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Thermodynamic Optimization for an Endoreversible Dual-Miller Cycle (DMC) with Finite Speed of Piston

Power output (P), thermal efficiency (η) and ecological function (E) characteristics of an endoreversible Dual-Miller cycle (DMC) with finite speed of the piston and finite rate of heat transfer are investigated by applying finite time thermodynamic (FTT) theory. The parameter expressions of the non-dimensional power output (P¯), η and non-dimensional ecological function (E¯) are derived. The relationships between P¯ and cut-off ratio (ρ), between P¯ and η, as well as between E¯ and ρ are demonstrated. The influences of ρ and piston speeds in different processes on P¯, η and E¯ are investigated. The results show that P¯ and E¯ first increase and then start to decrease with increasing ρ. The optimal cut-off ratio ρopt will increase if piston speeds increase in heat addition processes and heat rejection processes. As piston speeds in different processes increase, the maximum values of P¯ and E¯ increase. The results include the performance characteristics of various simplified cycles of DMC, such as Otto cycle, Diesel cycle, Dual cycle, Otto-Atkinson cycle, Diesel-Atkinson cycle, Dual-Atkinson cycle, Otto-Miller cycle and Diesel-Miller cycle. Comparing performance characteristics of the DMC with different optimization objectives, when choosing E¯ as optimization objective, η improves 26.4% compared to choosing P¯ as optimization objective, while P¯ improves 74.3% compared to choosing η as optimization objective. Thus, optimizing E is the best compromise between optimizing P and optimizing η. The results obtained can provide theoretical guidance to design practical DMC engines.


Introduction
Finite time thermodynamics (FTT) theory [1][2][3][4][5][6][7][8][9][10][11] plays an increasingly important role in analyzing and optimizing performance characteristics of the thermodynamic processes [12][13][14] and cycles [15][16][17][18][19]. With the development of FTT, its research objects extended from conventional heat engine [20][21][22], refrigerator and heat pump [23] to unconventional systems, such as chemically driven engine [24], quantum engine [25][26][27][28][29][30][31] and energy selective electron engine [32][33][34]. Until now, scholars have performed many FTT studies for internal combustion engine (ICE) cycles [35]. Analyses of the different optimization objective functions are also important work for studying performance characteristics of the ICE cycles. Some new optimization objective functions on the basis of the power output (P) and thermal efficiency (η), such as the specific power [36,37], power density [38,39], exergetic performance [40][41][42][43] and finite time exergoeconomic performance [44,45] had been proposed. Besides, Angulo-Brown [46] first introduced the ecological function E = P − T L σ for the heat engine cycle DMC can be simplified to other gas cycles; the performance characteristics of other gas cycles are special cases of those of DMC. Based on the work mentioned above, this paper establishes an endoreversible DMC model with finite speed of the piston and finite rate of HT. The power output, thermal efficiency and ecological function are investigated based on assuming piston speeds are unequal constants in different processes by combining with FTT and FST [75,85]. The parameter expressions of non-dimensional power output, thermal efficiency and non-dimensional ecological function are derived. The effects of design parameter and piston speeds on the performance of the cycle are analyzed, and the impact degrees of the time in each process on the performance of the cycle are compared. variable specific heat ratio [95] and nonlinear variable specific heat ratio [95] of working fluid, respectively, analyzed and optimized P , η and E of the cycles. You et al. [97] replaced the two reversible adiabatic processes of the DMC with two polytropic processes, studied P , η and E of the cycle. DMC can be simplified to other gas cycles; the performance characteristics of other gas cycles are special cases of those of DMC. Based on the work mentioned above, this paper establishes an endoreversible DMC model with finite speed of the piston and finite rate of HT. The power output, thermal efficiency and ecological function are investigated based on assuming piston speeds are unequal constants in different processes by combining with FTT and FST [75,85]. The parameter expressions of non-dimensional power output, thermal efficiency and non-dimensional ecological function are derived. The effects of design parameter and piston speeds on the performance of the cycle are analyzed, and the impact degrees of the time in each process on the performance of the cycle are compared.  Assuming the model is an air-standard cycle and the working fluid is an ideal gas. The working fluid absorbs heat in → 2 3 and → 3 4 processes, and releases heat in → 5 6 and → 6 1 processes. In the processes of →  Assuming the model is an air-standard cycle and the working fluid is an ideal gas. The working fluid absorbs heat in 2 → 3 and 3 → 4 processes, and releases heat in 5 → 6 and 6 → 1 processes. In the processes of 2 → 3 and 3 → 4 , the quantities of heat provided by heat source T H are Q H1 and Q H2 , respectively. In the processes of 5 → 6 and 6 → 1 , the quantities of heat released to heat sink T L are Q L1 and Q L2 , respectively. According to Refs. [68,90,91], one can assume that the law of HT obeys q ∝ (∆T), there are where U H1 , U H2 and U L1 , U L2 are HT coefficients, W/ m 2 · K ; F H1 , F H2 and F L1 , F L2 are HT areas of the heat exchangers between the working fluid and the heat reservoir, m 2 ; t 2−3 , t 3−4 , t 5−6 and t 6−1 are the times in processes 2 → 3 , 3 → 4 , 5 → 6 and 6 → 1 , s; m is mass of working fluid, kg;

