REACTION WASHER, FIXING SOCKET ASSEMBLY, THREADED FIXER FOR OBJECT FIXING, REACTION TORQUE POWER TOO

专利摘要:
reaction washer, fixing socket set, threaded fastener for fixing objects, reaction torque tool with free arm to tighten, loosen or tighten and loosen a threaded fastener and method for tightening, loosening or tightening and loosening, with reduction seizing. the present invention relates to the applicant's system (hytorc® z®), belonging to the field of tools, comprising: washers (1), located under nuts (36) and screw heads (22) of various types; pistols (10) with impact mechanism and a torque multiplier combining rapid descent with calibrated torque; sockets (15) with external (17) and internal (16) gloves; grooved adapters and reaction plates for reverse compatibility with torque / voltage systems (hytorc®), including square drive systems (avanti®), limited distance system (stealth®), air guns (jgun®), the multiplier electric pistol (flash®) others; the combination of washer (hytorc® z®) and friction washer (hytorc® friction washertm) including a double-sided washer (85) for contractor under a nut (36) or screw head (22) on the other side of the gasket (30) and double drive displacement connections (hytorc® z®) for narrow distances when torque / tension systems from (hytorc®) are used.
公开号:BR112016014225B1
申请号:R112016014225-0
申请日:2014-12-17
公开日:2021-04-27
发明作者:John Kurt Junkers；Xiaoxing Zhang；Eric P. Junkers
申请人:Hytorc Div. Unex Corporation；
IPC主号:

专利说明:

1) Cross Reference to Related Orders - This king-vindicated order is a priority and / or is a patent continuation application or continuation in part of the following common and pending patent applications, the complete copies of which are incorporated herein. by reference: US patent application no. 62 / 012.009, with deposit date of June 13, 2014, entitled “APPARATUS FOR TIGHTENING THREADED FASTENERS”; Patent Application for Patent Cooperation Treatment no. PCT / US2014 / 035375, with deposit date of April 24, 2014, entitled “APPARATUS FOR TIGHTENING THREADED FASTENERS”; U.S. patent application no. 61 / 940,919, with deposit date of February 18, 2014, entitled “APPARATUS FOR TIGHTENING THREADED FAS-TENERS”; U.S. patent application no. 61 / 916,926, with deposit date of December 17, 2013, entitled “APPARATUS FOR TIGHTENING THREADED FASTENERS”; U.S. patent application no. 13 / 577,995, with filing date of August 9, 2012, entitled “APPARATUS FOR TIGHTENING THREADED FASTENERS”, which claims priority of the Patent Application for the Treatment of Patent Cooperation no. PCT / IB2011 / 001019, with filing date of February 9, 2011, entitled “APPARATUS FOR TIGHTENING THREADED FASTENERS”, which claims priorities of U.S. Patent Applications nos. 61 / 430,105 and 61 / 302,598, with deposit date of January 5, 2011 and February 9, 2010, both entitled “APPARATUS FOR TIGHTENING THREADED FASTENERS”; and U.S. patent application no. 13 / 113,693, with filing date of May 23, 2011, entitled "METHOD FOR TIGHTENING AND LOOSENING THREADED CONNECTORS", which is a U.S. divisional patent application no. 12 / 429,040, with filing date of April 23, 2009, entitled "WASHER FOR TIGHTENING AND LOOSENING THREADED CONNECTORS", which is now U.S. patent no. 8,079,795, having the Expedition Date of December 20, 2011, entitled “WASHER FOR TIGHTENING AND LOOSENING THREADED CONNECTORS".
2) History - Threaded fasteners including screws, studs, nuts and washers are known and used in traditional bolting applications. Maintenance and repair of industrial applications starts with loosening and ends with the tightening of these threaded fasteners. Naturally, the industry seeks to reduce production loss during routine and / or emergency maintenance and / or repair.
3) There are two methods for tightening and / or loosening a screw, torque and tension. Until the applicant's innovations, however, it was not possible to apply hydraulic torque and hydraulic tension with the same tool. Operators needed separate tools to apply torque and tension to threaded fasteners.
4) Torque has benefits because: it can be applied to most existing threaded fasteners; it is necessary within 5% (five percent) of the pre-calculated turning resistance of the nut; prevents unintentional loosening; guarantees a more uniform circumferential screw load than tension; and overcomes problems with uneven lubrication applications, foreign particulate matter under the nut or at the top of the flange and minor damage to the thread. The torque has, however, losses because: it is subject to thread friction and face friction, both of which are unknown; requires the use of a spare wrench applied to the nut on the other side of the application to keep the bottom of the threaded fastener still; results in unknown residual load on the screw; and it is subject to the torsion load of the screw and side, both adversely affecting the screwing applications. The sustainable and precise use of torque when screwing requires establishing thread and support face friction and eliminating torsional and lateral load.
