slides of the talk
TRANSCRIPT
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Solving Polynomial Systems
using Numerical Homotopies
Jan Verschelde
Department of Math, Stat & CSUniversity of Illinois at ChicagoChicago, IL 60607-7045, USA
email: [email protected]
URL: http://www.math.uic.edu/~jan
University of Minnesota at Duluth9 November 2006
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Outline
• Polynomial systems arise in science and engineering
— for this talk: mainly mechanism design.
• Numerical homotopy continuation algorithms
are pleasingly parallel.
• Newton with deflation to recondition isolated singularities.
page 0
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Chebyshev’s straight line mechanism (1875)
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 1 of C
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 2 of C
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 2 of C
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 2 of C
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 2 of C
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 2 of C
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
page 2 of C
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Cognates of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
One Cognate of Chebyshev’s mechanism
Kenneth J. Waldron and Gary L. Kinzel: Kinematics, Dynamics, and Design of Machinery.Second Edition, John Wiley & Sons, 2003.
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a 4-bar linkage
Five-Point Path Synthesis
Design a 4-bar linkage = design trajectory of coupler point.
Input: coordinates of points on coupler curve.
Output: lengths of the bars of the linkage.
C.W. Wampler: Isotropic coordinates, circularity and Bezout
numbers: planar kinematics from a new perspective.
Proceedings of the 1996 ASME Design Engineering Technical Conference.
Irvine, CA, Aug 18–22, 1996.
A.J. Sommese and C.W. Wampler: The Numerical Solution of Systems
of Polynomials Arising in Engineering and Science.
World Scientific, 2005.
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a 4-bar linkage
Isotropic Coordinates
• A point (a, b) ∈ R2 is mapped to z = a + ib, i =
√−1.
• (z, z) = (a + ib, a − ib) ∈ C2 are isotropic coordinates.
• Observe z · z = a2 + b2.
• Rotation around (0, 0) through angle θ is multiplication by eiθ.Multiply by e−iθ to invert the rotation.
• Abbreviate a rotation by Θ = eiθ,then its inverse Θ−1 = Θ, satisfying ΘΘ = 1.
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a 4-bar linkage
The Loop Equations
Let A = (a, a) and B = (b, b) be the fixed base points.
Unknown are (x, x) and (y, y), coordinates of the other two pointsin the 4-bar linkage.
For given precision points (pj , pj), assuming θ0 = 1, (pj + xθj + a)(pj + xθj + a) = (p0 + x + a)(p0 + x + a)
(pj + yθj + b)(pj + yθj + b) = (p0 + y + b)(p0 + y + b)
Since the angle θj corresponding to each (pj , pj) is unknown,five precision points are needed to determine the linkage uniquely.
Adding θj θj = 1 to the system leads to 12 equations in 12 unkowns:(x, x), (y, y), and (θj , θj), for j = 1, 2, 3, 4.
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a 4-bar linkage
12
theta[1]*Theta[1]-1;
theta[2]*Theta[2]-1;
theta[3]*Theta[3]-1;
theta[4]*Theta[4]-1;
-.4091256991*x*theta[1]-1.061607555*I*x*theta[1]+1.157260179-.3374636810*X+.1524877812*I*X
-.3374636810*x-.1524877812*I*x-.4091256991*X*Theta[1]+1.061607555*I*X*Theta[1];
.4011300738*x*theta[2]-1.146477955*I*x*theta[2]+1.338182778-.3374636810*X+.1524877812*I*X
-.3374636810*x-.1524877812*I*x+.4011300738*X*Theta[2]+1.146477955*I*X*Theta[2];
.3705985316*x*theta[3]-1.454067014*I*x*theta[3]+2.114519894-.3374636810*X+.1524877812*I*X
-.3374636810*x-.1524877812*I*x+.3705985316*X*Theta[3]+1.454067014*I*X*Theta[3];
.3188425748*x*theta[4]-.850446965*I*x*theta[4]+.6877863684-.3374636810*X+.1524877812*I*X
-.3374636810*x-.1524877812*I*x+.3188425748*X*Theta[4]+.850446965*I*X*Theta[4];
-1.742137552*y*theta[1]-.3932004150*I*y*theta[1]+1.524665181+.9955481716*Y+.8208949212*I*Y
+.9955481716*y-.8208949212*I*y-1.742137552*Y*Theta[1]+.3932004150*I*Y*Theta[1];
-.9318817788*y*theta[2]-.4780708150*I*y*theta[2]-.5680292799+.9955481716*Y+.8208949212*I*Y
+.9955481716*y-.8208949212*I*y-.9318817788*Y*Theta[2]+.4780708150*I*Y*Theta[2];
-.9624133210*y*theta[3]-.7856598740*I*y*theta[3]-.1214837957+.9955481716*Y+.8208949212*I*Y
+.9955481716*y-.8208949212*I*y-.9624133210*Y*Theta[3]+.7856598740*I*Y*Theta[3];
-1.014169278*y*theta[4]-.1820398250*I*y*theta[4]-.6033068118+.9955481716*Y+.8208949212*I*Y
+.9955481716*y-.8208949212*I*y-1.014169278*Y*Theta[4]+.1820398250*I*Y*Theta[4];
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homotopy continuation
Numerical Homotopy Continuation Methods
If we wish to solve f(x) = 0, then we construct a system g(x) = 0whose solutions are known. Consider the homotopy
H(x, t) := (1 − t)g(x) + tf(x) = 0.
