Apparatus for tightening screw fasteners

Abstract

This application is directed to protecting applicant's HYTORC® Z system, which includes a multi-speed / multi-torque mode tool having a torque multiplication and oscillation mechanism without the use of an external reaction abutment, a force transmission means for use with such tool that produces in-line coaxial action and reaction, a drive means and a shift means that can be attached to a washer below a nut for use with such tool and force transmission means, associated washers and fasteners for use with such tool, force transmission means and drive means, and associated accessories for use with such tool, force transmission means, drive means, washers and fasteners. The HYTORC® Z System includes: Z-washers placed under various types of nuts or bolt heads, with multiple shapes, sizes, shapes, and serrations of engagement perimeter, such as washer / fastener radius engagement differentials, and with friction bias surfaces having relatively high friction against the flange surface and relatively low friction against the nut, such as friction coefficient increasing treatment means of various types, sizes, and locations; HYTORC® Z-gun, which combines high speed rundown for calibrated torque and incorporates a powerful intermittent (impact, vibration, ultrasonic, etc.) mechanism and a precise torque multiplier into the same tool; HYTORC® Z-socket with dual drive coaxial action and reaction, with an outer sleeve that reacts on the Z-washer and an inner sleeve that turns the nut or bolt head; AVANTI and ICE square drive systems, STEALTH Limited Clearance HYTORC® Z-Spline Adapters and Reaction Plates for compatibility with HYTORC® Z-Series Multipliers, Pneumatic JGUN Series, FLASH Guns, and Lithium Series Multipliers, etc.; HYTORC® Z-Washer and HYTORC® Z-Double Friction Washer combinations, including double-sided friction-enhanced face washers and / or HYTORC® Z-Nuts / Bolts for counter torque under the nut or bolt head on the opposite side of the joint; HYTORC® Z-Double Drive Offset Links for tight clearances using the HYTORC® Torque / Tension System and the HYTORC® Z-Oscillating Mechanism applied thereto; Z-Squirter Washers; Z-DTI Washers; HYTORC® Z-Washer and Nut Assemblies; Anti-Loosening Z-Washers and combinations thereof. Further disclosure includes tapered fastener assemblies, tapered torsion couplings, two-piece tapered nut assemblies, two-piece tapered threaded nut assemblies, HYTORC® Anti-Loosening Z-washers, nuts, smart studs, and any combination thereof.

Description

[Technical field]

[0001] (CROSS REFERENCE TO RELATED APPLICATIONS AND PATENTS) This application claims priority to and / or is either a continuation or continuation-in-part of the following commonly owned and / or co-pending patent applications, the entireties of which are incorporated herein by reference: U.S. patent application Ser. No. 62 / 887,357, entitled "Apparatus for Tightening a Threaded Fastener," filed on August 15, 2019; U.S. patent application Ser. No. 62 / 754,563, entitled "Apparatus for Tightening a Threaded Fastener," filed on November 1, 2018; U.S. patent application Ser. No. 15 / 570,743, entitled "Apparatus for Tightening a Threaded Fastener," filed on October 30, 2017; No. 15 / 570,684, entitled "Apparatus for Tightening a Threaded Fastener," filed on October 30, 2017; U.S. patent application Ser. No. 15 / 570,670, entitled "Apparatus for Tightening a Threaded Fastener," filed on October 30, 2017; International Application No. PCT / US2017 / 059121, entitled "Apparatus for Tightening a Threaded Fastener," filed on October 30, 2017; No. 63 / 302,389, filed March 2, 2016, entitled "Apparatus for Tightening a Threaded Fastener," and International Application No. PCT / US2017 / 020548, filed March 2, 2017, entitled "Apparatus for Tightening a Threaded Fastener," which claims priority to International Application No. PCT / US2016 / 029899, ​​filed April 28 ... which claims priority to International Application No. PCT / US2016 / 029899, ​​filed April 28, 2016, entitled "Apparatus for Tightening a Threaded Fastener," which claims priority to International Application No. No. 62 / 302,389, filed March 2, 2016, entitled "Apparatus for Tightening a Threaded Fastener," and International Application PCT / US2016 / 029899, ​​filed April 28, 2016, which claims priority to U.S. patent application Ser. No. 62 / 153,619, filed April 28, 2015, entitled "Apparatus for Tightening a Threaded Fastener;"No. 62 / 012,009, entitled "Apparatus for tightening a screw fastener," filed June 13, 2014; International Application No. PCT / US2014 / 035375, entitled "Apparatus for tightening a screw fastener," filed April 24, 2014; U.S. Patent Application No. 61 / 940,919, entitled "Apparatus for tightening a screw fastener," filed February 18, 2014; No. 61 / 916,926, entitled "Apparatus for Tightening a Threaded Connector," filed December 17, 2013; U.S. patent application Ser. No. 13 / 577,995, entitled "Apparatus for Tightening a Threaded Connector," filed August 9, 2012; and U.S. patent application Ser. No. 13 / 113,693, entitled "Method for Tightening and Loosening a Threaded Fastener," filed May 23, 2011. No. PCT / US2014 / 70996, filed December 17, 2014, entitled "Apparatus for Tightening a Threaded Fastener"; U.S. Patent Application No. 62 / 012,009, filed June 13, 2014, entitled "Apparatus for Tightening a Threaded Fastener"; International Application No. PCT / US2014 / 035375, filed April 24, 2014, entitled "Apparatus for Tightening a Threaded Fastener"; No. 61 / 940,919, filed February 18, 2014, entitled "Apparatus for Tightening Threaded Fasteners," and International Application No. PCT / US2014 / 71000, filed December 17, 2014, which claims priority to U.S. patent application Ser. No. 61 / 916,926, filed December 17, 2013, entitled "Apparatus for Tightening Threaded Fasteners;"No. 61 / 430,105 and No. 61 / 302,598, filed on January 5, 2011 and February 9, 2010, respectively, entitled "Apparatus for Tightening Threaded Fasteners"; U.S. Patent Application No. 13 / 577,995, filed on August 9, 2012, entitled "Apparatus for Tightening Threaded Fasteners"; and U.S. Patent Application No. PCT / US2012 / 023693, filed on February 2, 2012, entitled "Apparatus for Tightening Threaded Fasteners"; No. 61 / 370,015, filed August 2, 2010, which claims priority to International Application No. PCT / IB2011 / 002658, entitled "CONIC GEOMETRY FOR TORSIONAL COUPLING DURING BOLT TIGHTENING," which claims priority to U.S. application Ser. No. 13 / 814,229, filed March 27, 2013, entitled "Apparatus for Tightening Threaded Fasteners," 371(c)(1)(2)(4); U.S. application Ser. No. 62 / 153,619, filed April 28, 2015, entitled "Apparatus for Tightening Threaded Fasteners," and / or U.S. application Ser. No. 62 / 302,389, filed March 2, 2016, entitled "Apparatus for Tightening Threaded Fasteners.";

[0002] This application is related to the following patent application(s), the entireties of which are incorporated herein by reference: U.S. Patent No. 5,931,618, entitled "Direct Tension Indicating Washer," which is a continuation of U.S. Patent No. 5,769,581, issued on June 23, 1998, and entitled "Direct Tension Indicating Washer"; U.S. Patent No. 6,425,718, entitled "Direct Multiple Tension Indicating Washer With First and Second Height Bumps," issued on July 30, 2002; U.S. Patent No. 8,002,641, entitled "Method of Making Direct Tension Indicating Washer," issued on August 23, 2011; U.S. Patent No. 8,079,795, entitled "Washer for Fastening and Loosening Threaded Connectors," issued on December 20, 2011; and U.S. Patent No. 8,079,795, entitled "Method for Fastening and Loosening Threaded Connectors," issued on March 17, 2015. No. 8,978,232, entitled "Fastening Device"; U.S. Patent No. 5,137,408, filed December 3, 1991, for "Mechanical Tensioning Device"; U.S. Patent No. 5,318,397, filed May 7, 1992, for "Mechanical Tensioning Device"; U.S. Patent No. 5,622,465, filed April 26, 1996, for "Locking Nut"; U.S. Patent No. 5,640,749, filed June 13, 1995, for "Method and Apparatus for Stretching and Loosening a Stud"; U.S. Patent No. 5,888,041, filed October 17, 1997, for "Locking Nut"; and U.S. Patent No. 6,254,322, filed March 3, 1998, for "Bolt, Washer and Sleeve With Bolt Member for Applying Force to the Bolt Member and Sleeve." [Background technology]

[0003] Threaded fasteners, including bolts, studs, nuts and washers, are known and used in traditional bolting applications. Maintenance and repairs in industrial applications begin with loosening and end with tightening these threaded fasteners. Naturally, industries seek to reduce production loss during scheduled, unplanned and / or emergency maintenance and / or repairs.

[0004] Mechanical fastening with helical threaded elements is typically accomplished with bolts, studs, screws, nuts and washers. Washers are thin members that can be placed between the fastener and the fixed part. Washers are typically used to prevent damage due to friction of the assembled elements. Washers are also commonly used to distribute stress evenly and control friction losses.

[0005] Conventional nuts are usually made from a single piece of continuous, homogenous steel. The outer geometry usually has a rotational coupling feature so that it can be tightened by applying torque with an outer mating device or tool. The most common rotational coupling feature is a hexagon, but any other rotational coupling means are possible, including features such as squares, multiple hexagons, slots, splines, grooves, or holes. The nuts usually have an inner diameter with helical threads to mate with the threads of the stud, which allows the nut to translate on the stud with only relative rotational motion between the stud and the nut. In other words, they are used to hold and / or transfer loads to male threaded fasteners.

[0006] There are two ways to tighten and / or loosen threaded fasteners: torque and tension. However, until applicant's innovation, hydraulic torque application and hydraulic tension application could not be performed with the same tool. An operator required separate tools to torque and tension a threaded fastener.

[0007] The torque method has the advantages of being applicable to most existing threaded fasteners, being accurate to within five percent (5%) of the precalculated rotational resistance of the nut, avoiding unintended loosening, ensuring a more uniform circumferential bolt load than the tension method, and overcoming uneven lubrication, foreign particles on the underside of the nut or on the top surface of the flange, and minor thread damage. However, the torque method has the disadvantages of being subject to both unknown thread and facial friction, requiring the use of a backup wrench applied to the nut on the other side to hold the bottom of the threaded fastener stationary, resulting in unknown residual bolt loads, and subjecting the bolt torsion and side loads, both of which adversely affect bolting applications. To sustainably and accurately use the torque method in bolting, it is necessary to achieve thread and bearing facial friction and eliminate torsion and side loads.

[0008] The advantage of the tension method is the absence of torsion and side loads. However, the tension method has the following disadvantages: it requires the bolt to extend beyond the nut and around it by at least the bolt diameter so that it can be pulled upwards by the tensioning tool, which often requires bolt and nut replacement, is accurate to within 25% of the estimated rotational resistance, results in unpredictable manual nut seating, suffers from both unknown thread and facial friction, often does not over-tighten and stretch the fastener, leads to uncontrolled fastener loosening due to load transfer from the puller, and results in unknown residual bolt loads. To use the tension method sustainably and accurately in bolting, it is necessary to eliminate stud / bolt tension and load transfer.

[0009] Torque power tools are known to those skilled in the art and include those that are pneumatically, electrically, and hydraulically driven. Torque power tools generate a rotational force and an equal and opposite reaction force to tighten and / or loosen threaded fasteners. Hydraulic tensioning devices use a tensioning tool to apply hydraulic pressure to the bolt. The hydraulic pressure is typically 10% to 20% higher than the desired bolt extension, which causes the stud to be over-tensioned. The nut is then hand-tightened until snug, the pressure on the cylinder is relieved, the stud springs back, and the load is transferred from the bridge to the nut, which compresses the joint with a clamping force.

[0010] In relation to torque, traditional reaction fixtures abut against a viable and accessible stationary object, such as an adjacent fastener, to prevent the tool housing from rotating backwards while the fastener is rotating forwards. This abutment force exerts a pulling force, or side load, perpendicular to the bolt axis on the nut to be tightened or loosened. The reaction force of a square drive tool is transmitted through a reaction arm that tends to untwist the cylinder end of the tool and / or bend the drive tool. Applicant's innovation in coaxial reaction transmission can be found in HYTORC®·AVANTI®. The evolution of the traditional reaction fixtures of the prior art is disclosed, for example, in US Pat. Nos. 5,993,133, 5,949, 5,103, 5,106, 5,109, 5,113, 5,116, 5,117, 5,118, 5,119, 5,120, 5,132, 5,143, 5,151, 5,152, 5,153, 5,154, 5,155, 5,156, 5,157, 5,158, 5,159, 5,160, 5,161, 5,162, 5,163, 5,164, 5,165, 5,166, 5,167, 5,168, 5,169, 5,171, 5,172, 5,173, 5,174, 5,175, 5,176, 5,177, 5,178, 5,179, 5,182, 5,183, 5,186, 5,187, 5,189, 5,190, 5,192, 5,197,

[0011] The industry is moving away from cumbersome and complicated hydraulic tensioning devices, and also away from torque applications based on applying twist and side loads to fasteners. True mechanical tensioning has become very popular.

[0012] Applicant has developed and solved many bolting challenges with its HYTORC® NUT® mechanical tensioning device product line, and drivers and tools for use therewith. The HYTORC® NUT is an example of a self-reacting nut and includes an inner sleeve, an outer sleeve, and a washer. The washer is used as a reaction point for application of input torque to the outer sleeve. In a reaction fastener, the outer sleeve acts as a nut while the inner sleeve is an extension of the stud and is rotationally coupled with the washer. This rotational coupling prevents sliding motion between the inner sleeve and the stud threads during application of torque to the outer sleeve. A self-reacting nut with the same outer shape as a conventional nut experiences higher bearing surface stresses. The bearing surface stresses are greater because the inner diameter of the outer sleeve is increased to allow space for the inner sleeve which causes a thinner wall thickness than a standard nut.

[0013] Additionally, devices are known for connecting or mating the reaction or output shaft of a torque output device to a fastener used in bolting. Self-reacting three-part mechanical tension fasteners typically have splined, hexagonal or square features that allow for torsional coupling with the reaction member of the torque input device. This is accomplished with mechanical rotational interference between the two parts. This interference is typically created by male and female engagement between any two mating features that prevent rotation between the two parts.

[0014] Applicant has evolved bolting and solved many bolting challenges with its HYTORC® SMARTSTUD® mechanical tensioning device product line and associated drivers and tools. HYTORC® SMARTSTUDs are an example of a three-piece mechanical tensioning stud device. They consist of a stud, a nut, and a washer. The studs have male threads on both ends. Beneath the top threads, the studs have a spline or other geometry that provides rotational coupling with the inside diameter of the washer. The top side of the stud also has a spline or other geometry that allows for rotational coupling with the reaction shaft of the torque input device. The nut is internally threaded to engage the top threads of the stud. The nut will have a spline or other geometry to allow for introduction of torque from the torque input device. The washer has an inner geometry that rotatably mates with the spline or other geometry below the top threads of the stud.

[0015] In bolting applications, the stresses are typically close to the elastic limit of the material. The reaction features that connect the HYTORC® SMARTSTUD to the torque input device usually need to be oversized to prevent damage to the elastic material. Thus, it is not possible with known coupling features to apply large torques against internal features such as square, hexagonal or internal splined holes on the top surface of the stud. Therefore, highly stressed bolting applications must have an external feature on the top side of the stud that can connect a large enough reaction shaft from the torque input device.

[0016] In other words, the HYTORC® NUT has two sleeves, one inside the other, whereby the inner sleeve is mated with a splined washer such that only axial movement of the inner sleeve is permitted. The inner sleeve is threaded onto the stud or bolt as a unit. A proprietary driver holds the inner sleeve and rotates the outer sleeve. The stud is pulled up along with the inner sleeve and tensioned without overstretching and springback, similar to hydraulic tensioning devices. The inner nut never turns against the stud threads under load, eliminating the possibility of galling or other damage to the bolt threads. HYTORC® NUT mechanically utilizes tool action and reaction forces during tightening and loosening, converts torque into bolt stretching without twisting instead of pulling as in tension methods, allows accurate bolt load calibration, accurately sets and achieves desired residual bolt extension or load compared to torque methods, eliminates side loads, twisting, load transfer and loosening, reaction arms, back-up wrenches, pullers and bridges, eliminates bolt extension measurements for critical applications, increases safety, error-free bolting, joint reliability and speed, reduces bolting time by over 50%, and works on all joints without modification. It improves torque and tension by stretching the bolt instead of pulling it, preventing unsafe and fastener- and joint-damaging mechanical rebound. Operator sets and achieves bolt load at 30%-90% of yield point anywhere.

[0017] The technological evolution of HYTORC® NUT and HYTORC® SMARTSTUD is disclosed, for example, in Applicant's US Pat. Nos. 5,991,133, 5,991,143, 5,991,152, 5,991,162, 5,991,172, and 5,991,182, the entireties of which are incorporated herein by reference.

[0018] However, the HYTORC® NUT and HYTORC® SMARTSTUD have their own set of challenges. The end user must replace the standard nut with a precision machined, treated, and lubricated unit. In addition, the inner sleeve must be relatively radially thick at the connection point with the washer. Such a connection can sometimes hold the entire reaction force applied to the outer sleeve. In addition, the HYTORC® NUT is expensive to manufacture and is often difficult to sell to end users of traditional bolts who want to minimize costs. Furthermore, in some versions of the HYTORC® NUT, the nut must be constructed with two sleeves, and since the outer diameter of the sleeves must match the outer diameter of a regular nut, both sleeves require less material than a regular nut. This requires the use of high-strength materials, which can cause some customers to be reluctant to change materials and fear the unknown. Other versions of the HYTORC® NUT require bolt modifications, which are expensive and not easily accepted by the industry.

[0019] Applicant has developed bolting and solved many of its challenges with the HYTORC® product line and drivers and tools for use therewith. The HYTORC® WASHER® was the first example of a reaction washer used as a reaction point for torquing the nuts and bolts of helical threaded fasteners. The reaction washer is positioned in the load path of the bolt or stud and thus always experiences the same load. In a reaction washer system, a turning torque is applied to the upper nut or bolt while an opposite reaction torque is applied to the reaction washer. The upper nut or bolt and the mating reaction washer experience the same load and torque. Thus, only frictional forces govern the relative motion. The components with the lower coefficient of friction tend to move while the other components remain relatively fixed.

[0020] HYTORC®·WASHER® self-reacting load washers have an internal threaded section that mates with the threads of a traditional bolt. The washer fits under a regular nut, preventing the bolt from turning while providing a reaction point for a driving tool. The washer is tightened with a unique dual socket. The outer socket holds the washer and the inner socket turns the regular nut, which pulls the stud up through the washer. The reaction force of the tool is converted into a holding force that holds the HYTORC®·WASHER in place. The holding force holds the section, and therefore the bolt, in place as the nut is turned until the bolt stretches, driving an axial section into the HYTORC®·WASHER. This improves torque and tension by stretching the bolt instead of pulling it. With no load transfer-relaxation or mechanical rebound, stretches up to 90% of yield point are possible.

[0021] HYTORC® WASHERs provide known bearing surface friction for more uniform residual bolt load, do not require precision machining of countersink surfaces, minimize torsion and side load in the bolting process, prevent the bolt from rotating with the nut, produce straight axial bolt extension without the need for reaction arms and back-up wrenches, increase uniformity of residual bolt load and perimeter joint compression, reduce setup time, increase bolting speed, even in upside-down applications the bolt is axially oriented allowing hands-free operation, increase bolting security, and minimize the risk of fastener and joint damage.

[0022] Innovations in the HYTORC® WASHER product line, and drivers and tools for use therewith, are disclosed, for example, in Applicant's US Pat. Nos. 2004 / 0139995, 2004 / 0139995, and 2006 / 0139974, the entireties of which are incorporated herein by reference.

[0023] However, the HYTORC®·WASHER presents a series of challenges. The washer adds unnecessary height to bolting applications. End end users must often replace standard studs and bolts with longer versions due to regulations that require two or more threads to protrude from the nut when tightened. In addition, the HYTORC®·WASHER is more expensive to manufacture than traditional washers and is often difficult to sell to cost-minimizing end users of traditional bolts. Furthermore, the HYTORC®·WASHER will rotate freely and in the opposite direction if the nut friction is high. In operation, the HYTORC®·WASHER has two facial frictions and the nut has facial and thread friction, so the overall friction of each is close to the same, i.e. the HYTORC®·WASHER may rotate or the nut may rotate. To avoid this, a preload is required. This preload cannot be achieved if both the HYTORC®·WASHER and the nut are rotated downwards at the same time. Finally, although side load and torsion are eliminated, corrosion still builds up in the threads, thereby not eliminating thread galling.

[0024] The Applicant has further developed industrial bolt fastening and solved many bolt fastening problems with HYTORC® and SMARTWASHER® product lines, as well as drivers and tools for use therewith. Such a multi-purpose washer having such self-reaction used for tightening and loosening screw connectors includes a nut and a bolt having an axis, and the bolt is introduced into an object with the washer interposed between the nut and the object, so that the first bearing surface of the washer on one axial side cooperates with the nut, and the second bearing surface of the washer on the opposite axial side cooperates with the object. The washer includes a radially outer body having a radially inner opening configured to be larger than the diameter of the bolt and a radially outer surface configured to absorb the reaction force of the tool, and the washer further includes a radially inner portion disposed radially within the outer body within the radially inner opening and engageable with the threads of the bolt, and this portion can be coupled to the outer body by limited axial frictional movement with respect to the body, and the washer further includes a spacer configured to be disposed between the radially inner segment and the nut, and the spacer is also disposed radially within the outer body within the radially inner opening and is axially spaced from the radially inner portion. The outer body, the radially inner portion, and the spacer can be assembled, disassembled, and used together or individually.

[0025] The Applicant used the radially outer body and the radially inner portion together interposed between the nut and the object for applications where uniform and accurate bolt elongation is required. When the nut is rotated by a tool with a given force, the radially outer body receives a given force from the tool in the opposite direction. While the radially outer body remains stationary, the radially inner portion engaging the threads of the bolt actively resists the rotation of the bolt. Only the bolt elongates or relaxes. In this case, the washer consists of a radially outer body and a radially inner segment and functions as a tension washer.

[0026] Applicant has used a radially outer body, a radially inner part and a spacer interposed between the nut and the object for applications where precise bolt elongation is required and where the bolt elongation must be controlled. When the nut is turned by a tool with a given force, the radially outer body receives a given force from the tool in the opposite direction. The radially outer body remains stationary while the radially inner part, which engages with the bolt thread, actively prevents the bolt from turning. Only the bolt elongates or relaxes, while the radially inner part moves axially, while the spacer limits the axial movement of the part. In this case, the washer consists of the radially outer body, the radially inner part and the spacer, and functions as a precision washer.

[0027] Applicant has used only the radially outer body of the washer between the nut and the object for typical applications where uniform and precise bolt elongation is not required. The radially outer face of the body is used to absorb an equal and opposite reaction force when the tool applies a turning force to the nut. The nut turns but the radially outer body remains stationary, and in this case the washer consists of only the radially outer body and functions as a reaction washer.

[0028] The HYTORC® SMARTWASHER offers the benefits of the HYTORC® WASHER in a lower cost, more flexible package. The technological advances in the HYTORC® SMARTWASHER product line, and drivers and tools for use therewith, are disclosed, for example, in Applicant's U.S. Patent No. 6,313,633, the entirety of which is incorporated herein by reference.

[0029] However, the HYTORC® SMARTWASHER suffers from the same set of challenges as the HYTORC® WASHER. The washer adds unnecessary height to bolting applications. End users must often replace standard studs and bolts with longer versions due to regulations that require two or more threads to protrude from the nut when tightened. In addition, the HYTORC® SMARTWASHER is more expensive to manufacture than traditional washers and is often difficult to sell to cost-minimizing end users of traditional bolts. Specifically, applicants have found that uniform, accurate, and precise bolt extension is not possible when only the radially outer body of the HYTORC® SMARTWASHER is used as a reaction washer. In addition, the use of thread inserts with the radially outer body has provided uniform and accurate bolt extension, but stud travel is limited to the washer thickness. Travel is further hindered by the use of spacers. Finally, although side loads and twisting are eliminated, corrosion still accumulates on the threads, which does not eliminate thread galling.

[0030] Furthermore, the HYTORC® SMARTWASHER will rotate freely and in the opposite direction if the nut friction is high. During operation, the HYTORC® SMARTWASHER has two facial frictions and the nut has facial and thread friction, so the total friction of each is close to the same, i.e. the HYTORC® SMARTWASHER may rotate or the nut may rotate. To avoid this, a preload is required. This preload cannot be achieved if both the HYTORC® SMARTWASHER and the nut are rotated downwards at the same time.

[0031] For conventional reaction washer systems, lubricant must be applied to selectively bias the washer to remain stationary under higher friction than the nut or stud, which causes the stud or nut to rotate and generate a load through the helical mating threads. The necessary lubricant for biasing is undesirable and makes it difficult to control the step in the reaction washer installation process. Even a small amount of lubricant on a conventional reaction reaction washer has the detrimental effect of allowing the reaction washer to rotate or slip in front of the nut or bolt. If the washer rotates in front of the helical threaded bolt or nut, the system cannot generate the bolt load. Improper management of the lubricant or friction surface often results in unintended sliding or rotation of conventional reaction washers.

[0032] Other examples of reaction washers in the prior art include those disclosed in U.S. Pat. Nos. 5,233,133, 5,293,322, 5,293,333, the entirety of which are incorporated herein by reference. These reaction washers are intended as an alternative to jam nuts and Belleville washers, since they store preload or live load energy by elastically deforming under load. In most embodiments, threaded holes are incorporated to minimize side loads applied to the bolt. The area of ​​contact of these concave and / or convex reaction washers with the object is small compared to the total surface area of ​​the bottom washer face. Non-threaded holes are disclosed in one embodiment. Friction enhancements include ridges, such as nibs in a hex washer shape, planar knurled extensions that are cut or dug into the object surface. Substantially flat reaction washers without friction enhancements are also disclosed.

[0033] Applicant has sought to increase fastener rotation speeds in fluid operated torque power tools. The HYTORC® XXI® is a fluid operated wrench having a fluid operated drive including a cylinder, a piston having a piston rod with a piston rod end reciprocable within the cylinder, a ratchet mechanism having a ratchet with a plurality of teeth, and at least two pawls operatively connectable to the piston rod end and engageable with teeth of the ratchet, such that during a forward stroke of the piston, one of the at least two pawls engages with at least one ratchet tooth while the other of the at least two pawls ratchet over the at least one ratchet tooth, whereas during a return stroke of the piston, the other of the at least two pawls engages with the at least one ratchet tooth while the one of the at least two pawls ratchet over the at least one ratchet tooth. At least one of the at least two pawls is disengageable from the teeth of the ratchet and can be lifted above the teeth of the ratchet. The HYTORC® XXI also includes a disengagement unit actuable by an operator separately from the drive, which acts on at least one pawl to separate it from the ratchet teeth and lift it above the ratchet teeth. This anti-backlash feature allows the ratchet to rotate backwards to release accumulated twist and material bending, so the fluid-operated wrench can be removed from the job. The HYTORC® XXI is the world's first continuously rotating hydraulic wrench. This wrench makes the tool up to three times faster than other wrenches on the market. The HYTORC® NUT and HYTORC® WASHER are particularly advantageous when used with the HYTORC® XXI. The HYTORC® XXI is disclosed in Applicant's U.S. Pat. No. 5,399,433, the entire contents of which are incorporated herein by reference.

[0034] Applicant then applied its thorough understanding and innovation in torque power tools to handheld pneumatic torque multiplier tools, specifically by creating the HYTORC®·jGUN® product line, and drivers and tools for use therewith. Applicant markets these tools under the trade names HYTORC®·jGUN Single Speed, Dual Speed, and Dual Speed ​​Plus. Once the nut strikes the flange face, there is only a small degree of rotation to tighten or loosen the nut. Customers desire high rotation speeds to quickly run down or run up the nut. Known impact wrenches that provide high run down and run off speeds have the disadvantage of being inaccurate and rotating slowly when the nut strikes the flange face. Conversely, known handheld torque power tools, while torque accurate, are relatively slow when running up and down a fastener. Yet, they are significantly faster than impact guns when the nut turns on the flange face.

[0035] The motor housing in hand-held torque multiplier tools is separate from the gear housing so that the torque cannot exceed the torque resistance of the operator's arm / hand. Otherwise, the motor housing of the tool cannot be held and would spin in the operator's hand. Numerous motor-driven torque multipliers are available on the market, some of which have dual speed mechanisms, some react at the bolt tip, which requires a special bolt, and others have a reaction arm. Whatever torque or speed is applied, these gear housings rotate in the opposite direction to the output shaft. At high speeds, the rotating parts in existing hand-held torque multiplier tools require bearings because the gear and output shaft rotate at high speeds within the gear housing. High-torque versions of such tools are too large and too heavy.

[0036] The HYTORC® jGUN product line includes tools with run-down or run-up speeds. The gear housing along with the inner gear assembly and output drive rotate in the same direction at the same high speed. The operator simply switches the tool from applying a rotational force to the gear and output shaft in one direction and simultaneously applying an opposite rotational force to the gear housing. Note that the HYTORC® NUT and HYTORC® WASHER product lines, and drivers and tools for use therewith, are compatible with the HYTORC® jGUN dual speed. For example, in the high speed / low torque embodiment of the HYTORC® jGUN dual speed, the drive socket with the nut and the reaction socket with the HYTORC® WASHER always rotated together and at the same high speed and low torque. The HYTORC® WASHER and nut are held together as one unit by a pin until the nut seats on the HYTORC® WASHER. The torque increases and the pin breaks down by shear, so that the nut is rotated at high torque and low speed while the HYTORC®·WASHER becomes a stationary object and therefore a reaction point. The integration of the HYTORC®·WASHER with known nuts is no longer acceptable, because the broken joint pieces affect the coefficient of friction, can lead to galling of the threads and can leave harmful and unwanted deposits at the thread interface.