5) Tension has benefits, since it is free of torsional and lateral loads. The tension, however, has negative points because: it requires that the screw protrudes at least in its diameter on the nut and around it, so that it can be pulled upwards by a tensioner, which often needs replacing the screw and nut; it is only needed within 25% of the assumed turning resistance; results in unpredictable manual nesting of the nut; it is subject to thread friction and face friction, both unknown; often pulls excessively, does not extend the fastener; results in uncontrollable relaxation of the fastener due to the transfer of load from the extractor and results in unknown residual screw load. The sustainable and accurate use of tightening tension requires the elimination of pin / screw traction and load transfer.
6) Electric torque tools are known in the art and include pneumatically, electrically and hydraulically driven tools. Electric torque tools produce a turning force to tighten and / or loosen the threaded fastener and an equal and opposite reaction force. Hydraulic tensioners use an extra-tor to apply hydraulic pressure to the bolt, which usually results in a bolt elongation of 10% to 20% greater than desired, causing the pin to be pulled excessively. Then, the nut is tightened by hand until firm; the pressure in the cylinder is released; the pin recedes; and the load is transferred from the bridge to the nut, thereby compressing the joint with the clamping force.
7) With respect to torque, traditional reaction fasteners are contiguous with viable and accessible stationary objects, such as adjacent fasteners, to prevent the tool housing from rotating backwards while the fastener rotates forward. This supporting force applies an extraction force or lateral load, perpendicular to the screw axis on the nut to be tightened or loosened. The reaction force of square drive tools travels through the reaction arm trying to unscrew the end of the tool cylinder and / or bend the drive. It should be noted the applicant's innovation in the transfer of coaxial reaction force found in HYTORC® AVANTI®. The evolution of traditional reaction fixings in the prior art 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 of the applicant, full copies of which are hereby incorporated by reference.
8) The sector has been moving away from impractical and complicated hydraulic tensioners, even from the application of torque to the fastener due to the torsional and lateral load. In fact, mechanical tensioning is very popular.
9) The applicant has advanced in screwing and solved many process challenges with its HYTORC NUT ™ mechanical tensioning product lines, drives and tools for use with them. This tensioning nut has two sleeves, one inside the other, so that the inner sleeve is connected to a corrugated washer to allow axial movement of the inner sleeve only. It is threaded onto a pin or screw as a unit. A proprietary drive is maintained over the inner sleeve and rotates the outer sleeve. The pin is pulled up together with the inner sleeve and is tensioned without excess extension and return, as with a hydraulic tensioner. The inner nut never rotates against the threads of the pin under load, eliminating the possibility of seizing the screw thread or other damage.
10) HYTORC NUT ™ mechanically uses the action and reaction force of the tool during tightening and loosening; converts torque into a torsion-free screw extension instead of pulling as tension; it allows the calibration of the screw load with precision with the exact adjustment and obtaining the desired elongation or residual screw load, in comparison to the torque; eliminates lateral loading, torsion, transfer and relaxation of cargo, reaction arms, spare keys, extractors and bridges; eliminates screw elongation measurements for critical applications; increases safety, screwing without error, reliability and speed of the joint; reduces screwing times by more than 50%; and can be used on all joints without alteration. It improves torque and tension by stretching the screws instead of pulling them, implying the unsafe mechanical rebound, capable of damaging the fastener and the joint. The operator sets and achieves the screw load anywhere between 30% and 90% flow.
11) The evolution of HYTORC NUT ™ is described, for example, in US Patent Nos. 5,318,397; 5,499,9558; 5,341,560; 5,539,970; 5,538,379; 5,640,749; 5,946,789; 6,152,243; 6,230,589; 6,254,323; 6,254,323; and 6,461,093 on behalf of the applicant, full copies thereof are hereby incorporated by reference.
12) HYTORC NUT ™, however, has its set of problems. End users must replace standard nuts with precision machined, treated and lubricated units. In addition, the inner sleeve must be relatively thick radially at the point of connection with the washer. Sometimes, this connection can maintain the entire reaction force applied to the outer sleeve. In addition, it is expensive to produce HYTORC NUT ™ and it is often difficult to sell the nut to traditional bolting end users interested in reducing costs. In addition, in some versions of HYTORC NUT ™, the nut has to be made with two gloves, the outside diameter of which must correspond to the outside diameter of a normal nut, so that both gloves have less material than a normal nut . For this, it is necessary to use highly resistant materials, which causes reluctance on the part of customers to exchange materials and fear of the unknown. In other versions of HYTORC NUT ™, the screw needs to be modified, which is expensive and is not easily accepted by the industry.
13) The applicant has made further progress in industrial bolting and has solved many challenges with its HYTORC WASHER ™ product lines, drives and tools for use with them. HYTORC WASHER ™ was the first example of reaction washers used as reaction points for tightening nuts and bolts on helically threaded fasteners. The reaction washers are positioned on the loading path of the screw or pin, thus undergoing an equal and identical load. In reaction washer systems, rotational torque is applied to the top nut or bolt, while the opposite reaction torque is checked in the reaction washer. The top nut or bolt and the corresponding reaction washer are subjected to the same and identical load and torque. Therefore, the relative movement is controlled only by the frictional forces. The component with the lowest friction coefficient will tend to move while the other component remains relatively anchored.
