Patent Description:
The subject of this patent application relates generally to threaded fasteners with locking structures and features for preventing loosening of the fastener once tightened and to prevent tampering.

By way of background, standard threaded fasteners, such as screws, bolts, nuts, and the like, loosen over time due to vibration. Thread locking compound is applied to standard fasteners, but is messy and must be reapplied each time the fastener removed. Nuts and bolts with a nylon patch must be oriented correctly and can lose locking effectiveness if the fastener requires removing. Basically, many existing locking systems incur permanent damage in one or both the tightening and loosening process. Further, existing locking fasteners do not provide adequate anti-tampering features to prevent unauthorized removal. As such, what is needed is a fastener system that can be tightened and loosened numerous times without creating substantial permanent damage to the fastener's locking features the causing the locking effectiveness to degrade. <CIT> describes a theft resistant valve cap including a liner adapted for threaded engagement with a standard pneumatic tire stem valve, a sleeve rotatably mounted with the liner to shroud it and an interlocking feature to selectively prevent axial displacement between the liner and the sleeve. An interlocking mechanism extends between the liner and the sleeve and limits axial movement therebetween, while allowing rotational movement. To remove the cap from the valve stem, a key is employed which forms an interference fit with the shoulders in the liner, once exposed. <CIT> discloses a known fastener.

Aspects of the present invention fulfill these needs and provide further related advantages as described in the following summary.

The invention is a fastener as described in claim <NUM>, a fastener as described in claim <NUM> and a method as described in claim <NUM>.

Aspects of the present invention teach certain benefits in construction and use which give rise to the exemplary advantages described below.

The present invention provides a fastener comprising: a first fastener component having a first head portion, a first cylindrical body portion extending from the first head portion along a first cylindrical axis, a first thread formed on the first cylindrical body portion about the first cylindrical axis, the first thread having a first thread handedness; a second fastener component having a second head portion, a second cylindrical body portion extending from the second head portion along a second cylindrical axis, a through hole formed through the second head portion and the second cylindrical body portion along the second cylindrical axis, a second thread formed on the second cylindrical body portion about the second cylindrical axis, the second thread having a second thread handedness opposite the first thread handedness, at least a part of the first cylindrical body portion of the first fastener being positioned within the through hole such that the first threads are situated within the through hole and the first cylindrical axis is substantially coaxial with the second cylindrical axis to form an axis of rotation; and a rotating joint that captures the part of the first cylindrical body portion of the first fastener within the through hole of the second fastener component to prohibit axial movement between the first fastener component and the second fastener component along the axis of rotation and permits axial rotation between the first fastener component and the second fastener component about the axis of rotation; wherein the first fastener component is configured to be rotated in a first rotational direction about the axis of rotation and simultaneously the second fastener component is configured to be rotated in a second rotational direction about the axis of rotation, the second rotational direction being opposite the first rotational direction. The invention also provides method of driving a threaded fastener of the invention, comprising: providing a first threaded fastener positioned within an axial through hole of a second threaded fastener, the first threaded fastener being coupled to the second threaded fastener through a rotating joint configured to limit substantial axial movement between the first fastener component and the second fastener component along a common axis of rotation, the rotating joint configured to permit axial rotation between the first fastener component and the second fastener component about the common axis of rotation; and applying, simultaneously, a first torque to the first threaded fastener configured to rotate the first threaded fastener in a first rotational direction about a common thread axis and a second torque to the second threaded fastener configured to rotate the second threaded fastener in a second rotational direction about the common thread axis, wherein the common thread axis is substantially colinear the common axis of rotation. Also disclosed herein is a locking threaded fastener comprising a first fastener, a second fastener, and a rotating joint coupling the first fastener axially within the second fastener. The first fastener includes a first cylindrical body portion extending along a first cylindrical and a first thread formed on an outer surface of the first cylindrical body portion. The second fastener includes a second cylindrical body portion extending along a second cylindrical axis, with a through hole formed through the second cylindrical body portion along the second cylindrical axis, and a second thread formed on the second cylindrical body portion about the second cylindrical axis. The rotating joint captures at least a part of the first cylindrical body portion of the first fastener within the through hole of the second fastener component, such that the first threads are situated within the through hole and the first cylindrical axis is substantially coaxial with the second cylindrical axis to form an axis of rotation. The rotating joint limits substantial axial movement between the first fastener component and the second fastener component along the axis of rotation, and permits axial rotation between the first fastener component and the second fastener component about the axis of rotation. Further, the first thread is configured with a first thread handedness and the second thread is configured with a second thread handedness opposite the first thread handedness.