[0037] When not used with the HYTORC® WASHER, the HYTORC® jGUN required the use of a reaction fixture to deflect the reaction force generated during nut turning against a stationary object. Rundown speed must be limited to avoid the reaction arm slamming into an adjacent nut at high speeds, which could otherwise cause an accident if the operator's limbs are in its path. Reaction arm abutment is necessary for the low speed, high torque modes for tightening or loosening fasteners. However, reaction arms are not desirable for the high speed, low torque modes of operation, again to avoid accidents and OSHA recordable situations.

[0038] Applicant has applied its thorough understanding and innovation in torque power tools with reaction attachments and the HYTORC® jGUN product line to further develop handheld pneumatic torque multiplier tools. Applicant has created the HYTORC® FLIP-Gun product line, and drivers and tools for use therewith. The HYTORC® FLIP-Gun includes a positionable reaction arm. When positioned in a first position, the torque multiplication unit is switched to a high speed, low torque mode, and the reaction arm can be used as a handle by an operator while perpendicular to the tool axis. When the reaction arm is in a second position coaxial to the tool axis, the torque multiplication unit is switched to a low speed, high torque mode, and the reaction arm can abut against a stationary object because high torque cannot be absorbed by the operator.

[0039] Often application characteristics adversely affect the bolting operation, including, for example, corroded, dirty, kinked, debris-containing, burred, galled, irregular, misoriented, misaligned, and / or unevenly lubricated stud and nut threads and surfaces. Such adverse bolting application characteristics often result in significant production losses. Naturally, the industry seeks to reduce production losses during scheduled, unscheduled, and / or emergency maintenance and / or repairs.

[0040] Applicant has further innovated handheld pneumatic torque multiplier tools, specifically by creating the HYTORC®·THRILL® product line, and drivers and tools for use therewith. The HYTORC®·THRILL is a handheld, dual mode output driven torque multiplier tool that operates in both reaction force free and reaction force assisted tightening and loosening of industrial fasteners. The tool includes a motor for generating a rotational force for rotating a fastener, a rotational force multiplication mechanism for a low speed / high torque mode including a plurality of rotational force multiplication transmitters, a rotational force impact mechanism for a high speed / low torque mode including a plurality of rotational force impact transmitters, a housing operatively coupled to at least one multiplication transmitter, and a reaction arm for transmitting a reaction force generated in the housing during the low speed / high torque mode to a stationary object, wherein during the low speed / high torque mode, the at least two multiplication transmitters rotate relative to one another, and during the high speed / low torque mode, the at least two multiplication transmitters are unified to achieve a hammer action from the impact mechanism. Advantageously, the HYTORC® THRILL minimizes vibration exposure to the operator, provides high rotational inertia due to the high mass resulting from the cooperation of the multiplier and impactor mechanisms in the high speed, low torque mode, which increases the torque output of the impactor mechanism, allows fasteners to be run down and run off at high speeds without the use of reaction fixtures, and loosens stuck, highly torqued or corroded fasteners from joints when higher torque is required than can be absorbed by the operator to overcome highly adverse threaded fastening application characteristics such as thread and face deformation and / or thread galling, and tightens fasteners to a desired higher and more precise torque using reaction fixtures in the second mode.

[0041] The impact mode cannot operate on the HYTORC® THRILL during low speed / high torque (multiplication) mode because the positionable reaction arm engages a stationary object and the impact mechanism is locked out during torque multiplication mode. However, it should be noted that during high speed / low torque mode, the rotational force from the motor is transferred through the initial step of the multiplication mechanism to the output shaft, thereby running down or up a nut or bolt head that offers little or no resistance. The impact mechanism is activated when a fastener exhibits adverse bolting characteristics and thus requires an intermittent force to overcome such deformation.

[0042] Please refer to Applicant's latest technological advances in the electrically powered HYTORC®·FLASH® Guns and the portable HYTORC®·Lithium·Series® Guns which are electrically powered but have batteries.

[0043] Technical developments in drivers and tools for use with the HYTORC® jGUN, FLIP-Gun, THRILL, HYTORC® FLASH gun, and HYTORC® Lithium Series guns are disclosed, for example, in Applicant's U.S. Pat. Nos. 3,613,633; 3,613,655; 3,711,317; and 3,893,367, the entireties of which are incorporated herein by reference.

[0044] Despite recent innovations by applicant's THRILL, side loading and thread galling remain major problems in industrial bolting applications and are not addressed at all by commercially available multiplier tools. Galling is material wear caused by a combination of friction and adhesion between metal surfaces during lateral movement or sliding, often due to insufficient lubrication. When material galls, parts are pulled from the contacting surfaces and become stuck or even friction welded to the adjacent surfaces, especially when the forces compressing the surfaces together are large. Galling often occurs in high load, low speed applications. It involves the visible transfer of material as it adheres and pulls from one surface, and the material remains stuck to the other surface in the form of bumps. Galling is not usually a gradual process, but occurs immediately and spreads rapidly as the bumps induce larger galling.

[0045] Corrosion of fasteners that have been tightened for a long time usually occurs between the mating threads of the nut and bolt, and between the nut and the flange. Corrosion can be caused by several things including chemicals, heat, moisture, and lubricants. In high temperature applications, for example, lubricants applied during tightening dry out and bind the threads together over time. Additionally, chemical reactions in and out of containers often cause galvanic corrosion. During loosening, female thread corrosion pushes dried grease along the bolt threads. The reaction force applied to a stationary object exerts an equal force on the near side of the nut to be turned. In fact, the side load, or abutment force, on a tool can be three to four times its pound-foot torque output, because the abutment point of the reaction arm is often half when it is more than a foot (30.48 cm) away from the center of the drive.

[0046] This side load causes the nut and bolt threads to engage with enormous force on the side closest to where the load is applied, so dried grease builds up in that location as the nut is turned. Irregularities in the threads often cannot be overcome. Only half the threads between the bolt and nut are engaged and the threads begin to grip. This causes the bolt threads to gall, requiring significantly higher torque and therefore significantly higher side load to remove the nut. This can destroy the bolt and nut threads. Fasteners often bind to the extent that all of the turning force is used by thread friction. This can result in failure of the fastener or the tool turning the fastener. The torque power tool initially used to tighten the fastener is often not sufficient to loosen the same corroded fastener. Such corroded fasteners may require pound-feet loosening torque values ​​that are one to three times the tightening torque, and additional more powerful tools may be required. High temperature bolting applications, such as in turbines and casings, are usually critical and require stainless or precision manufactured fasteners with extremely high replacement costs. In addition, the use of precision thread bolts, which have recently become popular, increases this problem.

[0047] Thread galling can still occur when the tool does not apply a side load to the fastener because dried grease accumulates in the mating threads during the loosening of the nut. Such loosening requires a torque at one point that is higher than the original tightening torque. Such torque, when applied, results in thread galling. This also occurs between the inner and outer sleeves when using the HYTORC® NUT. It is common practice for operators to hit corroded fasteners with a sledgehammer to break up the corrosion before applying the loosening torque. This practice is dangerous, can destroy the bolt threads that extend beyond the nut, and is barbaric. Unwanted galling can also occur between the face of the nut and the face of the flange because the side load changes the vertical orientation of the nut as it is being turned. This increases the turning friction of the nut and makes the bolt load generated by the loosening torque unpredictable, which leads to poor aesthetics, non-parallel joint closure, system leaks, and tool, fastener, and joint failures.

[0048] Known washers can reduce surface galling between the threaded fastener and the nut and joint because the washers are constructed of a harder material. ASME PCC-1-2010, Appendix M states, "By providing a smooth, low-friction bearing surface for the nut, through-hardened steel washers are generally recognized to improve the conversion of input torque to bolt preload. The washers protect the flange contact surface from damage caused by the rotating nut, an important consideration when torque methods (manual or hydraulic) are used for bolt tightening." However, known washers do not minimize and / or eliminate surface galling and thread galling caused by side loads. Known washers can also move when tightened, so the washer can rotate with the nut or bolt head instead of remaining fixed. This can affect the torque-tension relationship.

[0049] Another purpose of installing washers in a typical bolted system is to distribute the load under the bolt head and nut by providing a larger area under stress, otherwise the bearing stress of the bolt may exceed the bearing strength of the connecting material, which will result in loss of bolt preload and material creep.

[0050] Hardening treatments, such as nitriding, have been found to prevent galling on the friction surfaces of fasteners. Nitriding hardens the surface of the metal, but makes it more susceptible to fracture, especially when tensile stresses are present. Nitriding can be used to prevent galling on compression elements such as washers, but other bolt elements such as studs are not good candidates for nitriding. Studs are exposed to pure tensile stresses under load and therefore may suffer catastrophic fracture if the stud is nitrided. Nuts are safer, but have hoop stresses from thread loads. These hoop stresses are tensile in nature. Nuts have much more downside tensile stresses than studs, but there is still a risk of fracture against a hardened surface. Fractures propagating in a stud or nut are more likely to lead to catastrophic load loss in the fastener. Fractures propagating in a washer do not lead to load loss.

[0051] Design engineers remain focused on the integrity of bolted joints, which are prone to losing preload when subjected to shear loads caused by lateral vibration. Prior art threaded fastener locking solutions such as lock nuts and standard two-piece wedge and serrated lock washers do not optimize the integrity of bolted joints.

[0052] The Junker test is an industry-accepted mechanism for comparing the relative performance of fastener locking solutions. It allows design engineers to identify fasteners that will function under a wide range of conditions without loosening. The Junker test procedure, described in the ISO 16139, DIN 65151 and DIN 25201-4B standards, allows for the collection of accurate and repeatable test data. Unclamped fastener specimens are subjected to lateral vibration cycles at increasing displacement values ​​until they loosen. Clamped joints are then tested under the same conditions. The preload is plotted against the number of load cycles to evaluate the loosening behavior of the clamped fasteners. [Prior art documents] [Patent documents]

[0053] [Patent Document 1] U.S. Pat. No. 4,671,142 [Patent Document 2] U.S. Pat. No. 4,706,526 [Patent Document 3] U.S. Patent No. 5,016,502 [Patent Document 4] U.S. Reissue Patent No. 33,951 [Patent Document 5] U.S. Patent No. 6,152,243 [Patent Document 6] U.S. Design Patent No. 500060 [Patent Document 7] U.S. Patent No. 7,765,895 [Patent Document 8] U.S. Pat. No. 5,318,397 [Patent Document 9] U.S. Pat. No. 5,499,9558 [Patent Document 10] U.S. Pat. No. 5,341,560 [Patent Document 11] U.S. Patent No. 5,539,970 [Patent Document 12] U.S. Pat. No. 5,538,379 [Patent Document 13] U.S. Pat. No. 5,640,749 [Patent Document 14] U.S. Pat. No. 5,946,789 [Patent Document 15] U.S. Patent No. 6,152,243 [Patent Document 16] U.S. Patent No. 6,230,589 [Patent Document 17] U.S. Patent No. 6,254,323 [Patent Document 18] U.S. Patent No. 6,254,323 [Patent Document 19] U.S. Patent No. 6,461,093 [Patent Document 20] U.S. Patent No. 6,490,952 [Patent Document 21] U.S. Patent No. 6,609,868 [Patent Document 22] U.S. Patent No. 6,929,439 [Patent Document 23] U.S. Patent No. 6,883,401 [Patent Document 24] U.S. Pat. No. 6,986,298 [Patent Document 25] U.S. Patent No. 7,003,862 [Patent Document 26] U.S. Patent No. 7,066,053 [Patent Document 27] U.S. Patent No. 7,125,213 [Patent Document 28] U.S. Patent No. 7,188,552 [Patent Document 29] U.S. Patent No. 7,207,760 [Patent Document 30] U.S. Pat. No. 7,735,397 [Patent Document 31] U.S. Patent No. 8,079,795 [Patent Document 32] U.S. Patent No. 7,462,007 [Patent Document 33] U.S. Pat. No. 7,857,566 [Patent Document 34] U.S. Patent No. 6,298,752 [Patent Document 35] U.S. Patent No. 6,490,952 [Patent Document 36] U.S. Patent No. 6,609,868 [Patent Document 37] U.S. Patent No. 6,929,439 [Patent Document 38] U.S. Patent No. 6,883,401 [Patent Document 39] U.S. Patent No. 6,929,439 [Patent Document 40] U.S. Patent No. 6,883,401 [Patent Document 41] U.S. Pat. No. 6,986,298 [Patent Document 42] U.S. Patent No. 7,003,862 [Patent Document 43] U.S. Patent No. 7,066,053 [Patent Document 44] U.S. Patent No. 7,125,213 [Patent Document 45] U.S. Patent No. 7,188,552 [Patent Document 46] U.S. Patent No. 7,207,760 [Patent Document 47] U.S. Pat. No. 7,735,397 [Patent Document 48] U.S. Pat. No. 7,641,579 [Patent Document 49] U.S. Patent No. 7,798,038 [Patent Document 50] U.S. Patent No. 7,832,310 [Patent Document 51] U.S. Pat. No. 7,950,309 [Patent Document 52] U.S. Patent No. 8,042,434 [Patent Document 53] U.S. Design Patent No. 608,614 [Patent Document 54] U.S. Patent Application Serial No. 13 / 577,995 Summary of the Invention

[0054] What is needed is a simplified tool, driver and washer configuration and operation, elimination of reaction, bending and pulling forces, and increased bolting speed, efficiency, reliability and repeatability, all at a low cost. Accordingly, the present invention has been devised to solve these problems.

[0055] The invention of the present application will now be described, by way of example only, with reference to the accompanying drawings, in which: [Brief description of the drawings]

[0056] [Figure 1A] FIG. 1A is a top perspective view of a first embodiment of a HYTORC®·Z® washer. [Figure 1B] FIG. 1B is a bottom (underside) perspective view of a first embodiment of a HYTORC® Z-Washer. [Figure 1C] FIG. 1C is a side perspective view of a first embodiment of a HYTORC® Z-Washer. [Figure 2A] FIG. 2A is an upward facing perspective view showing a joint to be closed by a threaded fastener including the Z-fastener being a nut and Z-washer of FIGS. 1A-1C. [Figure 2B] 2A-2B are perspective views looking down showing a joint to be closed by a threaded fastener including the Z-fastener being a nut and Z-washer of FIGS. 1A-1C. [Figure 3A]FIG. 3A is a side view showing the HYTORC® Z-Gun, a reaction arm-less power tool for tightening and / or loosening Z-fasteners with minimal galling. [Figure 3B] FIG. 3B is a perspective view of the HYTORC®·Z® Gun, a reaction arm-less power tool for tightening and / or loosening Z-fasteners with minimal galling. [Figure 3C] FIG. 3C is a side view illustrating the HYTORC® Z-Gun, a reaction arm-less power tool for tightening and / or loosening Z-fasteners with minimal galling. [Figure 4A] FIG. 4A is a perspective view showing the tightened joint and the tightened Z-fastener. [Figure 4B] FIG. 4B is a side view showing the tightened joint and tightened Z-fasteners. [Figure 5A] FIG. 5A is a perspective cross-sectional view of a HYTORC® Z® socket, a dual actuation coaxial action-reaction socket assembly. [Figure 5B] FIG. 5B is a perspective view of the HYTORC® Z® socket, a dual drive coaxial action-reaction socket assembly. [Figure 5C] FIG. 5C is a perspective view of the HYTORC® Z socket, a dual drive coaxial action-reaction socket assembly. [Figure 5D] FIG. 5D is a side cross-sectional view of the HYTORC® Z socket, a dual actuation coaxial action-reaction socket assembly. [Figure 6A] FIG. 6A is a bottom view showing the Z-washer friction coefficient increasing treatment means and the associated forces acting on the Z-fastener. [Figure 6B] FIG. 6B is a top view showing the Z-washer friction coefficient increasing treatment means and the associated forces acting on the Z-fastener. [Figure 6C]FIG. 6C is a bottom view showing the Z-washer friction coefficient increasing treatment means and the associated forces acting on the Z-fastener. [Figure 6D] FIG. 6D is a bottom view showing the Z-washer friction coefficient increasing treatment means and the associated forces acting on the Z-fastener. [Figure 6E] FIG. 6E is a side view showing the Z-washer friction coefficient increasing treatment means and the associated forces acting on the Z-fastener. [Figure 7A] FIG. 7A shows multiple views of Z-washers having various sizes and widths of Z-washer friction coefficient increasing treatments, such as stripe knurling. [Figure 7B] FIG. 7B shows multiple views of Z-washers having various sizes and widths of Z-washer friction coefficient increasing treatments, such as stripe knurling. [Figure 7C] FIG. 7C shows multiple views of Z-washers having various sizes and widths of Z-washer friction coefficient increasing treatments, such as stripe knurling. [Figure 8A-8L] 8A-8L are plan views showing various embodiments of Z-washers having various shapes. [Figure 8D1] FIG. 8D1 is a perspective top view of another alternative embodiment of the Z-washer. [Figure 8D2] FIG. 8D2 is a perspective bottom view of another embodiment of the Z-washer. [Figure 8D3] FIG. 8D3 is a perspective side view of another embodiment of a Z-washer. [Figure 8D4-8D10] 8D4-8D10 are side cross-sectional views showing various types, sizes and locations of Z-washer friction coefficient increasing treatment means. [Figure 9A] FIG. 9A is a side cross-sectional view showing another Z-fastener and Z-socket type for use with a Z-washer. [Figure 9B] FIG. 9B is a side cross-sectional view showing another Z-fastener and Z-socket type for use with a Z-washer. [Figure 10] FIG. 10 is a side cross-sectional view of an alternative Z washer and Z socket, where the washer diameter is smaller than the nut diameter. [Figure 11A] FIG. 11A shows an example of various embodiments of Z-sockets having various dimensions and widths. [Figure 11B] FIG. 11B shows other examples of various embodiments of Z-sockets having various dimensions and widths. [Figure 11C] FIG. 11C shows other examples of various embodiments of Z-sockets having various dimensions and widths. [Figure 12A] FIG. 12A is a perspective view showing the application of the Z System to a HYTORC® torque tool including a spline adapter, reaction plate, and offset link. [Figure 12B] FIG. 12B is a perspective view showing the application of the Z System to a HYTORC® torque tool including a spline adapter, reaction plate, and offset link. [Figure 12C] FIG. 12C is a perspective view showing the application of the Z System to a HYTORC® torque tool including a spline adapter, reaction plate, and offset link. [Figure 13A] FIG. 13A is a perspective view showing the application of the Z System to a HYTORC® torque tool including a spline adapter, reaction plate, and offset link. [Figure 13B] FIG. 13B is a perspective view showing the application of the Z System to a HYTORC® torque tool including a spline adapter, reaction plate, and offset link. [Figure 14A] FIG. 14A is a perspective view showing the application of the Z System to a HYTORC® torque tool including a spline adapter, reaction plate, and offset link. [Figure 14B] FIG. 14B is a perspective view showing the application of the Z System to a HYTORC® torque tool including a spline adapter, reaction plate, and offset link. [Figure 15A] FIG. 15A is a perspective view showing the application of HYTORC® Double-Sided Friction Washers to the Z® System. [Figure 15B] FIG. 15B is a perspective view showing the application of HYTORC® double-sided friction washers to the Z system. [Figure 15C] FIG. 15C is a side view showing the application of HYTORC® double-sided friction washers to the Z system. [Figure 15D] FIG. 15D is a perspective view showing the application of HYTORC® double-sided friction washers to the Z system. [Figure 15E] FIG. 15E is a perspective view showing the application of HYTORC® double-sided friction washers to a Z system. [Figure 15F] FIG. 15F is a perspective view showing the application of HYTORC® double-sided friction washers to a Z system. [Figure 15G] FIG. 15G is a side view showing the application of HYTORC® double-sided friction washers to the Z system. [Figure 15H] FIG. 15H is a perspective view showing the application of HYTORC® Z Nuts / Bolts to the Z System. [Figure 15I] FIG. 15I is a side view showing the application of HYTORC®·Z® nuts / bolts to the Z system. [Figure 15J] FIG. 15J is a perspective view showing the application of HYTORC® Z Nuts / Bolts to the Z System. [Figure 15K] FIG. 15K is a side view showing application of HYTORC® Z Nuts / Bolts to the Z System. [Figure 16A] FIG. 16A is a perspective view of one embodiment of the present invention in the form of a tool 10A in a low speed, high torque ("LSHT") mode. [Figure 16B] FIG. 16B is a perspective view of one embodiment of the present invention in the form of tool 10B in a high speed low torque ("HSLT") mode. [Figure 17A] FIG. 17A is a side cross-sectional view of tool 10A in "LSHT" mode. [Figure 17B] FIG. 17B is a side cross-sectional view showing tool 10B in "HSLT" mode. [Figure 18] FIG. 18 is a side cross-sectional view of the rotational force multiplication assembly 200 and the vibration force assembly 300 of the tool 10A in LSHT mode. [Figure 19] FIG. 19 is a perspective cross-sectional view of the drive tool housing assembly 101, drive tool handle assembly 103, and associated interior components of tools 10A and 10B. [Figure 20] FIG. 20 is a perspective view of a mode shifting assembly 400 of tool 10A and tool 10B. [Figure 21A] FIG. 21A is a side cross-sectional view of an embodiment of the present invention in the form of a tool 10F. [Figure 21B] FIG. 21B is a side cross-sectional view of an embodiment of the present invention in the form of a tool 10G. [Figure 22A] FIG. 22A is a side cross-sectional view of an embodiment of the invention in the form of tool 10H. [Figure 22B] FIG. 22B is a side cross-sectional view of an embodiment of the invention in the form of tool 10I. [Figure 23A] FIG. 23A is a top view of an embodiment in the form of a Z·Squirter washer 2301 for direct tension indication. [Figure 23B] FIG. 23B is a bottom view of Z·Squirter washer 2301. [Figure 23C] FIG. 23C is a cross-sectional view of Z·Squirter washer 2301 taken along line 2314 in FIG. 23A. [Figure 23D] FIG. 23D is an enlarged view of a portion of FIG. 23C. [Fig. 24A-24F] 24A-24F show the status of the Z·Squirter washer 2301 during the installation process. [Figure 24G] FIG. 24G is a top view of an embodiment in the form of a Z·DTI washer 2401 for direct tension indication. [Fig. 24H] FIG. 24H is a bottom view of washer 2401. [Figure 24I] FIG. 24I is a cross-sectional view of washer 2401. [Figure 24J] FIG. 24J is an enlarged view of a portion of FIG. 24I. [Fig. 25A-25E] 25A-25E show multiple views of one embodiment of the HYTORC® Z Washer Nut Assembly 2502. [Figures 26A-26D] 26A-26D show multiple views of one embodiment of a HYTORC® Z washer and nut assembly 2602. [Figures 27A-27D] 27A-27D show multiple views of one embodiment of a HYTORC® Z washer and nut assembly 2702. [Figure 28A] FIG. 28A is a perspective view of a threaded fastener having an embodiment of the present invention of a two-piece conical nut assembly 2801. [Figure 28B] FIG. 28B is a side and / or cross-sectional view of inner and outer sleeves and a threaded fastener for use with the two-part conical nut assembly 2801. [Figure 28C] FIG. 28C is a side view of inner and outer sleeves and a threaded fastener for use with the two-part conical nut assembly 2801. [Fig. 29A-29F] 29A-29F are side cross-sectional views of various embodiments of two-piece conical nut assemblies of the present invention having various step amounts, dimensions, geometries, right angles and / or spacing. [Fig. 30A-30D] 30A-30D show several views of an embodiment of the present invention in the configuration of an apparatus 3001 for torsionally coupling a threaded fastener 3010 and a torque input device 3002. FIG. [Figure 31A-31C] 31A-31C are perspective views of various embodiments of apparatus for torsionally coupling threaded fasteners and torque input devices of the present invention having various step amounts, dimensions, geometries, angles, and / or spacing. [Fig. 32A-32C] 32A-32D show multiple views of one embodiment of the present invention of a two-piece tapered nut assembly 3202. [Fig. 33A-33C] 33A-33C show multiple views of one embodiment of a HYTORC® Z-Washer and two-piece tapered nut assembly 3202B. [Fig. 34A-34C] 34A-34C show multiple views of one embodiment of the present invention of a two-piece tapered screw nut assembly 3402. [Fig. 35A-35C] 35A-35C show multiple views of one embodiment of the present invention of a HYTORC® Z-Washer and two-piece tapered nut assembly 3402B. [Figure 36-39] 36-39 are perspective views of several embodiments of HYTORC® Anti-Loosening Z® Washers. [Fig. 40A-40D] 40A-40D are perspective views of multiple embodiments of the HYTORC® Anti-Loosening Z-Nut. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0057] (HYTORC® Z System) The present invention covers Applicant's HYTORC® Z System, which involves a multi-speed / multi-torque mode tool with a torque multiplication and oscillation mechanism without external reaction abutment means, a force transmission means for use with such tool to provide in-line coaxial action and reaction, a drive means and shift means for use with such tool and force transmission means that allows a washer to be mounted under a nut, associated washers and fasteners for use with such tool, force transmission means, and drive means, and associated accessories for use with such tool, force transmission means, drive means, washers, and fasteners.

[0058] The HYTORC® Z system includes: Z-washers positioned under various types of nut or bolt heads with engageable perimeters of various shapes, sizes, geometries, and serrations, e.g., washer / fastener radial engagement differentials; frictionally biased surfaces, e.g., friction coefficient increasing means, of various types, sizes, and locations, having relatively high friction against the flange face and relatively low friction against the nut; HYTORC® Z-guns incorporating high power intermittent (impact, vibration, ultrasonic, etc.) mechanisms and precision torque multipliers in the same tool combining high speed rundown and calibrated torque; HYTORC® Z-sockets with dual drive coaxial action-reaction with an outer sleeve to react against the Z-washer and an inner sleeve to turn the nut or bolt head; AVANTI and ICE square drive systems, STEALTH limited clearance system; HYTORC®·Z® spline adapters and reaction plates for backward compatibility with HYTORC® torque / tension systems including pneumatic jGUN Series, FLASH Guns and Lithium·Series electrical multipliers, etc.; HYTORC®·Z washers and combinations of HYTORC® double sided friction washers with double sided friction assist surfaces and / or HYTORC®·Z nuts / bolts for counter torque on the underside of the nut or bolt head on the other side of the joint; HYTORC®·Z dual drive offset links for tight clearance when using HYTORC® torque / tension systems; HYTORC®·Z oscillating mechanisms applied therefrom; Z·Squirter washers; Z·DTI washers; HYTORC®·Z washer and nut assemblies; anti-loosening Z washers and combinations thereof. Also included are tapered fastener assemblies, tapered torsion couplings, two-piece tapered nut assemblies, two-piece tapered threaded nuts, HYTORC® Anti-Loosening Z-washers, nuts and smart studs, and combinations thereof.

[0059] (HYTORC(R) Z Washer) International bolting standards require hardened washers to be placed under industrial threaded fasteners. HYTORC® Z Washers are Applicant's proprietary hardened washers. Such washers provide a reaction point directly under the nut or bolt head of the fastener during tightening and / or loosening. HYTORC® Z Washers are used with industrial threaded fasteners of the type that have a coaxial reaction surface, a stud, and a nut that can be threadedly engaged with the stud, or a stud head that is coupled to the stud. These washers eliminate potential pinch points for the operator's hands. The operator does not have to search for a good stationary object to react against. Straight coaxial tension almost eliminates bending and / or side loading of the stud. They provide a smooth, consistent, low friction surface against which the nut or bolt head turns. The top surface has a polished surface against which the nut or bolt head turns. These washers provide an enhanced friction bottom surface. The tool will react against this lower surface.

[0060] Z-washers protect the flange faces from damage or embedment, and distribute the bolt load evenly around the joint due to the larger surface area. They can be manufactured in a wide variety of inch and metric sizes from a wide variety of material options for each application. They comply with all ASME, ASTM and API requirements for size, hardness and thickness. They work with pneumatic, hydraulic, electric and hand torque tools. And by adding a companion friction washer, they eliminate the need for a backup wrench to prevent the opposing nut from turning with the bolt.

[0061] Applicant's recent research and development on Z-washers includes building prototypes and experimentally evaluating various thicknesses, outer engagement sizes, outer engagement geometries and serrations, low friction coatings and treatments on the fastener engaging side (top side), size, shape and location of friction enhancing features on the flange engaging side (bottom side), such as knurling patterns, size and shape of chamfers on the bottom, top, inner and outer surfaces, material specifications, and heat treatment specifications.

[0062] FIG 1A shows a first embodiment of a HYTORC® Z Washer 1 for use with a HYTORC® torque / tension system. It is a perspective view showing the upper side, or upper bearing surface 2, of washer 1. FIG 1B is a perspective view showing the lower side, or lower bearing surface 3, of washer 1. And FIG 1C is a side view showing the outer end, or bearing side 4, of washer 1.

[0063] Generally, the washer 1 is annular in shape with an inner gap 5. As shown in FIG. 1, the annular shape of the washer 1 includes radially extending, flower-like projections 6. Generally, the upper bearing surface 2 is smooth and has a relatively low surface friction against a nut or bolt head. It is noted that a lubricant can be used on the upper bearing surface 2 to reduce the surface friction between the upper bearing surface 2 and the nut, bolt head, or any other such threaded fastener. The lower bearing surface 3 is characterized as having a relatively high surface friction against a flange surface. The lower bearing surface 3 is shown with a smooth inner side surface 3A and a rough friction enhancer, such as a knurl 7, having a higher surface friction. The radial raised knurl pattern 7 increases the surface friction of the lower bearing surface 3. In the illustrated embodiment, the knurled surface 7 is in the form of a ring or annulus disposed beyond the smooth surface 3A. The outer projections 6 include a sloped surface 8 at a predetermined angle configured between the lower bearing surface 3 and the bearing side surface 4.

[0064] Washer 1 has a ring radius R 1A , protrusion radius R 1L , knurl radius R 1K , and the gap radius R 1Vhas. The washer 1 has a height H 1 , a first inclined surface height H 1Bi , a second inclined surface height H 1Bii , a knurl height H 1K , and an inclined surface angle ° 1 has.

