Volume 58 Issue 02 March 2025
Mathematical Curiosities

Geometry of the Phase Lag

<strong>Figure 1.</strong> Point mass that is subject to the Hookean force \(- \omega_0 ^2 z\), the drag, and the external force \(F e^{i\omega t}\). The \(x\)-coordinate satisfies \((1)\), and the steady state solution of \((1)\) corresponds to the circular motion of \(z\) with angular velocity \(\omega\) of the forcing.
Figure 1. Point mass that is subject to the Hookean force \(- \omega_0 ^2 z\), the drag, and the external force \(F e^{i\omega t}\). The \(x\)-coordinate satisfies \((1)\), and the steady state solution of \((1)\) corresponds to the circular motion of \(z\) with angular velocity \(\omega\) of the forcing.

Standard sophomore discussions of forced linear oscillations tend to rely on formulas, often without intuitive answers to some of the following basic questions:

  1. Why does the phase lag \(\varphi\) lie between \(0\) and \(\pi\) for damped oscillators?
  2. Why is \(\varphi =  0\) or \(\pi\) in the absence of damping?
  3. Why is \(\varphi =  \pi /2\) when \(\omega = \omega_0\), the natural frequency (i.e., the frequency of the same oscillator without damping)?

All of these questions refer to the harmonic oscillator with viscous drag and subject to sinusoidal forcing:

\[\ddot x + c \dot x + \omega _0 ^2  x = F \cos \omega t, \tag1\]

where \(\omega_0^2 = k\) is Hooke’s constant. We chose mass \(m=1\) without a loss of generality. As a standard step, one complexifies \((1)\), i.e., considers \(x\) as the coordinate of point \(z\) in the plane satisfying

\[\ddot z + c \dot z + \omega_0 ^2  z = F e^{i \omega t}. \tag2\]

Since complex numbers may spook some students, we can equivalently say that \(x\) in \((1)\) is the \(x\)-coordinate of the point mass that is pulled by the Hookean spring with force \(- \omega_0^2 z\) towards the origin, also subject to both the drag force \(-c \dot z\) that is linear in velocity and the external force of constant magnitude \(F\) that spins with angular velocity \(\omega\), like a spinning jet engine attached to the mass.

<strong>Figure 2.</strong> The damped case. As the driving frequency \(\omega\)—i.e., the angular velocity—increases, more inward force is needed to help the spring.
Figure 2. The damped case. As the driving frequency \(\omega\)—i.e., the angular velocity—increases, more inward force is needed to help the spring.

The steady state solution of \((1)\) corresponds to the circular motion of the point mass, and the phase lag \(\varphi\) in Figure 1 is the angle by which the direction of response \(z\) lags behind the direction of the forcing. Figure 1 answers the aforementioned questions 1-3 as follows:

  1. In the presence of damping, the tangential component \(F \sin \varphi\) must be positive to compensate the drag, hence \(\varphi \in (0,  \pi )\).
  2. In the undamped case \(c=0\), the tangential component of forcing must vanish so that \(\varphi = 0\) or \(\pi\); otherwise, the particle will have nonzero tangential acceleration and be unable to maintain constant speed.
  3. The case \(\varphi =  \pi /2\) amounts to purely tangential forcing. Since the drag is also tangential and the speed of circular motion is constant, the forcing exactly cancels the drag. We can then pretend that neither drag nor forcing is present; what’s left is a circular motion of the undamped unforced oscillator with Hooke’s constant \(\omega_0 ^2\) and hence with frequency \(\omega_0\). But the frequency of our circular motion is also \(\omega\), so that \(\omega = \omega _0\). Thus, \(\omega = \omega _0\) is equivalent to \(\varphi =  \pi /2\).

Figures 2 and 3 illustrate several additional properties that are stated and explained in the respective captions.

<strong>Figure 3.</strong> The undamped case. If the forcing frequency is smaller than the natural frequency, more inward force is needed to weaken the spring to maintain a frequency that is lower than \(\omega _0\). Conversely, if we insist on a high-frequency circular motion, we must help the spring by pulling the mass inwards, thus explaining \(\varphi =  \pi\). The borderline case \(\omega = \omega_0\) is possible only if \(F=0\) in the undamped case.
Figure 3. The undamped case. If the forcing frequency is smaller than the natural frequency, more inward force is needed to weaken the spring to maintain a frequency that is lower than \(\omega _0\). Conversely, if we insist on a high-frequency circular motion, we must help the spring by pulling the mass inwards, thus explaining \(\varphi = \pi\). The borderline case \(\omega = \omega_0\) is possible only if \(F=0\) in the undamped case.

I deliberately avoided calculations, which are typically done via complex numbers. These calculations are actually made redundant through the use of Newton’s second law: from Figure 1,

\[\begin{eqnarray}F \sin  \varphi &=& c \omega R \cr \\ F \cos \varphi &=& \omega ^2 R- \omega_0 ^2 R. \end{eqnarray}\]

The first equation expresses the balance between the tangential component of forcing and the drag, thus assuring constant speed along the circle. The second equation states that the centripetal force \(\omega ^2 R\) is the resultant of the spring force and the radial component of the driving force.

The lag \(\varphi\) and amplitude \(R\) come out of these formulas, but my goal was to instead gain some insight into phase lag without calculation.


The figures in this article were provided by the author.

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