
the liquid container are detected by encoders fitted to each
motor. In order to evaluate only the experimental results,
level sensors were installed in this apparatus. The position
of the level sensor for measuring sloshing is placed at
position A installed in the transfer direction as shown in
Fig. 1. This sensor is placed to measure the first mode
sloshing in the transfer direction, but not sloshing in the
tilting direction.
AC servo motor
and Encoder for transfer
AC servo motor
and Encoder for tilting
Ball screw
Liquid Container
(R0.12x0.3m)
Level sensor
Nozzule of container
Transfer
Rotation Water
Tray
Transfer
Fig. 1. Schematic diagram of the experimental apparatus
For the AC servo motor using in this apparatus, the
transfer functions PX(s) and PT (s) from the input voltage
u(t) to the position yx(t) and angle yt(t) are respectively
given in the form of the following first-order lag model with
an integrator,
P (s) =Y (s)U(s)
=Km
s(Tms + 1)(1)
, where Tm is the time constant and Km is the gain. These
parameters were identified by adding a step-wise input to
the apparatus. As a result, the parameters of the motor
model for the transfer PX (s) were obtained as Kmx =0.1663[m/sV] and Tmx = 0.0060[s], and those for the
tilting PT (s) were obtained as Kmt = 24.71[deg/sV] and
Tmt = 0.008[s].
In general, if the cylindrical container is not tilted, the
natural frequency fn for a (1,1)-model sloshing of a perfect
fluid is represented by the following equation[2].
fn =12π
√g
Rε1tanh(ε1
hs
R) (2)
, where hs is the static liquid level, R is the radius of the
cylindrical container, g is the gravitational acceleration, and
ε1 is the least positive root for a first-order derivative of
the first kind Bessel function (ε1 = 1.841). In this study,
the target liquid level hs is 0.16[m] and the radius of the
cylindrical container is R = 0.12[m]. Hence, the natural
frequency fn is calculated as 1.9379[Hz] (12.17[rad/s]). As
shown in Fig.1, the process of pouring molten metal in the
casting industry uses the following actions. The container is
tilted forward to pour the molten metal into a mold. In the
self-transfer-type automatic pouring robot, the position of
the container from which the liquid is poured into a mold
is transferred in synchronization with the movement of the
mold. Then, because the quantity of liquid in a container
and the container’s angle are changed, the natural frequency
varies, and these values cannot be obtained from Eq. (2).
So, in the following section, we will show how the natural
frequency of sloshing can be determined for the dynamic
tilting of a container.
III. ESTIMATION OF THE NATURAL
FREQUENCY OF SLOSHING DURING TRNSFER
INCLUDING DYNAMIC TILTING USING WIGNER
DISTRIBUTION
A. Control system and sloshing data for analysis
In order to generate sloshing data, a control system as
shown in Fig. 2 is constructed for a liquid container transfer
system. PX (s) and PT (s) are motor models for transfer and
tilting respectively represented by Eq. (1). SX (s) shows the
sloshing dynamics in the liquid container. Therefore, yx and
yt show the position and tilting angle of liquid container,
and sx is the sloshing caused by the control input ux. This
is measured by level sensor as shown in Fig. 1. The property
of sloshing dynamics SX(s) is varied by the tilting angle yt
as shown in Fig. 2. For transfer control, a position feedback
control system using a feedback controller KX is built for
the motor PX(s). In order to generate sloshing for obtaining
the sloshing data, the feedback controller KX uses only the
proportional gain. In this paper, the transfer reference rx is a
trajectory determined by integrating the maximum velocity
and maximum acceleration, and the starting point is set to
0[m] and the endpoint is 0.24[m]. In order to tilt the liquid
container to 55[deg] and suppress the sloshing caused by
the tilting motion, the control input ut to the tilting motor is
designed using the Hybrid Shape Approach[2]. Moreover, in
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order to change the property of sloshing dynamics, forward
tilting begins at 9[s] as shown in Fig. 3, and backward tilting
begins at 15.5[s]. Hence, the natural frequency of sloshing
will be varied at the time interval of 9 ∼ 15.5[s].
