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<h1 class="title">EUSPEN</h1>
<div id="table-of-contents">
<h2>Table of Contents</h2>
<div id="text-table-of-contents">
<ul>
<li><a href="#orge70c9fa">1. Tutorial: Design concepts for sub-micrometer positioning&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_huub_janssen">@huub_janssen</span></span></a>
<ul>
<li><a href="#org4d57dc8">1.1. Positioning Terminology</a></li>
<li><a href="#org09dc82b">1.2. Principles of accuracy</a></li>
<li><a href="#org5d21825">1.3. Case 1 - Estimate the virtual play</a></li>
<li><a href="#org239a118">1.4. Conventional elements for constraining DoFs</a></li>
<li><a href="#orgc0e8d42">1.5. Compliant elements for constraining DoFs</a>
<ul>
<li><a href="#org86cfe7a">1.5.1. Basic leaf springs and folded leaf springs</a></li>
<li><a href="#org0fce8d2">1.5.2. 1dof Parallel Guiding</a></li>
<li><a href="#org5a83ffc">1.5.3. Rotation Compliant Mechanism</a></li>
<li><a href="#org8e46840">1.5.4. Z translation</a></li>
<li><a href="#org768b521">1.5.5. X-Y-Rz Stage</a></li>
<li><a href="#org83869c4">1.5.6. Compliant mechanism with only one fixed dof</a></li>
<li><a href="#org95ef2cf">1.5.7. Summary</a></li>
<li><a href="#orgdea6e81">1.5.8. Examples</a></li>
<li><a href="#org023165e">1.5.9. Mechatronics positioning challenge</a></li>
<li><a href="#org8ba1f18">1.5.10. Case - Play Free parallel Stage</a></li>
</ul>
</li>
<li><a href="#org6ac1615">1.6. Thin plate design</a>
<ul>
<li><a href="#orga184791">1.6.1. Thin plate in torsion</a></li>
<li><a href="#orga980f37">1.6.2. Difference between open and close profile</a></li>
</ul>
</li>
</ul>
</li>
<li><a href="#org722c8d4">2. Keynote: Mechatronic challenges in optical lithography&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_hans_butler">@hans_butler</span></span></a>
<ul>
<li><a href="#orgf01d58f">2.1. Introduction</a></li>
<li><a href="#org04ac4d4">2.2. Chip manufacturing loop</a></li>
<li><a href="#org14e1ab2">2.3. Imaging process - Basics</a></li>
<li><a href="#org77e0820">2.4. From stepper to scanner</a></li>
<li><a href="#org7a7053b">2.5. Dual stage scanners</a></li>
<li><a href="#orgf65e5b1">2.6. Immersion technology</a></li>
<li><a href="#org5413197">2.7. Multiple Patterning</a></li>
<li><a href="#org75d5fa9">2.8. Machine layout</a></li>
<li><a href="#org01e20ab">2.9. EUV Lithography</a></li>
<li><a href="#org3ab05ad">2.10. The future: high-NA EUV</a></li>
<li><a href="#org0d75012">2.11. Challenges for future Optical Lithography machines</a></li>
<li><a href="#org87aad3d">2.12. Conclusion</a></li>
</ul>
</li>
<li><a href="#orgcd72101">3. Designing anti-aliasing-filters for control loops of mechatronic systems regarding the rejection of aliased resonances&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_ulrich_schonhoff">@ulrich_schonhoff</span></span></a>
<ul>
<li><a href="#org796f9c0">3.1. The phenomenon of aliasing of resonances</a></li>
<li><a href="#org7349a1d">3.2. Nature, Modelling and Mitigation of potentially aliasing resonances</a></li>
<li><a href="#org75b474a">3.3. Anti aliasing filter design</a>
<ul>
<li><a href="#orgbefe637">3.3.1. Introduction</a></li>
<li><a href="#org9a11cd5">3.3.2. Concept of equivalent delay</a></li>
<li><a href="#org6fc2424">3.3.3. Budgeting of phase lag</a></li>
<li><a href="#org20609a3">3.3.4. Selecting the filter order</a></li>
<li><a href="#org0a2996e">3.3.5. Reducing the phase lag</a></li>
</ul>
</li>
<li><a href="#orgf86f6b0">3.4. Conclusion</a></li>
</ul>
</li>
<li><a href="#orgc9d2ab6">4. Flexure positioning stage based on delta technology for high precision and dynamic industrial machining applications&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_mikael_bianchi">@mikael_bianchi</span></span></a>
<ul>
<li><a href="#org9bb0e04">4.1. Introduction</a></li>
<li><a href="#orgdb95969">4.2. Design</a>
<ul>
<li><a href="#orga1ed7ab">4.2.1. Description of the Delta robot</a></li>
<li><a href="#org22da605">4.2.2. Modelling and validation of the delta robot</a></li>
<li><a href="#org0577955">4.2.3. Control design for high trajectory tracking</a></li>
<li><a href="#orgb986c00">4.2.4. Electronic board</a></li>
</ul>
</li>
<li><a href="#orgdb37311">4.3. Results</a>
<ul>
<li><a href="#orgd4e788f">4.3.1. Current control</a></li>
<li><a href="#orgc1a2cc2">4.3.2. Trajectory tracking: results with laser interferometer and encoder</a></li>
</ul>
</li>
<li><a href="#org232dfb2">4.4. Conclusion</a></li>
</ul>
</li>
<li><a href="#org994338d">5. Multivariable performance analysis of position-controlled payloads with flexible eigenmodes&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_luca_mettenleiter">@luca_mettenleiter</span></span></a>
<ul>
<li><a href="#org5544143">5.1. Motivation</a></li>
<li><a href="#org9ef976f">5.2. Performance analysis with different sensitivity functions</a></li>
<li><a href="#orgd425b1f">5.3. Example system</a></li>
<li><a href="#org4fe2f03">5.4. Conclusion</a></li>
</ul>
</li>
<li><a href="#orgd103664">6. High-precision motion system design by topology optimization considering additive manufacturing&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_arnoud_delissen">@arnoud_delissen</span></span></a>
<ul>
<li><a href="#orgd50c76f">6.1. Introduction</a></li>
<li><a href="#orge9c19e5">6.2. Case</a></li>
<li><a href="#org9ec1e67">6.3. Manufacturing process</a></li>
<li><a href="#orgd66ab28">6.4. Topology optimization</a></li>
<li><a href="#org8aec71c">6.5. Performance Comparison</a></li>
<li><a href="#org4ac24dc">6.6. Conclusion</a></li>
</ul>
</li>
<li><a href="#org8339350">7. A multivariable experiment design framework for accurate FRF identification of complex systems&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_nic_dirkx">@nic_dirkx</span></span></a>
<ul>
<li><a href="#org99a275f">7.1. Introduction</a></li>
<li><a href="#org8fb5a28">7.2. Role of directions and constrains in multivariable excitation design</a></li>
<li><a href="#orgb94f6c1">7.3. Solving the optimization problem</a></li>
<li><a href="#orgad68ea0">7.4. Experimental validation</a></li>
<li><a href="#orgfc6daca">7.5. Conclusion</a></li>
</ul>
</li>
<li><a href="#org667ea80">8. Keynote: High precision mechatronic approaches for advanced nanopositioning and nanomeasuring technologies&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_eberhard_manske">@eberhard_manske</span></span></a>
<ul>
<li><a href="#org553e8db">8.1. Coordinate Measurement Machines (CMM)</a></li>
<li><a href="#org37bb04e">8.2. Difference between CMM and nano-CMM</a></li>
<li><a href="#orgd233180">8.3. How to do nano-CMM</a></li>
<li><a href="#orgbf2f0e6">8.4. Concept - Minimization of the Abbe Error</a></li>
<li><a href="#orgbebebfa">8.5. Minimization of residual Abbe error</a></li>
<li><a href="#orgce68d81">8.6. Compare of long travel guiding systems</a></li>
<li><a href="#org56ef278">8.7. Extended 6 DoF Abbe comparator principle</a></li>
<li><a href="#orgadc2544">8.8. Practical Realisation</a></li>
<li><a href="#orgba7571a">8.9. Tilt Compensation</a></li>
<li><a href="#orgc5bebce">8.10. Comparison of long travail guiding systems - Bis</a></li>
<li><a href="#orgdd01e46">8.11. Drive concept</a></li>
<li><a href="#orgb627d19">8.12. NPMM-200 with extended measuring volume</a></li>
<li><a href="#org78c9d88">8.13. measurement capability</a></li>
<li><a href="#orgb080103">8.14. Extension of the measuring range (700mm)</a></li>
<li><a href="#org4f4bd8f">8.15. Inverse kinematic concept - Tetrahedrical concept</a></li>
<li><a href="#org5454cab">8.16. Inverse kinematic concept - Scanning probe principle</a></li>
<li><a href="#org5504362">8.17. Inverse kinematic concept - Compact measuring head</a></li>
<li><a href="#org41b2fcb">8.18. Inverse kinematic concept - Scanning probe principle</a></li>
<li><a href="#orgf154e61">8.19. Conclusion</a></li>
</ul>
</li>
<li><a href="#org88525c7">9. Reducing control delay times to enhance dynamic stiffness of magnetic bearings&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_jan_philipp_schmidtmann">@jan_philipp_schmidtmann</span></span></a></li>
<li><a href="#org5f07b1a">10. Digital twins in control: From fault detection to predictive maintenance in precision mechatronics&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_koen_classens">@koen_classens</span></span></a>
<ul>
<li><a href="#org5076a19">10.1. Motivation</a></li>
<li><a href="#orgd70c54c">10.2. Predictive Maintenance</a></li>
<li><a href="#org10f60ea">10.3. Objectives</a></li>
<li><a href="#org339e449">10.4. Null-space based FDI</a></li>
<li><a href="#org7c2ed17">10.5. Roadmap from fault detection to predictive maintenance</a></li>
</ul>
</li>
</ul>
</div>
</div>
<div id="outline-container-orge70c9fa" class="outline-2">
<h2 id="orge70c9fa"><span class="section-number-2">1</span> Tutorial: Design concepts for sub-micrometer positioning&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_huub_janssen">@huub_janssen</span></span></h2>
<div class="outline-text-2" id="text-1">
</div>
<div id="outline-container-org4d57dc8" class="outline-3">
<h3 id="org4d57dc8"><span class="section-number-3">1.1</span> Positioning Terminology</h3>
<div class="outline-text-3" id="text-1-1">
<ul class="org-ul">
<li><b>Accuracy</b>:
Accuracy describes how close the mean result is to the reference value. (Figure <a href="#org57e29de">1</a>)</li>
<li><b>Repeatability</b>:
Repeatability describes the variation between results. (Figure <a href="#org57e29de">1</a>)</li>
<li><b>Resolution</b>:
The resolution of a system is equal to the smallest incremental step that can be made (Figure <a href="#orgb8c95ba">2</a>)</li>
<li><b>Stability</b>:
The stability of a system is the maximum deviation from a constant reference value over time.
The stability is always related to the time frame taken into account. (Figure <a href="#orga0c4984">3</a>)</li>
</ul>
<div id="org57e29de" class="figure">
<p><img src="figs/position_terminology.png" alt="position_terminology.png" />
</p>
<p><span class="figure-number">Figure 1: </span>Accuracy and Repeatability</p>
</div>
<div id="orgb8c95ba" class="figure">
<p><img src="./figs/position_resolution.png" alt="position_resolution.png" />
</p>
<p><span class="figure-number">Figure 2: </span>Position Resolution</p>
</div>
<div id="orga0c4984" class="figure">
<p><img src="./figs/position_stability.png" alt="position_stability.png" />
</p>
<p><span class="figure-number">Figure 3: </span>Position Stability</p>
</div>
</div>
</div>
<div id="outline-container-org09dc82b" class="outline-3">
<h3 id="org09dc82b"><span class="section-number-3">1.2</span> Principles of accuracy</h3>
<div class="outline-text-3" id="text-1-2">
<p>
Limited stiffness, play and friction will induce an hysteresis for a positioning system as shown in Figure <a href="#org1a0ab5f">4</a>.
</p>
<p>
The hysteresis can actually help estimating the play and friction present in the system.
</p>
<div id="org1a0ab5f" class="figure">
<p><img src="figs/stiffness_friction.png" alt="stiffness_friction.png" />
</p>
<p><span class="figure-number">Figure 4: </span>Stiffness, play and Friction</p>
</div>
<p>
Ways to make the hysteresis smaller:
</p>
<ul class="org-ul">
<li>avoid play (=&gt; use compliant elements)</li>
<li>minimize friction</li>
<li>use high stiffness</li>
</ul>
<p>
The position uncertainty of a system can be estimated as follow (Figure <a href="#org740f08f">5</a>):
</p>
\begin{equation}
\text{Position Uncertainty} = \text{play} + 2 \times \text{Virtual Play}
\end{equation}
<p>
where the virtual play can be estimated as follow:
</p>
\begin{equation}
\text{Virtual Play} = \frac{\text{Friction Force}}{\text{Actuator Stiffness}} = \frac{F_w}{c}
\end{equation}
<div id="org740f08f" class="figure">
<p><img src="figs/position_uncertainty.png" alt="position_uncertainty.png" />
</p>
<p><span class="figure-number">Figure 5: </span>Hysterestis, play and virtual play</p>
</div>
<p>
When considering dynamics, the goal is to make the first resonance frequency much higher than the frequency of the wanted motion.
Thus, the general recommendation is then to minimize mass and to increase stiffness.
</p>
<p>
Moreover, we generally want things to be predictable:
</p>
<ul class="org-ul">
<li>constant, preferably no friction.
