Initial commit
111
paper/.latexmkrc
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@@ -0,0 +1,111 @@
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||||
#!/bin/env perl
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|
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# Shebang is only to get syntax highlighting right across GitLab, GitHub and IDEs.
|
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# This file is not meant to be run, but read by `latexmk`.
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||||
|
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# ======================================================================================
|
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# Perl `latexmk` configuration file
|
||||
# ======================================================================================
|
||||
|
||||
# ======================================================================================
|
||||
# PDF Generation/Building/Compilation
|
||||
# ======================================================================================
|
||||
|
||||
@default_files=('dehaeze26_cubic_architecture.tex');
|
||||
|
||||
# PDF-generating modes are:
|
||||
# 1: pdflatex, as specified by $pdflatex variable (still largely in use)
|
||||
# 2: postscript conversion, as specified by the $ps2pdf variable (useless)
|
||||
# 3: dvi conversion, as specified by the $dvipdf variable (useless)
|
||||
# 4: lualatex, as specified by the $lualatex variable (best)
|
||||
# 5: xelatex, as specified by the $xelatex variable (second best)
|
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$pdf_mode = 1;
|
||||
|
||||
# Treat undefined references and citations as well as multiply defined references as
|
||||
# ERRORS instead of WARNINGS.
|
||||
# This is only checked in the *last* run, since naturally, there are undefined references
|
||||
# in initial runs.
|
||||
# This setting is potentially annoying when debugging/editing, but highly desirable
|
||||
# in the CI pipeline, where such a warning should result in a failed pipeline, since the
|
||||
# final document is incomplete/corrupted.
|
||||
#
|
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# However, I could not eradicate all warnings, so that `latexmk` currently fails with
|
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# this option enabled.
|
||||
# Specifically, `microtype` fails together with `fontawesome`/`fontawesome5`, see:
|
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# https://tex.stackexchange.com/a/547514/120853
|
||||
# The fix in that answer did not help.
|
||||
# Setting `verbose=silent` to mute `microtype` warnings did not work.
|
||||
# Switching between `fontawesome` and `fontawesome5` did not help.
|
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$warnings_as_errors = 0;
|
||||
|
||||
# Show used CPU time. Looks like: https://tex.stackexchange.com/a/312224/120853
|
||||
$show_time = 1;
|
||||
|
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# Default is 5; we seem to need more owed to the complexity of the document.
|
||||
# Actual documents probably don't need this many since they won't use all features,
|
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# plus won't be compiling from cold each time.
|
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$max_repeat=7;
|
||||
|
||||
# --shell-escape option (execution of code outside of latex) is required for the
|
||||
#'svg' package.
|
||||
# It converts raw SVG files to the PDF+PDF_TEX combo using InkScape.
|
||||
#
|
||||
# SyncTeX allows to jump between source (code) and output (PDF) in IDEs with support
|
||||
# (many have it). A value of `1` is enabled (gzipped), `-1` is enabled but uncompressed,
|
||||
# `0` is off.
|
||||
# Testing in VSCode w/ LaTeX Workshop only worked for the compressed version.
|
||||
# Adjust this as needed. Of course, only relevant for local use, no effect on a remote
|
||||
# CI pipeline (except for slower compilation, probably).
|
||||
#
|
||||
# %O and %S will forward Options and the Source file, respectively, given to latexmk.
|
||||
#
|
||||
# `set_tex_cmds` applies to all *latex commands (latex, xelatex, lualatex, ...), so
|
||||
# no need to specify these each. This allows to simply change `$pdf_mode` to get a
|
||||
# different engine. Check if this works with `latexmk --commands`.
|
||||
set_tex_cmds("--shell-escape -interaction=nonstopmode --synctex=1 %O %S");
|
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|
||||
# Use default pdf viewer
|
||||
$pdf_previewer = 'zathura';
|
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|
||||
# option 2 is same as 1 (run biber when necessary), but also deletes the
|
||||
# regeneratable bbl-file in a clenaup (`latexmk -c`). Do not use if original
|
||||
# bib file is not available!
|
||||
$bibtex_use = 2; # default: 1
|
||||
|
||||
# Change default `biber` call, help catch errors faster/clearer. See
|
||||
# https://web.archive.org/web/20200526101657/https://www.semipol.de/2018/06/12/latex-best-practices.html#database-entries
|
||||
$biber = "biber --validate-datamodel %O %S";
|
||||
|
||||
# Glossaries
|
||||
add_cus_dep('glo', 'gls', 0, 'run_makeglossaries');
|
||||
add_cus_dep('acn', 'acr', 0, 'run_makeglossaries');
|
||||
|
||||
sub run_makeglossaries {
|
||||
if ( $silent ) {
|
||||
system "makeglossaries -q -s '$_[0].ist' '$_[0]'";
|
||||
}
|
||||
else {
|
||||
system "makeglossaries -s '$_[0].ist' '$_[0]'";
|
||||
};
|
||||
}
|
||||
|
||||
# ======================================================================================
|
||||
# Auxiliary Files
|
||||
# ======================================================================================
|
||||
|
||||
# Let latexmk know about generated files, so they can be used to detect if a
|
||||
# rerun is required, or be deleted in a cleanup.
|
||||
# loe: List of Examples (KOMAScript)
|
||||
# lol: List of Listings (`listings` and `minted` packages)
|
||||
# run.xml: biber runs
|
||||
# glg: glossaries log
|
||||
# glstex: generated from glossaries-extra
|
||||
push @generated_exts, 'loe', 'lol', 'run.xml', 'glstex', 'glo', 'gls', 'glg', 'acn', 'acr', 'alg';
|
||||
|
||||
# Also delete the *.glstex files from package glossaries-extra. Problem is,
|
||||
# that that package generates files of the form "basename-digit.glstex" if
|
||||
# multiple glossaries are present. Latexmk looks for "basename.glstex" and so
|
||||
# does not find those. For that purpose, use wildcard.
|
||||
# Also delete files generated by gnuplot/pgfplots contour plots
|
||||
# (.dat, .script, .table).
|
||||
$clean_ext = "%R-*.glstex %R_contourtmp*.*";
|
||||
179
paper/dehaeze26_cubic_architecture.bib
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@@ -0,0 +1,179 @@
|
||||
@article{stewart65_platf_with_six_degrees_freed,
|
||||
author = {Stewart, D.},
|
||||
title = {A Platform With Six Degrees of Freedom},
|
||||
journal = {Proceedings of the institution of mechanical engineers},
|
||||
volume = 180,
|
||||
number = 1,
|
||||
pages = {371--386},
|
||||
year = 1965,
|
||||
publisher = {Sage Publications Sage UK: London, England},
|
||||
}
|
||||
|
||||
|
||||
|
||||
|
||||
@article{geng94_six_degree_of_freed_activ,
|
||||
author = {Geng, Z. J. and Haynes, L. S.},
|
||||
title = {Six Degree-Of-Freedom Active Vibration Control Using the
|
||||
Stewart Platforms},
|
||||
journal = {IEEE Transactions on Control Systems Technology},
|
||||
volume = 2,
|
||||
number = 1,
|
||||
pages = {45--53},
|
||||
year = 1994,
|
||||
doi = {10.1109/87.273110},
|
||||
url = {https://doi.org/10.1109/87.273110},
|
||||
keywords = {parallel robot, cubic configuration},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@article{preumont07_six_axis_singl_stage_activ,
|
||||
author = {Preumont, A. and Horodinca, M. and Romanescu, I. and de
|
||||
Marneffe, B. and Avraam, M. and Deraemaeker, A. and Bossens, F. and
|
||||
Abu Hanieh, A.},
|
||||
title = {A Six-Axis Single-Stage Active Vibration Isolator Based on
|
||||
Stewart Platform},
|
||||
journal = {Journal of Sound and Vibration},
|
||||
volume = 300,
|
||||
number = {3-5},
|
||||
pages = {644--661},
|
||||
year = 2007,
|
||||
doi = {10.1016/j.jsv.2006.07.050},
|
||||
url = {https://doi.org/10.1016/j.jsv.2006.07.050},
|
||||
keywords = {parallel robot},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@article{jafari03_orthog_gough_stewar_platf_microm,
|
||||
author = {Jafari, F. and McInroy, J. E.},
|
||||
title = {Orthogonal Gough-Stewart Platforms for Micromanipulation},
|
||||
journal = {IEEE Transactions on Robotics and Automation},
|
||||
volume = 19,
|
||||
number = 4,
|
||||
pages = {595--603},
|
||||
year = 2003,
|
||||
doi = {10.1109/tra.2003.814506},
|
||||
url = {https://doi.org/10.1109/tra.2003.814506},
|
||||
issn = {1042-296X},
|
||||
keywords = {parallel robot, cubic configuration},
|
||||
month = 8,
|
||||
