Machine Kinematics
solved, then drawn
Field

What a joint is

Every field before this one declares its joints and then counts what they take away. A count cannot tell a pin from a slide: both are one, and the two mechanisms you get by swapping them are not related at all. What a joint permits is a set of displacements closed under composition — a group — and the six lower pairs turn out to be the six groups a surface can have as its own symmetry. The same instrument, run on a whole mechanism, separates the two kinds of overconstraint by an integer.
Six surfaces, six groups, six pairs. The six lower pairs, drawn as the surfaces they are. A lower pair is two bodies touching over a surface rather than at a point or along a line, and that is the same thing as saying the surface slides on itself — so what the joint permits is the surface's own symmetry group. Each caption is computed from the surface's normals and not from the pair's name: a plane gives three freedoms and planar motion, a sphere gives three and spherical motion, a plain cylinder gives two, a shaft with collars gives one rotation, a prism gives one translation, and a thread gives one screw whose pitch comes back as the thread's own lead. Eleven surfaces were tried and six groups came out, which is where the number in every textbook's table comes from.

A joint is a surface that slides on itself

Lower pairs derived from their own surfaces: the twists that carry a surface onto itself, computed as the null space of a tangency matrix, with a plane giving three, a cylinder two and a thread reporting its own lead.

 Every surface tried, and the group it permits. The census the six lower pairs come out of. Each row is a surface, sampled at 240 points; the freedoms column is six minus the rank of a matrix with one row per point, saying that the velocity a twist gives that point is tangent to the surface. Nothing is fitted and no shape is recognised — the surface's own normals write the matrix down. Three different surfaces of revolution give the same group, which is the content of the classification; two surfaces give nothing, which is what almost every surface gives. Eleven surfaces, six groups. The last column is the ratio of the smallest singular value kept to the largest discarded, so a row reading 10¹⁵ is not near being reclassified by anybody's tolerance.

Six, and no others

The census of self-sliding surfaces: why exactly six groups appear as the full symmetry group of a surface, why four of the twelve subgroups never do, and what the rank gap says about the decision.

 One point, six groups, six shapes. A group has no picture, so here is the next best thing: fix one point of the moving body — the marked one — and draw everywhere the group can send it. A prismatic pair sends it along a line, a revolute round a circle, a helical along a helix, a cylindrical over a cylinder, a spherical over a sphere, a planar over a plane. Those six shapes are the six surfaces the previous figures drew, which is not a coincidence and is the field's first argument read backwards: a lower pair's surface is an orbit of its own group, which is exactly why the surface can slide on itself.

The count cannot tell a pin from a slide

Why a mobility count is the dimension of a group and loses everything else: three one-freedom pairs with identical counts, identical ranks and completely different permitted sets.

 The twelve kinds of freedom, and which are joints. Every connected group of rigid displacements, up to where its axis points and where its origin sits. There are twelve, the height on the page is the dimension, and a line means the lower one is contained in the upper — computed by asking whether each generator of the smaller lies in the span of the larger, with all twelve built about a common axis. Filled discs are joints: six of the twelve are the symmetry group of a surface and can be a single pair, and six are not and have to be built out of a chain. There is nothing at dimension five, which is not obvious and is checked rather than assumed: twenty thousand random five-dimensional subspaces of the twists were closed under the bracket, and every one generated the whole of the six.

Twelve kinds of freedom

The classification of the connected subgroups of the rigid displacements, decided by three integers read off a basis, with the six that are lower pairs and the five with no dimension five between them.

 How often a set of screws is a group. Take a subspace of the twists at random and ask whether it is closed under the Lie bracket — whether doing two of its motions in one order and undoing them in the other leaves you inside it. Every one-dimensional subspace is, trivially and importantly: a single screw always generates a one-parameter subgroup, which is the same statement as every screw is a joint somebody could build. Above one dimension, not one of eighty thousand is a group, and every one of them generates the whole of the rigid displacements at the first bracket. So a mechanism whose motion lies inside a proper subgroup is not merely unusual; it is a coincidence of measure zero — and it is the coincidence every planar mechanism, every spherical one and every Sarrus linkage on this site is built on.

Almost nothing is a group

How rare it is for a set of screws to be a group: a census of eighty thousand random subspaces with no closed one above dimension one, and the bracket of two revolute joints as the smallest case.

