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Thomas Dehaeze 2024-10-29 19:18:00 +01:00
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@ -226,19 +226,19 @@ CLOSED: [2024-10-26 Sat 15:26]
* Introduction :ignore:
In the previous section, all the struts were mounted and individually characterized.
Now the nano-hexapod is assembled using a mounting procedure described in Section ref:sec:test_nhexa_mounting.
Prior to the nano-hexapod assembly, all the struts were mounted and individually characterized.
In Section ref:sec:test_nhexa_mounting, the assembly procedure of the nano-hexapod is presented.
In order to identify the dynamics of the nano-hexapod, a special suspended table is developed which consists of a stiff "optical breadboard" suspended on top of four soft springs.
The Nano-Hexapod is then fixed on top of the suspended table, such that its dynamics is not affected by complex dynamics except from the suspension modes of the table that can be well characterized and modelled (Section ref:sec:test_nhexa_table).
To identify the dynamics of the nano-hexapod, a special suspended table was developed, which consisted of a stiff "optical breadboard" suspended on top of four soft springs.
The Nano-Hexapod was then fixed on top of the suspended table such that its dynamics is not affected by complex dynamics except from the suspension modes of the table that can be well characterized and modeled (Section ref:sec:test_nhexa_table).
The obtained nano-hexapod dynamics is analyzed in Section ref:sec:test_nhexa_dynamics, and compared with the Simscape model in Section ref:sec:test_nhexa_model.
* Nano-Hexapod Assembly Procedure
<<sec:test_nhexa_mounting>>
The assembly of the nano-hexapod is quite critical to both avoid additional stress in the flexible joints (that would result in a loss of stroke) and for the precise determination of the Jacobian matrix.
The goal is to fix the six struts to the two nano-hexapod plates (shown in Figure ref:fig:test_nhexa_nano_hexapod_plates) while the two plates are parallel, aligned vertically, and such that all the flexible joints do not experience any stress.
Do to so, a precisely machined mounting tool (Figure ref:fig:test_nhexa_center_part_hexapod_mounting) is used to position the two nano-hexapod plates during the assembly procedure.
The assembly of the nano-hexapod is critical for both avoiding additional stress in the flexible joints (that would result in a loss of stroke) and for the precisely determining the Jacobian matrix.
The goal was to fix the six struts to the two nano-hexapod plates (shown in Figure ref:fig:test_nhexa_nano_hexapod_plates) while the two plates were parallel and aligned vertically so that all the flexible joints did not experience any stress.
To do so, a precisely machined mounting tool (Figure ref:fig:test_nhexa_center_part_hexapod_mounting) is used to position the two nano-hexapod plates during the assembly procedure.
#+name: fig:test_nhexa_received_parts
#+caption: Received Nano-Hexapod plates (\subref{fig:test_nhexa_nano_hexapod_plates}) and mounting tool used to position the two plates during assembly (\subref{fig:test_nhexa_center_part_hexapod_mounting})
@ -260,10 +260,10 @@ Do to so, a precisely machined mounting tool (Figure ref:fig:test_nhexa_center_p
#+end_subfigure
#+end_figure
The mechanical tolerances of the received plates are checked using a FARO arm[fn:1] (Figure ref:fig:test_nhexa_plates_tolerances) and are found to comply with the requirements[fn:2].
The mechanical tolerances of the received plates were checked using a FARO arm[fn:1] (Figure ref:fig:test_nhexa_plates_tolerances) and were found to comply with the requirements[fn:2].
The same is done for the mounting tool[fn:3]
The two plates are then fixed to the mounting tool as shown in Figure ref:fig:test_nhexa_mounting_tool_hexapod_top_view.
The main goal of this "mounting tool" is to position the flexible joint interfaces (the "V" shapes) of both plates such that a cylinder can rest on the 4 flat interfaces at the same time.
The two plates were then fixed to the mounting tool, as shown in Figure ref:fig:test_nhexa_mounting_tool_hexapod_top_view.
The main goal of this "mounting tool" is to position the flexible joint interfaces (the "V" shapes) of both plates so that a cylinder can rest on the 4 flat interfaces at the same time.
#+name: fig:test_nhexa_dimensional_check
#+caption: A Faro arm is used to dimensionally check the received parts (\subref{fig:test_nhexa_plates_tolerances}) and after mounting the two plates with the mounting part (\subref{fig:test_nhexa_mounting_tool_hexapod_top_view})
@ -286,12 +286,12 @@ The main goal of this "mounting tool" is to position the flexible joint interfac
#+end_figure
The quality of the positioning can be estimated by measuring the "straightness" of the top and bottom "V" interfaces.
This corresponds to the diameter of the smallest cylinder that contains all points of the measured axis.
This is again done using the FARO arm, and the results for all the six struts are summarized in Table ref:tab:measured_straightness.
The straightness is found to be better than $15\,\mu m$ for all the struts[fn:4], which is sufficiently good to not induce significant stress of the flexible joint during the assembly.
This corresponds to the diameter of the smallest cylinder which contains all points along the measured axis.
This was again done using the FARO arm, and the results for all six struts are summarized in Table ref:tab:measured_straightness.
The straightness was found to be better than $15\,\mu m$ for all struts[fn:4], which is sufficiently good to not induce significant stress of the flexible joint during assembly.
#+name: tab:measured_straightness
#+caption: Measured straightness between the two "V" for the six struts. These measurements are performed two times for each strut.
#+caption: Measured straightness between the two "V" shapes for the six struts. These measurements were performed twice for each strut.
#+attr_latex: :environment tabularx :width 0.35\linewidth :align Xcc
#+attr_latex: :center t :booktabs t
| *Strut* | *Meas 1* | *Meas 2* |
@ -303,22 +303,10 @@ The straightness is found to be better than $15\,\mu m$ for all the struts[fn:4]
| 5 | $7\, \mu m$ | $5\, \mu m$ |
| 6 | $6\, \mu m$ | $7\, \mu m$ |
The encoder rulers and heads are then fixed to the top and bottom plates respectively (Figure ref:fig:test_nhexa_mount_encoder).
The encoder heads are then aligned to maximize the received contrast.
# 1. Fix the bottom plate with the cylindrical tool
# 2. Put the top plate on the granite
# 3. Put the cylindrical tool and bottom plate on top of the top plate (Figure ref:fig:test_nhexa_mounting_tool_hexapod_bot_view).
# This position the bottom plate with respect to the top plate in X, Y, Z, Rx, Ry
# 4. Put the pin to position/fix the Rz.
# Now the two plates should be position and clamped together
# 5. Verify the coaxiality between the flexible joint interfaces
# 6. Fix the 6 encoder heads and rulers
# 7. Fix the 6 struts
# 8. Remove the pin and the mounting spacer
The encoder rulers and heads were then fixed to the top and bottom plates, respectively (Figure ref:fig:test_nhexa_mount_encoder), and the encoder heads were aligned to maximize the received contrast.
#+name: fig:test_nhexa_mount_encoder
#+caption: Mounting of the encoders to the Nano-hexapod. The rulers are fixed to the top plate (\subref{fig:test_nhexa_mount_encoder_rulers}) while the encoders heads are fixed to the botom plate (\subref{fig:test_nhexa_mount_encoder_heads})
#+caption: Mounting of the encoders to the Nano-hexapod. The rulers are fixed to the top plate (\subref{fig:test_nhexa_mount_encoder_rulers}) while encoders heads are fixed to the bottom plate (\subref{fig:test_nhexa_mount_encoder_heads})
#+attr_latex: :options [htbp]
#+begin_figure
#+attr_latex: :caption \subcaption{\label{fig:test_nhexa_mount_encoder_rulers}Encoder rulers}
@ -337,11 +325,11 @@ The encoder heads are then aligned to maximize the received contrast.
#+end_subfigure
#+end_figure
The six struts are then fixed to the bottom and top plates one by one.
First the top flexible joint is fixed such that its flat reference surface is in contact with the top plate.
This is to precisely known the position of the flexible joint with respect to the top plate.
Then the bottom flexible joint is fixed.
After all six struts are mounted, the mounting tool (Figure ref:fig:test_nhexa_center_part_hexapod_mounting) can be disassembled, and the fully mounted nano-hexapod as shown in Figure ref:fig:test_nhexa_nano_hexapod_mounted is obtained.
The six struts were then fixed to the bottom and top plates one by one.
First, the top flexible joint is fixed so that its flat reference surface is in contact with the top plate.
This step precisely determines the position of the flexible joint with respect to the top plate.
The bottom flexible joint is then fixed.
After mounting all six struts, the mounting tool (Figure ref:fig:test_nhexa_center_part_hexapod_mounting) can be disassembled, and the nano-hexapod as shown in Figure ref:fig:test_nhexa_nano_hexapod_mounted is fully assembled.
#+name: fig:test_nhexa_nano_hexapod_mounted
#+caption: Mounted Nano-Hexapod
@ -358,20 +346,20 @@ After all six struts are mounted, the mounting tool (Figure ref:fig:test_nhexa_c
When a dynamical system is fixed to a support (such as a granite or an optical table), its dynamics will couple to the support dynamics.
This may results in additional modes appearing in the system dynamics, which are difficult to predict and model.
Two prevent this issue, strategy adopted here is to mount the nano-hexapod on top a suspended table with low frequency suspension modes.
To prevent this issue, the strategy adopted here is to mount the nano-hexapod on top a suspended table with low frequency suspension modes.
In such a case, the modes of the suspended table are chosen to be at much lower frequency than those of the nano-hexapod such that they are well decoupled.
An other key advantage is that the suspension modes of the suspended table can be easily modelled using Simscape.
Therefore, the measured dynamics of the nano-hexapod on top of the suspended table can be compared to a simscape model representing the same experimental conditions.
In this case, the modes of the suspended table were chosen to be at much lower frequency than those of the nano-hexapod such that good decoupling is obtained.
Another key advantage is that the suspension modes of the table can be easily modeled using Simscape.
Therefore, the measured dynamics of the nano-hexapod on top of the suspended table can be compared to a Simscape model representing the same experimental conditions.
The model of the Nano-Hexapod can thus be precisely tuned to match the measured dynamics.
The developed suspended table is presented in Section ref:ssec:test_nhexa_table_setup.
The developed suspended table is described in Section ref:ssec:test_nhexa_table_setup.
The modal analysis of the table is done in ref:ssec:test_nhexa_table_identification.
Finally, the Simscape model representing the suspended table is tuned to match the measured modes (Section ref:ssec:test_nhexa_table_model).
Finally, the Simscape model representing the suspended table was tuned to match the measured modes (Section ref:ssec:test_nhexa_table_model).
** Matlab Init :noexport:ignore:
#+begin_src matlab
%% test_nhexa_table.m
%% test_nhexa_1_suspended_table.m
#+end_src
#+begin_src matlab :tangle no :exports none :results silent :noweb yes :var current_dir=(file-name-directory buffer-file-name)
@ -403,11 +391,11 @@ Finally, the Simscape model representing the suspended table is tuned to match t
The design of the suspended table is quite straightforward.
First, an optical table with high frequency flexible mode was selected[fn:5].
Then, four springs[fn:6] were selected with low enough spring rate such that the suspension modes are below 10Hz.
Then, four springs[fn:6] were selected with low spring rate such that the suspension modes are below 10Hz.
Finally, some interface elements were designed, and mechanical lateral mechanical stops were added (Figure ref:fig:test_nhexa_suspended_table_cad).
#+name: fig:test_nhexa_suspended_table_cad
#+caption: CAD View of the vibration table. Purple cylinders are representing the soft springs.
#+caption: CAD View of the vibration table. The purple cylinders are representing the soft springs.
#+attr_latex: :width 0.7\linewidth
[[file:figs/test_nhexa_suspended_table_cad.jpg]]
@ -417,7 +405,7 @@ Finally, some interface elements were designed, and mechanical lateral mechanica
In order to perform a modal analysis of the suspended table, a total of 15 3-axis accelerometers[fn:7] were fixed to the breadboard.
Using an instrumented hammer, the first 9 modes could be identified and are summarized in Table ref:tab:test_nhexa_suspended_table_modes.
The first 6 modes are suspension modes (i.e. rigid body mode of the breadboard) and are located below 10Hz.
The next modes are flexible modes of the breadboard as shown in Figure ref:fig:test_nhexa_table_flexible_modes, and located above 700Hz.
The next modes are the flexible modes of the breadboard as shown in Figure ref:fig:test_nhexa_table_flexible_modes, and are located above 700Hz.
#+attr_latex: :options [t]{0.45\linewidth}
#+begin_minipage
@ -476,20 +464,20 @@ The next modes are flexible modes of the breadboard as shown in Figure ref:fig:t
** Simscape Model of the suspended table
<<ssec:test_nhexa_table_model>>
The Simscape model of the suspended table simply consists of two solid bodies connected by 4 springs.