publisher = {Institute of Electrical and Electronics Engineers (IEEE)},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@phdthesis{hanieh03_activ_stewar,
|
||||
author = {Abu Hanieh, A.},
|
||||
keywords = {parallel robot},
|
||||
school = {Universit{\'e} Libre de Bruxelles, Brussels, Belgium},
|
||||
title = {Active isolation and damping of vibrations via Stewart
|
||||
platform},
|
||||
year = 2003,
|
||||
}
|
||||
|
||||
|
||||
|
||||
@book{preumont18_vibrat_contr_activ_struc_fourt_edition,
|
||||
author = {Preumont, A.},
|
||||
title = {Vibration Control of Active Structures - Fourth Edition},
|
||||
year = 2018,
|
||||
publisher = {Springer International Publishing},
|
||||
url = {https://doi.org/10.1007/978-3-319-72296-2},
|
||||
doi = {10.1007/978-3-319-72296-2},
|
||||
keywords = {favorite, parallel robot},
|
||||
series = {Solid Mechanics and Its Applications},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@article{thayer02_six_axis_vibrat_isolat_system,
|
||||
author = {Thayer, D. and Campbell, M. and Vagners, J. and
|
||||
von Flotow, A.},
|
||||
title = {Six-Axis Vibration Isolation System Using Soft Actuators
|
||||
and Multiple Sensors},
|
||||
journal = {Journal of Spacecraft and Rockets},
|
||||
volume = 39,
|
||||
number = 2,
|
||||
pages = {206--212},
|
||||
year = 2002,
|
||||
doi = {10.2514/2.3821},
|
||||
url = {https://doi.org/10.2514/2.3821},
|
||||
keywords = {parallel robot},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@article{mcinroy00_desig_contr_flexur_joint_hexap,
|
||||
author = {McInroy, J. E. and Hamann, J. C.},
|
||||
title = {Design and Control of Flexure Jointed Hexapods},
|
||||
journal = {IEEE Transactions on Robotics and Automation},
|
||||
volume = 16,
|
||||
number = 4,
|
||||
pages = {372--381},
|
||||
year = 2000,
|
||||
doi = {10.1109/70.864229},
|
||||
url = {https://doi.org/10.1109/70.864229},
|
||||
keywords = {parallel robot},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@phdthesis{li01_simul_fault_vibrat_isolat_point,
|
||||
author = {Li, X.},
|
||||
keywords = {parallel robot},
|
||||
school = {University of Wyoming},
|
||||
title = {Simultaneous, Fault-tolerant Vibration Isolation and
|
||||
Pointing Control of Flexure Jointed Hexapods},
|
||||
year = 2001,
|
||||
}
|
||||
|
||||
|
||||
|
||||
@inproceedings{mcinroy99_dynam,
|
||||
author = {McInroy, J. E.},
|
||||
title = {Dynamic modeling of flexure jointed hexapods for control
|
||||
purposes},
|
||||
booktitle = {Proceedings of the 1999 IEEE International Conference on
|
||||
Control Applications (Cat. No.99CH36328)},
|
||||
year = 1999,
|
||||
doi = {10.1109/cca.1999.806694},
|
||||
url = {https://doi.org/10.1109/cca.1999.806694},
|
||||
keywords = {parallel robot},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@article{furutani04_nanom_cuttin_machin_using_stewar,
|
||||
author = {Furutani, K. and Suzuki, M. and Kudoh, R.},
|
||||
title = {Nanometre-Cutting Machine Using a Stewart-Platform Parallel
|
||||
Mechanism},
|
||||
journal = {Measurement Science and Technology},
|
||||
volume = 15,
|
||||
number = 2,
|
||||
pages = {467--474},
|
||||
year = 2004,
|
||||
doi = {10.1088/0957-0233/15/2/022},
|
||||
url = {https://doi.org/10.1088/0957-0233/15/2/022},
|
||||
keywords = {parallel robot, cubic configuration},
|
||||
}
|
||||
|
||||
|
||||
|
||||
@article{yang19_dynam_model_decoup_contr_flexib,
|
||||
author = {Yang, X. and Wu, H. and Chen, B. and Kang, S. and Cheng, S.},
|
||||
title = {Dynamic Modeling and Decoupled Control of a Flexible
|
||||
Stewart Platform for Vibration Isolation},
|
||||
journal = {Journal of Sound and Vibration},
|
||||
volume = 439,
|
||||
pages = {398--412},
|
||||
year = 2019,
|
||||
doi = {10.1016/j.jsv.2018.10.007},
|
||||
url = {https://doi.org/10.1016/j.jsv.2018.10.007},
|
||||
issn = {0022-460X},
|
||||
keywords = {parallel robot, flexure, decoupled control},
|
||||
month = 1,
|
||||
publisher = {Elsevier BV},
|
||||
}
|
||||
|
||||
567
paper/dehaeze26_cubic_architecture.org
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@@ -0,0 +1,567 @@
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||||
#+TITLE: Decoupling Properties of the Cubic Architecture
|
||||
:DRAWER:
|
||||
#+LANGUAGE: en
|
||||
#+EMAIL: dehaeze.thomas@gmail.com
|
||||
#+AUTHOR: Dehaeze Thomas
|
||||
|
||||
#+BIND: org-latex-image-default-option "scale=1"
|
||||
#+BIND: org-latex-image-default-width ""
|
||||
|
||||
#+LaTeX_CLASS: scrreprt
|
||||
#+LaTeX_CLASS_OPTIONS: [a4paper, 10pt, DIV=12, parskip=full, bibliography=totoc]
|
||||
#+LATEX_HEADER: \input{preamble.tex}
|
||||
#+LATEX_HEADER_EXTRA: \input{preamble_extra.tex}
|
||||
#+LATEX_HEADER_EXTRA: \bibliography{dehaeze26_cubic_architecture.bib}
|
||||
|
||||
#+BIND: org-latex-bib-compiler "biber"
|
||||
:END:
|
||||
|
||||
#+latex: \clearpage
|
||||
|
||||
* Build :noexport:
|
||||
#+NAME: startblock
|
||||
#+BEGIN_SRC emacs-lisp :results none :tangle no
|
||||
(add-to-list 'org-latex-classes
|
||||
'("scrreprt"
|
||||
"\\documentclass{scrreprt}"
|
||||
("\\chapter{%s}" . "\\chapter*{%s}")
|
||||
("\\section{%s}" . "\\section*{%s}")
|
||||
("\\subsection{%s}" . "\\subsection*{%s}")
|
||||
("\\paragraph{%s}" . "\\paragraph*{%s}")
|
||||
))
|
||||
|
||||
;; Remove automatic org heading labels
|
||||
(defun my-latex-filter-removeOrgAutoLabels (text backend info)
|
||||
"Org-mode automatically generates labels for headings despite explicit use of `#+LABEL`. This filter forcibly removes all automatically generated org-labels in headings."
|
||||
(when (org-export-derived-backend-p backend 'latex)
|
||||
(replace-regexp-in-string "\\\\label{sec:org[a-f0-9]+}\n" "" text)))
|
||||
(add-to-list 'org-export-filter-headline-functions
|
||||
'my-latex-filter-removeOrgAutoLabels)
|
||||
|
||||
;; Remove all org comments in the output LaTeX file
|
||||
(defun delete-org-comments (backend)
|
||||
(loop for comment in (reverse (org-element-map (org-element-parse-buffer)
|
||||
'comment 'identity))
|
||||
do
|
||||
(setf (buffer-substring (org-element-property :begin comment)
|
||||
(org-element-property :end comment))
|
||||
"")))
|
||||
(add-hook 'org-export-before-processing-hook 'delete-org-comments)
|
||||
|
||||
;; Use no package by default
|
||||
(setq org-latex-packages-alist nil)
|
||||
(setq org-latex-default-packages-alist nil)
|
||||
|
||||
;; Do not include the subtitle inside the title
|
||||
(setq org-latex-subtitle-separate t)
|
||||
(setq org-latex-subtitle-format "\\subtitle{%s}")
|
||||
|
||||
(setq org-export-before-parsing-hook '(org-ref-glossary-before-parsing
|
||||
org-ref-acronyms-before-parsing))
|
||||
#+END_SRC
|
||||
|
||||
* Notes :noexport:
|
||||
** Journal
|
||||
https://asmedigitalcollection.asme.org/mechanicaldesign
|
||||
|
||||
Guide: https://www.asme.org/publications-submissions/journals/information-for-authors/journal-guidelines/writing-a-research-paper
|
||||
|
||||
#+begin_quote
|
||||
Research papers undergo full peer review. Authors are encouraged to prepare concise manuscripts that convey clearly the significance of the work. Research Papers do not have a specified length but are usually 8,000 to 12,000 words with 5-8 figures or tables.
|
||||
#+end_quote
|
||||
|
||||
** TODO [#B] Add more content from the PhD thesis?
|
||||
|
||||
Maybe add:
|
||||
- [[file:~/Cloud/work-projects/ID31-NASS/phd-thesis-chapters/B1-nass-geometry/nass-geometry.org::*Review of Stewart platforms][Review of Stewart platforms]]
|
||||
- [[file:~/Cloud/work-projects/ID31-NASS/phd-thesis-chapters/B1-nass-geometry/nass-geometry.org::*Effect of geometry on Stewart platform properties][Effect of geometry on Stewart platform properties]]
|
||||
|
||||
* Introduction :ignore:
|
||||
|
||||
The Cubic configuration for the Stewart platform was first proposed by Dr. Gough in a comment to the original paper by Dr. Stewart [[cite:&stewart65_platf_with_six_degrees_freed]].
|
||||
This configuration is characterized by active struts arranged in a mutually orthogonal configuration connecting the corners of a cube, as shown in Figure ref:fig:detail_kinematics_cubic_architecture_example.
|
||||
|
||||
Typically, the struts have similar length to the cube's edges, as illustrated in Figure ref:fig:detail_kinematics_cubic_architecture_example.
|
||||
Practical implementations of such configurations can be observed in Figures ref:fig:detail_kinematics_jpl, ref:fig:detail_kinematics_uw_gsp and ref:fig:detail_kinematics_uqp.
|
||||
It is also possible to implement designs with strut lengths smaller than the cube's edges (Figure ref:fig:detail_kinematics_cubic_architecture_example_small), as exemplified in Figure ref:fig:detail_kinematics_ulb_pz.
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_architecture_examples
|
||||
#+caption: Typical Stewart platform cubic architectures in which struts' length is similar to the cube edges's length (\subref{fig:detail_kinematics_cubic_architecture_example}) or is taking just a portion of the edge (\subref{fig:detail_kinematics_cubic_architecture_example_small}).
