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Table 1. Micro steam-turbine design specifications. B. Kareem et al. Description Turbine type Expected power Steam mass flow rate Efficiency Specification Axial flow, impulse flow steam nicro turbine 5.5 kW 0.0275 kg/s 75% Design specifications Description Stage Rotation speed Turbine inlet temperature Specific heat capacity of steam Specification Multistage >1500 rpm 400 ̊C 0.03571/mol∙ ̊C [18]. In an impulse turbine all the enthalpy change takes place in the stationary nozzles. This action has made the impulse stages liable to low axial thrust loads on the rotor. The velocity diagram for the impulse turbine with directions of movement, angle of incidence or contact and the resulting velocities for Euler’s equation are in Figure 2, where V, is absolute inlet steam velocity; V1, is relative inlet steam velocity (to moving blades); W, is blade tangential speed; V2, is rela- tive exit steam velocity (neglecting losses); V3, is absolute exit steam velocity; θ, is vector difference between V and W or nozzle discharge angle; θ1, is vector dif- ference between V1 and W; θ2, is vector difference between V2 and W; and θ3, is vector difference between V3 and W. On these bases, absolute inlet velocity, V of the impulse turbine was obtained from Equation (2), while the vector difference (nozzle discharge angle), θ was estimated as 30 ̊ using Equation (3) (giving efficiency of turbine, η as 75%. This outcome rendered optimum absolute inlet steam velocity, Voptimum to be 0.5 using Equation (4). V = 44.7 × (ΔH)0.5 (2) η = cos2θ. (3) Voptimum = 2W/Cos θ (that is W/V = 0.5) (4) By considering minimum rotational output speed (>1500 rpm), while input speed of 8000 rpm (ώ, 942.48 rad/s) were considered over the linear velocity re- quired from the blade mounted on rotor diameter 300 mm (r, 150 mm) obtained from W = rώ, using a rotor diameter of 300 mm as 142 m/s. Hence, the absolute velocity of steam flow is 326.48 m/s while the resultant blade velocity is 142 m/s. Followed from Equations (2)-(4), ΔHstage was estimated as 53.34 kJ/kg making a total of Ns equal to 5 stages under the ΔHavail of 266.67 kJ/kg available. The blade of the turbine was airfoil-designed to enable maximum use of the energy from steam for rotation [19]. The geometry of entry and exit of steam into/from the blade was optimized by considering the pitch and chord lengths of the blades (Figure 3). The principal parameters considered in the design are blade profile (airfoil cross section), blade solidity/pitch to chord ratio, blade aspect ratio/height to chord ratio, and blade stacking. Standard designed procedures of the stated parameters were modified to optimally meet the micro power requirement level of the turbine. DOI: 10.4236/jpee.2018.611009 115 Journal of Power and Energy EngineeringPDF Image | Design of Steam Turbine for Electric Power Production Using Heat Energy from Palm Kernel Shell
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