FIELD OF THE INVENTION

The present invention relates generally to a socket tool. More specifically, the present invention relates to a double-sided socket so that the user can tighten a fastener through one of the socket opening and loosen a damaged fastener through the opposite socket opening.

BACKGROUND OF THE INVENTION

In actuality, the tool industry keeps developing various tools with advanced designs, durable material and at a faster rate thanks to the advanced manufacturing and designing methods developed by the human species. Hex bolts, nuts, screws, and other similar threaded devices are used to secure and hold multiple components together by being engaged to a complimentary thread, known as a female thread. The general structure of these types of fasteners is a cylindrical shaft with an external thread and a head at one end of the shaft. The external thread engages a complimentary female thread tapped into a hole or a nut and secures the fastener in place, fastening the associated components together. The head receives an external torque force and is the means by which the fastener is turned, or driven, into the female threading. The head is shaped specifically to allow an external tool like a socket to apply a torque to the fastener in order to rotate the fastener and engage the complimentary female threading to a certain degree. This type of fastener is simple, extremely effective, cheap, and highly popular in modern construction. One of the most common problems in using these types of fasteners, whether male or female, is the tool slipping in the head portion, or slipping on the head portion. This is generally caused by either a worn fastener or tool, corrosion, overtightening, or damage to the head portion of the fastener. It is an objective of the present invention to provide a selectable driver and extractor tool body that enables the user to tighten a fastener and remove a damage fastener. The present invention is a double-sided socket driver so that the users can selectively complete two different tasks with a single tool body. More specifically, one side of the double-sided socket driver can be utilized to tighten a fastener as a driving socket while the other side of the double-sided socket driver can be utilized to loosen a damage fastener as a grip socket.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a top perspective view of the present invention, showing the second torque-tool socket.

FIG. 2 is a bottom perspective view of the present invention, showing the first torque-tool socket.

FIG. 3 is a side view of the present invention, showing the plane upon which a cross sectional view is taken shown in FIG. 4.

FIG. 4 is a cross section view of the present invention taken along line 4-4 of FIG. 3. FIG. 5 is a cross section view of the present invention taken along line 4-4 of FIG. 3. FIG. 6 is a side view of the present invention, showing the plane upon which a cross sectional view is taken shown in FIG. 7-9.

FIG. 7 is a cross section view of the present invention taken along line 7-7 of FIG. 6, showing the configuration of the second torque-tool socket.

FIG. 8 is a cross section view of the present invention taken along line 8-8 of FIG. 6, showing the configuration of the hexagonal engagement bore.

FIG. 9 is a cross section view of the present invention taken along line 9-9 of FIG. 6, showing the configuration of the first torque-tool socket.

FIG. 10 is a perspective view of the present invention.

FIG. 11 is a perspective view of an alternative embodiment of the present invention.

FIG. 12 is a perspective view of the male adaptor of the present invention.

FIG. 13 is a side view of the male adaptor of the present invention. FIG. 14 is a perspective view of an alternative embodiment of the male adaptor.

DETAIL DESCRIPTIONS OF THE INVENTION

All illustrations of the drawings are for the purpose of describing selected versions of the present invention and are not intended to limit the scope of the present invention.

The present invention is a selectable driver and extractor tool body designed so the user can perform multiple tasks with a single tool body. The user can use the present invention to tighten or loosen any fastener such as a nut or bolt, similar to traditional wrench socket designs. The user can also use the present invention to loosen damaged fasteners such as nut or bolt. The present invention is configured similar to traditional wrench socket. However, one side of the present invention is utilized to loosen or tighten fastener, and the other side of the present invention is utilized to loosen damaged fasteners. Both loosening and fastening can be either clockwise or counterclockwise direction depending on the fastener thread orientation. A torque tool applies rotational force to the present invention via a male adaptor 44 that transfer the rotational force of the torque tool to the present invention. The present invention is compatible with malemember based head fasteners that utilize a male-member head design, also known as male fasteners. Such male-member based head fasteners include, but are not limited to, twelve point bolt, hex bolts, and nuts. In addition, the present invention is compatible with fasteners of a right-hand thread and fasteners of a left-hand thread. Furthermore, the present invention may be altered and configured to fit different types and different sizes of fasteners.

