CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority U.S. Patent App. No. 63/381,364, filed October 28, 2022, and U.S. Patent App. No. 18/468,408, filed September 15, 2023, each of which is incorporated by reference in its entirety.

BACKGROUND

[0002] In woodworking, it is generally necessary to prevent undesired workpiece movement when using a tool to remove material from the workpiece. In some cases, the workpiece may be guided against a fence or the like. In other cases, the workpiece must be completely immobilized, using clamps, vises, or the like.

[0003] Workholding devices designed to immobilize a workpiece can be grouped into four major categories. The descriptions below assume that the fixturing plate or surface is in the horizontal plane.

[0004] Top-thrusting holds: top-thrusting holds apply a downforce to the top of the workpiece, pressing it firmly against a fixturing plate or surface, and directly preventing the workpiece from lifting. Friction forces between the bottom of the workpiece and the fixturing surface prevent the workpiece from moving laterally. Examples include: C-clamps, F-clamps, pivot-type hold-down clamps, and hold-fasts. Advantages: top-thrusting holds are generally simple and reliable. Disadvantage: top-thrusting holds block tool access to a portion of the workpiece’s top surface and side surfaces. Top-thrusting holds generally protrude substantially above the top surface of the workpiece. This is a major problem for CNC routers in particular, as they can interfere with the machines’ working volume, and increase the risk of a tool crash.

[0005] Side-thrusting holds: side-thrusting holds restrain opposing sides of the workpiece, directly capturing the workpiece between holding-device surfaces. Friction forces between the sides of the workpiece and the holding-device surfaces restrain the workpiece from moving laterally or vertically. Examples include: vises, wedges, toe clamps, and pocket fixtures. Advantages: side-thrusting holds permit tool access to the entire top surface of the workpiece. Disadvantages: side-thrusting holds block tool access to a portion of the workpiece’s side surfaces. Side-thrusting holds generally consume substantial surface area outboard of the workpiece sides. Side-thrusting holds are incompatible with thin or flexible workpieces.

[0006] Bottom holds: bottom holds directly secure the bottom surface of workpieces to a fixturing surface. Examples include: adhesives (including double-sided tape) and vacuum tables. Advantages: bottom holds permit tool access to the entire top surface and side surfaces of the workpiece. Disadvantages: adhesive holds require extra time for setup and removal, and require consumable adhesive supplies. Vacuum holds are not suitable for small workpieces and are generally the most expensive workholding option.

[0007] Through holds: through holds are fasteners that penetrate the workpiece and secure it to the fixturing surface. Examples include: screws and composite nails. Advantages: through holds permit tool access to the entire side surfaces of the workpiece. Disadvantages: for many workpieces, holes for through fasteners are unacceptable. Through fasteners may block tool access to a portion of a workpiece’s top surface. With the exception of through screws that are precisely positioned to mate with threaded holes in a fixturing plate, through holds progressively damage the fixturing surface.

[0008] What is needed is a compact low profile edge clamp for securing workpieces, in conjunction with a T-nut and T-slot optimized for wooden surfaces, having fastener and slot geometries that enable far higher clamping forces.

SUMMARY

[0009] In one aspect, an edge clamp for use in clamping a workpiece to a fixturing plate is provided, wherein the workpiece includes a top surface and one or more side, the edge clamp comprising: a body having a top surface, wherein a clamp portion extends laterally from the body, and wherein a stabilizer portion extends downwardly from the body; an aperture extending through a thickness of the body from the top surface; wherein the clamp portion includes a lower surface having at least one clamp pad, and wherein the stabilizer portion includes a side surface having at least two registration surfaces separated by a stabilizer groove.

[0010] In another aspect, a fixturing system for use in clamping a workpiece to a fixturing plate is provided, wherein the workpiece includes a top surface and one or more side, the fixturing system comprising: an edge clamp, comprising: a body having a top surface, wherein a clamp portion extends laterally from the body, and wherein a stabilizer portion extends downwardly from the body; an aperture extending through a thickness of the body from the top surface; wherein the clamp portion includes a lower surface having at least one clamp pad, and wherein the stabilizer portion includes a side surface having at least two registration surfaces separated by a stabilizer groove; a structural element having an outer surface and inner surfaces defining a T-slot, wherein the T-slot has a central section that is open at the outer surface, and further has a pair of undercut sections projecting from opposite sides of the central section, and the inner surfaces of the structural element include a pair of inner surfaces facing inward across the pair of undercut sections of the T-slot; a T-nut having an outer portion receivable in the central section of the T- slot, a screw-threaded bore in the outer portion, and an inner portion with a pair of clamping surfaces projecting from opposite sides of the outer portion; and a threaded fastener extending through the aperture from the top surface and into the screw-threaded bore.

BRIEF DESCRIPTION OF THE FIGURES

[0011] The accompanying figures, which are incorporated in and constitute a part of the specification, illustrate various example systems and methods and are used merely to illustrate various example aspects. In the figures, like elements bear like reference numerals.

[0012] FIG. 1 illustrates a plan view of an example woodworking table 10 including at least one T-slot 19.

[0013] FIG. 2A illustrates a top plan view of a T-nut 30.

[0014] FIG. 2B illustrates an upper perspective view of T-nut 30.

[0015] FIG. 2C illustrates a side elevation view of T-nut 30.

[0016] FIG. 2D illustrates a front elevation view of T-nut 30.

[0017] FIG. 2E illustrates a bottom plan view of T-nut 30.

[0018] FIG. 2F illustrates a lower perspective view of T-nut 30.

[0019] FIG. 3A illustrates an upper perspective view of T-nut 30.

