SKIBS
-
0G HAVTEKNIK
Department of Ocean Engin eeri ng
PREDICTION
OF.
POWER OF SE IPS::
by
Sv. Aa. Harvald
DANMARKS TEKNISKE HØJSKOLE
The Technical University of Denmark
LYNGBY Danmark
CONTENTS O. Suxmnary Page i 1. Introduction 1 2. Necessary Power 2
3. Type Ship Methods and Statistical Methods 18
4. Essential Parametérs for Prediction of Power 19
5. Diagrams for Prediction of Power 23
6. Piecewise Methods for Prediction of Powér 26
7. Ship Model Experiments 43
8. Control of Power Estimates 44
9. Conclusions 45
10. Symbols and Units 46
SUMMARY.
Different methods for predicting the required power for the propulsion of
mer-chant ships are desctibed. Diagrams give the relation between the expected power
necesSary for transporting a desired
vo-lume of cargo at a given velocity. Such a
prediction is very rough. Therefore,
dia-grams giving the power as a function of block coefficient, displacement,
length-displacement ratio and. velocity have also been constructed. Finally, the method
normally used at the Department of Ocean
Engineering, The Technical University of Denmark is outlined.
1 INTRODUCTION1
When making preliminary proposals for new ships or
transportation studies the vitalj question facing the
ship-owner, naval architect, politician, economist or student is
often how much power is necessary. The answer can be found in different ways. Just as in preliminary ship design there are three groups of methods to choose between:
Type Ship Methods Statistical Methods Piecewise Methods
When the first-mentioned method is used, a type ship has
to be chosen. The type ship must be of the same type as the
type in the proposal. Further, the main dimensions of the type ship and the velocity must be nearly the saine as
expected for the proposal. An Admiralty. Coefficient for the
type ship is calculated
2, A A'3 y3 C P where A = displacement V = speed P = power
This Admiralty Coefficient is then used for the proposal when predicting the necessary power for propulsion.
Results from model tests and from ship trials can form basis for type ship methods but they can also form basis for
statistical methods. Possibly a regression analysis can be carried out on the results to find optimum solutions.
Results from model tests, from theoretical considerations and from ship trials are the foundation of the piecewise me-thods. With such a method the special features of the pro-posai can be taken into consideration in a better and more
logical way than with other two groups of methods. In addition the piecewise method can be used within a very
broad area. The different methods are still being developed.
2. NECESSARY POWERS
To get an impression of the power necessary for trans-porting a given volume of cargo at a given velocity the diagrams Figs. 1, 2, 3, 4, 5 and 6 have been constructed.
For ships built during the periods:
the shaft power is given as a function of the deadweight
and the velocity of the ship. All data have been taken from
t:
1877-
1929
II: 1930 - 1939
III: 1940 - 1949
IV: 1950 - 1959
V: 1960 - 1969 VI: 1970 - 1977the Registers of the Classification Societies.
The following signatures have been used in the diagrams:
4
for the veìocity - intervals: 3,1- 3,5 andFor fixed values of the velocities a set of average curves
have been drawn. As time has passed the deadweight and the velocity of the ships have increased and with this also the power necessary for propulsion. it is worth noting that.
the system of average curves fits the points on the diagrams
from the different periods very well. Thus,. the technological
developments have not resulted in much better ship forms or
propellers than earlier, and as time has passed. it has only
been practically possible to increase the dimensions of the Ships and the amount of power available for propulsion.
Fig. 7 also gives an impression of the development. The
same average curves as in Figs. ito 6 have been inserted,
and in this net the data for three ships all named "Selandia"
have been plotted. The first. "Selandia" was a twin-screw
cargo and passenger ship built in 1912 by Burmeister & Wain
and the world's first ocean-going motor vessel. The second
"Selandia" was a single-screw cargo and passenger ship built in 1938 by Nalcskov Shipyard; and the third, built in 1972 is
a triple-screw container ship with one of the most powerful diesel engine installations ever used in a merchant vessel.
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NThis ship, too, was built by Burmeister & WaLn. it will be
observed that, in spite of the big differences between the
three ships, the data fit very well in the system of curves. For shipowners with ships all of almost the saine type,
diagrams giving shaft power as a function of deadweight and speed.can give a very safe predetermination of the power
required for propulsion. Such diagrams for tankers, bulk carriers and shelter deck vessels are given in Figs.. 8, 9 and 10, respectively. For other types of ships, it is more convenient to use the displacement instead of the deadweight as a parameter, e.g. as shown for train ferries, tugs and
icebreakers, in Figs. li, 12 and 13, respectively.