The present invention is a selectable driver and extractor tool body that incorporates multiple fastener driving sockets into a single device. Thereby enabling the user to drive fasteners of varying shape and size or remove damaged fasteners, without searching through multiple tools. The present invention is a cost and space saving system. The male adaptor 44 of the present invention employs an internal mounting system to ensure that the present invention is secured to the male adaptor 44 and the male adaptor 44 efficiently transfers torque from the torque tool. In reference to FIG. 1-4, the present invention comprises a first torque-tool socket 1, a second torque-tool socket 7, an attachment body 13, and a hexagonal engagement bore 17. The first torque-tool socket 1 is adjacently connected to the attachment body 13 thus defining a first socket opening. The second torque-tool socket 7 is adjacently connected to the attachment body 13 and positioned opposite of the first torque-tool socket 1. As a result, a second socket opening is defined opposite of the first socket opening. A rotational axis 2 of the first torque-tool socket 1, a central axis 16 of the attachment body 13, and a rotational axis 8 of the second torque-tool socket 7 are positioned collinear to each other thus defining an overall cylindrical shape to the present invention. The hexagonal engagement bore 17 traverses through the attachment body 13 and positioned concentric and along the central axis 16 of the attachment body 13. As a result, the hexagonal engagement bore 17 is able to create a passageway from the first torque-tool socket 1 to the second torque-tool socket 7.

To deploy the present invention, the user inserts a proximal end of the male adaptor 44 into the first torque-tool socket 1 or the second torque-tool socket 7 so that the male adaptor 44 can engaged within the attachment body 13. For example, when the user needs to deploy the first torque-tool socket 1, the male adaptor 44 is inserted through the second torque-tool socket 7 and into the attachment body 13. When the user needs to deploy the second torque-tool socket 7, the male adaptor 44 is inserted through the first torque-tool socket 1 and into the attachment body 13. Once the proximal end of the male adaptor 44 is inserted into the present invention, the user can insert a distal end of the male adapter into the torque tool. The present invention is then able to rotate around the central axis 16 of the attachment body 13.

In reference to FIG. 4, the attachment body 13 further comprises a first base 14 and a second base 15. More specifically, the attachment body 13 is extended from the first base 14 to the second base 15. An outer wall of the attachment body 13 is preferably formed into a cylindrical shape and adjacently connected to an outer wall of the first torque-tool socket 1 and the second torque-tool socket 7. Furthermore, the first torquetool socket 1 is adjacently connected to the first base 14 and outwardly extended away from the first base 14. The second torque-tool socket 7 is adjacently connected to the second base 15 and outwardly extended away from the second base 15. The hexagonal engagement bore 17 traverses from the first base 14 to the second base 15 so that the passageway from the first torque-tool socket 1 to the second torque-tool socket 7 can receive and lock the male adaptor 44.

In reference to FIG. 4, the present invention further comprises a first annular retention-groove 19. The first annular retention-groove 19 traverses into the attachment body 13 from the hexagonal engagement bore 17 and positioned adjacent to the first torque-tool socket 1. The first annular retention-groove 19 provides a ring shaped empty space within the attachment body 13 to prevent accidental dislodging of the present invention from the male adapter. To facilitate this, the male adapter comprises a retention mechanism that is integrated into a hex portion 34 of the male adaptor 44. Preferably, the retention mechanism of the present invention is a spring-loaded ball. Once the male adaptor 44 is inserted into the attachment body 13 via the second torque-tool socket 7, the retention mechanism is able to engage with the second annular retention-groove 20 thus securing the present invention to the male adaptor 44. Furthermore, the hex portion 34 of the male adaptor 44 is then able to engage with the hexagonal engagement bore 17 thus eliminating any displacement or lateral movement of the present invention during operation. As a result of the second annular retention-groove 20 and the placement of the male adaptor 44, the user can use the first torque-tool socket 1 to loosen or tighten any fastener.

