Machine and method for cutting oval shapes

Abstract: A machine is provided for cutting oval shapes in planar workpieces, wherein the blade is dynamically oriented so as to maintain its cutting axis constantly tangent to the line of cutting. It utilizes a pivotably mounted cutter head (178) to which is attached an orienting arm (230) that is arcuately reciprocated by an element (124) moving unidirectiona­ ally in a circle, the direction of circular movement being opposite to that in which the cutting head proceeds.

Description: Sheets of cardboard mat, glass and other materials are frequently cut to provide components having openings and/or perimeters of circular or elliptical (generally referred to as "oval") configuration. Such components are widely used for mounting and framing of pictures and the like. Machines are known in the art, and are commercially available, for cutting planar workpieces to such shapes; exemplary is the device described in Pierce United States Patent No. 4,112,793, issued September 12, 1978. Although the device of the Pierce patent is highly effective for its intended purposes, it has an inherent drawback, attributable to the manner by which the cutting blade is mounted. As is true of virtually all machines of the kind described in the Pierce patent, the blade, supported to permit it to freely swivel, is positioned to trail slightly behind the axis of pivoting, thereby enabling it to seek an appropriate approach angle. This arrangement is disadvantageous for several reasons. Most significantly, such machines are not capable of cutting perfect ovals because the blade has a tendency to proceed in a straight line; the deviation from a true elliptical path is particularly noticeable when the minor axis of the shape is relatively small compared to its major axis. Secondly, the trailing blade tends to produce an oval that "leans"; that is, the major and minor axes are tilted slightly from those of a true Cartesian oval. Finally, such an arrangement results in indefiniteness in the starting and finishing points of the blade, often causing those points to be noncoincident, ultimately producing imperfections along the cut. It is recognized that at least certain of the foregoing deficiencies can be overcome by dynamically orienting the blade so as to maintain its cutting axis constantly tangent to the elliptical path that is generated. A commercially available device that is intended to operate in that general manner utilizes a control arm, attached to one end to a pivotable cutter head, which rotates about and follows, at its opposite end, an oblong cam. The mechanism does not however produce true tangency at all points of the oval, and it is unsatisfactory for other reasons as well; perhaps most notably, it employs no associated support, instead being positioned for use simply by fastening it to a base board through the workpiece itself. Accordingly, it is the broad object of the present invention to provide a novel combination, machine and method for cutting oval shapes in planar workpieces, which shapes are virtually free of distortion and of imperfections along the line of cutting. A more specific object is to provide such a combination, machine and method in which the cutting axis of the blade or wheel employed is dynamically oriented so as to maintain true tangency to the cut line or score at all points therealong. Another object of the invention is to provide a novel machine for cutting shapes in planar workpieces, which permits facile and effective clamping, and precise positioning, of the workpiece, and which permits accurate cutting of bevels from either the front or back of the workpiece, and convenient and accurate V-grooving thereof. Another more specific object is to provide a novel clamping system affording the foregoing benefits, which is, in addition, of relatively uncomplicated design and construction, which does not intrude into the cutting space, and which imposes no load on the cutting mechanisms or on the support structure therefor. An additional more specific object is to provide a novel cutting head and head assembly affording the foregoing benefits, which is, in addition, of relatively uncomplicated design and construction, and which is capable of readily disposing either of two blades in an optimal position for effective cutting of the workpiece. SUMMARY OF THE INVENTION It has now been found that certain of the foregoing and related objects of the invention are attained by the provision of a machine for cutting elliptical shapes as claimed in claim 1. Other objects of the invention are attained by the provision of a method for cutting an elliptical shape in a planar workpiece as claimed in claim 21. A machine embodying the invention for cutting in oval shape in a planar workpiece, can include a base having a flat upper surface for supporting a planar workpiece; mounting means for mounting a cutting element, having a cutting axis in general alignment with a first axis of the mounting means; means supporting the mounting means for pivotal movement about a second axis generally parallel to the centerline of the machine and generally perpendicular to the first axis; a first mechanism for moving the supporting means so as to move the mounting means along an oval path substantially in the indicated plane and concentric with the centerline of said machine; and an orientation control system. The first mechanism will include a mounting piece and an elongate arm member, the arm member having an outer end portion on which the supporting means is mounted, and having an inner end portion slidably mounted in the mounting piece for selectively variable extension therefrom, along the longitudinal axis thereof and in a plane spaced above and parallel to said first-mentioned plane. The orientation control system will comprise a hub, and means supporting the hub on the machine centerline for rotation thereabout. It