Theoretical Model
The experiment exhibits clear nonlinear behavior due to the conical spring, the analytical formulation used below retains the linear stiffness terms. Figs. 13 and 16 clearly show that the experimental mass-conical spring system exhibits nonlinear behavior.
Because the conical springs behave differently in tension and compression, the motion over each vibration cycle can be separated into tension and compression segments. To model this, we use the following nonlinear formulation in which the restoring force includes higher-order displacement terms arising from the graded coil geometry. Thus, the governing equations of motion are written as
(52)\[\begin{equation}
\begin{aligned}
m_{1}^{\mathrm{eff}}\,\ddot{u}_1 &= k_1\!\left(F e^{i\omega_d t}-u_1\right)
- k_2\left(u_1-u_2\right)
- k_2^{\prime}\left(u_1 - u_2\right)_{+}^2
- k_2^{\prime\prime}\left(u_1 - u_2\right)_{+}^3
- \eta\,\dot{u}_1, \\
m_{2}^{\mathrm{eff}}\,\ddot{u}_2 &= - k_2\left(u_2-u_1\right)
+ k_2^{\prime}\left(u_1 - u_2\right)_{+}^2
+ k_2^{\prime\prime}\left(u_1 - u_2\right)_{+}^3
- \eta\,\dot{u}_2.
\end{aligned}
\end{equation}\]
Here, \(m_{1}^{\mathrm{eff}}\) and \(m_{2}^{\mathrm{eff}}\) include the distributed mass of the springs based on \(m^{\mathrm{eff}} = m + m_k/3\) [Rao and Yap, 1995]. Because mass 1 connects to both springs, we write \(m_{1}^{\mathrm{eff}} = m + m_{k,1}/3 +m_{k,2}/3\), whereas for mass 2, \(m_{2}^{\mathrm{eff}} = m + m_{k,2}/3\). The variables \(u_1\) and \(u_2\) represent the displacements from equilibrium, \(F\) and \(\omega_d\) denote the drive amplitude and frequency, and \(\eta\) represents viscous damping. \(k_1\) is the stiffness of the linear spring connecting mass 1 to the shaker, and \(k_2\) is the nominal stiffness of the conical spring. The terms \(k_2^{\prime}\) and \(k_2^{\prime\prime}\) represent the quadratic and cubic nonlinear stiffness components. The Heaviside function \((\cdot)_{+}\) ensures that the nonlinear terms are activated only under compression.
Given the nonlinear nature of the mass–conical spring model, we employ a regular perturbation technique to obtain an approximate solution. Introducing a small, dimensionless parameter \(\epsilon\) (\(\epsilon \ll 1\)), Eq. (5) can be rewritten as
The nonlinear model can be rewritten by introducing a small dimensionless parameter \(\epsilon\) (\(\epsilon \ll 1\)) such that the nonlinear stiffness contributions enter at \(\mathcal{O}(\epsilon)\). Thus, the equations of motion take the form
(53)\[\begin{equation}
\begin{aligned}
m_1^{\mathrm{eff}}\,\ddot{u}_1 &=
k_1\!\left( F e^{i\omega_d t} - u_1 \right)
- k_2 \left( u_1 - u_2 \right)
- \epsilon k_2^{\prime}\left( u_1 - u_2 \right)^2
- \epsilon k_2^{\prime\prime}\left( u_1 - u_2 \right)^3
- \eta\,\dot{u}_1, \\
m_2^{\mathrm{eff}}\,\ddot{u}_2 &=
- k_2 \left( u_2 - u_1 \right)
+ \epsilon k_2^{\prime}\left( u_1 - u_2 \right)^2
+ \epsilon k_2^{\prime\prime}\left( u_1 - u_2 \right)^3
- \eta\,\dot{u}_2.
\end{aligned}
\end{equation}\]
As the springs behave differently when it is tension or compression, we can divide the equation of motion into two different sections. In each vibrating period, there are compression and tension regions. Conical spring behaves nonlinearly when it is in compression. \(k_2^{'}\) and \(k_2^{''}\) are the quadratic and cubic nonlinear stiffness terms.
Relative Motion in Compression and Tension:
(54)\[\begin{equation}
\Delta(t) = u_0(t) - v_0(t) = (A_0 - B_0)e^{i\omega_d t}
\end{equation}\]
Here \(A_0\) and \(B_0\) are the amplitude response of the masses. This is the complex quantity with time varying real and imaginary parts, but the physical displacement is the real part:
(55)\[\begin{equation}
\mathrm{Re}[\Delta(t)] = \mathrm{Re}[(A_0 - B_0)e^{i\omega_d t}]
\end{equation}\]
Spring is in:
\[\begin{equation*}
\text{Tension when }\mathrm{Re}[(A_0 - B_0)e^{i\omega_d t}] > 0
\end{equation*}\]
\[\begin{equation*}
\text{Compression when }\mathrm{Re}[(A_0 - B_0)e^{i\omega_d t}] < 0
\end{equation*}\]
Let,
(56)\[\begin{equation}
C = A_0 - B_0 = |C|e^{i\phi} \Rightarrow \mathrm{Re}[\Delta(t)] = |C|\cos(\omega_d t + \phi)
\end{equation}\]
Since \(\cos\) is always symmetric and oscillatory, it always spans both positive and negative values, unless \(|C| = 0\), i.e., \(A_0 = B_0\). We want:
\[\begin{equation*}
\mathrm{Re}[(A_0 - B_0)e^{i\omega_d t}] \ge 0 \text{ for all } t.