Note that it is very difficult to make a system with constant friction in practice, so better make a system with no friction.</li>
<li>no play</li>
<li>high stiffness</li>
<li>low pass</li>
</ul>
</div>
</div>
<div id="outline-container-org5d21825" class="outline-3">
<h3 id="org5d21825"><span class="section-number-3">1.3</span> Case 1 - Estimate the virtual play</h3>
<div class="outline-text-3" id="text-1-3">
<p>
Estimate the virtual play of the system in Figure <a href="#org8f2fbfc">6</a> with following characteristics:
</p>
<ul class="org-ul">
<li>Payload: \(m = 20\,kg\)</li>
<li>Friction coefficient in drive direction: \(f = 0.05\)</li>
<li>Table stroke: \(L = 300\,mm\)</li>
<li>Screw spindle inner diameter: \(d = 8\, mm\)</li>
<li>Spindle Material: Stainless steel</li>
</ul>
<div id="org8f2fbfc" class="figure">
<p><img src="./figs/case_1.png" alt="case_1.png" />
</p>
<p><span class="figure-number">Figure 6: </span>Studied system for &ldquo;Case 1&rdquo;</p>
</div>
<p>
First the friction force can be calculated as the vertical mass times the friction coefficient:
</p>
\begin{equation}
F_w = (mg) f
\end{equation}
<p>
Then, the axial stiffness of the screw spindle is computed:
</p>
\begin{equation}
c = \frac{A}{L} E
\end{equation}
<p>
with:
</p>
<ul class="org-ul">
<li>\(A = \pi d^2\) is the screw section area</li>
<li>\(L = 300\,mm\) is the screw length</li>
<li>\(E\) is the Young modulus of stainless steel</li>
</ul>
<p>
And finally:
</p>
\begin{equation}
\text{Virtual Play} = \frac{F_w}{c} \approx 0.6\,\mu m
\end{equation}
</div>
</div>
<div id="outline-container-org239a118" class="outline-3">
<h3 id="org239a118"><span class="section-number-3">1.4</span> Conventional elements for constraining DoFs</h3>
<div class="outline-text-3" id="text-1-4">
<p>
There exist many conventional elements for constraining DoFs.
Some of them are:
</p>
<ul class="org-ul">
<li>Struts with ball joint: 1DoF constrained (Figure <a href="#org7ffe0d1">7</a>)</li>
<li>Ball bearing: 5DoF constrained (Figure <a href="#org7eb26ba">8</a>)</li>
<li>Guide with roller bearing: 4DoF constrained (Figure <a href="#orga536d37">9</a>)</li>
<li>Roller rail guide: 5DoF constrained (Figure <a href="#org0be3769">10</a>)</li>
</ul>
<div id="org7ffe0d1" class="figure">
<p><img src="./figs/ball_joint.png" alt="ball_joint.png" />
</p>
<p><span class="figure-number">Figure 7: </span>Ball Joint</p>
</div>
<div id="org7eb26ba" class="figure">
<p><img src="./figs/ball_bearing.png" alt="ball_bearing.png" />
</p>
<p><span class="figure-number">Figure 8: </span>Ball Bearing</p>
</div>
<div id="orga536d37" class="figure">
<p><img src="./figs/roller_bearing.png" alt="roller_bearing.png" />
</p>
<p><span class="figure-number">Figure 9: </span>Roller Bearing</p>
</div>
<div id="org0be3769" class="figure">
<p><img src="./figs/roller_rail_guide.png" alt="roller_rail_guide.png" />
</p>
<p><span class="figure-number">Figure 10: </span>Roller Rail Guide</p>
</div>
</div>
</div>
<div id="outline-container-orgc0e8d42" class="outline-3">
<h3 id="orgc0e8d42"><span class="section-number-3">1.5</span> Compliant elements for constraining DoFs</h3>
<div class="outline-text-3" id="text-1-5">
</div>
<div id="outline-container-org86cfe7a" class="outline-4">
<h4 id="org86cfe7a"><span class="section-number-4">1.5.1</span> Basic leaf springs and folded leaf springs</h4>
<div class="outline-text-4" id="text-1-5-1">
<p>
An example of a complaint element is shown in Figure <a href="#org8dc71b0">11</a>.
</p>
<div id="org8dc71b0" class="figure">
<p><img src="figs/compliant_1dof.png" alt="compliant_1dof.png" />
</p>
<p><span class="figure-number">Figure 11: </span>Example of 1dof constrained compliant element</p>
</div>
<p>
Other types of compliant elements include:
</p>
<ul class="org-ul">
<li>Leaf spring: constrains 3 dof (Figure <a href="#orge850703">12</a>)</li>
<li>Folded leaf spring: constrains only 1dof (Figure <a href="#orgd534a74">13</a>)
These are generally used in combination with other folded leaf springs.</li>
<li>Flexure pivots: constrains 5 dofs (Figure <a href="#orgc5cb04d">14</a>)</li>
</ul>
<div id="orge850703" class="figure">
<p><img src="./figs/leaf_springs.png" alt="leaf_springs.png" />
</p>
<p><span class="figure-number">Figure 12: </span>Leaf springs</p>
</div>
<div id="orgd534a74" class="figure">
<p><img src="./figs/folded_leaf_springs.png" alt="folded_leaf_springs.png" />
</p>
<p><span class="figure-number">Figure 13: </span>Folded Leaf springs</p>
</div>
<div id="orgc5cb04d" class="figure">
<p><img src="./figs/flexure_pivots.png" alt="flexure_pivots.png" />
</p>
<p><span class="figure-number">Figure 14: </span>Flexure Pivots (5dof constrained)</p>
</div>
</div>
</div>
<div id="outline-container-org0fce8d2" class="outline-4">
<h4 id="org0fce8d2"><span class="section-number-4">1.5.2</span> 1dof Parallel Guiding</h4>
<div class="outline-text-4" id="text-1-5-2">
<p>
Parallel guiding can be made using two leaf springs (Figure <a href="#org350d065">15</a>):
</p>
<ul class="org-ul">
<li>2 parallel leaf springs</li>
<li>Force actuator in center of parallelism (middle of the leaf springs) to avoid coupled rotation</li>
<li><p>
Sag in vertical direction as a function as the horizontal displacement.
This sag is predictible and reproducible:
</p>
\begin{equation}
\delta z = 0.6 \frac{x^2}{L}
\end{equation}</li>
<li>Vertical stiffness negatively affected by displacement</li>
<li>Take care of maximum buckling (Figure <a href="#orge7b7db8">16</a>)</li>
<li>Improve buckling load and Z stiffness by reinforced mid-section (Figure <a href="#org8fa0c61">17</a>)</li>
</ul>
<div id="org350d065" class="figure">
<p><img src="./figs/parallel_guiding.png" alt="parallel_guiding.png" />
</p>
<p><span class="figure-number">Figure 15: </span>Parallel guiding</p>
</div>
<div id="orge7b7db8" class="figure">
<p><img src="./figs/buckling.png" alt="buckling.png" />
</p>
<p><span class="figure-number">Figure 16: </span>Example of bucklink</p>
</div>
<div id="org8fa0c61" class="figure">
<p><img src="./figs/reinforced_leaf_springs.png" alt="reinforced_leaf_springs.png" />
</p>
<p><span class="figure-number">Figure 17: </span>Reinforced leaf springs</p>
</div>
</div>
</div>
<div id="outline-container-org5a83ffc" class="outline-4">
<h4 id="org5a83ffc"><span class="section-number-4">1.5.3</span> Rotation Compliant Mechanism</h4>
<div class="outline-text-4" id="text-1-5-3">
<p>
Figure <a href="#org5b565cd">18</a> shows a rotation compliant mechanism:
</p>
<ul class="org-ul">
<li>3 leaf springs</li>
<li>no sensitive for thermal load on the body: as the central part heat ups and expand, the center line of the rotation stays at the same position</li>
</ul>
<div id="org5b565cd" class="figure">
<p><img src="./figs/rotation_leaf_springs.png" alt="rotation_leaf_springs.png" />
</p>
<p><span class="figure-number">Figure 18: </span>Example of rotation stage using leaf springs</p>
</div>
</div>
</div>
<div id="outline-container-org8e46840" class="outline-4">
<h4 id="org8e46840"><span class="section-number-4">1.5.4</span> Z translation</h4>
<div class="outline-text-4" id="text-1-5-4">
<p>
Figure <a href="#org717c209">19</a> shows a Z translation mechanism:
</p>
<ul class="org-ul">
<li>5 struts (&ldquo;needles&rdquo;)</li>
<li>Not sensitive for thermal loads on body</li>
</ul>
<p>
The problem is that when it moves vertical, there will also be some z rotation because the length of the strut is fixed (stiff).
This parasitic rotation is however predictable.
</p>
<div id="org717c209" class="figure">
<p><img src="./figs/vertical_stage_compliant.png" alt="vertical_stage_compliant.png" />
</p>
<p><span class="figure-number">Figure 19: </span>Z translation using 5 struts</p>
</div>
<p>
An alternative is to use folder leaf springs (Figure <a href="#orgec1f57f">20</a>), and this avoid the parasitic rotation.
</p>
<div id="orgec1f57f" class="figure">
<p><img src="./figs/vertical_stage_leafs.png" alt="vertical_stage_leafs.png" />
</p>
<p><span class="figure-number">Figure 20: </span>Z translation using 5 folded leaf springs</p>
</div>
</div>
</div>
<div id="outline-container-org768b521" class="outline-4">
<h4 id="org768b521"><span class="section-number-4">1.5.5</span> X-Y-Rz Stage</h4>
<div class="outline-text-4" id="text-1-5-5">
<p>
An X-Y-Rz stage can be done either using 3 struts (Figure <a href="#org6d944d8">21</a>) or using 3 folded leaf springs (Figure <a href="#org892297b">22</a>).
</p>
<div id="org6d944d8" class="figure">
<p><img src="./figs/x_y_rz_stage.png" alt="x_y_rz_stage.png" />
</p>
<p><span class="figure-number">Figure 21: </span>X,Y,Rz using 3 struts</p>
</div>
<div id="org892297b" class="figure">
<p><img src="./figs/x_y_rz_leafs.png" alt="x_y_rz_leafs.png" />
</p>
<p><span class="figure-number">Figure 22: </span>X,Y,Rz using 3 folded leaf springs</p>
</div>
</div>
</div>
<div id="outline-container-org83869c4" class="outline-4">
<h4 id="org83869c4"><span class="section-number-4">1.5.6</span> Compliant mechanism with only one fixed dof</h4>
<div class="outline-text-4" id="text-1-5-6">
<p>
The compliant mechanism shown in Figure <a href="#org8297e4a">23</a> only constrain the rotation about the y-axis.
</p>
<div id="org8297e4a" class="figure">
<p><img src="./figs/case_1_leaf_springs.png" alt="case_1_leaf_springs.png" />
</p>
<p><span class="figure-number">Figure 23: </span>5dof motion, only the Ry is constrained</p>
</div>
</div>
</div>
<div id="outline-container-org95ef2cf" class="outline-4">
<h4 id="org95ef2cf"><span class="section-number-4">1.5.7</span> Summary</h4>
<div class="outline-text-4" id="text-1-5-7">
<ul class="org-ul">
<li>compliant elements enable defined movements</li>
<li>Hinges or guidings can be used for small movements</li>
<li><b>No play, No friction, No wear, No contamination</b></li>
<li><b>but limited rotation, need a constant force to hold in place</b></li>
</ul>
</div>
</div>
<div id="outline-container-orgdea6e81" class="outline-4">
<h4 id="orgdea6e81"><span class="section-number-4">1.5.8</span> Examples</h4>
<div class="outline-text-4" id="text-1-5-8">
<p>
An example of a complex compliant mechanism is shown in Figure <a href="#org31f7389">24</a>.
</p>
<div id="org31f7389" class="figure">
<p><img src="./figs/compliant_example_1.png" alt="compliant_example_1.png" />
</p>
<p><span class="figure-number">Figure 24: </span>Design concept</p>
</div>
<p>
Figure <a href="#org927256e">25</a> shown a reinforced part to avoid buckling and improve vertical stiffness.
</p>
<div id="org927256e" class="figure">
<p><img src="./figs/linear_bearing_leafs.png" alt="linear_bearing_leafs.png" />
</p>
<p><span class="figure-number">Figure 25: </span>Use leaf springs instead of linear roller bearings</p>
</div>
</div>
</div>
<div id="outline-container-org023165e" class="outline-4">
<h4 id="org023165e"><span class="section-number-4">1.5.9</span> Mechatronics positioning challenge</h4>
<div class="outline-text-4" id="text-1-5-9">
<p>
A X-Y-Rz stage is shown in Figure <a href="#org8365473">26</a>.
To make this stage usable for nano-metric positioning, the following ideas where used:
</p>
<ul class="org-ul">
<li>Use parallel mechanisms instead of serial one:
<ul class="org-ul">
<li>no stacking of errors</li>
<li>smaller, stiffer, in one plane</li>
</ul></li>
<li>Symmetry:
<ul class="org-ul">
<li>Use 3 identical voice coil actuators</li>
<li>Use 3 identical sensors</li>
<li>Center position insensitive for temperature change</li>
</ul></li>
<li>Flexure only;
<ul class="org-ul">
<li>no friction</li>
<li>no play</li>
<li>no wear</li>
<li>no particule (important for clean rooms)</li>
<li>no service</li>
</ul></li>
<li>Continuously under control:
<ul class="org-ul">
<li>no alignment / crosstalk issues between axes</li>
<li>voice coil / sensors combination determines performance</li>
</ul></li>
</ul>
<div id="org8365473" class="figure">
<p><img src="./figs/xyRz_positioning_challenge.png" alt="xyRz_positioning_challenge.png" />
</p>
<p><span class="figure-number">Figure 26: </span>Example of X-Y-Rz positioning stage</p>
</div>
<p>
<iframe width="440" height="335" src="https://www.youtube.com/embed/OjNnHa6O9A8" frameborder="0" allowfullscreen></iframe>
</p>
</div>
</div>
<div id="outline-container-org8ba1f18" class="outline-4">
<h4 id="org8ba1f18"><span class="section-number-4">1.5.10</span> Case - Play Free parallel Stage</h4>
<div class="outline-text-4" id="text-1-5-10">
<p>
Figure <a href="#org9c33c0a">27</a> shows a parallel mechanism that should be converted to a compliant mechanism.
