The present paper deals with the problems of yaw angle effects on podded propulsor performance. The study aims at providing insights on characteristics of podded propulsors in azimuthing condition. In this regard, a wide numerical simulation that concerned yaw angle effect measurement on podded propeller performance was performed. The ReynoldsAveraged Navier Stokes (RANS) based solver is used in order to study the variations of hydrodynamic characteristics of podded propulsor at various angles. At first, the propeller is analyzed in open water condition in absence of pod and strut. Next flow around pod and strut are simulated without effect of propellers. Finally, the whole unit is studied in zero yaw angle and azimuthing condition. Structured and unstructured mesh techniques are used for single propeller and podded propulsor. The performance curves of the propeller obtained by numerical method are compared and verified by the experimental results. The characteristic parameters including the torque and thrust of the propeller, the axial force and side force of unit are presented as function of velocity advance ratio and yaw angle. The results shows that the propeller thrust, torque and podded unit forces in azimuthing condition depend on velocity advance ratio and yaw angle.
APPENDIX NOTATION

CPPressure coefficient

D Propeller diameter

FxAxial force

FySide force

J Velocity advance ratio

k Turbulence kinetic energy

KQPropeller torque coefficient

KTPropeller thrust coefficient

KfxAxial force coefficient

KfySide force coefficient

n Propeller angular velocity (RPS)