Other features and advantages of aspects of the present invention will become apparent from the following more detailed description, taken in conjunction with the accompanying drawings, which illustrate, by way of example, the principles of aspects of the invention.

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate aspects of the disclosed subject matter in at least one of its exemplary embodiments, which are further defined in detail in the following description. Features, elements, and aspects of the disclosure are referenced by numerals with like numerals in different drawings representing the same, equivalent, or similar features, elements, or aspects, in accordance with one or more embodiments. The drawings are not necessarily to scale, emphasis instead being placed upon illustrating the principles herein described and provided by exemplary embodiments of the invention. In such drawings:.

<FIG> is an assembled top front perspective view of an exemplary embodiment of a locking threaded fastener disclosed herein;
<FIG> is an assembled cross-sectional top front perspective view of the locking threaded fastener of <FIG>;
<FIG> is an assembled cross-sectional side view of the locking threaded fastener of <FIG>;
<FIG> is a cross-sectional top front perspective view of the second fastener;
<FIG> is a top front perspective view of the first fastener;
<FIG> is a cross-sectional top front perspective view of the first fastener of <FIG>;
<FIG> is an assembled top front perspective view of another exemplary embodiment of a locking threaded fastener disclosed herein;
<FIG> is an assembled cross-sectional top front perspective view of the locking threaded fastener of <FIG>;
<FIG> is an assembled cross-sectional side view of the locking threaded fastener of <FIG>;
<FIG> is a cross-sectional top front perspective view of the second fastener;
<FIG> is a top front perspective view of the first fastener;
<FIG> is a cross-sectional top front perspective view of the first fastener of <FIG>;
<FIG> is an assembled cross-sectional side view of the locking threaded fastener shown aligned with and ready to be threaded to a mating component;
<FIG> is a top front perspective schematic view of an exemplary screwdriver tool, illustrating the internal gear train; and
<FIG> is a cross-sectional top front perspective schematic view of the screwdriver tool of <FIG>.

The present system in one or more embodiments provides a locking fastener that includes a first threaded fastener axially positioned within an axial through hole of a second threaded fastener, and captured therein by a rotating joint that permits rotation of the first threaded fastener and the second threaded fastener relative to one another about a common thread axis. In one or more embodiments, the first threaded fastener thread handedness is opposite to the second threaded fastener thread handedness. Additionally disclosed, is a screwdriver tool configured to simultaneously engage and oppositely rotate the first threaded fastener and the second threaded fastener into a mating component having a first mating thread and a second mating thread configured to receive the first threaded fastener and the second threaded fastener, respectively, driven at the same axial advance distance for each tum. Once tightened, the present locking fastener resists loosening and provides a tamper-resistant hold due to the requirement that the first threaded fastener and the second threaded fastener be simultaneously rotated at the same rate, but in opposite rotational directions, in order to be extracted from the mating threads.

An exemplary embodiment of the present locking thread fastener <NUM> (which may also be referred to herein as a fastener) is illustrated in an assembled configuration in <FIG>. In one or more embodiments, the locking thread fastener <NUM> comprises a first fastener <NUM>, a second fastener <NUM>, and a rotating joint <NUM>.

Referring also to <FIG>, the first fastener <NUM> comprises a first head portion <NUM> with a first cylindrical body portion <NUM> extending in an axial direction therefrom, defining a first cylindrical axis along the cylindrical axis that is colinear with the common axis of rotation <NUM> (as shown in <FIG>). The first head portion <NUM> includes a first screw drive feature <NUM>, which in this example embodiment, is a hex socket screw drive <NUM>. A first thread <NUM> is formed on the outer surface <NUM> of the first cylindrical body portion <NUM> defining a thread axis that is colinear with the common axis of rotation <NUM>. The first thread <NUM> includes a first thread handedness, either a right-hand thread or a left-hand thread. The illustrated embodiment further includes an annular flange <NUM> extending laterally (e.g., radially) from the outer surface <NUM> of the first cylindrical body portion <NUM>; or in the illustrated example, the annular flange <NUM> extends from the first head portion <NUM>. The exact position of the annular flange along the length of the first fastener <NUM> can change according to the requirements of the application. However, in many embodiments, the annular flange <NUM> with be positioned above the first thread <NUM>, with all or at least a portion of the first head portion <NUM> protruding above the annular flange <NUM>. In one or more embodiments the annular flange <NUM> is flush with the top of the first head portion <NUM>. The purpose of the annular flange <NUM> will be discussed in greater detail below in reference to the rotating joint <NUM>.

