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Energies 2019, 12, x FOR PEER REVIEW Energies 2019, 12, x FOR PEER REVIEW 14 of 22 14 off222 stream of the flow in the turbine domain of the optimised design (Figure 16). It can be noted that the EEnneregrgieises2200119,91, 21,22, 7x9F1OR PEER REVIEW stream of the flow in the turbine domain of the optimised design (Figure 16). It can be noted that the stream of the flow in the turbine domain of the optimised design (Figure 16). It can be noted that the well-matched configuration of the rotor blades with respect to the upstream guide vanes is the main well-matched configuration of the rotor blades with respect to the upstream guide vanes is the main blades with respect to the upstream guide vanes is the main reason for low flow incidence in the well-matched configuration of the rotor blades with respect to the upstream guide vanes is the main reason for low flow incidence in the optimum design. reason for low flow incidence in the optimum design. optimum design. reason for low flow incidence in the optimum design. 10 1 10 1 14 of 22 910 9 89 8 78 7 67 6 56 5 45 4 34 3 23 2 12 1 1.0 Optimized 1.0 2.0 3.0 4.0 2.0 3.0 4.0 (a) (a) Initial (a) Initial Initial Optimized Optimized 01 00.0 0.0 0.0 1.0 φ2.0 φ φ 3.0 4.0 0.9 1 0.9 0.80.9 0.8 0.70.8 0.7 0.60.7 0.6 0.50.6 0.5 0.40.5 0.4 0.30.4 0.3 0.20.3 0.2 0.10.2 0.1 0.1 00.0 0.0 0.0 1.0 φ 2.0 φ φ 3.0 4.0 1.0 2.0 3.0 4.0 1.0 2.0 3.0 4.0 Initial Initial (b) (b) Initial Optimized Optimized (b) Optimized Figure 14. Comparison of the torque coefficient (a) and efficiency (b) of the optimised design against Figure 14. Comparison of the torque coefficient (a) and efficiency (b) of the optimised design against Figure 14. Comparison of the torque coefficient (a) and efficiency (b) of the optimised design against thFeiignuitrieal1o4.uCtfolomwptaurrisboineogfethome teotrqyu. (eHcoreifzfiocnietanlta(xa)isa:nfldoweffciocieefnficyie(nbt).of the optimised design against the initial outflow turbine geometry. (Horizontal axis: flow coefficient). the initial outflow turbine geometry. (Horizontal axis: flow coefficient). the initial outflow turbine geometry. (Horizontal axis: flow coefficient). Figure 15. Velocity vectors in the turbine domain of the initial geometry at ∆P = 1400 Pa. Figure 15. Velocity vectors in the turbine domain of the initial geometry at ∆P = 1400 Pa. Figure 15. Velocity vectors in the turbine domain of the initial geometry at ∆P0 = 1400 Pa. Figure 15. Velocity vectors in the turbine domain of the initial geometry at ∆P = 1400 Pa. Figure16.Velocityvectorsintheturbinedomainoftheoptimisedgeometryat∆P =1400Pa. Figure 16. Velocity vectors in the turbine domain of the optimised geometry at 0 = 1400 Pa. Figure 16. Velocity vectors in the turbine domain of the optimised geometry at = 1400 Pa. Figure 16. Velocity vectors in the turbine domain of the optimised geometry at = 1400 Pa. 6.2. Energy Transfer in Radially Outward and Inward Flow Turbines 6.2. Energy Transfer in Radially Outward and Inward Flow Turbines 6.2. Energy Transfer in Radially Outward and Inward Flow Turbines 6.2. Energy Transfer in Radially Outward and Inward Flow Turbines The Euler turbine equation can be written as the summation of energy transfer terms. These energy The Euler turbine equation can be written as the summation of energy transfer terms. These The Euler turbine equation can be written as the summation of energy transfer terms. These terms are the change in dynamic energy (associated with absolute velocity), change in centrifugal The Euler turbine equation can be written as the summation of energy transfer terms. These energy terms are the change in dynamic energy (associated with absolute velocity), change in energy terms are the change in dynamic energy (associated with absolute velocity), change in energy terms are the change in dynamic energy (associated with absolute velocity), change in C C CTT T ηη ηPDF Image | Unidirectional Radial-Air-Turbine OWC Wave Energy Converters
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