Introduction
The main concern of the present paper is the response behaviour of a ship to steering in course-control, both manual and automatic;
what measures or
characteristic figures should be used to describe the response be-haviour and how to evaluate the figures for a given ship.In
this subject, ship motion
is rather moderate and consequently the response be-haviour is described reasonably with a linear differential equation,. .
Ti T2 .s.6-F(Ti-F T2).0+0=104 KT35., ( 1 ) * Faculty of Engineering, Osaka University.
** Kobe University of Mrcantile Marine.
112
0 denoting the yaw-rate and 3 the rudder
angle. This equation is obtained from the coupled equations of yaw and sway motions, excluding nonlinear terms and also coupling with forward motion, since both effects are negligible for small motions.
The first-order system approximation, sometimes called K-T analysis, starts from this equation to jive another and more simple equation,
( 1')
where T=
T2 T3. _This mathematicalmodel of ship response is quite simple, yet able to describe the basic characteristic of a ship in steering, thus having extensive utility
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Archief
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8. A New Procedure of Manoeuvring Model Experiment
Kensaku NOMOTO*, Member & Keiichi Kanmum**, Member (From J.S.N.A. Japan, Vol. 126 Dec. 1969)
Summary.
Response behaviour of a ship to steering is described with the transfer function in
steer-ing Ye(10)=K(1 -1-iwT3)/(1 iw Ti)(1 iwT2)1). A simplified analysis with just a pair of indices K and T is based upon this idea and has a wide utility to measure and to asses
manoeuvra-bility of ships. This simplification is, however, no more valid for the analysis and synthesis -.take of steering control of a ship, in which we should take an automatic steering device
and/or a human operator into account.2) Here the complete transfer function should be called
upon to describe the ship behaviour.
This paper relates to a new procedure of defining the transfer function and the tour characteristic constants K, Ti, Ti and T3 of a given ship, using a radio-controlled, free-sailing model. This principle can also be adopttd to a full-size experiment. The procedure
employs two mancgivres; parallel shifting of the ship's track and periodic steering with a
numberof frequencies. Both manoeuvres can be performed in a conventional towing basin. The harmonic analysis of the parallel shift manoeuvre gives, together with the amplitude
and phase of yawing motion measured on the periodic steering, an information enough to
assess the transfer function of a ship, which facilitates to determine the characteristic
constants K, Ti, etc.
These constants are composed of eight stability derivatives (coefficients of the linear equation of motion), so that we can define these derivatives through the present approach
if four of these derivatives are given byany other sources, for example, oblique towing test. The data involved were obtained at the Osaka University Experiment Tank No. 2, using
in practical applications.
For the analysis and synthesis of automatic
and manual course control, however, this
simplified approach is no more satisfactorybecause the term Kna in Eq. (1) plays an
important role in this subject2). Here we should call upon Eq. (1) and the four charac-teristic constants K, T1, T2 and T3
These constants are composed of the linear coefficients of the coupled equations of yaw and sway. These coefficients represent the inertia of, and the hydrodynamic forces
act-ing upon a ship. We can thus evaluate
the constants of a given ship by defining
the hydrodynamic coefficients, often called "hydrodynamic derivatives.", from captivemodel experiments with either the planar.
motion mechanism or rotating arm facilities.Another method of evaluating these
con-stants, which the present paper relates to,
is to stimulate a radio controlled model by actuating the rudder and simultaneously
re-cording the time histories of yaw-rate (h
and rudder angle 8. The harmonic analysis of the recordedand 5 gives the transfer
function of 'a ship in steering (we may also call it the frequency response) at a number of different frequencies. This makes itpos-sible
to evaluate
the characteristic con-stants'). It should be noted that in this ap-proach we need not know what forces actupon a ship but only know What
rudder movement induces what ship motion. As a consequence we can adopt it for a full size experiment as well as for models.The rudder movement used in this experi-ment can be of any type in principle. It will be useful, however, if a rudder movement is devised which causes no eventual change
of ship's heading, because it can be
em-ployed, for experiments on a conventional towing tank with a reasonable width. The practical advantage using a conventional
tank for a steering experiment needs, no
further emphasis. The present paper
pro-poses two manoeuvres of this kind. One isthe parallel shifting of ship's track using
an automatic coure-keeping device Rd board113
A New Procedure of Manoeuvring Model Experiment
/with
and the other a pyliodic, or sinusoidal steer-ing commenced(ra a cosine phase.