[0065] Figure 2A is an upward-facing perspective view showing the joint 30 to be closed, and Figure 2B is a downward-facing perspective view showing the joint 30 to be closed. The joint 30 includes a first member 31 and a second member 32 that are clamped in a facing relationship by a fastener 20 widely known to those skilled in the art as a bolt. The fastener 20 has a first end 21 with a bolt head 22 and a second end 23 with a threaded engagement portion 24. The second end 23 of the fastener 20 is inserted through an opening 33 provided in the first and second members 31 and 32. The opening extends from the bearing surface 34 of the second member 32 to the bearing surface 35 of the first member 32. In preparation for the tightening process, the washer 1 is placed over the second end 23 with the support lower surface 3 facing the bearing surface 35. A nut 36 is placed over the second end 23.

[0066] The Z-washer is used only on one side of the joint, and no other washer should be used under it. It is then desirable to perform normal lubrication of the bolt and nut. The lubricant is only required between the bolt threads and between the nut or bolt head and the upper surface of the Z-washer, and should not be used between the washer and the flange. Note that the exact torque value for a given bolt depends heavily on the lubricant used. Normally, no lubricant is required on the rear nut or bolt head.

[0067] A typical industrial bolting practice is to adjust the stud so that when the stud is tightened, its top end projects two to three threads above the nut. This is for testing purposes to ensure full engagement of the nut and stud. There is usually no reason for the stud to extend more than this, and any excess length should be adjusted on the other side of the flange to allow the socket to engage the entire nut without hindrance. It is acceptable in high corrosion areas for the stud to be flush with the nut after tightening to reduce the risk of thread damage and to allow for easier removal of the nut. Advantageously, the thickness of the washer 1 is ideal. If the washer is excessively thick, insufficient male threads will be available to the fastener system. Conversely, if the washer is insufficiently thick, it may break under high compressive loads.

[0068] (HYTORC (registered trademark) Z Gun (general)) A reaction arm-less torque power tool for tightening and loosening industrial screw fasteners of the type having a coaxial reaction surface, a stud, and a nut or a stud head coupled to the stud, with minimal galling, the reaction arm-less torque power tool including a motor for generating a rotational force, a drive for transmitting the rotational force, a rotational force multiplication mechanism within a housing including a rotational force multiplication transmitter corresponding to all torque modes from low resistance to high resistance, and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable in all torque modes from low resistance to high resistance.

[0069] Standard air impact wrenches hammer bolts with uncontrolled force accompanied by high noise and excessive vibration. The HYTORC® Z-Gun is a precision torque multiplier that produces consistent, measured power on bolt after bolt without the uncontrolled force, high noise, and / or excessive vibration of standard air impact wrenches. The Z-Gun is the world's first precisely torqued pneumatic bolting tool without a reaction arm. It ensures uniform and accurate bolt loading. The Z-Gun incorporates a high-power impact mechanism and precision torque multiplier in the same tool combining fast rundown and calibrated torque. It is operated by a pistol grip trigger and features a directional control switch for tightening or loosening, a speed selection handle for high and low speeds, and a self-reacting socket drive that engages the Z-washer on the underside of the nut. The impact mechanism tightens / loosens nuts regardless of corrosion or thread defects. The torque multiplier breaks out of or tightens the fastener. The gun works with Z-washers so there are no external reaction arms, pinch points, or inaccurate side loads. This gun gets any screw driving job done faster, safer, and better than ever before, all with one tool.

[0070] The Z Gun incorporates a dual speed capability that is controlled by simply shifting quickly from a high speed rundown mode to a low speed torque applied power mode and back again. In high speed mode, the dual sockets spin at hundreds of revolutions per minute, but the torque is limited so that the tool does not spin or bounce in the operator's hand. Shifting the selector upwards locks the tool into the power / torque mode and the nut or bolt is automatically tightened to the desired torque based on the calibrated pneumatic fluid pressure.

[0071] Advantageously, the Z-Gun addresses industry concerns and issues of hydraulic, pneumatic, or electric torque intensifying tools. The Z-Gun maximizes the benefits and eliminates the drawbacks of torque and tension methods, and maximizes the benefits and eliminates the drawbacks of HYTORC® NUT®, HYTORC® WASHER®, HYTORC® AVANTI®, HYTORC® XXI®, HYTORC® jGUN®, HYTORC® FLIP-Gun®, and HYTORC® THRILL®, which can create galling of threaded engagements due to side loads and dried corrosion buildup. It also provides high rotational inertia due to the high mass resulting from the cooperation of the multiplier and impact mechanism in intermittent force mode, thereby increasing the torque output of the impact mechanism, allowing fasteners to run down and run off at high speeds without the use of reaction arms when higher torques than can be absorbed by the operator are required to overcome adverse threaded fastening application characteristics, loosening highly torqued or corroded fasteners that are stuck in their joints, and tightening fasteners to a higher and more precise torque desired using a coaxial reaction surface in high resistance torque mode. The vibration force mechanism can be activated while the nut is tightened to pulverize the dried corrosion before applying full torque to the nut when loosening the nut. This results in reduced torque required to loosen industrial threaded fasteners, and pulverized dried grease does not accumulate or concentrate in the threaded portions. Additionally, during tightening and loosening, the nut remains parallel to the joint surface, the threads do not experience large and irregular side loads, and the facial and thread friction is more consistent. This ensures a more uniform torque load and therefore uniform joint compression, thereby avoiding leaks and gasket failure during tightening. Additionally, tooling is simplified, reducing the risk of operator error and increasing operator safety.

[0072] Industrial threaded fasteners 20 are typically tightened using hydraulic, pneumatic, or electrically powered torque, tension, and / or torque-tension tools. FIGS. 3A, 3B, and 3C show a reaction arm-less power tool 10, the HYTORC® Z-Gun, for tightening and / or loosening fasteners 20 with minimal galling. Tool 10 includes a motor for generating a turning force, a drive for transmitting the turning force, a turning force multiplication mechanism in a housing including a turning force multiplication transmitter for all torque modes from low resistance to high resistance, and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable in all torque modes from low resistance to high resistance. It is noted that tool 10 operates in a high speed, low torque ("HSLT") mode as shown as tool 10A in FIGS. 3A and 3B, and a low speed, high torque ("LSHT") mode as shown as tool 10B in FIG. 3C.

[0073] Tool 10A of Figures 3A and 3B, and tool 10B of Figure 3C include a drive input / output assembly 100, a rotational force multiplication assembly 200, a vibration force assembly 300, a mode shifting assembly 400, and a dual drive output / reaction socket assembly 15, such as a HYTORC® Z socket.

[0074] In the HSLT mode, the tool 10A compresses the washer 1 between the seated nut 36 on the preloaded fastener 20 and the pretightened joint 30 to a predetermined tightening torque, decompresses the washer 1 between the nut 36 on the unloaded fastener 20 and the loosened joint 30 from a predetermined tightening torque, and / or vibrates the pressurized washer 1 between the tightened nut 36 on the loaded fastener 20 and the tightened joint 30 to sufficiently break up the bolt thread corrosion. In the LSHT mode, the tool 10B pressurizes the washer 1 between the tightened nut 36 on the loaded fastener 20 and the tightened joint 30 to a predetermined tightening torque, and / or pressurizes the washer 1 between the seated nut 36 on the pre-loosened fastener 20 and the pre-loosened joint 30 from a predetermined tightening torque.

[0075] In the HSLT mode, the tool 10A seats the nut 36 on the fastener 20 or both the nut 36 and washer 1 by running down the nut 36 with a rotational force in one direction and compressing the washer 1 on the preloaded fastener 20 on the pretightened joint 30 to a predetermined tightening torque, runs up the seated nut 36 or both the seated nut 36 and compressed washer 1 on the pre-loosened fastener 20 on the pre-loosened joint 30 from a predetermined loosening torque with a rotational force in the opposite direction, or applies vibration (impact) to the tightened nut 36 over the pressurized washer 1 to apply vibration sufficiently to break up the thread corrosion. In the LSHT mode, the tool 10B tightens a seated nut 36 on a compressed washer 1 on a preloaded fastener 20 on a pretightened joint 30 with a rotational force in one direction to a predetermined tightening torque and applies a reaction force in the opposite direction to the compressed washer 1, or loosens a tightened nut 36 over a pressurized washer 1 on a loaded fastener 20 on a tightened joint 30 from a predetermined tightening torque with a rotational force in the opposite direction and applies a reaction force in one direction to the pressurized washer 1.

[0076] In operation, the tool 10B in the LSHT mode switches to the tool 10A in the HSLT mode when the nut 36 is unseated and the washer 1 is decompressed with a predetermined loosening torque. In operation, the tool 10A in the HSLT mode switches to the tool 10B in the LSHT mode when the nut 36 is seated and the washer 1 is decompressed with a predetermined tightening torque or the thread corrosion is sufficiently broken. Note that the operator uses the mode shift assembly 400 to switch the tool from the LSHT mode to the HSLT mode or vice versa. The mode shift assembly 400 is a manual switch, but may be automatic. Similarly, the activation or deactivation of the vibration (impact) force assembly 300 may be performed manually or automatically. Note that the LSHT mode can be switched from torque-adjusted to vibration-assisted or vice versa, and the HSLT mode can be switched from vibration-adjusted to torque-assisted or vice versa. The vibration (impact) force assembly 300 can continue to operate even if the washer 1 begins or stops rotating. The LSHT mode can also provide vibration assistance to loosen the nut 36, helping to overcome chemical, heat, and / or lubrication corrosion and avoid galling of the bolt threads.

[0077] When a fastener is torqued, facial friction, thread friction, and bolt load are generated. Friction and bolt load are inversely proportional. As friction increases, the amount of bolt load generated decreases. The speed at which the fastener is tightened has a significant effect on the amount of friction and therefore the bolt load generated in the joint to be closed. Advantageously, the Z Gun can take advantage of the principle that the thread and under-head friction coefficients decrease with increasing rotational speed.

[0078] The Z Gun works as follows, for example: Assume a job requires using the Z Gun A1 to tighten a 1 1 / 2 inch stud with a 2 3 / 8 inch nut to a torque of 520 lb-ft (705.03 Nm). The Z Gun A1 is used for a torque range of 300 to 1200 lb-ft (406.75 to 1626.98 Nm). The Z Gun A1 is equipped with a standard drive size 3 / 4 inch square drive and has dimensions (L x W x H) of 11.92 inches (30.27 cm) x 3.29 inches (8.35 cm) x 9.47 inches (24.74 cm). The radius of the drive output housing is 1.98 inches (4.93 cm). The height and width of the handle are 6.94 inches (17.63 cm) and 2.12 inches (5.38 cm), respectively. The RPMs for rundown and final torque are 4000 and 7, respectively. The torque on the tool is determined by the air pressure supplied by the Filter / Regulator / Lubricator (FRL). The operator consults the appropriate pressure / torque conversion table for this value. In this case, 520 lb-ft (705.03 Nm) of final torque corresponds to 50 psi (344.73 KPa) of air pressure. The operator therefore sets the FRL air supply pressure to 50 psi (344.73 KPa).

[0079] 3B, the tool 10A runs down the nut 36 until it abuts the flange in HSLT mode. The washer 1' is compressed between the seated nut 36' and the seated joint 30'. In rundown (HSLT) mode, the shifter (mode shift assembly 400) is in the down position and the tool 10A is held with both hands.

[0080] According to FIG. 3C, to begin torque application in LSHT mode, the operator pulls the shifter 400 toward himself in an upward position. The seated nut 36' is engaged, ensuring that the outer reaction socket 17 completely surrounds the compressed washer 1'. Note that there is no pinch point as both hands are safely out of the clamping zone around the seated nut 36'. The operator depresses the trigger until the tool 10B stalls and no longer advances the inner drive socket 16. The operator applies 520 lb-ft (705.03 Nm) of torque to the tightened nut 36'' and pressurized washer 1'', and any other nuts will get the same clamping force as long as the FRL pressure is in place. FIGS. 4A and 4B show a tightened joint 30'', including a tightened fastener 20'', a tightened nut 36'', and a pressurized washer 1''.

[0081] Additionally, bevel 8 assists washer 1 in removing weld fillets formed between flanges and pipes at joints and other clearance issues. Additionally, bevel 8 assists outer reaction socket 17 in engaging and rotationally coupling with washer 1. Bevel 8 can also accommodate modifications made to outer reaction socket 17 to allow for use in inverted bolting applications.

[0082] The operator reverses the process of removing the tightened nut 36", now beginning in LSHT mode. Time and corrosion can make a knot and / or bolt more difficult to remove than it is to tighten. Since achieving a specific torque value is not critical in loosening, the operator can increase the FRL air pressure to or near its maximum and provide nearly full power to the tool. The directional control is switched to loosening. The operator applies the tool 10B to the application and positions the inner drive socket 16 over the tightened nut 36", and the outer reaction socket 17 over the pressurized washer 1". The author pulls the speed selector 400 upward, activates the tool 10B, and subsequently loosens the tightened nut 36" until it can be turned by hand, turning off the reaction force of the pressurized washer 1". The operator runs off the nut 36 by shifting the speed selector 400 to the HSLT position. Recall that the vibration force mechanism can be activated while the nut is tight to pulverize the dried corrosion before applying full torque to the nut as it is loosened. This reduces the torque required to loosen industrial threaded fasteners, and pulverized dried grease does not accumulate or concentrate on the threads.

[0083] Additionally, Figures 16-23 and the associated portions of this specification provide a detailed discussion of the HYTORC® Z Gun.

[0084] (HYTORC(R) Z socket) The benefits of Z-washers are optimized when used with HYTORC® Z-Sockets, which have dual actuating coaxial action and reaction. The outer sleeve reacts against the Z-washer, while the inner sleeve turns the washer (top) and adjacent nut or bolt head. Some of the inventions and HYTORC®'s unique dual socket systems do exactly this. Best of all, the Z-Gun with Z-Sockets obtains all the benefits of this reaction-free technology in the fastest and easiest format. A portion of the outer socket surrounds the Z-washer and rotatably couples with splines on the torque tool body. The inner socket couples to the drive of the tool and turns the nut. The Z-Gun impact action runs down the nut rapidly, then shifts effortlessly into a controlled torque application mode while reacting against the Z-washer. There are no external pinch points or unwanted side loads. For the first time, controlled torque is possible with an air tool without sacrificing speed and flexibility. These unique socket assemblies exceed all applicable ANSI standards for toughness and safety and come in a full range of inch and metric sizes to suit any job.

[0085] Applicant has disclosed important features regarding washers in HYTORC®·WASHER related patent applications. Washers positioned within the load track either rotate with the nut (or bolt head) or remain stationary; the washer never rotates in a counter direction to the nut due to facial friction and load compression. Applicant's innovation determined the effect of turning off the reaction force of an in-line washer. Despite the frictional advantage gained from thread inserts, the HYTORC®·WASHER is feasible due to this observation.

[0086] In general, the joint to be closed in the present invention is tightened with a bolt and a nut. The bolt is inserted through a hole in the joint with a hardened washer adjacent to its bolt head. The nut is threaded onto the bolt with an adjacent hardened washer that is geometrically engageable. The inner application socket rotates the nut to tighten the joint, and the outer reaction socket transfers the reaction force of the tool to the geometrically engageable hardened washer. As the application torque on the joint increases, the reaction force of the application torque increases proportionally. The rotatably coupled outer socket geometrically engages the hardened washer. The hardened washer eliminates rotation of the tool relative to the operator due to the reaction force.

[0087] 5A, 5B and 5C are perspective views of the dual drive coaxial action-reaction socket assembly 15. FIG. 5A is a combined cross-sectional perspective view. FIG. 5B is a combined cross-sectional view. FIG. 5C is an exploded perspective view. FIG. 5D is a top cross-sectional view of the dual drive coaxial action-reaction socket assembly 15 on a clamped joint 30".

[0088] In the HSLT mode as shown in Figures 3A and 3B, the socket assembly 15 is substantially for transmitting an oscillatory form of rotational force in one direction to the nut 36 and washer 1. In the LSHT mode as shown in Figure 3C, the results of which are shown in Figures 4A and 4B, the socket assembly 15 is substantially for transmitting a multiplied form of rotational force in one direction to the nut 36 and a corresponding reactive multiplied form in another direction to the washer 1 acting as a stationary object.

[0089] Referring to FIG. 5A, the inner drive socket 16 includes an inner edge 52 with a means 51 for engaging a nut or bolt head. The outer reaction socket 17 has a lower inner edge 62 with a washer 1 engagement means 61 for engaging the washer outer end 4 or the outer socket engagement means 9. The inner drive socket 16 is disposed substantially inside the outer reaction socket 17. The inner and outer sockets are coupled to each other via a socket coupling means 18. The sockets are rotatable in opposite directions relative to each other cooperatively via the tool housing. The lower inner edge 62 and its washer 1 engagement means 61, as well as the outer end 4 of the washer 1 and its outer socket engagement means 9, are substantially vertical. The outer reaction socket 17 includes a lower outer end 63 with a tapered surface inclined inwardly toward the bottom of the lower inner edge 62. The bottom surface 54 of the inner socket 16 rotates on and / or over the top surface 64 of the lower inner edge 65 of the outer socket 17. Additionally, socket coupling means 18 is adapted for use with HYTORC® hydraulic square drive tools. Socket coupling means 18A is adapted for use with HYTORC® pneumatic and electric torque guns, such as tools 10A (and 10B).

[0090] Washer 1 has a ring radius R 1A , protrusion radius R 1L , knurl radius R 1K , and the central hole radius R 1V The washer 1 has a height H 1W , First slope height H 1Bi , second slope height H 1Bii , knurl height H 1K and a slope angle of °1. The nut 36 has a hexagonal radius R 36N and height H 36N The outer reaction socket 17 has a washer engagement radius R 17W The washer engagement radius R 17W is the washer / outer socket gap width G 1A This gap width G 1Ahelps the outer reaction socket 17 to easily engage the washer 1. 1L The clearance space 19 having the gap 19a provides sufficient clearance between the inner socket 16 and the outer socket 17. The inner socket 16 is free to rotate on the upper surface 64.

[0091] It should be noted that any suitable engagement geometry will work, such as those disclosed in the HYTORC® patents and patent applications incorporated herein by reference. However, attention should be directed to U.S. Patent No. 8,631,724, issued Jan. 21, 2014, entitled "FASTENING SOCKETS, WASHERS AND FASTENERS USED WITH THE WASHERS AND THE FASTENING SOCKETS," which is incorporated herein by reference in its entirety. The outer socket engagement means of the '724 patent does not engage the outer surface of the washer, but merely the "outer end portion," thereby increasing the probability of failure.

[0092] The outer reaction socket 17 of the tool 10A is idle and inactive in the HSLT mode. It is not splined to the housing of the turning force multiplication assembly 200. The impact and / or vibration force transmitter of the vibration force assembly 300 is splined to the output drive shaft. The output drive shaft rotates the inner drive socket 16 to run up or down the nut 36 on the fastener 20. However, the outer reaction socket 17 of the tool 10B is rotatably coupled and geometrically engaged with the washer 1 under the nut 36. When the nut 36' is seated, the compressed washer 1' serves as a stationary object by which the housing of the turning force multiplication assembly 200 reacts via the reaction socket 17. With the housing of the turning force multiplication assembly 300 held stationary, the turning force multiplication transmitter tightens the seated nut 36'' via the turning force output drive shaft.

[0093] During operation of any embodiment having a reaction socket assembly of the present invention, the drive socket rotates a nut or bolt head. During operation of one embodiment of such a tool, the reaction socket remains stationary during HSLT mode. During operation of another embodiment of such a tool, the reaction socket rotates in the same direction as the drive socket during HSLT mode, but remains stationary during LSHT mode. During operation of another embodiment of such a tool, the reaction socket remains stationary during HSLT mode, or rotates in the opposite direction to the drive socket, but remains stationary during LSHT mode.

[0094] In other words, the reaction socket is always operatively coupled to the nut or bolt head during all torque modes from low resistance to high resistance, and the reaction socket is operatively coupled to the housing and the coaxial reaction surface for transferring a reaction force to the coaxial reaction surface during the high resistance torque mode, and is operatively coupled to the housing and the coaxial reaction surface during the low resistance torque mode or the intermittent force mode, or is operatively coupled to the housing and operatively disengaged from the coaxial reaction surface during the low resistance torque mode or the intermittent force mode.

[0095] In other words, the torque output tool of the present invention includes a drive means for coupling with a drive socket of the dual drive coaxial action-reaction socket assembly to rotate a nut or bolt head, a reaction means for coupling with the reaction socket of the dual drive coaxial action-reaction socket assembly to transmit a reaction force to a washer, a coupling means between the drive means and the reaction means, and at least two operating modes including a high speed, low torque mode and a low speed, high torque mode, wherein when the coupling means between the drive means and the reaction means is activated in the high speed, low torque mode, the reaction socket is caused to rotate in one direction, but when the coupling means is deactivated in the high torque, low speed mode, the reaction socket is caused to rotate.

[0096] In other words, the torque output tool of the present invention includes a drive means for coupling a drive socket to a nut or bolt head, a first reaction means and a second reaction means for coupling a reaction socket to a washer, and at least two operating modes, i.e., a high speed low torque mode and a low speed high torque mode, in which the drive socket is rotated by the drive means during both modes to rotate the nut or bolt head, and the reaction socket is coupled to the washer below the nut or bolt head, and the torque output tool of the present invention further includes a first reaction means for preventing the reaction socket from rotating in the low speed high torque mode while the washer absorbs a high magnitude reaction force, and a second reaction means for preventing the reaction socket from rotating in the high speed low torque mode while the operator absorbs a low magnitude reaction force. In this case, the rotational force multiplication assembly containing the spline adapter is the first reaction means. The mode shifting assembly switching arm having the spline adapter is the second reaction means.

[0097] The dual socket, specifically the reaction sleeve (socket), of the present invention was developed for use with HYTORC® electric, hydraulic, and pneumatic torque / tension systems. To provide maximum clearance between the tool reaction system and the surrounding high speed environment, it was necessary to minimize the outside diameter of the reaction sleeve. In order to minimize the outside diameter of the reaction sleeve, it was also necessary to minimize the outside diameter of the action socket.

[0098] In general, numerous part geometries were devised for the sleeves, sockets, and adapter rings of the present invention. All possible components were prototyped and experimentally evaluated at the HYTORC® Research and Development Center. Qualification testing included subjecting the parts to specific application loads for countless cycles. Various material and heat treatment options were also experimentally evaluated.

[0099] It is noted that in those portions of this specification relating to Figures 16-23, HYTORC® Z sockets are additionally discussed.

[0100] (HYTORC® Z-Washer Fastener Radial Engagement Differential) In torque tools with prior art reaction fixtures, the reaction torque is equal to and opposite to the action torque. The reaction force exerted by the reaction arm is much larger at nearby stationary objects. The reaction force is multiplied by distance, i.e., reaction arm length. In fact, the side load, or reaction abutment force, of the tool can be two to four times its torque output at an abutment point that is, for example, 1 / 2 foot (15.24 cm) away from the torque axis of the drive. This larger reaction force is concentrated at only that one location. Inevitably, a shorter reaction arm transmits a smaller reaction abutment force to the abutment point that is closer to the torque axis of the drive. Naturally, a very short reaction arm transmits a reaction abutment force similar to the torque tool output, but slightly larger, because the abutment point is so close to the torque axis of the drive.

[0101] Thread irregularities result in poor thread fastening characteristics. Among other disadvantages, side loads cause the nut and bolt threads to engage with huge forces on the near side, where forces are applied such that dried grease accumulates in place as the nut turns. Often only a small portion of the total thread surface area engages between the bolt and nut. This causes the bolt threads to gall. This requires significantly higher torque to loosen the nut, and therefore significantly higher side loads. This chain of events destroys the bolt and nut threads. At the point where all of the turning force is used by the thread friction, the fastener locks up or binds. This can lead to failure of the fastener or the tool turning the fastener.

[0102] Torque power tools are often insufficient to loosen the same corroded fasteners, which require loosening torque values ​​two to four times higher than the tightening torque, requiring more powerful tools to cause loosening. High temperature bolting applications, such as in turbines and casings, are usually critical and require stainless or precision manufactured fasteners, which entail extremely high replacement costs. In addition, the use of precision thread bolts, which have recently become popular, increases this problem.

[0103] Similarly, the reaction torque is equal and opposite to the action torque in the HYTORC® dual drive coaxial action-reaction socket assembly. However, the reaction boost characteristic is also applicable. Referring again to applicant's patent disclosures relating to the HYTORC® WASHER and HYTORC® SMARTWASHER®, these washers had a radius approximately similar to that of the nut. The reaction force applied to these washers was of similar magnitude to the equal and opposite reaction torque. This helps explain why HYTORC® WASHERs® and SMARTWASHERs® sometimes rotated with the nut or bolt head.

[0104] Those skilled in the art of industrial bolting have recognized the need to use relatively similar fastener component sizes. In a normal bolting operation, it is not important whether the torque is applied to the bolt head or the nut. This of course assumes that the bolt head and nut faces have the same diameter and the contact surfaces are the same to provide the same coefficient of friction. If they are not the same, this is important. For example, the nut has a flange and the bolt head does not. If the tightening torque is determined assuming that the nut is tightened but the bolt head is tightened later, the bolt may be overloaded. Typically, 50% of the torque is used to overcome the friction below the tightening surface. Thus, the smaller the friction radius, the higher the torque will be in the threads of the bolt, which will result in over tightening. If the opposite is true, i.e., the bolt head is tightened and then the nut is tightened later, the bolt will be under tightened.

[0105] Just as an extremely long reaction arm applies an extremely large reaction force to a nearby stationary object, an extremely short reaction arm applies a reaction abutment force similar to the torque tool output, but slightly larger in magnitude. In this sense, the outer reaction socket 17 can be thought of as a 360° reaction arm. The 360° reaction arm applies a reaction abutment force similar to the torque tool output, but slightly larger in magnitude, infinitely around the outer end 4 of the washer 1. In effect, the outer reaction socket 17 applies a larger reaction abutment force to the reaction washer 1 below the nut 36. This can be accomplished by simply having a slightly larger washer 1 (that geometrically engages the outer reaction socket 17) than the nut 36 (that geometrically engages the inner drive socket 16). Applicant's fundamental observations regarding washers, coupled with this new observation, ensure a stationary washer to react.

[0106] 5D, the outer end 4 of the pressurized washer 1″ extends beyond the outer end 37 of the tightened nut 36″. In particular, the reaction force 92 acting in another direction 94 received by the washer outer end 4 is greater than the action torque 91 acting in one direction 93 received by the nut 36. The pressurized washer 1″ absorbs the reaction force 92 of the tool 10B, so that the tool 10B applies the action torque 91 to the seated nut 36′ and applies a slightly larger but opposite reaction force 92 to the washer outer end 4. The seated nut 1′ rotates, but the compressed washer 1′ remains stationary. This relative positioning, i.e., the washer outer end 4 being farther away from the center of rotation, or turning force axis A10, than the nut outer end 37, is one innovative feature of the present invention. The reaction force 92 is a distance R from the turning force axis A10. 1A The force acting on the washer 1 acts through an effective leverage arm of the outer socket 17 spaced apart by 10 mm, which tends to hold the washer 1 stationary. As a result of the difference in radii of the outer polygonal engagement portion, the washer 1 remains stationary on the joint 30 as the fastener 20 is tightened or loosened, rather than rotating with the nut 36.

[0107] HYTORC(R) Z Washer Friction Coefficient Increasing Treatment Means 6, this is a bottom view of the lower bearing surface 3 configured with friction coefficient increasing treatment means 60. A nut 36 is shown adjacent to the smooth upper bearing surface 2. Friction is lower at the engagement of the smooth contact surfaces 2 and 38 between the nut 36 and washer 1 than at the engagement of the rough contact surface 3 and flange surface 30. Thus, the nut 36 will tend to rotate and the washer 1 will tend to remain stationary.

[0108] Figures 6B, 6C, 6D and 6E illustrate this phenomenon. Figure 6B shows the nut 36 being torqued and pressed against the upper bearing surface 2 of the washer 1. The upper bearing surface 2 and the lower bearing surface 38 of the washer 1 are smooth. During the tightening process, the friction force 71r between the nut 36 and the washer 1 acts in one direction 92. The compression force Fn of the nut 36 is directed toward the rotational force axis A.10 acts downward on the washer 1 along the same. The radius r is the effective friction radius, or the distance from the rotational force axis A 10 to the center of the friction area 73r of the bearing lower surface 38 of the nut 36.

[0109] FIG. 6C shows that the washer 1 is pressed against the bearing surface 35 of the joint 30. The bearing surface 35 and the bearing lower surface 3 of the washer 1 are frictionally engaged with a load. During the tightening process, the frictional force 72 between the washer 1 and the joint 30 R acts in another direction 93. The compressive force F of the joint 30 b acts upward on the washer 1 along the rotational force axis A 10 The radius R is the effective friction radius, or the distance from the rotational force axis A 10 to the center of the friction area 74 of the bearing lower surface 3 of the washer 1 R .

[0110] FIG. 6D shows a combination of FIGS. 6B and 6C. FIG. 6E shows F n and F b . Since the compressive force F generated by the nut 36 tightened on the fastener 20 is equal on both sides of the washer 1, F c = F n = F b = F c . The frictional force (F R ) = μ * F c , where μ is the coefficient of friction. Since the effective friction radius of the friction coefficient increasing means 60, or R, is larger than the effective friction radius of the nut 36, or r, F c * R > F c * r. This means that the torque for overcoming the friction between the nut 36 and the washer 1 is smaller than the torque for overcoming the friction between the friction coefficient increasing means 60 of the washer 1 and the joint 30.

[0111] Returning to the example of FIG. 6A, the friction coefficient increasing means 60 has, for example, an inner diameter R 7The radially raised knurling pattern 7 is shown having a radially raised radius R of approximately maximum radius R to maximize torque (TRMAX) while still below the compression region of the nut 36. MAX At the same distance as is feasible for the axis of rotation A 10 As the clamping force is increased, the knurling pattern 7 is fixed on the material of the flange face 35, thereby resisting attempts by the washer 1 to rotate with the nut 36. The coefficient of friction μ remains constant and is multiplied by the constant compression force Fc to produce a constant friction force (F b ) The reaction torque (TR) is F*R. The maximum torque occurs near the maximum radius, R. MAX Therefore, TRMAX=F*R MAX In other words, the effective friction radius R of washer 1 is greater than the effective friction radius r of nut 36. In general, the effective friction radius of the Z-washer of the present invention is greater than the effective friction radius of the nut or bolt head. Note that traditional bolting applications and mechanics principles (statics, dynamics, etc.) for describing the forces involved are well known to those skilled in the art.

