Response-based method for determining the extreme behaviour of floating offshore platforms
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Transcript of Response-based method for determining the extreme behaviour of floating offshore platforms
Response-based method for determining
the extreme behaviour of floating
offshore platforms
Said Mazaheri*, Martine J. Downie
School of Marine Science and Technology, University of Newcastle upon Tyne, NE1 7RU, UK
Received 23 March 2004; accepted 4 August 2004
Available online 28 October 2004
Abstract
The accurate prediction of extreme excursion and mooring force of floating offshore
structures due to multi-variete environmental conditions which requires the joint probability
analysis of environmental conditions for the worst case situation is still impractical as the
processing of large amount of met-ocean data is required. On the other hand, the simplified
multiple design criteria (e.g. the N-year wave with associated winds and currents) recommended
by API known as traditional method does lead neither to the N-year platform response nor to
the N-year mooring force. Therefore, in order to reduce the level of conservatism as well as
uncertainties involved in the traditional method the response-based method can be used as a
reliable alternative approach. In this paper this method is described. In order to perform the
calculations faster using large databases of sea states, Artificial Neural Networks (ANN) is
designed and employed. In the paper the response-based method is applied to a 200,000 tdw
FPSO and the results are discussed.
q 2004 Elsevier Ltd. All rights reserved.
Keywords: Floating offshore platforms; Artificial neural networks; Mooring system; Response-based method;
Hydrodynamics
Ocean Engineering 32 (2005) 363–393
www.elsevier.com/locate/oceaneng
0029-8018/$ - see front matter q 2004 Elsevier Ltd. All rights reserved.
doi:10.1016/j.oceaneng.2004.08.004
* Corresponding author. Tel.: C44 191 222 5863; fax: C44 191 222 5491.
E-mail address: [email protected] (S. Mazaheri).
Nomenclature
Ajk added-mass matrix
AP projected area normal to the force (m2)
Awp vessel’s water plane area (m2)
B beam of the hull (m)
BA beam of the aftermost section (m)
BS beam of the right end section (bow) (m)
Bjk the matrix of damping coefficients
Ccu current coefficient
CD drag coefficient
CT finite draft correction factor
Cii wave drift damping
Cjk the matrix of the hydrostatic restoring coefficients
D draft of vessel (m)
FA1 acceleration force in surge mode due to wave (kN)
FCurrent current force (kN)
FWave (freq) first-order oscillatory wave force (kN)
FWave (steady) steady wave force (kN)
FWave (slowdrift) slow drift wave force (kN)
FWave (steady) steady wind force (kN)
FWave (slowdrift) slow drift wind force (kN)
Fp1 dynamic pressure force in surge mode due to wave (kN)
Fi force in the ith mode (kN)
Fj the amplitude of the 1st order wave induced loads (kN)
FN Froude number�GM distance between the vessel’s metacentre and the vessel’s gravity points (m)
GT distance between the turret mooring point and the vessel’s centre of gravity
(m)
Hs significant wave height (m)
I(z) turbulence intensity
Iwp water plane moment of inertia (m4)
Kq the rotational mooring stiffness (kN m)
L length between perpendiculars (m)
L1 the integration domain over the no N-shadow part of the water plane curve
Lm the distance between the turret mooring point and the vessel’s centre of
gravity (m)�Mc current induced yaw moment (kN m)
Mi moment in the ith mode
Mjk mass matrix
P wave’s dynamic pressure (kN/m2)
Q dynamic magnification factor
S wetted surface of the hull (m)
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393364
S(f) wind spectrum
S(u) wave spectrum
SF(m) the spectral density of the slow drift excitation forces
Sjk mooring stiffness matrix (kN/m)
T mooring force (kN)
T1 mean wave period (s)
TH Horizontal mooring force (kN)
UC current velocity (m/s)
V undisturbed mean hourly wind speed (m/s)
VWind mean hourly wind speed (m/s)�Vwi mean hourly wind speed (m/s)
V 0(t) fluctuating wind gust velocity (m/s)
ZG centre of the gravity (m)
a wave’s particle acceleration (m2/s)
aij sectional added-mass component
bij sectional damping component
d damping factor
g gravity acceleration (m2/s)
h water depth (m)
k wave number
kx the mooring stiffness in x mode (kN/m)
ky the mooring stiffness in y mode (kN/m)
s cable length (m)
xy coordinate system based on the FPSO (Platform)
x 0y 0 coordinate system coincides with wave direction and wave’s crest
w submerged weight of mooring cable per unit length (N/m)
a wind direction in respect to x (deg.)
b current angle in respect to x (deg.)
g wave angle in respect to x (deg.)
x wave surface elevation (m)
xa wave amplitude (m)
hk vessel’s displacement (m)
_hk vessel’s velocity (m/s)
€hk vessel’s acceleration (m2/sec)
q 0i vessel’s rotational angle at time i
k surface drag coefficient
l wave length (m)
r water density (t/m3)
rair air density (t/m3)
f velocity potential
f cable angle in respect to x-axis (deg.)
fw cable angle at water line surface (deg.)
f0 cable angle at sea floor (deg.)
