# 12.1 The mechanics of bouncing

A. Why do things bounce?

If you have been following the pattern of chapters so far, you might be expecting an “underpinnings” chapter next. Well, the next topic doesn’t need a whole chapter of underpinning, but this first section does indeed give some background information for the musical applications in the ensuing sections. The questions of interest all involve collisions and bouncing.

We have already said a little about the mechanics of bouncing, when we discussed impact hammers for frequency response measurement, back in section 2.2.6. In order to get a first impression of how hammers behave we used a very crude approximation: we allowed for the mass of the hammer and an effective stiffness acting between this mass and the structure being tapped, but we treated that structure as being rigid. We did not allow for the fact that the structure would vibrate in response to the tap — which is of course the point of tapping in the first place, whether we are thinking of a vibration measurement or a percussionist hitting a drum or a marimba bar. In the course of this section we will rectify this omission.

A particularly simple kind of collision involving bouncing is illustrated in Fig. 1. This shows two identical steel balls, suspended from a frame so that they can only move along a circular arc. We start with one ball stationary, and we release the other from a height. They collide, and the result is that the moving ball stops dead, while the stationary ball moves off with the same speed that the moving ball had before the collision. The second ball swings out and then returns, and the process repeats in the opposite direction.

A variant of this example is shown in Fig. 2. This shows the same toy as in Fig. 1, but now there are five identical balls. We drop a ball at one end, and the ball at the opposite end flies off — but apparently without the balls in between moving at all. There is a simple way to see why this behaviour could have been anticipated. Suppose there was a very small space between each ball and the next one. When you drop the first ball, the first thing that happens is exactly the same as in Fig. 1: the first ball stops dead, and the second one moves off at the original speed. But in a very short time this ball will hit the third ball. The second ball, in its turn, will stop dead while the third ball moves off. This process would be repeated all the way along the chain, however many balls we had, until the last ball is launched. This one doesn’t have another one to hit, so it flies off, swings upwards, returns, and repeats the process in reverse.

One way to think about the result of the first impact seen in Fig. 1 is that we have used a mass (the right-hand ball) to strike a pendulum. This caused the pendulum to vibrate, in the rather stately way that a swinging pendulum does. It has only a single vibration frequency, and we saw a half-cycle of that vibration before the ball returned, and a second impact occurred with the original mass. But if we had moved the first mass, our “striker”, smartly out of the way, the pendulum would have continued to swing. This is a simple model for what happens when a percussionist hits a marimba bar, or an acoustician hits a violin bridge with a small impulse hammer in order to measure its vibration response. In both cases, multiple impacts are usually not wanted (for reasons we will explore shortly). You want the percussion beater or the impulse hammer to rebound out of the way, leaving the structure free to vibrate.

But there may also be a conflicting requirement. If you want to make the loudest sound on the marimba, you would like to put as much energy as possible into the vibration. You supply a certain amount of kinetic energy in the moving beater, just before it strikes. The most you could possibly hope would be for all that energy to go into vibration of the struck object. This is exactly the situation we saw in Fig. 1. The first ball transferred all its kinetic energy to the second ball, the swinging pendulum. The first ball did not rebound so as to get out of the way, and a second impact followed shortly afterwards. If something similar happened to the marimba player, they might describe the result as a “buzz” or as “chattering” of the beater. For practical purposes, we need a compromise: transfer a reasonable amount of kinetic energy, but allow a clean bounce.

There is a third important factor: the frequency spectrum of the force applied by the bouncing beater, which will determine the brightness or mellowness of the resulting sound. We will see shortly that there is an interesting interaction between the three factors, linked to the design of the beater and also to the vibration characteristics of the object you are tapping. This interaction plays out somewhat differently in different applications: we will find contrasting requirements for an impact hammer for an acoustic measurement, the choice of beaters or drumsticks for a percussionist, and the design of a suitable clapper for a church bell.