Its characteristics are:
</p>
<ul class="org-ul">
<li>1mm stroke</li>
<li>1:5 lever arm</li>
<li>10kg payload</li>
<li>distance between hinges: 5nmm</li>
<li>thickness t: 40mm</li>
<li>Material: aluminium</li>
</ul>
<div id="org9c33c0a" class="figure">
<p><img src="./figs/play_free_parallel_stage.png" alt="play_free_parallel_stage.png" />
</p>
<p><span class="figure-number">Figure 27: </span>Example of a parallel stage that should be converting to a compliant mechanism</p>
</div>
<p>
The goals are to:
</p>
<ul class="org-ul">
<li>Make design using elastic hinges</li>
<li>Maximize vertical stiffness</li>
<li>Determine vertical stiffness</li>
</ul>
<p>
The solution is shown in Figure <a href="#org62c66af">28</a>.
</p>
<div id="org62c66af" class="figure">
<p><img src="./figs/play_free_parallel_stage_solution.png" alt="play_free_parallel_stage_solution.png" />
</p>
<p><span class="figure-number">Figure 28: </span>Case Solution</p>
</div>
</div>
</div>
</div>
<div id="outline-container-org6ac1615" class="outline-3">
<h3 id="org6ac1615"><span class="section-number-3">1.6</span> Thin plate design</h3>
<div class="outline-text-3" id="text-1-6">
</div>
<div id="outline-container-orga184791" class="outline-4">
<h4 id="orga184791"><span class="section-number-4">1.6.1</span> Thin plate in torsion</h4>
<div class="outline-text-4" id="text-1-6-1">
<p>
Thin plates are very important for compliant mechanisms.
</p>
<p>
The torsion stiffness of a thing plate is linear with the length of the thin plate:
</p>
\begin{equation}
k = \frac{G I_p}{L}
\end{equation}
<p>
with \(G\) the shear modulus:
</p>
\begin{equation}
G \approx 0.3 E
\end{equation}
<p>
where \(E\) is the young modulus
</p>
<p>
Then
</p>
\begin{equation}
I_p = \frac{1}{3} h t^3 = \frac{1}{3} A t^2
\end{equation}
<p>
where \(A\) is the area of the cross section.
</p>
<div id="org61eb4e4" class="figure">
<p><img src="./figs/thin_plate_torsion.png" alt="thin_plate_torsion.png" />
</p>
<p><span class="figure-number">Figure 29: </span>A plate under torsion</p>
</div>
</div>
</div>
<div id="outline-container-orga980f37" class="outline-4">
<h4 id="orga980f37"><span class="section-number-4">1.6.2</span> Difference between open and close profile</h4>
<div class="outline-text-4" id="text-1-6-2">
<p>
The close profile has much more torsional stiffness than the open profile.
</p>
<p>
Just by opening the tube, we have a much smaller torsional stiffness (but almost same axial stiffness for instance).
</p>
<div id="orgff9dde7" class="figure">
<p><img src="./figs/open_close_profil_torsion_stiffness.png" alt="open_close_profil_torsion_stiffness.png" />
</p>
<p><span class="figure-number">Figure 30: </span>Stiffness comparison open and closed tube (torsion)</p>
</div>
<p>
We have similar behavior with an open/closed box.
If we remove one side of the cube shown in Figure <a href="#org2fd62d0">31</a>, we would have much smaller torsional stiffness along the axis perpendicular to the removed side.
</p>
<div id="org2fd62d0" class="figure">
<p><img src="./figs/closed_box.png" alt="closed_box.png" />
</p>
<p><span class="figure-number">Figure 31: </span>Closed box.</p>
</div>
<p>
If we use triangles, we obtain high torsional stiffness as shown in Figure <a href="#org748e105">32</a>.
</p>
<div id="org748e105" class="figure">
<p><img src="./figs/torsion_stiffness_box_double_triangle.png" alt="torsion_stiffness_box_double_triangle.png" />
</p>
<p><span class="figure-number">Figure 32: </span>Open box (double triangle)</p>
</div>
<p>
Frames are usually corresponding to open-boxes with have a small stiffness in torsion.
On way to reinforce it is using triangles.
</p>
<p>
A nice way to have a 1dof flexure guiding with stiff frame is shown in Figure <a href="#org6bd60a0">33</a>.
</p>
<div id="org6bd60a0" class="figure">
<p><img src="./figs/z_stage_triangles.png" alt="z_stage_triangles.png" />
</p>
<p><span class="figure-number">Figure 33: </span>Box with integrated flexure guiding</p>
</div>
</div>
</div>
</div>
</div>
<div id="outline-container-org722c8d4" class="outline-2">
<h2 id="org722c8d4"><span class="section-number-2">2</span> Keynote: Mechatronic challenges in optical lithography&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_hans_butler">@hans_butler</span></span></h2>
<div class="outline-text-2" id="text-2">
</div>
<div id="outline-container-orgf01d58f" class="outline-3">
<h3 id="orgf01d58f"><span class="section-number-3">2.1</span> Introduction</h3>
<div class="outline-text-3" id="text-2-1">
<p>
<b>Question</b>: in chip manufacturing, how do developments in optical lithography impact the mechatronic design?
</p>
<p>
Main developments:
</p>
<ul class="org-ul">
<li>Scanning &amp; dual stage scanning</li>
<li>Immersion</li>
<li>Multiple patterning</li>
<li>Extreme ultra violet lithography</li>
</ul>
</div>
</div>
<div id="outline-container-org04ac4d4" class="outline-3">
<h3 id="org04ac4d4"><span class="section-number-3">2.2</span> Chip manufacturing loop</h3>
<div class="outline-text-3" id="text-2-2">
<p>
In this presentation, only the exposure step is discussed (lithography).
</p>
<div id="org44d9063" class="figure">
<p><img src="./figs/asml_chip_manufacturing_loop.png" alt="asml_chip_manufacturing_loop.png" />
</p>
<p><span class="figure-number">Figure 34: </span>Chip manufacturing loop</p>
</div>
</div>
</div>
<div id="outline-container-org14e1ab2" class="outline-3">
<h3 id="org14e1ab2"><span class="section-number-3">2.3</span> Imaging process - Basics</h3>
<div class="outline-text-3" id="text-2-3">
<ul class="org-ul">
<li>An illuminator provides light at constant wavelength \(\lambda\)</li>
<li>The pattern on the reticle diffracts the light into order</li>
<li>At least +/-1st orders need to be captures.
This will induce a sinusoidal wave on the wafer as shown in Figure <a href="#orgaefc651">35</a>.</li>
<li>Wafer and mast are placed on high accuracy moving stages</li>
</ul>
<div id="orgaefc651" class="figure">
<p><img src="./figs/asml_imaging_process.png" alt="asml_imaging_process.png" />
</p>
<p><span class="figure-number">Figure 35: </span>Imaging process - basics</p>
</div>
</div>
</div>
<div id="outline-container-org77e0820" class="outline-3">
<h3 id="org77e0820"><span class="section-number-3">2.4</span> From stepper to scanner</h3>
<div class="outline-text-3" id="text-2-4">
<p>
Before, one chip was illumating at a time, but people wanted to make bigger chips.
However, if was difficult to make larger lenses.
</p>
<p>
The solution was to use a scanner, were both the mask and wafer are on moving stages.
This implied many requirements in dynamics and accuracy!
</p>
<div id="org62795f7" class="figure">
<p><img src="./figs/asml_stepper_to_scanner.png" alt="asml_stepper_to_scanner.png" />
</p>
<p><span class="figure-number">Figure 36: </span>From stepper to scanner</p>
</div>
</div>
</div>
<div id="outline-container-org7a7053b" class="outline-3">
<h3 id="org7a7053b"><span class="section-number-3">2.5</span> Dual stage scanners</h3>
<div class="outline-text-3" id="text-2-5">
<p>
Both the reticle stage and wafer stage are moving.
In order to have the same throughput, higher stage accelerations are required.
</p>
<p>
This implies some mechatronics challenges:
</p>
<ul class="org-ul">
<li>higher stage acceleration</li>
<li>higher accuracy</li>
<li>interaction between stages</li>
</ul>
<p>
Which are solved by:
</p>
<ul class="org-ul">
<li>Larger forces =&gt; balance masses</li>
<li>Stage dynamical design for high bandwidth control</li>
<li>Control coupling between stages (one control system can act as a disturbance to another controlled system =&gt; feedforward)</li>
</ul>
<div id="org5b87344" class="figure">
<p><img src="./figs/asml_dual_stage_scanners.png" alt="asml_dual_stage_scanners.png" />
</p>
<p><span class="figure-number">Figure 37: </span>Machine based on the dual stage scanners</p>
</div>
</div>
</div>
<div id="outline-container-orgf65e5b1" class="outline-3">
<h3 id="orgf65e5b1"><span class="section-number-3">2.6</span> Immersion technology</h3>
<div class="outline-text-3" id="text-2-6">
<p>
Water is used between the lens and the wafer to increase the &ldquo;NA&rdquo; and thus decreasing the &ldquo;critical dimension&rdquo;.
</p>
<p>
The &ldquo;hood&rdquo; is there to prevent any bubble to enter the illumination area (Figure <a href="#org01b66e2">38</a>).
The position of the &ldquo;hood&rdquo; is actively control to follow the wafer stage (that can move in z direction and tilt).
</p>
<p>
Three solutions are used for the positioning control of the &ldquo;hood&rdquo; system (Figure <a href="#org740b9cb">39</a>):
</p>
<ul class="org-ul">
<li>Disturbance decoupling</li>
<li>Iterative learning control</li>
<li>Feed-forward control from the Wafer control signal</li>
</ul>
<div id="org01b66e2" class="figure">
<p><img src="./figs/asml_hood_system.png" alt="asml_hood_system.png" />
</p>
<p><span class="figure-number">Figure 38: </span>Hood System</p>
</div>
<div id="org740b9cb" class="figure">
<p><img src="./figs/asml_immersion.png" alt="asml_immersion.png" />
</p>
<p><span class="figure-number">Figure 39: </span>Control system for the &ldquo;hood&rdquo;</p>
</div>
</div>
</div>
<div id="outline-container-org5413197" class="outline-3">
<h3 id="org5413197"><span class="section-number-3">2.7</span> Multiple Patterning</h3>
<div class="outline-text-3" id="text-2-7">
<p>
The multiple patterning approach adds few mechatronics challenges:
</p>
<ul class="org-ul">
<li>Position accuracy limited to ~4nm due to interferoemter position measurement (variation of temperature/pressure of air)</li>
<li>Stage swap is complex and time-consuming</li>
</ul>
<p>
This was solved by:
</p>
<ul class="org-ul">
<li>Using encoder instead of interferometers</li>
<li>Use long stroke motor: h-stage =&gt; new wafer stage concept</li>
</ul>
</div>
</div>
<div id="outline-container-org75d5fa9" class="outline-3">
<h3 id="org75d5fa9"><span class="section-number-3">2.8</span> Machine layout</h3>
<div class="outline-text-3" id="text-2-8">
<p>
Each stage is controlled with 6dof lorentz short stroke actuators (Figure <a href="#orgfcf8a87">40</a>).
The magnet stage can move horizontally (due to reaction forces of the wafer stages): it asks as a balance mass.
</p>
<div id="orgfcf8a87" class="figure">
<p><img src="./figs/asml_machine_layout_bis.png" alt="asml_machine_layout_bis.png" />
</p>
<p><span class="figure-number">Figure 40: </span>Machine layout</p>
</div>
</div>
</div>
<div id="outline-container-org01e20ab" class="outline-3">
<h3 id="org01e20ab"><span class="section-number-3">2.9</span> EUV Lithography</h3>
<div class="outline-text-3" id="text-2-9">
<p>
Vacuum is required which implies:
</p>
<ul class="org-ul">
<li>no bearings</li>
<li>no cooling</li>
</ul>
<p>
All the optics are reflective:
</p>
<ul class="org-ul">
<li>extremely accurately polished</li>
<li>challenge: keep mirrors optimally positioned</li>
</ul>
<p>
Wafer stage:
</p>
<ul class="org-ul">
<li>Move at high speed and accelerations</li>
<li>Challenge: in vaccum</li>
<li>Solved by: machanically suspended balance mass, and interferoemter position meaured can be used because it is in vacuum now</li>
</ul>
<div id="org615e868" class="figure">
<p><img src="./figs/asml_euv.png" alt="asml_euv.png" />
</p>
<p><span class="figure-number">Figure 41: </span>Schematic of the ASML EUV machine</p>
</div>
</div>
</div>
<div id="outline-container-org3ab05ad" class="outline-3">
<h3 id="org3ab05ad"><span class="section-number-3">2.10</span> The future: high-NA EUV</h3>
<div class="outline-text-3" id="text-2-10">
<div id="org73dd8cd" class="figure">
<p><img src="./figs/asml_na_euv.png" alt="asml_na_euv.png" />
</p>
<p><span class="figure-number">Figure 42: </span>The CD will be 8nm</p>
</div>
<p>
In order to do so, high &ldquo;opening&rdquo; of the optics is required which is very challenges because the reflectiveness of mirror is decreasing as high angle of incidence (Figure <a href="#orgeb53528">43</a>).