14) The HYTORC WASHER ™ automatic reaction load washer has an internal thread segment connected to the thread of a traditional screw. It fits under a normal nut and prevents the screw from turning, while providing a reaction point for the drive tool. It is fastened with a proprietary double socket. An external socket secures the washer and an in-suit socket rotates the normal nut, thereby pulling the pin upward through the washer. The reaction force of the tool is converted into a holding force that keeps the HYTORC WASHER ™ stationary. This keeps the segment, as well as the screw, stationary when the nut is being rotated until the elongation of the spindle causes an axial segment to move inside the HYTORC WASHER ™. It improves torque and tension by stretching the screws instead of pulling them out. The lack of load transfer relaxation or mechanical rebound allows for a 90% flow.
15) HYTORC WASHER ™: provides a supporting facial friction for a more uniform residual screw load; it does not require precision machining of the point face; minimizes torsion and lateral loading of the screwing procedure; prevents the screw from turning together with the nut; creates the straight axial stretch of the screw without the need for reaction arms and spare keys; increases the residual screw load and the uniformity of compression of the circumferential joint; reduces the adjustment time; increases the speed of screwing; allows the screwing to become axially oriented and uniform without the use of hands in inverted applications; increases the safety of screwing and minimizes the risk of damage to the fastener and the joint.
16) The evolution of the HYTORC WASHER ™ product lines and attachments and tools for use with them is revealed, for example, in the US patents of applicant 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 entire copies of which are hereby incorporated by reference.
17) HYTORC WASHER ™, however, has its set of problems. It adds unnecessary height to the screwing applications. End users often need to replace standard bolts and screws with longer versions due to regulations requiring two or more threads to protrude from the nut after tightening. In addition, HYTORC WASHER ™ production is more expensive than traditional washers and is often difficult to sell to traditional screwing end users interested in reducing costs. In addition, HYTORC WASHER ™ rotates freely and in the opposite direction if the friction of the nut is greater. During operation, HYTORC WASHER ™ has two facial frictions and the nut has one facial and one thread friction, so that the general friction of each one is almost identical, which means that HYTORC WASHER ™ can rotate or the nut can rotate. To avoid this, a preload is required which cannot be achieved if both the HYTORC WASHER ™ washer and the nut are both facing downwards. Finally, despite the elimination of lateral load and torsion, corrosion still accumulates in the threads, thus not eliminating the seizure of the thread.
18) The applicant has made further progress in industrial screwing and has solved many screwing challenges with its HYTORC SMARTWASHER ™ product lines, drives and tools for use with them. This multi-purpose automatic reaction washer used to tighten and loosen threaded connectors, including a nut, a screw having a shaft and introduced into an object with interposition of the washer between the nut and the object so that a first surface of the face of washer support on one axial side cooperates with a nut and a second surface of the washer support face on an opposite axial side cooperates with the object. The washer includes: a radially external body having a radially internal opening adapted to be larger than a diameter of the screw and a radially external surface adapted to absorb a reaction force from a tool; a radially internal segment engageable with a screw thread, located radially inside the external body in the radially internal opening and connectable to the external body with a limited axial friction movement in relation to the body; and a spacer adapted to be located between the radially internal segment and the nut and also located radially within the external body in the radially internal and axially spaced opening of the radially internal segment. The external body, the radially internal segment and the spacer can be assembled and disassembled together and can be used together or individually.
19) The applicant used the radially external body and the radially internal segment, interposed together between the nut and the object, for applications where uniform and precise elongation of the screw was necessary. When the nut is rotated by the tool with the given force, the radially external body receives the given force in an opposite direction from the tool. The radially external body remains stationary, while the radially internal segment that engages the screw thread positively prevents the screw from turning. The screw just stretches or relaxes. In this case, the washer, composed of the radially external body and the radially internal segment, functions as a tension washer.
20) The applicant used the radially external body, the radially internal segment and the spacer, interposed between the nut and the object, for applications where precise screw elongation was required and the screw elongation had to be controlled. When the nut is rotated by the tool with the given force, the radially external body receives the given force in an opposite direction from the tool. The radially external body remains stationary, while the radially internal segment, which positively engages the screw threads, prevents the screw from turning. The screw only stretches 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, composed of the radially external body, the radially internal segment and the spacer, functions as a high precision washer.
21) The applicant used only the radially external body of the air-alley, interposed between the nut and the object, for regular applications, when a uniform and precise screw elongation was not necessary. The radially external 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 external body remains stationary, in which case the washer, composed only of the radially external body, functions as a reaction washer.
22) HYTORC SMARTWASHER ™ offers many of the advantages of HYTORC WASHER ™ in a cheaper and more flexible packaging. The evolution of the HYTORC SMARTWAS-HER ™ product lines and drives and tools for use with them is revealed, for example, in US patent no. 8,079,795, in the name of the applicant, whose full copy is hereby incorporated by reference .
