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A study of hydrodynamics of three-dimensional
planing surface
Nan Xie*, Dracos Vassalos, Andrzej Jasionowski
Department of Naval Architecture and Marine Engineering, The Ship Stability Research Centre,
Universities of Strathclyde and Glasgow, Henry Dyer Building, 100 Montrose Street, Glasgow G4 0LZ, UK
Received 6 August 2004; accepted 2 February 2005
Available online 2 April 2005
Abstract
The hydrodynamic problem of 3D planing surface is studied by a finite element approach. The
planing surface is represented by a number of pressure patches whose strengths are constant at each
element. The unknown pressure strength is obtained by using the free surface elevation condition
under the planing surface and Kutta condition at the transom stern. Previous studies indicate that,
when the constant pressure distribution method is used, the number of buttocks should be less than
five or six, otherwise the calculated pressure distribution will start to oscillate and even become
divergent. In the present study, after careful examination of the influence coefficients, it is found that
the accuracy of the influence coefficients matrix is very important to the convergence of the solution,
especially when the number of elements is relatively high. The oscillation of the pressure distribution
can be avoided by constant element method if the influence coefficients are sufficiently accurate. The
predicted results of the present paper with more number of buttocks are in good agreement with other
researchers’. It is concluded that the irregularity of the pressure distribution found in previous studies
is most likely caused by the low accuracy in their calculation of the influence coefficients, not by the
method itself.
q 2005 Elsevier Ltd. All rights reserved.
Keywords: Hydrodynamics; Planing; 3D; Pressure distribution; Numerical prediction
Ocean Engineering 32 (2005) 1539–1555
www.elsevier.com/locate/oceaneng
0029-8018/$ - see front matter q 2005 Elsevier Ltd. All rights reserved.
doi:10.1016/j.oceaneng.2005.02.003
* Corresponding author.
E-mail addresses: [email protected] (N. Xie), [email protected] (D. Vassalos), a.jasionowski@
na-me.ac.uk (A. Jasionowski).
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551540
1. Introduction
The study of hydrodynamics of planing is important for high speed marine vessels. The
hydrodynamic forces on the hull and its appendages developed during forward motion can
be sufficient to support the craft and raise a substantial proportion of the hull out of the
water. The determination of the planing induced hydrodynamic force is an important part
in the analysis of vessel performance.
Early studies on planing problems were seen in the 1930s, but until the 1960s
theoretical investigations were restricted mainly to linearized two-dimensional planing
(Maruo, 1951). The three-dimensional planing problem was tackled in the 1960s, but
always with restrictions on either the planing speed or aspect ratio of the planing surface
(Maruo, 1967; Wang and Rispin, 1971; Shen and Ogilve, 1972; Tuck, 1975). Doctors
(1975) may be the first to study the three-dimensional planing without these restrictions. In
his approach, finite pressure elements were adopted to represent the wetted area of a
planing surface and in an iterative procedure the wetted area was adjusted to satisfy the
trailing-edge Kutta condition until it finally reached a constant, but the pressure
distributions thus obtained were seriously oscillatory. Wellicome and Jahangeer (1978)
and Tong (1989) prescribed the wetted area in advance, then calculated the pressure
distribution and shape of transom. The pressure oscillation, which Doctors found, was
avoided when the number of buttocks was not more than five or six, otherwise it would still
occur. The reason for such oscillation was believed to be the pressure discontinuities at the
side edges of the constant pressure element they employed. To avoid the pressure
oscillation problem, Cheng and Wellicome (1994) developed a pressure strip method, in
which a planing surface is represented by an assemblage of strips of transversely variable
pressure placed on the mean free surface. The pressure oscillatory problem was
successfully removed. More recently, Wang (2003) used linear pressure distribution over
each element with continuous pressure over the length of the planing surface. However,
the solution of the pressure distribution still had oscillatory behaviour, a similar wavy
behaviour of the inversed pressure solution on a flat plate can be also seen in the work of
Tuck et al. (2002).