[0112] Stated another way, the resistance of washer 1 to sliding or rotating during the application of a reaction torque is a function of the load and the coefficient of friction. The following expressions show the relationship between sliding force, friction, load and torque in a reaction washer: Sliding force resistance = (friction coefficient) x (load) FR=μ*F N In the formula, F R = force (resistance), μ = coefficient of friction, and F N = normal force (gravity or load).

[0113] In a threaded fastener, the force to overcome friction and produce sliding or rotation is a function of the applied torque and the friction radius. Therefore, the force to produce sliding can be expressed as: F S = (torque) / (friction radius) F S =T / rF In the formula, F R = force (sliding), T = torque, and rF = effective friction radius. Therefore, in fasteners, F S =F R T / rF=μ*F N , therefore T=μ*rF*F N It is.

[0114] The above expression shows that the resistance to sliding under torque is a function of the friction coefficient, load, and radius of the friction surface. This effective friction radius is usually determined as the average of the central hole radius and the bearing outer surface radius. As the friction radius increases, the resistance to sliding or rotation also increases. Therefore, it is clear that increasing the washer friction radius relative to the friction radius of the nut or bolt will fix the washer to the nut or bolt. Since these are equal and opposite torque forces, the reaction washer and the nut or bolt will always have the same applied bolt load torque force. When similar materials and lubricants are applied throughout, the friction coefficient is the same in the fastener. Therefore, by increasing the friction radius of the washer bearing surface, one can ensure that the washer will remain fixed to the nut or bolt in all tightening situations.

[0115] The washer friction radius is increased by biasing the bearing surface outward. This can be accomplished by adding surface features to the outermost bearing surface areas while ignoring the innermost areas. Due to the high loads and typical recessing of the mating surfaces, only minor selective surface conditioning is required to effectively increase the friction radius.

[0116] The location and footprint of the friction coefficient increasing treatment means, such as the raised knurling features, and their relationship to the footprint of the nut or bolt head ensure the effectiveness of the Z system. The underside of the washer includes a friction coefficient increasing treatment means positioned outwardly, which defines a friction portion for engagement with the surface of the joint. The friction portion is disposed around the outer periphery of the underside and extends inwardly to a width less than the full width of the washer body. The friction enhancing surface tends to lock up the nut by maintaining the bolt load, thereby preventing unintended loosening. In other words, roughening the underside of the washer ensures significant friction between the joint and the washer when tightening or loosening the fastener. The frictional forces generated between the washer and the joint are significant, and this action of the frictional forces reliably prevents undesired rotation of the washer during loading and the initial stages of unloading.

[0117] Surprisingly, experimentally repeatable performance is not obtained when friction-enhancing surface 7 completely occupies underside 3 of washer 1 or is positioned at or relatively close to the central hole of underside 3. In most cases, this configuration results in experimental failure and washer 1 rotates with nut 36.

[0118] The Z-washer concept works just as well with just the outer ring having friction coefficient increasing treatments. It is not necessary to have both a smooth inner portion, i.e., inner surface 3A, and a roughened outer portion. However, the different surface configurations on the underside of the washer help provide a frictional bias across the underside and between the underside and the topside of the washer.

[0119] This application seeks to define, claim and protect a reaction type washer with an outwardly shifted friction area, e.g., a reaction washer that biases friction radially outward against the nut. This results in a novel and unobvious friction surface radial shift that prevents the washer from spinning in front of the nut. Prior art reaction type washers without friction bias tended to spin, especially when used on hard surfaces. They performed marginally well and only worked on ideal surfaces and in ideal conditions. The spinning of reaction type washers undesirably led to flange face damage, inefficient industrial bolting and system maintenance operations, and economic losses. The outwardly positioned friction coefficient increasing treatment of the present invention maintains a flawless flange face, increases the efficiency of industrial bolting and system maintenance operations, and minimizes economic losses.

[0120] Returning to Figure 5D, the washer / fastener radial engagement differential, i.e., outer end 4 of washer 1 being farther away from the center of rotation, or turning force axis A10, than outer end 37 of nut 36, serves as another embodiment of the friction coefficient increasing treatment means of the present invention. The larger washer / flange surface area with the longer engagement radius increases facial friction over the smaller nut / washer surface area with the shorter engagement radius.

[0121] Stated another way, in the bolting application of the present invention, the frictional torque generated by the washer flange surface area interaction is greater than the frictional torque generated by the nut-washer surface area interaction. The washer remains stationary, so that a retaining socket can be non-rotatably mounted on the tool housing. The retaining socket is engaged with the outer polygonal edge of the washer, while the tightening tool operatively engages the nut. The washer is compressed under the nut during tightening, and the tool housing is fixed against rotation relative to the washer. The washer absorbs the reaction moments and reaction forces of the tool housing, which are opposite to the tightening torque, and which the tool housing transmits to the compressed washer. No external reaction means are required.

[0122] 7A, 8B and 7C show various washer sizes and widths of friction coefficient increasing treatments such as knurled strips. FIG. 7A shows an inner cavity, or central hole 5 for use with the smaller size M14 bolts. 7A Washer 1 having 7A The striped knurling 7 7A The bottom surface of the support 3 7A However, the lower surface of the bearing 3 7A is void 5 7A Adjacent to the smooth inner surface 3A 7A In reality, the smooth inner surface 3A 7A However, the gap 5 for receiving the fastener 20 7A And, streaky knurling 7 7A It is composed between the washer 1 and 7A is the inner radius r in7A , outer radius r out7A , inner knurl radius r inK7A , outer knurl radius r outK7A , and the protrusion radius r L7A Similar dimensions may apply, but are not shown in Figures 7B and 7B.

[0123] It should be remembered that HYTORC® WASHERs® and HYTORC® SMARTWASHERs® add unnecessary height to bolting applications. The thickness of a Z-Washer of the present invention is typically less than its outside diameter. For example, the outside diameter D of the washer disclosed in the figures is 1.2 mm. 1A Thickness H 1W The average ratio is about 0.08 and may range from 0.04 to 0.12. Other ratios are also representative of the Z-washers of the present invention. Other ratios include: 35N Washer height H for 1W The average ratio of is about 0.170, and may be 0.10 to 0.30, and the diameter D of the nut 36 Washer diameter D for 1A is approximately 1.10 and may be between 0.80 and 1.40. These ratios are provided for illustrative purposes only.

[0124] It is noted that important aspects of friction bias in a Z system are difficult to quantify. For example, the relative surface areas of the washer and nut (or bolt head) have minimal effect on friction bias results with a Z system. In fact, smaller threaded fasteners may have different ratios than larger threaded fasteners.

[0125] The most useful data involves the calculation of the effective friction radius of the washer and threaded fastener. Z-washers function extremely reliably because the friction coefficient increasing treatment means is selectively biased from the central hole toward the outer end. The effective friction radius of the washer is greater than the effective friction radius of the threaded fastener. For example, the effective friction radius of a washer having radial stripes of friction coefficient increasing treatment means on its underside is the center of the stripes. Note that this discussion correctly assumes the ideal case where the bolt load is evenly distributed under the nut or bolt head with the use of Z-washers.

[0126] Note that while frictional enhancements may not be necessary in many applications, they ensure that the washer will remain stationary in all applications regardless of the relative washer / fastener surface area or engagement radius, the relative fastener / joint material hardness, and the relative fastener / joint surface treatments, such as lubricants (such as molykote) or coatings (such as paint). Frictional enhancements have a strong impact at the beginning of the tightening process when very little or no load is present on the stud and / or nut. This frictional bias always begins to hold the washer in place.

[0127] Alternatively, the friction coefficient increasing treatment means may include roughened surfaces, polygonal surfaces, splines, knurls, spikes, grooves, slots, protruding points, scoring, or other such protuberances. Other options include press-fit ridges, concentric or spiral rings, radial riffles or teeth, waffle patterns, etc. Any operation that forces the outer surface region to have a more aggressive interaction with the flange face, such as knurling, sanding, blasting, milling, machining, forging, casting, forming, shaping, roughening, stamping, engraving, punching, bending, or simply removing the inner region, may be sufficient. It is noted that combinations of such friction coefficient increasing treatment means may be utilized. In the case where the washer 1 (engaging the outer reaction socket 17) is slightly larger than the nut 36 (engaging the inner drive socket 16), the friction coefficient increasing treatment means may not be required and may be positioned anywhere around the washer underside, or may be positioned substantially beyond the effective friction radius of the nut or bolt head around the washer underside. To obtain the properties of the present invention, it is sufficient for the washer underside to be flat. However, the opposing friction surface may be tapered outwardly, so that the outer edge of the friction ring is thicker than the inner edge. However, if necessary, the washer, and thus its underside, may have a curvature. Particularly good results are obtained with a convex curvature towards the joint. This is disclosed in U.S. Patent No. 7,462,007, entitled "Reactive Biasing Fasteners," issued December 9, 2008, the entirety of which is incorporated herein by reference. However, the washer of the present invention does not provide an axial biasing force to the elongated bolt.

[0128] In general, the reaction washer of the present invention for industrial bolting includes a profile that allows rotational coupling with a torque application device and a bearing friction undersurface area that is discontinuous and selectively biased in an area outward from the central bore. These surface friction features are selectively configured on the undersurface of the washer except for an area portion near the radius of the central bore. These surface friction features may be configured via knurling, sanding, blasting, milling, machining, forging, casting, forming, shaping, roughening, stamping, engraving, punching, bending. The surface friction features may be configured by simply removing material near the reaction washer bore. The surface friction features may be configured to have discontinuous surfaces and / or textures configured in the area outward from the bore and / or positioned singly, randomly, or in any row arrangement.

[0129] (different Z-washer geometry) 8A-8L show alternative shapes of washer 1. The washer of the present invention may have an outer end (and its corresponding engagement means) shaped with any geometry suitable for non-rotatably engaging with an inner edge (and its corresponding engagement means) of an outer socket shaped with a corresponding suitable or nearly identical geometry. The standard commercial shape of Z-washer 1 is a "flower pattern" washer. A flower pattern includes inwardly extending concave portions and outwardly extending convex portions, which are provided in a radially alternating pattern around an imaginary reference circle centered at the midpoint of the washer. Figures 8B, 8E, 8G, 8H, and 8I are obvious derivatives of such flower-shaped washers. Note that Figure 8K shows a multi-faceted engagement and Figure 8J shows a spline engagement. Both can be considered as flowers shaped with an increased number of engagement teeth.

[0130] Other suitable geometries include shapes such as triangles, curvilinear triangles, squares, rectangles, parallelograms, rhombus, trapezoids, trapezoids, kite shapes, pentagons, hexagons, heptagons, octagons, nonagons, decagons, circles with outer ridges, ellipses, or ovals, although the outer edges of any suitable shape may be curved rather than angled to facilitate engagement with the Z-sockets of the present invention.

[0131] 8D1, 8D2, and 8D3 are schematic diagrams of Z-washer 1 of FIG. 8D for use with various power tools. 8D The embodiment of the washer 1 is shown. 8D 1 shows a top, bottom, and side perspective view, as well as a cross-sectional view of a washer 1. 8D Washer 1 has an annular hexagonal shape with similar dimensions and characteristics as those shown in Figures 1A, 1B, and 1C, except for the "8D" subscript. 8D The hexagonal shape of the hexagon has radially extending side corners 6 8A These side corners form a hexagon-like shape. Generally, the bearing upper surface 2 8D is smooth and has lower surface friction, and the lower bearing surface 3 8D Friction enhancing means or bottom corner 7 8D The surface friction is higher. In addition, a lubricant is used on the upper surface of the bearing. 8D The surface friction between the radial lower corner 7 and the threaded nut 36, or any other such threaded fastener, can be reduced. 8D The bottom surface of the support is 38 Dの Increases surface friction. Side corners 68 (not shown) Dは , bearing top surface 2 8D and bearing side 4 8D A slope 8 that forms a predetermined angle between 8D Such a slope 8 may include 8D The bearing may define an outer end portion including a tapered surface and engaging teeth. The tapered surface faces outwardly toward the lower bearing surface 3. 8D and bearing side 4 8D It gradually slopes towards

[0132] Washer 18D In particular, the ring radius R 8A , protrusion radius R 8L , knurl radius R 8K , and the gap radius R 8V The washer 1 has a height H 8 , First slope height H 8Bi , second slope height H 8Bii , knurl height H 8K , and the slope angle ° 8 Such a slope 8 8A is washer 1 8A bevel 8 assists in clearing flange corner radii and other clearance issues. Additionally, bevel 8 assists the outer reaction socket in engaging and rotationally coupling with washer 1. Bevel 8 can also accommodate modifications made to outer reaction socket 17 to allow for inverted bolting applications.

[0133] (Another configuration of the friction coefficient increasing means of the Z-washer) 8D4-8D10 show washers 1 having various iterations of friction bias surfaces that have relatively high friction against the flange surfaces and relatively low friction against the nut. 8D In other words, washers 1 having friction coefficient increasing treatment means of various types, sizes, and locations are shown. 8D These variations are shown in Figure 1. 8D8D3 is shown with a frictional enhancement, but applies to all reaction washers disclosed in this invention. FIG. 8D4 is shown without frictional enhancements, simply with a smooth underside. FIG. 8D5 is shown with frictional enhancements configured recessed into the inside of the underside of the washer by removing material adjacent the central hole. FIG. 8D6 shows a relatively thin strip of frictional enhancement configured on the outer edge portion of the underside. FIG. 8D7 shows a relatively thick strip of frictional enhancement configured equidistant from the inner edge and outer edge portion of the underside. FIG. 8D8 shows a relatively thin strip of frictional enhancement 1X wide configured 1X from the outer edge of the underside and 2X from the inner edge. FIG. 8D9 shows a frictional enhancement, in this case a downwardly sloping ring with sharp edges configured on the outer edge of the underside. Washer 1 shown curved 8D5 The washer 1 does not provide an axial bias force to the elongated bolt. 8D5 may have no change in height except for sharp edges.

[0134] As shown in FIG. 8D10, the washer of the present invention may be provided with a configuration for positive locking engagement with the outer reaction socket. Such positive locking engagement means may be provided in the washer 1. 8D The outer reaction socket includes corresponding engagement means for allowing hands-free operation, and when the nut is seated, hands-free operation is achieved in inverted bolting applications.

[0135] Prior art disclosures of reaction style washers for industrial bolting having friction surfaces do not discuss the importance of the location or coverage of such friction surfaces. Applicant has found that friction coefficient increasing treatments, when placed on the inside diameter of the washer near the bolt, or on the entire underside of the washer, tend to cause the washer to move or rotate with the nut. These strategies have been marginally successful, sometimes resulting in the washer becoming stationary. In other words, more friction treatments over a larger portion, the entirety, and / or the inner portion of the underside of the washer are significantly less effective than friction treatments over smaller and / or outer portions.

[0136] (Alternate fastener and Z socket types for use with Z washers) FIG. 9A illustrates a bolt having a bolt head 20A threaded into a blind hole and a washer 1 for use with a dual drive coaxial action-reaction socket assembly 15. 8D FIG. 9B shows a socket head bolt 20B threaded into a blind hole and a washer 1 for use with the improved dual drive coaxial action-reaction socket assembly 15C. 8D Various fastener geometries may be used with Z system tools, parts, and accessories with appropriate design modifications as shown in Figure 9B. The improved socket assembly 15C includes a male fastener drive engagement means 16C rather than a working socket 16.

[0137] (reduced Z-washer surface area) FIG. 10 shows a pressurized washer 1 10A” Outer edge of 4 10A 5D, except that the washer outer end 44 is tapered from the outer end 37 of the tightened nut 36". 10A A reaction torque force 92 acting in another direction 94 is received by 10A is less than the torque force 91 acting in one direction 93 received by the nut 36. 10A” is the reaction torque force 92 of tool 10B. 10Aabsorbing the force, tool 10B applies an applied torque 91 to seated nut 36' and washer outer end 4 10A Lower reaction force 92 10A Add Washer 1 10A To prevent the nut 36 from rotating with the aggressive friction enhancer 7 10A The seated nut 36' will rotate, but the washer 10 10A’ remains stationary. Such relative positioning, i.e., friction enhancing means 7 10A , and thus 1 10A It is an innovative feature of the present invention that the effective friction radius of reaction force 92 is farther away from the center of rotation, or turning force axis A10, than the effective friction radius of nut 36. 10A is the axis of rotation A 10 Approximately distance R from 10A The outer socket 17 is connected to the washer 1. 10A As a result of the difference in effective friction radius, the washer 1 10A 3A, 3B, and 3C remain stationary on joint 30 rather than rotating with nut 36 as fastener 20 is tightened or loosened. Note that bottom surface 54 of inner socket 16 rotates onto and / or over top surface 64 of lower inner edge 65A of outer socket 17A. In this case, inner socket 16 and outer socket 17A may experience additional surface friction due to the greater surface area of ​​top surface 64A.

[0138] In other words, washers with an outer end that terminates with or is shortened from the outer end of the nut or bolt head can be used with HYTORC®·Z. In such cases, it is necessary for the underside of the washer to be configured with aggressive friction coefficient increasing treatments to ensure that the effective friction radius of the washer is greater than the effective friction radius of the nut or bolt head. Aggressive friction enhancing means can also produce good results when the reaction force received by the outer end of the washer is approximately equal to or lower than the working torque received by the outer end of the nut or bolt head. In these situations, such aggressive friction enhancing means may include roughened surfaces, polygonal surfaces, splines, knurls, spikes, grooves, slots, protruding points, or other such protuberances. Offsetting the aggressive friction coefficient increasing treatments beyond R20 is still a key feature in this case. It should be noted that the improved outer socket 17A requires advanced design to engage and rotatably couple with the washer 1. The modified outer socket 17A also allows for upside down bottle fastening applications.

[0139] (Different Z socket sizes) 11A, 11B, and 11C show an outer socket 17 having straight walls. 11A and an outer socket 17 having tapered walls. 11B and 17 11C Various reaction socket sizes are shown, including. These variations allow different sizes of threaded fasteners and HYTORC® Z Washers to be used with the same Z Gun. Other configurations may be used as desired.

[0140] (Z System applied to HYTORC® torque tools) HYTORC® has developed spline adapters and reaction plates to adapt the Z system to a range of electric, hydraulic and pneumatically operated torque output tool models for normal clearance, low clearance and offset link bolting applications. FIG. 12A shows the socket coupling means, or spline adapter 18 and 18A, as discussed in connection with FIGS. 5A, 5B, 5C and 5D. The spline adapter 18A is designed for use with HYTORC® pneumatic and electric torque guns, such as the Z gun 10A (and 10B) also shown in FIG. 12B. It is shaped as an annular ring with splined engagement portions on the inside and outside. The inner drive socket 16 and the outer reaction socket 17 of the dual drive socket 15 are cooperatively coupled to each other and for relative rotation in LSHT mode via the socket coupling means 18A, and through the tool housing and / or other known and / or proprietary means.

[0141] As shown in FIG. 12C, spline adapter 18 is configured for use with applicant's hydraulic torque tools, such as the HYTORC® ICE10C and HYTORC® AVANTI10D, and other such tools. It is shaped as a stepped annular ring with fused upper and lower portions having different radii. The upper ring has an inner splined engagement portion with a shorter radius for non-rotatably engaging with the splined reaction support portions 19A and 19B of tools 10C and 10D. The lower ring has an outer reaction socket. 17 The dual drive socket 15A has an outer splined engagement portion with a longer radius for non-rotatably engaging a splined portion provided on the inner drive socket 16 and the outer reaction socket 17 of the dual drive socket 15A are cooperatively coupled to one another and for relative rotation via socket coupling means 18A through the tool housing and / or other known and / or proprietary means.

[0142] 13A and 13B show a Z reaction pad 17B for use with the HYTORC® STEALTH 10E, which is configured primarily for low clearance bolting applications. The reaction pad 17B is shaped to match the dimensions of the STEALTH 10E and is non-rotatably attached to the tool housing via pins or screws. The Z pad 17B non-rotatably engages the Z washer 1.

[0143] (Z system applied to HYTORC® offset links) The advantages of the Z system can be achieved by a unique dual drive interchangeable offset link, such as device 80. Link 80 is powered by HYTORC®'s proprietary coaxial action and reaction torque tools, such as the HYTORC® ICE10C hydraulic torque tool or the HYTORC® Z-GUN 10B (or 10A) pneumatic torque multiplier tool. Other such tools include HYTORC®'s proprietary jGUN single speed, jGUN dual speed plus, AVANTI10D and / or STEALTH10E. Other such unique dual drive interchangeable offset links are fully disclosed in the following co-owned and / or co-pending patent applications, the entireties of which are incorporated herein by reference: The specification includes International Application No. PCT / US2014 / 035375, filed April 244, 2014, entitled "APPARATUS FOR TIGHTENING THREADED FASTENERS," and U.S. Patent Application No. 61 / 940,919, filed February 188, 2014, entitled "APPARATUS FOR TIGHTENING THREADED FASTENERS."

[0144] 14A and 14B are top and bottom perspective views of an offset drive link assembly 80 for transmitting and multiplying torque from a HYTORC® ICE 10C to tighten or loosen a threaded fastener (not shown) on a Z-washer 1. Link 80 includes a drive input assembly 81, a drive output assembly 82, and a reaction assembly 83.

[0145] Generally, during a tightening operation, the knurled lower surface of Z-washer 1 rests on the joint to be closed, while the bottom surface of the nut or bolt head to be tightened rests on the smooth upper surface of Z-washer 1. The outer end of Z-washer 1 non-rotatably engages and reacts within a recess in the outer reaction socket of reaction assembly 83 while the inner socket of drive output assembly 82 tightens the nut or bolt head on Z-washer 1.

[0146] Advantageously, the offset drive link assembly allows access to fasteners previously inreachable due to, for example, protruding threads, limited clearance, and obstructions; makes practical electrically, hydraulically, manually, and / or pneumatically driven devices previously unavailable; enables advanced materials previously unavailable, for example, aircraft grade aluminum; configures modular components, for example, hexagonal reduce-increase drive bushings, male and female drive adapters, to match the characteristics of a bolting application; provides precise and customized torque multiplication; controls the application of drive and reaction forces; overcomes corrosion, thread and face deformation, avoids bolt thread wear; negates side loads; ensures balanced bolt loads for symmetrical joint compression; simplifies link and tool use; minimizes the risk of operator error; and maximizes bolting safety.

[0147] (HYTORC® Z System used with HYTORC® Double-Sided Friction Washers) 15A-15G, during use of the HYTORC® Z system, it may be necessary to prevent the back nut or bolt head from rotating depending on the relative friction conditions during operation. When necessary, the operator inserts HYTORC®'s proprietary double-sided friction washer 85 under the back nut or bolt head 22. Its two friction-enhancing surfaces 86 and 87 prevent the bolt head 22 from rotating, especially as soon as a load begins to be applied to the bolt 24. In general, the friction considerations associated with Z-washer 1 also apply to friction-enhancing surfaces 86 and 87. Similar benefits as with the lower bearing surface 3 of Z-washer 1 are achieved by strategically placing friction-enhancing means on surfaces 86 and 87.

[0148] In other words, the HYTORC® proprietary washer system, or dual counter torque washer system, includes a first washer (e.g., Z-washer 1) having an outer reaction engagement means and one friction surface for use under the nut or bolt head to be tightened or loosened, and a second washer (e.g., double-sided friction washer 85) having two friction surfaces for use under the nut or bolt head on the other side of the joint. This dual counter torque washer system controls the fastener thread friction and facial friction to achieve better conversion of torque to bolt load by preventing the stud or bolt from rotating together. Furthermore, the use of double-sided friction washer 85 eliminates the need for a back-up wrench. Note that any friction coefficient increasing treatment means discussed for the HYTORC® Z-washers also apply to the HYTORC® double-sided friction washer 85.

[0149] Note that this dual opposing torque washer system can be used with any part, any combination, or all of the HYTORC® Z system. Remember, torque friction is unknown and tension bolt loosening is unknown. This washer system in tandem eliminates uncontrolled face friction and uncontrolled side loads, thereby improving bolt load accuracy in torque and tension. HYTORC® double sided friction washers may be used without the Z washers which achieves some of the benefits mentioned above.

[0150] Additionally, direct tension indicating washers, or Squirter washers, may be used with any part, any combination, or all of the HYTORC® Z System, as disclosed in the following U.S. patents issued to Applied Bolting Technology Products, Inc., all of which are incorporated herein by reference: U.S. Patent No. 5,769,581; U.S. Patent No. 5,931,618; U.S. Patent No. 6,425,718; and U.S. Patent No. 8,002,641. In one particularly advantageous embodiment, another HYTORC® proprietary washer system, or dual counter torque and / or load indicating washer system (not shown), includes a first washer with an outer reaction engagement means and one friction surface (such as Z-washer 1) for use under the nut or bolt head to be tightened or loosened, and a second washer with two friction surfaces for use under the nut or bolt head on the opposite side of the joint (such as double-sided friction washer 85) that includes Squirter washer properties. This dual counter torque washer system stops the rotation of the stud or bolt and clearly indicates once the bolting operation is performed to control the fastener thread and facial friction to achieve better translation from torque to bolt load. Note that any of the friction coefficient increasing treatments discussed with respect to HYTORC® Z-washers are applicable to HYTORC® double-sided friction washer 85 that includes Squirter washer properties.

[0151] HYTORC® Z System for use with HYTORC® Z Nuts or Z Bolts Applicant's recent Z System related research and development includes the application of friction coefficient increasing treatments to nuts and bolt heads as discussed with respect to HYTORC® Z Washers. As explained in connection with Figures 15A-15G, during use of the HYTORC® Z System, it may be necessary to prevent the back nut (not shown) or bolt head from rotating, depending on the relative friction conditions of operation. One solution is the use of HYTORC®'s proprietary double-sided friction washer 85 under the back nut or bolt head 22.

[0152] 15H-15K, another solution is the application of the friction coefficient increasing treatment described for the HYTORC®·Z washers to the nuts and bolt heads, such as the back nut (not shown) or the bottom surface of bolt heads 22A and / or 22B. Their respective friction enhancing surfaces 86A and 86B keep bolt heads 22A and 22B from rotating, especially as soon as a load begins to be applied to bolts 24A and 24B. Note that the friction enhancement of 86A is quite similar to that of washer 1, as shown in many of the figures. However, the friction enhancement of 86B is quite similar to that of washer 1 of FIG. 8D9. 8D5 is very similar to that of

[0153] In other words, the HYTORC® proprietary washer and nut or bolt system, or counter torque Z-washer and Z-nut or Z-bolt system, includes a first washer with an outer reaction engagement means and one friction surface for use under the nut or bolt head to be tightened or loosened (such as Z-washer 1), and a nut or bolt with a low friction surface on the opposite side of the joint (such as Z-bolt head 22A). The Z-washer-Z-nut / bolt system stops the stud or bolt from turning and eliminates the need for a back-up wrench in order to control the fastener thread and facial friction to achieve better transfer of torque to bolt load. Additionally, the Z-washer-Z-nut / bolt system is an alternative to dual counter torque washer systems when they are more expensive and / or less effective.

[0154] Generally, most of the discussion of FIGS. 1-15G pertains to the HYTORC® Z system, and more specifically to Z-washers 1-15G. 8D7 The discussion of Figures 7 and 8 (e.g., type and arrangement of friction coefficient increasing treatments and outer engagement geometry) may be applied to the rear nuts and / or bolt heads of Figures 15H-15K.

[0155] The Z Washer-Z Nut / Bolt System may be used with any, any combination, or all of the HYTORC®-Z System. Remember that torque has unknown friction and tension has unknown bolt loosening. The Z Washer-Z Nut / Bolt System may be combined and / or combined as part of a combination to improve bolt load accuracy of torque and surface tension, to eliminate uncontrolled surface friction and uncontrolled side loads.

[0156] (HYTORC(R) Z Gun (Details)) 16A and 16B, which are perspective views of tools 10A and 10B, originally shown in Figures 3A-3C as HYTORC® Z Guns. Tools 10A and 10B include a drive input and output assembly 100, a rotational force multiplication assembly 200, a vibration force assembly 300, a mode shifting assembly 400, and a dual drive output and reaction socket assembly 15, or a HYTORC® Z Socket.

[0157] As an example, reference is made to Figure 17A, which is a cross-sectional side view of tool 10A in "LSHT" mode, and Figure 17B, which is a cross-sectional side view of tool 10B in "HSLT" mode.

[0158] 17A and 17B show the drive input-output assembly 100 of the tools 10A and 10B. The drive input components can include a drive tool housing 101 containing a drive generating mechanism 102, a handle assembly 103, and a switching mechanism 104. The drive generating mechanism 102 is shown configured to generate a torque turning force 91 in one direction 93 to rotate the nut 36 and is configured as a motor drive means including a hydraulic, pneumatic, electric, or manual motor. The drive tool housing 101 is shown generally as a cylinder with a handle assembly 103 held by an operator. The handle assembly 103 includes a switching mechanism 104 for switching the drive generating mechanism 102 between an inoperative position and an operative position and vice versa. A turning force input shaft 121 couples the drive input components of the drive input-output assembly 100 to the turning force multiplication assembly 200 and the vibration force assembly 300 and transfers turning force 91 between said assemblies. The turning force output shaft 122 includes a drive portion 123, which may be configured, for example, as a square drive. The turning force output shaft 122 couples the drive output components of the drive input and output assembly 100 with the turning force multiplication assembly 200 and the vibration force assembly 300, and transmits a multiplied or vibration form of the turning force 91 between said assemblies and the dual drive output and reaction socket assembly 15. In one mode of operation, the reaction spline adapter 443 receives a torque reaction force 92 in an opposite direction 94.

