MaT
SNetherlands
Marine Technological Research7
7
MOORING LINE DYNAMICS Phase II - Part I
Correlation study: Analysis
MaTS report VM-V-5 III
November 1984
L
Netherlands Industrial Council for Oceanology
P1984-1
-VOL.3
Industriele Raad voor de Oceanologie
Marien Technologisch Speurwerk
The Netherlands Industrial Council for Oceanology (IRO) and its Marine Technological Research (MaTS)
From the start in the early sixties Dutch industry was involved in the development of the oil and gas resources of the North Sea. The first platforms on the southern part of the UK Continental Shelf were
constructed and installed by the Dutch. From then on the Dutch industry has been building up its name and reputation in all activities related to
design, construction and installation of equipment for exploration and development of oil and gas.
Soon the need was felt for a co-ordinating body to further the interests of the Dutch offshore industry.
To this end the Netherlands Industrial Council for Oceanology (IRO) was founded in 1971. In this context the term oceanology referred to coastal engineering, underwater technology, sea-mining, shipbuilding, energy
production, equipment manufacture, offshore supply, fishery and recreation and related advisory and supervisory activities amongst which pollution control.
The activities of IRO were, however, soon focussing on the production of oil and gas offshore. By now some 250 companies involved in
above-mentioned activities have become member of IRO. Through the years the IRO has grown to the following set of tasks:
it forms a platform for all people involved in offshore activities in the Netherlands;
it provides information on offshore activities in the world. One of the channels of information is formed by the 'IRO-Journal' a weekly which gives a short overview of up-to-date information;
it provides information on its members to interested parties. Amongst others the IRO is present on the main offshore exhibitions in the world representing its 240 members. Furthermore IRO publishes the Netherlands Offshore Catalogue, in which it gives descriptions of its member
companies and their activities;
it takes care of contacts with government authorities, taking a seat in scientific committees and other consultative bodies;
it stimulates and draws attention to new possibilities in the field of oceanology which might become of economical importance;
it co-ordinates combined efforts of groups of several companies to operate on foreign markets;
it initiates, co-ordinates and desseminates results of applied research in the offshore field through its Marine Technological Research (MaTS) efforts.
MaTS projects are jointly financed by government and industry. They are meant to raise the standard of Dutch offshore technology and they are aimed at satisfying the need for knowledge on middle long term. It is the responsibility of the MaTS organisation to sort out strategic research
fields within the offshore context and to develop relevant projects in these fields; futhermore to promote and manage these projects and to disseminate the results.
c\17
c.svL_1 e Di
Netherlands Ship Mode! Basin
The VVageningeniEde Laboratories of Maritime Research Institute Netherlands
(MARIN)
2. HaacFeeg: P.O. Bor a 673C AA Wageningen.
The Ne;heriands
Telephone + 31 8370 93911. Teiex 45148 nsmb n1 Ede Laboralory. 10. Niels 53-irs1raa 6716 AM Ede Teleb,.one + 31 8383 37177
7
Report No. 45064-3RD
MOORING LINE DYNAMICS
Phase II Part 1
Correlation Study: Analysis
Report No. 45064-3-RD
MOORING LINE DYNAMICS
Phase II - Part 1
Correlation Study: Analysis
N.S.M.B. Order No. Z 45064
Ordered by: Industriele Raad voor de Oceanologie Marien Technologisch Speurwerk (MaTS)
Project VM-V-5
Postbus 215 2600 AE DELFT
Reported by: Ir H.J.J. van den Boom
Approved by: Dr Ir G. van Oortmerssen
HOEDs
Netherlands Ship Model Basin
-1-Report No. 45064-3-RD CONTENTS Page INTRODUCTION 3 MODEL TESTS 4 SIMULATIONS 7 DISCUSSION 9 CONCLUSIONS 16 NOMENCLATURE 18 Photographs 19 Tables (6) Figures (33)
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-2-Report No. 45064-3-RD
1. INTRODUCTION
As part of the MaTS research program, MARIN performed an extensive
investigation into the "Dynamics of mooring lines". This project
comprised the development of a computer program named DYNLINE for the prediction of the dynamic behaviour of anchor chains and steel wires due to upper-end oscillations. The first phase of this study,
viz, the development of the mathematical model, is discussed in
MARIN Report No. 45064-2-RD.
The present report describes the results of phase II; a correlation study on harmonic oscillation model tests and DYNLINE simulations. The test program comprised water depths of 75, 150, 300 and 608 m. The mooring lines investigated were single component 76 mm and 152
mm chains, 76 mm steel wire and a 76 mm chain-wire combi-line. In
total eleven combinations of mooring lines and water depths were
subject of study. A review of these situations is given in Table 1.
For each situation five frequencies of horizontal oscillation in
the range of the wave frequencies were applied. For several situa-tions various amplitudes of horizontal oscillasitua-tions as well as ver-tical oscillations were part of the test program.
In addition to the measurements of upper-end and lower-end line
forces, the motions of the line at one marked position were
re-corded by underwater video.
All data concerning the configurations of the test program and the relevant results of the experimental and numerical tests are pre-sented separately in part 2 of this report (Report No. 45064-4-RD) entitled: "MOORING LINE DYNAMICS, Phase II - Part 2, Correlation Study: Data Report"
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2. MODEL TESTS
The tests for 75, 150, and 300 m water depth were carried out in
the Basin for Unconventional Maritime Structures at a scale of
1:19, 1:38 and 1:76, respectively. The dimensions of this basin are 220 m x 4 m with a water depth of 3.98 m. The tests for 608 m water depth were performed in MARIN's Vacuum Towing Tank, measuring 240 m
x 18 m x 8 m, at a scale of 1:76. The depressurizing options of
this facility were not utilized during this test program. All tests were carried out in accordance with Froude's law of similitude.