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 365
u angular wave frequency (rad/s)
ue frequency of encounter (rad/s)
un natural frequency (rad/s)
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393366
1. Introduction
For the design and evaluation of mooring systems of floating offshore structures two
different environmental conditions are usually considered. These conditions are named as
the ‘maximum design condition’ and the ‘maximum operating condition’. According to
API (American Petroleum Institute., 1995) mooring systems should be designed for the
combination of the wind, wave and current conditions causing the extreme load, in the
design environment. In the practice this is often approximated by the use of multiple
design criteria, e.g. the N-year wave with associated winds and currents or the N-year wind
with associated waves and winds. It is obvious that the most sever directional combination
of wind wave and current forces should be specified according to the site’s environmental
condition. Moreover, API indicates that if the floating offshore structure is designed to
continue production during a severe storm, the maximum operating condition should be
the same as the maximum design condition. In practice, severe met-ocean parameters, i.e.
the N-year values of wind speed, wave height and current velocity are often assumed to
occur simultaneously (Standing et al., 1997). This leads neither to the N-year vessel’s
response nor to the N-year mooring force as the N-year values of met-ocean parameters are
not inline with the N-year values of vessel’s responses for a number of reasons.
In the first place the probability of occurrence of the N-year values of met-ocean
parameters with coincident propagation directions is extremely low. This means that the
N-year environmental condition is not the combination of the N-year values of individual
met-ocean parameters. To overcome this problem joint probability analysis of the
environmental conditions is necessarily required. The approach of determining the worst
case possibilities when more than one parameter is involved, for example for wave height
and period, wind speed and wave height and wave height and current, is commonly
adopted. However, when more than two environmental parameters affect the response,
then a multi-dimensional joint probability diagram should be used, which is very difficult
because a large amount of data is needed (Barltrop et al., 1998).
Secondly, the distribution of met-ocean parameters does not coincide with the
distribution of the vessel’s responses and mooring forces. This means that even
determining the N-year severe environmental condition accurately does not lead to the
N-year values of the vessel’s responses and mooring forces. For example Standing et al.
(1997) showed that using 100-year values of wind speed, wave height and current velocity
at the same time to calculate the vessel’s responses will end up with results with return
periods much longer than 100 years. In addition, the results presented by Incecik et al.
(1998) showed that the most severe mooring loads may not occur when wind, wave and
current are collinear and are at their maximum values.
In this paper a different approach to the response-based method is developed. It is based
on the response-based hydrodynamic model (SAMRES) developed by the first author
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 367
and makes use of the following theories. Artificial Neural Networks (ANN) is then
employed to simplify the response calculation of the vessel as the met-ocean parameters
vary. This simplification allows the response-based method to perform quickly whilst
processing long-term met-ocean data.
2. Response-based approach
A reliable method to predict the maximum motion responses of a turret-moored FPSO
subjected to arbitrary wind, current and wave loads for an N-year life period, which is
essential for the design of the mooring system, is still under development. Over the last
few years the response-based approach has been developed to reduce the level of
conservatism as well as the uncertainties involved in traditional methods for determining
vessel’s extreme responses due to arbitrary environmental loads over her service life. The
response-based approach was first applied to assess the extreme loading design
combinations on a fixed jacket platform by Marshall and Rezvan (1995). Later, Standing
et al. (1997) showed that by using the response-based method the 100-year maximum
resultant excursion of an FPSO reduces to about 75–80% of the maximum excursion
predicted using a traditional collinear combination of 100-year wind, 100-year current and
100-year waves. It is believed that the response-based calculation procedure will yield
more accurate results than those obtained by traditional methods. In the response-based
method one determines vessel responses using environmental data associated with the
place where the platform is going to be installed. For this purpose a model to predict the
responses of the vessel is required. In order to perform the calculations based on large
databases of sea states fast enough to be practical, some simplifications are needed. For
example, the time taken to process 6 months of data used in the spectral analysis with the
simple response model presented by Khor and Barltrop (1999) was about 4 days. Standing
et al. (1997) employed response surface modelling to simplify the response of the vessel as
a function of wind speed, wave height, spectral peak wave period, current speed, wind and
current heading angles. Using another approach, Incecik et al. (1998) developed the
structure variable method to transform the multi-variate environmental record into a
univariate time series of mooring forces. In this paper a different approach to the response-
based method is developed. This approach is based on the first author’s response-based
model (SAMRES) by employing Artificial Neural Networks (ANN) as a simplification
tool to predict the platform responses due to met-ocean parameters. This approach is
briefly illustrated by the flowchart in Fig. 1. As can be seen on the flowchart,
environmental data, the vessel’s particulars, a mathematical response model and artificial
neural networks (ANN) are the main components of the proposed response-based
approach. The procedures involved in the response-based approach entail the following
tasks:
(1)
Building up a mathematical model in order to determine the loads and motions of aturret-moored FPSO due to wind, current and waves.
(2)
Obtaining the vessel’s responses by running the mathematical model over areasonable period of environmental data (e.g. 5 years).
Fig. 1. The flowchart of response-based approach.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393368
(3)
Setting up an artificial neural network (ANN) that has been trained and cross validatedusing sufficient data obtained from the mathematical model to ensure an accurate
representation of vessel responses as a function of environmental variables.
(4)
Using the ANN model to generate long-term vessel responses (e.g. using 25-year met-ocean data).