P (s)T
P (s)X
S (s)X
+-
Motor for tilting
Motor for transfer
Sloshing
y
y
s
u
u
r x
x
t
x
t
x
Controller
KX
Fig. 2. Control system for sloshing analysis
The experimental results using this control system are
shown in Fig. 3. Diagram (a) shows the position of the
liquid container, diagram (b) is the control input to the
transfer motor, diagram (c) shows the tilting angle, and (d)
is the control input to the tilting motor. In the experimental
results, after transfer of 0.24[m] from the origin , the liquid
container is tilted at up to 55[deg] as mentioned above.
Sloshing in this experiment is shown in Fig. 4. In this Fig.
4, the liquid level is lowered after 11.5[s], since the liquid
is poured from the container. Therefore, the liquid level is
0.16[m] before pouring and 0.087[m] after pouring.
B. Sloshing analysis using the Wigner Distribution
In order to analyze the sloshing caused by the transfer
and the tilting of the liquid container, Wigner Distribution
analysis is utilized. The Wigner Distribution is represented
by the following equation,
WD(t, f) =∫ ∞
−∞sx(t +
τ
2)s∗x(t − τ
2)e−j2πfτdτ (3)
, where t is time, and f is frequency. sx(t) is an analytical
signal, which represents the sloshing data in this paper, and
s∗x(t) is complex conjugate function of the analytical signal.
In Eq. (3), since the Wigner Distribution is the Fourier
0 10 200
0.1
0.2
0.3
Posi
tion
y x [m
]
0 10 20
−2
0
2
Con
trol
inpu
t ux [
V]
0 10 200
20
40
60
Time [s]
Tilt
ing
Ang
le y
t [de
g]
0 10 20−1
−0.5
0
0.5
1
Time [s]
Con
trol
inpu
t ut [
V]
(a) (b)
(c) (d)
Fig. 3. Experimental results of transfer path and tilting angle of container
0 5 10 15 20 25
−0.1
−0.05
0
0.05
Time [s]
Slos
hing
[m
]
Fig. 4. Experimental result of sloshing caused by transfer involve tilting
Transform of a autocorrelation function of the analytical
signal, it is thought that the Wigner Distribution results in
higher resolutions in the time and frequency domain than
does a Short Time Fourier Transform expressed as
Sp(t, f) =∣∣∣∣∫ ∞
−∞sx(t)w(τ )e−j2πfτdτ
∣∣∣∣2
(4)
, where w(t) is a window function.
However, the Wigner Distribution contains an interfer-
ence, which does not exist in real signals, when the analyt-
ical signal has more than two frequency spectrum bands at
the same time. In this study, the effect of interference in this
analysis of sloshing in the present process was insignificant,
because 1st mode sloshing is dominant, and thus sloshing
has an almost single natural frequency. Therefore, the
Wigner Distribution is thought to be available and useful
for this sloshing analysis.
Hilbert
transformConjugation
Butterfly
operation
Fourier
Transform
Window
Absolute
of real part
sx(t)
WD(t,f)analytical signal
Fig. 5. Computation process of Wigner Distribution
The computation process of the Wigner Distribution is
shown in Fig. 5. In the first step, a signal is sectioned by a
window. Next, in order to obtain the analytical signal sx(t)in Eq. (3), the Hilbert Transform is introduced for the signal
sectioned by the window. After that, a butterfly operation is
implemented for the analytical signal sx(t) and a conjugated
signal s∗x(t). In this process, the autocorrelation function of
the signal sectioned by the window is obtained, and energy
at the natural frequency of sloshing is emphasized. Then,
the signal after the butterfly operation is transformed by
5 10 15 20 25
−0.04
−0.02
0
0.02
0.04
Slos
hing
[m
]
Time [s]
Fig. 6. Sloshing data for analysis
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Fig. 7. Result of sloshing analysis by Wigner Distribution
6 8 10 12 14 16 18 20 221.4
1.6
1.8
2
2.2
2.4
Freq
uenc
y [H
z]
Time [s]
Fig. 8. Energy contour of sloshing by Wigner Distribution
Fourier Transform into the frequency domain. In the final
step, only the absolute the value of the real part of data in
the frequency domain is used to clarify the result, since the
analytical result is unclear because it contains the internal
interference. This process is implemented for each shift in
time. Therefore, the energy for the signal in the time and
frequency domain is obtained.
