Practical Ship Hydrodynamics
Practical Ship Hydrodynamics
Practical Ship Hydrodynamics
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166 <strong>Practical</strong> <strong>Ship</strong> <strong>Hydrodynamics</strong><br />
of the ship. Installed power P, cross-section area of the pipe A, andflow<br />
velocity v in the jet thruster are related by:<br />
T D Ð A Ð v 2<br />
P D 1 Ð 1<br />
2 Av2<br />
is here the efficiency of the thruster propeller. These equations yield:<br />
P v<br />
D<br />
T 2<br />
T<br />
D v2<br />
A<br />
D 0.8andv D 11 m/s yield typical relations: approximately 120 kN/m 2 thrust<br />
per thruster cross-section area and 7 kW power per kN thrust.<br />
With increasing speed, jet thrusters become less effective and rudders<br />
become more effective. The reason is that the jet is bent backwards and may<br />
reattach to the ship hull. The thrust is then partially compensated by an opposite<br />
suction force. This effect may be reduced by installing a second (passive) pipe<br />
without a propeller downstream of the thruster (Brix (1993)).<br />
5.2.8 CFD for ship manoeuvring<br />
For most ships, the linear system of equations determining the drift and yaw<br />
velocity in steady turning motion is nearly singular. This produces large relative<br />
errors in the predicted steady turning rate especially for small rudder angles<br />
and turning rates. For large rudder angle and turning rate, non-linear forces<br />
alleviate these problems somewhat. But non-linear hull forces depend crucially<br />
on the cross-flow resistance or the direction of the longitudinal vortices, i.e.<br />
on quantities which are determined empirically and which vary widely. In<br />
addition, extreme rudder forces depend strongly on the rudder stall angle<br />
which – for a rudder behind the hull and propeller – requires at least twodimensional<br />
RANSE simulations. Thus large errors are frequently made in<br />
predicting both the ship’s path in hard manoeuvres and the course-keeping<br />
qualities. (The prediction of the full ship is fortunately easier as at the higher<br />
Reynolds numbers stall rarely occurs). In spite of that, published comparisons<br />
between predictions and measurements almost always indicate excellent accuracy.<br />
A notable exception is Söding (1993a). The difference is that Söding<br />
avoids all information which would not be available had the respective model<br />
not been tested previously. The typical very good agreement published by<br />
others is then suspected to be either chosen as best results from a larger set of<br />
predictions or due to empirical corrections of the calculation method based on<br />
experiments which include the ship used for demonstrating the attained accuracy.<br />
Naturally, these tricks are not possible for a practical prediction where<br />
no previous test results for the ship design can be used. Thus the accuracy of<br />
manoeuvring predictions is still unsatisfactory, but differences between alternative<br />
designs and totally unacceptable designs may be easily detected using<br />
the available methods for manoeuvring prediction. With appropriate validation,<br />
it may also be possible to predict full-scale ship motions with sufficient