From 72676fbe54105fa774e9c4d0369afbec18ea5f8a Mon Sep 17 00:00:00 2001 From: Thomas Dehaeze Date: Fri, 16 Apr 2021 18:28:52 +0200 Subject: [PATCH] Add simscape model and first analysis --- STEPS/B4545A.STEP | 101022 ++++++++++ STEPS/B4545A_bot.STEP | 1097 + STEPS/B4545A_mid.STEP | 359 + STEPS/B4545A_top.STEP | 16385 ++ STEPS/B6090A.STEP | 252616 ++++++++++++++++++++++++ STEPS/B6090A_bot.STEP | 1195 + STEPS/B6090A_mid.STEP | 359 + STEPS/B6090A_top.STEP | 42845 ++++ STEPS/fixation_frame.STEP | 3044 + STEPS/interface_shaker.STEP | 843 + STEPS/modal_shaker.STEP | 887 + STEPS/square_shaker.STEP | 857 + STEPS/square_target.STEP | 696 + STEPS/support_pad.STEP | 1191 + figs/local_to_global_coordinates.pdf | Bin 0 -> 36018 bytes figs/local_to_global_coordinates.png | Bin 0 -> 21833 bytes figs/local_to_global_coordinates.svg | 151 + figs/simscape_vibration_table.pdf | Bin 0 -> 17453 bytes figs/simscape_vibration_table.png | Bin 0 -> 18163 bytes matlab/accelerometer_3d.slx | Bin 0 -> 28223 bytes 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@@ -34,17 +81,44 @@

This report is also available as a pdf.

-
-

1 Introduction

+
+

1 Introduction

+

+This document is divided as follows: +

+
    +
  • Section 2: the experimental setup and all the instrumentation are described
    • +
  • Section 3: the mathematics used to compute the 6DoF motion of a solid body from several inertial sensor is derived
    • +
  • Section 4: a Simscape model of the vibration table is developed
    • +
  • Section 5: the table dynamics is identified and compared with the Simscape model
    • +
+
+
-
+
+

2 Experimental Setup

+
+

+ +

+
+
+

2.1 CAD Model

+
+ +

vibration-table-cad-view.png

Figure 1: CAD View of the vibration table

+
+
-
+
+

2.2 Instrumentation

+
+

Here are the documentation of the equipment used for this vibration table:

@@ -54,32 +128,1148 @@ Here are the documentation of the equipment used for this vibration table:
  • Viscoelastic supports: 810002
  • Spring supports: MV803-12CC
  • Optical Table: B4545A
    • +
  • Triaxial Accelerometer: 356B18
    • +
  • OROS
    • +
    -
    -

    1.1 Suspended table

    -
    +
    +

    2.3 Suspended table

    +
    Dimensions
    450 mm x 450 mm x 60 mm
    Mass
    21.30 kg
    -
    +

    B4545A_Compliance_inLb-780.png

    Figure 2: Compliance of the B4545A optical table

    + +
    +

    2.4 Inertial Sensors

    +
    + + + +++ + + + + + + + + + + + + + + +
    Equipment
    (2x) 1D accelerometer PCB 393B05
    (4x) 3D accelerometer PCB 356B18
    +
    +
    +
    + +
    +

    3 Compute the 6DoF solid body motion from several inertial sensors

    +
    +

    + +

    +

    +Let’s consider a solid body with several accelerometers attached to it (Figure 3). +

    + + +
    +

    local_to_global_coordinates.png +

    +

    Figure 3: Schematic of the measured motions of a solid body

    +
    + +

    +The goal of this section is to see how to compute the acceleration/angular acceleration of the solid body from the accelerations \(\vec{a}_i\) measured by the accelerometers. +

    + +

    +The acceleration/angular acceleration of the solid body is defined as the vector \({}^O\vec{x}\): +

    +\begin{equation} +{}^O\vec{x} = \begin{bmatrix} + \dot{v}_x \\ \dot{v}_y \\ \dot{v}_z \\ \dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +

    +As we want to measure 6dof, we suppose that we have 6 uniaxial acceleremoters (we could use more, but 6 is enough). +The measurement of the individual vectors is defined as the vector \(\vec{a}\): +

    +\begin{equation} +\vec{a} = \begin{bmatrix} + a_1 \\ a_2 \\ a_3 \\ a_4 \\ a_5 \\ a_6 +\end{bmatrix} +\end{equation} + +

    +From the positions and orientations of the acceleremoters (defined in Section 3.1), it is quite straightforward to compute the accelerations measured by the sensors from the acceleration/angular acceleration of the solid body (Section 3.2). +From this, we can easily build a transformation matrix \(M\), such that: +

    +\begin{equation} +\vec{a} = M \cdot {}^O\vec{x} +\end{equation} + +

    +If the matrix is invertible, we can just take the inverse in order to obtain the transformation matrix giving the 6dof acceleration of the solid body from the accelerometer measurements (Section 3.3): +

    +\begin{equation} +{}^O\vec{x} = M^{-1} \cdot \vec{a} +\end{equation} + +

    +If it is not invertible, then it means that it is not possible to compute all 6dof of the solid body from the measurements. +The solution is then to change the location/orientation of some of the accelerometers. +

    +
    +
    +

    3.1 Define accelerometers positions/orientations

    +
    +

    + +Let’s first define the position and orientation of all measured accelerations with respect to a defined frame \(\{O\}\). +

    + +
    +
    Opm = [-0.1875, -0.1875, -0.245;
+       -0.1875, -0.1875, -0.245;
+        0.1875, -0.1875, -0.245;
+        0.1875, -0.1875, -0.245;
+        0.1875,  0.1875, -0.245;
+        0.1875,  0.1875, -0.245]';
+
    +
    + +

    +There are summarized in Table 1. +

    + + + + +++ ++ ++ ++ ++ ++ ++ + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + +
    Table 1: Positions of the accelerometers fixed to the vibration table with respect to \(\{O\}\)
     \(a_1\)\(a_2\)\(a_3\)\(a_4\)\(a_5\)\(a_6\)
    x-0.188-0.1880.1880.1880.1880.188
    y-0.188-0.188-0.188-0.1880.1880.188
    z-0.245-0.245-0.245-0.245-0.245-0.245
    + +

    +We then define the direction of the measured accelerations (unit vectors): +

    +
    +
    Osm = [0, 1, 0;
+       0, 0, 1;
+       1, 0, 0;
+       0, 0, 1;
+       1, 0, 0;
+       0, 0, 1;]';
+
    +
    + +

    +They are summarized in Table 2. +

    + + + + +++ ++ ++ ++ ++ ++ ++ + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + +
    Table 2: Orientations of the accelerometers fixed to the vibration table expressed in \(\{O\}\)
     \(\hat{s}_1\)\(\hat{s}_2\)\(\hat{s}_3\)\(\hat{s}_4\)\(\hat{s}_5\)\(\hat{s}_6\)
    x001010
    y100000
    z010101
    +
    +
    + +
    +

