A reaction washer and its fastening socket.

(54) Title: A REACTION WASHER AND ITS CLAMPING BUSHING.

(54) Title: A REACTION WASHER AND ITS FASTENING SOCKET.

(57) Summary

The present invention seeks to protect Applicant's HYTORC (r) Z (r) system, which includes tools that have multi-speed / multi-touch modes with torque multiplication and vibration mechanisms without the use of external reaction splices, a force transfer medium to produce coaxial action and reaction in line for use with such tools, clamping means and displacement means with the ability to mate with the washers under the nut for use with such tools and force transfer means, associated washers for use with such tools, force transfer means and clamping means, and accessories related for use with such tools, force transfer means, media, and lock washers. HYTORC (r) Z (r) washers located under nuts or bolt heads of various types that have perimeters that can be mated in multiple shapes, sizes, geometries and indentations, such as washer / fastener radius coupling differentials and faces frictionally chamfered with relatively higher friction against the flange surface and relatively lower friction against the nut, so that the coefficient of friction increases the treatment medium of various types, sizes and locations. HYTORC (r) Z (r) guns incorporate a powerful impact mechanism and a precise touch multiplier in the same tool that combines rapid loosening with calibrated torque. HYTORC (r) Z (r) bushings with double coaxial tightening and reacting action that have external sleeves to react on Z (r) washers and inner sleeves to turn nuts or bolt heads. HYTORC (r) Z (r) slotted adapters and reaction plates for backward compatibility with HYTORC (r) Z (r) torque / tension systems including AVANTI (r) square drive system, STEALTH (r) limited clearance, jGUN (r) pneumatic series, FLASH (r) electric gun multiplier and others. The HYTORC (r) Z (r) and HYTORC (r) Friction WasherTM combination includes a friction-enhanced double-sided washer for counter torque under a nut or bolt head on the other side of the joint, double-sided drag offset for tight clearances while using HYTORC (r) die / tension systems.

(57) Abstract

The present invention seeks to protect Applicant's HYTORC Z System which involves: tools having multi-speed / multitorque modes with torque multiplication and vibration mechanisms without use of external reaction abutments; a forced transfer means to yield in-line co-axial action and reaction for use with such tools; driving means and shifting means capable of attaching to washers under the nut for use with such tools and forced transfer means; associated washers for use with such tools, forced transfer means and driving means; and related accessories for use with such tools, forced transfer means, driving means and washers. HYTORC (r) Z (r) Washers located under nuts or bolt heads of various types having engageable perimeters of multiple shapes, sizes, geometries and serrations, such as washer / fastener radius engagement differentials, and frictionally biased faces with relatively higher friction against the flange surface and relatively lower friction against the nut, such as friction coefficient increasing treatment means of various types, sizes and locations. HYTORC Z (r) Guns incorporating a powerful impact mechanism and a precise torque multiplier in the same tool combining rapid run-down with calibrated torque. HYTORC (r) Z (r) Sockets with dual drive coaxial action and reaction having outer sleeves to react on Z (r) Washers and an inner sleeves to turn nuts or bolt heads. HYTORC (r) Z (r) Spline Adapters and Reaction Plates for backwards compatibility with HYTORC (r) 's torque / tension systems including the AVANTI (r) square drive system, the STEALTH (r) limited clearance system, the pneumatic jGUN ( r) series, the FLASH (r) Gun electric multiplier and more. HYTORC (r) Z (r) Washer and HYTORC (r) Friction Washerá # or combination including a dual friction-enhanced face washer for counter-torque under a nut or bolt head on the other side of the joint; and HYTORC (r) Z (r) Dual Drive Offset Links for tight clearances while using HYTORC (r) 's torque / tension systems.

A REACTION WASHER AND ITS CLAMPING BUSHING

Cross reference to related requests

This application either claims priority to and / or is either a continuation of the patent application or a continuation-in-part application of the following commonly owned and co-pending patent applications, the full copy of which is incorporated herein by reference: the number US application serial 62 / 012,009, which has a filing date of June 13, 2014, entitled APPARATUS FOR TIGHTENING THREADED FASTENERS; patent cooperation treaty application serial number PCT / US2014 / 035375, which has a filing date of April 24, 2014, titled APPARATUS FOR TIGHTENING THREADED FASTENERS; US application serial number 61 / 940,919, which has a filing date of February 18, 2014, titled APPARATUS FOR TIGHTENING THREADED FASTENERS; United States application serial number

61 / 916,926, which has a filing date of December 17, 2013, entitled APPARATUS TO TIGHTEN FASTENERS

THREADED; United States application serial number

13 / 577,995, which has a filing date of August 9,

2012, entitled FASTENER TIGHTENING APPARATUS

THREADED; which claims priority to the serial number of the patent cooperation treaty application PCT / IB2011 / 001019, which has a filing date of February 9, 2011, entitled

APPARATUS FOR TIGHTENING FASTENERS · THREADED; claiming priorities to US application serial numbers 61 / 430,105 and 61 / 302,598, which have the filing dates of January 5, 2011 and February 9, 2010, both entitled THREADED FASTENERS TIGHTENING APPARATUS; and US Application serial number 13 / 113,693, which has a filing date of May 23, 2011, entitled METHOD TO TIGHTEN AND LOOSEN THREADED CONNECTORS; which is a division of US application serial number 12 / 429,040, which has a filing date of April 23, 2009, entitled WASHER FOR TIGHTENING AND LOOSENING THREADED CONNECTORS, which is now US patent number 8,079,795, which has a publication date of December 20, 2011, entitled WASHER FOR TIGHTENING AND LOOSENING THREADED CONNECTORS.

Background of the Invention

Threaded fasteners, which include bolts, pins, nuts, and washers are known and used in traditional bolting applications. Industrial application maintenance and repair begins with loosening and ends with tightening these threaded fasteners. Naturally the industry seeks to reduce the loss of production during routine, maintenance and / or unforeseen and / or emergency repair.

There are two methods of tightening and / or loosening a bolt, torque and tension. Until the applicant's innovations, however, it was not possible to realize hydraulic torque and hydraulic tension with the same tool. Operators need separate tools for torque and tension of threaded fasteners.

Torque has benefits in that: it can be applied to most 5 existing threaded fasteners; accurate to within five percent (5%) of previously calculated nut turning resistance; prevents unintended loosening; it ensures even more circumferential bolt load than tension; and overcomes uneven lubrication applications, foreign particles under the nut or on top of the flange and minor damage to the thread. Torque, however, has drawbacks in that: it is subject to threaded friction and face friction, both of which are unknown; requires the use of a back wrench applied to the nut on the other side of the application to hold the lower portion of the threaded fastener immobile; the results of unknown bolt residual load; and is subject to bolt torque and side loading, both of which negatively affect bolting applications. Sustainable and accurate use of torque in bolting requires setting the tapping and supporting face frictions and elimination of torque and side loading.

Tension has advantages in that it is resistant to torsion and free of lateral load. Tension, however, has drawbacks in that; requires the bolt to protrude at least its diameter over and around the nut, so that it can be removed by a tensioner, which often requires replacement of the bolt and nut; only accurate within 25% assumed turning resistance; produces unpredictable hand nut placement; it is subject to threaded friction and face friction, both of which are unknown; they are often pulled further, do not stretch the bra; causes uncontrollable bra relaxation due to load transfer from the extractor; and results in the unknown residual bolt load. Sustainable and accurate use of tension in bolting requires elimination of pin / bolt removal and load transfer.

Power torque tools are known in the art and include those that unscrew pneumatically, electrically, and hydraulically. Power torque tools produce a twisting force to tighten and / or loosen the threaded fastener and an equal and opposite reaction force. Hydraulic tensioners use a puller to apply hydraulic pressure to the bolt, which typically results in 10% -20% greater than the desired bolt elongation, causing the bolt to be pulled further. The nut is then hand-tightened until firm; the pressure in the cylinder is released; the pin goes back; and the load is transferred from the bridge to the nut thereby compressing the joint with clamping force.

In relation to torque, traditional reaction fittings are butted against viable and accessible immovable objects, such as adjacent fasteners, to prevent the tool housing from rotating backward while the fastener rotates forward. This coupling force applies a pull force or lateral load, perpendicular to the bolt axis, on the nut to be tightened or loosened. The reaction force from the square drive tools travels through the torque arm trying to unscrew the cylinder end of the tool and / or bend the torque. Taking into account the applicant's innovation in coaxial reaction force transfer found in HYTORC® AVANTI®. The evolution of traditional prior art reaction accessories is disclosed, for example, in US Patent Nos. 4,671,142; 4,706,526; 5,016,502; Re. 33,951; 6,152,243; D500060; and 7,765,895 from Applicant, full copies of which are incorporated herein by reference.

The industry has moved away from cumbersome and complicated hydraulic tensioners, however, also from torque due to the twisting and lateral loading applied to the fastener. Indeed mechanical tension is quite popular.

Applicant improves bolting and solves many bolting problems with its HYTORC NUT ™ mechanical tensioner product lines and drive fingers and tools for use with them. This tension nut has two sleeves, one inside the other, whereby the inner sleeve is connected with a splined washer to allow axial movement of only the inner sleeve. Screws onto a pin or bolt as a unit. A proprietary drive finger stays on the inner sleeve and rotates the outer sleeve. The pin is pulled up along with the inner sleeve and tensioned without excessive extension and reverse effect, as with a hydraulic tensioner. The inner nut never turns against the pin threads under load, eliminating the possibility of galling of the bolt thread or other damage.

The HYTORC NUT ™: mechanically uses the action and reaction force of the tool during tightening and loosening; converts torque to non-torqued bolt extension rather than being pulled while in tension; enables precision bolt load calibration with fine tuning and achievement of desired elongation or residual bolt load, compared to torque; eliminates lateral loading, torsion, load transfer and relaxation, torque arms, recoil keys, extractors and bridges; eliminates bolt elongation measurements for critical applications; increases safety, error-free bolting, reliability and speed of joints; reduces bolting times by more than 50%; and they work in all joints and without alteration. Improves torque and tension by tightening bolts instead of pulling them out by preventing unsafe damaging mechanical elasticity of the fastener and hinge. Operators adjust and achieve bolt load between 30% to 90% of performance.

The evolution of the HYTORC NUT ™ is disclosed, for example, in US patent numbers 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 from applicant, full copies of which are incorporated herein by reference.

The HYTORC NUT ™, however, has its set of challenges. End users should replace standard 5 nuts with precision machined, treated and lubricated units.

Additionally, the inner sleeve has to be relatively radially thick at the point of connection with the washer. Sometimes this connection can maintain the full reaction force applied to the outer sleeve. In addition, the HYTORC NUT ™ 10 is expensive to produce and is often difficult to sell to traditional bolting end users at reduced cost. Furthermore, in some versions of the HYTORC NUT ™, the nut has to be made with two sleeves, the outer diameter of which has to meet the outer diameter of a regular nut, so both sleeves 15 have less material than a regular nut. This requires the use of materials of greater resistance, which causes reluctance on the part of customers to change materials and fear of the unknown. In other versions of the HYTORC NUT ™, the bolt needs to be altered, which is expensive and not easily acceptable 20 by the industry.

Applicant further improved industrial bolting and solved many bolting problems with its HYTORC WASHER ™ product lines and drive fingers and tools for use with them. The HYTORC WASHER ™ was the first example of 25 reaction washers used as reaction points for torque nuts and bolts in helically threaded fasteners. Reaction washers position themselves in the load pin or bolt path and therefore always experience the same and identical load. In reaction washer systems the turning torque is applied to the top nut or bolt while the opposite reaction torque is imparted to the reaction washer. The top nut or bolt and the coupling reaction washer experience the same and identical load and torque. Therefore the relative motion is governed only by friction forces. The component with the lowest coefficient of friction will have a tendency to move while the other component will remain relatively anchored.

The HYTORC WASHER ™ Self-Reacting Load Washer has an internal thread segment connected to the thread of a traditional bolt. It fits under a regular nut and prevents the bolt from turning, while providing a reaction point for the drag tool. It is tightened with a proprietary double bushing. An outer sleeve is held on the washer, and an inner sleeve turns the regular nut, thus capturing the pin through the washer. The reaction force of the tool is converted into a holding force that holds the HYTORC WASHER ™ immobile. This keeps the segment and therefore the bolt immobile when the nut is turned until the bolt elongation causes an axial segment to move inside the HYTORC WASHER ™. Improve torque and tension by tensioning the bolts instead of removing them. The lack of load-transfer-relaxation, or mechanical elasticity, allows tensioning at 90% performance.

The HYTORC WASHER ™: Provides known supporting face friction for more uniform residual bolt loading; does not require precision machining of facing; reduces torque and side loading of the bolting procedure; prevents the bolt from turning together with the nut; creates straight axle bolt tension without the need for torque arms and setback wrenches; increases residual bolt load and circumferential joint compression uniformity; reduces installation time; bolt speed increases; allows bolting to be axially oriented and hands-free even in inverted applications; increases bolting safety; and reduces the risk of damage to the fastener and joint.

The evolution of the HYTORC WASHER ™ product lines and drag fingers and tools for use therewith are disclosed, for example, in US Patent Nos. 6,490,952; 6,609,868; 6,929,439; 6,883,401; 6,986,298; 7,003,862; 7,066,053; 7,125,213; 7,188,552; 7,207,760; and 7,735,397, the full copies of which are incorporated herein by reference.

The HYTORC WASHER ™, however, has its set of challenges. Add the height needed for bolting applications. End users are often required to replace standard pins and bolts with longer versions due to regulations requiring two or more threads to protrude from the nut to be tightened. Additionally, the HYTORC WASHER ™ is more expensive to produce than traditional washers and is often difficult to sell to end users of traditional bolting at reduced cost. Also, the HYTORC WASHER ™ turns freely and in the opposite direction if the nut friction is higher. During operation the HYTORC WASHER ™ has two face frictions and the nut has one face and threaded friction, so the overall friction of each is almost identical, which means that the HYTORC WASHER ™ can rotate or the nut can rotate. To avoid this a preload is required which cannot be achieved if the HYTORC WASHER ™ and the nut are simultaneously turned. Finally despite the elimination of lateral load and torsion, corrosion still accumulates in the threads thereby not eliminating the galling of the thread.

Applicant further improves industrial bolting and solves many bolt mounting problems with its HYTORC WASHER ™ product lines and drive fingers and tools for use with them. This self-reacting multipurpose washer used to tighten and loosen threaded connectors that includes a nut, a bolt that has a shaft and is driven into an object with the interposition of the washer between the nut and the object so that a first surface of Support face of the washer on an axial side cooperates with a nut and a second surface of support face of the washer on an opposite axial side cooperates with the object. The washer includes: a radially outer body having a radially inner opening adapted to be larger than a diameter of the bolt and a radially outer surface adapted to absorb a reaction force from a tool; a radially inner segment engages with a thread of the bolt, located radially on the inside of the outer body at the radially inner opening, and connects it to the outer body with limited axial frictional movement relative to the body; and a spacer adapted to be located between the radially inner segment and the nut and also located radially within the outer body at the radially inner opening and axially spaced from the radially inner segment. The outer body, the radially inner segment, and the spacer are assembled and disassembled with each other and are used individually or unidle.

The applicant uses the radially outer body and the radially inner segment interposed together between the nut and the object for applications where continuous and accurate elongation of the bolt was necessary. When the nut is turned by the tool at the given force the radially outer body recurs the given force in an opposite direction from the tool. The radially outer body stops while the radially inner segment engages the bolt thread which positively prevents the bolt from turning. The bolt only lengthens or relaxes. In this case the washer 25 is made up of the radially outer body and radially inner segments functions as a tension washer.

Applicant uses the radially outer body, radially inner segment and spacer interposed between the nut and the object for applications where continuous and accurate elongation of the bolt was necessary and a bolt elongation must be controlled. When the nut is turned by the tool at the given force, the radially outer body receives the given force in an opposite direction from the tool. The radially outer body stops while the radially inner segment engages the bolt threads positively stops the bolt from rotating. The bolt only lengthens or relaxes and at the same time the radially inner segment moves axially, while the spacer limits the axial movement of the segment. In this case the washer is made up of the radially outer body, the radially inner segment, and the spacer functions as a high precision washer.

The applicant uses only the radially outer body of the washer interposed between the nut and the object for regular applications when continuous and exact elongation of the bolt was necessary. The radially outer surface of the body is used to absorb the equal and opposite reaction force when the tool applies the turning force to the nut. The nut rotates but the radially outer body stops, and in this case the washer is composed solely of the radially outer body functions as a reaction washer.

The HYTORC SMARTWASHER ™ provides many of the advantages of the HYTORC WASHER ™ in the lowest cost and most flexible package. The evolution of the HYTORC WASHER ™ product lines and drag fingers and tools for use therewith is disclosed, for example, in applicant's US patent number 8,079,795, a full copy of which is incorporated herein. by reference.

