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Damping and local control of mirror suspensions for laser interferometric gravitational wave detectors
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10.1063/1.4704459
/content/aip/journal/rsi/83/4/10.1063/1.4704459
http://aip.metastore.ingenta.com/content/aip/journal/rsi/83/4/10.1063/1.4704459

Figures

Image of FIG. 1.
FIG. 1.

Modified rendering of a CAD model of the main elements of an aLIGO quadruple suspension. There are two chains of 4 stages, numbered as shown. One supports the mirror (lowest mass in the front chain), the other provides a quiet platform at each level for actuation. The top 3 stages are supported on springs to improve vertical isolation. Stages 1 and 2 (and stage 3 of the reaction chain) incorporate adjustable/moveable mass to trim and balance the suspension. Stages 3 and 4 of the main chain are formed from fused silica and weigh 40 kg each. The test mass is polished and coated to form a mirror which hangs on 4 fused silica fibers of 0.2 mm radius and 600 mm length, to provide low thermal noise.

Image of FIG. 2.
FIG. 2.

A block diagram of a modal damping scheme for the 4 x modes. An estimator converts the incomplete sensor information into modal signals. The modal signals are then sent to damping filters, one for each DOF. The resulting modal damping forces are brought back into the Euler coordinate system through the transpose of the inverse of the eigenvector matrix Φ. Only stage 1 forces are applied to maximize sensor noise filtering to stage 4. Note that this figure applies to a four DOF system.

Image of FIG. 3.
FIG. 3.

The loop gain transfer function of an example 1 Hz modal oscillator with its damping filter. The plant contributes the large resonant peak and the damping filter contributes the remaining poles and zeros. The 10 Hz notch reduces the sensor noise amplification at the start of the gravitational wave detection band, where it is typically the worst. The large phase margin near the resonance permits tuning of the gain k to achieve a significant range of closed loop Qs. All the damping loops have the same basic shape but are shifted in frequency and gain (the notch remains at the same frequency).

Image of FIG. 4.
FIG. 4.

The components of the cost function Eq. (12) for the x DOF as a function of R calculated by the optimization routine. At each value of R the closed loop system performance is simulated using the estimator design based on the LQR solution with that particular R value.

Image of FIG. 5.
FIG. 5.

An amplitude spectrum showing a simulation of the mirror displacement along the x DOF under the influence of the optimized modal damping loop with R = 0.06. The black dashed line is the sensor noise and the green line is its contribution to the mirror displacement. The solid black line is the ground disturbance and the blue line is its contribution to the mirror displacement. The red line is the uncorrelated stochastic sum of both contributions.

Image of FIG. 6.
FIG. 6.

Complex frequency (s)-plane plot showing the poles × of the closed loop modal damping system. The reference system is represented by the bold (black) symbols, while the 100 trials of perturbed systems are represented by the finer (red) symbols. Each trial represents a system modified from the ideal using the random parameters described in the text. In this test 16% of the cases are unstable.

Image of FIG. 7.
FIG. 7.

Settling times for the four x modes of a quadruple suspension with pure velocity damping of variable strength at stage 1. The lowest mode (1) dominates yielding a shortest settling time of 18 s (to 2%), with damping strength 55 kg/s.

Image of FIG. 8.
FIG. 8.

Open loop Bode plot comparing damping laws for yaw. The damping law, low-pass filter, and mechanical plant are combined. The solid (blue) curves represent the differentiator law, with a suitable low-pass filter. The dashed (green) line shows the truncated differentiator with the pole at 3.5 Hz. The dotted (red) curve represents the interrupted differentiator. Finally the dashed-dotted (cyan) curve shows an example with resonant zeros and poles. The gains are adjusted to match at 10 Hz. Other filter parameters are given in the text.

Image of FIG. 9.
FIG. 9.

The magnitude of the transmissibility from the sensor input to motion of the suspended mirror, in rad/m. The 4 curves correspond to the same 4 control laws as in the previous figure. The “upper-limit” line shows the maximum value allowed for the transmissibility above 10 Hz.

Tables

Generic image for table
Table I.

Noise amplitude spectral density limits for the aLIGO test masses. Upper limits are set a factor of 10 below the intended instrumental noise floor, allowing for cross-coupling to the sensitive direction. Each limit falls as 1/f 2 from 10 Hz to 30 Hz. The interferometer is insensitive to roll, though roll noise can couple into, e.g., x in the mechanical system.

Generic image for table
Table II.

Settling time to 2% resulting from a unit impulse applied to the sensor input of the closed loop system. This is equivalent to the effect of an impulsive motion of the top mass, as observed at the test mass. The interrupted differentiator yields ≈15% quicker settling than the mean of the other methods.

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/content/aip/journal/rsi/83/4/10.1063/1.4704459
2012-04-18
2014-04-17
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752b84549af89a08dbdd7fdb8b9568b5 journal.articlezxybnytfddd
Scitation: Damping and local control of mirror suspensions for laser interferometric gravitational wave detectors
http://aip.metastore.ingenta.com/content/aip/journal/rsi/83/4/10.1063/1.4704459
10.1063/1.4704459
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