Cycle Model and Performance Analyses
C v and C p are specific heats at constant volume and constant pressure, J/(kg · K), they can be taken as constants because the working fluid is the ideal gas; and ε H1 , ε H2 and ε L1 , ε L2 are the effectiveness of heat exchangers in hot side and cold side, and they are given as: where N H1 , N H2 and N L1 , N L2 are numbers of heat exchangers HT unites in hot side and cold side, which are expressed as: The total heat addition quantity Q H is The total heat rejection quantity Q L is From Equations (1)-(4), one has The definitions of cut-off ratio and Miller cycle ratio are The following equation is obtained based on the second law of thermodynamics [89] T k Combining Equations (10), (13) and (15), the function of T 2 as related with T 5 is derived. Combining Equations (12), (14) and (15), the function of T 5 as related with T 2 is derived.

Analyses of Special Cases
Equations (19), (28) and (32) are expressions of η, P and E of an endoreversible DMC. When the temperatures at different state points reach certain relationships, they can be transformed into expressions of η, P and E of different simplified cycles with finite speed of the piston.
According to Refs. [68,90,93], it is set that T 0 = T L = 300 K, T H = 800 K, k = 1.4, ε H1 = ε H2 = ε L1 = ε L2 = 0.25, ρ = 1 ∼ 1.2, x = 1, 10, 100, y = 1, 10, 100, a = 1, 3, 6 and b = 1, 3, 6 in the calculations. Thus, the characteristics relationships between P and ρ, between P and η, as well as between E and ρ of an endoreversible DMC with finite speed of the piston can be obtained. Figures 2-4 show the non-dimensional power output (P) versus cut-off ratio (ρ), P versus thermal efficiency (η), and non-dimensional ecological function (E) versus ρ characteristics when x and y take different values, respectively. In Figures 2 and 4, one can see that P and E first increase and then start to decrease with increasing ρ. There are two different ρ when P and E reach to zeroes, respectively. Moreover, there are different optimal cut-off ratios (ρ opt ) to make P and E reach their maximum values, respectively. However, there are some differences between the curves of P versus ρ and E versus ρ. For example, the ending point of ρ is 1.111 corresponding to P = 0, but the ending point of ρ is 1.071 corresponding to E = 0. The reason is P should be larger than zero if E = 0 according to the definition of E = P − T 0 σ, which shrinks the range of ρ.  In Figures 2 and 4, it is obvious that the larger x and y are, the smaller the maximum values of P and E are. That is, the faster piston speeds in processes 3 → 4 and 6 → 1 are, the larger the maximum values of P and E are. Further, as x and y increase, the optimal ρ opt P corresponding to the maximum P and optimal ρ opt E corresponding to the maximum E will decrease, but the variation range of the optimal ρ opt P with x is larger than that of the optimal ρ opt P with y, the variation range of the optimal ρ opt E with y is larger than that of the optimal ρ opt E with x. The effects of y on P and E are more significant than those of x, which means the piston speed in constant pressure heat rejection process has more marked impact on P and E than in constant pressure heat addition process. It can be concluded from Figure 3 that x and y have no effect on η. The maximum η is equal to 0.622 whatever values x and y take. The reason is that W and Q H are uncorrelated with cycle time τ, leading to η be uncorrelated with x and y according to the definition of η = W/Q H . Moreover, as x and y increase, the thermal efficiency (η P ) at the maximum P will increase.  In Figures 2 and 4, it is obvious that the larger x and y are, the smaller the maximum values of P and E are. That is, the faster piston speeds in processes → 3 4 and → 6 1 are, the larger the maximum values of P and E are. Further, as x and y increase, the optimal ρ P opt corresponding to the maximum P and optimal ρ E opt corresponding to the maximum E will decrease, but the variation range of the optimal ρ P opt with x is larger than that of the optimal ρ P opt with y , the variation range of the optimal ρ E opt with y is larger than that of the optimal ρ E opt with