[0020] FIG. 3B illustrates an upper perspective view of a portion of woodworking table

10 including T-slot 19.

[0021] FIG. 3C illustrates an upper perspective view of a portion of woodworking table 10 including T-nut 30 engaged with T-slot 19.

[0022] FIG. 3D illustrates a front elevation view of T-nut 30.

[0023] FIG. 3E illustrates a front elevation view of a portion of woodworking table 10 including T-slot 19.

[0024] FIG. 3F illustrates a front elevation view of a portion of woodworking table 10 including T-nut 30 engaged with T-slot 19.

[0025] FIG. 4A illustrates an exploded view of a fixturing system 400 including a portion of woodworking table 10 including T-nut 30, a fixture 410, and T-slot 19.

[0026] FIG. 4B illustrates fixturing system 400 including a portion of woodworking table 10 including T-nut 30, a sectioned view of fixture 410, and T-slot 19.

[0027] FIG. 5A illustrates a free-body diagram of T-slot 19.

[0028] FIG. 5B illustrates another free-body diagram of T-slot 19.

[0029] FIG. 5C illustrates a free-body diagram of T-nut 30.

[0030] FIG. 5D illustrates a free-body diagram of a prior art T-slot.

[0031] FIG. 5E illustrates a free-body diagram of a prior art dovetail slot.

[0032] FIG. 5F illustrates a free-body diagram of a prior art dovetail slot. [0033] FIG. 6A illustrates an upper front perspective view of an edge clamp 600.

[0034] FIG. 6B illustrates a top plan view of edge clamp 600.

[0035] FIG. 6C illustrates an upper rear perspective view of edge clamp 600.

[0036] FIG. 6D illustrates a front elevation view of edge clamp 600.

[0037] FIG. 6E illustrates a side elevation view of edge clamp 600.

[0038] FIG. 6F illustrates a rear elevation view of edge clamp 600.

[0039] FIG. 6G illustrates a bottom plan view of edge clamp 600.

[0040] FIG. 6H illustrates a lower rear perspective view of edge clamp 600.

[0041] FIG. 61 illustrates a lower front perspective view of edge clamp 600.

[0042] FIG. 7A illustrates a plan view of a fixturing system 700 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600.

[0043] FIG. 7B illustrates a section view of fixturing system 700 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600.

[0044] FIG. 7C illustrates a side elevation view of fixturing system 700 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600.

[0045] FIG. 7D illustrates a rear elevation view of fixturing system 700 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600.

[0046] FIG. 7E illustrates an upper perspective view of fixturing system 700 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600.

[0047] FIG. 8A illustrates an upper perspective view of a fixturing system 800 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600.

[0048] FIG. 8B illustrates an upper perspective view of a fixturing system 800 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600.

DETAILED DESCRIPTION

[0049] Numerous T-slot router bits are commercially available for cutting T-slots directly into wood-based materials. However, the resulting slots are sized for use with conventional threaded fasteners that were designed for fastening metal parts and thus the slots are suitable for light clamping forces only. In the woodworking community, it is widely believed that prior art T- slots machined directly into wood-based materials are too fragile for general fixturing applications. Thus, a long-felt need exists for T-slots that are machined directly into wood-based materials and capable of applying the high clamping forces used in fixturing.

[0050] As shown in FIG. 1, an example of a structural element is provided in the configuration of a woodworking table 10. Woodworking table 10 may be a fixturing plate. In this embodiment, table 10 is formed of wood-based material such as, for example, natural wood or engineered materials including plywood, particle board, and fiberboard. Table 10 is formed from a non-metallic material. As shown in FIG. 1, table 10 in this example has a rectangular shape with opposite side edges 12 and opposite end edges 14. Table 10 has a planar top surface 16 and T-slots 19 that are open at top surface 16. In the illustrated embodiment, there are two parallel T-slots 19 reaching across the width of top surface 16 from one side edge 12 to an opposite side edge 12. T-slots 19 are open at the side edges 12. Two more parallel T-slots 19 reach along the length of top surface 16 from one end edge 14 to an opposite end edge 14, and are open at end edges 14. As shown, table 10 in the illustrated example does not contain metal T-tracks. Table 10 may include at least two T-slots 19 that intersect and/or cross one another.

[0051] FIGS. 2A-2F illustrate a T-nut 30 for engagement with the one or more T-slot 19. The woodworking system may include a plurality of T-nuts 30. Each T-nut 30 has the configuration shown in FIGS. 2A-2F. Each T-nut 30 has an upper portion or spine 40, and also has a lower portion 42 with clamping wings 43. Spine 40 has an elongated shape with opposite sides 44, opposite ends 46, and beveled comers 48. T-nut 30 has a planar top surface 50 on spine 40. T-nut 30 has a planar bottom surface 52 on lower portion 42. A screw-threaded bore 55 reaches vertically through at least a portion of a thickness of T-nut 30 from the center of top surface 50 to the center of bottom surface 52. Bore 55 has a nominal cross-sectional area for a screw-threaded shank on a fastener to be screwed into bore 55. Sockets 57 for anti-rotation pins also extend vertically through at least a portion of a thickness of T-nut 30.

[0052] Lower portion 42 of T-nut 30 also has an elongated shape with opposite sides 62, opposite ends 64, and beveled comers 66. A pair of clamping surfaces 72 on lower portion 42 of T-nut 30 project laterally away from opposite sides 44 of spine 40. Clamping surfaces 72 are oriented on an angle sloping downwardly from the direction of spine 40 to opposite sides 62 as further described below. Clamping surface 72 are equal in size, with each having a predetermined area.