In this study, the sloshing data shown in Fig. 4 is analyzed
using the Wigner Distribution. However, the data includes
the step-wise signal, since liquid in the container is poured.
The step-wise signal increases in the low frequency domain.
Therefore, in order to eliminate the step-wise signal from
the sloshing data, the sloshing data is pre-compensated by
the following equation,
sx(k) = sx(k) − 12N + 1
N∑m=−N
sx(k + m) (5)
, where t = k∆T , and ∆T is sampling time, which is
0.01[s] in this study. The second term in Eq. (5) represents
a moving average. N in the moving average is selected to
be 50 in order to obtain only sloshing which is different
from the liquid level. The sloshing data compensated by
Eq. (5) is shown in Fig. 6. In the analysis using the Wigner
Distribution, sloshing data from 3[s] to 26[s] is used, since
the sloshing to 3[s] includes the fluctuation of the liquid
surface due to the acceleration of transfer.
The result obtained by Wigner Distribution analysis of the
sloshing data is shown in Fig. 7. This analysis is performed
at a sampling time of 0.01[s] and a window size of 526,
Fig. 9. Result of sloshing analysis by Short Time Fourier Transform
6 8 10 12 14 16 18 20 221.4
1.6
1.8
2
2.2
2.4
Freq
uenc
y [H
z]Time [s]
Fig. 10. Energy contour of sloshing by Short Time Fourier Transform
which shifts from 6[s] to 23[s] in the sloshing data. In Fig.
7, the 1st mode sloshing appears near 2[Hz]. Moreover,
3rd mode sloshing and interference appear near 3[Hz] and
2.5[Hz] respectively. However, the natural frequency can be
easily estimated, since the 1st mode sloshing is the largest
at each time. If larger interference appears in the analysis,
Reduced Interference Distribution should be applied[6].
Furthermore, the Wigner Distribution for the sloshing
data is shown in Fig. 8, as an energy contour in the time and
frequency domain. Fig. 8 shows that the region covering the
greatest number of contour cycles has higher energy than
the other region. Therefore, the energy in the region from
6[s] to 8[s] and near 1.9[Hz] is the highest in the time-
frequency domain. It is seen that the energy peak during the
time span from 9[s] to 20[s] shifts toward a low frequency
when the liquid container is tilted.
As a comparison of the sloshing analysis using the
Wigner Distribution with other analytical methods, a slosh-
ing analysis using the well-known Short Time Fourier
Transform is shown in Fig. 9, and the energy contour in
time and frequency is shown in Fig. 10. In this analysis,
the window size and the shifting time are as the same
as those of the Wigner Distribution. In Fig. 9, 3rd mode
sloshing scarcely appears. Therefore, using Short Time
Fourier Transform, it is seen clearly that tilting varies
the sloshing property of liquid transfer. In this section,
Short Time Fourier Transform is apparently more useful
than the Wigner Distribution. However, with respect to the
representation of natural frequency, we remark that the
Short Time Fourier Transform is less accurate than the
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6 8 10 12 14 16 18 20 221.4
1.6
1.8
2
2.2
2.4Pe
ak F
requ
ency
[H
z]
Time [s]
Fig. 11. Peak frequency obtained from Wigner Distribution
6 8 10 12 14 16 18 20 221.4
1.6
1.8
2
2.2
2.4
Peak
Fre
quen
cy [
Hz]
Time [s]
Fig. 12. Peak frequency obtained from Short Time Fourier Transform
Wigner Distribution. The reason for this is described in the
next section.
