IYPT 2019 Team Croatia Table of contents Problem description Tapping a helical spring can make a sound like a laser shot in a sciencefiction movie Investigate and explain this phenomenon ID: 790139
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Slide1
Problem 8: „Sci-Fi Sound”
IYPT
2019
Team Croatia
Slide2Table of contents
Slide3Problem description:
„
Tapping a helical spring can make a sound like a “laser shot” in a
science-fiction
movie.
”
„
Investigate and explain this phenomenon.
”
Table of contents
Slide5The sound of a laser shot from SF
movies
can be produced by causing high-frequency vibrations in a long
rod
or a wire
,
made of
dispersive medium with property that the velocity of sound waves v is increased for higher frequencies and decreased for lower frequencies with an measurable delaying time TD between higher and lower part of the frequency spectrum. The delay time TD depends from …
Hypothesis
Slide6Propagation
of
vibration
in
a
dispersive mediumTheoretical modelNon dispresive materialPropagation of disturbances
Dispresive
material
Example
of
a
dispersion
diagram
The
sound
dispersion
can
be
observed from the following facts:The all vibrations in impacted material were caused
at
the
same
initial
time, but
in
a
dispersive
material
,
the
vibrations
, and their
sounds, on
higher frequencies (H) traveled
faster along
rod and
they, and
they have been heared
before vibrations
at smaller frequencies (L) [4].The phase velocity of movement
(v, m
/s)
of
a particular point on the vibrating rod depends on circular frequency (), or wave number (k) of a wave which is traveled along rod. 3. The movement of a group of waves with different phase velocities form an envelope which contains all waves and traveled along rod with the group velocity (vg, m/s) which is:
The propagation of the modulated wave (x,t) in a dispersive medium [8]
Slinky
spring
as a
long
and
stiff vibrating rod Unstrenched SlinkyFree
hanging
Slinky
Spring
The
Slinky
spring
is
made
from a stiff
prestressed wire, so it is modeled as a long stiff beam with cros
-sectional dimensions
b and h and length L
[4, 5].
b
h
F
v
FhDirections of forces during impact Slinky wireImpulsive excitation of the vertically
hanging Slinky spring
was by made by
a simple pendulum impact
Slide9Bending free
vibrations
of
Slinky
wire
Deformation due to bending of a beam element
with constant cross-section [7,11]Initially tapped or impacted Slinky without additional external force, can be described as a long thin beam with propagating an initial impuls and free bending vibrations in accordance to the Euler-Bernoulli theory while taking into account rotational inertia of the
cross
-
section
beam
[3
]:
w
(
x
,
t
)
+x
-x
x=0Propagating of
initial
displacement w(x,t
) in a
dispersive meadia dependent from
time and
position on the rod [3]
= 0
=EI bh= S
Slide10Slowdown
(2x)
show
of
the
Slinky’s bottom end vibrations after hits with pendulum.The solutions of the wave differentially equation for free bending beam consists from the product of the time harmonic time functions g(t) and the space functions (x) whose coefficients can be determined from boundary and initial conditions.
[3,7]:
const
.
2
n
= 0, 1,
2
, …,
+
B
+
D
n
+
E
n
cosh
+ Fnsinh n = 0, 1, 2, …, The beam free bending vibrations can have only some special values of angular frequencies n known as natural or eigenfrequencies n (n = 0, 1,…) which are constants of the observed vibratory system and connect time and space functions by relation [7] :
Slide11Also, dependence between
bending
wave
eigenfrequency
n and the wave number kn is given with the dispersion relation [4 - 7]:
n
= 0, 1,
2
, …,
The
phase
velocity
v
b
of harmonic movement of an
ith point, at the beam length
0< x<L [3,7]:
In
dependence
from
the
ratio of the terms in the nominator the two border cases can be formulated: one for lower frequencies, and the other for higher. n = 0, 1, 2, …,
Slide12Ad.1. For low
frequency
vibration
,
when
the thickness (h) of beam’s cross-section is smaller than the vibrations wavelength n (e.g. h = 0.0025 m kn < 420) or
the
dispersion
relation
and
the
phase
velocity relation have the folowing
forms [3,4,7]:
n
= 0, 1,
2
, …,
r
S … the radius of gyration of beam cross-section (m)cS … the phase velocity of
a particular point in a beam
material (m/s)kn …
the
wave number of nth bending waveI … the rotational inertia moment of a beam’s cross-section surfaceS … area of a beam cross-section surface (m2)n … the nth eigencircular frequency of a bending beam (rad/s) Low frequency bending movement of a beam cross-sections [7]
Slide13Ad. 2. For high frequency
waves
,
the
beam
deflection is completely determined by transversal and longitudinal waves and the dispersion and phase velocity relations showed non dispersive behaviour of the beam cross-section [11].n = 0, 1, 2, …,
or
High
frequency
transverse
and
quasi
-
longitudinal
movement
of
a
beam
cross-sections [3,7]
Due
to
dispersion
effect the lower frequencies had been recorded, and heard, with delayed time after high frequencies.