P Static pressure

Q Propeller torque

TproPropeller thrust

TpodPod thrust

TstrutStrut thrust

TunitUnit thrust

V Axial velocity

Velocity vector

δijKeronecker delta

ηproPropeller efficiency

ηunitTotal unit efficiency

μMolecular viscosity

ρFluid density

ωTurbulent dissipation rate

ψYaw angle
INTRODUCTION
Recently, podded propulsion systems are widely used in marine industry and becoming more popular, not only for passenger ships, but also for offshore drilling units and naval vessels. The main components of podded propulsor are strut, pod and propeller. In this system, an electrical motor is located inside a steerable pod housing which drives a fixed pitch propeller. The total unit is hung below the stern of ship by strut and can be rotating through 360
degrees
around its vertical axis. Therefore, thrust is generated in any direction that gives the better maneuverability. This device combines propulsion and maneuvering functions mutually (Carlton, 2007).
Two main configurations of podded systems are puller and pusher types. In the puller type, the propeller is located in the forward face of the pod and upstream of the strut. In the pusher type, the propeller is located in the downward face of the pod and downstream of the strut. Pusher type propellers have lower efficiency than puller type. In pusher type, the propeller works in the wake of the strut. In general, the efficiency of podded propulsor is lower than open water propeller. This matter is due to resistance of pod and strut. Therefore the resistance of unit is an important factor that cannot be ignored.
The conventional propulsion systems such as propellerrudder systems operate in the hull’s wake flow. Due to the hull’s presence, the flow distribution into the propeller is nonuniform and unsteady. The most significant hydrodynamic advantage of the podded propulsor is that the propeller is set in a more regular flow and works mainly in an open water flow that is uniform which results in little or no cavitation. It is necessary to utilize this system for ship propulsor, especially for vessels which need to be prevented from cavitation (Ghassemi and Ghadimi, 2008).
More recently, due to the market needs and in order to gain more efficiency by the podded systems, marine researchers have rigorously pursued this topic and much effort has been devoted to explore it numerically and experimentally. During the past two years, the 1st and 2nd TPod conferences have been held at the University of Newcastle (UK) and Universite de Bretagne Occidentale Brest (France) in 2004 and 2006 (ITTC, 2005; ITTC, 2008), respectively, and many researchers (like Kinnas, 2006; Bal et al., 2006) presented their latest findings. One of main operational problems of podded systems is bearing failure (Carlton, 2008). This mechanical failure occurs when there are unpredicted forces and moments which act on the podded system especially in yaw angle. Therefore, the study on variation of forces and moments in azimuthing condition is very important and required for design and optimization of podded systems.
Experimental studies of Szantyr (2001) were one of the early works for podded propulsor in azimuthing condition. He measured axial and transverse force and moment for podded drive to ±15° yaw angle. Reichel (2007) also presented result of comprehensive maneuvering open water tests of a pusher drive. Steering forces were measured in the range of yaw angle from 45° to +45°. In the recent work, Amini and Steen (2011) reported systematic model test results of the podded drives in different velocity advance ratios and different yaw angles. The tests were performed on the pulling and pushing modes for both open water and in behind conditions. An important study of this problem is the work carried out by Islam et al. (2007). Particular test equipment was designed and several different measurements were considered. The podded propulsor was tested in puller and pusher condition in different yawing angle from 30° to +30°. Their results showed that the unit force and moment coefficient depend on velocity advance ratio, yaw angle and yaw direction.
Numerical analysis of podded drive in azimuthing condition has not thus far been adequately explored. It is definitely imperative that we use more reliable numerical method in the design of such a propulsion system in order to understanding about flow pattern around podded drives. The present study focuses on hydrodynamic analysis of podded drive in azimuthing condition. The results included are the openwater characteristics of the single propeller and hydrodynamic performance of the puller type of the podded drive at various yaw angles.
NUMERICAL METHOD
It is a common practice to perform a model test to evaluate the hydrodynamic performance of a marine propeller or propulsion system. However, the model test is usually expensive and timeconsuming. Computational fluid dynamics (CFD) is a powerful tool for analyzing the performance of ship propulsion systems. Two methods are usually used in this field of CFD: inviscid and viscous methods. The inviscid method is usually based on potential theory, while the viscous method uses numerical solution of the NavierStokes and the continuity equations; offering many advantages over potential flow based methods. The viscous method has traditionally been employed for flow problems where turbulence, boundary layer, wake, and viscous resistance are important. Different solution approaches have been proposed during the past few years, such as the direct solution of the NavierStokes equations and the solution of ReynoldsAveraged NavierStokes (RANS) equation.