Effects of x and y on P, η and E
x . The effects of y on P and E are more significant than those of x , which means the piston speed in constant pressure heat rejection process has more marked impact on P and E than in constant pressure heat addition process. It can be concluded from Figure 3 that x and y have no effect on η . The maximum η is equal to 0.622 whatever values x and y take. The reason is that W and H Q are uncorrelated with cycle time τ , leading to η be uncorrelated with x and y according to the definition of η = / H W Q . Moreover, as x and y increase, the thermal efficiency ( η P ) at the maximum P will increase.

Effects of a and b on P , η and E
Figures 5-7 show P versus ρ , P versus η , and E versus ρ characteristics when a and b take different values, which are similar to curves of P versus ρ , P versus η , and E versus ρ characteristics under different x and y . In Figures 5 and 7, one can see that the smaller a and b are, the larger the maximum values of P and E are. That is, the shorter the times in processes increase, the optimal ρ P opt and optimal E opt ρ will decrease, but the variation range of the optimal P opt ρ with a is larger than that of the optimal P opt ρ with b , the variation range of the optimal E opt ρ with b is larger than that of the optimal E opt ρ with a . The effects of b on P and E are more significant than those of a , which means the piston speed in constant volume heat rejection process has more marked impact on P and E than that in constant volume heat addition process. It can be concluded from Figure 6 that a and b have no effect on η . The maximum η is equal to 0.622 whatever values a and b take. The reason is as same as that of η being uncorrelated with x and y . Moreover, as a and b increase, the thermal efficiency ( P η ) at the maximum P will increase