(5)
Analysing the resulting vessel responses statistically to predict its maximum excursionover an N-year life period.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 369
3. Mathematical response model
A typical form of an FPSO is shown in Fig. 2. A right handed coordinate system at the
conjunction of the water surface and the axis passing through the platform’s centre of
gravity is considered so that the centre of gravity can be defined as (0,0,KZG). The general
form of the response equation for this platform can be written as
ðM CAÞdh2
dt2CB
dh
dtC ðC CSÞh
Z FwaveðfreqÞ CFWaveðsteadyÞ CFWaveðslowdriftÞ CFWindðsteadyÞ CFWindðslowdriftÞ
CFCurrent (1)
where M, A, B, C and S are matrices of mass, added-mass, damping, hydrostatic restoring
and mooring stiffness coefficients, respectively, which can be written for an FPSO with
lateral symmetry as follows:
Mjk Z
M 0 0 0 MZG 0
0 M 0 KMZG 0 0
0 0 M 0 0 0
0 KMZG 0 I4 0 0
MZG 0 0 0 I5 0
0 0 0 0 0 I6
266666666664
377777777775
Ajk Z
A11 0 0 0 0 0
0 A22 0 A24 0 A26
0 0 A33 0 A35 0
0 A42 0 A44 0 A46
0 0 A53 0 A55 0
0 A62 0 A64 0 A66
266666666664
377777777775
Fig. 2. Definition of the coordinate system and motions of a turret-moored FPSO.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393370
Bjk Z
B11 0 0 0 0 0
0 B22 0 B24 0 B26
0 0 B33 0 B35 0
0 B42 0 B44 0 B46
0 0 B53 0 B55 0
0 B62 0 B64 0 B66
266666666664
377777777775
Cjk Z
0 0 0 0 0 0
0 0 0 0 0 0
0 0 C33 0 C35 0
0 0 0 C44 0 0
0 0 C53 0 C55 0
0 0 0 0 0 0
266666666664
377777777775
Sjk Z
S11 0 0 0 0 0
0 S22 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 0
0 0 0 0 0 S66
266666666664
377777777775
The details of obtaining the components of above matrices can be found in Faltinsen
(1990) and Salvesen et al. (1970).
3.1. Forces due to first-order waves
The velocity potential for an oblique wave with propagation angle of g in respect to x
axis can be defined as:
f Z0:5 gHs
u
cosh kðz ChÞ
cosh ðkhÞsinðkx0 KutÞ x0 Z x cos g Cy sin g (2)
Other wave components such as surface elevation, particle velocity, particle
acceleration and dynamic pressure can be derived from Eq. (2).
The wave induced surge force was calculated by considering the influence of the
platform’s lateral curvature. Strip theory is employed to calculate the sway and heave
forces by assuming that the length to beam ratio of the platform (FPSO) is not lower than
2.5 (ITTC, 1987). This means that the forces and moments are calculated by integrating
the inertia forces, which are the combination of the dynamic pressure and acceleration
Table 1
Main particulars of a 200,000 tdw FPSO
Length between perpendiculars (m) 310
Breadth (m) 47.20 m
Draft (m) 18.90
Volume of displacement (m3) 235,000
Block coefficient 0.85
Mid-ship section coefficient 0.995
Prismatic coefficient 0.855
Distance of centre of gravity to mid-ship section (m) 6.61
Height of centre of gravity (m) 13.32
Meta-centric height (m) 5.78
Longitudinal radius of gyration (m) 77.5
Transverse radius of gyration (m) 17.00
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 371
forces obtained at each cross section of the platform. The effects of wave direction and
shallow water conditions are also taken into account in deriving force equations.
Based on the method described above, a program was written in MATLAB and
executed for a 200,000 tdw FPSO whose particulars are given in Table 1. The results
obtained from the mathematical model showed a good correlation with those obtained by
Oortmerssen (1976) who used the 3D source technique (Figs. 3–12). This means that the
strip theory is consistent with the 3D source technique, particularly when lateral loads are
the aim of the calculation.
Fig. 3. Transfer function of wave induced surge force, gZ45.
Fig. 4. Transfer function of wave induced sway force, gZ45.
Fig. 5. Transfer function of wave induced sway force, gZ90.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393372
Fig. 6. Transfer function of wave induced heave force, gZ0.
Fig. 7. Transfer function of wave induced roll moment, gZ45.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 373
Fig. 8. Transfer function of wave induced roll moment, gZ90.
Fig. 9. Transfer function of wave induced pitch moment, gZ0.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393374
Fig. 10. Transfer function of wave induced pitch moment, gZ45.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 375
3.2. Forces due to steady waves
These forces are second-order forces which can be derived from the quadratic term of
the velocity potential. Havelock (1940) presented an empirical formula to calculate the
wave drift force acting on a fixed cylinder with vertical walls. This has been extended later
on by Besho (1958) to cover arbitrary bodies. Then Kwon (1982) has added three
coefficients to the Besho’s formula to take into account the effects of object’s speed, finite
draft and scattering. After that, Faltinsen (1990) presented a general frequency
independent formula to calculate the mean drift forces due to arbitrary waterline shaped
Fig. 11. Transfer function of wave induced yaw moment, gZ45.
Fig. 12. Transfer function of wave induced yaw moment, gZ90.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393376
bodies. In order to include the effects of wave direction, wave frequency, current and
arbitrary waterline shaped bodies on the calculation of the mean drift forces Mazaheri
(2002) has redeveloped Faltinsen’s formula by adding the finite draft coefficient and
current coefficient as follows:
Fi Z CT Ccu;i
rgz2a
2
ðL1
sin2ðq CgÞni dl (3)
The current coefficient, Ccu, can be derived from the ship added resistance formula
proposed by Faltinsen et al. (1980) as:
Ccu;i Z 1 C2uUC;i
g
The above formula is applicable to bluff bodies when Froude number is equal or less
than 0.2.
