## 7 Results
The associated loss analysis for D1 and D2 with respect to the reference is shown in Figure 16.2 Due to the higher temperature when the exhaust valve opens, D1 has higher exhaust losses than D2, which has higher exhaust losses than the reference. Because of the lower pressure, D1 and D2 have lower wall heat losses than the reference. D1 has the lowest peak pressure. Therefore, the decrease of the wall heat losses for D1 is higher than for D2. Figure 16.3 Energy losses for trajectory D1 and D2 with respect to REF. Figure 16.4 Comparison of trajectories REF, D1 and D2 related to the energy conversion of the electrical machine: volume change power, copper power losses, friction power losses and electric power depending on time. **Author Contributions:** Conceptualization, R.T. and A.G.; methodology, K.K. ; software, R.T. and A.G.; validation, R.T. and A.G.; formal analysis, K.K. ; investigation, R.T., A.G. and K.K. ; resources, A.G. and S.B. ; data curation, R.T. and A.G.; writing--original draft preparation, R.T., K.K. and A.G.; writing--review and editing, S.B., R.L. and H.R. ; visualization, R.T. and A.G.; supervision, H.R. and R.L. ; project administration, R.T. and A.G.; funding acquisition, R.T. All authors have read and agreed to the published version of the manuscript. **Funding:** This research received no external funding. **Institutional Review Board Statement:** Not applicable. **Informed Consent Statement:** Not applicable. **Data Availability Statement:** The data presented in this study are available on request from the corresponding author. The authors would like to know who re-uses their research materials and research data, which is why they would only share them on personal request. **Conflicts of Interest:** The authors declare no conflict of interest. **Nomenclature and Abbreviations** \begin{tabular}{l l l l} LHV & Lower heat value & \(E_{i}\) & Energy [J] \\ HTC & Heat transfer coefficient & \(m_{i}\) & Mass [kg] \\ PC & Personal computer & \(\eta_{i}\) & Efficiency [-] \\ PMSM & Permanent magnet excited & \(A_{i}\) & Area [\(m^{2}\)] \\ IMF & Indicated mean effective pressure & \(T\) & Temperature [K] \\ SI-Turb & Spark-Ignition Turbulent Flame & \(T_{in}\) & Inlet temperature [K] \\ TDCF & Top dead center firing & & \\ REF & Reference case & \(T_{out}\) & Outlet temperature [K] \\ A1 & Low TDC shift & \(t\) & Time [s] \\ A2 & High TDC shift & \(\alpha\) & Heat transfer coefficient [W/(m\({}^{2}\) K)] \\ B1 & Early piston acceleration & \(c_{p}\) & Mean specific heat capacity [J/(kg K)] \\ B2 & Late piston acceleration & \(P\) & Power [W] \\ C1 & Low stroke amplitude change & \(v\) & Velocity [m/s] \\ C2 & High stroke amplitude change & \(F\) & Force [N] \\ D1 & Combination of early piston & \(\mu\) & Friction coefficient [-] \\  & acceleration and low TDC shift & & \\ D2 & Combination of early piston & \(p\) & Cylinder pressure [Pa] \\  & acceleration and high TDC shift & \(i_{i}\) & Current [A] \\ \(T_{i}\) & Duration of the cycle [s] & \(\omega\) & Virtual angular velocity \\ \(\Delta T_{i}\) & Relative duration change [-] & \(\varphi\) & Virtual angle \\ \(k_{F}\) & Force constant [N/ A] & \(f\) & Frequency [Hz] \\ \(R\) & Ohmic resistance [\(\Omega\)] & \(B\) & Magnetic flux density [T] \\ \(u_{i}\) & Voltage [V] & \(\phi\) & Equivalence ratio [-] \\ \(\rho_{u}\) & Unburned density [kg/m\({}^{3}\)] & \(a\) & Acceleration [m/s\({}^{2}\)] \\ \(S_{T}\) & Turbulent flame speed [m/s] & \(S_{L}\) & Laminar flame speed [m/s] \\ \(C_{TFS}\) & Turbulent flame speed multiplier & \(C_{FKG}\) & Flame kernel growth multiplier [-] \\ \(R_{f}\) & Flame radius [m] & \(L_{i}\) & Integral length scale [-] \\ \(B_{m}\) & Maximum laminar speed [m/s] & \(B_{\phi}\) & Laminar speed roll-off value [m/s] \\ \(\phi_{m}\) & Equivalence ratio at maximum & \(T_{u}\) & Unburned gas temperature [K] \\ \(a_{e}\) & Temperature exponent [-] & \(\beta\) & Pressure exponent [-] \\ \(w\) & Average cylinder gas velocity & \(K_{i}\) & Model constant [-] \\ \end{tabular}