Effects of a and b on P, η and E
Figures 5-7 show P versus ρ, P versus η, and E versus ρ characteristics when a and b take different values, which are similar to curves of P versus ρ, P versus η, and E versus ρ characteristics under different x and y. In Figures 5 and 7, one can see that the smaller a and b are, the larger the maximum values of P and E are. That is, the shorter the times in processes 2 → 3 and 5 → 6 are, the larger the maximum values of P and E are. Further, as a and b increase, the optimal ρ opt P and optimal ρ opt E will decrease, but the variation range of the optimal ρ opt P with a is larger than that of the optimal ρ opt P with b, the variation range of the optimal ρ opt E with b is larger than that of the optimal ρ opt E with a. The effects of b on P and E are more significant than those of a, which means the piston speed in constant volume heat rejection process has more marked impact on P and E than that in constant volume heat addition process. It can be concluded from Figure 6 that a and b have no effect on η. The maximum η is equal to 0.622 whatever values a and b take. The reason is as same as that of η being uncorrelated with x and y. Moreover, as a and b increase, the thermal efficiency (η P ) at the maximum P will increase slightly. b are, the larger the maximum values of P and E are. That is, the shorter the times in processes → 2 3 and → 5 6 are, the larger the maximum values of P and E are. Further, as a and b increase, the optimal ρ P opt and optimal E opt ρ will decrease, but the variation range of the optimal P opt ρ with a is larger than that of the optimal P opt ρ with b , the variation range of the optimal E opt ρ with b is larger than that of the optimal E opt ρ with a . The effects of b on P and E are more significant than those of a , which means the piston speed in constant volume heat rejection process has more marked impact on P and E than that in constant volume heat addition process. It can be concluded from Figure 6 that a and b have no effect on η . The maximum η is equal to 0.622 whatever values a and b take. The reason is as same as that of η being uncorrelated with x and y . Moreover, as a and b increase, the thermal efficiency ( P η ) at the maximum P will increase slightly.    Figure 8 gives the curves between P and ρ , between η and ρ , as well as between E and ρ . When P , η and E are chosen as optimization objective functions, the DMC engines will be in different conditions. According to Figure 8, the following can be concluded.

Performance Comparison
(1) When P is chosen as optimization objective function, the maximum P is max 0.0035 P = , η   Figure 8 gives the curves between P and ρ , between η and ρ , as well as between E and ρ . When P , η and E are chosen as optimization objective functions, the DMC engines will be in different conditions. According to Figure 8, the following can be concluded.

Performance Comparison
(1) When P is chosen as optimization objective function, the maximum P is max 0.0035 P = , η  Figure 8 gives the curves between P and ρ, between η and ρ, as well as between E and ρ. When P,

Performance Comparison
η and E are chosen as optimization objective functions, the DMC engines will be in different conditions. According to Figure 8, the following can be concluded.
(1) When P is chosen as optimization objective function, the maximum P is P max = 0.0035, η corresponding to the maximum P is η P = 0.306. However, the maximum η is η max = 0.622, η P /η max = 0.492, so choosing P as optimization objective function sacrifices most of η. (2) When η is chosen as optimization objective function, P corresponding to the maximum η is P η = 0, P η /P max = 0. Although η can reach the maximum, P is zero when optimizing η. Thus, choosing η as optimization objective function is unreasonable. (3) When E is chosen as optimization objective function, the maximum E is E max = 0.0017, P corresponding to the maximum E is P E = 0.0026, P E /P max = 0.743, η corresponding to the maximum E is η E = 0.470, η E /η max = 0.756. Thus, choosing E as optimization objective function can improve η compared with choosing P as optimization objective function and can also improve P compared with choosing η as optimization objective function. (4) There are P η < P E < P max and η P < η E < η max . When E is chosen as optimization objective function, P and η may be smaller than their maxima, but they can reach relatively large values at the same time. Hence, optimizing E is the best compromise optimization between optimizing P and optimizing η. . When E is chosen as optimization objective function, P and η may be smaller than their maxima, but they can reach relatively large values at the same time. Hence, optimizing E is the best compromise optimization between optimizing P and optimizing η .

Corollary 75-25
In thermodynamic (and thermoeconomic) optimization of some endoreversible models of heat engines, there is a reduction of the total entropy production (Corollary 75-25 [98,99]) when the ecological function is maximized in comparison with that obtained under maximum power output. Corollary 75-25 means that the maximization of the ecological function leads to an engine performance with a power output around 75% of the maximum power output and an entropy production rate around 25% of the entropy production rate at maximum power condition [98,99].
The curves of power output, ecological function and entropy generation rate versus cut-off ratio for the endoreversible Dual-Miller cycle are depicted in Figure 9. The values of maximum power output, power output corresponding to maximum ecological function, entropy generation rate corresponding to maximum power output and entropy generation rate corresponding to maximum ecological function are listed in Table 1. They show that the property of ecological function is also concordant with Corollary 75-25 for the endoreversible Dual-Miller cycle with finite speed of the piston.

