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(exhaust gas, point h), then the difference decreases rapidly along the gas heater until it reaches a very small value on the other end of the gas heater, where the inlet of the heat source (exhaust gas, point g) and the outlet of the supercritical CO2 (point d) are located. Due to the difference in Cp variations, the temperate profiles in both MHX and IHX will be influenced. T‐∆h charts for the integrated total heat exchanger length (MHX and IHX) with different CO2 mass flow rates are plotted in the following figures to show this influence (Figure 4‐6 a and b)17. From the figures, one can see that except for a short increase when supercritical CO2 first enters the IHX (point b), the temperature profile of supercritical CO2 in the IHX is fairly flat due to the sharp increase of its Cp (point b‐point c). When it flows further through the gas heater (point c – point d), the temperature of supercritical CO2 will increase rapidly due to the sharp decrease of its Cp value (see Figure 4‐5). This characteristic provides the carbon dioxide transcritical power cycle with more advantages in low‐grade heat source recovery than power cycles using other working fluids. Due to the sharp increase of its Cp value in the IHX, the supercritical CO2 can recover a substantial amount of energy from the expansion outlet (point e to point f in Figure 4‐6) without an obvious increase in its temperature (point c). Therefore, after recovering a significant amount of energy from the expansion outlet, the supercritical CO2 still has a huge potential to further recover the energy in low‐grade heat source when it enters the gas heater. Consequently, the specific energy content of supercritical CO2 will be higher, and thus a lower mass flow can be achieved compared to the working fluids that do not have this characteristic of Cp variation. 17 The state points correspond to points in figure 2 56PDF Image | Thermodynamic Cycles using Carbon Dioxide
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