SKIBS -0G HAVTEKNIK
Department öf Ocean Engineering
WA}E: DISTRIBIFI IONS
IDANMARICS TEKNISKE HØJSKOLE
The Technical University of Denmark
LNGBY' Danmark
by
.Sv.Aa.Harvald. and Jan M.He
PREFACE
The paper
WAKE DISTRIBUTIONS was presented 1978.11.22 at the
International Symposium on Future Tasks and Problems
of Model Basins held on the occasion of
75 jAHRE, Versuchsansta].t für Wasserbau und Schiffbau, Berlin 1903-1978
In the introduction to the paper the following was mentioned:
It is always the desire of a propeller designer to design a propeller which would at a certain speed and a certain number
of revolutions absorb a minimum amount of power. Further, it
is necessary that the propeller is free from cavitation and that the pressure variation over the blades and the ship hull
is reasonable, thus avoiding noise and vibration.
In order to get these requirements fulfilled he must know
the velocities with which the water flows to the propeller disc.
In other words, he must know the wake distribution. One
can define wake as the numerical difference between the velo-city of the ship and the velovelo-city with which the water flows
to the propeller. By dividing this difference by the velocity
of the ship the wake fraction is obtained as:
V-V
AV
Primarily it is the effective wake fraction the designer would
like to know, that is the wake fraction determined by the
pro-peller acting as a wake measurer and a wake integrator. By
self propulsion model tests the effective wake fraction is
determined. It looks very simple, but nevertheless there are
torque identity respectively are different; secondly, it
should be noted that repeated experiments, with the same pro-peller or with other propro-pellers having the same diameter and
pitch, do not give same wake fraótions. A standard deviation
up to about 15 per cent can be detected.
Later when designing a propeller by use of the circulation theory it is of interest to know the radial variation of the
wake fraction. The radial distribution of the wake fraction
can be determined by means of blade wheels, resistance rings
or pitot tube measurements. The blade wheel method is the
simplest. The diagrams shown in Fig. i can also be used for
this estimation when taking into account the scale effect and
when a very high degree of accuracy is not required.
0,70
w
0,60 0,50 0h40 0,30 2O 0.2 0/. 0,6 0.8 nR .0.10w
o u-roRW FORP V-6:0.75 65 065 0.7 0.1O0 0,2 Fig.i.
0.70w
0,60 0,40 0,30 FORM CORRECTION L = length of waterline B breadth on waterline D propeller diameter = block coefficient 04 06 08 /R 1.0The radial variation of the wake fraction of
single screw ship models (L 7 m, R = tip
radius and r = distance from axis to section
in propeller blade). °/L WL:Qtl 0.06
IuuIu
I.'mII
Iiil'u'.
-uIiI'
_,.u-r
) 02 04 0S 08 FI1i 'L 4.O.I3 0,04 6:075 0,65w
wmc
(C)
MODEL SCALE 1:6 1:6
R0UGESS I R0UGHSS fl
Fig. ii. The wake distributions for Victory ship models.
SCALE 1:40 1:36
1:25 1:23
1:30
e(a)
Fig. iii. The modified wake distribution of the
scale A = 6 Victory ship model.
With regard to the wake distribution on the propeller disc a vast amount of data has been collected during recent years but
only a few relevant results have been published. 2mong the
pub-lished data there are some from the Dutch: experiments with
models of different scale ratios o the Victory ship. Fig. ii
shows the wake distribution for these models. It will be
no-ticed that the wake field changes from model to model The
very undulated curves are unrealistic and have been modified
later by the model basin (Fig. iii).
From the model experiments the designer had to establish
a picture of the wake field for the real ship.