First, a reminder of the simple calculation of the behaviour of a bouncing hammer from section 2.2.6. The hammer is only in contact with the structure for a very short time, but during that time we know that a force must act to prevent the hammer-head from penetrating into the structure. The simplest idealisation of that force is to imagine a very stiff spring separating the two components. In the case of our bouncing steel balls, for example, this contact spring force is provided by small deformations of the steel in a tiny region around the contact, as indicated in a sketch in Fig. 3. For the purposes of a simple model we can replace this by a contact spring joining two rigid balls, as sketched in Fig. 4. Figure 3. Close-up of the region near the contact point, when the steel balls from Fig. 1 collide. Contact stiffness is provided by small deformations of the steel in the region shaded red. Figure 4. The two colliding spheres from Fig. 3, with the deforming region replaced by a contact spring.

During contact, we now have the two rigid masses linked by a spring. This combination will produce a resonance frequency, as usual — it is called a contact resonance. At the moment when contact begins, the balls are moving towards one another, so while they remain in contact the spring force will follow a sinusoidal waveform at the resonance frequency. If the balls were sticky so that they remained together thereafter, the result would be the dashed curve in Fig. 5. But in the absence of stickiness, the force can only be compressive. Once the model calls for a tensile force, we know that the balls will in fact separate. So (within this simple model) the contact force during a single impact should follow a half-cycle of the sinusoidal wave, as shaded in red in Fig. 5. Figure 5. The force between two colliding objects, allowing for their mass and for a linear contact spring as in Fig. 4. The force would follow a half-cycle of a sinusoidal waveform at the frequency determined by the ratio of contact stiffness to mass, until bouncing occurred when that sinusoidal force would need to go negative. (Figure reproduced from Fig. 1 of section 2.2.6.)

We can find the corresponding spectrum of the contact force by calculating the Fourier transform of this half-cycle of sine wave: the details were given in section 2.2.6. Two typical examples are shown in Fig. 6, reproduced from Fig. 3 of that section. The plot shows results for two different values of the contact resonance frequency. For the lower frequency (red curve), the amplitude of the force spectrum is only high up to about 700 Hz, while for the higher frequency (black curve) it extends up to around 4 kHz. The resonance frequency is determined, as usual, by the ratio of the contact stiffness to the mass. So a low stiffness or a high mass tends to give a low resonance frequency, and correspondingly low bandwidth. A low mass or a high stiffness gives the opposite result, and a high bandwidth. In other words, a heavy, soft beater gives a more gentle, mellow tone from a struck object, while a light, hard one gives a crisper, brighter sound: exactly as every percussionist knows. Figure 6. The spectrum of the hammer force from Fig. 5, for two different contact resonance frequencies: 300 Hz in red; 1500 Hz in black. The vertical scale is logarithmic, expressed in decibels (dB): each interval of 20 dB means the force has changed by a factor of 10. (Figure reproduced from Fig. 3 of section 2.2.6.)

B. The missing ingredients

So far, so good: the simple model gives us some plausible and useful information. However, there are four separate reasons why it is incomplete, and therefore potentially unrealistic. We will outline all four issues, and then explore the consequences using computer simulations of a model problem which will allow us to add them in one at a time.

For the first missing ingredient, look back for a moment at Fig. 1. Without writing down any equations, we can glimpse an important aspect of the underlying physics of collision. Because the two balls are identical and the collision is exactly aligned along the line joining the centres of the balls, everything is symmetrical. After the first collision the ball that was initially stationary moves off with (almost exactly) the same speed that the moving ball previously had, and this tells us two things: the total kinetic energy stays the same, and the total momentum stays the same. (Both kinetic energy and momentum are calculated from the mass and the speed of the balls. Since the balls have the same mass and the speed stays the same, both quantities must be the same before and after the collision.)

However, I have glossed over something. Momentum really is conserved in a collision, but kinetic energy is not quite conserved: some energy will always be lost. If nothing else, the audible “click” of the bouncing balls means that a small amount of energy has been carried away in the form of sound waves. With our steel balls the loss is very small, but if the balls had been made of something like wood a higher proportion of the energy might be lost, mainly converted into heat associated with the contact deformation sketched in Fig. 3. The ratio of kinetic energies before and after a collision can be used to define a coefficient of restitution which can then be incorporated into a simulation model: some details of this and other aspects of the mathematical modelling of more realistic collisions are given in the next link.

