IMPROVEMENTS IN PARALLEL LINK MACHINE DESIGN

Abstract: A hexapod machine is disclosed in which six adjustable length struts couple to a controllably moveable platform at three triangularly spaced locations at each of which a pair of struts couple together and to the platform at a bifurcated universal joint. The struts extend away from the platform and through machine nodes defined at triangularly spaced-apart locations in a machine sub-frame, and at each such node a strut extending from one platform location and the next adjacent strut from the next adjacent platform location come together and cross each other in respective hemispheres of a bifurcated sphere journalled for multidirectional pivotal movement in a socket in the sub-frame. The hemispheres each contain a motor which is frictionally engaged with the respective strut so as to enable it to be driven through the hemisphere to adjust its effective length. By control of the motors, the platform position and orientation can be adjusted in space. Also disclosed is a pentapod machine in which a tripod with three adjustable legs defines the position of a first tool support, and the position of a second spaced-apart tool support is defined by two adjustable legs, a tool being supported between said two supports.

Description: IMPROVEMENTS IN PARALLEL LINK MACHINE DESIGN Field of the Invention: This invention concerns improvements in parallel link machine design. Parallel link mechanisms, in contrast to serial link mechanisms, function in dependence upon the movements of plural linkages working in concert to determine a position, whereas in serial link mechanisms each linkage operates independently. The Hexapod (see for example WO-A-9217313) is an example of a parallel link machine. The invention provides new configurations of parallel link mechanisms, which confer advantages of dexterity, compactness, ergonomics and value engineering. In one aspect of the invention, a new 'bifurcated' drive mechanism is proposed for a Hexapod. It enables two struts to be driven through the same notional focal point, thereby minimising the number of nodes that need to be supported and calibrated. It also enables a wide separation of nodes for a given package size, which improves the stiffness and accuracy. A new kinematic arrangement is also proposed that mitigates the polar nature of the available dexterity, and thereby provides for a more usable articulation range. In another aspect, the invention also relates to a novel geometry that could be described as a Pentapod, in that it has only five struts acting in parallel. The five strut lengths define an unambiguous 5 axis position. The sixth axis is in common with a spindle, which consequently does not affect normal articulation. Similar to the improved Hexapod, the kinematics enables a consistent range of articulation throughout its working volume. Background of the Invention: Hexapods are parallel link mechanisms where six variable length struts act together to establish the fully constrained position of an end effector. They have been commonly employed to articulate flight simulators and increasingly in robotics and multi axis machine tools. Many alternative solutions have been proposed, but all have necessarily been compromises, often resulting in mechanical complexity. The ideal geometry is an octahedron with three nodes at the top and three at the bottom and six struts forming successive triangles in between. In practice this geometry has only been possible where the struts vary their length telescopically between the node joints. This severely limits the ratio of maximum to minimum strut length and hence the articulation range of the hexapod. Alternatively the struts can pass through the focal points of the nodes to change their effective length between the nodes. However, current designs require that the support frame must then support six individual nodes rather than three shared nodes. Additionally in order to ensure that the withdrawn struts cannot interfere with each other behind the frame, the nodes have to be sufficiently displaced from each other. For a given frame size this reduces the base length of the strut triangles, worsening the vertex positioning leverage. Also the base frame now supports six nodes so will be subject to more. bending moments and calibration errors. Struts have been successfully engineered using hydraulics or screw shafts - in particular ball screws for precise mechanisms. Ball screws however are expensive to make accurately and are generally massive, limiting their length and the speed with which they can be moved. They also do not assist in the application of a suitable length measuring transducer. Either the engineering becomes even more complex or you have to infer the length of the strut from the degree of rotation of the nut - not ideal. Hexapods are naturally polar devices. As a result they find it easier to point their end effector towards the outside of their workspace, rather than inwards towards its center. It would certainly be an advantage if a hexapod demonstrated a more consistent tilting ability over more of its workspace. Hexapods are also 6 axis, although for machine tool use the common axis with the spindle serves little useful purpose (other than torque constraint). It would be helpful if this extra articulation could also be employed to extend the tilt range. Hexapod machine tools have currently been packaged such that the workpiece has to be negotiated between either the struts or a similarly obtrusive machine frame. This does not permit ready vertical loading of