At present it is almost impossible to solve this problem
in a correct manner for three reasons. Firstly, one has to
evaluate the accuracy of the measurements at every point. It
is our impression that the standard deviation on such wake
measurements is about 0,05. Sometimes at the same point of
the propeller disc there may be differences in wake fraction
values as large as 0,25 for repeated model experiments. Secondly,
C,. -
--
---- /
,,
I
/
--I, Iy
'I*NTARY TESS CI
,
,,
L,j,
!I
I,
/}'
qs'Q-s__)
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i i-!oI,
----s-,. v=,t:3mJg If
-.,
-.'.'-: -
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ojo 60 50 040 30 J---.--i QO QiO SMOOTH MODELFig. iiii. 'Computer rings' in the wake field
behind a single screw ship model.
during the experiments and then the curves for constant wake are
drawn by use of the computer. The contours for constant wake
fractión may take the shape of rings because of the particular interpolatión method used by the computer for plotting Let us call these rings as computer rings. Such rings are shown on Fig.
iiii and-
do not exist in
reality. Thirdly, one has to take intoaccount the scale effect on the wake. In the full-scale trial
condition the mean wake fraction is about 70 per cent of the model wake fraction while the mean wake fraction in the service
condition is nearly the same as that of the model experiment. Still we know very little about the wake field behind the real
ship in relation to the wake field of the model.
Over a number of years our institute has studied wake pro-blems and in the papr some of our latest investigations
re-garding wake diBtributions are reported.
Further, some remarks to the paper are stated in the Ap-pendix after the paper.
WAKE DISTRIBUTIONS
Stmmtary.
In order to get a better insight of the wake field behind a ship and especially to have a better knowledge of the influence of such factors as speed,roughness,stern form and rudder,a series of model experiments were car-ried out. The experience gained concerning these matters is discussed together
with an evaluation of the reliability of the five hole pitot tube measurements.
Introduction.
In the post-war period where the ships have grown bigger and bigger together with an ever increasing speed, there has been an increasing demand for a better knowledge of the wake field behind the ship It has been necessary to introduce a
better and more detailed description of the wake field in order to design more efficient propellers which also had a reasonable pressure variation over the blades and the ship hull thus
avoid-ing noise and vibration.
Today it is more or less a standard procedure to carry out wake measurements together with the more ordinary towing tank
tests when a new ship is being designed. Also a number of full
scale measurements have been taken during special trial trips.
In spite of this vast amount of data collected there is still a considerable lack of knowledge regarding the wake
dis-tribution and the factors influencing it. The object of the investigations.
The main object of the investigation carried out by the 15H was to look for some of the factors involved in shaping the wake field and how they influence. It is of great importance to know this in the search for a method which can predict the wake field for the real ship in a reasonably good and safe manner.
The factors investigated were: - Speed of vessel
- Friction due to roughness
- Form of the sterñ
- Rudder influence,
results the reliability of wake measurements was also
inve-stigated.
3. Description of the tests.
Becaùse the ISH has no test facilities it orders the tests
in a towing
tank in the same way as any shipyard or designof-fice does Also the results are delivered to the ISH in the
same standard fashion as to any other customer.
The wooden model used has the following main particulars:
Lorgitudina1 center of buoyancy is 0,134 in forward of
ainidship. The model corresponds to a bulk carrier of approx.
50.000 t dead-weight. Fig. 1 shows the body plan and the
pro-file of the stern and stem.
Most of the test were carried out without rudder and with
a simplified stern form as shown in Fig. 1. In some of the
last tests series the stern was shaped as shown in Fig. 8. Most
of the tests were carried out with a smooth model. The
inve-stigation of the influence of the roughness was done in the
following way: Streamlines at model speed 1,3 rn/s and 2,0 rn/s
were determined by the wet paint method (Figs. 2, 3 and 4). A strip of coarse sand or rough gravel (granite of size between
4 nun and 8 mm) was glued between streamline 5 at velocity 2,0 rn/s
and a streamline located 60 mm outward from streamline 5 at
midship lection. At first the strip was fitted from midship
to the stern and later for the whole length of the vessel (see
Fig. 4).
At all the tests a row of cylindrical studs of 2,5 mm in diameter was fitted near the stem of the model for turbulence
stimulation.
Length on waterline L = L = 7,534 w
Length between perpendicular = 7,360 in
Breadth moulded B = 1,115 in Draught T = 0,432 w Wetted surface S = 12,087 w2 Displacement V = 2,742 in3 Block coefficient 6 = 0,755 6 = 0,773 pp
Midship section coefficient ß = 0,996
±
SICL ,1018-ID
Fig. 1. Body plan, profile of stern and Btem of model.