23) HYTORC SMARTWASHER ™, however, has its set of problems, similar to those of HYTORC WASHER ™. It adds unnecessary height to the screwing applications. Often, end users need to replace standard pins and bolts with longer versions due to regulations requiring two or more threads to protrude from the nut after tightening. In addition, HYTORC SMARTWASHER ™ production is more expensive than traditional washers and is often difficult to sell to traditional screwing end users interested in reducing costs. In particular, the applicant believed that a uniform, accurate and precise elongation of the screw is not possible when only the radially external body of the HYTORC SMARTWASHER ™ is used as a reaction washer. In addition, the use of the threaded insert with the radially external body produces a uniform and precise elongation of the screw, but the pin path is limited to the thickness of the washer. The path is also prevented by the use of the spacer. Finally, despite the elimination of lateral load and torsion, corrosion still accumulates in the threads, thus not eliminating the seizure of the thread.
24) In addition, HYTORC SMARTWASHER ™ rotates freely and in the opposite direction, if the friction of the nut is greater. During operation, HYTORC SMARTWASHER ™ has two facial frictions and the nut has one facial and one thread friction, so that the general friction of each one is almost identical, which means that the HYTORC SMARTWAS- HER ™ can rotate or the nut can turn. To avoid this, it is necessary to apply a preload that cannot be obtained if both the HYTORC SMARTWASHER ™ washers and the nut are simultaneously turned downwards.
25) With conventional reaction washer systems, lubricant should be applied to selectively induce the washer to remain stationary under higher friction than the nut or pin. This allows the pin or nut to rotate, generating load by means of corresponding helicoidal threads. The oblique movement of the necessary lubricant is an unwanted and difficult control step in the process of installing reaction washers. Even small amounts of lubricant in a conventional reaction washer will have the adverse effect of allowing the reaction washer to rotate or slip before the nut or bolt. When the washer rotates before the screw or helically threaded nut, the system cannot generate the screw load. Inadequate control of lubrication or friction surfaces often results in sliding or involuntary turning of conventional reaction washers.
26) Other examples of prior art reaction washers include those described in US Patent Nos. 7,462,007 and 7,857,566, full copies of which are hereby incorporated by reference. These reaction washers should replace Belleville locknuts and washers, as they deform resiliently under load to store preload or live load energy. In most models, the incorporation of a threaded hole aims to minimize the lateral load on the screw. The area that comes into contact with the object of these concave and / or convex reaction washers is small compared to the total surface area of the lower surface of the washer. A threadless hole is revealed in one embodiment. Friction improvements include protrusions, such as hexagonal washer-shaped points or flat serrated extensions, that bite or lodge on the surface of the object. A substantially flat reaction washer is also revealed to have no friction improvements.
27) The applicant made efforts to increase the speed of rotation of the fastener in fluid-operated electromechanical tools. The HYTORC® XXI® is a fluid operated wrench having a fluid operated drive including a cylinder; a piston reciprocally movable in the cylinder and having a piston rod with a piston rod end; a ratchet mechanism having a shell provided with a plurality of teeth; and at least two lugs operatively connectable with the end of the piston rod and can be attached to the ratchet teeth so that during a piston stroke, one of the at least two latches engages at least one ratchet tooth, while the other of at least two ratchets in at least one ratchet tooth, while during a piston return stroke the other of at least two tongues engages at least one ratchet tooth, while one of at least two tongues engages in at least one hunting tooth. At least one of the at least two tongues is detachable and can be lifted above the ratchet teeth. The HYTORC® XXI® also includes a disengagement unit that can be activated by an operator separately from the drive and can act on at least one tongue in order to distinguish it and lift it above the hollow teeth. This anti-recoil feature allows the ratchet to rotate backwards to release an accumulated twist and flex of the material so that the fluid operated wrench can be removed from work. HYTORC® XXI® is the world's first constantly turning hydraulic wrench. This makes this tool up to three times faster than any other key on the market. Note that the benefits of HYTORC NUT ™ and HYTORC WASHER ™ are enhanced when used with HYTORC® XXI®. HYTORC® XXI® is disclosed in Applicant's US Patent No. 6,298,752, the complete copy of which is incorporated herein by reference.
28) The applicant then applied its complete understanding and innovation in electric torque tools to manual pneumatic torque intensifier tools, specifically by creating the HYTORC® jGUN® product lines and actuators 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. As soon as the nut reaches the flange surface, the degree of rotation to tighten or loosen it is very small. Customers want high turning speeds to quickly lower or raise sows. The known impact wrenches that provided high speed of descent and withdrawal had disadvantages of lack of precision and slow rotation when the nut hits the flange face. Conversely, the known portable torque power tools had precise torque, but were relatively slow to move the fasteners up and down. They were still much faster than impact guns when the nut was turned on the flange face.