\end{equation*}\]
That’s only possible if:
\[\begin{equation*}
\mathrm{Im}[A_0 - B_0] = 0 \quad \text{and} \quad \mathrm{Re}[A_0 - B_0] > 0
\end{equation*}\]
And the exponential has no time-varying sign. So, the real part of the oscillation is constant and strictly positive. But this contradicts the nature of the harmonic forcing unless the two amplitudes are equal and real. So, in general: The spring is in compression during half the period and in tension during the other half, unless the phase and amplitude of \(A_0\) and \(B_0\) are tuned to suppress one side.
Let:
(57)\[\begin{equation}
\Delta(t) = (A_0 - B_0)e^{i\omega_d t}
\end{equation}\]
\[\begin{equation*}
\Rightarrow \mathrm{Re}[\Delta(t)] = \mathrm{Re}[C]\cos(\omega_d t) - \mathrm{Im}[C]\sin(\omega_d t)
\end{equation*}\]
So, define:
\[\begin{equation*}
\mathrm{Re}[\Delta(t)] = R\cos(\omega_d t + \phi), \quad R = |C|
\end{equation*}\]
Spring is in tension:
\[\begin{equation*}
\cos(\omega_d t + \phi) > 0 \Rightarrow \omega_d t + \phi \in \left(-\frac{\pi}{2}, \frac{\pi}{2}\right)
\end{equation*}\]
Spring is in compression:
\[\begin{equation*}
\cos(\omega_d t + \phi) < 0 \Rightarrow \omega_d t + \phi \in \left(\frac{\pi}{2}, \frac{3\pi}{2}\right)
\end{equation*}\]
Asymptotic Perturbation Solution of displacement:
(58)\[\begin{equation}
u_1 = u_{1,0} + \epsilon u_{1,1} + \epsilon^2 u_{1,2}, \qquad
u_2 = u_{2,0} + \epsilon u_{2,1} + \epsilon^2 u_{2,2}
\end{equation}\]
Applying the solution to Eq. (51). We get,
(59)\[\begin{equation}
\begin{aligned}
m_1^{\mathrm{eff}}(\ddot{u}_{1,0} + \epsilon \ddot{u}_{1,1} + \epsilon^2 \ddot{u}_{1,2}) &=
k_1(Fe^{i\omega_d t} - u_{1,0} - \epsilon u_{1,1} - \epsilon^2 u_{1,2}) \\
&\quad - k_2\!\left[(u_{1,0} - u_{2,0}) + \epsilon(u_{1,1} - u_{2,1}) +
\epsilon^2(u_{1,2} - u_{2,2})\right] \\
&\quad - \epsilon k_2^{\prime}\!\left[(u_{1,0} - u_{2,0}) + \epsilon(u_{1,1} - u_{2,1}) +
\epsilon^2(u_{1,2} - u_{2,2})\right]^2 \\
&\quad - \epsilon^2 k_2^{\prime\prime}\!\left[(u_{1,0} - u_{2,0}) +
\epsilon(u_{1,1} - u_{2,1}) + \epsilon^2(u_{1,2} - u_{2,2})\right]^3 \\
&\quad - \eta(\dot{u}_{1,0} + \epsilon \dot{u}_{1,1} + \epsilon^2 \dot{u}_{1,2})
\\
m_2^{\mathrm{eff}}(\ddot{u}_{2,0} + \epsilon \ddot{u}_{2,1} + \epsilon^2 \ddot{u}_{2,2}) &=
- k_2\!\left[(u_{2,0} - u_{1,0}) + \epsilon(u_{2,1} - u_{1,1}) +
\epsilon^2(u_{2,2} - u_{1,2})\right] \\
&\quad - \epsilon k_2^{\prime}\!\left[(u_{2,0} - u_{1,0}) + \epsilon(u_{2,1} - u_{1,1}) +
\epsilon^2(u_{2,2} - u_{1,2})\right]^2 \\
&\quad - \epsilon^2 k_2^{\prime\prime}\!\left[(u_{2,0} - u_{1,0}) +
\epsilon(u_{2,1} - u_{1,1}) + \epsilon^2(u_{2,2} - u_{1,2})\right]^3 \\
&\quad - \eta(\dot{u}_{2,0} + \epsilon \dot{u}_{2,1} + \epsilon^2 \dot{u}_{2,2})
\end{aligned}
\end{equation}\]
Let’s consider:
\[\begin{equation*}
\Delta_0 = u_{1,0} - u_{2,0},\quad
\Delta_1 = u_{1,1} - u_{2,1},\quad
\Delta_2 = u_{1,2} - u_{2,2}
\end{equation*}\]
Ignoring the higher power terms of \(\epsilon\), for mass 1, we get,
(60)\[\begin{equation}
\begin{aligned}
m_1^{\mathrm{eff}}(\ddot{u}_{1,0} + \epsilon \ddot{u}_{1,1} + \epsilon^2 \ddot{u}_{1,2}) &=
k_1(Fe^{i\omega_d t} - u_{1,0} - \epsilon u_{1,1} - \epsilon^2 u_{1,2}) \\
&\quad - k_2(\Delta_0 + \epsilon\Delta_1 + \epsilon^2\Delta_2) \\
&\quad - \epsilon k_2^{\prime}(\Delta_0 + \epsilon\Delta_1)^2
- \epsilon^2 k_2^{\prime\prime}(\Delta_0)^3 \\
&\quad - \eta(\dot{u}_{1,0} + \epsilon \dot{u}_{1,1} + \epsilon^2 \dot{u}_{1,2})