The 4 springs are here modelled with "bushing joints" that have stiffness and damping properties in x, y and z directions.
The 3D representation of the model is displayed in Figure ref:fig:test_nhexa_suspended_table_simscape where the 4 "bushing joints" are represented by the blue cylinders.
The Simscape model of the suspended table consists simply of two solid bodies connected by 4 springs.
The 4 springs are here modeled with "bushing joints" that have stiffness and damping properties in x, y, and z directions.
The 3D representation of the model is shown in Figure ref:fig:test_nhexa_suspended_table_simscape where the 4 "bushing joints" are represented by blue cylinders.
#+name: fig:test_nhexa_suspended_table_simscape
#+caption: 3D representation of the simscape model
#+attr_latex: :width 0.8\linewidth
[[file:figs/test_nhexa_suspended_table_simscape.png]]
The model order is 12, and it represents the 6 suspension modes.
The inertia properties of the parts are set from the geometry and material densities.
The model order is 12, which corresponds to the 6 suspension modes.
The inertia properties of the parts were determined from the geometry and material densities.
The stiffness of the springs was initially set from the datasheet nominal value of $17.8\,N/mm$ and then reduced down to $14\,N/mm$ to better match the measured suspension modes.
The stiffness of the springs in the horizontal plane is set at $0.5\,N/mm$.
The obtained suspension modes of the simscape model are compared with the measured ones in Table ref:tab:test_nhexa_suspended_table_simscape_modes.
The obtained suspension modes of the Simscape model are compared with the measured modes in Table ref:tab:test_nhexa_suspended_table_simscape_modes.
#+begin_src matlab
%% Configure Simscape Model
@ -527,12 +515,12 @@ ws = ws(imag(ws) > 0);
:END:
In this section, a suspended table with low frequency suspension modes and high frequency flexible modes was presented.
This suspended table will be used in Section ref:sec:test_nhexa_dynamics for dynamical identification of the Nano-Hexapod.
The objective is to be able to accurately identify the dynamics of the nano-hexapod, isolated from complex support dynamics.
The key point of this strategy is to be able to accurately model the suspended table.
This suspended table is used in Section ref:sec:test_nhexa_dynamics for dynamical identification of the Nano-Hexapod.
The objective is to accurately identify the dynamics of the nano-hexapod, isolated from complex support dynamics.
The key point of this strategy was the ability to accurately model the suspended table.
To do so, a modal analysis of the suspended table was performed in Section ref:ssec:test_nhexa_table_identification, validating the low frequency suspension modes and high frequency flexible modes.
Then, a multi-body model of this suspended table was tuned to match with the measurements (Section ref:ssec:test_nhexa_table_model).
Then, a multi-body model of this suspended table was tuned to match the measurements (Section ref:ssec:test_nhexa_table_model).
* Nano-Hexapod Measured Dynamics
:PROPERTIES:
@ -542,8 +530,8 @@ Then, a multi-body model of this suspended table was tuned to match with the mea
** Introduction :ignore:
The Nano-Hexapod is then mounted on top of the suspended table as shown in Figure ref:fig:test_nhexa_hexa_suspended_table.
All the instrumentation (Speedgoat with ADC, DAC, piezoelectric voltage amplifiers and digital interfaces for the encoder) are setup and connected to the nano-hexapod using many cables.
The Nano-Hexapod was then mounted on top of the suspended table, as shown in Figure ref:fig:test_nhexa_hexa_suspended_table.
All instrumentation (Speedgoat with ADC, DAC, piezoelectric voltage amplifiers and digital interfaces for the encoder) were configured and connected to the nano-hexapod using many cables.
#+name: fig:test_nhexa_hexa_suspended_table
#+caption: Mounted Nano-Hexapod on top of the suspended table
@ -551,11 +539,11 @@ All the instrumentation (Speedgoat with ADC, DAC, piezoelectric voltage amplifie
[[file:figs/test_nhexa_hexa_suspended_table.jpg]]
A modal analysis of the nano-hexapod is first performed in Section ref:ssec:test_nhexa_enc_struts_modal_analysis.
It will be used to better understand the measured dynamics from actuators to sensors.
The results of the modal analysis will be useful to better understand the measured dynamics from actuators to sensors.
A block diagram schematic of the (open-loop) system is shown in Figure ref:fig:test_nhexa_nano_hexapod_signals.
The transfer function from controlled signals $\mathbf{u}$ to the force sensors voltages $\mathbf{V}_s$ and to the encoders measured displacements $\mathbf{d}_e$ are identified in Section ref:ssec:test_nhexa_identification.
The effect of the payload mass on the dynamics is studied in Section ref:ssec:test_nhexa_added_mass.
A block diagram of the (open-loop) system is shown in Figure ref:fig:test_nhexa_nano_hexapod_signals.
The frequency response functions from controlled signals $\mathbf{u}$ to the force sensors voltages $\mathbf{V}_s$ and to the encoders measured displacements $\mathbf{d}_e$ are experimentally identified in Section ref:ssec:test_nhexa_identification.
The effect of the payload mass on the dynamics is discussed in Section ref:ssec:test_nhexa_added_mass.
#+begin_src latex :file test_nhexa_nano_hexapod_signals.pdf
\definecolor{instrumentation}{rgb}{0, 0.447, 0.741}
@ -597,15 +585,15 @@ The effect of the payload mass on the dynamics is studied in Section ref:ssec:te
#+end_src
#+name: fig:test_nhexa_nano_hexapod_signals
#+caption: Block diagram of the system. Command signal generated by the speedgoat is $\mathbf{u}$, the measured dignals are $\mathbf{d}_{e}$ and $\mathbf{V}_s$. Units are indicated in square brackets.
#+caption: Block diagram of the studied system. The command signal generated by the speedgoat is $\mathbf{u}$, and the measured dignals are $\mathbf{d}_{e}$ and $\mathbf{V}_s$. Units are indicated in square brackets.
#+attr_latex: :scale 1
#+RESULTS:
[[file:figs/test_nhexa_nano_hexapod_signals.png]]
** Matlab Init :noexport:ignore:
#+begin_src matlab
%% test_nhexa_dynamics.m
% Identification of the nano-hexapod dynamics from u to dL and to Vs
%% test_nhexa_2_dynamics.m
% Identification of the nano-hexapod dynamics from u to de and to Vs
% Encoders are fixed to the plates
#+end_src
@ -632,16 +620,16 @@ The effect of the payload mass on the dynamics is studied in Section ref:ssec:te
** Modal analysis
<<ssec:test_nhexa_enc_struts_modal_analysis>>
In order to ease the future analysis of the measured plant dynamics, a basic modal analysis of the nano-hexapod is performed.
Five 3-axis accelerometers are fixed on the top platform of the nano-hexapod (Figure ref:fig:test_nhexa_modal_analysis) and the top platform is excited using an instrumented hammer.
To facilitate the future analysis of the measured plant dynamics, a basic modal analysis of the nano-hexapod is performed.
Five 3-axis accelerometers were fixed on the top platform of the nano-hexapod (Figure ref:fig:test_nhexa_modal_analysis) and the top platform was excited using an instrumented hammer.
#+name: fig:test_nhexa_modal_analysis
#+caption: Five accelerometers fixed on top of the nano-hexapod to perform a modal analysis
#+attr_latex: :width 0.7\linewidth
[[file:figs/test_nhexa_modal_analysis.jpg]]
Between 100Hz and 200Hz, 6 suspension modes (i.e. rigid body modes of the top platform) are identified.
At around 700Hz, two flexible modes of the top plate are observed (see Figure ref:fig:test_nhexa_hexa_flexible_modes).
Between 100Hz and 200Hz, 6 suspension modes (i.e. rigid body modes of the top platform) were identified.
At around 700Hz, two flexible modes of the top plate were observed (see Figure ref:fig:test_nhexa_hexa_flexible_modes).
These modes are summarized in Table ref:tab:test_nhexa_hexa_modal_modes_list.
#+name: tab:test_nhexa_hexa_modal_modes_list
@ -680,29 +668,30 @@ These modes are summarized in Table ref:tab:test_nhexa_hexa_modal_modes_list.
** Identification of the dynamics
<<ssec:test_nhexa_identification>>
The dynamics of the nano-hexapod from the six command signals ($u_1$ to $u_6$) the six measured displacement by the encoders ($d_{e1}$ to $d_{e6}$) and to the six force sensors ($V_{s1}$ to $V_{s6}$) are identified by generating a low pass filtered white noise for each of the command signals, one by one.
The dynamics of the nano-hexapod from the six command signals ($u_1$ to $u_6$) to the six measured displacement by the encoders ($d_{e1}$ to $d_{e6}$) and to the six force sensors ($V_{s1}$ to $V_{s6}$) were identified by generating low-pass filtered white noise for each command signal, one by one.
The $6 \times 6$ FRF matrix from $\mathbf{u}$ ot $\mathbf{d}_e$ is shown in Figure ref:fig:test_nhexa_identified_frf_de.
The diagonal terms are displayed using colorful lines, and all the 30 off-diagonal terms are displayed by grey lines.
The diagonal terms are displayed using colored lines, and all the 30 off-diagonal terms are displayed by gray lines.
All the six diagonal terms are well superimposed up to at least $1\,kHz$, indicating good manufacturing and mounting uniformity.
Below the first suspension mode, good decoupling can be observed (the amplitude of the all of off-diagonal terms are $\approx 20$ times smaller than the diagonal terms).
All six diagonal terms are well superimposed up to at least $1\,kHz$, indicating good manufacturing and mounting uniformity.
Below the first suspension mode, good decoupling can be observed (the amplitude of all off-diagonal terms are $\approx 20$ times smaller than the diagonal terms).
From 10Hz up to 1kHz, around 10 resonance frequencies can be observed.
The first 4 are suspension modes (at 122Hz, 143Hz, 165Hz and 191Hz) which correlate the modes measured during the modal analysis in Section ref:ssec:test_nhexa_enc_struts_modal_analysis.
Then, three modes at 237Hz, 349Hz and 395Hz are attributed to the internal strut resonances (this will be checked in Section ref:ssec:test_nhexa_comp_model_coupling).
Except the mode at 237Hz, their amplitude is rather low.
Two modes at 665Hz and 695Hz are attributed to the flexible modes of the top platform.
Three modes at 237Hz, 349Hz and 395Hz are attributed to the internal strut resonances (this will be checked in Section ref:ssec:test_nhexa_comp_model_coupling).
Except for the mode at 237Hz, their impact on the dynamics is small.
The two modes at 665Hz and 695Hz are attributed to the flexible modes of the top platform.
Other modes can be observed above 1kHz, which can be attributed to flexible modes of the encoder supports or to flexible modes of the top platform.
Up to at least 1kHz, an alternating pole/zero pattern is observed, which renders the control easier to tune.
This would not have been the case if the encoders were fixed to the struts.
Up to at least 1kHz, an alternating pole/zero pattern is observed, which makes the control easier to tune.
This would not have occurred if the encoders were fixed to the struts.
#+begin_src matlab
%% Load identification data
%% Identification of the transfer function from u to de and from u to Vs without payload
% Load identification data
load('test_nhexa_identification_data_mass_0.mat', 'data');
%% Setup useful variables
% Setup useful variables
Ts = 1e-4; % Sampling Time [s]
Nfft = floor(1/Ts); % Number of points for the FFT computation
win = hanning(Nfft); % Hanning window
@ -711,14 +700,14 @@ Noverlap = floor(Nfft/2); % Overlap between frequency analysis
% And we get the frequency vector
[~, f] = tfestimate(data{1}.u, data{1}.de, win, Noverlap, Nfft, 1/Ts);
%% Transfer function from u to dLm
% Transfer function from u to de
G_de = zeros(length(f), 6, 6);
for i = 1:6
G_de(:,:,i) = tfestimate(data{i}.u, data{i}.de, win, Noverlap, Nfft, 1/Ts);
end
%% Transfer function from u to Vs
% Transfer function from u to Vs
G_Vs = zeros(length(f), 6, 6);
for i = 1:6
@ -727,7 +716,7 @@ end
#+end_src
#+begin_src matlab :exports none
%% Bode plot for the transfer function from u to dLm
%% Bode plot for the transfer function from u to de
figure;
tiledlayout(3, 1, 'TileSpacing', 'Compact', 'Padding', 'None');
@ -774,15 +763,15 @@ exportFig('figs/test_nhexa_identified_frf_de.pdf', 'width', 'wide', 'height', 60
#+end_src
#+name: fig:test_nhexa_identified_frf_de
#+caption: Measured FRF for the transfer function from $\mathbf{u}$ to $\mathbf{d}_e$. The 6 diagonal terms are the colorfull lines (all superimposed), and the 30 off-diagonal terms are the shaded black lines.