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_architecture_example}Classical Cubic architecture}
|
||||
#+attr_latex: :options {0.49\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :scale 1
|
||||
[[file:figs/detail_kinematics_cubic_architecture_example.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_architecture_example_small}Alternative configuration}
|
||||
#+attr_latex: :options {0.49\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :scale 1
|
||||
[[file:figs/detail_kinematics_cubic_architecture_example_small.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
|
||||
Several advantageous properties attributed to the cubic configuration have contributed to its widespread adoption [[cite:&geng94_six_degree_of_freed_activ;&preumont07_six_axis_singl_stage_activ;&jafari03_orthog_gough_stewar_platf_microm]]: simplified kinematics relationships and dynamical analysis [[cite:&geng94_six_degree_of_freed_activ]]; uniform stiffness in all directions [[cite:&hanieh03_activ_stewar]]; uniform mobility [[cite:&preumont18_vibrat_contr_activ_struc_fourt_edition, chapt.8.5.2]]; and minimization of the cross coupling between actuators and sensors in different struts [[cite:&preumont07_six_axis_singl_stage_activ]].
|
||||
This minimization is attributed to the fact that the struts are orthogonal to each other, and is said to facilitate collocated sensor-actuator control system design, i.e., the implementation of decentralized control [[cite:&geng94_six_degree_of_freed_activ;&thayer02_six_axis_vibrat_isolat_system]].
|
||||
|
||||
These properties are examined in this section to assess their relevance for the nano-hexapod.
|
||||
The mobility and stiffness properties of the cubic configuration are analyzed in Section ref:ssec:detail_kinematics_cubic_static.
|
||||
Dynamical decoupling is investigated in Section ref:ssec:detail_kinematics_cubic_dynamic, while decentralized control, crucial for the NASS, is examined in Section ref:ssec:detail_kinematics_decentralized_control.
|
||||
Given that the cubic architecture imposes strict geometric constraints, alternative designs are proposed in Section ref:ssec:detail_kinematics_cubic_design.
|
||||
The ultimate objective is to determine the suitability of the cubic architecture for the nano-hexapod.
|
||||
|
||||
* Static Properties
|
||||
<<ssec:detail_kinematics_cubic_static>>
|
||||
** Stiffness matrix for the Cubic architecture
|
||||
|
||||
Consider the cubic architecture shown in Figure ref:fig:detail_kinematics_cubic_schematic_full.
|
||||
The unit vectors corresponding to the edges of the cube are described by equation eqref:eq:detail_kinematics_cubic_s.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_s}
|
||||
\hat{\bm{s}}_1 = \begin{bmatrix} \frac{\sqrt{2}}{\sqrt{3}} \\ 0 \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_2 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{-1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_3 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{ 1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_4 = \begin{bmatrix} \frac{\sqrt{2}}{\sqrt{3}} \\ 0 \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_5 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{-1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_6 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{ 1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_schematic_cases
|
||||
#+caption: Cubic architecture. Struts are represented in blue. The cube's center by a black dot. The Struts can match the cube's edges (\subref{fig:detail_kinematics_cubic_schematic_full}) or just take a portion of the edge (\subref{fig:detail_kinematics_cubic_schematic})
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_schematic_full}Full cube}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :scale 0.9
|
||||
[[file:figs/detail_kinematics_cubic_schematic_full.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_schematic}Cube's portion}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :scale 0.9
|
||||
[[file:figs/detail_kinematics_cubic_schematic.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
Coordinates of the cube's vertices relevant for the top joints, expressed with respect to the cube's center, are shown in equation eqref:eq:detail_kinematics_cubic_vertices.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_vertices}
|
||||
\tilde{\bm{b}}_1 = \tilde{\bm{b}}_2 = H_c \begin{bmatrix} \frac{1}{\sqrt{2}} \\ \frac{-\sqrt{3}}{\sqrt{2}} \\ \frac{1}{2} \end{bmatrix}, \quad
|
||||
\tilde{\bm{b}}_3 = \tilde{\bm{b}}_4 = H_c \begin{bmatrix} \frac{1}{\sqrt{2}} \\ \frac{ \sqrt{3}}{\sqrt{2}} \\ \frac{1}{2} \end{bmatrix}, \quad
|
||||
\tilde{\bm{b}}_5 = \tilde{\bm{b}}_6 = H_c \begin{bmatrix} \frac{-2}{\sqrt{2}} \\ 0 \\ \frac{1}{2} \end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
In the case where top joints are positioned at the cube's vertices, a diagonal stiffness matrix is obtained as shown in equation eqref:eq:detail_kinematics_cubic_stiffness.
|
||||
Translation stiffness is twice the stiffness of the struts, and rotational stiffness is proportional to the square of the cube's size $H_c$.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_stiffness}
|
||||
\bm{K}_{\{B\} = \{C\}} = k \begin{bmatrix}
|
||||
2 & 0 & 0 & 0 & 0 & 0 \\
|
||||
0 & 2 & 0 & 0 & 0 & 0 \\
|
||||
0 & 0 & 2 & 0 & 0 & 0 \\
|
||||
0 & 0 & 0 & \frac{3}{2} H_c^2 & 0 & 0 \\
|
||||
0 & 0 & 0 & 0 & \frac{3}{2} H_c^2 & 0 \\
|
||||
0 & 0 & 0 & 0 & 0 & 6 H_c^2 \\
|
||||
\end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
However, typically, the top joints are not placed at the cube's vertices but at positions along the cube's edges (Figure ref:fig:detail_kinematics_cubic_schematic).
|
||||
In that case, the location of the top joints can be expressed by equation eqref:eq:detail_kinematics_cubic_edges, yet the computed stiffness matrix remains identical to Equation eqref:eq:detail_kinematics_cubic_stiffness.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_edges}
|
||||
\bm{b}_i = \tilde{\bm{b}}_i + \alpha \hat{\bm{s}}_i
|
||||
\end{equation}
|
||||
|
||||
|
||||
The stiffness matrix is therefore diagonal when the considered $\{B\}$ frame is located at the center of the cube (shown by frame $\{C\}$).
|
||||
This means that static forces (resp torques) applied at the cube's center will induce pure translations (resp rotations around the cube's center).
|
||||
This specific location where the stiffness matrix is diagonal is referred to as the "Center of Stiffness" (analogous to the "Center of Mass" where the mass matrix is diagonal).
|
||||
|
||||
** Effect of having frame $\{B\}$ off-centered
|
||||
|
||||
When the reference frames $\{A\}$ and $\{B\}$ are shifted from the cube's center, off-diagonal elements emerge in the stiffness matrix.
|
||||
|
||||
Considering a vertical shift as shown in Figure ref:fig:detail_kinematics_cubic_schematic, the stiffness matrix transforms into that shown in Equation eqref:eq:detail_kinematics_cubic_stiffness_off_centered.
|
||||
Off-diagonal elements increase proportionally with the height difference between the cube's center and the considered $\{B\}$ frame.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_stiffness_off_centered}
|
||||
\bm{K}_{\{B\} \neq \{C\}} = k \begin{bmatrix}
|
||||
2 & 0 & 0 & 0 & -2 H & 0 \\
|
||||
0 & 2 & 0 & 2 H & 0 & 0 \\
|
||||
0 & 0 & 2 & 0 & 0 & 0 \\
|
||||
0 & 2 H & 0 & \frac{3}{2} H_c^2 + 2 H^2 & 0 & 0 \\
|
||||
-2 H & 0 & 0 & 0 & \frac{3}{2} H_c^2 + 2 H^2 & 0 \\
|
||||
0 & 0 & 0 & 0 & 0 & 6 H_c^2 \\
|
||||
\end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
This stiffness matrix structure is characteristic of Stewart platforms exhibiting symmetry, and is not an exclusive property of cubic architectures.
|
||||
Therefore, the stiffness characteristics of the cubic architecture are only distinctive when considering a reference frame located at the cube's center.
|
||||
This poses a practical limitation, as in most applications, the relevant frame (where motion is of interest and forces are applied) is located above the top platform.
|
||||
|
||||
It should be noted that for the stiffness matrix to be diagonal, the cube's center doesn't need to coincide with the geometric center of the Stewart platform.
|
||||
This observation leads to the interesting alternative architectures presented in Section ref:ssec:detail_kinematics_cubic_design.
|
||||
|
||||
** Uniform Mobility
|
||||
|
||||
The translational mobility of the Stewart platform with constant orientation was analyzed.
|
||||
Considering limited actuator stroke (elongation of each strut), the maximum achievable positions in XYZ space were estimated.
|
||||
The resulting mobility in X, Y, and Z directions for the cubic architecture is illustrated in Figure ref:fig:detail_kinematics_cubic_mobility_translations.
|
||||
|
||||
The translational workspace analysis reveals that for the cubic architecture, the achievable positions form a cube whose axes align with the struts, with the cube's edge length corresponding to the strut axial stroke.
|
||||
These findings suggest that the mobility pattern is more subtle than sometimes described in the literature [[cite:&mcinroy00_desig_contr_flexur_joint_hexap]], exhibiting uniformity primarily along directions aligned with the cube's edges rather than uniform spherical distribution in all XYZ directions.
|
||||
This configuration still offers more consistent mobility characteristics compared to alternative architectures illustrated in Figure ref:fig:detail_kinematics_mobility_trans.
|
||||
|
||||
The rotational mobility, illustrated in Figure ref:fig:detail_kinematics_cubic_mobility_rotations, exhibits greater achievable angular stroke in the $R_x$ and $R_y$ directions compared to the $R_z$ direction.
|
||||
Furthermore, an inverse relationship exists between the cube's dimension and rotational mobility, with larger cube sizes corresponding to more limited angular displacement capabilities.
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_mobility
|
||||
#+caption: Mobility of a Stewart platform with Cubic architecture. Both for translations (\subref{fig:detail_kinematics_cubic_mobility_translations}) and rotations (\subref{fig:detail_kinematics_cubic_mobility_rotations})
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_mobility_translations}Mobility in translation}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :scale 1
|
||||
[[file:figs/detail_kinematics_cubic_mobility_translations.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_mobility_rotations}Mobility in rotation}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :scale 1
|
||||
[[file:figs/detail_kinematics_cubic_mobility_rotations.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
* Dynamical Decoupling
|
||||
<<ssec:detail_kinematics_cubic_dynamic>>
|
||||
** Introduction :ignore:
|
||||
|
||||
This section examines the dynamics of the cubic architecture in the Cartesian frame which corresponds to the transfer function from forces and torques $\bm{\mathcal{F}}$ to translations and rotations $\bm{\mathcal{X}}$ of the top platform.
|
||||
When relative motion sensors are integrated in each strut (measuring $\bm{\mathcal{L}}$), the pose $\bm{\mathcal{X}}$ is computed using the Jacobian matrix as shown in Figure ref:fig:detail_kinematics_centralized_control.
|
||||
|
||||
#+name: fig:detail_kinematics_centralized_control
|
||||
#+caption: Typical control architecture in the cartesian frame
|
||||
[[file:figs/detail_kinematics_centralized_control.png]]
|
||||
|
||||
** Low frequency and High frequency coupling
|
||||
|
||||
As derived during the conceptual design phase, the dynamics from $\bm{\mathcal{F}}$ to $\bm{\mathcal{X}}$ is described by Equation eqref:eq:detail_kinematics_transfer_function_cart.
|
||||
At low frequency, the behavior of the platform depends on the stiffness matrix eqref:eq:detail_kinematics_transfer_function_cart_low_freq.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_transfer_function_cart_low_freq}
|
||||
\frac{{\mathcal{X}}}{\bm{\mathcal{F}}}(j \omega) \xrightarrow[\omega \to 0]{} \bm{K}^{-1}
|
||||
\end{equation}
|
||||
|
||||
In Section ref:ssec:detail_kinematics_cubic_static, it was demonstrated that for the cubic configuration, the stiffness matrix is diagonal if frame $\{B\}$ is positioned at the cube's center.
|
||||
In this case, the "Cartesian" plant is decoupled at low frequency.
|
||||
At high frequency, the behavior is governed by the mass matrix (evaluated at frame $\{B\}$) eqref:eq:detail_kinematics_transfer_function_high_freq.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_transfer_function_high_freq}
|
||||
\frac{{\mathcal{X}}}{\bm{\mathcal{F}}}(j \omega) \xrightarrow[\omega \to \infty]{} - \omega^2 \bm{M}^{-1}
|
||||
\end{equation}
|
||||
|
||||
To achieve a diagonal mass matrix, the center of mass of the mobile components must coincide with the $\{B\}$ frame, and the principal axes of inertia must align with the axes of the $\{B\}$ frame.