The HYTORC SMARTWASHER ™, however, has its set of challenges, similar to those of the HYTORC WASHER ™. Height required for bolting applications is added. End users often must replace standard pins and bolts with longer versions due to regulations requiring two or more threads to protrude from the nut to be tightened. Additionally, the HYTORC SMARTWASHER ™ is more expensive to produce than traditional washers and is often difficult to sell to end users of traditional bolting at reduced cost. Notably, the applicant believes that even accurate continuous elongation of the bolt was not possible when only the radially outer day HYTORC SMARTWASHER ™ body is used as a reaction washer. The additional use of the threaded insert with the given radially outer body produced the continuous and exact elongation of the bolt but the travel of the pin is limited to the thickness of the washer. Travel is made even more difficult by using the separator. Finally despite the elimination of lateral load and torsion, corrosion still accumulates in the threads thereby not eliminating the galling of the thread.

Also, the HYTORC SMARTWASHER ™ turns freely and in the opposite direction if the nut friction is higher. During operation the HYTORC SMARTWASHER ™ has two face frictions 5 and the nut has one face friction and one thread friction, so the overall friction of each is almost identical, which means that the HYTORC SMARTWASHER ™ can rotate or the nut can rotate. To avoid this, it is required that it is not carried out if the HYTORC SMARTWASHER ™ and the nut are simultaneously turned 10 times.

With conventional reaction washer systems, the lubricant must be applied to selectively push the washer to still remain under higher friction than the nut or pin. This allows the pin or nut to rotate and generate load 15 through the helical mating threads. The required lubricant push member is an undesirable and difficult one for the control stage in the reaction washer installation process. Even small amounts of lubricant in a conventional reaction washer will have the adverse effect of allowing the reaction washer to rotate or displace the nut or bolt earlier.

When the washer rotates before the bolt or helically threaded nut, the system cannot generate bolt load. Improper handling of lubrication or friction surfaces often results in inadvertent slippage or thrust of conventional reaction washers.

Other examples of reaction washers in the prior art include those described in US Patent Numbers 7,462,007 and 7,857,566, full copies of which are incorporated herein by reference. These Reaction Washers are offered as substitutes for Belleville Locknuts and Washers as they elastically deform under load to store preload energy or live load. In most embodiments, the incorporation of a threaded hole seeks to reduce the lateral load on the bolt. The object contacting area of ​​these concave and / or convex reaction washers is low compared to the total surface area of ​​the lower washer surface. A non-threaded hole is disclosed in one embodiment. Friction enhancements include protrusions, such as points on the hexagonal washer shape or flat splined extensions, that penetrate or dig into the object surface. Also disclosed is a substantially flat reaction washer having frictionless enhancements.

The applicant made efforts to increase the clamping rotational speed in fluid-operated torque power tools. The HYTORC® XXI® is a fluid-operated wrench that has: a fluid-operated clamp that includes a cylinder; a piston reciprocatingly movable in the cylinder and having a piston rod with a piston rod end; a ratchet mechanism having a ratchet provided with a plurality of teeth; and at least two latches operably connectable with the piston rod end and acceptable with the ratchet teeth such that during a piston advance stroke one of the at least two latches engages with at least one ratchet tooth while the other from at least two latches on at least one ratchet tooth, while during a return stroke of the piston the other of the at least two latches engages with at least one ratchet tooth while one of the at least two latch pawls engages on at least one ratchet latch. At least one of the at least two latches is detachable from and liftable above the ratchet teeth. The HYTORC® XXI® also includes a decoupling unit that is actuated by a separate operator upon tightening and can act on at least one latch in order to distinguish it from and lift it above the ratchet teeth. This anti-kickback feature allows the ratchet to rotate rearward to release jamming torque and material flex, so the fluid-operable wrench can be pulled out of a job. The HYTORC® XXI® is the world's first continuously turning hydraulic wrench. That makes this tool up to three times faster than any other wrench on the market. Bearing in mind that the benefits of HYTORC NUT ™ and HYTORC WASHER ™ are accentuated when used with HYTORC® XXI®. HYTORC® XXI® is disclosed in applicant's US patent number 6,298,752, a full copy of which is incorporated herein by reference.

The applicant then applied its in-depth knowledge and innovation in power torque tools to torque intensifying pneumatic armless tools, specifically creating HYTORC® jGUN® product lines and drive fingers and tools for use with them. The applicant markets these tools under the trade names HYTORC® jGUN® Single Speed, Dual Speed ​​and Dual Speed ​​Plus. Once the nut hits the flange surface the degree of twist is too small to tighten or loosen. Customers want high turning speeds to quickly tighten and loosen nuts. Known air wrenches, which provide high tightening and loosening speed, had drawbacks of inaccuracy and slow turning once the nut hits the flange face. By contrast, known torque armless power tools were torque accurate, but relatively slow in tightening and loosening fasteners. They were still much faster than pneumatic guns once the nut was turned on the flange face.

The motor housing on tools without known torque intensification arm was independent of the gearbox such that the torque could not exceed an operator arm / hand torque resistance. Otherwise, the tool motor housing could not be retained and will be rotated by the operator's hand. There are many motor driven torque multipliers on the market and some of them had two speed mechanisms, some of them reacted at the bolt tip, requiring special bolts, and others with a reaction arm. No matter what torque or speed was applied, its gear housing rotated in the opposite direction of the output shaft. At high speed, turning parts in then-existing tools without a torque-intensifying arm required bearings because the gears and output shaft rotate so fast in the gearbox. The high-torque versions of these tools were too big and too heavy.

The HYTORC® jGUN® product lines include a tool that has a tightening and loosening speed where the entire gearbox together with the inner gear assembly and the output tightening rotates at the same high speed in the same direction. The operator simply changes the tool by applying a turning force to the gears and the output shaft in one direction and simultaneously a turning force opposite to the gearbox. Note that the HYTORC NUT ™ and HYTORC WASHER ™ product lines and the pinch fingers and tools for use with them are compatible with the HYTORC® jGUN® Dual Speed. For example, at higher speed, the lower torque of the HYTORC® jGUN® Dual Speed ​​mode the clamping sleeve that has the nut and the reaction sleeve that the HYTORC WASHER ™ has as long as they rotate together and at the same higher speed and the same lower torque. The HYTORC WASHER ™ and nut are integrated as a unit by the shanks until the nut rests on the HYTORC WASHER ™. Torque increases and stems disintegrate by cutting, so that the nut is turned with higher torque and slower speed, while the HYTORC WASHER ™ becomes an immobile object and therefore a point of reaction. The integration of the HYTORC WASHER ™ and a known nut is no longer acceptable because broken fitting parts affect the coefficient of friction, can cause thread galling and leave damaging unwanted deposits on the thread interfaces.

When not used with the HYTORC WASHER ™, the HYTORC® jGUN® required use of reaction accessories to deflect the reaction force generated during nut turning, to a stationary object. The loosening speed had to be limited to prevent the reaction arm from being slammed against the adjacent nut at high speed, which could cause an accident if the operator's limbs were in shape. A torque arm splice is necessary for the low speed, high torque mode of operation to tighten or loosen fasteners. But the reaction arm is undesirable for the high-speed, low-torque mode - again to avoid accidents and recordable OSHA situations.

Applicant has applied its in-depth knowledge and innovation in power torque tools having reaction accessories and the HYTORC® jGUN® product lines to further promote torque-intensifying pneumatic armless tools. The applicant has created the HYTORC® FLIP-GUN® product lines and the drag fingers and tools for use with them. The HYTORC® FLIP-GUN® includes a positionable reaction arm. When placed in a first position, the torque intensifier unit is switched to a high speed, low torque mode and the reaction arm can be used as a sleeve by the operator, while in a direction perpendicular to the axis of tool. When the reaction arm is placed in a second position coaxial with the tool axis the torque intensifier unit is switched to low speed, the high torque mode and the reaction arm can butt against a stationary object as the high torque cannot be absorbed by the operator.

Application characteristics often adversely affect bolting jobs and include, for example, pin and nut corroded, contaminated, dirty, twisted, debris laden, burred, rough, uneven, disoriented, misaligned and / or out of alignment. unevenly lubricated. Often times loss of production is compounded by such adverse bolted application characteristics. Naturally the industry seeks to reduce the loss of production during routine, unforeseen and / or emergency maintenance and / or repair.

Applicant further innovated its torque intensifying pneumatic armless tools, specifically creating the 25 HYTORC® THRILL® product lines and drive fingers and tools for use with them. The HYTORC® THRILL® is a dual-mode motor-driven torque intensifier armless tool that operates in reaction-free and reaction-assisted tightening and loosening of industrial fasteners. It includes: a motor to generate a turning force to turn the fastener; a turning force multiplication mechanism for a lower speed / higher torque mode including a plurality of turning force multiplication transmitters; a twist force impact mechanism for a higher speed / lower torque mode including a plurality of twist force impact transmitters; a housing operatively connected to at least one multiplication transmitter; a reaction arm for transferring a reaction force generated in the housing during the higher speed / lower torque mode to a stationary object; wherein during the lowest speed / highest die mode at least two multiplier transmitters rotate relative to each other; and wherein during the higher speed / lower die mode mode at least two multiplier transmitters are unitary to achieve a hammering motion from the impact mechanism. Advantageously, the HYTORC® THRILL®: reduces the operator's exposure to vibrations; provides greater turning inertia in higher speed mode, lower torque due to greater mass of the cooperation between the impact and multiplication mechanisms, which increases the torque output of the impact mechanism; loosening and removing fasteners at higher speed without the use of a reaction mount even when greater than absorbable torque is required by an operator to overcome substantial adverse bolting application characteristics such as thread and facial deformation and / or galling of thread; and loosened or corroded high-touch fasteners that are glued to their joints and tightening fasteners to a higher and more precise torque desired with the use of a reaction apparatus in the second mode.

Impact mode is not operable on the THRILL® during slower speed / higher torque (multiplication) mode because: the positionable reaction arm is butted against a stationary object; and the impact mechanism locks during the torque multiplication mode. But keep in mind that during the higher speed / higher torque mode, the turning force from the motor is transferred through the initial stage of the multiplier mechanism to the output shaft to loosen and tighten a nut or bolt head that exhibits little or no resistance. The impact mechanism is activated when the fastener exhibits adverse bolting characteristics that therefore require intermittent force to overcome such deformities.

The evolution of the HYTORC® jGUN®, FLIP-Gun® and THRILL® product lines and the pinch fingers and tools for use with them are disclosed, for example, in US Patent Numbers and Nos. State request

Applicant's States: 6,490,952; 6,609,868; 6,929,439; 6,883,401;

6,986,298; 7,003,862; 7,066,053; 7,125,213; 7,188,552; 7,207,760; 7,735,397; 7,641,579; 7,798,038; 7,832,310; 7,950,309; 8,042,434; D608,614; and 13 / 577,995, full copies of which are incorporated herein by reference.

Despite the applicant's recent innovations with the THRILL®, side loading and thread galling remain the major problems in industrial bolting applications and have not been addressed at all by intensifier tools on the market. Galling is significant material wear caused by a combination of friction and adhesion between metal surfaces during transverse movement, or sliding, often due to poor lubrication. When a wear portions of material are pulled out from a contact surface and stick to or even friction weld to the adjacent surface, especially if there is a large amount of force compressing the surfaces together. Chafing often occurs in high load, low speed applications. This involves the visible transfer of material as it is adhesively removed from one surface, leaving it glued to the other in the form of a raised shoulder. Chafing is generally not a gradual process, but it occurs rapidly and spreads rapidly as raised bumps induce more chafing.

Corrosion of a long-corroded tight fastener usually occurs between the mating threads of the nut and bolt and the nut and flange. Corrosion can come from a number of sources, including chemistry, heat, moisture, and lubrication. In high temperature applications, for example, the lubrication applied during tightening dries and bonds the threads together over time. On the other hand, chemical reactions inside and outside the tank often cause galvanic corrosion. During loosening, internal thread corrosion pushes dry grease along the bolt threads. The reaction force applied to the stationary object applies an equal force on the near side of the nut to be rotated. In fact, the lateral load, or splice force, for a tool can be 3x to 4x its torque performance in ft.lbs (m / kg), because the splice point of the torque arm is at often half if not less than a foot away from the center of the tightening. This lateral loading causes the nut and bolt threads to engage with enormous force on the side close to where it is applied so that the dry grease manages to pile up there when the nut is turned. Irregularities in the threads often cannot be overcome. Only half of the threads between the bolt and the nut are engaged and the threads begin to clamp. This causes the bolt thread to overstretch and require substantially more torque and thus substantially more lateral loading to take on the nut, which can ruin the bolt and nut threads. The fastener often locks up to the point where all the turning force is used by thread friction, which can lead to the fastener breaking or the tool turning. The torque power tool originally used to tighten the fastener is often insufficient to loosen the corroded fastener itself. Such corroded fasteners may require loosening torque values ​​of 1x to 3x more than the tightening torque in ft.lbs (m / kg) and an additional more powerful tool may be required. High temperature bolting applications such as turbines and frames are generally critical requiring either precision or stainless steel fabricated fasteners with sky-high replacement costs. In addition, the use of fine thread bolts, which is very popular in recent times, multiplies this problem.

Even if no lateral load is applied by the tool to the fastener, thread galling can still occur as dry grease accumulates on the mating threads during loosening of the nut. Such loosening requires at a given moment a higher torque than the original tightening torque, which occurs when applied in the thread galling. This even happens with the HYTORC NUT ™ between the inner and outer sleeves. It is customary in the industry for operators to hit corroded fasteners with a sledgehammer to pulverize corrosion prior to applying loosening torque. This habit is dangerous, it can ruin the bolt threads that extend over the nut, and it is uncivilized. Adverse galling also occurs between the face of the nut and the face of the flange, as the lateral load changes a perpendicular orientation of the nut to be turned. This in turn increases the turning friction of the nut and causes the bolt load generated by unpredictable loosening torque causing aesthetic joint closures, adverse non-parallels, system leaks, and 5 tool, fastener and joint failures.

Known washers can reduce surface galling between the threaded fastener, the nut, and the joint since the washer is made of a harder material. ASME PCC-1-2010 Appendix M states that: it generally recognizes that the use of fully hardened steel washers will improve the translation of torque input into bolt preload, providing a smooth bearing surface and low friction for the nut . The washers protect the flange mating surfaces from damage caused by a turning nut. These are 15 important considerations when using torque methods (either manual or hydraulic) to tighten bolts. Known washers, however, do not reduce and / or eliminate surface galling and thread galling created by side loading. And the known washers can move when being tightened so that the washer can rotate with the bolt or locknut instead of remaining fixed. This can affect the torque tension ratio.

Another purpose of installing washers in a common bolting system is to distribute the loads under the heads of 25 bolts and nuts, providing a larger area under tension.

Otherwise, the bearing stress of the bolts may exceed the bearing strength of the connecting materials and this leads to loss of bolt preload and slow material advance.

What is needed is: simplification in the tool, design and operation of the screwdriver and washer; elimination of reaction forces of bending and extraction; increased bolting speed, efficiency, reliability and reproduction, all at low cost. Therefore, the present inventions have been devised to solve these problems.

SPECIFICATION

The inventions of the present application may be described by way of example only with reference to the accompanying drawings, of which:

Figures 1A-1C are perspective views of an upper and lower surface and a side view of a first embodiment of a HYTORC® Z® washer;

Figures 2A-2B are opposite upward and downward perspective views of a joint to be closed by a threaded fastener including the Z® washer of Figures 1A-1C and a nut, a Z® fastener;

Figures 3A-3C are side and perspective views of a power tool without a torque arm, a HYTORC® Z® gun, for reduced galling tightening and / or loosening of the Z® fastener;

Figures 4A-4B are perspective and side views of the tight fitting and tight Z® fastener;

Figures 5A-5D are perspective, perspective cross-section, and side cross-sectional views of a reaction and double tightening coaxial action assembly, a HYTORC® Z® socket;

Figures 6A-6E are top down, bottom up and side views of treatment means for increasing the friction coefficient of washer Z® and related forces activating the Z® fastener;

Figures 7A-7C are multiple views of various modalities of washer Z®s with various dimensions and widths of treatment means for increasing the friction coefficient of washer Z® as knurled bands;

Figures 8A-8L are top-down views of various embodiments of Z®s washer with varied shapes;

Figures 8D1-8D3 are perspective views of an upper and lower surface and a side view of another embodiment of a Z® washer;

Figures 8D4-8D10 are cross-sectional side views of various types, sizes and locations of treatment means for increasing the friction coefficient of washer Z®;

Figures 9A-9B are cross-sectional side views of alternative Z® fastener and Z® cap types for use with Z®s washers;

Figure 10 is a cross-sectional side view of an alternative Z® washer and Z® bushing such that the diameter of the washer is smaller than that of the nut;

Figures 11A-11C are multiple views of various embodiments of Z® bushings with varying widths and dimensions;

Figures 12A-14B are perspective views of the application of the Z® system to HYTORC® torque tools including the slotted adapters, reaction plates and displacement links;

Figures 15A-15G are perspective and side views of the application of a HYTORC® Dual Oriented Friction Washer to the Z® System;

Figure 16A is a perspective view of one embodiment of the present invention in the form of tool 10A in a lower speed, higher torque (LSHT) mode;

Figure 16B is a perspective view of one embodiment of the present invention in the form of tool 10B in a higher speed, lower torque (HSLT) mode;

Figure 17A is a side, cross-sectional view of tool 10A in LSHT mode;

Figure 17B is a side, cross-sectional view of tool 10B in HSLT mode;

Figure 18 is a side, cross-sectional view of a twist force multiplication assembly 200 and a vibration force assembly 300 of tool 10A in LSHT mode;

Fig. 19 is a perspective, cross-sectional view of a clamp tool housing assembly 101, a clamp tool sleeve assembly 103, and related interior components of tool 10A and tool 10B;

Figure 20 is a perspective view of a mode change assembly 400 of tool 10A and tool 10B;

Figure 21A is a side, cross-sectional view of an embodiment of the present invention in the form of a tool 10F;

Figure 21B is a side, cross-sectional view of an embodiment of the present invention in the form of a 10G tool;

Figure 22A is a side, cross-sectional view of an embodiment of the present invention in the form of a tool 10H; and

Figure 22B is a side, cross-sectional view of one embodiment of the present invention in the form of a tool 101.