The constant pressure approach provides relatively simple mathematical formulation
and therefore is easier to facilitate numerical implementations. The authors have applied
this method to the prediction of wash wave field of the Air-Lifted Catamaran (Xie et al.,
2004). The aim of the present paper is to re-examine the application of the ‘constant
pressure distribution’ method in the study of planing hydrodynamics. Within the frame of
linearized potential flow theory, the free surface elevation induced by the planing hull is
represented by pressure distribution over the wetted area. The wetted area of the planing
hull is discretized using a number of rectangular elements over which the pressure
strengths are constant. The induced free surface elevations within the wetted area are set to
be equal to the hull surface vertical coordinates. At the transom stern, the pressure is equal
to the atmospheric pressure, i.e. the planing pressure is zero in order to satisfy Kutta
condition. The free surface depression at the stern will be equal to the immersed depth of
the local trailing edge, which is also unknown. Solution of the linear algebraic equations
will be the pressure strengths on each element and the immersed depth of the trailing edge.
Previous studies indicated that when the number of buttocks was more than five or six,
N. Xie et al. / Ocean Engineering 32 (2005) 1539–1555 1541
the pressure would become oscillatory. Since the oscillatory pressure distribution on the
planing surface has not been supported by model test measurements, it can be concluded
that the pressure oscillation found in previous studies are caused by numerical
inaccuracies.
The elements of the matrix of the linear algebraic equations are the induced coefficients
between control points and the pressure elements. The pressure elements, representing the
planing hull, are deployed on the water surface forming a rectangular pressure patch which
is also moving at high speed, usually the element length based Froude Number
FrZU=ffiffiffiffigl
pO6:0, in which U is the craft speed, l is the length of the element, and g is the
acceleration due to gravity. Therefore, the free surface elevations (or induced coefficients)
are very small within the wetted area range. This requires high accuracy in the calculation
of the coefficients, especially in the cases when the number of elements is relatively large.
2. Mathematical formulation
The planing of a craft at a constant forward speed U on the otherwise calm water can be
equivalently transformed into a stationary planing craft, which is represented by a pressure
distribution, on the surface of a uniform incoming flow with speed U. It is also assumed
that the fluid is inviscid with an infinite depth, and the disturbance to the main stream
caused by the craft is small. The coordinate system oxyz is defined with xoy plane located
at the undisturbed free surface; the xoz plane is the symmetric about the central plane of
the craft; the oz axes is positive upwards and goes through the centre of trailing edge; the
ox axes is positive towards to the bow of the craft. A diagram of the coordinate system is
shown in Fig. 1.
The potential of disturbance should satisfy the following equations:
Laplace equation in the fluid domain:
4xx C4yy C4zz Z 0 (1)
On the free surface the velocity potential 4 and the surface elevation 2Z2(x,y) satisfy
the linearized kinematical and dynamical boundary conditions
U2x C4z Z 0; on z Z 0 (2)
pðx; yÞ
rCg2ðx; yÞKU4x Z 0 on z Z 0 (3)
U
x
y z
oplaning
surface
Fig. 1. Coordinate system.
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551542
on the bottom and far upstream condition
4z Z 0 z ZKN or x ZCN (4)
The boundary value problem (1)–(4) is solved by using Fourier transformation method,
and the following expression can be obtained (Wehausen and Laitone, 1960)
4ðx; y; zÞ Z1
p2rU
ððS
pðx;hÞdxdh
ðp=2
0dq sec q P:V:
ðN
0
k ekz
k Kk0 sec2qsin½kðx
KxÞcos q�cos½kðy KhÞsin q�dk Kk0
prU
!