will also include a first slide having opposite end portions, one of the end portions being mounted in the hub for selectively variable extension therefrom radially with respect to the centerline, and perpendicular thereto, and the other end portion projecting from the hub. A second slide will have one of its end portions mounted in the hub and parallel to the first slide, and its other end portion will have a coupling component on it, the "other" end portions of the first and second slides both projecting in the same direction from the hub. The control system will further include an elongate orienting arm having opposite end portions, one of the end portions being engaged with the mounting means and the other end portion being pivotably engaged with the coupling component of the second slide, the orienting arm being slidably engaged with either the mounting means or the coupling component. The machine will also include means for transmitting movement from the first mechanism to the first slide member, so as to effect rotation of the hub about the machine centerline. The means for transmitting will comprise cooperating components operatively connected to the mounting piece of the first mechanism and to the other end portion of the fist slide member, with the component connected to the mounting piece being of selectively variable position so as to enable it to follow a circular path about the centerline during operation of the first mechanism. As the supporting means moves along an oval path, the cutting axis of the mounting means will thereby be constantly maintained substantially tangent to it. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a fragmentary perspective view of a machine embodying the present invention; Figure 2 is a fragmentary plan view of the machine of Figure 1; Figure 3 is a fragmentary sectional view of the machine, taken along line 3-3 of Figure 2 and drawn to an enlarged scale; Figure 4 is a fragmentary, exploded perspective view showing features of the mechanism of the machine by which control of the path of movement and orientation of the cutting head are achieved; Figures 5A-5E are sequential schematic representations showing, in accordance with the invention, an orientation control arm for a cutting head at progressive positions during the cutting of one quadrant of an oval, and also showing geometric elements involved in producing the head orientation control; Figure 6 is a fragmentary sectional view, taken along line 6-6 of Figure 3 and drawn to an enlarged scale, showing the cutting head and its support structure, employed in the machine of Figures 1-4; Figure 7 is a perspective view of the cutting head, with the operating spool for one of the blades displaced from the supporting wall for clarity of illustration; Figure 8 is a fragmentary elevational view of the cutting head; Figure 9 is a fragmentary front elevational view of the clamping system employed in the machine of the invention; and Figure 10 is a fragmentary end elevational view thereof. DETAILED DESCRIPTION OF THE ILLUSTRATED EMBODIMENTS Turning now in detail to Figures 1-4 of the appended drawings, therein illustrated is a machine embodying the present invention and including a rectangular base board 10 yieldingly supported upon a pair of U-shaped runners 12, the base board being secured thereto by nut and bolt fasteners 16 (one of which is shown in Figure 3) with a small conical coil spring 18 interposed therebetween. A stand, generally designated by the numeral 14, is secured to the rear ends of the runners 12 by fasteners passing through flanges 20 at the lower ends of legs 22, and an overhead support arm, generally designated by the numeral 26, is bolted to the upper cross-piece 24 of the stand 14, to project forwardly therefrom over the base board 10. A slot 28 extends along the longitudinal axis of the arm 26 in the forward, free end portion thereof. Two parallel, rectilinear gibs 30 (normally made of a low-friction synthetic resinous material, such a Delrin) are secured to the upper surface of the arm at the opposite ends of the slot 28. The gibs have smooth inner surfaces, and one of them may be formed with oversized holes for receipt of the screws 32 with which it is held in place on the arm 26, so as to permit fine adjustment to attain strict perpendicularity to the axis of the slot 28. Although not illustrated, the upper surface of the arm 26, in the area between the gibs 30, will normally have a low-friction surface component thereon, such as may be provided by a suitably configured plastic covering washer. An upper disk, generally designated by the numeral 34, is disposed on the top surface of the arm 26 with its circumferential edge bearing upon the inside surfaces of the two gibs 30. It has a slot 36 therethrough formed along a diametric axis and extending essentially to one side of the center of the disk; a distance scale 38 is provided adjacent the slot 36. A center shaft assembly is rotatably and slidably received within the slot 28 of the arm 26, and includes a cylindrical core piece 40 carrying a cylindrical plastic bushing 42, dimensioned to span the slot 28 and to closely engage its lateral surfaces. A lower disk 44 is attached to the core piece 40 by a screw 46, with a plastic washer 45 interposed therebetween, and the components are affixed against relative rotation by pins 50. The upper end of the core piece 40 has a diametrically extending tongue element 52, the parallel side surfaces of which slidably engage the lateral surfaces of the slot 36 of the upper disk 34. Extending axially through the core piece 40 is a threaded bore 54, at the upper end of which is engaged the threaded shank 56 of a clamping knob 58, and at the lower end of which the screw 46 is engaged. A U-shaped clamping block 60 is disposed on top of the disk 34, and has a channel 62 extending through it within which the tongue element 52 of the