In order to study the effect of yaw angle on podded drive performance, different numerical methods have been used from potential method or potential/viscous method to pure viscous method. In azimuthing condition, there is interaction between the pod, propeller, and strut. Therefore, the viscous effect is an important phenomenon in hydrodynamic analysis.
The numerical methods based on potential flow theory have been used widely and successfully to predict the performance of conventional propellers. Ghassemi and Ghadimi (2008) predicted podded drive performance using potential flow method. Also Liu et al. (2009) applied unsteady panel method code for predicting unsteady forces, torques and bending moments for a podded propulsor unit model at various yaw angles. Their results showed that there is a discrepancy between numerical results and experimental data at large yaw angles. Due to viscous effects in large yaw angle, the interaction between propeller, pod and strut increases. Also at these angles drag of propeller, pod, and strut increase to high values because of flow separation. For this matter, potential results should be corrected at large yaw angles by estimating proper value for pod drag.
RANS solvers are capable to take into account the viscous and turbulence effects for podded drive. First RANS simulation for podded drive has been done by SanchezCaja et al. (1999). They presented a fully viscous method for analysis of these systems. Also, Koushan and Krasilnikov (2008) used unsteady RANS solver for simulating the flow around pulling and pushing pod propeller in azimuthing condition from 45° and +45° yaw angle.
In this work, the finite volume based RANS solver is applied to predict the hydrodynamic performance of marine propeller and podded propulsor. By these simulations, characteristics of flow around the marine propeller and puller podded drive are presented including pressure distribution and open water performance curves in zero angle and oblique flow. The computational results are discussed and compared with the experimental data.
GOVERNING EQUATIONS
Resulting unit thrust from podded propulsor is sum of three components:
where T
_{pro}
, T
_{pod}
, and T
_{strut}
are components of thrust from the propeller, pod, and the strut respectively.
For podded propulsor, coefficients of propeller thrust, unit thrust, axial and side force are defined as:
where F
_{x}
and F
_{y}
are total forces on the whole unit in x and y direction respectively. These coefficients are important factors in design of podded drives affecting propulsion and maneuvering specifications. Also velocity advance ratio, propeller efficiency, and total unit efficiency can be defined as:
The governing equations for the mass and momentum conservation can be stated as:
where
denotes the velocity vector, p is the static pressure and
represents the stress tensor given by:
In which
μ
is the molecular viscosity and I denotes the unit tensor. Using the Reynolds averaging approach, the Navier Stokes equations can be expressed as:
where
δ _{ij}
is the Keronecker delta, and
shows the Reynolds stresses.
It is rather difficult to model the components of Reynolds stress tensor, because it requires detailed and unavailable data about turbulent structures in the flow. The kε and kω models are the most widely used turbulence models for external aerodynamics and hydrodynamics analyses. In this paper, the two equation standard kω model which was developed by Wilcox (1998) is employed where one equation involves the turbulence kinetic energy (k) representing the velocity scale and the other takes the turbulent dissipation rate (ω) into account representing the length scale. The twoequation standard kω turbulence model accounting for the effect of turbulence is
where σ
_{k}
and σ
_{ω}
are the turbulent Prandtl numbers for k and ω, respectively. The turbulent viscosity, μ
_{t}
, is computed by combining k and ω as follows:
The rotation of the propeller in the fluid environment is modeled using Moving Reference Frame (MRF) method. By using MRF method, the flow around propeller can be modeled in a steadystate manner. In this case, governing equations is solved with additional acceleration terms. The computational domain is divided into stationary and moving frames. For an arbitrary point in solution field, the absolute velocity,
can be defined with the following relation:
where
is position vector from the origin of the moving frame and
is the angular velocity vector.
The governing equations of fluid flow in a moving reference frame can be written in two different ways: absolute velocity formulation or relative velocity formulation. The mass and momentum equations in the relative velocity formulation can be stated as:
where
is the Coriolis acceleration and
is the centripetal acceleration.
GEOMETRY AND COMPUTATION GRID
For better understanding of the behavior of forces and moments act on podded drives, three models were created: a single propeller model, pod and strut alone model and a puller podded drive. The Cartesian coordinates are used, where (