V
Fig. 2. Wave system and streamlines.
Fig. 3. Wave system and streamlines.
SCELO1S-IO V .2,mh
____
0
----,---- __p ¡
MOL 7O$-tO ¡
Fig. 4. Body plans With streamlines and strip of coarse sand.
*0*-IC
I
14
fooeo 0 0 0 0 D -e 0 D 5C 0ODO
\ 0
0 0 D O 0 0 e e , O O O O Okt:r
1-c /°'
¿000 ° T7---o&sc
BL SL I IL 0 jA B ICFig. 6. Measuring points:
Model as single-screw ship. Model as 11twin-screw" ship.
Model with modified stern and with rudder.
The wake was measured with a five hole pitot tube as de-scribed in (51. The tests were performed with the model both as
a single- and as a twin-screw ship with the points of
measure-ments being located as shown in Fig. 6. The five holes in the
ball of the pitot tube were through plastic tube with boiled
water connected to five pressure transducers. The transducers
sent signals to a computer
which
calculated the mean value ofeach of the five signals and which produced a paper tape with the recorded mean values for later calculation of the three
velocity components V, V and V, defined by:
= VA is the velocity in the fore-aft direction
V is the velocity in the port-starbord direction
is the velocity in the vertical direction.
The results were presented in a tabular form and as a
com-puter plot of equal Vs-curves and the velocity vectors in
the plane of the propeller disk.
v-v
The wake fration w is computed as: w = , where V
is the model speed.
For the sake of comparison the potential wake fraction
(wy) is calculated for a double body of the model using a
source/sink method. (The calculations have been done by Kristin Rasmussen in connection with his work for the master's degree
The results of the tests i.e. the wake measurements and the streamlines are presented here as they were delivered from the
towing tank. No reanalyzing, adjustment, fitting or fairing
have been made to the data. So the conclusions are drawn on
the basis of test data anyone would obtain from a commercial
towing tank.
4.2. Velocity dependance.
Most of the tests were done at two velocities: 1,3 rn/s and 2,0 m/s corresponding to approx. 6,5 rn/s and 10,0 rn/s (13 and 20 knots) for the full scale ship.
The axial wake distribution for the two velocities is
shown in Figs. lB and C, Figs. 7E and F, Figs. 7G and H and as cross curves in Fig. 10.
The picture is a little diffused. If, however, each
con-stant wake curve at one velocity is compared with the corre-sponding curve at the other velocity it will be found that the wake fraction at any particular point over most of the propeller
disc will be reduced with approx. 0,07 when the velocity is
in-creased from 1,3 rn/s to 2,0 rn/s. Only in part of the upper area
of the propeller disc this is not the case and therefore the volumetric mean wake fraction is only changed from 0,47 to 0,45
for the smooth ship and from 0,62 to 0,58 for the ship with
the gravel strip due to the change in the velocity.
As a comparison it can be mentioned that the volumetric wake fraction for a propeller behind a flat plate will only decrease by approx. 0,01 according to the von KärmAn's
empi-rical formulae ((1] p. 18). 4.3. Roughness dependance.
It is a coimiion knowledge that the friction belt for the
full scale ship is relatively thinner than for the model at corresponding velocities. If one operates in model scale it is very difficult to realïse how the contraction of the friction belt can occv. It is much easier to study an increase in the
thickness of the friction belt by increasing the roughness of
the model thus allowing an investigation of the Influence
V,t'3mJs 'x_1
w
CiLw
// 1
V2m/s
('I
)J/I
-' 10 vo vo vo. ¶0 il o,io!Jj)FULLSTPE
e.. E . Ft
i I -- ---. 1.
f, ¡/,
I -TISI'(
...J¡/
- - , -L ! ¡/ ,iQ*._
W.
