Threaded fastener having a thread crest greater than its thread root and v angles on the crest and root

Abstract

An interlocking thread with a tooth-cross-section that is wider at its crest than at its root and with V angles located both along the crest and the root which tightens into a tapped hole that has a similar thread cross-section.

Claims

1-10. (canceled)

11. A fastener, comprising: a shaft having a first end including means to rotate said shaft, said shaft having a thread projecting from an outer periphery of said shaft and spiraling along its length, said thread defined by an upper flank, a lower flank, a root adjacent said shaft and crest remote from said shaft, said upper and lower flanks being separated by a V shaped indentation and diverging outwardly from each other away from said root and defining a dovetail, wherein an apex of said V shaped indentation has an acute angle.

12. The fastener of claim 1, wherein said V shaped indentation is defined by facing inner surfaces of said upper and lower flanks, the inner surfaces converging towards said root to form said V shape.

13. The fastener of claim 2, wherein said two surfaces converge at said apex.

14. A method of fabricating the fastener of claim 1, comprising: a first flank forming step wherein said upper and lower flanks are formed on said shaft parallel to one another; and a second flank forming step wherein said upper and lower flanks are swaged outwardly to define said V shaped indentation and dovetail.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0017] FIG. 1 is a plan view of the threaded fastener having a portion cut away to show the thread profile.

[0018] FIG. 1A amplifies the cut away.

[0019] FIG. 2 reflects the fastener as it engages a complementary bore and force dissipation vectors.

[0020] FIG. 3 reflects a tapered shaft and shear load reactions.

[0021] FIG. 4 is a side view of the tap.

[0022] FIG. 4A is a top view of the tap.

[0023] FIG. 4B is a bottom view of the tap.

DESCRIPTION OF PREFERRED EMBODIMENTS

[0024] Considering the drawings, wherein like reference numerals denote like parts throughout the various drawing figures, reference numeral 10 is directed to the threaded fastener according to the present invention

[0025] In general, the fastener 10 includes a shaft 2 preferably of substantially cylindrical configuration or with a taper. FIG. 3 shows a tapered fastener. If the female bore (which receives the fastener FIG. 2) is dimensioned greater than the smallest taper diameter of the fastener 10 but smaller than the greatest taper diameter of the fastener 10, an interference fit results, similar to having varying thread pitch (i.e. increasing from bottom to top).

[0026] The fastener 10 has a first end 4 adjacent a top thereof and a second end 6 defining a bottom. Note that the use of terms such as top, bottom, horizontal, etc. are made relative to the drawings appended herewith but are not intended to be directionally limiting. First end 4 may include means to rotate the shaft, such as a hex head or recess H.

[0027] The shaft 2 includes an integrally formed thread 12 spirally deployed thereabout. In one embodiment, any cross-section of the thread would appear as a dovetail having an upper pressure angle or flank 16 on a top side thereof and a lower pressure angle or flank 17 on a lower side thereof. The outer surface extending between the upper flank and lower flank defines a crest. The dovetail is supported on the shaft 2 by the root. Areas on the shaft 2 between adjacent dovetails define root gaps 18.

[0028] Threaded member 10 of FIG. 1 has a longitudinal axis 11 which passes through the center of the member. An external thread portion 12 is helically wound around the circumference of the member 10. The external thread portion 12 is defined between a minor diameter 13 (at root gap 18) and crest diameter 14.

[0029] Interlocking pressure angles (upper) 16 and (lower) 17 are located between the crest diameter 14 and the minor diameter 13. Male and female V angles 19 and 20 are found with the male V angle 19 at the root gap 18 and female V angle 20 at the exterior crest surface of the pressure angles 16 and 17.

[0030] In section, each upper pressure angle 16 is parallel to its others. Similarly, each lower pressure angle 17 is parallel to its others. An included angle between an upper and lower pressure angle may range between 14 and 34 degrees and is preferably 24 degrees.

[0031] The root gaps 18 are interrupted by projections which define male V angles 19. The V shaped pressure angles 19 are formed (in section) by two angle surfaces 19a and 19b which converge as they extend from shaft 2. Preferably, the projections 19a, b define a V angle having an acute apex remote from the shaft 2. The subtended acute angle ranges between 65-85 degrees, and preferably is 75 degrees.

[0032] The fastener's crest includes a female V angle 20 formed (in section) by two angle surfaces 20a and 20b which converge as they extend towards the shaft 2. These surfaces 20 a, b define an indentation in the crest thread and form a V angle having an acute angle where the surfaces converge. Preferably the angle is 60 degrees and can range from 50 to 70 degrees.

[0033] It is preferred that the gap 18 and the crest periphery 22 retain (respectively) shaft material and thread material. That is, the V angles should not extend all the way to the extremities of pressure angles 16, 17. This adds strength to resist shear, torsion, bending, and vertical loading parallel to the long axis 11.

[0034] FIG. 2 shows a female threaded section 30 with a similar internal threaded profile engaged with a male threaded section 10 to create an interlocking joint. The significance of this instant invention is notably found in the benefits of function when the thread profile is engaged into a matching profile. Several unique and important interactions occur as the helical rotation causes abutted clamping force between two objects.

[0035] First there is the interlocking grip of the double opposing hook threads that prevent outward movement of the sidewalls of the female object.

[0036] Second there is the continued gripping of the sidewalls in the event of vertical upward or downward loading. FIG. 2 shows a vertical down load A being opposed by the fastener's reaction forces B, C, D, E, F and G. A compressive load, by adding up load M, produce the same reactive forces on the thread, as would a tensile load (i.e. with load A and M in opposite outward directions. Specifically, compressive load M contact with surfaces B, G, and D, while load A is opposed by C, E and F.

[0037] Third there is the resistance to vertical shear loads in situations where it can be used to attach sidewalls together. FIG. 3 shows shear loads J and H opposed by forces B, C, D, E, F and G.

[0038] Fourth there is the resistance to bending moments where bending of joined sidewalls is probable. FIG. 2 shows a bending moment BM opposed by surfaces/reaction forces B, C, D, E, F and G.

[0039] Fifth there is the increased sealing ability of the threaded joint due to its complexity (surface to surface contact, e.g. FIG. 2) where gas and/or liquid tight seal is required.

[0040] Sixth there is an ability to form this thread by conventional thread fabricating processes such as cold rolling. Here, the pressure flanks 16, 17 are flared outwardly during formation of the female V. In other words, the flanks 16, 17 are first formed parallel to each other and then swaged outwardly which make it possible to manufacture cost effectively enough to compete with standard bolts and screws.

[0041] FIGS. 4, 4A and 4B show the tap 40 which forms the bore 30. In essence a driving head 42 rotates the tap 40 so that the flutes remove material. The contour of the flute mirrors the fastener (detailed in FIG. 1A) and bears similar reference numerals (incremented by 100). Thus 116 and 117 are cutting elements that form the upper and lower pressure angle flanks 16, 17 respectively. Male V angle 19 and female V angle 20 are formed by cutting elements 119 and 120 respectively.

[0042] Cutting elements 119 and 120 are especially important in that they remove material providing clearance in advance of and in concert with cutting elements 116 and 117, making it possible to form the dovetail threads in a single tapping process. This avoids sequential tapping which therefore avoids potential problems of misalignment when tapping in multiple stepsnot to mention added time required.