</p>
<div id="orgeb53528" class="figure">
<p><img src="./figs/asml_reflection_angle.png" alt="asml_reflection_angle.png" />
</p>
<p><span class="figure-number">Figure 43: </span>Change of reflection of a mirror as a function of the angle of indicence</p>
</div>
</div>
</div>
<div id="outline-container-org0d75012" class="outline-3">
<h3 id="org0d75012"><span class="section-number-3">2.11</span> Challenges for future Optical Lithography machines</h3>
<div class="outline-text-3" id="text-2-11">
<p>
<b>Challenges</b>:
</p>
<ul class="org-ul">
<li>Double wafer stage acceleration</li>
<li>Much bigger mirrors</li>
<li>Tighter accuracy specifications despite</li>
</ul>
<p>
<b>Solutions</b>:
</p>
<ul class="org-ul">
<li>Stage and mirror dynamics, high bandwidth control</li>
<li>Dynamics architecture: improved isolation, multiple isolate sets</li>
<li>Heating compensation</li>
</ul>
</div>
</div>
<div id="outline-container-org87aad3d" class="outline-3">
<h3 id="org87aad3d"><span class="section-number-3">2.12</span> Conclusion</h3>
<div class="outline-text-3" id="text-2-12">
<p>
The conclusions are:
</p>
<ul class="org-ul">
<li>Lithographic tools are the main enabler for over shrinking device sizes</li>
<li>New (optical) requirements lead to new mechatronic challenges:
<ul class="org-ul">
<li>Larger fields / better imaging: from stepping to scanning</li>
<li>Larger wafer size: dual stage scanners</li>
<li>Immersion: wafer stage &amp; hood control</li>
<li>Multiple patterning: planar motors and encoder technology</li>
<li>EUV: all-vacuum stages</li>
<li>High-NA EUV: new optics, much larger accelerations</li>
</ul></li>
</ul>
</div>
</div>
</div>
<div id="outline-container-orgcd72101" class="outline-2">
<h2 id="orgcd72101"><span class="section-number-2">3</span> Designing anti-aliasing-filters for control loops of mechatronic systems regarding the rejection of aliased resonances&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_ulrich_schonhoff">@ulrich_schonhoff</span></span></h2>
<div class="outline-text-2" id="text-3">
</div>
<div id="outline-container-org796f9c0" class="outline-3">
<h3 id="org796f9c0"><span class="section-number-3">3.1</span> The phenomenon of aliasing of resonances</h3>
<div class="outline-text-3" id="text-3-1">
<p>
Weakly damped flexible modes of the mechanism can limit the performance of motion control systems.
</p>
<p>
For discrete time controlled systems, there can be an additional limitation: aliased resonances which are rarely discussed.
</p>
<div id="orgff30765" class="figure">
<p><img src="./figs/aliasing_resonances.png" alt="aliasing_resonances.png" />
</p>
<p><span class="figure-number">Figure 44: </span>Example of high frequency lighlty damped resonances</p>
</div>
<p>
The aliasing of signals is well known (Figure <a href="#org991d424">45</a>).
</p>
<p>
However, aliasing in systems can also happens and is schematically shown in Figure <a href="#org58fa071">46</a>.
</p>
<div id="org991d424" class="figure">
<p><img src="./figs/aliasing_signals.png" alt="aliasing_signals.png" />
</p>
<p><span class="figure-number">Figure 45: </span>Aliasing of Signals</p>
</div>
<div id="org58fa071" class="figure">
<p><img src="./figs/aliasing_system.png" alt="aliasing_system.png" />
</p>
<p><span class="figure-number">Figure 46: </span>Aliasing of Systems</p>
</div>
<p>
The poles of the system will be aliased and their location will change in the complex plane as shown in Figure <a href="#org887a67a">47</a>.
</p>
<p>
More precisely:
</p>
<ul class="org-ul">
<li>the imaginary parts of the poles mirror about the Nyquist frequency</li>
<li>the real parts of the poles remain equal</li>
</ul>
<p>
Therefore, the damping of the aliased resonances are foreseen to have larger dampings.
</p>
<div id="org887a67a" class="figure">
<p><img src="./figs/aliasing_poles.png" alt="aliasing_poles.png" />
</p>
<p><span class="figure-number">Figure 47: </span>Aliasing of poles in the complex plane</p>
</div>
<p>
Let&rsquo;s consider two systems with a resonance:
</p>
<ol class="org-ol">
<li>below the Nyquist frequency (blue dashed)</li>
<li>above the Nyquist frequency (green dashed)</li>
</ol>
<p>
Then looking at the same systems in the digital domain, one can see thathen the resonance is above the Nyquist frequency (Figure <a href="#org7840b0d">48</a>):
</p>
<ul class="org-ul">
<li>the resonance mirrors</li>
<li>the damping is increased</li>
</ul>
<p>
Therefore, when identifying a low damped resonance, it could be that it comes form a high frequency low damped resonance.
</p>
<div id="org7840b0d" class="figure">
<p><img src="./figs/aliasing_above_nyquist.png" alt="aliasing_above_nyquist.png" />
</p>
<p><span class="figure-number">Figure 48: </span>Aliazed resonance shown on the Bode Diagram</p>
</div>
<div id="org1dee6a4" class="figure">
<p><img src="./figs/alising_much_above_nyquist.png" alt="alising_much_above_nyquist.png" />
</p>
<p><span class="figure-number">Figure 49: </span>Higher resonance frequency</p>
</div>
</div>
</div>
<div id="outline-container-org7349a1d" class="outline-3">
<h3 id="org7349a1d"><span class="section-number-3">3.2</span> Nature, Modelling and Mitigation of potentially aliasing resonances</h3>
<div class="outline-text-3" id="text-3-2">
<p>
The aliased modes can for instance comes from local modes in the actuators that are lightly damped and at high frequency (Figure <a href="#org5d53938">50</a>)
</p>
<div id="org5d53938" class="figure">
<p><img src="./figs/alising_nature.png" alt="alising_nature.png" />
</p>
<p><span class="figure-number">Figure 50: </span>Local vibration mode that will be alized</p>
</div>
<p>
The proposed idea to better model aliasing resonances is to include more modes in the FEM software as shown in Figure <a href="#org30599cf">51</a> and then perform an order reduction in matlab.
</p>
<div id="org30599cf" class="figure">
<p><img src="./figs/aliasing_modeling.png" alt="aliasing_modeling.png" />
</p>
<p><span class="figure-number">Figure 51: </span>Common procedure and proposed procedure to include aliazed resonances</p>
</div>
</div>
</div>
<div id="outline-container-org75b474a" class="outline-3">
<h3 id="org75b474a"><span class="section-number-3">3.3</span> Anti aliasing filter design</h3>
<div class="outline-text-3" id="text-3-3">
</div>
<div id="outline-container-orgbefe637" class="outline-4">
<h4 id="orgbefe637"><span class="section-number-4">3.3.1</span> Introduction</h4>
<div class="outline-text-4" id="text-3-3-1">
<ul class="org-ul">
<li>Anti-aliasing filtering can be used to reject aliasing of resonances and to maintain the stability of the control loop</li>
<li>However, its phase lag deteriorates the control loop performances:
<ul class="org-ul">
<li>phase margin decreases (Figure <a href="#orgf316dbb">52</a>)</li>
<li>sensitivity peak increases (Figure <a href="#orgf4db4d3">53</a>)</li>
</ul></li>
<li>Thus, the anti-aliasing filter should be targeted at sufficient rejection at least possible phase lag</li>
</ul>
<div id="orgf316dbb" class="figure">
<p><img src="./figs/alising_filter_introduction.png" alt="alising_filter_introduction.png" />
</p>
<p><span class="figure-number">Figure 52: </span>Example of the effect of aliased resonance on the open-loop</p>
</div>
<div id="orgf4db4d3" class="figure">
<p><img src="./figs/aliasing_sensitivity_effect.png" alt="aliasing_sensitivity_effect.png" />
</p>
<p><span class="figure-number">Figure 53: </span>Example of the effect of aliased resonance on sensitivity function</p>
</div>
</div>
</div>
<div id="outline-container-org9a11cd5" class="outline-4">
<h4 id="org9a11cd5"><span class="section-number-4">3.3.2</span> Concept of equivalent delay</h4>
<div class="outline-text-4" id="text-3-3-2">
<p>
<b>Concept</b>:
</p>
<ul class="org-ul">
<li><p>
At frequencies well below its poles and zeros, a continuous time filter \(F(j\omega)\) shows almost linear phase:
</p>
\begin{equation}
\arg\big( F(j\omega) \big) \approx -T_e \omega
\end{equation}</li>
<li><p>
Thus, <b>the phase lag of the filter can be fairly correctly represented by a time delay (below the pole frequency)</b>.
The equivalent delay is:
</p>
\begin{equation}
T_e = \sum_{i=1}^{N_p} \frac{\xi_{pi}}{\omega_{0pi}} - \sum_{i=1}^{N_z} \frac{\xi_{zi}}{\omega_{0zi}}
\end{equation}</li>
<li>where \(\omega_{0pi}\) is the natural frequency \(\xi_{pi}\) is the damping of the \(N_p\) poles of \(F(s)\).
Similarly, \(\omega_{0zi}\) is the natural frequency \(\xi_{zi}\) is the damping of the \(N_z\) zeros of \(F(s)\).</li>
</ul>
<p>
<b>Examples</b> (Figure <a href="#orgea4ccda">54</a>):
</p>
<ul class="org-ul">
<li>First order low pass filter:
\[ \xi_p = 1 \Rightarrow T_e = \frac{1}{\omega_c} \]</li>
<li>Second order Butterworth low pass filter:
\[ \xi_p = \frac{1}{\sqrt{2}} \Rightarrow T_e = \sqrt{2} \frac{1}{\omega_c} \]</li>
<li>First order lead:
\[ \xi_z = 1 \Rightarrow T_e = - \frac{1}{\omega_c} \]</li>
</ul>
<div id="orgea4ccda" class="figure">
<p><img src="./figs/aliasing_equivalent_delay.png" alt="aliasing_equivalent_delay.png" />
</p>
<p><span class="figure-number">Figure 54: </span>Magnitude, Phase and Phase delay of 3 filters</p>
</div>
</div>
</div>
<div id="outline-container-org6fc2424" class="outline-4">
<h4 id="org6fc2424"><span class="section-number-4">3.3.3</span> Budgeting of phase lag</h4>
<div class="outline-text-4" id="text-3-3-3">
<p>
The budgeting of the phase lag is done by expressing the phase lag of each element by a time delay (Figure <a href="#org6b9cd83">55</a>)
</p>
<div id="org6b9cd83" class="figure">
<p><img src="./figs/aliasing_budget_phase.png" alt="aliasing_budget_phase.png" />
</p>
<p><span class="figure-number">Figure 55: </span>Typical control loop with several phase lag / time delays</p>
</div>
<p>
The equivalent delay of each element are listed in Figure <a href="#org7435874">56</a>.
</p>
<div id="org7435874" class="figure">
<p><img src="./figs/aliasing_budget_table.png" alt="aliasing_budget_table.png" />
</p>
<p><span class="figure-number">Figure 56: </span>Equivalent delay for all the elements of the control loop</p>
</div>
</div>
</div>
<div id="outline-container-org20609a3" class="outline-4">
<h4 id="org20609a3"><span class="section-number-4">3.3.4</span> Selecting the filter order</h4>
<div class="outline-text-4" id="text-3-3-4">
<p>
The filter order can be chosen depending on the frequency of the resonance.
Some example of Butterworth filters are shown in Figure <a href="#org37a3d02">57</a> and summarized in Figure <a href="#orgd79f6c5">58</a>.
</p>
<div id="org37a3d02" class="figure">
<p><img src="./figs/aliasing_filter_order_bode.png" alt="aliasing_filter_order_bode.png" />
</p>
<p><span class="figure-number">Figure 57: </span>Example of few Butterworth filters</p>
</div>
<div id="orgd79f6c5" class="figure">
<p><img src="./figs/aliasing_filter_order_table.png" alt="aliasing_filter_order_table.png" />
</p>
<p><span class="figure-number">Figure 58: </span>Butterworth filters</p>
</div>
</div>
</div>
<div id="outline-container-org0a2996e" class="outline-4">
<h4 id="org0a2996e"><span class="section-number-4">3.3.5</span> Reducing the phase lag</h4>
<div class="outline-text-4" id="text-3-3-5">
<p>
The equivalent delay of a low pass (here second order) depends on its damping, since:
\[ T_e = -2 \frac{\xi_{zi}}{\omega_{0zi}} \]
</p>
<div id="org31dadfe" class="figure">
<p><img src="./figs/aliasing_reduce_phase_lag.png" alt="aliasing_reduce_phase_lag.png" />
</p>
<p><span class="figure-number">Figure 59: </span>Change of the phase delay with the damping of the filter</p>
</div>
</div>
</div>
</div>
<div id="outline-container-orgf86f6b0" class="outline-3">
<h3 id="orgf86f6b0"><span class="section-number-3">3.4</span> Conclusion</h3>
<div class="outline-text-3" id="text-3-4">
<p>
The phenomenon of aliasing of resonances:
</p>
<ul class="org-ul">
<li>Aliasing of resonances is an issue in discrete-time controlled mechatronic systems and <b>can limit the performance</b> and even <b>render the closed loop system unstable</b></li>
<li>Resonances above the Nyquist Frequency appear <b>aliased</b> at mirrored frequency for the discrete-time controller</li>
<li>Aliased resonances show <b>increased damping</b> compared to the original resonances</li>
<li>To find out if a resonance is an aliased one or not, change the sampling frequency and see if the frequency of the resonance is changing or not</li>
</ul>
<p>
Nature, modelling and mitigation of potentially aliasing resonances:
</p>
<ul class="org-ul">
<li>The origin are typically local resonances of the sensor and actuator components</li>
<li>Careful modelling and selecting dominant modes above the Nyquist frequency is commended</li>
</ul>
<p>
Anti-aliasing filter design:
</p>
<ul class="org-ul">
<li>Anti-Aliasing filter design is the <b>trade-off between rejection and phase-lag</b></li>
<li>The concept of <b>equivalent delay</b> allows to budget and design the phase lag</li>
<li>The order selection of anti alising-filter based on the required rejection is shown</li>
<li>Several approaches to reduce overall phase lag are presented</li>
</ul>
</div>
</div>
</div>
<div id="outline-container-orgc9d2ab6" class="outline-2">
<h2 id="orgc9d2ab6"><span class="section-number-2">4</span> Flexure positioning stage based on delta technology for high precision and dynamic industrial machining applications&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_mikael_bianchi">@mikael_bianchi</span></span></h2>
<div class="outline-text-2" id="text-4">
</div>
<div id="outline-container-org9bb0e04" class="outline-3">
<h3 id="org9bb0e04"><span class="section-number-3">4.1</span> Introduction</h3>
<div class="outline-text-3" id="text-4-1">
<ul class="org-ul">
<li><b>Goal</b>: flexure positioning stage to do high precision and high dynamic/acceleration positioning.