#+caption: Measured FRF for the transfer function from $\mathbf{u}$ to $\mathbf{d}_e$. The 6 diagonal terms are the colored lines (all superimposed), and the 30 off-diagonal terms are the gray lines.
#+RESULTS:
[[file:figs/test_nhexa_identified_frf_de.png]]
Similarly, the $6 \times 6$ FRF matrix from $\mathbf{u}$ to $\mathbf{V}_s$ is shown in Figure ref:fig:test_nhexa_identified_frf_Vs.
Alternating poles and zeros is observed up to at least 2kHz, which is a necessary characteristics in order to apply decentralized IFF.
Similar to what was observed for the encoder outputs, all the "diagonal" terms are well superimposed, indicating that the same controller can be applied for all the struts.
The first flexible mode of the struts as 235Hz is appearing, and therefore is should be possible to add some damping to this mode using IFF.
Alternating poles and zeros can be observed up to at least 2kHz, which is a necessary characteristics for applying decentralized IFF.
Similar to what was observed for the encoder outputs, all the "diagonal" terms are well superimposed, indicating that the same controller can be applied to all the struts.
The first flexible mode of the struts as 235Hz has large amplitude, and therefore, it should be possible to add some damping to this mode using IFF.
#+begin_src matlab :exports none
%% Bode plot of the IFF Plant (transfer function from u to Vs)
@ -832,16 +821,16 @@ exportFig('figs/test_nhexa_identified_frf_Vs.pdf', 'width', 'wide', 'height', 60
#+end_src
#+name: fig:test_nhexa_identified_frf_Vs
#+caption: Measured FRF for the transfer function from $\mathbf{u}$ to $\mathbf{V}_s$. The 6 diagonal terms are the colorfull lines (all superimposed), and the 30 off-diagonal terms are the shaded black lines.
#+caption: Measured FRF for the transfer function from $\mathbf{u}$ to $\mathbf{V}_s$. The 6 diagonal terms are the colored lines (all superimposed), and the 30 off-diagonal terms are the shaded black lines.
#+RESULTS:
[[file:figs/test_nhexa_identified_frf_Vs.png]]
** Effect of payload mass on the dynamics
<<ssec:test_nhexa_added_mass>>
As one major challenge in the control of the NASS is the wanted robustness to change of payload mass, it is necessary to understand how the dynamics of the nano-hexapod changes with a change of payload mass.
One major challenge in the control of the NASS is the wanted robustness to a change of payload mass; therefore, it is necessary to understand how the dynamics of the nano-hexapod changes with a change in payload mass.
In order to study this change of dynamics with the payload mass, up to three "cylindrical masses" of $13\,kg$ each can be added for a total of $\approx 40\,kg$.
To study how the dynamics changes with the payload mass, up to three "cylindrical masses" of $13\,kg$ each can be added for a total of $\approx 40\,kg$.
These three cylindrical masses on top of the nano-hexapod are shown in Figure ref:fig:test_nhexa_table_mass_3.
#+name: fig:test_nhexa_table_mass_3
@ -851,14 +840,22 @@ These three cylindrical masses on top of the nano-hexapod are shown in Figure re
[[file:figs/test_nhexa_table_mass_3.jpg]]
#+begin_src matlab
%% Load identification Data
%% Set to true only if all the FRF matrices should again computed
% from the experimental data
compute_frf = false;
if compute_frf
#+end_src
#+begin_src matlab
%% Identification of the FRF matrices from u to de and to Vs
% Load identification Data
meas_added_mass = {...
load('test_nhexa_identification_data_mass_0.mat', 'data'), ....
load('test_nhexa_identification_data_mass_1.mat', 'data'), ....
load('test_nhexa_identification_data_mass_2.mat', 'data'), ....
load('test_nhexa_identification_data_mass_3.mat', 'data')};
%% Setup useful variables
% Setup useful variables
Ts = 1e-4; % Sampling Time [s]
Nfft = floor(1/Ts); % Number of points for the FFT computation
win = hanning(Nfft); % Hanning window
@ -867,6 +864,7 @@ Noverlap = floor(Nfft/2); % Overlap between frequency analysis
% And we get the frequency vector
[~, f] = tfestimate(meas_added_mass{1}.data{1}.u, meas_added_mass{1}.data{1}.de, win, Noverlap, Nfft, 1/Ts);
% FRF from u to de
G_de = {};
for i_mass = [0:3]
@ -876,7 +874,7 @@ for i_mass = [0:3]
end
end
%% IFF Plant (transfer function from u to Vs)
% FRF from u to Vs
G_Vs = {};
for i_mass = [0:3]
@ -887,37 +885,42 @@ for i_mass = [0:3]
end
#+end_src
The identified dynamics are then saved for further use.
#+begin_src matlab :exports none :tangle no
% The identified dynamics are then saved for further use.
save('matlab/mat/test_nhexa_identified_frf_masses.mat', 'f', 'G_Vs', 'G_de')
#+end_src
#+begin_src matlab :eval no
% The identified dynamics are then saved for further use.
save('./mat/test_nhexa_identified_frf_masses.mat', 'f', 'G_Vs', 'G_de')
#+end_src
#+begin_src matlab
end
#+end_src
#+begin_src matlab :exports none
%% Load the identified transfer functions
frf_ol = load('test_nhexa_identified_frf_masses.mat', 'f', 'G_Vs', 'G_de');
#+end_src
The obtained frequency response functions from actuator signal $u_i$ to the associated encoder $d_{ei}$ for the four payload conditions (no mass, 13kg, 26kg and 39kg) are shown in Figure ref:fig:test_nhexa_identified_frf_de_masses.
As expected, the frequency of the suspension modes are decreasing with an increase of the payload mass.
The low frequency gain does not change as it is linked to the stiffness property of the nano-hexapod, and not to its mass property.
As expected, the frequency of the suspension modes decreased with increasing payload mass.
The low frequency gain does not change because it is linked to the stiffness property of the nano-hexapod and not to its mass property.
The frequencies of the two flexible modes of the top plate are first decreased a lot when the first mass is added (from $\approx 700\,Hz$ to $\approx 400\,Hz$).
This is due to the fact that the added mass is composed of two half cylinders which are not fixed together.
It therefore adds a lot of mass to the top plate without adding stiffness in one direction.
When more than one "mass layer" is added, the half cylinders are added with some angles such that rigidity are added in all directions (see how the three mass "layers" are positioned in Figure ref:fig:test_nhexa_table_mass_3).
In that case, the frequency of these flexible modes are increased.
In practice, the payload should be one solid body, and no decrease of the frequency of this flexible mode should be observed.
The apparent amplitude of the flexible mode of the strut at 237Hz becomes smaller as the payload mass is increased.
The frequencies of the two flexible modes of the top plate first decreased significantly when the first mass was added (from $\approx 700\,Hz$ to $\approx 400\,Hz$).
This is because the added mass is composed of two half cylinders that are not fixed together.
Therefore, it adds a lot of mass to the top plate without increasing stiffness in one direction.
When more than one "mass layer" is added, the half cylinders are added at some angles such that rigidity is added in all directions (see how the three mass "layers" are positioned in Figure ref:fig:test_nhexa_table_mass_3).
In this case, the frequency of these flexible modes is increased.
In practice, the payload should be one solid body, and no decrease in the frequency of this flexible mode should be observed.
The apparent amplitude of the flexible mode of the strut at 237Hz becomes smaller as the payload mass increased.
The measured FRF from $u_i$ to $V_{si}$ are shown in Figure ref:fig:test_nhexa_identified_frf_Vs_masses.
For all the tested payloads, the measured FRF always have alternating poles and zeros, indicating that IFF can be applied in a robust way.
The measured FRFs from $u_i$ to $V_{si}$ are shown in Figure ref:fig:test_nhexa_identified_frf_Vs_masses.
For all tested payloads, the measured FRF always have alternating poles and zeros, indicating that IFF can be applied in a robust manner.
#+begin_src matlab :exports none
%% Bode plot for the transfer function from u to dLm - Several payloads
%% Bode plot for the transfer function from u to de - Several payloads
masses = [0, 13, 26, 39];
figure;
tiledlayout(3, 1, 'TileSpacing', 'Compact', 'Padding', 'None');
@ -970,7 +973,7 @@ exportFig('figs/test_nhexa_identified_frf_de_masses.pdf', 'width', 'half', 'heig
#+end_src
#+begin_src matlab :exports none
%% Bode plot for the transfer function from u to dLm
%% Bode plot for the transfer function from u to de
figure;
tiledlayout(3, 1, 'TileSpacing', 'Compact', 'Padding', 'None');
@ -1046,15 +1049,14 @@ exportFig('figs/test_nhexa_identified_frf_Vs_masses.pdf', 'width', 'half', 'heig
After the Nano-Hexapod was fixed on top of the suspended table, its dynamics was identified.
The frequency response functions from the six DAC voltages $\mathbf{u}$ to the six encoders measured displacements $\mathbf{d}_e$ displays alternating complex conjugate poles and complex conjugate zeros up to at least 1kHz.
At low frequency, the coupling is small, indicating correct assembly of all parts.
This should enables the design of a decentralized positioning controller based on the encoder for relative positioning purposes.
The suspension modes and flexible modes measured during the modal analysis (Section ref:ssec:test_nhexa_enc_struts_modal_analysis) are also observed in the dynamics.
Lot's of other modes are present above 700Hz, which will inevitably limit the achievable bandwidth.
The observed effect of the payload's mass on the dynamics is quite large, which also represent a complex control challenge.
At low frequencies, the coupling is small, indicating the correct assembly of all parts.
This should enable the design of a decentralized positioning controller based on the encoders for relative positioning purposes.
The suspension and flexible modes measured during the modal analysis (Section ref:ssec:test_nhexa_enc_struts_modal_analysis) are also observed in the dynamics.
Many other modes are present above 700Hz, which will inevitably limit the achievable bandwidth.
The observed effect of the payload's mass on the dynamics was quite large, which also represents a complex control challenge.
The frequency response functions from the six DAC voltages $\mathbf{u}$ to the six force sensors voltages $\mathbf{V}_s$ all have alternating complex conjugate poles and complex conjugate zeros.
This indicates that it should be possible to implement decentralized Integral Force Feedback in a robust way.
This alternating property holds for all the tested payloads.
The frequency response functions from the six DAC voltages $\mathbf{u}$ to the six force sensors voltages $\mathbf{V}_s$ all have alternating complex conjugate poles and complex conjugate zeros for all the tested payloads.
This indicates that it is possible to implement decentralized Integral Force Feedback in a robust manner.
* Nano-Hexapod Model Dynamics
:PROPERTIES:
@ -1064,8 +1066,8 @@ This alternating property holds for all the tested payloads.
** Introduction :ignore:
In this section, the measured dynamics done in Section ref:sec:test_nhexa_dynamics is compared with the dynamics estimated from the Simscape model.
The nano-hexapod simscape model is therefore added on top of the vibration table Simscape model as shown in Figure ref:fig:test_nhexa_hexa_simscape.
In this section, the dynamics measured in Section ref:sec:test_nhexa_dynamics is compared with those estimated from the Simscape model.
The nano-hexapod simscape model was therefore added on top of the vibration table Simscape model, as shown in Figure ref:fig:test_nhexa_hexa_simscape.
#+name: fig:test_nhexa_hexa_simscape
#+caption: 3D representation of the simscape model with the nano-hexapod on top of the suspended table. Three mass "layers" are here added
@ -1073,7 +1075,7 @@ The nano-hexapod simscape model is therefore added on top of the vibration table
[[file:figs/test_nhexa_hexa_simscape.png]]
The model should exhibit certain characteristics that are verified in this section.
First, it should match the measured system dynamics from actuators to sensors that were presented in Section ref:sec:test_nhexa_dynamics.
First, it should match the measured system dynamics from actuators to sensors presented in Section ref:sec:test_nhexa_dynamics.
Both the "direct" terms (Section ref:ssec:test_nhexa_comp_model) and "coupling" terms (Section ref:ssec:test_nhexa_comp_model_coupling) of the Simscape model are compared with the measured dynamics.
Second, it should also represents how the system dynamics changes when a payload is fixed to the top platform.
This is checked in Section ref:ssec:test_nhexa_comp_model_masses.
@ -1207,16 +1209,16 @@ sim_ol = load('test_nhexa_simscape_masses.mat', 'G_Vs', 'G_de');
frf_ol = load('test_nhexa_identified_frf_masses.mat', 'f', 'G_Vs', 'G_de');
#+end_src
The Simscape model of the nano-hexapod is first configured with 4-DoF flexible joints, 2-DoF APA and rigid top and bottom platforms.