core piece 40 is received. The operating handle, generally designated by the numeral 65, consists of a bar 64 with a knob 66 rotatably mounted on one end and with an aperture 68 through its opposite end, the latter receiving the shaft 56 of the clamping knob 58 (with a washer 57 interposed under the head), to thereby attach the handle to the center shaft assembly. The clamping block 60 mounts a laterally extending, transparent indicator piece 70, disposed over the scale 38 so as to permit setting of the center shaft assembly at any selected point along the length of the slot 36; the first line on the scale, nearest the center of the disk, lies at the geometric center thereof. It should be noted that the components are of suitable lengths and thicknesses to ensure that the upper disk 34 will be clamped between the block 60 and the core piece 40 when the knob 58 is tightened, to affix the center shaft assembly to the disk while leaving both free to move relative to the support arm 26. As will be appreciated by those skilled in the art, the mechanism hereinabove described employs the "Scottish yoke" principle, which is also embodied in the machine shown in the above identified Pierce United States Patent No. 4,112,793. It serves to permit generation of elliptical shapes, each with a major axis that varies from its minor axis by a dimension that is determined by the setting of the center shaft assembly relative to the center of the disk, at an "offset" value. To the extent that it may be helpful to an understanding of the form and operation of the Scottish yoke mechanism employed herein, the specification of the aforesaid said Pierce patent is incorporated hereinto by reference. An extruded metal housing, generally designated by the numeral 72, is secured (by screws, not shown) to the lower disk 44 of the center shaft assembly, and has a downwardly opening compound passageway 74 therethrough, which is configured to slidably mount a cutter arm, generally designated by the numeral 76, and a transmission slide, generally designated by the numeral 78. A distance scale 80 is provided along the length of the cutter arm 76, and a clamping screw 82 extends through the wall of the housing 72 and into the passageway 74; it cooperates with a shoe (not seen), which bears upon the side of the cutter arm 76 opposite to that on which the scale 80 is provided, so as to secure the arm in any selected position of extension. The transmission slide 78 is similarly engaged in selected positions of extension from the housing 72 by use of the locking screw 84. A pin 86, fixed adjacent one end of the slide 78, projects downwardly through the open bottom of the passageway into engagement in a circular socket 88 (normally lined with a bushing) formed into one end of a half slide 90; a half-dog set screw 94 is affixed to the opposite end of the slide 90, and a distance scale 92 extends longitudinally along one of its side surfaces. A hub assembly consisting of two identical pieces, each generally designed by the numeral 96, is disposed beneath the housing 72. Hub piece 96 consists of a circular base portion 98 providing a circumferential shoulder 100 thereabout, and a pair of projecting parallel walls 102 define a channel 104 between them. A cover plate 106 is secured over the channel 104 on the end faces of the walls 102 by four screws 108, and the plate is notched at 110 for a reason that will be clear from what follows. The hub pieces 96 are affixed to one another with the faces of the base portions 98 in confronting contact and with the channels 104 thereof in alignment; they are held together by screws (not shown) engaged within the apertures 112. The shoulders 100 cooperate to form a circumferential groove, by which the assembly is rotatably mounted in the circular opening 114 of an angular mounting bracket, generally designated by the numeral 116; it should be noted that the hub assembly is thereby positioned to rotate on its own axis, coincident with the centerline of the machine. The half-slide 90 is slidably engaged within the channel 104 of the uppermost hub piece 96, the half-dog set screw 94 carried thereby serving to limit outward extension and thereby to prevent inadvertent disassembly; as can be seen, the tip of the screw 94 is seated within the slot 118 formed into the inner surface of the disk portion 98. The mated hub piece 96 slidably engages an actuating full slide 120, which has a scale 122 along one lateral surface and which carries a depending pin 124 at its outer end. It should be noted that the actual distance between the integers (and the graduations) of the scales 38, 80 and 122, on the upper disk 34, the cutter arm 76, and the full slide 120, respectively, are the same, whereas the corresponding distances on the scale 92 of the half slide 90 are half those values. The distances shown on the scales 38, 92 and 122 are representative of the offset (in inches) that is to be produced; the distances shown on the scale 80 are representative of the minor diameter value that the oval is to have. The full slides 90 and 120 are held in selected positions by use of locking screws 84, which are threadably engaged within the walls 102 of the hub pieces 96. Secured to the underside of the supporting arm 26 are four rollers 126, which are circularly disposed at 90° angular intervals relative to the machine centerline. The rollers 126 engage within their circumferential grooves 128 the outer marginal edge of a support ring 130, for rotation under the arm 26. Two posts 132, separated by 120°, are attached to the ring 130, and they in turn support the angle bracket 116, the ends of the bracket arms 134 being provided with apertures for the receipt of screws 138 for that purpose. As previously noted, the support system is so constructed as to position the center of the circular opening 114 in the angle bracket 116 (and thereby the axis of rotation of the hub