A simple analytical model describing instable squeaking noise has been proposed, as shown in Figure 4(a) and Equation (8) (Eaton, 1975). The Figure of motion for mass M is given by,where X is the displacement of the mass (m) at time (t); ν is the drive velocity; c is the damping coefficient of dX/dt; k is the spring stiffness constant; F is the frictional resistance. The solution to this differential equation depends on the damping ratio ζ, where λ is the gradient of the friction versus speed curve (i.e., Stribeck curve), as shown in Figure 4(b). Equation (9) is summarized in the following section, and it gives a comprehensive explanation of the reasons for the generation of squeaks as well as the methods to control them (Reddyhoff et al., 2015). If ζ = 0, a marginally stable constant amplitude is considered; if 0 < ζ < 1, a stable amplitude with underdamped decaying oscillation is considered; if ζ ≥ 1, a stable amplitude with overdamped and non-oscillatory vibration is considered. To control the damping ratio, the value of damping coefficient (c) should be increased, and the value of the λ, i.e., – dμ/dν should be negative. To be precise, the TPV material should be developed to ensure a high degree of damping (loss factor), and the friction coefficient of surface should be changed from boundary friction to viscous friction, which is proportional to speed. Similarly, the compression set of the TPV material should have a low value to improve the wind noise insulation