The HYTORC® Z® system. The present invention aims to protect Applicant's HYTORC® Z® system consisting of: tools having multi-speed / multi-torque modes with torque multiplication and vibration mechanisms without the use of external reaction joints; a force transfer means for producing an in-line coaxial action and reaction and for use with such tools; clamping means and displacement means capable of attaching to the washers under the nut for use with such tools and force transfer means; associated washers for use with such tools, force transfer means, and clamping means; and related accessories for use with such tools, force transfer means, clamping means and washers.

The HYTORC® Z® system includes the following: washer Z®s located under the heads of different types of nuts or bolts that have mating perimeters of multiple shapes, sizes, geometries, and splines, such as washer / fastener radius coupling differentials and frictionally oriented faces pushed with relatively friction greater against the flange surface and relatively less friction against the nut, as treatment means for increasing the coefficient of friction of various kinds, sizes and locations; HYTORC Z® guns that incorporate a powerful impact mechanism and a precise torque multiplier in the same tool that combines rapid loosening with calibrated torque; HYTORC® Z® bushings with double tightening coaxial action and reaction that have outer sleeves to react on Z®s washers and inner sleeves to turn nut or bolt heads; HYTORC® Z® Slotted Adapters and Reaction Plates for backward compatibility with HYTORC® Torque / Tension Systems including AVANTI® and ICE® Square Torque Systems, STEALTH® Limited Clearance System, jGUN® Series pneumatic, FLASH® gun and LITHIUM series electric multipliers and more; the combination of the HYTORC® Z® washer and the HYTORC® Dual Friction Washer ™ that includes a dual friction enhanced face washer for counter torque under a nut or bolt head on the other side of the joint; HYTORC® Z® tightening double offset connections for tight clearances during when using HYTORC® torque / tension systems; and HYTORC® Z® vibration mechanisms applied to them.

The HYTORC® Z® washer. International bolting standards require hardened washers to be placed under industrial threaded fasteners. HYTORC® Z® Washers are applicant's proprietary hardened washers that became the reaction point directly under the fastener bolt or locknut during tightening and / or loosening. HYTORC® Z® Washers are used with industrial threaded fasteners of the type that have a coaxial reaction surface, a pin, and either a threadedly engaging nut with the pin or a pin head connected to the pin. They remove any of the possible breakpoints for operator stubs. Operators do not need to search for satisfactory stationary objects on which to react. The straight coaxial tension all without eliminating bending and / or lateral loading of the pin. They provide a smooth, uniform, low-friction top surface on which the bolt or locknut rotates; the top has a polished surface against which the bolt or locknut will rotate. They provide an improved friction bottom surface against which the tool will react.

Z® washers protect flange surfaces from damage or fouling and evenly distribute bolt load around the joint due to the larger surface area. They can be made in a wide range of inch sizes and metric sizes from a full range of material options for every application. They meet all ASME, ASTM and API requirements for dimensions, hardness and thickness. They work with pneumatic, hydraulic, electric and manual torque tools. And with the addition of an associated friction washer, the need for a recoil wrench is eliminated to prevent the opposite nut from turning along with the bolt.

Research and development related to the applicant's recent Z® washer includes prototyping and experimentally evaluating different: thicknesses; external coupling sizes; outer coupling geometries and splines; low friction coatings and treatments on fastener mating sides (top); sizes, shapes and locations of friction enhancements, such as knurled patterns, on flange mating sides (bottom); sizes and shapes of chamfers on the bottom, top, inside and outside faces; material specifications; and heat treatment specifications.

Figure 1A shows a first embodiment of a HYTORC® Z® 1 washer for use with HYTORC® torque / tension systems. It is a perspective view of an upper side, or upper bearing face, 2 of the washer 1. Figure 1B shows a perspective view of a lower side, or a lower bearing face, 3 of the washer 1. And the Figure 1C shows a side view of an edge side, or lateral bearing face, 4 of the washer 1.

Generally the washer 1 has an annular shape having an inner void 5. As shown in Figure 1, the annular shape of the washer 1 includes radially extending lobes 6 that form a flower-like shape. In general, an upper bearing face 2 is smooth, with relatively low surface friction against the bolt or locknut. Note that lubricants can be used on the upper bearing face 2 at low surface friction between them and the nut, bolt head, or any other threaded fastener. A lower bearing face 3 is textured with relatively higher surface friction against the flange surface. The lower bearing face 3 is shown to have a smooth inner surface 3A and approximate frictional improvements, such as knurling, 7 with increased surface friction. The knurled radial relief pattern 7 increases the lower bearing face surface friction 3. In the illustrated embodiment, the knurled surface 7 takes the form of a ring located beyond the smooth surface 3A. The outer lobes 6 include angled chamfered faces 8 formed between the lower bearing face 3 and the lateral bearing face 4.

The washer 1 has, among others, the annular radius Ri_TO, a lobe radius R_1L, a knurling radius Ri_K and a hollow radius Rw Washer 1 has a height Hi, a first chamfer height H_1Bi, a second bevel height H_{1 B}¡H a knurling height H_iK and a bevel angle V

Figure 2A shows an upward opposite perspective view and Figure 2B shows an opposite downward perspective view of a joint 30 that will be closed. The joint 30 includes a first member 31 and a second member 32 that are held in face-to-face relationship by a fastener 20, commonly known in the art as a bolt. The fastener 20 has a first end 21 that has a head bolt 22 and a second end 23 that has a threaded coupling 24. The second end 23 of the fastener 20 is inserted through an opening 33 in the first and second members 31 and 32 that extend from a bearing face 34 of the second member 32 to a bearing face 35 of the first member 32. In the In preparation for a tightening process, the washer 1 is placed on the second end 23 with the lower bearing face 3 towards the bearing face 35. The threaded nut 36 is placed on the second end 23.

The Z® washer is used only on one side of the joint and no other washer should be used under it. Normal bolt and nut lubrication practices should be followed. The lubricant is only needed on the bolt threads and between the bolt or locknut and the top of the Z® washer, and should not be used between the washer and the flange. Note that the correct torque value for any given bolt is highly dependent on the lubricant used. Normally no lubricant is required on the rear side bolt or locknut.

Common industrial bolting practice is to adjust the pin so that when the upper end is tightened, 2-3 threads will protrude on the nut. This is for inspection purposes to ensure that the nut and pin are fully engaged. Generally, there is no reason for the pin to extend further than this, and any excess length must be adjusted for the other side of the flange so that the gland can engage the entire nut without obstruction. It is permissible in high corrosion areas for the pin to be flush with the nut after tightening to decrease the risk of thread damage and so that the nut can be more easily removed. Advantageously the washer of thickness 1 is ideal. If the washer were excessively thick, the fastening system would have insufficient male threads available. Conversely, if the washer were thick enough, it could fail under high compression loads.

The HYTORC® Z® gun (in general). A power tool without torque arm for the reduced galling tightening and / or loosening of an industrial threaded fastener of the type having a coaxial reaction surface, a pin, and either a threadedly pin-engaging nut or a pin head connected to the pin includes: a motor for generating a turning force; a squeeze to transfer the turning force; a turning force multiplication mechanism in a housing that includes a turning force multiplication transmitter for all torque modes from least resistance to greatest resistance; and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable during all torque modes from lower resistance to higher resistance.

Standard air wrenches hammer the bolt with uncontrolled force with high noise and excessive vibrations. The HYTORC Z® Gun is a precision torque multiplier that produces consistent, measured energy on bolt after bolt without the uncontrolled force, high noise, and / or excessive vibration of standard hydraulic wrenches. The Z® Gun is the world's first precision torque reaction arm pneumatic bolt-on tool. Uniform and accurate bolt loading is ensured. The Z® Gun incorporates a powerful impact mechanism and a precise torque multiplier in the same tool that combines rapid loosening with 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 bushing tightening that engages the low Z® washer. the nut. Impact mechanism racks nuts compress or decompress threads regardless of corrosion. The multiplier mechanism removes the fasteners or tightens the fasteners. They work with the Z® washer so there is no external reaction arm, no compression points and no inaccurate lateral loads. It does any bolting job faster, safer and better than ever, all with one tool.

The Z® Gun has a built in dual speed capability that is controlled by simply and quickly changing from high speed loosening mode to low speed torque power and vice versa. In high speed mode the double bushing rotates at several hundred revolutions per minute, but the torque is limited so that the tool cannot rotate or kickback in the operator's hands. Shifting the selector up locks the tool in power / torque mode and the nut or bolt is tightened to the desired torque automatically, based on calibrated pneumatic fluid pressures.

Advantageously, the Z® gun addresses industrial companies and tool problems that intensify hydraulic, pneumatic or electrical torque. It is: maximizes the benefits of and eliminates the drawbacks of torque and tension; maximizes the benefits of and eliminates the drawbacks HYTORC NUT ™, HYTORC WASHER ™, HYTORC® AVANTI®, HYTORC® XXI®, HYTORC® jGUN®, HYTORC® FLIP-Gun® and HYTORC® THRILL® - which can cause threaded couplings to the lateral load and accumulation of desiccated corrosion; reduces exposure to operator vibration; provides greater inertia in intermittent force mode due to a greater cooperative mass between the multiplication and impact mechanisms, which increases the torque output of the impact mechanism; loosen and remove fasteners at a higher speed without the use of a torque arm, even when greater torque than absorbable by an operator is required to overcome adverse bolting application characteristics; loosens very tight and / or corroded fasteners stuck to their joints and tightens fasteners to a desired higher and more precise torque using a coaxial reaction surface in higher strength torque mode. The vibrating force mechanism can be activated when the nut is tightened to spray dry corrosion prior to applying full torque to the nut for loosening. This results in less torque needed to loosen the industrial threaded fastener, and dry powdered grease does not accumulate or concentrate on portions of the threads. Furthermore, during the tightening and loosening of the nut they are kept parallel to the joint face and the threads are not subjected to the enormous and irregular lateral load making the face and thread friction more consistent. This ensures a more uniform torque load and therefore even joint compression to prevent leakage and joint failure in tightening. Furthermore, the use of the tool is simplified, the risk of operator error is reduced, and operator safety is increased.

The Industrial Threaded Fastener 20 is commonly tightened using torque, tension, and / or torque, and the tensioning tool is hydraulically, pneumatically, or electrically actuated. Figures 3A, 3B and 3C show a power tool without torque arm 10, the HYTORC® Z® Gun, for reduced galling tightening and / or loosening of fastener 20. Tool 10 includes a motor for generating a turning force; a squeeze to transfer the turning force; a turning force multiplication mechanism in a housing that includes a turning force multiplication transmitter for all torque modes from least resistance to greatest resistance; and at least one vibration force mechanism including a vibration transmitter for an operable intermittent force mode operable during all torque modes from low resistance to high resistance. Note that tool 10 operates at a higher speed, the lowest torque mode (HSLT), as shown as tool 10^to of Figures 3A and 3B, and a lower speed, higher torque (LSHT) mode 20, as shown as tool 10B of Figure 3C.

The tool 10A of Figures 3A and 3B and the tool 10B of Figure 3C include: a pinch inlet and outlet assembly 100; a turning force multiplication assembly 200; a vibration force assembly 25 300; a mode change assembly 400; and a double clamp outlet and 15 reaction sleeve assembly, such as the HYTORC® Z® sleeve.

In the HSLT 10A mode tool either: the washer 1 is compressed between the bearing nut 36 on the preloaded fastener 20 on the pre-tightened joint 30 at a predetermined pre-tightening torque; washer 1 between nut 36 on unloaded fastener 20 on loosened joint 30 is decompressed from predetermined pre-tightening torque; and / or the snap washer 1 is vibrated between the tight nut 36 on the loaded fastener 20 over the tight joint 30 to properly spray the bolt thread corrosion. In LSHT mode tool 10B either: washer 1 is pressurized between tightened nut 36 on loaded fastener 20 and union 30 is tightened to a predetermined tightening torque; and / or the washer 1 between the supported nut 36 on the pre-loosened fastener 20 is compressed on the pre-loosened joint 30 from the predetermined tightening torque.

In HSLT 10A mode tool either: loosen either nut 36 or nut 36 and washer 1 on fastener 20 with turning force in one direction to supported nut 36 and washer 1 is compressed over pre-loaded fastener 20 over pre-tightened joint 30 at a predetermined pre-tightening torque; either the supported nut 36 or the supported nut 36 and the compressed washer 1 on the pre-loosened fastener 20 on the pre-loosened joint 30 is tightened with the turning force in the opposite direction from the predetermined pre-loosening torque; or the tight nut 36 is vibrated (impacts) on the snap washer 1 to apply vibration to properly spray the threaded corrosion. In the LSHT 10B mode tool either: the nut 36 supported on the compressed washer 1 on the 5 preloaded fastener 20 on the pre-tightened joint 30 is tightened with the turning force in one direction at the predetermined tightening torque and the reaction force in the direction opposite to the compressed washer 1; or the tight nut 36 on the lock washer 1 on the loaded fastener 20 on the tight joint 30 10 is loosened with the turning force in the opposite direction from the predetermined tightening torque and the reaction force is applied in a direction a snap washer 1.

During operation the tool 10B in LSHT mode changes to tool 10A in HSLT mode after loosening the nut 36 and decompressing the washer 1 to the predetermined pre-loosening torque. During the operation of tool 10A in HSLT, it changes to tool 10B in LSHT mode to any: the nut 36 is seated and the washer 1 is decompressed to the predetermined tightening torque; or suitable threaded corrosion spray. Note that the operator uses the 400 mode shift assembly to shift the tool from LSHT mode to HSLT mode or vice versa. Note that the 400 mode shift mount is a manual switch, but it can be automatic. Likewise, keep in mind that the activation or deactivation of the vibration force (impact) assembly 300 can occur either manually or automatically. Note that the LSHT mode can be changed from torque regulated to vibration assisted or vice versa, and that the HSLT mode can be changed from vibration regulated to torque assisted or vice versa. Note that the vibration force (impact) assembly 300 can continue to operate even if washer 1 starts or stops turning. And note that the LSHT mode can be vibration assisted by loosening nut 36 to help overcome chemical, heat, and / or lubrication corrosion and prevent bolt thread galling.

Applying torque to a fastener creates facial friction, thread friction, as well as bolt loading. Friction and bolt load are inversely proportional: as friction increases, the amount of bolt load generated decreases. The speed at which a fastener is tightened has a pronounced effect on the amount of friction, and therefore the bolt load generated in a joint that will close. Advantageously, the Z® gun is able to use the principle that the thread coefficients and under the head of friction decrease as the rotation speed increases.

The Z® gun operates, for example, as follows. Assume a job requires tightening the pins 1½¹¹ (308 cm) with 2 nuts^3/8 (6.033 cm) at 520 ft-lbs (744.8 kg per ft) of torque using a Z®-Gun-A1. The Z®-Gun-A1 is used for ranges of 300-1200 pound-feet (447-1788 kg per foot) of torque. The Z®-GunA1 comes with a standard square drive torque size of (1.90 cm) and has dimensions (LxWxH) of 11.92 (30.27 cm) per

3.29 (8.35 cm) by 9.47 (24.05 cm). The torque outlet housing has a radius of 1.98 (5.02 cm). The cuff height and width are 6.94 (17.62 cm) and 2.12 (5.38 cm), respectively. Loosening and final torque RPMs range from about 5 to 4,000 to 7, respectively. The turning force of the tool is determined by the air pressure supplied by a filter / regulator / lubricator (FRL). The operator consults the corresponding pressure / torque conversion table for this value. In this case, 520 pound-feet (744.8 10 kg per foot) of final torque corresponds to a pneumatic pressure of 50 psi. Thus, the operator sets the FRL supply pressure to 50 psi.

From Figure 3B, tool 10A loosens nut 36 until it is snug against the flange in HSLT mode. The washer 1 For 15 cable 1 'is compressed between the supported nut 36' and the supported joint 30 '. In loosening mode (HSLT), the displacer (400 mode shift mount) is in the down position and tool 10A is held in both hands.