assembly) on the centerline of the machine (as so designated in the Figures). The centerline constitutes an axis extending normal to the parallel planes of the upper surfaces of the support arm 26 and the base board 10, at the intersection of the slot 28 with an imaginary medial line extending parallel to the confronting surfaces of the gibs 30, halfway therebetween. A pin 140 extends downwardly from the ring 130 at a point equidistantly spaced from the posts 132. Bracket 142, attached by screws 144 against the top wall of the housing 72, extends therefrom within a longitudinal channel 146 formed along the top of the cutter arm 76. The bracket 142 is slotted lengthwise to slidably receive the pin 140 that depends from the ring 130, as a result of which the ring is rotated by action of the cutter arm 76, so as to avoid interference between the arm and the posts 132 that support the bracket 116. With additional reference now to Figures 6-8, the cutter head assembly, mounted upon the free cutter end of the cutter bar 76, includes an F-shaped bracket, generally designated by the numeral 150. The laterally extending elements 152, 154 of the bracket are formed with vertically aligned openings 156, 158, within which are seated, respectively, a bushing 160 and a bearing sleeve 162. The bushing 160 has an upper flange portion 161, and the element 154 of the bracket has a circumferential lip portion 155 extending inwardly over the opening 158. A mounting post has an enlarged head portion 164 abutted against the bottom surface of the cutter arm 76, and is secured thereto by a screw 166 engaged within its threaded bore 167. The post has two reduced-diameter cylindrical bearing portions 168, 172, which serve to pivotably support the bracket 150, and a threaded intermediate portion 170 therebetween. The threaded portion 170 engages a knurled collar 174, which bears upon the bushing flange portion 161 and is turned to effect adjustment of the vertical position of the bracket 150 on the mounting post. The cutter head assembly is mounted upon the vertical leg portion 176 of the bracket 150, and includes a body having a lateral wall portion 178 and a base block 180. A medial channel 182 extends along the back surface of the wall portion 178, and slidably engages the leg portion 176 of the bracket to ensure proper orientation of the cutter head, the assembly being maintained by engagement of the screw 188 within the threaded aperture 189. The base block of the cutter head extends laterally from the wall portion 178 and has downwardly converging surfaces 190 on opposite sides thereof (which are slightly convergent outwardly, as well). Secured to each of the surfaces 190, by use of screws 192, is a guideplate 194, the inside surface of which is indented at 196 to define a channel in cooperation with the confronting surface 190. The plates 194 are confined by an outer wall portion 198 on the base block 180. A cutting blade 200 is slidably engaged within each of the slots 196, and has a sharpened bottom edge and an aperture 202 through the top end thereof. A set screw 204 extends through the plate 194 to bear upon the blade 190, creating (when properly adjusted) frictional resistance to help maintain the blade in any selected position within the channel 196, while permitting ready movement thereof when desired. Associated with each blade 200 is a positioning spool, generally designated by the numeral 206, and consisting of a circular base portion 208 and cylindrical barrel or handle portion 210. A passageway 212 extends through the spool, and receives a mounting screw 214, and threaded end of which is engaged in a threaded aperture 216 in the lateral wall portion 178 of the cutter head body. The passageway 212 includes an enlarged diameter outer section 212′, with a circumferential shoulder formed at the inner end thereof. One end of a coil spring 218 is seated upon the internal shoulder, and the opposite end thereof bears upon the head of the screw 214, thereby creating a biasing force of adjustable strength to displaceably maintain the spool against the wall portion 178. Adjacent the aperture 216 is a semi-circular slot 220, within which is engaged a short pin 222 extending from the inner face of the circular base portion 208 of the spool; this serves of course to limit rotation. A small pin or finger 226 extends radially from a tapered intermediate section 224 of the barrel portion 210, which is engaged within the aperture 202 in the top end of the associated blade 200. As will be self-evident, turning of the positioning spool will serve to raise and lower the coupled blade, to an extent limited by the corresponding slot 220, and the biasing force of the spring 218 will help to maintain it in position. It will be noted that the edge of the wall portion 178 has a scale 228 on each shoulder, which cooperates with the indicating line 231 on the circumference of the spool base portion to permit reproducible adjustment of the extent of projection of the blade 200 beyond the bottom face 296 of the head. An orientation control arm, generally designated by the numeral 230, is rigidly attached at one end (as by use of screws, not illustrated) to the underside of the lower bracket element 152, and extends laterally therefrom toward the center of the machine. A slot 232 is formed along most of the length of the arm 230, and engages the pin 124 that depends from the full slide 120. Centrally mounted at the rear of the base board 10 of the machine is a locking block 234, having a channel in which is slidably received the tail piece 236 of a T-bar. The tail piece 234 has a distance scale 240 extending longitudinally along an upper surface, and the locking block 236 has a thumb screw 242 extending through it for securing the tail piece, and thereby the crosspiece 238 attached to its forward end, in any selected position over the base board 10. An inverted, U-shaped clamping