By continuation, we trace the paths starting at the knownsolutions of g(x) = 0 to the desired solutions of f(x) = 0,for t from 0 to 1.
homotopy continuation methods are symbolic-numeric:homotopy methods treat polynomials as algebraic objects,continuation methods use polynomials as functions.
geometric interpretation: move from general to special,solve special, and move solutions from special to general.
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homotopy continuation
Product Deformations
y
1
0.0
1.0
x
1.5
−0.5
−1.0
−1 20−2
−1.5
0.5
y
1
0.0
1.0
x
1.5
−0.5
−1.0
−1 20−2
−1.5
0.5
γ
x2 − 1 = 0
y2 − 1 = 0︸ ︷︷ ︸start system
(1−t) +
x2 + 4y2 − 4 = 0
2y2 − x = 0︸ ︷︷ ︸target system
t, γ ∈ C
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homotopy continuation
The theorem of Bezout
f = (f1, f2, . . . , fn)
di = deg(fi)
total degree D :
D =n∏
i=1
di
g(x) =
α1xd11 − β1 = 0
α2xd22 − β2 = 0
...
αnxdnn − βn = 0
start
system
αi, βi ∈ C
random
Theorem: f(x) = 0 has at most D isolated solutions in Cn,
counted with multiplicities.
Sketch of Proof: V = { (f,x) ∈ P(HD) × P(Cn) | f(x) = 0 }Σ′ = {(f,x) ∈ V | det(Dxf(x)) = 0}, Σ = π1(Σ′), π1 : V → P(HD)Elimination theory: Σ is variety ⇒ P(HD) − Σ is connected.Thus h(x, t) = (1 − t)g(x) + tf(x) = 0 avoids Σ, ∀t ∈ [0, 1).
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homotopy continuation
Implicitly defined curves
Consider a homotopy hk(x(t), y(t), t) = 0, k = 1, 2.
By ∂∂t on homotopy: ∂hk
∂x∂x∂t
+ ∂hk
∂y∂y∂t
+ ∂hk
∂t∂t∂t
= 0, k = 1, 2.
Set ∆x := ∂x∂t , ∆y := ∂y
∂t , and ∂t∂t = 1.
Increment t := t + ∆t
Solve
[∂h1
∂x∂h1
∂y
∂h2
∂x∂h2
∂y
] [∆x
∆y
]= −
[∂h1
∂t
∂h2
∂t
](Newton)
Update
{x := x + ∆x
y := y + ∆y
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homotopy continuation
Predictor-Corrector Methods
loop
1. predict
8<:
tk+1 := tk + ∆t
x(k+1) := x(k) + ∆x
2. correct with Newton
3. if convergence
then enlarge ∆t
continue with k + 1
else reduce ∆t
back up and restart at k
until t = 1.
[t*,x*]
secant predictor
t
[t1,x1]
0.3
0.1
0.4
0.2
−0.1
0.0
−0.2
0.250.0 1.00.750.5
[t0, x0]
[t*,x*]
Euler predictor
[t1,x1]
0.4
0.3
0.2
0.1
0.0
−0.1
−0.2
t
1.00.750.50.250.0
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homotopy continuation
Robustness of Continuation Methods
sure to find all roots at the end of the paths?