ððS
pðx;hÞdxdh
ðp=2
0sec3 q ek0z sec2q cos½k0ðx KxÞsec q�cos½k0ðy
KhÞsec2q sin q�dq (5)
where S is the area on which the pressure is applied and k0Zg/U2 is the wave number. The
expression for free surface elevation 2(x,y) can be obtained by substituting 4(x,y,z) into the
free surface condition (3):
2ðx; yÞ Z1
p2rg
ððS
pðx;hÞdxdh
ðp=2
0P:V:
ðN
0
k2 cos½kðx KxÞcos q�
k Kk0 sec2q
!cos kðy KhÞsin q� �
dkdq Ck2
0
prg
ððS
pðx;hÞdxdh
ðp=2
0
sin½k0ðx KxÞsec q�
cos4q
!cos½k0ðy KhÞsec2q sin q�dq Kpðx; yÞ
rgð6Þ
In the present approach, rectangular pressure patches are adopted. Without losing
generality, let S be a rectangular area of length L and width B, which is divided into Nx
elements in length direction and Ny in the beam direction leading to a total of NTZNx!Ny
small rectangular elements. The free surface elevation at jth control point now becomes
2ðxj;yjÞZXNT
iZ1
pi
rg
1
p2
ððSi
dxdh
ðp=2
0P:V:
ðN
0
k2 cos½kðxj KxÞcos q�
k Kk0 sec2q
8><>:
!cos½kðyj KhÞsin q�dkdq
9=;C
XNT
iZ1
pi
rg
k20
p
ððSi
dxdh
ðp=2
0
sin½k0ðxj KxÞsec q�
cos4q
8><>:
!cos½k0ðyj KhÞsec2q sin q�dq
9=;K
pðxj;yjÞ
rgZ
XNT
iZ1
pi
rgDji j Z1;.;NT
ð7Þ
N. Xie et al. / Ocean Engineering 32 (2005) 1539–1555 1543
where Dji is the non-dimensional free surface elevation at field point (xj,yj) induced by the
rectangular pressure element of unit strength at (xi,hi) and can be expressed as (Kim and
Tsakonas, 1981)
Dðxj; yj; xi;hiÞ ZKdji K1
2p2
X8
mZ1
ðK1ÞmC1Re
ðp=2
0
expðik0 sec2qsmðqÞÞ
sin q cos q
!½E1ðik0 sec2qsmðqÞÞK ipð1 KsgnðsmÞÞ�dq
�ð8Þ
where dji is static free surface depression
dji Z
1 ðxj; yjÞ is inside Si
0:5 ðxj; yjÞ is on the boundary of Si
0:25 ðxj; yjÞ is on the corner of Si
0 ðxj; yjÞ is out of Si
8>>>><>>>>:
(9)
smðqÞ Z
ðxj Kxi KaiÞcos q C ðyj Khi KbiÞsin q m Z 1
ðxj Kxi KaiÞcos q C ðyj Khi CbiÞsin q m Z 2
ðxj Kxi CaiÞcos q C ðyj Khi CbiÞsin q m Z 3
ðxj Kxi CaiÞcos q C ðyj Khi KbiÞsin q m Z 4
ðxj Kxi KaiÞcos q K ðyj Khi CbiÞsin q m Z 5
ðxj Kxi KaiÞcos q K ðyj Khi KbiÞsin q m Z 6
ðxj Kxi CaiÞcos q K ðyj Khi KbiÞsin q m Z 7
ðxj Kxi CaiÞcos q K ðyj Khi CbiÞsin q m Z 8
8>>>>>>>>>>>>>>>><>>>>>>>>>>>>>>>>:
(10)
ai, bi are half-length and width of ith pressure element, and E1(w) is the exponential
integral of complex argument, which can be defined as (Abramowtiz and Stegun, 1970)
E1ðwÞ Z
ðN
0
eKðtCwÞ
t Cwdt (11)
There is also a series expression for this integral
E1ðwÞ ZKg K lnðwÞKXN
nZ1
ðK1Þnwn
n$n!(12)
where gZ0.5772156649., which is also known as Euler’s constant.
3. Determination of pressure distribution on planing hull
A pressure element representation of a flat planing hull is shown in Fig. 2. Assuming
that there are Nx cuts in the length direction and Ny cuts in the beam direction, the free
surface elevation at jth control point can be obtained by adding the induced contributions
Spray rootignored
L
B
Fig. 2. Representation of a flat planning hull by pressure elements.