In the diagram for the train ferries lines corresponding
2/
= k L
'
have been inserted.
With regard to the diagram for the tugs it will be ob-served that there is a relatively large scatter on the points, due to the fact that the propeller and the machinery of the tug are primarily designed to give big thrust at low velocity.
In discussing the problem "Necessary Power", the question
of extra power haS to be mentioned.
Extra power means here the power in excess of the power necessary.for giving the ship the desired speed on trial.
The extra power is also called service allowance and, provides
for extra resistance of wind, sea, fouling of the hull etc. Some shipowners want very little extra power while others
require a löt.
A little extra power means only that, in bad weather,the
ship has to work at 'a low speed, normally without risk to the ship and 'the crew for that reason.
Further, there is a te.ndency to give big ships relatively less extra power than small ships. The desired extra power can vary from 10% to about 40% of the power necessary in
trial cond.itïons. .
In special cases, the extra power can be about 20.0%, as
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18
propellers at each end, working in fairways filled with
pack-ice. On the other hand, in some cases, the speed stated
can,. for various reasons, only be obtained when the ship is working in following wind and sea. In other words, the
extra power has been a negative amount. This also means
that the scattering of the points must be very large in dia-grams where the power installed is given only as a function
of deadweight and speed.
TYPE SHIP METHODS AND STATISTICAL METHQDSI Using a type ship method, first an Admiralty Coefficient
Ac for the type. ship is calculated and then the power for the proposal:
L«3 y3
_p
p A C where .and VP
are the displacement and the desiredspeed for the proposed ship, respectively. A great deal of
information about Ac is availáhie and a preliminary design
formula for A can be given by
= 3,7 (/r: +
L iS the length of the ship in metres and V is the speed
in metres per second. The power P will be in kilowatts if in the formula is the mass in tons of 1000 kilogrammes. Thus the type ship method and a statistical method are
com-bined.
Another formula of thistype for prediction of power
has been proposed by Watson [11]. In metric units and slight-ly modified, the formula is.:
= 510 v3(40 - Q,017 L + 400(K-1)2 -12 )
where
P = power in kw
4 = displacement mass in t V = speed in rn/s
L = length of ship in m
K = the constant in the Alexander formula
â = K - 0,5 -y- (kn/ft½) i.e. K l,Ô6 't
6 = block coefficient
n= revolutions per second
This formula is built up in a rclatively logical way of all
the most essential parameters for the power required.
Neglecting the influence of the block coefficient, the
formula becomes
-2,
5,0 A V3 (33 - 0,01714
15000-llOn't
Application of the formulae given above must be done with
care.. The formulae norival.lyfit special types and sizes
of ships, and applied outside this area, the results can be
wrong. it is not often mentioned within which area th
formulae can be applied. In that respect diagrams showing the relàtions between the different parameters give a. better survey of the field of application.
ESSENTIAL PARAMETERS FOR PREDICTION. OF POWER,
When
constructing
a diagram for the prediction of. powerfor the propulsion of ships the choice of parameters is of
the greatest importance. There are many conceivable
para-meters, and if simple diagrams are wanted, a selection must
take place.
To a great extent, parameters of importance for the ship resistance must also be of importance for the power
neces-sary fòr the propulsion f the ship at a given velocity or
20
Froude number. Thus, the principal dimensions and parameters describing the form of the ship will determine both the ship
resistance and the power for propulsion. At previous occa-sions (see "Ship Resistance" [4]) the author has used the
following parameters for describing the form:
Length-displacement ratio L/
Longitudinal prismatic coefficient
Breadth-draught ratio B/T
Longitudinal position of
centre of buoyancy LCB/L
If the ship has sections which are distinctly U-shaped
or V-shaped and if the ship has bulbous bow or special appen-dages, allowance must be made for this. in addition the con-dition of the hull surface influences the ship resistance.
The above-mentioned parameters are also among the para-meters determining the thrust deduction and the waké and
thereby the
hull,
efficiency. Furthermore, the. propeller(s),the positión of the propeller(s) and the form and position
of the rudder(s) influence the hull efficiency.