29) The motor housing of the known portable torque intensifier tools was independent of the gearbox, so that the torque could not exceed the torque resistance of the operator's arm / hand. Otherwise, the tool box of the tool could not be maintained and would rotate in the operator's hand. There were many motorized torque multipliers on the market and some of them had two speed mechanisms, some of them reacted at the tip of the screw, which required the use of special screws and others with a reaction arm. No matter what torque or speed was applied, its gearbox rotated in the opposite direction to the output shaft. At high speed, the rotating parts of the portable torque-intensifying tools then in existence required bearings, because the gears and the output shaft rotated very fast in the gearbox. The high torque versions of these tools were very large and very heavy.
30) The HYTORC® jGUN® product lines include a tool with descending or ascending speed in which the entire gearbox, together with the internal gear set and the output drive, 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 the gearbox. It should be noted that the HYTORC NUT ™ and HYTORC WASHER ™ product lines and drives and tools for use with them are compatible with the HYTORC® jGUN® Dual Speed. For example, at a higher speed, the lower torque mode of the HYTORC® jGUN® Dual Speed, the drive socket having the nut and the reaction socket having the HYTORC WASHER ™ always rotated together and at the same higher speed and with the same lower torque. The HYTORC WASHER ™ and the nut are integrated as a pin unit until the nut is seated on the HYTORC WASHER ™. The torque increases and the pins are disintegrated by shearing, so that the nut is rotated with a higher torque and a lower speed, while the HYTORC WASHER ™ becomes a stationary object and, therefore, a reaction point . The integration of HYTORC WASHER ™ and a known nut is no longer accepted because the broken connection pieces affect the friction coefficient, which can cause the thread to seize and leave unwanted and harmful deposits on the screw interfaces.
31) When not used with HYTORC WASHER ™, HYTORC® jGUN® required the use of reaction devices to deflect the reaction force generated when turning the nut to a stationary object. The descent speed had to be limited to prevent the reaction arm from being hit against the adjacent nut at high speed, which could cause an accident if the operator's ends were in the way. The support of a reaction arm is required for the low speed, high torque operating mode to tighten or loosen fasteners. But the reaction arm is not desirable for high speed, low torque operating mode - again to avoid accidents and situations reportable to OSHA.
32) The applicant has applied its complete understanding and innovation in torque electric tools equipped with reaction devices and the HYTORC® jGUN® product lines to further advance portable pneumatic torque intensifier tools. The applicant created the HYTORC® FLIP-GUN® product lines, drives and tools for use with them. HYTORC® FLIPGUN® includes a positionable reaction arm. When placed in a first position, the torque intensifier unit is switched to high speed and low torque mode and the reaction arm is usable as a cable by the operator while in a direction perpendicular to the tool axis. When the reaction arm is placed in a second position coaxial to the tool axis, the torque intensifier unit is switched to low speed and high torque mode and the reaction arm can rest on a stationary object, as the high torque it cannot be absorbed by the operator.
33) Application characteristics often adversely affect bolting services and include, for example, nut pins and threads and corroded, dirty, crooked surfaces, with residues, burrs, rough, irregular, disoriented, misaligned and / or unevenly lubricated. Production loss is often exacerbated by these adverse screwing application characteristics. Naturally, the industry seeks to reduce production loss during routine, unforeseen and / or emergency maintenance and / or repair.
34) The applicant also innovated its portable pneumatic torch power tools, specifically creating the HYTORC® THRILL® product lines and actuators and tools for use with them. HYTORC® THRILL® is a dual-function torque-enhancing portable power tool that operates in tightening and loosening industrial fasteners, without reaction and in a reaction-assisted manner. It includes: a motor to generate a turning force to rotate the fastener; a swing force multiplier mechanism for a lower speed / higher torque mode, including a plurality of swing force multiplication transmitters; a swing force impact mechanism for a higher speed / lower torque mode, including a plurality of swing force impact transmitters; a housing operationally connected with at least one multiplication transmitter; a reaction arm to transfer a reaction force generated in the housing during the lowest speed / highest torque mode to a stationary object; being that during the lowest speed / highest torque mode, at least two multiplication transmitters rotate in relation to each other; and being that during the highest speed / lowest torque mode at least two multiplication transmitters are unitary to obtain a hammering movement of the impact mechanism. Advantageously, HYTORC® THRILL® minimizes the operator's exposure to vibration; provides high speed inertia at the highest speed, lowest torque mode due to a high mass resulting from the cooperation between the multiplication and impact mechanisms, which increases the torque output of the impact mechanism; lowers and removes fasteners at high speed without the use of a reaction device, even when a torque greater than that absorbable by an operator is required to overcome substantially adverse bolting application characteristics, such as the deformation of the thread and the face and / or thread seizure; and loosen highly tightened or corroded fasteners that are attached to their joints and tighten fasteners to the highest and most accurate torque desired with the use of a reaction device in the second mode.
35) The impact mode is not operable on THRILL® during the lowest speed / highest torque (multiplication) mode because: the positionable reaction arm rests on a stationary object and the impact mechanism is blocked during the mode multiplication of torque. But note that during the highest speed / lowest torque mode, the rotating force of the motor is transferred through the initial stage of the multiplication mechanism to the output shaft to lower or raise a nut or screw head that shows little or no resistance. The impact mechanism activates when the fastener demonstrates adverse fastening characteristics, thus requiring intermittent force to overcome these deformities.