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551544
from all the pressure elements and expressed as
2j ZXNT
iZ1
Dji
pi
rgj Z 1;.;NT (13)
where jZ jy C ðjx K1ÞNy; iZ iyC ðix K1ÞNy; jy, ijZ1,.,Ny, jx,ixZ1,.,Nx and NTZNx!Ny. On the other hand, the body boundary condition requires
2j Z xjxtan t CHjy
j Z jy C ðjx K1ÞNy; jx Z 1;.;Nx; jy Z 1;.;Ny (14)
where xjxis the longitudinal distance from trailing edge, t is the trim angle and Hjy
is the
immersed depth of the trailing-edge for the jyth buttock.
In order to satisfy Kutta condition, zero pressure is assigned for the trailing-edge:
pi Z 0 i Z iy C ðix K1ÞNy; ix Z 1; iy Z 1;.;Ny (15)
Substituting (13) and (15) into (14), the following linear algebraic equations are obtained
XNT
iZ1
D̂jip̂i Z Ej (16)
where
p̂i Z
Hiy
B tan ti Z iy C ðix K1ÞNy; ix Z 1; iy Z 1;.;Ny
pi
Brg tan ti Z iy C ðix K1ÞNy; ix Z 2;.;Nx; iy Z 1;.;Ny
8><>: (17)
D̂ji Z
K1 jZjy Cðjx K1ÞNy; iZ iy Cðix K1ÞNy; ix Z1;jx Z1;.;Nx; jy Ziy; jy;iy Z1;.;Ny
0 jZjy Cðjx K1ÞNy; iZ iy Cðix K1ÞNy; ix Z1;jx Z1;.;Nx; jy siy; jy;iy Z1;.;Ny
Dji jZjy Cðjx K1ÞNy; iZ iy Cðix K1ÞNy; ix Z2;.;Nx; jx Z1;.;Nx; jy;iy Z1;.;Ny
8><>:
(18)
Ej Zxjx
Bj Z jy C ðjx K1ÞNy; jx Z 1;.;Nx; jy Z 1;.;Ny (19)
N. Xie et al. / Ocean Engineering 32 (2005) 1539–1555 1545
Solutions of (16) will be the trailing-edge profile and the pressure at each control point.
In the actual calculation, the surface symmetry is taken into account and only those control
points on one side of the hull will be used.
A number of non-dimensional parameters are used in this study which are defined as:
The non-dimensional pressure coefficient
cp Zp
0:5rU2 tan tZ
2
C2v
p̂ (20)
where Cv ZU=ffiffiffiffiffiffigB
pis the beam Froude number.
The non-dimensional lift force:
CL ZLift
0:5rU2BL tan tZ
PNTiZNyC1 pið4aibiÞ
0:5rU2BL tan t(21)
The non-dimensional location of pressure centre
LCP Z lCP=L (22)
which is measured from the trailing-edge.
