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1 S.Gras, MKI Postdoctoral Symposium, 2013
Acoustic Mode Damper For Parametric Instabilities Control
Slawek Gras, MKI, 2013
2
Introduction
S.Gras, MKI Postdoctoral Symposium, 2013
-map spacetime geometry of BH, -study of nonlinear dynamics of space time curvature, -measure of mass and radii of NS, -probe large scale structure .
Great objectives for gravitational wave astrophysics:
L+δL2
L-δL1 12, LLLth
L
L
Detection idea in a nutshell:
λGW = 300 ÷ 30,000 km
Detection bandwidth 10 Hz to 1 kHz
L ~ 4 km, ΔL ~ 10-18 m (proton ~ 10-15 m)
Suspended mirrors act as “freely-falling” test masses
in horizontal plane for frequencies f >> fpend hLL
Relative phase change of the laser beam, λ0 = 10-6 m, manifests as a gravitational wave signal
3
High power interferometer
Courtesy of G. Harry
S.Gras, MKI Postdoctoral Symposium, 2013
c
L
rr
rr
c
LN
2
12
2
21
21
1) Gain phase by increasing number of round trip:
N = 70 : times optically extended
2) Reduce quantum noise above 200 Hz Statistical error arising from photon averaging at the dark port (output)
Eopt = 25 J!!!
Idea of optical cavity:
4
Optical cavity
S.Gras, MKI Postdoctoral Symposium, 2013
nFSRnf l
reso:longitudinal modes (Gaussian beam)
NqpnFSRqpnf t
reso ,,2 :transvers modes
87.04.37 kHzFSR
FSR1
0 m
reso
t
reso
l
reso ffff
Highly possible that some acoustic modes overlap with transverse optical modes: resonance condition
For Advanced LIGO:
Example of modes shapes:
What if modes much in shape and frequency? This leads to Parametric Instability
5
Parametric Instability
Two processes present in the loop: 1. Test mass mechanical mode scatters fundamental mode (pump) into the higher order mode 2. After round trip scattered mode returns to the test mass and couples via radiation pressure into the mechanical mode
Parametric Instability as a feedback loop:
Feed back loop gain (R) describes the dynamic of the system: - Gain > 1 energy is pumped in to the test mass -> positive feed back - > Parametric Instability
S.Gras, MKI Postdoctoral Symposium, 2013
6
PI in Advanced LIGO
Numerical results strongly suggest that parametric instability cannot be ignored. A control scheme need to be design.
Unstable modes can occur in the frequency range 10- 90 kHz.
S.Gras, MKI Postdoctoral Symposium, 2013
Some acoustic modes may become unstable with high probability
Parametric Instability threat: - signal port contamination, - lost of the cavity lock.
7
Parametric gain
Optical power in the arm cavities ~ 830 kW
Test mass Q-factor ~ 10e+7
Overlapping parameter (spatial matching) > 0.01
Detuning parameter (frequency matching) ~ 0
1
hom,
FQPR mmopt
By changing Q-factor of the test masses should be possible to lower R gain at desired frequency range 10 ÷ 90 kHz
S.Gras, MKI Postdoctoral Symposium, 2013
8
Test mass
S.Gras, MKI Postdoctoral Symposium, 2013
Objectives: 1) Mode damping in the frequency range 10-90 kHz. 2) Minimum 10 -fold Q-factor reduction . 3) Negligible thermal noise degradation in 10 – 1000 Hz, negligible = < 1% detector strain degradation.
9
Quality factor
S.Gras, MKI Postdoctoral Symposium, 2013
Q
tA
2exp 0
0
Hzf 200
6Q
noscillatio ofradian per lost energy
storedenergy Q
Strain Stress
10 deg
In lossy materials stress lags strain by φ loss angle.
Dissipation of energy manifests as a decrease of a displacement amplitude.
1
tan
1Q
Q factor, φ loss angle, η loss factor are commonly use to describe dissipation in any mechanical system
10
,
k
k
k
kk
E
E
The loss factor η of the system can be visualized as a weighted of the loss factors of the parts with stored energies as weighted constants.