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_payload
|
||||
#+caption: Cubic stewart platform with top cylindrical payload
|
||||
#+attr_latex: :width 0.6\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_payload.png]]
|
||||
|
||||
To verify these properties, a cubic Stewart platform with a cylindrical payload was analyzed (Figure ref:fig:detail_kinematics_cubic_payload).
|
||||
Transfer functions from $\bm{\mathcal{F}}$ to $\bm{\mathcal{X}}$ were computed for two specific locations of the $\{B\}$ frames.
|
||||
When the $\{B\}$ frame was positioned at the center of mass, coupling at low frequency was observed due to the non-diagonal stiffness matrix (Figure ref:fig:detail_kinematics_cubic_cart_coupling_com).
|
||||
Conversely, when positioned at the center of stiffness, coupling occurred at high frequency due to the non-diagonal mass matrix (Figure ref:fig:detail_kinematics_cubic_cart_coupling_cok).
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_cart_coupling
|
||||
#+caption: Transfer functions for a Cubic Stewart platform expressed in the Cartesian frame. Two locations of the $\{B\}$ frame are considered: at the center of mass of the moving body (\subref{fig:detail_kinematics_cubic_cart_coupling_com}) and at the cube's center (\subref{fig:detail_kinematics_cubic_cart_coupling_cok}).
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_cart_coupling_com}$\{B\}$ at the center of mass}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_cart_coupling_com.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_cart_coupling_cok}$\{B\}$ at the cube's center}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_cart_coupling_cok.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
** Payload's CoM at the cube's center
|
||||
|
||||
An effective strategy for improving dynamical performances involves aligning the cube's center (center of stiffness) with the center of mass of the moving components [[cite:&li01_simul_fault_vibrat_isolat_point]].
|
||||
This can be achieved by positioning the payload below the top platform, such that the center of mass of the moving body coincides with the cube's center (Figure ref:fig:detail_kinematics_cubic_centered_payload).
|
||||
This approach was physically implemented in several studies [[cite:&mcinroy99_dynam;&jafari03_orthog_gough_stewar_platf_microm]], as shown in Figure ref:fig:detail_kinematics_uw_gsp.
|
||||
The resulting dynamics are indeed well-decoupled (Figure ref:fig:detail_kinematics_cubic_cart_coupling_com_cok), taking advantage from diagonal stiffness and mass matrices.
|
||||
The primary limitation of this approach is that, for many applications including the nano-hexapod, the payload must be positioned above the top platform.
|
||||
If a design similar to Figure ref:fig:detail_kinematics_cubic_centered_payload were employed for the nano-hexapod, the X-ray beam would intersect with the struts during spindle rotation.
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_com_cok
|
||||
#+caption: Cubic Stewart platform with payload at the cube's center (\subref{fig:detail_kinematics_cubic_centered_payload}). Obtained cartesian plant is fully decoupled (\subref{fig:detail_kinematics_cubic_cart_coupling_com_cok})
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_centered_payload}Payload at the cube's center}
|
||||
#+attr_latex: :options {0.49\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_centered_payload.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_cart_coupling_com_cok}Fully decoupled cartesian plant}
|
||||
#+attr_latex: :options {0.49\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_cart_coupling_com_cok.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
** Conclusion
|
||||
|
||||
The analysis of dynamical properties of the cubic architecture yields several important conclusions.
|
||||
Static decoupling, characterized by a diagonal stiffness matrix, is achieved when reference frames $\{A\}$ and $\{B\}$ are positioned at the cube's center.
|
||||
Note that this property can also be obtained with non-cubic architectures that exhibit symmetrical strut arrangements.
|
||||
Dynamic decoupling requires both static decoupling and coincidence of the mobile platform's center of mass with reference frame $\{B\}$.
|
||||
While this configuration offers powerful control advantages, it requires positioning the payload at the cube's center, which is highly restrictive and often impractical.
|
||||
|
||||
* Decentralized Control
|
||||
<<ssec:detail_kinematics_decentralized_control>>
|
||||
** Introduction :ignore:
|
||||
|
||||
The orthogonal arrangement of struts in the cubic architecture suggests a potential minimization of inter-strut coupling, which could theoretically create favorable conditions for decentralized control.
|
||||
Two sensor types integrated in the struts are considered: displacement sensors and force sensors.
|
||||
The control architecture is illustrated in Figure ref:fig:detail_kinematics_decentralized_control, where $\bm{K}_{\mathcal{L}}$ represents a diagonal transfer function matrix.
|
||||
|
||||
#+name: fig:detail_kinematics_decentralized_control
|
||||
#+caption: Decentralized control in the frame of the struts.
|
||||
[[file:figs/detail_kinematics_decentralized_control.png]]
|
||||
|
||||
The obtained plant dynamics in the frame of the struts are compared for two Stewart platforms.
|
||||
The first employs a cubic architecture shown in Figure ref:fig:detail_kinematics_cubic_payload.
|
||||
The second uses a non-cubic Stewart platform shown in Figure ref:fig:detail_kinematics_non_cubic_payload, featuring identical payload and strut dynamics but with struts oriented more vertically to differentiate it from the cubic architecture.
|
||||
|
||||
#+name: fig:detail_kinematics_non_cubic_payload
|
||||
#+caption: Stewart platform with non-cubic architecture
|
||||
#+attr_latex: :width 0.6\linewidth
|
||||
[[file:figs/detail_kinematics_non_cubic_payload.png]]
|
||||
|
||||
** Relative Displacement Sensors
|
||||
|
||||
The transfer functions from actuator force in each strut to the relative motion of the struts are presented in Figure ref:fig:detail_kinematics_decentralized_dL.
|
||||
As anticipated from the equations of motion from $\bm{f}$ to $\bm{\mathcal{L}}$ eqref:eq:detail_kinematics_transfer_function_struts, the $6 \times 6$ plant is decoupled at low frequency.
|
||||
At high frequency, coupling is observed as the mass matrix projected in the strut frame is not diagonal.
|
||||
|
||||
No significant advantage is evident for the cubic architecture (Figure ref:fig:detail_kinematics_cubic_decentralized_dL) compared to the non-cubic architecture (Figure ref:fig:detail_kinematics_non_cubic_decentralized_dL).
|
||||
The resonance frequencies differ between the two cases because the more vertical strut orientation in the non-cubic architecture alters the stiffness properties of the Stewart platform, consequently shifting the frequencies of various modes.
|
||||
|
||||
#+name: fig:detail_kinematics_decentralized_dL
|
||||
#+caption: Bode plot of the transfer functions from actuator force to relative displacement sensor in each strut. Both for a non-cubic architecture (\subref{fig:detail_kinematics_non_cubic_decentralized_dL}) and for a cubic architecture (\subref{fig:detail_kinematics_cubic_decentralized_dL})
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_non_cubic_decentralized_dL}Non cubic architecture}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_non_cubic_decentralized_dL.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_decentralized_dL}Cubic architecture}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_decentralized_dL.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
** Force Sensors
|
||||
|
||||
Similarly, the transfer functions from actuator force to force sensors in each strut were analyzed for both cubic and non-cubic Stewart platforms.
|
||||
The results are presented in Figure ref:fig:detail_kinematics_decentralized_fn.
|
||||
The system demonstrates good decoupling at high frequency in both cases, with no clear advantage for the cubic architecture.
|
||||
|
||||
#+name: fig:detail_kinematics_decentralized_fn
|
||||
#+caption: Bode plot of the transfer functions from actuator force to force sensor in each strut. Both for a non-cubic architecture (\subref{fig:detail_kinematics_non_cubic_decentralized_fn}) and for a cubic architecture (\subref{fig:detail_kinematics_cubic_decentralized_fn})
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_non_cubic_decentralized_fn}Non cubic architecture}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_non_cubic_decentralized_fn.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_decentralized_fn}Cubic architecture}
|
||||
#+attr_latex: :options {0.48\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.95\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_decentralized_fn.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
** Conclusion
|
||||
|
||||
The presented results do not demonstrate the pronounced decoupling advantages often associated with cubic architectures in the literature.
|
||||
Both the cubic and non-cubic configurations exhibited similar coupling characteristics, suggesting that the benefits of orthogonal strut arrangement for decentralized control is less obvious than often reported in the literature.
|
||||
|
||||
* Cubic architecture with Cube's center above the top platform
|
||||
<<ssec:detail_kinematics_cubic_design>>
|
||||
** Introduction :ignore:
|
||||
|
||||
As demonstrated in Section ref:ssec:detail_kinematics_cubic_dynamic, the cubic architecture can exhibit advantageous dynamical properties when the center of mass of the moving body coincides with the cube's center, resulting in diagonal mass and stiffness matrices.
|
||||
As shown in Section ref:ssec:detail_kinematics_cubic_static, the stiffness matrix is diagonal when the considered $\{B\}$ frame is located at the cube's center.
|
||||
However, the $\{B\}$ frame is typically positioned above the top platform where forces are applied and displacements are measured.
|
||||
|
||||
This section proposes modifications to the cubic architecture to enable positioning the payload above the top platform while still leveraging the advantageous dynamical properties of the cubic configuration.