x
,
y
,
z
) denotes downstream, starboard, and upward direction, respectively. The origin of the coordinates is located at the center of the propeller hub. In puller drive calculation, positive direction is selected as downstream, starboard, and upward direction and positive yaw angles correspond to crossflow coming from portside.
In order to model the propeller in the fluid environment the solution field is divided into global and subdomain cylindrical frames, as depicted in
Fig. 1
. The subdomain frame simulates the propeller rotation and employs the Coriolis acceleration terms in the governing equations for the fluid. The global frame surrounds the subdomain frame. The global frame is a circular cylinder with 4
D
diameter, where
D
is the propeller diameter. The distance between the subdomain frame and inlet is nearly 4
D
, while it is nearly 6
D
for the outlet and dynamic frame. The same method is used for puller drive and pod alone but the dimensions of frames are selected related to the pod length. The positions of inlet and outlet are respectively 2.5
L_{Pod}
and 5
L_{Pod}
, where
L_{Pod}
is the pod length. The diameter of global frame is selected as 6
L_{Pod}
.
The model of solution field for single propeller (left) and puller podded drive (right).
For a single propeller, the solution field is divided into six blocks. Rotating block is meshed with unstructured tetrahedral cells and the other blocks are meshed with structured hexahedral cells. The unstructured grid causes a smoother discretization near the leading and trailing edge of the propeller. Surface of propeller and hub are meshed with the size of 0.01
D
. Also, four prismatic cells with the size of 0.001
D
are selected for boundary layer on propeller surface. The grid size for a single propeller is about 1.5
million
. Number of cells and value of wall Yplus parameters for these cases are shown in
Table 1
. The pod alone and puller drive are modeled with two and ten blocks respectively and unstructured tetrahedral cells are used in rotating block and static blocks. The mesh distribution of puller drive is shown in
Fig. 2
. Number of cells for pod alone and puller drive is about 1.1, 1.9
million
respectively.
Grid sizes and y^{+} values.
Mesh block around puller podded drive.
BOUNDARY CONDITIONS AND NUMERICAL SETUP
The governing equations of this problem are solved by the finite volume method based on the RANS equations. The Fluent 6.3 software was used to solve the RANS equations. Based on literatures published in the application of Fluent in the simulation of the flow around conventional propellers (Seo et al., 2010; Kulczyk et al., 2007), it is used in this study to investigate the open water hydrodynamic performance of the podded propeller.
The simple algorithm is used for solving the pressurevelocity coupling equations. The second order upwind discretization scheme is utilized for the momentum, turbulent kinetic energy, and turbulent dissipation rate in this problem.
The fluid (water) was assumed as an incompressible fluid, therefore; on the inlet boundary uniform velocity was imposed and on the outlet boundary, the static pressure was set to zero. The noslip wall condition was imposed on the propeller blades, pod, and strut.
FLOW ANALYSIS
The numerical method mentioned above is employed for the simulation of viscous flow around conventional marine propellers and puller podded drive. At first, the propeller is analyzed in open water condition in the absence of the pod and strut. Next flow around pod and strut are simulated without effect of propellers. Finally, the whole unit is studied in zero yaw angle and azimuthing condition.
 Grid dependency study
In this section, a single propeller model is selected. This is base propeller model geometry with 15° hub taper angle that was used by Liu in podded propeller research program (Liu, 2006). The characteristic curves and performance data of the propeller are determined by the experimental tests in the cavitation tunnel.
Tables 2
and
3
give the main dimensions and particular geometry data for propeller model respectively.
In order to get an evaluation of the grid uncertainty, the grid dependency study is conducted for single propeller. The study of the propeller performance in the open water condition was carried out for three different mesh resolutions. The best compromise between element size and accuracy has been obtained by results of this work. These models were simulated at
J
=0.6 and the results were compared to the experimental results. Results of the mesh convergence study are summarized in
Table 4
. The relative errors of thrust coefficient and torque coefficient for fine mesh was considered small, therefore fine mesh level is selected for further analysis.
Main dimensions of propeller model.
Main dimensions of propeller model.
Particular of propeller geometry.
Particular of propeller geometry.
The relative error of CFD results with respect to the experiments for grid dependency study.
The relative error of CFD results with respect to the experiments for grid dependency study.
 Single propeller
Assuming the constant rotational velocity for the propeller, its performance is investigated for different inlet velocities to obtain the characteristics of the propellers in open water conditions. The propeller angular speed is 15
rps