potentially heavy parts. Hexapods are six axis mechanisms, whereas strictly it is not necessary for a multi axis machine tool to articulate about more than five, since the sixth is in common with the axis of the spindle. It would save costs if only five servo powered struts were able to constrain the necessary five degrees of freedom. Objects and Summary of the Invention: It is an object of the invention to simplify the kinematics of parallel link mechanisms to make them easier to calibrate, deliver a more useable working volume in a smaller package size, and in particular to reduce their mechanical complexity in order to reduce their cost. It is a further object of this invention to provide for a more ergonomic machine package that gives ready access to the workspace, is easy to maintain and is lightweight without sacrificing stiffness. It is a first aspect of this invention to use a friction drive concept to change the effective lengths of the struts, which can then be low cost and lightweight. This technique avoids the mechanical complexity in otherwise restraining the torque generated by the more typical screw drive strut. It also enables the simple integration of a strut length encoder. It also facilitates very long struts and/or very fast movement by reducing the static and inertial mass. It is a further aspect of this invention to produce a new style of parallel link mechanism that needs only five servo axes to deliver five degrees of freedom. The simplification saves the cost and the error budget of what otherwise would be a redundant axis. The proposed hexapod uses simple rigid struts that pass through their supporting nodes at one end, permitting almost unlimited extension. However in this invention each strut is mounted in a hemisphere and has a "D" end profile such that it can lie close to the hemisphere's end plane but does not encroach beyond it. In this way when two hemispheres are brought together, the struts in each half can pass each other even as the relative angular displacement of the two hemispheres changes. The fact that the struts cannot both literally pass through the common focal point of the two hemispheres does not introduce any serious buckling moments or errors. Even if the strut is mounted with a loose tolerance, the strut length is not seriously compromised as this error is normal to the strut; i.e. if the strut is lm long and the displacement error is 1mm, the measured length error would only be 0.5 micron. The combined effect is like a bifurcated drive sphere with two struts passing through it. The struts can be produced by the extrusion of aluminium or the pultrusion of a suitable composite (such as carbon fibre). With a substantially hollow section they deliver much better stiffness to weight than a solid strut and consequently also have higher resonant frequencies that are easier to damp. They are held and driven by frictional contact with rollers otherwise retained in each hemispherical node. This style of drive is often referred to as a capstan or friction drive. As the strut doesn't need to rotate or hold an external thread, a linear measurement scale can be readily incorporated. With the read head located in the hemispheres, this will then read the absolute displaced length; rather than a nut rotation that is subject to several stages of mechanical error. Also the measurement scale can be mounted on a thermally neutral substrate (like carbon fiber or Zerodor) such that length measurement is not unduly effected by changes in temperature. Because the circumference of a friction wheel is necessarily greater than the lead pitch of a ball-screw, a gearbox needs to be introduced for the motor to increase its torque and reduce its speed. Conventional gearboxes all suffer from backlash, which can only be reduced at significant cost. In a preferred embodiment, 4 friction rollers are used to support the strut, and are all driven. This reduces the holding preload necessary to ensure adequate friction to avoid skidding compared with having perhaps just one friction drive wheel and the rest 'idling'. They would all have "V" profile rims to make two contact zones with the struts runners. These runners can be made out of suitably hard material and are retained on either side of the strut profile. The bifurcated drive spheres are retained in a split socket ring, permitting the struts to pass through the joint. The two rings are preloaded together to main a constant clamping force around the sphere. They are internally recessed such that all the contact occurs along a bearing strip running along the top and bottom edges of the socket. To minimize the friction the socket should extend as far around the drive sphere as is consistent with acceptable strut articulation. Determining the movement range of each strut necessary to enable the planned working volume and factoring in the struts "D" profile allows the boundary locus to be optimized. The resulting boundary looks like two non-mirroring lobes. An elastomeric boot can encapsulate each side of the joint from the socket rim to the further boot that protects the strut. This will retain a suitable lubricant and protect the joint from particulate ingress. The other ends of the 6 struts are connected in pairs into 3 bifurcated ring joints mounted in a triangular configuration on the effector frame. Each joint must permit the strut pair to change its vertex angle and freely tilt and twist about a common focal point. A simple way of achieving this is one of the subjects of this invention. A precision ball is retained by a short support shaft to the