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Forced damped two-degree-of-freedom system

Short answer

Matrix equation: [M]{ẍ}+[C]{ẋ}+[K]{x}={F}. Steady‑state amplitudes are obtained from {X}=[Z(ω)]⁻¹{F} with impedance matrix Z = -ω²M + iωC + K. Static coupling involves off‑diagonal stiffness, dynamic coupling off‑diagonal mass; principal coordinates diagonalise M and K.

For a two-degree-of-freedom spring-mass-damper system with a harmonic force F1sin⁡ωtF_1\sin\omega t acting on mass m1m_1, write the equations of motion in matrix form and explain how the steady-state amplitudes are obtained. Explain static and dynamic coupling and principal (normal) coordinates.

Equations of motion

Take masses m1,m2m_1, m_2, springs k1k_1 (wall to m1m_1), k2k_2 (between masses), dampers c1,c2c_1, c_2 in parallel with them, and force F1sin⁡ωtF_1\sin\omega t on m1m_1.

[m100m2]{x¨1x¨2}+[c1+c2−c2−c2c2]{x˙1x˙2}+[k1+k2−k2−k2k2]{x1x2}={F1sin⁡ωt0}\begin{bmatrix} m_1 & 0 \\ 0 & m_2 \end{bmatrix}\begin{Bmatrix} \ddot{x}_1 \\ \ddot{x}_2 \end{Bmatrix} + \begin{bmatrix} c_1+c_2 & -c_2 \\ -c_2 & c_2 \end{bmatrix}\begin{Bmatrix} \dot{x}_1 \\ \dot{x}_2 \end{Bmatrix} + \begin{bmatrix} k_1+k_2 & -k_2 \\ -k_2 & k_2 \end{bmatrix}\begin{Bmatrix} x_1 \\ x_2 \end{Bmatrix} = \begin{Bmatrix} F_1\sin\omega t \\ 0 \end{Bmatrix}

or [M]{x¨}+[C]{x˙}+[K]{x}={F}[M]\{\ddot{x}\} + [C]\{\dot{x}\} + [K]\{x\} = \{F\}.

Steady-state amplitudes

Write the force as F1eiωtF_1e^{i\omega t} and the response as {x}={X}eiωt\{x\} = \{X\}e^{i\omega t}. Substituting:

[−ω2[M]+iω[C]+[K]]{X}={F}\left[-\omega^2[M] + i\omega[C] + [K]\right]\{X\} = \{F\}

The bracket is the mechanical impedance matrix [Z(ω)][Z(\omega)] with entries Zrs=−ω2mrs+iωcrs+krsZ_{rs} = -\omega^2 m_{rs} + i\omega c_{rs} + k_{rs}. Then

{X}=[Z(ω)]−1{F},X1=Z22F1Z11Z22−Z122,X2=−Z12F1Z11Z22−Z122\{X\} = [Z(\omega)]^{-1}\{F\}, \qquad X_1 = \frac{Z_{22}F_1}{Z_{11}Z_{22} - Z_{12}^2}, \quad X_2 = \frac{-Z_{12}F_1}{Z_{11}Z_{22} - Z_{12}^2}

The amplitudes are complex: ∣Xr∣|X_r| is the amplitude, and the argument gives the phase lag behind the force. Damping makes the denominator never vanish, so the resonance peaks are finite.

Coupling

  • Static (elastic) coupling: the stiffness matrix has off-diagonal terms (k12≠0k_{12} \ne 0); a static force on one coordinate displaces the other.
  • Dynamic (inertia) coupling: the mass matrix has off-diagonal terms (m12≠0m_{12} \ne 0), e.g. a vehicle body with the c.g. not midway between the axles.
  • The coupling depends on the choice of coordinates, not on the system.

Principal (normal) coordinates

They are special coordinates in which both [M][M] and [K][K] become diagonal, so the equations are uncoupled and each is a single-degree-of-freedom equation:

q¨r+ωr2qr=0,{x}=[Φ]{q}\ddot{q}_r + \omega_r^2 q_r = 0, \qquad \{x\} = [\Phi]\{q\}

where [Φ][\Phi] is the matrix of mode shapes. Each principal coordinate vibrates in one mode only.

✓ Answer checked by Claude Opus 5.5 (high effort)

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