CT coefficient is given as:
CT Z 1 KexpðK2kDÞ
By applying Eq. (3), the surge drift force for a stationary barge shape vessel with a
beam of B subjected to head sea waves can be simplified as:
F1 Z CT
rgz2a
2
ðB
sin2ðq C0Þdy Z CT
rgz2a
2B (4)
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 377
Now by defining the surge drift force coefficient R1(u) as
R1ðuÞ ZF1
12
rgz2aB
and substituting F1 from Eq. (4), the surge drift force coefficient becomes:
R1ðuÞ Z CT
This means that the surge drift force coefficient for a stationary rectangular barge-shape
vessel subjected to head sea waves is equal to the finite draft coefficient. This surge drift
force coefficient is compared with those obtained by Kwon (1982), Fujii and Takahashi
(1975), and Helvacioglu’s experiments (1990) favourably in high wave frequencies
(Fig. 13).
For an FPSO with a general water plane area shown in Fig. 14 by assuming that the
most left and right curvature parts can be replaced by a half-circle with a diameter equal to
the beam of the middle rectangular section, the mean drift loads in regular waves in surge,
sway and yaw modes can be written as:
F1 Z CT 1 C2uUCcos b
g
� rgz2
a
2
ðL1
sin2ðq CgÞsinq dl ðsurgeÞ (5)
Fig. 13. Comparisons between different surge drift force coefficients.
Fig. 14. The water plane area of a 200,000 tdw FPSO.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393378
F2 Z CT 1 C2uUCsin b
g
� rgz2
a
2
ðL1
sin2ðq CgÞcos q dl ðswayÞ (6)
F6 Z CT 1 C2uUCsin b
g
� rgz2
a
2
ðL1
sin2ðq CgÞðx cos q Ky sin qÞ dl ðyawÞ (7)
In order to obtain the mean drift loads in irregular waves, the following equation can be
employed
�Fsi Z 2
ðN
0sðuÞ
Fiðu;b;gÞ
z2a
� du i Z 1;.; 6 (8)
where S(u) is the sea spectrum which can be defined according to 15th ITTC as
SðuÞ
H2s T1
Z0:11
2p
uT1
2p
� K5
exp K0:44uT1
2p
� K4 �where:ðN
0SðuÞdu Z m0
ðN
0uSðuÞdu Z m1
m1
m0
Z2p
T1
Hs Z 4ffiffiffiffiffiffim0
p
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 379
Fi(u,b,g) is the ith mean force component in regular waves with the circular frequency
of u and arbitrary direction of g in the presence of arbitrary current with angle of b.
Applying Eq. (8) to a general FPSO leads to the following mean drift loads in irregular
waves in surge, sway and yaw modes:
�Fs1 Z rg
H2s
16CT 1 CFn1
4p
T1
ffiffiffiffiL
g
s" #4
3r cos g
� ðSurgeÞ (9)
�Fs2 Z rg
H2s
16CT 1 CFn2
4p
T1
ffiffiffiffiB
g
s" #4
3r sin g CL2 sin gjsin gj
� ðSwayÞ (10)
�Fs6 Z rg
H2s
16CT 1 CFn2
4p
T1
ffiffiffiffiB
g
s" #2
3r singðL0
1 KL02Þ
�
C ðL022 KL0
12Þsin gjsin gjC1
3rðL0
1 CL02Þsin 2g
ðYawÞ (11)
3.3. Forces due to slow drift waves
The slow drift excitation loads can be written either in time series or in spectral form. It
is obvious that the spectral form can be much simpler to use for design calculations rather
than the time series form. The spectral density of the slow drift excitation loads can be
calculated according to Pinkster (1975) as:
SFðmÞ Z 8
ðN
0SðuÞSðu CmÞ
Fi u C m2
� �z2
a
� 2
du (12)
where Fi(uC(m/2)) is the mean wave load component at the frequency of uC(m/2) or in
other words we can say that ðFiðuC ðm=2ÞÞ=z2aÞ is the mean wave load coefficient at the
frequency of uC(m/2)
Fig. 15 shows the spectral density of slow drift excitation load for a 200,000 tdw FPSO
subjected to a head sea which can be represented by a P–M spectrum with significant wave
height of 5 m and the peak frequency of 9.61 s. The figure explains that the presence of the
current can only alter the lower frequency part of the spectrum by increasing the area
under that part of the spectrum.
3.4. Forces due to steady winds
The steady mean wind loads on an FPSO can be determined by using the following drag
formula
FW ;i Z 1=2rairCDAPV2 (13)
Fig. 15. Second order surge force spectrum.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393380
where
rair Z 1:21!10K3ðt=m3Þ at 20 8C
CD is the drag coefficient, which varies for different type of structures. According to the
API the drag coefficient varies between 0.5 and 1.5.
V is undisturbed mean hourly wind speed at the location of the force centre and it can be
obtained from the following formula
�Vz Z �VzR
z
zR
� 0:125
where z is the height of the force centre and zR is the reference height.
3.5. Forces due to wind gusts
Wind gusts with significant energy at periods of the order of magnitude of minute can
produce slowly varying oscillations of marine structures. According to ISSC no appreciable
difference between various spectral formulations for dimensionless frequencies greater than
approximately 0.02 is existed. The Harris wind spectrum can be defined as
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 381
fSðf Þ
V210
Z4k ~f
ð2 C ~f2Þ5=6
(14)
~f Z Lf =V10
L is the length scale and k is the surface drag coefficient.