effector frame. The first strut is connected to a ring that loosely circumscribes the sphere with an inward facing "N" profile. On either side further bearing rings are installed internally conforming to the sphere in the manner of a split socket. These baring rings are made out of a low friction plastic such as a compound of PTFE. They can accommodate a small reduction in diameter because of their thermoplastic nature, which also helps them grip the sphere sympathetically. PTFE in particular will slowly deform under pressure to conform to its constraints. The second strut is connected to another slightly offset ring that runs alongside the first strut ring with an inward facing chamfer to trap one of the bearing rings. A second 'preload' ring similarly traps the second bearing ring from the other side and is preloaded towards the second strut ring (typically by fasteners with disc spring washers). The preload effectively squeezes both of the strut rings against the upper chamfers of the bearing rings; thereby constraining them to a common pivot axis that also passes through the focal point of the sphere. The common axis allows the struts to change their vertex angle; and the pair act together like a socket ring permitting three degrees of freedom about the sphere. These components can be produced at low cost because they are self- centering and conforming; and receive all of their critical accuracy from a single turning operation set-up. The joint resembles a rod end bearing and as such can accommodate 360 degrees of rotation about its support stub axis. Correctly aligned this helps to ensure the most useful overall joint articulation. Also the tension or compression in the struts is applied largely normal to the sphere thereby not pinching it and unduly increasing the friction as would occur in a conventional ball and socket. If the sphere and the rings were subject to different temperatures, the preload would accommodate the change moving the struts slightly apart along their common pivot axis and thereby introducing very little net strut length error. This is again unlike a conventional ball and socket joint where in similar circumstances the ball will tend to pop out of the socket and directly effect the strut length. The entire joint can be encapsulated in an elastomeric boot that can also contain a suitable lubricant; thereby ensuring long life and minimum friction. Most current hexapods have had a symmetrical arrangement of base frame and effector frame, generally with the mechanism suspended vertically.. The tilt range of the effector is then modified by the overall suspended angle of the mechanism in a polar fashion. Typically if the effector can tilt by +-45 degrees and the mechanism heals over by 45 degrees then the tilt in a Cartesian frame of reference would be +0-90 degrees. This is generally a disadvantage. This invention proposes a kinematic arrangement where the hexapod acts from one side (rather than above) but with the spindle still pointing down, and where the effector frame has an angular offset from the general mechanism. In this configuration rotation permitted in the spindle axis (which is generally greater than in the tilt axes) is instead 'mixed in' to the tilt axes to extend their useful range. This makes sense also because the more useful working volume is a cylinder larger in diameter than its height. Therefore with the mechanism acting principally horizontally, the polar behavior that compromises the tilt range occurs over the smaller z displacements. In the preferred x-y plane no tilt bias is generated. Furthermore by tilting the effector frame a tilt range bias can be introduced which mitigates the z displacement polar effect when the struts are short and thereby helps to maintain a consistent tilt range. It has been found that with such an arrangement a tilt range of +-45 degrees can be maintained over all of the x,y and most of the z. A collateral benefit is that the frame supporting the drive nodes is now closer to the work deck and therefore easier to integrate rigidly. It also does not obstruct the vertical space, enabling more ergonomic access. The frame holding the work deck and the adjacent more vertical frame holding the drive nodes can be integrated into a single casing (or split for manufacturing convenience). This casting may have a 'smooth' internal surface (for easy machine cleaning) and external webs to stiffen it along its node to node force concentrations. A further tubular framework can then support the casing at a convenient height and also help to stiffen it. This framework looks like another hexapod, the upper 3 nodes supporting the work deck area and with the lower triangle having a single node to the rear. From this node two further support struts rise up in a "N" to connect with the back of the vertical part of the frame (at a junction of stiffening webs). A cover can be provided like an open pod or cowling that encloses the whole working volume. This can be pivoted and supported on gas springs so that it can be raised clear of the workspace, providing excellent all round access. The frame castings and cover can be sized to enable only the desired work and articulation space. This keeps the machine very compact. In one embodiment a machine with a footprint of about lm*1.3m has a 3 axis volume of 600mm dia. *400mm high, and a full tilt 6 axis volume of 400mm dia. *250mm high. The combined effect of an efficient node to node framework, lightweight hexapod mechanism and a tailored enclosed space is a machine that is close to an order of magnitude smaller and lighter