[0159] FIG. 18 is a side cross-sectional view of the turning force multiplication assembly 200 and the vibration force assembly 300 of the tool 10A in LSHT mode. FIG. 18 also shows portions of the drive force input / output assembly 100. Components not shown in other views include the turning force output shaft bearing 191. FIG. 19 is a perspective cross-sectional view of the drive tool housing assembly 101, drive tool handle assembly 103, and associated interior components of the tools 10A and 10B. Components shown include the handle / rear cover 131, gasket 137 adjacent the rear cover 131 and the rear of the housing 101, the motor assembly 102, and the air valve assembly 132 having an outer air valve 133 and an inner air valve 134 held in place by dowel pins 135. The rear cover 131 attaches to the rear of the housing 101 and holds such components within the housing 101 by BHCS torque screws 136. The trigger assembly 150 includes the switching mechanism 104, the spring 151, the trigger shaft bushing 152, and the trigger rod 153. The handle 103 includes a control valve assembly with a control valve 157 and a dowel pin 156, a conical spring 161, a regulator valve spacer 162, and two O-rings 163, one between the control valve assembly 155 and the inner regulator housing 164 and one between the inner regulator housing 164 and a bottom plate 173. A mesh screen 171 is disposed between the bottom plate 173 and a noise filter 172. A socket head bolt 174 connects these components, as well as the bottom plate 173 with the gasket 176, to the handle assembly 103. An air fitting 715 protrudes from the bottom plate 173 and connects to the inner regulator housing 164. Handle push button assembly 180 (not shown) allows the operator to change the rotational force direction and includes a push button handle insert 181 , a push button rack 182 , a spring 183 , and a connector 184 .

[0160] The rotational force multiplication assembly 200 includes a plurality of rotational force multiplication transmitter assemblies and includes a rotational force multiplication mechanism 210 within a rotational force multiplication mechanism housing 201 for a substantially LSHT mode. In the embodiment shown in FIGS. 17A and 17B, the rotational force multiplication assembly 200 includes five multiplication transmitter assemblies 211, 212, 213, 214, and 215. Needless to say, there are numerous well-known types of force multiplication mechanisms. Generally, the rotational force multiplication transmitter assemblies 211-215 constitute a rotational force multiplication mechanism 210, a compound epicyclic gear system. The compound epicyclic gear system may include a plurality of outer planetary gears that rotate around a central sun gear. The planetary gears may be mounted on a movable carrier, and these carriers themselves can rotate relative to the sun gear. Such a compound epicyclic gear system may include an outer ring gear that engages the planetary gears. A simple epicyclic gear system has one sun, one ring, one carrier, and one planetary set. The compound epicyclic gear system can include a meshing planetary structure, a stepped planetary structure, and / or a multi-stage planetary structure. Compared with a simple epicyclic gear system, the advantages of a compound epicyclic gear system are a larger reduction ratio, a higher torque-to-weight ratio, and a more flexible form.

[0161] The torque multiplication transmitter assemblies 211-215 may include gear cages, planetary gears, planetary gears, ring gears, sun gears, oscillating gears, cycloidal gears, epicyclic gears, connectors, spacers, shift rings, retaining rings, bushings, bearings, caps, transmission gears, transmission shafts, locating pins, drive wheels, springs, or any combination or portion thereof. The torque multiplication transmitters, e.g., 211-215, may include other similar components. It should be noted that the torque input shaft 121 may be considered a torque multiplication transmitter, and specifically, it is the first stage motor sun gear of the torque multiplication transmitter 211. Torque multiplication assemblies are well known, disclosed and described. An example is disclosed and described in Applicant's U.S. Pat. No. 7,950,309, the entirety of which is incorporated herein by reference.

[0162] Figure 18 shows portions of the torque multiplication assembly 200 in greater detail than Figures 17A and 17B. Components of the torque multiplication assembly 200 shown in Figure 18 and not shown in Figures 17A and 17B include the lock nut 250, the lock washer 249, the bearing 241, the housing adapter 247, the bearing spacer 252, the inner retaining ring 243, the bearing 242, the gearbox connector 248, the upper and lower inner retaining rings 251, the upper and lower ball bearings 246, the double sealed bearing 244, and the inner retaining ring 245.

[0163] The vibration force assembly 300 includes a vibration force mechanism 310 in a vibration force mechanism housing 301, substantially for HSLT mode, including one or more vibration transmitters. In the embodiment shown in Figures 17A and 17B, the vibration force assembly 300 includes two vibration transmitters, specifically impact transmitters 311 and 312. Of course, there are a variety of known vibration force mechanisms, and often involve an impact force mechanism consisting of an anvil and a rotating hammer. The hammer is rotated by a motor, and the anvil has a resistance to rotation. Each impact provides a hammer force. This hammer force is sent to an output drive.

[0164] In general, the vibration force assembly may include a vibration force mechanism, such as an ultrasonic force mechanism including an ultrasonic force transmitter, a mass imbalance force mechanism including a mass imbalance force transmitter, or any other time-dependent disturbance (load, displacement, or velocity) mechanism including a time-dependent disturbance (load, displacement, or velocity) force transmitter. Further vibration force assemblies may include hammers, anvils, connectors, spacers, shift ring retaining rings, bushings, bearings, caps, transmission gears, transmission shafts, locating pins, drive wheels, springs, or any combination thereof. The vibration transmitters, such as 311 and 312, may include other known similar components. FIG. 18 also shows a dowel pin 320.

[0165] Typically, the RPM of tools 10A and 10B decreases as the torque output increases. Alternatively, activation or deactivation of the vibration force mechanism 310 may be such that the force mechanism 310 is disabled or enabled when the RPM decreases or exceeds a predetermined value. In HSLT mode, the vibration force mechanism 310 provides a rotational force to the nut. In LSHT mode, the vibration force mechanism 310 acts as an extension to transmit the rotational force from one part of the tool to another. It is noted that the vibration force mechanism 310 may be located proximate to the tool motor, proximate to the tool output drive, or anywhere in between.

[0166] In HSLT mode, the vibration force mechanism 310 always receives and rotates the rotational force, the housing may or may not receive the rotational force, and the torque output is relatively low, so the housing does not need to react. Note that in the embodiment of Figures 17A and 17B, the vibration force mechanism 310 can only operate in a high speed mode, e.g., HSLT mode. That is, at low speeds, e.g., LSHT mode, where the torque boosting mechanism is operable, there is no shock and / or minimal vibration. During HSLT mode, the at least two multiplication transmitters are single and rotate with the hammer to assist the hammer action from the impact mechanism. Note that if the fastener shows little or no corrosion, thread and face deformation, and / or thread galling, the vibration force mechanism 310 may not be necessary in HSLT mode.

[0167] The slide action mode shift assembly 400 is for substantially shifting the tool 10A from the LSHT mode to the HSLT mode and the tool 10B from the HSLT mode to the LSHT mode. In the embodiment shown in Figures 17A and 17B, the slide action mode shift assembly 400 includes a shifter base 401, a shifter collar 442, a splined shifter swivel 443, a shifter spline ring 445, an outer shift ring 456, and an inner shift assembly 450. The inner shift assembly 450 includes an inner shift bushing 452, an inner shift ring 453, and a coupling ball bearing 454, as shown in Figures 17A and 17B.

[0168] The slide action mode shift assembly 400 may include a manual assembly (sequential manual, asynchronous, or preselector) or an automatic assembly (manumatic, semi-automatic, electro-hydraulic, Saxomat, dual clutch, or continuously variable), torque converter, pump, planetary gears, clutches, belts, valves, connectors, spacers, shift ring retaining rings, bushings, bearings, collars, locking balls, caps, transmission gears, transmission shafts, synchronizers, locating pins, drive wheels, springs, or any combination or portion thereof. The mode shift components may include other known similar components. Of course, there are a variety of known mode shift assemblies and often involve shift components consisting of collars, rings, and locking balls.

[0169] FIG 18 illustrates portions of the slide action mode shift assembly 400 in greater detail than FIGS. 17A and 17B. Additional components of the shift assembly 400 shown in FIG 18 and not shown in FIGS. 17A and 17B include inner retaining rings 451, 457 and 459, lower and upper bushings 446 and 447, and shifter ring reaction plug 458. FIG 20 illustrates a perspective view of the mode shift assembly 400 of tool 10A and tool 10B. FIG 20 illustrates a substantial exterior portion of the mode shift assembly 400. Components not shown in other figures include lock shaft cap 402, handle insert 403, handle grip 404, pull handle 405, actuator link and shifter pin 406, pivot pin 407, shifter extension bracket 410, SHCS 411, shifter fastener assembly 430, lower and upper shifter links 441, wave spring 448, and holder spline 490.

[0170] 5A-5D, which are perspective cross-sectional views showing the dual drive output and reaction socket assembly 15 of tools 10A and 10B, and the dual drive output and reaction socket assembly 15A of tools 10C and 10D.

[0171] In the LSHT mode, the dual drive output and reaction socket assembly 15 is substantially for transmitting a multiplied form of the rotational force 91 in one direction 93 to the nut 36 and a corresponding multiplied form of the reaction force 92 in another direction 94 to the Z-washer 1 acting as a stationary object. In the HSLT mode, the dual drive output and reaction socket assembly 15 is substantially for transmitting an oscillating form of the rotational force 91 in one direction to the nut 36 or the nut 36 and the washer 1. In the embodiment shown in Figures 17A and 17B, the dual drive output and reaction socket assembly 15 includes an inner drive socket 16 and an outer reaction socket 17. The outer reaction socket 17 is non-rotatably engageable with the reaction spline shifter swivel 443 during the LSHT mode. Of course, there are various well-known engagement mechanisms for transmitting the rotational and reaction forces to a threaded fastener and its nut and its washer. These mechanisms include castellations, splines, and other geometries.

[0172] The tool 10A operates in the LSHT mode as follows: The operator pulls the shifter base 401 towards the rearward position. The coupling / locking ball bearing 454 disengages from the torque multiplier housing 201 and engages the shifter spline ring 445 inside the reaction spline shifter swivel 443. The shifter base 401 is coupled to the torque multiplier housing 201. The torque multiplier transmitters 211-215 are unlocked and can rotate freely relative to one another. The operator also pulls the shifter base 401 towards the rearward position, engaging the vibration (impact) force spline ring 453 of the shift assembly with the vibration (impact) force housing 301. This locks up the vibration (impact) force transmitters 311 and 312 and thus the vibration (impact) force assembly. This then allows the turning force output drive shaft 120 to be driven by the fifth gear cage of the turning force multiplication transmitter 215. The fifth gear cage is splined to the vibration (impact) force mechanism housing 301. The splined shifter swivel 443 is splined to the reaction socket 17. The reaction socket 17 is then geometrically engaged with the washer 1 under the nut 36. When the nut 36 is seated, the compressed lock disk washer 1 serves as a stationary object. By means of this stationary object, the turning force multiplication mechanism housing 201 turns off the reaction of the reaction socket 17. With the turning force multiplication mechanism housing 201 held stationary, the turning force multiplication transmitters 211-215 tighten the seated nut 36 via the turning force output drive shaft 120.

[0173] Generally, operation of the tool 10B requires activation or deactivation of the impact mechanism 310. The slide action mode shift assembly 400 can shift the tool 10A between the multiplication mechanism 210, the impact mechanism 310, a portion of the multiplication mechanism 210 (e.g., one of the multiple multiplication transmitters), a portion of the impact mechanism 310 (e.g., one of the multiple impact transmitters), or any combination thereof.

[0174] The tool 10B operates in the HSLT mode as follows: The operator pushes the shifter base 401 towards a forward position. The coupling / locking ball bearing 454 engages the turning force multiplication mechanism housing 201 and the vibration (impact) force mechanism housing 301. The shifter spline ring 445 disengages from the inside of the reaction spline shifter swivel 443, thereby rendering it idle and inactive. The reaction socket 17 is therefore idle and inactive, since it is not splined to the turning force multiplication mechanism housing 201. With the coupling / locking ball bearing 454 engaged with the vibration (impact) force mechanism housing 301, the turning force multiplication transmitters 211-215 are locked up and cannot rotate relative to one another. The turning force multiplication assembly 200 therefore rotates as a single mass via the turning force input shaft 121. The motor 102 rotates the turning force input shaft 121 including the first stage sun motor gear of the turning force multiplication transmitter 211. The operator also pushes the shifter base 401 towards the forward position, disengaging the vibration (impact) force spline ring 453 of the shift assembly from the vibration (impact) force mechanism housing 301. This unlocks the vibration (impact) force transmitters 311 and 312 and thus the vibration (impact) force assembly 300. The vibration (impact) force mechanism housing 301 is splined to the fifth gear cage of the turning force multiplication transmitter 215. The vibration (impact) force transmitter 312 (anvil) is splined to the turning force output drive shaft 120. The turning force output drive shaft 120 runs the nut 36 up or down on the stud 23 by the impact of the vibration (impact) force transmitter 311 (hammer).

[0175] Returning to FIGS. 3A-3C and 4A-4B, generally and from the perspective of the nut 36, tool 10A tightens, loosens, or tightens and loosens the nut 36 in the LSHT mode, and tool 10B runs up, runs down, or runs up and runs down the nut 36 in the HSLT mode. Generally and from the perspective of the washer 1, tool 10A pressurizes washer 1''' between a tightened nut 36' on a loaded stud 23' and a tightened joint 30' to a predetermined tightening torque and / or compresses washer 1''' between a seated nut 36' on a pre-relaxed stud 23' and a pre-relaxed joint 30' from a predetermined tightening torque. Generally and from the perspective of the nut 36, in the HSLT mode, tool 10B pressurizes washer 1''' between a pre-loaded stud 23' and a tightened joint 30' to a predetermined tightening torque and / or compresses washer 1''' between a seated nut 36' on a pre-relaxed stud 23' and a pre-relaxed joint 30' from a predetermined tightening torque. Compressing washer 1' to a predetermined tightening torque between seated nut 21' on 23' and pre-tightened joint 30', decompressing washer 1 from a predetermined tightening torque between nut 36 on stud 23 and loosened joint 30, or vibrating pressurized washer 1" between tightened nut 21" on loaded stud 23" and tightened joint 30" sufficiently pulverizes bolt thread corrosion. Note that reference numbers with "'" and """ represent similar force magnitudes.

[0176] In the HSLT mode, the tool 10B seats the nut 36' on the stud 23' or both the nut 36 and washer 1' by running down with a rotational force 91 in one direction 93 and compressing the washer 1' on the pre-tightened joint 30' to a predetermined tightening torque, runs up the seated nut 36' or both the seated nut 36' and compressed washer 1" on the pre-loosened stud 23' on the pre-loosened joint 30' from a predetermined pre-loosened torque with a rotational force 92 in the opposite direction 94, or vibrates (impacts) the tightened nut 36" over the pressurized washer 1" to a predetermined tightening torque. Vibration is applied to sufficiently pulverize the corrosion. During the LSHT mode, the tool 10A tightens a seated nut 36' on a compressed washer 1' on a preloaded bolt 23' on a pretightened joint 30' to a predetermined tightening torque with a turning force 91 in one direction 93 and applies a reaction force 92 in the opposite direction 93 to the compressed washer 1', or loosens a tightened nut 36" over a pressurized washer 1" on a loaded stud 23" on a tightened joint 30' from a predetermined tightening torque with a turning force 92 in the opposite direction 94 and applies a reaction force 91 in one direction 93 to the pressurized washer 1". Note that reference numbers with "'" and """ represent similar force magnitudes.

[0177] In operation, the tool 10A switches to the tool 10B in the HSLT mode when the nut 36 in the LSHT mode is unseated and the washer 1 is decompressed with a predetermined pre-loosening torque. In operation, the tool 10B switches from the HSLT mode to the tool 10A in the LSHT mode when the nut 36 is seated and the washer 1 is decompressed with a predetermined tightening torque or the thread corrosion is sufficiently broken down. Note that the operator uses the mode shift assembly 400 to switch the tool from the LSHT mode to the HSLT mode or vice versa, but such a switch may include other known similar components. The mode shift assembly 400 is a manual switch, but may be automatic. Similarly, the activation or deactivation of the vibration (impact) force assembly 300 may be manual or automatic. The LSHT mode can be switched from torque-adjusted to vibration-assisted or vice versa, and the HSLT mode can be switched from vibration-adjusted to torque-assisted or vice versa. The vibration (impact) force assembly 300 can continue to operate even if the washer 1 begins or stops rotating. The LSHT mode can also provide vibration assistance to loosen the nut 36, helping to overcome chemical, heat, and / or lubrication corrosion and avoid galling of the bolt threads.

[0178] It should be noted that the power tool for tightening and loosening industrial fasteners with reduced galling according to the present invention may also be characterized in that the turning force multiplication mechanism-housing 201 is operatively coupled to at least one of the turning force multiplication transmitters 211-215, such that during LSHT mode at least two of the multiplication transmitters 211-215 rotate relative to one another, and during HSLT mode at least two of the multiplication transmitters 211-215 are unified to assist the hammering action provided by the turning force impact mechanism 310. During HSLT mode, the combination of the turning force multiplication assembly 200 including the turning force output drive shaft 120 and the housing rotates as a single mass in the same direction. This provides inertia that improves the torque output of the impact mechanism to overcome corrosion, thread deformation, and face deformation and to avoid galling of the bolt threads.

[0179] A method is disclosed for tightening and loosening two parts together with minimal galling in an industrial fastener 20 of the type having a nut 36, a washer 1, and a stud 23 by a power tool (10A and 10B) of the type having a motor 102 for generating a torque, a drive (122 and 123) for transmitting the torque 91, a torque multiplication mechanism for LSHT mode including torque multiplication transmitters 211-215, a torque multiplication mechanism 210 in a housing 201, a vibration force mechanism for HSLT including vibration transmitters 311, 312, a drive socket 16 operatively coupled to a nut 36, and a reaction socket 17 operatively coupled to a washer 1 for transmitting a reaction force 92 to the washer 1 during a LSHT mode, and operatively coupled to or disengaged from the washer 1 during a HSLT mode. Such a method may include placing a washer 1 on the stud free end 25, placing a nut 36 over the washer 1 on the stud free end 25, running down the nut 36 or the nut 36 and washer 1 on the stud free end 25 to a predetermined tightening torque in the HSLT mode to seat the nut 36 and compress the washer 1, switching the HSLT mode to a LSHT mode, and applying torque to the seated nut 36 to tighten it to the predetermined tightening torque in the LSHT mode, and then tightening the nut 36. Pressurizing and loosening the washer 1 between the tightened nut 36 and the tightened joint 30 includes placing the tool 10A over the tightened nut 36 and the pressurized washer 1, applying a torque to loosen the tightened nut 36 over the pressurized washer 1 to a predetermined loosening torque in the LSHT mode, switching from the LSHT mode to the HSLT mode, and in the HSLT mode, running up the seated nut 36 on the stud free end or the seated nut 36 and the compressed washer 1. The loosening method further includes applying vibration to break up the bolt thread corrosion by vibrating the tightened nut 36 over the pressurized washer 1 in the HSLT mode, and switching from the HSLT mode to the LSHT mode.

[0180] The above-described tools 10A and 10B, and the following tools 10F, 10G, 10H, and 10I can generally be described as torque power tools for tightening, loosening, or tightening and loosening a type of industrial screw fastener having coaxial reaction surfaces, studs, and nuts threadable onto the studs or stud heads coupled to the studs with minimal slippage. Tools 10A, 10B, 10F, 10G, 10H, and 10I include a motor for generating a rotational force, a drive unit for transmitting the rotational force, a rotational force multiplication mechanism within a housing including a rotational force multiplication transmitter corresponding to all torque modes from low resistance to high resistance, and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable during all torque modes from low resistance to high resistance.

[0181] Alternatively, the above-described tools 10A and 10B, and the following tools 10F, 10G, 10H, and 10I can be described as power tools for tightening and loosening a type of industrial screw fastener having nuts, washers, and studs with minimal slippage. The tools include a motor for generating a rotational force, a drive unit for transmitting the rotational force, a rotational force multiplication mechanism within a housing including a rotational force multiplication transmitter corresponding to a continuous torque mode, and a vibration force mechanism including a vibration transmitter for an intermittent torque mode, an intermittent force mode, or both an intermittent torque mode and an intermittent force mode.

[0182] Referring to FIG. 21A as an example, this is a cross-sectional view showing an embodiment of the present invention as tool 10F. Tool 10F is a power tool for tightening, loosening, or tightening and loosening a type of industrial screw fastener 801 having a stud and a nut threadable onto the stud with minimal slippage. Tool 10F includes a drive input / output assembly 810, a rotational force multiplication assembly 820, a vibration force assembly 830, a mode shift assembly 840, and a drive output socket reaction arm assembly 850.

[0183] Referring to FIG. 21B, by way of example, which is a cross-sectional view showing an embodiment of the present invention as tool 10G. Tools 10F and 10G are similar as indicated by the overlapping reference numbers. Tool 10G is a reaction arm-less power tool for tightening, loosening, or tightening and loosening industrial threaded fasteners 802 of the type having a coaxial reaction surface, such as a HYTORC® Z Washer 1, a stud, and a nut threadable onto the stud, with minimal galling. Tool 10G includes a drive input and output assembly 810, a turning force multiplication assembly 820, a vibration force assembly 830, a mode shifting assembly 840, and a dual drive output and reaction arm assembly 855 similar to the HYTORC® Z Socket 15.

[0184] Tools 10F and 10G include a rotary force multiplication mechanism having one or more gear stages. The vibration force mechanism includes a rotary force impact mechanism having a hammer and anvil, and an intermittent force mechanism 860 consisting of an ultrasonic force mechanism including an ultrasonic force transmitter, a mass imbalance force mechanism including a mass imbalance force transmitter, or any other time-dependent disturbance (load, displacement, rotation, or velocity) mechanism including a time-dependent disturbance (load, displacement, rotation, or velocity) force transmitter. Tool 10F is a modified HYTORC® THRILL gun that includes the intermittent force mechanism 860. Tool 10G is a modified HYTORC® Z gun that includes the intermittent force mechanism 860.

[0185] 22A, which is a cross-sectional view of an embodiment of the present invention as tool 10H. Tool 10H is a power tool for tightening, loosening, or tightening and loosening industrial threaded fasteners 901 of the type having a stud and a nut threadable onto the stud with minimal galling. Tool 10H includes a drive input and output assembly 910, a rotational force multiplication assembly 920, a vibration force assembly 960, a mode shifting assembly 940, and a drive output socket and reaction arm assembly 950.

[0186] Referring to FIG. 22B by way of example, this is a cross-sectional view of an embodiment of the present invention as tool 10I. Tools 10H and 10I are similar as indicated by the overlapping reference numbers. Tool 10I is a reaction arm-less power tool for tightening, loosening, or tightening and loosening industrial threaded fasteners 901 of the type having a coaxial reaction surface, such as a HYTORC® Z washer 1, a stud, and a nut threadable onto the stud, with minimal galling. Tool 10I includes a drive input and output assembly 910, a turning force multiplication assembly 920, a vibration force assembly 960, a mode shifting assembly 950, and a dual drive output and reaction arm assembly 955 similar to the HYTORC® Z socket 15.

[0187] Tools 10H and 10I include a rotational force multiplication mechanism including one or more gear stages. Vibration force mechanism 960 includes an ultrasonic force mechanism including an ultrasonic force transmitter, a mass imbalance force mechanism including a mass imbalance force transmitter, or any other time dependent disturbance (load, displacement, rotation, or velocity) mechanism including a time dependent disturbance (load, displacement, rotation, or velocity) force transmitter. Tool 10H is a HYTORC® jGUN Gun Dual Speed ​​Plus including an intermittent force mechanism 960. Tool 10I is a HYTORC® jGUN Gun Dual Speed ​​Plus including an intermittent force mechanism 960 and a dual drive output and reaction socket assembly 955 similar to the HYTORC® Z Socket 15.

[0188] In addition to tools 10A, 10B, 10G, and 10I, a drive socket is operatively coupled to the nut. The reaction socket may be operatively coupled to the housing and the coaxial reaction surface for transmitting a reaction force to the coaxial reaction surface during a high resistance torque mode. Alternatively, the reaction socket may be operatively coupled to the housing and the coaxial reaction surface or operatively coupled to the housing and operatively disengaged from the coaxial reaction surface during a low resistance torque mode or an intermittent force mode. The drive socket is designated as an inner socket and the reaction socket is designated as an outer socket.

[0189] The following discussion pertains to tools 10A, 10B, 10F, 10G, 10H and 10I. Note that for ease of explanation, whenever a "nut" or "fastener" is mentioned, this includes the possibility of a stud head attached to a stud, a nut and washer on the stud and / or over the stud, a stud head attached to a stud and a washer over the stud. Note that any suitable fastener geometry, such as an Allen key connection, a shoulder socket head screw "SSC" head, a button socket head screw "SHBS" head, a Hexagonal Socket Head Screw "HHCS" head, a Round Head Slotted Screw "RHSS" head, a Flat Head Torx Screw "FHTS" head, a Socket Head Set Screw "SSS" head, or a Socket Head Screw "SHCS" head, may be used with the present invention.

[0190] In these discussions, the coaxial reaction surface is described as a washer. However, in some cases, the washer may be integral with or coupled to the joint to be tightened or loosened. In other cases, the coaxial reaction surface is a portion of the stud that extends beyond the nut. In still other cases, the coaxial reaction arm may abut against a stationary object that is feasible and accessible to facilitate tightening and loosening with minimal galling.

[0191] In general, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following while in the intermittent force mode: the tool may run down the nut, or the nut and washer with an intermittent rotational force in one direction; the tool may run up the nut, or the nut and washer with an intermittent rotational force in the opposite direction; or the tool may shock, vibrate, or both shock and vibrate the nut, or the nut and washer, or the stud head and washer with an intermittent rotational force to apply vibration and rotation, an intermittent vibration force to apply vibration, or both in opposite directions.

[0192] More specifically, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following during the intermittent force mode: The tool may run down the nut, or the nut and washer, with an intermittent rotational force in one direction to seat the nut from a limitably rotatable state with significant adverse bolting application characteristics to a predetermined tightening torque state and compress the washer between the joint to be tightened and the seated nut; The tool may run up the nut, or the nut and washer, with an intermittent rotational force in the opposite direction to unseat the nut from a limitably rotatable state with significant adverse bolting application characteristics and decompress the washer between the joint to be loosened and the unseatable nut. Alternatively, the tool may impact, vibrate, or both impact and vibrate the nut, or the nut and washer, with an intermittent rotational force to apply vibration and rotation in opposite directions, an intermittent vibratory force to apply vibration, or both, to go from an insufficiently comminuted thread erosion condition to a fully comminuted thread erosion condition. For example, the tool may generate ultrasonic waves via an ultrasonic generator, such as vibration force mechanism 960.

[0193] Often an intermittent force (shock, vibration, ultrasonic, etc.) is necessary during rundown to tightly compress the washer between the nut and the flange face. Without such compression from the shock, the washer may not experience the reaction forces due to the two frictions of the two washer faces. When properly compressed, the washer face abutting the nut experiences clockwise rotational friction due to the torque output of the tool, and an equal and opposite counterclockwise rotational friction due to the reaction force. As such, the rotational friction from the washer face abutting the flange face prevents the washer from rotating. In other words, the tool is configured to hold the washer stationary while rotating the nut. This eliminates the normal side loads and surface differences between the nuts. Thread and facial friction is better controlled for improved conversion of torque to fastener load.

[0194] In general, tools 10A, 10B, 10F, 10G, 10H and 10I may do any of the following during the high resistance torque mode: the tool may tighten a nut with a slow, high torque rotational force in one direction and apply a reaction force to a washer in the opposite direction, and / or the tool may loosen a nut with a slow, high torque rotational force in the opposite direction and apply a reaction force to a washer in the one direction.

[0195] More specifically, tools 10A, 10B, 10F, 10G, 10H and 10I may do any of the following during the high resistance torque mode: the tool may tighten a nut from a predetermined tightening torque condition to a predetermined tightening torque condition by torquing up the nut with a slow speed, high torque rotational force in one direction and pressurizing a washer between the loosened joint and the tightened nut by applying a reaction force to the washer in the opposite direction; and / or the tool may loosen a nut from a predetermined tightening torque condition to a predetermined tightening torque condition by torquing down the nut with a slow speed, high torque rotational force in the opposite direction and depressurizing a washer between the loosened joint and the loosened nut by applying a reaction force to the washer in the one direction.

[0196] In general, tools 10A, 10B, 10F, 10G, 10H and 10I may do either of the following during the low resistive torque mode: the tool may run down a nut, or a nut and washer, with a high speed, low torque rotational force in one direction, and / or the tool may run up a nut, or a nut and washer, with a high speed, low torque rotational force in the opposite direction.

[0197] More specifically, tools 10A, 10B, 10F, 10G, 10H and 10I may do any of the following during the low resistance torque mode: the tool may run down the nut, or the nut and washer, with a high speed, low torque rotational force in one direction to seat the nut from a freely rotatable state with insignificant detrimental bolting application characteristics to a predetermined tightening torque state and compress the washer between the joint to be tightened and the seated nut, and / or the tool may run up the nut, or the nut and washer, with a high speed, low torque rotational force in the opposite direction to unseat the nut from a predetermined tightening torque state to a freely rotatable state with insignificant detrimental bolting application characteristics and decompress the washer between the joint to be loosened and the unseatable nut.

[0198] In general, tools 10A, 10B, 10F, 10G, 10H and 10I may tighten, loosen or tighten and loosen a nut in a high resistance torque mode. The tools may perform run-up, run-down or impact on the nut or the nut and washer in an intermittent torque mode or a low resistance torque mode. The tools may switch from the intermittent torque mode to the high resistance torque mode when the nut is seated and the washer is compressed at a predetermined tightening torque condition and / or when the thread corrosion is sufficiently milled. The tools may switch from the high resistance torque mode to the intermittent torque mode and / or to the low resistance torque mode when the nut is unseated and the washer is decompressed at a predetermined pre-relaxed torque condition. The tools may switch from the low resistance torque mode to the high resistance torque mode when the nut is seated and the washer is compressed at a predetermined tightening torque condition.

[0199] During operation, the tool can switch from high resistive torque mode to intermittent torque mode, high resistive torque mode to low resistive torque mode, low resistive torque mode to intermittent torque mode, low resistive torque mode to high resistive torque mode, intermittent torque mode to high resistive torque mode, or intermittent torque mode to low resistive torque mode.