Slide14Mathematically
modeled
bending
cases
CASE
1: Bending waves on a vertically free hanging
Slinky
modeled
as a
beam
with
upper
clamped
and
bottom free end (a uniform
cantilever beam) with the wave number
kn
n
= 0, 1, 2, …,
Example
of the 1st to 5th bending modes (x/L) for
a free vibrating clamped-free
end beam
CASE
2: Bending waves on a vertically hanging and full elongated Slinky modeled as a beam with both end clamped (a uniform clamped-clamped beam) with the wave number knExample of the 1st to 5th bending modes (x/L) for a free vibrating clamped-free end beam n = 0, 1, 2, …,
Slide16For
both
modeled
cases
the
time function gn(t) is builded from a harmonic and vanishing wave subfunctions [3]:exp
Mathematically
modelling
of
wave
damping
and
emitted
sound
..
t
he
wave
loss factor
In the acoustic consideration the Slinky wire is modeled as continuous line sound source under transversal oscillations. Each segment of line (x) is an unbaffled simple source which generate the increment of sound pressure pressure level (SPL) in the air [10].
The far field acoustic field at point p(r,
,t)
produced by line source of length L and radius
a [10] p(r,,t) … sound pressure (Pa); j = U0,n … the amplitude of the wave velocity0 … the density of air (1.2 kg/m3)c
a … the velocity of sound in air (343 m/s)
Table of contents
Slide18Case
Number
of Slinky
coils
included
in
bending
vibrations, NfreeNo. 1: Slinky helical spring with Clamped end - Free end48No.2: Slinky helical spring with Clamped end – Clamped end48Experimental measurementsCaseLength or
number
of
coils
No.3
Straight
steel
wire
clamped
on both endsd = 1.20 mm L = 1.55 m No. 4 Home-made
hellical spring with Clamped end - Free endSteel wire d = 1.20 mm with the Inner diameter of helix D = 72 mm Number of coils:
N = 86Lfree hanging = 1.880 mLtotal
= 18.80 m
Slide19CASE 2. Number of coils free for bending N
free
at the vertically hanging full elongated Slinky at distance
L
12
= 1.885 m
:
2.1) 80
separated coils, 1 coil clamped at the bottom and 5 coil clamped at the upper end2.2) 70 separated coils, 1 coil clamped at the bottom and 15 coils clamped at the upper end2.3) 60 separated coils, 1 coil clamped at the bottom and 25 coils clamped at the upper endCASE 1. Number of coils free for bending Nfree at the vertically free hanging Slinky:1.1) 80 separated coils, 5 unseparated coils at the bottom
end
, 1
coil
clamped
at
the
upper
end
1.2) 70
separated
coils, 5 unseparated coils at the bottom end, 11 coils clamped at the
upper end1.3) 60 separated coils, 5 unseparated coils at the bottom end, 21 coils clamped at
the upper endAnalysed
cases (by mathematical modeling and experimentally testing)
Slide20Properties of the used
Slinky
helixoidal
spring
Total
number of coils: N = 86The out diameter of unstrenched slinky Dout = 68.95 mmThe measured total mass m = 0.2156 kgDimension of cross-section: b x h = 2.50 x 0.50 mmThe total length of Slinky wire L = 18.8293 mThe single coil Slinky’s spring constant (calculated) kc = 75.125 N/m The Slinky spring constant (calculated) Kq =
2.046 N/m
The
Young
modulus
of
steel
E = 2
10
11
PaSteel density = 7800 kg/m3Poisson’s
coefficient = 0.3
Case 1. Free hanging Slinky
Case 2. Slinky with clamped ends
Slide21The measured
mass
of
steel
pendulum
ball mp = 0.03267 kgThe measured diameter of steel pendulum ball dp = 20 mm.The measured length of pendulum string Lp = 0.845 mThe measured distance between pendulum at rest and Slinky Lps = 0.100 mThe measured pendulum oscilation amplitude La = 0.200 mThe calculated velocity of pendulum ball at the impact point v = 0.3395
m/s
The
calculated
forces
of
the
pendulum
impact
Fh = 0.0648 N, Fv =
0.0077 NThe duration of impact between pendulum ball and Slinky, ti = 0.170 sThe kinetic energy of pendulum ball transmitted to the
Slinky Ek= 0.0056 J
Properties of the pendulum
Slide22Table of contents
Slide23Proof
of
acoustic
dispersion
Frequency
(Hz)
Time (s)Sound intensity (dB)Time (s)
Slide24Phase
1.
Intial
disturbance
of the
slinky
wire and decomposition of elastic deformations in a wire segment Phase 3. The waves continue to propagate throughout the Slinky but are almost inaudible due to dampningPhase 2. Resulting bending waves propagate through the Slinky wire, rebounding from it’s ends and forming a modulated
wave
which
is
constantly
dampned
Acoustic
dispersion
takes
place,
resulting in a audible laser shot sound.Phase
4.Silence phase with low frequency oscilations
2
34
The anatomy of typical
sound recorded on Slinky clamped at
both ends Analysis
of experimental results
1
Slide25Phase
1.