than conventional 5 axis machine tools: Integrating a tool rack into the frame casting can facilitate automatic tool-change. Conveniently this would be behind the work deck where it can be reached by the spindle but does not obstruct the workspace, and arranged such as to hold the tools at an angle facing inwards. A suitably equipped spindle can then deposit its old tool in a vacant retainer and pick up the new one from the available selection. Apart from a moveable swarf shield the rack is passive, therefore low cost and robust. All the movement to effect the tool-change is performed by the hexapod at no cost or complexity premium. The machine packaging concept thus far described suits its application as a self contained machining cell. However the light weight and elegant 3 node mounting of this style of hexapod lets it be supported by simple open tubular frameworks, to enable much increased working volume or integration with other factory automation. One such framework is proposed where the three drive nodes are connected by frame members and arranged with one node at the bottom and the upper two nodes leaning inwards. Six frame members describe a tetrahedron that supports the lower of the drive nodes at its vertex (with one base node to the rear). The other two drive nodes are then connected by frame members to both the front two base nodes, and in a "V to the rear base node. This architecture is fully constrained and does not obstruct the struts either in front or behind. It enables a mechanism module to roam over uncommitted space where the user may construct his bespoke work-cell. It could be mounted on a turntable (as a seventh axis) which enables wide all round reach as would particularly benefit a robotics application. Thus far the mechanism has been described retained on its side. Some applications may benefit from it being mounted vertically. In such an embodiment frame members would again connect the three drive nodes, but this time pairs of struts connected together like a hexapod without a base frame would support them. If these struts were of adjustable length (such as telescopic), the three base nodes could be freely located around the work-cell (both above and below it) and the mechanism optimally positioned. The invention as so far described concerns the embodiments of a hexapod with six nodes and six variable length struts. However there is another fundamentally different geometry which can be employed for multi-axis machine tools. It has been referred to hereinbefore as a Pentapod. In this embodiment only five struts are employed acting between seven nodes. They are arranged as a tripod and a "V. The spindle acts as a spacer between the vertex of the tripod and the vertex of the "V. Individual drive nodes support the other ends of the struts. They are naturally spaced apart so the withdrawn struts cannot interfere at the rear. This arrangement is more economical in only needing 5 servo axes. The sixth axis not otherwise constrained is the one in common with the spindle, so does not limit the necessary 5 axis articulation. Spindle torque will introduce some small bending moments into the struts, but these forces are generally readily managed. This architecture delivers consistent maximum tilt over its entire preferred x,y plane. Some polar bias is introduced with z displacement, more on the inner facing side (x min) than the outer (x max). The preferred drive concept would be a friction drive as described for the hexapods bifurcated nodes, except in this case the nodes are individual spheres (not hemispheres). The struts can then have more efficient round rather than "D" cross sections, with runners still supporting them on opposite sides. Also with free use of the whole sphere, more economical bearing arrangements can be used to retain the friction wheels; and more space afforded to the motor. Sockets rings can again retain the spherical drive nodes, being preloaded together to maintain stiffness and sealed on either side with a boot. Because the drive spheres can rotate in the plane of the socket the struts do not need a swivel enabling end connection (as in the hexapod). The vertex for the tripod is a trifurcated joint whose design is also one of the subjects of this invention. The object is to being four struts together at a common focal point, such that two pairs of struts share common pivot axes and that one pair can additionally tilt and rotate about the other. The pair that need to articulate about the focal point are substantially arranged as the previously described 'rod end' style bifurcated ring joint as used to support the effector of the hexapod. Only in this case the ball is itself bifurcated, comprising of two hemispherical shells. One shell is connected to the 'reference' strut, the other to the spacer frame that runs between the two nodes. They are held together by the 'rod end' bifurcated joint ring and additionally constrained to a common pivot axis by internal mating radial features. The preload established on the outer bifurcated ring reflects through the whole joint, theoretically maintaining all bearing interfaces at the required pressure. The joint can be encapsulated in a protective boot that also retains suitable lubricant. The fact that the 'reference' strut can only pivot in one axis with respect to the spindle is a blessing as it acts to counter the spindle torque. This capability becomes increasingly necessary if the lower two struts do not share a common pivot point as the feed force of the spindle could introduce some additional torque. It is desirable to