C. Estimation of sloshing’s natural frequency
In order to estimate the natural frequency of sloshing
using the Wigner Distribution, the energy peak on each time
is plotted, as shown in Fig. 11. The peak frequency before
tilting the container is 1.95[Hz], and the peak frequency
after tilting is 1.85[Hz]. The static liquid level before the
container is tilted is 0.16[m], then the theoretical natural fre-
quency of sloshing as represented in Eq.(2) is 1.9379[Hz].
As well, the static liquid level after tilting is 0.087[m],
and thus the sloshing’s theoretical natural frequency is
1.8207[Hz]. Therefore, it is seen that the peak frequency in
the Wigner Distribution has estimated the natural frequency
of sloshing as well. In this paper, the peak frequency in
the Wigner Distribution is called the sloshing’s estimated
natural frequency. Furthermore, in this analysis, the useful
result is obtained such that the estimated natural frequency
during tilting is in a lower frequency domain than that after
tilting.
In order to compare the sloshing’s estimated natural
frequency as obtained by the Wigner Distribution, the
estimated result obtained by Short Time Fourier Transform
is shown in Fig. 12. By comparison of Fig. 11 and Fig.
12, the Wigner Distribution shows an impressively high
resolution. If the window size of the Short Time Fourier
Transform is increased in order to achieve higher resolution
in the frequency domain, the accuracy in the time domain
become lessens. Therefore, for the estimation of natural
frequency, it is seen that the Wigner Distribution is effective.
D. Simulation of sloshing by sloshing’s estimated naturalfrequency
The following model is used to verify the sloshing’s
estimated natural frequency. Initially, the sloshing model,
m
c
l
θ
L
hs
h
x
Fig. 13. Pendulum model for sloshing in the liquid container
in which the liquid container is not tilted, is introduced.
We assume that the sloshing in the liquid container is
approximated by the pendulum model[7] shown in Fig. 13.
In Fig. 13, x-direction is the transfer direction of the liquid
container and L is the diameter of the liquid container. his the level of the static liquid and hs is a fluctuation of
the static liquid level, while m indicates the weight of the
liquid in the container and c and l indicate the coefficient
of the fluid’s viscosity and the length of the pendulum for
sloshing. Further, θ indicates the angle of the slope of the
sloshing.
In Fig. 13, the differential equation regarding θ is shown
in the following equation[7].
ml2 θ − mlx cos θ + mgl sin θ + cl2θcos2θ = 0 (6)
Then, the liquid level hs is represented by the equation
hs =L
2tan θ (7)
The linearization of Eqs.(6) and (7) produce the follow-
ing: θ = − c
m θ − gl θ + 1
l xhs = L
2 θ(8)
, where θ 0. Therefore, the transfer function of Eq.(8) is
represented as follows:
Sx(s) =Hs(s)A(s)
=Kω2
n
s2 + 2ζωns + ω2n
(9)
, where a(t) = x(t), K = L
2g
ωn =√
gl , ζ = c
2m
√lg
(10)
In the sloshing model involving tilting, the sloshing’s
natural frequency ωn in Eq. (9) varies. Therefore, the
transfer function of the sloshing model caused by transfer
involving tilting is represented as follows:
Sx(s, τ) =KΩ2
s2 + 2ζΩs + Ω2
∣∣∣∣Ω=ωn(τ)
(11)
, where ωn(τ ) is the sloshing’s estimated natural frequency
in Fig. 11.
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10 12 14 16 18 20 22
-0.02
-0.01
0
0.01
0.02S
losh
ing [
m]
SimulationExperiment
10 12 14 16 18 20 22
-0.02
-0.01
0
0.01
0.02
Slo
shin
g [
m]
Time [s]
(a) Fixed natural frequency
(c) Wigner Distribution
10 12 14 16 18 20 22
-0.02
-0.01
0
0.01
0.02
Slo
shin
g [
m]
(b) Short Time Fourier Transform
Fig. 14. Comparison with sloshing simulations and experiments
Simulation results using Eq. (11) are shown in Fig. 14.
In order to compare the proposed sloshing model in Eq.
(11) with the natural frequency obtained by the Wigner
Distribution, the sloshing model including a constant natural
frequency fixed at 1.9379[Hz] and that with a natural
frequency are estimated by Short Time Fourier Transform.