The stiffness of the flexible joints are chosen based on the values estimated using the test bench and based on FEM.
The parameters of the APA model are the ones determined from the test bench of the APA.
The $6 \times 6$ transfer function matrices from $\mathbf{u}$ to $\mathbf{d}_e$ and from $\mathbf{u}$ to $\mathbf{V}_s$ are extracted then from the Simscape model.
The Simscape model of the nano-hexapod was first configured with 4-DoF flexible joints, 2-DoF APA, and rigid top and bottom plates.
The stiffness values of the flexible joints were chosen based on the values estimated using the test bench and on the FEM.
The parameters of the APA model were determined from the test bench of the APA.
The $6 \times 6$ transfer function matrices from $\mathbf{u}$ to $\mathbf{d}_e$ and from $\mathbf{u}$ to $\mathbf{V}_s$ are then extracted from the Simscape model.
A first feature that should be checked is that the model well represents the "direct" terms of the measured FRF matrix.
First, is it evaluated how well the models matches the "direct" terms of the measured FRF matrix.
To do so, the diagonal terms of the extracted transfer function matrices are compared with the measured FRF in Figure ref:fig:test_nhexa_comp_simscape_diag.
It can be seen that the 4 suspension modes of the nano-hexapod (at 122Hz, 143Hz, 165Hz and 191Hz) are well modelled.
The three resonances that were attributed to "internal" flexible modes of the struts (at 237Hz, 349Hz and 395Hz) cannot be seen in the model, which is reasonable as the APA are here modelled as a simple uniaxial 2-DoF system.
At higher frequencies, no resonances can be seen in the model, as the as the top plate and the encoder supports are modelled as rigid bodies.
It can be seen that the 4 suspension modes of the nano-hexapod (at 122Hz, 143Hz, 165Hz and 191Hz) are well modeled.
The three resonances that were attributed to "internal" flexible modes of the struts (at 237Hz, 349Hz and 395Hz) cannot be seen in the model, which is reasonable because the APAs are here modeled as a simple uniaxial 2-DoF system.
At higher frequencies, no resonances can be observed in the model, as the top plate and the encoder supports are modeled as rigid bodies.
#+begin_src matlab :exports none
%% Diagonal elements of the FRF matrix from u to de
@ -1305,7 +1307,7 @@ exportFig('figs/test_nhexa_comp_simscape_Vs_diag.pdf', 'width', 'half', 'height'
#+end_src
#+name: fig:test_nhexa_comp_simscape_diag
#+caption: Comparison of the diagonal elements (i.e. "direct" terms) of the measured FRF matrix and the identified dynamics from the Simscape model. Both for the dynamics from $u$ to $d_e$ (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from $u$ to $V_s$ (\subref{fig:test_nhexa_comp_simscape_Vs_diag})
#+caption: Comparison of the diagonal elements (i.e. "direct" terms) of the measured FRF matrix and the dynamics identified from the Simscape model. Both for the dynamics from $u$ to $d_e$ (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from $u$ to $V_s$ (\subref{fig:test_nhexa_comp_simscape_Vs_diag})
#+attr_latex: :options [htbp]
#+begin_figure
#+attr_latex: :caption \subcaption{\label{fig:test_nhexa_comp_simscape_de_diag}from $u$ to $d_e$}
@ -1322,13 +1324,13 @@ exportFig('figs/test_nhexa_comp_simscape_Vs_diag.pdf', 'width', 'half', 'height'
#+end_subfigure
#+end_figure
** Modelling dynamical coupling
** Modeling dynamical coupling
<<ssec:test_nhexa_comp_model_coupling>>
Another wanted feature of the model is that it well represents the coupling in the system as this is often the limiting factor for the control of MIMO systems.
Another desired feature of the model is that it effectively represents coupling in the system, as this is often the limiting factor for the control of MIMO systems.
Instead of comparing the full 36 elements of the $6 \times 6$ FFR matrix from $\mathbf{u}$ to $\mathbf{d}_e$, only the first "column" is compared (Figure ref:fig:test_nhexa_comp_simscape_de_all), which corresponds to the transfer function from the command $u_1$ to the six measured encoder displacements $d_{e1}$ to $d_{e6}$.
It can be seen that the coupling in the model is well matching the measurements up to the first un-modelled flexible mode at 237Hz.
Similar results are observed for all the other coupling terms, as well as for the transfer function from $\mathbf{u}$ to $\mathbf{V}_s$.
It can be seen that the coupling in the model matches the measurements well up to the first un-modeled flexible mode at 237Hz.
Similar results are observed for all other coupling terms and for the transfer function from $\mathbf{u}$ to $\mathbf{V}_s$.
#+begin_src matlab :exports none
%% Comparison of the plants (encoder output) when tuning the misalignment
@ -1407,15 +1409,15 @@ exportFig('figs/test_nhexa_comp_simscape_de_all.pdf', 'width', 'full', 'height',
#+end_src
#+name: fig:test_nhexa_comp_simscape_de_all
#+caption: Comparison of the measured (in blue) and modelled (in red) frequency transfer functions from the first control signal $u_1$ to the six encoders $d_{e1}$ to $d_{e6}$
#+caption: Comparison of the measured (in blue) and modeled (in red) frequency transfer functions from the first control signal $u_1$ to the six encoders $d_{e1}$ to $d_{e6}$
#+RESULTS:
[[file:figs/test_nhexa_comp_simscape_de_all.png]]
The APA300ML are then modelled with a /super-element/ extracted from a FE-software.
The APA300ML was then modeled with a /super-element/ extracted from a FE-software.
The obtained transfer functions from $u_1$ to the six measured encoder displacements $d_{e1}$ to $d_{e6}$ are compared with the measured FRF in Figure ref:fig:test_nhexa_comp_simscape_de_all_flex.
While the damping of the suspension modes for the /super-element/ is underestimated (which could be solved by properly tuning the proportional damping coefficients), the flexible modes of the struts at 237Hz and 349Hz are well modelled.
While the damping of the suspension modes for the /super-element/ is underestimated (which could be solved by properly tuning the proportional damping coefficients), the flexible modes of the struts at 237Hz and 349Hz are well modeled.
Even the mode 395Hz can be observed in the model.
Therefore, if the modes of the struts are to be modelled, the /super-element/ of the APA300ML may be used, at the cost of obtaining a much higher order model.
Therefore, if the modes of the struts are to be modeled, the /super-element/ of the APA300ML can be used at the cost of obtaining a much higher order model.
#+begin_src matlab
%% Load the plant model with Flexible APA
@ -1499,21 +1501,21 @@ exportFig('figs/test_nhexa_comp_simscape_de_all_flex.pdf', 'width', 'full', 'hei
#+end_src
#+name: fig:test_nhexa_comp_simscape_de_all_flex
#+caption: Comparison of the measured (in blue) and modelled (in red) frequency transfer functions from the first control signal $u_1$ to the six encoders $d_{e1}$ to $d_{e6}$
#+caption: Comparison of the measured (in blue) and modeled (in red) frequency transfer functions from the first control signal $u_1$ to the six encoders $d_{e1}$ to $d_{e6}$
#+RESULTS:
[[file:figs/test_nhexa_comp_simscape_de_all_flex.png]]
** Modelling the effect of payload mass
** Modeling the effect of payload mass
<<ssec:test_nhexa_comp_model_masses>>
Another important characteristics of the model is that it should well represents the dynamics of the system for all considered payloads.
Another important characteristic of the model is that it should represents the dynamics of the system well for all considered payloads.
The model dynamics is therefore compared with the measured dynamics for 4 payloads (no payload, 13kg, 26kg and 39kg) in Figure ref:fig:test_nhexa_comp_simscape_diag_masses.
The observed shift to lower frequency of the suspension modes with an increased payload mass is well represented by the Simscape model.
The complex conjugate zeros are also well matching with the experiments both for the encoder outputs (Figure ref:fig:test_nhexa_comp_simscape_de_diag_masses) and the force sensor outputs (Figure ref:fig:test_nhexa_comp_simscape_Vs_diag_masses).
The observed shift of the suspension modes to lower frequencies with increased payload mass is well represented by the Simscape model.
The complex conjugate zeros also well match the experiments both for the encoder outputs (Figure ref:fig:test_nhexa_comp_simscape_de_diag_masses) and the force sensor outputs (Figure ref:fig:test_nhexa_comp_simscape_Vs_diag_masses).
Note that the model displays smaller damping that what is observed experimentally for high values of the payload mass.
Note that the model displays smaller damping than that observed experimentally for high values of the payload mass.
One option could be to tune the damping as a function of the mass (similar to what is done with the Rayleigh damping).
However, as decentralized IFF will be applied, the damping will be brought actively, and the open-loop damping value should have very little impact on the obtained plant.
However, as decentralized IFF will be applied, the damping is actively brought, and the open-loop damping value should have very little impact on the obtained plant dynamics.
#+begin_src matlab :exports none
%% Bode plot for the transfer function from u to de
@ -1615,7 +1617,7 @@ exportFig('figs/test_nhexa_comp_simscape_Vs_diag_masses.pdf', 'width', 'half', '
#+end_src
#+name: fig:test_nhexa_comp_simscape_diag_masses
#+caption: Comparison of the diagonal elements (i.e. "direct" terms) of the measured FRF matrix and the identified dynamics from the Simscape model. Both for the dynamics from $u$ to $d_e$ (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from $u$ to $V_s$ (\subref{fig:test_nhexa_comp_simscape_Vs_diag})
#+caption: Comparison of the diagonal elements (i.e. "direct" terms) of the measured FRF matrix and the dynamics identified from the Simscape model. Both for the dynamics from $u$ to $d_e$ (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from $u$ to $V_s$ (\subref{fig:test_nhexa_comp_simscape_Vs_diag})
#+attr_latex: :options [htbp]
#+begin_figure
#+attr_latex: :caption \subcaption{\label{fig:test_nhexa_comp_simscape_de_diag_masses}from $u$ to $d_e$}
@ -1633,8 +1635,8 @@ exportFig('figs/test_nhexa_comp_simscape_Vs_diag_masses.pdf', 'width', 'half', '
#+end_figure
In order to also check if the model well represents the coupling when high payload masses are used, the transfer functions from $u_1$ to $d_{e1}$ to $d_{e6}$ are compared in the case of the 39kg payload in Figure ref:fig:test_nhexa_comp_simscape_de_all_high_mass.
Excellent match between the experimental coupling and the model coupling is observed.
The model therefore well represents the system dynamical coupling for different considered payloads.
Excellent match between experimental and model coupling is observed.
Therefore, the model effectively represents the system coupling for different payloads.
#+begin_src matlab :exports none
%% Comparison of the plants (encoder output) when tuning the misalignment
@ -1713,7 +1715,7 @@ exportFig('figs/test_nhexa_comp_simscape_de_all_high_mass.pdf', 'width', 'full',
#+end_src
#+name: fig:test_nhexa_comp_simscape_de_all_high_mass
#+caption: Comparison of the measured (in blue) and modelled (in red) frequency transfer functions from the first control signal $u_1$ to the six encoders $d_{e1}$ to $d_{e6}$
#+caption: Comparison of the measured (in blue) and modeled (in red) frequency transfer functions from the first control signal $u_1$ to the six encoders $d_{e1}$ to $d_{e6}$
#+RESULTS:
[[file:figs/test_nhexa_comp_simscape_de_all_high_mass.png]]
@ -1725,23 +1727,23 @@ exportFig('figs/test_nhexa_comp_simscape_de_all_high_mass.pdf', 'width', 'full',
As illustrated in this section, the developed Simscape model accurately represents the suspension modes of the Nano-Hexapod.
Both FRF matrices from $\mathbf{u}$ to $\mathbf{V}_s$ and from $\mathbf{u}$ to $\mathbf{d}_e$ are well matching with the measurements, even when considering coupling (i.e. off-diagonal) terms, which are very important from a control perspective.
At frequency above the suspension modes, the Nano-Hexapod model becomes inaccurate as the flexible modes are not modelled.
It was shown that modelling the APA300ML using a "super-element" allows to model the internal resonances of the struts.
The same could be done with the top platform and the encoder supports, but the model order would be higher and may become unpractical for simulation purposes.
At frequencies above the suspension modes, the Nano-Hexapod model became inaccurate because the flexible modes were not modeled.
It was found that modeling the APA300ML using a "super-element" allows to model the internal resonances of the struts.
The same can be done with the top platform and the encoder supports; however, the model order would be higher and may become unpractical for simulation.
* Conclusion
The goal of this test bench was to obtain an accurate model of the nano-hexapod that can then be included on top of the micro-station model.