• dealing with curve jumping:
1. fix #Newton steps to force quadratic convergence;
2. rerun clustered paths with same discretization of t.
• Robust step control by interval methods, see
R.B. Kearfott and Z. Xing: An interval step control for continuation
methods. SIAM J. Numer. Anal. 31(3): 892–914, 1994.
• Root of multiplicity µ will appear at the end of the pathsas a cluster of µ roots.
Use “endgames”, eventually in multi-precision arithmetic.
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homotopy continuation
Complexity Issues
The Problem: a hierarchy of complexity classes
P : evaluation of a system at a point
NP : find one root of a system
#P : find all roots of a system (intractable!)
Complexity of Homotopies: for bounds on #Newton steps in alinear homotopy, see
L. Blum, F. Cucker, M. Shub, and S. Smale: Complexity and Real
Computation. Springer 1998.
M. Shub and S. Smale: Complexity of Bezout’s theorem V: Polynomial
Time. Theoretical Computer Science 133(1):141–164, 1994.
On average, we can find an approximate zero in polynomial time.
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homotopy continuation
Solving the Loop Equations
Recall: 12 equations in 12 unknowns.
All equations are quadratic, so the total degree is 212 = 4, 096.
+ Tracking 4,096 takes 25 minutes on a modern computer.
− Of the 4,096 paths, only 36 will converge.
→ 4,060 wasted paths!
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deflation algorithm
Singularities are keeping us in business
numerical analysis: bifurcation points and endgames
Rall (1966); Reddien (1978); Decker-Keller-Kelley (1983);Griewank-Osborne (1981); Hoy (1989);Deuflard-Friedler-Kunkel (1987); Kunkel (1989, 1996);Morgan-Sommese-Wampler (1991); Li-Wang (1993, 1994);Allgower-Schwetlick (1995); Ponisch-Schnabel-Schwetlick (1999);Allgower-Bohmer-Hoy-Janovsky (1999); Govaerts (2000)
computer algebra: standard bases (SINGULAR)
Mora (1982); Greuel-Pfister (1996); Marinari-Moller-Mora (1993)
numerical polynomial algebra: multiplicity structure
Moller-Stetter (1995); Mourrain (1997);Stetter-Thallinger (1998); Dayton-Zeng (2005)
deflation: Ojika-Watanabe-Mitsui (1983); Lecerf (2003)
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deflation algorithm
Twelve lines tangent to four spheres
Frank Sottile and Thorsten Theobald: Lines tangents to 2n − 2 spheres in Rn
Trans. Amer. Math. Soc. 354pages 4815-4829, 2002.
Problem:Given 4 spheres,find all lines tangentto all 4 given spheres.
Observe:12 solutions in groups of 4.
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deflation algorithm
Twelve lines tangent to four spheres
Frank Sottile and Thorsten Theobald: Lines tangents to 2n − 2 spheres in Rn
Trans. Amer. Math. Soc. 354pages 4815-4829, 2002.
Problem:Given 4 spheres,find all lines tangentto all 4 given spheres.
Observe:3 lines of multiplicity 4.
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deflation algorithm
An Input Polynomial System
x0**2 + x1**2 + x2**2 - 1;
x0*x3 + x1*x4 + x2*x5;
x3**2 + x4**2 + x5**2 - 0.25;
x3**2 + x4**2 - 2*x2*x4 + x2**2 + x5**2 + 2*x1*x5 + x1**2 - 0.25;
x3**2 + 1.73205080756888*x2*x3 + 0.75*x2**2 + x4**2 - x2*x4 + 0.25*x2**2
+ x5**2 - 1.73205080756888*x0*x5 + x1*x5
+ 0.75*x0**2 - 0.86602540378444*x0*x1 + 0.25*x1**2 - 0.25;
x3**2 - 1.63299316185545*x1*x3 + 0.57735026918963*x2*x3
+ 0.66666666666667*x1**2 - 0.47140452079103*x1*x2 + 0.08333333333333*x2**2
+ x4**2 + 1.63299316185545*x0*x4 - x2*x4 + 0.66666666666667*x0**2
- 0.81649658092773*x0*x2 + 0.25*x2**2
+ x5**2 - 0.57735026918963*x0*x5 + x1*x5 + 0.08333333333333*x0**2
- 0.28867513459481*x0*x1 + 0.25*x1**2 - 0.25;
Original formulation as polynomial system: Cassiano Durand.