The fluctuating drag force due to gust can be obtained by defining the gust velocity as a
combination of mean wind velocity and the fluctuating gust velocity in the main drag force
equation. By neglecting the squared term of the fluctuating gust velocity, the fluctuating
drag force due to wind gust becomes:
F 0DðtÞ Z rairCDAPV 0ðtÞ (15)
Therefore, the power spectrum of the gust force in Hz can be determined as:
SWF ðf Þ Z ðCDAPrair
�VÞ2Sðf Þ (16)
The power spectrum can also be calculated in circular frequency by employing the
following equation:
SWF ðuÞ Z
1
2pSW
F ðf Þ (17)
3.6. Forces due to current
The longitudinal drag force due to an arbitrary current on an FPSO is mainly due to
frictional forces and can be calculated by the following approximate formula given by
Faltinsen (1990)
F1 Z0:075
ðlog10 Rn K2Þ21
2rSU2
C cos bjcos bj (18)
where
Rn ZUCLjcos bj
n
vZ1.19!10K6 m2/s for 15 8C water temperature. S is the wetted surface of the vessel.
The transverse current force can be calculated by writing the drag force formula
for the vessel’s cross section and integrating it over the vessel’s length. So, it can be
written as
FC2 Z
1
2rU2
Csin bjsin bj
ðL
CDðxÞDðxÞdx (19)
where CD(x) is the cross-sectional drag coefficient and D(x) is the sectional draught.
Current can also produce a yaw moment. This moment is the sum of the Munk moment
and the viscous moment due to cross-flow (Faltinsen, 1990) which can be calculated by
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393382
the following equation:
F6 Z1
2rUCsin bjsin bj
ðL
CDðxÞDðxÞx dx C1
2U2
CðA22 KA11Þsin 2b|fflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflffl{zfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflffl}Munk moment
K kL2m|{z}
Due to mooring
(20)
where A11 and A22 are the vessel’s added masses in surge and sway, respectively.
3.7. Equilibrium angle
A turret moored FPSO subjected to met-ocean loads, i.e. wind, waves and current
weathervanes until the platform reaches an equilibrium position (Fig. 16). The first-order
wind and current forces are static forces. Meanwhile, the mean drift wave loads, which is
the result of the second-order wave effects is also a static force. These forces rotate
the vessel to its equilibrium position. In addition to these static forces, the first-order wave
forces which is time varying forces should be considered for determining the vessel’s
equilibrium angle. The reason is that the first-order wave loads are varying like a sine
function as shown in Fig. 17. Between t0 and t1 the vessel will rotate from its initial
position ‘P0’ to position ‘P1’ (Fig. 18). Therefore, the angle between the vessel and the
propagation direction of the incoming waves will reduce which cause a reduction in
rotational moment. As from this stage ‘t1’ towards ‘t2’ the direction of wave loads will
change then the vessel will rotate backward to position ‘P2’ where is somewhere between
‘P0’ and ‘P1’. At this stage the direction of wave loads will change again and the vessel
will rotate forward again to position ‘P3’. This forward and backward fluctuation will
continue until the vessel reaches its equilibrium position ‘Pn’. So, it can be concluded that,
however, the first-order wave forces are dynamic forces and fluctuate the vessel but these
forces will rotate the vessel to its equilibrium angle. A vessel subjected to environmental
loads would stand at an equilibrium heading angle where all rotational moments cancel
each other and there are no any resultant rotational moment acting on the vessel. The total
Fig. 16. Comparison between wave drift damping derived from different methods.
Fig. 17. The equilibrium angle of a turret-moored FPSO subjected to arbitrary wind, wave and current loads.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 383
rotational moment can be calculated by adding up the following equations:
�Mwind Z1
2rairj �Vwisin aj �Vwisin a
XAo;n1CD;onxo C
ðLTB
LTA
CDiSixidx
�(21)
�MWave Z rg0:5Hw
1
k
sinh ðkhÞKsinh kðh KDÞ
cosh ðkhÞ
� ðLTB
LTA
2sinðkx cos gÞ�
!sin kBi
2sin g
� cos ut K2cosðkx cos gÞsin k
Bi
2sin g
� sin ut
�x dx
C0:5Hsu2 cosh k KD
2Ch
� �sinhðkhÞ
ðLTB
LTA
½a22;isinðkx cos gÞcos ut
Ka22;icosðkx cos gÞsin ut�x dx
(22)
�Mc Z1
2rU2
Csin bjsin bj
ðLTB
LTA
CDðxÞDðxÞx dx C1
2U2
CðA22 KA11Þsin 2b|fflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflffl{zfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflfflffl}Munk moment
(23)
The equilibrium heading for a 200,000 tdw FPSO (Table 1) due to different set of
environmental conditions are given in Table 2.
Fig. 18. Typical time varying first-order wave loads.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393384
The second order wind weathervaning effect can be analysed by calculating the
second order rotational moment about the turret-mooring point due to gusty wind.
Practically speaking a floating offshore platform can only be able to respond
dynamically to high speed short term gust (Barltrop et al., 1998, pages 2-33 and
2-34). In other words, there is not sufficient time for the low speed short term gust to
excite a floating offshore structure. For example, the 3-s fluctuating wind gust
velocity, V 0(t), for 30 m/s mean hourly wind speed would be around 14 m/s while this
figure for a 30-s gust velocity would be around 7 m/s. Applying the wind gust effect
on the equilibrium heading angle calculation of a turret-moored FPSO will lead to a
few degree fluctuation (Mazaheri, 2003).