The harmonic analysis on the result of the former experiment gives the frrouency
res-ponse of a ship at low and intermediate
frequencies and the latter provides directly the same response at high frequencies. Gathering the two together, the frequency response of a ship is defined at a reasonable extent of frequency range and this, in turn, facilitates to determine all the characteristicconstants K, Ti, etc.
1. Parallel Shift Manoeuvre A Transient
Response Technique
1.1 Mathematical Treatment
Taking the Laplace transform of the both
sides of
Eq,(1), we define the transfer
function in steering,
MVP] K(1-Fpf3)
$(1')
L[o] (1+p7:1)i+PT2)'where p=a+io, is a complex number.
Since Eq. (2) is valid for every combination of ship motion ,fi(t) and the rudder movement
b(t) that induced the motiOn, it
can be
rewritten in a form to evaluate the transfer function from any combination of and 5
that induced the cb, that is;
oo
gy(f)aPidt
-\5(t)elgdt0
where sb is a ship moti..op, and ö the rudder movement that induced-Ali-lotion.
Both integrals of the denominator and
numerator of this equation converge with
a--,0+ in case of course-stable ships,
viz.Ti) 0,
(note that
7'3and Ti are always
positive), so that we can write
K(1 -I- ha T3) (1-1-iwn)(1+u,,T2)
=
o(or-,e-i" (It
aTo(t)e
e-i-iclt(2)
App y ngIi
Eq. (3) to the rudder angle
andyaw-rate records obtained at a sequence of
manoeuvre, we can compute
Y,(iw) at anumber of w.
According to the theory of the
transfer function, 11'4/(0)1 is the amplitude ratio of a yaw-rate harmonics with a frequencyw to arudder angle harmonics with the
same co, both harmonics being involved respectivelyin and 8 that caused the 0. Sirnilarl/Arg
Ys(iw) represents the phase lag ofthe same yaw-rate harmonics after the rudder angle harmonics.
We can thus
determine. the frequency response of a ship in steering at a number of w from At) and o(t) recorded.For the parallel shift manoeuvre, however, Eq. (3) gives indefinite form at w=0, since the amounts
0(o0)=si,(t)dt and ö(t)d 1
0
must be null for this manoeuvre. In conse-quence Eq. (3) fails to define Ys(icu) accurately
at low frequencies from the parallel shift
experiment.
In order to overcome this, we use a modi-fied form of Eq. (2), viz.
1,[$i
go]
L[a] L[avp
Correspondingly Eq. (3) is modified to be
cesb(t)e-a'e-"iclt
0
e-a' e-tat{ o(GP)dr.}dl
0 1
l's(iw). I i m
d-.0+
3 7
Eq. (4) gives a definite Ys(la,)
even at w=0
and is able to define Ys(iw) accurately at low and intermediate frequencies from the paral-lel shift manoeuvre.On the other hand, the integrals in Eq. (4)
as applied to the parallel shift
manoeuvre becomes very small in value with increasingw.
So that the harmonic analysis
on thismanoeuvre can not work well at high fre-quencies. For such a frequency range, the other type of experiment,. viz, thesinusoidal (or periodic) steering provides a good source for evaluating Ys(i co). This will be discussed later.
1.2 Instrumentation and Experimental Practice
Fig. 1 shows the arrangement of apparatus aboard a radio-controlled, free-sailing model
equipped for frequency response steering
experiments. Fig. 2 illustrates schematically how a free-sailing model takes offVfrom the
towing carriage after being accelerated up to the specified speed and then how it makes the parallel shifting, of its track.
A 'pair of towing guides holds the model by electro-magnetic force during accelerating, while heave and pitch remain free by
func-tion of rollers on each guide. When
the carriage has reached the specified speed, the operator turns off the electromagnet to free the model V and at the same time deceleratesthe carriage for a few moments. A few
seconds after take-off, the rudder is put on to a small amount (usually 50) by radiocom-mand. The carriage follows theV model atV a
12
-1. Towing Guide (aft) V2. Steering Gear
3. Automatic Steering Device 4. Rate
Gyro Amplifier 5. Rate Giro 6. Recorder 7. Radio-control Receiver 8. V
Speed-measuring Counter 9. Timer 10, Directional Gyro 11. Speed Pick-Up 12. Towing Guide (fore) 13. Batteries
A New Procedure of Manoeuvring Model Experiment . 115
reverse the rudder and turn on automatic
steer. system. (t): ship's heading
I(t): rudder angle
/ .
