VPCH1EF
Lab.
Technische Hogeschaol
y. Scheepbouwkunde
STABILITY ANALYSIS AND PREDICTION OF PERFORMANCE FOR A OFOIL SAILING BOAT
PART 2 DYNAMIC STABILITY ANALYSIS
Yutaka Masuyama
Kanazawa Institute of Technology
SUMMARY
A dynamic stability analysis for a hydrofoil sailing boat
has been carried out on the boat with two surface-piercing dihedral front foils and an inverted "T" rear foil. The small-disturbance theory was applied to the analysis with accounting
for the interaction between the longitudinal and lateral motions.
Stability derivatives were calculated for the hydrofoils and the
sail. As a result of the analysis, it was clarified that there
was a critical sailing state for the maximum attainable boat
velocity which was lower than that of the conventional
predictions for the hydrofoil sailing boat. When the velocity exceeded the maximum velocity determined as the critical sailing state, the boat fell into static instability or divergence.
i INTRODUCTION
r
is essential to conduct a dynamic stability analysis, because the
boat is balancing with dynamic lift force on the hydrofoils.
Although the dynamic stability analysis has already been
conducted by Kaplan et al? for a powered hydrofoil craft, there
is little information about the analysis available for the case
of sailing boat. The motion of the powered craft can be analyzed through classifying into longitudinal and lateral directions because the craft is symmetrical with respect to the centerline
with advancing straightforward at equilibrium state. However,
for the case of the sailing boat the dynamic stability analysis
must be conducted with accounting for the interaction of the
motions in a longitudinal
and
lateral directions.2)
In the present paper as a succession of the part i which presented an estimation method of the equilibrium state and the
high velocity sailing characteristics with foil-born mode, the
dynamic stability for a hydrofoil sailing boat is examined. For the examination, the stability derivatives for sail were obtained
by partially differentiating the aerodynamic forces acting on it,
and those for the hydrofoils were calculated using the procedure proposed by Kaplan et al? The results of analysis were then
confirmed by the numerical simulation conducted using non-linear
equations of motion.
2 LINEARIZED EQUATIONS OF MOTION AND CHARACTERISTIC EQUATION
The motion of hydrofoil sailing boat referring to the body
axes is described by the Euler's equation as follows:
m(LQW-RV)
X,
f RU - PW) Ym(W4 PV -QU)
ZIII k- í
k+PQ -QR( !
) K 1yyI( R2 P2)
RP( 1zz Mi k-
(t'- QR)
- PQ( I- J, )
N.,The Euler angle rates are also given by
0
P+(Qsinø+Rcosø)tanø,
e
Qcosø--Rsinø,
1(Qs:nO-1-Rcosø)sec&
From the results of equilibrium sailing state analysis, it was
indicated that the angles of pitch, heel and leeway were
relatively small, especially in pitch. Thus the perturbed equations of motion can be reduced from the Euler's equation as
follows:
m (ü+qw,-rv0)
4X-mg
m (ü+r uo- Pw,)
4Y+mgcos'bo,
rn (th±pv,-qu0)
iZ-mgçbsinc/i0,
Irr blzr 7
4K
=4M,
1zz t Izr j'4N.
In the equation the symbols with zero suffix indicate the values
in equilibrium state, and the symbols without suffix for
velocities (u,v and w), angular velocities (p,q and r) and angles and O ) indicate the deviations from their equilibrium
respectively.
Since the sailing boat runs usually accomodating with
sideslip and heel, causing that aerodynamic force on sail directs
differently to the advancing course, the deviations in any
directions affect simultaneously on both motions in longitudinal
and lateral directions. From this aspect, it is required to
carry out the stability analysis using all of the formulae in
Eq.(3). The motion around z axis, however, would not be affect
for the dynamic stability analysis, although it should be treated in the course stability analysis. Thus the last formula in
Eq.(3) and the terms of r and i' are eliminated. As
consequence, the linearized equations of motion can be expressed
by the following Eq.(4).
m(ú-qw0)
4XmgO,
m (f3 pub)
4Y±mgcb
m(th+pvo_qu0)4Zmgct4)o,
4K,
I0q
4M.