The second-order wave effects on vessel’s equilibrium angle can be determined by
applying the slowly varying yaw drift excitation moment. It is expected that the second-
order wave effects fluctuate the floating platform just with a few degree amplitude around
its equilibrium angle. Analysing the second-order effects of wind and wave loads on a
200,000 tdw tanker showed that a few degree fluctuations can be expected. Also, a vessel
can be moved from one of her equilibrium angle to the other one if the first equilibrium
Fig. 19. Vessel fluctuations due to first-order wave loads.
Table 2
Equilibrium heading angle of a 200,000 tdw FPSO subjected to arbitrary wind, wave and current loads
Wind Wave Current Vessel’s
equilibrium
heading
angle (q)
a Vwi (m/s) g Hs (m) b Uc (m/s)
0 30 45 5 0 1 223
0 30 90 5 0 1 265
0 30 135 5 0 1 313
0 30 225 5 0 1 48
45 30 0 5 0 1 3
45 30 45 5 0 1 225
45 30 90 5 0 1 268
45 30 135 5 0 1 310
45 30 225 5 0 1 46
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 385
heading angle was happened to be in a position that wind and wave forces were acting
from the aft of the vessel (Mazaheri, 2003).
3.8. SAMRES model
SAMRES is a hydrodynamic response model for calculating responses of a floating
offshore platform subjected to arbitrary wind, wave and current loads. This hydrodynamic
response model is written in MATLAB and it is based on the theories described earlier. It
should be noted that the forces are calculated on the vessel at its equilibrium heading
angle. In general SAMRES solves Eq. (1). The total platform’s response in each mode of
motion is calculated as
�Xi Z XWaveðsteadyÞ;i C �XWaveðfreqÞ;i C �XWaveðslowdriftÞ;i CXWindðsteadyÞ;i
C �XWindðslowdriftÞ;i CXCurrent;i (24)
where
�Xi
is the mean square value of the vessel’s response due to wind, wave andcurrent loads in mode i,
XWaveðsteadyÞ;i
is the vessel’s response due to steady wave load in mode i, �XWaveðferqÞ;i is the mean square value of the vessel’s response due to frequency waveload in i mode,
�XWaveðslowdriftÞ;i is the mean square value of the vessel’s response due to slow drift waveload in i mode,
XWind(stready),i
is the vessel’s response due to steady wind load in i mode, �XWindðslowdriftÞ;i is the mean square value of the vessel’s response due to wind gust load in imode,
XCurrent
is the vessel’s response due to steady current load in i mode.S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393386
4. The ANN model
The ANN model can be most adequately characterised as a computational model with
additional abilities such as adaptation and learning. The interpolation, and in some cases
extrapolation, capability is very powerful particularly when mapping a multi-dimensional
input data space to a multi-dimensional output data space (Roskilly and Mesbahi, 1996).
Therefore, ANN as an powerful regression tool can be implemented together with
SAMRES hydrodynamic model to predict the platform’s excursions. In general SAMRES
model calculates platform responses as a function of met-ocean data and platform’s
particulars. So, for a specific platform it can be expressed as
Y Z f ðXÞ (25)
where Y is platform responses (output data), f is the hydrodynamic response function, X is
the met-ocean parameters (input data).
The values of input and output matrices (X and Y) should be normalised. The following
formula can be used for normalising input and output values:
Table 3
Some of the input and output series of the data used in ANN
Vwind(m/s) awi Hs (m) gwa current
(m/s)
bac Surge
(m)
Sway
(m)
Excur.
(m)
32 136 2 73 1 233 1.09 4.04 4.18
10 206 3 148 1 115 0.13 1.04 1.05
14 31 4 321 1 40 0.48 3.87 3.90
25 53 8 68 2 242 9.52 1.06 9.58
23 124 5 88 2 265 2.06 5.61 5.98
25 103 3 228 2 321 0.84 0.01 0.84
12 224 4 280 1 343 0.46 1.13 1.22
21 302 2 229 1 8 0.41 0.00 0.41
28 139 5 309 1 59 1.25 41.18 41.20
20 206 7 248 2 76 6.07 0.52 6.09
33 329 3 298 2 159 0.27 68.15 68.15
33 177 2 61 1 232 1.49 0.62 1.61
24 228 8 307 2 262 4.57 24.80 25.22
26 179 8 341 1 157 7.56 21.70 22.97
13 180 6 4 1 65 2.05 0.58 2.13
20 179 4 315 1 210 0.56 13.68 13.69
25 150 5 125 2 331 1.77 26.30 26.36
11 204 6 326 1 43 2.16 1.53 2.64
34 166 4 237 2 197 1.96 0.40 2.00
25 254 3 211 1 120 0.77 0.15 0.79
16 243 2 162 2 40 0.05 4.67 4.67
21 160 5 302 2 251 0.86 15.37 15.39
35 282 7 240 2 40 7.42 1.01 7.49
16 302 5 97 2 138 0.81 2.75 2.86
25 76 3 298 1 56 0.19 26.93 26.94
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 387
Normalised value ZReal value KMin: value
Max: value KMin: value
The ANN model tries to utilise f(X) according to the existing input data, X, and the
relevant output data, Y, obtained from the hydrodynamic mathematical model.
