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However, in reality the work input to the pump exceeds the enthalpy increase due to irreversibilities, such as friction, and we have that [33] ηp = h2s − h1 h2 − h1 h2 = h1 + h2s − h1 ηp W ̇ p = m ̇ wf · (h2 − h1) (2.17) (2.18) (2.19) For Rankine cycles using steam as the working fluid, the pump work in relation to the turbine work is small, and often neglected in calculations. However for Rankine cycles using organic fluids, the ratio of pump work to turbine work (BWR) can reach 16% [38]. (2) →− (3) Isobaric heat addition in the boiler. The pressurized water is heated and vaporized in the boiler. The heat input which is absorbed by the water equals the product of the mass flow rate of the water and the difference of the specific enthalpies of the water, before and after the boiler. The governing equation for the heat addition into the cycle is [33] Q ̇ in = m ̇ wf · (h3 − h2) (2.20) (3) →− (4) Isentropic expansion in the turbine. The water, now in vaporized form as steam, is expanding through the turbine, giving off a part of its energy as work to the turbine blades resulting in a rotational motion of the turbine around its shaft. The rotational, mechanical, energy of the rotating shaft is then converted into electrical energy by use of a electrical generator. In the ideal case the work output is given as W ̇T =m ̇wf·(h3−h4) (2.21) However, in reality the enthalpy drop over the expander (most often an axial turbine) is reduced due to irreversibilites. This is accounted for by the isentropic efficiency of the expander. ηT = h3 − h4 h3 − h4s h4 = h3 − ηT · (h3 − h4s) W ̇T =m ̇wf·(h3−h4) (4) →− (1) Isobaric heat rejection in the condenser. After the turbine the fluid exists as a liquid-vapor mixture. The vapor content of the mixture is 22PDF Image | Analysis of Organic Rankine Cycles for a Boiler Station
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