The angular velocities are also reduced to çt p and q. The velocity of the C.G. in the true vertical direction is then
expressed as follows:
w - u0 O + y0
(5) The perturbed force along x axis is expressed in terms of derivatives as
4X-Xu+Xvv+x+xww+xthw+x+xP+x.
(6)+ XeO + XqO+ XO+ X,, h
(4)
-: u, eAt,
e',
u V1 e2', w w, e",
O
O e,
h -- h, e2'Substituting these expressions into Eq.(7) and cancelling throughout by et , we obtain the six simultaneous equations:
(mA -
X)
u, - (XA + X,,) V, - (X,, A +X)
w -
(XA2 + Xp 1 +X) I'i+ { -XA +
(mwo-Xq) 2+
(mg-Xe) } O,-X h,
O,(Y 2
YqA+ Y6) OlYh h, = O,
-Zu,- (Z;A+Z,)v,+ { (m-Z)A-z}w,+ { -ZA2±(mvo-Zp) A + (mg0-Z) } i
_{ZA2+(muo+Zg)A+Zo}0I_Zhh,O,
-Kku,- (K;A+K,) y,- (K,A+K) w,+{
_(KA2+Kq1±Ke)OI_KAhIO,
-M u, - (M;A +1v!,) y, - (M,A ±M) w,
- (MA2 +MA +) (/),
+ { (¡y,, M) 22 Mq A -M6 } 0,- MA h, = O,
-w,-v0,+u00,+A h,
O(7)
(9)
zIY, 4Z, ¿1K and 4M are also expressed by similar formulae as
Eq.(6). Substituting these expressions into Eqs.(4) and (5), we can rewrite the linearized equations of motion as follows:
,nù+mwoO+mgô Xu--XVX;V-XwW-Xsi,W
xX-
xb
X80-X0-X0Xh
O,mv - mw0
- mgçb - Y, u -
Y,v-Y; b - Yw - Yb
-
Yp _ Y Y6 0 Y OY 0 -
Yk h O,mw + mVO4 mu0O + mg'0l'
_Zu_Z,V_ZZwWZc,W
Z_ZpZZe0ZqÛ
Z0-ZhO,
- K u - K, u
K,i' -
w - K,, t-KK-K KoOKq0K0K=0,
Ô M, u M, u - M, b -Mw -
M,th-M' -M -M
-
0- MQO -MO-Mh
= O, - W + - V0 = OSince the equations of motion are linear, their solutions can be expressed as follows:
}
r
Now we have the stability determinant as,
above equation.
A' + ¡7 A7 +
f6 16 + f A +f4 A
+f3 A3+f2 A2+f, A+f0 -
0 (11)The necessary and sufficient condition to make the solutions stable is determined by either applying the Routh's discriminant method to the coefficients of Eq.(11), or solving Eq.(11)
to find directly the roots without positive real parts.
3 STABILITY DERIVATIVES
3.1 Derivatives of Hydrofoil
The results of equilibrium sailing state analysis indicated
6
mA-Xe
-
XA - X -X,,A -X,, -X622 - X,,2 - X XA2 + (mw0Xq)A-+ (mg-Xe)
-
(m-)A-y
-Y,,A-Y-Y6A2-(mwo±Yp)A -A2-}A-Y
- (mg+ Y)
-Ya,
Z62 -Z
(m-Z)A-Z
-Z,A2 + (mv0-Zp)A-ZA2 -
(mu0f Zh+ (mqo-4)
-z8
0(10)
-K
K-K
-K,-K
(I-Kt)A2-KpA
K22KqAK8
-KA--M
-MA-44
-MthA-M-M.A2-MA-M
(J-M)A2-MA
-MA -M80 0 -1
-y0
u0 1that the leeway angle was relatively small. Hence we may follow
the calculation procedure of Kaplan et al'?