    3.2 Transformation matrix from motion of the solid body to accelerometer measurements

    +
    +

    + +

    + +

    +Let’s try to estimate the x-y-z acceleration of any point of the solid body from the acceleration/angular acceleration of the solid body expressed in \(\{O\}\). +For any point \(p_i\) of the solid body (corresponding to an accelerometer), we can write: +

    +\begin{equation} +\begin{bmatrix} +a_{i,x} \\ a_{i,y} \\ a_{i,z} +\end{bmatrix} = \begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z +\end{bmatrix} + p_i \times \begin{bmatrix} +\dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +

    +We can write the cross product as a matrix product using the skew-symmetric transformation: +

    +\begin{equation} +\begin{bmatrix} +a_{i,x} \\ a_{i,y} \\ a_{i,z} +\end{bmatrix} = \begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z +\end{bmatrix} + \underbrace{\begin{bmatrix} + 0 & p_{i,z} & -p_{i,y} \\ + -p_{i,z} & 0 & p_{i,x} \\ + p_{i,y} & -p_{i,x} & 0 +\end{bmatrix}}_{P_{i,[\times]}} \cdot \begin{bmatrix} +\dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +

    +If we now want to know the (scalar) acceleration \(a_i\) of the point \(p_i\) in the direction of the accelerometer direction \(\hat{s}_i\), we can just project the 3d acceleration on \(\hat{s}_i\): +

    +\begin{equation} +a_i = \hat{s}_i^T \cdot \begin{bmatrix} +a_{i,x} \\ a_{i,y} \\ a_{i,z} +\end{bmatrix} = \hat{s}_i^T \cdot \begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z +\end{bmatrix} + \left( \hat{s}_i^T \cdot P_{i,[\times]} \right) \cdot \begin{bmatrix} +\dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +

    +Which is equivalent as a simple vector multiplication: +

    +\begin{equation} +a_i = \begin{bmatrix} +\hat{s}_i^T & \hat{s}_i^T \cdot P_{i,[\times]} +\end{bmatrix} +\begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z \\ \dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} = \begin{bmatrix} +\hat{s}_i^T & \hat{s}_i^T \cdot P_{i,[\times]} +\end{bmatrix} {}^O\vec{x} +\end{equation} + +

    +And finally we can combine the 6 (line) vectors for the 6 accelerometers to write that in a matrix form. +We obtain Eq. \eqref{eq:M_matrix}. +

    +
    +

    +The transformation from solid body acceleration \({}^O\vec{x}\) from sensor measured acceleration \(\vec{a}\) is: +

    +\begin{equation} \label{eq:M_matrix} +\vec{a} = \underbrace{\begin{bmatrix} +\hat{s}_1^T & \hat{s}_1^T \cdot P_{1,[\times]} \\ +\vdots & \vdots \\ +\hat{s}_6^T & \hat{s}_6^T \cdot P_{6,[\times]} +\end{bmatrix}}_{M} {}^O\vec{x} +\end{equation} + +

    +with \(\hat{s}_i\) the unit vector representing the measured direction of the i’th accelerometer expressed in frame \(\{O\}\) and \(P_{i,[\times]}\) the skew-symmetric matrix representing the cross product of the position of the i’th accelerometer expressed in frame \(\{O\}\). +

    + +
    + +

    +Let’s define such matrix using matlab: +

    +
    +
    M = zeros(length(Opm), 6);
+
+for i = 1:length(Opm)
+    Ri = [0,         Opm(3,i), -Opm(2,i);
+         -Opm(3,i),  0,         Opm(1,i);
+          Opm(2,i), -Opm(1,i),  0];
+    M(i, 1:3) = Osm(:,i)';
+    M(i, 4:6) = Osm(:,i)'*Ri;
+end
+
    +
    + +

    +The obtained matrix is shown in Table 3. +

    + + + + +++ ++ ++ ++ ++ ++ ++ + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + +
    Table 3: Effect of a displacement/rotation on the 6 measurements
     \(\dot{x}_x\)\(\dot{x}_y\)\(\dot{x}_z\)\(\dot{\omega}_x\)\(\dot{\omega}_y\)\(\dot{\omega}_z\)
    \(a_1\)0.01.00.00.240.0-0.19
    \(a_2\)0.00.01.0-0.190.190.0
    \(a_3\)1.00.00.00.0-0.240.19
    \(a_4\)0.00.01.0-0.19-0.190.0
    \(a_5\)1.00.00.00.0-0.24-0.19
    \(a_6\)0.00.01.00.19-0.190.0
    +
    +
    + +
    +

    3.3 Compute the transformation matrix from accelerometer measurement to motion of the solid body

    +
    +

    + +

    + +

    +In order to compute the motion of the solid body \({}^O\vec{x}\) with respect to frame \(\{O\}\) from the accelerometer measurements \(\vec{a}\), we have to inverse the transformation matrix \(M\). +

    +\begin{equation} +{}^O\vec{x} = M^{-1} \vec{a} +\end{equation} + +

    +We therefore need the determinant of \(M\) to be non zero: +

    +
    +
    det(M)
+
    +
    + +

    +The obtained inverse of the matrix is shown in Table 4. +

    + + + + +++ ++ ++ ++ ++ ++ ++ + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + +
    Table 4: Compute the displacement/rotation from the 6 measurements
     \(a_1\)\(a_2\)\(a_3\)\(a_4\)\(a_5\)\(a_6\)
    \(\dot{x}_x\)0.00.70.5-0.70.50.0
    \(\dot{x}_y\)1.00.00.50.7-0.5-0.7
    \(\dot{x}_z\)0.00.50.00.00.00.5
    \(\dot{\omega}_x\)0.00.00.0-2.70.02.7
    \(\dot{\omega}_y\)0.02.70.0-2.70.00.0
    \(\dot{\omega}_z\)0.00.02.70.0-2.70.0
    +
    +
    +
    + +
    +

    4 Simscape Model

    +
    +

    + +

    +

    +In this section, the Simscape model of the vibration table is described. +

    + + +
    +

    simscape_vibration_table.png +

    +

    Figure 4: 3D representation of the simscape model

    +
    +
    +
    +

    4.1 Simscape Sub-systems

    +
    +

    + +

    + +

    +Parameters for sub-components of the simscape model are defined below. +

    +
    + +
    +

    4.1.1 Springs

    +
    +

    + +

    + +

    +The 4 springs supporting the suspended optical table are modelled with “bushing joints” having stiffness and damping in the x-y-z directions: +

    + +
    +
    spring.kx = 1e4; % X- Stiffness [N/m]
+spring.cx = 1e1; % X- Damping [N/(m/s)]
+
+spring.ky = 1e4; % Y- Stiffness [N/m]
+spring.cy = 1e1; % Y- Damping [N/(m/s)]
+
+spring.kz = 1e4; % Z- Stiffness [N/m]
+spring.cz = 1e1; % Z- Damping [N/(m/s)]
+
+spring.z0 = 32e-3; % Equilibrium z-length [m]
+
    +
    +
    +
    + +
    +