make the lower struts share a common vertex point, but there is equally a need to let the spindle act along the axis between the tripod and "V" nodes. To accommodate both preferences a bifurcated ring joint would have to have a large diameter in order to allow the spindle to pass through it, and then would be difficult to seal. A reasonable compromise is to accept a displacement between the lower strut pivot points in order to allow a spindle to be mounted between them. Basic rod end type joints can then support the strut ends. For the low cost market for which the Pentapod is proposed, flexibility in the type of spindle or end effector employed is advantageous. Perhaps most desirable is not to have a spindle at all, but a compatible mount for a powered hand tool like a Dremmel. This would allow the user to replace the most vulnerable part of any machine tool - the spindle - at low cost, and also provides access to the wide range of cutting, grinding and polishing fittings available for it. By its nature the Pentapod has a spindle axis orthogonal to the 'centerline' of the mechanism. It can therefore be 'packaged' much like the side acting hexapod previously described, with a side acting mechanism and horizontal work deck. However because it is envisaged that the Pentapod will be significantly smaller and will generate considerably lower frame loads than the previously described hexapod, it can be offered as a 'desk top' model without the additional external tubular framework. A single casting can then incorporate the entire support structure from drive nodes to work deck. A single cowling can again enclose the workspace ensuring safe and clean usage. In order that the present invention, in all of its aspects, might be clearly understood, exemplary embodiments will hereinafter be described with reference to the accompanying drawings. Description of the Drawings: Fig. 1 is a perspective view of an exemplary Hexapod embodying the present invention; Fig. 2 shows an alternative Hexapod embodiment; Fig. 3 shows the embodiment of Fig. 2 with its support leg mounting points differently arranged; Figs. 4A and 4B show, respectively, schematic plan and sectional side elevation views of a hemispherical friction drive arrangement for a D-section Hexapod strut; Figs. 5A, 5B and 5C are different perspective views of a horizontally mounted hexapod arrangement having a vertical spindle orientation; Fig. 6 is a perspective view of yet another Hexapod embodiment; Figs. 7A and 7B show, respectively, a side elevation view and a top plan view of a workstation incorporating two Hexapods as in Fig. 6; Figs. 8A and 8B are front and rear perspective views of an exemplary Pentapod embodying the present invention; Figs. 9A, 9B and 9C are, respectively, schematic front and side elevation views and a top plan view of a Pentapod mechanism; Figs. 10A, 10B and IOC are views similar to those of Figs. 7A, 7B and 7C but showing a different Pentapod arrangement; and Figs. 11A and 11B show, respectively, an exploded view and a side elevation view of a trifurcated joint. Detailed Description of the Embodiments An embodiment of a 6 node hexapod is shown in Fig. 1. The struts (e.g. 1) cross over in, and can pass through bifurcated drive spheres (e.g. 2), supported in sockets (e.g. 4). The other ends of the struts join in pairs at bifurcated spherical joints (e.g. 7) connected with each other by sub-frame 8. As will be described in detail hereinafter, each strut 1 has a semi-circular section and has friction wheel runners bonded to its sides. Each bifurcated drive sphere 2 allows two struts 1 to pass through it as near . to its split line as practical. Each drive sphere 2 is joumalled in a spherical socket 4 having bi-lobar socket windows 3 that permit symmetrical articulation of the strut pair, traversing each drive sphere 2. The sockets 4 are formed by corner moldings that connect to spacer struts (e.g. 5) which define the distance between drive sphere focal points and can be adjustable in length and to respective support legs. (e.g. 6). The bifurcated joints 7 permit respective pairs of struts to share a common focal point, articulating about 3 axes as a pair and able to change their relative subtended angle. By control of the friction drives in each drive sphere hemisphere, the lengths of the struts between the drive sphere focal points and the bifurcated joints 7 can be controlled so as to determine the position and orientation of the sub-frame 8. Fig. 2 shows an embodiment of a similar hexapod concept to that illustrated in Fig. 1, except that the support struts are now additionally joined at their ends 1 and can have their lengths changed by being telescopic with twist-to- lock extension lock (e.g. 2). The drive node spacer (e.g. 5) is now much longer, increasing the working volume without compromising the kinematics. Fig. 3 shows the same hexapod as is illustrated in Fig. 2, but this time with the mounting points for the support legs being repositioned according to the situation preference. The only rule to maintain structure stiffness is that all three strut pairs have to act in significantly different planes. The bifurcated drive spheres in the Hexapod embodiments described with reference to Figs. 1, 2 and 3 may be as shown in Figures 4A and 4B which show schematic top plan and sectional side elevation views of one hemispherical half of such a sphere. As shown, each hemisphere comprises a housing 14 which contains an electric motor 10 driving a pinion 9 which is in frictional engagement (as will be described in detail hereinafter) with friction