for the stability derivatives of each hydrofoil. Formulae for the derivatives
are
described in the Appendix using the
hydrodynamic forces. The derivatives of the force acting in normal direction to
the
hydrofoil panel, F3, , are resolved into y and z directions as
F,
r,
(i- 1--4)
T 11 COS ï',
(12)
where [' is a dihedral angle of the foil
and jz u, y, w, p, q, ,
, h,
ì,
w,and ¿. Consequently, the derivatives of foil
system for the forces X, Y and Z are obtained as,
x1=x,
Y,==>y,j,
(13)The derivatives for the moments K and M with respect
to u,
y, w, p, q, sr, j and
¿i are calculated as
K =
(z,,
y, - y, ,)M,= (X1 , - Z11 X,)
and considering the difference of application point of
perturbed forces which are caused by the change of both submerged area and depth of submergence, the moments with respect to
,
and h are
also calculated as
K, y, - Y,j z,) + (ze,, y,1
-
Y1M1 =
(x1,
z -
z,
x) +
(xi,1z,, - Z,,, z,,)
} (14)
}
3.2 Derivatives of Sail
Since we may take both '' and to be zero in the equation
for the velocity components of the relative wind for the sail
which is described in part 1, the equation can be simplified as
follows:
(JA = U + U5 COS T
VA = V + (iST Sin 7- COs 0,
W = W - UST Sin T.. sin ø
Among these components we may neglect the value of WA , because of
its relative smallness and its irrelevancy with the sail
performance. Then the relative wind velocity, U , and relative
wind direction, (3 , are expressed respectively as follows:
= u+
V2= (U+U5
cos r)2 + (V+U- sin r7 cos
Ø)2= sin' (VA/USA)
V + UST sin Yr COS 0
tan () = tan
(U+UST Cos YTThe aerodynamic forces, X and Y , are calculated by the
following relationships:
where
X5= P0U1, C5A/2
YS= PaU Cy5A,r/2
8
} (19)
cxS= Cils
cos 8A+ CL$ sin ß(20)
Cils Sfl 11A CLS COS 13A
}
The derivative of X with respect to u is
a x5 a x a x a u a x5 BA
-
au -
U5,, OUaBA au
Upon partially differentiating both sides of Eqs.(17) and (18) by
U, we have
OUSA
ÔU -
UA COSBAOBA V4 SÍ71BA
OU
U2
USASubstitution of Eqs.(22) and (23) into Eq.(21) yields
ac55
Xus = Po USA
(2
C5 cos-8 BA sin BA)
Furthermore, from Eq.(20) we have
ac5
ac
cos BA+ COS Sifl BA
aBA
a CLX
a BA B + CLS COS BA
6CDS acLS
aBA a9A SU2 BA COSCOSBA 011A COSBA+ CLS Sifl BA
Finally substituting Eqs.(20) and (25) into Eq.(24), we obtain
X5 POuSAAS{_2cQ5cos2BA+
+C)
COS BASÍfl BAa CLS
- ( a
BA + CO5) sin2 BASimilarly, the derivatives of Y with respect to u is given as
aC5 = Pa USA A5 { - 2 CLS COS2 BA ( BA
-
Cos) cos BA St BA ( +Cu) Sin2
BAL
The derivatives of Xsand with respect to y are obtained in a similar way as follows:
(aCDS aCLS
Xr5 = p USA A5 { - a
ßA
C1)
COS2 í
+ (
- c)
cos 13A Sifl IA+ 2CLS Sjfl2 lIA
a c
Y,S= ßaUsAs {_
(S
± c)
cos2ß-
aj,
+ CLS) cos lIA Sin lIA_2Cstn2lIA}
The
(Cs
/òßA)
and (C5 /ø) in the above equations
correspondto the slope of the lines representing the relationships of C and C versus attack angle of the sail indicated in Fig. 6 of part 1.
The derivatives of X and Y with respect to p and q are
obtained as follows:
xps=xv5z5,
Yps--Yvszs (30)XqsXus Z YqE =YuS Zs (31)
where z5 (negative value) is coordinate for C.E. of the sail. In the same manner the derivatives of moments Ks and M5 are given as follows:
K5 = -
Y,45 zs, M5= X1s Zs (32) Krs = - Yv5 Zs. Mrs = X5 zs , (33) K5 = Y5Z,
M5 = - X, z , (34) Kqs = - Y5 M45 =X5 : (35)lo
The derivatives of Z are assumed to zero because of
negligible influence of the sail force on the motion in the
direction. Consequently, summing up the derivatives of
hydrofoils and sail, we obtain the total stability derivatives
of the boat, where the derivatives of aerodynamic force on the
hull were not taken into account because they are considerably smaller than those for the sail.