    4.1.2 Inertial Shaker (IS20)

    +
    +

    + +

    + +

    +The inertial shaker is defined as two solid bodies: +

    +
      +
    • the “housing” that is fixed to the element that we want to excite
      • +
    • the “inertial mass” that is suspended inside the housing
      • +
    + +

    +The inertial mass is guided inside the housing and an actuator (coil and magnet) can be used to apply a force between the inertial mass and the support. +The “reacting” force on the support is then used as an excitation. +

    + + + + +++ ++ + + + + + + + + + + + + + + + + + + + + + + + + + + + +
    Table 5: Summary of the IS20 datasheet
    CharacteristicValue
    Output Force20 N
    Frequency Range10-3000 Hz
    Moving Mass0.1 kg
    Total Mass0.3 kg
    + +

    +From the datasheet in Table 5, we can estimate the parameters of the physical shaker. +

    + +

    +These parameters are defined below +

    +
    +
    shaker.w0 = 2*pi*10; % Resonance frequency of moving mass [rad/s]
+shaker.m = 0.1; % Moving mass [m]
+shaker.m_tot = 0.3; % Total mass [m]
+shaker.k = shaker.m*shaker.w0^2; % Spring constant [N/m]
+shaker.c = 0.2*sqrt(shaker.k*shaker.m); % Damping [N/(m/s)]
+
    +
    +
    +
    + +
    +

    4.1.3 3D accelerometer (356B18)

    +
    +

    + +

    + +

    +An accelerometer consists of 2 solids: +

    +
      +
    • a “housing” rigidly fixed to the measured body
      • +
    • an “inertial mass” suspended inside the housing by springs and guided in the measured direction
      • +
    + +

    +The relative motion between the housing and the inertial mass gives a measurement of the acceleration of the measured body (up to the suspension mode of the inertial mass). +

    + + + + +++ ++ + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + +
    Table 6: Summary of the 356B18 datasheet
    CharacteristicValue
    Sensitivity0.102 V/(m/s2)
    Frequency Range0.5 to 3000 Hz
    Resonance Frequency> 20 kHz
    Resolution0.0005 m/s2 rms
    Weight0.025 kg
    Size20.3x26.1x20.3 [mm]
    + +

    +Here are defined the parameters for the triaxial accelerometer: +

    +
    +
    acc_3d.m = 0.005; % Inertial mass [kg]
+acc_3d.m_tot = 0.025; % Total mass [m]
+
+acc_3d.w0 = 2*pi*20e3; % Resonance frequency [rad/s]
+
+acc_3d.kx = acc_3d.m*acc_3d.w0^2; % Spring constant [N/m]
+acc_3d.ky = acc_3d.m*acc_3d.w0^2; % Spring constant [N/m]
+acc_3d.kz = acc_3d.m*acc_3d.w0^2; % Spring constant [N/m]
+
+acc_3d.cx = 1e2; % Damping [N/(m/s)]
+acc_3d.cy = 1e2; % Damping [N/(m/s)]
+acc_3d.cz = 1e2; % Damping [N/(m/s)]
+
    +
    + +

    +DC gain between support acceleration and inertial mass displacement is \(-m/k\): +

    +
    +
    acc_3d.g_x = 1/(-acc_3d.m/acc_3d.kx); % [m/s^2/m]
+acc_3d.g_y = 1/(-acc_3d.m/acc_3d.ky); % [m/s^2/m]
+acc_3d.g_z = 1/(-acc_3d.m/acc_3d.kz); % [m/s^2/m]
+
    +
    + +

    +We also define the sensitivity in order to have the outputs in volts. +

    +
    +
    acc_3d.gV_x = 0.102; % [V/(m/s^2)]
+acc_3d.gV_y = 0.102; % [V/(m/s^2)]
+acc_3d.gV_z = 0.102; % [V/(m/s^2)]
+
    +
    + +

    +The problem with using such model for accelerometers is that this adds states to the identified models (2x3 states for each triaxial accelerometer). +These states represents the dynamics of the suspended inertial mass. +In the frequency band of interest (few Hz up to ~1 kHz), the dynamics of the inertial mass can be ignore (its resonance is way above 1kHz). +Therefore, we might as well use idealized “transform sensors” blocks as they will give the same result up to ~20kHz while allowing to reduce the number of identified states. +

    + +

    +The accelerometer model can be chosen by setting the type property: +

    +
    +
    acc_3d.type = 2; % 1: inertial mass, 2: perfect
+
    +
    +
    +
    +
    + +
    +

    4.2 Identification

    +
    +

    + +

    +
    + +
    +

    4.2.1 Number of states

    +
    +

    +Let’s first use perfect 3d accelerometers: +

    +
    +
    acc_3d.type = 2; % 1: inertial mass, 2: perfect
+
    +
    + +

    +And identify the dynamics from the shaker force to the measured accelerations: +

    +
    +
    %% Name of the Simulink File
+mdl = 'vibration_table';
+
+%% Input/Output definition
+clear io; io_i = 1;
+io(io_i) = linio([mdl, '/F'],  1, 'openinput');  io_i = io_i + 1;
+io(io_i) = linio([mdl, '/acc'],  1, 'openoutput'); io_i = io_i + 1;
+
+%% Run the linearization
+Gp = linearize(mdl, io);
+Gp.InputName  = {'F'};
+Gp.OutputName  = {'a1', 'a2', 'a3', 'a4', 'a5', 'a6'};
+
    +
    + +
    +size(Gp)
+State-space model with 6 outputs, 1 inputs, and 12 states.
+
    + + +

    +We indeed have the 12 states corresponding to the 6 DoF of the suspended optical table. +

    + +

    +Let’s now consider the inertial masses for the triaxial accelerometers: +

    +
    +
    acc_3d.type = 1; % 1: inertial mass, 2: perfect
+
    +
    + +
    +
    %% Name of the Simulink File
+mdl = 'vibration_table';
+
+%% Input/Output definition
+clear io; io_i = 1;
+io(io_i) = linio([mdl, '/F'],  1, 'openinput');  io_i = io_i + 1;
+io(io_i) = linio([mdl, '/acc'],  1, 'openoutput'); io_i = io_i + 1;
+
+%% Run the linearization
+Ga = linearize(mdl, io);
+Ga.InputName  = {'F'};
+Ga.OutputName  = {'a1', 'a2', 'a3', 'a4', 'a5', 'a6'};
+
    +
    + +
    +size(Ga)
+State-space model with 6 outputs, 1 inputs, and 30 states.
+
    + + +

    +And we can see that 18 states have been added. +This corresponds to 6 states for each triaxial accelerometers. +

    +
    +
    + +
    +

    4.2.2 Resonance frequencies and mode shapes

    +
    +

    +Let’s now identify the resonance frequency and mode shapes associated with the suspension modes of the optical table. +