towelfree, /
in1
1
b., running- L____ //
I -well i. automatic steering steady 1
transient stage
Fig. 2
model ships trajectory
+state carria e enlarged Illustration of a Parallel Manoeuvre Test Shift
proper distance until recovering
it at the
tank end. As soon as the heading
devia-tion reaches a given angle (usually 30), a
photo-electronic switching circuit attached
to the directional gyroscope turns on the
automatic course-keeping device, the
com-mand course being the
original heading parallel to the tank centre-line. Hereafter the rudder is automatically controlled sothat its angle is always proportional to thehead-ing error. This results in the parallel shifting of the ship's track. The automatic course-keeping device should be adjusted to
be rather underdamped so that the ship
motion approach to a regular
damped or sustained yawing eventually.It is because
such a periodic yawing is moredefinitive and therefore more suitable for the -integration up to infinite timeof Eq. (4), than the smooth but somewhat fickle motion which would occur if a well-damped course-keeping con-trol was employed.In carrying out this experiment,
specialattention should be attached to guide
the model accurately parallel to the tankcentre-7
line during towing and also to see that the
c
carriage speed is kept exactly the same as
the free-sailing speed of the model at
take-off. Otherwise initial disturbances may
af-fect the ship motion and spoil the result:
As for measurement devices, care should be taken to minimize the stray drift of the di-rectional and rate gyroscopes.1.3 Calculation
Numerical calculation of the integrals of Eq. (4) as applied for the parallel shift mano-euvre is carried out in two parts. Taking a time tc, after which the ghip motion is regard-ed to be a regular dampregard-ed or sustainregard-ed oscil-lation, we perform numerical integration of
the numerator as well as the denominator
from 1=0 to i.
The integrations from tg to 03 can be done formally,for after the time
10 the integrands are both definitive functions
of the form of damped or sustained oscilla-tion whose frequency, amplitude and if any,'
damping ratio can be evaluated from the
records obtained.If there was no initial disturbance and the parallel shifting of ship track was performed
perfectly, we would not need any further
calculation.
In practice, however, the
ob-tained records of ship motion and rudder
movement may contain some effects of these disturbances. Special care should be taken to minimize them, but small disturbanceef-fects may be corrected
in the following!manner.
In making this correction we need to know the response
behaviour of a given ship.
This is obviously a paradox.. A reasonable procedure to solve itis to apply the K-T
analysis" to the initial part of the parallel
shift manoeuvre thus evaluating the indices K and T, denoted here as Kg and Tg respec-tively, and to use them as the first approxi-mation of the response .behaviour to be em-ployed for the correction.
If the relative
amount of the correction is small then, this is adequate.The correction is composed of five parts.
The first to the fourth are the
corrections( 5 )
Base Line after No.123 Corrections Base Line after No.1,2,3,4Corrections,
Fig. 3 Notations used in Analysing the Parallel Shift Manoeuvre
This final adjustment of Dm., the last stage of the correction, becomes a step-by-step converging process starting with Ifd
as the
first approximation, and eventually it is per-formed with the equation that0.+ Ta(0:00-00) 1+ CY:god Ke final Dm., Irscom 1+ C
c
+Tc(siicç/.o)}.to --2 .30a,rrecLori dt .o Su' ( 7 )where Ife, Te, to 0. and cbcorreued are defined
Eq. (4) using °mewl and n
previously a.nd Ygon is 178(0) first reached by
-,-corrected before the
final adjustment of Dm..
Using this Dm., the final Aorremod is fixed and all the correctionsare completed. Putting these final Ocorrecwa and Ammmwd into Eq. (4),
Ye(lo,) is computed at a series of frequencies. Incidentally, Ys(0), that is K, is determined eventually at this stage of correction,
seperately from Ye(iw) at non-zero frequencies;
the abovementioned step-by-step converging process provides the final Ys(0) as well as
Dm..