4 RESULTS OF STABILITY ANALYSIS
The dynamic stability analysis was performed in all of the
possible equilibrium sailing state as a function of sail trim
angle, E. . Table i shows an example of the calculated derivatives
for the hydrofoil and the sail in the dimensional value for the
case of UST= lOm/s, ITZ 90° and E. 25° . The submerged length of
front starboard and port foils are 0.30 and 0.79m, respectively.
The derivatives of the front port and rear foil are dominant among those of hydrofoils, because these foils have larger submerged area than the others. It also can be seen that the derivatives of the sail occupy the large portion to those for the
force X and the moment K.
The Eq.(l1) are solved using Bairstow's method. The
examples of the root locus diagrams for the cases of U51- 10, 14
and 18m/s at E 90° are shown in Figs. 1, 2 and 3 respectively. The simultaneous movements of the eight roots are represented
with decreasing the E. , and the corresponding variations of
sailing state parameters have already been illustrated in Figs.
low, the real parts of all roots are negative and the movements
of them are relatively small. With decreasing the E the
movements of the roots become large gradually, and then one of
them on the real axis becomes positive at 20°, 30° and 38° for UST
= 10, 14 and 18m/s, respectively. This means that, regardless of
wind velocity, the boat falls into a static instability or divergence at small E which yields high velocity. As mentioned in part 1, it should be noted that the boat becomes unstable when the submerged length of starboard (windward) foil, Jr-, , becomes
smaller than about 0.lm, although the equilibrium equations can be solved until LF, becomes to zero, i.e. taking off from water
surface.
Figure 4 is polar diagram which compares the boat velocity
at the limit for stable sailing determined by the present
analysis (solid curve) with the highest velocity derived by the
equilibrium equations (dot-dash-curve) for UST 10, 14 and 18m/s. Each shift of the solid curve from the dot-dash-one is shown by the shaded zone where the boat is actually unstable although the
equilibrium equations give some solutions. It appears that the conventional performance prediction through the equilibrium equations results in the over-estimation by 5 to 10% for the
maximum attainable velocity. Dotted curve in the figure shows
the stability limit derived by the calculation excluding sail
derivatives for each wind velocity. Comparing the curve with that for including sail derivatives (solid curve), the latter is shifted to higher velocity side than the former by about 5% for the cases of U3-1-= 14 and 18m/s although both curves almost coincide for
UT=
lOm/s. According to the result of analysispresented in Fig. 4, the sail has the roles not only as the
thrusting device but as a stabilizer at high wind velocity.
5 NUMERICAL SIMULATION USING NON-LINEAR EQUATIONS OF MOTION
In order to confirm the validity of both linearization of equations of motion and calculation of the derivatives described in the previous sections, the motion of the boat was simulated numerically using non-linear equations at the same condition in
which the dynamic stability analysis was conducted. The
simulation was carried out under the five-degree-of-freedom
(with O ) with fixing the rudder angle to the equilibrium
state value by applying the Runge-Kutta-Gill method. The forces and moments for Eq.(1) are calculated by the following procedure.
First, the length and depth of submerged part of hydrofoils at
any moments are determined from the contemporary attitude of the
boat, Then, velocity components for the center of submerged part
of each foil and C.E. of the sail are calculated as
U = U +
Qz, -
Ry, = V + Rx, - Pz1 = W + Py, - Qx1Since attack angle of each part can be obtained from these velocity components, we have the forces and moments using the
formulae described in part 1. Where, the added mass effect of
the foil was also included for the motion normal to the foil
panel. The applicability of the calculation method for the
hydrofoil system was confirmed through towing tank test including
regular wave conditions.
The simulation results for E- 30° , 25° and 20° under the
wind condition of UCT lOm/s and 900 are shown in Figs. 5, 6
and 7 respectively. For roll disturbance of p -0.5rad/s at
t 5s, the time dependent fluctuations of , , and U of the
boat were illustrated in the figures. In accordance with the
results of dynamic stability analysis, these parameters
representing the motions of the boat fluctuated without
divergence for 30° and 25°, whereas for 20° they varied
abruptly with followed by the immediate capsize of the boat.
In Fig. 5, for 30° , the fluctuations damped rapidly and
the boat exhibits high stability. Since the nearest complex eigenvalues to the imaginary axis indicated in Fig. i are -0.887± 2.672j, the period and the time to half amplitude of the fluctuation are 2.35 and 0.78s respectively. These values agree well with the simulation results.