CL./11/
,/ t
c_._ / SMOOTH MODEL. BL. C V2pm/sSMOOTH ¡ (io
(
7'
SMOOTHi
/ /
MODEL'J
\.
/'
MODEL10
N.," /
G
L.---'
Hi
. ftL
Fig. 7. Wake distributions for the model:
Calculated potential wake (Kristin Rasmussen, ISH, 1978). Smooth model, V = 1,3 rn/s.
Smooth model, V = 2,0 ut/s.
Strip of coarse sand from stein to amidships, V = 2,0 in/s. Strip of coarse sand from stem to stern, V = 1,3 rn/s. Strip of coarse sand from stem to stern, V = 2,0 nI/s.
Wake measured as for a twin-screw ship
without bossings (smooth model), V = 1,3 rn/s.
Wake measured as for a twin-screw ship
by means of this extra roughness an increase of the thickness
of the friction belt was locally obtained.
In order to investigate where the friction is most impor-tant for the wake distribution the gravel strip was introduced
first
theforward
partand next also on the aft partof the.
rnodel.
The resultS of the test. areshownin
Figs. 7D, E and Fand as cross curves in Fig. 10.
The forward 1/2 strip was found to have
none
or littleinfluence on the wake distribution. The curves for constant
axial wake with and without gravels fitted cross each other rather casually and it is more or less just the level which is
lifted. The disturbance from the gravel in the forward part
of the model spread in a fan-shaped manner all over the
sur-face. As a result of this the volumetric mean wake fraction
was ±ncreased from. 0,46 to 0,48.
The results of the teste with the fore to aft gravel strip
were somewhat different. In an area of the top part of the
propeller disc and. approx.. half propeller radius (R/2) away
from the centerplane an increase of axial wake fraction up to 0,25 was recorded There was a gradual change of the wake
in-crease from.thjs area to the bottoni area of the propeller disc
from 0,25 to approx. zero. At the velocity of 1,3 rn/s the
volumetric mean wake fraction was increased from 0,47 to 0,62
and at 2,0 rn/s it was changed from 0,46 to 0,58.
The wake fields at all the investigated conditions was very inhomogeneous and with quite a lot of rather casually distributed
t1islands".' These irregularities are much bigger than those
found in the investigations made in Japan with "Yagoi Maru" and
her. models (61.. Looking closer to the constant wake curves in
the area where the largest changes. occur because of the gravel
strip, one finds that the curves have moved in a direction of
approx. 550 to horizontal (see Figs. 7B and E and also 7C and
F),. The wake field was apparently altered in a very complicated
way when the böundary layer was changed. On the whole it seems that the contour for constant wake for the model is displaced at a right angle to its original position when the roughness of
Fig. 8. Profile of model with modified stern and rudder..
the surface is varied.. This indicates that the contour for constant axial wake for the full scale ship probably will be displaced in the same way when they are derived from the model
results. If so, the correction theory, proposed by Sasajima
in 1966 (4] is probably not absolutely correct. The method
proposed by Hoekstra in 1974 (2] seems to come close although the mathematical formulations given in connection with the
theory is too complicated if the not so accurate data from the
model test are taken into account (see section 5). It is the
authors' opinion that the wake distribution found by means of
model tests can be used primarily to judge whether the wake field is adequately homogeneous or not. A method for such an
evaluation is proposed by Odabasi and Fitzsimmons (3].
The wake data necessary for propeller and pressure varia-tion calculavaria-tions can be produced by multiplying the measured data with some coefficients taking the model scale into account.
It seems that doing anything else is just to hide our ignorance. 4.4. The, influence of stern form.
Most of the tests were made with a simplified ship stern
form. Some of the later tests were made with a modified stern
as shown in Fig. 8. There was no significant change in the
wake distribution (see Figs. 9 A og B).
4.5. influence of the rudder.
Because of the test technique used in the experiments most.
of the measurements taken were without rudder. Only at some of
the later tests the measurements were made when the model had a rudder fitted as shown in
Fig.
8. Figs. 9C and D show the test results for the two velocities 1,3 rn/s and 2,0 rn/s.V.13tm/s î,-I. I\\'k i
"A
rT
¡CH
, w
i,.
j QO\
I,!