A special mechanical oscillator (shown by photographs on page 19)
was used to enforce sinusoidal motions at the upper-end of the
line. This device was built of a steel frame connected to a driving shaft by means of three worm-gear transmissions. Each frame
connec-tion was free to rotate in the vertical plane of the frame but
could be fixed to the frame with respect to the horizontal motions (outer gears) and vertical translatory motions (centre gear). The
stroke of each gear was adjusted by
means of a high accuracy
spindle. The frequency of oscillation was adjusted by the number of revolutions of an electromotor which was connected to the central shaft by means of a non-slip nylon belt. A guiding system prevented transverse motions of the steel frame.
Although this test set-up enables arbitrary two-dimensional ellip-tical motions, only pure sinusoidal horizontal and verellip-tical
oscil-lations were generated in this test program.
The oscillator was firmly connected to the towing carriage, above the basin, parallel to the side walls of the basin. The upper-end of the mooring line was connected to the oscillator frame by means
of a roller type bearing with a 2-component strain gauge force
transducer in it's centre (see photographs on page 19). The centre
of the force transducer was approximately 3 cm above the basin's
water level.
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Report No. 45064-3RD
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5
The anchor-end of the line was connected to a tank-fixed space
frame in the 4 m deep tank and to a heavy weight in the 8 m deep
tank. During all tests the line was parallel to the tank wall at a distance of approximately 1.5 m (4 m basin) and 8 m (8 m tank) from the nearest tank wall.
For the present test program of the same model chains were used as
tested in phase I. The particulars of these chains are listed in
Table 2 while a photograph is presented in Report No. 45062-2-RD. The 76 mm steel wire was geometrically scaled with respect to its
diameter. By use of flexible 1 x 19 steel model wires the
elasticity however was not correctly scaled as indicated in Table
2. The line length to water depth ratio amounted to 7 for all
situations except for situation No. 11 where a ratio of 5 was
applied.
Prior to the testing all model lines were "statically"
pre-ten-sioned up to a high percentage of their breaking strengths.
Following this static loading, each line was subjected to artifi-cial ageing by means of high frequency-large stroke oscillations in the test set-up. This loading is aimed at removing plastic deforma-tions and hysteresis elongation effects known to be linked to new
chains and steel wires.
After this procedure the required initial tension To (at the mean upper-end position) was adjusted by moving the towing carriage. At the correct tension the carriage was fixed to the tank by means of pneumatic break devices. Pre-tensions of approximately 30 per cent of the breaking load were adjusted in order to include the mean and low frequency excursions of the upper-end of the line due to the motions of a floating structure. Since the test program contained geometrically similar situations (Table 1) some information on the effect of pre-tension could be extracted from the test results by means of scaling. After the pre-tension (To) was adjusted and the
carriage fixed, the maximum quasi-static tensions (T0+) were measured by applying the maximum excursions (stroke).
Report No. 45064-3-RD
KOMM:
Netherlands Ship Model Basin
-6-During all tests, which had a duration of approximately 300 seconds
at full scale, the upper-end vertical and horizontal line force components and the tension at the anchor point were measured. The oscillatory motion of the upper-end was measured by means of a po-tentiometer device. After preliminary on-line statistical analysis and an inspection on Ultra-Violet paper charts, the oscillation and the forces were recorded on magnetic tape at a sampling rate of 25 Hz (model scale) for further analysis.
During all tests underwater video recordings were made of a line mark located at approximately 2.23 m (model scale) from the
upper-end of the line. For this purpose a video camera was positioned
athwart of this mark at a distance of approximately 2.0 m (model
scale). In order to quantify the recorded motions a wire grid with
a mesh width of 0.15 m was placed parallel to the line at a
dis-tance of approximately 0.30 m (model scale).
The system of co-ordinates used is given in Figure 1.
Neglecting the transient starting phenomena, the recorded tension
records were used to derive the maximum dynamic tension (T+). To
this end the average value of some 20 tension peaks was taken.
Plots of the measured records are given in Figures 16 through 121 in Part 2 of this report.
For all tests the so-called "dynamic amplification factor" defined as the ratio of the maximum tension in the real dynamic situation (T+), to the maximum quasi-static tension corresponding to the same maximum excursion in the dynamic case (To+)
A review of all tests and the ensuing results are presented in
Tables 4, 5 and 6. For each configuration the dynamic tension am-plifications are plotted on the basis of the frequency of oscilla-tion in Figures 21 through 33.
Report No. 45064-3-RD
3. SIMULATIONS
For all situations tested in the model basins, time domain computa-tions were carried out by means of the program DYNLINE.
The static line configuration at the pre-tension adjusted in the
basin, required by DYNLINE, was computed by MARIN's computer pro-gram FLEX3D. This program allows arbitrary line components and
three-dimensional line loading to be considered and generates posi-tion and tension at each required posiposi-tion along the line.
The line discretizations chosen as input for DYNLINE are presented together with the line characteristics in Figures 2 through 20. It
should be noted that the line mass, underwater weight, volumetric
diameter and elasticity were scaled from the model values
deter-mined experimentally (Table 2).
For each configuration a numerical quasi-static analysis was
carried out using DYNLINE by applying a low frequency upper-end
oscillation. Assuming negligible dynamic tension effects, this
pro-cedure was used to verify the input of DYNLINE and to derive the
numerical pre-tension and maximum quasi- static tension.
The integration time step was adjusted to a value which provided
numerical stability at a maximum of 25 Newton-Raphson iterations at each time step and a tension criterion of 1 per cent. In this way time steps of 0.1 and 0.2 seconds were used for the lower frequen-cies and small amplitudes in case of the chain configurations. For the other situations the time step had to be reduced to 0.01 s for severe steel wire dynamics.
The sea floor spring stiffness used corresponded to a static
de-flection of 0.10 m for the lower water depths up to 0.50 m for 608
m. These seafloor springs contained a critical damping term in
order to prevent bottom impact resonances.
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Time record plots of the forced oscillation, the end-tensions and
the motions at the "video-mark" node are presented in Part 2 of
this report for the oscillation frequency of 1.0 rad/s.
It should be noted that the plotting routine utilized a sampling
rate equal to the DYNLINE integration time step, whereas the model test results have been plotted at a sampling rate of 25 Hz divided by the model scale squared according to Froude's law of similitude.