The control architecture should be as simple as possible.</li>
<li><b>Application</b>: micromachinign for fabrication of 3d structures</li>
<li><b>Possible field</b>: watch industry, electronics, optics, &#x2026;</li>
<li><b>Possible technologies</b>: laser, milling, electro discharge machine</li>
<li><b>Objectives</b>: improve the productivity reaching high accelerations at high precision</li>
</ul>
</div>
</div>
<div id="outline-container-orgdb95969" class="outline-3">
<h3 id="orgdb95969"><span class="section-number-3">4.2</span> Design</h3>
<div class="outline-text-3" id="text-4-2">
</div>
<div id="outline-container-orga1ed7ab" class="outline-4">
<h4 id="orga1ed7ab"><span class="section-number-4">4.2.1</span> Description of the Delta robot</h4>
<div class="outline-text-4" id="text-4-2-1">
<p>
<b>Technical choice</b>: flexure based delta robot (Figure <a href="#org3c83644">60</a>).
</p>
<ul class="org-ul">
<li>Advantages: high mechanical precision without backlash</li>
<li>Disadvantage: the motion is coupled, some transformations are required from motor coordinates to machine coordinates (Figure <a href="#orgf1389d2">61</a>)</li>
</ul>
<div id="org3c83644" class="figure">
<p><img src="./figs/flexure_delta_robot.png" alt="flexure_delta_robot.png" />
</p>
<p><span class="figure-number">Figure 60: </span>Picture of the Delta Robot</p>
</div>
<div id="orgf1389d2" class="figure">
<p><img src="./figs/flexure_delta_robot_schematic.png" alt="flexure_delta_robot_schematic.png" />
</p>
<p><span class="figure-number">Figure 61: </span>x1, x2 x3 are the motor positions. f1,f2 f3 are the force motors. x,y,z are the position of the final point in cartesian coordinates</p>
</div>
</div>
</div>
<div id="outline-container-org22da605" class="outline-4">
<h4 id="org22da605"><span class="section-number-4">4.2.2</span> Modelling and validation of the delta robot</h4>
<div class="outline-text-4" id="text-4-2-2">
<p>
Lagrange equations are used to model the dynamics of the delta robot.
The motor positions are used as the general coordinate system.
</p>
<p>
The system is then linearized around the working point (Figure <a href="#org9669a7d">62</a>).
</p>
<div id="org9669a7d" class="figure">
<p><img src="./figs/flexure_equations.png" alt="flexure_equations.png" />
</p>
<p><span class="figure-number">Figure 62: </span>Linearized equations of the Delta Robot</p>
</div>
<p>
Then the parameters are identified from experiment (Figure <a href="#orgb23f064">63</a>).
</p>
<div id="orgb23f064" class="figure">
<p><img src="./figs/flexure_identification.png" alt="flexure_identification.png" />
</p>
<p><span class="figure-number">Figure 63: </span>Identification fo the transfer function from \(F_1\) to \(x_1\)</p>
</div>
<p>
The measurement of the coupling is move complicated as shown in Figure <a href="#orgfc70e4f">64</a>.
</p>
<div id="orgfc70e4f" class="figure">
<p><img src="./figs/flexure_identification_coupling.png" alt="flexure_identification_coupling.png" />
</p>
<p><span class="figure-number">Figure 64: </span>Problem of identifying the coupling between F1 and x2 at low frequency</p>
</div>
</div>
</div>
<div id="outline-container-org0577955" class="outline-4">
<h4 id="org0577955"><span class="section-number-4">4.2.3</span> Control design for high trajectory tracking</h4>
<div class="outline-text-4" id="text-4-2-3">
<p>
Control requirements:
</p>
<ul class="org-ul">
<li>Precise position control of the coupled system (+/-10nm steps)</li>
<li>Minimal trajectory error at high frequency (+/- 100nm at +/- 1g acceleration)</li>
<li>Higher resonances attenuation</li>
<li>Whole motion system is considered as a standard cartesian XYZ axes for the user (do the inverse/forward kinematics inside the control architecture)</li>
</ul>
<div id="org51a068e" class="figure">
<p><img src="./figs/flexure_control_concept.png" alt="flexure_control_concept.png" />
</p>
<p><span class="figure-number">Figure 65: </span>Control concept used for the Delta robot</p>
</div>
</div>
</div>
<div id="outline-container-orgb986c00" class="outline-4">
<h4 id="orgb986c00"><span class="section-number-4">4.2.4</span> Electronic board</h4>
<div class="outline-text-4" id="text-4-2-4">
<p>
A 3 axis servo control board as been developed (Figure <a href="#org8cf523f">66</a>) which includes:
</p>
<ul class="org-ul">
<li>identification algorithm of the coupled system integrated in the board</li>
<li>interpolator for sensors</li>
</ul>
<p>
<img src="./figs/flexure_electronics_board.png" alt="flexure_electronics_board.png" />]
</p>
</div>
</div>
</div>
<div id="outline-container-orgdb37311" class="outline-3">
<h3 id="orgdb37311"><span class="section-number-3">4.3</span> Results</h3>
<div class="outline-text-3" id="text-4-3">
</div>
<div id="outline-container-orgd4e788f" class="outline-4">
<h4 id="orgd4e788f"><span class="section-number-4">4.3.1</span> Current control</h4>
<div class="outline-text-4" id="text-4-3-1">
<p>
Step response of the current control loop is shown in Figure <a href="#org40feccd">66</a>.
</p>
<div id="org40feccd" class="figure">
<p><img src="./figs/flexure_current_control_results.png" alt="flexure_current_control_results.png" />
</p>
<p><span class="figure-number">Figure 66: </span>Step response for the current control loop</p>
</div>
</div>
</div>
<div id="outline-container-orgc1a2cc2" class="outline-4">
<h4 id="orgc1a2cc2"><span class="section-number-4">4.3.2</span> Trajectory tracking: results with laser interferometer and encoder</h4>
<div class="outline-text-4" id="text-4-3-2">
<p>
XY renishaw interferometers used to verify the performance of the system (Figure <a href="#orgdadeab1">67</a>).
</p>
<div id="orgdadeab1" class="figure">
<p><img src="./figs/flexure_sensors.png" alt="flexure_sensors.png" />
</p>
<p><span class="figure-number">Figure 67: </span>Experimental setup to verify the performances of the system</p>
</div>
<p>
Some results are shown in Figures <a href="#orgf6e03a9">68</a>, <a href="#org237c9ba">69</a> and <a href="#org6fa7951">70</a>.
</p>
<div id="orgf6e03a9" class="figure">
<p><img src="./figs/flexure_results.png" alt="flexure_results.png" />
</p>
<p><span class="figure-number">Figure 68: </span>Circuit motion results and point to point motion results</p>
</div>
<div id="org237c9ba" class="figure">
<p><img src="./figs/flexure_steps.png" alt="flexure_steps.png" />
</p>
<p><span class="figure-number">Figure 69: </span>Step response of the system</p>
</div>
<div id="org6fa7951" class="figure">
<p><img src="./figs/flexure_dynamics_errors.png" alt="flexure_dynamics_errors.png" />
</p>
<p><span class="figure-number">Figure 70: </span>Measured dynamical errors</p>
</div>
</div>
</div>
</div>
<div id="outline-container-org232dfb2" class="outline-3">
<h3 id="org232dfb2"><span class="section-number-3">4.4</span> Conclusion</h3>
<div class="outline-text-3" id="text-4-4">
<p>
As a conclusion, here are the identified conditions for precise and high dynamic positioning:
</p>
<ul class="org-ul">
<li>Mechanics <b>without backlash</b> and <b>resonances in higher frequency</b></li>
<li><b>Feedforward</b> with correct parameters</li>
<li><b>High bandwidth</b> position control and precise encoder</li>
<li>Low noise current sensors and high bandwidth current control</li>
</ul>
<p>
Resonances at mid frequencies are an issue for further improvements.
</p>
</div>
</div>
</div>
<div id="outline-container-org994338d" class="outline-2">
<h2 id="org994338d"><span class="section-number-2">5</span> Multivariable performance analysis of position-controlled payloads with flexible eigenmodes&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_luca_mettenleiter">@luca_mettenleiter</span></span></h2>
<div class="outline-text-2" id="text-5">
</div>
<div id="outline-container-org5544143" class="outline-3">
<h3 id="org5544143"><span class="section-number-3">5.1</span> Motivation</h3>
<div class="outline-text-3" id="text-5-1">
<p>
Flexible eigenmodes are present in every system component and leads to::
</p>
<ul class="org-ul">
<li>controller bandwidth limitation (Figure <a href="#org45714bd">71</a>)</li>
<li>additional cross-coupling in the system behavior (Figure <a href="#org15f1277">72</a>)</li>
</ul>
<p>
=&gt; can lead to stability problems
</p>
<div id="org45714bd" class="figure">
<p><img src="./figs/mimo_flexible_modes.png" alt="mimo_flexible_modes.png" />
</p>
<p><span class="figure-number">Figure 71: </span>Limitation of the control bandwidth due to flexible eigenmodes</p>
</div>
<div id="org15f1277" class="figure">
<p><img src="./figs/mimo_flexible_modes_coupling.png" alt="mimo_flexible_modes_coupling.png" />
</p>
<p><span class="figure-number">Figure 72: </span>Coupling due to flexible eigenmodes</p>
</div>
<p>
In order to estimate the performances of a system, the sensitivity function can be used (Figure <a href="#org9a90837">73</a>).
</p>
<div id="org9a90837" class="figure">
<p><img src="./figs/mimo_sensitivity_performance.png" alt="mimo_sensitivity_performance.png" />
</p>
<p><span class="figure-number">Figure 73: </span>Bode plot of a typical Sensitivity function</p>
</div>
</div>
</div>
<div id="outline-container-org9ef976f" class="outline-3">
<h3 id="org9ef976f"><span class="section-number-3">5.2</span> Performance analysis with different sensitivity functions</h3>
<div class="outline-text-3" id="text-5-2">
<p>
There are different way to analyse the sensitivity function base on different plants (Figure <a href="#org01b0767">74</a>):
</p>
<ol class="org-ol">
<li>the <b>full system</b> (complicated):
\[ L_{full} = \begin{bmatrix}L_{11} & L_{12} \\ L_{21} & L_{22} \end{bmatrix} \]</li>
<li>the <b>diagonal system</b> (ignoring interaction)
\[ L_{diag} = \begin{bmatrix}L_{11} & 0 \\ 0 & L_{22} \end{bmatrix} \]</li>
<li>the <b>loop interaction system</b> (the one proposed here)
\[ L^{LI} = \begin{bmatrix}L_1^{LI} & 0 \\ 0 & L_2^{LI} \end{bmatrix} \]</li>
</ol>
<p>
The loop interaction methods created a SISO system that also represents the coupling in the system.
One loop is closed at a time, and the coupling effects are taken into account.
</p>
<div id="org01b0767" class="figure">
<p><img src="./figs/mimo_sensitivity_functions.png" alt="mimo_sensitivity_functions.png" />
</p>
<p><span class="figure-number">Figure 74: </span>Visual representation of the three systems</p>
</div>
</div>
</div>
<div id="outline-container-orgd425b1f" class="outline-3">
<h3 id="orgd425b1f"><span class="section-number-3">5.3</span> Example system</h3>
<div class="outline-text-3" id="text-5-3">
<p>
In order to compare the use of the three systems to estimate the performances of a MIMO system, the system shown in Figure <a href="#org5edc027">75</a> is used.
The 4 top masses are used to represent a payload that will add coupling in the system due to its resonances.
</p>
<p>
A diagonal PID controller is used.
</p>
<div id="org5edc027" class="figure">
<p><img src="./figs/mimo_example_system.png" alt="mimo_example_system.png" />
</p>
<p><span class="figure-number">Figure 75: </span>Schematic representation of the example system</p>
</div>
<p>
The bode plot of the MIMO system is shown in Figure <a href="#org4d2bac8">76</a> where we can see the resonances in the off-diagonal elements.