. The propeller thrust and torque are computed for a range of advance ratios from 0.2 to 1.0.
Fig. 3
represents the pressure distribution on back side and face side of the propeller at
J
=0.2. As observed in the figure, high pressure is at face side and low pressure is at back side.
Fig. 4
shows the vorticity distribution in x direction on the planes of 0.25
D
and 0.5
D
behind propeller. These counters are presented at
J
=0.2 (heavy condition) and
J
=1.0 (light condition). The tip and hub vortices can be founded in wake region. The xvorticity strength decreased in downstream with increase of
X/D
.
The pressure distribution on back (left) and face (right) side of the propeller at J=0.2.
Contours of Xvorticity on YZ planes behind propeller at J=0.2 and J=1.0.
The axial velocity contours of wake flow at J=0.2.
Also, the axial velocity distribution for propeller in transverse planes is shown in
Fig. 5
. It is clearly observed that the velocity at the propeller downstream position is high. In
X/D
=0.0, high speed zones shaped on back side of propeller near 0.7
R
, and low speed zones founded near the propeller tip. In
X/D
=2.0, concentric circles formed between 0.7
R
and the blade tip. Quantitatively, the pressure distribution coefficient for propeller
at four radii (
r/R
=0.3, 0.5, 0.7, and 0.9) is shown in
Fig. 6
. The blade sections of the propeller are well shaped to generate the moderate pressure distributions.
Fig. 7
shows the hydrodynamic characteristic curves obtained by analysis and its comparison with the experimental data. The results show that there is a good agreement between the experimental data and CFD results particularly for advance ratio 0.2 to 0.8. It can be seen that propeller thrust coefficient is underpredicted, while the propeller torque coefficient is overpredicted. In these range of advance ratio (
J
=0.2 to 0.8), the relative errors of CFD results with respect to the experiments for thrust coefficient, and torque coefficient at different advance ratio (J) are shown in
Table 5
. In general, the relative error for K
_{Q}
is greater than that for K
_{T}
at the same velocity advance ratio. The relative error of K
_{T}
and K
_{Q}
is less than 4% and +5% within the range
J
=0.2 to 0.6. The error starts to grow outside this range. According to these results, the error is slight in design condition and there is a discrepancy between numerical results and experimental data at very high speed condition, (
J
≥1).
The pressure coefficient distribution at J=0.2.
The experimental and computational characteristic curves of the single propeller.
The relative error of CFD results with respect to the experiments for single propeller.
The relative error of CFD results with respect to the experiments for single propeller.
 Pod and strut alone
The flow around the pod and strut is fully 3dimensional and nonsymmetric in nature. In this section, the pod and strut have been analyzed in RANS solver without propeller effects. The nondimensional data of the pod and strut is presented in
Table 6
. Profiles of the pod and strut is similar to the one used by Islam et al. (2007). A cylindrical domain was created around the pod and strut and an unstructured mesh was used. The noslip wall boundary conditions are applied on the pod and strut body. Flow characteristics around the pod and strut were evaluated in zero yaw angle and azimuthing condition at different inlet velocity. Yawing angles of the pod and strut are changed from +30° to 30° with 5° increment. The inflow velocity is selected same as single propeller advance ratio from 0.2 to 1.0.
Figs. 8
and
9
show velocity and pressure distribution predicted on the strut at zero and +30 yaw angle respectively. These counters are plotted in
Z/L_{pod}
=0.5 at
J
=0.6. The results are as expected. As seen in these Figs., the velocity is reduced on the side on which the flow hits the strut. Also, a high pressure is observed at a location where the flow hits the strut. The pressure on the opposite side of the strut remains mostly unaffected at the surface of them.
The nondimensional main particulars of pod and strut.
The nondimensional main particulars of pod and strut.
The velocity (left) and pressure (right) distribution around strut at zero yaw angle.
The velocity (left) and pressure (right) distribution around strut at +30° yaw angle.
 Puller podded drive
This section presents a validation study of RANS predictions of podded drive in azimuthing condition. A model of puller podded drive including propeller, pod, and strut has been established and the whole of unit has been analyzed in RANS solver. Flow characteristics around the propeller, pod and strut were evaluated. The puller drive is studied in zero yaw angle and azimuthing condition. Computational results are compared with experimental works of Islam et al. (2007). The total forces on puller drive in each direction and propeller thrust and torque are computed for a range of advance ratios from 0.2 to 0.8. In these calculations, the angular speed of propeller is set to 15
rps
as the one in model test. The angular speed of propeller is assumed to be constant. The range of Reynolds Number of blades is 2.4×10
^{5}
≤
Rn
≤ 1.2×10
^{6}
and for pod housing is about 3.7×10
^{5}
≤
Rn
≤ 1.8×10
^{6}
. Yawing angles of the podded drive are changed from +30° to 30° with 5° increment. Here,
Figs. 10