[0053] FIGS. 3A-3F illustrate T-nut 30, and T-slot 19, separate from one another and engaged with one another. Each T-slot includes a central section 80 and a channel 82 beneath central section 80. Central section 80 is open at horizontal top surface 16 of table 10. Central section 80 corresponds to and is slightly larger than, spine 40. Channel 82 has a pair of undercut sections 84 reaching laterally from central section 80. Angled inner surfaces 90 of the table 10 face downward over undercut sections 84 of channel 82. Central section 80 is further laterally defined by inwardly directed faces 83 of T-slot overhangs 85. Overhangs 85 are arranged above, and defined by, undercut sections 84.

[0054] Each T-nut 30 is sized and shaped to fit within T-slot 19 as shown in FIGS. 3C and 3F. The width SW of spine 40 is slightly less than the width of the T-slot 19 at central section 80. The width of T-nut 30 at lower portion 42 is slightly less than the width of T-slot 19 at channel 82. The thickness of T-nut 30 between bottom surface 52 and clamping surfaces 72 is slightly less than the height of the T-slot 19 in undercut sections 84 of channel 82. In this configuration, T-nut 30 can be inserted into T-slot 19 through its open end for sliding movement to any desired position along the length of T-slot 19.

[0055] T-nut 30 has a pair of clamping surfaces 72 that are oriented at an angle WA relative to bottom surface 52. Clamping surfaces 72 are higher at their end near spine 40, and lower at their end near opposite sides 62. Angle WA may be between about 5 degrees and about 30 degrees. Angle WA may be between about 10 degrees and about 25 degrees. Angle WA may be between about 15 degrees and about 20 degrees. Angle WA may be about 18 degrees. Angle WA is the same as angle SA.

[0056] In considering angle WA, the static friction angle (also known as the “angle of friction”) is relevant. The static friction angle is the angle, relative to horizontal, of a planar surface at which an object placed thereon will begin to slide. The term “static friction angle” refers specifically to the friction of the T-nut material on the T-slot material. If p is the static coefficient of friction and cp is the static friction angle, then p = tan(cp). Angle WA must be small enough for clamping wings 43 to fit vertically within T-nut 30’ s height budget, while still leaving an adequate T-nut spine height SH above clamping wings 43. Angle WA must be less than or equal to the static friction angle, which ensures that clamping forces do not cause T-nut 30 to wedge open T-slot 19, and thus bend table 10 about the relatively thin section remaining beneath T-slot 19.

[0057] T-nut 30’ s spine 40 must not protrude above top surface 16 of table 10, as that space is reserved for the objects to be clamped (e.g., fixture 410). Thus the minimum height of inwardly directed faces 83 is equal to spine height SH. Inwardly directed faces 83 serve as linear guides for spine 40 and for various workholding accessories, and must have a minimum thickness that is adequate for this purpose. T-slot 19 may be milled deeper than the overall height of T-nut 30, in which case the thickness of inwardly directed faces 83 will be greater than the minimum. [0058] T-slot 19 has a pair of inner surfaces 90 that engage clamping surfaces 72, and that are oriented at an angle SA relative to a bottom surface of T-slot 19, which is parallel with top surface 16. Inner surfaces 90 are higher at their end near central section 80 and are lower at their laterally outer end. Angle SA may be between about 5 degrees and about 30 degrees. Angle SA may be between about 10 degrees and about 25 degrees. Angle SA may be between about 15 degrees and about 20 degrees. Angle SA may be about 18 degrees. Angle SA is the same as angle WA

[0059] A threaded fastener (e.g., threaded fastener 412) may engage threaded bore 55 to impart a force upon T-nut 30 when T-nut 30 is oriented in T-slot 19. The threaded fastener may be a 1/4” -20 threaded fastener, 5/16”- 18 threaded fastener, M6xl threaded fastener, such as a bolt, screw, or threaded rod. Optimally, the threaded fastener is compatible with standard workholding accessories used in woodworking.

[0060] T-nut 30 may have an overall height (including spine 40 and lower portion 42) that is small enough for mating with T-slot 19 machined within an 18 mm (0.7”) thick plywood, which is a material commonly used for constructing woodworking jigs and fixtures, while still leaving enough material thickness below T-slot 19 for the required bending stiffness.

[0061] Tables 10 are commonly made of a hardwood plywood, nominally 18 mm thick (although often marketed as %” thick). The height of T-slot 19, and thus the mating T-nut 30, is limited by the thickness of table 10. As T-slot 19 is milled deeper, the table section remaining beneath T-slot 19 becomes thinner. Given that the bending stiffness of the thin section is proportional to the cube of its thickness, it is important to keep T-slot 19 as shallow as possible.

[0062] Wood-based materials have relatively low strength properties, as compared to structural metals. When a woodworking table/fixturing plate is made of wood, it is therefore much more important to minimize the stresses that result from a given clamping force. With the geometry of T-slot 19, the bending moments and shear forces are highest at the roots of T-slot overhangs 85. Angling clamping surfaces 72 of clamping wings 43 increases the root thickness of the corresponding T-slot overhangs 85, which reduces the stresses at the roots without increasing the overall depth of T-slot 19. Angling clamping surfaces 72 of clamping wings 43 also increases the root thickness of clamping wings 43, thereby enabling T-nut 30 to be constructed of lower- strength materials, such as synthetic polymers.

[0063] Wing angle WA does not have to be large in order to provide a useful increase in clamping-force capability. A wing angle WA of only five degrees, for example, applied to clamping wings 43 that are 1/2” wide with a 1/8” tip thickness, increases the root thicknesses of both clamping wing 43 and T-slot overhang 85 by 0.044”, or 35%. This provides a 35% increase in shear strength, and an 82% increase in bending strength, of T-nut 30.