</p>
<div id="org4d2bac8" class="figure">
<p><img src="./figs/mimo_example_bode.png" alt="mimo_example_bode.png" />
</p>
<p><span class="figure-number">Figure 76: </span>Bode plot of the full MIMO system</p>
</div>
<p>
In Figure <a href="#org692dc48">77</a> is shown that the sensitivity function computed from the SISO system is not correct.
Whereas for the &ldquo;interaction method&rdquo; system, it is correct and almost match the full system sensibility.
However, as expected, the off-diagonal sensibilities are not modelled.
</p>
<div id="org692dc48" class="figure">
<p><img src="./figs/mimo_example_sensitivity.png" alt="mimo_example_sensitivity.png" />
</p>
<p><span class="figure-number">Figure 77: </span>Bode plots of sensitivity functions</p>
</div>
</div>
</div>
<div id="outline-container-org4fe2f03" class="outline-3">
<h3 id="org4fe2f03"><span class="section-number-3">5.4</span> Conclusion</h3>
<div class="outline-text-3" id="text-5-4">
<p>
The conclusion are the following and summarized in Figure <a href="#org1167178">78</a>:
</p>
<ul class="org-ul">
<li>Choice of suitable analysis method is key concept in mechatronics engineering</li>
<li>Various methods for analysis of multivariable systems available:
<ul class="org-ul">
<li>Full system always delivers reliable information, but much analysis effort</li>
<li>Loop interaction method delivers reliable information, only if the system is weakly or symmetrically coupled</li>
<li>Diagonal system delivers unreliable information, as it does not take multivariable character into account</li>
</ul></li>
</ul>
<div id="org1167178" class="figure">
<p><img src="./figs/mimo_results.png" alt="mimo_results.png" />
</p>
<p><span class="figure-number">Figure 78: </span>Comparison of the three methods to deal with a MIMO system</p>
</div>
</div>
</div>
</div>
<div id="outline-container-orgd103664" class="outline-2">
<h2 id="orgd103664"><span class="section-number-2">6</span> High-precision motion system design by topology optimization considering additive manufacturing&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_arnoud_delissen">@arnoud_delissen</span></span></h2>
<div class="outline-text-2" id="text-6">
</div>
<div id="outline-container-orgd50c76f" class="outline-3">
<h3 id="orgd50c76f"><span class="section-number-3">6.1</span> Introduction</h3>
<div class="outline-text-3" id="text-6-1">
<p>
The goal of this project is to perform a topology optimization of a 6dof magnetic levitated stage suitable for vacuum.
</p>
<p>
For the current system (Figure <a href="#org2b8fb41">79</a>), the bandwidth is limited by the short-stroke dynamics (eigenfrequencies).
</p>
<p>
The goal here is to make the eigen-frequency higher as this will allow more bandwidth.
</p>
<div id="org2b8fb41" class="figure">
<p><img src="./figs/mimoopt_6dof_stage.png" alt="mimoopt_6dof_stage.png" />
</p>
<p><span class="figure-number">Figure 79: </span>Schematic of the 6dof levitating stage</p>
</div>
</div>
</div>
<div id="outline-container-orge9c19e5" class="outline-3">
<h3 id="orge9c19e5"><span class="section-number-3">6.2</span> Case</h3>
<div class="outline-text-3" id="text-6-2">
<p>
More precisely, the goal is to automatically maximize the three eigen-frequencies of the system shown in Figure <a href="#org25cd024">80</a>.
</p>
<div id="org25cd024" class="figure">
<p><img src="./figs/mimoopt_case.png" alt="mimoopt_case.png" />
</p>
<p><span class="figure-number">Figure 80: </span>System to be optimized</p>
</div>
</div>
</div>
<div id="outline-container-org9ec1e67" class="outline-3">
<h3 id="org9ec1e67"><span class="section-number-3">6.3</span> Manufacturing process</h3>
<div class="outline-text-3" id="text-6-3">
<p>
The manufacturing process must be embedded in the optimization such that the obtained design is producible.
The process is shown in Figure <a href="#org5044b47">81</a>.
</p>
<div id="org5044b47" class="figure">
<p><img src="./figs/mimoopt_process.png" alt="mimoopt_process.png" />
</p>
<p><span class="figure-number">Figure 81: </span>Manufacturing process</p>
</div>
</div>
</div>
<div id="outline-container-orgd66ab28" class="outline-3">
<h3 id="orgd66ab28"><span class="section-number-3">6.4</span> Topology optimization</h3>
<div class="outline-text-3" id="text-6-4">
<p>
<b>Problem</b>: for a given volume, maximize the eigen-frequencies of the system.
</p>
<p>
To do so, the system is discretized into small elements (Figure <a href="#orga1e35c0">82</a>).
Then, a Finite Element Analysis is performed to compute the eigen-frequencies of the system.
Finally, for each element, the &ldquo;gradient is computed&rdquo; and we determine if material should be added or removed.
</p>
<p>
This is done in 3D. The individual 1mm x 1mm x 1mm elements are shown in Figure <a href="#orga1e35c0">82</a>.
The number of elements is 1 million (=&gt; 15 minutes per iteration to compute the 3 eigen-frequencies).
</p>
<div id="orga1e35c0" class="figure">
<p><img src="./figs/mimoopt_3d_opti.png" alt="mimoopt_3d_opti.png" />
</p>
<p><span class="figure-number">Figure 82: </span>Results of the topology optimization and zoom to see individual elements</p>
</div>
</div>
</div>
<div id="outline-container-org8aec71c" class="outline-3">
<h3 id="org8aec71c"><span class="section-number-3">6.5</span> Performance Comparison</h3>
<div class="outline-text-3" id="text-6-5">
<p>
The obtained mass and eigen-frequencies of the optimized system and the solid equivalents are compared in Figure <a href="#orgdf752d6">83</a>.
</p>
<div id="orgdf752d6" class="figure">
<p><img src="./figs/mimoopt_performance.png" alt="mimoopt_performance.png" />
</p>
<p><span class="figure-number">Figure 83: </span>Comparison of the obtained performances</p>
</div>
<p>
Identification on the realized system shown that the obtained eigen-frequencies are very closed to the estimated ones (Figure <a href="#org602e72c">84</a>).
</p>
<div id="org602e72c" class="figure">
<p><img src="./figs/mimoopt_frf_identification.png" alt="mimoopt_frf_identification.png" />
</p>
<p><span class="figure-number">Figure 84: </span>Results very close to simulation (~1% for the eigen frequencies)</p>
</div>
</div>
</div>
<div id="outline-container-org4ac24dc" class="outline-3">
<h3 id="org4ac24dc"><span class="section-number-3">6.6</span> Conclusion</h3>
<div class="outline-text-3" id="text-6-6">
<ul class="org-ul">
<li>Increase in performance (~2x) compared to solid designs</li>
<li>A design is obtained in ~ 1 day</li>
<li>Practical constraints are incorporated in the optimization</li>
<li>The method is validated in practice by a demonstrator</li>
</ul>
</div>
</div>
</div>
<div id="outline-container-org8339350" class="outline-2">
<h2 id="org8339350"><span class="section-number-2">7</span> A multivariable experiment design framework for accurate FRF identification of complex systems&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_nic_dirkx">@nic_dirkx</span></span></h2>
<div class="outline-text-2" id="text-7">
</div>
<div id="outline-container-org99a275f" class="outline-3">
<h3 id="org99a275f"><span class="section-number-3">7.1</span> Introduction</h3>
<div class="outline-text-3" id="text-7-1">
<p>
<b>Goal</b>: Need for higher quality FRF models that are used to:
</p>
<ul class="org-ul">
<li>Controller design</li>
<li>Observer design</li>
<li>System diagnostics</li>
<li>Parametric modelling</li>
</ul>
<p>
High quality FRFs requires careful design of excitation \(w\).
</p>
<p>
Typical experimental identification of the FRFs is shown in Figure <a href="#org8d0aaf8">85</a>.
</p>
<p>
The design trade-off is:
</p>
<ul class="org-ul">
<li>Maximize input gain to minimize FRF uncertainty</li>
<li>Bounded signal \(u\) and \(y\) to remain within operating limited (actuator/amplifier power limitations and limited move ranges)</li>
</ul>
<div id="org8d0aaf8" class="figure">
<p><img src="./figs/frf_introduction.png" alt="frf_introduction.png" />
</p>
<p><span class="figure-number">Figure 85: </span>schematic of the identification of the FRF</p>
</div>
<p>
For SISO systems:
</p>
<ul class="org-ul">
<li>Only the frequency size of the excitation signal should be optimized</li>
</ul>
<p>
For MIMO systems:
</p>
<ul class="org-ul">
<li>the gains and <b>directions</b> should be frequency wise optimized</li>
</ul>
<p>
<b>Objective</b>:
</p>
<ul class="org-ul">
<li>establish optimal experiment design framework that optimize the excitation signal to obtain MIMO FRFs with low uncertainty</li>
</ul>
</div>
</div>
<div id="outline-container-org8fb5a28" class="outline-3">
<h3 id="org8fb5a28"><span class="section-number-3">7.2</span> Role of directions and constrains in multivariable excitation design</h3>
<div class="outline-text-3" id="text-7-2">
<p>
The classical way to estimate MIMO FRFs is the following:
</p>
<ul class="org-ul">
<li>First start with one direction and increase the gain until constrains is attained (Figure <a href="#org95dcd0d">86</a>)</li>
<li>Do the same with the second input</li>
</ul>
<p>
This lead to non-optimal FRFs estimation.
</p>
<div id="org95dcd0d" class="figure">
<p><img src="./figs/frf_direction_excitation.png" alt="frf_direction_excitation.png" />
</p>
<p><span class="figure-number">Figure 86: </span>Example of a SISO approach to identify MIMO FRFs</p>
</div>
<p>
When having a MIMO approach and choosing both the direction and gain of the excitation inputs, we can obtained much better FRFs uncertainty while still fulfilling the constraints (Figure <a href="#org63a3995">87</a>).
</p>
<div id="org63a3995" class="figure">
<p><img src="./figs/frf_mimo.png" alt="frf_mimo.png" />
</p>
<p><span class="figure-number">Figure 87: </span>Example of the MIMO approach that gives much better FRFs</p>
</div>
</div>
</div>
<div id="outline-container-orgb94f6c1" class="outline-3">
<h3 id="orgb94f6c1"><span class="section-number-3">7.3</span> Solving the optimization problem</h3>
<div class="outline-text-3" id="text-7-3">
<p>
The optimization problem is to minimize the model uncertainty by choosing the design variables which are the magnitude and direction of the inputs \(w\).
</p>
<p>
The optimization is a two step process as shown in Figure <a href="#org19d32cd">88</a>:
</p>
<ol class="org-ol">
<li>first identification without optimization that allows to have data to run the optimization process</li>
<li>second identification with optimized input direction and gain</li>
</ol>
<p>
The problem with this optimization problem is that it is not convex in general and has a log of design variables.
There is no general methods to solve this problem, a dedicated algorithm is required.
</p>
<p>
In this work, two algorithms are proposed and not further detailed here.
</p>
<div id="org19d32cd" class="figure">
<p><img src="./figs/frf_optimization_steps.png" alt="frf_optimization_steps.png" />
</p>
<p><span class="figure-number">Figure 88: </span>Two step optimization process</p>
</div>
</div>
</div>
<div id="outline-container-orgad68ea0" class="outline-3">
<h3 id="orgad68ea0"><span class="section-number-3">7.4</span> Experimental validation</h3>
<div class="outline-text-3" id="text-7-4">
<p>
Experimental identification of a 7x8 MIMO plant was performed in for different cases:
</p>
<ol class="org-ol">
<li>non optimized SISO approach (grey)</li>
<li>optimized SISO approach (blue)</li>
<li>optimized MIMO approach using SSDR (first algorithm proposed) (green)</li>
<li>optimized MIMO approach using RR (second algorithm proposed) (red)</li>
</ol>
<p>
The obtained FRFs are shown in Figure <a href="#orgdcacefc">89</a>.
</p>
<div id="orgdcacefc" class="figure">
<p><img src="./figs/frf_experiment.png" alt="frf_experiment.png" />
</p>
<p><span class="figure-number">Figure 89: </span>Obtained MIMO FRFs</p>
</div>
<p>
A comparison of one of the obtained FRFs is shown in Figure <a href="#orgdbffc8e">90</a>.
It is quite clear that the MIMO approach can give much lower FRF uncertainty.
The RR proposed algorithm is giving the best results
</p>
<div id="orgdbffc8e" class="figure">
<p><img src="./figs/frf_experiment_optimized.png" alt="frf_experiment_optimized.png" />
</p>
<p><span class="figure-number">Figure 90: </span>Example of one of the obtained FRF</p>
</div>
</div>
</div>
<div id="outline-container-orgfc6daca" class="outline-3">
<h3 id="orgfc6daca"><span class="section-number-3">7.5</span> Conclusion</h3>
<div class="outline-text-3" id="text-7-5">
<ul class="org-ul">
<li>The uncertainty of the obtained FRF are obtained by doing several experimental identification with a deterministic input signal.
The FRF are computed multiple times, and the spread of the results at each frequency represents this uncertainty.</li>
<li>Exploiting directionality in excitation design enables significant FRF quality improvement</li>
<li>Multivariable design involves hard non-convex optimization problem</li>
<li>Computationally tractable design framework for large scale MIMO systems established</li>
<li>Near global optimal quality achieved on wafer stage setup using RR algorithm</li>
</ul>
</div>
</div>
</div>
<div id="outline-container-org667ea80" class="outline-2">
<h2 id="org667ea80"><span class="section-number-2">8</span> Keynote: High precision mechatronic approaches for advanced nanopositioning and nanomeasuring technologies&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_eberhard_manske">@eberhard_manske</span></span></h2>
<div class="outline-text-2" id="text-8">
</div>
<div id="outline-container-org553e8db" class="outline-3">
<h3 id="org553e8db"><span class="section-number-3">8.1</span> Coordinate Measurement Machines (CMM)</h3>
<div class="outline-text-3" id="text-8-1">
<p>
Examples of Nano Coordinate Measuring Machines are shown in Figure <a href="#orgbbd79cc">91</a>.