4. Numerical methods
Most numerical work is for the evaluation of the induced coefficients Dji in (8) in which
singularities in the integrands and their highly oscillatory behaviour are two main
problems to be dealt with. It can be seen that the integrands in (8) have highly oscillatory
behaviour when q approaches p/2. A commonly used method is to make a variable change
of uZtan q to stretch the dimension in the fast oscillation area. However, numerical tests
indicate that the evaluation of the induced coefficients requires high accuracy in order to
obtain accurate pressure solution. The truncation of the integrals will depend on the vessel
speed, size of the pressure element and location of the control points. In the present study,
the following variable changes are adopted
u Zjgj
sin q
cos2qm Z 1; 4; 6; 7
jdjsin q
cos2qm Z 2; 3; 5; 8
8><>: (23)
where gZgðyjKhiKbiÞ=U2, dZgðyjKhiCbiÞ=U
2, gs0 and ds0. By doing this, the
integrals in (8) become
J1m Z
ðp=2
0
expðik0 sec2qsmðqÞÞ
sin q cos qE1ðik0 sec2
qsmðqÞÞdq
Z
ðN
0
2u eitmðuÞ
4u2 Cg2 K jgjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cg2
p E1ðitmÞdu m Z 1; 4; 6; 7 (24)
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551546
J2m ZKip
ðp=2
0
expðik0 sec2qsmðqÞÞ
sin q cos q½1 KsgnðsmðqÞÞ�dq
ZKip
ðN
0
2u eitmðuÞ
4u2 Cg2 K jgjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cg2
p ½1 KsgnðtmðuÞÞ�du
m Z 1; 4; 6; 7
(25)
J1m Z
ðp=2
0
expðik0 sec2qsmðqÞÞ
sin q cos qE1ðik0 sec2qsmðqÞÞdq
Z
ðN
0
2u eitmðuÞ
4u2 Cd2 K jdjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cd2
p E1ðitmÞdu m Z 2; 3; 5; 8 (26)
J2m ZKip
ðp=2
0
expðik0 sec2qsmðqÞÞ
sin q cos q½1 KsgnðsmðqÞÞ�dq
ZKip
ðN
0
2u eitmðuÞ
4u2 Cd2 K jdjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cd2
p ½1 KsgnðtmðuÞÞ�du m Z 2; 3; 5; 8 (27)
where
tmðuÞ
ffiffiffi2
pau
G1
Cg
jgju m Z 1ffiffiffi
2p
bu
G1
Cg
jgju m Z 4ffiffiffi
2p
au
G1
Kg
jgju m Z 6ffiffiffi
2p
bu
G1
Kg
jgju m Z 7
8>>>>>>>>>>><>>>>>>>>>>>:
(28)
tmðuÞ Z
ffiffiffi2
pau
G2
Cd
jdju m Z 2ffiffiffi
2p
bu
G2
Cd
jdju m Z 3ffiffiffi
2p
au
G2
Kd
jdju m Z 5ffiffiffi
2p
bu
G2
Kd
jdju m Z 8
8>>>>>>>>>>><>>>>>>>>>>>:
(29)
where G1 Zffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffijgj
ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2Cg2
pKg2
q, G2Z
ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffijdj
ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2Cd2
pKd2
q, aZgðxjKxiCaiÞ=U
2 and
bZgðxjKxiKaiÞ=U2. It can be seen that the highly oscillatory behaviour of the
integrands has been eliminated as u/N (i.e. q/p/2). In fact, tm(u)fGu as u/N from
(28) and (29).
N. Xie et al. / Ocean Engineering 32 (2005) 1539–1555 1547
The second problem in the numerical calculations is the convergence of the integrals in
(24)–(27). The integrals have logarithmic singularity at lower limit uZ0. In fact
limu/0
2u
4u2 Cg2 K jgjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cg2
p =1
uZ 1; lim
u/0
2u
4u2 Cd2 K jdjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cd2
p =1
uZ 1
(30)
This singularity can be removed by the following method:
J1m Z
ðN
0
2u eitmðuÞE1ðitmðuÞÞ
4u2 Cg2 K jgjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cg2
p Keitmð0ÞE1ðitmð0ÞÞ
u
" #du
C
ðN
0
eitmð0ÞE1ðitmð0ÞÞ
udu
m Z 1; 4; 6; 7
(31)
J2m ZKip
ðN
0
2u eitmðuÞ½1 KsgnðtmðuÞÞ�
4u2 Cg2 K jgjffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi4u2 Cg2
p Keitmð0Þ½1 Ksgnðtmð0ÞÞ�
u
" #du
K ip
ðN
0
eitmð0Þ½1 Ksgnðtmð0ÞÞ�
udu
m Z 1; 4; 6; 7
(32)
Similar expressions can be derived for mZ2, 3, 5, 8. It can be shown that the second
integral in (31) and (32) have no contribution when they are summarised over all m. The
integrands in the first integral of (31) and (32) are regular at uZ0 (i.e. qZ0). The
convergence behaviours of (31) and (32) at their upper limits are analysed as follows
For large w, the following asymptotic expression can be used (Abramowitz and Stegun,
1970)
ew E1ðwÞ Z1
wK
1
w2C
2!