|
||||
|
||||
Three key parameters define the geometry of the cubic Stewart platform: $H$, the height of the Stewart platform (distance from fixed base to mobile platform); $H_c$, the height of the cube, as shown in Figure ref:fig:detail_kinematics_cubic_schematic_full; and $H_{CoM}$, the height of the center of mass relative to the mobile platform (coincident with the cube's center).
|
||||
|
||||
Depending on the cube's size $H_c$ in relation to $H$ and $H_{CoM}$, different designs emerge.
|
||||
In the following examples, $H = 100\,mm$ and $H_{CoM} = 20\,mm$.
|
||||
|
||||
** Small cube
|
||||
|
||||
When the cube size $H_c$ is smaller than twice the height of the CoM $H_{CoM}$ eqref:eq:detail_kinematics_cube_small, the resulting design is shown in Figure ref:fig:detail_kinematics_cubic_above_small.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cube_small}
|
||||
H_c < 2 H_{CoM}
|
||||
\end{equation}
|
||||
|
||||
# TODO - Add link to Figure ref:fig:nhexa_stewart_piezo_furutani (page pageref:fig:nhexa_stewart_piezo_furutani)
|
||||
This configuration is similar to that described in [[cite:&furutani04_nanom_cuttin_machin_using_stewar]], although they do not explicitly identify it as a cubic configuration.
|
||||
Adjacent struts are parallel to each other, differing from the typical architecture where parallel struts are positioned opposite to each other.
|
||||
|
||||
This approach yields a compact architecture, but the small cube size may result in insufficient rotational stiffness.
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_above_small
|
||||
#+caption: Cubic architecture with cube's center above the top platform. A cube height of 40mm is used.
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_small_iso}Isometric view}
|
||||
#+attr_latex: :options {0.36\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_small_iso.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_small_side}Side view}
|
||||
#+attr_latex: :options {0.30\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_small_side.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_small_top}Top view}
|
||||
#+attr_latex: :options {0.30\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_small_top.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
** Medium sized cube
|
||||
|
||||
Increasing the cube's size such that eqref:eq:detail_kinematics_cube_medium is verified produces an architecture with intersecting struts (Figure ref:fig:detail_kinematics_cubic_above_medium).
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cube_medium}
|
||||
2 H_{CoM} < H_c < 2 (H_{CoM} + H)
|
||||
\end{equation}
|
||||
|
||||
This configuration resembles the design proposed in [[cite:&yang19_dynam_model_decoup_contr_flexib]] (Figure ref:fig:detail_kinematics_yang19), although their design is not strictly cubic.
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_above_medium
|
||||
#+caption: Cubic architecture with cube's center above the top platform. A cube height of 140mm is used.
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_medium_iso}Isometric view}
|
||||
#+attr_latex: :options {0.36\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_medium_iso.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_medium_side}Side view}
|
||||
#+attr_latex: :options {0.30\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_medium_side.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_medium_top}Top view}
|
||||
#+attr_latex: :options {0.30\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_medium_top.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
** Large cube
|
||||
|
||||
When the cube's height exceeds twice the sum of the platform height and CoM height eqref:eq:detail_kinematics_cube_large, the architecture shown in Figure ref:fig:detail_kinematics_cubic_above_large is obtained.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cube_large}
|
||||
2 (H_{CoM} + H) < H_c
|
||||
\end{equation}
|
||||
|
||||
#+name: fig:detail_kinematics_cubic_above_large
|
||||
#+caption: Cubic architecture with cube's center above the top platform. A cube height of 240mm is used.
|
||||
#+attr_latex: :options [htbp]
|
||||
#+begin_figure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_large_iso}Isometric view}
|
||||
#+attr_latex: :options {0.36\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_large_iso.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_large_side}Side view}
|
||||
#+attr_latex: :options {0.30\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_large_side.png]]
|
||||
#+end_subfigure
|
||||
#+attr_latex: :caption \subcaption{\label{fig:detail_kinematics_cubic_above_large_top}Top view}
|
||||
#+attr_latex: :options {0.30\textwidth}
|
||||
#+begin_subfigure
|
||||
#+attr_latex: :width 0.9\linewidth
|
||||
[[file:figs/detail_kinematics_cubic_above_large_top.png]]
|
||||
#+end_subfigure
|
||||
#+end_figure
|
||||
|
||||
** Platform size
|
||||
|
||||
For the proposed configuration, the top joints $\bm{b}_i$ (resp. the bottom joints $\bm{a}_i$) and are positioned on a circle with radius $R_{b_i}$ (resp. $R_{a_i}$) described by Equation eqref:eq:detail_kinematics_cube_joints.
|
||||
|
||||
\begin{subequations}\label{eq:detail_kinematics_cube_joints}
|
||||
\begin{align}
|
||||
R_{b_i} &= \sqrt{\frac{3}{2} H_c^2 + 2 H_{CoM}^2} \label{eq:detail_kinematics_cube_top_joints} \\
|
||||
R_{a_i} &= \sqrt{\frac{3}{2} H_c^2 + 2 (H_{CoM} + H)^2} \label{eq:detail_kinematics_cube_bot_joints}
|
||||
\end{align}
|
||||
\end{subequations}
|
||||
|
||||
Since the rotational stiffness for the cubic architecture scales with the square of the cube's height eqref:eq:detail_kinematics_cubic_stiffness, the cube's size can be determined based on rotational stiffness requirements.
|
||||
Subsequently, using Equation eqref:eq:detail_kinematics_cube_joints, the dimensions of the top and bottom platforms can be calculated.
|
||||
|
||||
* Conclusion
|
||||
:PROPERTIES:
|
||||
:UNNUMBERED: t
|
||||
:END:
|
||||
|
||||
The analysis of the cubic architecture for Stewart platforms yielded several important findings.
|
||||
While the cubic configuration provides uniform stiffness in the XYZ directions, it stiffness property becomes particularly advantageous when forces and torques are applied at the cube's center.
|
||||
Under these conditions, the stiffness matrix becomes diagonal, resulting in a decoupled Cartesian plant at low frequencies.
|
||||
|
||||
Regarding mobility, the translational capabilities of the cubic configuration exhibit uniformity along the directions of the orthogonal struts, rather than complete uniformity in the Cartesian space.
|
||||
This understanding refines the characterization of cubic architecture mobility commonly presented in literature.
|
||||
|
||||
The analysis of decentralized control in the frame of the struts revealed more nuanced results than expected.
|
||||
While cubic architectures are frequently associated with reduced coupling between actuators and sensors, this study showed that these benefits may be more subtle or context-dependent than commonly described.
|
||||
Under the conditions analyzed, the coupling characteristics of cubic and non-cubic configurations, in the frame of the struts, appeared similar.
|
||||
|
||||
Fully decoupled dynamics in the Cartesian frame can be achieved when the center of mass of the moving body coincides with the cube's center.
|
||||
However, this arrangement presents practical challenges, as the cube's center is traditionally located between the top and bottom platforms, making payload placement problematic for many applications.
|
||||
|
||||
To address this limitation, modified cubic architectures have been proposed with the cube's center positioned above the top platform.
|
||||
Three distinct configurations have been identified, each with different geometric arrangements but sharing the common characteristic that the cube's center is positioned above the top platform.
|
||||
This structural modification enables the alignment of the moving body's center of mass with the center of stiffness, resulting in beneficial decoupling properties in the Cartesian frame.
|
||||
|
||||
* Bibliography :ignore:
|
||||
#+latex: \printbibliography[heading=bibintoc,title={Bibliography}]
|
||||
BIN
paper/dehaeze26_cubic_architecture.pdf
Normal file
469
paper/dehaeze26_cubic_architecture.tex
Normal file
@@ -0,0 +1,469 @@
|
||||
% Created 2025-11-26 Wed 09:39
|
||||
% Intended LaTeX compiler: pdflatex
|
||||
\documentclass[a4paper, 10pt, DIV=12, parskip=full, bibliography=totoc]{scrreprt}
|
||||
|
||||
\input{preamble.tex}
|
||||
\input{preamble_extra.tex}
|
||||
\bibliography{dehaeze26_cubic_architecture.bib}
|
||||
\author{Dehaeze Thomas}
|
||||
\date{\today}
|
||||
\title{Decoupling Properties of the Cubic Architecture}
|
||||
\hypersetup{
|
||||
pdfauthor={Dehaeze Thomas},
|
||||
pdftitle={Decoupling Properties of the Cubic Architecture},
|
||||
pdfkeywords={},
|
||||
pdfsubject={},
|
||||
pdfcreator={Emacs 30.2 (Org mode 9.7.34)},
|
||||
pdflang={English}}
|
||||
\usepackage{biblatex}
|
||||
|
||||
\begin{document}
|
||||
|
||||
\maketitle
|
||||
\tableofcontents
|
||||
|
||||
\clearpage
|
||||
The Cubic configuration for the Stewart platform was first proposed by Dr. Gough in a comment to the original paper by Dr. Stewart \cite{stewart65_platf_with_six_degrees_freed}.
|
||||
This configuration is characterized by active struts arranged in a mutually orthogonal configuration connecting the corners of a cube, as shown in Figure \ref{fig:detail_kinematics_cubic_architecture_example}.
|
||||
|
||||
Typically, the struts have similar length to the cube's edges, as illustrated in Figure \ref{fig:detail_kinematics_cubic_architecture_example}.
|
||||
Practical implementations of such configurations can be observed in Figures \ref{fig:detail_kinematics_jpl}, \ref{fig:detail_kinematics_uw_gsp} and \ref{fig:detail_kinematics_uqp}.