Figure 6, for= 25°, indicates that the initial fluctuation
damps moderately, but the fluctuation continues with constant
amplitude. Since it is apparent from the simulations with
various values of rudder angle that the amplitude of the
fluctuation is sensitively affected whereas the period of the
fluctuation is unaffected by the angle, the continued fluctuation observed in Fig. 6 can be considered as so-called self-excited vibration due to the deviation of the value of rudder angle from
its equilibrium one. The occurrence of the
self-excited-vibration-like fluctuation is a signal of approaching the
critical sailing state. The nearest complex eigenvalues to the
imaginary axis for this case are -0.496± 2.890j, giving the
period of fluctuation of 2.17s, although the period derived by the simulation is 1.4s. This discrepancy seems to be caused by the enlarged non-linear effect due to decrease in the foil
submerged length which is used for the calculation of
hydrodynamic force.
The simulation was also conducted at the condition without initial disturbance to clarify the instability of the boat for
£= 20° as shown in Fig. 8. At this value of , the boat tends to
heel to leeward side and capsizes without disturbance as same as the case of Fig. 7. The and change monotonously in Fig. 8, which apparently corresponds to the static instability determined
by the dynamic stability analysis. The eigenvalue on the real
axis is 0.767 in this case, giving the time to double amplitude of 0.90s, which agrees well with the simulation result in Fig. 8. Consequently, the numerical simulation with the non-linear equations resulted in the confirmation of the validity of dynamic stability analysis. Through the calculation and the numerical simulation conducted in the present study, an useful method to design the high performance hydrofoil sailing boat was developed.
6 CONCLUSION
As a succession of part 1, the method of dynamic stability analysis for a hydrofoil sailing boat was presented. Since the
motions of the boat in longitudinal and lateral directions affected each other for the sailing boat, the dynamic stability
was examined with accounting for their interaction. Stability
r
the aerodynamic forces acting on it, although those for the
hydrofoils were calculated using the procedure proposed by Kaplan
et al.
The dynamic stability analysis was performed in all of the
possible equilibrium sailing state which had been presented in
the part 1. The results of analysis indicated that, at higher
velocity the boat fell into a static instability or divergence
with limiting the maximum attainable boat velocity. It was
clarified that the unstable state was occurred when the submerged length of windward foil became smaller than about O.lm, although the equilibrium state could be obtained until the length becomes to zero, i.e. taking off from water surface, for the conventional performance prediction without incl'uding the stability analysis. Thus it became apparent that the conventional prediction gave the over-estimated value for the maximum velocity. It was also clarified that the sail worked as the stabilizer of the boat at higher wind velocity in conjunction with its original role as the
thrusting device. The validity of the results of dynamic
stability analysis was confirmed by the numerical simulation using non-linear equations. Throughout the present study one of the useful methods for designing the high performance hydrofoil sailing boat was provided with adequateness of the calculation in the stability analysis.
NOMENCLATURE
As sail area
CD, CDS drag coefficients of hydrofoil and sail
CL, CLS
lift coefficients of hydrofoil and sailc chord length of hydrofoil
D, Ds drag forces acting on hydrofoil and sail
F hydrodinamic force acting in normal direction to the
foil panel
g acceleration due to gravity
H vertical height of C.G. from water surface level