 One point, six groups, six shapes. A group has no picture, so here is the next best thing: fix one point of the moving body — the marked one — and draw everywhere the group can send it. A prismatic pair sends it along a line, a revolute round a circle, a helical along a helix, a cylindrical over a cylinder, a spherical over a sphere, a planar over a plane. Those six shapes are the six surfaces the previous figures drew, which is not a coincidence and is the field's first argument read backwards: a lower pair's surface is an orbit of its own group, which is exactly why the surface can slide on itself.

What a point sees

Orbits as the only picture of a displacement group, with the orbit of a lower pair's group turning out to be the pair's own surface, and the stabiliser as what a single point cannot see.

 How many dimensions each chain's displacements occupy. Every chain in the field, with the dimension its reached displacements' logarithms occupy. A chain of n joints always has n freedoms; what varies is whether those freedoms compose. Where the bar equals the joint count the motion is inside a group and the group is named; where it reaches six there is no proper group containing the motion, and the two chains that do are the ones whose axes were chosen at random. Nothing about the joints themselves differs — three pins are three pins, and the two rows differ only in where the axes point.

A chain multiplies

The displacement set of a serial chain as a product of subgroups, with the span of the logarithms as the test for whether the product is itself a group.

 Four joints that give a group, and four that do not. Two chains of four revolute-and-slide joints, each drawn at its home position with its joint axes dashed, and each with a cloud of the tool positions it reaches. The counts are identical: four joints, four freedoms, the same Jacobian rank everywhere off a singularity. On the left the three pins are parallel and the slide is along them, and the displacement set is the Schoenflies group — every translation and one rotation direction, four dimensions, closed. On the right the axes are at random and the set is four-dimensional too, and it is inside no group smaller than all the rigid displacements. The instrument is in the caption of each panel: take the logarithms of the displacements the chain reaches and count the dimensions they occupy. Four means a group. Six means there is nothing to be inside.

Four joints that give a group, and four that do not

A SCARA arm against four pins at random, and three parallel pins against three that are nearly parallel: identical counts and ranks, spans of four and six.

 What every pair of groups meets in. The intersection of two subgroups is always a subgroup — that needs no computation — and which one is the useful part. This is the design rule behind every parallel machine in these essays: choose legs whose groups meet in the motion the platform is wanted to have, and it has that motion whatever the leg lengths are, with no synthesis and no tolerance. The row and column are built about different axes, at right angles, because an intersection is a statement about particular subgroups rather than about their kinds: two planar groups with the same normal meet in the whole of themselves, and two with different normals meet in a line.

Legs intersect

Parallel mechanisms as intersections of displacement subgroups, with the intersection table that says which pair of legs leaves a platform which motion.

 Sarrus, as two planes meeting in a line. Each arm of Sarrus's linkage is three pins with parallel axes, so each arm holds the platform inside a planar group — the one whose normal is that arm's axis direction. The platform has to satisfy both, so what it may do is the intersection, and the intersection of two planar groups whose normals are not parallel is the one-dimensional group of translations along their common perpendicular. The platform goes up and down and does nothing else, and that is the exact straight line the spatial field measured to 10⁻¹⁶ of its span — arrived at here with no mechanism solved and no tolerance anywhere. Drag the arms towards each other: the answer is a translation at every angle but zero, where the two groups become one group and the intersection jumps to three dimensions. That is the linkage built flat, and it is the configuration in which it stops being a straight-line mechanism.

Two planes meeting in a line

Sarrus's linkage as the intersection of two planar displacement groups, with the exact straight line as a one-dimensional translation group and the flat configuration as the degeneracy.

 Four instruments, and only the last one names the group. Every instrument these essays have for an overconstrained loop, on the same six mechanisms. Kutzbach's count gives −2 for a planar four-bar and −2 for Bennett's. The rank of the constraint Jacobian gives three and three. Both are right and neither separates them. The last two columns are this field's: the span is how many dimensions the logarithms of the displacements the moving link actually reaches occupy, and closes at is the dimension after those are closed under the bracket. A planar four-bar closes at three and the three are planar motion; Sarrus closes at one, a translation, which is the exact straight line the spatial field measured by solving the mechanism sixty times. Bennett closes at six: its displacements occupy four dimensions and no group smaller than all of them contains those four. That is what "paradoxical" has meant in the earlier essays, stated as an integer.

Compose two positions and see where you land

The group axiom run as an experiment on six overconstrained loops, separating subgroup overconstraint from paradoxical by a closure dimension rather than by an angle.