The goal of this test bench was to obtain an accurate model of the nano-hexapod that could then be included on top of the micro-station model.
This strategy was to measure the nano-hexapod in conditions where all factors that could have impacted the nano-hexapod dynamics were taken into account.
This was done by developing a suspended table with low frequency suspension modes which can be accurately modelled.
This strategy was to identify the nano-hexapod dynamics under conditions in which all factors that could have affected the nano-hexapod dynamics were considered.
This was achieved by developing a suspended table with low frequency suspension modes that can be accurately modeled.
While the dynamics of the nano-hexapod was indeed impacted by the dynamics of the suspended platform, this impact was also taken into account in the Simscape model, and a good match was obtained.
Although the dynamics of the nano-hexapod was indeed impacted by the dynamics of the suspended platform, this impact was also considered in the Simscape model, and a good match was obtained.
Obtaining a model accurately representing the complex dynamics of the Nano-Hexapod was made possible by the modelling approach used during this work.
This approach consisted of tuning and validating models of individual components (such as the APA and flexible joints) using dedicated test benches.
Only then, the different models could be combined to form the Nano-Hexapod dynamical model.
If a model of the nano-hexapod was developed in one time, it would be difficult to tune all model parameters to match the measured dynamics, or even to know if the model "structure" would be adequate to represents the system dynamics.
Obtaining a model that accurately represents the complex dynamics of the Nano-Hexapod was made possible by the modeling approach used in this study.
This approach involved tuning and validating models of individual components (such as the APA and flexible joints) using dedicated test benches.
The different models could then be combined to form the Nano-Hexapod dynamical model.
If a model of the nano-hexapod was developed in one time, it would be difficult to tune all the model parameters to match the measured dynamics, or even to know if the model "structure" would be adequate to represent the system dynamics.
* Bibliography :ignore:
#+latex: \printbibliography[heading=bibintoc,title={Bibliography}]
@ -2191,6 +2193,6 @@ end
[fn:6]"SZ8005 20 x 044" from Steinel. The spring rate is specified at $17.8\,N/mm$
[fn:5]The 450 mm x 450 mm x 60 mm Nexus B4545A from Thorlabs.
[fn:4]As the accuracy of the FARO arm is $\pm 13\,\mu m$, the true straightness is probably better than the values indicated. The limitation of the instrument is here reached.
[fn:3]The height dimension is better than $40\,\mu m$. The diameter fit of 182g6 and 24g6 with the two plates is verified.
[fn:2]Location of all the interface surfaces with the flexible joints are checked. The fits (182H7 and 24H8) with the interface element are checked.
[fn:3]The height dimension is better than $40\,\mu m$. The diameter fitting of 182g6 and 24g6 with the two plates is verified.
[fn:2]Location of all the interface surfaces with the flexible joints were checked. The fittings (182H7 and 24H8) with the interface element were also checked.
[fn:1]Faro Arm Platinum 4ft, specified accuracy of $\pm 13\mu m$

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@ -1,4 +1,4 @@
% Created 2024-10-29 Tue 15:32
% Created 2024-10-29 Tue 19:17
% Intended LaTeX compiler: pdflatex
\documentclass[a4paper, 10pt, DIV=12, parskip=full, bibliography=totoc]{scrreprt}
@ -24,19 +24,19 @@
\clearpage
In the previous section, all the struts were mounted and individually characterized.
Now the nano-hexapod is assembled using a mounting procedure described in Section \ref{sec:test_nhexa_mounting}.
Prior to the nano-hexapod assembly, all the struts were mounted and individually characterized.
In Section \ref{sec:test_nhexa_mounting}, the assembly procedure of the nano-hexapod is presented.
In order to identify the dynamics of the nano-hexapod, a special suspended table is developed which consists of a stiff ``optical breadboard'' suspended on top of four soft springs.
The Nano-Hexapod is then fixed on top of the suspended table, such that its dynamics is not affected by complex dynamics except from the suspension modes of the table that can be well characterized and modelled (Section \ref{sec:test_nhexa_table}).
To identify the dynamics of the nano-hexapod, a special suspended table was developed, which consisted of a stiff ``optical breadboard'' suspended on top of four soft springs.
The Nano-Hexapod was then fixed on top of the suspended table such that its dynamics is not affected by complex dynamics except from the suspension modes of the table that can be well characterized and modeled (Section \ref{sec:test_nhexa_table}).
The obtained nano-hexapod dynamics is analyzed in Section \ref{sec:test_nhexa_dynamics}, and compared with the Simscape model in Section \ref{sec:test_nhexa_model}.
\chapter{Nano-Hexapod Assembly Procedure}
\label{sec:test_nhexa_mounting}
The assembly of the nano-hexapod is quite critical to both avoid additional stress in the flexible joints (that would result in a loss of stroke) and for the precise determination of the Jacobian matrix.
The goal is to fix the six struts to the two nano-hexapod plates (shown in Figure \ref{fig:test_nhexa_nano_hexapod_plates}) while the two plates are parallel, aligned vertically, and such that all the flexible joints do not experience any stress.
Do to so, a precisely machined mounting tool (Figure \ref{fig:test_nhexa_center_part_hexapod_mounting}) is used to position the two nano-hexapod plates during the assembly procedure.
The assembly of the nano-hexapod is critical for both avoiding additional stress in the flexible joints (that would result in a loss of stroke) and for the precisely determining the Jacobian matrix.
The goal was to fix the six struts to the two nano-hexapod plates (shown in Figure \ref{fig:test_nhexa_nano_hexapod_plates}) while the two plates were parallel and aligned vertically so that all the flexible joints did not experience any stress.
To do so, a precisely machined mounting tool (Figure \ref{fig:test_nhexa_center_part_hexapod_mounting}) is used to position the two nano-hexapod plates during the assembly procedure.
\begin{figure}[htbp]
\begin{subfigure}{0.59\textwidth}
@ -54,10 +54,10 @@ Do to so, a precisely machined mounting tool (Figure \ref{fig:test_nhexa_center_
\caption{\label{fig:test_nhexa_received_parts}Received Nano-Hexapod plates (\subref{fig:test_nhexa_nano_hexapod_plates}) and mounting tool used to position the two plates during assembly (\subref{fig:test_nhexa_center_part_hexapod_mounting})}
\end{figure}
The mechanical tolerances of the received plates are checked using a FARO arm\footnote{Faro Arm Platinum 4ft, specified accuracy of \(\pm 13\mu m\)} (Figure \ref{fig:test_nhexa_plates_tolerances}) and are found to comply with the requirements\footnote{Location of all the interface surfaces with the flexible joints are checked. The fits (182H7 and 24H8) with the interface element are checked.}.
The same is done for the mounting tool\footnote{The height dimension is better than \(40\,\mu m\). The diameter fit of 182g6 and 24g6 with the two plates is verified.}
The two plates are then fixed to the mounting tool as shown in Figure \ref{fig:test_nhexa_mounting_tool_hexapod_top_view}.
The main goal of this ``mounting tool'' is to position the flexible joint interfaces (the ``V'' shapes) of both plates such that a cylinder can rest on the 4 flat interfaces at the same time.
The mechanical tolerances of the received plates were checked using a FARO arm\footnote{Faro Arm Platinum 4ft, specified accuracy of \(\pm 13\mu m\)} (Figure \ref{fig:test_nhexa_plates_tolerances}) and were found to comply with the requirements\footnote{Location of all the interface surfaces with the flexible joints were checked. The fittings (182H7 and 24H8) with the interface element were also checked.}.
The same is done for the mounting tool\footnote{The height dimension is better than \(40\,\mu m\). The diameter fitting of 182g6 and 24g6 with the two plates is verified.}
The two plates were then fixed to the mounting tool, as shown in Figure \ref{fig:test_nhexa_mounting_tool_hexapod_top_view}.
The main goal of this ``mounting tool'' is to position the flexible joint interfaces (the ``V'' shapes) of both plates so that a cylinder can rest on the 4 flat interfaces at the same time.
\begin{figure}[htbp]
\begin{subfigure}{0.49\textwidth}
@ -76,9 +76,9 @@ The main goal of this ``mounting tool'' is to position the flexible joint interf
\end{figure}
The quality of the positioning can be estimated by measuring the ``straightness'' of the top and bottom ``V'' interfaces.
This corresponds to the diameter of the smallest cylinder that contains all points of the measured axis.
This is again done using the FARO arm, and the results for all the six struts are summarized in Table \ref{tab:measured_straightness}.
The straightness is found to be better than \(15\,\mu m\) for all the struts\footnote{As the accuracy of the FARO arm is \(\pm 13\,\mu m\), the true straightness is probably better than the values indicated. The limitation of the instrument is here reached.}, which is sufficiently good to not induce significant stress of the flexible joint during the assembly.
This corresponds to the diameter of the smallest cylinder which contains all points along the measured axis.
This was again done using the FARO arm, and the results for all six struts are summarized in Table \ref{tab:measured_straightness}.
The straightness was found to be better than \(15\,\mu m\) for all struts\footnote{As the accuracy of the FARO arm is \(\pm 13\,\mu m\), the true straightness is probably better than the values indicated. The limitation of the instrument is here reached.}, which is sufficiently good to not induce significant stress of the flexible joint during assembly.
\begin{table}[htbp]
\centering
@ -94,12 +94,11 @@ The straightness is found to be better than \(15\,\mu m\) for all the struts\foo
6 & \(6\, \mu m\) & \(7\, \mu m\)\\
\bottomrule
\end{tabularx}
\caption{\label{tab:measured_straightness}Measured straightness between the two ``V'' for the six struts. These measurements are performed two times for each strut.}
\caption{\label{tab:measured_straightness}Measured straightness between the two ``V'' shapes for the six struts. These measurements were performed twice for each strut.}
\end{table}
The encoder rulers and heads are then fixed to the top and bottom plates respectively (Figure \ref{fig:test_nhexa_mount_encoder}).
The encoder heads are then aligned to maximize the received contrast.
The encoder rulers and heads were then fixed to the top and bottom plates, respectively (Figure \ref{fig:test_nhexa_mount_encoder}), and the encoder heads were aligned to maximize the received contrast.
\begin{figure}[htbp]
\begin{subfigure}{0.49\textwidth}
@ -114,14 +113,14 @@ The encoder heads are then aligned to maximize the received contrast.
\end{center}
\subcaption{\label{fig:test_nhexa_mount_encoder_heads}Encoder heads}
\end{subfigure}
\caption{\label{fig:test_nhexa_mount_encoder}Mounting of the encoders to the Nano-hexapod. The rulers are fixed to the top plate (\subref{fig:test_nhexa_mount_encoder_rulers}) while the encoders heads are fixed to the botom plate (\subref{fig:test_nhexa_mount_encoder_heads})}
\caption{\label{fig:test_nhexa_mount_encoder}Mounting of the encoders to the Nano-hexapod. The rulers are fixed to the top plate (\subref{fig:test_nhexa_mount_encoder_rulers}) while encoders heads are fixed to the bottom plate (\subref{fig:test_nhexa_mount_encoder_heads})}
\end{figure}
The six struts are then fixed to the bottom and top plates one by one.
First the top flexible joint is fixed such that its flat reference surface is in contact with the top plate.
This is to precisely known the position of the flexible joint with respect to the top plate.
Then the bottom flexible joint is fixed.
After all six struts are mounted, the mounting tool (Figure \ref{fig:test_nhexa_center_part_hexapod_mounting}) can be disassembled, and the fully mounted nano-hexapod as shown in Figure \ref{fig:test_nhexa_nano_hexapod_mounted} is obtained.
The six struts were then fixed to the bottom and top plates one by one.
First, the top flexible joint is fixed so that its flat reference surface is in contact with the top plate.
This step precisely determines the position of the flexible joint with respect to the top plate.
The bottom flexible joint is then fixed.
After mounting all six struts, the mounting tool (Figure \ref{fig:test_nhexa_center_part_hexapod_mounting}) can be disassembled, and the nano-hexapod as shown in Figure \ref{fig:test_nhexa_nano_hexapod_mounted} is fully assembled.
\begin{figure}[htbp]
\centering
@ -135,29 +134,29 @@ After all six struts are mounted, the mounting tool (Figure \ref{fig:test_nhexa_
When a dynamical system is fixed to a support (such as a granite or an optical table), its dynamics will couple to the support dynamics.
This may results in additional modes appearing in the system dynamics, which are difficult to predict and model.
Two prevent this issue, strategy adopted here is to mount the nano-hexapod on top a suspended table with low frequency suspension modes.
To prevent this issue, the strategy adopted here is to mount the nano-hexapod on top a suspended table with low frequency suspension modes.
In such a case, the modes of the suspended table are chosen to be at much lower frequency than those of the nano-hexapod such that they are well decoupled.