[0064] T-nut 30 may include an overall height that is large enough for accepting standard machine screw fastener lengths to mount fixtures of arbitrary thicknesses. The fastener must be long enough to pass through the fixture and engage threaded bore 55 sufficiently to retain T-nut 30 loosely for insertion into T-slot 19, but not so long that the threaded fastener extends beyond the bottom of T-nut 30 and jams into the bottom surface of T-slot 19 when tightened. Thus, T- nut 30 may have an overall height great enough to permit this length of fastener travel. To apply a full clamping force, the threaded fastener must have at least four full threads of engagement with T-nut 30. The minimum overall height of T-nut 30 may be equal to the commercially available machine screw length increment plus the minimum thread engagement distance (four full threads). [0065] In one embodiment, T-nut 30 includes an overall height based upon a 1/4” -20 threaded fastener, which is available in length increments of 1/8” (0.125”), and has a thread pitch of 0.05”, giving a minimum overall height of T-nut 30 equal to 0.125” + 4(0.05”) = 0.325”.

[0066] In another embodiment, T-nut 30 includes an overall height based upon a M6xl threaded fastener, which is available in length increments of 5 mm, and has a thread pitch of 1 mm, giving a minimum overall height of T-nut 30 equal to 5 mm + 4(1 mm) = 9 mm (0.354”).

[0067] In another embodiment, T-nut 30 has an overall height of 9.5 mm (0.375”) to accommodate tolerance variations.

[0068] T-nut 30 may include a spine width SW that is wide enough to house a threaded hole or threaded insert for the chosen fastener diameter(s), with sufficient structural material remaining on each side of the hole or fastener to withstand the longitudinal bending moments induced by the clamp-screw force. In one embodiment, spine width SW is designed to accommodate a 5/16” outside diameter threaded insert; T-nut 30 may be formed from a glass-fiber reinforced thermoplastic; and spine width SW may be at least about 1/2” wide. Spine width SW may be limited to about 1/2” wide in this embodiment to minimize the overall width of T-nut 30 and T-slot 19 (minimizing the width of T-slot 19 may minimize T-slot 19’ s effect upon the strength of table 10).

[0069] In one embodiment, the maximum rated clamp load of 1/4” -20 ASTM A307 Grade A machine screw is 859 lb. Certain domestic hardwoods have compressive strengths approaching 2000 psi. Pecan wood, for example, has a compressive strength perpendicular to the grain of 1720 psi (see Wood handbook — Wood as an engineering material, Chapter 4, Mechanical Properties of Wood. U.S. Department of Agriculture, Forest Service, Forest Products Laboratory). To limit the surface pressure to less than 1720 psi at the rated machine-screw clamping force of 859 lb., the minimum clamping area is 859 lb. / 1720 psi = 0.5 in ² . This is approximately ten times the nominal cross-sectional area of a 1/4” threaded fastener, or synonymously, is a clamping-area ratio of 10: 1. To minimize the size of T-nut 30, a nominal clamping area of 0.5 in ² may be selected. When used in wood materials having lower compressive strengths, the applied threaded fastener screw torque and force can be reduced accordingly. In one embodiment, as a compromise between minimizing overall length and overall width, and to roughly equalize lateral and longitudinal stresses under load, T-nut 30 may have a length:width aspect ratio of 1 : 1.

[0070] The total clamping surface area (that is, the area of clamping surfaces 72 of clamping wings 43 that contacts inner surfaces 90 of T-slot overhangs 85) must be large enough that the surface pressure generated by the threaded fastener’s screw force is less than the compressive strength of the wooden T-slot material. The maximum threaded fastener screw force is roughly proportional to the nominal cross-sectional area of the threaded fastener (e.g., fastener 412)

[0071] T-nut 30 may include an overall length (that is, the distance between opposite ends 64) and an overall width (that is, the distance between opposite sides 62), each of which may be minimized to the extent practical. To minimize the required spacing between T-nuts 30 in the same T-slot 19, the overall length of T-nut 30 should be minimized to the extent practical.

[0072] Thus for a given T-slot 19 material, the required clamping surface area is also roughly proportional to the nominal cross-sectional area of the threaded fastener. The total clamping area = (T-nut 30 overall length) x (T-nut 30 overall width - spine width SW). For a T- nut 30 having a length:width aspect ratio of 1 : 1 and a spine width SW of 1/2”, the clamping surface area is 0.5 in ² . Where N = overall length of T-nut 30, then 0.5 in ² = N x (N - 1/2”). N ² - 0.5N - 0.5 = 0. Applying the quadratic equation, N = { 1, -0.5}. As a result, and because the length and width dimension N must have a positive value, T-nut 30’ s overall width and overall length is 1”, which is equal to four times the diameter of the threaded fastener (e.g., fastener 412). Each clamping wing 43 then has a nominal width of (1” - 1/2”) / 2 = 1/4”, which is equal to the diameter of the threaded fastener.

[0073] FIGS. 4A and 4B illustrate a fixturing system 400 including a portion of woodworking table 10 including T-nut 30, a fixture 410, and T-slot 19. T-nut 30 and wooden T- slot 19 include geometries optimized specifically for wood-based fixturing slot materials. A threaded fastener 412 passes through a fixture 410, via an aperture 414, and into bore 55 of T-nut 30. When tightened, threaded fastener 412 engaging threaded bore 55 forces clamping surfaces 72 of clamping wings 43 against inner surfaces 90 of T-slot overhangs 85, immobilizing fixture 410. Additionally, when tightened, threaded fastener 412 engaging threaded bore 55 forces fixture 410 downwardly into contact with top surface 16 of table 10, further ensuring the immobilization of fixture 410 relative to table 10.