wheels 8. Each wheel has a lesser diameter portion 17 defining a pinion which frictionally engages respective pairs of strut drive wheels 18a, 18b and 18c, 18d. The strut drive wheels 18a, 18b, 18c and 18d themselves have lesser diameter roller portions which frictionally engage the sides of the struts 1. As abovementioned, within each bifurcated drive sphere a strut 1 is retained by friction rollers 18a, 18b, 18c, 18d, each extending to become the larger friction wheels (e.g. 3). These wheels have an elastomeric band 12 and a springy steel band 13. Where they contact each other or the smaller pinion gears 16 and 17 or the motor input gear 9 they deform slightly to retain contact pressure under elastomeric and spring band preload. Also the struts have runners (e.g. 2) which are supported in elastomeric saddles 19, such that they and the saddle deform under contact pressure to retain preload. By this means all the frictional interfaces can be maintained at a useful working pressure. The elastomeric saddles 19 are each bonded into an axial depression in the edge of a strut, which then have the runners 2 bonded into them. An encoder track can be bonded into an upper depression 20. The runners can comprise spring steel rods. The combined friction drive wheels 18 and larger friction wheels 3 are supported at their ends on needle roller bearings 5 for rotation about axles 4 supported between end plates 6 and 15, the latter also serving to support the motor 10. " Reference numeral 7 shows a ball otherwise part of a radial array running in a gothic arch groove around the hemisphere. This locates adjacent hemispheres and permits them to rotate about a common pivot axis. Reference numeral 16 shows an optional idler wheel. Adding it into the gear train increases the number of frictional drive interfaces with a commensurate reduced need for contact pressure. It also helps to keep the train synchronized and thereby better able to deal with local corruption. Figs. 5A, 5B and 5C show three illustrative views of an embodiment of a packaged hexapod machine where the mechanism is mounted principally horizontally and the spindle head sub-frame at an offset angle. The six struts la-f are shown crossing over in pairs as they pass through the bifurcated drive spheres. In this case they are shown protectively shrouded with an elastomeric concertina cover. The three bifurcated rod end type joints 2a, b and c connect the strut ends to the spindle housing 5. A casting 3 constitutes both frame and packaging. It starts as a dish surrounding a worktable 4, and curls up to become the mounting for the drive spheres. On its backward facing side it has integrated ribs to act as stiffeners. The worktable 4 is retained by webs to the dish of the frame casting 3, permitting swarf to fall through to an underside collector. The spindle unit 5 is shown at its center default position. A cover 6 with integrated windows is shown in its raised position and can be lowered to isolate the work area. Support leg members (+3 on the base level) are provided for the frame casting and attached to the frame casting, at the five points 8a-f and meet at base level at the three points 9a, b and c. Referring now to Fig. 6, this shows an embodiment of a six node hexapod with three bifurcated drive nodes (e.g. 1) and three bifurcated link nodes (e.g. 2) with the six legs (e.g. 3) connecting the same able to be driven through the drive nodes thereby varying their effective lengths. The support framework consists of three base struts connecting the rigid base junctions 7, 8 and 9. Three further struts connect each base junction to a common vertex junction 10 that also supports a bifurcated drive node. Two further struts then extend up to the peak junctions 11 and 12 that also support bifurcated drive nodes. Four further struts then connect back down to the base junctions (two from each node) such that the rear struts connect to a common base junction 9 and the forward struts connect to adjacent base junctions 7 and 8. Such a structure is kinematically pure in that all forces have been resolved into tension or compression. It comprises of a total of thirteen struts. The spindle unit 4 is attached to the three link nodes. An array of holders for alternate tools 5 can be situated such as to enable the spindle head to articulate around so as to be able to auto-change the current tool. In this embodiment the lower tripod of the support frame is in-filled with panels (e.g. 6) so as to enclose system services. Figs. 7A and 7B show side and plan views of two, six node hexapod modules essentially as described in Fig. 6. Each is mounted on rails such that for each module, the two forward base nodes (e.g. 1 and 2) run on a common rail (e.g. 3) and such that the rear base nodes (e.g. 4) run on parallel and discreet rails (e.g. 5). In this embodiment the two modules can run on separate rail pairs on either side of the workpiece 6, being driven along the rails by a linear motor system, for example. An embodiment of a Pentapod machine is shown in Figs. 8 A and 8B. The five struts la-e pass through individual drive spheres supported by annular sockets retained by a frame casting 6. Three of the struts (a, b and e) terminate at a common focus trifurcated joint 2, the other two have individual universal joints 3 connecting them to the spindle support. The struts are shown shrouded with elastomeric concertina covers. The trifurcated joint 2 permits two struts la and lb to have a common pivot axis and as a pair to articulate with three degrees of freedom about a common pivot point and with a