A highly dissipative element cannot contribute significantly to the total loss factor if it does not participate considerably in the total strain energy.
If a damper is in the form of a resonator, high E can be obtained despite of high loss factor of the damper -> better damping performance.
Damping mechanism
fWdiss 2
By adding a lossy element to the test mass , one can change the effective loss factor of such system.
tan
On the other hand, thermal noise is proportional to the averaged energy dissipation (W). Therefore is required to keep η as low as possible at 10 – 1000 Hz.
f
S.Gras, MKI Postdoctoral Symposium, 2013
diss
TH WfS )(
11
Acoustic mode damper
S.Gras, MKI Postdoctoral Symposium, 2013
The best candidate for a lossy element which can be attached to the test masses is piezo material: - Material properties can be
dynamically controlled,
- Loss factor can be tuned to the desired value,
- Condition , easy to obtain.
f
Hard piezo ceramics has high Q factor (Q > 1000), what leads to small intrinsic energy dissipation in detection bandwidth.
12
σ
σ
σ σ
σ
σ compression bending
shear
Active direction of piezo material
Mode 33 Mode 31 Mode 15
electrode
~ C R,I,C
piezo
external impedence
Careful design of electronic circuit allows controlling piezo element mechanical properties to the desired values.
S.Gras, MKI Postdoctoral Symposium, 2013
13
low R high R
low k
high k
Piezo element loss factor
k – electromechanical coupling coefficient, the intrinsic property of piezo material. Higher k, higher loss available for damping. R – resistor, peak position depends on the resistor value.
S.Gras, MKI Postdoctoral Symposium, 2013
14
Reaction mass
Electrical conductive epoxy
Epoxy
PZT/Piezo crystal
Base
TEST MASS
R (+C,L)
Heat RI2
Acoustic mode damper (AMD)
S.Gras, MKI Postdoctoral Symposium, 2013
15
2.0 mm
2.5 mm
3.0 mm
3.0 mm
2.0
mm
Thermal noise analysis
Piezo element dimenssions: Test Mass: ITM, Piezo manufacturer: Physics Instruments, Q-factor: 2200, k15 = 0.63, R = 250 kΩ, Polarization: perpendicular to the laser beam Base diameter: 120 mm Reaction mass: 1g AMD location: 130 mm from the front face No of AMDs: 1 AMD per TM
Specification:
S.Gras, MKI Postdoctoral Symposium, 2013
16
6 resonant AMD modes available to extract energy from test mass: 12 kHz – 65 kHz
2 x Flag-poles
2 x antiFlag-poles
Compression Rotation
AMD resonances
Fx-mode Fy-mode
aFx-mode aFy-mode
C-mode R-mode
S.Gras, MKI Postdoctoral Symposium, 2013
17
Thermal noise
Finite element modeling is used for thermal noise analysis.
Epoxy
AMD
S.Gras, MKI Postdoctoral Symposium, 2013
18
Shear AMD
at
0.55%
If 2 AMDs per TM expected degradation is ~1.0%
Max. 0.6 % degradation in the range 10 – 1000 Hz.
S.Gras, MKI Postdoctoral Symposium, 2013
19
1- epoxy TM-base (0.04) 2- epoxy base-piezo (0.04) 3- epoxy piezo-RM (0.04) 4- epoxy RM-Resistor (0.04) 5- Base (1e-7) 6- RM (1e-4) 7- Resistor (0.1) 8- Piezo (4.3e-3 at 300Hz)
AMD
i
ii
effE
E
AMD loss budget at 300 Hz
dominant TN source
-
S.Gras, MKI Postdoctoral Symposium, 2013
20
Acoustic mode suppression
S.Gras, MKI Postdoctoral Symposium, 2013
Results show effective mode suppression. Very promising results.
21
Conclusions
1) AMD configuration shows acceptable thermal noise level not exceeding 1% of the detector sensitivity, 2) Better choice of epoxy can further reduce influence of AMD on thermal noise, 4) High Q-factor shear piezo ceramics is the best candidate for AMD, 5) Damping performance suggests that AMD is a very promising candidate for Parametric Instability control.
S.Gras, MKI Postdoctoral Symposium, 2013