Centers of the spheres at the vertices of a tetrahedron: Thorsten Theobald.
Algebraic numbers sqrt(3), sqrt(6), etc. approximated by double floats.
The system has 6 isolated solutions, each of multiplicity 4.
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deflation algorithm
Solutions at the End of Continuation
Two solutions in a cluster: (real and imaginary parts)
solution 1 :
x0 : -7.07106803165780E-01 3.77452918725401E-08
x1 : -4.08248430737360E-01 -1.83624917064964E-07
x2 : 5.77350143082334E-01 -8.36140714113780E-08
x3 : -2.50000000000000E-01 -1.57896818458518E-16
x4 : 4.33012701892221E-01 -9.11600174682333E-17
x5 : 9.56878363411174E-08 1.54062878745083E-07
solution 2 :
x0 : -7.07106794356709E-01 -1.29682370414209E-07
x1 : -4.08248217029256E-01 1.11010906008961E-07
x2 : 5.77350304985648E-01 -8.03312536501087E-08
x3 : -2.50000000000001E-01 -1.74789416181029E-16
x4 : 4.33012701892220E-01 -1.00914936462574E-16
x5 : -6.07788020445124E-08 -1.39412292964849E-07
this is the input to our deflation algorithm
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deflation algorithm
Newton’s Method for Overdetermined Systems
Singular Value Decomposition of N -by-n Jacobian matrix Jf :
Jf = UΣV T , U and V are orthogonal: UT U = IN , V T V = In,
and singular values σ1 ≥ σ2 ≥ · · · ≥ σn as the only nonzeroelements on the diagonal of the N -by-n matrix Σ (N > n).
The condition number cond(Jf (z)) = σ1σn
.
Rank(Jf (z)) = R ⇐⇒ Σ = diag(σ1, σ2, . . . , σR, 0, . . . , 0).
At a multiple root z0: Rank(Jf (z0)) = R < n.
Close to z0, z ≈ z0 : σR+1 ≈ 0, or |σR+1| < ε, ε is tolerance.
Moore-Penrose inverse: J+f = V Σ+UT , with R = Rank(Jf ),
and Σ+ = diag( 1σ1
, 1σ2
, . . . , 1σR
, 0, . . . , 0).
Then ∆z = −Jf (z)+f(z) is the least squares solution.
Dedieu-Shub (1999); Li-Zeng (2005)
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deflation algorithm
Deflation Operator Dfl reduces to Corank One
Consider f(x) = 0, N equations in n unknowns, N ≥ n.
Suppose Rank(A(z0)) = R < n for z0 an isolated zero of f(x) = 0.
Choose h ∈ CR+1 and B ∈ C
n×(R+1) at random.
Introduce R + 1 new multiplier variables λ = (λ1, λ2, . . . , λR+1).
Dfl(f)(x, λ) :=
f(x) = 0
A(x)Bλ = 0
hλ = 1
Rank(A(x)) = R
⇓corank(A(x)B) = 1
Compared to the deflation of Ojika, Watanabe, and Mitsui:(1) we do not compute a maximal minor of the Jacobian matrix;(2) we only add new equations, we never replace equations.
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deflation algorithm
Newton’s Method with Deflation��
��
Input: f(x) = 0 polynomial system;
x0 initial approximation for x∗;
ε tolerance for numerical rank.
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deflation algorithm
Newton’s Method with Deflation��
��
Input: f(x) = 0 polynomial system;
x0 initial approximation for x∗;
ε tolerance for numerical rank.
�[A+, R] := SVD(A(xk), ε);
xk+1 := xk − A+f(xk);Gauss-Newton
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deflation algorithm
Newton’s Method with Deflation��
��
Input: f(x) = 0 polynomial system;
x0 initial approximation for x∗;
ε tolerance for numerical rank.
�[A+, R] := SVD(A(xk), ε);
xk+1 := xk − A+f(xk);Gauss-Newton
��������
�������
�������
�������R = #columns(A)?Yes�����Output: f ;xk+1.
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deflation algorithm
Newton’s Method with Deflation��
��
Input: f(x) = 0 polynomial system;
x0 initial approximation for x∗;
ε tolerance for numerical rank.
�[A+, R] := SVD(A(xk), ε);
xk+1 := xk − A+f(xk);Gauss-Newton
��������
�������
�������
�������R = #columns(A)?Yes�����Output: f ;xk+1.