That is,
K= Yecon
-1+C
( 8 )
respectively for the initial motion, rudder
neutral position error, residual steady turning and imperfect parallel shifting of the track. All four of these corrections are carried out together, using the equation that,
Ocorreacd = Om sbie( 1 rt/Te)
Aorreculd =
where 'on,: measured 0(t),
: time average of Tit sbm for 1e<t<00
Om : time average of (OM t)
for tc<t<co
t, and Te being defined earlier in this section, and where
a(r)dr, , o(t) being
0
' the rudder angle,
Dm: D computed from measured O(t)
b.:
time average of Dm
dt for te<t<00Dm.:
time average of (Dmi) ,1)
for 1e<t<00.
These time average quantities
4c<t<00can be evaluated from the slope of, and the parallel offset from a straight line passing the origin with the same slope of the mean curves of Om and Dm in steady state, as is
shown in Fig. 3.
Dm., may, however, besomewhat modified at the next step of
cor-rection.
Now putting Ocorromed and Aorremcd into Eq.
(4), we first get
Ye(o). This Ys(0) shouldsatisfy the equation that
Yeco) =sbco 71(thoo Oo ). ( 6 )
This requires some adjustment of Dm., which at the same time also causes some change in the value of Ygo).
Eq. (6) is introduced by integrating Eq.(1)
from t=0 to co, taking the residual turning
rate Om and the initial yaw-rate Oo into
account. The relation that Yeco)= K is also considered.
2. Sinusoidal Steering
Taking a periodic rudder movement,
30 COS cort
where do denotes the half amplitude of rudder motion and (0,..247; the frequency, being the period.
Eq. (2) gives us the steady state motion of a ship induced by this steering as follows;
si;=I Y.(i(0,)1 ao cos {fort+ Arg Y;(imr)}.
It
is then obvious that measuring the
amplitudes of yaw-rate and rudder motion on a sinusoidal steering experiment provides 178(iar,)1 and the phase lag of yaw rate after rudder angle, Arg Irs(icor).
This type of experiment is only practical for rather high frequencies because a vast extent of testing water would be required at low frequencies. It
is thus reasonable to
choose the parallel shift manoeuvre to define Y,(ia)) at low and intermediate frequencies and the sinusoidal steering, at high frequencies.In order to perform the sinusoidal steering
experiment in a towing basin, the model
launcher mentioned at 1.2 is conveniently
A New Procedure of Manoeuvring Model Experiment
M. P.: Model Point, S. P.: Ship Point
117
used;' accelerating the model With the towing carriage in the same manner as previouslY
mentioned, but keeping the rudder at the
extreme position of the sinusoidal motion namely 50, either to -starboard or port. As
soon as the model halbeen set free from the carriage, a microswitch fitted oil the towing
guide automatically turns on the periodic
rudder movement which is produced by a
scotch-yoke mechanism built in the steeringgear. R h
This procedure iOlies to commence the
periodic steering e a " cosine " phase and
as the result the mean track of the model
becomes parallel to the tank centre-line. A fine, adjustment mechanism for the middle position of rudder swing is advantageous to keep the model track exactly parallel to the tank centre-line, by eliminating miscellane-ous fasymmetric effects.
3. Examples of the Present Procedure with Two Todd Series Models
Table 1 indicates, in the two left columns, the principal particulars of the two 4.5 metre Table 1 Particulars of the Models
f
Present Data Leeuwen equiv. to (132) . Eda Motora Fujin° 60 B 2(158)i (158) M. No.152 M. No.158 70 (152)
Length between Perpendiculars, L(m) 4:5- 4.5 2.258 1.525 1.5251 2.0
Length/Breadth,
a
L/B 7.0 7.5 7.0 7. 0 7. 5 7.Breadth/DT-MirIt B/d 2.5 2.5 2.5 2.68 2.5 2. 5
Length/Drt a
Lid - 17.5 18.75 17.5 18.75 18.75 18.75Block Coefficient, Cb 0.7 0.6 0.7 0.7' O.6 0. 6
L. C. B. from Midstiip, I. c. b. O. 5%f. 1. 5%a. O. 5%f. O. 5%f. 1. 5%a. 1. 5% a.
Radius of Gyration, O. 25 L O. 25 L O. 25 L O. 25 L O. 25 L 0. 20L
Rudder Area Ratio, A R/L d 1/66. 7 1/66. 6 1/67.8 1/62. 5 1/62. 5 1/62.5
Rudder Height 0. 755 d 0. 75-5 d 0. 756 d 0. 750 d 0. 750 d 0. 750d
Propeller Diameter 0. 70 d 0. 666d 0. 70 d 0. 70 d 1 0. 70 d O. 70 d
Propeller Pitch Ratio 1. 10 1.075 1. 10 0. 945 0. 945 1.073
Number of Blades 4 4 4 4 4
Direction of Rotation Right Right Right Right Right Right
Frotide Number 0.2 0.2 0.2 0.2 0.2 0.2
models out of the Todd 60 series, whose
re-sponse behaviour in steering was obtained through the present procedure at the Osaka University Experiment Tank No. 2, 80m x
7 m x 3.6 m. This table also carries the par-ticulars of some geometrically similar models
whose steering characteristics have been
given from the captive model experiments,
Tank Test Frequency Response Analysis Sin Steerin 1.0
I.