Per Figure 3C, to start torque in LSHT mode, the operator pulls the stripper 400 toward him in the up position. The supported nut 36 'engages ensuring that the outer reaction bushing 17 fully encompasses the compressed washer T. Take into account the lack of compression points, since both hands are safe outside the tightening zone around the nut supported 36 '. Operator depresses trigger until tool 10B stops and inner clamp bushing 16 no longer advances. Operator has applied 520 foot-pounds (744.8 kg per foot) of torque to locknut 36 and washer pressure 1, and every other nut will get the same tightening force while maintaining the FRL pressure. Figures 4A and 4B show a clamp joint 30 that includes clamp 20, clamp nut 36, and snap washer 1.

Note that the chamfered faces 8 help the washer 1 in cleaning the weld worms that form between the flanges and pipes at the joint 30 and other cleaning problems. Furthermore, the beveled faces 8 assist the external reaction bushing in the coupling and combination of rotation with the washer 1. The chamfered faces 8 can also accept modifications made to the outer reaction bushing 17 to allow its use in reverse bolting applications.

The operator reverses the process for removal by tightening nut 36, this time starting in LSHT mode. The effects of time and corrosion can make nuts and / or bolts more difficult to remove than they were to tighten. Since achieving a specific torque value is not a cause for concern in loosening, the operator can increase the FRL air pressure at or near its maximum, giving the live tool nearly full. A steering control is changed to loosen. The operator applies the tool 10B to the application and positions an inner clamp bushing 16 on the tightened nut 36 and an outer reaction socket 17 on the snap washer 1. The operator pulls the speed selector 400 up, the tool is activated 10B and continue to loosen the tight nut 36 until it can be turned by hand and reacts off the snap washers 1. The operator shifts the speed selector 400 to the HSLT position to remove the nut 36. Remember that the vibration force mechanism can be activated when the nut is tightened to spray dry corrosion before applying full torque to the loosening nut. . This results in less torque required to loosen the industrial threaded fastener, and dry spray grease does not accumulate or concentrate on portions of threads.

Note that the portions of this specification associated with Figures 16-23 provide an in-depth discussion of the HYTORC Z® Gun and related tools.

HYTORC® Z® Caequillos. The benefits of the Z® washer are optimized when used with HYTORC® Z® bushings that have double tightening coaxial action and reaction. The outer sleeves react on the Z®s washers and the inner sleeves rotate the heads of adjacent nuts or bolts (on top) of the washers. Several proprietary HYTORC® dual sleeve systems of the present invention do exactly the same. First and foremost, the Z® Gun that has a Z® Socket is the fastest and easiest way to get the full benefits of this backlash-free technology.

Portions of the outer sleeve surround the Z® washer and rotatably engage with knurls on the torque tool housing. The inner bushing connects to the tightening tool and turns the nut. The impact action of the Z® gun loosen quickly and then effortlessly switch to torque controlled mode as they react against the Z® washer. There are no external compression points or unwanted side loads. For the first time controlled torque is possible with an air tool, without sacrificing speed and flexibility. These proprietary bushing mounts exceed all applicable ANSI standards for toughness and safety and come in a wide range of inch (cm) and metric sizes to suit any job.

Applicant discloses important features about washers in its HYTORC WASHER ™ related patent filings. The washers placed in the load path rotate with the nut (or head bolt) or remain immobile; The washers never rotate in the opposite direction to the nut due to face friction and load compression. Applicant's innovation determined the efficiency of the inline washer reaction. Despite the friction benefits of the threaded insert, the HYTORC WASHER ™ is viable because of this observation.

Generally the joints to be closed of the present invention are tightened by means of a bolt and a nut. The bolt, which has a hardened washer adjacent to its head bolt, is inserted through holes in the joint. The nut, which has an adjacent attachable geometrically hardened washer, is screwed onto the bolt. An internal action bushing turns the nut and tightens the joint and an external reaction bushing transfers the reaction force from the tool to the geometrically coupled hardened washer. As the action torque to the joint increases, the reaction force of the action torque increases proportionally. The rotatably coupled outer bushing is geometrically coupled with the hardened washer which eliminates rotation of the tool relative to the operator due to reaction force.

Figures 5A, 5B and 5C are perspective views of the double tightening coaxial action and reaction assembly 15. Figure 5A is an assembled cross-sectional perspective view. Figure 5B is an assembled perspective view. Figure 5C is an exploded perspective view. FIG. 5D is a planar cross-sectional view of the double tightening coaxial action and reaction bushing assembly 15 on the tight fitting 30.

In HSLT mode, as shown in Figures 3A and 3B, the bushing assembly 15 is substantially for transferring a vibrated form of a turning force to the nut 36 and the washer 1 in one direction. In LSHT mode, as shown in Figure 3C, the results of which are shown in Figures 4A and 4B, the bushing assembly 15 is substantially to transfer a multiplied form of turning force to the nut 36 at a direction and the corresponding multiplied shape of a reaction force in another direction to the washer 1, which acts as a stationary object.

Referring to FIG. 5A, inner clamp bushing 16 includes inner rim 52 with nut or bolt head engagement means 51. Outer reaction bushing 17 has a lower inner edge 62 with a washer engaging means 61 for engaging the outer edge of washer 4, or outer sleeve engagement means 9. The inner clamp sleeve 16 is positioned substantially within outer reaction sleeve 17. They are coupled to each other through a socket engagement means 18. The sockets rotate cooperatively and relatively in opposite directions through the tool housing. The lower inner edge 62 and its a washer engaging means 61 and outer edge 4 of washer 1 and its outer sleeve engaging means 9 are substantially vertical. The outer reaction bushing 17 includes a lower outer edge 63 having an inwardly sloping conical surface towards a lower portion of the lower inner edge 62. A lower face 54 of the inner bushing 16 rotates in and / or on an upper face 64 of a lower inner edge 65 of outer bushing 17. Note that bushing coupling means 18 is designed for use with HYTORC® hydraulic square tightening tools. Note that Bushing Coupling Means 18A are designed for use with HYTORC® Pneumatic and Electric Torque Guns such as Tool 10A (and 10B).

The washer 1 has, among others, the annular radius R_1A, lobe radius R_1L, knurling radius R_1K and a center hole radius R_1V. Washer 1 has a height H_1W, a first beveled height H_{1 B}¡, A second beveled height Hibü, a knurled height H_1K and a beveled angle Nut 36 has a hex radius R_36N and a height H₃₆n- The outer reaction bushing 17 has a washer engagement radius Ri₇w including a washer / outer gland gap width Gi_TO assisting the outer reaction bushing 17 in the easy coupling washer 1. A gap space 19 having a clearance height H_1Lprovides sufficient clearance between the inner and outer bushings 16 and 17. The inner bush 16 is free to rotate on the upper face 64.

Note that any suitable mating geometry will be made, such as that disclosed in HYTORC® patents and patent applications incorporated herein by reference. But take into account US Patent Number 8,631,724, which has a publication date of January 21, 2014, entitled LOCKING BUSHES, WASHERS, AND FASTENERS USED WITH WASHERS AND LOCKING BUSHINGS, a full copy of which is incorporated herein by reference. The outer sleeve engaging means of the '724 patent does not engage the outer surface of a washer, but merely an outer edge portion, thereby increasing the chances of failure.

The outer reaction socket 17 of the tool 10A is free and inactive in HSLT mode. It is not knurled coupled with the rotary force multiplication mounting housing 200. The impact force and / or vibration transmitters of the vibrating force assembly 300 are knurled coupled to an output pinch shaft, which rotate the bearing bush. inner tightening 16 to tighten and loosen nut 36 on fastener 20. The outer reaction bushing 17 of the tool 10B, however, is rotatably and geometrically coupled with the washer 1 under the nut 36. By supporting the nut 36 ', the compressed washer 1' serves as the immobile object by which the housing of the rotary force multiplication assembly 200 reacts through the reaction bushing 17. With the rotary force multiplication assembly housing 300 still retained, the rotary force multiplication transmitters tighten the input nut 36 through the rotary force output tightening shaft.

During the operation of any embodiment of tools having reaction sleeve assemblies of the present invention, the clamping sleeve rotates either a nut or bolt head. During operation of one embodiment of such a tool the reaction bushing is still in HSLT mode. During operation of another embodiment of such a tool the reaction sleeve rotates in the same direction as the clamp sleeve in HSLT mode but remains stationary in LSHT mode. And during the operation of another embodiment of such a tool the reaction sleeve either stops or rotates in the opposite direction with the clamping sleeve in HSLT but remains stationary in LSHT mode.

In other words, the clamp bushing is always operatively connected to either the bolt or locknut during all torque modes from low resistance to high resistance. And the reaction socket is either: operatively connected to the housing and the coaxial reaction surface to transfer a reaction force to the coaxial reaction surface during the higher resistance torque mode; operatively connected to the housing and the coaxial reaction surface either during the torque mode of least resistance or in the intermittent force mode; or operatively connected to the housing and operatively disconnected from the coaxial reaction surface either during the torque mode of least resistance or in the intermittent force mode.

In other words, a power torque tool of the present invention includes: a tightening means for connecting with a tightening socket of a double tightening coaxial action and reaction socket assembly to turn a nut or bolt head; a reaction means for connecting with a reaction bushing of the double tightening coaxial reaction and action bushing assembly to transmit the reaction force to a washer; a connection means between the clamping and reaction means; at least two modes of operation including a high speed low torque mode and a low speed high torque mode; wherein the clamp bushing is rotated in one direction by the clamping means, during the low speed high torque mode and the high speed low torque mode; wherein the reaction bushing is rotated in one direction when the connecting means between the tightening and reaction means is activated in high speed low torque mode, but the washer does not rotate when the connecting means is deactivated in low mode high torque speed.

And in other words, a power torque tool of the present invention includes: a tightening means for connecting a tightening sleeve to a nut or bolt head; a first reaction means and a second reaction means for connecting a reaction socket to a washer; at least two modes of operation - a high speed low torque mode and a low speed high torque mode; wherein the clamping sleeve is rotated by the clamping means during both modes to rotate the bolt or locknut; wherein the reaction bushing connects to a washer under the bolt or locknut; a first reaction means that stops said reaction bushing from rotating in low speed high torque mode while the washer recovers a reaction force of greater magnitude; and a second reaction means that stops the reaction bushing from rotating in high speed low torque mode while an operator recovers a reaction force of lesser magnitude. In this case, a rotary force multiplication assembly that houses the knurled adapter is the first reaction medium. And an arm shift mode shift mount that has a knurled adapter is the second means of reaction.

The dual bushings, particular reaction sleeves (bushings), of the present invention have been developed for use in combination with all HYTORC® electrical, hydraulic and pneumatic torque / tension systems. They were necessary to reduce the outside diameters of the reaction sleeves to provide maximum clearance between the tool reaction systems and the surrounding fastener environments. By reducing the outside diameters of the required reaction sleeves they reduce the outside diameters of the action sleeves as well.

Generally, numerous part geometries have been devised for the adapter sleeves, bushings, and rings of the present invention. All components were possible prototypes and experimentally evaluated at the HYTORC® research and development center. Quality testing includes subjecting parts to their particular application load for countless cycles. Various materials and heat treatment alternatives were also evaluated experimentally.

Note that the portions of this specification associated with Figures 16-23 provide additional discussion of HYTORC Z® glands.

HYTORC® Z® Washer - Radial Fastener Coupling Differential. In torque tools with prior art reaction accessories, the reaction torque is equal to and opposite to the action torque. But the reaction force applied by the reaction arm is much higher on an immobile object nearby. The reaction force is multiplied by the distance, the length of the reaction arm. In fact the lateral load or reaction coupling force, for a tool can oscillate from 2x to 4x its torque output at the assembly points a distance of, for example, Vi foot (0.15 meters) from the axis of force of twist tightening. Whose greater reaction force is concentrated in just that location. Naturally the shorter reaction arms transfer less reaction coupling force to the coupling points closest to the axis of force of rotation of the clamp. It stands to reason that an extremely short reaction arm would transfer a reaction coupling force of similar magnitude, albeit slightly larger, than the torque tool output because the coupling point is very close to the force axis of twist tightening.

Thread irregularities produce adverse bolting characteristics. Among other drawbacks, side loading causes the nut and bolt threads to engage with enormous force on the near side where it is applied such that dry grease piles up there when the nut is turned. Often only small fractions of total threaded surface areas will engage between the bolt and the nut. This causes the bolt threads to stray, requiring substantially more torque and thus substantially more lateral loading to loosen the nut. This chain of events often ruins the bolt and nut threads. The fastener locks or binds at the point where all the turning force is used by thread friction, which can lead to breakage of the fastener or tool when rotating.

The mechanical torque tool originally used to tighten the fastener is often insufficient to loosen the corroded fastener itself. Such corroded fasteners may require loosening torque values ​​ranging from 2x to 4x greater than the tightening torque required by a more powerful tool for breaking loosening. High temperature bolting applications, such as turbines and frames, are often critical requiring either precision or stainless steel fabricated fasteners with extremely high replacement costs. In addition, the use of fine thread bolts, which is very popular in recent times, multiplies this problem.

Likewise, the reaction torque is equal to and opposite to the action torque in the HYTORC® Double Tighten Coaxial Reaction and Action Bushing Assembly. But the reaction force intensification characteristic is applicable as well. Referring again to applicant's related patent disclosures HYTORC WASHER ™ and SMARTWASHER ™, these washers had radii substantially similar to that of the nut.

The reaction forces applied to these washers were of similar magnitude to that of the equal and opposite reaction torque. This helps explain why HYTORC WASHERs ™ and SMARTWASHERs ™ sometimes rotate with the bolt or locknut.

Industrial bolting professionals have recognized the need to use relatively similar fastener component sizes. In normal bolting operations it does not matter whether the cap bolt or nut is torqued. This assumes, of course, that the head bolt and the nut face are of the same diameter and where the contact surfaces are the same to produce the same coefficient of friction. If not, then it doesn't matter. In saying that the nut was flanked and the head bolt was not. If the tightening torque was determined assuming the nut was to be tightened but the cap bolt was subsequently tightened then the bolt could be overloaded. Commonly 50% of the torque is used to overcome friction under the clamping surface. Therefore, a smaller friction radius will result in more torque going into the bolt thread and therefore being tighter. If the inverse were true, that is, the torque was determined assuming that the head bolt was to be tightened and then the nut was subsequently tightened, the bolt would be under tight.

Just as an extremely long reaction arm applies an extremely greater reaction force to a nearby immobile object, an extremely long reaction arm extremely short applies a force of similar magnitude, though slightly greater, than the tool output of torque. In this regard, the outer reaction bushing 17 can be considered a 360 ° reaction arm application than the 5 reaction coupling force of similar magnitude, though slightly larger, than the torque tool output infinitely around the outer edge. 4 of washer 1. In fact, outer reaction bushing 17 applies a greater reaction engagement force to reaction washer 1 under nut 36. This can only be achieved by having a washer 1 slightly larger geometrically shaped coupling of the outer reaction sleeve 17 than a nut 36 - geometrically shaped coupling of the inner clamping sleeve 16. The applicant's fundamental observation about the washers coupled with 15 is new observation ensures a washer in which it still reacts.

Referring to Figure 5D, the outer edge 4 of the snap washer 1 extends beyond an outer edge 37 of the tightened nut 36. It should be noted that a reaction force 20 92 acting in another direction 94 received by the outer edge of washer 4 is greater than an action torque 91 acting in a direction 93 received by nut 36. The snap washer 1 absorbs the reaction force 92 from the tool 10B such that the tool 10B applies the action torque 91 to the 25 supported nut 36 'and applies a reaction force 92 slightly greater but opposite to the outer edge of washer 4. The supported nut 1 'rotates but the compressed washer 1' remains immobile. This relative positioning, that is, that the outer edge of washer 4 is further from the center of rotation, or the axis of force of rotation A₁₀, that the outer edge nut 37, is an innovative aspect of the present invention. The reaction force 92 acts through the effective lever arm of the outer sleeve 17 at a distance R_1Aaway from the axis of rotation force A₁₀, which tends to still hold washer 1. As a result of the difference in radius of the outer polygonal couplings, washer 1 remains stationary at joint 30 instead of rotating with nut 36 while fastener 20 is tightened or loosened.

Treatment means to increase the friction coefficient of the HYTORC® Z® washer. With reference to the figures. 6, this shows a bottom up view of the lower bearing face 3 formed with treatment means for increasing the coefficient of friction 60. The nut 36 is shown on the smooth upper bearing face 2. The frictional forces are lower between the nut 36 and the washer 1 in the coupling of smooth contact surfaces 2 and 38 than the coupling of the rough contact surface 3 and flange surface 30. Thus the nut 36 tends to rotate and the washer 1 tends to remain stationary.