Referring now to <FIG>, the second fastener <NUM> comprises a second head portion <NUM> with a second cylindrical body portion <NUM> extending in an axial direction therefrom, defining a second cylindrical axis along the cylindrical axis that is colinear with the common axis of rotation <NUM> (as shown in <FIG>). The second head portion <NUM> includes a second screw drive feature <NUM>, which in this example embodiment, is a spanner screw drive <NUM> comprising a plurality of spanner head pin holes <NUM> formed into the annular top surface <NUM> of the second head portion <NUM> arranged in a circle about the annular top surface <NUM>, and configured to receive the mating prongs of a screwdriver tool. A second thread <NUM> is formed on the outer wall surface <NUM> of the second cylindrical body portion <NUM>, defining a thread axis that is colinear with the common axis of rotation <NUM>. An axial through hole <NUM> is formed through the second fastener <NUM>, with the axis of the axial through hole <NUM> along the cylindrical axis that is colinear with the common axis of rotation <NUM>. The axial through hole <NUM> defines an inner wall surface <NUM> of the second fastener <NUM>, where the axial through hole <NUM> is larger in diameter than the second cylindrical body portion <NUM>, such that there is an annular gap between the first thread <NUM> of the first cylindrical body portion <NUM> and the inner wall surface <NUM> to permit clearance for the threading of the first thread <NUM> into a mating component.

Although the above explained and illustrated embodiment of the present fastener <NUM> describe the second fastener <NUM> having the second thread <NUM> is formed on the outer wall surface <NUM> of the second cylindrical body portion <NUM>, in alternative embodiments, the second thread <NUM> can be formed on the inner wall surface <NUM> of the second cylindrical body portion <NUM>.

The first thread <NUM> of the first fastener <NUM> includes a first thread handedness, either a right-hand thread or a left-hand thread, that is opposite, in one or more embodiments, the second thread handedness od second thread <NUM> of the second fastener <NUM>. For example, if the first thread handedness is right-handed (e.g., a clockwise rotation will cause an axial advance into the mating thread), the second thread handedness will be left-handed (e.g., an anticlockwise rotation will cause an axial advance into the mating thread). In another example embodiment, if the first thread handedness is left-handed, then the second thread handedness will be right-handed. In this example embodiment, the first thread <NUM> is left-handed, such that a torque that produces movement in the first rotational direction <NUM> (anticlockwise when viewed from the top) will result in the first fastener <NUM> axially advancing into its respective mating thread (which will be described in greater detail in reference to <FIG>). Additionally, in this example embodiment, the second thread <NUM> of the second fastener <NUM> is right-handed, such that a torque that produces movement in the second rotational direction <NUM> (clockwise when viewed from the top) will result in the second fastener <NUM> axially advancing into its respective mating thread. Although, in the illustrated embodiment of the present fastener <NUM> the first fastener <NUM> and the second fastener <NUM> are oppositely threaded, they can be like threaded where both have the same thread handedness.

In one or more example embodiments, and as shown in <FIG>, the rotating joint <NUM> comprises the annular flange <NUM> extending from the first fastener <NUM> and an annular groove <NUM> formed into the inner wall surface <NUM> of the second fastener <NUM>. The perimetral edge portion <NUM> of the annular flange <NUM> is positioned within the annular groove <NUM> within the through hole <NUM> of the second fastener <NUM>. In one or more embodiments, the width of the annular groove <NUM> is just sufficient to prohibit substantial axial movement or axial play of the first fastener <NUM>, yet sufficiently wide to permit a slip fit, where the edge portion <NUM> of the annular flange <NUM> is permitted to rotate and slide through the annular groove <NUM> without an unacceptable level of binding that would prohibit threading of the present fastener <NUM>. In one or more embodiments, the width of the annular groove <NUM> is substantially wider than the thickness of the annular flange <NUM>, to limit the axial movement or axial play of the first fastener <NUM> to a predefined distance, such less than one fourth of a first thread pitch of the first thread <NUM>, or less than one half of the first thread pitch of the first thread <NUM>, or less than three fourths of the first thread pitch of the first thread <NUM>, or less than one of the first thread pitch of the first thread <NUM>. Although axial play may not be necessary or desired in many circumstances, there may be times where it may be advantageous to permit slight axial play so that the first thread <NUM> of the first fastener <NUM> can be aligned with the second thread <NUM> of the second fastener <NUM> to permit smooth and simultaneous threading of both without binding and to loosen tolerances for mass production.

