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Energies 2020, 13, 370 6 of 31 on this novel layout is by Wu et al. [28], who optimized the performance of dual recuperated cycles (called “dual stage”) for WHR from exhaust gases with inlet temperatures in the range 250–500 ◦C. For the highest exhaust temperature of 500 ◦C, the dual recuperated cycle was found to improve by 4.5% the total heat recovery efficiency of the single recuperated cycle (i.e., 23.22% versus 18.77%). Furthermore, the highest performance was obtained at maximum pressures that were a few MPa lower than the corresponding ones for the single recuperated cycle. The authors showed that the performance of the dual recuperated cycle could be only marginally improved (less than 0.5%) by the addition of a third turbine and third recuperator. The performance comparison was extended to economic aspects in the recent study by Wang et al. [29], who carried out a thermodynamic and exergoeconomic optimization of a dual recuperated s-CO2 power cycle for WHR from a 2.9 MW internal combustion engine. The significant improvement in the net power output (22.2%) and the almost negligible increase in the cost compared to the single recuperated cycle obtained after the multi-objective optimization made the dual recuperated cycle the recommended choice. Instead, the addition of a third turbine and recuperator stage was found to be detrimental from both aspects. Astolfi et al. [30] recently evaluated the performance of the dual recuperated cycle (called “cascade recuperative”) for WHR in a wide temperature range between 200 and 600 ◦C. The authors showed that this layout always provides a higher power output than the single recuperated and recompression cycles for the utilization of waste heat sources having a high cooling grade. In particular, in the absence of any constraint on the minimum heat source outlet temperature, the total heat recovery efficiency was found to reach approximately 25% for a waste heat source at 550 ◦C. Thus, it clearly appears from these studies that the dual recuperated cycle has a high potential to improve the performance of traditional s-CO2 layouts in WHR applications. The claimed 22% to 24% gain in power compared to the single recuperated cycle closely matches that attainable by the single flow split with dual expansion and partial heating layouts having a similar complexity. So, an important need stands out for a systematic comparison between these three novel layouts based on a common basis to extend the study by Wright et al. [22]. A prerequisite to that is a deeper understanding of the topology of each power system, i.e., the way in which constituent parts (equipment) are interrelated or arranged. 1.5. Decomposition of Complex Plants into Elementary Thermodynamic Cycles Advanced layouts of power cycles are not easily comprehensible. The rationale behind the sequence of basic plant components and the design of heat transfer network within the system is not within everyone’s reach. The inventors of novel plant layouts often conceal the basic idea leading to a new plant proposal. To make the comprehension of advanced layouts easier, a method was conceived within the research group of the present first author, which traces the origin of the new layouts to the well-known Rankine and Brayton cycles. At the beginning, the method was merely applied to understand the genesis of advanced layouts based on the gas turbine. More recently, it has been codified in an algorithm to automatically generate new layouts of power cycles. The main development stages are briefly summarized in the following. In the proposal and application of the Heatsep method, Lazzaretto and Toffolo [31] showed that the synthesis of energy system configurations can be considered as an operation in which one or more thermodynamic cycles are composed into a single system. These cycles may be open or closed and the working fluids may be different. The different cycles may be separated, as in a combined gas/steam combined cycle, or partially superimposed, as in a steam gas injected gas turbine (STIG) or humid air turbine cycle (HAT). They share common transformations after their working fluids are merged (e.g., using mixers) and their common paths end when the streams are separated in other components (e.g., in splitters or condensers). In a further study, Lazzaretto and Manente [32] showed that the advanced oxy-combustion cycles, like the S-Graz or the H2/O2 power cycles, can be thought of as the superimposition of Brayton cycles operated by steam and/or CO2 and steam Rankine cycles with high temperature reheat and three expansion stages. Even though the analysis remained at a descriptive level, the authors could identify a clear evolution of the layouts ofPDF Image | Novel Supercritical CO2 Power Cycles for Waste Heat Recovery
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