An other key advantage is that the suspension modes of the suspended table can be easily modelled using Simscape.
Therefore, the measured dynamics of the nano-hexapod on top of the suspended table can be compared to a simscape model representing the same experimental conditions.
In this case, the modes of the suspended table were chosen to be at much lower frequency than those of the nano-hexapod such that good decoupling is obtained.
Another key advantage is that the suspension modes of the table can be easily modeled using Simscape.
Therefore, the measured dynamics of the nano-hexapod on top of the suspended table can be compared to a Simscape model representing the same experimental conditions.
The model of the Nano-Hexapod can thus be precisely tuned to match the measured dynamics.
The developed suspended table is presented in Section \ref{ssec:test_nhexa_table_setup}.
The developed suspended table is described in Section \ref{ssec:test_nhexa_table_setup}.
The modal analysis of the table is done in \ref{ssec:test_nhexa_table_identification}.
Finally, the Simscape model representing the suspended table is tuned to match the measured modes (Section \ref{ssec:test_nhexa_table_model}).
Finally, the Simscape model representing the suspended table was tuned to match the measured modes (Section \ref{ssec:test_nhexa_table_model}).
\section{Experimental Setup}
\label{ssec:test_nhexa_table_setup}
The design of the suspended table is quite straightforward.
First, an optical table with high frequency flexible mode was selected\footnote{The 450 mm x 450 mm x 60 mm Nexus B4545A from Thorlabs.}.
Then, four springs\footnote{``SZ8005 20 x 044'' from Steinel. The spring rate is specified at \(17.8\,N/mm\)} were selected with low enough spring rate such that the suspension modes are below 10Hz.
Then, four springs\footnote{``SZ8005 20 x 044'' from Steinel. The spring rate is specified at \(17.8\,N/mm\)} were selected with low spring rate such that the suspension modes are below 10Hz.
Finally, some interface elements were designed, and mechanical lateral mechanical stops were added (Figure \ref{fig:test_nhexa_suspended_table_cad}).
\begin{figure}[htbp]
\centering
\includegraphics[scale=1,width=0.7\linewidth]{figs/test_nhexa_suspended_table_cad.jpg}
\caption{\label{fig:test_nhexa_suspended_table_cad}CAD View of the vibration table. Purple cylinders are representing the soft springs.}
\caption{\label{fig:test_nhexa_suspended_table_cad}CAD View of the vibration table. The purple cylinders are representing the soft springs.}
\end{figure}
\section{Modal analysis of the suspended table}
@ -166,7 +165,7 @@ Finally, some interface elements were designed, and mechanical lateral mechanica
In order to perform a modal analysis of the suspended table, a total of 15 3-axis accelerometers\footnote{PCB 356B18. Sensitivity is \(1\,V/g\), measurement range is \(\pm 5\,g\) and bandwidth is \(0.5\) to \(5\,\text{kHz}\).} were fixed to the breadboard.
Using an instrumented hammer, the first 9 modes could be identified and are summarized in Table \ref{tab:test_nhexa_suspended_table_modes}.
The first 6 modes are suspension modes (i.e. rigid body mode of the breadboard) and are located below 10Hz.
The next modes are flexible modes of the breadboard as shown in Figure \ref{fig:test_nhexa_table_flexible_modes}, and located above 700Hz.
The next modes are the flexible modes of the breadboard as shown in Figure \ref{fig:test_nhexa_table_flexible_modes}, and are located above 700Hz.
\begin{minipage}[t]{0.45\linewidth}
\begin{center}
@ -224,9 +223,9 @@ The next modes are flexible modes of the breadboard as shown in Figure \ref{fig:
\section{Simscape Model of the suspended table}
\label{ssec:test_nhexa_table_model}
The Simscape model of the suspended table simply consists of two solid bodies connected by 4 springs.
The 4 springs are here modelled with ``bushing joints'' that have stiffness and damping properties in x, y and z directions.
The 3D representation of the model is displayed in Figure \ref{fig:test_nhexa_suspended_table_simscape} where the 4 ``bushing joints'' are represented by the blue cylinders.
The Simscape model of the suspended table consists simply of two solid bodies connected by 4 springs.
The 4 springs are here modeled with ``bushing joints'' that have stiffness and damping properties in x, y, and z directions.
The 3D representation of the model is shown in Figure \ref{fig:test_nhexa_suspended_table_simscape} where the 4 ``bushing joints'' are represented by blue cylinders.
\begin{figure}[htbp]
\centering
@ -234,11 +233,11 @@ The 3D representation of the model is displayed in Figure \ref{fig:test_nhexa_su
\caption{\label{fig:test_nhexa_suspended_table_simscape}3D representation of the simscape model}
\end{figure}
The model order is 12, and it represents the 6 suspension modes.
The inertia properties of the parts are set from the geometry and material densities.
The model order is 12, which corresponds to the 6 suspension modes.
The inertia properties of the parts were determined from the geometry and material densities.
The stiffness of the springs was initially set from the datasheet nominal value of \(17.8\,N/mm\) and then reduced down to \(14\,N/mm\) to better match the measured suspension modes.
The stiffness of the springs in the horizontal plane is set at \(0.5\,N/mm\).
The obtained suspension modes of the simscape model are compared with the measured ones in Table \ref{tab:test_nhexa_suspended_table_simscape_modes}.
The obtained suspension modes of the Simscape model are compared with the measured modes in Table \ref{tab:test_nhexa_suspended_table_simscape_modes}.
\begin{table}[htbp]
\centering
@ -256,17 +255,17 @@ Simscape & 1.3 Hz & 1.8 Hz & 6.8 Hz & 9.5 Hz\\
\section*{Conclusion}
In this section, a suspended table with low frequency suspension modes and high frequency flexible modes was presented.
This suspended table will be used in Section \ref{sec:test_nhexa_dynamics} for dynamical identification of the Nano-Hexapod.
The objective is to be able to accurately identify the dynamics of the nano-hexapod, isolated from complex support dynamics.
The key point of this strategy is to be able to accurately model the suspended table.
This suspended table is used in Section \ref{sec:test_nhexa_dynamics} for dynamical identification of the Nano-Hexapod.
The objective is to accurately identify the dynamics of the nano-hexapod, isolated from complex support dynamics.
The key point of this strategy was the ability to accurately model the suspended table.
To do so, a modal analysis of the suspended table was performed in Section \ref{ssec:test_nhexa_table_identification}, validating the low frequency suspension modes and high frequency flexible modes.
Then, a multi-body model of this suspended table was tuned to match with the measurements (Section \ref{ssec:test_nhexa_table_model}).
Then, a multi-body model of this suspended table was tuned to match the measurements (Section \ref{ssec:test_nhexa_table_model}).
\chapter{Nano-Hexapod Measured Dynamics}
\label{sec:test_nhexa_dynamics}
The Nano-Hexapod is then mounted on top of the suspended table as shown in Figure \ref{fig:test_nhexa_hexa_suspended_table}.
All the instrumentation (Speedgoat with ADC, DAC, piezoelectric voltage amplifiers and digital interfaces for the encoder) are setup and connected to the nano-hexapod using many cables.
The Nano-Hexapod was then mounted on top of the suspended table, as shown in Figure \ref{fig:test_nhexa_hexa_suspended_table}.
All instrumentation (Speedgoat with ADC, DAC, piezoelectric voltage amplifiers and digital interfaces for the encoder) were configured and connected to the nano-hexapod using many cables.
\begin{figure}[htbp]
\centering
@ -275,23 +274,23 @@ All the instrumentation (Speedgoat with ADC, DAC, piezoelectric voltage amplifie
\end{figure}
A modal analysis of the nano-hexapod is first performed in Section \ref{ssec:test_nhexa_enc_struts_modal_analysis}.
It will be used to better understand the measured dynamics from actuators to sensors.
The results of the modal analysis will be useful to better understand the measured dynamics from actuators to sensors.
A block diagram schematic of the (open-loop) system is shown in Figure \ref{fig:test_nhexa_nano_hexapod_signals}.
The transfer function from controlled signals \(\mathbf{u}\) to the force sensors voltages \(\mathbf{V}_s\) and to the encoders measured displacements \(\mathbf{d}_e\) are identified in Section \ref{ssec:test_nhexa_identification}.
The effect of the payload mass on the dynamics is studied in Section \ref{ssec:test_nhexa_added_mass}.
A block diagram of the (open-loop) system is shown in Figure \ref{fig:test_nhexa_nano_hexapod_signals}.
The frequency response functions from controlled signals \(\mathbf{u}\) to the force sensors voltages \(\mathbf{V}_s\) and to the encoders measured displacements \(\mathbf{d}_e\) are experimentally identified in Section \ref{ssec:test_nhexa_identification}.
The effect of the payload mass on the dynamics is discussed in Section \ref{ssec:test_nhexa_added_mass}.
\begin{figure}[htbp]
\centering
\includegraphics[scale=1,scale=1]{figs/test_nhexa_nano_hexapod_signals.png}
\caption{\label{fig:test_nhexa_nano_hexapod_signals}Block diagram of the system. Command signal generated by the speedgoat is \(\mathbf{u}\), the measured dignals are \(\mathbf{d}_{e}\) and \(\mathbf{V}_s\). Units are indicated in square brackets.}
\caption{\label{fig:test_nhexa_nano_hexapod_signals}Block diagram of the studied system. The command signal generated by the speedgoat is \(\mathbf{u}\), and the measured dignals are \(\mathbf{d}_{e}\) and \(\mathbf{V}_s\). Units are indicated in square brackets.}
\end{figure}
\section{Modal analysis}
\label{ssec:test_nhexa_enc_struts_modal_analysis}
In order to ease the future analysis of the measured plant dynamics, a basic modal analysis of the nano-hexapod is performed.
Five 3-axis accelerometers are fixed on the top platform of the nano-hexapod (Figure \ref{fig:test_nhexa_modal_analysis}) and the top platform is excited using an instrumented hammer.
To facilitate the future analysis of the measured plant dynamics, a basic modal analysis of the nano-hexapod is performed.
Five 3-axis accelerometers were fixed on the top platform of the nano-hexapod (Figure \ref{fig:test_nhexa_modal_analysis}) and the top platform was excited using an instrumented hammer.
\begin{figure}[htbp]
\centering
@ -299,8 +298,8 @@ Five 3-axis accelerometers are fixed on the top platform of the nano-hexapod (Fi
\caption{\label{fig:test_nhexa_modal_analysis}Five accelerometers fixed on top of the nano-hexapod to perform a modal analysis}
\end{figure}
Between 100Hz and 200Hz, 6 suspension modes (i.e. rigid body modes of the top platform) are identified.
At around 700Hz, two flexible modes of the top plate are observed (see Figure \ref{fig:test_nhexa_hexa_flexible_modes}).
Between 100Hz and 200Hz, 6 suspension modes (i.e. rigid body modes of the top platform) were identified.
At around 700Hz, two flexible modes of the top plate were observed (see Figure \ref{fig:test_nhexa_hexa_flexible_modes}).
These modes are summarized in Table \ref{tab:test_nhexa_hexa_modal_modes_list}.
\begin{table}[htbp]
@ -342,48 +341,48 @@ These modes are summarized in Table \ref{tab:test_nhexa_hexa_modal_modes_list}.
\section{Identification of the dynamics}
\label{ssec:test_nhexa_identification}
The dynamics of the nano-hexapod from the six command signals (\(u_1\) to \(u_6\)) the six measured displacement by the encoders (\(d_{e1}\) to \(d_{e6}\)) and to the six force sensors (\(V_{s1}\) to \(V_{s6}\)) are identified by generating a low pass filtered white noise for each of the command signals, one by one.
The dynamics of the nano-hexapod from the six command signals (\(u_1\) to \(u_6\)) to the six measured displacement by the encoders (\(d_{e1}\) to \(d_{e6}\)) and to the six force sensors (\(V_{s1}\) to \(V_{s6}\)) were identified by generating low-pass filtered white noise for each command signal, one by one.
The \(6 \times 6\) FRF matrix from \(\mathbf{u}\) ot \(\mathbf{d}_e\) is shown in Figure \ref{fig:test_nhexa_identified_frf_de}.
The diagonal terms are displayed using colorful lines, and all the 30 off-diagonal terms are displayed by grey lines.
The diagonal terms are displayed using colored lines, and all the 30 off-diagonal terms are displayed by gray lines.
All the six diagonal terms are well superimposed up to at least \(1\,kHz\), indicating good manufacturing and mounting uniformity.
Below the first suspension mode, good decoupling can be observed (the amplitude of the all of off-diagonal terms are \(\approx 20\) times smaller than the diagonal terms).
All six diagonal terms are well superimposed up to at least \(1\,kHz\), indicating good manufacturing and mounting uniformity.