In reference to FIG. 4, the present invention further comprises a second annular retention-groove 20. The second annular retention-groove 20 traverses into the attachment body 13 from the hexagonal engagement bore 17 and positioned adjacent to the second torque-tool socket 7. The second annular retention-groove 20 provides a ringshaped empty space within the attachment body 13 to prevent accidental dislodging of the present invention from the male adapter. To facilitate this, the male adapter comprises the retention mechanism that is integrated into the hex portion 34 of the male adaptor 44. Preferably, the retention mechanism of the present invention is a spring-loaded ball. Once the male adaptor 44 is inserted into the attachment body 13 via the first torque-tool socket 1, the retention mechanism is able to engage with the first annular retention-groove 19 thus securing the present invention to the male adaptor 44. Furthermore, the hex portion thus eliminating any displacement or lateral movement of the present invention during operation. As a result of the first annular retention-groove 19 and the placement of the male adaptor 44, the user can use the second torque-tool socket 7 to loosen or tighten any fastener.

Alternatively, the present invention may incorporate a single retention groove. More specifically, the single retention groove traverses into the hexagonal engagement bore 17 that is utilized to secure the male adaptor 44 to the attachment body 13.

The industry standard square adaptors that applies toque to wrench sockets are formed into the square shape. Generally, the industry standard square adaptor are sized into sizes such as ’A”, 3/8”, A”, %’ 1 ’ . The hex portion 34 of the male adaptor 44 utilized within the present invention is shaped into a hexagonal shape to precisely engage with the hexagonal engagement bore 17. It would be obvious that the male adaptor 44 that applies rotational torque to the present invention has to be a smaller in diameter than the smallest opening of the first torque-tool socket 1 or the second torque-tool socket 7. The present invention overcomes the problem of wrench socket size limitations, particularly when the wrench socket is tapered, by using the hex portion 34 of the male adaptor 44 (hexagonal shape) versus the industry standard square adaptors.

In reference to FIG. 6 and FIG. 8, the hexagonal engagement bore 17 comprises a plurality of lateral walls 18 that extends along the central axis 16 of the attachment body 13. The plurality of lateral walls 18 is radially distributed around the central axis 16 of the attachment body 13 in an arrangement of the hexagonal shape. Each of the plurality of lateral walls 18 comprises a flat section and an arc section, wherein the flat section and the arc section are adjacent connected to each other. A ratio between a distance for the flat section of a pair of opposing walls of the plurality of lateral walls 18 and a diameter (diagonal length) of the hexagonal engagement bore 17 about the arc section of the pair of opposing walls of the plurality of lateral walls 18 is approximately 1 : 1.154. More specifically, the ratio 1 : 1.154 is significantly smaller than the length to diameter (diagonal length) ratio of the industry standard square adaptors that is approximately 1 : 1.414. For example, a A” industry standard square engagement bore has a distance of 6.35 mm between a pair of opposing flat surface of the standard square engagement bore and a diameter (diagonal length) of 8.98 mm between a pair of opposing connection points of the standard square engagement bore. Whereas a W hexagonal engagement bore 17 has a length of 6.35 mm and a diameter (diagonal length) of 7.33 mm. Generally, the approximate 20% reduction in the diameter (diagonal length) of the hexagonal engagement bore 17 results in smaller sized production of the present invention and additional wall thickness for the attachment body 13. The length of the hexagonal engagement bore 17 along the central axis 16 from the first base 14 to second base 15 is greater than a length of the first torque tool socket 1 along the rotational axis 2 from first base 14 to the outer edge 3. The length of the hexagonal engagement bore 17 along the central axis 16 from first base 14 to second base 15 is greater than a length of the second torque tool socket 7 along the rotational axis 8 from second base 15 to the outer edge 9.