A bold line in diagram (a) is the simulation result ob-
tained by using the sloshing model with the fixed natural
frequency, and the bold lines in diagrams (b) and (c) are
the simulation results obtained by the proposed sloshing
model in Eq. (11) using Short Time Fourier Transform and
Wigner Distribution, respectively. In both (a), (b), and (c),
the thin lines indicate the experimental result of sloshing
caused by the transfer involving the tilting as shown in Fig.
3. Fig. 14 includes the results obtained by 9[s] to 23[s],
since these clearly show the sloshing’s properties varied due
to the tilting. The results show that, the sloshing model
having a fixed natural frequency and using Short Time
Fourier Transform does not closely represent the sloshing
we are attending to here. On the other hand, the results
of the proposed sloshing model correlated closely with
the experimental result, demonstrating that the proposed
method using the Wigner Distribution accurately explains
the sloshing caused by transfer involving tilting.
IV. SLOSHING SUPPRESSION CONTROL USING
THE HYBRID SHAPE APPROACH
In order to suppress sloshing, a control system is designed
using the Hybrid Shape Approach. This approach, described
in detail in [2], is a method for starting control and vibration
damping, and satisfies hybrid specifications in both the
frequency domain (gain margin, phase margin, vibration
characteristics, and so on) and the time domain (transient
response, settling time, overshoot, restriction of control
input, and so on) by using real-time feedback of only the
container’s position data.
In the approach described in the previous paper, sloshing
can be damped by furnishing the controller with a notch
filter at the sloshing’s natural frequency. In this paper, a
time-varying notch filter corresponding to the sloshing’s
estimated natural frequency is introduced into the original
Hybrid Shape Approach. The design method using this
approach is described in the following.
A. Control system
For position control and sloshing suppression, the system
shown in Fig. 2 is used. In order to suppress sloshing, a
feedback controller KX is designed using Hybrid Shape
Approach and is equipped with a time-varying notch filter.
B. Selection of control element
In order to satisfy the desired specifications, the controller
is formulated as follows.
Kx(s, τ) =n∏
i=1
Ki(s, τ) (12)
Eq. (1) descibes a servo system equipped with an integrator.
Thus, according to the Internal Model principle, a propor-
tional control (P control) system is sufficient to avoid the
offset. Therefore, the proportional gain (K1) is selected as
the first element of the controller Kx(s, τ) given by Eq.
(12).
K1 = KP (13)
In order to reduce the influences of higher-mode sloshing
and noise, a low-pass filter (K2), which makes the controller
express low gain at a high frequency domain, is selected as
the second element of the controller.
K2 =1
Tls + 1(14)
A time-varying notch filter (K3) is selected as the final
element of the controller in order to suppress sloshing.
K3 =s2 + 2ζΩs + Ω2
s2 + Ωs + Ω2
∣∣∣∣Ω=ω(τ)
(15)
The parameter ζ in Eq.(15) is given as ζ = 0.001, and
ωn(τ ) is given as the sloshing’s estimated natural frequency
in Fig. 11. The notch filter makes it possible to suppress
residual vibration without directly measuring the liquid
vibration. Finally, the transfer function of the controller are
given as Eq.(16).
Kx(s, τ) =3∏
i=1
Ki
=KP (s2 + 2ζΩs + Ω2)
(Tls + 1)(s2 + Ωs + Ω2)
∣∣∣∣Ω=ωn(τ)
(16)
In Eq.(16), KP and Tl are unknown parameters. These
parameters are reasonably determined by solving an opti-
mization problem.
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C. Formulation of design specifications
In the Hybrid Shape Approach, various control specifica-
tions in the time and frequency domains can be given. The
specifications of the controller in both domains are formu-
lated by making use of penalty function, and the controller
Kx(s, τ) is then calculated to satisfy those specifications.
In the control design, Spec.(I) ∼ Spec.(III) were given for
the controller.