[0074] Spine 40 of T-nut 30 fits slidably into central section 80 of T-slot 19 between inwardly directed faces 83. Spine 40 provides structural rigidity to T-nut 30, positive lateral positioning relative to table 10, a threaded bore 55 for fastener 412, and sockets 57 for anti-rotation pins 416.

[0075] One or more anti-rotation pin 416 may extend between one or more T-nut socket 57 and one or more fixture socket 418. One or more anti-rotation pin 416 is configured to eliminate rotation between T-nut 30 and fixture 410. Anti-rotation pin 416 may be an unthreaded dowel pin configured to be fastened or captured into one or more T-nut socket 57 and one or more fixture socket 418, parallel to fastener 412’ s longitudinal axis, and free to slide in one or both of T-nut socket 57 and fixture socket 418.

[0076] In practice, T-nut 30 is attached to fixture 410 loosely, but with engagement of one or more anti-rotation pin 416 in both one or more T-nut socket 57 and one or more fixture socket 418. Anti-rotation pin(s) 416 act as linear guide(s) for T-nut 30 as fastener 412 rotates and causes T-nut 30 to move toward or away from fixture 410. As such, T-nut 30 when oriented on the bottom of fixture 410 is simple to align with T-slot 19 by a user whose vantage point is above fixture 410. Where fixture 410 includes multiple T-nuts 30, as is common for larger fixtures 410, anti-rotation pin(s) 416 keep T-nuts 30 oriented in the same direction, parallel to T-slots 19, thus making the simultaneous sliding of multiple T-nuts 30 into multiple T-slots 19 quite easy. If T- nuts 30 were permitted to rotate, keeping multiple T-nuts 30 aligned for insertion into multiple T- slots 19 is often complicated and difficult. Once fixture 410 is placed where desired relative to table 10, with engagement of each T-nut 30 with the appropriate T-slots 19, fastener 412 is tightened to cause clamping surfaces 72 of clamping wings 43 to engage with inner surfaces 90 of T-slot overhangs 85, immobilizing fixture 410.

[0077] Prior art T-nuts, as well as other fasteners commonly used in T-slots, have no antirotation pins and thus no means of orientation control until captured by a T-slot. As a practical matter, this means that the person installing a fixture must hold the fixture with one hand, while reaching beneath it with the other hand, typically blindly, to orient the T-nut or fastener head for insertion into the T-slot. For fixtures with a single T-nut or fastener, this procedure is unnecessarily slow and awkward. Larger fixtures, however, may have four or more T-nuts or fasteners, typically with pairs of T-nuts/fasteners needing to enter parallel T-slots simultaneously. For such fixtures, positive T-nut orientation control dramatically increases the speed and ease of fixture installation. [0078] FIG. 5A is a free-body diagram of T-slot 19 illustrating the forces and moments imparted into table 10 during clamping of a fixture (not shown). T-slot 19 includes inner surfaces 90 oriented at an angle SA equal to 18 degrees. A force of 0.5 Fc is directed downward onto top surface 16 by a fixture (not shown), which is counteracted by a force of 0.5 Fc directed upward onto inner surface 90 by a clamping wing (not shown). The clamping wing (not shown) also imparts a force of 0.16 Fc laterally onto inner surface 90, which is counteracted by a force 0.16 Fc laterally within the thin section remaining beneath T-slot 19. Finally, the clamping wing (not shown) imparts a moment equal to 0.16d Fc within the thin section remaining beneath T-slot 19, where d is the vertical distance from the center of the thin section to the center of pressure of the clamping wing.

[0079] FIG. 5B is a free-body diagram of T-slot 19 illustrating the forces and moments imparted into T-slot overhang 85 during clamping of a fixture (not shown). Table 10 is considered to be non-rigid for this analysis, thus the free-body diagram represents a single T-slot overhang 85, to which 1/2 of the clamping force Fc is applied. Forces FN and Ff are the normal force and the friction force, respectively, applied by T-nut clamping wing 43.

[0080] Derivation of the clamping wing wedging-threshold angle 0\v includes:

1) F _X = F _N sin(6) - F _f cos(6) = 0;

2) Ff = p • FN {at the onset of sliding};

3) FN sin(9w) = p • FN COS(9W);

4) p = sin(9w) / cos(9w) = tan(0w);

5) tan(cp) = tan(9w); and

6) 0w = cp.

[0081] When the clamping wing angle WA is less than the friction angle, friction forces proportional to the clamping force oppose any sliding of the clamping wings 43 on T-slot overhangs 85. T-nut 30 then functions as a brace that ties together the opposing T-slot overhangs 85, stiffening table 10 in bending about T-slot 19. Stated differently, T-nut 30 acts to tie T-slot overhangs 85 rigidly together, rather than to spread them apart from one another.

[0082] FIG. 5C is a free-body diagram of T-nut 30. Wing angle WA must be less than, or equal to, the complement of the static friction angle. This ensures that T-nut 30 will always self-release when the clamping-screw force is removed from T-nut 30. That is, T-nut 30 will not become jammed in T-slot 19.

[0083] As illustrated in FIG. 5C, a free-body diagram depicts the forces acting on T-nut 30, just after the clamp screw force has been removed. FN and Ff are the normal forces and the friction forces, respectively, applied by T-slot overhang 85. Due to the symmetry of T-nut 30 and T-slot 19, the vector magnitudes are equal on each clamping wing 43.

[0084] Derivation of the clamping wing self-releasing threshold angles \|/SR and 0SR includes:

2) Ff = p • FN {at the onset of sliding};

3) p • F _N COS(\|/SR) = FN sin(ysR);

4) p = sin(ysR) / COS(\|/SR) = tan(ysR);

5) tan(cp) = tan(ysR);

6) ysR = cp;

7) 0SR = 90° - \|/SR = 90° - cp.