K.1.413 T:=3.414 Tir.0.452 T=1.01by van Leeuweno, Eda anp Crane and
Motora and Fujino8) respectively.Figs. 4 and 5 show the results of the
analysis in the form of a Bode diagram, the abscissa representing loglow' and the ordinate logiol Ysi(ial)1 and Arg Yial) respectively.
w is the freqnency of the harmonic com-ponents contained in ship motion and rudder
Fig. 4 Steering Transfer Funtion of M. No. 15ias obtained by Frequency Response Experiment
M.No.152 Tank Test
°Z. W
Experiment
Linear Analysis with no regard to cu-dependence
Fig. 5 Steering Transfer Function of M. No. 159 as obtained by Frequency Response Experiment
A New Procedure of Mano movement and 175(i0)) the transfer function in steering, I It3(i0))1 being amplitude ratio of the
harmonic components of ship motion to that of rudder movement and Arg Ys(iw), denoted as 07 in the figures, the phase difference be-tween the two.
nI'= ) and 17.'(io,')=Ys(i0))/
are the non-dimensionalequivalents of a, and Ys(ico) respectively, where V denotes forward speed and L ship length.
The larger points indicate the results of
harmonic
analysis on the
parallel shift manoeuvre. A number of repeated experi-ments have resulted in some scatter seen inthe figure, from which we can say that
the repeatability of this procedure is rather fair.The result of the .harmonic analysis of the parallel shift connects reasonably, with the result of the sinusoidal steering experiments, which is indicated with smaller points.
At the high frequency range where logiom' >0.3, the harmonic analysis is less
reli-able and tends to result in bad scatter, as
just a small amount of such a high
fre-quency component is contained in the ship motion and rudder movement. The sinusoidal steering should then 'called upon to define accurately 11,(ia)) in such a high frequency range.
Refering to Figs. 4 and 5, 17,(ico) obtained from sinusoidal steering with frequencies for
which logia>0.5 shows a particular
be-haviour against 01. This behaviour can not be interpreted with the transfer function of the form of Eq. (2) with any constant K, T1, 7'2 and T3.Indeed the same tendency is
found for the Ys(ico) computed from
frequency-dependent K, T1, etc. at very high frequencies,
which have been given by van Leeuwen,
using the forced yaw experiment for 2.2
metre model of the same 60 series formo.It
is therefore concluded that the particular ten-dency of 11;(i(0) at very high frequency results from frequency dependence of thecharac-teristic constants K, T1, etc.
euvring Model Experiment 11
In
I
carryijig out the sinusoidal steering, the rudder 11jIL amplitude is choosen to be 4° for log (0'.0 0.3, 8° for log 0,'=0.3-05, and 16° and 32° for log 0/.0.5-1.0, in order to keep the yaw amplitude small enough to suit the linear analysis, yet not too small to cause in accuracy.
In order to examine the tank wall effect a series of sinusoidal steering experiments
for the same models were performed on a
wide, open-air basin. The comparative studyshowed that the wall effect was not
signi-ficant in this case, that .is, 4.5 metre model at a reasonable forward speed in a 7 metre wide towing tank.
in
4. Determing K, T1, T2 and T3
A
The harmonic analysis on the parallel shift manoeuvre gives, together with the results
of a series of sinusoidal steering
experi-ments, the transfer function
17,(iw)at all
significant freqencies. This gives a complete description of the response behaviour of a
ship in steering, that is to be used in the
analysis and synthesis of course-control. It will be sometimes convenient, however, to use the constants K, T1, etc., which are
the coefficients of the transfer function,
instead of a complex function Y3(ini) itself.These constants can be determined by
apply-ing a
" curve-fitting " procedure to Ys(ia,obtained from model experiment.