• Spec.(I): The controller gain should be less than 0[dB]
at ω = 314[rad/s] in order to decrease the influences
of the higher-order sloshing mode and noise. A penalty
is given if the following constraint does not hold:
|K(τ, ω)| < 0[dB] (17)
• Spec.(II): Due to the restriction of the input magni-
tudes, the input voltage u should not exceed a mag-
nitude of ±10[V]. A penalty is given if the following
constraint does not hold:
max |u| < 10[V] (18)
• Spec.(III): Maximum overshoot should not exceed a
magnitude of 10−3[m]. A penalty is given if the
following constraint does not hold:
max(Os) < 10−3[m] (19)
D. Formulation of an optimization problem
The following optimization problem using penalty terms
is formulated with Eq. (17) ∼ Eq. (19)
minK(s)
J = Ts + JP (20)
where,
JP = w1 + w2 + · · ·+ wi + · · · ,
Ts = mint | |yf − y(t + σ)| < ye, σ > 0 , (21)
and t is the time, y(t) is the position of the container at
time t, yf is the target position, Ts is the settling time to the
reference trajectory rx in the control system shown in Fig.
2, and ye is the admissible error set to 10−3[m]. Minimizing
Ts indicates that the trajectory of the container quickly
reaches the target point. If none of the above constraint
conditions are held, the penalty function wi in Eq. (20) is
added as wi = 108 to the cost function J . The index i of
wi corresponds to the above specification number.
E. Computation of a controller
Feedback controller Kx(s, τ ) in Eq. (16) is derived to
minimize the cost function given in Eq. (20). The simplex
method [8] is adopted as the optimization method, where the
reflection coefficient is α = 1.0, the expansion coefficient
is β = 0.5, and the contraction coefficient is γ = 2.0. The
solution obtained by the simplex method is not always the
globally optimal one. Hence, the initial simplex values and
weights of the cost function are modified in order to obtain
the desired characteristics of the controller. The initial
simplex values were assigned to be KP = (17.2, 50, 1)
and Tl = (0.01, 0.005, 0.1). The reference trajectory of the
transfer system using optimization was determined by inte-
grating the maximum velocity and maximum acceleration
of the present experimental apparatus. In the design, the
starting point was set to be yx = 0[m], relay point was
set to be yx = 0.24[m], and the endpoint was set to be yx
= 0.48[m]. A starting time when shifting from the relay
point to the endpoint was 14[s], and thus the tilting angle
is 55[deg]. This situation is the transfer at the middle time
point of tilting as shown in Fig. 16.
As a result, around 20 iterations were required for
convergence, and it took about 36 seconds to compute
an optimization problem when using a personal computer
(Pentium IV 2.4GHz CPU). In the computation, Kp = 9.10and Tl = 0.055 were obtained as cost function J = 3.21.
The frequency response of the controller is shown in
Fig.15. In Fig. 15, the gains of proposed controller at
τ = 0[s], τ = 15[s], and τ = 25[s] are shown. The
proposed controller at τ = 0[s] represents the tilting angle
at 0[deg] before tilting, τ = 15[s] indicates the tilting
angle at 55[deg] as the maximum forward tilting, and τ =25[s] indicates the tilting angle at 0[deg] as after following
backward tilting. From this figure, it can be seen that the
controller gain decreases at the sloshing’s estimated natural
frequency. Also, it can be confirmed that it is less than
0[dB] at ωl=314[rad/s] (50[Hz]). Since the gains decrease
monotonously decreasing in the high-frequency domain, it
is also clear that the controller can decrease the influences
of high-mode sloshing and noise. Furthermore, a high-speed
transfer of the container is achieved because the controller
is high-gain in the low-frequency domain.
100
101
102
−40
−20
0
20
Angular frequency [rad/s]
Gai
n [d
B]
τ =0[s] τ =15[s]
τ =25[s]
Fig. 15. Bode diagram of the proposed controller
The simulation results using the developed controller
confirmed that the container quickly transferred to the target
point, and the restriction of the magnitude of control input
was satisfied. These results cannot be shown here due to the
limitations of this paper; however, the effectiveness of this
system can be evaluated by the experimental results shown
in the following section, because the experimental results
are almost the same as those of the simulation.