    + +
    +
    acc_3d.type = 2; % 1: inertial mass, 2: perfect
+
+%% Name of the Simulink File
+mdl = 'vibration_table';
+
+%% Input/Output definition
+clear io; io_i = 1;
+io(io_i) = linio([mdl, '/F'],      1, 'openinput');  io_i = io_i + 1;
+io(io_i) = linio([mdl, '/acc_O'],  1, 'openoutput'); io_i = io_i + 1;
+
+%% Run the linearization
+G = linearize(mdl, io);
+G.InputName  = {'F'};
+G.OutputName  = {'ax', 'ay', 'az', 'wx', 'wy', 'wz'};
+
    +
    + +

    +Compute the resonance frequencies +

    +
    +
    ws = eig(G.A);
+ws = ws(imag(ws) > 0);
+
    +
    + +

    +And the associated response of the optical table +

    +
    +
    x_mod = zeros(6, 6);
+
+for i = 1:length(ws)
+    xi = evalfr(G, ws(i));
+    x_mod(:,i) = xi./norm(xi);
+end
+
    +
    + +

    +The results are shown in Table 7. +The motion associated to the mode shapes are just indicative. +

    + + + + +++ ++ ++ ++ ++ ++ ++ + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + + +
    Table 7: Resonance frequency and approximation of the mode shapes
    \(\omega_0\) [Hz]5.65.65.78.28.28.2
    x0.10.70.00.00.20.0
    y0.70.10.00.00.00.2
    z0.00.01.00.00.00.0
    Rx0.70.10.00.00.11.0
    Ry0.10.70.00.01.00.1
    Rz0.00.00.01.00.00.0
    +
    +
    +
    + +
    +

    4.3 Verify transformation

    +
    +
    +
    %% Options for Linearized
+options = linearizeOptions;
+options.SampleTime = 0;
+
+%% Name of the Simulink File
+mdl = 'vibration_table';
+
+%% Input/Output definition
+clear io; io_i = 1;
+io(io_i) = linio([mdl, '/F'],  1, 'openinput');  io_i = io_i + 1;
+io(io_i) = linio([mdl, '/acc'],  1, 'openoutput'); io_i = io_i + 1;
+io(io_i) = linio([mdl, '/Absolute_Accelerometer'],  1, 'openoutput'); io_i = io_i + 1;
+
+%% Run the linearization
+G = linearize(mdl, io, 0.0, options);
+G.InputName  = {'F'};
+G.OutputName = {'a1', 'a2', 'a3', 'a4', 'a5', 'a6', ...
+                'Dx', 'Dy', 'Dz', 'Rx', 'Ry', 'Rz'};
+
    +
    + +
    +
    G_acc = inv(M)*G(1:6, 1);
+G_id = G(7:12, 1);
+
    +
    + +
    +
    bodeFig({G_acc(1), G_id(1)})
+bodeFig({G_acc(2), G_id(2)})
+bodeFig({G_acc(3), G_id(3)})
+bodeFig({G_acc(4), G_id(4)})
+bodeFig({G_acc(5), G_id(5)})
+bodeFig({G_acc(6), G_id(6)})
+
    +
    +
    +
    +
    + +
    +