[0085] The clamping-wing angle WA must be large enough to create strong profile sections in both the clamping wings 43 and the T-slot overhangs 85. Given that both T-nuts 30 and T-slots 19 are made from materials that are much weaker than steel, the right-angle profiles of conventional metal T-nuts are very suboptimal. Applying a downward angle to clamping surfaces 72 of clamping wings 43, however, creates a tapered cross-section both in clamping wings 43 and in T-slot overhangs 85. This increases the root thickness of both structural elements, thereby greatly increasing their clamping-load capacity, without increasing the overall height of T-nut 30 or T-slot 19.

[0086] In one embodiment, T-slot overhang 85 includes a minimum thickness of inwardly directed faces 83, and thus a T-nut spine height SH above clamping wings 43, of 1/8”. The measured static friction angle of the chosen reinforced-plastic T-nut 30 material on hardwood ranges from approximately 18 degrees to 20 degrees. An 18 degree friction angle corresponds to a minimum coefficient of friction of p = Tan(l 8 degrees) = 0.32. The complement of the measured friction angle ranges from 70 degrees to 72 degrees. An 18 degree clamping angle (angles WA and SA) satisfies both friction-angle requirements, creates adequately strong profile sections, and consumes only 0.25” * tan(18°) = 0.081” of the T-nut 30’ s height budget. This leaves 0.375” - 0.125” - 0.081” = 0.169” of the T-nut 30’ s height budget for fillets at the roots of clamping wings 43 and T-slot overhangs 85. These fillets reduce the stress concentrations at the interior comers, and thus enable higher clamping forces. As an 18 degree clamping-wing angle WA is approximately equal to the static friction angle, it will only brace T-slot 19 to a small degree. If a greater bracing effect is desired, however, a high-friction texture may be molded into T-nut 30’ s clamping surfaces 72, thereby increasing the coefficient of friction and the static friction angle without increasing T-nut 30’s production cost. [0087] In the free-body diagrams described below with respect to FIGS. 5D-5F, fixturing- plate sections are shown for prior-art designs. The thin section of the fixturing plate/woodworking table is considered non-rigid for this analysis, so each free-body diagram shows a single fixturing- slot overhang, to which 1/2 of the clamping force Fc is applied (physically, by the object being clamped). Arrows represent the force vectors acting on the fixturing-slot overhang, as well as any resulting internal force and bending moment at the center of the fixturing plate’s thin section. For simplicity, friction forces are neglected in these free-body diagrams.

[0088] The sum of the Y-axis forces must equal zero. Thus FY — 'A Fc. Fx — FN sin(9); FY = FN COS(9); => FX/FY = tan(9); where FN is the force normal to the clamping surface. Fx = FY • tan(0) = ’A tan(0) Fc. The sum of the moments about the center of the thin section must equal zero. Thus MH = d • Fx = ’A d • tan(0) Fc, where d is the vertical distance from the center of the thin section to the center of pressure of the clamping wing.

[0089] FIG. 5D is a free-body diagram of a prior art T-slot. This prior art T-slot includes a 0 degree clamping angle, which is consistent with standard machine tool T-slots, but is a poor choice for use in wooden fixturing plates/woodworking tables. The clamping area ratios of standard machine-tool T-slot nuts range from 1.8: 1 to 4.3: 1. These nuts are intended for use in metal T-slots, where larger surface areas are not required.

[0090] FIG. 5E is a free-body diagram of a prior art dovetail slot. This prior art fixturing slot includes a 45 degree clamping angle. This high degree clamping angle will act to spread fixturing slot overhangs apart, resulting in a large bending moment in the thin section remaining beneath the fixturing slot, and large lateral forces that may exceed the strength of a wood-based fixturing slot.

[0091] FIG. 5F is a free-body diagram of a prior art dovetail slot. This prior art fixturing slot includes a 76 degree clamping angle. This high degree clamping angle will act to spread fixturing slot overhangs apart, resulting in a large bending moment in the thin section remaining beneath the fixturing slot, and large lateral forces that may exceed the strength of a wood-based fixturing slot. This high degree clamping angle yields lateral forces on the fixturing slot that are up to four times greater than the clamping force. This high degree clamping angle may also cause the nuts to jam in the fixturing slot, requiring significant force to remove it from the fixturing slot. [0092] The steep clamping-wing angles used in the above prior-art examples have serious shortcomings when used with relatively thin woodworking tables/fixturing plates made of woodbased materials. Most critically, steep clamping-surface angles create a strong wedging effect, which tends to spread open the top of the fixturing slot when clamping forces are applied. Because the fixturing slot depth is typically about half the thickness of a 3/4” (or an 18 mm) thick fixturing plate, the fixturing plate’ s thin-section bending stiffness is reduced by a factor of about eight. Any net bending moment resulting from applying a clamping force to the fixturing-slot nut will bow the thin section.

[0093] Example 1 - Wedging of Nut and Bowing of Fixture Plate:

[0094] Tests were conducted to identify wedging of the nut within the slot and bowing of the fixture plate. A 2” x 2” x 18 mm Baltic birch plywood pressure pad was clamped to fixturing slots milled into wooden test specimens. The pad had a central 1/4” clearance hole for threaded fasteners. To reduce fixture-friction effects, UHMW polyethylene tape was bonded to the bottom of the pad. The pressure pad was then clamped to the test specimen using a 1/4” -20 threaded fastener and a 1-1/8” diameter x 1/8” thick load-distribution washer. The test specimen was placed in a fixture that constrained its motion in the horizontal plane only.

