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359 volume to run. The ORC configurations are therefore more technically feasible, due to the lower size requirements of 360 the heat exchangers. 361 The temperature difference between the hot and the cold flow (dT) dramatically affects to the reduction of bsfc. A 362 change from dT = 10◦C to dT = 20◦C reduces the size of the heat exchangers by about 50%, but this change also 363 increases the bsfc by about 3 percentage points. 364 Finally, the results show that the irreversibilities in the expander and pump can lead to an increase between 2 and 365 4 percentage points the bsfc. In concrete terms, 3 percentage points of bsfc increment in the most feasible case (6r) 366 with respect to the ideal (6i) case. 367 5. Conclusions 368 This paper describes a methodology to optimize a bottoming cycle which recovers low temperature waste heat 369 sources to generate mechanical power in vehicles. The methodology followed is to select the waste heat sources, the 370 optimum working fluid, the expander machine, the pump, the heat exchangers and the thermodynamic characteristics 371 of the cycle, according to different initial limitations or goals initially established. The goals are usually a reduction in 372 bsfc, with a low effect on the engine space requirements and low costs. In order to illustrate the methodology, the case 373 of an implementation of a bottoming cycle in a HDD engine has been described and a realistic result of a maximum 374 improvement of about 5 % in bsfc has been obtained. In the heat sources selection, a power and exergy study of each 375 waste heat source is required in order to analyze which ones are the most useful for the generation of power output. 376 Taking different criteria into account , depending on the problem to solve, the optimal solution can be the recovering 377 of all the available heat sources or only the available heat sources with high temperature levels. Many heat sources to 378 recover imply high output power in the bottoming cycle but unfortunately, it also implies high heat exchanger volumes 379 and a complex control of the cycle and additionally, it can decrease the bottoming cycle average efficiencies. 380 The working fluid selection strongly affects to the performance of the bottoming cycle. Considering the case of 381 the HDD engine, the highest reduction in bsfc is produced when the water RC is used. But these RC configurations 382 need high heat exchanger volumes to run. The ORC configurations are more technically feasible due to lower size 383 requirements of the heat exchangers (about 50% lower than RC configurations), but produce lower power than the RC 384 configurations (leading to differences of 3 percentage points in bsfc). 385 The minimum temperature difference in the heat exchangers (dT) dramatically affects the reduction of bsfc. So, 386 the heat exchanger sizing must be determined correctly to optimize the bsfc with low space requirement. In the case 387 of the HDD engine, changing the dT from 10 ◦C to 20 ◦C leads to a decrease of the volume required by the heat 388 exchangers by about 60 % and increases the bsfc by about 3 percentage points. 389 Therefore, considering the complexity of selecting the heat sources, the working fluid and the minimum temper- 390 ature difference in the heat exchangers, this paper presents an iterative methodology to obtain the goal defined in the 13PDF Image | Methodology to design a bottoming Rankine cycle
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