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Energies 2019, 12, x FOR PEER REVIEW 13 of 22 Energies 2019, 12, x FOR PEER REVIEW 13 of 22 both geometries = 1400 Pa, in Figure 13, clearly illustrates the lower air velocity at the mid-chord both geometries = 1400 Pa, in Figure 13, clearly illustrates the lower air velocity at the mid-chord Energies 2019, 12, 2791 of the optimised design. 13 of 22 of the optimised design. 6 6 5 4 3 2 1 0 5 (a) 4 3 2 1 (a) Initial Initial Optimized 0 Optimized 0 [Pa] 0 [Pa] 12 12 1 10 8 6 4 2 0 4 3.0 4.0 0 (b) 8 6 4 2 0 Initial (b) 0.0 1.0 Optimized 0.0 1.0 2.0 φ φ 2.0 3.0 Initial Optimized Figure 12. Comparison of flow rate (a) and the input coefficient (b) of the optimised design with the Figure 12. Comparison of flow rate (a) and the input coefficient (b) of the optimised design with the Figure 12. Comparison of flow rate (a) and the input coefficient (b) of the optimised design with the initial outflow turbine geometry. ((a) Horizontal axis: total-static pressure drop, (b) Horizontal axis: initial outflow turbine geometry. ((a) Horizontal axis: total-static pressure drop, (b) Horizontal axis: initial outflow turbine geometry. ((a) Horizontal axis: total-static pressure drop, (b) Horizontal axis: flowflocwoecffioecfifeincite).nt). flow coefficient). .0 Figure 13. Comparison of the velocity contour of the initial and the optimised geometries at Figure 13. Comparison of the velocity contour of the initial and the optimised geometries at = ∆P =1400Pa. Figure 13. Comparison of the velocity contour of the initial and the optimised geometries at = 1400 Pa. 0 1400 Pa. As illustrated in Figure 14a, torque coefficient of the optimised design has improved significantly As illustrated in Figure 14a, torque coefficient of the optimised design has improved compared to the initial design, which according to the design characteristics of both geometries, is As illustrated in Figure 14a, torque coefficient of the optimised design has improved significantly compared to the initial design, which according to the design characteristics of both mostly due to 10 degrees higher LE angle and smaller chord length of the optimised design compared significantly compared to the initial design, which according to the design characteristics of both geometries, is mostly due to 10 degrees higher LE angle and smaller chord length of the optimised to the initial geometry. According to Figure 14b, the optimised geometry has 30% higher peak efficiency geometries, is mostly due to 10 degrees higher LE angle and smaller chord length of the optimised design compared to the initial geometry. According to Figure 14b, the optimised geometry has 30% than the initial design, which has been obtained by finding the optimum combination of the input design compared to the initial geometry. According to Figure 14b, the optimised geometry has 30% higher peak efficiency than the initial design, which has been obtained by finding the optimum parameters used in this study. For the optimised design, the operational flow range is smaller than the higher peak efficiency than the initial design, which has been obtained by finding the optimum combination of the input parameters used in this study. For the optimised design, the operational initial design and the peak efficiency point has moved towards smaller flow coefficients. This fact was combination of the input parameters used in this study. For the optimised design, the operational flow range is smaller than the initial design and the peak efficiency point has moved towards smaller previously explained by comparing the flowrate versus pressure drop of both geometries in Figure 12a. flow range is smaller than the initial design and the peak efficiency point has moved towards smaller flow coefficients. This fact was previously explained by comparing the flowrate versus pressure drop It can be noted from the above-mentioned results that shape of the rotor blade can significantly affect flow coefficients. This fact was previously explained by comparing the flowrate versus pressure drop of both geometries in Figure 12a. It can be noted from the above-mentioned results that shape of the the turbine’s performance including torque and the power conversion. The velocity vectors in the of both geometries in Figure 12a. It can be noted from the above-mentioned results that shape of the rotor blade can significantly affect the turbine’s performance including torque and the power rotor domain of both geometries near their peak efficiency points (at ∆P0 = 1400 Pa) are illustrated rotor blade can significantly affect the turbine’s performance including torque and the power conversion. The velocity vectors in the rotor domain of both geometries near their peak efficiency in Figures 15 and 16. Comparing these figures shows that although the initial design allows more conversion. The velocity vectors in the rotor domain of both geometries near their peak efficiency points (at = 1400 Pa) are illustrated in Figures 15 and 16. Comparing these figures shows that flowrate into theturbine domain, the rotor cannot efficiently convert the input power due to the energy points (at = 1400 Pa) are illustrated in Figures 15 and 16. Comparing these figures shows that although the initial design allows more flowrate into the turbine domain, the rotor cannot efficiently losses in the domain. As shown in Figure 15, there are huge incident losses at the leading-edge of although the initial design allows more flowrate into the turbine domain, the rotor cannot efficiently convert the input power due to the energy losses in the domain. As shown in Figure 15, there are the rotor blades in the initial design while there is a perfect stream of the flow in the turbine domain convert the input power due to the energy losses in the domain. As shown in Figure 15, there are huge incident losses at the leading-edge of the rotor blades in the initial design while there is a perfect of the optimised design (Figure 16). It can be noted that the well-matched configuration of the rotor huge incident losses at the leading-edge of the rotor blades in the initial design while there is a perfect Q [m^3/s] Q [m^3/s] CA CAPDF Image | Unidirectional Radial-Air-Turbine OWC Wave Energy Converters
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