[0095] The test specimens were formed from Baltic birch plywood having 13 plies. The test specimens were 6” long and 3” wide. The face-grain orientation was lateral. The slot orientation was lateral. The slot position was centered on the specimen.

[0096] Table 1. Wedging and Bowing Test Data

[0097] As illustrated, nuts with wing angles of 45 degrees, 18 degrees, and 76 degrees were tested. A torque of 40 in. -lb. was applied to the 1/4” -20 threaded fastener, resulting in a clamping force of approximately 880 lbs. As illustrated, the nut (T-nut 30) having an 18 degree wing angle exhibited about 1/5 of the measured bow of the 45 degree and 76 degree wing angle nuts. The 18 degree wing angle nut exhibited about 1/4 of the stiffness adjusted bow as the 45 degree wing angle nut, and about 1/14 of the stiffness adjusted bow as the 76 degree wing angle nut. Finally, the 76 degree wing angle nut was jammed within its fixturing slot, requiring about 85 lbs. of force to dislodge it.

[0098] FIGS. 6A-6I illustrate an edge clamp 600. Edge clamp 600 includes a body 602 from which a clamp portion 604 extends laterally, and from which a stabilizer portion 606 extends downwardly. Edge clamp 600 includes a vertical aperture 608 extending completely through the thickness of body 602. Aperture 608 may include a chamfered edge 609. Edge clamp 600 may include one or more finger lobe 610 extending from the rear of body 602. [0099] Edge clamp 600 includes at least one clamp pad 612 on the lower surface of clamp portion 604, opposite the top surface 603 of body 602. Edge clamp 600 may include two clamp pads 612 separated by a recess 614.

[00100] Edge clamp 600 includes two registration surfaces 616 on a side surface of stabilizer portion 606, opposite the rear of edge clamp 600. Edge clamp 600 includes a stabilizer groove 618 between the two registration surfaces 616. Stabilizer groove 618 may include a segment of a cylindrical bore that is coaxial with aperture 608.

[00101] FIGS. 7A-7E illustrate a fixturing system 700 including woodworking table 10 with a T-nut 30 and T-slot 19, and a workpiece 728 secured using edge clamp 600. System 700 may include a plurality of edge clamps 600, positioned on multiple sides of workpiece 728.

[00102] A threaded fastener 720 extends through aperture 608 into screw-threaded bore 55 of T-nut 30. Threaded fastener 720 includes a head 722, a shank 724, and threads 726. Threaded fastener 720 may be a flat head machine screw. Head 722 may contact and engage chamfered edge 609. Shank 724 may be oriented in stabilizer groove 618. Threads 726 may engage bore 55. Shank 724 may have a smooth surface. Shank 724 may have a threaded surface. Shank 724 may have a textured surface.

[00103] Workpiece 728 includes a top surface 730 and one or more side 732. Workpiece 728 may be used as a fixture (including, for example, fixture 410). Edge clamp 600’ s one or more clamp pad 612 engages top surface 730. In one aspect, edge clamp 600’ s registration surfaces 616 may contact and engage side 732. In another aspect, edge clamp 600’ s registration surfaces 616 contact and engage side 732.

[00104] In one aspect, fastener 720 may contact and engage side 732. In another aspect, fastener 720 contacts and engages side 732. Shank 724 may be the portion of fastener 720 contacting side 732.

[00105] As illustrated most clearly in FIG. 7B, which is a sectional view taken about line A-A in FIG. 7A, a portion of head 722 overlaps side 732 and extends at least partially over top surface 730.

[00106] FIGS. 8A and 8B illustrate a fixturing system 800 including woodworking table 10 with a T-nut 30 and T-slot 19, and workpiece 728 secured using edge clamp 600. FIG. 8A illustrates use of edge clamp 600 to clamp a rabbet joint. FIG. 8B illustrates use of edge clamp 600 to clamp a slot.

[00107] Edge clamp 600 is a diminutive top-thrusting workholding clamp. It is optimized for the workholding requirements of CNC routers, and for use with T-slot 19 and T-nut 30. When used in fixturing system 700, 800, edge clamp 600 maximizes workpiece (e.g., workpiece 728) positioning versatility by enabling edge clamp 600 to be placed anywhere along the length of T- slot 19. Edge clamp 600 is compatible with a wide range of workpiece thicknesses by simply using a threaded fastener 720 of the appropriate length. Edge clamp 600 maintains an ultra-low clamp profile relative to the top surface 730 of the workpiece, to minimize potential interference with tooling. Edge clamp 600 minimizes the clamp’s footprint inboard of side 732, to maximize the machinable area of the workpiece’s top surface. Edge clamp 600 minimizes the clamp’s footprint outboard of sides 732, to maximize the size of workpiece that can be mounted on a given fixturing plate (e.g., woodworking table 10), and to maximize the fixturing density of multiple small workpieces. Edge clamp 600 maximizes the available downforce on the workpiece to maximize the friction forces that prevent the workpiece from moving laterally. Edge clamp 600 applies only compressive forces to the fixturing plate material, to eliminate the potential of fixturing slot (e.g., T-slot 19) pull-out or tear-out.

[00108] T-slots 19 can be configured as a two-dimensional grid on table 10. As edge clamp 600 can be positioned anywhere along T-slot 19, fastener 720 can be positioned arbitrarily close to, and even in contact with, side 732 of workpiece 728. If centered on a T-slot 19 intersection, even very small workpieces 728 can be clamped on four sides.