It should be emphasised that it is impractical to calculate the platform’s responses
using the SAMRES model with long-term met-ocean parameters as it takes a
considerable time. Therefore, in order to make the model more accessible and
practical, the use of ANN model has been adopted. This model has been designed,
tested and validated using the platform’s excursion data predicted by the SAMRES
model. Taking into account the nature of input and output data displayed as an
example in Table 3, a (6-10-3) multi-layer feed forward network, which has one
hidden layer containing 10 neurons, has been selected (Fig. 19). The number of
neurons in input and output layers has been chosen according to the number of input
and output parameters. But, the number of neurons in hidden layer has been
calculated (decided) on a trial and basis in which the minimum means square error
has been achieved in both training and cross-validation procedure. Eq. (1) for the
deigned ANN model can be written as:
Y Z a sig1
fsig½AX�g
� B Cb (26)
where YZ[Surge, Sway, Total], Surge is vessel’s excursion in surge mode, Sway is
vessel’s excursion in sway mode, and Total is total vessel’s excursion, a and b are
normalisation factors which are:
a Z
0:0360 K0:3100
0:0025 0:0450
0:1500 K0:2500
0:0025 0:0475
0:9000 K0:8500
0:0025 0:0500
b Z
0:0947 0:0486
0:0109 0:0500
0:0109 0:0492
A and B are coefficient matrices which are
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393388
A Z
4:3899 23:4794 9:8039 2:9633 6:8804 11:9349
1:8872 2:6946 7:9440 6:2699 0:2288 4:4961
0:5779 0:8103 7:3273 0:9930 0:3290 1:7961
5:3140 16:7633 12:1113 4:6270 6:6249 17:3256
3:4854 0:1798 0:3999 31:2892 0:4736 0:4161
3:3931 1:2402 0:1614 24:0280 0:2692 2:2755
27:5614 0:8846 2:0947 19:8817 1:7678 10:8667
0:71087 0:99665 9:01257 1:22143 0:40466 2:20914
6:53625 20:6188 14:89688 5:69117 8:148615 21:3104
4:28709 0:22114 0:491884 38:48569 0:58247 0:5118
BZ
0:2357 1:2071 2:6545 0:3262 0:6652 0:4590 0:0291 0:489236 0:638572 0:440601
1:3489 0:7285 1:3145 1:3087 3:4134 3:3863 1:6033 1:96311 3:27685 3:25081
1:2387 0:5467 1:2972 1:2180 3:1552 3:0949 1:5018 1:82698 3:02898 2:97106
sigðxÞZ1
1CeKx
,
X is the input matrix which can be defined as:
X Z ½HS;g;Vwind;a;UCurrent;b�
5. Implementing the approach to an FPSO
In order to implement the approach a 200,000 tdw FPSO whose particulars are
described in Table 1 is considered. The platform is assumed to be installed in a place
where the long term met-ocean data is assumed to occur as specified in Table 4. SAMRES
hydrodynamic model is used to produce enough input and output data in order to design
the ANN model as described earlier. Fig. 20 shows how the ANN model can precisely
predict the platform excursions in surface modes of motion. Then the designed ANN
model, Eq. (26), is applied to predict data series of platform’s excursion due to long term
met-ocean data. The result of this simulation is illustrated in the form of the annual
frequency of platform’s excursion in Fig. 21. Fisher Tippett (FT) distribution method is
then applied to predict the maximum platform’s excursion in various return periods.
Fig. 22 shows the platform’s excursion against KLN(KLN(P)) in which the return period
can be obtained. The relation between return period (N) and KLN(KLN(P)) is expressed
in Table 5.
Table 4
The range of environmental parameters
Statistics Parameters
V (m/s) a (deg.) Hs (m) g (deg.) Vc (m/s) b (deg.)
Minimum 10 0 2 0 1 0
Maximum 35 360 8 360 2 360
Fig. 20. Comparisons between Desired excursions and ANN’s predictions (cross-validation).
Fig. 21. A multi-layer feedforward network (6-10-3). Note: Hs is wave height; g, wave angle; Vwind, mean hourly
wind velocity; a, wind direction; Ucurrent, current velocity; b, current angle and W1/W2 is weighting factor.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 389
Fig. 22. Annual frequency of vessel’s excursion.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393390
6. Conclusions
The strip theory was used in developing mathematical response model (SAMRES)
instead of 3D analysis for reason of simplification and computational efficiency. The
features in the approach adopted include a method for accounting lateral curvature effects of
the hull on surge using Gauss’ theorem to handle the pressure integration. Another aspect
was the inclusion of the Munk moment (Faltinsen, 1990) in the calculation of the current
induced yaw. The surge mode was also included in the coupled equations of motions.
Table 5
The relation between return period ‘N’ and ‘KLN(KLN(P))’
Return Period (N) (Year) P KLN(KLN(P))
1.1 0.09 K0.87
1.2 0.17 K0.58
1.3 0.23 K0.38
1.4 0.29 K0.23
1.5 0.33 K0.09
1.6 0.38 0.02
1.7 0.41 0.12
1.8 0.44 0.21
1.9 0.47 0.29
2 0.50 0.37
5 0.80 1.50
10 0.90 2.25
20 0.95 2.97
25 0.96 3.20
50 0.98 3.90
100 0.99 4.60
Fig. 23. Vessel’s excursion prediction using FT method.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 391
The results of this approach were shown to agree closely with those of Oortmerssen (1976)
who used the 3D source technique. Faltinsen’s wave drift formula (1990) was redeveloped
by adding finite draft coefficient. The results obtained from this formula compared
favourably with results obtained in Helvacioglu’s experiments (1990). In addition, the
influence of the current on the wave mean drift force was taken into account by considering
the current coefficient derived from the ship added resistance formula. The formula for the
calculation of the wave drift damping was extended to cover high wave frequencies as well
as low wave frequencies. The results compared with asymptotic formula (Fig. 23) showed
good agreement in high frequency band. The weathervaning effects were also included in
calculations of forces and excursions of the platform due to environmental loads. The
analysis of the second-order effects of wind and wave forces on the case study platform
showed that only a few degree fluctuations occurs around the platform’s equilibrium angle.