Figures 6B, 6C, 6D and 6E explain this phenomenon. Figure 6B shows the nut 36 being torqued and compressed against the upper bearing face 2 of the washer 1. The upper bearing face 2 and a lower bearing face 38 of the nut 1 are smooth. During a tightening process, a friction force 71_rbetween the nut 36 and the washer 1 acts in a direction 92. A compression force F_n of nut 36 acts on washer 1 in a downward direction along the axis of force rotation A₁₀. A radius r is a friction radius! effective, or the distance from the axis of rotation force A₁₀ to a center of frictional area 73_r from the lower bearing face 38 of the nut 36.

FIG. 6C shows the washer 1 being compressed against bearing face 35 of joint 30. Bearing face 35 and lower bearing face 3 of washer 1 are frictionally and load-coupled. During a tightening process, a friction force 72_r between washer 1 and joint 30 acts in another direction 93. A compression force F_b joint 30 acts on washer 1 in an upward direction along the axis of rotational force A₁₀ A radius R is an effective friction radius, or the distance from the axis of rotational force A₁₀ to a center of friction area 74_R from lower bearing face 3 of washer 1.

Figure 6D shows a combination of Figures 6B and 6C. Figure 6E shows F_n and F_b. A compression force F_c generated by the nut 36 that tightens the fastener 20 is equal on both sides of the washer 1 such that F_n = F_b = F_c. The friction force (F_r) = μ * F_c, where μ is the coefficient of friction. Bear in mind that the effective frictional radius of the treatment means for increasing the friction coefficient 60, or R, is greater than the effective friction radius of the nut 36, or, such that Fe * R> Fe * r . This means that the torque to overcome the friction between the nut 36 and the washer 1 is less than the torque to overcome the friction between the treatment means to increase the coefficient of friction 60 of the washer 1 and the union 30.

Referring again to the example in Figure 6A, the treatment means for increasing the coefficient of friction 60 is shown, for example, as the radial relief knurled pattern 7, having an inner radius R₇. Radial relief knurled pattern 7 is shown located so far from the axis of rotational force A₁₀ as possible at a substantially maximum radius, R_MAx, to maximize torque (t_RMAx) while still below a compression zone of the nut 36. As the clamping force increases, the knurling pattern 7 fits itself into the flange face material 35, thereby resisting the attempt of washer 1 to rotate with nut 36. The coefficient of friction, μ, is kept constant and multiplied by the constant compressive force Fe to produce a constant frictional force (F_b). The reaction torque (t_r) is F * R. Maximum torque can be achieved at substantially maximum radius, R_Max> such that t_RMax = F * Rmax- In other words, the effective frictional radius, R, of washer 1 is greater than the effective frictional radius, r, of nut 36. The generally effective friction radius of washer

Z®s of the present invention is greater than a friction radius! effective of nut or bolt heads. Note that the principles of mechanics (static, dynamic, etc.) to describe traditional bolting applications and associated forces are well known in the art.

Explained another way, the resistance of washer 1 sliding or turning while applying reaction torque is a function of load and coefficient of friction. The following expressions represent the relationships between the sliding force, friction, load, and torque in a reaction washer:

Sliding force resistance = (coefficient of friction) x (load)

F_r = μ * F_n where: F_R = force (resistance), μ = coefficient of friction and F_n = normal force (weight or load).

In a threaded fastener the force to overcome friction and create slip or twist is a function of the applied torque and the friction radius. Thus the force to create sliding can be expressed as:

F_s = (torque) Z (Radius of friction)

Fs - t / tf where: F_R = force (sliding), τ = torque and r_F = effective friction radius. Therefore in a bra:

Fs ⁼ Fr r / r_F = μ * F_n, in such a way that:

τ = μ * r_F * F_n

The above expression shows that the sliding resistance under torque is the function of the coefficient of friction, the load and the radius of the friction surface. This effective friction radius is generally taken to be the center bore hole mean and outer bearing face radii. As the friction radius increases the resistance to sliding or turning increases. Thus, it is understood that a means of increasing the washer friction radius relative to the nut or bolt friction radius will anchor the washer relative to the nut or bolt. Because they are equal and opposite torque forces, washers and reaction nuts or bolts will always have identical applied bolt load torque forces. The coefficients of friction are identical in fasteners when similar materials and lubricants are applied throughout. By increasing the friction radius of the washer bearing face therefore, you can ensure that the washers will remain anchored relative to the nut or bolt in all clamping situations.

The washer friction radius is increased by pushing the bearing surface outward. This can be done by adding the surface features to the outermost area of ​​the bearing face, neglecting the innermost areas. Due to the high loads and common embedment of the mating surfaces only light selective surface conditioning is required to effectively increase the friction radius.

The area of ​​position and coverage of the treatment means to increase the coefficient of friction, for example, the characteristic of knurling in relief, and its relationship with the footprint of the bolt or locknut ensures the effectiveness of the Z® System. The lower surface of the washer includes externally placed coefficient of friction increasing treatments, which defines a friction portion! for mating with the joint surface. The frictional portion is positioned around an outer peripheral portion of the lower surface and extends inwardly to a width less than the full width of the washer body. The frictionally enhanced surface tends to lock the nut while maintaining bolt load, thereby preventing unintended loosening. In other words, the bottom surface of the washer is roughened in order to ensure substantial friction between the joint and the washer from tightening or loosening of the fastener. The frictional forces developed between the washer and the joint are substantial and reliable and serve to prevent unwanted rotation of the washer on the load and during the initial unloading stage.

Unexpected experimentally repeatable performance is not possible if by the frictionally enhanced surface 7 it completely covers or is placed in or relatively close to the center hole of the bottom surface 3 of washer 1. Most of the time, this configuration fails and washer 1 rotate with nut 36.

The Z® washer concept similarly works with simply an outer ring that has the coefficient of friction increasing treatments. It is not necessary to have the smooth inner portion, that is, the inner surface 3A, and a rough outer portion. But the different surface textures of the bottom side of the washer do not help with frictional thrust on the bottom surface as a whole and between the bottom and top sides of the washer.

This application is intended to define, claim and protect a reaction type washer with outwardly shifted friction zone, for example a reaction washer friction radius outer thrust relative to the nut. This produces a new, non-obvious shift of the friction surface radius that prevents the washer from turning before the nut. The prior art reaction type washer without frictional thrust tends to rotate, especially when used on hard surfaces. They were marginal in performance and performed only under ideal conditions on ideal surfaces. Spinning reaction type washers undesirably caused flange face damage, bolting maintenance operations and inefficient industrial systems and economic losses. Even the washers with external positioning of treatment means for increasing the coefficient of friction of the present invention maintain flawless flange faces, increase the efficiency of bolting and industrial system maintenance operations, and reduce economic loss.

Referring again to FIG. 5D, in relation to radial washer / fastener coupling differentials, that is, outer edge 4 of washer 1 is further from the center of rotation, or axis of force of rotation Ai₀, that the outer edge 37 of the nut 36, serves as another embodiment of treatment means for increasing the coefficient of friction of the present invention. The larger washer / flange surface area having a longer engagement radius increases face friction over the smaller nut / washer surface area having a shorter engagement radius.

Explained another way, in bolting applications of the present invention, the friction torque generated by the washer-flange surface area interaction is greater than the friction torque generated by the nut-washer surface area interaction. The washer remains stationary in such a way that it is possible to attach a non-rotatable clamping sleeve relative to the tool housing. The clamping sleeve engages the outer polygonal edge of the washer while the tightening tool is operably engaged with the nut. By tightening the washer it compresses under the nut and the tool housing is secured against rotation relative to the washer. The washer absorbs the reaction moment and reaction force from the tool housing that is opposite the tightening torque and is deflected into the compressed washer. No external reaction medium is necessary.

Figures 7A, 7B and 7C show various washer dimensions and widths of treatment means for increasing the coefficient of friction as knurled bands. Figure 7A shows a washer 1_7A with internal hole, or central hole, 5_7Afor use with an M14 bolt, a relatively small size. The knurled band 7_7A covers the majority of the surface area of ​​the lower bearing face 3_7A. However, the lower bearing face 3_7A has a hole 5_7A adjacent to smooth inner surface 3A_7A. In fact the smooth inner surface 3A is formed_7A between gap 5_7A, which accepts bra 20 and knurled band 7_7A. Washer 1_7Ahas an inner radius, r_inK₇A> an outer radius, r_0Ut7A, an inside knurling radius, r_inK7A> an outer knurling radius, r_0UtK7A, and a lobe radius, r_L7A. Similar dimensions are applicable to but not shown in Figures 7B and 7C.

Remember that HYTORC WASHER ™ and HYTORC SMARTWASHER ™ add unnecessary height to bolting applications. The thicknesses of the Z®s washers of the present invention are commonly small compared to their outside diameters. For example, the average thickness ratio H_1W to outside diameter D_1A of the washers described in the drawings is approximately 0.08 and can range from 0.04 to 0.12. Other relationships describe the Z® washers of the present invention, including: the average height ratio H_1W from the washer to the height H36N of the nut is approximately 0.170 and can range from 0.10 to 0.30; the average diameter ratio Di_TO of washer and diameter D₃₆ of the nut is approximately 1.10 and can range from 0.80 to 1.40. These proportions are provided for descriptive purposes only,

Take into account the difficulty of quantifying the significant frictional thrust characteristics of the Z® system. For example, the relative surface areas of washers and nuts (or bolt heads) will greatly affect frictional thrust results with the Z® system. Indeed, relatively small threaded fasteners can have very different ratios than relatively large threaded fasteners.

The most informative data involves calculating the effective friction radius of the washer and the threaded fastener. The Z®s washer works reliably because the coefficient of friction increasing treatments are selectively pushed away from the center bore and toward the outer edge. 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 that has a radial band of coefficient of friction increasing treatments on its underside is the center of that band. Note that this discussion correctly assumes the ideal case where the bolt load is evenly distributed under the bolt or locknut due to the use of the Z® washer.

Note that friction improvements may not be necessary in many applications, although it ensures that the washer remains immobile in all applications, regardless of: relative washer areas / clamping surface or mating radii; fastener / hardness of relative bonding material; and relative fastener / bonding surface treatments such as lubricants (Molycoat, etc.) or coatings (paint, etc.). The friction improvements became shocking at the beginning of a tightening process where little or no load is present on the pin and / or nut. This friction thrust initiates the retention of the washer at all times.

Alternatively the treating means for increasing the coefficient of friction includes ridges, polygonal surfaces, grooves, knurls, spikes, grooves, grooves, protrusions, or other projections. Other options include press fit projections, spiral or concentric rings, radial ridges or teeth, honeycomb patterns, etc. Any operation that forces the outer surface areas to have a more aggressive interaction with the flange surface such as selectively knurling, sanding, warping, milling, machining, forging, molding, forming, profiling, stamping, engraving, puncturing, bending or even just releasing internal areas is sufficient. Note that combinations of such treatment means can be used to increase the coefficient of friction. If the washer 1 - outer reaction bushing coupling 17 is slightly larger than the nut 36 - inner clamping bushing coupling 16, treatment means for increasing the coefficient of friction may also not be necessary; they can be positioned anywhere on the lower washer surface; or they may be positioned substantially beyond an effective friction radius of the bolt or locknut on the lower washer surface. To achieve the inventive properties it is even sufficient that the washer underside. The surface rubs! The opposition, however, can also be externally tapered, whereby the outer edge of the friction ring is thicker than the inner edge. However, if required, the washer and therefore its underside can also have a curvature. Particularly good results are obtained with a convex curve towards the joint. This is disclosed in US Patent Number 7,462,007, which has a publication date of December 9, 2008, entitled Reactive Push Fasteners, a full copy of which is incorporated herein by reference. Keep in mind, however, that the washers of the present invention impart non-axial thrust force to the elongated bolt.

Generally the reaction washers of the present invention for industrial bolting include: an outer shape that allows twist engagement with a torque applying device; and a bottom bearing friction surface region that is discontinuous and selectively pushed outward from the center bore. These surface friction characteristics are selectively created at the bottom of the washer and exclude any portion of the zone near the radius of the center hole. These surface friction characteristics can be created through knurling, sanding, warping, milling, machining, forging, molding, forming, profiling, roughing, stamping, engraving, puncturing or bending. Surface friction characteristics can be created by just releasing the material near the reaction washer hole. The surface friction characteristics can also be either: created with discontinuous surfaces and / or textures that appear in an outer zone or zones of the hole; and / or positioned singularly, randomly or in any array arrangement.

Alternative Z® Washer Geometries. Figures 8A to 8L show alternative shapes for washer 1. The washers of the present invention may have an outer edge (and corresponding coupling means) profiled with any suitable geometry for non-rotatable engagement with the inner edge of outer bushing (and its corresponding coupling means) profiled with a corresponding suitable or substantially identical geometry. The standard commercial form of Z® 1 washer is a flower pattern washer, which includes inwardly extending concave portions and outwardly extending convex portions that are alternately and repeatedly provided in a radial direction around a circle of imaginary reference that is centered on a central point of the washer. Figures 8B, 8E, 8G, 8H and 8I are clear derivations of such flower-shaped washers. Note that Figure 8K shows a multi-sided shaped coupling and Figure 8J shows the slot coupling, both of which can be considered flower shaped with increasing numbers of coupling teeth.

Other suitable geometries include shapes such as triangle, curvilinear triangle, square, rectangle, parallelogram, rhombus, trapezoid, trapezoid, rhombus, pentagon, hexagon, heptagon, octagon, nonagon, decagon, circle with outer projections, ellipse, or oval. Note that the outer edges of any suitable shape may be curved, rather than angular, to facilitate easy engagement with the Z® bushings of the present invention.

Figures 8D1, 8D2 and 8D3 show the embodiment of Figure 8D, Z® 1 washer₈d for use with various power tools. The perspective views of the upper and lower faces and 15 a side view, in cross section of the washer 1_SD, respectively, are displayed. Usually washer 1_8D It has an annular hexagonal shape having similar dimensions and characteristics, as shown in Figures 1A, 1B and 1C, except for a subscript 8D. The hexagonal shape of the washer 1_8D includes 20 radially extending side corners 6_8A that form a hexagon-like shape. Generally, an upper bearing face 2_8D is smooth with less surface friction and a lower bearing face 3₈d has friction enhancements, or lower corners, 7₈d with increased surface friction. Note 25 that lubricants can be used on the upper bearing face 2_8D less surface friction between it and the threaded nut 36, or any other threaded fastener. Radial bottom corners 78d increase surface friction of bottom bearing face 3₈d The side corners 6_8D although not shown, may include angular beveled faces 8₈d formed between the upper bearing face 2₈d and a side bearing face 4_8D. Such 8 beveled faces₈d can offset the outer edge portion that includes conical surfaces and mating teeth, the conical surfaces gradually slope outward and toward the lower bearing face 3₈d and side bearing face 4_8D.

Washer 1_8D has, among others, an annular radius R_8A, a lobe radius R_8L, a knurling radius R_8K and a gap radius R_8V. Washer 1_8D has a height H₈, a first beveled height H_8B¡, A second beveled height H_8B¡Í, a knurling height H₈k and a bevel angle °₈. Such 8 beveled faces_8A can help washer 1_8A in will clean a corner radius on a flange and other slack problems. In addition the chamfered faces 8 assist the external reaction bushing in rotary engagement and engagement with the washer 1. The chamfered faces 8 can also accept modifications to the outer reaction bushing 17 to allow reverse bolting applications.

Alternative placement of treatment media to increase the friction coefficient of washer Z®. Figures 8D4 - 8D10 show washer 1_8D with several iterations of frictionally pushed faces with relatively greater friction against the

ΊΑ relatively less flange surface and friction against the nut. In other words, washer 1₈d is shown with different types, sizes and locations of treatment media to increase the coefficient of friction. Note that these variations are shown with washer 1_8D but they apply to all reaction washers described in the present invention. Figure 8D4 is shown with non-friction enhancement, only a smooth underside. Figure 8D5 is shown with frictional enhancements that are scored with the underside of the washer by removing material near the center hole. Fig. 8D6 shows a relatively thin friction enhancement band formed on an outer edge portion of the bottom face. Figure 8D7 shows a relatively thick band of friction enhancements formed at equal distances from an inner edge and the outer edge portion of the bottom face. Figure 8D8 shows a relatively thin band having a 1X width of friction enhancements formed at a distance of 1X from the outer edge and 2X from the inner edge of the bottom face. Figure 8D9 shows friction enhancing means, in this case a downward sloping ring having sharp edges formed on the outer edge of the underside. Washer 1₈d5, while shown curved, imparts elongated bolt non-axial thrust force. Alternatively washer 1_8Ds may not have height variations except for sharp edges.

As shown in Figure 8D10, the washers of the present invention can also be provided with configurations for positive locking engagement with the outer reaction sleeve. Such positive locking couplings are notches formed in the outer edge of the washer 1 8d- The external reaction bushing would include corresponding coupling means to allow armless operation, and once the nut is supported, armless operation of a inverted bolting application.