w3K
3!
w4C/ (33)
Therefore, the first integral in (31) is convergent. On the other hand, the integrand in the
first integral of (32) are oscillatory functions whose amplitudes monotonically decay as
m/N, thus the convergence can easily be achieved (similar to an alternating decay
series).
Another problem should be mentioned in the numerical calculation is that there are
logarithmic singularities in the integrands of (31). In fact, when
q Z q� Z tanK1 jxj KxiGaij
jyj KhiHbij
� �(34)
sm(q)Z0 for some of m 0s and therefore tm(u)Z0, the exponential function E1(itm) in
(31) will have logarithmic singularity, as can be seen in (12). Although theoretically this
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551548
singularity is integrable, in order to get high accurate results, proper numerical integration
scheme should be used.
For the cases of gZ0 or dZ0, one can leave those terms whose sm(q) are the same and
their contributions counteract each other, then the same procedure can be used.
5. Numerical results and discussions
The hydrodynamics of 3D flat planing surface is studied using the above method. The
wetted area is prescribed in advance, the pressure distribution and the transom profile is
determined by constant pressure element distribution method, in which the free surface
elevations at the control points are equal to the vertical coordinates of the local flat planing
surface.
The integrals in the induced coefficients expressions (31) and (32) are truncated at the
upper limits and calculated by using Simpson’s rule of integration. Since J1m usually
converges faster than J2m, the upper limits of integration of J2m should be larger than those
of J1m in the numerical calculations. Fig. 3 shows sample of the integrands after removing
the singularity at qZ0 in the integrals of the induced coefficients. In this example, the
integrand of J13 has a logarithmic singularity at uz4, as shown in Fig. 3a; the integration
around the singularity point will make major contributions to the integral. Therefore,
-0.60
-0.50
-0.40
-0.30
-0.20
-
0.00
0.10
0 2 4 6 8 10u
f1
m=8
m=3
-0.9
-0.6
-0.3
0.0
0.3
0.6
0.9
0 5 10 15 20u
f2
m=4
m=5
sample integrands in (31)
sample integrands in (30)
0.10
(a)
(b)
Fig. 3. Sample of integrands in the induced coefficients.
N. Xie et al. / Ocean Engineering 32 (2005) 1539–1555 1549
highly accurate scheme should be used. The integrand of J25 shows oscillatory decay
behaviour, as can be seen in Fig. 3b. A number of numerical tests have been carried out to
test the convergence of the integrals. It is found that the accuracy of the induced
coefficients plays a dominant role in the behaviour of the predicted pressure distributions.
If the induced coefficients (Dji in (13)) are not accurate enough, the pressure solution will
oscillate in a similar way to those found in previous studies (Tong, 1989; Doctors, 1975;
Wang, 2003; Tuck et al., 2002), even if the number of buttocks is three or four (not shown
here). The reason may be that the coefficients with low accuracy can damage the matrix of
unknown pressure equations and lead to erroneous solution. Table 1 shows an example of
the induced coefficients for a pressure element of b/aZ1.34, FrZU=ffiffiffiffigl
pZ9:04, where
lZ2a, a and b are half-length and beam of the element, respectively. A 3D view is also
shown in Fig. 4.