Although the above explained and illustrated embodiment of the present fastener <NUM> describe a flange rigidly extending from the first fastener <NUM>, other arrangements are possible to provide the rotating joint <NUM>. For example, an annular groove can be formed on the outer surface <NUM> of the first fastener <NUM> and the inner wall surface <NUM> of the second fastener <NUM>. A retaining ring can be sized to span between the two aligned annular grooves to create the rotating joint <NUM>. If at least one of the annular grooves is made sufficiently deep, the retaining ring (installed within one of the annular grooves) can be deformed inwards or outwards within the deep annular groove, snapping back when aligned with the other annular groove.

When assembled, the first fastener <NUM> is configured to be captured within the through hole <NUM> of the second fastener <NUM> by the rotating joint <NUM>, which substantially limits movement between the first fastener <NUM> and the second fastener <NUM> along the common axis of rotation <NUM>. Further, the rotating joint <NUM> permits rotation of the first fastener <NUM> and the second fastener <NUM> relative to one another about the common axis of rotation <NUM>. Thus, the first fastener <NUM> and the second fastener <NUM> are permitted to rotate relative to one another in the same direction or in opposite directions when not being threaded.

In one or more embodiments, the first thread <NUM> of the first fastener <NUM> and the second thread <NUM> of the second fastener <NUM> have like thread pitches, such that the first rotational speed of the first fastener <NUM> is equal in magnitude (although opposite in direction) to the second rotational speed of the second fastener <NUM>, since the lead or axial distance traveled per revolution is the same for both the first fastener <NUM> and the second fastener <NUM>. Thus, the first fastener <NUM> and the second fastener <NUM> can be driven at the same rotational rate.

In one or more embodiments, the first thread <NUM> of the first fastener <NUM> and the second thread <NUM> of the second fastener <NUM> have dissimilar thread pitches, such that the first rotational speed of the first fastener <NUM> is unequal in magnitude to the second rotational speed of the second fastener <NUM>, due to the lead or axial distance traveled per revolution different for the first fastener <NUM> compared to the second fastener <NUM>. If the first fastener <NUM> and the second fastener <NUM> were to be simultaneously rotated at the same rotational speed and in opposite directions, the first thread <NUM> and the second thread <NUM> would quickly bind within their respective mating threads.

When the first thread <NUM> of the first fastener <NUM> and the second thread <NUM> of the second fastener <NUM> have dissimilar thread pitches (where lead and pitch are the same for a single start thread) the relationship of the angular speed at which the first fastener <NUM> and the second fastener <NUM> must be rotated can be expressed in one or more embodiments as Linner * ((αinner / T<NUM>) / <NUM>°) = Louter * ((βouter / T<NUM>) / <NUM>°), where Linner and Louter indicate the lead of the first thread <NUM> and the second thread <NUM> respectively, αinner and βouter indicate the angle in degrees the first fastener <NUM> and the second fastener <NUM> are rotated by respectively (β denotes an inverse angle compared to α), and T<NUM> indicates total time during which both rotations are exerted. Thus, in order to smoothly and simultaneously thread both the first fastener <NUM> and the second fastener <NUM> into a mating component, the lead of both the first thread <NUM> and the second thread <NUM> must be considered in the design of the screwdriver tool.

Now, turning to <FIG>, a second example embodiment of the locking fastener <NUM> is illustrated. As shown in <FIG>, the first fastener <NUM> comprises a first head portion <NUM> with a first cylindrical body portion <NUM> extending in an axial direction therefrom, defining a first cylindrical axis along the cylindrical axis that is colinear with the common axis of rotation <NUM> (as shown in <FIG>). The first head portion <NUM> includes a first screw drive feature <NUM>, which in this example embodiment, is a hex socket screw drive <NUM>. A first thread <NUM> is formed on the outer surface <NUM> of the first cylindrical body portion <NUM> defining a thread axis that is colinear with the common axis of rotation <NUM>. The first thread <NUM> includes a first thread handedness. Instead of an annular flange, the illustrated embodiment includes an annular groove <NUM> formed into the first head portion <NUM> or the first cylindrical body portion <NUM>.