The designed ANN model in conjunction with the hydrodynamic SAMRES model was
used to carry out response based predictions to determine excursions of a series of
platforms due to long-term of met-ocean data. Fig. 24 shows how the ANN model can
considerably reduce the simulation time.
Fig. 24. Training and simulating tasks of the ANN model along with the required time for doing those tasks.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393392
The response-based method applied to the case study platform subjected to long-
term met-ocean data showed that the traditional method based on the combination of
N-year wind, N-year wave and N-year current cannot lead to N-year platform’s
excursion. In the case study considered, applying the response-based method showed
that the 50-year return period of the platform’s excursion due to particular met-ocean
data is around 60 m (Fig. 22) which has occurred due to a combination of maximum
12-year wave height and 8-year wind speed. Using the traditional method which
means applying 50-year wave height and wind speed makes the platform to move
around 80 m. Therefore, it can be concluded that the traditional method based on the
combination of N-year wind, wave and current loads for predicting the N-year
platform excursion provides a very conservative estimate.
References
American Petroleum Institute, 1995.Anon., 1995. Recommended practice for design and analysis of
stationkeeping systems for floating structures. American Petroleum Institute, Washington, DC. 107 pp.
Barltrop, N.D.P., Centre for Marine and Petroleum Technology. and Oilfield Publications Limited., 1998.
Floating structures: a guide for design and analysis. Publication/Centre for Marine and Petroleum
Technology; 101/98. Cmpt;Opl, Aberdeen, UK, Houston, TX, USA, 2 v. pp.
Besho, M., 1958. On the wave pressure acting on a fixed cylindrical body. Zosen Kiokai 1958;, 103 (in Japanese).
Faltinsen, O.M., 1990. Sea Loads on Ships and Offshore Structures, Cambridge Ocean Technology Series, 1.
Cambridge University Press, Cambridge. 328 pp.
Faltinsen, O.M., Minsaas, K., Liapis, N., Skjordal, S.O., 1980. Prediction of Resistance and Propulsion of a Ship
in a Seaway, in: Inui, T. (Ed.), Thirteenth Symposium on Naval Hydrodynamics. The Shipbuilding Research
Association of Japan, Tokyo, pp. 505–530.
Fujii, H., Takahashi, T., 1975. Experiments Study on the Resistance Increase of a Ship in Regular Oblique Waves,
14th ITTC, Ottawa.
Havelock, T.H., 1940. The pressure of water waves upon a fixed obstacle. Proceedings of Royal Society of
London Series A 1940;, 409–421.
Helvacioglu, I.H., 1990. Dynamic analysis of coupled articulated tower and floating production system. PhD
Thesis, University of Glasgow, Glasgow, 267 pp.
Incecik, A., Bowers, J., Mould, G., Yilmaz, O., 1998. Response-based extreme value analysis of moored offshore
structures due to wave, wind, and current. Journal of Marine Science and Technology 3, 145–150.
ITTC, 1987.Anon., 1987. The report of the Seakeeping Committee, 18th International Towing Tank Conference,
Kobe, Japan 1987.
Khor, L.H., Barltrop, N.D.P., 1999. A method of analysis for the extreme response of an offshore floating and
weathervaning platform subjected to wave, current and wind from different directions. Journal of the Society
for Underwater Technology 24 (1), 11–17.
Kwon, Y.J., 1982. The effect of weather particularly short sea waves on the ship speed performance. PhD Thesis,
University of Newcastle, Newcastle Upon Tyne, 267 pp.
Marshall, P., Rezvan, M., 1995. Response based criteria for west of Shetlands. Journal of Offshore Technology 3
(2), 42–45.
Mazaheri, S., 2002. The development of second-order loads and motions of an FPSO as a part of response-based
approach, First PG Research Conference. Dept. of Marine Tech., Newcastle University.
Mazaheri, S., 2003. Response-based analysis of an FPSO due to arbitrary wave, wind and current loads. PhD
Thesis, Newcastle University, Newcastle upon Tyne, UK.
Oortmerssen, G.V., 1976. The Motions of a Moored ship in Waves. PhD Thesis, TU Delft, Wageningen, 138 pp.
Pinkster, J.A., 1975. Low-frequency phenomena associated with vessels moored at sea. Society of Petroleum
Engineers Journal 1975;, 487–494.
S. Mazaheri, M.J. Downie / Ocean Engineering 32 (2005) 363–393 393
Roskilly, A.P.R., Mesbahi, E., 1996. Marine system modelling using artificial neural networks: an introduction to
the theory and practice. Transactions of the Institute of Marine Engineers 108 (Part 3).
Salvesen, N., Tuck, E.O., Faltinsen, O., 1970. Ship motions and sea loads, The Society of Naval Architects and
Marine Engineers 1970 p. 6.
Standing, R.G., Thomas, D.O., Ahilan, R.V., Corr, R.B., Snell, R.O., 1997. The development of a response-based
design methodology for FPSOs in exposed locations, Conference on Progress in Economics, Design and
Installation of Moorings and Anchors to Realise the potential of Deep Water fields, Aberdeen 1997.