In addition, the efficiency of the propeller and the total propulsive efficiency depend upon the dimensions and
form of the propeller(s). Fig. 14,gives an impression of the influence of the size of propeller upon the power
neces-sary for propulsion. Ship "U" is a bulk çarrier of about
50000 t. deadweight equipped with different propellers [6]. Using a large, slowly running propeller instead of a small, fast running propeller on the ship "U" at a speed of 8,5 rn/s
(16,5 knots), the necessary power for propulsion of ship "U" can be reduced by about 50 per cent.
Thus, at least 12 parameters are essential 'for the pre-diction of the power for propulsion of the ship. A diagram'
for predicting the power cannot be constructed in such a way
that all parameters are taken into account in the right way.
A standardization of some of the parameters has to take place. If it is assumed that diagrams predicting the power for pro-pulsion may only involve four parameters, the following
25000
20000
kW
15000
io 000
5000
O oSH
v=
'Pu
8,5,4
(m)
6Fig. 14. Necessary power for ship "U" equipped with
different propellers.
n
3,022
parameters are suggested:
= displacement.. Hereby the size of the ship is
fixed.
V = speed of ship. The power f or propulsïon will at least depend on the third power of the speed.
= - block coefficient, which to some extent
describes the form of the ship.
i
= length-displacement ratio, which iS a form coefficient that has almost no correlation to
the block coefficient.
This means that all other parämeters have to be stan-dardized, which can be done in the following manner:
Hull form. The sections of the "standard"-form are
neither distinctly U-shaped nor distinctly V-shaped. Further, it is assumed that the "standard"-form is a form with well designed lines and with an
ortho-dox non-bulbous bow.
B/T = breadth-draught ratio. For most of the ships this
ratio is in the neìghbourhood of 2,5. For large
Ships, i.e. ships with a displacement in excess of
200000 t, the. ratio is about 3,0. Therefore,
these two ratios may be chosen as a standard.
LCB = longitudinal position of centre of buoyancy. The
position of LCB.is assumed to be optimum. As
mentioned in "Ship Resistance" ((4] p. 3), the
op-timum LCB is
unfortunately
a quantity that is insome doubt.
Appendages. The "standard" form has no special
appen-dages. The rudder is a double plated rudder and,
in relation to the propeller,placed in accordance with the rules of the classifidation societies.
Number of propellers. It is assumed that the number of
própellers has very little influence on the power necessary for propulsion of the ship at a given
speed. The standard ship may be a single-screw
ship.
D Propeller diameter. It is assumed that the diameter
of the propeller (four bladed) is optimum (if possible) and less than two-thirds of the draught
of the ship fully loaded.
n Rate of revolution. It is supposed that standard ships are equipped with, a diesel engine running at
a rate of revolution corresponding to maximum con
tinuous rating.
V = Speed of ship on trial. Further, this means that the
surface of the ship is smooth in the standard con-dition.
Service Allowance. The diagrams will be valid only for
shïps in trial conditions. For service conditions allowances have to be made, depend', ing on the
sail-ing route. The values of these allowances can be given as percentages of the power necessary under
trial conditions.
DIAGRAMS FOR PREDICTION OF POWERI
As mentioned in chapter 4, the parameters in diagrams for prediction of power can be
i
L/V V
Therefore, first the effective power
E has been
ship forms: : loo t 200 t - 300 t - 500 t 833 t - 1000 t - 1667 t - 3333 t 5000 t - 7100 t - 14300 t - 21500 t 28500 t 37700 t 50000 t - 100000 t 142900 t - 200000 t - 300000 t 500000 t - 1000000 t I L/V : 4,0 - 5,0 - 6,0 - 7,0
(only some few 7,0-forms have been calculated)
: 0,55 - 0,60 - 0,65 - 0,70 0,80 - 0,85
V : From 3 rn/s to 13,4 rn/s
For the small ships the power has only been calculated at small velocities and for the
big ships only at big velocities.
In the calculation of the total ship resistance coeffi-cient CT the incremental resistance coefficoeffi-cient CA has been varied in such a way that
for disp1acement i = 1000 t 0A = 0,6
bObO t
0,4 . io100000 t O
1000000 t - 0,6 ' 10
All forms have been standardized as mentioned.in the
preceding chapter.