\\
m_1^{\mathrm{eff}}(\ddot{u}_{1,0} + \epsilon \ddot{u}_{1,1} + \epsilon^2 \ddot{u}_{1,2}) &=
[k_1(Fe^{i\omega_d t} - u_{1,0}) - k_2\Delta_0 - \eta \dot{u}_{1,0}] \\
&\quad + \epsilon[-k_1 u_{1,1} - k_2\Delta_1 - k_2^{\prime}\Delta_0^2 - \eta\dot{u}_{1,1}] \\
&\quad + \epsilon^2[-k_1 u_{1,2} - k_2\Delta_2 - 2k_2^{\prime}(\Delta_0 \Delta_1)
- k_2^{\prime\prime}(\Delta_0^3) - \eta\dot{u}_{1,2}]
\end{aligned}
\end{equation}\]
Let’s consider:
\[\begin{equation*}
\Delta_0 = u_{2,0} - u_{1,0},\quad
\Delta_1 = u_{2,1} - u_{1,1},\quad
\Delta_2 = u_{2,2} - u_{1,2}
\end{equation*}\]
For Mass 2, we get,
(61)\[\begin{equation}
\begin{aligned}
m_2^{\mathrm{eff}}(\ddot{u}_{2,0} + \epsilon \ddot{u}_{2,1} + \epsilon^2 \ddot{u}_{2,2}) &=
[-k_2(\Delta_0) - \eta\dot{u}_{2,0}] \\
&\quad + \epsilon[-k_2\Delta_1 - k_2^{\prime}\Delta_0^2 - \eta\dot{u}_{2,1}] \\
&\quad + \epsilon^2[-k_2\Delta_2 - 2k_2^{\prime}(\Delta_0 \Delta_2)
- k_2^{\prime\prime}\Delta_0^3 - \eta\dot{u}_{2,2}]
\end{aligned}
\end{equation}\]
The Equation of Motion for each order of displacement is,
\[\begin{flalign*}
\epsilon^0:\quad
m_1^{\mathrm{eff}} \ddot{u}_{1,0} &= k_1\left(Fe^{i\omega_d t} - u_{1,0}\right) - k_2\left(u_{1,0} - u_{2,0}\right) - \eta \dot{u}_{1,0}
&& \\
m_2^{\mathrm{eff}} \ddot{u}_{2,0} &= -k_2\left(u_{2,0} - u_{1,0}\right) - \eta \dot{u}_{2,0} &&
\end{flalign*}\]
\[\begin{flalign*}
\epsilon^1:\quad
m_1^{\mathrm{eff}} \ddot{u}_{1,1} &= -k_1 u_{1,1} - k_2\left(u_{2,1} - u_{1,1}\right) - k_2^{\prime}\left(u_{1,0} - u_{2,0}\right)^2 - \eta \dot{u}_{1,1}
&& \\
m_2^{\mathrm{eff}} \ddot{u}_{2,1} &= -k_2\left(u_{2,1} - u_{1,1}\right) - k_2^{\prime}\left(u_{2,0} - u_{1,0}\right)^2 - \eta \dot{u}_{2,1} &&
\end{flalign*}\]
Let’s consider the solution of the displacement term as,
\[\begin{equation*}
\dot{u}_{1,n-1} = i\omega_d C_{1,n-1} e^{i\omega_d t},\qquad
\dot{u}_{2,n-1} = i\omega_d C_{2,n-1} e^{i\omega_d t}
\end{equation*}\]
\[\begin{equation*}
\ddot{u}_{1,n-1} = -\omega_d^2 C_{1,n-1} e^{i\omega_d t},\qquad
\ddot{u}_{2,n-1} = -\omega_d^2 C_{2,n-1} e^{i\omega_d t}
\end{equation*}\]
We apply this in the equation, then we get,
\[\begin{equation*}
-m_1^{\mathrm{eff}} \omega_d^2 C_{1,0} e^{i\omega_d t} =
k_1\left(Fe^{i\omega_d t} - C_{1,0} e^{i\omega_d t}\right)
- k_2\left(C_{1,0} e^{i\omega_d t} - C_{2,0} e^{i\omega_d t}\right)
- i\eta\omega_d C_{1,0} e^{i\omega_d t}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow -m_1^{\mathrm{eff}} \omega_d^2 C_{1,0} =
k_1(F - C_{1,0}) - k_2(C_{1,0} - C_{2,0}) - i\eta\omega_d C_{1,0}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow (-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i\eta\omega_d) C_{1,0}
- k_2 C_{2,0} = k_1 F
\end{equation*}\]
\[\begin{equation*}
-m_2^{\mathrm{eff}} \omega_d^2 C_{2,0} e^{i\omega_d t} =
k_2\left(C_{1,0} e^{i\omega_d t} - C_{2,0} e^{i\omega_d t}\right)
- i\eta\omega_d C_{2,0} e^{i\omega_d t}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow -m_2^{\mathrm{eff}} \omega_d^2 C_{2,0} =
k_2(C_{1,0} - C_{2,0}) - i\eta\omega_d C_{2,0}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow -k_2 C_{1,0} + (-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i\eta\omega_d) C_{2,0} = 0
\end{equation*}\]
The amplitude of zeroth order displacement is,
\[\begin{equation*}
C_{1,0} = \frac{k_1 F(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i\eta\omega_d)}