36) The evolution of the HYTORC® jGUN®, FLIP-Gun® and THRILL® product lines and drives and tools for use with them is revealed, for example, in the US patents and patent applications of the applicant 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; 7,735,397; 7,641,579; 7,798,038; 7,832,310; 7,950,309; 8,042,434; D608,614; and 13 / 577,995, the complete copies of which are hereby incorporated by reference.
37) Despite the applicant's recent innovations with THRILL®, side loading and thread seizing remain important problems in industrial bolting applications and have not been addressed by the intensifying tools on the market. Gripping is the wear and tear of material caused by a combination of friction and adhesion between metal surfaces during transverse movement, or sliding, often due to unsatisfactory lubrication. When a material wears out, portions are pulled out of a contact surface and adhere or even are frictionally welded to the adjacent surface, especially if there is a large amount of force compressing the surfaces. Seizing often occurs in high load and low speed applications. It involves the visible transfer of material, when it is pulled out adhesively from one surface, leaving it stuck to the other in the form of a raised shapeless mass. Seizures are generally not a gradual process, but they do occur and spread rapidly when the raised, masses induce more seizures.
38) Corrosion of a fastener corroded for a long time since tightening generally occurs between the nut engaging threads and the bolt and the nut and the flange. Corrosion can have several origins, including chemical, heat, moisture and lubrication. In high temperature applications, for example, the lubrication applied during the tightening dries and joins the threads over time. In addition, chemical reactions inside and outside the container often cause galvanic corrosion. During loosening, corrosion of the internal thread pushes the grease that has dried along the threads of the screw. The reaction force applied to the stationary object applies an equal force to the side next to the nut to be rotated. In fact, the lateral load or supporting force for a tool can be 3 to 4 times its torque output in feet-pounds, because the reaction arm's support point is often half, if not less, than a foot of distance from the center of the drive. This lateral load causes the nut and bolt threads to engage with enormous force on the side where it is applied so that the dry grease accumulates there when the nut is turned. Irregularities in threads can often not be overcome. Only half of the threads between the bolt and the nut are engaged and the threads start to seize. This causes the screw thread to seize, which requires substantially more torque and thus substantially more lateral load to remove the nut, which can damage the screw and nut threads. The fastener often blocks to the point where all the turning force is used by the thread friction, which can lead to the breakage of the fastener or the tool that rotates it. The torque tool originally used to tighten the fastener is often insufficient to loosen the same corroded fastener. These corroded fasteners may need loosening torque values 1 to 3 times more foot-pounds than tightening torque and an additional, more powerful tool may be required. High temperature bolting applications, such as, for example, turbines and housings, are generally critical, requiring stainless or precision-made fasteners with extremely high replacement costs. In addition, the use of thin threaded screws, which is already very popular, multiplies this problem.
39) Even if no lateral load is applied by the tool to the fastener, thread seizure can still occur when dry grease accumulates on the coupling threads during loosening of the nut. This loosening requires, at one point, a higher torque than the original tightening torque, which when applied results in thread seizing. This is true even with HYTORC NUT ™ between the inner and outer sleeves. It is customary in the industry for operators to hit corroded fasteners with a sledgehammer to spray corrosion before applying loosening torque. This habit is dangerous because it can damage the threads of the screw, extending through the nut and is not civilized. There is also adverse seizing between the face of the nut and the face of the flange, as the lateral load changes the perpendicular orientation of the nut to be rotated. This in turn increases the turning force of the nut and makes the bolt load created by the loosening torque unpredictable, which causes adverse aesthetics, non-parallel joint closures, system leaks and tool, fastener and joint failures.
40) Known washers can reduce the seizure of the surface between the threaded fastener, the nut and the gasket when the washer is made of a harder material. Appendix M of ASME PCC-1-2010 states that: "It is generally recognized that the use of fully hardened steel washers improves the translation of the torque input into the bolt preload by providing a smooth, low-friction bearing surface for the nut. The washers protect the contact surfaces of the flange from damage caused by a rotating nut. These are important considerations when using torque application methods (either manual or hydraulic) to tighten bolts. " The known washers, however, do not minimize and / or eliminate the surface clamping and thread seizure created by the side load. And the known washers can move when they are being tightened so that the washer can rotate with the nut or screw head instead of remaining fixed. This can affect the torque voltage relationship.
41) Another objective of installing washers in a typical bolting system is to distribute the loads under the screw and nut heads providing a larger area under tension.
42) Otherwise, the supportive tension of screws may exceed the supporting force of the connection materials and lead to loss of screw preload and material slippage.
43) What is needed is: simplification of the design and operation of the tool, drive and washer; elimination of reaction, bending and traction forces; increased speed, efficiency, reliability and repeatability of screwing, all at low cost. The present invention has therefore been developed to address these issues.