member 244 is disposed over the crosspiece 234, and is substantially coextensive therewith. Identical clamping mechanisms are provided at the opposite ends of the crosspiece and clamping member. Each consists of an L-shaped clamp head 246, having a nose portion 248 engaged under the base board 10 and a neck portion 250 seated within the space between the forward and rearward walls 252, 254 of the clamping member. Extending through aligned bores 256, 258 in the clamp head 246 and the crosspiece 234, respectively, and through an aperture 260 in the top wall 262 of the clamping member, is a rod 264 having a threaded lower end 266 and a transverse pin 268 through its upper end. An operating lever, generally designated by the numeral 270, is assembled with the rod 264, and includes a handle portion 272 and a head portion on which sidewalls 274 define external and internal arcuate bearing surfaces 276, 278; the opposite ends of the pin 268 are engaged within the sidewalls 274. A nut 280, having a knurled knob thereon, is threadably engaged on the end 266 of the rod 264, and is seated within the clamp head 246. Interposed between the top wall 262 of the clamping member 244 and the upper surface of the crosspiece 234 is a coil spring 282. A small pin 284 projects rearwardly from the crosspiece 234, and is engaged within a slot 286 formed through the back wall 254 of the clamping member. The front wall 254 thereof is formed with a rib 288 extending longitudinally therealong, the rib 288 having a flat upper surface upon which the arcuate surface 276 of the lever sidewall 274 bears; the internal arcuate surface 278 bears upon the top wall 262. As will be apparent, in preparation to cut a workpiece such as the mat sheet 290 shown in the drawings the T-bar is initially positioned in the locking block 234 so as to properly locate the mat on the base board 10 (the latter normally having a slip sheet or covering sheet 291 thereupon for optimal utility); the clamping member is provided with a distance scale 296 along its forward wall portion 252, to permit facile centering of the workpiece. With the clamping member 244 in its elevated position (as shown in the several Figures), a marginal portion of the mat 290 may be inserted beneath the lower edge 294 of the front wall portion 252 to abut against the forward face of the crosspiece 238. Elevating the handle portions 272 of the operating levers 270 will cause the underlying contacting surface (which may have a strip of high-friction and/or cushioning material applied thereto) of the clamping member 244 to be forced downwardly (by the action of the arcuate surfaces 276, 278 upon the cooperating elements), thereby causing the edge surface to tightly grip the marginal portion of the mat 290. Different thicknesses of workpieces can readily be accommodated by adjustment of the height of the clamping member 244. This is accomplished simply by tightening or loosening the nuts 280, thereby raising or lowering the clamping member, as necessary. To commence the cutting operation, the cutter arm 76 will be extended from the housing 272 a distance corresponding to the minor axis of the oval shape that is to be cut, utilizing the scale 80 thereon (which may be read directly to indicate the minor diameter). The knob 58 is loosened to permit shifting of the upper disk 34 (which would normally be done with the handle rotated 90° from the position shown in Figure 1, so as to align the slot 36 with the gibs 30) to establish the desired offset, utilizing the indicator 70 in cooperation with the scale 38 on the disk 34; the sum of twice the offset value plus the cutter arm extension reading will equal the value of the major diameter of the oval to be cut. The coupled transmission bar 78 and the half slide 90 are also extended from the housing 72 and the upper hub piece 96, respectively, to provide the same offset reading on the scale 92 as is indicated on the scale 38; the actuating slide 120 is extended from the lower hub piece 96 in which it is mounted, once again to provide the same offset reading on the scale 122. The knurled collar 174 is thereafter rotated so as to bring the bottom face 296 of the cutter head into sliding contact with the mat 290. Depending upon whether the mat is being cut from what is to be its front or its rear surface, one or the other of the blades 200 will then be extended as necessary to produce the desired degree of penetration, by turning of the associated spool 206. Moving the handle 65 (in a counterclockwise direction) will of course cause the disk 34 and the center shaft assembly to rotate in the same direction. Due to the constraints imposed by the gibs 30 however, the center shaft assembly will be forced to slide along the slot 28 in the upper support arm 26, while the disk migrates back and forth along an axis parallel to the faces of the gibs. This will superimpose the established offset distance upon the otherwise circular path of the cutter head 150, thereby causing it to circumscribe an oval. (As will be self-evident, if the center shaft assembly were positioned at the center of the disk 38 the resultant shape would be that of a circle, since no offset would be imposed.) As the center shaft rotates on its own axis, and simultaneously moves back and forth through the centerline of the machine, the geometry of the system (with the slides set as described) will cause the pin 86 on the transmission bar 78 to follow a circular path, in a clockwise direction (i.e., opposite to the direction of rotation of the disk 34). As a result, the hub assembly will rotate in the same direction within the center bracket 116, in turn causing the pin 124 to move clockwise and to circumscribe a circular path. Rotational movement of the pin 124 (following its circular path) within the slot 232 of the orientation bracket 230 will translate to a reciprocating pivotal action to the cutter head 150. Again