Numerical tests have also been carried out to study the effects of location of control
point on the solution of pressure distribution. It is found that placing the control point at
the centre of element is the best choice so far. The reason may be that the differences
between the flow patterns down stream and up stream of the pressure element are
significant due to the high element length based Froude Number (Fr), see Fig. 4. Another
reason may be that, in the present constant pressure distribution method, the ‘self-induced
coefficient’ is different from that of conventional source distribution method, in which the
self-induced coefficient is 2p (Newman, 1978). Fig. 5 shows an example of the self-
induced coefficients at the central line for a pressure element with length Froude Number
FrZ7.08 and b/aZ1.67, 1.00 and 0.56, respectively. It can be seen that the self-induced
coefficients vary significantly along the flow direction, especially for the element with
lower beam-length ratio. This corresponds to the cases in which higher number of buttocks
Table 1
Sample of the induced coefficients (b/aZ1.34, FrZ9.04, X, longitudinal distance from centre of the element
divided by length (2a); Y, lateral distance from the centre of element divided by beam (2b))
X Y
0 1 2 3 4
K7 K0.809781!10K1 0.267377!10K1 0.552860!10K2 0.246351!10K2 0.143168!10K2
K6 K0.697273!10K1 0.231254!10K1 0.481483!10K2 0.216792!10K2 0.126788!10K2
K5 K0.582469!10K1 0.194874!10K1 0.405869!10K2 0.185975!10K2 0.110599!10K2
K4 K0.465847!10K1 0.157250!10K1 0.338853!10K2 0.155573!10K2 0.952134!10K3
K3 K0.347012!10K1 0.119831!10K1 0.265249!10K2 0.128658!10K2 0.806927!10K3
K2 K0.227081!10K1 0.826154!10K2 0.201714!10K2 0.104593!10K2 0.676633!10K3
K1 K0.102581!10K1 0.485673!10K2 0.139680!10K2 0.829829!10K3 0.562147!10K3
0 0.367811!10K2 0.214768!10K2 0.988816!10K3 0.622272!10K3 0.464104!10K3
1 0.156091!10K2 0.944974!10K3 0.661455!10K3 0.476320!10K3 0.386360!10K3
2 0.758113!10K3 0.576489!10K3 0.459877!10K3 0.372690!10K3 0.322092!10K3
3 0.510338!10K3 0.374945!10K3 0.354668!10K3 0.312561!10K3 0.268896!10K3
4 0.417445!10K3 0.303526!10K3 0.240145!10K3 0.258015!10K3 0.226030!10K3
5 0.275688!10K3 0.231732!10K3 0.245897!10K3 0.207067!10K3 0.189273!10K3
6 0.170239!10K3 0.255575!10K3 0.182931!10K3 0.166518!10K3 0.161186!10K3
7 0.153567!10K3 0.182703!10K3 0.181568!10K3 0.149332!10K3 0.138721!10K3
Fig. 4. Three-dimensional view of the induced coefficients of a pressure element (X, longitudinal distance from
centre of the element divided by length (2a); Y, lateral distance from the centre of element divided by beam (2b),
fnZU=ffiffiffiffiffiffiffiffi2ag
p).
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551550
is employed. If the control points are not properly selected, the pressure solution could be
incorrect, even oscillatory. Fig. 6 shows a 3D view of the self-induced coefficients for an
element of b/aZ1.00 at FrZ7.08.
Fig. 7 shows comparison of pressure coefficients at the central line of a flat planing plate
of B/LZ0.5, FrZ2.24, where in the present method, nine buttocks were used (NyZ9). The
pressure distribution is free of oscillation and in good agreement with other researchers. It
can be seen that the present results have a better agreement with Cheng and Wellicome’s
and Wang and Rispin’s results than Tong’s, who also used the constant pressure element
distributions. The reason may be due to Tong’s number of buttocks is too few (less than 5).
Fig. 8 shows pressure distribution at central line for B/LZ1.0 and vessel Froude Number
FrZ2.24, the number of buttocks are 5 and 7, respectively, the present results are in
-0.020
-0.015
-0.010
-
0.000
0.005
0.010
-0.5 -0.3 -0.1 0.1 0.3 0.5X
D
b/a=1.67
b/a=1.00
b/a=0.56
0.005
fn=7.08
Fig. 5. Sample of pressure element self-induced coefficients at central line (X, longitudinal distance from centre of
the element divided by length (2a).