At very high frequencies, the aforemen-tioned frequency dependence becomes
pro-minent. From the viewpoint of describing
the response behaviour of a ship in course-control, however, this frequency dependence
is not of great importance, because very
little high frequency harmonic component is contained in any real ship motion and rudder movement.We can thus take Ys(i0) obtained at the low and intermediate frequency, say logiow.
= and determine the characteristic constants which represent the response be-haviour of a given ship except at very high frequency motion.
non-dimen-sional equivalent,
/f1(1 +la,' T3')
YsVal)
.(1+1w' Ti')(1+ icy' 7y) where ys, ys
i( V
/( V
L L=
1 (1-7)
and 2, 3= V Ti, 2, 3,V being the forward speed and L ship length. From this equation we get
7.2'+ T2' 1
K' lYs'r x
(al T3' cos Arg Arg Ys')
7'2' T2' 1 1
K' co" w"1 1's' x
(alTs' sin Arg Ys' + cos Arg Ys')
(8 )
This pair of equations can be made at every w', the unknown quantities being K', T1', 7'2' and T3'. Any two pairs of these equations made at two different d could define these unknowns in principle. A more practical and reasonable way is to apply the least mean square methods to a number of pairs of the equations set up at the same number of co, properly distributed over the low and inter-mediate frequency range.
In Table 2,
the right upper columns,
K, T1,
etc. obtained through the present
approach for the 4.5 metre 60 series models are listed. The Ti' and T3' shown are determined by the least mean square method applied for the CO range where loglool= 1.00.3. K' is seperately obtained at the final
stage of correction stated at 1.3.
The solid lines in Figs. 4 and 5 indicate
the I Ys' (la/)j and Arg YAiol) computed with these K', T1', etc.,
fitting well with the
Ys'(ico') points obtained from the harmonic
analysis of the parallel shift and the
sinu-soidal steering, except at the very high fre-quency range.5. Comparative Studies of the Present Results
With Other Data
5.1 Comparison with Turning and Zig-zag
Test Results
Figs. 6 and 7 indicate the results of steady
turning and spiral tests, and Figs. 8 and 9
zig-zag trial results of the same 4.5 metre models. The experiments were carried out at the Osaka University Manoeuvring Ex-perimental Pond, using the radio-controlled, free-sailing model technique.
The index K' at an infinitesimal motion, as extrapolated from the spiral and zig-zag
test results in the manner shown in the
figures, agree fairly well with K' derived
from the harmonic analysis of the parallel shift motion. 0.5 0.4 0.3 0.2 0.1 !,40-30 -20' -70' 0,3 0.2 0.1 -40' -30* -20' -10*
Fig. 6 Turning Test Results of M. No. la
0.5
Fig. 7 Turning Test Results of M. No. 15
o./ 10* 20' 30' 4(
M
1=FA NV 0.2 0.3 0.4 0514i
r.zocoir
r
r'
0.05 0.10 015 0.20
Fig. 8 Z-Test Results of M. No. 1
2 11(
2
A New Procedure of Manoeuvring Model Experiment
0.0.5 0.10 0.15 0.20
Fig. 9 Z-Test Resu ts of M. No. 151 On the other hand, another index T' at an infinitesimal motion from the zig-zag test is much less than T' obtained from the present approach with the assumption that T= T1+
7'2 T3; the former is roughly as much as
70% of the latter. It should be remembered however that the assumption T= T1+ n- T3may not be totally correct.
At the same time one can argue that the ship motion on the parallel shift and sinusoidal steering is not exactly infinitesimal. The root mean square value of the non-dimensional yaw-rate,
on the first two swings of
parallel shift is in this case approximately 0.04 and at the later stages, much less. The K' and T' at rmi=0.04, as derived from the spiral and zig-zag tests, are also indicated in Table 2.