�No
f := Dfl(f)(x, λ) =
8<:
f(x) = 0
G(x, λ) = 0; Deflation Step
bλ := LeastSquares(G(xk+1, λ));
k := k + 1; xk := (xk, bλ);
�
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deflation algorithm
12 Lines Tangent to 4 Spheres revisited
Continuation methods find 24 solutions, clustered in groups of 4.
The rank at all solutions is 4, corank is 2.
One deflation suffices to restore quadratic convergence.
An average condition number drops from 3.4E+8 to 1.1E+2.
We can compute the solutions
with accuracy close to machine precision,
on a system with approximate coefficients,
given with double float precision.
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deflation algorithm
A Bound on the Number of Deflations
Theorem (Anton Leykin, JV, Ailing Zhao):The number of deflations needed to restore the
quadratic convergence of Newton’s method converging
to an isolated solution is strictly less than the
multiplicity.
Duality Analysis of Barry H. Dayton and Zhonggang Zeng:
(1) tighter bound on number of deflations; and
(2) special case algorithms, for corank = 1.
(Proceedings of ISSAC 2005)
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deflation algorithm
A Hierarchy of Structures
Coefficient-Parameter
Polyhedral Methodspolynomial
products
Linear Products
Multihomogeneous
Total Degree
S
S
S
S
S
Seasierstart
system
�
more efficient(fewer paths)
�A
Below line A: solving start systems is done automatically.
Above line A: special ad-hoc methods must be designed.
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parallel robots
Assembly of Stewart-Gough Platforms
end plate, the platform
is connected by legs to
a stationary base
Forward Displacement Problem:Given: position of base and leg lengths.Wanted: position of end plate.
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parallel robots
The Equations for the Platform Problem
workspace R3 × SO(3): position and orientation
SO(3) = { A ∈ C3×3 | AHA = I, det(A) = 1 }
more efficient to use Study (or soma) coordinates:[e : g] = [e0 : e1 : e2 : e3 : g0 : g1 : g2 : g3] ∈ P
7 quaternions onthe Study quadric: f0(e, g) = e0g0 + e1g2 + e2g2 + e3g3 = 0,excluding those e for which ee′ = 0, e′ = (e0,−e1,−e2,−e3)
given leg lengths Li, find [e : g] leads to
fi(e, g) = gg′+(bb′i+aia′i−L2
i )ee′+(gb′ie
′+ebig′)−(ge′a′
i+aieg′)
− (ebie′a′
i + aieb′ie
′) = 0, i = 1, 2, . . . 6
⇒ solve f = (f0, f1, . . . , f6), 7 quadrics in [e : g] ∈ P7
expecting 27 = 128 solutions...
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parallel robots
Literature on Stewart-Gough platforms
M. Raghavan: The Stewart platform of general geometry has 40
configurations. ASME J. Mech. Design 115:277–282, 1993.
B. Mourrain: The 40 generic positions of a parallel robot. In
Proceedings of the International Symposium on Symbolic and Algebraic
Computation, ed. by M. Bronstein, pages 173–182, ACM 1993.
F. Ronga and T. Vust: Stewart platforms without computer? In Real
Analytic and Algebraic Geometry, Proceedings of the International
Conference, (Trento, 1992), pages 196–212, Walter de Gruyter 1995.
M.L. Husty: An algorithm for solving the direct kinematics of general
Stewart-Gough Platforms. Mech. Mach. Theory, 31(4):365–380, 1996.
C.W. Wampler: Forward displacement analysis of general
six-in-parallel SPS (Stewart) platform manipulators using soma
coordinates. Mech. Mach. Theory 31(3): 331–337, 1996.
P. Dietmaier: The Stewart-Gough platform of general geometry can
have 40 real postures. In Advances in Robot Kinematics: Analysis and
Control, ed. by J. Lenarcic and M.L. Husty, pages 7–16. Kluwer 1998.
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parallel robots
Coefficient-Parameter Homotopies
Solve system f(x,q) = 0 with natural parameters q ∈ Cm.
1. solve system once for a generic choice q0 of the parameters;
2. to move from generic to specific instance q1, use homotopy
f(x,q(t)) = f(x, (1 − t)q0 + tq1) = 0, for t from 0 to 1.