[0200] Activation or deactivation of the impact mechanism or torque multiplication mechanism may be manual or automatic. Thus, the switching mechanism may be manual or automatic. Furthermore, the switching mechanism, and thus any mode, or combination of modes and corresponding mechanisms, may be automatically activated according to the observed load on the fastener. For example, the galling-minimized power tool of the present invention may require vibration and / or impact to break up corrosion in a tightened fastener and to run up or down the nut at high speeds. A torqued nut cannot be turned by mere vibration and / or impact. An operator may need to activate vibration and / or impact to break up dried corrosion in a torqued nut. This can be done independently of or in combination with the torque multiplication mechanism. As mentioned above, the torque required to loosen the nut is greater than the initial tightening torque as the lubricant dries or disappears, corrosion is present, and the stud is still loaded and stretched. In other words, it takes a higher torque value to unload the stud to the unstretched state. Once the nut is loosened, it can be rotated or run-up at higher speeds during low resistance torque mode and / or intermittent torque mode. However, there are times when the nut must be released on a corroded and / or damaged or defective stud thread. Often this requires vibration and / or intermittent force in combination with a torque multiplier. During run-down, the nut is rotated at higher speeds during low resistance torque mode and / or intermittent torque mode. Here, the low resistance torque mode alone may not be sufficient to overcome the corroded and / or damaged or defective stud thread. Equally often this requires vibration or intermittent force in combination with a torque multiplier. The present invention solves these problems.

[0201] Generally disclosed is a method for tightening, loosening, or tightening and loosening an industrial threaded fastener of the type having a coaxial reaction surface, a stud, and a nut or stud head coupled to the stud threadably engageable with the stud, with minimal galling, by a reaction arm-less torque power tool, the reaction arm-less torque power tool including a motor for generating a turning force, a drive for transmitting the turning force, a turning force multiplication mechanism in a housing including a turning force multiplication transmitter for all torque modes from low resistance to high resistance, and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable in all torque modes from low resistance to high resistance. The tightening method includes running down the nut, the stud head, the nut and the coaxial reaction surface, or the stud head and the coaxial reaction surface in one direction, and applying torque to tighten the nut or stud head in the one direction while turning off the reaction of the coaxial reaction surface in the opposite direction. A method of loosening includes applying a torque to loosen the nut or the stud head in the one direction while turning off reaction of the coaxial reaction surface in the other direction, and running up the nut, the stud head, the nut and the coaxial reaction surface, or the stud head and the coaxial reaction surface in the opposite direction.

[0202] The following discussion relates to a reaction arm-less torque power tool configuration according to the present invention for tightening and loosening industrial screw fasteners with minimal galling, where similar terms such as intensifier, multiplier, and multiplication, and impact and impaction are interchangeable.

[0203] More specifically, in one embodiment of the impact mode, the tool housing and gear stages remain stationary while the impact rattles. If the impact mechanism is remote from the motor, a shaft from the motor runs through the center of the multiplier to the impact mechanism and from there to the output drive. If the impact mechanism is directly behind the motor and in front of the multiplier, the motor drives the impact mechanism and a shaft runs from the impact mechanism through the center of the multiplier to the output drive.

[0204] In another embodiment of the impact mode, the tool housing and the gear stage rotate in unison while the impact rattles by locking up the gear stage. This can be achieved by coupling the sun gear to the ring gear, the sun gear to the gear cage, or the gear cage to the ring gear of the planetary stage. In either case, the gear cage and the housing act as a single rotating extension from the motor to the impact mechanism or from the impact mechanism to the output drive of the tool.

[0205] In another embodiment of the impact mode, the tool housing remains stationary and the gear cage rotates in unison while the impact rattles by locking up the gear cages with each other. If the impact mechanism is remote from the motor, the gear cage acts like an extension of the inside of the housing from the motor to the impact mechanism. If the impact mechanism is directly behind the motor and in front of the multiplier, the gear cage acts like an extension of the inside of the housing from the impact mechanism to the output drive of the tool.

[0206] Typically, during LSHT mode, at least two multiplication transmitters rotate relative to each other. On the multiplication board, the tool housing always rotates in the opposite direction to the sun gear and the multiplier output shaft. For this reason the tool housing must react. When the torque is multiplied by the multiplier, the rotation speed is low, so the impact mechanism is ineffective. If the impact mechanism is placed after the multiplier, close to the output drive of the tool, it will not impact if it rotates with the last sun gear. If the impact mechanism is placed before the multiplier, close to the motor, it rotates at a high speed and needs to be locked.

[0207] In one embodiment where the impact mechanism is remote from the motor, the following occurs: the impact mechanism remains stationary while the multiplier rotates, the output shaft from the motor extends to the multiplier for torque multiplication and the last sun gear extends through the impact mechanism to the output drive. When the impact mechanism is located immediately behind the motor and before the multiplier, the output shaft from the motor extends through the impact mechanism to the multiplier for torque multiplication and the last sun gear extends to the output drive.

[0208] In another embodiment, the impact mechanism rotates at the speed of the last sun gear of the force application multiplier. If the impact mechanism is remote from the motor, the output shaft from the motor extends to the multiplier for torque multiplication, the last sun gear rotates the impact mechanism, which rotates the output shaft of the tool. When the impact mechanism is located immediately behind the motor and before the multiplier, rotating the impact mechanism to rotate the multiplier results in an impact. This must be avoided. On the other hand, the impact mechanism can be locked by locking the hammer on the impact housing or by locking the hammer on the anvil. The impact mechanism acts as an extension between the motor output drive and the first sun gear of the multiplier.

[0209] The speed of the last sun gear of the multiplier may be high enough to operate the impact mechanism. Impact of the output shaft of the tool can be avoided by locking the hammer to the impact housing, the hammer to the anvil, the impact housing to the tool housing, or the hammer to the tool housing.

[0210] In a particular embodiment of the LSHT mode, the multiplication mechanism is located near the motor and in front of the impact mechanism. The motor bypasses the multiplication mechanism and extends its output through at least one part of the multiplication mechanism by a pin facing the output drive. In another particular embodiment of the LSHT mode, the impact mechanism is located near the motor and in front of the multiplication mechanism. The impact mechanism extends its output through at least one part of the multiplication mechanism by a pin facing the output drive.

[0211] A power tool according to the present invention for tightening and loosening industrial fasteners with minimal galling is described herein as having two or three modes, namely, a low speed high torque mode, a high speed low torque mode, and an intermittent force mode. Of course, the at least two modes described herein are merely exemplary. Additional modes can be added to one or the other modes and / or to the input means and / or the output means. Of course, the present invention is not limited to only two speeds but can have a variety of speeds. For example, known torque intensifying tools are typically output by air or electric motors. The force output and rotational speed of such motors are often increased or decreased by planetary gears or the like which may be part of the motor. Often known torque intensifying tools temporarily eliminate one or some of the intensifying means for increasing the tool motor rotational speed. Other known torque intensifying tools use gear increase and / or decrease mechanisms, either as separate components or adjacent to the motor, for increasing or decreasing the shaft rotational speed. The present invention may also include such gear speed-up and / or speed-down mechanisms as separate components, as part of the multiplication transmitter and multiplication mechanism 210, or as part of the vibration transmitter and vibration mechanism 310. Indeed, the multiplication assembly 200 may be configured to have multiple multiplication transmitters contained within multiple multiplication assembly housings.

[0212] (Z·Squirter Washer) 23A is a top view and FIG. 23B is a bottom view of a hybrid·Z® direct tension indicating, or Z·Squirter washer 2301. The Z·Squirter washer 2301 has similar characteristics to the washer 1 illustrated in the previous figures of this application and to the direct tension indicating washers disclosed in the following U.S. patents issued to Applied Bolting Technology Products, Inc.: U.S. Pat. Nos. 5,769,581, 5,931,618, 6,425,718, and 8,002,641, all of which are incorporated herein by reference.

[0213] Z·Squirter washer 2301 is configured with a protuberance 2312 having a height H23C on a first surface 2314 and a corresponding recess 2316 on a second surface 2318. FIG. 23C is a schematic diagram of the Z·Squirter washer 2301 of FIG. 23A. First aspect FIG. 23D is a cross-sectional view of Z·Squirter washer 2301 taken along 2314, and FIG. 23D is an enlarged view of a portion of FIG. 23C. Z·Squirter washer 2301 extends from each recess 2316 to the outer edge of second surface 2318. blood 23D. The Z·Squirter washer 2301 also includes a channel 2362. The recess 2316 is filled with an indicating material 2364, as shown in detail in FIG. 23D. The Z·Squirter washer 2301 is manufactured in a process similar to the direct tension indicating washers disclosed in U.S. Pat. Nos. 5,769,581, 5,931,618, 5,931,618, 6,425,718, and 8,002,641. For example, a tool and die are used to stamp the Z·Washer 1 with the ridges 2312, recesses 2316, and channels 2362. Other processes such as metal machining or metal casting can be used to construct the Z·Squirter washer 2301. In some cases, the metal product is heat treated by quenching and tempering after forming to create spring-like load / deformation characteristics. In the exemplary embodiment, Z·Squirter washer 2301 is made from carbon steel, although stainless steel, non-ferrous metals, and other alloy products may also be used. Display material 2364 is an extrudable elastomeric solid material, such as pigmented silicone.

[0214] 24A to 24F are R 1VFIG. 24A shows the position of the Z·Squirter washer 2301 adjacent to the bolt head 2350, which has a radius similar to that of the bolt head 2312, threaded into a nut 2352 (not shown). The condition shown in FIG. 24A is identified as Stage 1, where the bolt 2350 is at rest. As the bolt 2350 is tightened, the underside of the bolt head contacts the ridge 2312 and begins to compress the ridge 2312 towards the first surface 2314, as shown in FIG. 24B. In this condition, identified as Stage 2, the ridge 2312′ on the first surface 2314 grows to a height H 24B 24C is a close-up of one of the indentations 2316 showing the force exerted by the ridges 2312′ forcing the display material 2364′ into the channel 2362. As the bolts 2350 are further tightened, the height H of the ridges 2312″ increases to the predetermined height H 24D Below this, the ridge 2312 is compressed and tightening is discontinued. At this point, the bolt installer knows that the bolt tension is above the minimum required. This condition is identified as Stage 3 and is shown in FIG. 24D, where FIG. 24E shows the ridge 2312 in comparison to the ridge 2312″. FIG. 24F is a close-up of one of the indentations 2316 showing the force exerted by the ridge 2312″ forcing the material 2364″ through the channel 2362. The bolt installer knows that once the indicating material 2364″ is forced through the channel 2362, the tension in the bolt is equal to or exceeds the minimum required, and also that the indicating material 2364″ is visible on the surface of the bolted application.

[0215] In general, the Z·Squirter washer 2301 functions as a load indicating device as well as a reaction point for torque application, which includes the following features and / or advantages:be made of a hardened steel alloy or other resistant material; provide a solid surface upon which the threaded nut or bolt head can turn; protect the bolt joint face from embedding or damage due to the turning and loading of the threaded nut or bolt head; distribute the resulting clamping force of the bolt over a larger area than the clamping force of the nut or bolt head alone; have external engaging features which can engage a mating socket or similar fastener connected to a torque tool to provide a point against which the socket or fastener can react; thus having a roughened or machined underside which fits next to the joint and when compressed provides sufficient frictional resistance to resist the torque induced in the nut or bolt; have a smooth or low friction upper surface upon which the nut or bolt head can turn; have surface ridges or protrusions which are intended to flatten under a predetermined amount of compressive stress under the nut or bolt head; with or without flowable or soft rubber; the ridges are designed to provide a spring that will hold the bolt in place under the pressure of the washer. the outer reaction arm is used to eliminate pinch points commonly encountered with hydraulic bolting tools, thereby providing greater safety for the tool operator; eliminating the difficulty of finding a suitable outer reaction point for a torque tool, improving safety and speed; eliminating the detrimental effects of side loading and bending of the bolt or other fastener during application of torque with the outer reaction arm by allowing for the application of linear axial tension; working in conjunction with other fasteners and accessories to reduce associated back nut twisting; working similarly to so-called "tension" tools which generate bolt loads by direct extension of the bolt or stud without the use of large torque values; "Squirts" or other indications that the bolt load has reached the desired level as the washer ridges are flattened or sufficiently compressed and the indicating material is visible.

[0216] (Z·DTI washer) FIG. 24G is a top view and FIG. 24H is a bottom view of a hybrid Z-direct tension indication, or Z·DTI washer 2401. The Z-DTI washer 2401 has properties similar to washers 1 and 2301 shown in the previous figures and similar properties to direct tension indication washers disclosed in the following U.S. patents issued to J&M TURNER Inc, FJonathan MTurner, TurnAnut LLC and TurnaSure LLC, and U.S. patent applications filed by them: U.S. Patent No. 5,015,132; U.S. Patent No. 5,370,483; U.S. Patent No. 5,667,346; U.S. Patent No. 7,635,243; U.S. Patent No. 9,863,457; U.S. Patent Application No. 2018 / 0291945, all of which are incorporated herein by reference.

[0217] Z·DTI washers, such as 2401, include a raised ridge configured on an upper surface and a corresponding recess configured on an underside. FIG. 24I is a cross-sectional view of Z·DTI washer 2401, and FIG. 24J is an enlarged view of a portion of FIG. 24I. Z·DTI washer 2401 may also include a display material. Note that much of the discussion related to Z·2301 also applies to Z·DTI washers, such as 2401. As with many known variations of these washers, Z·DTI washers, such as 2401, share the common feature of a ridge that is aligned with and centered over the recess.

[0218] One alternative embodiment of a Z·DTI washer similar to 2401 but not shown in the drawings includes one or more indentations on the lower surface that are offset from one or more ridges on the upper surface, with the one or more indentations being located farther from the central hole of the annular body than the one or more ridges. By offsetting the ridges and indentations, the washer is strengthened and more suitable for use in joint assemblies having enlarged or oversized holes. Several variations applicable to Z·DTI washers similar to 2401 are disclosed in U.S. Pat. No. 9,863,457, which is incorporated herein by reference in its entirety.

[0219] One alternative embodiment of a Z·DTI washer similar to 2401, but not shown in the drawings, includes the following: The Z·DTI washer has an annular body and one or more U-shaped horseshoe ridges. The annular body includes a central hole, a circumference, an outer end, a first face, and a second face opposite the first face. Each of the horseshoe ridges has a height, an apex closest to the central hole, and an opening directed toward the outer end. The horseshoe ridges are integral with the annular body and are stamped and partially sheared away from the annular body to protrude from the first face of the annular body and leave one or more corresponding recesses in the second face of the annular body. The horseshoe ridges may be radially offset from their corresponding recesses. The display material is initially encapsulated and contained within the area on the first face defined by each of the horseshoe ridges. It should be noted that several variations of the 2401 that are applicable to Z·DTI washers are disclosed in U.S. Patent Application Publication No. 2018 / 0291945, the entirety of which is incorporated herein by reference.

[0220] In general, a Z·DTI washer such as the 2401 serves as a reaction point for torque application as well as a load indicating device. It includes the following features and / or advantages:be made of a hardened steel alloy or other resistant material; provide a solid surface upon which the threaded nut or bolt head can turn; protect the bolt joint face from embedding or damage due to the turning and loading of the threaded nut or bolt head; distribute the resulting clamping force of the bolt over a larger area than the clamping force of the nut or bolt head alone; have external engaging features which can engage a mating socket or similar fastener connected to a torque tool to provide a point against which the socket or fastener can react; thus having a roughened or machined underside which fits next to the joint and when compressed provides sufficient frictional resistance to resist the torque induced in the nut or bolt; have a smooth or low friction upper surface upon which the nut or bolt head can turn; have surface ridges or protrusions which are intended to flatten under a predetermined amount of compressive stress under the nut or bolt head; with or without flowable or soft rubber; the ridges are designed to provide a spring that will hold the bolt in place under the pressure of the washer. the outer reaction arm is used to eliminate pinch points commonly encountered with hydraulic bolting tools, thereby providing greater safety for the tool operator; eliminating the difficulty of finding a suitable outer reaction point for a torque tool, improving safety and speed; eliminating the detrimental effects of side loading and bending of the bolt or other fastener during application of torque with the outer reaction arm by allowing for the application of linear axial tension; working in conjunction with other fasteners and accessories to reduce associated back nut twisting; working similarly to so-called "tension" tools which generate bolt loads by direct extension of the bolt or stud without the use of large torque values; "Squirts" or other indications that the bolt load has reached the desired level as the washer ridges are flattened or sufficiently compressed and the indicating material is visible.

[0221] (HYTORC® Z Washer and Nut Assembly) During the torque application process, an equal and opposite reaction force is generated and must be transmitted to the appropriate reaction point, i.e., to a stationary object. Referring again to FIGS. 2-5, Z-washer 1 is disposed between upper surface 35 of fitting 30 and bearing surface 8 of threaded nut 36. In FIGS. 25A-25E, Z-washer 2501 is integrally configured adjacent to lower bearing surface 2538 of threaded nut 2536. HYTORC® Z-washers are fully disclosed in this application and in commonly owned and / or co-pending international applications, the entireties of which are incorporated herein by reference, namely, International Application No. PCT / US2014 / 70996, entitled "Apparatus for Tightening Threaded Fasteners," filed Dec. 17, 2014, and / or International Application No. PCT / US2014 / 71000, entitled "Apparatus for Tightening Threaded Fasteners," filed Dec. 17, 2014. The HYTORC®·Z washer and nut assembly 2502 includes a threaded nut 2536 and a reaction washer 2501 for receiving the counter torque generated due to tightening or loosening of a threaded fastener.

[0222] The reaction washer 2501 includes an outer end 2514 having a geometry 2519 that allows for rotational coupling with a torque device via a dual drive coaxial action and reaction assembly (not shown), and an underside 2513 having a friction coefficient increasing treatment 2517 biased toward an area outward from the central bore 2515. The reaction washer 2501 is removably attached to a threaded nut 2536. The bond between the reaction washer 2501 and the threaded nut 2536 breaks at or before a predetermined pre-torque, with the reaction washer 2501 being the appropriate reaction point. In this example, the reaction washer 2501 and assembly 2502 separate when the compressive, frictional forces overcome such bond and the bond breaks. Any suitable bonding and / or connection method and / or agent may be used, such as, for example, adhesives, glues, epoxies, magnets, solvents, solders, welding, etc. Such bonding and / or connecting methods and / or agents may be selected, tailored, and / or developed with specific, advantageous, and repeatable properties to suit any bolting application. It is noted that such a combination creates a nut-washer assembly with similar advantages as a HYTORC® NUT.

[0223] 26A-26D, the Z-washer 2601 is configured adjacent to and freely rotatable against the lower bearing surface 2638 of the threaded nut 2236. HYTORC® Z-washers are fully disclosed in this application and in co-owned and / or co-pending international applications, the entireties of which are incorporated herein by reference, namely, International Application No. PCT / US2014 / 70996, filed Dec. 17, 2014, entitled "Apparatus for Tightening Threaded Fasteners," and / or International Application No. PCT / US2014 / 71000, filed Dec. 17, 2014, entitled "Apparatus for Tightening Threaded Fasteners." The HYTORC® Z-washer and nut assembly 2602 includes a threaded nut 2636 and a reaction washer 2601 for receiving counter torque generated due to tightening or loosening of a threaded fastener.

[0224] The reaction washer 2601 includes an outer end 2614 having a geometry 2619 that allows rotational coupling with a torque device via a dual drive coaxial action and reaction assembly (not shown), and a lower surface 2613 having a friction coefficient increasing treatment 2617 biased in an area outward from the central bore 2615. A portion of the lower reaction washer 2601 adjacent the central bore 2615 is removed such that the lower inner end 2662 has a tapered surface that slopes outwardly toward the lower surface 2613.

[0225] The threaded nut 2636 has an outer surface 2622 with a geometric configuration 2626. The geometric configuration 2626 is also configured as a coupling means 2629 for non-rotatably engaging with an active part of a torque device. A portion of the lower threaded nut 2636 adjacent the outer surface 2622 is removed such that the lower outer end 2663 has a tapered surface that slopes outwardly and downwardly. In other words, the lower surface 2638 is manipulated (deformed or squeezed outwardly) to define a lip that engages with the lower inner end 2662 of the reaction washer 2601. In other words, the nut or stud head and the reaction washer are connected by a protrusion that extends outwardly and downwardly from the lower surface of the nut or stud head and engages with a recess that extends inwardly and upwardly from the lower surface of the reaction washer. The engagement of the assemblies 2602 is held together, allowing free rotation of the lead nut 2636 and reaction washer 2601.

[0226] Free rotation between the reaction washer 2601 and the threaded nut 2636 stops at or before a predetermined pre-torque, and the reaction washer 2601 becomes the appropriate reaction point. In this example, free rotation between the reaction washer 2601 and the threaded nut 2636 stops once compression and friction forces overcome such connection.

[0227] Any suitable connection method and / or structure may be used. For example, an o-ring may be used. In one embodiment, a plastic o-ring shears off at or before a predetermined torque. In another embodiment, a rubber o-ring creates an interference fit that is overcome at or before a predetermined torque. In another embodiment, FIGS. 27A-27D, the connection structure is configured as a deformable press-fit tab to create an interference fit that is overcome at or before a predetermined torque. Such methods and / or structures may be selected, tailored, and / or developed with specific, advantageous, and repeatable characteristics to meet any bolting application. The HYTORC®·Z washer and nut assembly 2702 includes a threaded nut 2736 and a reaction washer 2701 for receiving counter torque generated due to tightening or loosening of a threaded fastener. It is noted that such a combination creates a nut-washer assembly with similar advantages as the HYTORC®·NUT.

[0228] The reaction washer 2501, 2601, 2701 and / or any reasonable variation thereof, when used with the device 2502, 2602, 2702 and / or any reasonable variation thereof, may be used as a suitable reaction point during tightening and / or loosening of a threaded fastener. The friction coefficient increasing treatment 2517, 2617, 2717 and / or any reasonable variation thereof may include any of the following: roughening, polygonal surfaces, splines, knurls, spikes, grooves, slots, protruding points or corners, other such protrusions, or any combination thereof. They may be constructed by any of the following: knurling, sanding, blasting, milling, machining, forging, casting, shaping, forming, roughing, stamping, engraving, punching, bending, releasing the washer material near the central hole, or any combination thereof. Such friction coefficient increasing treatments may be evenly distributed across the lower surface 2513, 2613, 2713 and / or any reasonable variations thereof and / or may be located away from the radius of the central hole 2515, 2615, 2715 and / or any reasonable variations thereof. They may be configured either singly, randomly, in an array, or any combination thereof. These reaction washers have an effective friction radius that is greater than the effective friction radius of the threaded nut 2536, 2636, 2736 and / or any reasonable variations thereof.

[0229] In general, reaction washers 2501, 2601, 2701, and / or any reasonable variations thereof, and screw nuts 2536, 2636, 2736, and / or any reasonable variations thereof, may be held together in any predictable and deformable manner to prevent unintentional disassembly of assemblies 2502, 2602, 2702 and / or any reasonable variations thereof.

[0230] Advantageously, the reaction washer and screw nut assemblies 2502, 2602, 2702 and / or any reasonable variations thereof improve bolting speed, efficiency, reliability, repeatability, and safety through control of the nut geometry used with a particular reaction washer, control of the reaction washer used with a particular stud and / or thread size, and prevention of lost components.

[0231] (Tapered Fastener Assembly) 28A-28C, by way of example, there is shown a device 2801-step cone fastener assembly according to an embodiment of the present invention. The device 2801 has an inner sleeve 2810 and an outer sleeve 2820, and is used with a threaded stud 2830, by way of example. The inner sleeve 2810 is rotatably and threadably engageable with the stud 2830, rotatably and tape-like engageable with the outer sleeve 2820, and non-rotatably engageable with the working portion of the torque input device. The outer sleeve 2820 is non-rotatably wrapped with the reaction portion of the torque input device, and rotatably and tapered wrapped with the inner sleeve 2810. When the inner sleeve 2810 is rotated by the working portion of the torque input device, it applies a load to the stud 2830 to close the joint (not shown).

[0232] Inner sleeve 2810 is an annular body and is configured as a sleeve as shown in Figures 28A and 28B. It has an inner surface 2811 having an inner helical thread means 2815 engageable with an outer surface 2831 having an outer helical thread means 2834 of stud 2830. It has an outer surface 2812 and a cylindrical formation 2816 rotatably engageable with inner surface 2821 along with a cylindrical formation 2825 of outer sleeve 2820. It further has a lower surface 2814 rotatably engageable with inner surface 2821.

[0233] The cylindrical configuration 2816 is shaped as an inverted truncated cone of a stepped cone, with a tapered or conical appearance from the bottom up. Each step on the exterior surface 2812 is gradually smaller from the top to the bottom. The exterior hollow cylindrical feature is removed from the exterior of the inner sleeve 2810 at a shallow depth. Successive exterior hollow cylindrical features are removed at regular length and width intervals. Each successive feature begins where the previous feature stops. The geometric pattern of removed exterior cylindrical features continues until space limits the addition of another interior cylindrical feature.

[0234] The inner sleeve 2810 further has an upper surface 2813 with a coupling means 2817, which may be defined by a plurality of axially extending and circumferentially spaced apart holes, for non-rotatably engaging an active portion of a torque input device.

[0235] The outer sleeve 2820 is an annular body and is configured as a sleeve, as shown in FIG. 28B. It has an inner surface 2821 with a cylindrical configuration 2825 that rotatably engages with an outer surface 2812 with a cylindrical configuration 2816 of the inner sleeve 2810. The outer sleeve 2820 has an outer surface 2822 with a coupling means 2827. The coupling means 2827 is comprised of a plurality of axially extending and circumferentially spaced outer spines. The coupling means 2827 non-rotatably engages with an inner spine of a reaction portion of the torque input device.

[0236] The cylindrical feature 2825 is shaped as a stepped cone frustum, with a tapered or conical appearance from the top down. Each step on the inner surface 2821 is gradually smaller from the top to the bottom. The inner cylindrical features are removed from the inside of the outer sleeve 2820 at a shallow depth. Successive inner cylindrical features are removed at intervals of constant length and width. Each successive feature begins where the previous feature stops. The geometric pattern of removed inner cylindrical features continues until space limits the addition of another inner cylindrical feature.

[0237] The stud 2830 has a cylindrical shape with an external helical thread means 2834 for mating with the internal helical thread means 2815 of the inner sleeve 2810. The tip 2832 of the stud 2830 has a coupling means 2833 which may be constituted by a polygonal configuration 2835, in this case a hexagonal shape. The polygonal configuration 2835 allows for rotational coupling with a torque input device.

[0238] The stepped conical fastener geometry of the device 2801 creates a tensile load on the stud 2830 by mechanical sliding action through a helical inclined plane between the stud threads 2834 and the inner sleeve threads 2815. The torque input device applies rotation under torque to the inner sleeve coupling means 2817 while reacting the torque on the outer sleeve external splines 2827 to create a sliding helical threading action. When the outer surface 2812 and the inner surface 2821 are substantially smooth, the outer sleeve 2820 rotates against the inner sleeve 2810 28. The reaction element of the torque input device is rotationally coupled to the tip 2832 of the stud 2830 by coupling means 2833. This prevents rotation of the stud 2830 and allows relative sliding action between the inner sleeve threads 2815 and the stud threads 2834. Stud translation occurs in proportion to the resistance to such translation as the torque input device continues to apply torque to the inner sleeve 2810 while reacting on the outer sleeve external spline 2827, rotationally coupled to the stud 2830 by coupling means 2833.

[0239] The inner sleeve coupling means 2817 may be configured with any suitable geometric shape or may be used with other means or features for rotational coupling with a torque input device, such as gear teeth, hexagons, double hexagons, castellations, or any other common geometric shape that allows for rotational coupling. One possible alternative is a hexagonal shape shown as 2947 in FIG. 29A.

[0240] The outer sleeve coupling means 2826 may be configured with any suitable geometric shape or may be used with other means or features for rotational coupling with a torque input device, such as gear teeth, hexagons, double hexagons, castellations, or any other common geometric shape that allows for rotational coupling. One possible alternative is a hexagonal shape shown as 2956 in FIG. 29B.

[0241] It should be noted that the amount, size, geometry and spacing of the removed exterior (inner sleeve 2810) and interior (outer sleeve 2820) cylindrical features may be varied to optimize the properties of device 2801, such as stress bias, depending on the application.

[0242] FIG. 28B shows an inner sleeve 2810 with four outer cylindrical features removed at fixed length and width intervals. FIG. 28B shows an outer sleeve 2820 with four inner cylindrical features removed at fixed length and width intervals. As shown in FIG. 29C, varying the amount, size, geometry and spacing from one removed outer and inner cylindrical feature to the next changes the nominal angle, step height and step width of the outer surface 2962 with cylindrical configuration 2966 and the inner surface 2961 with cylindrical configuration 2965. Alternatively, the step length may be dimensioned infinitely small to create a nearly smooth taper. The outer portion of the inner sleeve 2810 and the inner portion of the outer sleeve 2820 may each be removed in one step to create a smooth conical surface.

[0243] 29D shows an outer surface 2972 ​​with a cylindrical configuration 2976 and an inner surface 2971 with a cylindrical configuration 2975 with mating surfaces of various vertical spacing, or step heights. This allows movement on selective steps only when the other step is loaded. Plastic deformation thus allows vertical movement and strategically biases the stress distribution across each stepped surface. In other words, the increased gap or spacing between the mating surfaces of the inner sleeve 2810 and outer sleeve 2820 allows radial expansion during loading.

[0244] 29E shows an outer surface 2982 with a cylindrical configuration 2986 and an inner surface 2981 with a cylindrical configuration 2985 with mating surfaces of varying step surface angles. This promotes a more uniform and controlled bias stress distribution across the steps. In other words, either or both of the inner sleeve 2810 and the outer sleeve 2820 can have step vertical surfaces with varying pitch angles to bias stress to preferential horizontal step surfaces.

[0245] FIG. 29F shows the outer sleeve 2820 with inner features at the bottom that mate with similar mating outer features added to the stud 2830. These can include splines, knurls, hexagons, slots, double hexagons, or other geometric shapes. They allow axial translation of the stud 2830, but couple the rotational movement of the outer sleeve 2820 and the stud 2830. Both the coupling means 2833 consisting of a polygonal configuration 2835 and the need to couple this hexagon with the reaction member of the torque input device are no longer necessary. The inner spline 2998 and the mating outer spline 2999 respectively constitute the spline interface between the outer sleeve 2820 and the stud 2830.

