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137 level distributions very different and 2) The maximum reduction of brake specific fuel consumption will be achieved 138 in these operative points for the two cycles studied in this paper. The total waste power of the engine (summarizing all 139 the heat sources) is represented in the engine map (Figure 3). The contour lines in Figure 3 were created on the basis 140 of the eleven engine operating points. The Kriging interpolation method [30] was applied on all contour lines of the 141 figures in the paper using a surface mapping software (SURFACE v8.0) [31]. Figure 3 shows that the available power 142 increases with the crankshaft speed and the engine load. The highest waste heat power corresponds to the 1800 rpm 143 and 100% load, because this is the point where the most fuel is injected. While 600 rpm and 0% does not practically 144 generate any waste heat. 145 The waste heat power of the HDD engine is up to 420 kW. But this power can be used to improve the engine 146 efficiency if it is converted into mechanical work. The exergetic study of these waste heat sources can evaluate which 147 is the maximum obtainable work in each engine operating point. The exergy represents the maximum work that can 148 be extracted from a thermodynamic cycle from an initial state (state 1) to an environment state (state 0). Thus, the 149 exergy is obtained as Equation (2) shows: Ex =m ̇ (h −h)−T(s −s) (2) flow flow 1 0 0 1 0 150 In this way, the exergy variation between two states (from 1 to 2) with the same environmental conditions can be 151 obtained as Equation (3) shows: △Ex =m ̇ (h −h)−T(s −s) (3) flow1−2 flow 2 1 02 1 152 The exergies of the waste heat sources considered in this study can be calculated as a total exergy (exhaust gases) 153 using Equation (2) or as variation of exergy (intercooler, aftercooler, EGR and cooling water) using Equation (3). The 154 exergetic levels of the waste heat sources at 1800 rpm -100 % load and 1200 rpm and 25 % load are listed in Table 2 155 Adding all these wasted exergies, the total waste exergy can be calculated. Figure 4 shows this total waste exergy on 156 the engine map. 157 When the results are analyzed in terms of exergy, we can state that a third of the total waste power could be 158 converted into mechanical power by a thermodynamic cycle, if the external and internal irreversibilities are not con- 159 sidered. 160 It is worth noting that in a thermodynamic cycle, the highest exergy destruction will further mainly take place 161 during the heat transfer process in the heat exchangers. The greater the temperature difference between the cooled 162 fluid and the heated fluid, the greater the exergy destruction [32–35]. On the other hand, this temperature difference 163 will depend strongly on the selected working fluid 164 3.3. Selection of the waste heat sources 165 The third step is the selection of the waste heat sources. The selection process depends on the goals and limitations 166 fixed in the specification problem (first step). To illustrate the methodology exposed in this paper, two different 6PDF Image | Methodology to design a bottoming Rankine cycle
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