SEE MORE DETAIL

The second missing ingredient also concerns the details of what happens near the contact point. As sketched in Fig. 4, I introduced a contact spring to represent the force causing the rebound. So far, I have implicitly assumed that this is a “normal” spring obeying Hooke’s law: force proportional to displacement of the ends of the spring. But mathematical modelling of the deformation and consequent force during an impact between two spheres, for example, makes a different prediction. The analysis was first carried out by Heinrich Hertz (the same German scientist that the unit of frequency is named after), and so the behaviour is known as “Hertzian contact”. Some details are given in the previous link, but the main conclusion is that in place of a linear contact spring we should use a nonlinear spring, in which the force rises more rapidly than the linear relation given by Hooke’s law. This nonlinear spring makes mathematical predictions much more difficult, but it is very simple to incorporate into a numerical simulation model.

The third missing ingredient is something we mentioned earlier in this section. The whole point of hitting a percussion instrument, for example, is to make a noise. The instrument starts to vibrate as a result of the collision, and of course this influences the details of the collision process. Kinetic energy is transferred to this vibration, bringing into play additional degrees of freedom to describe the vibration modes of the struck object.

The fourth missing ingredient is closely related to the third: the impact hammer or drumstick will also be set into vibration by the contact force. It is a “well-known fact” among percussionists that different sticks will produce different sound. We have already seen that the mass and contact stiffness can make a big difference to the spectrum of contact force, and hence to the sound. But do the vibration resonances of a drumstick also play a significant role? The previous link shows how the effect of vibration, both of the struck object and of the drumstick, can be included in a simple simulation model.

C. Simulation results for hitting a rigid surface

To explore the influence of these various factors we will look at a simple model system, vaguely resembling a percussion instrument like a cymbal being hit with a drumstick. The “instrument” is a rectangular thin plate, hinged round its boundary, and the “drumstick” is a hinged-free bending beam which hits the plate (through a contact spring) with its free end. The system is sketched in Fig. 7, and some details of how the model has been implemented in the computer were given in the previous link. This model is not meant to be an accurate representation of any real musical instrument, of course — we are looking for qualitative insights by varying the model parameters to get an impression of, for example, the circumstances that will lead to multiple impacts between the plate and the drumstick. Figure 7. The idealised system to be used to investigate bouncing. A thin rectangular plate (the “instrument”, shown in blue) is struck by a beam (the “drumstick”, shown in dark red), hinged at the far end. During contact, a spring (in bright red) provides the contact force.

The relevant vibration behaviour of the plate and the drumstick will be adjusted by specifying the total mass and the lowest vibration resonance frequency of each. Other details, such as the assumed aspect ratio of the plate, the striking position on the plate, and the damping factors for both plate and drumstick will be kept fixed (if you are curious, they are specified in the previous link).

The first step is to verify that the model reproduces the behaviour sketched in Fig. 5 when the plate is effectively rigid, and the lowest resonance frequency of the stick is so high that it doesn’t affect the behaviour. Specifically, we make the plate mass 500 metric tons, and the first stick resonance 10 kHz. We also assume a linear contact spring, as in the theoretical calculation. The red curve in Fig. 8 then shows the computed waveform of contact force for a particular choice of the stick mass and contact stiffness. It does indeed show the expected shape, a half-cycle of a sine wave before a clean bounce occurs and contact is lost.

The blue curve in Fig. 8 shows what happens if we replace the linear contact spring with a Hertzian spring, with a stiffness chosen to give more or less the same contact time. There is still a single, symmetrical pulse of force, but the shape is subtly different. At the moment of first contact, the force builds up less abruptly than with the linear spring. But the force grows progressively more steeply a little later in the pulse, a direct result of the “hardening spring” behaviour. Figure 8. The computed force pulse when both stick and plate are effectively rigid, computed for a linear contact spring (red curve) and for a Hertzian spring (blue curve). The mass of the drumstick was 0.1 kg, the linear spring stiffness was $k_c =88.6 ~ \mathrm{kN/m}$, and the stiffness of the Hertzian spring was chosen to give approximately the same contact time (the value was $k_H = 695 ~ \mathrm{kN/m}^{3/2}$).

