## 3 Results and Discussion
### The Effects of Deflection of Propeller Shaft on Pressure and Deform Distribution  
Figure 10 shows the distribution of the water film pressure, contact pressure, elastic deformation, and thermal deformation under the deflected propeller shaft. Figure 10a shows that the deflected shaft causes asymmetric hydrodynamic pressure distribution. By comparing the results plotted in Figure 10a, it was found that the external force is mainly carried by the asperity contact in the current simulated case, which demonstrates that the asperity contact plays a crucial role in the actual operating condition of the WLRSB. The results shown in Figure 10 indicate that the maximum fluid pressure, contact pressure, elastic deformation, and thermal deformation are mainly located on the water outlet side when the deflection of the propeller shaft is considered. This is because the deflected shaft decreases the lubrication gap close to the water inlet, thereby resulting in an increase in hydrodynamic pressure, asperity contact, and frictional heat. Figure 10c shows that negative elastic deformation occurs near the maximum elastic deformation; this is due to the fact that the rubber can be treated as an incompressible material owing to its Poisson's ratio being near to 0.5. Moreover, Figure 10d indicates that the thermal deformation of the groove region is less than that of the pressured region; this is because the water flow in the groove removes a large amount of heat, thus reducing the thermal expansion in such a region. In general, it can be concluded that strong hydrodynamic and contact effects are yielded at the outlet water side of the JWR system when deflection of the propeller shaft is considered.  
\begin{table}
\begin{tabular}{c c c c} \hline
**Parameter** & **Value** & **Parameter** & **Value** \\ \hline Inner radius/\(R_{1}\) & 45 mm & External force/\(M\) & 10 kN \\ Outer radius/\(R_{2}\) & 50 mm & Bearing density/\(\rho_{R}\) & 1500 kg/m\({}^{3}\) \\ Clearance/C & 0.15 mm & Rubber thermal conductivities/\(k_{R}\) & 0.288 W/(m\(\cdot\)K) \\ Bearing width/\(L\) & 160 mm & Rubber specific heat/\(C_{PR}\) & 1700 J/(kg\(\cdot\)K) \\ Groove radius/\(R_{g}\) & 2.5 mm & Rubber thermal expansion/\(T_{R}\) & 121 \(\mu\)m/(m\(\cdot\)K) \\ Groove width/\(W_{g}\) & 6 mm & Water viscosity/\(\eta\) & 8.944 \(\times\) 10\({}^{-4}\) Pa\({}_{\cdot}\)s \\ Groove number/\(n_{g}\) & 8 & Water density/\(\rho_{W}\) & 1000 kg/m\({}^{3}\) \\ Journal elastic modulus/\(E_{J}\) & 210 GPa & Water thermal conductivities/\(k_{W}\) & 0.61 W (m\(\cdot\)K) \\ Journal Poisson ratio/\(\
u_{J}\) & 0.3 & Water specific heat/\(C_{PW}\) & 4200 J/(kg\(\cdot\)K) \\ Journal density/\(\rho_{J}\) & 7800 kg/m\({}^{3}\) & Heat transfer coefficient/\(h_{h}\) & 80 W(m\({}^{2}\cdot\)K) \\ Journal thermal conductivities/\(k_{J}\) & 50 W/(m\(\cdot\)K) & Inlet temperature/\(T_{c}\) & 20 \({}^{\circ}\)C \\ Journal specific heat/\(C_{Pl}\) & 460 J/(m\(\cdot\)K) & Ambient temperature/\(T_{\infty}\) & 20 \({}^{\circ}\)C \\ Journal thermal expansion/\(T_{J}\) & 11.9 \(\mu\)m/(m\(\cdot\)K) & Friction coefficient/\(\mu_{C}\) & 0.15 \\ Bearing elastic modulus/\(E_{R}\) & 7.85 \(\times\) 10\({}^{8}\) Pa & Journal roughness/\(\
u_{J}\) & 0.5 \(\mu\)m \\ Bearing Poisson ratio/\(\
u_{R}\) & 0.47 & Rubber roughness/\(\
u_{R}\) & 0.6 \(\mu\)m \\ Bearing hardness/\(H_{B}\) & \(5\times\) 10\({}^{7}\) Pa & & \\ \hline \end{tabular}
\end{table}
Table 1: The basic parameters of the proposed model.