As already noticed in Report No. 45064-2-RD, the computed tension
records contain in general high frequency parasitical components
due to the line discretization. Therefore the maximum dynamic ten-sion was derived from the low-pass filtered upper-end tension for those situations where parasitical components were observed. Time record plots of these filtered tensions are included in Part 2 of
this report.
Similar to the experimental procedure, dynamic amplification fac-tors (T+/T0 +) were derived from the numerical results (Tables 4, 5 and 6) and are presented in the Figures 21 through 33.
Report No. 45064-3-RD
4. DISCUSSION
Chains
In the water depth of 75 m for both the 76 mm and 152 mm chains a
good agreement was found between experimental and numerical
re-sults. The time record correlations are affected by some high fre-quency parasitical tensions due to snap-loads occurring in the nu-merical model when the line has been slack. The tension peaks,
how-ever, show a perfect agreement as illustrated by Figures 23a and
23b in Part 2. The dynamic amplification factor increased rapidly for frequencies of oscillation larger than 0.5 rad/s. It should be
noted, however, that the stroke of oscillation was kept constant at
all frequencies. Hence for the higher frequency region this
re-sulted in unrealistic excitations. Nevertheless the agreement
between DYNLINE and model test results was reasonable. For the
highest frequencies some overpredictions as well as underprediction
was found.
In 150 m water depth the agreement between the measured and
compu-ted tensions was less satisfactory for the 76 mm chain. In this
situation a clear underprediction (10 to 25 per cent) was given by
DYNLINE for all amplitudes of oscillation in both the horizontal
and vertical mode. The largest differences were found in the drag dominated region (Figure 24). Even for conditions yielding nearly sinusoidal tension records (no slackness) these differences were found (Figure 34 in Part 2). For the large amplitudes of oscilla-tion the measured tension records showed a typical peak enhancement while the numerical results are characterized by broad global peaks
with several secondary oscillations superimposed which were however removed by low-pass filtering (Figure 38 and 45 in Part 2).
-No explanation could be given for the differences in dynamic ampli-fications. Since these discrepances are observed in the drag domi-nated region, one may suspect the drag modelling to fail.
On the
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Netherlands Ship Model Basin
10
other hand however it should be pointed out that the same model
test set-up was used for situation No. 8 which provided a good
agreement between model test and numerical results.
The amplitude dependency of the dynamic effects was similar in
model tests and numerical model (Figure 24). When comparing hori-zontal and vertical oscillation results, it may be concluded that
for the vertical mode the dynamic effects are slightly less and
shifted to higher frequencies. The line discretization (16 nodes)
for the 76 mm chain
was also used for situation No. 5 (152 mmchain). These simulations resulted in a perfect deterministic agreement with the measured tensions for all amplitudes of
oscil-lation (Figure 26). The increase in amplitude of excitation resulted in an increase of maximum dynamic amplification which oc-curred at lower frequencies of oscillation. The reduction of dynam-ic effects at high frequencies, due to the reduction of global line motions, is clearly indicated by Figure 26. The model test results for the large strokes (Figure 65 in Part 2) show that, the start of each tension peak after slackness is the low frequency equivalent of the high frequency oscillatory numerical results. From the same
records it can be concluded that the maximum tension amplitude is almost equal for both line ends. Besides the "harmonic" components,
the measured tension records also contained some low frequency
effects, possibly due to higher modes of line motion or
three-di-mensional motions. Such effects were not found in long duration
simulations.
Since situation No. 5 basically describes the same geometrical con-figuration as situation No. 1, some information on the effect of pre-tension on the dynamic behaviour of the line is also included in this test program. Scaling the results of situation No. 1 by a factor 2 for the motions and consequently by 8 for tensions and
1//2 for the frequencies of oscillation, dynamic amplification factors for situation No. 5 were derived for a pre-tension of
Report No. 45064-3-RD
Netherlands Ship Model Basin
the 152 mm chain breaking load. In this taut condition, with only
200 m (out of 1050 m) line at the sea floor, the dynamic effects
were slightly higher when compared with the 5000 kN initial tension (Figure 26). It should be noted, however, that the maximum quasi-static tension (T0+) amounted to approximately 16,000 kN which
almost equals the breaking strength of the full scale chain.
For the deep water situations No. 7 and 8 (300 m) both the 76 mm and 152 mm chain resulted in broad tension peaks. Slackness in the line occurred at the upper-end during a fraction of each oscilla-tion period but longer so at the lower-end. For both situations a perfect deterministic agreement between measurements and computa-tions was found (Figures 29 and 30). In the numerical results, sec-ondary tension components at the tension peaks caused a tension
in-crease up to approximately 10 per cent which was removed by low
pass filtering. Some discrepancies at the higher frequencies may be
due to (3 dimensional) higher modes of motions and test set-up
vibrations.
As situation No. 8 is geometrically similar to situation No. 4, the results of the latter configuration were also scaled to situation No. 8 in order to investigate the influence of pre-tension (Figure 30). The same conclusions drawn from the situations No. 1 and 5 can be deduced there.
In general terms the agreement between experimental and numerical results is good for all chain-water depth combinations with the
ex-ception of situation No. 4. At a pre-tension of 30 per cent of the breaking strength, the chains show important dynamic effects in the drag dominated frequency region (0.50 - 0.30 rad/s). At high fre-quencies of oscillation extremely large dynamic amplifications of tension were observed, but it is emphasized here that the amplitude of oscillation was unrealistically large regarding the motions of present-day moored floating structures.
Report No. 45064-3-RD
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Netherlands Ship Model Basin
-12-On the basis of Figure 26, a strong dependency of dynamic tensions on the amplitude of oscillation can be concluded. It should be not-ed, however, that this effect may originate from the strongly non-linear static load-excursion relationship of this configuration.
The results of situations No. 1 and 4 were scaled to compare with
those of configurations of No. 5 and 8 respectively, and it was
found that the dynamic amplification does not strongly
depend on the "pre-tension" (at 30 and 60 per cent of the breaking strength)
in these cases.