[00109] Due to the greatly reduced clamp reach requirements, fastener 720 also serves as edge clamp 600’ s structural frame. Fastener 720 is free to rotate within the edge clamp 600, but shank 724 prevents head 722 from tilting when clamping forces are applied. The anti-tilting function works as the result of stabilizer groove 618 bearing on shank 724.

[00110] Because the edge clamp 600’ s tilting moment resulting from forces on clamp pad 612 is always in the same direction, the side of the aperture 608 nearest workpiece 728 can be slotted open, leaving zero clearance between the fastener 720 and workpiece 728. What remains of aperture 608 is stabilizer groove 618 that bears on the side of shank 724 opposite workpiece 728, and opposes the tilting moment resulting from clamp pad 612 forces.

[00111] Unlike a full cylindrical bore, the open stabilizer groove 618 allows fastener 720 to be placed in direct contact with side 732 of workpiece 728. This minimizes the distance from the center of pressure of clamp pad(s) 612 to fastener 720’ s axis of rotation, which in turn minimizes the tilting moment applied to fastener 720.

[00112] Because fastener 720 is positioned directly against workpiece 728, almost half the length of T-nut 30 is beneath workpiece 728. The T-slot 19 material is captured between workpiece 728 and T-nut 30, and thus T-slot 19 material receives an almost entirely compressive load. This makes inexpensive MDF (medium density fiberboard) an acceptable material for sacrificial fixturing plates (aka spoilboards or wasteboards) (e.g., table 10), even though MDF has a relatively poor internal bond strength (typically about 130 psi).

[00113] As illustrated in FIGS. 8A and 8B, if rabbets or slots for receiving clamp portion 604 are milled into the sides of workpiece 728, the entire clamp may be located beneath the top surface of the workpiece.

[00114] The total surface area chosen for clamp pads 612 is a compromise between surface pressure on workpiece 728 and the overall size of edge clamp 600. In one aspect, the surface area of clamp pads 612 may be about 0.15 in ² . At a clamping force of 100 lb. per edge clamp 600, for example, this chosen surface area will generate a surface pressure of 666 lb. /in ² , which is well within the rated compression strength of most hardwoods.

[00115] In one aspect, partially threaded fasteners 720 are used, such that stabilizer groove 618 bears on a smooth cylindrical shank 724. Even with the clamp geometry optimized to minimize the tilting moment on edge clamp 600, the pressure between the fastener 720 and the molded-plastic stabilizer groove 618 can be enough to impress thread marks into stabilizer groove 618, and thus cause edge clamp 600 misalignment.

[00116] Given that edge clamp 600 is free to rotate about fastener 720, anti-rotation features are needed to prevent edge clamp 600 from rotating while tightening fastener 720. Edge clamp 600 incorporates several complementary anti-rotation features.

[00117] When positioning edge clamp 600, registration surfaces 616 located on each side of stabilizer groove 618 are pressed against side 732 of workpiece 728. This orients edge clamp 600 correctly, and helps oppose rotational moments while tightening fastener 720.

[00118] A high-friction texture on clamp pads 612 opposes any lateral movement of clamp pads 612 as fastener 720 is tightened. A sandpaper-like texture is preferably molded directly into clamp pads 612, which dramatically reduces the tendency of edge clamp 600 to rotate during tightening. In addition, the high-friction texture prevents edge clamp 600 from being pushed laterally off of workpiece 728, which can otherwise be a concern when using long fasteners 720. [00119] Recess 614 between clamp pads 612 increases the average moment arm between the fastener 720 rotational axis and clamp pad 612 friction forces. This increases the anti-rotation friction torque that can be generated by clamp pads 612.

[00120] Finger lobes 610, similar to those found on clamping knobs, may be molded into the backside of edge clamp 600. During workpiece setup, finger lobes 610 enable the operator to oppose edge clamp 600 rotation with one hand, while tightening fastener 720 with the other.

[00121] To the extent that the term “includes” or “including” is used in the specification or the claims, it is intended to be inclusive in a manner similar to the term “comprising” as that term is interpreted when employed as a transitional word in a claim. Furthermore, to the extent that the term “or” is employed (e.g., A or B) it is intended to mean “A or B or both.” When the applicants intend to indicate “only A or B but not both” then the term “only A or B but not both” will be employed. Thus, use of the term “or” herein is the inclusive, and not the exclusive use. See Bryan A. Garner, A Dictionary of Modern Legal Usage 624 (2d. Ed. 1995). Also, to the extent that the terms “in” or “into” are used in the specification or the claims, it is intended to additionally mean “on” or “onto.” To the extent that the term “substantially” is used in the specification or the claims, it is intended to take into consideration the degree of precision available in manufacturing. To the extent that the term “selectively” is used in the specification or the claims, it is intended to refer to a condition of a component wherein a user of the apparatus may activate or deactivate the feature or function of the component as is necessary or desired in use of the apparatus. To the extent that the term “operatively connected” is used in the specification or the claims, it is intended to mean that the identified components are connected in a way to perform a designated function. As used in the specification and the claims, the singular forms “a,” “an,” and “the” include the plural. Finally, where the term “about” is used in conjunction with a number, it is intended to include ± 10 % of the number. In other words, “about 10” may mean from 9 to 11.

[00122] As stated above, while the present application has been illustrated by the description of embodiments and aspects thereof, and while the embodiments and aspects have been described in considerable detail, it is not the intention of the applicants to restrict or in any way limit the scope of the appended claims to such detail. Additional advantages and modifications will readily appear to those skilled in the art, having the benefit of the present application. Therefore, the application, in its broader aspects, is not limited to the specific details, illustrative examples shown, or any apparatus referred to. Departures may be made from such details, examples, and apparatuses without departing from the spirit or scope of the general inventive concept.