Referring to <FIG>, the second fastener <NUM> comprises a second head portion <NUM> with a second cylindrical body portion <NUM> extending in an axial direction therefrom, defining a second cylindrical axis along the cylindrical axis that is colinear with the common axis of rotation <NUM> (as shown in <FIG>). The second head portion <NUM> includes a second screw drive feature <NUM>, which in this example embodiment, is a spanner screw drive <NUM> comprising a plurality of spanner head pin holes <NUM> formed into the annular top surface <NUM> of the second head portion <NUM> arranged in a circle about the annular top surface <NUM>, and configured to receive the mating prongs or pins of the screwdriver tool. A second thread <NUM> is formed on the inner wall surface <NUM> of the second cylindrical body portion <NUM>, defining a thread axis that is colinear with the common axis of rotation <NUM>. An axial through hole <NUM> is formed through the second fastener <NUM>, with the axis of the axial through hole <NUM> along the cylindrical axis that is colinear with the common axis of rotation <NUM>. The axial through hole <NUM> defines the inner wall surface <NUM> of the second fastener <NUM>, where the axial through hole <NUM> is larger in diameter than the second cylindrical body portion <NUM>, such that there is an annular gap between the first thread <NUM> of the first cylindrical body portion <NUM> and the inner wall surface <NUM> to permit clearance for the threading of the first thread <NUM> into a mating component.

Although the above explained and illustrated embodiment of the present fastener <NUM> describe the second fastener <NUM> having the second thread <NUM> is formed on the inner wall surface <NUM> of the second cylindrical body portion <NUM>, in alternative embodiments, the second thread <NUM> can be formed on the outer wall surface <NUM> of the second cylindrical body portion <NUM>.

Referring to <FIG>, the rotating joint <NUM> comprises the annular flange <NUM> extending from the inner wall surface <NUM> of the second fastener <NUM> and an annular groove <NUM> formed into the first fastener <NUM> (either the first head portion <NUM>, as illustrated, or the first cylindrical body portion <NUM>). The exemplary annular flange <NUM> forms a washer-like protrusion into the through hole <NUM> of the second fastener <NUM>. The perimetral edge portion <NUM> of the annular flange <NUM> is positioned within the annular groove <NUM>. In one or more embodiments, the width of the annular groove <NUM> is just sufficient to prohibit substantial axial movement or axial play of the first fastener <NUM>, yet sufficiently wide to permit a slip fit, where the edge portion <NUM> of the annular flange <NUM> is permitted to rotate and slide through the annular groove <NUM> without an unacceptable level of binding that would prohibit threading of the present fastener <NUM>.

Although the above explained and illustrated embodiment of the present fastener <NUM> describe a flange rigidly extending from the second fastener <NUM>, other arrangements are possible to provide the rotating joint <NUM>. For example, an annular groove can be formed on the outer surface <NUM> of the first fastener <NUM> and the inner wall surface <NUM> of the second fastener <NUM>. A retaining ring can be sized to span between the two aligned annular grooves to create the rotating joint <NUM>. If at least one of the annular grooves is made sufficiently deep, the retaining ring (installed within one of the annular grooves) can be deformed inwards or outwards within the deep annular groove, snapping back when aligned with the other annular groove.

Looking at <FIG>, a bonding seam <NUM> can be seen as a dashed line at the top of the annular groove <NUM> formed into the first head portion <NUM> of the first fastener <NUM>. To aid in assembly, the first fastener <NUM> or second fastener <NUM> can be split into two parts. Here, the socket head portion <NUM> of the first head portion <NUM> is bonded to the top end of the threaded portion <NUM> of the first cylindrical body portion <NUM>, with the socket head portion <NUM> defining the top of the annular groove <NUM>. To assemble the fastener <NUM> the threaded portion <NUM> can be inserted through the through hole <NUM> from the underside of the annular flange <NUM>; and the socket head portion <NUM> can be mated to the threaded portion <NUM> from the top side of the annular flange <NUM>. The two parts can be threaded together, bonded, welded (i.e., spot welded, friction welded, brazed, etc.), or joined by some other process to capture the annular flange <NUM> within the annular groove <NUM> and provide a bond sufficient to withstand the expected torque of insertion and/or extraction of the fastener <NUM>.

Instead of creating a two-part first fastener <NUM> as described above, the first fastener <NUM> can be designed with a malleable first head portion <NUM> that can be bent over, crushed in a riveting process, or other process that can create the annular groove <NUM> or other structure that provides a similar function thereto. Yet another exemplary manufacturing method could entail molding or printing the fastener <NUM>, with the annular flange <NUM> injection molded or printed within the annular groove <NUM>, which can thereafter be freed (if any thin webbing or the like connects the annular flange <NUM> to the annular groove <NUM>) by twisting the first fastener <NUM> and the second fastener <NUM> relative to one another.