    5 Identification of the table’s dynamics

    +
    +

    + +

    +

    Author: Dehaeze Thomas

    -

    Created: 2021-04-08 jeu. 11:44

    +

    Created: 2021-04-16 ven. 18:28

    diff --git a/vibration-table.org b/vibration-table.org index d0afbda..38e7481 100644 --- a/vibration-table.org +++ b/vibration-table.org @@ -50,11 +50,24 @@ * Introduction +This document is divided as follows: +- Section [[sec:experimental_setup]]: the experimental setup and all the instrumentation are described +- Section [[sec:meas_transformation]]: the mathematics used to compute the 6DoF motion of a solid body from several inertial sensor is derived +- Section [[sec:simscape_model]]: a Simscape model of the vibration table is developed +- Section [[sec:table_dynamics]]: the table dynamics is identified and compared with the Simscape model + +* Experimental Setup +<> +** Introduction :ignore: +** CAD Model + #+name: fig:vibration-table-cad-view #+caption: CAD View of the vibration table #+attr_latex: :width 0.8\linewidth [[file:figs/vibration-table-cad-view.png]] +** Instrumentation + #+begin_note Here are the documentation of the equipment used for this vibration table: - Modal Shaker: Watson and Gearing @@ -62,6 +75,8 @@ Here are the documentation of the equipment used for this vibration table: - Viscoelastic supports: [[file:doc/810002_doc.pdf][810002]] - Spring supports: [[file:doc/9129fcb6ec46bb52925bb16155a850f3be01c479.pdf][MV803-12CC]] - Optical Table: [[https://www.thorlabs.com/thorproduct.cfm?partnumber=B4545A][B4545A]] +- Triaxial Accelerometer: [[https://www.pcb.com/products?model=356b18][356B18]] +- OROS #+end_note ** Suspended table @@ -74,5 +89,616 @@ Here are the documentation of the equipment used for this vibration table: #+attr_latex: :width 0.8\linewidth [[file:figs/B4545A_Compliance_inLb-780.png]] +** Inertial Sensors + +| Equipment | +|----------------------------------| +| (2x) 1D accelerometer [[https://www.pcbpiezotronics.fr/produit/accelerometre/393b05/][PCB 393B05]] | +| (4x) 3D accelerometer [[https://www.pcbpiezotronics.fr/produit/accelerometres/356b18/][PCB 356B18]] | + +* Compute the 6DoF solid body motion from several inertial sensors +<> +** Introduction :ignore: +Let's consider a solid body with several accelerometers attached to it (Figure [[fig:local_to_global_coordinates]]). + +#+begin_src latex :file local_to_global_coordinates.pdf :post pdf2svg(file=*this*, ext="png") :exports results +\newcommand\irregularcircle[2]{% radius, irregularity + \pgfextra {\pgfmathsetmacro\len{(#1)+rand*(#2)}} + +(0:\len pt) + \foreach \a in {10,20,...,350}{ + \pgfextra {\pgfmathsetmacro\len{(#1)+rand*(#2)}} + -- +(\a:\len pt) + } -- cycle +} +\begin{tikzpicture} + \draw[rounded corners=1mm, fill=blue!30!white] (0, 0) \irregularcircle{3cm}{1mm}; + + \node[] (origin) at (0, 0) {$\bullet$}; + \begin{scope}[shift={(origin)}] + \def\axissize{0.8cm} + \draw[->] (0, 0) -- ++(\axissize, 0) node[above left]{$x$}; + \draw[->] (0, 0) -- ++(0, \axissize) node[below right]{$y$}; + \draw[fill, color=black] (0, 0) circle (0.05*\axissize); + \node[draw, circle, inner sep=0pt, minimum size=0.4*\axissize, label=left:$z$] (yaxis) at (0, 0){}; + \node[below right] at (0, 0){$\{O\}$}; + \end{scope} + + \coordinate[] (p1) at (-1.5, -1.5); + \coordinate[] (p2) at (-1.5, -1.5); + \coordinate[] (p3) at ( 1.5, -1.5); + \coordinate[] (p4) at ( 1.5, -1.5); + \coordinate[] (p5) at ( 1.5, 1.5); + \coordinate[] (p6) at ( 1.5, 1.5); + + \draw[->] (p1)node[]{$\bullet$} -- ++(0, 1)node[right]{$a_1$}; + \node[draw, circle, inner sep=0pt, minimum size=0.3cm, label=left:$a_2$] at (p2){}; + \draw[fill, color=black] (p2) circle (0.05); + \draw[->] (p3)node[]{$\bullet$} -- ++(1, 0)node[right]{$a_3$}; + \node[draw, circle, inner sep=0pt, minimum size=0.3cm, label=left:$a_4$] at (p4){}; + \draw[fill, color=black] (p4) circle (0.05); + \draw[->] (p5)node[]{$\bullet$} -- ++(1, 0)node[right]{$a_5$}; + \node[draw, circle, inner sep=0pt, minimum size=0.3cm, label=left:$a_6$] at (p6){}; + \draw[fill, color=black] (p6) circle (0.04); +\end{tikzpicture} +#+end_src + +#+name: fig:local_to_global_coordinates +#+caption: Schematic of the measured motions of a solid body +#+RESULTS: +[[file:figs/local_to_global_coordinates.png]] + +The goal of this section is to see how to compute the acceleration/angular acceleration of the solid body from the accelerations $\vec{a}_i$ measured by the accelerometers. + +The acceleration/angular acceleration of the solid body is defined as the vector ${}^O\vec{x}$: +\begin{equation} +{}^O\vec{x} = \begin{bmatrix} + \dot{v}_x \\ \dot{v}_y \\ \dot{v}_z \\ \dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +As we want to measure 6dof, we suppose that we have 6 uniaxial acceleremoters (we could use more, but 6 is enough). +The measurement of the individual vectors is defined as the vector $\vec{a}$: +\begin{equation} +\vec{a} = \begin{bmatrix} + a_1 \\ a_2 \\ a_3 \\ a_4 \\ a_5 \\ a_6 +\end{bmatrix} +\end{equation} + +From the positions and orientations of the acceleremoters (defined in Section [[sec:accelerometer_pos]]), it is quite straightforward to compute the accelerations measured by the sensors from the acceleration/angular acceleration of the solid body (Section [[sec:transformation_motion_to_acc]]). +From this, we can easily build a transformation matrix $M$, such that: +\begin{equation} +\vec{a} = M \cdot {}^O\vec{x} +\end{equation} + +If the matrix is invertible, we can just take the inverse in order to obtain the transformation matrix giving the 6dof acceleration of the solid body from the accelerometer measurements (Section [[sec:transformation_acc_to_motion]]): +\begin{equation} +{}^O\vec{x} = M^{-1} \cdot \vec{a} +\end{equation} + +If it is not invertible, then it means that it is not possible to compute all 6dof of the solid body from the measurements. +The solution is then to change the location/orientation of some of the accelerometers. + +** Matlab Init :noexport:ignore: +#+begin_src matlab :tangle no :exports none :results silent :noweb yes :var current_dir=(file-name-directory buffer-file-name) +<> +#+end_src + +#+begin_src matlab :exports none :results silent :noweb yes +<> +#+end_src + +#+begin_src matlab :tangle no +addpath('matlab/') +#+end_src + +** Define accelerometers positions/orientations +<> +Let's first define the position and orientation of all measured accelerations with respect to a defined frame $\{O\}$. + +#+begin_src matlab +Opm = [-0.1875, -0.1875, -0.245; + -0.1875, -0.1875, -0.245; + 0.1875, -0.1875, -0.245; + 0.1875, -0.1875, -0.245; + 0.1875, 0.1875, -0.245; + 0.1875, 0.1875, -0.245]'; +#+end_src + +There are summarized in Table [[tab:accelerometers_table_positions]]. + +#+begin_src matlab :exports results :results value table replace :tangle no :post addhdr(*this*) +data2orgtable(Opm, {'x', 'y', 'z'}, {'$a_1$', '$a_2$', '$a_3$', '$a_4$', '$a_5$', '$a_6$'}, ' %.3f '); +#+end_src + +#+name: tab:accelerometers_table_positions +#+caption: Positions of the accelerometers fixed to the vibration table with respect to $\{O\}$ +#+attr_latex: :environment tabularx :width 0.55\linewidth :align Xcccccc +#+attr_latex: :center t :booktabs t :float t +#+RESULTS: +| | $a_1$ | $a_2$ | $a_3$ | $a_4$ | $a_5$ | $a_6$ | +|---+--------+--------+--------+--------+--------+--------| +| x | -0.188 | -0.188 | 0.188 | 0.188 | 0.188 | 0.188 | +| y | -0.188 | -0.188 | -0.188 | -0.188 | 0.188 | 0.188 | +| z | -0.245 | -0.245 | -0.245 | -0.245 | -0.245 | -0.245 | + +We then define the direction of the measured accelerations (unit vectors): +#+begin_src matlab +Osm = [0, 1, 0; + 0, 0, 1; + 1, 0, 0; + 0, 0, 1; + 1, 0, 0; + 0, 0, 1;]'; +#+end_src + +They are summarized in Table [[tab:accelerometers_table_orientations]]. + +#+begin_src matlab :exports results :results value table replace :tangle no :post addhdr(*this*) +data2orgtable(Osm, {'x', 'y', 'z'}, {'$\hat{s}_1$', '$\hat{s}_2$', '$\hat{s}_3$', '$\hat{s}_4$', '$\hat{s}_5$', '$\hat{s}_6$'}, ' %.0f '); +#+end_src + +#+name: tab:accelerometers_table_orientations +#+caption: Orientations of the accelerometers fixed to the vibration table expressed in $\{O\}$ +#+attr_latex: :environment tabularx :width 0.35\linewidth :align Xcccccc +#+attr_latex: :center t :booktabs t :float t +#+RESULTS: +| | $\hat{s}_1$ | $\hat{s}_2$ | $\hat{s}_3$ | $\hat{s}_4$ | $\hat{s}_5$ | $\hat{s}_6$ | +|---+-------------+-------------+-------------+-------------+-------------+-------------| +| x | 0 | 0 | 1 | 0 | 1 | 0 | +| y | 1 | 0 | 0 | 0 | 0 | 0 | +| z | 0 | 1 | 0 | 1 | 0 | 1 | + +** Transformation matrix from motion of the solid body to accelerometer measurements +<> + +Let's try to estimate the x-y-z acceleration of any point of the solid body from the acceleration/angular acceleration of the solid body expressed in $\{O\}$. +For any point $p_i$ of the solid body (corresponding to an accelerometer), we can write: +\begin{equation} +\begin{bmatrix} +a_{i,x} \\ a_{i,y} \\ a_{i,z} +\end{bmatrix} = \begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z +\end{bmatrix} + p_i \times \begin{bmatrix} +\dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +We can write the cross product as a matrix product using the skew-symmetric transformation: +\begin{equation} +\begin{bmatrix} +a_{i,x} \\ a_{i,y} \\ a_{i,z} +\end{bmatrix} = \begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z +\end{bmatrix} + \underbrace{\begin{bmatrix} + 0 & p_{i,z} & -p_{i,y} \\ + -p_{i,z} & 0 & p_{i,x} \\ + p_{i,y} & -p_{i,x} & 0 +\end{bmatrix}}_{P_{i,[\times]}} \cdot \begin{bmatrix} +\dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +If we now want to know the (scalar) acceleration $a_i$ of the point $p_i$ in the direction of the accelerometer direction $\hat{s}_i$, we can just project the 3d acceleration on $\hat{s}_i$: +\begin{equation} +a_i = \hat{s}_i^T \cdot \begin{bmatrix} +a_{i,x} \\ a_{i,y} \\ a_{i,z} +\end{bmatrix} = \hat{s}_i^T \cdot \begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z +\end{bmatrix} + \left( \hat{s}_i^T \cdot P_{i,[\times]} \right) \cdot \begin{bmatrix} +\dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} +\end{equation} + +Which is equivalent as a simple vector multiplication: +\begin{equation} +a_i = \begin{bmatrix} +\hat{s}_i^T & \hat{s}_i^T \cdot P_{i,[\times]} +\end{bmatrix} +\begin{bmatrix} +\dot{v}_x \\ \dot{v}_y \\ \dot{v}_z \\ \dot{\omega}_x \\ \dot{\omega}_y \\ \dot{\omega}_z +\end{bmatrix} = \begin{bmatrix} +\hat{s}_i^T & \hat{s}_i^T \cdot P_{i,[\times]} +\end{bmatrix} {}^O\vec{x} +\end{equation} + +And finally we can combine the 6 (line) vectors for the 6 accelerometers to write that in a matrix form. +We obtain Eq. eqref:eq:M_matrix. +#+begin_important +The transformation from solid body acceleration ${}^O\vec{x}$ from sensor measured acceleration $\vec{a}$ is: +\begin{equation} \label{eq:M_matrix} +\vec{a} = \underbrace{\begin{bmatrix} +\hat{s}_1^T & \hat{s}_1^T \cdot P_{1,[\times]} \\ +\vdots & \vdots \\ +\hat{s}_6^T & \hat{s}_6^T \cdot P_{6,[\times]} +\end{bmatrix}}_{M} {}^O\vec{x} +\end{equation} + +with $\hat{s}_i$ the unit vector representing the measured direction of the i'th accelerometer expressed in frame $\{O\}$ and $P_{i,[\times]}$ the skew-symmetric matrix representing the cross product of the position of the i'th accelerometer expressed in frame $\{O\}$. +#+end_important + +Let's define such matrix using matlab: +#+begin_src matlab +M = zeros(length(Opm), 6); + +for i = 1:length(Opm) + Ri = [0, Opm(3,i), -Opm(2,i); + -Opm(3,i), 0, Opm(1,i); + Opm(2,i), -Opm(1,i), 0]; + M(i, 1:3) = Osm(:,i)'; + M(i, 4:6) = Osm(:,i)'*Ri; +end +#+end_src + +The obtained matrix is shown in Table [[tab:effect_motion_on_meas]]. + +#+begin_src matlab :exports results :results value table replace :tangle no :post addhdr(*this*) +data2orgtable(M, {'$a_1$', '$a_2$', '$a_3$', '$a_4$', '$a_5$', '$a_6$'}, {'$\dot{x}_x$', '$\dot{x}_y$', '$\dot{x}_z$', '$\dot{\omega}_x$', '$\dot{\omega}_y$', '$\dot{\omega}_z$'}, ' %.2f '); +#+end_src + +#+name: tab:effect_motion_on_meas +#+caption: Effect of a displacement/rotation on the 6 measurements +#+attr_latex: :environment tabularx :width 0.45\linewidth :align Xcccccc +#+attr_latex: :center t :booktabs t :float t +#+RESULTS: +| | $\dot{x}_x$ | $\dot{x}_y$ | $\dot{x}_z$ | $\dot{\omega}_x$ | $\dot{\omega}_y$ | $\dot{\omega}_z$ | +|-------+-------------+-------------+-------------+------------------+------------------+------------------| +| $a_1$ | 0.0 | 1.0 | 0.0 | 0.24 | 0.0 | -0.19 | +| $a_2$ | 