5.2 Comparison with Captive Model
Experiments
The same ship forms of the Todd 60 series
/21
that were used in the present survey had
been tested with the captive model technique by a number of authors'', 43.'', to yield the values of the hydrodynamic derivatives. The constants K, T1, etc. can be simply calculated from these derivatives for each case and they are also listed in Table 2. For the forced-yaw results, the derivatives at (0=-0 are used to compose K, T1, etc:.cApparently there is still some inconsistanc-19 in results among different models, which may be caused partly by difference in model size, propeller loading and also relative rudder size (cf. Table 1). It seems, however, that as for the two domi.-nant constants K and T1, the different ap-proaches with different model size give roughly similar figures. On the other hand, T2 and T3 given from the present approach seem to be too large, compared with the ones from captives model experiments.Recalling here how T3 is composed of the hydrodynamic derivatives'), we get
Ya
in' +mu' T3 ' Yfii )
Determining Y/, N A', "17,;' and Na' from the
oblique tow experiment for the same models
+my' are derived using this
equation utilizing T3 which is already determined m'+;ny' thus obtained is indicated in Table 2 at the columns of the present data.These values of the lateral virtual mass
are unreasonably large and therefore we areforced to conclude that the
T3' obtained through the present procedure is too large.As an alternative approach, we may
( 1 ) first determine Ta' from in' ± u
estimated and Ili', N,', Yo' and Na' pro-vided by the oblique tow and
( 2 )
then determine K', T1' and T2' from
11;(i0/) derived from free model results using Eq. (8).
The dotted lines in Figs. 4 and 5 indicate
the Y
) Composed of K', T1, etc. thusdetermined. In this way a reasonable value
of T3' is given, but the simulation of the
Ys(i0) obtained becomes worse in theinter-mediate frequency range, as shown in the
*: Unreasonably large, cf. Sec. 5.2.
PMM: Planar Motion Mechanism. RA: Rotating Arm.
figures.
This paradoxial results will need
further studies, while it is of the first
im-portance from the standpoint of
course-control to determine the transfer function
Y g(i co) at all significant frequencies, with less
regard to evaluating each individual coef-ficient, K', T11, etc.
Acknowledgement
The experiment involved in this paper was 'Carried outas graduation work at the Osaka 'University by Mr. H. Kashima and Mr. 0. Yamamoto in 1968 to 69. Thi4
acknowledge-ment is made for their contribution in this work.
References
1). K. NOMOTO et al.: On the Steering Qualities
of Ships, J. Soc. Nay. Arch. Japan, Vol. 99,
101, (1956-57), English version published in
International Shipbuilding Progress, (1957).
K. NOMOTO: Directional Stability of
Automa-tically Steered Ships, J. Soc. Nay. Arch. Japan,
Vol. 104, (1959). English version published in
DTMB Rep. 1464, (1960). on the,
S. MOTORA and M. FUJINO: Measurement of
the Stability Derivatives by Means of Forced Leeuwen
PMM
Eda & Crane .
RA Motora& Fujino Present Data -Remarks for Present (152) 70 (152) 60B2 (158) PMM(158) M. No.152 M. No. 158 Data 1.11 1.60 1.12 K' 1.26 1.41 2.80 3.60 2.59 3.12 Ti' 3.12 3.41 Freq. 0.31 0.30 0.23 0.09 Ti' 0.52 0.45 Resp. 0.71 0.70 0.66 T3' 1.33 1.01 (1) 2.40 3.20 2.21 T' 2.30 2.85 rm.' K' 0 1.24 1.43 0.04 1.07 1.08 Zig-Zag. T' 0 1.56 2.00 0.04 1.33 1.39 K' 0 1.29 1.41 0.04 1.14 1.15 Spiral 0.388 0.324 0.270 0.330 Yp' 0.339 0.318 Oblique 0.100 0.104 0.108 0.115 Np' 0.091 0.099 Tow 0.037 0.052 0.046 - Ye' 0.052 0.042 0.019 0.025 0.022 No' 0.024 0.021 (2) 0.401 0.380 0.330 0.335 ne +mi,' 0.718* 0.523* 0.0213 0.0237 0.0215 0.0104 /2-1-../Y 0.023 0.023 Derived 0.133 0.125 0.078 0.107 nz'± tn.' - Y, 0.040 0.061 from 0.060 0.066 0.067 0.060 - Nr' 0.041 0.043 (1)± (2) 0.0125 0.0125 0.0100 0.0064
Il
0.0125 0.0100A New Procedure of Manoeuvring Model Experiment 123
Yawing Technique, (written in English), J. Soc. Nay. Arch. Japan, Vol. 118, (1965).
4) G. VAN LEEIJWEN: The Lateral Damping and
Added Mass of Horizontally Oscillating Ship.
model. Tech. University Delft, Pub. No. 23,
(1964).
5) H. EDA and L. CRANE: Manoeuvii-trg
Charac-teristics of Ships in Calm Water and,j,ii Waves,