The disclosures of industrial bolt-on reaction style washers having prior art friction surfaces do not discuss the importance of the location or extent of coverage of such friction surfaces. The applicant disclosed that the treatment means for increasing the friction coefficient located on any inner washer radius near the bolt or especially the lower part of the washer tends towards the movement of the washer or rotation with the nut. These strategies were marginally successful producing steel washers occasionally. In other words, more larger, full and / or inner portion friction treatments of the lower portion of washers are substantially less effective than smaller and / or outer portion friction treatments.

Alternate Fastener and Z® Socket Types for use with Z® Washer. Figure 9A shows washer 1₈d for use with a bolt having a 20A head bolt threaded into a knockout hole and HYTORC® double tightening coaxial action and reaction sleeve mounting 15. Figure 9B shows the 1sd washer for use with a flange bolt. Modified HYTORC® double tightening coaxial action cap 20B threaded into a blind hole and 15C reaction sleeve mounting. Various fastener geometries can be used with Z® System tools, parts and accessories with corresponding design changes, as shown in Figure 9B. Modified socket assembly 15C includes male fastener tightening engagement means 16C in place of action socket 16.

Reduced Z® washer surface area. Figure 10 is similar to Figure 5D except that an outer edge 4₁₀a of a snap washer 1ioa is constrained from the outer edge 37 of the tightened nut 36. It should be noted that the reaction torque force 92_10A acting in another direction 94 received by the outer edge of washer 4_10A it may be less than the action torque force 91 acting in a direction 93 received by the nut 36. The pressure washer 1i_0A absorbs reaction torque force 92_10Aof tool 10B such that tool 10B applies action torque 91 to supported nut 36 'and less reaction force can be applied 92₁₀a to outer edge of washer 4₁₀aAggressive friction improvements 7₁₀a are necessary to prevent washer 1i_0A turn with nut 36. Supported nut 36 'turns but compressed washer 1_10A' it stops. This relative positioning, that is, the friction improvement 7_10A and therefore an effective friction radius of washer 1_10A being further from the center of rotation, or the axis of rotation force A10, than an effective friction radius of nut 36, is an innovative aspect of the present invention. Reaction Force 92i₀a acts through an outer sleeve 17A at a distance R₁₀a or so far from the axis of rotational force A₁₀, which tends to keep the washer 1_10A still. As a result of the difference in the radii of effective friction, washer 1₁₀a remains stationary at junctions 30 instead of turning with nut 36 while fastener 20 is tightened or loosened. Note that the lower face 54 of the inner sleeve 16 rotates in and / or on an upper face 64A of a lower inner edge 65A of the outer sleeve 17A. In this case the inner sleeve 16 and the outer sleeve 17A may experience additional facial friction due to a larger surface area of ​​the upper face 64A.

In other words, washers that have outer edges that either co-terminate with or constrain from an outer edge of the bolt or lock nut can be used with the HYTORC® Z® System. In such cases, it is necessary for the lower surface of the washer to be formed with the treatment means for increasing the coefficient of friction to ensure that the effective friction radius of the washer is greater than an effective friction radius of the bolt or locknut. . Successful results are likely with aggressive friction enhancements, even if the reaction force received by the outer flange of washer is substantially equal to or less than the action torque received by an outer edge of the nut or bolt head. In these situations, such aggressive friction enhancements may include bumps, polygonal surfaces, couplings, knurls, pins, grooves, grooves, protrusions, or other such projections. Compensation of the treatment media to increase the friction coefficient beyond R₂₀ it is still an important feature in this case. Note that modified outer sleeve 17A requires a sophisticated design to rotatably mate and combine with washer 1. Note that modified outer sleeve 17A may also allow reverse bolt applications.

Alternative Z® Socket sizes. Figures 11A, 11B and 11C show various sizes of reaction sleeve, including outer sleeve 17n_TO that has straight walls and 17ub and 17-nc outer caps that have tapered walls These variations allow threaded fasteners and HYTORC® washer Z®s of different sizes to be used with the same Z® Gun. Other settings can be used as required.

Z® Syistem applied to HYTORC® torque tools. HYTORC® has developed slotted adapters and reaction plates to adapt the Z® System to its matrix of electrically, hydraulically and pneumatically operated torque power tool models for regular clearance, low clearance, and offset link bolted applications. Figure 12A shows socket engagement means, or slotted adapters, 18 and 18A, as discussed in relation to Figures 5A, 5B, 5C and 5D. The 18A Slotted Adapter is designed for use with HYTORC® Electric and Pneumatic Torque Guns, such as Z® Gun 10A (and 10B), as shown again in figure 12B. It is formed as an annular ring that has grooved couplings on its inner and outer sides. The inner clamping sleeve 16 and the outer reaction sleeve 17 of the double clamping sleeve 15 are cooperatively coupled to each other and relatively rotatable in opposite directions in LSHT mode through the tool housing and / or other known means and / or from owners through the bushing coupling means 18A.

As shown in Figure 12C, Grooved Adapter 18 is designed for use with Applicant's Hydraulic Torque Tools such as the HYTORC® ICE® 10C and 10D the HYTORC® AVANTI® and other such tools. It is formed as a progressive annular ring with a fused upper portion and a lower portion having a different radius. The top ring has a shorter radius and interior grooved couplings to non-rotatably engage with the reaction support grooved portions 19A and 19B of tools 10C and 10D. The lower ring has a longer radius and outer grooved couplings to non-rotatably engage with grooved portions on outer reaction bushing 16. The inner clamp bushing 16 and the double washer bushing outer reaction bushing 17 15A are cooperatively coupled together and relatively rotatable in opposite directions through tool housings and / or other known and / or proprietary means through the bushing coupling means 18.

Figures 13A and 13B show a 17B Z® reaction pad for use with the HYTORC® Stealth® 10E designed primarily for low clearance bolting applications. Reaction pad 17B is shaped to fit the dimensions of STEALTH® 10E and non-rotatably attached to the tool housing via terminals or screws. Z® Reaction Pad 17B mates non-rotatably with Z® 1 washer.

Z® Syistem applied to HYTORC® sliding link. The benefits of the Z® System are achievable with interchangeable, dual-fit displacement links, such as the 80 apparatus. The 80 link is driven by proprietary HYTORC® coaxial action and reaction torque tools, such as the HYTORC® ICE® 10C Hydraulic Torque Tool or HYTORC® Z® 10B (or 10A) Pneumatic Gun Torque Multiplier. Other such tools include HYTORC® proprietary jGUN® Single Speed, jGUN® Dual Speed ​​Plus, AVANTI® 10D and / or STEALTH® 10E. Such proprietary dual-clamp interchangeable displacement links are fully described in the following co-owned and co-pending patent applications, full copies of which are incorporated herein by reference: PCT Patent Cooperation Treaty Application Serial Number / US2014 / 035375, which has a filing date of April 24, 2014, entitled APARATO PARA

TIGHTEN THREADED FASTENERS; and US application serial number 61 / 940,919, which has a filing date of February 18, 2014, entitled APPARATUS TO TIGHTEN THREADED FASTENERS.

Figures 14A and 14B show top and bottom perspective views of the displacement tightening link assembly 80, for transmitting and multiplying torque of HYTORC® ICE® 10C to tighten or loosen a threaded fastener (not shown) on Z® washer. 1. Link 80 includes: a clamping force input assembly 81; a clamping force outlet assembly 82; and a reaction force assembly 83.

Generally, during a tightening operation, a lower knurled face of Z® 1 washer rests on a joint to be closed while a lower face of a cap bolt or nut to be tightened rests on an upper smooth face of Z® 1 washer The outer edges of the Z® 1 washer non-rotatably engage with and react in a groove of an outer reaction bushing of the reaction force assembly 83. Meanwhile, an inner bushing of the clamping force output assembly

8 2 tighten the nut and bolt head onto the Z® washer 1.

Advantageously, the offset pinch link assembly: allows access to previously inaccessible fasteners due to, for example, projecting threads, clearances and! limited obstructions; make previously unusable devices practical by tightening them electrically, hydraulically, manually and / or

pneumatically; make previously unusable viable materials feasible, such as aircraft grade aluminum; create modular components, such as increment and hex reduction torque bushings, male to female torque adapters, to meet bolt-on application characteristics; produces precise and customizable torque multiplication; controls clamping force and application of reaction force; overcomes corrosion, thread and facial deformation; prevents galling of the bolt thread; cancels side loading; ensures balanced bolt load for symmetrical joint compression; simplifies the link and tool of use; reduces the risk of operator errors; and maximizes bolting safety.

The HYTORC® Z® system is used with a HYTORC® double opposed friction washer. Using Figures 15A - 15G, it may be necessary to keep the rear bolt or locknut turning depending on the relative friction conditions at play during use of the HYTORC® Z® system. If necessary, the operator inserts a proprietary HYTORC® 85 Dual Counter Friction Washer under the counter 22 bolt or locknut. Its two opposing friction cards 86 and 87 keep the head bolt 22 rotating, especially as soon as the load begins to be applied to the bolt 24. Generally, friction discussions related to Z® Washed 1 apply to improved friction faces 86 and 87. Similar benefits, as in lower bearing face 3 of Z® washer 1, are achieved by strategically placing friction enhancements on faces 86 and 87.

In other words, a proprietary HYTORC® washer system, or double lock washer system, includes a first washer that has external reaction force engagement means and a friction face for use under a head bolt or nut. that will tighten or loosen (such as Z® 1 washer), and a second washer that has two friction faces for use under a nut or bolt head on the other side of the joint (such as, 85 double opposed friction washer) . This dual lock washer system stops the pin or bolt from rotating along, in order to control fastener thread and face friction for a better translation of torque to bolt load. Note that any of the friction coefficient increase treatments discussed in relation to the HYTORC® Z® washer are applicable to the HYTORC® 85 double opposed friction washer.

Please note that this double lock washer system can be used with any portion, any combination, or the entire HYTORC® Z® System. Remember that torque has unknown friction and tension has unknown bolt relaxation. This washer system can come in a set to eliminate uncontrollable face friction and uncontrollable side loading to improve bolt loading accuracy of torque and tension.

The HYTORC® Z® Gun (in detail). Referring to Figures 16A and 16B by way of example, these show the perspective views of tools 10A and 10B, originally shown in Figures 3A-3C as the HYTORC Z® Gun. Tools 10A and 10B include: clamp inlet and outlet mount 100; rotation of the force multiplication assembly 200; vibration force mount 300; offset mount in mode 400; and double clamp outlet and 15 reaction socket mount, or the HYTORC® Z® Socket.

Referring to Fig. 17A by way of example, this shows a side cross-sectional view of tool 10A in LSHT mode. Referring to Fig. 17B by way of example, this shows a side cross-sectional view of tool 10B in HSLT mode.

Figures 17A and 17B show the clamping inlet and outlet assembly 100 of tools 10A and 10B. The torque input components include the torque tool housing 101 which contains a torque generating mechanism 102, the sleeve assembly 103, and a switch mechanism 104. The torque switching Mechanism 102 generates the torque turning force 91 in a direction 93 to rotate the nut 36 and is shown formed as a motor tightening means that may include either a hydraulic, pneumatic, electric or manual motor. The clamping tool housing 101 is generally shown as a cylindrical body with the sleeve assembly 103, which is held by the operator. Sleeve assembly 103 includes a toggle mechanism 104 for toggling torque generating mechanism 102 between an inoperative position and an operative position, and vice versa. A rotational force input shaft 121 connects the tightening input components of the tightening input and output assembly 100 with the tightening force multiplying assembly 200 and the vibrating force assembly 300 and transfers the turning force 91 between them. A rotary force output shaft 122 includes a clamping piece 123, which may be formed, for example, as a square clamp. The turning force output shaft 122 connects the tightening output components of the tightening input and output assembly 100 with the twisting force multiplying assembly 200 and the vibrating force assembly 300 and transfers a multiplied or vibrated form of the turning force 91 between them and the double tightening reaction and outlet bushing assembly 15. In one mode of operation, a reaction force slotted adapter 443 receives the torque reaction force 92 in the opposite direction 94.

Fig. 18 is a side cross-sectional view of the twist force multiplier assembly 200 and the force vibrate assembly 300 of the tool 10A in LSHT mode. Figure 18 also shows portions of the tightening input and output assembly 100. Components not otherwise shown in other figures include the rotational force output shaft bearing 191. FIG. 19 is a is a perspective cross-sectional view of the tightening tool housing assembly 101, the tightening tool sleeve assembly 103, and related interior components of the tool 10A and the tool 10B. Figure 19 shows the clamping inlet and outlet assembly portions 100. The components shown include: a sleeve back cover 131; an adjacent rear cover 131 of gasket 137 and the rear of the housing 101; engine mount 102; an air valve assembly 132 having an outside air valve 133 and an inside air valve 134 held in place by a pin 135. The back cover 131 is attached to the rear of and held on such components in the housing 101 by the torque screws of BHCS 136. A trigger assembly 150 includes: toggle mechanism 104; springs 151; a trigger shaft bushing 152; and a trigger rod 153. Handle 103 includes: a control valve assembly 155 with a control valve 157 and a pin 156; a conical spring 161; a check valve spacer 162; O-rings 163, one formed between the control valve assembly 155 and an inner regulator housing 164 and one formed between the inner regulator housing 164 and the bottom plate 173. A mesh screen 171 is formed between the bottom plate 173 and a noise filter 172. A head socket screw 174 connects such components and bottom plate 173 having a gasket 176 to sleeve assembly 103. A pneumatic fitting 175 is extruded from bottom plate 173 and connects to inner regulator housing 164. A sleeve push button assembly 180 (not shown) allows an operator to change the direction of the turning force and includes; a push button sleeve insert 181; a push button frame 182; a spring 183; and connectors 184.

Swing force multiplication assembly 200 includes a swing force multiplication mechanism 210 in a swing force multiplication mechanism housing 201 substantially for LSHT mode that includes a plurality of swing force multiplication transmitter mounts . In the embodiments shown in Figures 17A and 17B, the rotary force multiplier assembly 200 includes five (5) multiplier transmitter assemblies 211, 212, 213, 214, and 215. It is to be understood that there are numerous known types of force multiplication mechanisms. Generally, turning force multiplication transmitter assemblies 211-215 compensate for turning force multiplication mechanism 210, a compound epicyclic gear system. A plurality of outer planetary gears may be included that rotate about a central sun gear. The planetary gears can be mounted on movable carriers which in turn can rotate relative to the sun gear. Such compound epicyclic gear systems can include outer ring gears that mesh with the planet gears. Simple epicyclic gear systems have a sun gear, ring, carrier, and planet set. Composite planetary gear systems can include mesh planetary structures, progressive planetary structures, and / or multi-stage planetary structures. Compared to simple epicyclic gear systems, compound epicyclic gear systems have the advantages of higher reduction ratio, higher torque-to-weight ratio, and more flexible settings.

211215 force multiplier transmitter assemblies may include: gearboxes; planetary gears; ring gears; solar gears; oscillation gears; cycloidal gears; epicyclic gears; connectors; spacers; slip rings; retaining rings; bushings; bearings; tapas; transmission gears; transmission shafts; positioning rods; adjustment wheels; springs; or any combination or portion thereof. The rotary force multiplication transmitters 211 to 215 may include others known as components as well. Bear in mind that the turning force input shaft 121 can also be considered a turning force multiplication transmitter; specifically it is a first stage motor sun gear of the torque multiplier transmitter 211. Rotary force multiplier assemblies are well known and are disclosed and described. An example is disclosed and described in applicant's US patent number 7,950,309, a complete copy of which is incorporated herein by reference.

Figure 18 shows more detail the portions of the rotary force multiplication assembly 200 than Figures 17A and 17B. The components of the rotary force multiplication assembly 200 shown in Figure 18 and not in Figures 17A and 17B include: a lock nut 250; a lock washer 249; a bearing 241; a housing adapter 247; a bearing spacer 252; an inner retaining ring 243; a bearing 242; a gearbox connector 248; an upper part and a lower inner retaining ring 251; an upper and lower ball bearing 246; a double sealed bearing 244; and an inner retaining ring 245.

The vibration force assembly 300 includes a vibration force mechanism 310 in a vibration force mechanism housing 301 substantially for HSLT mode that includes either one or a plurality of vibration transmitters. In the embodiment shown in Figures 17A and 17B, the vibration force assembly 300 includes two vibration transmitters, specifically shock 311 and 312. It is to be understood that there are several known vibration force mechanisms, and they often involve impact force mechanisms consisting of an anvil and a rotating hammer. The hammer is turned by the motor and the anvil has a turning resistance. Each impact imparts a hammering force, which is transmitted to the output torque.

Generally, vibration force assemblies can include vibration force mechanisms, such as ultrasonic force mechanisms that include ultrasonic force transmitters; mass imbalance force mechanisms, including mass imbalance force transmitters, or any other time-varying (load, displacement, or speed) disturbance mechanisms that include time-varying (load, displacement, or speed) disturbance force transmitters ). Additional vibration force assemblies may include: hammers; anvils; connectors; spacers; slip rings, retaining rings; bushings; bearings; tapas; transmission gears; transmission shafts; positioning rods; adjustment wheels; springs; or any combination thereof. Vibration transmitters like 311 and 312 can include other known components as well. Figure 18 also shows a plug 320.