|
||||
It is also possible to implement designs with strut lengths smaller than the cube's edges (Figure \ref{fig:detail_kinematics_cubic_architecture_example_small}), as exemplified in Figure \ref{fig:detail_kinematics_ulb_pz}.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.49\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,scale=1]{figs/detail_kinematics_cubic_architecture_example.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_architecture_example}Classical Cubic architecture}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.49\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,scale=1]{figs/detail_kinematics_cubic_architecture_example_small.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_architecture_example_small}Alternative configuration}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_architecture_examples}Typical Stewart platform cubic architectures in which struts' length is similar to the cube edges's length (\subref{fig:detail_kinematics_cubic_architecture_example}) or is taking just a portion of the edge (\subref{fig:detail_kinematics_cubic_architecture_example_small}).}
|
||||
\end{figure}
|
||||
|
||||
|
||||
Several advantageous properties attributed to the cubic configuration have contributed to its widespread adoption \cite{geng94_six_degree_of_freed_activ,preumont07_six_axis_singl_stage_activ,jafari03_orthog_gough_stewar_platf_microm}: simplified kinematics relationships and dynamical analysis \cite{geng94_six_degree_of_freed_activ}; uniform stiffness in all directions \cite{hanieh03_activ_stewar}; uniform mobility \cite[, chapt.8.5.2]{preumont18_vibrat_contr_activ_struc_fourt_edition}; and minimization of the cross coupling between actuators and sensors in different struts \cite{preumont07_six_axis_singl_stage_activ}.
|
||||
This minimization is attributed to the fact that the struts are orthogonal to each other, and is said to facilitate collocated sensor-actuator control system design, i.e., the implementation of decentralized control \cite{geng94_six_degree_of_freed_activ,thayer02_six_axis_vibrat_isolat_system}.
|
||||
|
||||
These properties are examined in this section to assess their relevance for the nano-hexapod.
|
||||
The mobility and stiffness properties of the cubic configuration are analyzed in Section \ref{ssec:detail_kinematics_cubic_static}.
|
||||
Dynamical decoupling is investigated in Section \ref{ssec:detail_kinematics_cubic_dynamic}, while decentralized control, crucial for the NASS, is examined in Section \ref{ssec:detail_kinematics_decentralized_control}.
|
||||
Given that the cubic architecture imposes strict geometric constraints, alternative designs are proposed in Section \ref{ssec:detail_kinematics_cubic_design}.
|
||||
The ultimate objective is to determine the suitability of the cubic architecture for the nano-hexapod.
|
||||
\chapter{Static Properties}
|
||||
\label{ssec:detail_kinematics_cubic_static}
|
||||
\section{Stiffness matrix for the Cubic architecture}
|
||||
|
||||
Consider the cubic architecture shown in Figure \ref{fig:detail_kinematics_cubic_schematic_full}.
|
||||
The unit vectors corresponding to the edges of the cube are described by equation \eqref{eq:detail_kinematics_cubic_s}.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_s}
|
||||
\hat{\bm{s}}_1 = \begin{bmatrix} \frac{\sqrt{2}}{\sqrt{3}} \\ 0 \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_2 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{-1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_3 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{ 1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_4 = \begin{bmatrix} \frac{\sqrt{2}}{\sqrt{3}} \\ 0 \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_5 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{-1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix} \quad
|
||||
\hat{\bm{s}}_6 = \begin{bmatrix} \frac{-1}{\sqrt{6}} \\ \frac{ 1}{\sqrt{2}} \\ \frac{1}{\sqrt{3}} \end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,scale=0.9]{figs/detail_kinematics_cubic_schematic_full.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_schematic_full}Full cube}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,scale=0.9]{figs/detail_kinematics_cubic_schematic.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_schematic}Cube's portion}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_schematic_cases}Cubic architecture. Struts are represented in blue. The cube's center by a black dot. The Struts can match the cube's edges (\subref{fig:detail_kinematics_cubic_schematic_full}) or just take a portion of the edge (\subref{fig:detail_kinematics_cubic_schematic})}
|
||||
\end{figure}
|
||||
|
||||
Coordinates of the cube's vertices relevant for the top joints, expressed with respect to the cube's center, are shown in equation \eqref{eq:detail_kinematics_cubic_vertices}.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_vertices}
|
||||
\tilde{\bm{b}}_1 = \tilde{\bm{b}}_2 = H_c \begin{bmatrix} \frac{1}{\sqrt{2}} \\ \frac{-\sqrt{3}}{\sqrt{2}} \\ \frac{1}{2} \end{bmatrix}, \quad
|
||||
\tilde{\bm{b}}_3 = \tilde{\bm{b}}_4 = H_c \begin{bmatrix} \frac{1}{\sqrt{2}} \\ \frac{ \sqrt{3}}{\sqrt{2}} \\ \frac{1}{2} \end{bmatrix}, \quad
|
||||
\tilde{\bm{b}}_5 = \tilde{\bm{b}}_6 = H_c \begin{bmatrix} \frac{-2}{\sqrt{2}} \\ 0 \\ \frac{1}{2} \end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
In the case where top joints are positioned at the cube's vertices, a diagonal stiffness matrix is obtained as shown in equation \eqref{eq:detail_kinematics_cubic_stiffness}.
|
||||
Translation stiffness is twice the stiffness of the struts, and rotational stiffness is proportional to the square of the cube's size \(H_c\).
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_stiffness}
|
||||
\bm{K}_{\{B\} = \{C\}} = k \begin{bmatrix}
|
||||
2 & 0 & 0 & 0 & 0 & 0 \\
|
||||
0 & 2 & 0 & 0 & 0 & 0 \\
|
||||
0 & 0 & 2 & 0 & 0 & 0 \\
|
||||
0 & 0 & 0 & \frac{3}{2} H_c^2 & 0 & 0 \\
|
||||
0 & 0 & 0 & 0 & \frac{3}{2} H_c^2 & 0 \\
|
||||
0 & 0 & 0 & 0 & 0 & 6 H_c^2 \\
|
||||
\end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
However, typically, the top joints are not placed at the cube's vertices but at positions along the cube's edges (Figure \ref{fig:detail_kinematics_cubic_schematic}).
|
||||
In that case, the location of the top joints can be expressed by equation \eqref{eq:detail_kinematics_cubic_edges}, yet the computed stiffness matrix remains identical to Equation \eqref{eq:detail_kinematics_cubic_stiffness}.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_edges}
|
||||
\bm{b}_i = \tilde{\bm{b}}_i + \alpha \hat{\bm{s}}_i
|
||||
\end{equation}
|
||||
|
||||
|
||||
The stiffness matrix is therefore diagonal when the considered \(\{B\}\) frame is located at the center of the cube (shown by frame \(\{C\}\)).
|
||||
This means that static forces (resp torques) applied at the cube's center will induce pure translations (resp rotations around the cube's center).
|
||||
This specific location where the stiffness matrix is diagonal is referred to as the ``Center of Stiffness'' (analogous to the ``Center of Mass'' where the mass matrix is diagonal).
|
||||
\section{Effect of having frame \(\{B\}\) off-centered}
|
||||
|
||||
When the reference frames \(\{A\}\) and \(\{B\}\) are shifted from the cube's center, off-diagonal elements emerge in the stiffness matrix.
|
||||
|
||||
Considering a vertical shift as shown in Figure \ref{fig:detail_kinematics_cubic_schematic}, the stiffness matrix transforms into that shown in Equation \eqref{eq:detail_kinematics_cubic_stiffness_off_centered}.
|
||||
Off-diagonal elements increase proportionally with the height difference between the cube's center and the considered \(\{B\}\) frame.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cubic_stiffness_off_centered}
|
||||
\bm{K}_{\{B\} \neq \{C\}} = k \begin{bmatrix}
|
||||
2 & 0 & 0 & 0 & -2 H & 0 \\
|
||||
0 & 2 & 0 & 2 H & 0 & 0 \\
|
||||
0 & 0 & 2 & 0 & 0 & 0 \\
|
||||
0 & 2 H & 0 & \frac{3}{2} H_c^2 + 2 H^2 & 0 & 0 \\
|
||||
-2 H & 0 & 0 & 0 & \frac{3}{2} H_c^2 + 2 H^2 & 0 \\
|
||||
0 & 0 & 0 & 0 & 0 & 6 H_c^2 \\
|
||||
\end{bmatrix}
|
||||
\end{equation}
|
||||
|
||||
This stiffness matrix structure is characteristic of Stewart platforms exhibiting symmetry, and is not an exclusive property of cubic architectures.
|
||||
Therefore, the stiffness characteristics of the cubic architecture are only distinctive when considering a reference frame located at the cube's center.
|
||||
This poses a practical limitation, as in most applications, the relevant frame (where motion is of interest and forces are applied) is located above the top platform.
|
||||
|
||||
It should be noted that for the stiffness matrix to be diagonal, the cube's center doesn't need to coincide with the geometric center of the Stewart platform.
|
||||
This observation leads to the interesting alternative architectures presented in Section \ref{ssec:detail_kinematics_cubic_design}.
|
||||
\section{Uniform Mobility}
|
||||
|
||||
The translational mobility of the Stewart platform with constant orientation was analyzed.
|
||||
Considering limited actuator stroke (elongation of each strut), the maximum achievable positions in XYZ space were estimated.
|
||||
The resulting mobility in X, Y, and Z directions for the cubic architecture is illustrated in Figure \ref{fig:detail_kinematics_cubic_mobility_translations}.
|
||||
|
||||
The translational workspace analysis reveals that for the cubic architecture, the achievable positions form a cube whose axes align with the struts, with the cube's edge length corresponding to the strut axial stroke.
|
||||
These findings suggest that the mobility pattern is more subtle than sometimes described in the literature \cite{mcinroy00_desig_contr_flexur_joint_hexap}, exhibiting uniformity primarily along directions aligned with the cube's edges rather than uniform spherical distribution in all XYZ directions.
|
||||
This configuration still offers more consistent mobility characteristics compared to alternative architectures illustrated in Figure \ref{fig:detail_kinematics_mobility_trans}.
|
||||
|
||||
The rotational mobility, illustrated in Figure \ref{fig:detail_kinematics_cubic_mobility_rotations}, exhibits greater achievable angular stroke in the \(R_x\) and \(R_y\) directions compared to the \(R_z\) direction.
|
||||
Furthermore, an inverse relationship exists between the cube's dimension and rotational mobility, with larger cube sizes corresponding to more limited angular displacement capabilities.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,scale=1]{figs/detail_kinematics_cubic_mobility_translations.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_mobility_translations}Mobility in translation}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,scale=1]{figs/detail_kinematics_cubic_mobility_rotations.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_mobility_rotations}Mobility in rotation}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_mobility}Mobility of a Stewart platform with Cubic architecture. Both for translations (\subref{fig:detail_kinematics_cubic_mobility_translations}) and rotations (\subref{fig:detail_kinematics_cubic_mobility_rotations})}
|
||||
\end{figure}
|
||||
\chapter{Dynamical Decoupling}
|
||||
\label{ssec:detail_kinematics_cubic_dynamic}
|
||||
This section examines the dynamics of the cubic architecture in the Cartesian frame which corresponds to the transfer function from forces and torques \(\bm{\mathcal{F}}\) to translations and rotations \(\bm{\mathcal{X}}\) of the top platform.