third strut le sharing the same notional pivot point and able to tilt independently in one axis with respect to the spindle support. A removable hand router 4 is shown fitted into the spindle support, this being but an example of the provision of a tool in the pentapod. A worktable 5 is supported by webs to the dish of the frame casting 6 which curls up from the dish around the worktable to go on and support the drive spheres. The frame casting could be assembled out of two parts with an interface 7 filled with a damping elastomer. The frame casting is supported on three legs 8 and has a removable underside swarf tray 9 and a cover 10 with integrated windows shown in its elevated position. Figures 9A, 9B and 9C show a conceptual front and side elevation and top plan of a large format pentapod mounting scheme. The dotted cylinder indicates the working volume. An alternative node layout of a large format pentapod is shown in Figures 10A, 10B and IOC. The dotted cylinder indicates the working volume. An exploded view and a sectional illustration of a trifurcated joint, are shown in Figs 11A and 11B. A strut carrying ring 1 is trapped between two annular wedges 5 and 6, in turn trapped between a strut supporting ring 3 and a clamping ring 2. The assembly clamps around a strut supporting hemisphere 4 and a reference hemisphere 12. When the clamping ring 2 is tightened against the strut supporting ring 3 it squeezes the wedges 5 and 6 inwards to increase their holding preload, and in turn retains all the moving parts under similar preload. In more detail, the strut carrying ring 1 has two inward sloping contact faces. The clamp down ring 2 has an inward sloping contact face. The strut supporting ring 3 has an extended cutaway flange to allow strut 1 to exit when the clamp down ring 2 is attached. It also has an inward sloping contact face. The articulating hemisphere 4 includes a conforming annular ball track with the reference hemisphere 7 about which it can then rotate on a common axis. The annular wedges 5 and 6 conform to the curvature of the hemispheres on their inward surface and have conforming outward sloping contact faces with the parts 1, 2 and 3. A shell 7 retains the reference hemisphere 12 via supports 8 and 9. Balls 10 run in an annular gothic arch profile track on the reference hemisphere 12, a complementary track being provided on the other hemisphere 4. Reference numeral 11 shows provision for one of the fasteners employed to retain and preload the clamp down ring 2 against the strut supporting ring 3. The invention having been described in the foregoing by reference to specific embodiments, it is to be appreciated that the embodiments are in all respects exemplary and that modifications and variations are possible without departure from the spirit and scope of the appended claims. For example, the multiple machine arrangement of Figs. 7A and 7B could be differently arranged and could utilize different machines and/or different machine combinations. Several similar or different machines could share a long single rail pair and be arranged to operate under a control program enabling the different modules to cooperate in the machining of the same workpiece or to work on different components. In a flexible facility, modules could be arranged to be movable between different rail systems to optimize on the current application need.

Claims: CLAIMS: 1. A machine comprising elongate struts that can be driven through machine nodes to vary the effective strut length, and wherein at least two struts share a bifurcated common node. 2. A machine as claimed in claim 1 constituting a hexapod structure. 3. A machine as claimed in claim 2 wherein said hexapod structure comprises six elongate struts defining with a sub-frame and a platform movable relative thereto six nodes, three of said nodes connecting alternate strut pair ends to the platform by means of multi-axis couplings and three of said nodes defined in said sub-frame comprising bifurcated common nodes retaining adjacent strut pairs such that the struts can pass through and cross over each other with pivotal movement about a common axis. 4. A machine as claimed in claim 3 wherein alternate strut pair ends couple to the platform with bifurcated multi-axis couplings. 5. A machine as claimed in claim 3 wherein the strut ends connect to the platform each by way of its own discrete multi-axis coupling. 6. A machine as claimed in any of the preceding claims wherein said bifurcated common nodes each comprise two hemispheres, one for each strut passing through the respective machine node, the two hemispheres being spherically arranged with respect to each other so as to be pivotable relative to each other about a common axis, and the spherical arrangement being retained in a complementary socket providing for multi-axis movement thereof. 7. A machine as claimed in claim 6 wherein each of said hemispheres comprises a strut drive motor. 8. A machine as claimed in claim 7 wherein the strut drive motor is adapted to drive the respective strut through the respective hemisphere by means of a friction drive. 9. A machine as claimed in claim 8 wherein said friction drive comprises opposite pairs of driven rollers frictionally engaging opposite sides of the respective strut. 10. A machine as claimed in claim 9 wherein said rollers are each coupled to larger diameter wheels which span the strut width and mutually contact each other in respective pairs, at least one such pair being driving by a pinion which is driven by the motor. 