Further, with regard to the rate of revolütion, the
24
following standardization is used:
For ships wïth displacement
up to 1000 t: n = 8,33 revs/sec (500 revs/mm) from 1000 to 2000 t: n = 6,67 revs/sec (400 revs/mm) from 2000 to 3000 t: n = 5,00 revs/sec (300 revs/mm) from 3000 to 5000 t: n = 3,33 revs/sec (200 revs/mm)
from 5000 to 7500 t: n = 2.50 revs/sec (150 revs/mm) from 7500 to 12500 t: n = 2,08 revs/sec (125 revs/mm) from 12500 to 25000 t: n = 1,92 revs/seò (115 revs/mm) from 25000 to 50000 t: n = 1,83 revs/sec (110 revs/mm)
from 50000 and up: n = 1,67 revs/sec
(100 revs/mm)
After the effective power has been calculated the shaft power is determined as follows: By use of the
.ISH-Logarith-mic Propeller Diagrams, which are based on the results from the Wageningen screw serieS B (Fig. 23), the optimum
propel-ler diameter for the standardized ship form is determined. if the diämeter is less than two-thirds of the draught, the
propeller efficiency Ti0, the advance coefficient J and
the pitch ratio are read directly from the propeller diagram. If the diameter is bigger than two-thirds, a diameter of two-thirds of the draught is used in the cálculations.
The hull efficiency
H = is calculated using the waké coefficient w and the thrust deduction coefficient t
estimated from the diagrams in "Wake of Merchant Ships"
([5] Figs. 52 and 104), taking into account that it is the trial trip condItion that is to be designed for (Wtriai "
0,7 wmei).
The diagrams giving w and t for models of
single-screw ships are reproduced in Fig. 25 in a slightly modified
version..
The shaft power is then calculated by
BflHflBTIS
where = propeller efficiency in the "behind" condition =
T1OTiR n0.
R
relative rotative efficiency)26
All the results are plotted in diagrams (see Figs. 15-21), each diagram corresponding to a fixed value of the block
coefficient 6 (0,55, 0,60, 0,65, 0,70, 0,75, 0,80 and 0,85).
In these diagrams the abscissa is the displacement of the
ship in t (of 1000 kg) and the ordinate is the powár in kW
for propulsion òf the ship. Curves of constant speed for
three length-displacement ratios are inserted. By using re-latively large steps in the speed variation in the diagrams,
the curves for different length-displacement ratios at a constant speed become placed in groups, which facilitates
the later use of the diagrams. All curves in the diagrams are faired partly by hand, partly by use of a Hewlett-Packard
9830 A calculator.
The diagrams, Figs. 15-21, can be used in the preliminary prediction of the power necessary for propulsion at a given speed, but it has to be borne in mind that it is the power for the standard ship in the standard condition that is
estimated. In every case, service allowance has to be added
in accordance with the wishes of the coming owners.
The designer of the ship often has his own standard forni for the hull. It is then advantageous for him to make power curves for this standard form using the same parameters as
in the diagrams mentioned above. The use of such diagrams results in a very reliable prediction of the power.
PIECEWISE METHODS FOR PREDICTiON OF POWER.
In the previous chapter the prediction method normally used at the Department of Ocean Engineering, The Technical
University of Denmark, has been partly described. In the
following, a more detailed description will take place.
A. Dimensions of ship. It i assumed that the principal
dimensions for the proposed ship are already fixed or that the power has tobe estimated for a series of proposals with given dimensions to find optimum
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34
For the prediction of the power, the following principal
dimensions have to be known:
Leñgth of waterline L
Breadth B
Draught T
Further, it is assumed that the displacement volume V at
the draught T of the proposai is known.
B. Form data for ship. From the displacement volume and the
principal dimensions the block coefficient t5 = is
fixed. The midship section coefficient is fixed in
accordance with the type of ship. Hereby, the prismatic
coefficient p is also fixed. The longitudinal position
of the centre of buoyancy (LCB) is determined on the basis of trim calculations and of cónsiderations regarding the
best possible positión. The form of the hull might then possibly be one of thé forms from the series in
"Form-data" (2]. Ali hydrostatic data are hereby easily
deter-mined. Also the wetted suif ace S can be calculated in a simple manner by use of "Formdata" or by use of "Wettéd Surface of Merchant Ship Forms" [3]. A good result with
regard to S may further be oltained by use of a formula
given by E.R. Muxnford (1]. The formula is
S = . B + 1,7 T)
where LP is the length between the perpendiculars, B
the moulded beam, T the moulded draft and the
-block coefficient based on
C. Resistance. By use of "Ship Resistance" (4] the resi-stance R and the effective power E for a "standard" ship form -can be calculated.
R
= cT½PVS
(N)-= RV (kW)