|
||||
When relative motion sensors are integrated in each strut (measuring \(\bm{\mathcal{L}}\)), the pose \(\bm{\mathcal{X}}\) is computed using the Jacobian matrix as shown in Figure \ref{fig:detail_kinematics_centralized_control}.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\centering
|
||||
\includegraphics[scale=1]{figs/detail_kinematics_centralized_control.png}
|
||||
\caption{\label{fig:detail_kinematics_centralized_control}Typical control architecture in the cartesian frame}
|
||||
\end{figure}
|
||||
\section{Low frequency and High frequency coupling}
|
||||
|
||||
As derived during the conceptual design phase, the dynamics from \(\bm{\mathcal{F}}\) to \(\bm{\mathcal{X}}\) is described by Equation \eqref{eq:detail_kinematics_transfer_function_cart}.
|
||||
At low frequency, the behavior of the platform depends on the stiffness matrix \eqref{eq:detail_kinematics_transfer_function_cart_low_freq}.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_transfer_function_cart_low_freq}
|
||||
\frac{{\mathcal{X}}}{\bm{\mathcal{F}}}(j \omega) \xrightarrow[\omega \to 0]{} \bm{K}^{-1}
|
||||
\end{equation}
|
||||
|
||||
In Section \ref{ssec:detail_kinematics_cubic_static}, it was demonstrated that for the cubic configuration, the stiffness matrix is diagonal if frame \(\{B\}\) is positioned at the cube's center.
|
||||
In this case, the ``Cartesian'' plant is decoupled at low frequency.
|
||||
At high frequency, the behavior is governed by the mass matrix (evaluated at frame \(\{B\}\)) \eqref{eq:detail_kinematics_transfer_function_high_freq}.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_transfer_function_high_freq}
|
||||
\frac{{\mathcal{X}}}{\bm{\mathcal{F}}}(j \omega) \xrightarrow[\omega \to \infty]{} - \omega^2 \bm{M}^{-1}
|
||||
\end{equation}
|
||||
|
||||
To achieve a diagonal mass matrix, the center of mass of the mobile components must coincide with the \(\{B\}\) frame, and the principal axes of inertia must align with the axes of the \(\{B\}\) frame.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\centering
|
||||
\includegraphics[scale=1,width=0.6\linewidth]{figs/detail_kinematics_cubic_payload.png}
|
||||
\caption{\label{fig:detail_kinematics_cubic_payload}Cubic stewart platform with top cylindrical payload}
|
||||
\end{figure}
|
||||
|
||||
To verify these properties, a cubic Stewart platform with a cylindrical payload was analyzed (Figure \ref{fig:detail_kinematics_cubic_payload}).
|
||||
Transfer functions from \(\bm{\mathcal{F}}\) to \(\bm{\mathcal{X}}\) were computed for two specific locations of the \(\{B\}\) frames.
|
||||
When the \(\{B\}\) frame was positioned at the center of mass, coupling at low frequency was observed due to the non-diagonal stiffness matrix (Figure \ref{fig:detail_kinematics_cubic_cart_coupling_com}).
|
||||
Conversely, when positioned at the center of stiffness, coupling occurred at high frequency due to the non-diagonal mass matrix (Figure \ref{fig:detail_kinematics_cubic_cart_coupling_cok}).
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_cubic_cart_coupling_com.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_cart_coupling_com}$\{B\}$ at the center of mass}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_cubic_cart_coupling_cok.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_cart_coupling_cok}$\{B\}$ at the cube's center}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_cart_coupling}Transfer functions for a Cubic Stewart platform expressed in the Cartesian frame. Two locations of the \(\{B\}\) frame are considered: at the center of mass of the moving body (\subref{fig:detail_kinematics_cubic_cart_coupling_com}) and at the cube's center (\subref{fig:detail_kinematics_cubic_cart_coupling_cok}).}
|
||||
\end{figure}
|
||||
\section{Payload's CoM at the cube's center}
|
||||
|
||||
An effective strategy for improving dynamical performances involves aligning the cube's center (center of stiffness) with the center of mass of the moving components \cite{li01_simul_fault_vibrat_isolat_point}.
|
||||
This can be achieved by positioning the payload below the top platform, such that the center of mass of the moving body coincides with the cube's center (Figure \ref{fig:detail_kinematics_cubic_centered_payload}).
|
||||
This approach was physically implemented in several studies \cite{mcinroy99_dynam,jafari03_orthog_gough_stewar_platf_microm}, as shown in Figure \ref{fig:detail_kinematics_uw_gsp}.
|
||||
The resulting dynamics are indeed well-decoupled (Figure \ref{fig:detail_kinematics_cubic_cart_coupling_com_cok}), taking advantage from diagonal stiffness and mass matrices.
|
||||
The primary limitation of this approach is that, for many applications including the nano-hexapod, the payload must be positioned above the top platform.
|
||||
If a design similar to Figure \ref{fig:detail_kinematics_cubic_centered_payload} were employed for the nano-hexapod, the X-ray beam would intersect with the struts during spindle rotation.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.49\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_cubic_centered_payload.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_centered_payload}Payload at the cube's center}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.49\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_cubic_cart_coupling_com_cok.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_cart_coupling_com_cok}Fully decoupled cartesian plant}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_com_cok}Cubic Stewart platform with payload at the cube's center (\subref{fig:detail_kinematics_cubic_centered_payload}). Obtained cartesian plant is fully decoupled (\subref{fig:detail_kinematics_cubic_cart_coupling_com_cok})}
|
||||
\end{figure}
|
||||
\section{Conclusion}
|
||||
|
||||
The analysis of dynamical properties of the cubic architecture yields several important conclusions.
|
||||
Static decoupling, characterized by a diagonal stiffness matrix, is achieved when reference frames \(\{A\}\) and \(\{B\}\) are positioned at the cube's center.
|
||||
Note that this property can also be obtained with non-cubic architectures that exhibit symmetrical strut arrangements.
|
||||
Dynamic decoupling requires both static decoupling and coincidence of the mobile platform's center of mass with reference frame \(\{B\}\).
|
||||
While this configuration offers powerful control advantages, it requires positioning the payload at the cube's center, which is highly restrictive and often impractical.
|
||||
\chapter{Decentralized Control}
|
||||
\label{ssec:detail_kinematics_decentralized_control}
|
||||
The orthogonal arrangement of struts in the cubic architecture suggests a potential minimization of inter-strut coupling, which could theoretically create favorable conditions for decentralized control.
|
||||
Two sensor types integrated in the struts are considered: displacement sensors and force sensors.
|
||||
The control architecture is illustrated in Figure \ref{fig:detail_kinematics_decentralized_control}, where \(\bm{K}_{\mathcal{L}}\) represents a diagonal transfer function matrix.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\centering
|
||||
\includegraphics[scale=1]{figs/detail_kinematics_decentralized_control.png}
|
||||
\caption{\label{fig:detail_kinematics_decentralized_control}Decentralized control in the frame of the struts.}
|
||||
\end{figure}
|
||||
|
||||
The obtained plant dynamics in the frame of the struts are compared for two Stewart platforms.
|
||||
The first employs a cubic architecture shown in Figure \ref{fig:detail_kinematics_cubic_payload}.
|
||||
The second uses a non-cubic Stewart platform shown in Figure \ref{fig:detail_kinematics_non_cubic_payload}, featuring identical payload and strut dynamics but with struts oriented more vertically to differentiate it from the cubic architecture.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\centering
|
||||
\includegraphics[scale=1,width=0.6\linewidth]{figs/detail_kinematics_non_cubic_payload.png}
|
||||
\caption{\label{fig:detail_kinematics_non_cubic_payload}Stewart platform with non-cubic architecture}
|
||||
\end{figure}
|
||||
\section{Relative Displacement Sensors}
|
||||
|
||||
The transfer functions from actuator force in each strut to the relative motion of the struts are presented in Figure \ref{fig:detail_kinematics_decentralized_dL}.
|
||||
As anticipated from the equations of motion from \(\bm{f}\) to \(\bm{\mathcal{L}}\) \eqref{eq:detail_kinematics_transfer_function_struts}, the \(6 \times 6\) plant is decoupled at low frequency.
|
||||
At high frequency, coupling is observed as the mass matrix projected in the strut frame is not diagonal.
|
||||
|
||||
No significant advantage is evident for the cubic architecture (Figure \ref{fig:detail_kinematics_cubic_decentralized_dL}) compared to the non-cubic architecture (Figure \ref{fig:detail_kinematics_non_cubic_decentralized_dL}).
|
||||
The resonance frequencies differ between the two cases because the more vertical strut orientation in the non-cubic architecture alters the stiffness properties of the Stewart platform, consequently shifting the frequencies of various modes.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_non_cubic_decentralized_dL.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_non_cubic_decentralized_dL}Non cubic architecture}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_cubic_decentralized_dL.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_decentralized_dL}Cubic architecture}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_decentralized_dL}Bode plot of the transfer functions from actuator force to relative displacement sensor in each strut. Both for a non-cubic architecture (\subref{fig:detail_kinematics_non_cubic_decentralized_dL}) and for a cubic architecture (\subref{fig:detail_kinematics_cubic_decentralized_dL})}
|
||||
\end{figure}
|
||||
\section{Force Sensors}
|
||||
|
||||
Similarly, the transfer functions from actuator force to force sensors in each strut were analyzed for both cubic and non-cubic Stewart platforms.
|
||||
The results are presented in Figure \ref{fig:detail_kinematics_decentralized_fn}.
|
||||
The system demonstrates good decoupling at high frequency in both cases, with no clear advantage for the cubic architecture.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_non_cubic_decentralized_fn.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_non_cubic_decentralized_fn}Non cubic architecture}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.48\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.95\linewidth]{figs/detail_kinematics_cubic_decentralized_fn.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_decentralized_fn}Cubic architecture}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_decentralized_fn}Bode plot of the transfer functions from actuator force to force sensor in each strut. Both for a non-cubic architecture (\subref{fig:detail_kinematics_non_cubic_decentralized_fn}) and for a cubic architecture (\subref{fig:detail_kinematics_cubic_decentralized_fn})}
|
||||
\end{figure}
|
||||
\section{Conclusion}
|
||||
|
||||
The presented results do not demonstrate the pronounced decoupling advantages often associated with cubic architectures in the literature.