44) REPORT - The inventions of the present application can be described, by way of example only, with reference to the attached drawings, in which:
45) Figures 1A to 1C are perspective views of an upper and lower surface and a side view of a first embodiment of a HYTORC® Z® washer;
46) Figures 2A to 2B are perspective views facing up and down of a joint to be closed by a threaded fastener including the Z® washer of Figures 1A to 1C and a nut, a Z® fastener;
47) Figures 3A to 3C are seen in perspective and side of a free tool with a reaction arm, a HYTORC® Z® gun for tightening and / or loosening the Z® fastener with reduced grip;
48) Figures 4A to 4B are seen in perspective and side of the tight joint and the fastened Z® fastener;
49) Figures 5A to 5D are seen in perspective, in cross-section in perspective and in lateral cross section of a double actuation coaxial action and reaction set, a HYTORC® Z® socket;
50) Figures 6A to 6E are seen from top to bottom, bottom to top and sides of treatment means to increase the friction coefficient of the Z® washer and related forces acting on the Z® fastener;
51) Figures 7A to 7C are multiple views of various modalities of Z® fasteners with various dimensions and widths of treatment means to increase the friction coefficient of the Z® washer, as crimped strips;
52) Figures 8A to 8L are seen from top to bottom of various types of Z® washers with varying shapes;
53) Figures 8D1 to 8D3 are seen in perspective of an upper and lower surface and a side view of another modality of a Z® washer;
54) Figures 8D4 to 8D10 are cross-sectional side views of various types, sizes and locations of treatment media to increase the friction coefficient of the Z® washer;
55) Figures 9A to 9B are cross-sectional side views of alternative types of Z® fastener and Socket Z® for use with Z® washers;
56) Figure 10 is a side cross-sectional view of an alternative Z® washer and Z® socket so that the diameter of the air-alley is smaller than that of the nut;
57) Figures 11A to 11C are multiple views of various modalities of Z® sockets with varying dimensions and widths;
58) Figures 12A to 14B are seen in perspective of the application of the Z® system in the HYTORC® torque tools including grooved adapters, reaction plates and displaced connections;
59) Figures 15A to 15G are perspective and side views of the application of a double-sided friction washer HYTORC® in the Z® system;
60) Figure 16A is a perspective view of another mode of the present invention in the form of tool 10A in a lower speed and higher torque ("LSHT") mode;
61) Figure 16B is a perspective view of an embodiment of the present invention in the form of tool 10B in a higher speed and lower torque ("HSLT") mode;
62) Figure 17A is a cross-sectional, side view of tool 10A in LSHT mode;
63) Figure 17B is a cross-sectional, side view of tool 10B in HSLT mode;
64) Figure 18 is a cross-sectional, side view of the turning force multiplication set 200 and a vibrating force set 300 of the tool 10A in LSHT mode;
65) Figure 19 is a perspective view, in cross-section of a drive tool housing assembly 101, a drive tool cable assembly 103 and related internal components of tool 10A and tool 10B;
66) Figure 20 is a perspective view of a 400 mode change assembly of tool 10A and tool 10B;
67) Figure 21A is a cross-sectional, side view of an embodiment of the present invention in the form of a tool 10F;
68) Figure 21B is a cross-sectional, side view of an embodiment of the present invention in the form of a 10G tool;
69) Figure 22A is a cross-sectional, side view of an embodiment of the present invention in the form of a tool 10H; and
70) Figure 22B is a cross-sectional, side view of an embodiment of the present invention in the form of a tool 10I.
71) The HYTORC® Z® System. The present invention seeks to protect the applicant's HYTORC® Z® System which involves: tools having multiple speed / multiple torque modes with torque multiplication and vibration mechanisms without the use of external reaction supports; a means of transferring force to produce coaxial action and reaction suitable for use with these tools; drive means and transmission means capable of connecting to washers under the nut for use with these tools and means for transferring force; associated washers for use with these tools, power transfer means and drive means; and related accessories for use with these tools, power transfer means, drive means and washers.
72) The HYTORC® Z® System includes the following: HYTORC® Z® washers located under nuts and screw heads of various types having multiple shape interlocking perimeters, sizes, geometries and cutouts, as radius hitch differentials of washer / fastener and friction inclined faces with relatively higher friction against the flange surface and relatively lower friction against the nut, as means of treatment to increase the friction coefficient of various types, sizes and locations HYTORC Z® guns incorporating a powerful impact mechanism and an accurate torque multiplier in the same tool combining rapid descent with calibrated torque; HYTORC® Z® sockets with double actuation coaxial action and reaction with external gloves to react on Z® Washers and internal gloves to turn nuts or screw heads; Grooved HYTORC® Z® Adapters and Reaction Plates for reverse compatibility with HYTORC® torque / tension systems including AVANTI® and ICE® square drive systems, the STEALTH® limited distance system, the jGUN® pneumatic series , the FLASH® Pistol and the LITHIUM Series electric multipliers and more; the combination of HYTORC® Z® Washer and HYTORC® Friction Was-her ™ Double Friction Washer including an improved friction double sided washer for contractor under a nut or screw head on the other side of the joint and Double Displacement Connections HYTORC® Z® drive for tight distances when HYTORC® torque / tension systems are used.