</p>
<div id="orgbbd79cc" class="figure">
<p><img src="./figs/prec_cmm.png" alt="prec_cmm.png" />
</p>
<p><span class="figure-number">Figure 91: </span>Example of Coordinate Measuring Machines</p>
</div>
</div>
</div>
<div id="outline-container-org37bb04e" class="outline-3">
<h3 id="org37bb04e"><span class="section-number-3">8.2</span> Difference between CMM and nano-CMM</h3>
<div class="outline-text-3" id="text-8-2">
<p>
With classical CMM, the Abbe-principle is not fulfilled in the x and y directions (Figure <a href="#orge8fd671">92</a>).
</p>
<p>
The Abbe error can be determined with:
</p>
\begin{equation}
\Delta l_{x,y,z} = l_{x,y,z} \sin \Delta \phi_{x,y,z}
\end{equation}
<p>
Even with the best spindle: \(l_{x,y} = 100 mm\) and \(\Delta \phi = 2 \text{arcsec}\), we obtain an error of:
</p>
\begin{equation}
\Delta l = 0.1 \mu m
\end{equation}
<p>
which is not compatible with nano-meter precisions.
</p>
<p>
Then, the classical CMM will not work for nano precision
</p>
<div id="orge8fd671" class="figure">
<p><img src="./figs/prec_cmm_nano_cmm.png" alt="prec_cmm_nano_cmm.png" />
</p>
</div>
</div>
</div>
<div id="outline-container-orgd233180" class="outline-3">
<h3 id="orgd233180"><span class="section-number-3">8.3</span> How to do nano-CMM</h3>
<div class="outline-text-3" id="text-8-3">
<p>
High precision mechatronic approaches are required for advanced nano-positionign and nano-measuring technologies:
</p>
<ul class="org-ul">
<li>High precision measurement concept</li>
<li>High precision measurement systems</li>
<li>High precision nano-sensors</li>
</ul>
<p>
Combined with:
</p>
<ul class="org-ul">
<li>Advanced automatic control</li>
<li>Advanced measuring strategies</li>
</ul>
</div>
</div>
<div id="outline-container-orgbf2f0e6" class="outline-3">
<h3 id="orgbf2f0e6"><span class="section-number-3">8.4</span> Concept - Minimization of the Abbe Error</h3>
<div class="outline-text-3" id="text-8-4">
<p>
In order to minimize the Abbe error, the measuring &ldquo;lines&rdquo; should have a common point of intersection (Figure <a href="#orgcf86afd">93</a>).
</p>
<p>
The 3D-realization of Abbe-principle is as follows:
</p>
<ul class="org-ul">
<li>3 interferometers: cartesian coordinate system</li>
<li>probe located as the intersection point of the interferometers</li>
</ul>
<div id="orgcf86afd" class="figure">
<p><img src="./figs/prec_nano_cmm_concept.png" alt="prec_nano_cmm_concept.png" />
</p>
<p><span class="figure-number">Figure 93: </span>Error minimal measuring principle</p>
</div>
</div>
</div>
<div id="outline-container-orgbebebfa" class="outline-3">
<h3 id="orgbebebfa"><span class="section-number-3">8.5</span> Minimization of residual Abbe error</h3>
<div class="outline-text-3" id="text-8-5">
<p>
Still some residual Abbe error can happen as shown in Figure <a href="#org1cf94c9">94</a> due to both a change of angle and change of position.
</p>
<div id="org1cf94c9" class="figure">
<p><img src="./figs/prec_abbe_min.png" alt="prec_abbe_min.png" />
</p>
<p><span class="figure-number">Figure 94: </span>Residual Abbe error</p>
</div>
</div>
</div>
<div id="outline-container-orgce68d81" class="outline-3">
<h3 id="orgce68d81"><span class="section-number-3">8.6</span> Compare of long travel guiding systems</h3>
<div class="outline-text-3" id="text-8-6">
<p>
In order to have the Abbe error compatible with nano-meter precision, the precision of the spindle should be less and one arcsec which is not easily feasible with air bearing of precision roller bearing technologies as shown in Figure <a href="#orgf502550">95</a>.
</p>
<div id="orgf502550" class="figure">
<p><img src="./figs/prec_comp_guid.png" alt="prec_comp_guid.png" />
</p>
<p><span class="figure-number">Figure 95: </span>Characteristics of guidings</p>
</div>
</div>
</div>
<div id="outline-container-org56ef278" class="outline-3">
<h3 id="org56ef278"><span class="section-number-3">8.7</span> Extended 6 DoF Abbe comparator principle</h3>
<div class="outline-text-3" id="text-8-7">
<p>
The solution used was to measure in real time the angles of the frame using autocollimators as shown in Figure <a href="#org6d205f6">96</a> and then to minimize this tilt by close loop operation with additional actuators.
</p>
<p>
The angular measurement error and control is less than \(0.05 \text{arcses}\) which make the residual Abbe error:
</p>
\begin{equation}
\Delta l < 0.05\,nm
\end{equation}
<p>
Without an error-minimal approach, nano-meter precision cannot be achieved in large areas.
</p>
<div id="org6d205f6" class="figure">
<p><img src="./figs/prec_6dof_abbe.png" alt="prec_6dof_abbe.png" />
</p>
<p><span class="figure-number">Figure 96: </span>Use of additional autocollimator and actuators for Abbe minimization</p>
</div>
</div>
</div>
<div id="outline-container-orgadc2544" class="outline-3">
<h3 id="orgadc2544"><span class="section-number-3">8.8</span> Practical Realisation</h3>
<div class="outline-text-3" id="text-8-8">
<p>
A practical realization of the Extended 6 DoF Abbe comparator principle is shown in Figure <a href="#org1ffd9ad">97</a>.
</p>
<div id="org1ffd9ad" class="figure">
<p><img src="./figs/prec_practical_6dof.png" alt="prec_practical_6dof.png" />
</p>
<p><span class="figure-number">Figure 97: </span>Practical Realization of the</p>
</div>
</div>
</div>
<div id="outline-container-orgba7571a" class="outline-3">
<h3 id="orgba7571a"><span class="section-number-3">8.9</span> Tilt Compensation</h3>
<div class="outline-text-3" id="text-8-9">
<p>
To measure compensate for any tilt, two solutions are proposed:
</p>
<ol class="org-ol">
<li>Use a zero point angular auto-collimator (Figure <a href="#org9558f11">98</a>)
<ul class="org-ul">
<li>Resolution: 0.005 arcsec</li>
<li>Stability (1h): &lt; 0.05 arcsec</li>
</ul></li>
<li>6 DoF laser interferoemter (Figure <a href="#orga876de3">99</a>)
<ul class="org-ul">
<li>Resolution: 0.00002 arcsec</li>
<li>Stability (1h): &lt; 0.00005 arcsec</li>
</ul></li>
</ol>
<div id="org9558f11" class="figure">
<p><img src="./figs/prec_tilt_corection.png" alt="prec_tilt_corection.png" />
</p>
<p><span class="figure-number">Figure 98: </span>Auto-Collimator</p>
</div>
<div id="orga876de3" class="figure">
<p><img src="./figs/prec_tilt_corection_bis.png" alt="prec_tilt_corection_bis.png" />
</p>
<p><span class="figure-number">Figure 99: </span>6 Interferometers to measure tilts</p>
</div>
</div>
</div>
<div id="outline-container-orgc5bebce" class="outline-3">
<h3 id="orgc5bebce"><span class="section-number-3">8.10</span> Comparison of long travail guiding systems - Bis</h3>
<div class="outline-text-3" id="text-8-10">
<p>
Now, if we actively compensate the tilts are shown previously, we can fulfill the requirements as shown in Figure <a href="#orgecb2dc4">100</a>.
</p>
<p>
<b>Measurement and control technology to minimize Abbe errors to achieve</b>:
</p>
<ul class="org-ul">
<li>sub-nanometer precision</li>
<li>smaller moving mass</li>
<li>better dynamics</li>
</ul>
<div id="orgecb2dc4" class="figure">
<p><img src="./figs/prec_comp_guid_bis.png" alt="prec_comp_guid_bis.png" />
</p>
<p><span class="figure-number">Figure 100: </span>Characteristics of the tilt compensation system</p>
</div>
</div>
</div>
<div id="outline-container-orgdd01e46" class="outline-3">
<h3 id="orgdd01e46"><span class="section-number-3">8.11</span> Drive concept</h3>
<div class="outline-text-3" id="text-8-11">
<p>
Usually, in order to achieve a large range over small resolution, each axis of motion is a combination of a coarse motion and a fine motion stage.
The coarse motion stage generally consist of a stepper motor while the fine motion is a piezoelectric actuator.
</p>
<p>
The approach here is to use an <b>homogenous drive concept for increase dynamics</b> (Figure <a href="#orge54b0db">101</a>).
</p>
<p>
Only one linear voice coil actuator is used which with large moving range and sub-nanometer resolution can be achieve at one time.
</p>
<div id="orge54b0db" class="figure">
<p><img src="./figs/prec_drive_concept.png" alt="prec_drive_concept.png" />
</p>
<p><span class="figure-number">Figure 101: </span>Voice Coil Actuator</p>
</div>
</div>
</div>
<div id="outline-container-orgb627d19" class="outline-3">
<h3 id="orgb627d19"><span class="section-number-3">8.12</span> NPMM-200 with extended measuring volume</h3>
<div class="outline-text-3" id="text-8-12">
<p>
The NPMM-200 machine can be seen in Figure <a href="#org150fbb7">102</a>.
</p>
<p>
Characteristics:
</p>
<ul class="org-ul">
<li>Measuring range: 200 mm x 200 mm x 25 mm</li>
<li>Resolution: 20 pm</li>
<li>Abbe comparator principle</li>
<li>6 laser interferometers</li>
<li>Active angular compensation</li>
<li>Position uncertainty &lt; 4 nm</li>
<li>Measuring uncertainty up to 30 nm</li>
</ul>
<div id="org150fbb7" class="figure">
<p><img src="./figs/prec_mechanics.png" alt="prec_mechanics.png" />
</p>
<p><span class="figure-number">Figure 102: </span>Picture of the NPMM-200</p>
</div>
<p>
The NPMM-200 actually operates inside a Vacuum chamber as shown in Figure <a href="#org554bcf5">103</a>.
</p>
<div id="org554bcf5" class="figure">
<p><img src="./figs/prec_vacuum_cham.png" alt="prec_vacuum_cham.png" />
</p>
<p><span class="figure-number">Figure 103: </span>Vacuum chamber used</p>
</div>
</div>
</div>
<div id="outline-container-org78c9d88" class="outline-3">
<h3 id="org78c9d88"><span class="section-number-3">8.13</span> measurement capability</h3>
<div class="outline-text-3" id="text-8-13">
<p>
Some step responses are shown in Figure <a href="#orgd17844c">104</a> and show the nano-metric precision of the machine.
</p>
<div id="orgd17844c" class="figure">
<p><img src="./figs/prec_results_meas.png" alt="prec_results_meas.png" />
</p>
<p><span class="figure-number">Figure 104: </span>Sub nano-meter position accuracy</p>
</div>
<p>
Picometer steps can even be achieved as shown in Figure <a href="#org217d869">105</a>.
</p>
<div id="org217d869" class="figure">
<p><img src="./figs/prec_results_pico.png" alt="prec_results_pico.png" />
</p>
<p><span class="figure-number">Figure 105: </span>Picometer level control</p>
</div>
</div>
</div>
<div id="outline-container-orgb080103" class="outline-3">
<h3 id="orgb080103"><span class="section-number-3">8.14</span> Extension of the measuring range (700mm)</h3>
<div class="outline-text-3" id="text-8-14">
<p>
If the measuring range is to be increase, there are some limits of the moving stage principle:
</p>
<ul class="org-ul">
<li>large moving masses (~300kg)</li>
<li>powerful drive systems required</li>
<li>nano-meter position capability problematic</li>
<li>large heat dissipation in the system</li>
<li>dynamics and dynamic deformation</li>
</ul>
<p>
The proposed solution is to use <b>inverse dynamic concept for minimization of moving masses</b>.