I-n
IN
:.-WH eò L ___ ftb y
rTl
V 2ß m,, SLw
B ILD
iFig.
9. Influence of stern
and rudder on wake distribution.SMOOTh MOCEI. HALF StRIPE CF SAP FLLL STRIPE OF SAND
TOP OF DISC D(TRE CF DISC R.4BELOW CENTRE BOTTOM OF ffiO DISC
Fig.
10. Cross curves of the wake distribution atThe rudder does not change the general character of the wake
field, only the value is changed mainly because of the potential
wake field of the rudder. The mean increase of the axial wake
fraction at the observation points is for 1,3 rn/s approx. 0,016 and for 2,0 rn/s approx. 0,023.
5. Reliability of wake measurements.
It has always been difficult to carry out measurements of
wake with the five-hole pitot tube and the tests are very
time-consuming.
The time spent has been cut considerably byintro-ducing the electronic and online computer techniques but new source of errors has also been introduced and tests must often
be repeated.
The tests described here involved many measurements; only
one parameter was changed at a time. The test period lasted
about half a year. The water temperature in the towing tank
increased from 13,8° C to 17,2° during the period but it is
assumed that this had no influence on the results. Some of the
measurements were repeated by running the model both as a
single-screw ship and as a double-single-screw ship without propeller bossings.
Consequently, the same wake field was measured twice at a certain
interval of time. This means that the measurements,
calcula-tions and computer interpolacalcula-tions were carried out without
being able to correlate them during the tests. Also the computer
programs used for single- and twin-screw ships are different.
The data can therefore be used as a basis for estimating the
uncertainty of the f lye-hole pitot tube technique.
If Figs. 7B and C are compared with Figs. 7G and H it is
seen that very great differences can exist
between
thetwo sets
of measurements. The corresponding curves are even seen to
cross each other at angles of about 900. At some points the
difference in wake values is as big as 0,25. Normally the
ob-served difference is approx. ±0,05.
This means that the undulations of the wake curves often are more or less random and perhaps the "islands" with very high or low wake values do not exist in connection with a real
ship. Owing to this only the overall picture of the wake
distri-bution is to be relied upon and there is no reason to trust a
of small models must also be considered as having very little
significance in practice. 6. Conclusions.
The friction belt is decreased as the velocity is increased.
The contraction occurs more or less in a direction
perpen-dicular to the constant wake contours. However, some
irre-gularities at the top of the propeller were observed for
the model used in these investigations.
The constant wake contours are displaced when the
rough-ness is varied. The direction of the displacements is
more or less perpendicular to the contours. Increased
friction means increased wake. It is likely that the sanie
takes place when going from model to ship.
Moderate variation of the ship stern has little or no
influence on the wake distribution.
The rudder increases the wake but does not change the
distribution significantly.
The five-hole pitot tube measurement technique is
rela-tively unreliable.
It is necessary to carry out many measurements if a
rea-sonably safe determination of the wake is required. A
single standard test performed commercially could very easily ai7e a rather erroneous impression of the wake
distribution. An improved wake measurement technique is
very much needed. 7. References.
[i] Harvald, Sv. Aa.:"Wake of Merchant Ships. The Danish Technical Press,
Copenhagen, 1950.
[2] Hoekstra, M.:"Prediction of Full Scale Wake Characteristics Based on Model Wake Survey", Symposium on High Powered Propulsion of Large Ships,Netherlands Ship Model Basin,Publication No. 490, Wageningen
1974, Part i p. XII, 1.
Odabasi, Y. and Fitzsimmons, P.A. "Alternative Methods for Wake Quality
Assessment", International Shipbuilding Progress ,Voi.25, February 1978, No. 282, p. 34.
Sasajima, H. and Tanaka,I.:"On the Estimation of Wake of Ships",Eleventh
International Towing Tank Conference, Tokyo, 1966, p. 140.
[5] ilòvi, V.:"A Five Hole Spherical Pitot Tube for Three Dimensional Wake Measurement", Hydro- and Aerodynamics Laboratory, Report No. Hy-3, Lyngby-Denmark, 1964.