Generally the RPM of 10A and 10b tools decrease as torque output increases. The activation or deactivation of the vibrating force mechanism 310, alternatively, may be such that when the RPMs fall below or go beyond a predetermined number, the vibrating force mechanism 310 becomes ineffective or effective. In the HSLT 310 mode vibration force mechanism a turning force is provided to the nut. In the LSHT 310 mode vibration force mechanism acts as an extension to transmit the turning force from one part of the tool to another. Note that the vibration force mechanism 310 may be located near the tool motor, near the tool outlet pinch, or anywhere in between.

In HSLT mode, the vibration force mechanism 310 always receives a turning force and turns; the housing may or may not receive a turning force; and the torque output is relatively low, so the casing doesn't have to react. Note that in the embodiments of FIG. 17A and 17B, the vibration force mechanism 310 is operatively only in a higher speed mode, such as the HSLT mode. This in turn means that at a lower speed when the torque intensifier mechanism is operable, such as LSHT mode, there is no shock and / or minimal vibration. During HSLT mode, at least two multiplier transmitters are unitary and rotate with the hammer to increase inertia and aid in the hammering motion of the impact mechanism. Note that when a fastener exhibits little or no corrosion, threading, and facial deformation and / or thread galling, the vibration force mechanism 310 may not be necessary in HSLT mode.

The action mode shift assembly 400 is substantially for shift tool 10A from LSHT mode to HSLT mode and tool 10B from HSLT mode to LSHT mode. In the embodiments shown in Figures 17A and 17B, the sliding action mode displacement assembly 400 includes: a displacer base 401; a displacer collar 442; a slotted displacer swivel 443; a slotted travel swivel 445; an external displacement ring 456; and an inner offset assembly 450. The inner shift assembly 450, as shown in Figures 17A and 17B includes: an inner shift bushing 452; an inner shift ring 453; and 454 coupling ball bearings.

The slide action mode shift mount 400 may include: manual mounts (manual sequential, non-synchronous, or preselected) or automatic (pneumatic, semi-automatic, electro-hydraulic, Saxomat, dual clutch, or continuously variable); torque converters; pumps; planetary gears; clutches; bands; valves; connectors; spacers; shift ring retaining rings; bushings; bearings; necklaces; lock balls; tapas; transmission gears; transmission shafts; synchronizers; positioning rods; squeeze wheels; springs; or any combination or portion thereof. Mode scroll components can include others known as components as well. It is to be understood that there are various known mode shift assemblies, and often involve shift components consisting of locking collars, rings, and balls.

FIG. 18 shows more details of portions of the action mode slide assembly 400 than FIGS. 17A or 17B. Additional components of offset assembly 400 shown in Figure 18 and not shown in Figures 17A and 17B include: inner retaining rings 451, 457, and 459; a lower and upper bushing 446 and 447; and displacer ring reaction terminals 458. Figure 20 is a perspective view of the mode shift assembly 400 of tool 10A and tool 10B. Figure 20 shows substantial outer portions of the mode offset assembly 400. Components otherwise not shown in other figures include: a locking shaft cap 402; a handle insert 403; a handle handle 404; an extraction handle 405; an actuator link and displacer stem 406; a pivot rod 407; a displacer extension bracket 410; SHCS 411; a displacer fastener assembly 430; a lower portion and an upper displacer link 441; a wave spring 448; and support slots 449.

Referring again to Figures 5A-5D, they show a cross-sectional perspective view of the outlet bushing assembly and double tightening reaction 15 of tool 10A and tool 10B and outlet bushing assembly and double tightening reaction. 15A of tool 10C and tool 10D.

In LSHT mode, the double tightening reaction and outlet bushing assembly 15 is substantially to transfer a multiplied form of turning force 91 to nut 36 in one direction 39 and the corresponding multiplied form of reaction force 92 in another. direction 94 to washer Z® 1, which acts as a stationary object. In HSLT mode, the double tightening reaction and outlet bushing assembly 15 is substantially to transfer a vibrated form of turning force 91 to either the nut 36 or the nut 36 and the washer 1 in one direction 93. In the mode Shown in mounting Figures 17A and 17B, the double clamp reaction and outlet bushing assembly 15 includes an inner clamp bushing 16 and an outer reaction bushing 17. The outer reaction bushing 17 is non-rotatably engageable with the reaction force displacer swivel 443 during LSHT mode. It is to be understood that there are various known coupling mechanisms for transferring rotational and reaction forces to threaded fasteners and nuts and washers thereof, including casing, grooving, and other geometries.

Tool 10A operates by means of the following in LSHT mode. The operator pulls the displacer base 401 to a forward position. The engaging / locking ball bearings 454 are disengaged from the rotary force multiplier mechanism housing 201 and engaged with the displacer slotted ring 445 within the reaction force slotted displacer swivel 443. The displacer base 401 is connected to the rotary force multiplication mechanism housing 201. The rotary force multiplication transmitters 211-215 are unlocked and released to rotate relative to each other. Operator pulling of the displacer base 401 to a rear position also engages the displacement mounting vibration force (impact) slotted ring 453 with the vibration force (impact) mechanism housing 301. This locks the vibration (shock) force transmitters 311 and 312 and thus the vibration (shock) force assembly 300. And this allows the turning force output tightening shaft 120 to be turned by the fifth Swing force multiplication transmitter gearbox 215, which is grooved-coupled with vibration (impact) force mechanism housing 301. Slotted displacer swivel 443 is grooved engaged with reaction bushing 17. And reaction bushing 17 is geometrically engaged with washer 1 under nut 36. By supporting nut 36, compressed lock disc washer 1 serves as the immobile object by which the rotary force multiplication mechanism housing 201 reacts outside the reaction sleeve 17. With the rotary force multiplication mechanism housing 201 still retained, the rotary force multiplier transmitters 211-215 tighten the bearing nut 36 through the rotary force output tightening shaft 120.

Generally the operation of the tool 10B requires the activation or deactivation of the impact mechanism 310. Sliding action mode shift assembly 400 can shift tool 10A between either: multiplier mechanism 210; impact mechanism 310; part of multiplication mechanism 210 (as, for example, one of the plurality of multiplication transmitters); part of impact mechanism 310 (as, for example, one of the plurality of impact transmitters); or any combination thereof.

Tool 10B therefore operates in HSLT mode.

The operator pushes the displacer base 401 into a forward position of the engagement / lock ball bearings 454 engaged with the rotary force multiplying mechanism housing 201 and the vibration (impact) force mechanism housing 301. Slotted displacer ring 445 disengages from inner reaction force slotted displacer swivel 443 thus, rendering it immobile and inactive. Therefore the reaction bushing 17 is immobile and inactive because it does not engage by grooves with the rotary force multiplication mechanism housing 201. With coupling / locking ball bearings 454 coupled with the vibration force mechanism housing (impact) 301, turning force multiplication transmitters 211 215 are blocked and cannot turn relative each other. Therefore the rotary force multiplier assembly 200 rotates as a unit mass through the rotary force input shaft 121. The motor 102 rotates the rotary force input shaft 121 which includes the first motor sun gear. turning force multiplication transmitter stage 211. The operator pushing the displacer base 401 to a forward position also disengages the displacement (impact) mounting force groove ring 453 from the vibration (impact) force mechanism housing 301. This unlocks the force transmitters vibration (impact) 311 and 312 and thus the vibration (impact) force assembly 300. Vibration (impact) force mechanism housing 301 is slot-coupled with fifth gearbox of swing force multiplier transmitter 215. Vibration (impact) force transmitter 312 (anvil), is slot-coupled to the turning force output tightening shaft 120, which rotates tightens or loosens the nut 36 on the pin 23 by the impact of the vibration force transmitter (impact) 311 (hammer).

Referring again to Figures 3A-3C and Figures 4A4B, in general and from the perspective of nut 36, tool 10A either tightens, loosens or tightens and loosens nut 36 in LSHT mode. And a 10B tool either tightens, loosens or tightens and loosens nut 36 in HSLT mode. In general and from the point of view of washer 1, tool 10A, in LSHT mode, either: snap washer 1 between tightening nut 36 on load pin 23 and tightening union 30 to predetermined tightening torque ; and / or compresses the washer 1 'between the supported nut 36' on the pre-loosened pin 23 'at the pre-loosened joint 30' of the predetermined tightening torque. In general and from the point of view of the washer 1, tool 10B in HSLT mode, either: compress the washer 1 'between the nut supported 21' on the preloaded pin 23 'in the pre-tightened joint 30' at the predetermined pre-tightening torque; compresses the washer 1 between the nut 36 on the pin 23 at the loosened joint 30 of the predetermined pre-tightening torque; or vibrates the snap washer 1 between the tight nut 21 on loaded pin 23 at the tight joint 30 to properly pulverize the bolt thread corrosion. Note that reference numbers with 'and represent similar force magnitudes.

During HSLT mode tool 1OB either: loosens either nut 36 or nut 36 and washer 1 on pin 23 with turning force 91 in a direction 93 to seat nut 36 'and compresses washer 1 'on the preloaded pin 23' at the pre-tightened joint 30 'with a predetermined pre-tightening torque; loosens either supported nut 36 'or supported nut 36' and compressed washer 1 'on pre-loosened pin 23' at pre-loosened joint 30 'with turning force 92 in a direction opposite 94 from the predetermined pre-loosening torque; or vibrates (impacts) the tight nut 36 on the lock washer 1 to apply vibration to properly spray the threaded corrosion. During LSHT mode the tool 10A either: tightens the supported nut 36 'on the compressed washer 1' on the preloaded bolt 23 'at the pre-tightened joint 30' with turning force 91 in a direction 93 with the predetermined tightening torque and applies reaction force 92 in the opposite direction 93 to the compressed washer 1 '; or loosen the tight nut 36 on the lock washer Γ 'on the tight pin 23 at the tight joint 30 with turning force 92 in the opposite direction 94 from a predetermined tightening torque and apply reaction force 91 in a direction 93 to the snap washer 1. Note that reference numerals with 'and represent similar force quantities.

During operation the tool 10A switches from the

LSHT to tool 10B in HSLT mode does not support nut 36 and decompresses washer 1 at the predetermined pre-loosening torque. During operation, the tool 10B changes from the HSLT mode to the tool 10A in the LSHT mode to either: 5 support the nut 36 and decompress the washer 1 with the predetermined pre-tightening torque; or proper spraying of threaded corrosion. Note that the operator uses the offset assembly in mode 400, to change the tool from the LSHT mode to the HSLT mode or vice versa, but such a change may include other known similar components as well. Note that the 400 mode shift mount is a manual shift, but it can be automatic. Likewise, keep in mind that the activation or deactivation of the vibration (impact) force assembly 300 can occur either manually or automatically. Note that LSHT mode can be changed from torque regulated to vibration assisted or vice versa, and where HSLT mode can be changed from vibration regulated to torque assisted or vice versa. Note that vibration force (shock) assembly 300 can continue to operate even if washer 1 starts or stops rotation. And note that the LSHT mode can be vibration assisted to loosen nut 36 to help overcome chemical, heat and / or lubrication corrosion and prevent threaded bolt galling.

Note that power tools for reduced galling tightening and loosening of industrial fasteners

100 According to the present invention it can also be characterized in that: the rotary force multiplication mechanism housing 201 is operatively connected with at least one rotary force multiplication transmitter 211-215; during LSHT mode at least two of the multiplying transmitters 211-215 rotate relative to each other; and during HSLT mode at least two of the multiplier transmitters 211-215 are unitary to aid the hammering motion imparted by the rotary force impact mechanism 310. During HSLT mode, pinch shaft output 10 turning force 120 and the combination of turning force multiplying assembly 200 including its housing rotates as a unit mass in the same direction. This creates the inertia that improves the torque output of the impact mechanism to overcome corrosion, tapping and facial deformation and prevent threaded bolt galling.

Methods of tightening and loosening with reduced galling of two portions relative to each other with industrial fasteners 20 of the type having the nut 36, the washer 1 and the pin 23 with a power tool (10A and 10B) of the type having: the motor 102 to generate a turning force; clamping (122 and 123) to transfer turning force 91; the turning force multiplication mechanism 210 in the turning force multiplying mechanism housing 201 for the LSHT mode including the turning force multiplication transmitters 211 25 215; the 310 Vibration Force Mechanism for HSLT which includes

101 the vibration transmitter 311, 312; clamp bushing 16 operatively connected to nut 36; reaction bushing 17: during LSHT mode, operatively connected to washer 1 to transfer reaction force 92 to washer 1; and during HSLT mode, either operatively connected to or operatively disconnected from washer 1. Such a method including: wherein the tightening includes: placing the washer 1 on a free pin end 25; place nut 36 over washer 1 at free pin end 25; loosening, in HSLT mode, either the nut 36 or nut 36 and the washer 1 at the free pin end 25 to a predetermined pre-tightening torque to the seat nut 36 and compresses the washer 1; switch from HSLT mode to LSHT mode; and tight torque, in the LSHT mode, supporting the nut 36 at a predetermined tightening torque and presses the washer 1 between the tight nut 36 and the tight fitting 30; wherein loosening includes: positioning tool 10A during tightening of nut 36 and snap washer 1; loose torque, in LSHT mode, tighten nut 36 on snap washer 1 to a predetermined tightening torque; switch from LSHT mode to HSLT mode; and tightening, in HSLT mode, either supported nut 36 or supported nut 36 and compressed washer 1 on the free pin end 25. The loosening method further includes: vibrating, in HSLT mode, tightening nut 36 over the pressure washer 1 to apply vibration to spray the threaded bolt corrosion; and switch from HSLT mode to

102 by LSHT.

Tools 1OA and 1OB, above, and tools 10F, 10G, 10H, and 101, below, are generally describable as power tools for reduced galling tightening and loosening of an industrial threaded fastener of the type having a coaxial reaction surface, a pin and either a nut threadably engaged with the pin or a pin head connected to the pin. Tools 10A, 10B, 10F, 10G, 10H, and 101 include: a motor for generating a turning force; a squeeze to transfer the turning force; a turning force multiplication mechanism in a housing that includes a turning force multiplication transmitter for all torque modes from least resistance to greatest 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.

Alternatively, tools 10A and 10B, above, and tools 10F, 10G, 10H, and 101 below, are describable as power tools for reduced galling tightening and loosening of an industrial fastener of the type having a nut, a washer, and a pin. , tools including: a motor to generate a turning force; a squeeze to transfer the turning force; a turning force multiplication mechanism in a housing that includes a turning force multiplication transmitter for a continuous torque mode; a force mechanism of

103 vibration that includes a vibration transmitter for either: an intermittent torque mode; an intermittent force mode; or both intermittent torque mode and intermittent force mode.

Referring to Figure 21A by way of example, this shows a cross-sectional view of an embodiment of the present invention as tool 10F, a power tool for tightening and loosening with reduced galling or both tightening and loosening of an industrial threaded fastener. 801 of the type having a pin and nut threadably engageable with the pin. Tool 10F includes: a clamp inlet and outlet assembly 810; a turning force multiplication assembly 820; a vibration force assembly 830; a mode shift mount 840; and a torque arm mounting and clamping outlet bushing 850.

Referring to FIG. 21B by way of example, this shows a cross-sectional view of an embodiment of the present invention as the 10G tool. The 10F and 10G tools are similar as seen by duplication of reference numbers. The 10G tool is a torque armless power tool for tightening and loosening with reduced galling or both tightening and loosening of an 802 industrial threaded fastener of the type having a coaxial reaction surface, such as HYTORC® Z® 1 washer , a pin and a nut that can be threadedly engaged with the pin. Tool 10G includes: a clamping inlet and outlet assembly 810; a montage

104 turning force multiplication 820; a vibration force assembly 830; a mode shift mount 840; and dual clamp outlet and 855 reaction socket assembly, which is similar to HYTORC® Z® Socket 15.

Tools 10F and 10G include a rotary force multiplying mechanism with either one or a plurality of gear stages. A vibrating force mechanism includes: a turning force impact mechanism having a hammer and anvil; and an intermittent force mechanism 860 of either: an ultrasonic force mechanism including an ultrasonic force transmitter; a mass unbalance force mechanism including a mass unbalance force transmitter; or any other time-varying (load, displacement, spin, or speed) tampering mechanism that includes a time-varying (load, displacement, turn, or speed) disturbance force transmitter. Tool 10F represents a modified HYTORC® THRILL® Gun that includes the 860 Intermittent Force Mechanism. Tool 10G represents a modified HYTORC® Z® Gun that includes the 860 Intermittent Force Mechanism.

Referring to Fig. 22A by way of example, this shows a cross-sectional view of an embodiment of the present invention such as the 10H tool, a power tool for tightening and loosening with reduced galling, or both tightening and loosening of a threaded fastener. Industrial 901 of the type having a threaded pin and nut

105 with the pin. Tool 10H includes: a clamp inlet and outlet assembly 910; a turning force multiplication assembly 920; a vibration force assembly 960; a mode shift mount 940; and a torque arm mounting and clamping outlet bushing 950.