In reference to FIG. 6 and FIG. 9, the first torque-tool socket 1 further comprises a plurality of drive walls 6. More specifically, the plurality of drive walls 6 is radially distributed around the rotational axis 2 of the first torque-tool socket 1. Each of the plurality of drive walls 6 is perpendicular to an outer edge 3 of the first torque-tool socket 1. Preferably, the plurality of drive walls 6 are oriented in a hexagonal configuration to tighten or loosen a hexagonal fastener. However, the plurality of drive walls 6 can be oriented with any other types of geometric shapes to receive different types of industry standard fasteners. Furthermore, the first torque-tool socket 1 further comprises a first edge-diameter 4 and a first base-diameter 5 as shown in FIG. 5. The first edge-diameter 4 is delineated in between a pair of opposing walls of the plurality of drive walls 6 and positioned adjacent to an outer edge 3 of the first torque-tool socket 1. The first basediameter 5 is delineated in between the pair of opposing walls of the plurality of drive walls 6 and positioned adjacent to the first base 14 of the attachment body 13. In order to fully engaged with the fasteners, a ratio between the first base-diameter 5 and the first edge-diameter 4 is approximately 1 : 1 within the first torque-tool socket 1.

In reference to FIG. 6-7, the second torque-tool socket 7 further comprises a plurality of helical walls 12. More specifically, the plurality of helical walls 12 is radially distributed around the rotational axis 8 of the second torque-tool socket 7. Each of the plurality of helical walls 12 is tapered from an outer edge 9 of the second torque-tool socket 7 to the second base 15 of the attachment body 13. The tapered arrangement of the plurality of helical walls 12 enables the user to remove a damage fastener. Because the helical walls 12 is tapered, the benefits of the smaller diameter engagement bore 17, and the configuration of the male adaptor 44, would be even more obvious for the present invention.

More specifically, as shown in FIG. 10, the helical walls 12 comprises a plurality of ridges 21 and a plurality of ridge lines 22 that are vertically offset and not parallel with the rotational axis 8. The plurality of ridges 21 is extended from the second base 15 to the outer edge 9. The plurality of ridges 21 is preferably angled, offset, not ninety degrees perpendicular with the socket second base 15. The plurality of ridges 21 is angled from the second base 15 to the outer edge 9, in a clockwise direction when viewed from the outer edge 9 towards the second base 15. In other words, each of the plurality of ridge lines 22 is angled and contorted in a clockwise direction from the second base 15 to the outer edge 9 when viewed from the outer edge 9 towards the second base 15, and do not intersect the outer edge 9 or the second base 15 at right angles. Depending on the angle of orientation, each of the plurality of ridge lines 22 intersect the second base 15 and the outer edge 9 at acute angle between a range of 75 degrees and 89 degrees and/or at obtuse angle between a range of 91 degrees and 105 degrees. For left hand threaded fasteners, the plurality of ridge lines 22 is contorted in a counterclockwise direction from the second base 15 to the outer edge 9 when viewed from the outer edge 9 towards the second base 15. The plurality of ridge lines 22 is preferably sharp, straight, and preferably symmetrical but not parallel with each other from the second base 15 to the outer edge 9. In other words, a distance between a pair of adjacent ridge lines 22 adjacent to second base 15 is generally not equal to a distance between a pair of adjacent ridge lines 22 adjacent to the outer edge 9. The plurality of ridge lines 22 is preferably not vertically curved or spiral, however a curved or spiral could be used if the user prefers for certain applications. The plurality of ridge lines 22 may further incorporate a small radius at the meeting point of two corresponding ridges 21. On either side of each of the plurality of ridge lines 22, the plurality of ridges comprises a descending slope 23 and a concave channel 24. The descending slope 23 is preferably curved and joins the concave channel 24, which is also preferably curved of the same or similar radius. The concave channels 24 join each other at a channel base 25 to form an arc. However, the concave channels 24 may be of a non-curved shape such as angular shape or shapes to form the concave channels 24. In alternative embodiments, shown in FIG. 11, the descending slope 23 may be a flat portion and positioned on either side of the ridge line 22 and in between the ridge line 22 and the concave channel 24. The length distance of the flat portions perpendicular to the rotational axis 8 may be equal or unequal with each other and may be greater or less than a length of the concave channel 24. The benefits of the flat portion may assist in superior torque transfer to fastener due to larger engagement field. The flat portions would generally follow the length of each of the plurality of ridge lines 22 from the second base 15 to outer edge 9. The plurality of ridge lines 22 and the concave channel 24 are preferably configured symmetrical with each other from the second base 15 to the outer edge 9.