Fig. 6. Sample of self-induced coefficients of a element (X, longitudinal distance from centre of the element
divided by 2a, Y, lateral distance from the centre of the element divided by 2b).
N. Xie et al. / Ocean Engineering 32 (2005) 1539–1555 1551
good agreement with Wang et al.’s results and do not show any oscillation. Figs. 9 and 10
show pressure distribution for flat planing plate of B/LZ1.2 and FrZ1.5 for different
number of buttocks. The number of pressure strips is NxZ11. The convergence of the
present method can be seen from these figures. Fig. 11 is the three-dimensional
configuration of the pressure distribution on a flat planing hull of B/LZ1.2 and FrZ1.5.
The pressure distributions on the entire region do not show any oscillation, which validates
the present numerical method. Fig. 12 shows the calculated transom profile for B/LZ0.5,
FrZ2.24.
0.0
0.5
1.0
1.5
2.0
0.0 0.2 0.4 0.6 0.8 1.0
Cp
Tong
Cheng&Wellicome
present
Wang&Rispin
B/L=0.5, Fn=2.24
x/L
Fig. 7. Central line pressure distribution (B/LZ0.5, FrZ2.24).
0.0
0.5
1.0
1.5
2.0
0.0 0.2 0.4 0.6 0.8
Wang&Rispin
present, Ny=7present, Ny=5
X/L
CP
Fig. 8. Central line pressure distribution (B/LZ1.0, FrZ2.24).
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551552
6. Concluding remark
In the present paper, hydrodynamics of three-dimensional planing surface is studied
within linear potential theory. The planing surface is represented by a number of pressure
elements whose strengths are constant. The induced free surface elevations under
the planing surface is set to be the vertical coordinates of the planing surface, and also a
zero pressure condition, i.e. Kutta condition is applied at the trailing-edge of the planing
surface. A numerical method is proposed for the evaluation of the influence coefficient
matrix. The predicted pressure distributions using the present method are in good
agreement with other researchers’, which used different approaches. One of the important
findings of the present study is that the pressure distribution will not show oscillatory
behaviour using the constant pressure distribution method when the induced coefficients
0
1
2
3
4
5
6
-0.5 -0.3 -0.1 0.1 0.3 0.5y/B
Cp
Ny=11
Ny=9
Ny=7
Ny=5
Ny=3
B/L=1.2, Fn=1.5, Nx=11
Fig. 9. Pressure distribution at ixZ11 on flat planing hull (B/LZ1.2, FrZ1.50).
Fig. 11. Three-dimensional configuration of pressure distribution on flat planing hull (B/LZ1.2, FrZ1.50) (CLZ0.988, LCPZ0.721).
0.0
0.5
1.0
1.5
2.0
2.5
3.0
0.0 0.2 0.4 0.6 0.8 1.0x/L
CpB/L=1.2, Fn=1.5, Nx=11
4#, Ny=5
2#, Ny=9
1#, Ny=11
Fig. 10. Pressure distribution at central line of a flat planing hull (B/LZ1.2, FrZ1.50).
N. Xie et al. / Ocean Engineering 32 (2005) 1539–1555 1553
B/L=0.5, Fn=2.24
–2.0
–1.5
–1.0
–0.5
0.0–0.5 –0.3 –0.1 0.1 0.3 0.5y/B
H /
[B
tan
(tao
)]
Fig. 12. Predicted trailing-edge profile for flat planing hull (B/LZ05, FrZ2.24).
N. Xie et al. / Ocean Engineering 32 (2005) 1539–15551554
are evaluated with high accuracy. The irregularity of the pressure distribution in the
previous studies using the same method is most likely due to the inaccuracies in the
calculation of the pressure element induced coefficients, not the method itself.
Acknowledgements
The present study is partially supported by the 5th Framework EU project EFFISES, the
EU funding is grateful. The authors also thank Dr. X.M. Cheng and Professor L. Doctors
for their valuable discussions and reviewing on the manuscript.
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