The dynamic effects seem to reduce with an increase of
water depth.
Knowing that tangential upper-end motions dominate the dynamic
fects, this apparent reduction can be explained by geometrical
ef-fects and the increase of constant tension by the weight of
the free hanging chain.
The 152 mm chain exhibited lower dynamic amplifications
in 75 m of water when compared with the 76 mm chain, but a strong enhancement for 150 m and almost equal values for 300 m.
Steel wires
As already stated in Section 2, the 76 mm steel wire mooring line was not correctly to scale with respect to the line elasticity. The
elasticity of the model wires used, corresponded to full scale
lines with a stiffness which is 10 to 60 times the actual values in use for aged offshore mooring lines (see Table 2). The results ob-tained from model tests and DYNLINE simulations
can therefore not
be considered as realistic but should be used
for correlation
purposes only.
Furthermore it should be noted that the "pre-tension" used for the steel wire differed from the chain values for practical
Report No. 45064-3-RD
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Netherlands Ship Model Basin
-13-For the 75 m water depth (situation No. 3) a pre-tension of 420 kN was adjusted. In this situation the 525 m long line was completely free from the sea floor. These tests yielded smooth tension
peaks
with long periods of slackness even at low frequencies of oscilla-tion. This means that the line "flies" in the water under the in-fluence of inertia (gravity) and drag only, as was clearly observed during the model tests.
A good agreement with the DYNLINE results is shown by Figure 23. It
appeared that the dynamic effects grew rapidly with increasing fre-quencies but reduced again at frefre-quencies above 1.0 rad/s.
In situation No. 6 (150 m water depth, pre-tension 811 kN) the dy-namic amplification started at low frequencies of oscillation and increased 4 up to 7 at its maximum. Figure 27 shows these results, illustrated a reduction of the dynamic ratio with increased stroke. The absolute magnitude of maximum tensions, however, increased with
the stroke but not as much as the maximum quasi-static values.
Though the differences for the smaller amplitude are significant, DYNLINE provided reasonable results for the larger amplitudes.
The
differences in this trend may be explained by the small shift in the initial condition and the strong non-linearity of the
static
load-displacement curve. Configuration 6 was also subjected to
vertical oscillations (Figure 28).
Figure 31 summarizes the results for situation No. 9. The effects observed in situation No. 6 were more pronounced here. Evaluating
the discrepancies between numerical and experimental results it
should be noted that the static load of the model wire is extremely non-linear due to the large material stiffness. Comparing the ex-perimental quasi-static tensions with those obtained_from DYNLINE,
it can be concluded that the material stiffness may be one of the explanations for the differences found, since the bending
stiffness
Report No. 45064-3-RD
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-14-Since the full scale material elasticity and pre-tension was not
kept constant for all test situations no general conclusions with respect to the effects of water depth and pre-tension can be drawn. Also a comparison with mooring chains cannot be made. Taking into account that the differences between model tests and numerical
re-sults decrease with reduction of the material elasticity of the
model wire (Figures 31, 27 and 23 respectively), it may be expected that for realistic material elasticities DYNLINE will provide valid
results.
Combi-lines
Composite lines built up from 76 mm chain (lower half) and 76 mm wire (upper half) were tested in water depths of 300 m (situation No. 10) and 608 m (situation No. 11).
Both situations were tested at a scale of 1:76. Hence, during the model tests of 1 mm chain and 1 mm wire of equal length was used. It should be noted that at full scale the steel wire dominates the elasticity of such lines while in the model tests the wire section hardly contributed to the line elongation. The static configuration for these situations featured long on-bottom line sections as shown by Figures 19 and 20. Using total line lengths of 2100 m and 3040 m
for 300 m and 608 m water depth respectively, 80 per cent of the
chain was on the sea floor in both static configurations.
The tests at both water depths provided nearly the same results
when comparing the tension records (Figures 112 and 118 in Part 2) and the dynamic amplification ratios (Figures 32 and 33). In par-ticular, situation No. 10 yielded dynamic tension contributions at low frequencies of oscillation as demonstrated by extra model tests and simulations for 0.13 and 0.25 rad/s. The dynamic amplification
of tension is almost constant for frequencies above 0.50 rad/s
(Figures 32 and 33). The test results were slightly overpredicted by DYNLINE for situation No. 10 and confirmed for situation No. 11.
Report No. 45064-3-RD
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-15-The numerical tension records showed the usual high frequency
os-cillation at the start of each tensioning after slackness. Some
tension variations at these points were also observed in the mea-sured records. The simulated tension peaks showed also additional
frequency components which were suspected to be due to numerical
effects and use of low-pass filtering a perfect agreement with the experimental records was found.
When compared to the single component steel wires and chains, the
combi-lines featured extra tension amplification in the low
fre-quency region but a clear reduction of dynamic effects at higher
frequencies. As stated before, the dynamic tension effects are
mainly due to tangential upper-end oscillation, therefore the
initial vertical upper-end line angle should be taken into account
when evaluating the differences between the results of different
configurations. Vertical components of upper-end motion may contribute significantly in configurations with large 4,-values
(Figure 1).
Motions recorded by underwater video
A good qualitative agreement was found between the motions recorded
by video and corresponding node motions computed by DYNLINE. The
amplitudes of motion appeared to exceed the computed values by some 5 to 10 per cent, but this may be due to the distance between the line and the wire grid and the direction of the video which was not completely perpendicular to the mooring line.
Report No. 45064-3-RD
5. CONCLUSIONS
From the deterministic correlation between the results of the
harmonic oscillation model tests and mathematical simulations for
eleven combinations of different water depths and types of mooring lines, the following conclusions can be drawn:
The computer program DYNLINE provides accurate tension records
due to harmonic upper-end line oscillations.
Frequency independent (average) hydrodynamic coefficients
ob-tained from model tests can be used to describe the fluid reac-tive forces on the line.