{(-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i\eta\omega_d)(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\end{equation*}\]
\[\begin{equation*}
C_{2,0} = \frac{k_1 k_2 F}
{(-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i\eta\omega_d)(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\end{equation*}\]
For the case of first order amplitude, we get,
\[\begin{equation*}
m_1^{\mathrm{eff}} \ddot{u}_{1,1} = -k_1 u_{1,1} - k_2(u_{2,1} - u_{1,1})
- k_2^{\prime}(u_{1,0} - u_{2,0})^2 - \eta \dot{u}_{1,1}
\end{equation*}\]
\[\begin{equation*}
m_2^{\mathrm{eff}} \ddot{u}_{2,1} = -k_2(u_{2,1} - u_{1,1})
- k_2^{\prime}(u_{2,0} - u_{1,0})^2 - \eta \dot{u}_{2,1}
\end{equation*}\]
Using substitution method and applying solution of \(u_1\) and \(u_2\), we get,
\[\begin{equation*}
-8m_1^{\mathrm{eff}} \omega_d^2 C_{1,1} e^{2i\omega_d t}
=
-k_1 (2C_{1,1} e^{2i\omega_d t})
-k_2 (2C_{1,1} e^{2i\omega_d t}-2C_{2,1} e^{2i\omega_d t})
-k_2^{\prime} (C_{1,0} e^{i\omega_d t}-C_{2,0} e^{i\omega_d t})^2
-4i\eta\omega_d C_{1,1} e^{2i\omega_d t}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow
-8m_1^{\mathrm{eff}} \omega_d^2 C_{1,1} e^{2i\omega_d t}
=
-k_1 (2C_{1,1}) e^{2i\omega_d t}
-2k_2 (C_{1,1}-C_{2,1}) e^{2i\omega_d t}
-k_2^{\prime} (C_{1,0}-C_{2,0})^2 e^{2i\omega_d t}
-4i\eta\omega_d C_{1,1} e^{2i\omega_d t}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow
-8m_1^{\mathrm{eff}} \omega_d^2 C_{1,1}
=
-2k_1 C_{1,1}
-2k_2(C_{1,1}-C_{2,1})
-k_2^{\prime}(C_{1,0}-C_{2,0})^2
-4i\eta\omega_d C_{1,1}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow
(-8m_1^{\mathrm{eff}} \omega_d^2+2k_1+2k_2+4i\eta\omega_d)\,C_{1,1}
-2k_2 C_{2,1}
=
k_2^{\prime}(C_{1,0}-C_{2,0})^2
\end{equation*}\]
And
\[\begin{equation*}
-8m_2^{\mathrm{eff}} \omega_d^2 C_{2,1} e^{2i\omega_d t}
=
-k_2(2C_{2,1} e^{2i\omega_d t}-2C_{1,1} e^{2i\omega_d t})
-k_2^{\prime}(C_{2,0} e^{i\omega_d t}-C_{1,0} e^{i\omega_d t})^2
-4i\eta\omega_d C_{2,1} e^{2i\omega_d t}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow
-8m_2^{\mathrm{eff}} \omega_d^2 C_{2,1} e^{2i\omega_d t}
=
-k_2(2C_{2,1}-2C_{1,1}) e^{2i\omega_d t}
-k_2^{\prime}(C_{2,0}-C_{1,0})^2 e^{2i\omega_d t}
-4i\eta\omega_d C_{2,1} e^{2i\omega_d t}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow
-8m_2^{\mathrm{eff}} \omega_d^2 C_{2,1}
=
2k_2(C_{1,1}-C_{2,1})
-k_2^{\prime}(C_{2,0}-C_{1,0})^2
-4i\eta\omega_d C_{2,1}
\end{equation*}\]
\[\begin{equation*}
\Rightarrow
-2k_2 C_{1,1}
+(-8m_2^{\mathrm{eff}} \omega_d^2+2k_2+4i\eta\omega_d)\,C_{2,1}
=
k_2^{\prime}(C_{1,0}-C_{2,0})^2
\end{equation*}\]
Using elimination method, we get,
\[\begin{equation*}
C_{1,1}
=
\frac{
k_2^{\prime}(C_{1,0}-C_{2,0})^2\left((-8m_2^{\mathrm{eff}} \omega_d^2+2k_2+4i\eta\omega_d)+2k_2\right)
}{
(-8m_1^{\mathrm{eff}} \omega_d^2+2k_1+2k_2+4i\eta\omega_d)(-8m_2^{\mathrm{eff}} \omega_d^2+2k_2+4i\eta\omega_d)-4k_2^2
}
\end{equation*}\]
\[\begin{equation*}
C_{2,1}
=
\frac{
k_2^{\prime}(C_{1,0}-C_{2,0})^2\left((-8m_1^{\mathrm{eff}} \omega_d^2+2k_1+2k_2+4i\eta\omega_d)+2k_2\right)
}{
(-8m_1^{\mathrm{eff}} \omega_d^2+2k_1+2k_2+4i\eta\omega_d)(-8m_2^{\mathrm{eff}} \omega_d^2+2k_2+4i\eta\omega_d)-4k_2^2
}
\end{equation*}\]
To elucidate the measured trends for Bit 1, we linearize the two-mass, two-spring dimer:
(62)\[\begin{equation}
\begin{aligned}
m_1^{\mathrm{eff}} \ddot{u}_1 &= k_1 (F e^{i\omega_d t} - u_1) - k_2 (u_1 - u_2) - \eta \dot{u}_1, \\
m_2^{\mathrm{eff}} \ddot{u}_2 &= k_2 (u_1 - u_2) - \eta \dot{u}_2.