[0246] In standard bolting industry terminology, the device 2801 includes a nut (inner sleeve 2810) and a washer (outer sleeve 2820). The standard bolting flush nut and washer interface is modified. The torque reaction point is moved upwards compared to a traditional 3-piece fastener. The device of the present invention utilizes the concept of a traditional 3-piece fastener, which allows for surface conditioning of the outer sleeve to prevent galling using a traditional nut and washer device, and holds radial strain so that the inner sleeve can be surface conditioned with minimal risk of fracture.

[0247] Generally, a two-piece taper nut assembly for use with a threaded fastener and a stud or bolt of a torque device includes a rigid inner member having an inner surface threadably engageable with the fastener and an outer surface defined by a plurality of steps defining a taper, and an outer member having a reverse tapered inner surface non-rotatably engageable with the tapered outer surface of the inner member, the two-piece nut assembly applying a load to the threaded fastener when rotated by the working portion of a torque device. The inner member is superficially, partially, or fully metallurgically hardened.

[0248] Advantageously, the load bearing surface area between the inner and outer members allows for strategically biased vertical and radial stress distribution without requiring a substantial increase in overall dimension; allows for three dimensional load bearing surface area rather than the traditional two dimensional plane; allows for more efficient and evenly distributed load bearing distribution over the load bearing surface area; allows for higher torsional strength; allows for devices small enough to fit into tight and / or confined spaces typical of industrial bolting applications and having lower mass, size and volume; eliminates thread galling and prevents catastrophic failure and load loss that previously limited the use of hardening processes with threaded fasteners.

[0249] (Tapered Torsion Coupling) 30A-30D, by way of example, there is shown an apparatus 3001 for torsionally coupling a threaded fastener 3010 to a torque input device 3002, in accordance with an embodiment of the present invention. The apparatus 3001 has a first coupling member 3003 having a tapered outer surface 3004 and a polygonal configuration 3005, and a second coupling member 3013 having a reverse tapered inner surface 3014 and a polygonal configuration 3015 non-rotatably engagable with the tapered outer surface 3004 of the first coupling member 3003.

[0250] In other words, the device 3001 torsionally couples a torque input device 3002 of the type having a shank 3030 and a threaded fastener 3010 with a tapered axial bore 3012 at its distal end. The device 3001 includes a coupling member 3003 having a reverse tapered outer surface 3004 non-rotatably engagable with the tapered axial bore 3012.

[0251] The discussion relating to the quantity, size, geometry and spacing of the removed outer (inner sleeve 2810) and inner (outer sleeve 2820) cylindrical features of FIGS. 28A-10 generally applies to the removed outer (first coupling member 3003) and inner (second coupling member 3004) cylindrical features of FIGS. 30A-30D. join This applies to the amount, size, geometry and spacing of the polygonal features of the first and second connecting members (member 3013). Note that the interface between the inner sleeve 2810 and the outer sleeve 2820 is cylindrical and therefore smooth, thus allowing relative rotation. Note, however, that the interface between the first and second connecting members is polygonal and angled, such that relative rotation is not possible.

[0252] A conical shape for the torsional coupling of the threaded fastener and the torque output device results in better load stress distribution. In the embodiment of Fig. 30A-30D, a low profile coupling geometry is introduced that allows the torsional coupling feature on the top of the stud to be configured inward. This distributes the stresses more evenly and therefore allows for more efficient packaging of the coupling features.

[0253] Typically, a stepped 12-point hole on the top surface of the stud is used to torsionally couple with a three-piece mechanical stud tensioning device and / or device for use with the stud. An inner 12-point feature is placed on the top of the stud at a shallow depth. Successive 12-point features are each smaller in size at a shallow depth, and are incrementally added at each starting point where the previous 12 points stopped. The pattern of decreasing 12-point geometry decreases until space limits the addition of another 12 points. Advantageously, a torque input device shaft with an outer alignment feature for each of the steps would allow for evenly distributed stress distribution and high torsional strength while reducing the mass and volume of the stud.

[0254] As shown in Figures 31B and 31C, varying the depth and size change from one 12-point feature to the next increases or decreases the nominal angle of the cone shape they form. The 12-point feature can be replaced with any geometric shape that prevents rotation between the two parts, such as the hexagon in Figure 31A. Additionally, the step depth can be made infinitely small to create a smooth taper. Mixed step sizes and geometries can be used to optimize the manufacture of such couplings.

[0255] (2-piece tapered nut assembly) See, by way of example, Figures 32A-32D, which show a two-part nut assembly 3202 for use with either a stud or bolt of a threaded fastener (not shown), and a torque device (not shown), including a rigid inner member 3210 having an inner surface threadably engageable with a fastener and an outer surface defined by a plurality of steps defining a taper, and an outer member 3220 having a reverse tapered inner surface non-rotatably engageable with the tapered outer surface of the inner member, the two-part nut assembly 3202 applying a load to the threaded fastener when rotated by the working portion of the torque device. The inner member is superficially, partially, or fully metallurgically hardened.

[0256] The inner member 3210 is a geometric body that is configured as a threaded insert, as shown in Figures 32B and 32C. It has an inner surface 3211 with an inner helical thread means 3217 that is engagable with an outer surface 3221 with an outer helical thread means of a stud or bolt of a threaded fastener. It has an outer surface 3212 with a geometric configuration 3216 that is non-rotatably engagable with the inner surface 3221 with a geometric configuration 3225 of the outer member 3220. The inner member 3210 further has a lower surface 3218 adjacent and co-terminating with the lower surface 3230 of the outer member 3220.

[0257] In this exemplary embodiment, the geometric configuration 3216 is shaped as a modified inverted frustum of a hexagonal pyramid with angles that have a tapered or conical appearance from above the lower surface. The radius of each step on the outer surface 3212 gradually decreases from top to bottom. The outer hollow modified hexagonal features are removed from the outside of the inner member 3210 at a relatively shallow depth. Successive outer hollow modified hexagonal features are removed at regular length and width intervals. Each successive feature begins where the previous feature stops. The geometric pattern of removed outer modified hexagonal features continues until space (height) limits the addition of another such feature.

[0258] The inner member 3210 further has an upper surface 3213. The upper surface 3213 may have coupling means, similar to the coupling means 2817 of the stepped-cone fastener assembly 2801, for non-rotatably engaging an action portion of a torque device.

[0259] The outer member 3220 is a geometric body and is configured as a sleeve, as shown in FIGS. 32A-32C. It has an inner surface 3221 with a geometric configuration 3225 that is non-rotatably engageable with the outer surface 3212 of the inner member 3210. The outer member 3220 has an outer surface 3222 with a geometric configuration 3226. The geometric configuration 3226 is configured as a coupling means 3229 that non-rotatably engages with a working portion of a torque device. The rotational coupling means 3229 is configured as a modified hexagonal feature in this exemplary embodiment, but may be configured in any suitable geometric shape. And may be similar to the coupling means 2827 of the stepped cone fastener assembly 2801.

[0260] In this exemplary embodiment, the geometric configuration 3225 is shaped as a modified frustum of an angled hexagonal pyramid that also has a tapered or conical appearance from the bottom up. The radius of each step of the inner surface 3221 gradually decreases from top to bottom. The inner modified hexagonal features are removed from the inside of the outer member 3220 at a relatively shallow depth. Successive inner modified hexagonal features are removed at regular length and width intervals. Each successive feature begins where the previous feature stops. The geometric pattern of removed inner modified hexagonal features continues until space limits the addition of another inner modified hexagonal feature.

[0261] More generally, the outer surface 3212 of the inner member 3210 and the inner surface 3221 of the outer member 3220 are configured as any suitable rotational coupling means (polygonal and angled in nature) such that the inner member 3210 and the outer member 3220 are not relatively rotatable. In effect, this rotational coupling allows the action of the torque device to apply a load to the threaded fastener when the device 3202 is rotated by either the inner member 3210, the outer member 3220, or both the inner member 3210 and the outer member 3220. Note that the outer member 3220 substantially surrounds the inner member 3210. Note that the inner member 3210 and the outer member 3220 may be pressed together in a predictable deformable manner to prevent unintentional unraveling and / or any loosening resulting from partially mated surfaces of the device 3202.

[0262] The geometry of the load bearing surface area between the inner member 3210 and the outer member 3220 allows for improved and strategically biased normal and radial stress distribution without having to substantially increase the diameter of the device 3202. The geometric configurations 3216 and 3225 may be shaped as either stepped conical frustums with angles for the relatively low steps or smooth conical frustums with angles for the relatively high steps. It is noted that variable step amounts, dimensions, geometries, angles and / or spacing may be used to achieve such advantages.

[0263] One such improvement to geometric configuration 3216 includes a rounded corner 3218 for improved distribution of hoop stress from thread loads. It is noted that geometric configuration 3216 may be configured with any suitable geometric shape. One improvement to geometric configuration 3225 includes a rounded corner 3227 for improved distribution of hoop stress from thread loads. The rounded corner 3227 also accommodates the rounded corner 3218 on the inner member 3210. It is noted that geometric configuration 225 may be configured with any suitable geometric shape. The top surface 3213 may include a top end portion 3215 as shown in FIG. 32B to improve distribution of bolting stresses. The outer member 3220 further has a top surface 3223 as shown in FIG. 32B. The top surface 3223 slopes downwardly to improve distribution of bolting stresses. The lower surface 3230 may include a bottom end portion 3228 as shown in FIG. 32C to improve distribution of bolting stresses.

[0264] See Figures 32C and 32D. As an example, device 3202 and device 3202A are shown. The taper of the inner member 3210 of device 3202 increases from the upper surface 3213 to the lower surface 3218. Similarly, the taper of the outer member 3220 decreases from the upper surface 3223 to the lower surface 3230. Device 3202 shows a preferred embodiment. Conversely, the taper of the inner member 3210A of device 3202A decreases from the upper surface 3213A to the lower surface 3218A. Similarly, the taper of the outer member 3220A increases from the upper surface 3223A to the lower surface 3230A. Figure 32D shows an alternative embodiment that may be used in limited circumstances. It should be noted that additional features may be included in device 3202A to increase its implementation versatility. One such feature may include a lip configured on the upper surface 3213A and extending radially outward to ensure that the outer member 3220A remains adjacent to the inner member 3210A during loading.

[0265] Recall that the device 3202 of the present invention eliminates thread galling. Catastrophic damage and load loss previously limited the use of hardening treatments for threaded fasteners. Advantageously, however, the inner member 3210 of the device 3202 is superficially, partially, or fully metallurgically hardened. Many metallurgical hardening treatments can be used, such as flame hardening, induction hardening, carburizing, boriding, nitriding, cyaniding, carbonitriding, ferritic carbonitriding, annealing, quenching, aging, tempering, heat treating (differential, flame, induction, case hardening, etc.), cold treating (cryogenic), or any combination thereof. Because the non-metallurgically hardened outer member 3220 substantially surrounds the metallurgically hardened inner member 3210, cracks that would result in catastrophic damage and / or load loss are prevented by the device 3202.

[0266] The stepped cone fastener configuration of device 3202 creates a tensile load on the stud or bolt by mechanical sliding action through a helical ramp between the stud threads and the inner member threads 3217. A sliding helical thread action is created by applying a rotation under torque to either the inner member 3210, the outer member 3220, or both the inner member 3210 and the outer member 3220 using a torque device.

[0267] (HYTORC® Z-Washers for use with two-piece tapered nut assemblies) An equal and opposite reaction force is generated during the torquing process and must be transferred to the appropriate reaction point, i.e., stationary object. Note that the lower surfaces 3218 and / or 3230 of the inner and / or outer members 3210 and / or 3220 are at the upper surface of the joint, as shown in FIG. 32C. Alternatively, reaction washers 3301 may be configured between these lower surfaces and the upper surface of the joint, as shown in FIGS. 33A-33C. Reaction washers 3301 are configured as HYTORC®·Z washers, which are fully disclosed in this application and the following co-owned and / or co-pending international applications, all of which are incorporated herein by reference: No. PCT / US2014 / 70996, filed Dec. 17, 2014, entitled "Apparatus for Tightening a Threaded Fastener," and / or PCT / US2014 / 71000, filed Dec. 17, 2014, entitled "Apparatus for Tightening a Threaded Fastener." The apparatus 3202B includes a two-part nut assembly 3202 and a reaction washer 3301 for receiving a counter torque generated by tightening or loosening a threaded fastener.

[0268] The reaction washer 3301 includes an outer end 3304 with a geometric configuration 3309 that allows for rotational coupling with a torque device via a dual drive coaxial action and reaction assembly (not shown), and an underside 3303 with a friction coefficient increasing treatment 3307 biased to an area outward from the central bore 3305. The reaction washer 3301 is shown removably attached to the two-part nut assembly 3202. The bond between the reaction washer 3301 and the two-part nut assembly 3202 breaks at a predetermined pre-torque, with the reaction washer 3301 being the appropriate reaction point. In this example, when compression and friction forces overcome this bond, the reaction washer 3301 and nut assembly 3202 separate. Any suitable method of attachment can be used. It is noted that such a combination creates a nut-washer assembly with similar advantages as the HYTORC® NUT. Alternatively, the reaction washer 3301 and the nut assembly 3202 may be separate components.

[0269] The reaction washers 3301 may be used as suitable reaction points during tightening and / or loosening of threaded fasteners used with the device 3202. The friction coefficient increasing treatments 3307 may include any of the following: roughening, polygonal surfaces, splines, knurls, spikes, grooves, slots, protruding points or corners, other such protrusions, or any combination thereof. They may be constructed by any of the following: knurling, sanding, blasting, milling, machining, forging, casting, forming, shaping, roughing, stamping, engraving, punching, bending, removing washer material near the central hole, or any combination thereof. Such friction coefficient increasing treatments may be evenly distributed across the lower surface 3303 or may be located away from the radius of the central hole 3305. They may be constructed either singly, randomly, in an array, or any combination thereof. These reaction washers have an effective friction radius that is greater than the effective friction radius of the assembly 3202.

[0270] It should be noted that the description of device 2801 in Figs. 28-29 applies to device 3202. However, recall that the inner and outer sleeves of device 2801 are not rotatably coupled and therefore are not relatively rotatable. For example, upper surface 3213 could have coupling means similar to coupling means 2817 of stepped cone fastener assembly 2801 that would non-rotatably engage with the working part of a torque device. Such inner member coupling means may be configured with any suitable geometric shape or may be used with other means or features for rotational coupling with a torque device, such as gear teeth, hexagons, double hexagons, castellations, or any other common geometric shape that allows for rotational coupling. One possible alternative is a hexagonal shape shown as 2747 in Fig. 29A. Similarly, the outer member coupling means 3229 may be configured with any suitable geometry or may be used with other means or features for rotational coupling with a torque device, such as gear teeth, hexagons, double hexagons, castellations, or any other common geometry that allows for rotational coupling. One possible alternative is a hexagonal shape shown as 2956 in FIG. 29B. It should be noted that the amount, size, shape and spacing of the outer (inner member 3210) and inner (outer member 3220) cylindrical features removed may be varied depending on the application to optimize the properties of the device 3202, such as, for example, stress bias.

[0271] 32A-32C show an inner sleeve 3210 having four outer cylindrical features removed at fixed length and width intervals and an outer sleeve 3220 having four inner cylindrical features removed at fixed length and width intervals. However, as shown in FIG. 29C, varying the amount, size, geometry, and spacing from one removed outer and inner cylindrical feature will change the nominal angle, step height, and step width. Alternatively, the step length may be sized infinitesimally small to create a nearly smooth taper. The angled outer portion of the inner sleeve 3210 and the angled inner portion of the outer sleeve 3220 may be removed in one step to create a relatively smooth yet rotationally coupled conical surface.

[0272] 32A-32C show the mating surfaces of the inner and outer members 3210, 3220 with a constant vertical spacing or step height. FIG. 29D shows that the mating surfaces of the device 3202 can have a varying vertical spacing, or step height. This allows movement on selective steps only when the other step is loaded. Plastic deformation thus allows vertical movement and strategically biases the stress distribution across each stepped surface. In other words, the increased gap or spacing between the mating surfaces of the inner and outer sleeves 2810, 2820 allows radial expansion during loading. Note that this feature may have limited applicability due to the metallurgically hardened nature of the inner member 3210.

[0273] 32A-32C show the mating surfaces of the inner member 3210 and outer member 3220 having a constant step surface angle, i.e., 90°. FIG. 29E shows that the mating surfaces of the device 3202 can have varying step surface angles. This promotes a more uniform and controlled bias stress distribution across the steps. In other words, either or both of the inner member 3210 and outer member 3220 can have stepped vertical surfaces with various pitch angles to bias the stress to a preferential horizontal stepped surface.

[0274] Note that the description of apparatus 3001 in FIGS. 30 and 31 may be adapted to apparatus 3202. However, recall that apparatus 3001 is an alternative to a known rotatable coupling between a torque device and a stud, while apparatus 3202 is an alternative to a known screw nut. For example, as shown in FIGS. 31B and 31C, the depth change and size change from one 12 - point feature to the next will increase or decrease the nominal angle of the conical shape in which these features are configured within apparatus 3202. The 12 - point feature may be replaced with any geometric shape that prevents rotation between two parts such as the hexagon of FIG. 31A. Further, the depth of the step can be made infinitely small to create a smooth taper. To optimize the manufacture of such a coupling, mixed step sizes and geometries can be used.

[0275] A screw fastener having either a stud or bolt and apparatus 3202 is disclosed herein. An air - driven, electric - driven, hydraulic - driven, or manually - driven torque device is disclosed herein for tightening or loosening such a screw fastener. And a system consisting of such a screw fastener device and a torque device is disclosed herein.

[0276] In general, the two-piece nut assemblies disclosed herein reduce the dimensions limiting the bolting clearance compared to known three-piece nut assemblies and enhance the prevention of thread galling, breakage, and load loss compared to known nuts. The load-bearing surface area between the inner and outer members allows for strategically biased vertical and radial stress distribution without the need for a substantial increase in dimensions. They effectively handle the tensile hoop stresses typical of industrial threaded nuts in such a way that minimizes the possibility of fracture. In other words, the compact dimensions and selective metallurgical hardening of the nut assemblies disclosed herein minimize the risk of fracture and prevent load loss from any fracture that may be formed. The two-piece construction isolates the parts subject to the highest tensile hoop stresses, i.e., the parts near the female threads, preventing fractures from migrating through the entire assembly. The thread-generating hoop stresses are strictly confined to the inner member. The strains and deformations that lead to fracture initiation in the hardened or surface-hardened parts are controlled. And even if fractures are formed, they only migrate through the hardened inner member of the assembly and do not result in catastrophic load loss.

[0277] It will be understood that each of the above-described elements, or two or more together, may find useful application in other kinds of configurations different from the types described above. The features disclosed in the foregoing description, the following claims, and / or the accompanying drawings are expressed in their specific form or as means for performing a disclosed function, or as methods or processes for achieving a disclosed result, and may be utilized, as appropriate, separately or in any combination of such features to realize the invention in various of its various forms. One such embodiment includes a Z·Squirter washer in combination with a two-piece tapered nut assembly in any of the configurations disclosed with respect to Figures 25, 26, 27, 33 and / or any portion thereof.

[0278] (2-piece tapered threaded nut assembly) 34A-34C, which illustratively include a two-part taper threaded nut assembly 3402 for use with either a stud or bolt of a threaded fastener (not shown), and a torque device (not shown), the torque device including a rigid inner member 3410 having an inner surface threadably engageable with the fastener and an outer surface defined by a taper-defining thread configuration, and an outer member 3420 having an inner surface defined by a tapered thread configuration and a threadably engageable reverse taper thread configuration on the outer surface of the inner member 3410, the two-part nut assembly 3402 applying a load to the threaded fastener when rotated by the working portion of the torque device. The inner member is superficially, partially, and / or fully metallurgically hardened.

[0279] The inner member 3410 is a geometric body and is configured as a threaded insert as shown in Figures 34B and 34C. It has an inner surface 3411 having an inner helical thread means 3417 engageable with an outer surface having an outer helical thread means of a stud or bolt of a threaded fastener. It rotatably engages with an inner surface 3421 having a geometric configuration or reverse taper thread configuration 3425 of the outer member 3420. The inner member 3410 further has a lower surface 3418 adjacent to and terminating with a lower surface 3430 of the outer member 3420.

[0280] In this exemplary embodiment, the tapered thread configuration 3416 is shaped as a modified inverted frustum of a smooth conical pyramid with a tapered or conical appearance from the lower surface up. The radius of each thread on the outer surface 3412 gradually decreases from top to bottom. The outer hollow circular feature is removed from the outside of the inner member 3410 at a relatively shallow depth. Successive outer hollow circular features are removed at intervals of successive lengths and widths. Each successive feature begins where the previous feature stops. The geometric pattern of removed outer circular features continues until space (height) limits the addition of another such feature.

[0281] The inner member 3410 further has an upper surface 3413. The upper surface 3413 may have coupling means similar to the coupling means 2817 of the stepped-cone fastener assembly 2801 that would non-rotatably engage an active portion of a torque device.

[0282] The outer member 3420 is a geometric body configured as a sleeve as shown in FIGS. 34A-34C. It has an inner surface 3421 with a reverse taper thread configuration 3425 rotatably engageable with the outer surface 3412 of the inner member 3410. The outer member 3420 has an outer surface 3422 with a geometric configuration 3426. The geometric configuration 3426 is also configured as a coupling means 3429 for non-rotatably engaging with the working portion of a torque device. The rotational coupling means 3429 is configured as a modified hex feature in this exemplary embodiment, but may be configured in any suitable geometric shape. And may be similar to the coupling means 2827 of the stepped cone fastener assembly 2801.

[0283] In this exemplary embodiment, the reverse taper thread configuration 3425 is shaped as a modified frustum of a smooth conical pyramid with a tapered or conical appearance from the lower surface up. The radius of each thread on the inner surface 3421 gradually decreases from top to bottom. An inner circular feature is removed from the inside of the outer member 3420 at a relatively shallow depth. Successive inner circular features are removed at intervals of successive lengths and widths. Each successive feature begins where the previous feature stops. The geometric pattern of removed inner circular features continues until space limits the addition of another inner circular feature.

[0284] More generally, the outer surface 3412 of the inner member 3410 and the inner surface 3421 of the outer member 3420 are shaped as any suitable relatively rotatable means (essentially circular and smooth) such that the inner member 3410 and the outer member 3420 are relatively rotatable until the inner member 3410 and the outer member 3420 are suitably assembled. In fact, until the operative portion of the torque device is suitably assembled, this relatively rotatable means applies a load to the screw fastener when the device 3402 is rotated by the inner member 3410, the outer member 3420, or both the inner member 3410 and the outer member 3420. Note that the outer member 3420 substantially surrounds the inner member 3210. Note also that the inner member 3210 and the outer member 3420 may be pressed together in a predictable deformation manner to prevent any unintended disassembly resulting from the partially mating surfaces of the device 3402 and / or to relieve any stress.

[0285] The geometric shape of the load-bearing surface area between the inner member 3410 and the outer member 3420 is improved and enables a strategically biased vertical and radial stress distribution without substantially increasing the diameter of the device 3402. The tapered screw configurations 3416 and 3425 can be shaped as either a frustum of a smooth stepped cone for a relatively low number of steps or a frustum of a smoothly inclined cone for a relatively high number of steps. Note that such advantages can be achieved using variable step amounts, dimensions, geometries, angles, and / or spacing. Improvements to improve the distribution of the bolt tightening stress can include features similar to those described in the drawings. 32B, for example, is the upper end portion 3215, the inclined upper surface 3223, and / or the lower end portion 3228, as well as the rounded corners 3218 and 3227.

[0286] Referring to FIG. 34C, as an example, the device 3402 is shown. The taper of the inner member 3410 of the device 3402 increases from the upper surface 3413 to the lower surface 3418. Similarly, the taper of the outer member 3420 decreases from the upper surface 3423A to the lower surface 3430. Another embodiment of the device 3402 (not shown) may correspond to the device 3202A of FIG. 32D.

[0287] Recall that the device 3402 of the present invention eliminates thread galling. Destructive damage and load loss previously limited hardening treatments for threaded fasteners. Advantageously, however, the inner member 3410 of the device 3402 is superficially, partially, or fully metallurgically hardened. Many metallurgical hardening processes can be used, such as flame hardening, induction hardening, carburizing, boriding, nitriding, cyaniding, carbonitriding, ferritic carbonitriding, annealing, quenching, aging, tempering, heat treating (differential, flame, induction, case hardening, etc.), cold treating (cryogenic), or any combination thereof. Cracking that would otherwise result in catastrophic damage and / or load loss is prevented by the device 3402, as the non-metallurgically hardened outer member 3420 substantially surrounds the metallurgically hardened inner member 3410.

[0288] The smooth conical fastener shape of the device 3402 creates a tensile load on the stud or bolt by mechanical sliding action through a helical ramp between the stud threads and the inner member threads 3417. The sliding helical thread action is produced by applying rotation under torque to the inner member 3410, the outer member 3420, or both the inner member 3410 and the outer member 3420 using a torque device.

[0289] (HYTORC® Z-Washers for use with two-piece tapered lead-nut assemblies) An equal and opposite reaction force is generated during the torquing process and must be transferred to the appropriate reaction point, i.e., stationary object. Note that the lower surfaces 3418 and / or 3430 of the inner and / or outer members 3410 and / or 3420 are at the upper surface of the joint, as shown in FIG. 34C. Alternatively, reaction washers 3501 may be configured between these lower surfaces and the upper surface of the joint, as shown in FIGS. 35A-35C. Reaction washers 3501 are configured as HYTORC®·Z washers, which are fully disclosed in this application and in co-owned and / or co-pending international applications, which are incorporated herein by reference in their entirety. No. PCT / US2014 / 70996, having a filing date of December 17, 2014, entitled "Apparatus for Tightening Threaded Fasteners" and / or PCT / US2014 / 71000, having a filing date of December 17, 2014, entitled "Apparatus for Tightening Threaded Fasteners". Apparatus 3402B includes a two-part tapered nut assembly 3402 and a reaction washer 3501 for receiving a counter torque generated by tightening or loosening a threaded fastener. Note the description of apparatus 3202B in the figure. Figures 33A-33C can be adapted to apparatus 3402B in the figure. Note the description of apparatus 2801 in Figures 28-29, can be adapted to apparatus 3402 and 3402B. The description of device 3001 in Figures 30 and 31 may be applied to devices 3402 and 3402B.

[0290] Disclosed herein are threaded fasteners having a stud or bolt and either of devices 3402 and 3402B. Disclosed herein are pneumatically, electrically, hydraulically or manually actuated torque devices for tightening and loosening such threaded fasteners. And disclosed herein are systems of such threaded fastener devices and torque devices.

[0291] Generally, the two-piece nut assembly disclosed herein has reduced dimensions that limit bolt-tightening clearances compared to known three-piece nut assemblies, and enhances the prevention of screw wear, breakage, and load loss compared to known nuts. The load-bearing surface area between the inner and outer members enables strategically biased vertical and radial stress distributions without substantially increasing the dimensions. They effectively handle the tensile hoop stresses typical of industrial screw nuts in a way that minimizes the potential for failure. In other words, the compact dimensions and selective metallurgical hardening of the nut assemblies disclosed herein minimize the risk of breakage and prevent load loss from any breakage that may occur by isolating the portion that is subject to the highest tensile hoop stress, i.e., near the female thread, preventing the breakage from propagating throughout the assembly. The screw-generated hoop stress is tightly constrained within the inner member. The strain and deformation leading to breakage at the hardened or case-hardened portion are controlled. And even if breakage occurs, they only move through the hardened inner member of the assembly and do not result in catastrophic load loss.

[0292] It will be understood that each of the elements described above, or two or more of them in combination, may find useful applications in other types of configurations different from the types described above. The features disclosed in the foregoing description, the following claims, and / or the accompanying drawings may be expressed in their specific forms, or in terms of means for performing the disclosed functions, or in terms of methods or processes for achieving the disclosed results, and may be used, as appropriate, separately or in any combination of such features, to implement the invention in its various forms. One such embodiment includes a Z·Squirter washer combined with a two-piece tapered nut assembly in any configuration disclosed with respect to FIGS. 25, 26, 27, 33 and / or any portion thereof.

[0293] (HYTORC®·Anti-Loosening·Z washer) Applicant's recent Z System related research and development includes the application of a friction coefficient increasing treatment to both sides of HYTORC® Z Washers, as previously mentioned, to prevent self-loosening of threaded fasteners due to vibration.

[0294] 36A and 36B show perspective views of an embodiment in the form of a HYTORC® Anti-Loosening Z-Washer 3601. The anti-loosening reaction washer 3601 is fully disclosed in this application and the following commonly owned and / or co-pending international applications, the entireties of which are incorporated herein by reference: International Application No. PCT / US2014 / 70996, entitled "Apparatus for Tightening Threaded Fasteners," filed December 17, 2014; and / or International Application No. PCT / US2014 / 71000, entitled "Apparatus for Tightening Threaded Fasteners," filed December 17, 2014; The washer 3601 includes an outer end 3604 having a geometric configuration 3609 that allows for rotational coupling with a torque device via a dual drive coaxial action and reaction assembly (not shown), a lower surface 3603 having a friction coefficient increasing treatment 3607A offset in an area outwardly from the central bore 3605, and an upper surface 3602 having a friction coefficient increasing treatment 3607B offset in an area outwardly from the central bore 3605.

[0295] Recall that bolted connections tend to lose the desired load when subjected to shear loads caused by lateral vibration. The addition of friction coefficient increasing treatment 3607B to the top surface of reaction washer 3601 is novel and unobvious to the applicant and serves as a threaded fastener locking solution. The results include increasing the security of the bolted joint by limiting and preventing vibration induced self-loosening of the threaded fastener. In fact, washer 3601 easily passed the Junker test showing strong performance under a wide range of conditions without loosening. In contrast, the industry standard flat washer promptly failed the Junker test, indicating weak performance under a wide range of conditions and a substantial risk of loosening. Z-Washer 1 also failed the Junker test, but performed much better than the industry standard flat washer.