16
are presented and discussed for the calculations of the puller drive.
The pressure distribution on pod, strut, and back (left) and face (right) side of the propeller at zero yaw angle for puller propeller (J=0.2).
The experimental and computational characteristic curves of the puller drive at zero angle.
The velocity pathline on pod, strut and propeller at 30 yaw angle for puller propeller at J=0.6.
Variation of propeller thrust coefficient with yaw angle for puller podded drive.
Variation of propeller torque coefficient with yaw angle for puller podded drive.
Variation of total unit axial force coefficient with yaw angle for puller podded drive.
Variation of total unit side force coefficient with yaw angle for puller podded drive.
The relative error of CFD results with respect to the experiments for puller drive.
The relative error of CFD results with respect to the experiments for puller drive.
Fig. 10
shows pressure distribution on pod, strut, and propeller at zero yaw angle at an advance ratio of
J
=0.6. High pressure is on the face and low pressure is on the back side. The minimum pressures are located on the leading edge of the propeller blades, close to the tip. Since the strut and the pod are located in the downstream of the propeller, so the induced velocities from propeller change the inflow to the strut and pod. Swivel flow behind propeller blades has tangential and radial velocity. Therefore the surface pressure contours of the pod and strut are asymmetrical.
The propeller thrust and torque coefficients for puller podded drive in straight condition are presented in
Fig. 11
and compared by the experimental results. There is a good agreement between the numerical and the experimental results. The relative error of CFD results with respect to the experiments are shown in
Table 7
. It can be seen that the relative error of K
_{T}
and K
_{Q}
is less than 5% and +6% within the range
J
=0.2 to 0.6. The error increases at high advance ratio. According to these results, the propeller torque coefficient is overpredicted with RANS solver, while the propeller thrust coefficient is underpredicted.
Also, the performance of the puller podded drive is studied in azimuthing condition and results are compared by the experimental data. The results included are the propeller thrust coefficient, propeller torque coefficient, total unit axial force coefficient, and total unit side force coefficient at various yaw angles.
The streamlines at downstream of the puller drive for 30° yaw angle at an advance ratio of
J
=0.6 are shown in
Fig. 12
. At large yaw angles, as the flow passes over the propeller, the oblique flow and propeller slipstream induce strong vortex and separation on the pod and strut. As seen, due to the propellers’ actions, the flows are accelerated toward downstream.
Figs. 13
and
14
show the propeller thrust and torque coefficients for a range of advance ratios and yaw angles. According to these results, the propeller thrust and torque predictions for all advance ratios are in overall agreement with the test data. In general, the relative error for propeller torque is greater than that for propeller thrust at the same velocity advance ratio. Also, larger deviations are seen at high heading angles. The results for
J
=0.4 and
J
=0.6 are in better agreement with the test data than the other advance ratios.
Fig. 13
shows the propeller thrust coefficient for a range of advance ratios and yaw angles. In positive angles and negative angles, the propeller thrust coefficient increases with increasing yaw angle. This behavior is similar for all advance coefficients. As seen in
Fig. 13
, curves of the propeller thrust coefficients are symmetrical at positive and negative yaw angles. In azimuthing condition, the effective advance coefficient in the direction of the propeller axis is reduced. This results in higher thrust in the corresponding operating conditions.
The variation propeller torque coefficients are shown in
Fig. 14
. The same behavior is found in the propeller torque coefficient. The propeller torque coefficient increases when yaw angle is increased from zero to positive or negative yaw angles and the propeller thrust coefficients are approximately symmetrical at positive and negative yaw angles.
The total unit axial and side force coefficients for the puller podded drive at different yaw angles are presented in
Figs. 15
and
16
and compared with test data. In general, the total axial and side forces are predicted close to the test data.
As shown in
Fig. 15
, the total unit axial force coefficient decreases with increasing yaw angle. Curves of the axial force coefficients are not symmetrical at positive and negative yaw angles. In puller podded drive, the inflow on the pod and strut is influenced by propeller induced wake flow and the interaction between the propeller wake and the strut is dominated. This results in asymmetry in total unit axial force curve. For all advance ratios, the maximum value of the axial force coefficient is obtained at yaw angle +5° approximately.
Fig. 16
shows the side force coefficient variation with yaw angle. As shown, for all advance coefficients, the side force coefficient increases when yaw angle is increased to the left (negative yaw angle) or right (positive yaw angle). Also, side force coefficients for puller drive increase with increasing advance coefficient. The zero side force is found at the small yaw angle about 2°. Due to the propeller wake rotation and strut interactions, there is a small side force in straight condition (zero yaw angle) for podded drives.
CONCLUSIONS