The "Dynamic amplification ratio" for tension as defined in the
present study strongly depends on non-linearity of the static
load-excursion relation- ship of the mooring line and should
therefore be treated with care.
Dynamic amplification of tension may be considerable especially for combinations of high amplitudes and high frequencies of oscillation.
The influence of the direction of motion on the dynamic tension strongly depends on the configuration. Keeping in mind that in-line upper-end oscillations will dominate the dynamic behaviour of the line, it is preferable to define the motions in terms of "tangential" and "normal" rather than vertical and horizontal
di-rections.
The ultimate amplification of tension strongly depends on the
motion characteristics of the floating structure at higher fre-quencies (0.5 - 1.5 rad/s).
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l6-Report No. 45064-3-RD
- Chain-wire combi-lines exhibited dynamic amplification even at
low frequencies of oscillation (0.25 - 0.50 rad/s).
Wageningen, November 1984. NETHERLANDS SHIP MODEL BASIN
Dr Ir M.W.C. Oosterveld
Head Research and Development Division
AGvD/gt
HOHM
Report No. 45064-3-RD
NOMENCLATURE
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Netherlands Ship Model Basin
B = width
BS = breaking strength
D = diameter
dc = volumetric diameter
EA = product of line elasticity and cross-section area
FX = horizontal upper-end force component
FZ = vertical upper-end force component
FX-A = tension at anchor point
L = length
M = mass
S = stroke T = tension
To = initial tension or "pre-tension"
T +0 = maximum quasi-static tension T+ = maximum dynamic tension
W = weigth
A = model scale
= vertical line angle in rad
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Mooring Line Dynamics
REVIEW OF SITUATION No. 1 TO 11
NOTE: * Horizontal and vertical oscillations
° Situation No. 4 corresponds to situation No. 8 by scaling Situation No. 1 corresponds to situation No. 5 by scaling
Netherlands Ship Model Basin
Table 1
Water depth 75 m A = 19 Water depth 150 m A = 38 Water depth 300 m A = 76 Water depth 608 m A = 76 Chain D = 0.076 m Situation 10 Situation 4*0 Situation 7 -Chain D = 0.152 m ---Situation 2 Situation 5° Situation 8° Steel wire D = 0.076 m Situation 3 Situation 6* Situation 9 Combi-line D = 0.076 m Situation 10 Situation 11Report 45064-3-RD
Mooring Line Dynamics
PARTICULARS OF ANCHOR CHAINS Chain type: DIN 766 (D = 0.076 m)
PARTICULARS OF STEEL WIRES
(D = 0.076 m)
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Table 2
Model chains Prototype chain
o BS = 4.38*106 N - EA = 0.694*10- N D B L M W d EA A M W , d EAa mm mm mm kg/m N/m inc N*105 kg/m N/m mc N*10-1.0 4.2 7.9 0.021 0.177 0.0019 0.03 76 124 1043 0.144 1.19 2.0 6.8 12.0 0.080 0.690 0.0036 0.11 38 119 1021 0.137 0.60 4.0 14.2 22.8 0.338 2.374 0.0076 7.00 19 125 1063 0.144 4.90 8.0 26.9 40.1 1.383 11.801 0.0151 22.00 9.5 128 1092 0.144 1.93
Model wires Prototype wire
8 EA = 3.2*10S N - 4.4*10 N _ D mm M kg/m W N/m dcm EA 5 N*10 A m kg/m W N/m dcm EA N*1010 1.0 0.00401 0.034 0.001 0.5 76 23.2 204 0.076 2.3 2.0 0.0164 0.144 0.002 2.3 38 24.3 213 0.076 1.3 4.0 0.0608 0.540 0.004 5.1 19 22.5 199 0.076 0.36
Report No. 45064-3-RD
Mooring Line Dynamics
DYNLINE INPUT DATA
Static deflection of sea floor (depend on water depth)
Time increment (depend on situation)
Starting time
Duration of simulation
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0.10 - 0.50 m
0.01 - 0.20 s
2 oscillations 5 oscillations
Table 3
Line discretization according to Figures 2
- 20
Line data according to Table 2
Normal added inertia coefficient 1.60
Tangential added inertia coefficient 0.20
Normal drag coefficient 1.30
Tangential drag coefficient 0.40
Report No. 45064-3-RD
Mooring Line Dynamics
REVIEW OF THE TESTS AND THE RESULTS
K2HT131
Table 4
Netherlands Ship Model Basin
Oscillation Model test DYNLINE
Situ-at ion Test No. Fre-quency LA) Stroke s Quasi-static Dynamic Dynamic ratio Quasi-static Dynamic Dynamic ratio No. in rad/s in m T0 in kN T + 0 in kN T+ in kN T+ T 0 in kN T + 0 in kN T+ in kN T+ T + 0 T +0 1 6654 0.51
2.0
1259 1995 2720 1.36 1280 2000 2818 1.41 66580.76