0.0 | 0.0 | 1.0 | -0.19 | 0.19 | 0.0 | +| $a_3$ | 1.0 | 0.0 | 0.0 | 0.0 | -0.24 | 0.19 | +| $a_4$ | 0.0 | 0.0 | 1.0 | -0.19 | -0.19 | 0.0 | +| $a_5$ | 1.0 | 0.0 | 0.0 | 0.0 | -0.24 | -0.19 | +| $a_6$ | 0.0 | 0.0 | 1.0 | 0.19 | -0.19 | 0.0 | + +** Compute the transformation matrix from accelerometer measurement to motion of the solid body +<> + +In order to compute the motion of the solid body ${}^O\vec{x}$ with respect to frame $\{O\}$ from the accelerometer measurements $\vec{a}$, we have to inverse the transformation matrix $M$. +\begin{equation} +{}^O\vec{x} = M^{-1} \vec{a} +\end{equation} + +We therefore need the determinant of $M$ to be non zero: +#+begin_src matlab :results value replace :exports both :tangle no +det(M) +#+end_src + +The obtained inverse of the matrix is shown in Table [[tab:compute_motion_from_meas]]. + +#+begin_src matlab :exports results :results value table replace :tangle no :post addhdr(*this*) +data2orgtable(inv(M), {'$\dot{x}_x$', '$\dot{x}_y$', '$\dot{x}_z$', '$\dot{\omega}_x$', '$\dot{\omega}_y$', '$\dot{\omega}_z$'}, {'$a_1$', '$a_2$', '$a_3$', '$a_4$', '$a_5$', '$a_6$'}, ' %.1f '); +#+end_src + +#+name: tab:compute_motion_from_meas +#+caption: Compute the displacement/rotation from the 6 measurements +#+attr_latex: :environment tabularx :width 0.45\linewidth :align Xcccccc +#+attr_latex: :center t :booktabs t :float t +#+RESULTS: +| | $a_1$ | $a_2$ | $a_3$ | $a_4$ | $a_5$ | $a_6$ | +|------------------+-------+-------+-------+-------+-------+-------| +| $\dot{x}_x$ | 0.0 | 0.7 | 0.5 | -0.7 | 0.5 | 0.0 | +| $\dot{x}_y$ | 1.0 | 0.0 | 0.5 | 0.7 | -0.5 | -0.7 | +| $\dot{x}_z$ | 0.0 | 0.5 | 0.0 | 0.0 | 0.0 | 0.5 | +| $\dot{\omega}_x$ | 0.0 | 0.0 | 0.0 | -2.7 | 0.0 | 2.7 | +| $\dot{\omega}_y$ | 0.0 | 2.7 | 0.0 | -2.7 | 0.0 | 0.0 | +| $\dot{\omega}_z$ | 0.0 | 0.0 | 2.7 | 0.0 | -2.7 | 0.0 | + +* Simscape Model +<> +** Introduction :ignore: +In this section, the Simscape model of the vibration table is described. + +#+name: fig:simscape_vibration_table +#+caption: 3D representation of the simscape model +#+attr_latex: :width 0.8\linewidth +[[file:figs/simscape_vibration_table.png]] + +** Matlab Init :noexport:ignore: +#+begin_src matlab :tangle no :exports none :results silent :noweb yes :var current_dir=(file-name-directory buffer-file-name) +<> +#+end_src + +#+begin_src matlab :exports none :results silent :noweb yes +<> +#+end_src + +#+begin_src matlab :tangle no +addpath('matlab/') +#+end_src + +#+begin_src matlab +open('vibration_table.slx') +#+end_src + +** Simscape Sub-systems +<> + +Parameters for sub-components of the simscape model are defined below. + +*** Springs +<> + +The 4 springs supporting the suspended optical table are modelled with "bushing joints" having stiffness and damping in the x-y-z directions: + +#+begin_src matlab +spring.kx = 1e4; % X- Stiffness [N/m] +spring.cx = 1e1; % X- Damping [N/(m/s)] + +spring.ky = 1e4; % Y- Stiffness [N/m] +spring.cy = 1e1; % Y- Damping [N/(m/s)] + +spring.kz = 1e4; % Z- Stiffness [N/m] +spring.cz = 1e1; % Z- Damping [N/(m/s)] + +spring.z0 = 32e-3; % Equilibrium z-length [m] +#+end_src + +*** Inertial Shaker (IS20) +<> + +The inertial shaker is defined as two solid bodies: +- the "housing" that is fixed to the element that we want to excite +- the "inertial mass" that is suspended inside the housing + +The inertial mass is guided inside the housing and an actuator (coil and magnet) can be used to apply a force between the inertial mass and the support. +The "reacting" force on the support is then used as an excitation. + +#+name: tab:is20_characteristics +#+caption: Summary of the IS20 datasheet +#+attr_latex: :environment tabularx :width 0.4\linewidth :align lX +#+attr_latex: :center t :booktabs t :float t +| Characteristic | Value | +|-----------------+------------| +| Output Force | 20 N | +| Frequency Range | 10-3000 Hz | +| Moving Mass | 0.1 kg | +| Total Mass | 0.3 kg | + +From the datasheet in Table [[tab:is20_characteristics]], we can estimate the parameters of the physical shaker. + +These parameters are defined below +#+begin_src matlab +shaker.w0 = 2*pi*10; % Resonance frequency of moving mass [rad/s] +shaker.m = 0.1; % Moving mass [m] +shaker.m_tot = 0.3; % Total mass [m] +shaker.k = shaker.m*shaker.w0^2; % Spring constant [N/m] +shaker.c = 0.2*sqrt(shaker.k*shaker.m); % Damping [N/(m/s)] +#+end_src + +*** 3D accelerometer (356B18) +<> + +An accelerometer consists of 2 solids: +- a "housing" rigidly fixed to the measured body +- an "inertial mass" suspended inside the housing by springs and guided in the measured direction + +The relative motion between the housing and the inertial mass gives a measurement of the acceleration of the measured body (up to the suspension mode of the inertial mass). + +#+name: tab:356b18_characteristics +#+caption: Summary of the 356B18 datasheet +#+attr_latex: :environment tabularx :width 0.5\linewidth :align lX +#+attr_latex: :center t :booktabs t :float t +| Characteristic | Value | +|---------------------+---------------------| +| Sensitivity | 0.102 V/(m/s2) | +| Frequency Range | 0.5 to 3000 Hz | +| Resonance Frequency | > 20 kHz | +| Resolution | 0.0005 m/s2 rms | +| Weight | 0.025 kg | +| Size | 20.3x26.1x20.3 [mm] | + +Here are defined the parameters for the triaxial accelerometer: +#+begin_src matlab +acc_3d.m = 0.005; % Inertial mass [kg] +acc_3d.m_tot = 0.025; % Total mass [m] + +acc_3d.w0 = 2*pi*20e3; % Resonance frequency [rad/s] + +acc_3d.kx = acc_3d.m*acc_3d.w0^2; % Spring constant [N/m] +acc_3d.ky = acc_3d.m*acc_3d.w0^2; % Spring constant [N/m] +acc_3d.kz = acc_3d.m*acc_3d.w0^2; % Spring constant [N/m] + +acc_3d.cx = 1e2; % Damping [N/(m/s)] +acc_3d.cy = 1e2; % Damping [N/(m/s)] +acc_3d.cz = 1e2; % Damping [N/(m/s)] +#+end_src + +DC gain between support acceleration and inertial mass displacement is $-m/k$: +#+begin_src matlab +acc_3d.g_x = 1/(-acc_3d.m/acc_3d.kx); % [m/s^2/m] +acc_3d.g_y = 1/(-acc_3d.m/acc_3d.ky); % [m/s^2/m] +acc_3d.g_z = 1/(-acc_3d.m/acc_3d.kz); % [m/s^2/m] +#+end_src + +We also define the sensitivity in order to have the outputs in volts. +#+begin_src matlab +acc_3d.gV_x = 0.102; % [V/(m/s^2)] +acc_3d.gV_y = 0.102; % [V/(m/s^2)] +acc_3d.gV_z = 0.102; % [V/(m/s^2)] +#+end_src + +The