I ,I ,I moments of inertia about x, y and z axes
I product of inertia about z and x axes
j unit of complex number (zIi)
M, N moments of roll, pitch and yaw
Ls lift forces acting on hydrofoil and sail
l length of rotating arm of hydrofoil (see Fig. Al)
'F
length of submerged part of hydrofoilm mass of boat and crew
P, Q, R angular velocities in roll, pitch and yaw
perpendicular distance between C.G. and dihedral hydrofoil (see Fig. Al)
U, V, W velocity components of C.G. along x, y and z axes
UA VA ,WA velocity components of apparent wind along x, y and z
axes
UST true wind velocity
U apparent wind velocity (U+Vs+WA2)
VB boat velocity
(JU2+V2+W2)
attack angle in the plane of incident flow of hydrofoil attack angle of sail
angle of leeway
angle between apparent wind velocity and centerline of
boat
P
dihedral angle of hydrofoilT1 angle between true wind velocity and centerline of boat angle of rudder
E. trim angle of sail (angle between boom and centrline of boat)
angle between perpendicular line to the dihedral
hydro-o
foil and connecting line from C.G. to the tip of the foil (see Fig.A1)
angle between perpendicular line to the dihedral hydro-foil and connecting line from C.G. to the surface-piercing point of the foil (see Fig. Al)
root of characteristic equation density of air and water
c, 9,iT angles of heel, pitch and yaw (Euler angles)
(subscripts)
i l; front starboard hydrofoil
2; front port hydrofoil rear hydrofoil
4; rudder =5; sail
C center of submerged part of hydrofoil
REFERENCES
Kaplan,P., Hu,P.N. and Tsakonas,S.: Methods for Estimating the
Longitudinal and Lateral Dynamic Stability of Hydrofoil Craft, Stevens Institute of Technology E.T.T. Report No.691, 1958. Masuyama,Y.: Stability Analysis and Prediction of Performance
for a Hydrofoil Sailing Boat (Part 1) Equilibrium Sailing State Analysis, International Shipbuilding Progress,
Masuyama,Y. Motion of a Hydrofoil System in Waves, Jour. of the Kansai Soc. of Naval Architects, Japan, No.196, 1985. (in Japanese)
APPENDIX DERIVATIVES OF HYDROFOILS
In the case of a surface-piercing dihedral foil (i1,2), the
symbols such as ..4.,
2,i,
R,
and are defined as shown inFig. Al, where the submerged length of the foil, JFL , and
rotating arm length, J, are expressed as follows:
IF:
RF (tan C, - tan C0)
IA:
R (tan C
Ian Co) z 2The values of both ('dCD/&L,) and (CL/di%p1,) are determined using
the calculated values shown in the Figs. A3 and A4 of the part 1.
All of the derivatives of hydrofoils are listed as followings,
where the top of minus-plus sigìi is applied to the front
starboard foil and the bottom to the port.
20
I OC - p,,V8c, { ( aa)' + C01I lF Z = X1,+ X0S1 where, 1 F X,4,= T P,V,Cffic, 000 = ; p y: i c (---2 cos C1 then C0
IF, fCO\
R-= LÇ C, + C,(i = 4)
Xg,
_PVßIc,[2Cz,_((0CD),_C,}X.
cosi',],
(i=I-4
(A-9)
a
pq,
-
PvV8I, C, [2Cr, z,f(L),
+C01}cosr]
(i = I-4)
(A-lo)
due to change of submerged area
due to change of depth of submergence
- 0k' V8 C0
IFt Ci
(i= 1-4)
(A- 1)
=
-x. =
x,
ß., V8 C, c,- -- p
va ¡, cj((4Q-),
- --
p,,V81,, C1-
s.1/a ¡p, c, {(jQ),
(j
I - 4 )
- c, }
s1+ c,,} smi',,
- c
}i
(i
(i
(i
1 4)
I-4)
I 4 ) (A-2) 3) 4) 5)F,, = -
P,,, V ¡Fi c, { + C,,, } COS [' , ( i 1 4 )(A- 6)
= p V8 c ( ( C0),
- cj I ¡.
i : then X, + o. V8c, { (),CLIJR2, (Ian2 C -C,} ¡, z, Ian2C0),(:=l.2)(i=3)
(i
4)(A- 7)
ow V8 c,{ (Ç)1
-O CLi'D' = ßwV8Cj { + CO3} R (Ian2 C, - Ian2 C ),( i = 1.2)
-
o,
(i
3)
(A- 8)
L4 C, { 1,., 8 CL R
= T
cosC,(a
h"
cosC, then X8 p,,V2 Ci ¡ C01 +'1sinI
(i=3. 4) XII = X.18, + Xc,,p where,XII, =
-= -- p,,V2i
xl p.,, V82 C, C, r', ace, =pv
(a
),,,
F6, = CL, 1F, 2 '9CL=2
pV8/
c, '9h ) , Coi +x, =
-
{sin f
9C0= - -- p..v
h I CIÍF= -
.,VJ CisiniI +
'9CL =---- P,.VJIFIcI('9h),
22(i=
1. 2)due to change of submerged area
due to change of depth of submergence
(SCI)
(1=1
4) 2.(i =3)
'5'CL(=
I. 2. 4)(i =3)
--
(SCD(i
= I.