3670 1.84 4040 2.02 6655 1.01 5460 2.74 5416 2.71 6656 1.26 7040 3.53 7417 3.71 6657 1.50 8160 4.09 8949 4.47 2 6682 0.52 1.5 5095 7040 7040 1.00 5040 6936 7101 1.02 6685 0.76 8640 1.23 8421 1.21 66830.99
11200 1.59 10835 1.56 6684 1.23 16880 2.40 15222 2.19 6686 1.45 21440 3.05 19775 2.85 3 6790 0.352.0
420 2890 3040 1.05 376 2834-
-67850.50
3520 1.22 3669 1.29 6786 0.75 4180 1.45 4542 1.60 67880.89
4380 1.52 4880 1.72 67870.99
4520 1.56 5117 1.81 6791 1.25-
-
5000 1.76 6789 1.47 4800 1.66 3700 1.31 4 6710 0.522.0
1324 1535 1960 1.28 1319 1482 1754 1.18 6711 0.77 2420 1.58 2055 1.39 6712 1.02 2800 1.82 2244 1.51 6713 1.26 3020 1.97 2362 1.59 6714 1.50 3100 2.02 2595 1.75 4 6697 0.514.0
1324 1792 3000 1.67 1319 1688 2459 1.46 6698 0.75 3780 2.14 2983 1.77 6699 0.97 4140 2.31 3294 1.95 6700 1.22 4220 2.35 3422 2.03 6701 1.46 4000 2.23 3714 2.20 6702 1.92 3960 2.21 3718 2.20 4 67046705 0.510.766.0
1324 2082 4160 2.00 1319 1937 3278 1.69 4960 2.38 3913 2.02 6706 1.01 5230 2.51 _ 4029 2.08 6707 1.24 5000 2.40 4527 2.34 6708 1.47 4840 2.32 4745 2.45 4 6716 0.514.0
1369 1463 1840 1.26 1396 1505 1806 1.20 6717 0.77 2400 1.64 2171 1.44 VER- 6718 1.01 2860 1.95 2365 1.57 TICAL 6719 1.26 3140 2.15 2411 1.60 6720 1.49 3180 2.17 2435 1.62Report No. 45064-3-RD
Mooring Line Dynamics
REVIEW OF THE TESTS AND THE RESULTS
* Low-pass filtered
DD
Netherlands Ship Model Basin
Table 5
Oscillation Model test DYNLINE
Situ-Test Fre- Stroke Quasi- Dynamic Dynamic Quasi- Dynamic Dynamic
ation quency static ratio static ratio
No. w S No. in T0 T +0 T+ T+ T0 T +0 T+ T+ T0+ To+ rad/s in m in kN in kN in kN in kN in kN in kN 5 6668 0.51 2.0 5012 5880 6400 1.09 5110 5845 6312 1.08 6672
0.76
8000 1.36 8130 1.39 6669 1.01 10290 1.75 9454 1.62 6670 1.25 14240 2.42 13673 2.34 6671 1.48 23040 3.92 21600 3.70* 5 6663 0.514.0
5012 6725 9600 1.43 5110 6753 10157 1.50 66670.76
14320 2.13 14747 2.18 6664 1.01 276004.10
28000 4.15* 6665 1.25 40160 5.97 40800 6.04* 6666 1.48 42400 6.30 388005.75'
5 6673 0.516.0
5012 8140 15760 1.94 5110 8098 16754 2.07 66760.76
28960 3.56 27500 3.40* 6674 1.00 49200 6.04 50400 6.22* 6675 1.25 55600 6.83 551006.81'
6677 1.47 54500 6.70 448005.53'
6678 1.91 45440 5.58-
-6 6773
0.25
2.0
811 1240 2200 1.77 799 1215-
-6768 0.51 4180 3.37 4300 3.54 6769 0.76 5360 4.32 6235 5.13 6770 1.00 6040 4.87 7544 6.21 6771 1.25 6420 5.18 8600 7.08 6772 1.48 6600 5.32 9000 7.41 6 6767 0.25 3.0 811 2022 4160 2.06-
-
-
-6762 0.51 7180 3.55 _ _ 67630.76
8520 4.21-
-6764 1.00 9200 4.55-
-6765 1.25 9440 4.67-
-6766 1.46 9640 4.77
-
-6 6761
0.25
3.5 811 2797 5040 1.80 799 3680-
-6756 0.50 8380 3.00 11050 3.00 67570.76
9800 3.50 13300 3.61 6758 0.99 10600 3.79 _ 14270 3.88 6759 1.24 10650 3.81 15440 4.20 6760 1.46 10700 3.83 - -6 6780 0.25 2.0 842 885 940 1.06 830 875 - -6775 0.51 1160 1.31 1120 1.28 VER- 6776 0.76 1420 1.60 1440 1.65 TICAL 6777 1.00 1680 1.90 18202.08
6778 1.25 2000 2.26 2227 2.55 6779 1.48 2350 2.66 3000 3,43Mooring Line Dynamics
REVIEW OF THE TESTS AND THE RESULTS
* Low-pass filtered
Netherlands Ship Model Basin
Oscillation Model test DYNLINE
Situ-ation Test Fre-quency Stroke Quasi-static Dynamic Dynamic ratio Quasi-static Dynamic Dynamic ratio No. U) S No. in T0 T +0 T+ T+ T0 T +0 T+ T+ T0+ To+ rad/s in m in kN in kN in kN in kN in kN in kN 7 67296730 0.51
4.0
1346 1460 2040 1.40 1330 1428 1970 1.38 0.76 2640 1.81 2528 1.77 6731 1.00 33002.26
2900 2.03* 6732 1.23 3350 2.33 3000 2.10* 6733 1.46 31402.15
2500 1.75* 8 67230.51
4.0
4972 5472 6800 1.24 4985 5360 6438 1.20 6724 0.75 8960 1.64 8152 1.52 67250.99
124002.27
11600 2.16* 6726 1.21 14400 2.63 12200 2.27* 6727 1.44 140002.56
11200 2.09* 9 6735 0.514.0
1351 1694 8000 4.72 1335 1770 114406.46
6736 0.75 9100 5.37-
-6737 1.00 9350 5.51 14600 8.25 6738 1.22 9300 5.49
-
-6739 1.46 8910
5.26
155008.76
10 67546753 0.134.0
1245 1763 2040 1.16 1240 1716 1915 1.15 0.25 2860 1.62 2663 1.60 6748 0.49 3500 1.99 3684 2.21 6749 0.73 37602.13
39002.30*
6750 0.97 3920 2.22 4000 2.33* 6751 1.20 38602.19
4300 2.51* 6752 1.43 3740 2:12 39002.27*
11 1130101130110.25
4.1
1298 1480 2060 1.39 1250 1475 2080 1.41 0.49 2840 1.92 2896 1.96 113014 0.73 32802.22
3300 2.24* 113015 0.96 3440 2.32 3330 2.25* 113016 1.19 33802.28
32002.17*
113017 1.41 31602.14
32002.17*
113018 1.69 2700 1.82-
Report No. 45064-3-RD
Mooring Line Dynamics
MODEL TEST SET-UP AND DEFINITIONS
Z
HOHM,
Fig.
1Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 1 Water depth Chain diameter Chain length Oscillation Sx Quasi-static T0 Quasi-static T0+ 0
HOEM
Netherlands Ship Model Basin
75.0 0.076 m 525.0 2.0 1259.0 kN 1995.0 kN Fig. 2 13 99.8 m 416.3 m
Report No. 45064-3-RD
/
///A\\\\\\\\\w////7//<\\
Mooring Line Dynamics
SITUATION No. 2 Water depth 75.0 Chain diameter 0.152 m Chain length 525.0 Oscillation Sx 1.5 Quasi-static T0 5095.0 kN Quasi-static T0+ : 7040.0 kN Lk'1'
M113
1 3 123.1 mNetherlands Ship Model Basin
392.9 m
Video mark
Fig. 3
13
Report No. 45064-3-RD
1
/ ///A\\\\\\\\\V/ ///// /,<\\
Mooring Line Dynamics
SITUATION No. 3
Water depth 75.0
Steel wire diameter : 0.076 in
Steel wire length 525.0 Oscillation Sx 2.0 Quasi-static T0 420.0 kN Quasi-static T0+ 2890.0 kN
HOE13
Fig. ,4Netherlands Ship Model Basin
12
Video mark
1
Report No.
4 50 6 4- 3-RDMooring Line Dynamics
SITUATION No. 4 Water depth 150.0 in Chain diameter 0.076 in Chain length 1050.0 Oscillation Sx 2.0 Quasi-static T0 1324.0 kN Quasi-static T0+ 1535.0 kN
HOMDs
Netherlands Ship Model Basin
Fig. 5
16
464.3 m
Report No. 45064-3-RD
1
6
464.3 m
Mooring Line Dynamics
SITUATION No. 4 Water depth 150.0 m Chain diameter : 0.076 m Chain length 1050.0 in Oscillation Sx 4.0 in Quasi-static T0 : 1324.0 kN Quasi-static T0+ 1792.0 kN
HOWE)
Fig. 6Netherlands Ship Model Basin
16
562.4 in
Video mark
Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 4
Water depth : 150.0 in
Chain diameter 0.076 in
HOREM
Fig. 7Netherlands Ship Model Basin
16 Chain length : 1050.0 in Oscillation Sx : 6.0 in Quasi-static T0 1324.0 kN Quasi-static T0+ : 2082.0 kN 464.3 m 562.4 m
Report No. 45064-3-RD
1
///
\\\\ \
Mooring Line Dynamics
SITUATION No. 4 Water depth 150.0 in Chain diameter 0.076 in Chain length 1050.0 Oscillation Sz 4.0 Quasi-static T0 1369.0 kN Quasi-static To+ : 1463.0 kN
HOHM
Netherlands Ship Model Basin
Fig. 8
16 6\\\\\\\\(e////////
\\\\
\\V////
464.3 m 562.4 inA
Report No. 45064-3-RD
1
Mooring Line Dynamics
SITUATION No. 5 Water depth 150.0 Chain diameter 0.152 m Chain length 1050.0 Oscillation Sx 2.0 Quasi-static To : 5012.0 kN Quasi-static T0+ 5880.0 kN 6
HOM
Netherlands Ship Model Basin
559.9 m Video mark Fig. 9 16 464.1 m
///11'.
\\\ \,\ W/")11/./W/>/7 4\\
\
1Report No. 45064-3-RD
1
6
\\'' \\'.\\K\7/././
7///i74\\\\\\\
Mooring Line Dynamics
SITUATION No. 5
Water depth 150.0 in
Chain diameter : 0.152 in
HOW:3
Netherlands Ship Model Basin
Fig. 10
16 Video mark/
//,
\
464.1 m 559.9 m Chain length 1050.0 in Oscillation Sx : 4.0 in Quasi-static T0 : 5012.0 kN Quasi-static T0+ : 6725.0 kNA
Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 5 Water depth 150.0 m Chain diameter 0.152 m Chain length : 1050.0 m Oscillation Sx : 6.0 m Quasi-static T : 5012.0 kN 0 Quasi-static T0+ : 8140.0 kN
Netherlands Ship Model Basin
Fig. 11 16
HOhi
D) e_g) 464.1 m 559.9 mReport No. 45064-3-RD
Mooring Line Dynamics
HOME3
Fig. 12
Netherlands Ship Model Basin
13
SITUATION No. 6
Water depth : 150.0 m
Steel wire diameter : 0.076 m
Steel wire length : 1050.0 m
Oscillation Sx : 2.0 m Quasi-static To : 811.0 kN Quasi-static T0+ : 1240.0 kN 200.0 m 836.0 m
Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 6
Water depth 150.0 m Steel wire diameter 0.076 m Steel wire length : 1050.0 m
Oscillation
Sx 3.0 m
Quasi-static
T0 : 811.0 kN
Quasi-static T0+ : 2022.0 kN
Netherlands Ship Model Basin
Fig. 13
13
Report No. 45064-3-RD
/ ///,A\\\\\\W(///
Mooring Line Dynamics
SITUATION No. 6
Water depth 150.0 in Steel wire diameter 0.076 in Steel wire length : 1050.0 in
Oscillation Sx 3.5 in Quasi-static T0 : 811.0 kN Quasi-static T0+ : 2797.0 kN
HOED
200.0 inNetherlands Ship Model Basin
836.0 in
Video mark
Fig. 14
Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 6
Water depth : 150.0 m
Steel wire diameter : 0.076 m
Steel wire length 1050.0 m Oscillation Sz 2.0 m Quasi-static To : 842.0 kN Quasi-static T0+ : 885.0 kN
HOUL3
Fig. 15Netherlands Ship Model Basin
13
Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 7
Water depth : 300.0 m
Chain diameter : 0.076 m
Fig. 16
Netherlands Ship Model Basin
17 Chain length : 2100.0 m Oscillation Sx : 4.0 m Quasi-static T0 : 1346.0 kN Quasi-static T0+ : 1460.0 kN
Report No. 45064-3-RD