|
||||
Both the cubic and non-cubic configurations exhibited similar coupling characteristics, suggesting that the benefits of orthogonal strut arrangement for decentralized control is less obvious than often reported in the literature.
|
||||
\chapter{Cubic architecture with Cube's center above the top platform}
|
||||
\label{ssec:detail_kinematics_cubic_design}
|
||||
As demonstrated in Section \ref{ssec:detail_kinematics_cubic_dynamic}, the cubic architecture can exhibit advantageous dynamical properties when the center of mass of the moving body coincides with the cube's center, resulting in diagonal mass and stiffness matrices.
|
||||
As shown in Section \ref{ssec:detail_kinematics_cubic_static}, the stiffness matrix is diagonal when the considered \(\{B\}\) frame is located at the cube's center.
|
||||
However, the \(\{B\}\) frame is typically positioned above the top platform where forces are applied and displacements are measured.
|
||||
|
||||
This section proposes modifications to the cubic architecture to enable positioning the payload above the top platform while still leveraging the advantageous dynamical properties of the cubic configuration.
|
||||
|
||||
Three key parameters define the geometry of the cubic Stewart platform: \(H\), the height of the Stewart platform (distance from fixed base to mobile platform); \(H_c\), the height of the cube, as shown in Figure \ref{fig:detail_kinematics_cubic_schematic_full}; and \(H_{CoM}\), the height of the center of mass relative to the mobile platform (coincident with the cube's center).
|
||||
|
||||
Depending on the cube's size \(H_c\) in relation to \(H\) and \(H_{CoM}\), different designs emerge.
|
||||
In the following examples, \(H = 100\,mm\) and \(H_{CoM} = 20\,mm\).
|
||||
\section{Small cube}
|
||||
|
||||
When the cube size \(H_c\) is smaller than twice the height of the CoM \(H_{CoM}\) \eqref{eq:detail_kinematics_cube_small}, the resulting design is shown in Figure \ref{fig:detail_kinematics_cubic_above_small}.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cube_small}
|
||||
H_c < 2 H_{CoM}
|
||||
\end{equation}
|
||||
|
||||
This configuration is similar to that described in \cite{furutani04_nanom_cuttin_machin_using_stewar}, although they do not explicitly identify it as a cubic configuration.
|
||||
Adjacent struts are parallel to each other, differing from the typical architecture where parallel struts are positioned opposite to each other.
|
||||
|
||||
This approach yields a compact architecture, but the small cube size may result in insufficient rotational stiffness.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.36\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_small_iso.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_small_iso}Isometric view}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.30\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_small_side.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_small_side}Side view}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.30\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_small_top.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_small_top}Top view}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_above_small}Cubic architecture with cube's center above the top platform. A cube height of 40mm is used.}
|
||||
\end{figure}
|
||||
\section{Medium sized cube}
|
||||
|
||||
Increasing the cube's size such that \eqref{eq:detail_kinematics_cube_medium} is verified produces an architecture with intersecting struts (Figure \ref{fig:detail_kinematics_cubic_above_medium}).
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cube_medium}
|
||||
2 H_{CoM} < H_c < 2 (H_{CoM} + H)
|
||||
\end{equation}
|
||||
|
||||
This configuration resembles the design proposed in \cite{yang19_dynam_model_decoup_contr_flexib} (Figure \ref{fig:detail_kinematics_yang19}), although their design is not strictly cubic.
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.36\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_medium_iso.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_medium_iso}Isometric view}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.30\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_medium_side.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_medium_side}Side view}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.30\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_medium_top.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_medium_top}Top view}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_above_medium}Cubic architecture with cube's center above the top platform. A cube height of 140mm is used.}
|
||||
\end{figure}
|
||||
\section{Large cube}
|
||||
|
||||
When the cube's height exceeds twice the sum of the platform height and CoM height \eqref{eq:detail_kinematics_cube_large}, the architecture shown in Figure \ref{fig:detail_kinematics_cubic_above_large} is obtained.
|
||||
|
||||
\begin{equation}\label{eq:detail_kinematics_cube_large}
|
||||
2 (H_{CoM} + H) < H_c
|
||||
\end{equation}
|
||||
|
||||
\begin{figure}[htbp]
|
||||
\begin{subfigure}{0.36\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_large_iso.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_large_iso}Isometric view}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.30\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_large_side.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_large_side}Side view}
|
||||
\end{subfigure}
|
||||
\begin{subfigure}{0.30\textwidth}
|
||||
\begin{center}
|
||||
\includegraphics[scale=1,width=0.9\linewidth]{figs/detail_kinematics_cubic_above_large_top.png}
|
||||
\end{center}
|
||||
\subcaption{\label{fig:detail_kinematics_cubic_above_large_top}Top view}
|
||||
\end{subfigure}
|
||||
\caption{\label{fig:detail_kinematics_cubic_above_large}Cubic architecture with cube's center above the top platform. A cube height of 240mm is used.}
|
||||
\end{figure}
|
||||
\section{Platform size}
|
||||
|
||||
For the proposed configuration, the top joints \(\bm{b}_i\) (resp. the bottom joints \(\bm{a}_i\)) and are positioned on a circle with radius \(R_{b_i}\) (resp. \(R_{a_i}\)) described by Equation \eqref{eq:detail_kinematics_cube_joints}.
|
||||
|
||||
\begin{subequations}\label{eq:detail_kinematics_cube_joints}
|
||||
\begin{align}
|
||||
R_{b_i} &= \sqrt{\frac{3}{2} H_c^2 + 2 H_{CoM}^2} \label{eq:detail_kinematics_cube_top_joints} \\
|
||||
R_{a_i} &= \sqrt{\frac{3}{2} H_c^2 + 2 (H_{CoM} + H)^2} \label{eq:detail_kinematics_cube_bot_joints}
|
||||
\end{align}
|
||||
\end{subequations}
|
||||
|
||||
Since the rotational stiffness for the cubic architecture scales with the square of the cube's height \eqref{eq:detail_kinematics_cubic_stiffness}, the cube's size can be determined based on rotational stiffness requirements.
|
||||
Subsequently, using Equation \eqref{eq:detail_kinematics_cube_joints}, the dimensions of the top and bottom platforms can be calculated.
|
||||
\chapter*{Conclusion}
|
||||
The analysis of the cubic architecture for Stewart platforms yielded several important findings.
|
||||
While the cubic configuration provides uniform stiffness in the XYZ directions, it stiffness property becomes particularly advantageous when forces and torques are applied at the cube's center.
|
||||
Under these conditions, the stiffness matrix becomes diagonal, resulting in a decoupled Cartesian plant at low frequencies.
|
||||
|
||||
Regarding mobility, the translational capabilities of the cubic configuration exhibit uniformity along the directions of the orthogonal struts, rather than complete uniformity in the Cartesian space.
|
||||
This understanding refines the characterization of cubic architecture mobility commonly presented in literature.
|
||||
|
||||
The analysis of decentralized control in the frame of the struts revealed more nuanced results than expected.
|
||||
While cubic architectures are frequently associated with reduced coupling between actuators and sensors, this study showed that these benefits may be more subtle or context-dependent than commonly described.
|
||||
Under the conditions analyzed, the coupling characteristics of cubic and non-cubic configurations, in the frame of the struts, appeared similar.
|
||||
|
||||
Fully decoupled dynamics in the Cartesian frame can be achieved when the center of mass of the moving body coincides with the cube's center.
|
||||
However, this arrangement presents practical challenges, as the cube's center is traditionally located between the top and bottom platforms, making payload placement problematic for many applications.
|
||||
|
||||
To address this limitation, modified cubic architectures have been proposed with the cube's center positioned above the top platform.
|
||||
Three distinct configurations have been identified, each with different geometric arrangements but sharing the common characteristic that the cube's center is positioned above the top platform.
|
||||
This structural modification enables the alignment of the moving body's center of mass with the center of stiffness, resulting in beneficial decoupling properties in the Cartesian frame.
|
||||
\printbibliography[heading=bibintoc,title={Bibliography}]
|
||||
\end{document}
|
||||
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paper/figs/detail_kinematics_centralized_control.pdf
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paper/figs/detail_kinematics_non_cubic_decentralized_dL.pdf
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paper/figs/detail_kinematics_non_cubic_decentralized_dL.png
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paper/figs/detail_kinematics_non_cubic_decentralized_fn.pdf
Normal file
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35
paper/preamble.tex
Normal file
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\makeindex
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\makeglossaries
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134
paper/preamble_extra.tex
Normal file
@@ -0,0 +1,134 @@
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\usepackage{enumitem}
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|
||||
|
||||
\renewenvironment{verse}{\begin{my-verse}}{\end{my-verse}}
|
||||
|
||||
\usepackage{environ}% http://ctan.org/pkg/environ
|
||||
\NewEnviron{aside}{%
|
||||
\marginpar{\BODY}
|
||||
}
|
||||
|
||||
\renewenvironment{verbatim}{\VerbatimEnvironment\begin{minted}[]{text}}{\end{minted}}
|
||||
|
||||
\usepackage{soul}
|
||||
\sethlcolor{my-pale-grey}
|
||||
|
||||
\let\OldTexttt\texttt
|
||||
\renewcommand{\texttt}[1]{{\ttfamily\hl{\mbox{\,#1\,}}}}
|
||||
|
||||
\makeatletter
|
||||
\preto\Gin@extensions{png,}
|
||||
\DeclareGraphicsRule{.png}{pdf}{.pdf}{\noexpand\Gin@base.pdf}
|
||||
\preto\Gin@extensions{gif,}
|
||||
\DeclareGraphicsRule{.gif}{png}{.png}{\noexpand\Gin@base.png}
|
||||
\makeatother
|
||||
|
||||
\usepackage{hyperref}
|
||||
\hypersetup{
|
||||
colorlinks = true,
|
||||
allcolors = my-blue
|
||||
}
|
||||
|
||||
\usepackage{hypcap}
|
||||