 Why this measurement is not a derivative. The honest failure mode of the field's instrument, drawn rather than hidden. Every set looks like its own tangent space near the identity — that is what a tangent space is — so a chain sampled over a thousandth of a radian reports the dimension of its velocities, which is the number the screw system already gives. Four pins at random has four joints, and sampled over 10⁻⁹ radians its displacements occupy four dimensions; sampled over two radians they occupy six. The step is at 10⁻⁶, which is where the departure from the tangent space falls below the rank tolerance — so the position of the step is a fact about arithmetic and the two plateaux are facts about the mechanism. A group is a statement about displacements you could compose, and no derivative can make it.

The instrument that is not a derivative

Why a closure measurement needs a finite sampling range, what the step in span-against-range means, and how the screw system is the left-hand plateau of the same curve.

 Two permitted motions, and a composite that lifts off. A disc resting on a straight edge — a roller follower on a flat-faced cam, and the simplest higher pair there is. Two bodies touching at a point rather than over a surface, two freedoms: slide along the edge, and turn, because a disc is its own symmetry group about its centre. Both are permitted and both keep the contact exactly. Their composite does not. The faint discs are the two permitted displacements taken separately; the solid one is one followed by the other, and its centre sits 1.049 radii off the dashed line where a tangent disc's centre has to be. The excursion is exactly |t₂ sin φ₁| — the second displacement's slide times the sine of the first one's turn — derived from the two displacements rather than from the composition and agreeing to 10⁻¹⁶. A lower pair's freedoms compose and a higher pair's do not, which is why a joint's freedom count is the dimension of a group in one case and the dimension of nothing in the other.

A higher pair has no group

Higher pairs as permitted sets that are not groups, with the composition excursion of a disc on an edge measured against a closed form derived from the two displacements.

 slider crank: the closest pair at one position. Crank 1, connecting rod 3, the block sliding on the frame's own line. Every joint is where the solver put it, exactly as in the linkage field; the material is the only thing added. The heavy segment joins the two closest points over every pair of parts that is tested — which excludes pairs sharing a pin, since their material surrounds that pin by construction — and its length is the gap: -0.1400 here, between rod · guide, upper. A negative value is a penetration depth, the distance the pair would have to be moved apart, and it is drawn in the warning colour.

The block in the guide has a length

What a sliding pair costs once the block that realises it has a size: the guide length a stroke needs, by arithmetic and by a body search, and why the pair's own count is unchanged.

 Oldham's coupling: two slides between two offset shafts. An input hub on one axis and an output hub on a parallel axis 0.6 away, joined by a disc that slides in a slot across the input hub and carries a tongue across the output hub at 90° to the slot. At an input angle of 35° the disc has slid 0.491 along the slot and the output hub -0.344 along the tongue, and the output hub has turned through exactly the input's angle, because neither slide can change an orientation. The disc's centre, the dot, runs round the dashed circle of diameter 0.600 — the offset divided by sin 90° — and goes round it 2 times for each turn of the shafts.

A coupling that only translates

Shaft couplings classified by the group their hubs' relative displacements generate, sampled over a turn and closed under the bracket — Oldham's coupling at two slide angles, a parallel-crank coupling and two non-parallelogram four-bars; the equivalence between a constant velocity ratio and a translation group; the Oldham disc's centre running twice round a circle of diameter e/sin β; and the slides' peak speed of e/sin β, least at a right angle.

 A double Cardan joint in the W arrangement. Two universal joints on an intermediate shaft, the input arriving at 15° to it and the output leaving at 15°, bent the same way so that the input and output lines meet, with the intermediate shaft's two yokes in one plane. Each pin is found as the line square to its own shaft and to the pin it crosses, so the output's angle is solved rather than taken from a formula. The dashed marks are one on each hub. The shaded square is the plane that swaps the input's approach with the output's departure. At an input angle of 40° the output is at 40.00°, exactly in step.

Constant velocity is a mirror

Constant-velocity shaft joints classified two ways: the group their hubs' relative displacements generate (the spherical group S for every joint whose shafts meet, T2 or planar motion for parallel shafts), and the isometry that exchanges their hubs — the mirror in the bisecting plane for a single cross and the W double Cardan, the point reflection through the intermediate shaft's middle for the Z arrangement. The relative turn's size as the invariant a constant-velocity joint holds; the circle-involution argument that a hub swap fixes all configurations or none; phasing and unequal angles measured from the solved pins.

 Near its mirror, a double Cardan joint's lag is an ellipse in its two errors. A W double Cardan joint whose working angles average 15°, with a phasing error δ between its middle yokes across and a difference ε between its two working angles up, both in degrees. The curves are where the predicted lag spread over a turn, tan a·√((sin a·δ)² + ε²), is 0.05°, 0.1°, 0.15°, 0.2°. The dots are 35 joints solved from their pins, labelled with their measured spread in degrees; they meet the ellipse to 0.06% at worst. The ellipse is 3.86 times as wide as it is tall: at 15° a degree of phasing error does what 0.259° of mismatch between the angles does.