Referring to Fig. 22B by way of example, this shows a cross-sectional view of an embodiment of the present invention as tool 101. Tools 10H and 101 are similar as seen by the duplication of reference numerals. Tool 101 is a torque armless power tool for tightening and loosening with reduced galling or both tightening and loosening of a 901 industrial threaded fastener of the type having a coaxial reaction surface, such as HYTORC® Z® 1 washer , a pin and a nut that can be threadedly engaged with the pin. Tool 101 includes: a clamp inlet and outlet assembly 910; a turning force multiplication assembly 920; a vibration force assembly 960; a mode shift mount 950; and the double clamp outlet and 955 reaction socket assembly, which is similar to HYTORC® Z® Socket 15.

Tools 10H and 101 include a rotational force multiplication mechanism with either one or a plurality of gear stages. A vibrating force mechanism 960 includes either: an ultrasonic force mechanism that includes an ultrasonic force transmitter; a force mechanism of

106 mass unbalance including a mass unbalance force transmitter; or any other time-varying (load, displacement, spin, or speed) tampering mechanism that includes a time-varying (load, displacement, turn, or speed) disturbance force transmitter. Tool 10H represents a modified HYTORC® jGUN® Double Speed ​​Plus that includes the 960 intermittent force mechanism. Tool 101 represents a modified HYTORC® jGUN® Double Speed ​​Plus that includes the 960 intermittent force mechanism and the double tightening output and 955 reaction socket assembly, which is similar to HYTORC® Z® Socket 15.

In addition to tools 10A, 10B, 10G and 101 the clamping sleeve is operatively connected with the nut. The reaction bushing may be operatively connected to the housing and the coaxial reaction surface during the torque greater resistance mode to transfer a reaction force to the coaxial reaction surface. Alternatively, the reaction bushing may be operatively connected to the housing and the coaxial reaction surface or operatively connected to the housing and operatively disconnected from the coaxial reaction surface either during the least resistance torque mode or the intermittent force mode. . The clamp bushing is shown as an inner bushing and the reaction bushing is shown as an outer bushing.

The following discussion refers to tools 10A, 10B,

107

10F, 1OG, 1ΟΗ and 101. Note that to facilitate the description of any reference to a nut or fastener, it includes the possibility of: a head with a pin attached to a pin; with head attached to the pin and a washer on the pin. Note that any suitable fastener geometry can be used with the present invention, such as: an Alien key connection; a shoulder screw socket head (SSC); a round socket head screw (SHBS) head; a hex socket head screw (HHCS); a slotted round head screw (RHSB) head; a head of the flat head torx screw (FHTS); a socket head screw (SSS); or a socket head socket screw head (SHCS).

These discussions describe the coaxial reaction surface as a washer. In some cases, however, the washer may be formed either integral with or attached to a joint that will tighten or loosen. In other cases, the coaxial reaction surface is a portion of the bolt that extends beyond the nut. In still other cases, a coaxial reaction arm may be butted against a viable and accessible immobile object for tightening and loosening with reduced galling.

Washer 1 is generally shown as a

108 flower with knurled underside to provide reaction torque. By means of Figures 8A-8L, take into account the suitability of almost any external shape that non-rotatably engages with the reaction bushings, plates and links of the present invention. Also take into account the suitability of almost any surface feature that increases facial friction. Examples of external shapes include: any suitable geometric shape such as pentagon, hexagon, octagon, etc .; pressed holes; cuts; battlements; etc. Examples of surface friction enhancing characteristics include: patterns; finishes; treatments; coatings; plated; roughness; etc. inventively even before bearing of the nut and / or head bolt, the coaxial reaction surface becomes a viable and accessible coaxial immobile object into which the reaction forces of the tools are transferred.

Generally tools 10A, 10B, 10F, 10G, 10H, and 101 can do any of the following during intermittent force mode. Tools can loosen the nut or nut and washer with intermittent twisting force in one direction. Tools can loosen the nut or nut and washer with intermittent turning force in an opposite direction. Or the tools can either impact, vibrate or both impact and vibrate the nut or nut and washer, either with intermittent turning force to apply vibration and turning in the opposite direction, intermittent vibration force to apply vibration, or

109 both.

More specifically the 1OA, 1OB, 1OF, 1OG, 1OH and 101 tools can do any of the following during intermittent force mode. Tools can up-torque the nut or nut and washer with intermittent turning force in one direction to support the nut from a restrictively rotating state with significant adverse bolting application characteristics to a predetermined pre-torque state and compresses the washer between a union to be tightened and the nut sat. The tools can tighten the nut or nut and washer with the intermittent turning force in the opposite direction so as not to support the nut from the predetermined pre-tightening torque state to the restrictively rotatable state with significant adverse bolting application characteristics and decompresses the washer between the joint to be loosened and the unsupported nut. Either the tools can impact, vibrate, or both the nut and washer with intermittent twisting force to apply vibration and twisting in the opposite direction, intermittent vibration force to apply vibration, or both, from an improperly sprayed threaded corrosion state to a suitably pulverized threaded corrosion state. For example, tools can generate ultrasonic sound waves through an ultrasonic wave generator, such as the 960 Vibration Force Mechanism, to vibrate the fastener at ultra high speeds to spray the

110 threaded corrosion.

Often times, intermittent force (impact, vibration, ultrasonic, etc.) is required in loosening to firmly compress the washer between the nut and the flange face. In the absence of this impact the compression caused by the washer could not have the reaction force due to the two frictions of the two faces of the washer. When properly compressed, the washer face that engages the nut receives clockwise rotation friction due to the torque output from the tool and an equal and opposite counterclockwise rotation friction due to the reaction force. Such as, the rotating friction of the washer face that butts together the flange face prevents the washer from turning. In other words, the tool is designed to hold the washer stationary while turning the nut, which eliminates common side loading and nut-to-nut surface differences. Better control of thread and surface friction is achieved for improved translation of torque to fastener load.

Generally the 10A, 10B, 10F, 10G, 10H, and 101 tools can perform any of the following during the highest torque torque mode. Tools can tighten the nut with a lower speed, higher torque turning force in one direction, and apply a reaction force in an opposite direction to the washer. And / or tools can down-torque the nut with the lower speed, higher torque turning force in the opposite direction and apply the reaction force

111 in one direction to the washer.

More specifically the 1OA, 1OB, 1OF, 1OG, 1OH and 101 tools can perform any of the following during the highest strength torque mode. Tools can tighten the nut with the lower speed, higher torque turning force in one direction to tighten the nut from the predetermined pre-tightening torque state to a predetermined tightening torque state and apply the reaction force in the opposite direction to the washer to pressurize the washer between a loosened joint and the tight nut. And / or tools can down-torque the nut with lower speed, higher torque turning force in the opposite direction to loosen the nut from the predetermined tightening torque state to the predetermined pre-tightening torque state and apply the force of reaction in one direction to the washer to depressurize the washer between the loosened joint and the loosened nut.

Generally the 10A, 10B, 10F, 10G, 10H and 101 tools can perform any of the following during the least resistance torque mode. Tools can loosen nut or nut and washer with higher speed, lower torque turning force in one direction. And / or tools can tighten the nut or nut and washer with higher speed, lower torque turning force in the opposite direction.

More specifically the 10A, 10B, 10F, 10G, 10H and 101 tools can perform any of the following during the

112 least resistance torque mode. Tools can loosen the nut or nut and washer with higher speed, lower torque turning force in one direction to support the nut from a freely rotatable state with negligible adverse bolting application characteristics to the pre-torque state default and compress the washer between the joint to be tightened and the supported nut. And / or tools can tighten the nut or nut and washer with the higher speed, lower torque turning force in the opposite direction so as not to support the nut from the predetermined pre-tightening torque state to the freely rotatable state with application characteristics negligible adverse bolting and decompress the washer between the union to be loosened and the unsupported nut.

Generally the tools 10A, 10B, 10F, 10G, 10H and 101 can tighten, loosen or tighten and loosen the nut in the higher resistance torque mode. Tools can tighten, loosen, or impact the nut or nut and washer in the intermittent torque mode or the least resistance torque mode. Tools can be switched from intermittent torque mode to higher strength torque mode by supporting the nut and compressing the washer to the predetermined pre-torque state and / or proper spraying of threaded corrosion. The tools can switch from the higher resistance torque mode to the intermittent torque mode and / or the lower resistance torque mode by not supporting the nut and decompressing the washer in the torque state

113 pre-loosening. The tools can change from the least strength torque mode to the highest strength torque mode by supporting the nut and compressing the washer in the predetermined pre-tightening torque state.

In operation the tools can change: from the higher resistance torque mode to the intermittent torque mode; from the highest resistance torque mode to the lowest resistance torque mode; from least resistance torque mode to intermittent torque mode; from the least resistance torque mode to the highest resistance torque mode; from intermittent torque mode to higher resistance torque mode; or from intermittent torque mode to least resistance torque mode.

The activation or deactivation of the vibration mechanism or the torque multiplication mechanism can occur manually or automatically. Thus, the switching mechanism can be manual or automatic. Furthermore, the switching mechanism and therefore any mode or combination of modes and corresponding mechanisms can be activated automatically in accordance with an observed load on the fastener. For example, a reduced galling power tool of the present invention may need vibration and / or impact to pulverize corrosion into a tight lock and tighten or loosen the nut at high speed. The torque-tight nut cannot be tightened with just vibration and / or impact. An operator may need to activate vibration and / or impact to spray dry corrosion onto the tight fitting nut.

114 torque, which can occur independently of or in combination with the torque multiplying mechanism. As noted, the torque required to loosen the nut is greater than the initial tightening torque since the lubrication has dried up or is gone, corrosion is present, and the pin is still loaded and tensioned. In other words, the highest torque values ​​are taken to unload and release the pin. Once the nut is loosened it can be turned at a higher speed, or tightened, during the least resistance torque mode and / or intermittent torque mode. The nut, however, may have to be freed from corroded and / or damaged or defective pin threads. This often requires vibrating and / or intermittent force in combination with the torque multiplying mechanism. Loosening the nut rotates at a higher speed during low resistance torque mode and / or intermittent torque mode. Also in this case, the least resistance torque mode may only be insufficient to overcome corroded and / or damaged or faulty pin threads. Similarly, this often requires vibrating or intermittent force and / or intermittent force in combination with the torque multiplying mechanism. The present invention solves these problems.

Methods of tightening and / or loosening with reduced galling of an industrial threaded fastener of the type having a coaxial reaction surface, a pin, and either a nut threadedly engagable with the pin are generally disclosed.

115 or a pin head connected to the pin with a non-torque arm power tool of the type having: a motor for generating a turning force; a squeeze to transfer the turning force; a turning force multiplication mechanism in a housing that includes a turning force multiplication transmitter for all torque modes from least resistance to greatest resistance; and at least one vibration force mechanism including a vibration transmitter for intermittent force mode during all torque modes from low resistance to high resistance. The tightening method includes: loosening in one direction either the nut, the pin head, the nut and the coaxial reaction surface or the pin head and the coaxial reaction surface; and torque tightening in one direction either the nut or the pin head while reacting in the opposite direction away from the coaxial reaction surface. The loosening method includes: loosening torque in the opposite direction of either the nut or the pin head while reacting in a direction away from the coaxial reaction surface; and tightening in the opposite direction either the nut, the pin head, the nut and the coaxial reaction surface or the pin head and the coaxial reaction surface.

The following discussion pertains to non-torque arm power tool configurations for reduced galling tightening and loosening of industrial fasteners in accordance with the present invention. Bear in mind that the terms

116 they are interchangeable, such as: intensifier, multiplier, and multiplication; impact and impact.

More specifically, in one embodiment of the impact mode, the tool housing and gear stages stop while the impact rattles. When the impact mechanism is distant from the motor, a motor shaft passes through the center of the multipliers to the impact mechanism and from there to the output torque. When the impact mechanism is immediately after the motor and in front of the multipliers the motor drives the impact mechanism and a shaft goes from the impact mechanism through the center of the multipliers to the output torque

In another embodiment of the impact mode, the tool housing and gear stages rotate in unison while the impact rattles as the gear steps are locked. This can be achieved by connecting either: the sun gear with the ring gear; the sun gear with the gearbox; or the gearbox with the ring gear of a planetary stage. In each case, all gearboxes and casing act as a turning extension from the motor to the impact mechanism or from the impact mechanism to the tool output torque.

In another embodiment of the impact mode, the tool housing stops and the gearboxes rotate in unison while the impact rattles as the gearboxes lock together. When the impact mechanism is distant from the engine, the gearboxes act as an extension inside the

117 motor housing to the impact mechanism. When the impact mechanism is immediately after the engine and in front of the gearboxes or gearbox multipliers it acts as an extension into the interior of the impact mechanism housing to the output tightening of the tool.

Generally during LSHT mode at least two multiplier transmitters rotate relative to each other. In multiplier mode, the tool housing always rotates opposite the sun gears and the output shaft of the multipliers, so the tool housing has to react. When the torque is increased by the multiplier, the turning speed is so slow that the impact mechanism is ineffective. If the impact mechanism is located after the multiplier and close to the tool output torque, the impact mechanism will not impact if it rotates with the last sun gear. If the impact mechanism is located before the multiplier and close to the motor, the impact mechanism rotates at high speed and needs to be blocked.

In a mode where the impact mechanism is distant from the motor, the following occurs: the impact mechanism stops while the multipliers rotate; the motor's output shaft goes to the multiplier for torque multiplication; and the last sun gear extends through the impact mechanism to the output torque. When the impact mechanism is immediately after the motor and in front of the multipliers,

118 The output shaft of the motor passes through the impact mechanism to the multiplier for torque multiplication and the last sun gear is extended to the output torque.

In another embodiment, the impact mechanism is rotated at the speed of the last sun gear of the force application multipliers. When the impact mechanism is distant from the motor, the motor output shaft goes to the multiplier for torque multiplication and the last sun gear rotates the impact mechanism, which turns the output shaft of the tool. When the impact mechanism is immediately after the motor and in front of the multipliers, turning the impact mechanism to rotate the multipliers will result in an impact, which is to be avoided. On the other hand, the impact mechanism can be locked by locking the hammer with the impact casing, or by locking the hammer with the anvil. The impact mechanism acts as an extension between the motor output torque and the multiplier's first sun gear.

The speed of the last sun gear of the multiplier can be high enough to operate the impact mechanism. Impact on the output shaft of the tool is preventable by locking the hammer with the impact casing, the hammer with the anvil, the impact casing with the tool casing or the hammer with the tool casing.

In a specific mode of the LSHT mode, the multiplying mechanism is close to the engine and before the transmission mechanism.

119 impact. The motor bypasses the multiplier mechanism and extends its output force through at least a part of the multiplier mechanism by means of a stem to the output torque. In another specific embodiment of the LSHT mode, the impact mechanism is close to the engine and before the multiplier mechanism. The impact mechanism extends its output force through at least a part of the multiplication mechanism by means of a rod towards the output clamp.

The power tool for the reduced galling tightening and loosening of industrial fasteners according to the present invention is described herein as having two or three modes, the lower speed higher torque mode, the lower speed torque mode. higher speed and intermittent force mode. It is to be understood that at least two modes, as described herein, are merely examples. Additional modes may be added to one or the other modes and / or the input and / or output means. It is to be understood that the present invention is not limited to simply two speeds, but can have multiple speeds. For example, known torque intensifier tools are generally driven by air or electric motors. Often times the power output and rotational speeds of such motors are increased or decreased by means of planetary gears or the like, which can become part of the motor. Often known torque intensifier tools temporarily remove one or more of the intensifier media

120 to increase the rotational speed of the tool motor. Other known torque intensifier tools use gear intensification and / or reduction mechanisms as independent components or adjacent to the motor to increase and / or decrease shaft rotational speed. The present invention may also include such gear intensification and / or reduction mechanisms as independent components, as gearbox transmitters and part of gearbox 210 or as vibration transmitters and part of vibrate 310. In effect, the assembly of Multiplication 200 can be configured to have multiple multiplier transmitters housed in multiple multiplier mounting housings.

It will be understood that each of the elements described above, or two or more together, may also find a useful application in other types of constructions that differ from the types described above. The features disclosed in the foregoing description, or the following claims, or the accompanying drawings, expressed in their specific forms or in terms of a means to perform the disclosed function, or a method or process to achieve the disclosed result, as appropriate, it may, alone, or in any combination of such features, be used to carry out the invention in various forms thereof. Note that there may be slight differences in the descriptions of the numbered components in the specification.

121

Although the invention has been illustrated and described as embodied in a fluid-operated tool, it is not intended to be limited to the details shown, as various modifications and structural changes can be made without departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will thus fully reveal the essence of the present invention that others can, applying current knowledge, easily adapt for various applications without omitting features that, from the point of view of the prior art, quite constitute essential features of the generic or specific aspects of this invention.

When used in this specification and claims, the terms comprising, including, having, and variations thereof mean that specified features, steps, or integers are included. The terms should not be construed to exclude the presence of other characteristics, stages, or components.

122