\end{aligned}
\end{equation}\]
Here, \(m_1^{\mathrm{eff}}\) and \(m_2^{\mathrm{eff}}\) include the spring mass via \(m^{\mathrm{eff}} = m + m_k/3\) [Rao and Yap, 1995].
Because Mass 1 is connected to both springs, \(m_1^{\mathrm{eff}} = m + m_{k,1}/3 + m_{k,2}/3\), whereas for Mass 2, \(m_2^{\mathrm{eff}} = m + m_{k,2}/3\). \(u_1\) and \(u_2\) represent the displacements of the masses from equilibrium. \(F\) and \(\omega_d\) denote the driver amplitude and frequency, respectively, \(\eta\) represents viscous damping, \(k_1\) is the stiffness of the linear spring connecting the first mass to the driver, and \(k_2\) is the stiffness of the inter-mass conical spring.
Assuming harmonic motion \(u_1 = C_1 e^{i\omega_d t}\) and \(u_2 = C_2 e^{i\omega_d t}\) with complex amplitudes \(C_1\) and \(C_2\), substituting into Eq. (60) yields the algebraic system,
The linearized model for the mass-spring system is considered in Eq. (60), and the assumed harmonic ansatz for the displacement fields is
\[\begin{equation*}
u_1 = C_1 e^{i\omega_d t}, \qquad u_2 = C_2 e^{i\omega_d t}.
\end{equation*}\]
The first and second derivatives with respect to time are
\[\begin{equation*}
\dot{u}_1 = i\omega_d C_1 e^{i\omega_d t}, \quad \dot{u}_2 = i\omega_d C_2 e^{i\omega_d t}, \qquad
\ddot{u}_1 = -\omega_d^2 C_1 e^{i\omega_d t}, \quad \ddot{u}_2 = -\omega_d^2 C_2 e^{i\omega_d t}.
\end{equation*}\]
Substituting these expressions into Eq. (60) gives
(63)\[\begin{equation}
\begin{aligned}
&-m_1^{\mathrm{eff}}\omega_d^2 C_1 e^{i\omega_d t}
= k_1\!\left(F e^{i\omega_d t} - C_1 e^{i\omega_d t}\right)
- k_2\!\left(C_1 e^{i\omega_d t} - C_2 e^{i\omega_d t}\right)
- i\eta\omega_d C_1 e^{i\omega_d t}, \\[4pt]
\Rightarrow & \;
-m_1^{\mathrm{eff}}\omega_d^2 C_1 e^{i\omega_d t}
= \big[k_1(F - C_1) - k_2(C_1 - C_2) - i\eta\omega_d C_1\big] e^{i\omega_d t}, \\[4pt]
\Rightarrow \;
&-m_1^{\mathrm{eff}}\omega_d^2 C_1
= k_1(F - C_1) - k_2(C_1 - C_2) - i\eta\omega_d C_1, \\[4pt]
\Rightarrow & \;
(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)C_1 - k_2 C_2
= k_1 F.\\
&-m_2^{\mathrm{eff}}\omega_d^2 C_2 e^{i\omega_d t}
= k_2\!\left(C_1 e^{i\omega_d t} - C_2 e^{i\omega_d t}\right)
- i\eta\omega_d C_2 e^{i\omega_d t}, \\[4pt]
\Rightarrow & \;
-m_2^{\mathrm{eff}}\omega_d^2 C_2 e^{i\omega_d t}
= \big[k_2(C_1 - C_2) - i\eta\omega_d C_2\big] e^{i\omega_d t}, \\[4pt]
\Rightarrow & \;
-m_2^{\mathrm{eff}}\omega_d^2 C_2
= k_2(C_1 - C_2) - i\eta\omega_d C_2, \\[4pt]
\Rightarrow & \;
-k_2 C_1 + (-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d)C_2 = 0.
\end{aligned}
\end{equation}\]
Solving the above equations yields the amplitude responses of the two masses and the eigenmode frequencies.
(64)\[\begin{equation}
\begin{aligned}
C_1 &=
\frac{k_1 F \left(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i\eta\omega_d\right)}
{\left(-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i\eta\omega_d\right)
\left(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i\eta\omega_d\right) - k_2^2}, \\[4pt]
C_2 &=
\frac{k_1 k_2 F}
{\left(-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i\eta\omega_d\right)
\left(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i\eta\omega_d\right) - k_2^2}.