11. A machine as claimed in claim 10 wherein said pinion is coupled to a larger diameter wheel which is arranged to be driven by the motor by way of a pinion coupled to the motor drive shaft. 12. A machine as claimed in claim 10 or 11 wherein said wheels each retain an elastomeric band which in turn retains a flexible band, the arrangement being such that contact pressure between adjacent wheels or with a pinion flexes the outer band and compresses the elastomeric band. 13. A machine as claimed in any of claims 8 to 12 wherein said struts comprise elastomeric saddles on opposite sides thereof which each retain an elongate flexible rod to be contacted by said friction drive. 14. A machine as claimed in any of claims 6 to 13 wherein said struts are generally hemispherical or D-shaped in cross-section, and the two struts sharing a common node are arranged with their flat surfaces facing each other. 15. A machine as claimed in any of claims 3 to 14 wherein the three driven nodes are spaced apart by a generally triangular framework of adjustable members enabling the spacing of the nodes to be adjusted. 16. A machine as claimed in any of claims 6 to 15 wherein the three driven nodes are spaced apart by a generally triangular framework which is itself supported via at least two degree of freedom linkages to three pairs of adjustable length struts, said adjustable length struts being connected at their base ends with pivotable j oints in adj acent pairs . 17. A machine as claimed in claim 16 wherein said adjustable length struts each comprise two telescoping members with an internal air strut to act as a mass counterbalance and with powered clamping means at the telescoping interface. 18. A machine as claimed in any of claims 6 to 17 wherein the three ' driven nodes are supported in a generally vertical plane. 19. A machine as claimed in claim 18 wherein the three driven nodes are supported in a generally vertical plane by means of a cast or moulded body which has a generally horizontally extending point defining a support for a horizontal worktable. 20. A machine as claimed in claim 19 including a removable cover defining a wholly enclosed workspace with said cast or moulded body. 21. A machine comprising elongate struts that can be driven through machine nodes to vary the effective strut length, three of said struts being movably connected together at one end so as to define a first tool support movable in space in dependence upon the lengths of said three struts, and a further two of said struts being movably connected together at one end to define a second tool support movable in space in dependence upon the lengths of said two struts, and a tool supported between said first and second tool supports. 22. A machine as claimed in claim 21 wherein said nodes comprise spherical balls retained within complementary sockets permitting multi-directional pivotal movement of the balls. 23. A machine as claimed in claim 22 wherein said balls contain strut drive motors. 24. A machine as claimed in claim 23 wherein the struts are screw-threaded and the motors comprise driven members screw-threadedly engaged with the struts. 25. A machine as claimed in any of claims 21 to 24 wherein said first tool support is defined by a trifurcated coupling comprising a first strut supporting ring, a first annular wedge, a second strut supporting ring, a second annular wedge, and a retaining ring all fitted around a ball and arranged such that the annular wedges compress inwards and retain the ball and the other rings are spaced apart and supported by frusto-conical faces, the ball itself being bifurcated with one part constituting a retained base reference and another part being attached to a third strut and being joumalled with the said one part for pivotable movement relative thereto. 26. A machine comprising three adjustable length struts spaced apart and joumalled for multi-directional pivotal movement relative to a machine sub- frame at one end and movably connected together at their other ends so as to define a first tool support movable in free space in dependence upon the relative lengths of the three struts, and wherein a second tool support movable in free space is defined by the movably connected ends of two further adjustable length struts which at their other ends are spaced apart and joumalled for multi- directional pivotal movement relative to said sub-frame. 27. A machine as claimed in any of claims 21 to 26 wherein said machine sub- frame is substantially vertically oriented such that in a median position, said first and second tool supports are generally vertically arranged. 28. A machine as claimed in claim 27 wherein said machine sub-frame comprises a moulding or casting comprising a generally vertical part supporting said struts and a generally horizontal part defining a worktable, a cover being removably provided which, when in position, completely encloses said workspace. 29 - A friction drive motor for effecting relative longitudinal movement between the motor and an elongate member, said friction drive motor comprising opposite pairs of driven rollers frictionally engaging opposite sides of the elongate member, said opposed pairs of driven rollers being coupled to larger diameter wheels which frictionally engage with each other across the width of said elongate member.

Inventors: BAILEY RALPH PETER STEVEN, BAILEY, RALPH, PETER, STEVEN
Applicants: BAILEY RALPH PETER STEVEN, MAKEX LTD, BAILEY, RALPH, PETER, STEVEN, MAKEX LIMITED
Application year: 2001
Main classification: B23Q1
IPC codes: B23Q1, B23Q3, B23Q5, B23Q11, B25J11, B25J17, F16C11, F16H13, F16H19, F16H21, H02K7