[0296] 37, 38 and 39 show perspective views of another embodiment of washer 3601 in the form of HYTORC® Anti-Loosening Z Washers 3701, 3801 and 3901, respectively. Like washer 3601, washers 3701, 3801 and 3901 include outer ends having a geometry that allows rotational coupling with a torque device via a dual drive coaxial action and reaction assembly (not shown) and undersides having an increased coefficient of friction treatment biased from the central bore to an outer region. However, the increased coefficient of friction treatments 3707, 3807 and 3907 on upper surfaces 3702, 3802 and 3902 of washers 3701, 3801 and 3901 are different from the increased coefficient of friction treatment 3607B on upper surface 3602 of washer 3601. The friction coefficient increasing treatments 3707, 3807, and 3907 are biased inwardly towards their central holes which transition from wide to narrow.

[0297] Like washer 3601, washers 3701, 3801 and 3901 easily passed the Junker test indicating strong performance under a wide range of conditions without loosening. Such results also indicate that the location and surface area of ​​the friction coefficient increasing treatment is limited with minimal impact on resistance to loosening. In other words, the enhanced anti-loosening performance of the partially covered washers is similar to that of fully covered washers as well as prior art washers including Nordlock and Heico.

[0298] Unlike washer 3601 (having outwardly biased treatment 3607B) and fully coated washers (such as those in the prior art including Nord-Lock and Heico), washers 3701, 3801 and 3901 require less torque input during tightening to achieve a desired load. Additionally, washer 3901 requires less torque input than washer 3701, which in turn requires less torque input than washer 3801, to achieve a desired load.

[0299] Surprisingly, washer 3901 requires a similar torque input to achieve a desired load as smooth top Z-washer 1. Such results further validate Applicant's friction theory described above in connection with Figure 6. In other words, the required torque input to achieve a desired load is proportional to the distance from the central hole of any friction enhancement.

[0300] When applied to the reaction washers of the present invention, Applicant's effective friction radius bias ensures that the bolt or nut will not turn, i.e., slip in front of the washer. Anti-Loosening·Z Washers 3601, 3701, 3801 and 3901 further feature a two-sided friction enhanced washer with a selectively biased top friction area biased inward and a selectively biased lower friction area biased outward. This two-sided, selectively two-sided biasing concept allows for optimized torque input transmission, yet prevents unintended loosening from shear stresses caused by lateral vibrations. And it is certainly novel and non-obvious.

[0301] Design engineers are reminded that they continue to focus on bolted joint integrity by preventing load loss. Prior art threaded fastener locking approaches such as lock nuts and standard, two-piece wedge and serrated lock washers do not optimize bolted joint integrity. For example, over-torquing to achieve a desired load can take the fastener beyond the yield point and / or under-torquing can result in unintended loosening. Also, misalignment, torsional stresses and side loads are detrimental to bolted joint integrity.

[0302] Meanwhile, HYTORC® Anti-Loosening Z-Washers 3601, 3701, 3801 and 3901 optimize the integrity of bolted joints by improving tool, driver, fastener and washer design, simplification of action, reaction, twisting, bending, pulling forces, unintended load loss release, torque input translation, alignment, vibration resistance, bolting speed, efficiency, reliability, repeatability and safety at a low cost.

[0303] HYTORC® Anti-Loosening Z-Washers can be used with any part of the HYTORC® Z System, including: Z-washers placed under various types of nuts or bolt heads, with friction biasing surfaces having relatively high friction against the flange surface and relatively low friction against the nut, with multiple shapes, sizes, shapes, serrations of engagement perimeters, such as washer / fastener radius engagement differentials, and friction coefficient increasing treatment means of various types, sizes, and locations; HYTORC® Z-GUN, which combines high speed rundown for calibrated torque and incorporates a powerful impact mechanism and a precise torque multiplier into the same tool; HYTORC® Z-Socket, with dual drive coaxial action and reaction, with an outer sleeve that reacts on the Z-washer and an inner sleeve that turns the nut or bolt head; AVANTI and ICE Square Drive Systems, STEALTH Limited Clearance Systems, Pneumatic jGUN Series, FLASH Gun and Lithium Series HYTORC® Z spline adapters and reaction plates for compatibility with bolt multipliers and the like; HYTORC® Z washers and HYTORC® Z double sided friction washers combinations including double sided friction enhanced face washers and / or HYTORC® Z nuts / bolts for counter torque under the nut or bolt head on the other side of the joint; HYTORC® Z dual driven offset links for tight clearances using HYTORC® torque / tension systems and the HYTORC® Z oscillating mechanisms applied thereto; Z Squirter washers, Z DTI washers, HYTORC® Z washer and nut assemblies, tapered fastener assemblies, tapered torsional couplings, two part tapered nut assemblies, two part tapered threaded nut assemblies and any combination thereof.

[0304] (HYTORC(R) Anti-Loosening Z-Nuts and Smart Studs) Applicant's recent Z-System related research and developments include applying the above-mentioned friction coefficient increasing treatments to the underside of HYTORC® nuts and smart studs to prevent vibration induced self-loosening of threaded fasteners.

[0305] 40A-40D each show a perspective view of an embodiment of a HYTORC® Anti-Loosening Z-Nut 4001. The anti-loosening nut 4001 is configured as a HYTORC® NUT or self-reacting fastener, which is disclosed in the Background of this application and in the following commonly-owned issued U.S. patents, which are incorporated herein by reference in their entireties: Nos. 5,318,397, 5,499,9558, 5,341,560, 5,539,970, 5,538,379, 5,640,749, 5,946,789, 6,152,243, 6,230,589, 6,254,323, 6,254,323, and 6,461,093. Nut 4001 comprises an example of a self-reacting nut and includes an inner sleeve 4010, an outer sleeve 4020, and a washer 4030. It uses washer 4030 as a reaction point for application of an input torque to outer sleeve 4020. The outer sleeve 4020 functions as a nut, while the inner sleeve 4010 is an extension of the threaded stud 4050 and is rotationally coupled with a washer 4030. This rotational coupling prevents sliding motion between the inner sleeve 4010 and the threads of the stud 4050 during application of torque to the outer sleeve 4020.

[0306] In other words, the HYTORC® NUT has two sleeves, one inside the other, whereby the inner sleeve is connected with a splined washer to allow only axial movement of the inner sleeve. It is screwed onto the stud or bolt as a unit. A dedicated driver is secured to the inner sleeve and turns the outer sleeve. The stud is pulled upwards with the inner sleeve, similar to a hydraulic tensioning tool, and tensioned without overextension and springback. The inner sleeve never rotates against the threads of the stud under load, eliminating the possibility of galling or other damage to the bolt threads. Several other versions of the HYTORC® NUT are disclosed in the patents of the above names and may be used instead. Note that one or more threads and engagement features of nut 4001 are not precisely shown in Figs. 40A-40D.

[0307] Specific to these embodiments of the invention, the lower surface 4033 of the washer 4030 has a friction coefficient increasing treatment 4037 biased toward the area outwardly from the central bore 4005. It is noted that in the preferred version of the HYTORC® Anti-Loosening Z-Nut 4001, the upper surface 4032 does not have the friction coefficient increasing treatment, however, in other versions the upper surface 4032 may have such a treatment.

[0308] The HYTORC® Anti-Loosening Z Smart Studs are not shown in the drawings, but are an example of a three-piece mechanical tension stud device. They consist of a stud, a nut, and a washer. The studs have male threads on both ends. Beneath the top threads, the studs would also have a spline or other geometric shape to create a rotational coupling with the inside diameter of the washer. The top side of the stud would also have a spline or other geometric shape to allow for rotational coupling with the reaction shaft of the torque input device. The nut is internally threaded to engage the top threads of the stud. The nut would have a spline or other geometric shape to allow for the introduction of torque from the torque input device. The washer has an inner geometric shape that rotatably mates with the spline or other geometric shape below the top threads of the stud. Several other versions of the HYTORC® SMARTSTUDs are disclosed in the above named patents and could be used instead.

[0309] Unique to these HYTORC® Anti-Loosening Z Smart Stud embodiments, the underside of the washer has a friction coefficient increasing treatment biased from the central bore to the outer area. Note that in the preferred version of the HYTORC® Anti-Loosening Z Smart Stud, the top side does not have a friction coefficient increasing treatment. However, in other versions, the top side may have such a treatment.

[0310] Recall that bolted connections tend to lose the desired load when subjected to shear loads caused by lateral vibration. The addition of Applicant's novel and unobvious friction coefficient increasing treatment 4037 to the underside 4033 of the nut 4001 acts as a threaded fastener locking technique. The results include increasing the security of the bolted joint by limiting and preventing vibration induced self-loosening of the threaded fastener. In fact, the nut 4001 easily passed the Junker test without loosening, indicating strong performance under a wide range of conditions. The HYTORC® Anti-Loosening Z smart studs of the present invention yield similar Junker test results. In contrast, industry standard 3-piece self-reacting fasteners and mechanical tension stud devices failed the Junker test, indicating weak performance under a wide range of conditions with substantial risk of loosening.

[0311] HYTORC® Anti-Loosening Z-Nuts and Smart Studs can be used with any part of the HYTORC® Z System, including: Z-washers placed under various types of nuts or bolt heads, with friction biasing surfaces having relatively high friction against the flange surface and relatively low friction against the nut, with multiple shapes, sizes, shapes, serrations of engagement perimeters, such as washer / fastener radius engagement differentials, and various types, sizes, locations of friction coefficient increasing treatment means; HYTORC® Z-guns combining high speed run down for calibrated torque, incorporating a powerful impact mechanism and a precise torque multiplier in the same tool; HYTORC® Z-sockets having dual drive coaxial action and reaction, with an outer sleeve that reacts on the Z-washer and an inner sleeve that turns the nut or bolt head; AVANTI and ICE square drive systems, STEALTH limited clearance systems, pneumatic jGUN series, FLASH guns and HYTORC® Z spline adapters and reaction plates for compatibility with Lithium series multipliers and the like; HYTORC® Z washers and HYTORC® Z double sided friction washers combinations including double sided friction enhanced face washers and / or HYTORC® Z nuts / bolts for counter torque under the nut or bolt head on the other side of the joint; HYTORC® Z dual drive offset links for tight clearances using HYTORC® torque / tension systems and the HYTORC® Z oscillating mechanisms applied thereto; Z Squirter washers; Z DTI washers; HYTORC® Z washer and nut assemblies; tapered fastener assemblies; tapered torsional couplings; two part tapered nut assemblies; two part tapered threaded nut assemblies and any combination thereof.

[0312] (General Description) Any type of suitable element, size and material may be used with the present invention. Fastener categories such as wood screws, machine screws, sheet metal screws, self drilling SMS, hex bolts, carriage bolts, socket screws, set screws, j-bolts, shoulder bolts, sex screws, engagement screws, hanger bolts, etc.; head styles such as flat, oval, pan, truss, round, hex, hex washer, slotted hex washer, socket cap, button, etc.; drive types such as Phillips and Frearson, slot, combination, socket, hex, Allen, square, Torx, and multiple other geometric shapes; nut types such as hex, jam, cap, acorn, flange, square, torque lock, slotted, castle, etc.; washer types such as flat, fender, finish, square, dock, reaction, etc.; thread types such as sharp V, ANS standard (American national), unified, metric, square, ACME, Whitworth standard, circular thread, tooth thread, single start, double start, triple start, double square, triple ACME etc.

[0313] This application seeks to protect Applicant's HYTORC® Z System, which includes: A tool having multi-speed / multi-torque modes with torque multiplication and vibration mechanisms without the use of external reaction abutments, a force transmission means for use with such tool producing in-line coaxial action and reaction, a drive means and shifting means which can be attached to a washer below a nut for use with such tool and force transmission means, associated washers and fasteners for use with such tool, force transmission means and drive means, and associated accessories for use with such tool, force transmission means, drive means, washers and fasteners.

[0314] (summary) In general, the anti-loosening reaction washer of the present invention includes an outer end having a geometry that allows for rotational coupling with a power tool, a lower surface having a friction coefficient increasing treatment means biased in an area outward from a central aperture, and an upper surface having a friction coefficient increasing treatment means biased in an area toward the central aperture. The friction coefficient increasing treatment means surrounds the central aperture. In other words, the lower surface has an outer portion, with the friction coefficient increasing treatment means disposed about the outer portion and extending inwardly toward the central aperture to a width less than the width of the lower surface, and the upper surface has an inner portion, with the friction coefficient increasing treatment means disposed about the inner portion and extending outwardly from the central aperture to a width less than the width of the upper surface. In other words, the outer end defines a washer radius, the central bore defines a gap radius, the lower surface has an outer portion and the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly towards the central bore to define an inner radius greater than the gap radius, and the upper surface has an inner portion and the friction coefficient increasing treatment means is disposed about the inner portion and extends outwardly from the central bore to define an outer radius greater than the gap radius but less than the washer radius.

[0315] The direct tension indicating reaction washer includes an outer end having a geometry that allows for rotational coupling with a power tool, a lower surface having discrete depressions and friction coefficient increasing treatment means biased in an area outward from a central aperture, and an upper surface configured with discrete ridges. In other words, the lower surface has an outer portion and the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly toward the central aperture to a width that is less than the width of the lower surface. In other words, the outer end defines a washer radius, the central aperture defines a gap radius, and the lower surface has an outer portion and the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly toward the central aperture to define an inner diameter that is greater than the gap radius.

[0316] The anti-loosening direct tension indicating reaction washer includes an outer end having a geometry that allows for rotational coupling with a power tool, a lower surface having distinct indentations and friction coefficient increasing treatment means biased in an area outward from a central aperture, and an upper surface having distinct ridges and friction coefficient increasing treatment means biased in an area toward the central aperture. In other words, the lower surface has an outer portion and the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly toward the central aperture to a width less than the width of the lower surface, and the upper surface has an inner portion and the friction coefficient increasing treatment means is disposed about the inner portion and extends outwardly from the central aperture to a width less than the width of the upper surface. In other words, the outer end defines a washer radius, the central bore defines a gap radius, the lower surface has an outer portion and the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly towards the central bore to define an inner radius greater than the gap radius, and the upper surface has an inner portion and the friction coefficient increasing treatment means is disposed about the inner portion and extends outwardly from the central bore to define an outer radius greater than the gap radius but less than the washer radius.

[0317] The anti-loosening self-reacting mechanical tension nut of the present invention includes an inner sleeve, an outer sleeve, and a washer having an underside having friction coefficient increasing treatment means biased to an area biased outwardly from a central bore. In other words, the underside has an outer portion and the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly toward the central bore to a width less than the width of the underside. In other words, the outer end defines a washer radius, the central bore defines a gap radius, and the underside has an outer portion and the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly toward the central bore to define an inner diameter greater than the gap radius.

[0318] The HYTORC® Z system includes: Z-washers placed under various types of nuts or bolt heads, with friction biasing surfaces having relatively high friction against the flange surface and relatively low friction against the nut, with multiple shapes, sizes, shapes, serrations of engagement circumference, and various types, sizes, locations of friction coefficient increasing treatment means, such as washer / fastener radius engagement differentials; HYTORC® Z-Guns combining high speed rundown for calibrated torque, incorporating a powerful intermittent (impact, vibration, ultrasonic, etc.) mechanism and a precise torque multiplier in the same tool; HYTORC® Z-Sockets with dual drive coaxial action and reaction, with an outer sleeve that reacts on the Z-washer and an inner sleeve that turns the nut or bolt head; HYTORC® Torque / Tension Systems including AVANTI and ICE Square Drive Systems, STEALTH Limited Clearance Systems, and Pneumatic jGUN Series for backward compatibility; Z-spline adapters and reaction plates; HYTORC® Z-washers and HYTORC® Z-double sided friction washer combinations including HYTORC® Z-nuts / bolts for counter torque under the nut or bolt head on the other side of a joint, such as FLASH guns and lithium series electric multipliers; HYTORC® Z-double driven offset links for tight clearances using HYTORC® torque / tension systems and HYTORC® Z-oscillating mechanisms applied thereto; Z-squirter washers; Z-DTI washers; HYTORC® Z-washer and nut assemblies; tapered fastener assemblies; tapered torsional couplings; two-part tapered nut assemblies; two-part tapered threaded nut assemblies; HYTORC® Anti-Loosening Z-washers, nuts and smart assemblies, any combination thereof.

[0319] It will be understood that each of the above-mentioned elements, or two or more together, may find useful application in other kinds of configurations different from the types described above. The features disclosed in the foregoing description, or in the following claims, or in the accompanying drawings, expressed in their specific form, or in any combination of such features, as means for performing a disclosed function, or in a method or process for achieving a disclosed result, may be utilized, separately or in any combination of such features, as appropriate, to realize the invention in its diverse forms. Note that there are slight variations in the description of the numbered components in this specification.

[0320] While the present invention has been illustrated and described as embodied in and / or with a torque device, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing from the spirit of the invention.

[0321] Without further analysis, the foregoing sufficiently reveals the gist of the invention so that others may easily adapt it to various uses by applying their present knowledge without omitting features which in the light of the prior art actually constitute essential features of the invention as a whole or of specific embodiments thereof.

[0322] As used in this specification and claims, the terms "tapered", "tapered" and variations thereof mean that a particular feature, step, amount, dimension, geometry and spacing may be either gradual, abrupt, stepped and / or conical, inconsistent, changing, narrowing, decreasing, diminishing, smaller, thinner, etc. from one end to the other.

[0323] The words "comprising," "including," "having," and variations thereof, when used in the present specification and claims, mean that the specified features, steps, or integers are included. These terms are not to be interpreted as excluding the presence of other features, steps, or components. The present invention has the following aspects (configurations). [Aspect 1] 1. An anti-loosening reaction washer for receiving a counter torque generated by tightening or loosening of a threaded fastener, comprising: an outer end having a geometry that allows for rotational coupling with a power tool; a lower surface having a friction coefficient increasing treatment means biased in an area outward from the central aperture; an upper surface having a friction coefficient increasing treatment biased toward said central aperture; A reaction washer having an anti-loosening function. [Aspect 2] 2. The anti-loosening reaction washer according to claim 1, wherein the friction coefficient increasing treatment means surrounds the central hole. [Aspect 3] the underside having an outer portion, the friction coefficient increasing treatment means being disposed about the outer portion and extending inwardly towards the central aperture to a width less than a width of the underside; the upper surface having an inner portion, the friction coefficient increasing treatment means being disposed about the inner portion and extending outwardly from the central aperture to a width less than a width of the upper surface; 3. The anti-loosening reaction washer of claim 1 or 2, comprising: [Aspect 4] the outer end defining a washer radius; the central hole defining a gap radius; the lower surface having an outer portion, the friction coefficient increasing treatment means being disposed about the outer portion and extending inwardly toward the central aperture to define an inner diameter greater than the gap radius; the upper surface having an inner portion, the friction coefficient increasing treatment means being disposed about the inner portion and extending outwardly from the central hole to define an outer radius greater than the gap radius but less than the washer radius; 4. The anti-loosening reaction washer according to any one of aspects 1 to 3, comprising: [Aspect 5] 5. The anti-loosening reaction washer according to any one of aspects 1 to 4, wherein the upper surface and the lower surface are substantially flat. [Aspect 6] 6. The anti-loosening reaction washer according to any one of aspects 1 to 5, wherein the friction coefficient increasing treatment means on the upper surface has a larger surface area than the friction coefficient increasing treatment on the lower surface. [Aspect 7] A loosening prevention reaction washer as described in any one of aspects 1 to 6, wherein the friction coefficient increasing treatment means on the lower surface is selectively biased toward the outer end and the friction coefficient increasing treatment means on the upper surface is selectively biased toward the central hole. [Aspect 8] A loosening prevention reaction washer as described in any one of aspects 1 to 7, wherein the friction coefficient increasing treatment means on the lower surface is discontinuously biased in the region toward the outer end, and the friction coefficient increasing treatment means on the upper surface is discontinuously biased in the region toward the central hole. [Aspect 9] A loosening prevention reaction washer as described in any one of aspects 1 to 8, wherein the friction coefficient increasing treatment means on the lower surface is not located at or near the central hole, and the friction coefficient increasing treatment means on the upper surface is not located at or near the outer end. [Aspect 10] The anti-loosening reaction washer of any one of aspects 1 to 9, wherein the friction coefficient increasing treatment means includes any of a roughened surface, a polygonal surface, a spline, a knurl, a spike, a groove, a slot, a protruding point or corner, other such protrusions, or any combination thereof. [Aspect 11] 11. The anti-loosening reaction washer of any one of aspects 1 to 10, wherein an effective friction radius of the lower surface is greater than an effective friction radius of the screw fastener, and an effective friction radius of the upper surface is smaller than the effective friction radius of the screw fastener. [Aspect 12] A loosening prevention reaction washer as described in any one of aspects 1 to 11, wherein the friction coefficient increasing treatment means on the lower surface is positioned substantially beyond the effective friction radius of the nut or bolt head, and the friction coefficient increasing treatment means on the upper surface is positioned substantially within the effective friction radius of the nut or bolt head. [Aspect 13] 13. The anti-loosening reaction washer according to any one of aspects 1 to 12, wherein the lower surface includes a smooth surface formed between the central hole and the friction coefficient increasing treatment means. [Aspect 14] 1. A direct tension indicating reaction washer for receiving a counter torque generated by tightening or loosening a threaded fastener, comprising: an outer end having a geometry that allows for rotational coupling with a power tool; a lower surface having discrete depressions and friction coefficient increasing treatments biased in an area outward from the central aperture; an upper surface having individual ridges; Includes direct tension indicating reaction washer. [Aspect 15] 15. The direct tension indicating reaction washer of claim 14, wherein the friction coefficient increasing treatment means surrounds the central aperture. [Aspect 16] 16. The direct tension indicating reaction washer of any one of aspects 14-15, including a lower surface having an outer portion, the friction coefficient increasing treatment means being disposed about the outer portion and extending inwardly toward the central aperture to a width less than a width of the lower surface. [Aspect 17] the outer end defining a washer radius; the central hole defining a gap radius; the lower surface having an outer portion, the friction coefficient increasing treatment means being disposed about the outer portion and extending inwardly toward the central aperture to define an inner diameter greater than the gap radius; 17. The direct tension indicating reaction washer of any one of aspects 14 to 16, comprising: [Aspect 18] 18. The direct tension indicating reaction washer according to any one of aspects 14 to 17, wherein the lower surface is substantially flat. [Aspect 19] a top surface having a plurality of discrete ridges; a lower surface having a plurality of discrete depressions; 19. The direct tension indicating reaction washer of any one of aspects 14 to 18, comprising: [Aspect 20] 20. The direct tension indicating reaction washer of any one of aspects 14-19, wherein each of the separate recesses is configured opposite one of the ridges or offset from one of the ridges. [Aspect 21] The direct tension indicating reaction washer according to any one of aspects 14 to 20, wherein the protuberance is made of a material similar to that of the direct tension indicating reaction washer. [Aspect 22] 22. The direct tension indicating reaction washer of any one of claims 14 to 21, including an indicating material disposed in each of the separated recesses. [Aspect 23] 23. The direct tension indicating reaction washer of any one of aspects 14 to 22, including a plurality of channels configured in the lower surface, each channel leading from one of the plurality of recesses to an outer edge of the lower surface. [Aspect 24] A direct tension indicating reaction washer for preventing loosening, which refers to a reaction washer that is subjected to a counter torque generated by tightening or loosening of a threaded fastener, an outer end having a geometry that allows for rotational coupling with a power tool; a lower surface having individual depressions and friction coefficient increasing treatments biased in an area outward from the central aperture; an upper surface having individual ridges and friction coefficient increasing treatment means biased in areas toward the central aperture; Equipped with anti-loosening direct tension indicating reaction washer. [Aspect 25] 25. The anti-loosening direct tension indicating reaction washer of claim 24, wherein the friction coefficient increasing treatment means surrounds the central aperture. [Aspect 26] the underside having an outer portion, the friction coefficient increasing treatment means being disposed about the outer portion and extending inwardly towards the central aperture to a width less than a width of the underside; the upper surface having an inner portion, the friction coefficient increasing treatment means being disposed about the inner portion and extending outwardly from the central aperture to a width less than a width of the upper surface; 26. The anti-loosening direct tension indicating reaction washer of any one of aspects 24 to 25, comprising: [Aspect 27] an outer edge defining a washer radius; a central hole defining a gap radius; the lower surface having an outer portion, the friction coefficient increasing treatment means being disposed about the outer portion and extending inwardly toward the central aperture to define an inner diameter greater than the gap radius; the upper surface having an inner portion, the friction coefficient increasing treatment means being disposed about the inner portion and extending outwardly from the central hole to define an outer radius greater than the gap radius but less than the washer radius; 27. The anti-loosening direct tension indicating reaction washer of any one of aspects 24 to 26, comprising: [Aspect 28] 28. The anti-loosening direct tension indicating reaction washer of any one of aspects 24 to 27, wherein the upper surface and the lower surface are substantially flat. [Aspect 29] 1. An anti-loosening self-reacting mechanical tension nut, comprising: An inner sleeve; An outer sleeve; a washer having a lower surface with friction coefficient increasing treatment means biased toward an area outward from a central aperture; 1. An anti-loosening self-reacting mechanical tension nut comprising: [Aspect 30] 30. The anti-loosening, self-reacting mechanical tension nut of claim 29, wherein the friction coefficient increasing treatment means surrounds the central bore. [Aspect 31] 31. The anti-loosening, self-reacting mechanical tensioning nut of any one of claims 29 to 30, having an underside having an outer portion, and wherein the friction coefficient increasing treatment means is disposed about the outer portion and extends inwardly toward the central bore to a width that is less than a width of the underside. [Aspect 32] an outer edge defining a washer radius; a central hole defining a gap radius; the lower surface having an outer portion, the friction coefficient increasing treatment being disposed about the outer portion and extending inwardly toward the central aperture to define an inner diameter greater than the gap radius; 32. The anti-loosening, self-reacting mechanical tension nut of any one of aspects 29 to 31, comprising: [Aspect 33] 1. A fastening socket assembly comprising: an inner socket having an inner end having a nut or stud head engagement means; an outer socket having an inner end having a reaction washer engagement means for engaging an outer end of either the anti-loosening reaction washer of any one of aspects 1-13, the direct tension indicating reaction washer of any one of aspects 14-23, the anti-loosening direct tension indicating reaction washer of any one of aspects 24-28, or the anti-loosening self-reacting mechanical tension nut of any one of aspects 29-32; Equipped with a fastener socket assembly, the fastener socket assembly being disposed substantially inside the fastener socket, the fastener socket and the fastener socket coupled together by a mechanism that allows the fastener socket and the fastener socket to cooperate and rotate in opposite directions relative to one another. [Aspect 34] A screw fastener for fastening objects, comprising: Studs and Either a nut that can be screwed or loosened to be threadably engaged with the stud, or a stud head that can be screwed or loosened on the stud; A loosening prevention reaction washer according to any one of aspects 1 to 13, a direct tension indicating reaction washer according to any one of aspects 14 to 23, a loosening prevention direct tension indicating reaction washer according to any one of aspects 24 to 28, or a loosening prevention self-reacting mechanical tension nut according to any one of aspects 29 to 32, disposed between one of the objects and either the nut or the bolt head; A screw fastener comprising: [Aspect 35] 35. A threaded fastener as described in embodiment 34, comprising a HYTORC® double sided friction washer disposed between another object and another portion of the fastener that is not to rotate, the HYTORC® double sided friction washer having upper and lower surfaces configured with the friction coefficient increasing treatment of embodiment 1, preventing the other portion of the fastener from rotating. [Aspect 36] A rotational force generating mechanism; A drive device that transmits a rotational force; The fastening socket assembly of embodiment 33; and 36. A reaction arm free torque power tool for tightening, loosening, or both tightening and loosening a threaded fastener according to any one of aspects 34-35, comprising: [Aspect 37] 37. The reaction arm free torque power tool of embodiment 36, which is electrically, hydraulically or pneumatically driven. [Aspect 38] 37. The reaction arm free torque power tool of embodiment 36, comprising any of a HYTORC®·ICE®, HYTORC®·AVANTI®, HYTORC®·STEALTH®, HYTORC®·XXI®, HYTORC®·jGUN®, HYTORC®·FLIP-Gun®, HYTORC®·THRILL® gun, HYTORC®·Z® gun, HYTORC®·FLASH® gun, or a HYTORC®·Lithium·Series® gun. [Aspect 39] A screw fastener according to any one of aspects 34 to 35; and A reaction arm free torque power tool according to any one of aspects 36 to 38; A system for fastening objects comprising: [Aspect 40] Any novel feature or novel combination of features described in this specification and / or with reference to and / or shown in the accompanying drawings.

Claims

1. 1. An anti-loosening direct tension indicating reaction washer that is subjected to a counter torque generated by tightening or loosening of a threaded fastener, comprising: an outer end having a geometry that allows for rotational coupling with a power tool; a lower surface having a friction coefficient increasing treatment means biased in an area outward from the central aperture; an upper surface having a friction coefficient increasing treatment means biased in a region toward the central aperture; Equipped with the underside having an outer portion, the friction coefficient increasing treatment means being disposed on the outer portion and extending inwardly towards the central aperture to a width less than a width of the underside; the upper surface having an inner portion, the friction coefficient increasing treatment means being disposed on the inner portion and extending outwardly from the central aperture to a width less than a width of the upper surface; Equipped with anti-loosening direct tension indicating reaction washer.

2. 2. The anti-loosening direct tension indicating reaction washer of claim 1, wherein said friction coefficient increasing treatment means surrounds said central aperture.

3. an outer edge defining a washer radius; a central hole defining a gap radius; the lower surface having an outer portion, the friction coefficient increasing treatment means being disposed on the outer portion and extending inwardly toward the central aperture to define an inner diameter greater than the gap radius; the upper surface having an inner portion, the friction coefficient increasing treatment means being disposed on the inner portion and extending outwardly from the central hole to define an outer radius greater than the gap radius but less than the washer radius; 3. The anti-loosening direct tension indicating reaction washer according to claim 1 or 2, comprising:

4. The anti-loosening direct tension indicating reaction washer according to any one of claims 1 to 3, wherein said upper surface and said lower surface are substantially flat.

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