Although particular screw drive systems are illustrated herein for the first fastener <NUM>, <NUM> and the second fastener <NUM>, <NUM>, a wide variety of screw drives are compatible with the present locking thread fastener <NUM>, <NUM> such as slotted, cruciform (i.e., the Phillips screw drive, etc.), extemal polygon (i.e., the hex screw drive, etc.), the hexalobular socket screw drive (i.e., the TORX screw drive), and other screw drives. For example, outer surface <NUM>, <NUM> of second head portion <NUM>, <NUM> can be shaped as an external hex for receiving a hex socket.

Looking now at <FIG>, a mating fastener <NUM> (which may also be referred to as a nut in this example embodiment, as it acts somewhat like a binding barrel nut) can be seen aligned and ready for coupling to the present locking fastener <NUM>. The mating fastener <NUM> includes a body portion <NUM> extending from an optional head portion <NUM>. A stud <NUM> defines a central threaded hole <NUM> and a threaded ring <NUM> is defined by stud <NUM> and body portion <NUM> in a manner where the threaded ring <NUM> surrounds and is concentric with the central threaded hole <NUM>. The central threaded hole <NUM> has formed therein a first female thread <NUM> formed on an inner surface of stud <NUM>, and configured to receive therein the first fastener <NUM>, with the first threads <NUM> threadably engaged with the first female thread <NUM>. The threaded ring <NUM> has formed a second female threads <NUM> on surface of body portion <NUM> defining threaded ring <NUM>, and configured to receive therein the second fastener <NUM>, with the second thread <NUM> threadably engaged with the second female thread <NUM>. The handedness of the first female thread <NUM> is matched to the handedness of the first thread <NUM> of the first fastener <NUM>. The handedness of the second female thread <NUM> is matched to the handedness of the second thread <NUM> of the second fastener <NUM>. Thus, the handedness of the first female thread <NUM> and the second female thread <NUM> are opposite one another in this example embodiment. As described above, the first fastener <NUM> and the second fastener <NUM> must be simultaneously turned in opposite directions in order to be threaded into their respective threaded receptacles (e.g., the central threaded hole <NUM> and the threaded ring <NUM>, respectively).

Manufacturing the mating fastener <NUM> can be achieved, in one or more embodiments, by milling a large blind hole in the body portion <NUM> and tapping the hole to provide the second female thread and provide an outer nut. An inner nut can be created by milling and tapping a stud and concentrically attaching it to the bottom <NUM> of the large blind hole by a bonding process, a male thread on the stud, or other known means of attachment.

Although not shown, the mating fastener <NUM> can be configured for coupling to the present locking fastener <NUM>. In this example embodiment, the threaded ring <NUM> has formed a second female threads <NUM> on outer surface of stud <NUM> defining threaded ring <NUM>, and configured to receive therein the second fastener <NUM>, with the second thread <NUM> threadably engaged with the second female thread <NUM>.

The present specification also discloses a screwdriver using to fasten or loosen a locking fastener disclosed herein, such as, e.g., locking fastener <NUM>, <NUM>. Looking now at <FIG>, the inner workings of a screwdriver tool <NUM> is shown schematically. The input shaft <NUM> includes a sun gear <NUM> axially mounted thereon. A first driver portion <NUM> is formed on or attached to the input shaft <NUM>. An outer race <NUM> concentrically carries a ring gear <NUM> forming a bearing, with ball bearings <NUM> captured between the outer race <NUM> and the ring gear <NUM> (where the ring gear <NUM> acts much like an inner race), such that the ring gear <NUM> permitting to rotated relative to the outer race <NUM>, which is directly or indirectly fixed by one hand operating the tool and preventing rotation of the outer race <NUM>. A carrier <NUM> extends inwardly from and is mounted on the outer race <NUM>. A planet gear <NUM> is rotatably mounted to the carrier <NUM> and is positioned between the sun gear <NUM> and the ring gear <NUM>. The planet gear <NUM> transmits torque from the sun gear <NUM> to the ring gear <NUM>. As the input shaft <NUM> rotates in a first rotational direction <NUM>, the gear train <NUM> converts the first rotational direction <NUM> into an opposite second rotational direction <NUM>. Depending on the gearing ratios within the gear train <NUM>, the rotational speed of the input shaft <NUM> and the rotational speed of the ring gear <NUM> can be configured to be the same or different. The gear train <NUM> is designed to create a difference is the rotational speed of the input shaft <NUM> and the rotational speed of the ring gear <NUM> to match the difference in the first thread <NUM>, <NUM> pitch and the second thread <NUM>, <NUM> pitches, so that the first axial advance distance of the first thread <NUM>, <NUM> is the same as the second axial advance distance of the second thread <NUM>, <NUM> for each revolution. Although the screwdriver tool <NUM> is somewhat schematic is representation, it can be seen that the input shaft <NUM> directly drives the first fastener <NUM> through the first driver portion <NUM>, and drives the second fastener <NUM> through the second driver portion <NUM> moving with the ring gear <NUM>. In this way, the first fastener <NUM>, <NUM> and the second fastener <NUM>, <NUM> can be rotated in opposite directions at differing or the same speeds.