At t = 0, for q = q0, we have the maximal number of isolated
regular solutions. Singularities can occur only at t = 1.
A.P. Morgan and A.J. Sommese: Coefficient-parameter polynomial
continuation. Appl. Math. Comput., 29(2):123–160, 1989.
A.J. Sommese and C.W. Wampler: The Numerical Solution of Systems
of Polynomials Arising in Engineering and Science.
World Scientific, 2005.
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parallel robots
A family of Stewart-Gough platforms
6-6, 40 solutions 4-6, 32 solutions
4-4a, 16 solutions
4-4b, 24 solutions
3-3, 16 solutions
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multihomogenization
Multihomogeneous version of Bezout’s theorem
Consider the eigenvalue problem Ax = λx, A ∈ Cn×n.
Add one general hyperplanen∑
i=1
cixi + c0 = 0 for unique x.
Bezout’s theorem: D = 2n ↔ at most n solutions
Embed in multi-projective space: P × Pn, separating λ from x.
{λ} {x1, x2}1 1
1 1
0 1
degree table
⇐⇒
{λ} {x1, x2}λ + γ1 α0 + α1x1 + α2x2
λ + γ2 β0 + β1x1 + β2x2
1 c0 + c1x1 + c2x2
linear-product start system
The root count B = 1 · 1 · 1 + 1 · 1 · 1 + 0 · 1 · 1 is a permanent.
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multihomogenization
How to find the best partition?
A multi-homogeneous Bezout number depends on the choice of apartition of the set of unknowns. So, how to choose?
• Knowledge of the application, e.g.: eigenvalue problem.
• Enumerate all partitions and retain the partition with thesmallest Bezout number.
#unknowns 1 2 3 4 5 6 7 8 9 · · ·#partitions 1 2 5 15 52 203 877 4140 21147 · · ·C.W. Wampler: Bezout number calculations for multi-homogeneous
polynomial systems. Appl. Math. Comput. 51(2–3):143–157, 1992.
• Heuristics based on structures of the monomialsare effective in most of the practical cases.
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multihomogenization
linear-product start systems
f(x) =
8>><>>:
x1x22 + x1x3
3 − cx1 + 1 = 0 c ∈ C
x2x21 + x2x2
3 − cx2 + 1 = 0
x3x21 + x3x2
2 − cx3 + 1 = 0 D = 27
{x1} {x2, x3} {x2, x3} symmetric
{x2} {x1, x3} {x1, x3} supporting B = 21
{x3} {x1, x2} {x1, x2} set structure
Choose 7 random complex numbers c1, c2, . . . , c7 and create
g(x) =
8>><>>:
(x1 + c1)(c2x2 + c3x3 + c4)(c5x2 + c6x3 + c7) = 0
(x2 + c1)(c2x1 + c3x3 + c4)(c5x1 + c6x3 + c7) = 0
(x3 + c1)(c2x1 + c3x2 + c4)(c5x1 + c6x2 + c7) = 0
8 generating solutions
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multihomogenization
Solving the Loop Equations again
• Partition the unknowns in 6 groups:{{θ1, θ1}, {θ2, θ2}, {θ3, θ3}, {θ4, θ4}, {x, x}, {y, y}}.
• The 6-homogeneous Bezout number is 96
� 4,096 (= total degree).
• Solving takes only 16 seconds � 25 minutes,
but still 60 wasted paths.
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polyhedral homotopies
Polyhedral Homotopies
D.N. Bernshteın. Functional Anal. Appl. 1975.
B. Huber and B. Sturmfels. Math. Comp. 1995.
T.Y. Li. Handbook of Numerical Analysis. Volume XI. 2003.
T. Gao, T.Y. Li, and M. Wu. Algorithm 846: MixedVol:A software package for mixed volume computation.ACM Trans. Math. Softw. 31(4):555–560, 2005.
T. Gunji, S. Kim, M. Kojima, A. Takeda, K. Fujisawa,and T. Mizutani. PHoM – a polyhedral homotopycontinuation method for polynomial systems.Computing 73(4):55–77, 2004.
G. Jeronimo, G. Matera, P. Solerno, and A. Waissbein.Deformation techniques for sparse systems.arXiv:math.CA/0608714 v1 29 Aug 2006.