We can see a different comparison between these two force pulses if we take the FFT and look at their frequency spectra: the results are shown in Fig. 9, using the same plot colours as Fig. 8. The spectra are shown on a logarithmic (dB) scale, normalised in the same way as Fig. 6 so that the value tends to zero at very low frequency. For both pulses, the spectrum looks generically similar to Fig. 6: high values restricted to a relatively narrow band of low frequencies, then a pattern of sharp dips and secondary peaks with decreasing height. We can see that the Hertzian spring (blue curve) gives a slightly wider bandwidth at low frequency, and that the frequencies of the secondary peaks are all a little higher, while the peak heights decrease more rapidly (a consequence of the more gentle start and end of the pulse). Figure 9. Frequency spectra of the two force pulses shown in Fig. 8, shown with the same plot colours. The spectrum magnitude is shown on a dB scale normalised to the value zero at low frequency, as in Fig. 6

It is perhaps useful to see a broader view of how things change when the drumstick properties are varied. If we take a range of values of the mass and contact stiffness, we can compute a grid of cases and then show the results in graphical form rather similar to the “playability plots” we used earlier when talking about bowed string and wind instruments. Figure 10 shows the contact time, for a range of stick masses up to 200 g, and for a wide range of linear contact spring stiffnesses. (Because of the wide range, varying over a factor of 100, a logarithmic scale has been used on the vertical axis.) The colours show a curving pattern, which for this preliminary case simply follows the contour lines of the contact resonance frequency. Figure 10. Contact time, for drumsticks of a range of masses and tip stiffnesses impacting on an effectively rigid surface. A linear contact spring is assumed here, with a stiffness varying from 10 kN/m to 1000 kN/m on a logarithmic scale. The green circle marks the case shown in red in Figs. 8 and 9.

Figure 11 gives an indication of how the force spectrum varies over the same grid of simulated cases. The colours here show the spectral centroid, which gives a simple guide to the frequency content of each force waveform. The curves mark out the same contour lines of contact resonance frequency as in Fig. 10. Comparing Figs. 10 and 11, we see the expected behaviour: a light stick with a stiff tip gives a short contact time and a high spectral centroid implying a bright sound, while a heavy stick with a soft tip gives a long contact time, a lower spectral centroid, and a more mellow or muffled sound. However, at this stage there is no “sound”, because we are hitting an essentially rigid surface. Later, we will relax this assumption and hear some sound examples. Figure 11. Spectral centroid of the force pulse waveform, for the same grid of simulations as in Fig. 12.

Figures 12 and 13 show corresponding plots with a Hertzian contact spring. This time we do not have a simple mathematical result for how the contact force behaves, but in fact both plots look broadly similar to Figs. 10 and 11 for the linear spring. The same trends are followed, and you have to look rather carefully to spot the subtle differences in the shapes of the contours mapped out by the colour shading. Provisionally, then, the nature of the contact spring doesn’t make a huge difference to the predicted behaviour. Figure 12. Contact time for a similar grid of simulations to Fig. 10 except that the linear contact spring has been replaced by a Hertzian spring. The green circle marks the case shown in blue in Figs. 8 and 9. Figure 13. Spectral centroid of the force pulse for the same grid of simulations as in Fig. 12.

D. Simulations with flexible plates

If make our plate or our drumstick (or both) have more realistic dynamic behaviour, things immediately get more complicated. As a first step we will change the plate behaviour, leaving the drumstick still essentially rigid. Before showing detailed simulation results for this case, though, it is useful to introduce an approximate argument which tells us something important about what we can expect to see.

The basis of the argument is something we mentioned at the start of this section, when we talked about the transfer of kinetic energy from a moving “beater” to vibration of the structure which is struck. Every vibration mode that is excited uses up some of the kinetic energy that the drummer put into the moving drumstick. Perhaps this makes it intuitively plausible that there might be a limit to how many modes can be strongly excited before the supply of kinetic energy is “used up”.

This idea proves to be correct — the details are explained in the next link. The argument makes use of the force waveform shown in Fig. 5. We have already seen (see Fig. 6) that the frequency bandwidth associated with a pulse like this depends on the contact duration, or equivalently on the contact resonance frequency. When this force pulse is applied to a given structure, it is straightforward to calculate how strongly each mode will be excited.