due to geometric principles (which will be discussed hereinbelow), pivoting of the head under such control will constantly maintain the cutting axis of blade 200 in a relationship of true tangency to the oval path being followed, thereby producing a virtually perfect cut in the mat 290. To enable the pin 86 to move in a circle, in response to the compound movements of the center shaft assembly, it is necessary that the radius of the path circumscribed by the pin 86 (taken from the centerline of the machine) be exactly one-half the value of the offset distance set on the scale 38. To facilitate that, the actual distances between indicia on the scale 92 on the half slide 90 are one-half those that are provided between common indicia on the scale 38; thus, one need only set the cooperating parts at the same integer or graduation markings on the scales to achieve the required relationship. The distances on the scale 122 of the actuating slide 120 are the same as those on scale 38, to facilitate setting of the slide so as to enable the pin 124 to follow a path (about the centerline) having a radius equal to the offset distance, as is necessary to produce the required orientation control for the cutter head. As noted previously, the markings on the scale 80 denote minor diameter lengths, and so the actual distances between integers are half of the values indicated. The cutting head employed on the machine can readily be utilized for so-called "V-grooving" of mat board. To do so it is simply a matter of making a first cut with one of the blades in operative position, and thereafter making a second cut, along the same path, utilizing the other blade. As has been noted, the surfaces of the base portion against which the blades are mounted converge at an angle suitable to cause the blades to produce, by their cooperative action, a V-shaped cut. It might also be emphasized that the machine of the invention, and the underlying concepts, are equally applicable for cutting or scoring of workpieces other than mat board, such as glass; of course different forms of cutting heads, and elements, appropriate to the material of the workpiece, would be employed. Turning finally to Figures 5A-5E of the drawings, therein illustrated schematically and sequentially is the manner in which the cutter head orienting bracket moves, during the cutting of one quadrant of an oval, so as to maintain the cutter head in a relationship of precise tangency. They also illustrate the geometric principles underlying the invention. (It might be noted that the directions of movement are arbitrarily chosen to be opposite to those entailed in the machine embodiment hereinbefore described.) As the cutting head moves along an oval path "f," the locus of a point "C" on the axis of the cutter bar 76 (the bar axis being represented by the dash line "1" in these Figures) is a circle "c" generated in the direction opposite to that in which the cutter head proceeds. Orientation of the cutter bar is controlled by constraining points A and B (separated by the offset distance) on its axis to movement on perpendicular y and x axes through the point "O" at the center of the machine (and hence at the center of the oval shape "f" generated); point "A" corresponds to the rotational axis of the center support assembly of the machine, and point "B" may be considered to be an imaginary point on the axis of the cutter bar moving along an axis midway between the confronting jib surfaces. Since the pin 86 of the machine is positioned at point C, midway between points A and B, it generates the circle "c" having a radius equal to half the offset distance. In the Figures, the diameter of circle "a" corresponds to the minor diameter of the oval "f", and the radius of circle "b" equals the machine offset distance. Adding the diameter of circle "b" to the minor diameter circle "a" provides the major diameter of the oval, corresponding to the diameter of circle "d"; circle "e" is drawn to have the diameter of tangency, equal to the sum of the major and minor diameters. For example, setting the cutter bar to provide a six-inch minor diameter, and setting the upper disk to provide a two-inch offset, will produce an ellipse with a ten-inch major diameter. If the same offset value is set on the scales 92 and 127, the locus of pin 86 will be a two-inch diameter circle, and that of pin 124 will be a circle having a four-inch diameter. As can be seen, a line "2" drawn through point D on the offset radius circle "b", and point E on the tangency circle "e", will be perpendicular to a line of tangency "3" at all points on the oval "f". Consequently, disposing the arm 230 between the cutter head bracket 150 and the pin 124 (the latter corresponding to point D, at the offset distance and aligned on an axis "4" through the center point "O" and point "C") will impart the desired, always-tangent orientation to the axis of cutting of blade 200. It will be appreciated that the alignment of points "O", "C" and "D" on the axis "4" is produced in the machine by the relationships of the half and full slides 90, 120 in the hub assembly. Point "E" on the tangency circle "e" lies at the intersection of a line drawn parallel to the axis "1" of the cutter bar through the center point "O". The cutting blade 200 is located at the intersection of lines "6" and "7", drawn parallel to the y and x axes of the machine from points F and G, respectively; points "F" and "G" lie at the intersections of line 5 with minor and major diameter circles "a" and "d". Thus, it can be seen that the present invention provides a novel combination, machine and method for cutting oval shapes in planar workpieces, which shapes are virtually free of distortion and of imperfections along the line of cutting. The cutting axis of the blade or wheel employed is dynamically oriented so as to maintain true tangency to the cut or score line at all points therealong.