The present locking fastener, such as, e.g., locking fastener <NUM>, <NUM>, provides a means to lock the threads within a mating component and quickly remove the locking fastener without substantial permanent damage to the threads or the requirement for adhesive coating. A locking fastener disclosed herein, such as, e.g., locking fastener <NUM>, <NUM>, resists loosening due to vibration due to the requirement that the coaxial fastener components be simultaneously counterrotated to produce a similar axial advance distance for each turn. Thus, although vibration may tend to cause rotation of one of the two threaded fastener components in one rotational direction, loosening is not permitted due to a rotating joint disclosed herein, such as, e.g., rotating joint <NUM>, <NUM>, blocking axial advance of the would-be loosened threaded fastener component. Further, certain vibrations that may tend to cause loosening in one rotational direction may also cause tightening in the oppositely threaded fastener.

In closing, foregoing descriptions of embodiments of the present invention have been presented for the purposes of illustration and description. It is to be understood that, although aspects of the present invention are highlighted by referring to specific embodiments, one skilled in the art will readily appreciate that these described embodiments are only illustrative of the principles comprising the present invention. As such, the specific embodiments are not intended to be exhaustive or to limit the invention to the precise forms disclosed. Therefore, it should be understood that embodiments of the disclosed subject matter are in no way limited to a particular element, compound, composition, component, article, apparatus, methodology, use, protocol, step, and/or limitation described herein, unless expressly stated as such.

In addition, groupings of alternative embodiments, elements, steps and/or limitations of the present invention are not to be construed as limitations. Each such grouping may be referred to and claimed individually or in any combination with other groupings disclosed herein. It is anticipated that one or more alternative embodiments, elements, steps and/or limitations of a grouping may be included in, or deleted from, the grouping for reasons of convenience and/or patentability. When any such inclusion or deletion occurs, the specification is deemed to contain the grouping as modified, thus fulfilling the written description of all Markush groups used in the appended claims.

Certain embodiments of the present invention are described herein, including the best mode known to the inventors for carrying out the invention. Of course, variations on these described embodiments will become apparent to those of ordinary skill in the art upon reading the foregoing description. The inventor expects skilled artisans to employ such variations as appropriate, and the inventors intend for the present invention to be practiced otherwise than specifically described herein.

The words, language, and terminology used in this specification is for the purpose of describing particular embodiments, elements, steps and/or limitations only and is not intended to limit the scope of the present invention, which is defined solely by the claims. In addition, such words, language, and terminology are to be understood not only in the sense of their commonly defined meanings, but to include by special definition in this specification structure, material or acts beyond the scope of the commonly defined meanings. Thus, if an element, step, or limitation can be understood in the context of this specification as including more than one meaning, then its use in a claim must be understood as being generic to all possible meanings supported by the specification and by the word itself.

Unless otherwise indicated, all numbers expressing a characteristic, item, quantity, parameter, property, term, and so forth used in the present specification and claims are to be understood as being modified in all instances by the term "about. " As used herein, the term "about" means that the characteristic, item, quantity, parameter, property, or term so qualified encompasses a range of plus or minus ten percent above and below the value of the stated characteristic, item, quantity, parameter, property, or term. Accordingly, unless indicated to the contrary, the numerical parameters set forth in the specification and attached claims are approximations that may vary. For instance, as mass spectrometry instruments can vary slightly in determining the mass of a given analyte, the term "about" in the context of the mass of an ion or the mass/charge ratio of an ion refers to +/-<NUM> atomic mass unit. At the very least, and not as an attempt to limit the application of the doctrine of equivalents to the scope of the claims, each numerical indication should at least be construed in light of the number of reported significant digits and by applying ordinary rounding techniques.