\end{aligned}
\end{equation}\]
The algebraic solution of the masses are written as the stiffness matrix as,
\[\begin{equation*}
\begin{bmatrix}
-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 & -k_2 \\[3pt]
-k_2 & -m_2^{\mathrm{eff}}\omega_d^2 + k_2
\end{bmatrix}
\end{equation*}\]
The eigenmode frequency is taken as the determinant of the stiffness matrix as \(\det(K)=0\). This can be implemented by taking the real part of the stiffness matrix as (the eigenmode of the system does not come from the damping provided in the system),
(65)\[\begin{equation}
\begin{aligned}
&\det
\begin{bmatrix}
-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 & -k_2 \\[3pt]
-k_2 & -m_2^{\mathrm{eff}}\omega_d^2 + k_2
\end{bmatrix}
= 0, \\[6pt]
&(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2) - k_2^2 = 0, \\[6pt]
&m_1^{\mathrm{eff}}m_2^{\mathrm{eff}}\omega_d^4
- m_1^{\mathrm{eff}}k_2\omega_d^2
- m_2^{\mathrm{eff}}(k_1 + k_2)\omega_d^2
- k_2^2 = 0, \\[6pt]
&m_1^{\mathrm{eff}}m_2^{\mathrm{eff}}\omega_d^4
- \omega_d^2\!\left(m_1^{\mathrm{eff}}k_2
+ m_2^{\mathrm{eff}}k_1
+ m_2^{\mathrm{eff}}k_2\right)
+ k_2(k_1 + k_2) - k_2^2 = 0, \\[6pt] \quad
&m_1^{\mathrm{eff}}m_2^{\mathrm{eff}}\omega_d^4
- \omega_d^2\!\left(m_1^{\mathrm{eff}}k_2
+ m_2^{\mathrm{eff}}k_1
+ m_2^{\mathrm{eff}}k_2\right)
+ k_1k_2 = 0.
\end{aligned}
\end{equation}\]
Using the quadratic formula \(x = \frac{B \pm \sqrt{B^2 - 4AC}}{2A}\), the two roots of Eq. (63) yield the eigenmode frequencies,
(66)\[\begin{equation}
\omega_{01,02}^2 =
\frac{
m_1^{\mathrm{eff}} k_2 + m_2^{\mathrm{eff}}(k_1 + k_2)
\pm
\sqrt{
\left[m_1^{\mathrm{eff}} k_2 + m_2^{\mathrm{eff}}(k_1 + k_2)\right]^2
- 4 m_1^{\mathrm{eff}} m_2^{\mathrm{eff}} k_1 k_2
}
}{2 m_1^{\mathrm{eff}} m_2^{\mathrm{eff}}}.
\end{equation}\]
Substituting these into the stiffness matrix provides the corresponding eigenvectors, or eigenstates, of the dimer:
\[\begin{equation*}
\ket{E_1} = \frac{1}{\sqrt{2}}\begin{pmatrix}1\\1\end{pmatrix}, \qquad
\ket{E_2} = \frac{1}{\sqrt{2}}\begin{pmatrix}1\\-1\end{pmatrix}.
\end{equation*}\]
Applying the amplitude responses \(C_1\) and \(C_2\) to this orthonormal basis, the vibrational state vector of the system is written as
(67)\[\begin{equation}
\mathbf{U}=
\begin{bmatrix}
C_1 \\
C_2
\end{bmatrix}
\equiv
\psi_0 \ket{E_1} + \psi_1 \ket{E_2}
= \frac{1}{\sqrt{2}}\,\psi_0
\begin{bmatrix}
1 \\ 1
\end{bmatrix}
+ \frac{1}{\sqrt{2}}\,\psi_1
\begin{bmatrix}
1 \\ -1
\end{bmatrix}=
\frac{1}{\sqrt{2}}
\begin{bmatrix}
\psi_0 + \psi_1 \\
\psi_0 - \psi_1
\end{bmatrix}.
\end{equation}\]
We can calculate the coefficients of the superposition of states from the orthonormal basis of the eigenstates (\(\psi_{(0,d)}\) and \(\psi_{(1,d)}\)) for the linearized model at the fundamental characteristics of the masses. This can be written as
(68)\[\begin{equation}
\begin{aligned}
\psi_0 = \frac{C_1 + C_2}{\sqrt{2}}
&= \frac{1}{\sqrt{2}}
\bigg[
\frac{k_1 F(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d)}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\\[4pt]
&\qquad
+ \frac{k_1 k_2 F}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\bigg]
\\[6pt]
&= \frac{1}{\sqrt{2}}
\bigg[
\frac{k_1 F(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d)
+ k_1 k_2 F}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\bigg]
\\[6pt]
&= \frac{1}{\sqrt{2}}
\bigg[
\frac{k_1 F(-m_2^{\mathrm{eff}}\omega_d^2 + 2k_2 + i\eta\omega_d)}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\bigg],
\\[12pt]
\psi_1 = \frac{C_1 - C_2}{\sqrt{2}}
&= \frac{1}{\sqrt{2}}
\bigg[
\frac{k_1 F(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d)}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\\[4pt]
&\qquad
- \frac{k_1 k_2 F}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\bigg]
\\[6pt]
&= \frac{1}{\sqrt{2}}
\bigg[
\frac{k_1 F(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d)
- k_1 k_2 F}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\bigg]
\\[6pt]
&= \frac{1}{\sqrt{2}}
\bigg[
\frac{k_1 F(-m_2^{\mathrm{eff}}\omega_d^2 + i\eta\omega_d)}
{(-m_1^{\mathrm{eff}}\omega_d^2 + k_1 + k_2 + i\eta\omega_d)
(-m_2^{\mathrm{eff}}\omega_d^2 + k_2 + i\eta\omega_d) - k_2^2}
\bigg].