</p>
</div>
</div>
<div id="outline-container-org4f4bd8f" class="outline-3">
<h3 id="org4f4bd8f"><span class="section-number-3">8.15</span> Inverse kinematic concept - Tetrahedrical concept</h3>
<div class="outline-text-3" id="text-8-15">
<p>
The proposed concept is shown in Figure <a href="#org28ce603">106</a>:
</p>
<ul class="org-ul">
<li>mirrors and object to be measured are fixed</li>
<li>probe and interferometer heads are moved</li>
<li>laser beams virtually intersect in the probe tip</li>
<li>Tetrahedrical measuring volume</li>
</ul>
<p>
This fulfills the Abbe principe but:
</p>
<ul class="org-ul">
<li>large construction space</li>
<li>difficult guide and drive concept</li>
</ul>
<div id="org28ce603" class="figure">
<p><img src="./figs/prec_inverse_kin.png" alt="prec_inverse_kin.png" />
</p>
<p><span class="figure-number">Figure 106: </span>Tetrahedrical concept</p>
</div>
</div>
</div>
<div id="outline-container-org5454cab" class="outline-3">
<h3 id="org5454cab"><span class="section-number-3">8.16</span> Inverse kinematic concept - Scanning probe principle</h3>
<div class="outline-text-3" id="text-8-16">
<p>
An other concept, the scanning probe principle is shown in Figure <a href="#org12c8247">107</a>:
</p>
<ul class="org-ul">
<li>cuboidal measuring volume</li>
<li>Fixed x-y-z mirrors</li>
<li>moving measuring head</li>
<li>guide and drive system outside measuring volume</li>
</ul>
<div id="org12c8247" class="figure">
<p><img src="./figs/prec_inverse_kin_scan.png" alt="prec_inverse_kin_scan.png" />
</p>
<p><span class="figure-number">Figure 107: </span>Scanning probe principle</p>
</div>
</div>
</div>
<div id="outline-container-org5504362" class="outline-3">
<h3 id="org5504362"><span class="section-number-3">8.17</span> Inverse kinematic concept - Compact measuring head</h3>
<div class="outline-text-3" id="text-8-17">
<p>
In order to minimize the moving mass, compact measuring heads have been developed.
The goal was to make a lightweight measuring head (&lt;1kg)
</p>
<p>
The interferometer used are fiber coupled laser interferometers with a mass of 37g (Figure <a href="#org46c3488">108</a>).
</p>
<div id="org46c3488" class="figure">
<p><img src="./figs/prec_interferometers.png" alt="prec_interferometers.png" />
</p>
<p><span class="figure-number">Figure 108: </span>Micro Interferometers</p>
</div>
<p>
The concept is shown in Figure <a href="#org0a78898">109</a>:
</p>
<ul class="org-ul">
<li>6dof interferometers are used</li>
<li>one micro-probe</li>
<li>the total mass of the head is less than 1kg</li>
</ul>
<p>
There is some abbe offset between measurement axis of probe and of interferometer but <b>Abbe error compensation by closed loop control of angular deviations</b> is used.
</p>
<div id="org0a78898" class="figure">
<p><img src="./figs/prec_inverse_meas_head.png" alt="prec_inverse_meas_head.png" />
</p>
</div>
</div>
</div>
<div id="outline-container-org41b2fcb" class="outline-3">
<h3 id="org41b2fcb"><span class="section-number-3">8.18</span> Inverse kinematic concept - Scanning probe principle</h3>
<div class="outline-text-3" id="text-8-18">
<p>
As shown in Figure <a href="#org9a9e5e8">110</a>, the abbe error can be compensated from the two top interferometers as:
\[ \text{for } l_x = a: \quad \Delta l_{\text{Abbe}} = \Delta l_{\text{int}} \]
Thus the tilt and Abbe errors can be compensated for with sub-nm resolution.
</p>
<div id="org9a9e5e8" class="figure">
<p><img src="./figs/prec_abbe_compensation.png" alt="prec_abbe_compensation.png" />
</p>
<p><span class="figure-number">Figure 110: </span>Use of the interferometers to compensate for the Abbe errors</p>
</div>
</div>
</div>
<div id="outline-container-orgf154e61" class="outline-3">
<h3 id="orgf154e61"><span class="section-number-3">8.19</span> Conclusion</h3>
<div class="outline-text-3" id="text-8-19">
<p>
Proposed approaches to push the nano-positioning and nano-measuring technology:
</p>
<ul class="org-ul">
<li>Measurement and control technology to minimize Abbe errors</li>
<li>Homogeneous drive concept for increased dynamics</li>
<li>Inverse kinematic concept for minimization of moving mass</li>
<li>Abbe-error compensation by closed loop control of angular deviations</li>
</ul>
</div>
</div>
</div>
<div id="outline-container-org88525c7" class="outline-2">
<h2 id="org88525c7"><span class="section-number-2">9</span> Reducing control delay times to enhance dynamic stiffness of magnetic bearings&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_jan_philipp_schmidtmann">@jan_philipp_schmidtmann</span></span></h2>
<div class="outline-text-2" id="text-9">
<p>
This projects focuses on reducing the control delay times of a magnetic bearing shown in Figure <a href="#orgb424ee6">111</a>.
</p>
<div id="orgb424ee6" class="figure">
<p><img src="./figs/magn_bear_intro.png" alt="magn_bear_intro.png" />
</p>
<p><span class="figure-number">Figure 111: </span>6 DoF Position System - Concept</p>
</div>
<p>
Active magnetic bearings are unstable systems and require active control.
However, the active control of magnet forces leads to a control delay that limits the performances (stiffness) of the bearing.
</p>
<p>
Typical contributors to the control delay time are shown in Figure <a href="#org55b0313">112</a>.
</p>
<div id="org55b0313" class="figure">
<p><img src="./figs/magn_bear_delay.png" alt="magn_bear_delay.png" />
</p>
<p><span class="figure-number">Figure 112: </span>Typical Contributors to control delay time</p>
</div>
<p>
The reduction of the control time delay will increase the dynamic stiffness of the bearing as well as decrease the effects of external disturbances and hence improve the positioning errors (Figure <a href="#orgbd4e45a">113</a>).
</p>
<p>
The steps to reduce the control delay time are:
</p>
<ol class="org-ol">
<li>Eliminate BUSS-communication by merging position and current controller</li>
<li>Reduce cycle time by using rapid prototyping system</li>
<li>Reduce delay in PWM driver by using high PWM frequencies with SiC driver</li>
</ol>
<div id="orgbd4e45a" class="figure">
<p><img src="./figs/magn_bear_distur.png" alt="magn_bear_distur.png" />
</p>
<p><span class="figure-number">Figure 113: </span>The effect of control delay on stiffness</p>
</div>
<p>
Therefore, the position and current control have been merged into one controller (Figure <a href="#orgccc5d0d">114</a>).
</p>
<div id="orgccc5d0d" class="figure">
<p><img src="./figs/magn_controller.png" alt="magn_controller.png" />
</p>
<p><span class="figure-number">Figure 114: </span>Controller for position and current</p>
</div>
<p>
A dSpace rapid prototyping system is used for fast position and current control.
Characteristics of the used elements are shown in Figure <a href="#orgbbb279d">115</a>.
</p>
<div id="orgbbb279d" class="figure">
<p><img src="./figs/magn_bear_setup.png" alt="magn_bear_setup.png" />
</p>
<p><span class="figure-number">Figure 115: </span>Setup for reduced delay times</p>
</div>
<p>
Differences between the previous PWM controller and the new SiC controller are shown in Figure <a href="#org6b18297">116</a>.
The delay time is almost completely eliminated.
</p>
<div id="org6b18297" class="figure">
<p><img src="./figs/magn_bear_results.png" alt="magn_bear_results.png" />
</p>
<p><span class="figure-number">Figure 116: </span>Reduction of delay in PWM Driver</p>
</div>
<p>
Due to all the performed modifications, the control delay time could be reduced by 80%.
The next steps for this project are shown in Figure <a href="#org6ae1e74">117</a>.
</p>
<div id="org6ae1e74" class="figure">
<p><img src="./figs/magn_bear_conclusion.png" alt="magn_bear_conclusion.png" />
</p>
<p><span class="figure-number">Figure 117: </span>Next Steps</p>
</div>
</div>
</div>
<div id="outline-container-org5f07b1a" class="outline-2">
<h2 id="org5f07b1a"><span class="section-number-2">10</span> Digital twins in control: From fault detection to predictive maintenance in precision mechatronics&#xa0;&#xa0;&#xa0;<span class="tag"><span class="_koen_classens">@koen_classens</span></span></h2>
<div class="outline-text-2" id="text-10">
</div>
<div id="outline-container-org5076a19" class="outline-3">
<h3 id="org5076a19"><span class="section-number-3">10.1</span> Motivation</h3>
<div class="outline-text-3" id="text-10-1">
<p>
Models are usually for the control design part that can be either physical models (FEM, first principle) or data-driven models.
However, these models are usually not used after control system is implemented (Figure <a href="#org066d50c">118</a>).
</p>
<div id="org066d50c" class="figure">
<p><img src="./figs/twins_motivation.png" alt="twins_motivation.png" />
</p>
<p><span class="figure-number">Figure 118: </span>Typical of of models in a mechatronic system</p>
</div>
<p>
Here, the models are exploited to monitor the system and predict future possible failures in the system.
Use models as digital twin for <b>fault detection and Isolation for predictive maintenance in precision mechatronics</b> (Figure <a href="#orgd6796e6">119</a>).
</p>
<div id="orgd6796e6" class="figure">
<p><img src="./figs/twing_fdi.png" alt="twing_fdi.png" />
</p>
<p><span class="figure-number">Figure 119: </span>FDI is using the model of the plant</p>
</div>
</div>
</div>
<div id="outline-container-orgd70c54c" class="outline-3">
<h3 id="orgd70c54c"><span class="section-number-3">10.2</span> Predictive Maintenance</h3>
<div class="outline-text-3" id="text-10-2">
<p>
Classical maintenance happens when the system is not working anymore as shown in Figure <a href="#org99a74ba">120</a>.
</p>
<div id="org99a74ba" class="figure">
<p><img src="./figs/twins_predictive_maintenance.png" alt="twins_predictive_maintenance.png" />
</p>
<p><span class="figure-number">Figure 120: </span>Maintenance done when a failure is appearing</p>
</div>
<p>
It is possible to perform some preventive maintenance before a failure happens, but this is still not optimal.
</p>
<div id="org0920161" class="figure">
<p><img src="./figs/twins_predictive_maintenance_bis.png" alt="twins_predictive_maintenance_bis.png" />
</p>
<p><span class="figure-number">Figure 121: </span>Preventive Maintenance</p>
</div>
<p>
The idea here is to predict when the failure will happen in order to only do maintenance only when really necessary.
This will minimize the down time of the machine.
</p>
<div id="org5be6378" class="figure">
<p><img src="./figs/twins_predictive_maintenance_ter.png" alt="twins_predictive_maintenance_ter.png" />
</p>
<p><span class="figure-number">Figure 122: </span>Predictive maintenance</p>
</div>
</div>
</div>
<div id="outline-container-org10f60ea" class="outline-3">
<h3 id="org10f60ea"><span class="section-number-3">10.3</span> Objectives</h3>
<div class="outline-text-3" id="text-10-3">
<p>
The main objective is to develop a system monitoring approach for precision mechatronic systems, exploiting prior information (models) and integrating posterior information (real-time measured data).
</p>
<p>
Even though state of the art system monitoring are already in used in aerospace, process industry and automotive, there are few specificity for mechatronic systems:
</p>
<ul class="org-ul">
<li>Control loops</li>
<li>Large-scale MIMO systems (interaction)</li>
<li>Accurate models: Frequency Response Functions</li>
</ul>
</div>
</div>
<div id="outline-container-org339e449" class="outline-3">
<h3 id="org339e449"><span class="section-number-3">10.4</span> Null-space based FDI</h3>
<div class="outline-text-3" id="text-10-4">
<p>
The goal is to applied a decentralized Fault Detection on the system shown in Figure <a href="#org7b81bed">123</a> to detect actuator faults at \(J_1\).
This should take into account the control loop, interaction in the system and be FRF based.
</p>
<div id="org7b81bed" class="figure">
<p><img src="./figs/twings_fdi_test.png" alt="twings_fdi_test.png" />
</p>
<p><span class="figure-number">Figure 123: </span>Test System</p>
</div>
<p>
The architecture to estimate faults in the system is shown in Figure <a href="#org34e1be2">124</a>.
The goal is to design \(Q_u\) and \(Q_y\) such that \(\epsilon\) is a representation of faults in the system.
</p>
<div id="org34e1be2" class="figure">
<p><img src="./figs/twins_null_space_fdi.png" alt="twins_null_space_fdi.png" />
</p>
<p><span class="figure-number">Figure 124: </span>Residual Generator</p>
</div>
<p>
When a fault happens (Figure <a href="#org9e4cd15">125</a>), the outputs signals are not changing that much (because of feedback), however the system is able to find that there is a problem using the residual \(\epsilon\).
</p>
<div id="org9e4cd15" class="figure">
<p><img src="./figs/twins_results_fdi.png" alt="twins_results_fdi.png" />
</p>
<p><span class="figure-number">Figure 125: </span>Simulation Results</p>
</div>
<p>
<b>Procedure</b>:
</p>
<ul class="org-ul">
<li>Additive faults</li>
<li>Closed-loop</li>
<li>Interaction</li>
<li>start from identification</li>
</ul>
</div>
</div>
<div id="outline-container-org7c2ed17" class="outline-3">
<h3 id="org7c2ed17"><span class="section-number-3">10.5</span> Roadmap from fault detection to predictive maintenance</h3>
<div class="outline-text-3" id="text-10-5">
<p>
The proposed system can detect faults in the system (Figure <a href="#orgb23eff9">126</a>).
This proof of principle should now be applied on industrial systems.
Moreover, from the fault detection, predictive maintenance should be performed (Figure <a href="#orgb23eff9">126</a>).
</p>
<div id="orgb23eff9" class="figure">
<p><img src="./figs/twins_roadmap.png" alt="twins_roadmap.png" />
</p>
<p><span class="figure-number">Figure 126: </span>From proof of principle to industrial application</p>
</div>
<div id="org763994b" class="figure">
<p><img src="./figs/twins_roadmap_bis.png" alt="twins_roadmap_bis.png" />
</p>
<p><span class="figure-number">Figure 127: </span>From fault detection to predictive maintenance</p>
</div>
</div>
</div>
</div>
</div>
<div id="postamble" class="status">
<p class="author">Author: Dehaeze Thomas</p>
<p class="date">Created: 2020-11-20 ven. 09:23</p>
</div>
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