Corollary 75-25
In thermodynamic (and thermoeconomic) optimization of some endoreversible models of heat engines, there is a reduction of the total entropy production (Corollary 75-25 [98,99]) when the ecological function is maximized in comparison with that obtained under maximum power output. Corollary 75-25 means that the maximization of the ecological function leads to an engine performance with a power output around 75% of the maximum power output and an entropy production rate around 25% of the entropy production rate at maximum power condition [98,99].
The curves of power output, ecological function and entropy generation rate versus cut-off ratio for the endoreversible Dual-Miller cycle are depicted in Figure 9. The values of maximum power output, power output corresponding to maximum ecological function, entropy generation rate corresponding to maximum power output and entropy generation rate corresponding to maximum ecological function are listed in Table 1. They show that the property of ecological function is also concordant with Corollary 75-25 for the endoreversible Dual-Miller cycle with finite speed of the piston.
performance with a power output around 75% of the maximum power output and an entropy production rate around 25% of the entropy production rate at maximum power condition [98,99].
The curves of power output, ecological function and entropy generation rate versus cut-off ratio for the endoreversible Dual-Miller cycle are depicted in Figure 9. The values of maximum power output, power output corresponding to maximum ecological function, entropy generation rate corresponding to maximum power output and entropy generation rate corresponding to maximum ecological function are listed in Table 1. They show that the property of ecological function is also concordant with Corollary 75-25 for the endoreversible Dual-Miller cycle with finite speed of the piston.

Conclusions
The performances of the non-dimensional power output, thermal efficiency and non-dimensional ecological function of an endoreversible DMC with finite rate of HT are analyzed and optimized based on finite speed of the piston. Performance characteristics are discussed and analyzed when DMC are simplified to other cycles. The effects of ρ and piston speeds on performance of the cycle are examined via numerical examples. The results show that, the faster the piston speeds are, the larger the maximum values of P and E are. The optimal cut-off ratio ρ opt will increase if piston speeds increase in heat addition processes and heat rejection processes. The effects of time in constant volume heat rejection process on P and E are more marked than those of time in constant volume heat addition process, the effects of time in constant pressure heat rejection process on P and E are also more marked than those of time in constant pressure heat addition process. Choosing ecological function as optimization objective function is more significant compared with choosing power output and thermal efficiency as optimization objective functions.
The results obtained herein show that there are three aspects to improve the performance when designing the Dual-Miller cycle engines. Firstly, improving piston speed can increase the power output. Secondly, excessive times in heat addition and heat rejection processes have negative impacts on performance of the cycle engines, thus the times in heat rejection processes should be decreased as much as possible. Lastly, taking ecological function as a design criterion can improve comprehensive performance (power output and thermal efficiency) of the cycle engines.
The cut-off ratio is an important design parameter for Dual-Miller cycle heat engines; it can determine the running forms of the engines. For example, the heat engine can run with maximum power output, maximum thermal efficiency and maximum ecological function conditions. Thus, optimizing the cut-off ratio is necessary, and optimal cut-off ratio is also important to design heat engines with different conditions.
The obtained results herein are based on the assumptions that the working fluid is an ideal gas and its specific heat is constant. The specific heat of the working fluid will change with its temperature in actual heat engines. The variable specific heat characteristic of the working fluid will be considered in the next studies.
Acknowledgments: This paper is supported by The National Natural Science Foundation of China (Project No. 51576207). The authors wish to thank the reviewers for their careful, unbiased and constructive suggestions, which led to this revised manuscript.
Author Contributions: Zhixiang Wu, Lingen Chen and Huijun Feng collectively finished the manuscript. All authors have read and approved the final manuscript.

Conflicts of Interest:
The authors declare no conflict of interest.