Below the first suspension mode, good decoupling can be observed (the amplitude of all off-diagonal terms are \(\approx 20\) times smaller than the diagonal terms).
From 10Hz up to 1kHz, around 10 resonance frequencies can be observed.
The first 4 are suspension modes (at 122Hz, 143Hz, 165Hz and 191Hz) which correlate the modes measured during the modal analysis in Section \ref{ssec:test_nhexa_enc_struts_modal_analysis}.
Then, three modes at 237Hz, 349Hz and 395Hz are attributed to the internal strut resonances (this will be checked in Section \ref{ssec:test_nhexa_comp_model_coupling}).
Except the mode at 237Hz, their amplitude is rather low.
Two modes at 665Hz and 695Hz are attributed to the flexible modes of the top platform.
Three modes at 237Hz, 349Hz and 395Hz are attributed to the internal strut resonances (this will be checked in Section \ref{ssec:test_nhexa_comp_model_coupling}).
Except for the mode at 237Hz, their impact on the dynamics is small.
The two modes at 665Hz and 695Hz are attributed to the flexible modes of the top platform.
Other modes can be observed above 1kHz, which can be attributed to flexible modes of the encoder supports or to flexible modes of the top platform.
Up to at least 1kHz, an alternating pole/zero pattern is observed, which renders the control easier to tune.
This would not have been the case if the encoders were fixed to the struts.
Up to at least 1kHz, an alternating pole/zero pattern is observed, which makes the control easier to tune.
This would not have occurred if the encoders were fixed to the struts.
\begin{figure}[htbp]
\centering
\includegraphics[scale=1]{figs/test_nhexa_identified_frf_de.png}
\caption{\label{fig:test_nhexa_identified_frf_de}Measured FRF for the transfer function from \(\mathbf{u}\) to \(\mathbf{d}_e\). The 6 diagonal terms are the colorfull lines (all superimposed), and the 30 off-diagonal terms are the shaded black lines.}
\caption{\label{fig:test_nhexa_identified_frf_de}Measured FRF for the transfer function from \(\mathbf{u}\) to \(\mathbf{d}_e\). The 6 diagonal terms are the colored lines (all superimposed), and the 30 off-diagonal terms are the gray lines.}
\end{figure}
Similarly, the \(6 \times 6\) FRF matrix from \(\mathbf{u}\) to \(\mathbf{V}_s\) is shown in Figure \ref{fig:test_nhexa_identified_frf_Vs}.
Alternating poles and zeros is observed up to at least 2kHz, which is a necessary characteristics in order to apply decentralized IFF.
Similar to what was observed for the encoder outputs, all the ``diagonal'' terms are well superimposed, indicating that the same controller can be applied for all the struts.
The first flexible mode of the struts as 235Hz is appearing, and therefore is should be possible to add some damping to this mode using IFF.
Alternating poles and zeros can be observed up to at least 2kHz, which is a necessary characteristics for applying decentralized IFF.
Similar to what was observed for the encoder outputs, all the ``diagonal'' terms are well superimposed, indicating that the same controller can be applied to all the struts.
The first flexible mode of the struts as 235Hz has large amplitude, and therefore, it should be possible to add some damping to this mode using IFF.
\begin{figure}[htbp]
\centering
\includegraphics[scale=1]{figs/test_nhexa_identified_frf_Vs.png}
\caption{\label{fig:test_nhexa_identified_frf_Vs}Measured FRF for the transfer function from \(\mathbf{u}\) to \(\mathbf{V}_s\). The 6 diagonal terms are the colorfull lines (all superimposed), and the 30 off-diagonal terms are the shaded black lines.}
\caption{\label{fig:test_nhexa_identified_frf_Vs}Measured FRF for the transfer function from \(\mathbf{u}\) to \(\mathbf{V}_s\). The 6 diagonal terms are the colored lines (all superimposed), and the 30 off-diagonal terms are the shaded black lines.}
\end{figure}
\section{Effect of payload mass on the dynamics}
\label{ssec:test_nhexa_added_mass}
As one major challenge in the control of the NASS is the wanted robustness to change of payload mass, it is necessary to understand how the dynamics of the nano-hexapod changes with a change of payload mass.
One major challenge in the control of the NASS is the wanted robustness to a change of payload mass; therefore, it is necessary to understand how the dynamics of the nano-hexapod changes with a change in payload mass.
In order to study this change of dynamics with the payload mass, up to three ``cylindrical masses'' of \(13\,kg\) each can be added for a total of \(\approx 40\,kg\).
To study how the dynamics changes with the payload mass, up to three ``cylindrical masses'' of \(13\,kg\) each can be added for a total of \(\approx 40\,kg\).
These three cylindrical masses on top of the nano-hexapod are shown in Figure \ref{fig:test_nhexa_table_mass_3}.
\begin{figure}[htbp]
@ -392,21 +391,20 @@ These three cylindrical masses on top of the nano-hexapod are shown in Figure \r
\caption{\label{fig:test_nhexa_table_mass_3}Picture of the nano-hexapod with the added three cylindrical masses for a total of \(\approx 40\,kg\)}
\end{figure}
The identified dynamics are then saved for further use.
The obtained frequency response functions from actuator signal \(u_i\) to the associated encoder \(d_{ei}\) for the four payload conditions (no mass, 13kg, 26kg and 39kg) are shown in Figure \ref{fig:test_nhexa_identified_frf_de_masses}.
As expected, the frequency of the suspension modes are decreasing with an increase of the payload mass.
The low frequency gain does not change as it is linked to the stiffness property of the nano-hexapod, and not to its mass property.
As expected, the frequency of the suspension modes decreased with increasing payload mass.
The low frequency gain does not change because it is linked to the stiffness property of the nano-hexapod and not to its mass property.
The frequencies of the two flexible modes of the top plate are first decreased a lot when the first mass is added (from \(\approx 700\,Hz\) to \(\approx 400\,Hz\)).
This is due to the fact that the added mass is composed of two half cylinders which are not fixed together.
It therefore adds a lot of mass to the top plate without adding stiffness in one direction.
When more than one ``mass layer'' is added, the half cylinders are added with some angles such that rigidity are added in all directions (see how the three mass ``layers'' are positioned in Figure \ref{fig:test_nhexa_table_mass_3}).
In that case, the frequency of these flexible modes are increased.
In practice, the payload should be one solid body, and no decrease of the frequency of this flexible mode should be observed.
The apparent amplitude of the flexible mode of the strut at 237Hz becomes smaller as the payload mass is increased.
The frequencies of the two flexible modes of the top plate first decreased significantly when the first mass was added (from \(\approx 700\,Hz\) to \(\approx 400\,Hz\)).
This is because the added mass is composed of two half cylinders that are not fixed together.
Therefore, it adds a lot of mass to the top plate without increasing stiffness in one direction.
When more than one ``mass layer'' is added, the half cylinders are added at some angles such that rigidity is added in all directions (see how the three mass ``layers'' are positioned in Figure \ref{fig:test_nhexa_table_mass_3}).
In this case, the frequency of these flexible modes is increased.
In practice, the payload should be one solid body, and no decrease in the frequency of this flexible mode should be observed.
The apparent amplitude of the flexible mode of the strut at 237Hz becomes smaller as the payload mass increased.
The measured FRF from \(u_i\) to \(V_{si}\) are shown in Figure \ref{fig:test_nhexa_identified_frf_Vs_masses}.
For all the tested payloads, the measured FRF always have alternating poles and zeros, indicating that IFF can be applied in a robust way.
The measured FRFs from \(u_i\) to \(V_{si}\) are shown in Figure \ref{fig:test_nhexa_identified_frf_Vs_masses}.
For all tested payloads, the measured FRF always have alternating poles and zeros, indicating that IFF can be applied in a robust manner.
\begin{figure}[htbp]
\begin{subfigure}{0.49\textwidth}
@ -428,20 +426,19 @@ For all the tested payloads, the measured FRF always have alternating poles and
After the Nano-Hexapod was fixed on top of the suspended table, its dynamics was identified.
The frequency response functions from the six DAC voltages \(\mathbf{u}\) to the six encoders measured displacements \(\mathbf{d}_e\) displays alternating complex conjugate poles and complex conjugate zeros up to at least 1kHz.
At low frequency, the coupling is small, indicating correct assembly of all parts.
This should enables the design of a decentralized positioning controller based on the encoder for relative positioning purposes.
The suspension modes and flexible modes measured during the modal analysis (Section \ref{ssec:test_nhexa_enc_struts_modal_analysis}) are also observed in the dynamics.
Lot's of other modes are present above 700Hz, which will inevitably limit the achievable bandwidth.
The observed effect of the payload's mass on the dynamics is quite large, which also represent a complex control challenge.
At low frequencies, the coupling is small, indicating the correct assembly of all parts.
This should enable the design of a decentralized positioning controller based on the encoders for relative positioning purposes.
The suspension and flexible modes measured during the modal analysis (Section \ref{ssec:test_nhexa_enc_struts_modal_analysis}) are also observed in the dynamics.
Many other modes are present above 700Hz, which will inevitably limit the achievable bandwidth.
The observed effect of the payload's mass on the dynamics was quite large, which also represents a complex control challenge.
The frequency response functions from the six DAC voltages \(\mathbf{u}\) to the six force sensors voltages \(\mathbf{V}_s\) all have alternating complex conjugate poles and complex conjugate zeros.
This indicates that it should be possible to implement decentralized Integral Force Feedback in a robust way.
This alternating property holds for all the tested payloads.
The frequency response functions from the six DAC voltages \(\mathbf{u}\) to the six force sensors voltages \(\mathbf{V}_s\) all have alternating complex conjugate poles and complex conjugate zeros for all the tested payloads.
This indicates that it is possible to implement decentralized Integral Force Feedback in a robust manner.
\chapter{Nano-Hexapod Model Dynamics}
\label{sec:test_nhexa_model}
In this section, the measured dynamics done in Section \ref{sec:test_nhexa_dynamics} is compared with the dynamics estimated from the Simscape model.
The nano-hexapod simscape model is therefore added on top of the vibration table Simscape model as shown in Figure \ref{fig:test_nhexa_hexa_simscape}.
In this section, the dynamics measured in Section \ref{sec:test_nhexa_dynamics} is compared with those estimated from the Simscape model.
The nano-hexapod simscape model was therefore added on top of the vibration table Simscape model, as shown in Figure \ref{fig:test_nhexa_hexa_simscape}.
\begin{figure}[htbp]
\centering
@ -450,7 +447,7 @@ The nano-hexapod simscape model is therefore added on top of the vibration table
\end{figure}
The model should exhibit certain characteristics that are verified in this section.
First, it should match the measured system dynamics from actuators to sensors that were presented in Section \ref{sec:test_nhexa_dynamics}.
First, it should match the measured system dynamics from actuators to sensors presented in Section \ref{sec:test_nhexa_dynamics}.
Both the ``direct'' terms (Section \ref{ssec:test_nhexa_comp_model}) and ``coupling'' terms (Section \ref{ssec:test_nhexa_comp_model_coupling}) of the Simscape model are compared with the measured dynamics.
Second, it should also represents how the system dynamics changes when a payload is fixed to the top platform.
This is checked in Section \ref{ssec:test_nhexa_comp_model_masses}.
@ -458,16 +455,16 @@ This is checked in Section \ref{ssec:test_nhexa_comp_model_masses}.
\section{Nano-Hexapod model dynamics}
\label{ssec:test_nhexa_comp_model}
The Simscape model of the nano-hexapod is first configured with 4-DoF flexible joints, 2-DoF APA and rigid top and bottom platforms.
The stiffness of the flexible joints are chosen based on the values estimated using the test bench and based on FEM.
The parameters of the APA model are the ones determined from the test bench of the APA.
The \(6 \times 6\) transfer function matrices from \(\mathbf{u}\) to \(\mathbf{d}_e\) and from \(\mathbf{u}\) to \(\mathbf{V}_s\) are extracted then from the Simscape model.
The Simscape model of the nano-hexapod was first configured with 4-DoF flexible joints, 2-DoF APA, and rigid top and bottom plates.
The stiffness values of the flexible joints were chosen based on the values estimated using the test bench and on the FEM.
The parameters of the APA model were determined from the test bench of the APA.
The \(6 \times 6\) transfer function matrices from \(\mathbf{u}\) to \(\mathbf{d}_e\) and from \(\mathbf{u}\) to \(\mathbf{V}_s\) are then extracted from the Simscape model.
A first feature that should be checked is that the model well represents the ``direct'' terms of the measured FRF matrix.
First, is it evaluated how well the models matches the ``direct'' terms of the measured FRF matrix.
To do so, the diagonal terms of the extracted transfer function matrices are compared with the measured FRF in Figure \ref{fig:test_nhexa_comp_simscape_diag}.