\end{aligned}
\end{equation}\]
\(\psi_0\) and \(\psi_1\) represent the coefficients of the superposition of states at the driving frequency \((\omega_d)\).
The Bloch states angle can also be derived from the coefficients such that, \(\theta = 2\cos^{-1}(|\psi_0|).\)
From Eq. (66), let \(D = (-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i \eta \omega_d)(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i \eta \omega_d) - k_2^2.\)
So, the simplified equation becomes,
(69)\[\begin{equation}
\theta = 2 \cos^{-1}\!\left(
\left|\frac{1}{\sqrt{2}} \frac{k_1 F}{D} (-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2 + i \eta \omega_d)\right|
\right)
= 2 \cos^{-1}\!\left(
\left|\frac{k_1 F}{\sqrt{2} D}\right|
\sqrt{(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2)^2 + \eta^2 \omega_d^2}
\right).
\end{equation}\]
Similarly, the azimuthal angle of the Bloch states, \(\varphi = \arg(\psi_0) - \arg(\psi_1).\)
The simplified equation becomes,
(70)\[\begin{equation}
\arg(\psi_0) = \arg\!\left(
\frac{1}{\sqrt{2}}
\frac{k_1 F(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2 + i \eta \omega_d)}
{(-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i \eta \omega_d)
(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i \eta \omega_d) - k_2^2}
\right).
\end{equation}\]
Let the numerator \(N = k_1 F(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2 + i \eta \omega_d),\) This is the product of the real constants and a complex number. Fundamental property of the argument of a complex number suggests that, for any two complex numbers, the argument of their product is the sum of their arguments.
In that case,
\[\begin{equation*}
\arg(k_1 F(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2 + i \eta \omega_d))
= \arg(k_1 F) + \arg(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2 + i \eta \omega_d)
= \arg(k_1 F) + \tan^{-1}\!\left(\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2}\right).
\end{equation*}\]
And let the denominator \(D = (-m_1^{\mathrm{eff}} \omega_d^2 + k_1 + k_2 + i \eta \omega_d)(-m_2^{\mathrm{eff}} \omega_d^2 + k_2 + i \eta \omega_d) - k_2^2\).
So, the argument of the coefficient \(\psi_0\) is,
\[\begin{equation*}
\arg(\psi_0) = \arg(k_1 F)
+ \tan^{-1}\!\left(\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2}\right)
- \arg(D).
\end{equation*}\]
Similarly, for the case of \(\psi_1\), we get the phase of that term as,
\[\begin{equation*}
\arg(\psi_1) = \arg(k_1 F)
+ \tan^{-1}\left(\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2}\right)
- \arg(D).
\end{equation*}\]
The azimuthal angle \(\varphi\) for the linearized model can be written as,
(71)\[\begin{equation}
\begin{aligned}
\varphi &= \arg(\psi_0) - \arg(\psi_1) \\
&= \arg(k_1 F) + \tan^{-1}\!\left(\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2}\right) - \arg(D)
- \arg(k_1 F) - \tan^{-1}\!\left(\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2}\right) + \arg(D) \\
&= \tan^{-1}\!\left(\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2}\right)
- \tan^{-1}\!\left(\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2}\right) \\
&= \tan^{-1}\!\left(
\frac{
\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2}
- \frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2}
}{
\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2}
\frac{\eta \omega_d}{-m_2^{\mathrm{eff}} \omega_d^2}
}
\right) \\
&= \tan^{-1}\!\left(
\frac{
(-m \eta \omega_d^3 + m \eta \omega_d^3 - 2k_2 \eta \omega_d)
}{
(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2)(-m_2^{\mathrm{eff}} \omega_d^2)
}
\bigg/
\frac{
(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2)(-m_2^{\mathrm{eff}} \omega_d^2) + \eta^2 \omega_d^2
}{
(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2)(-m_2^{\mathrm{eff}} \omega_d^2)
}
\right) \\
&= \tan^{-1}\!\left(
\frac{-2 k_2 \eta \omega_d}{
(-m_2^{\mathrm{eff}} \omega_d^2 + 2k_2)(-m_2^{\mathrm{eff}} \omega_d^2) + \eta^2 \omega_d^2}
\right).
