## 3 Results and Discussions
### Advanced Exergetic Analysis  
In this way, an advanced exergetic analysis is proposed, finding the endogenous destroyed exergy that arises from the interception of the inclined line with the \(E_{F}-E_{P}-E_{L}\)[65], taking into account that this interception must be greater than zero and less than the \(E_{d,k}\) for each device. In Figure 11, the graphical method for obtaining the value of endogenous exergy destruction is shown for Pump 1, Pump 2, the condenser, the evaporator, the regenerator, and the turbine, where a four-point regression was performed between the exergy destruction between the exergy destruction of the cycle without the component to be studied (Ed others) and the total exergy destruction of the system (Efuel-Eproduct-Eloss), having the exergetic efficiency of the component as a fixed value and starting point in the graph [66]. By regressing to the point where the line is intercepted with the values of total exergy destroyed from the system, the endogenous exergy destruction values of each component can be found as follows: Pump 1 (Figure 11a) 0.11 kW, Pump 2 (Figure 11b) 0.27 kW, the condenser (Figure 11c) 4.01 kW, the evaporator (Figure 11d) 40.44 kW, the regenerator (Figure 11e) 38.92 kW, and the turbine 1.61 kW. It is observed that the evaporator and the regenerator have the highest values of endogenous exergy destroyed due to the fact that they are heat exchangers, it is possible that they are working inefficiently, and therefore it is necessary to take into account these components to make technical and economic improvements through advanced and exergo-economic analysis to find technical and economic improvements. Taking into account that some operating conditions are chosen for the unavoidable exergy, the selection of the parameters is given by the studies mentioned in Table 10.  
Figure 11: Exergy destroyed endogenously for (**a**) Pump 1; (**b**) Pump 2; (**c**) Condenser; (**d**) Evaporator; (**e**) Regenerator; and (**f**) Turbine. Taking into account the conditions in Table 10, together with the equations, which are found in the contents of Section 2.4, the division of the exergy destroyed into avoidable and unavoidable can be carried out, annexing this to the endogenous and exogenous part, obtaining avoidable and unavoidable parts of the endogenous and exogenous parts for each component for each of the components except for the condenser and regenerator, because they operate as a heat sink. Figure 12 shows that the percentage of the different divisions of the exergy destroyed found so far for each component, showing emphasis on the opportunities for both endogenous and exogenous improvements. According to Figure 12, the improvement opportunities differ for the Pump 2 component, i.e., 60.85% of endogenous character and 22.4% of exogenous character can be avoided. In addition, for the evaporator, 38.88% of endogenous character and 17.35% of exogenous character can be avoided. Likewise, the improvement opportunities for the turbine are more significant if it is of an exogenous nature with 63.8%, which means that the improvement opportunities depend on the components with which it interacts. Table 10 shows the values of exogenous exergy destroyed, which are similar to a study by [PERSON] et al. [36]. Their results in the ORC cycle, indicated that the greatest potential for improvement through technical modifications was in the turbine where 88% of the exergy destroyed in this way could be reduced by improving technology of the avoidable/endogenous component [44; 45; 67], whereas, in the pump, it could be reduced by 70% by means of operational optimization [68]. Similarly, in this study, a greater opportunity for improvement was observed in an endogenous way (60.85%) in Pump 2 where the organic fluid is transported, therefore the studies on the performance of organic