Abstract
Mechanisms with lower mobility can be studied by using tools that are directly deduced from those of spatial kinematics as screw theory. Nevertheless, ad-hoc tools that fully exploit the peculiarities of the displacement subgroups these mechanisms move in are usually more efficient both in showing mechanisms’ features and when used to conceive numerical algorithms. Planar displacements constitute a three-dimensional subgroup with many peculiarities that allow the use of simplified tools (e.g., complex numbers) for studying planar mechanisms. Here, the systematic use of three-dimensional vector spaces to represent link poses and velocities in planar motion and planar system of forces is investigated. The result is a novel coherent set of tools that make it possible to geometrically describe kinematics and dynamics of planar mechanisms in the three-dimensional configuration space of links’ planar poses. The effectiveness of this novel approach is shown through a case study.
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Notes
Here, the non-homogeneity is not a problem since these components will be always separately summed.
If σ A|1 = cos θ1 i + sin θ1 j + ζPA|1 k, σ A|2 = cos θ2 i + sin θ2 j + ζPA|2 k and σ A|3 = cos θ3 i + sin θ3 j + ζPA|3 k, then σ A|1 · σ A|2 × σ A|3 = ζPA|1sin(θ3 − θ2) + ζPA|2sin(θ1 − θ3) + ζPA|3sin(θ2 − θ1).
The addition and subtraction of slope angles, θrs, must be computed by choosing the values congruent modulo 2π that belong to the range ]−π, π] rad.
If σ A|1 = cos θ1 i + sin θ1 j + ζPA|1 k and σ A|2 = cos θ2 i + sin θ2 j + ζPA|2 k, then σ A|1 × σ A|2 = ζPA|1(cos θ2 j − sin θ2 i) − ζPA|2(cos θ1 j − sin θ1 i) + sin(θ2 − θ1) k.
Here, “passive” means without actuators. Moreover, all the kinematic pairs are supposed “ideal constraints” (i.e., without friction).
R and P denote revolute and prismatic pair, respectively.
Hereafter, an underlined R denotes an actuated R pair.
A PPM with 2RRR-RR architecture has been proposed by Pennock and Israr [13] as an adjustable six-bar linkage.
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Acknowledgments
This work has been developed at the Laboratory of Advanced Mechanics (MECH–LAV) of Ferrara Technopole, supported by UNIFE and MIUR funds and by Regione Emilia Romagna (District Councillorship for Productive Assets, Economic Development, Telematic Plan) POR-FESR 2007–2013, Attività I.1.1.
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Appendices
Appendix 1
The following vector equations can be written (see Fig. 5)
where the scalar coefficients wj, for j = 1,…,4, are unknowns to be determined; whereas, the explicit expressions of (B–A), (L–A) and (D–A) are given by Eqs. (25) and those of (M–L) and (E–D) by Eqs. (26).
The linear elimination of (I (1)71 –A) and (I (2)71 –A) from Eqs. (42) yields the following two vector equations
which are two linear systems of two scalar equations in two unknowns whose solution is
Formulas (44) provide the explicit expressions of the scalar coefficients wj, for j = 1,…,4, as a function of the mechanism configuration. Eventually, the introduction of such expressions into Eqs. (42) yields the explicit expressions of (I (1)71 –A) and (I (2)71 –A) as a function of the mechanism configuration.
Appendix 2
The time derivative of Eqs. (27a) and (27b) yields
where
The subtraction of the product of Eq. (45a) by n21 from the product of Eq. (45b) by n11 yields
whose comparison with Eq. (28b) gives, for g1 and g2, the following explicit expressions as a function of the mechanism configuration
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Di Gregorio, R. Kinematics and dynamics of planar mechanisms reinterpreted in rigid-body’s configuration space. Meccanica 51, 993–1005 (2016). https://doi.org/10.1007/s11012-015-0251-8
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DOI: https://doi.org/10.1007/s11012-015-0251-8