In this paper, a finite volume based RANS solver has been used to evaluate the performance of the podded drive in straight and azimuthing condition. The rotation of the propeller was modeled using MRF method and kω model was selected as turbulence model. Hydrodynamic analysis of a single propeller, pod and strut alone, and puller drive was investigated at various yaw angles and operating conditions. Openwater characteristics of the propeller and puller podded drive axial and lateral forces were compared with the experimental data.
Based on the result of CFD simulation, Openwater characteristics of the single propeller are in good agreement with the experimental data. Also the RANS predictions of puller drive forces for all advance ratios are in overall agreement with the test data. The relative error for propeller torque is greater than that for propeller thrust at the same advance ratio and larger deviations are seen at high yaw angles. In general, the thrust, torque, and unit force coefficients showed a strong dependence on the velocity advance ratio and yaw angle.
The numerical investigation of the flow characteristics around the puller podded drive at different yaw angles showed that for all advance coefficients, the propeller thrust coefficient increases with increasing yaw angle. This behavior is similar for negative angles and positive angles, and curves of the propeller thrust coefficients are symmetrical at positive and negative yaw angles. The same behavior is found in the propeller torque coefficient. At azimuthing condition when yaw angle is changed from straight condition to positive or negative angle, the effective velocity advance coefficient in the direction of the propeller axis is reduced. This results in higher thrust in the corresponding operating conditions.
Besides, the study proved that the total unit axial force coefficient decreases with increasing yaw angle and curves of the axial force coefficients are not symmetrical at positive and negative yaw angles. Induced velocities from propeller change the inflow to the strut and pod. At large yaw angles, as the flow passes over the propeller, the oblique flow and propeller slipstream induce strong vortex and separation on the pod and strut. Therefore the surface pressure contours of the pod and strut are asymmetrical and results in asymmetry in total unit axial force curve.
The results also indicated side force coefficients increases with increasing yaw angle and velocity advance ratio. In puller podded drive, due to the propeller wake rotation and strut interactions, there is a small side force in straight condition.
Acknowledgements
This research was supported by High Performance Computing Research Center (HPCRC) at Amirkabir University of Technology, which is acknowledged. Authors would like to thank the reviewers for their valuable comments.
Amini H.
,
Steen S.
2011
Shaft loads on azimuth propulsors in oblique flow and waves.
International Journal of Maritime Engineering
153, Part A1
9 
22
Bal S.
,
Akyildiz H.
,
Guner M.
2006
Preliminary results of a numerical method for podded propulsors.
In Proceedings of 2nd TPOD Conference.
University of Brest, France
35 October 2006
Carlton J.S.
2007
Marine propeller and propulsion.
2nd ed.
ButterworthHeinemann
Oxford
Carlton J.S.
2008
Podded propulsors: some results of recent research and full scale experience.
Journal of Marine Engineering and Technology
11
1 
14
Ghassemi H.
,
Ghadimi P.
2008
Computational hydrodynamic analysis of the propeller rudder and the AZIPOD systems.
Journal of Ocean Engineering
35
(1)
117 
130
Islam M.F.
,
Veitch B.
,
Liu P.
2007
Experimental research on marine podded propulsors.
Journal of Naval Architecture and Marine Engineering
4
(2)
57 
71
ITTC.
2005
The specialist committee on azimuthing podded propulsion. Final report and recommendations to the 24th ITTC. 2
In Proceedings of the 24th ITTC
Edinburgh, UK
2005
543 
600
ITTC.
2008
The specialist committee on azimuthing podded propulsion. Final report and recommendations to the 25th ITTC. 2
In Proceedings of the 25th ITTC
Fukuoka, Japan
2008
563 
603
Kinnas S.A
2006
Prediction of performance and design of propulsorsrecent advances and applications.
In Proceedings of 2nd TPOD Conference.
University of Brest, France
35 October 2006
Koushan K.
,
Krasilnikov V.I.
2008
Experimental and numerical investigation of an open thruster in oblique flow conditions.
In Proceedings of the 27th Symposium on Naval Hydrodynamics.
Seoul, Korea
510 October 2008
Kulczyk J.
,
Skraburski L.
,
Zawislak M.
2007
Analysis of screw propeller 4119 using the fluent system.
Archives of Civil and Mechanical Engineering
7
(4)
129 
138
Liu P.
2006
The design of a podded propeller base model geometry and prediction of its hydrodynamics.
Report, Institute for Ocean Technology, National Research Council Canada (IOTNRC)
Report no. TR200616
Liu P.
,
Islam M.
,
Veitch B.
2009
Unsteady hydromechanics of a steering podded propeller unit.
Journal of Ocean Engineering
36
(1213)
1003 
1014
Reichel M.
2007
Manoeuvring forces on azimuthing podded propulsor model.
Journal of Polish Maritime Research
14
(2)
3 
8
SanchezCaja A.
,
Rautaheimo P.
,
Siikonen T.
1999
Computation of the incompressible viscous flow around a tractor thruster using a slidingmesh technique.
In Proceedings of 7th International Conference on Numerical Ship Hydrodynamics.
France
1999
Seo J.H.
,
Seol D.M.
,
Lee J.H.
,
Rhee S.H.
2010
Flexible CFD meshing strategy for prediction of ship resistance and propulsion performance.
International Journal of Naval Architecture and Ocean Engineering
2
(3)
139 
145
Szantyr J.A.
2001
Experimental measurements of the hydrodynamic characteristics of the pod propulsor models.
Journal of Polish Maritime Research
8
(4)
3 
7
Wilcox D.C.
1998
Turbulence modeling for CFD.
2nd ed.
DCW Industries, Inc.
California