Mooring Line Dynamics
HOED
Fig. 17
Netherlands Ship Model Basin
17 SITUATION No. Water depth Chain diameter Chain length Oscillation Sx Quasi-static T 0 Quasi-static T0+ : 8 300.0 0.152 m 2100.0 4.0 4972.0 kN 5472.0 kN
Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 9
Water depth 300.0 m Steel wire diameter 0.076 m Steel wire length : 2100.0 m
Oscillation
Sx 4.0
Quasi-static To : 1351.0 kN
Quasi-static T0+ : 1694.0 kN
HORE
Fig. 18
Netherlands Ship Model Basin
13
1
Report No. 45064-3-RD
830.6 m
Mooring Line Dynamics
Chain diameter : 0.076 m
Wire diameter : 0.076 m
HOREM
Netherlands Ship Model Basin
7
///
.\\\.\\\\W / ///
/ ///
\\\
t////\
2060.3 m Video mark Fig. 19 17 // SITUATION No. 10 Water depth : 300.0 mTotal line length : 2100.0 m
Chain (lower part) : 1050.0 m
Wire (upper part) : 1050.0 m
Oscillation
Sx : 4.0 m
Quasi-static T
0 : 1245.0 kN
Report No. 45064-3-RD
Mooring Line Dynamics
SITUATION No. 11
Water depth : 608.0
Total line length : 3040.0
Chain (lower part) : 1520.0
Wire (upper part) : 1520.0 m
Chain diameter 0.076 m Wire diameter 0.076 m Oscillation Sx 4.1 m Quasi-static T0 : 1298.0 kN Quasi-static T0-1- : 1480.0 kN
HOEM
Netherlands Ship Model Basin
Fig. 20
18
Report No. 45064-3RD
7.5
5.0
2.5
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 1
W in rad/s
HOM,
Fig. 21
Netherlands Ship Model Basin
DYNLINE Measured Oscillation
0
S = 2.0
m0.5 1.0
Report No. 45064-3-RD
7.5
5.0
2.5
0
DYNLINE Measured Oscillation
0
S = 1.5
m0 Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 2
Hnin
Fig. 22
Netherlands Ship Model Basin
0 0.5
1 . 0
15
Report No. 45064-3-RD
7.5
5.0
2.5
DYNLINE
Mooring Line Dynamics
DYNAMIC RATIO Situation No. 3 Measured Oscillation 0 S = 2.0 m w in rad/s
HOMII3
Netherlands Ship Model Basin
Fig. 23
0.5 1.0
Report No. 45064-3RD
7.5
5.0
2.5
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 4
Netherlands Ship Model Basin
Fig. 24 DYNLINE Measured 0 a 0 Oscillation S =
2.0
m S = 4.0 m S = 6.0 m - --, ..---I'' ----
-
---A---
C - --o a - ---o ---_-_-_aLt _ ____ tic--
4,..../-
-- --
-0.5
Jo
1 . 5 w in rad/sReport No. 45064-3-RD
7.5
5.0
2.5
0
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 4 - Vertical oscillation
L) in rad/s
:HOH
Netherlands Ship Model Basin
Fig. 25
0
0.5
Report No. 45064-3-RD
7.5
5.0
2.5
0
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 5
OH73
Fig. 26
Netherlands Ship Model Basin
W in rad/s DYNLINE Measured 0 A 0 A Oscillation S = 2.0 m S = 4.0 m S = 6.0 m S = 4.0 in (From situation
-- T0=
5012 -T0 = 10072 No. 1) kN kN---//
,,,.
Z
cl,
\
0 AA
/I
/
//
/
,/
....\
N.
/
/
/
/
/''1
/
// 0//
,//1(
I/ ,/
,/
/
/
,,e4
.../.2'1/
.///4S/
1' ...,/
.
...--- ... --0.5 1.015
Report No. 45064-3-RD
7.5
5.0
2.5
0
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 6
U) in rad/s
HOU
Netherlands Ship Model Basin
Fig. 27
DYNLINE Measured 0 Oscillation S = 2.0 m S =3.5
m - A . ... ...r. ... ... .../
/
/
__..z ...1 ... ...IV
a.... .../
/
/
/
/
_ 00.5
1.0 1.57.5
5.0
2.5
0
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 6 - Vertical oscillation
Netherlands Ship Model Basin
Report No. 45064-3-RD
TNE75- Fig. 280
0.5
1.0 1.5
W in rad/s
DYNLINE Measured Oscillation
Report No. 45064-3-RD
4.07.5
5.02.5
0Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 7
DYNLINE Measured Oscillation
0 S = 4.0 m
0 0
Ki0a113
Netherlands Ship Model Basin
Fig. 29
0
0.5
1.0
15
7.5
5.0
2.5
0
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 8
w in rad/s
Netherlands Ship Model Basin
DYNLINE Measured Oscillation
0 S = 4.0 m T0=
4772 kN S = 4.0 m
T0 = 10592 kN (From situation No. 4)
----0
-r..--__________..,
-Report No. 45064-3-RD
OM]
Fig. 30
0 0.5
Report No. 45064-3-RD
7.5 5.02.5
0 W in rad/sMooring Line Dynamics
DYNAMIC RATIO
Situation No. 9
Netherlands Ship Model Basin
Fig. 31 DYNLINE 0 Measured Oscillation 0 S = 4.0 m 0 0 0 0 1.5 1.0
0.5
+0
7.5
5.0
2.5
0
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 10
DYNLINE Measured Oscillation
0 S = 4.0 m
0 0 0
_
Report No. 45064-3RD
L'MS DU IFig. 32
Netherlands Ship Model Basin
0
05
1.0 1.5
Report No. 45064-3-RD
7.5
5.0
2.5
0
Mooring Line Dynamics
DYNAMIC RATIO
Situation No. 11
DYNLINE Measured Oscillation
0 S = 4.1 m
HOEMI
Netherlands Ship Model Basin
Fig. 33
0 0.5
1.0