V. EXPERIMENTAL RESULTS
Using the liquid container transfer system as shown in
Fig. 1, the effectiveness of the proposed control system will
be verified in this section. The tilting condition is as the
same as that shown in Fig. 3, and the transfer reference
trajectory rx is as the same as that shown in Fig. ??.
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A controller with a notch filter, whose natural frequency
is fixed at 1.9379[Hz], is described for comparison with
the proposed system. The controller is designed using the
original Hybrid Shape Approach.
Fig. 16 shows the experimental results regarding the
position of the container, the control input to the motor
for transfer, and the tilting angle of the proposed control
system. Fig. 17 shows the experimental results of sloshing
when using controllers equipped with the fixed notch filter
and the time-varying notch filter. In Fig. 16, diagram (a)
shows position yx of the liquid container and reference
trajectory rx. The dashed line is the reference trajectory,
and the solid line shows that of the position of the liquid
container. Diagram (b) shows control inputs to the motor for
the transfer. Diagram (c) shows tilting angle of the liquid
container. In Fig. 17, diagram (a) shows the experimental
result from 0[s] to 8[s] when using the controller equipped
with the fixed notch filter, while diagram (b) shows that by
the proposed controller using time-varying notch filter. Dia-
grams (c) and (d) show the experimental results from 14[s]
to 22[s] when using controllers equipped with the fixed
notch filter and the time-varying notch filter, respectively. In
these diagrams, the static liquid level is set at 0.0[m]. The
tilting angle in both experiments using the fixed and time-
varying notch filter is the same. The experimental result
regarding the position of the container and the control input
to the fixed notch filter were almost same as those using
the time-varying notch filter. (These experimental results
were not shown due to the limitations of this paper.) The
settling times to controllers when using the fixed notch filter
and the time-varying notch filter were 3.17[s] and 3.21[s],
respectively, the controller using the fixed notch filter being
slightly faster than the proposed control system by 1.25[%].
Both controllers were able to damp sloshing at the tilting
angle 0[deg] shown in Fig. 17(a) and (b). However, in Fig.
17(c), the sloshing is caused by the transfer during tilting.
On the other hand, in Fig. 17(d), the sloshing is dampened
by the proposed control system equipped with the time-
varying notch filter. Therefore, during the transfer of a liquid
container involving tilting, the proposed control system can
achieve perfect sloshing suppression.
VI. CONCLUSIONS
In this paper, we proposed a design method for suppress-
ing sloshing in a liquid container during transfer involving
dynamic tilting. In order to estimate the varying natural
frequency of sloshing, the Wigner Distribution was applied.
A comparison of simulations of sloshing demonstrated
that the Wigner Distribution estimated the change of the
natural frequency more effectively than did conventional
Short Time Fourier Transform. A control system for liquid
container transfer involving tilting was then designed using
the Hybrid Shape Approach, utilizing a time-varying notch
filter. Experimental results showed that the proposed control
system effectively achieved sloshing suppression.
0 5 10 15 20 250
0.2
0.4
0.6
Posi
tion
[m]
0 5 10 15 20 250
0.5
1
1.5
Con
trol
inpu
t [V
]
0 5 10 15 20 250
20
40
60
Tilt
ing
angl
e [d
eg]
Time [s]
Reference trajectory
Transfer trajectory
Fig. 16. Experimental results by using the proposed controller
0 2 4 6 8−0.02
−0.01
0
0.01
0.02
Slos
hing
[m
]
0 2 4 6 8−0.02
−0.01
0
0.01
0.02
14 16 18 20 22−0.02
−0.01
0
0.01
0.02
Slos
hing
[m
]
Time [s]14 16 18 20 22
−0.02
−0.01
0
0.01
0.02
Time [s]
(a)Fixed notch filter from 0[s]
(b)Time−varying notch filter from 0[s]
(c)Fixed notch filter from 14[s]
(d)Time−varying notch filter from 14[s]
Fig. 17. Experimental results of sloshing caused by the control systemby using the fixed and the time varying notch filter
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