2. 4)
ô h(i =3)
(i
= 1(i
= 3) 2 4) 5h)},
S C0 X, " S h1' 2 } (A-12)where
= k, p, I, c. / 4 , (i i 4)
and k was taken to be 0.9 for calculation.
( EriD)
x,. = x. =
X,, = = o (i = I -4) (A-17)r,
ssn[',F=-rcosfl ,
=T n,
R, (tan + tan C,) / 2 (i = 1-4)(i=1-4)
(i = I 2) (A-18) (A-19)=0,
= m1 z (i=3) (i = 4) (A-20) Fi = ?fl Xir
(i = I 4) (A-21List of Table and Figures
Table 1 Example of stability derivatives of hydrofoils and sail for the case of Us1: lOm/s, T1 900 and F 250
(dimensional value)
Fig. i Root locus diagram for the case of U- lOm/s and T 90°
(dimensional value)
Fig. 2 Root locus diagram for the case of UST: 14m/s and 90'
(dimensional value)
Fig. 3 Root locus diagram for the case of U5-1: 18m/s and : 90°
(dimensional value)
Fig. 4 Polar diagram comparing the boat velocity at the limit for stable sailing with the highest velocity derived by the equilibrium equations
Fig. 5 Numerical simulation result showing the fluctuations of
roll, pitch and velocity for roll disturbance ( E 30°)
Fig. G Numerical simulation result showing the fluctuations of roll, pitch and velocity for roll disturbance ( 25
Fig. 7 Numerical simulation result showing the fluctuations of roll, pitch and velocity for roll disturbance ( a: 20°)
Fig. 8 Numerical simulation result showing the fluctuations of
roll, pitch, velocity and leeway angle without initial disturbance ( E 20°
Fig. Al Definition of symbols for surface-piercing dihedral foils (j: 1, 2)
Table 1 Example of stability derivatives of hydrofoils and sail for the case of UST lOm/s, y= 90° and 25°
(dimensional value)
St. Port Rear Rudder Sail Total
J
(i=1 ) (i=2) (i=3) (i=4) (i5) Dimension
u -1.59 -4.89 -4.23 -1.20 -9.48 -21.39 kgfs y 0.20 -4.09 0.0 0.74 29.08 25.93 m w 0.23 4.88 -0.57 0.0 -- 4.54 p 0.16 -4.96 0.0 -1.31 55.26 49.15 kqfs q -3.21 -12.48 -9.25 -2.11 18.02 -9.03 rad XJ -103.4 131.4 0.0 0.0 -- 28.0 kg! 0 42.1 48.6 0.0 -81.7 -- 9.0 rad h -52.0 -60.0 0.0 -35.2 -- -147.2 kqf/m 0.0 0.0 0.0 0.0 -- 0.0 kgf-s2 0.0 0.0 0.0 0.0 -- 0.0 m 0.0 0.0 0.0 0.0 -- 0.0 kgfs2 0.0 0.0 0.0 0.0 -- 0.0 rad u -6.6 36.3 0.0 6.4 5.7 41.8 kgfs y -26.7 -149.7 0.0 -56.7 -41.9 -275.0 ni w -31.8 178.4 0.0 0.0 -- 146.6 p -22.1 -181.6 0.0 99.9 -79.7 -183.5 kgfs q 13.1 -81.2 0.0 11.2 -10.9 -67.8 rad Y1 -505. -1172. 0. 0. -- -1677. kg! 6 196. -412. 0. 599. -- 383. rad h -241. 508. 0. 258. -- 525. kgf/m ' -0.46 -1.25 0.0 -0.88 -- -2.59 kgf-s2 i -0.56 1.49 0.0 0.0 -- 0.93 ni -0.39 -1.51 0.0 1.55 -- -0.35 kgf-s2 0.45 -1.20 0.0 0.0 -- -0.75 rad u -7.9 -43.2 -1.4 0.0 -- -52.5 kgfs y -31.8 178.4 0.0 0.0 -- 146.6 m w -37.9 -212.7 -515.9 0.0 -- -766.5 p -26.4 216.5 0.0 0.0 -- 190.1 kgf.s q 16. 97. -1199. 0. -- -1086. rad Z1 -601. 