It can be seen that the 4 suspension modes of the nano-hexapod (at 122Hz, 143Hz, 165Hz and 191Hz) are well modelled.
The three resonances that were attributed to ``internal'' flexible modes of the struts (at 237Hz, 349Hz and 395Hz) cannot be seen in the model, which is reasonable as the APA are here modelled as a simple uniaxial 2-DoF system.
At higher frequencies, no resonances can be seen in the model, as the as the top plate and the encoder supports are modelled as rigid bodies.
It can be seen that the 4 suspension modes of the nano-hexapod (at 122Hz, 143Hz, 165Hz and 191Hz) are well modeled.
The three resonances that were attributed to ``internal'' flexible modes of the struts (at 237Hz, 349Hz and 395Hz) cannot be seen in the model, which is reasonable because the APAs are here modeled as a simple uniaxial 2-DoF system.
At higher frequencies, no resonances can be observed in the model, as the top plate and the encoder supports are modeled as rigid bodies.
\begin{figure}[htbp]
\begin{subfigure}{0.49\textwidth}
@ -482,46 +479,46 @@ At higher frequencies, no resonances can be seen in the model, as the as the top
\end{center}
\subcaption{\label{fig:test_nhexa_comp_simscape_Vs_diag}from $u$ to $V_s$}
\end{subfigure}
\caption{\label{fig:test_nhexa_comp_simscape_diag}Comparison of the diagonal elements (i.e. ``direct'' terms) of the measured FRF matrix and the identified dynamics from the Simscape model. Both for the dynamics from \(u\) to \(d_e\) (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from \(u\) to \(V_s\) (\subref{fig:test_nhexa_comp_simscape_Vs_diag})}
\caption{\label{fig:test_nhexa_comp_simscape_diag}Comparison of the diagonal elements (i.e. ``direct'' terms) of the measured FRF matrix and the dynamics identified from the Simscape model. Both for the dynamics from \(u\) to \(d_e\) (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from \(u\) to \(V_s\) (\subref{fig:test_nhexa_comp_simscape_Vs_diag})}
\end{figure}
\section{Modelling dynamical coupling}
\section{Modeling dynamical coupling}
\label{ssec:test_nhexa_comp_model_coupling}
Another wanted feature of the model is that it well represents the coupling in the system as this is often the limiting factor for the control of MIMO systems.
Another desired feature of the model is that it effectively represents coupling in the system, as this is often the limiting factor for the control of MIMO systems.
Instead of comparing the full 36 elements of the \(6 \times 6\) FFR matrix from \(\mathbf{u}\) to \(\mathbf{d}_e\), only the first ``column'' is compared (Figure \ref{fig:test_nhexa_comp_simscape_de_all}), which corresponds to the transfer function from the command \(u_1\) to the six measured encoder displacements \(d_{e1}\) to \(d_{e6}\).
It can be seen that the coupling in the model is well matching the measurements up to the first un-modelled flexible mode at 237Hz.
Similar results are observed for all the other coupling terms, as well as for the transfer function from \(\mathbf{u}\) to \(\mathbf{V}_s\).
It can be seen that the coupling in the model matches the measurements well up to the first un-modeled flexible mode at 237Hz.
Similar results are observed for all other coupling terms and for the transfer function from \(\mathbf{u}\) to \(\mathbf{V}_s\).
\begin{figure}[htbp]
\centering
\includegraphics[scale=1]{figs/test_nhexa_comp_simscape_de_all.png}
\caption{\label{fig:test_nhexa_comp_simscape_de_all}Comparison of the measured (in blue) and modelled (in red) frequency transfer functions from the first control signal \(u_1\) to the six encoders \(d_{e1}\) to \(d_{e6}\)}
\caption{\label{fig:test_nhexa_comp_simscape_de_all}Comparison of the measured (in blue) and modeled (in red) frequency transfer functions from the first control signal \(u_1\) to the six encoders \(d_{e1}\) to \(d_{e6}\)}
\end{figure}
The APA300ML are then modelled with a \emph{super-element} extracted from a FE-software.
The APA300ML was then modeled with a \emph{super-element} extracted from a FE-software.
The obtained transfer functions from \(u_1\) to the six measured encoder displacements \(d_{e1}\) to \(d_{e6}\) are compared with the measured FRF in Figure \ref{fig:test_nhexa_comp_simscape_de_all_flex}.
While the damping of the suspension modes for the \emph{super-element} is underestimated (which could be solved by properly tuning the proportional damping coefficients), the flexible modes of the struts at 237Hz and 349Hz are well modelled.
While the damping of the suspension modes for the \emph{super-element} is underestimated (which could be solved by properly tuning the proportional damping coefficients), the flexible modes of the struts at 237Hz and 349Hz are well modeled.
Even the mode 395Hz can be observed in the model.
Therefore, if the modes of the struts are to be modelled, the \emph{super-element} of the APA300ML may be used, at the cost of obtaining a much higher order model.
Therefore, if the modes of the struts are to be modeled, the \emph{super-element} of the APA300ML can be used at the cost of obtaining a much higher order model.
\begin{figure}[htbp]
\centering
\includegraphics[scale=1]{figs/test_nhexa_comp_simscape_de_all_flex.png}
\caption{\label{fig:test_nhexa_comp_simscape_de_all_flex}Comparison of the measured (in blue) and modelled (in red) frequency transfer functions from the first control signal \(u_1\) to the six encoders \(d_{e1}\) to \(d_{e6}\)}
\caption{\label{fig:test_nhexa_comp_simscape_de_all_flex}Comparison of the measured (in blue) and modeled (in red) frequency transfer functions from the first control signal \(u_1\) to the six encoders \(d_{e1}\) to \(d_{e6}\)}
\end{figure}
\section{Modelling the effect of payload mass}
\section{Modeling the effect of payload mass}
\label{ssec:test_nhexa_comp_model_masses}
Another important characteristics of the model is that it should well represents the dynamics of the system for all considered payloads.
Another important characteristic of the model is that it should represents the dynamics of the system well for all considered payloads.
The model dynamics is therefore compared with the measured dynamics for 4 payloads (no payload, 13kg, 26kg and 39kg) in Figure \ref{fig:test_nhexa_comp_simscape_diag_masses}.
The observed shift to lower frequency of the suspension modes with an increased payload mass is well represented by the Simscape model.
The complex conjugate zeros are also well matching with the experiments both for the encoder outputs (Figure \ref{fig:test_nhexa_comp_simscape_de_diag_masses}) and the force sensor outputs (Figure \ref{fig:test_nhexa_comp_simscape_Vs_diag_masses}).
The observed shift of the suspension modes to lower frequencies with increased payload mass is well represented by the Simscape model.
The complex conjugate zeros also well match the experiments both for the encoder outputs (Figure \ref{fig:test_nhexa_comp_simscape_de_diag_masses}) and the force sensor outputs (Figure \ref{fig:test_nhexa_comp_simscape_Vs_diag_masses}).
Note that the model displays smaller damping that what is observed experimentally for high values of the payload mass.
Note that the model displays smaller damping than that observed experimentally for high values of the payload mass.
One option could be to tune the damping as a function of the mass (similar to what is done with the Rayleigh damping).
However, as decentralized IFF will be applied, the damping will be brought actively, and the open-loop damping value should have very little impact on the obtained plant.
However, as decentralized IFF will be applied, the damping is actively brought, and the open-loop damping value should have very little impact on the obtained plant dynamics.
\begin{figure}[htbp]
\begin{subfigure}{0.49\textwidth}
@ -536,40 +533,40 @@ However, as decentralized IFF will be applied, the damping will be brought activ
\end{center}
\subcaption{\label{fig:test_nhexa_comp_simscape_Vs_diag_masses}from $u$ to $V_s$}
\end{subfigure}
\caption{\label{fig:test_nhexa_comp_simscape_diag_masses}Comparison of the diagonal elements (i.e. ``direct'' terms) of the measured FRF matrix and the identified dynamics from the Simscape model. Both for the dynamics from \(u\) to \(d_e\) (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from \(u\) to \(V_s\) (\subref{fig:test_nhexa_comp_simscape_Vs_diag})}
\caption{\label{fig:test_nhexa_comp_simscape_diag_masses}Comparison of the diagonal elements (i.e. ``direct'' terms) of the measured FRF matrix and the dynamics identified from the Simscape model. Both for the dynamics from \(u\) to \(d_e\) (\subref{fig:test_nhexa_comp_simscape_de_diag}) and from \(u\) to \(V_s\) (\subref{fig:test_nhexa_comp_simscape_Vs_diag})}
\end{figure}
In order to also check if the model well represents the coupling when high payload masses are used, the transfer functions from \(u_1\) to \(d_{e1}\) to \(d_{e6}\) are compared in the case of the 39kg payload in Figure \ref{fig:test_nhexa_comp_simscape_de_all_high_mass}.
Excellent match between the experimental coupling and the model coupling is observed.
The model therefore well represents the system dynamical coupling for different considered payloads.
Excellent match between experimental and model coupling is observed.
Therefore, the model effectively represents the system coupling for different payloads.
\begin{figure}[htbp]
\centering
\includegraphics[scale=1]{figs/test_nhexa_comp_simscape_de_all_high_mass.png}
\caption{\label{fig:test_nhexa_comp_simscape_de_all_high_mass}Comparison of the measured (in blue) and modelled (in red) frequency transfer functions from the first control signal \(u_1\) to the six encoders \(d_{e1}\) to \(d_{e6}\)}
\caption{\label{fig:test_nhexa_comp_simscape_de_all_high_mass}Comparison of the measured (in blue) and modeled (in red) frequency transfer functions from the first control signal \(u_1\) to the six encoders \(d_{e1}\) to \(d_{e6}\)}
\end{figure}
\section*{Conclusion}
As illustrated in this section, the developed Simscape model accurately represents the suspension modes of the Nano-Hexapod.
Both FRF matrices from \(\mathbf{u}\) to \(\mathbf{V}_s\) and from \(\mathbf{u}\) to \(\mathbf{d}_e\) are well matching with the measurements, even when considering coupling (i.e. off-diagonal) terms, which are very important from a control perspective.
At frequency above the suspension modes, the Nano-Hexapod model becomes inaccurate as the flexible modes are not modelled.
It was shown that modelling the APA300ML using a ``super-element'' allows to model the internal resonances of the struts.
The same could be done with the top platform and the encoder supports, but the model order would be higher and may become unpractical for simulation purposes.
At frequencies above the suspension modes, the Nano-Hexapod model became inaccurate because the flexible modes were not modeled.
It was found that modeling the APA300ML using a ``super-element'' allows to model the internal resonances of the struts.
The same can be done with the top platform and the encoder supports; however, the model order would be higher and may become unpractical for simulation.
\chapter{Conclusion}
The goal of this test bench was to obtain an accurate model of the nano-hexapod that can then be included on top of the micro-station model.
The goal of this test bench was to obtain an accurate model of the nano-hexapod that could then be included on top of the micro-station model.
This strategy was to measure the nano-hexapod in conditions where all factors that could have impacted the nano-hexapod dynamics were taken into account.
This was done by developing a suspended table with low frequency suspension modes which can be accurately modelled.
This strategy was to identify the nano-hexapod dynamics under conditions in which all factors that could have affected the nano-hexapod dynamics were considered.
This was achieved by developing a suspended table with low frequency suspension modes that can be accurately modeled.
While the dynamics of the nano-hexapod was indeed impacted by the dynamics of the suspended platform, this impact was also taken into account in the Simscape model, and a good match was obtained.
Although the dynamics of the nano-hexapod was indeed impacted by the dynamics of the suspended platform, this impact was also considered in the Simscape model, and a good match was obtained.
Obtaining a model accurately representing the complex dynamics of the Nano-Hexapod was made possible by the modelling approach used during this work.
This approach consisted of tuning and validating models of individual components (such as the APA and flexible joints) using dedicated test benches.
Only then, the different models could be combined to form the Nano-Hexapod dynamical model.
If a model of the nano-hexapod was developed in one time, it would be difficult to tune all model parameters to match the measured dynamics, or even to know if the model ``structure'' would be adequate to represents the system dynamics.
Obtaining a model that accurately represents the complex dynamics of the Nano-Hexapod was made possible by the modeling approach used in this study.
This approach involved tuning and validating models of individual components (such as the APA and flexible joints) using dedicated test benches.
The different models could then be combined to form the Nano-Hexapod dynamical model.
If a model of the nano-hexapod was developed in one time, it would be difficult to tune all the model parameters to match the measured dynamics, or even to know if the model ``structure'' would be adequate to represent the system dynamics.
\printbibliography[heading=bibintoc,title={Bibliography}]