Physics/Option Modules/Engineering Physics/Engineering Applications of SHM
Physics · Engineering Physics · A2 Level

Engineering Applications of SHM

Across the last four lessons, this topic has built up a complete way of thinking about vibration: how to describe it (SHM), what happens when it's driven (forced vibration and resonance), and how to control it (damping). This closing lesson puts all four pieces to work on real engineering systems — vehicle suspension, vibration isolation, and rotating machinery balancing.

9 min read

Vehicle suspension: balancing comfort against control

A vehicle's suspension system is one of the clearest everyday examples of applied SHM engineering. It combines two components with deliberately different jobs: a spring, which provides a restoring force roughly proportional to displacement (approximating SHM behaviour), and a damper (commonly called a shock absorber), whose job is to dissipate the energy of any oscillation the spring alone would otherwise sustain.

Without a damper, a vehicle body supported only on springs would bounce for a long time after every bump — technically an almost undamped SHM oscillator, prone to a resonant response if driven repeatedly at its natural frequency, for instance by a rhythmic sequence of bumps. The damper is tuned close to critical damping (introduced in the previous lesson) precisely to prevent this: close to critical damping gives the fastest possible settling with little or no oscillatory bounce, striking a deliberate balance between comfort (some give in the suspension, absorbing the shock of a bump rather than transmitting it directly into the frame) and control (not continuing to oscillate uncontrollably after every bump, which would compromise both comfort and the tyres' grip on the road).

Worked exampleNatural frequency of a suspension system
01
A simplified suspension model treats one corner of a vehicle as a mass $m = 380\text{ kg}$ (the effective mass supported at that corner) resting on a spring of stiffness $k = 22{,}000\text{ N m}^{-1}$.
Spring stiffness $k$ and supported mass $m$ are the two physical properties that fix the natural frequency of this SHM-like system.
02
For this spring–mass system, the angular frequency is $\omega = \sqrt{\dfrac{k}{m}}$.
This is the standard relationship between angular frequency, stiffness and mass for a spring-supported oscillator behaving approximately as SHM.
03
Substituting values: $\omega = \sqrt{\dfrac{22000}{380}} \approx \sqrt{57.9} \approx 7.6\text{ rad s}^{-1}$.
Direct substitution into the formula above.
04
Converting to an ordinary frequency: $f = \dfrac{\omega}{2\pi} \approx 1.2\text{ Hz}$.
This is a realistic value — vehicle suspension natural frequencies typically sit around 1–1.5 Hz.
05
If the damper fitted to this suspension is too light, the body will oscillate at close to this 1.2 Hz frequency for several cycles after every bump, and could build a large, uncomfortable response if driven repeatedly near 1.2 Hz (for example by a rhythmic sequence of bumps, or worn tyres striking the road at a matching rate). If the damper is too heavy, the suspension becomes stiff and harsh, transmitting more of each bump's shock directly into the frame before the spring has time to absorb it smoothly.
This links the calculated natural frequency directly to the light-versus-heavy damping trade-off from the previous lesson.
example complete

Vibration isolation: mounting systems below the threat

A second major application turns the idea of natural frequency around. Rather than damping an oscillation after it starts, vibration isolation aims to stop external vibration from reaching a sensitive system in the first place. Sensitive equipment — precision measuring instruments, delicate electronics, or vibration-sensitive structures — is mounted on deliberately soft, compliant mounts rather than bolted rigidly to whatever is vibrating nearby.

The key design principle is to choose mounts soft enough that the mounted system's own natural frequency sits well below the frequency of the external vibration it needs to be isolated from. When the driving frequency of the external vibration is much higher than the mounted system's natural frequency, the mount transmits only a small fraction of that vibration through to the equipment — the softer the mount (the lower its natural frequency relative to the driving frequency), the more effectively it isolates the equipment from what's shaking around it. This is essentially the mirror image of the resonance-avoidance problem from the forced vibrations lesson: instead of keeping a driving frequency away from a component's natural frequency, vibration isolation keeps a mounted system's natural frequency deliberately far below the driving frequencies it will encounter.

Balancing rotating machinery

The third major application ties directly back to the forced vibrations lesson earlier in this topic. Rotating components — engine crankshafts, wheels, turbine rotors, compressor blades — are precision-balanced during manufacture specifically to minimise any off-centre distribution of mass. An imbalanced rotating component delivers a periodic driving force to its own mountings once per revolution, at a driving frequency equal to its rotation frequency, exactly as covered previously. Precision balancing reduces the size of that driving force at its source, rather than relying entirely on damping or careful choice of operating speed to manage its effects afterwards.

  • Balancing is typically carried out by measuring the vibration a rotating part produces as it spins, then adding or removing small amounts of mass at calculated positions until the vibration is minimised.
  • Even a very small imbalance can become a significant problem at high rotation speeds, since the driving force delivered by an imbalance generally increases sharply with rotation speed.
  • Balancing, avoiding operation near a supporting structure's natural frequency, and providing adequate damping are complementary strategies — real machines typically use more than one of them together.
One connected design toolkit

None of the three applications above stands alone — each is a direct, practical use of ideas built up across this whole topic. Suspension design uses the natural-frequency relationship from mechanical oscillations together with the damping regimes from the damping lesson. Vibration isolation is a deliberate, inverted use of the resonance-avoidance principle from forced vibrations. Rotating machinery balancing directly reduces the periodic driving force described in the forced vibrations lesson at its source. Seeing these as one connected toolkit, rather than three unrelated topics, is the single most useful way to hold this material together for application in unfamiliar engineering contexts.

Key takeaways

  • Vehicle suspension combines a spring (providing an SHM-like restoring force) with a damper tuned close to critical damping, balancing ride comfort against control.
  • A suspension system's natural frequency is set by its spring stiffness and supported mass, via $\omega = \sqrt{k/m}$.
  • Too little suspension damping risks resonant bouncing; too much makes the ride harsh by transmitting shock before it can be absorbed.
  • Vibration isolation mounts sensitive equipment on soft mounts so its natural frequency sits well below the frequency of vibration it needs isolating from, reducing transmission.
  • Rotating machinery (crankshafts, wheels, turbines) is precision-balanced to minimise the periodic driving force an imbalance would otherwise deliver to its mountings.
  • This topic forms one connected design toolkit: describe the oscillation with SHM, identify what happens if it's driven (forced vibration and resonance), control the response with damping, then apply all three in real engineering systems.
  • Every application in this closing lesson is a direct, practical use of the four ideas developed earlier in this topic, not a separate body of knowledge.