Intial
disturbance
of the
slinky
wire and decomposition of elastic deformations in a wire segment Phase 2. Resulting bending waves propagate through the Slinky wire, rebounding from it’s ends and forming a modulated wave which is constantly dampned
Acoustic
dispersion
takes
place,
resulting
in a
audible
laser
shot
sound.
Phase 4.Silence phase with
low frequency oscilations , without impacts between coils and with
Phase 3. Formation of the secondary
(internal) disturbances by impacts last sepparated coils with group of unsepparated coils
or wire holders.
2
1
3
4
The anatomy of typical sound recorded after hits free hanging Slinky Analysis of experimental results
3
4
3
Slide26Time delay
between
higher
and
lower
frequencies
Frequency (Hz)Time (s)
Slide27Dependency of frequency
delay
on
the
number
of
coils
Slide28Table of contents
Slide29The
Slinky
spring
as a
high
fequency
sound source was mathematically modelled using: wave equation for free flexural (F-wave) vibrations of a thin long beam with upper end clamped and bottom end freeRelation
for
acoustic
dipersion
Equation for acoustic pressure at the free space.
The
experiments
qualitatively
confirmed
the theoretical model,
showing
the phenomenom of acoustic dispersion which is visible in
delay time between higher and lower frequencies.Conclusions
Frequency
(Hz)Time (s)
Slide30The
experimental
results
show
a
linear
-like relation between echoes and depedency time as well as frequency delay time and number of coils.Conclusions
Slide31REFERENCES
[1]
P. Gash:
Fundamental Slinky Oscillation Frequency using a
Center
-of-Mass Model
[2]
V. Hen
č-Bartolić, P.Kulušić: Waves and optics, School book, Zagreb, 3rd edition (in Croatian), 2004[3] A. Nilsson, B. Liu: Vibro-Acoustics, Vol.1, Springer-Verlag GmbH, Berlin Heidelberg, 2015[4] F. S. Crafword: Slinky whistlers, Am. J. Phys
. 55(2),
February
1987, p.130-134
[5] F
. S
. Crafword:
Waves
, Berkeley Physics Course, Vol.3, Berkely, 1968
[6] W
. C
.
Elmore
,
M.A. Heald: Physics of waves, McGraw-Hill Book Company, New York,[7] J. G. Guyader: Vibration in continuous media
, ISTE Ltd, London, 2002[8] G. C. King: Vibrations and waves, John Wiley & Sons Ltd, London, 2009[9] Th. D.
Rossing, N. H., Fletcher: Principles of
vibration and sounds, Springer-VerlagNew York, lnc., 2004[10] L.E. Kinsle et.all: Fundamentals of Acoustics, 4th ed., John Willey & Sons, Inc, New York, 2000
[11] M. Géradin, D.J. Rixen: Mechanical
Vibrations: Theory and Application to Structural Dynamics, 3rd ed., John Wiley & Sons, Ltd, Chichester,
2015[12] C.Y. Wang , C.M. Wang:
Structural Vibration - Exact Solutions forStrings, Membranes,Beams, and Plates, CRC PressTaylor & Francis Group, Boca Raton, 2014[13] A.
Brandt: Noise and vibration analysis : signal analysis and experimental procedures, John Wiley & Sons Ltd, Chichester, 2011
Slide32Slide33A sound record in
deaf
room
.
Free
hanging
Slinky with Nfree=75 hits by steel pendulum (hanging on the string 0.6 m long, max. amplitude of pendulum before hit 0.48 m, distance between vertically hanging pendulum and Slinky before impact 0.34 m). Sound analysis /wave form and frequency spectrum conducted in the software Sonic Visualiser.
Sound
waveform
in
the
Phase
1
-
Formation
of an initial (external)
disturbances
Slide34Slide35Sound waveform in
the
Phase
2
-
Decomposition
of elastic deformations
Slide36Slide37Sound
waveform
in
the
Phase 3 – Generation, reflexing (and attenuation ) of bending vibrations
Slide38Slide39Sound waveform in
the
Phase
4
-
Silence
phase
Slide40Sound
waveform
in
the
Phase 5 - Formation of the secondary (internal) disturbances
Slide41Slide42Phase
1.
Formation
of
a
n
initial
(external) disturbances, by impacts or tapping a Slinky wire .Wire material was elastic deformed around impact point. Phase 3. Generation (and attenuation ) of free
bending
vibrations
superposed
with
reflections
of
disturbances
and waves from beam ends, with frequency twinning
and separation
Phase 2. Decomposition of elastic
deformations in a wire segment, with high speed propagation of disturbance over whole
wire length Phase
4.Silence phase with low frequency
oscilations , without impacts between coils
and with Phase 5. Formation of the secondary (internal) disturbances
by impacts last sepparated coils
with group of unsepparated coils or wire holders.
2
1
3
453The anatomy of typical sound recorded after hits free hanging Slinky Analysis of experimental results