\end{aligned}
\end{equation}\]
so the polar and azimuthal angle at bit 1 is:
(72)\[\begin{equation}
\begin{aligned}
\theta(\omega_d)
&=
2\cos^{-1}\left(
\left|\psi_{(0,d)}\right|
\right)
=
2\cos^{-1}\Bigg[
\frac{
|k_1 F|
}{
\sqrt{2}\,|D|
}
\sqrt{
\left(-m_2^{\mathrm{eff}}\omega_d^2 + 2k_2\right)^2
+
(\eta\omega_d)^2
}
\Bigg]
\\
\varphi(\omega_d)
&=
\arg(\psi_{(0,d)}) - \arg(\psi_{(1,d)})
=
\tan^{-1}\left(
\frac{
-2k_2\,\eta\omega_d
}{
(-m_2^{\mathrm{eff}}\omega_d^2 + 2k_2)(-m_2^{\mathrm{eff}}\omega_d^2)
+ \eta^2\omega_d^2
}
\right)
\end{aligned}
\end{equation}\]
The dynamic behavior of Bit 2 is governed by the evolution of the polar angle \(\theta\) and azimuthal angle \(\phi\), which are directly influenced by the vibration mode of the connecting spring. Notably, the spring exhibits a piecewise stiffness behavior: it responds linearly when in tension and nonlinearly when in compression. This intrinsic asymmetric introduces a mechanism by which nonlinear modal behavior can be selectively excited or suppressed depending on the amplitude and phase difference between mass displacements.
(73)\[\begin{equation}
\begin{aligned}
\psi_{(0,2\omega_d)} =
\frac{1}{\sqrt{2}}\,
\frac{
k_2^{\prime} (C_{1,0}-C_{2,0})^2
\left[-8(m_1^{\mathrm{eff}}+m_2^{\mathrm{eff}})\omega_d^2 + 2k_1 + 8k_2 + 8i\eta\omega_d\right]
}{
(-8m_1^{\mathrm{eff}}\omega_d^2 + 2k_1 + 2k_2 + 4i\eta\omega_d)
(-8m_2^{\mathrm{eff}}\omega_d^2 + 2k_2 + 4i\eta\omega_d)
- 4k_2^2
}
\\
\psi_{(1,2\omega_d)} =
\frac{1}{\sqrt{2}}\,
\frac{
k_2^{\prime}(C_{1,0}-C_{2,0})^2
\left[-8(m_2^{\mathrm{eff}}-m_1^{\mathrm{eff}})\omega_d^2 - 2k_1\right]
}{
(-8m_1^{\mathrm{eff}}\omega_d^2 + 2k_1 + 2k_2 + 4i\eta\omega_d)
(-8m_2^{\mathrm{eff}}\omega_d^2 + 2k_2 + 4i\eta\omega_d)
- 4k_2^2
}
\end{aligned}
\end{equation}\]
and the polar and azimuthal angle
(74)\[\begin{equation}
\begin{aligned}
\theta(2\omega_d)
&=
2\cos^{-1}\Bigg[
\frac{
|k_2^{\prime}|\,|C_1^{\prime} - C_2^{\prime}|^2
}{
\sqrt{2}\,V
}
\sqrt{
\left(-8(m_1^{\mathrm{eff}} + m_2^{\mathrm{eff}})\omega_d^2 + 2k_1 + 8k_2\right)^2
+ (8i\eta\omega_d)^2
}
\Bigg]
\\
\varphi(2\omega_d)
&=
\tan^{-1}\left[
\frac{
8\eta\omega_d
}{
-8(m_1^{\mathrm{eff}} + m_2^{\mathrm{eff}})\omega_d^2 + 2k_1 + 8k_2
}
\right]
-
\arg\left[
8(m_1^{\mathrm{eff}} - m_2^{\mathrm{eff}})\omega_d^2 - 2k_1
\right]
\end{aligned}
\end{equation}\]
Figure 17 summarizes the analytical prediction of the Bloch-state evolution for the first and second elastic bits. The zeroth-order solution (\(\epsilon^0\)) in Fig. 17 yields the time-independent coefficients of Bit 1 and reproduces the key features of the experimental Bloch trajectory shown in Fig. 16a, including the continuous sweep of the polar angle \(\theta(\omega_d)\) and the pronounced jump in the azimuthal angle \(\phi(\omega_d)\) obtained from Eq. (70). Introducing viscous damping \(\eta\) into the analytical model smooths the otherwise abrupt phase transition and produces intermediate \(\theta\) values, thereby capturing the rounded behavior observed experimentally. Increasing \(\eta\) gradually suppresses the magnitude of the \(\varphi\) jump, consistent with the experimental trend.
The first-order solution (\(\epsilon^1\)) generates the Bloch states for Bit 2 and yields the theoretical \(\theta(2\omega_d)\) and \(\varphi(2\omega_d)\) curves presented in Fig. 17 and Eq. (72). These curves qualitatively match the characteristic variations observed in the second-harmonic measurements of Fig. 16b, where the nonlinear response introduces additional structure and distortion in both angular trajectories. Although the analytical expressions assume idealized stiffness and simplified nonlinear contributions, the overall frequency-dependent evolution of \(\theta\) and \(\varphi\) agrees well with the experimentally measured trends. The remaining differences arise from realistic damping, asymmetric tension–compression behavior, and material-specific properties of the conical spring, all of which influence the exact shape and sharpness of the angular transitions.
The ability to freeze the internal phase while sweeping the state adiabatically is crucial for memory-type operations: information is written by selecting a point on the Bloch sphere with \(\omega_d\). It remains stable until \(\omega_d\) is changed. Hence, the time-independent logical elastic bit furnishes a robust, ambient-condition analogue of the idle qubit state that underpins quantum registers.