problem with using such model for accelerometers is that this adds states to the identified models (2x3 states for each triaxial accelerometer). +These states represents the dynamics of the suspended inertial mass. +In the frequency band of interest (few Hz up to ~1 kHz), the dynamics of the inertial mass can be ignore (its resonance is way above 1kHz). +Therefore, we might as well use idealized "transform sensors" blocks as they will give the same result up to ~20kHz while allowing to reduce the number of identified states. + +The accelerometer model can be chosen by setting the =type= property: +#+begin_src matlab +acc_3d.type = 2; % 1: inertial mass, 2: perfect +#+end_src + +** Identification +<> + +*** Number of states +Let's first use perfect 3d accelerometers: +#+begin_src matlab +acc_3d.type = 2; % 1: inertial mass, 2: perfect +#+end_src + +And identify the dynamics from the shaker force to the measured accelerations: +#+begin_src matlab +%% Name of the Simulink File +mdl = 'vibration_table'; + +%% Input/Output definition +clear io; io_i = 1; +io(io_i) = linio([mdl, '/F'], 1, 'openinput'); io_i = io_i + 1; +io(io_i) = linio([mdl, '/acc'], 1, 'openoutput'); io_i = io_i + 1; + +%% Run the linearization +Gp = linearize(mdl, io); +Gp.InputName = {'F'}; +Gp.OutputName = {'a1', 'a2', 'a3', 'a4', 'a5', 'a6'}; +#+end_src + +#+begin_src matlab :results output replace :exports results :tangle no +size(Gp) +#+end_src + +#+RESULTS: +: size(Gp) +: State-space model with 6 outputs, 1 inputs, and 12 states. + +We indeed have the 12 states corresponding to the 6 DoF of the suspended optical table. + +Let's now consider the inertial masses for the triaxial accelerometers: +#+begin_src matlab +acc_3d.type = 1; % 1: inertial mass, 2: perfect +#+end_src + +#+begin_src matlab +%% Name of the Simulink File +mdl = 'vibration_table'; + +%% Input/Output definition +clear io; io_i = 1; +io(io_i) = linio([mdl, '/F'], 1, 'openinput'); io_i = io_i + 1; +io(io_i) = linio([mdl, '/acc'], 1, 'openoutput'); io_i = io_i + 1; + +%% Run the linearization +Ga = linearize(mdl, io); +Ga.InputName = {'F'}; +Ga.OutputName = {'a1', 'a2', 'a3', 'a4', 'a5', 'a6'}; +#+end_src + +#+begin_src matlab :results output replace :exports results :tangle no +size(Ga) +#+end_src + +#+RESULTS: +: size(Ga) +: State-space model with 6 outputs, 1 inputs, and 30 states. + +And we can see that 18 states have been added. +This corresponds to 6 states for each triaxial accelerometers. + +*** Resonance frequencies and mode shapes +Let's now identify the resonance frequency and mode shapes associated with the suspension modes of the optical table. + +#+begin_src matlab +acc_3d.type = 2; % 1: inertial mass, 2: perfect + +%% Name of the Simulink File +mdl = 'vibration_table'; + +%% Input/Output definition +clear io; io_i = 1; +io(io_i) = linio([mdl, '/F'], 1, 'openinput'); io_i = io_i + 1; +io(io_i) = linio([mdl, '/acc_O'], 1, 'openoutput'); io_i = io_i + 1; + +%% Run the linearization +G = linearize(mdl, io); +G.InputName = {'F'}; +G.OutputName = {'ax', 'ay', 'az', 'wx', 'wy', 'wz'}; +#+end_src + +Compute the resonance frequencies +#+begin_src matlab +ws = eig(G.A); +ws = ws(imag(ws) > 0); +#+end_src + +And the associated response of the optical table +#+begin_src matlab +x_mod = zeros(6, 6); + +for i = 1:length(ws) + xi = evalfr(G, ws(i)); + x_mod(:,i) = xi./norm(xi); +end +#+end_src + +The results are shown in Table [[tab:mode_shapes]]. +The motion associated to the mode shapes are just indicative. + +#+begin_src matlab :exports results :results value table replace :tangle no :post addhdr(*this*) +data2orgtable([flip(imag(ws)/2/pi)'; flip(abs(x_mod),2)], {'$\omega_0$ [Hz]', 'x', 'y', 'z', 'Rx', 'Ry', 'Rz'}, {}, ' %.1f '); +#+end_src + +#+name: tab:mode_shapes +#+caption: Resonance frequency and approximation of the mode shapes +#+attr_latex: :environment tabularx :width 0.4\linewidth :align Xcccccc +#+attr_latex: :center t :booktabs t :float t +#+RESULTS: +| $\omega_0$ [Hz] | 5.6 | 5.6 | 5.7 | 8.2 | 8.2 | 8.2 | +|-----------------+-----+-----+-----+-----+-----+-----| +| x | 0.1 | 0.7 | 0.0 | 0.0 | 0.2 | 0.0 | +| y | 0.7 | 0.1 | 0.0 | 0.0 | 0.0 | 0.2 | +| z | 0.0 | 0.0 | 1.0 | 0.0 | 0.0 | 0.0 | +| Rx | 0.7 | 0.1 | 0.0 | 0.0 | 0.1 | 1.0 | +| Ry | 0.1 | 0.7 | 0.0 | 0.0 | 1.0 | 0.1 | +| Rz | 0.0 | 0.0 | 0.0 | 1.0 | 0.0 | 0.0 | + +** Verify transformation +#+begin_src matlab +%% Options for Linearized +options = linearizeOptions; +options.SampleTime = 0; + +%% Name of the Simulink File +mdl = 'vibration_table'; + +%% Input/Output definition +clear io; io_i = 1; +io(io_i) = linio([mdl, '/F'], 1, 'openinput'); io_i = io_i + 1; +io(io_i) = linio([mdl, '/acc'], 1, 'openoutput'); io_i = io_i + 1; +io(io_i) = linio([mdl, '/Absolute_Accelerometer'], 1, 'openoutput'); io_i = io_i + 1; + +%% Run the linearization +G = linearize(mdl, io, 0.0, options); +G.InputName = {'F'}; +G.OutputName = {'a1', 'a2', 'a3', 'a4', 'a5', 'a6', ... + 'Dx', 'Dy', 'Dz', 'Rx', 'Ry', 'Rz'}; +#+end_src + +#+begin_src matlab +G_acc = inv(M)*G(1:6, 1); +G_id = G(7:12, 1); +#+end_src + +#+begin_src matlab +bodeFig({G_acc(1), G_id(1)}) +bodeFig({G_acc(2), G_id(2)}) +bodeFig({G_acc(3), G_id(3)}) +bodeFig({G_acc(4), G_id(4)}) +bodeFig({G_acc(5), G_id(5)}) +bodeFig({G_acc(6), G_id(6)}) +#+end_src + +* Identification of the table's dynamics +<> +** Matlab Init :noexport:ignore: +#+begin_src matlab :tangle no :exports none :results silent :noweb yes :var current_dir=(file-name-directory buffer-file-name) +<> +#+end_src + +#+begin_src matlab :exports none :results silent :noweb yes +<> +#+end_src + +#+begin_src matlab :tangle no +addpath('matlab/') +#+end_src + * Bibliography :ignore: #+latex: \printbibliography diff --git a/vibration-table.pdf b/vibration-table.pdf index 1b837f9bd7a2f9c178174f79f43a303fd7cb5720..4dc6fce62a09b966b24ba2da21ae440c894ec34d 100644 GIT binary patch delta 307379 zcmZs?b95#__bnXTw(TdjZQHgv!4uoIHSr{w*fu7%ZD+!7-uJieUF&}L{?m1Kud}*p zb#?8t&#A7yarnyzoQ6nPpb-233ku|IcftM$g#6Ue9|}Uu??5+a)QHG=tg5v0!wN24 z%+1{G1Md&TepCzw_$MnxF@RwzR&(<5IobdyyJjN=gq$Q@ijwbYgGbYWc+ClzP8Y{k z7JL;3eAhk0_4-h&$&*CWDM%cJ*^``mGAm7N3Xu(n)zA2|eAbY7-mnh7;fnc8pr~uaA#IehlP+R-SJ-3rBM|cUKD&hyPekrnYcgtSLe87+?UN 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