SEE MORE DETAIL

The total kinetic energy of the vibrating structure can then be calculated. It depends on the contact resonance frequency: the higher that frequency, the higher the kinetic energy. There is a threshold value of the contact resonance frequency, above which the vibrating structure would require more kinetic energy than is available. This puts a limit on the shortest contact time that is possible if the drumstick is to rebound. At the threshold the incoming drumstick is stopped dead by the impact (just as we saw with the steel balls in Figs. 1 and 2). A second impact is almost certain to follow, when the vibrating structure returns and hits the stationary drumstick.

We will illustrate with results for two different vibrating systems. First, we look at an example of the vibrating plate described earlier (see Fig. 7), chosen to have total mass 200 g and a lowest resonance frequency 100 Hz. This plate will be impacted at the four different points shown in Fig. 14, and the resulting threshold values of the contact resonance frequency are shown as a function of the “hammer” mass in Fig. 15. Because the mass and the threshold frequency cover a very wide range, logarithmic scales have been used on both axes. Figure 14. Sketch of the vibrating plate used to illustrate the approximate calculation of a threshold contact resonance frequency. The plate is rectangular, with aspect ratio 1.55:1, total mass 200 g and a lowest resonance frequency 100 Hz. It has “hinged” boundaries all around its edge: the plate cannot move at the edge, but near the edge it is free to rotate about the edge line. The four tapping positions to be shown in Fig. 15 are indicated by red stars. They all lie on a line, and the proportional distances from the left-hand edge are respectively 0.05, 0.2, 0.3 and 0.5. Figure 15. Threshold contact resonance frequency for the vibrating plate, as a function of the mass of the “hammer” hitting the plate. The four curves correspond to the four excitation points shown in Fig. 14: from left to right the curves are coloured red, blue, green and black.

All four curves show a falling trend — a heavier hammer means that the threshold frequency is lower. Three of the tapping positions give rather similar results (the blue, green and black curves), but the position close to the edge of the plate (the red curve) shows a significantly higher frequency over the entire range. In other words, it is easier to excite a wide bandwidth of response in this plate by tapping close to an edge. It is important to recall that this plate has fixed edges all the way round, so that the plate “feels” relatively rigid for a tapping position near the edge.

This behaviour contrasts with our second example, a vibrating beam with free ends, like a marimba bar. The system, sketched in Fig. 16, is given the same total mass and the same lowest resonance frequency as the plate. Again, it is tapped at four different positions, giving the threshold results plotted in Fig. 17. All four curves show a falling trend again, but the shape and position of the curves is different from the ones in Fig. 15: changing the system you tap can make a big difference to the bandwidth you can excite with a given hammer. The main reason behind this contrast is the fact that the resonances of a plate come thick and fast after the first one, whereas the resonances of a bending beam are spaced progressively wider apart (see section 4.2.4 for some detailed analysis of this difference of modal density). Figure 16. Sketch of a vibrating beam used to illustrate the approximate calculation of a threshold contact resonance frequency. The beam has total mass 200 g and a lowest resonance frequency 100 Hz. It has free boundaries, like a marimba bar. The four tapping positions to be shown in Fig. 17 are indicated by red arrows. The proportional distances from the left-hand edge are respectively 0, 0.03, 0.1 and 0.4. Figure 17. Threshold contact resonance frequency for the vibrating beam, as a function of the mass of the “hammer” hitting the plate. The four curves correspond to the four excitation points shown in Fig. 16: from left to right the curves are coloured red, blue, green and black.

The other contrast with Fig. 15 lies in the position of the red curve relative to the others. Again this red curve is associated with tapping near the edge of the structure — in fact, right at the edge in this case. For the beam, the red curve lies below the others rather than above them as it did for the plate. The main reason this time is not to be sought in the difference between plates and beams, though. Instead, the important difference is in the edge conditions. The plate was fixed at the edge, while the beam is free at its ends. So now the red curve is the result of tapping at a position where the structure “feels” most floppy. This makes it harder to avoid multiple impacts. Figure 18. Map of contact time in the same format as Fig. 10, for a case in which the plate mass is 2 kg. The contact spring is linear, and all other parameters are the same as for Fig. 10.