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polyhedral homotopies
Geometric Root Counting
fi(x) =Xa∈Ai
ciaxa
cia ∈ C∗ = C \ {0}f = (f1, f2, . . . , fn)
Pi = conv(Ai)
Newton polytope
P = (P1, P2, . . . , Pn)
L(f) root count in (C∗)n desired properties
L(f) = L(f2, f1, . . . , fn) invariant under permutations
L(f) = L(f1xa, . . . , fn) shift invariant
L(f) ≤ L(f1 + xa, . . . , fn) monotone increasing
L(f) = L(f1(xUa), . . . , fn(xUa)) unimodular invariant
L(f11f12, . . . , fn) root count of product
= L(f11, . . . , fn) + L(f12, . . . , fn) is sum of root counts
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polyhedral homotopies
Geometric Root Counting
fi(x) =Xa∈Ai
ciaxa
cia ∈ C∗ = C \ {0}f = (f1, f2, . . . , fn)
Pi = conv(Ai)
Newton polytope
P = (P1, P2, . . . , Pn)
properties of L(f) V (P) mixed volume
invariant under permutations V (P2, P1, . . . , Pn) = V (P)
shift invariant V (P1 + a, . . . , Pn) = V (P)
monotone increasing V (conv(P1 + a), . . . , Pn) ≥ V (P)
unimodular invariant V (UP1, . . . , UPn) = V (P)
root count of product V (P11 + P12, . . . , Pn)
is sum of root counts = V (P11, . . . , Pn) + V (P12, . . . , Pn)
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polyhedral homotopies
Geometric Root Counting
fi(x) =Xa∈Ai
ciaxa
cia ∈ C∗ = C \ {0}f = (f1, f2, . . . , fn)
Pi = conv(Ai)
Newton polytope
P = (P1, P2, . . . , Pn)
L(f) root count in (C∗)n V (P) mixed volume
L(f) = L(f2, f1, . . . , fn) V (P2, P1, . . . , Pn) = V (P)
L(f) = L(f1xa, . . . , fn) V (P1 + a, . . . , Pn) = V (P)
L(f) ≤ L(f1 + xa, . . . , fn) V (conv(P1 + a), . . . , Pn) ≥ V (P)
L(f) = L(f1(xUa), . . . , fn(xUa)) V (UP1, . . . , UPn) = V (P)
L(f11f12, . . . , fn) V (P11 + P12, . . . , Pn)
= L(f11, . . . , fn) + L(f12, . . . , fn) = V (P11, . . . , Pn) + V (P12, . . . , Pn)
exploit sparsity L(f) = V (P) 1st theorem of Bernshteın
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polyhedral homotopies
3 stages to solve a polynomial system f(x) = 0
1. Compute the mixed volume (aka the BKK bound)of the Newton polytopes spanned by the supports A of f
via a regular mixed-cell configuration ∆ω.
2. Given ∆ω, solve a generic system g(x) = 0, using polyhedralhomotopies. Every cell C ∈ ∆ω defines one homotopy
hC(x, s) =∑a∈C
caxa +∑
a∈A\C
caxasνa , νa > 0,
tracking as many paths as the mixed volume of the cell C,as s goes from 0 to 1.
3. Use (1 − t)g(x) + tf(x) = 0 to solve f(x) = 0.
Stages 2 and 3 are computationally most intensive (1 � 2 < 3).
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polyhedral homotopies
Solving the Loop Equations once more
• The mixed volume equals 36 and is an exact root count.
584 milliseconds to compute the mixed volume
1 second 448 milliseconds to solve a random start system
1 second 800 milliseconds to track 36 paths to target system
• total time: 3 seconds and 868 milliseconds
better than the 16 seconds with multihomogenization
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polyhedral homotopies
A Static Distribution of the Workload
joint with Yan Zhuang
manager worker 1 worker 2 worker 3
Vol(cell 1) = 5
Vol(cell 2) = 4
Vol(cell 3) = 4
Vol(cell 4) = 6
Vol(cell 5) = 7
Vol(cell 6) = 3
Vol(cell 7) = 4
Vol(cell 8) = 8
total #paths : 41
#paths(cell 1) : 5
#paths(cell 2) : 4
#paths(cell 3) : 4
#paths(cell 4) : 1
#paths : 14
#paths(cell 4) : 5
#paths(cell 5) : 7
#paths(cell 6) : 2
#paths : 14
#paths(cell 6) : 1
#paths(cell 7) : 4
#paths(cell 8) : 8
#paths : 13
Since polyhedral homotopies solve a generic system g(x) = 0,we expect every path to take the same amount of work...