Notwithstanding that the numerical ranges and values setting forth the broad scope of the invention are approximations, the numerical ranges and values set forth in the specific examples are reported as precisely as possible. Any numerical range or value, however, inherently contains certain errors necessarily resulting from the standard deviation found in their respective testing measurements. Recitation of numerical ranges of values herein is merely intended to serve as a shorthand method of referring individually to each separate numerical value falling within the range. Unless otherwise indicated herein, each individual value of a numerical range is incorporated into the present specification as if it were individually recited herein.

Use of the terms "may" or "can" in reference to an embodiment or aspect of an embodiment also carries with it the alternative meaning of "may not" or "cannot. " As such, if the present specification discloses that an embodiment or an aspect of an embodiment may be or can be included as part of the inventive subject matter, then the negative limitation or exclusionary proviso is also explicitly meant, meaning that an embodiment or an aspect of an embodiment may not be or cannot be included as part of the inventive subject matter. In a similar manner, use of the term "optionally" in reference to an embodiment or aspect of an embodiment means that such embodiment or aspect of the embodiment may be included as part of the inventive subject matter or may not be included as part of the inventive subject matter. Whether such a negative limitation or exclusionary proviso applies will be based on whether the negative limitation or exclusionary proviso is recited in the claimed subject matter.

The terms "a," "an," "the" and similar references used in the context of describing the present invention (especially in the context of the following claims) are to be construed to cover both the singular and the plural, unless otherwise indicated herein or clearly contradicted by context. Further, ordinal indicators - such as, e.g., "first," "second," "third," etc. - for identified elements are used to distinguish between the elements, and do not indicate or imply a required or limited number of such elements, and do not indicate a particular position or order of such elements unless otherwise specifically stated. The use of any and all examples or exemplary language (e.g., "such as") provided herein is intended merely to better illuminate the present invention and does not pose a limitation on the scope of the invention otherwise claimed. No language in the present specification should be construed as indicating any non-claimed element essential to the practice of the invention.

Claim 1:
A fastener (<NUM>, <NUM>) comprising:
a first fastener component (<NUM>, <NUM>) having a first head portion (<NUM>, <NUM>), a first cylindrical body portion (<NUM>, <NUM>) extending from the first head portion along a first cylindrical axis, a first thread (<NUM>, <NUM>) formed on the first cylindrical body portion (<NUM>, <NUM>) about the first cylindrical axis, the first thread having a first thread handedness;
a second fastener component (<NUM>, <NUM>) having a second head portion (<NUM>, <NUM>), a second cylindrical body portion (<NUM>, <NUM>) extending from the second head portion along a second cylindrical axis, a through hole (<NUM>, <NUM>) formed through the second head portion (<NUM>, <NUM>) and the second cylindrical body portion (<NUM>, <NUM>) along the second cylindrical axis, a second thread (<NUM>, <NUM>) formed on the second cylindrical body portion (<NUM>, <NUM>) about the second cylindrical axis, the second thread (<NUM>, <NUM>) having a second thread handedness opposite the first thread handedness, at least a part of the first cylindrical body portion (<NUM>, <NUM>) of the first fastener (<NUM>, <NUM>) being positioned within the through hole (<NUM>, <NUM>) such that the first threads (<NUM>, <NUM>) are situated within the through hole (<NUM>, <NUM>) and the first cylindrical axis is substantially coaxial with the second cylindrical axis to form an axis of rotation (<NUM>, <NUM>); and
a rotating joint (<NUM>, <NUM>) that captures the part of the first cylindrical body portion of the first fastener within the through hole (<NUM>, <NUM>) of the second fastener component to prohibit axial movement between the first fastener component (<NUM>, <NUM>) and the second fastener component (<NUM>, <NUM>) along the axis of rotation (<NUM>, <NUM>) and permits axial rotation between the first fastener component (<NUM>, <NUM>) and the second fastener component (<NUM>, <NUM>) about the axis of rotation (<NUM>, <NUM>);
wherein the first fastener component (<NUM>, <NUM>) is configured to be rotated in a first rotational direction about the axis of rotation (<NUM>, <NUM>) and simultaneously the second fastener component (<NUM>, <NUM>) is configured to be rotated in a second rotational direction about the axis of rotation (<NUM>, <NUM>), the second rotational direction being opposite the first rotational direction.