Claims: A machine for cutting elliptical shapes of readily variable major and minor axes in a planar workpiece, comprising the combination: mounting means (180) for mounting a cutting element (200) having a cutting axis in general alignment with a first axis of said mounting means; means (150, 168, 172) supporting said mounting means (180) for pivotal movement about a second axis generally perpendicular to said first axis; a first mechanism (30, 34, 40, 72) for moving said supporting means so as to move said mounting means along an elliptical path of readily variable major and minor axes in a plane substantially normal to said second axis and concentric with a centerline of the machine; CHARACTERIZED BY means for pivoting said supporting means about said second axis as said supporting means moves along said elliptical path, so as to constantly maintain said first axis substantially tangent to said path, said means for pivoting including a second mechanism (90, 96, 116, 120), adapted to move a component thereof along a circular path of readily variable diameter about said machine centerline, and coupling means comprising first (124) and second (230) components operatively attached to said second mechanism and said mounting means, respectively, said first and second components being operatively interconnected and adapted to translate unidirectional circular motion of said first component into reciprocating pivotal movement of said second component. The combination of Claim 1 wherein said paths lie in parallel planes, and including means (78, 86, 88) operatively interconnecting said first (30, 34, 40, 72) and second (90, 96, 116, 120) mechanisms, said interconnecting means being of such character that driving of said first mechanism, so as to move said mounting means (180) in one direction along said elliptical path, drives said second mechanism so as to move said first component (124) in the opposite direction along said circular path, said interconnecting means and mechanisms being so synchronized an to cause said mounting means (180) and first component (124) to traverse their respective paths at the same angular rate. The combination of Claim 2 wherein said first mechanism includes means (28, 40, 58) for selectively establishing the major and minor axes of said elliptical path, and wherein said second mechanism includes means (90, 96, 120) for selectively establishing the diameter of said circular path. The combination of Claim 3 wherein said means for establishing of said first mechanism includes first and second parts (34, 40) of variable relative positions, one of said parts (34) having a first scale (38) thereon with integers representative of the length differential between said major and minor axes of said elliptical path, and the other of parts (40) being positionable with reference to said first scale (38) to set a value to establish said differential; and wherein said means for establishing (90, 96, 120) of said second mechanism includes third and fourth parts (96, 120) of variable relative positions, one of said third and fourth parts (120) having a second distance scale (122) thereon, and the other of said third and fourth parts (96) being positionable with reference to said second scale to set a value to establish said diameter of said circular path. The combination of Claim 4, wherein said first and second scales (38, 122) have common integers thereon, the actual linear distance between consecutive common integers on both of said scales being the same. The combination of Claim 1 wherein said second component of said coupling means comprises an elongate orienting arm (230) having opposite end portions, one of said end portions being engaged with said mounting means; and wherein said first component comprises a coupling element (124) rotatably engaged with the other end portion of said orienting arm (230), said orienting arm being slidably engaged with one of said mounting means (180) and said coupling element (124). The combination of Claim 6 wherein said other end portion of said orienting arm (230) has a longitudinal slot (232) extending therealong, wherein said coupling element (124) is a pin received in said longitudinal slot, and wherein said one end portion of said orienting arm is rigidly attached to said mounting means (180). The combination of Claim 3 wherein said first mechanism includes a center shaft (40) that is rotatable about its own axis, and means (30, 34) for dynamically shifting said center shaft along a rectilinear axis perpendicular to said axis of said center shaft and extending through said centerline, said first mechanism means (28, 40, 58) for selectively establishing serving to limit the travel of said center shaft to selected distances from said centerline, said center shaft (40) being operatively connected to said supporting means (150, 160, 172) to effect such movement of said mounting means along said elliptical path; wherein said second mechanism includes a hub member (96) mounted for rotation on said centerline; and wherein said interconnecting means (78, 86, 88) includes a first component (88) operatively connected to said hub member (96) and adapted to receive force, for rotating said hub member, at selectively variable radial distances from said centerline, and a second component (86) operatively connected to said center shaft (40) and adapted to apply force at said first component (88) for effecting such rotation. The combination of Claim 3 wherein said means (28, 40, 58) for establishing of said first mechanism includes first and second parts parts of variable relative positions, one of said parts (34) having a first scale (38) thereon with integers representative of the length differential between said major and minor axes of said elliptical path, and the other of said parts (40) being positionable with reference to said first scale to set a value to establish said differential; and wherein said interconnecting means (78, 86, 88) includes third and fourth parts (90, 96) of variable relative positions, one of said third and fourth parts (90) having a second distance scale (92) thereon, and the other of said third and fourth parts (96) being positionable with reference to said second scale to set the value of said radial distance from said centerline, said first and second scales (38, 92) having common integers thereon, the actual linear distance between consecutive integers on said second scale being half that which exists between said common integers on said first scale. The combination of Claim 8 wherein said interconnecting means (78, 86, 88) comprises a body (72) attached to said center shaft (40) for rotation therewith, a first rectilinear slide member (78) slidably received within said body, and a second rectilinear slide member (90) slidably received within said hub member (96), said first and second slide members having said first and second components (86, 88) of said interconnecting means thereon and being pivotably interengaged thereby to enable the transmission of motion from said center shaft (40) to said hub member (96). The combination of Claim 10 additionally including an elongate cutter arm member (76) with opposite end portions, one of said end portions having said supporting means (150, 168, 172) mounted thereon, and the other of said end portions being slidably received within said body (72) of said interconnecting means. The combination of Claim 11 additionally including an elongate actuating arm member (120) with opposite end portions, one of said end portions having said first