Generally, the second torque-tool socket 7 matches to the socket size of the first torque-tool socket 1. For example, when the first torque-tool socket 1 is sized as 1 inch driver socket to engaged with 1-inch fasteners, the second torque-tool socket 7 is also preferably sized to as 1 inch extractor socket to remove damage 1 inch fasteners. Furthermore, the second torque-tool socket 7 further comprises a second edge-diameter 10 and a second base-diameter 11 as shown in FIG. 5. The second edge-diameter 10 is delineated in between a pair of opposing ridge lines 22 of the plurality of helical walls 12 and positioned adjacent to an outer edge 9 of the second torque-tool socket 7. The second base-diameter 11 is delineated in between the pair of opposing ridge lines 22 of the plurality of helical walls 12 and positioned adjacent to the second base 15 of the attachment body 13. In order to fully engaged damaged fasteners, a ratio between the second base-diameter 11 and the second edge-diameter 10 ranges approximately 1 : 1.01 to 1 : 1.2 within the second torque-tool socket 7. Each of the plurality of ridge lines 22 has a degree of taper around the rotational axis 8 of the second torque-tool socket 7 that can vary by a range of between 1 degree and 10 degrees. The preferred range of taper between the of each of the plurality of ridge lines 22 adjacent to the outer edge 9 of the second torque-tool socket 7 and the second base 15 of the attachment body 13 is 2 degrees to 6 degrees.

In an alternative embodiment of the present invention, the first torque tool socket 1 may mimic all the features and components of the second torque tool socket 7 described aforementioned designed for use in either clockwise or counterclockwise direction. Alternatively, the second torque tool socket 7 may mimic all the features and components of the first torque tool socket 1 for the use in either clockwise or counterclockwise direction.

The preferred ratio range between a length of the second torque tool socket 7 along the direction of the rotational axis 8 and the second edge diameter 10 is a range of a length of a second edge-diameter 10 to a length 1 and 3 times a rotational axis 8 length. In other words, the second edge diameter 10 is 3 times the length of the second torque tool socket 7 along the direction of the rotational axis 8.

In reference to FIG. 12-14, the male adaptor 44 comprises a first end surface 33, a second end surface 32, a driver shaft 31, the hex portion 34, and at least one winged protrusion 26. More specifically, the male adaptor 44 extends from the first end surface 33 to the second end surface 32 as the at least one winged protrusion 26 laterally connected onto the male adaptor 44. The hex portion 34 is delineated from the first end surface 33 to the at least one winged protrusion 26. The driver shaft 31 is delineated from the second end surface 32 to the at least one winged protrusion 26. The male adaptor 44 may either be a single piece adaptor or alternatively may be separate pieces permanently joined to create a single piece. The at least one winged protrusion 26 is designed as the driver shaft 31 stop and depth limiter when inserted into the hexagonal engagement bore 17.