Now we are ready to see some simulation results. If the total mass of the plate is set to 2 kg, with a first resonance frequency at 100 Hz, the equivalent of Fig. 10 now looks like the plot in Fig. 18. Virtually nothing has changed: this plate is still heavy enough that the bouncing process is not affected significantly. But if we reduce the mass further to 200 g as in the case studied in Figs. 14 and 15, the result is shown in Fig. 19: this time something looks obviously different, especially in the upper right-hand region of the plot. To see what has happened, Fig. 20 shows a map of the same grid of simulations, coloured black where there was a single, clean bounce and in colours where a multiple impact of some kind occurred. These multiple impacts occur throughout the region that looked different in Fig. 19. Figure 19. Map of contact time in the same format as Figs. 10 and 18, for a case in which the plate mass is 200 g. The contact spring is linear, and all other parameters are the same as for Fig. 10. The green circle marks the case shown in detail in Fig. 21, and the black circle marks the case shown in Fig. 22. Figure 20. Map showing single impacts (black) and multiple impacts (colour) for the same set of simulations shown in Fig. 19. The colour scale indicated the ratio of the contact stiffness to the threshold value calculated by the approximate argument: the threshold given by the approximate argument is marked by the boundary of the region of white pixels.

The colour scale in Fig. 20 indicates the ratio of the contact stiffness to the threshold value calculated by the approximate argument, as in Fig. 15. Where the pixels become white, the approximate criterion has been reached or exceeded. But we can see in the plot that there is a substantial range of contact stiffness for which the simulations predict multiple impacts of some kind although the limiting stiffness from the approximate argument has not been reached. However, the general shape of the contours of these intermediate colours follows the trend marked by the edge of the patch of white pixels, so the approximate argument does give a useful indication of the pattern.

Some examples of the shape of the contact force waveforms for different plate masses are shown in Figs. 21 and 22. The red curve in Fig. 21 is the same as the red curve in Fig. 8, showing the half-sine shape when the impacted plate was effectively rigid. The blue curve shows the result for the same case with the plate mass 2 kg as in Fig. 18, and the green curve shows the result for the 200 g plate as in Fig. 19. The green circle in Figs. 19 and 20 marks the pixel corresponding to these three waveforms. The blue curve has slightly smaller magnitude than the red curve, because of energy transfer to the plate, but otherwise the pulse shape looks very similar. Comparing with Fig. 20, this pixel lies just above the region where single impacts occurred for the 200 g plate, and the green curve shows the kind of behaviour we might have guessed: a double-humped shape, but not quite losing contact in between to give multiple impacts. Figure 21. The pulses of contact force for parameter values corresponding to the green circle in Fig. 15, for the three cases so far analysed: the red curve shows the rigid plate as in Fig. 10, the blue curve shows the 2 kg plate from Fig. 14, and the green curve shows the 0.5 kg plate from Fig. 15.

Figure 22 shows corresponding results for the pixel marked by a black circle in Figs. 19 and 20. The red and blue pulses in this plot show a shorter contact time than the corresponding ones in Fig. 21, as expected with the higher contact stiffness. Looking at Fig. 20, we see that this pixel lies in the white region for the 200 g plate, where the criterion based on kinetic energy has been exceeded. The plot confirms this. The green curve shows a rather ragged waveform, with three separate impacts. There is a significant delay before the third impact: the drumstick had to wait for the vibrating plate to come back and hit it before it was thrown back, away from any further impacts. Figure 22. The pulses of contact force for parameter values corresponding to the black circle in Fig. 19, for the three cases: the red curve shows the rigid plate as in Fig. 10, the blue curve shows the 2 kg plate from Fig. 18, and the green curve shows the 200 g plate from Fig. 19. The green curves shows obvious multiple impacts.

Figures 23 and 24 show the corresponding frequency spectra to Figs. 21 and 22 respectively, plotted in the matching colours. In both cases we see that as the impacted plate gets lighter, the dips in the spectrum get shallower. For cases in which there is only a single impact, the relatively subtle modification to the pulse shape from impacting a vibrating plate has resulted in a smoother spectrum. But the green curve in Fig. 24 shows more ragged behaviour, which is perhaps not too surprising. We will come back to these observations in a bit — they have implications for measurements using an impulse hammer. Figure 23. Frequency spectra for the three pulses shown in Fig. 21, plotted in the corresponding colours. Figure 24. Frequency spectra for the three pulses shown in Fig. 22, plotted in the corresponding colours.