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polyhedral homotopies
An academic Benchmark: cyclic n-roots
The system
f(x) =
fi =n=1∑j=0
i∏k=1
x(k+j)mod n = 0, i = 1, 2, . . . , n − 1
fn = x0x1x2 · · ·xn−1 − 1 = 0
appeared in
G. Bjorck: Functions of modulus one on Zp whose Fourier
transforms have constant modulus In Proceedings of the Alfred
Haar Memorial Conference, Budapest, pages 193–197, 1985.
very sparse, well suited for polyhedral methods
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polyhedral homotopies
Results on the cyclic n-roots problem
Problem #Paths CPU Time
cyclic 5-roots 70 0.13m
cyclic 6-roots 156 0.19m
cyclic 7-roots 924 0.30m
cyclic 8-roots 2,560 0.78m
cyclic 9-roots 11,016 3.64m
cyclic 10-roots 35,940 21.33m
cyclic 11-roots 184,756 2h 39m
cyclic 12-roots 500,352 24h 36m
Wall time for start systems to solve the cyclic n-roots problems,using 13 workers, with static load distribution.
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polyhedral homotopies
Dynamic versus Static Workload Distribution
Static versus Dynamic on our cluster Dynamic on argo
#workers Static Speedup Dynamic Speedup Dynamic Speedup
1 50.7021 – 53.0707 – 29.2389 –
2 24.5172 2.1 25.3852 2.1 15.5455 1.9
3 18.3850 2.8 17.6367 3.0 10.8063 2.7
4 14.6994 3.4 12.4157 4.2 7.9660 3.7
5 11.6913 4.3 10.3054 5.1 6.2054 4.7
6 10.3779 4.9 9.3411 5.7 5.0996 5.7
7 9.6877 5.2 8.4180 6.3 4.2603 6.9
8 7.8157 6.5 7.4337 7.1 3.8528 7.6
9 7.5133 6.8 6.8029 7.8 3.6010 8.1
10 6.9154 7.3 5.7883 9.2 3.2075 9.1
11 6.5668 7.7 5.3014 10.0 2.8427 10.3
12 6.4407 7.9 4.8232 11.0 2.5873 11.3
13 5.1462 9.8 4.6894 11.3 2.3224 12.6
Wall time in seconds to solve a start system for the cyclic 7-roots problem.
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serial chains
Design of Serial Chains I
H.J. Su. Computer-Aided Constrained Robot Design Using Mechanism
Synthesis Theory. PhD thesis, University of California, Irvine, 2004.
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serial chains
Design of Serial Chains II
H.J. Su. Computer-Aided Constrained Robot Design Using Mechanism
Synthesis Theory. PhD thesis, University of California, Irvine, 2004.
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serial chains
Design of Serial Chains III
H.J. Su. Computer-Aided Constrained Robot Design Using Mechanism
Synthesis Theory. PhD thesis, University of California, Irvine, 2004.
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serial chains
For more about these problems:
H.-J. Su and J.M. McCarthy: Kinematic synthesis of RPSserial chains. In the Proceedings of the ASME DesignEngineering Technical Conferences (CDROM), Chicago, IL,Sep 2-6, 2003.
H.-J. Su, C.W. Wampler, and J.M. McCarthy: Geometricdesign of cylindric PRS serial chains.ASME Journal of Mechanical Design 126(2):269–277, 2004.
H.-J. Su, J.M. McCarthy, and L.T. Watson: Generalized linearproduct homotopy algorithms and the computation ofreachable surfaces. ASME Journal of Information andComputer Sciences in Engineering 4(3):226–234, 2004.
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serial chains
Results on Mechanical Design Problems
joint with Yan Zhuang
Bounds on #Solutions Wall Time
Surface Bezout linear-product Mixvol our cluster on argo
elliptic cylinder 2,097,152 247,968 125,888 11h 33m 6h 12m
circular torus 2,097,152 868,352 474,112 7h 17m 4h 3m
general torus 4,194,304 448,702 226,512 14h 15m 6h 36m
Wall time for mechanism design problems on our cluster and argo.
• Compared to the linear-product bound, polyhedral homotopiescut the #paths about in half.
• The second example is easier (despite the larger #paths)because of increased sparsity, and thus lower evaluation cost.
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