The at least one winged protrusion 26 comprises a bottom wing portion 28, an end surface 29, and a top wing surface 30 thus defining the parameters of each of the at least one winged protrusion 26. The benefit of the bottom wing surface 28 being tapered or ascending is the ability to limit and control the male adaptor 44 insertion depth. When the male adaptor 44 is inserted into the hexagonal engagement bore 17, the bottom wing surface 28 abuts with the outer edge 9 of the second torque-tool socket 7. Depending on the size of the second torque-tool socket 7, the engagement between the bottom wing surface 28 and the outer edge 9 would be at a specific location on the bottom wing surface 28 of the at least one winged protrusion 26, also known as an engagement point 39. In other words, because the bottom wing surface 28 is a tapered surface and positioned adjacent to the hex portion 34. The distance from the first end surface 33 to the connection point between the bottom wing surface 28 and the hex portion 34 is defined as an inner distance 36. The distance from the first end surface 33 to the connection point between the bottom wing surface 28 and the end surface 29 is defined as an outer distance 37. Furthermore, the inner distance 36 is smaller than the outer distance 37. As a result, when the male adaptor 44 is inserted into a smaller first torque-tool socket 1 or a smaller second torque-tool socket 7, the engagement point 39 would be closer to the inner distance 36 thus minimizing the inserted depth of the hex portion 34. Alternatively, when the male adaptor 44 is inserted into a larger first torque-tool socket 1 or a larger second torque-tool socket 7, the engagement point 39 would be closer to the outer distance 37 thus maximizing the inserted depth of the hex portion 34.

Because the bottom wing surface 28 intersects the hex portion 34 at an obtuse angle 35 and is ascending from the first end surface 33, the greater the distance of the bottom winged surface 28 engagement with the outer edge 9 from the hex portion 34 being the engagement point 39, the deeper the male adaptor 44 is able to be inserted into the second torque-tool socket 7. Alternatively, the closer the distance of the bottom winged surface 28 engagement with the outer edge 9 from the hex portion 34 being the engagement point 39, the shallower the male adaptor 44 is able to be inserted into the second torque-tool socket 7. The user could simply alter the angle of the obtuse angle 35 to change depth the male adaptor 44 that would be inserted into the second torque-tool socket 7. Even though the aforementioned engagement is explained in relation to the second torque-tool socket 7, the same principle applies when the male adaptor is engaged within the first torque-tool socket 1.

Further benefits of the present invention may include the ability to use a single male adapter 44 for various sized sockets saving the user cost and providing greater convenience and flexibility. For example, because the larger first torque-tool socket 1 or the larger second torque-tool socket 7 is longer in length and the fastener heads generally recess deeper into the socket body, for use on larger sockets the user could create a sharper angle between the at least one winged protrusion 26 and the bottom wing surface 28 to allow for deeper socket driver insertion and retain the benefit of magnetic fastener retention at the first end surface 33, likewise for the smaller first torque-tool socket 1 or the smaller second torque-tool socket 7, the user could lessen the angle between the at least one winged protrusion 26 and the bottom wing surface 28 to lessen the insertion depth of the male adaptor 44. A lateral width distance perpendicular to the rotational axis of each of the at least one winged protrusion 26 is preferably equal to or less than a width of each of the bracing surface lateral walls of the hex portion 34, however, in some embodiments it may be preferred for a lateral width distance of each of the at least one winged protrusion 26 is to be equal to or less than a cross-sectional diameter of the hex portion 34.

The bottom wing surface 28 is preferably a flat surface; however, as shown in FIG. 14, the surface could alternatively be at least one stepped surfaces 45 whereby each step can function as the engagement point 39 for different socket sizes, providing the user the ability to use a single male adaptor 44 for multiple socket sizes. The length of the step 45 both a parallel and perpendicular direction from the rotational axis may be any length as determined by the user for the specific size first torque tool socket 1 or second torque tool socket 7. Alternatively, the bottom surface 28 could be a concave or convex radial surface and yet providing the benefits described above. The top wing surface 30 maybe positioned at acute, right, or obtuse angles to the driver shaft 31 and is preferably flat but may be any shape or combination of shapes, A width of each of the at least one winged protrusion 26, perpendicular to a rotational axis of the male adaptor 44 and may be any width as preferred by the user.

Although the invention has been explained in relation to its preferred embodiment, it is to be understood that many other possible modifications and variations can be made without departing from the spirit and scope of the invention as hereinafter claimed.