Two errors, one ellipse

The first-order lag of a nearly symmetric double Cardan joint: the mirror-even and mirror-odd parts of an error, the closed-form slopes sin a·tan a for phasing and tan a for unequal angles checked to 10⁻⁶ at five angles in both arrangements, the quadrature of the two signatures, and the error budget each allows.

 Six balls, two grooves each, and a cage. A Rzeppa joint bent 20°, input shaft along z and output shaft turned about x. Each ball lies where the plane of its inner-race groove, through the input's axis, meets the plane of its outer-race groove, through the output's axis; at equal input and output angles every ball is in the plane bisecting the two shafts, and the cage holds them there. Left, from the side: the two shafts and the bisecting plane edge-on, the balls on it. Right, along the cage's normal: the six balls round their circle, the plane of the bend drawn across it. At an input angle of 0° a cage clearance of c lets the output lag or lead by up to 0.350 c radians, c in ball-circle radii.

A Rzeppa cage adds its clearances

A six-ball Rzeppa joint with clearance in its cage windows: the joint from the side and along the cage's normal, with the free lag at each input angle; the free lag over a third of a turn, falling to nought as each ball crosses the plane of the bend; three pairs of balls and their allowances against the worst ball and a root sum of squares; three to eight balls, with four unable to hold the lag; the free lag against the bend; and the exact problem at finite clearance against the linear rule.

 A slide spends one ball of every pair. A 6-ball Rzeppa joint bent 20°, at the symmetric position, with its cage slid along its own normal by 0 of the window clearance c and then tilted to allow the largest lag. Each column is one ball's window, from −c to +c, and the dot is where the ball sits in it at that lag: −1.00, 1.00, −1.00, 1.00, −1.00, 1.00 c. The lag is 0.3500 c. Opposite balls lie on one line through the joint's centre, so a lag or a tilt moves them opposite ways and a slide moves them the same way: whatever the slide gives one ball of a pair it takes from the other, and the lag falls as 1 − s/c.

A floating cage frees three balls and not six

A six-ball Rzeppa joint whose cage may slide along its normal: each ball's window at the largest lag with the cage slid, for six balls and for five; the free lag against how far the cage may slide for three to eight balls; the cage's limit and the offset grooves' limit against the groove offset; both over a ball pitch with tight tracks; the offset at which the grooves take over against the tracks' play; and the exact problem at finite clearance against the rule.

 Past the play, a caged joint shares its load and a grooved one leans on one ball. Two six-ball Rzeppa joints bent 20°, at an input angle of 15°, each twisted 0.03 of a window clearance past its free lag, with every contact a spring of the same stiffness and the cage and balls settled where the stored energy is least. Bars: each ball's share of the total contact load. Left, grooves offset 0.1, where the cage sets the play: 0.17, 0.20, 0.19, 0.16, 0.14, 0.15, 5.91 balls' worth. Right, grooves offset 0.7, where the grooves do: 0.00, 1.00, 0.00, 0.00, 0.00, 0.00, 1.00 balls' worth. Dotted: an even sixth.

A tight groove leans on one ball

Two six-ball Rzeppa joints twisted past their free play with every contact a spring: each ball's share of the load as the twist grows; how many balls' worth take the first load over a ball pitch at three groove offsets; how the sharing spreads with more twist; the hardest-pressed ball's load at equal torque; where the single-ball first load falls against which limit binds; and every case over a whole pitch as a table.

 Tighten the windows and the cage's limit drops below the grooves'. The six-ball Rzeppa joint bent 20° with its grooves offset 0.7 and a track play of one: across a ball pitch, the free lag the grooves alone allow (solid) and the cage alone allows with windows of clearance 0.5 (dashed). The joint's play is the smaller of the two. The cage is the limit wherever its curve is the lower, here at every input angle; it becomes the limit everywhere once the windows' clearance is below 0.559 of the track play. The largest play over the pitch is 0.163.

A tight cage spreads the load until the tracks join in

A six-ball Rzeppa joint with grooves offset 0.7 and its cage's windows tightened: the cage's and the grooves' free lags across a ball pitch as the windows close; the first load's spread against the window clearance; the spread as the twist grows, for four clearances and a caged joint; the hardest-pressed ball at equal torque over the caged joint's; the share of the load on the windows as the tracks join in; and a ledger.

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