component (124) of said coupling means thereon, and the other of said end portions being slidably received within said hub member (96), said actuating arm member and said second slide member extending parallel to one another. The combination of Claim 1 additionally including a base (10) having a flat upper surface for supporting a planar workpiece; wherein said first mechanism includes a mounting piece (72) and an elongate arm member (76), said arm member having an outer end portion on which said supporting means (150, 168, 172) is mounted, and having an inner end portion slidably mounted in said mounting piece for selectively variable extension therefrom, along the longitudinal axis thereof and in a plane spaced above and parallel to said first-mentioned plane; and wherein said second mechanism includes an orientation control system, comprising: (1) a hub (96); (2) means (116) supporting said hub on said machine centerline for rotation thereabout; (3) a first slide (90) having opposite end portions, one of said end portions being mounted in said hub for selectively variable extension therefrom radially with respect to said centerline, and perpendicular thereto, with the other end portion projecting from said hub; (4) a second slide (120) having opposite end portions, one of said end portions being so mounted in said hub and parallel to said first slide, the other end portions of said first and second slides both projecting in the same direction from said hub; said coupling means including a coupling component (124) on said other end portion of said second slide, and an elongate orienting arm (230) having opposite end portions, one of said end portions being engaged with said mounting means and the other of said end portions being pivotably engaged with said coupling component of said second slide, said orienting arm being slidably engaged with one of said mounting means and said coupling component; said combination also including means for transmitting movement from said first mechanism to said first slide member so as to effect rotation of said hub about said machine centerline, said means for transmitting comprising cooperating components (78, 86, 88) operatively connected to said mounting piece of said first mechanism and to said other end portion of said first slide member, said component (78) connected to said mounting piece being of selectively variable position so as to enable it to follow a circular path about said centerline during operation of said first mechanism; whereby, as said supporting means moves along an elliptical path, said cutting axis of said mounting means may be constantly maintained substantially tangent to said path. The combination of Claim 13 wherein said means for transmitting further comprises a third slide (78), slidably mounted in said mounting piece for movement of said cooperating component (86) of said first mechanism along an axis parallel to said longitudinal axis of said arm member (76). The combination of Claim 13 wherein said first and second slides (90, 120) both have scales (90, 122) thereon for indicating the distance of extension thereof, said slide scales having indicia thereon in common, with the indicia on said first slide scale (90) being spaced half the actual distance of that of said common indicia on said second slide scale (122). The combination of Claim 13 which includes a frame (14) united with said base (10), and an overhead support member (26) on said frame and having a plate portion overlying said base (10) upper surface. The combination of Claim 16 wherein said plate portion has a rectilinear slot (28) therethrough traversing said machine centerline, and has constraining means (30) thereon for constraining a circular component disposed on said plate portion to rectilinear movement along an axis of reciprocation that is perpendicular to the axis of said slot (28) and that also traverses said centerline, said first mechanism additionally including: (1) a circular component (34) slidably disposed on said plate portion and movable along said axis of reciprocation under the constraint of said constraining means (30), said circular component (34) having an elongated slot (36) therethrough extending diametrically and traversing the center thereof; (2) a center shaft assembly including a shaft component (40) slidably engaged within said diametrical slot (36), and means (54, 58) for disengagably affixing said shaft assembly against movement relative to said circular component at selectively variable positions along the length thereof, said shaft component (40) also being slidably and rotatably engaged within said slot (28) of said plate portion, and being adapted to effect rotary motion of said circular component (34) and lineal motion thereof along said axis of reciprocation, when affixed thereto; and (3) driving means (65) for effecting rotation of said center shift assembly, said mounting piece (72) being operatively connected to said shaft assembly for movement therewith. The combination of Claim 17 wherein said driving means comprises a handle (65) with a bar (64) attached adjacent one end to said center shaft assembly, and having manual gripping means (66) adjacent the opposite end, said bar (64) having a longitudinal axis aligned with the longitudinal axis of said elongate arm member (76) and being disposed thereover, said one end of said bar being disposed to the same side of said shaft assembly as said outer end of said arm member. The combination of Claim 17 wherein said means for supporting said hub (96) comprises a bracket assembly (116) supported by said frame (14) to dispose said hub at a level between said overhead support member (26) and said base (10). The combination of Claim 19 wherein said bracket assembly (116) is rotatably mounted on said overlying plate portion of said frame (14) and is operatively engaged with said driving means (65) for rotation at the same angular rate as said elongate arm member (76), to avoid interference therewith of any component of said bracket assembly. A method for cutting an elliptical shape in a planar workpiece, comprising the steps: fixedly positioning a planar workpiece; moving a pivotably mounted cutting element (200), having a cutting axis, in a given direction along an elliptical path in a plane parallel to the plane of aid workpiece and about a central axis normal thereto, the axis of pivotable mounting of said element (200) being generally parallel to said central axis and perpendicular to said cutting axis; characterized by: moving, in the direction opposite to said given direction, a drive element (124) along a circular path concentric with and in a plane parallel to that of said elliptical path, said cutting and drive elements (200, 124) being moved by manual force at the same rate of angular speed; and translating, by mechanical means, the circular movement of said drive element (124) into reciprocating pivotal movement of said cutting element (200), about said axis of pivotable mounting, so as to constantly maintain said cutting axis substantially tangent to said elliptical path as said cutting element (200) moves therealong. The method of Claim 21 wherein said elliptical path has a major and a minor diameter, and wherein the diameter of said circular path is equal to the difference between said major and minor diameters.

Inventors: KOZYRSKI VINCENT T, PETERS ALAN R, KOZYRSKI, VINCENT T., PETERS, ALAN R.
Applicants: FLETCHER TERRY CO, THE FLETCHER-TERRY COMPANY
Application year: 1989
Main classification: B23Q27
IPC codes: B26D1, B23Q27, B26F1