## 5 Experimental and Simulation Results Comparison  
A comparative analysis of the numerical and experimental results is presented in this section. Table 4 gives the strain and stress values obtained using the finite element method and experimental testing. The values are given for the force that equals 150% of \(F_{\rm Nmax}\) for the most critical moment of loading. In both numerical and experimental analyses, the highest strain occurs at the site of strain gauge 1, i.e., at the strain von Mises node (1377). Figure 11 shows comparative strain diagrams of strain gauge 1 (MT1) and the corresponding strain von Mises node (1377) for the most unfavorable load when the force \(F_{\rm N}\) reaches 150%. \begin{table}
\begin{tabular}{l c c c c c c c c c} \hline \hline Single-tooth meshing—Load 150\% & & & & & & & & & \\ \hline  & MT1 & MT2 & MT3 & MT4 & MT5 & MT6 & MT7 & MT8 & MT9 & MT10 \\ \hline \(\epsilon\)—ex., \(\mu\)m m\({}^{-1}\) & 473.75 & 390.26 & 333.91 & 218.09 & 106.51 & 297.37 & 300.36 & 300.63 & 280.83 & 305.38 \\ \hline \(\sigma\)—ex., MPa & 98.07 & 80.78 & 69.12 & 45.14 & 22.05 & 61.56 & 62.18 & 62.23 & 58.13 & 63.21 \\ \hline \(\epsilon\)—num.,\(\mu\)m m\({}^{-1}\) & 561.52 & 526.12 & 491.68 & 352.50 & 350.36 & 193.95 & 328.17 & 459.80 & 455.71 & 420.51 \\ \hline \(\sigma\)—num., MPa & 116.24 & 108.91 & 101.78 & 72.97 & 72.52 & 40.15 & 67.93 & 95.18 & 94.33 & 87.04 \\ \hline Double-tooth meshing—Load 150\% & & & & & & & & & \\ \hline  & MT1 & MT2 & MT3 & MT4 & MT5 & MT6 & MT7 & MT8 & MT9 & MT10 \\ \hline \(\epsilon\)—ex., \(\mu\)m m\({}^{-1}\) & 276.69 & 230.16 & 196.74 & 128.87 & 63.27 & 174.69 & 175.92 & 174.99 & 162.58 & 176.74 \\ \hline \(\sigma\)—ex., MPa & 57.28 & 47.64 & 40.73 & 26.68 & 13.10 & 36.16 & 36.42 & 36.22 & 33.65 & 36.59 \\ \hline \(\epsilon\)—num.,\(\mu\)m m\({}^{-1}\) & 277.21 & 259.73 & 242.73 & 174.02 & 172.96 & 95.75 & 162.01 & 226.99 & 224.97 & 207.59 \\ \hline \(\sigma\)—num., MPa & 57.38 & 53.76 & 50.25 & 36.02 & 35.80 & 19.82 & 33.54 & 46.99 & 46.57 & 42.97 \\ \hline Triple-tooth meshing—Load 150\% & & & & & & & & & \\ \hline  & MT1 & MT2 & MT3 & MT4 & MT5 & MT6 & MT7 & MT8 & MT9 & MT10 \\ \hline \(\epsilon\)—ex., \(\mu\)m m\({}^{-1}\) & 247.28 & 206.24 & 176.15 & 114.69 & 56.69 & 156.37 & 156.53 & 156.46 & 145.70 & 157.98 \\ \hline \(\sigma\)—ex., MPa & 51.19 & 42.69 & 36.46 & 23.74 & 11.73 & 32.37 & 32.40 & 32.39 & 30.16 & 32.70 \\ \hline \(\epsilon\)—num.,\(\mu\)m m\({}^{-1}\) & 249.47 & 233.74 & 218.45 & 156.61 & 155.66 & 86.17 & 145.80 & 204.28 & 202.47 & 186.82 \\ \hline \(\sigma\)—num., MPa & 51.64 & 48.39 & 45.22 & 32.42 & 32.22 & 17.84 & 30.18 & 42.29 & 41.91 & 38.67 \\ \hline \end{tabular}
\end{table} 
Table 4: Comparative results obtained using the finite element method and experimental testing. Figure 11: A comparative diagram of the numerical and experimental results obtained at site MT1 (node 1377) at the load of 150% of \(F_{\mathrm{N}}\) for (**a**) single–tooth meshing; (**b**) double–tooth meshing, and (**c**) triple–tooth meshing. The stresses that occur in the case of the single-tooth meshing are almost twice as high as that of the double-tooth or triple-tooth meshing of the cycloid disc and the ring gear. This is found in both numerical and experimental analyses. The difference in stresses between the double-tooth and the triple-tooth meshing is much smaller than between the single-tooth and the double-tooth meshing. A correlation analysis was conducted for the presented diagrams. The single tooth meshing results correlates 99.6% between the experimental and numerical results. The double-tooth and triple-tooth meshing results correlate 99.7% and 92.9% between the experimental and numerical results. The biggest deviation in correlation was the triple tooth meshing case because of the multiple meshing contacts and harder input force prediction. The correlation analyses show that the simulation setup follows the experimental procedure in more than acceptable boundaries.