1397. 0. 0. -- 796. kgf 0 233. 490. -67. 0. -- 656. rad h -288. -605. -29. 0. -- -922. kgf/m ' -0.56 1.49 0.0 0.0 -- 0.93 kgfs2 r -0.66 -1.77 -4.16 0.0 -- -6.59 ni -0.46 1.80 0.0 0.0 -- 1.34 kgfs2 0.54 1.43 -9.64 0.0 -- -7.67 rad u -5.5 44.0 0.0 -11.2 10.9 38.2 kgf.s y -22.1 -181.6 0.0 99.9 -79.7 -183.5 w -26.4 216.5 0.0 0.0 --190.1 p -18.3 -220.3 0.0 -176.3 -151.4 -566.3 kgf.s.m q 10.9 -98.5 0.0 -19.8 -20.7 -128.1 rad K.1 -518. -2022. 0. 0. -- -2540. kgfm 0 203. -721. 0. 0. -- -518. rad h -250. 890. 0. 0. -- 640. kg! " -0.39 -1.51 0.0 1.55 -- -0.35 kgf.s2 -0.46 1.80 0.0 0.0 -- 1.34 -0.32 -1.83 0.0 -2.74 -- -4.89 kgf.sm q 0.37 -1.46 0.0 0.0 -- -1.09 rad u 3.4 26.5 -11.2 -2.1 18.0 34.6 kgf-s y 26.1 -151.7 0.0 1.3 -55.3 -179.6 w 31. 181. -1198. 0. -- -986. p 22. -184. 0. -2. -105. -269. kgf.s.m q -19. -100. -2800. -4. -34. -2957. rad M.1 300. -936. 0. 0. -- -636. kgf.m 0 -113. -325. -155. 0. -- -593. rad h 139. 401. -67. 0. -- 473. kg! 0.45 -1.20 0.0 0.0 -- -0.75 kg!. s2 0.54 1.43 -9.64 0.0 -- -7.67 0.37 -1.46 0.0 0.0 -- -1.09 kgf.sm -0.44 -1.16 -22.36 0.0 -- -23.96 rad
-20
U5TlO mA
C T 9O0-15
-10
-5
Real axis
Fia.
iRoot locus diagram for the case of
iOn/s and 900 (dimensional value) X
50
O25°
o20°
UST14
fl). C VTg0
X 500 o 350 0o
30
-25
-20
-15
-10
t t u f 0 4airnensionai vaiue
Fig.
2root locus diagram for the case of UST= l4ri/s and
900
Fig.
3
Ioot locus diagram for the case of
UST= l8m/s and
90°
20
VB rn/slo
lo
20 150°stable sailing limit
(including sail derivatives)
do.
(excluding sait derivatives)
highest velocity by the
equilibrium equations
unstable region
90°
Fig. 4 Polar diagrari coraparing
the boat velocity at the 1irit for stable sailing with the highest velocity derived by the equilibrium equations
USI
I O -U51 10 rn,,5
Yî
90 C 30° u F I I I I 20 -5 10 1 3sec 40
Fig. 5Numerical simulation result showing the fluctuations
of
roll, pitch and velocity for roll disturbance
(E=
300)
m5
initial roll disturbance
Po
-0.5 rad/sec (at 5 sec
10-m/5 deg
-ich
-4 ¡'5 PS PSI \ J
\ Iinitial roll disturbance
Po
-o.s rad/sec (at 5 sec
G\f'JV\î'JV
Fig.
6
Nuiierical simulation result showing the fluctuations of roll, pitch and velocity for roll disturbance (= 25°)
-z:: sec 40 30 UST 1O rn/s
'YT9O°
C 25°¡ Ï I 10 20 2S 3G
35SeC4O
Fig. 7Numerical simulation result showing the fluctuations of roll, pitch and velocity for roll disturbance
(E= 200)
Uî :10
/5
Y :90°
C :20°
rn/S 1 Uinitial roll disturbance
Po : -0.5 rad/sec (at 5 sec)
d eg
-rn/S deg
40-
20-o -U511O rn/S T 9O0 withoutinitial disturbance
c I I 0 2 46
810
12
14
16 secl8
Fig. Op
\/ \\
/ / /.A1
port
starboard
Fig. AlDefinition of symbols for surface-niercing dihedral foils (i= 1,