(6] The 4th Research Committees:"Investigation into Effect of Fouling of a.
Ship and Propeller upon Propeller Performances of a Ship, The Report of the Shipbuilding Research Association of Japan, Tokyo,
APPENDIX
As mentioned in section 5 and in the
conclusion
6.e it wasfound that the measurements with the 5-hole pitot-tube are not
reliable. Fig. A.l shows an example from
investigations
atDavid W. Taylor Naval Ship Research and Development Center
(ref. 7]. This figure shows a comparison between three dif
fe-rent velocity measurement devices and it is seen that the
scat-tering of repeated meaSurements is considerable. At a distance
of 60 ¡mn from the
cylinder
the difference in velocitymeasure-ments is as large as 1,5 rn/s. Tests in a rotational flow
indicate that the pitot-measurement can be distorted by the
pressure in the vortices as mentioned by Müller in (ref. 8].
As also mentioned in the
conclusion
6.e an improved method of measurement technique is needed because of:improved accuracy
possibility to meaSure the wake thefl the propeller is preáetit
possibility to measure without disturbing the flow field
reduction in time and cost.
The one technique now emerging is the laser doppler
velocity-meter LDV) technique. The technique is well known and most of the
necessary apparatus is available as standard equipment. Halliwell
has described one way of adapting the LDV to ship science
(ref. 9, 10 & li] and Kux has used the WV in full scale
measure-ments on ships (ref. 12]. The Hamburg tank [HSVA] has taken
delivery of a WV equipment in the autumn of 1978 and Fig. A.2 and A.3 show schematically the instrument and the mounting on
the model, Fig. A.4 shows an alternative method to mount the
instrument
if a big model capable of carrying the instrumentcannot be used. This is the method also used by Halliwell.
The WV-methods seem to have small or no disadvantages and
what is left now is only to develop the instrumentation hard-ware so the instrument can be handled in an easy and fast way.
Scragg, C.A. and Sandell, D.A.: "A statistical Evaluation of Wake Surway Techniques", Proceedings: International Symposium on Ship Viscous Resistance, SSPA, Gôteborg 1978.
Müller, A.: "Comparison of Pitot-Tube and LDA in a Rotational Plow",
Proceedings WA Symposium, Technical University of Denmark,
Copenhagen 1975.
(9] Ralliwéll, N.A.: "Laser Anemometry in Ship Hydrodynamics", The Naval
Architect, May 1976.
(io] Balliwell, N.A.: "A Towing Tank Laser-Doppler Anemometer", The Naval
Architect, July 1978.
[1.1] Halliwell, N.A. and Rizzo, J.E.: "The Application of Laser-Doppler Anemometry in Ship Science't, Proceedings IDA Symposium, Technical University of Denmark, Copenhagen 1975.
[12] Kux, J.: "Application of Laser-Velocimetry to Ship Flow-Field
Measurements ), Proceedings, International Symposium on Ship Viscous Resistance, SSPA, Gothenburg 1978.
Fig.A.l. Comparison between measuring devices.
O HYDROTYPE 29 e o o o O
a
AERO-TVPHOT-WIRE 28 o o o o o o o o 27 Eo
2 Ao
o
Ao
o
a
o
o 25 Ag
..60 .30 0 30 60 POSITION (mm) CYLINDER tIPHOTO MULTIPLIER
MODEL FREE TO HEAVE AND PITCH
BACI( SCATTERED BEAM
MEASURING POINT
LASER
PLATFORM MOUNTED ON MODEL
Fig.A.2. Principal sketch of a Laser Doppler Velocitymeter (HSVA).
MEASURING POINT MOVED
BY MOVING PLATFORM WITH LASER AND OPTIC
Fig.A.3. Mounting of the LDV on a ship model.
MEASURING POINT MOVED
BY ZOOM -OPTIC
/
/
MODEL FIXED TO CARRIAGE
/
/ 1 /
Fig.A.4. Mounting of the LOV on the towing carriage.