73) The HYTORC® Z® Washer Washer. International bolting standards require hardened washers to be placed under industrial threaded fasteners. HYTORC® Z® Washers are hardened washers, proprietary to the applicant, which become the reaction point directly under the nut or head of the fastener screw during tightening and / or loosening. HYTORC® Z® Washers are used with industrial threaded fasteners of the type having a coaxial reaction surface, a pin and a threaded nut with the pin or pin head connected to the pin. They eliminate any possible tightening points of the operator's limbs. Operators do not need to look for satisfactory stationary objects to react to. Straight, coaxial tension adjustment eliminates curvature and / or lateral loading of the stud. They offer a smooth, consistent, low-friction upper surface on which the nut or screw head rotates; the top has a surface against which the nut or bolt head will rotate. They offer a lower surface with increased friction against which the tool will react.
74) Z® washers protect the flange surfaces from damage or embedding and evenly distribute the bolt load around the joint due to the larger surface area. They can be made in a wide variety of inch sizes or metric from a wide variety of material options for each application. They meet all the requirements of ASME, ASTM and API standards for dimensions, hardness and thickness. They work as pneumatic, hydraulic, electrical and manual torque tools. And with the addition of an associated friction washer, it eliminates the need for a spare wrench to prevent the opposite nut from turning in conjunction with the bolt.
75) The applicant's recent research and development with reference to Washer Z® includes producing a prototype and experimentally evaluating different thicknesses; external hitch sizes; external coupling geometries and cutouts; coatings and low friction treatments on the (upper) coupling sides of the fastener; sizes, shapes and places of intensification of friction, such as serration patterns, on the (lower) coupling sides of the flange; chamfer sizes and shapes on the bottom, top, inside and outside faces; material specifications; and heat treatment specifications.
76) Figure 1A shows a first modality of the HYTORC® Z® 1 Washer for use with HYTORC® torque / tension systems. It is a perspective view of an upper side, or upper support face 2 of washer 1. Figure 1B shows a perspective view of a lower side, or lower support face 3 of washer 1. And Figure 1C shows a view side of an edge side, or side support face 4 of washer 1.
77) In general, washer 1 has an annular shape with an internal gap 5. As shown in Figure 1, the annular shape of washer 1 includes radially extending lobes 6 that have the shape of a flower . In general, an upper bearing face 2 is smooth with relatively lower surface friction against the nut or screw head. Note that lubricants can be used on the upper support face 2 to reduce the surface friction between it and the nut, screw head or any other type of threaded fastener. A lower support 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 rough friction enhancements, such as protrusions 7, with higher surface friction. The pattern of raised radial projections 7 increases the surface friction of the lower bearing face 3. In the illustrated embodiment, the serrated surface 7 takes the form of a ring or ring located in addition to the smooth surface 3A. Other lobes 6 include angled chamfer faces 8 formed between the lower bearing face 3 and the lateral bearing face 4.
78) Washer 1 has, among other things, annular radius R1A, lobe radius R1L, projection radius R1K and span radius R1V. Washer 1 has a height H1, a first chamfer height H1Bi, a second chamfer height H1Bii, a projection height H1K and a chamfer angle ° 1.
79) Figure 2A shows a perspective view facing upwards and Figure 2B shows a perspective view facing downwards of a joint 30 to be closed. Gasket 30 includes a first member 31 and a second member 32 which are fixed face-to-face by a fastener 20, commonly known in the art as a screw. The fastener 20 has a first end 21 provided with a screw head 22 and a second end 23 provided with a threaded engagement 24. The second end 23 of the fastener 20 is inserted through an opening 33 in the first and second members 31 and 32, extending from a support face 34 of the second member 32 to a support face 35 of the first member 32. In preparing a tightening process, the washer 1 is placed on the second end 23 with lower support face 3 in the direction of support face 35. The threaded nut 36 is placed on the second end 23.
80) Washer Z® is used only on one side of the joint and no other washer should be used under it. Normal bolt and nut lubrication practices must be followed. Only lubricant is needed on the screw threads and between the nut and the screw head and on 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 screw depends a lot on the lubricant used. Normally, no lubricant is required on the back of the nut or bolt head.
81) The typical industrial bolting practice is to adjust the pin so that when it is tightened at the top end, 2 to 3 threads protrude above the nut. This is for inspection purposes to ensure that the nut and pin are fully engaged. There is generally no reason for the pin to extend further than this and any excess length must be adjusted to the other side of the flange so that the socket can engage the entire nut without obstruction. In areas of high corrosion, the pin is allowed to stay close to the nut after tightening in order to reduce the risk of damage to the thread and so that the nut can be removed easily. Advantageously, the thickness of the washer 1 is ideal. If the washer is excessively thick, the fastener system will have insufficient male threads available. On the other hand, if the washer is insufficiently thick, it can fail under high compression loads.
82) The HYTORC® Z® Pistol (In General). The tools 10A, 10B, 10F, 10G, 10H and 10I include: a motor to generate a turning force; a drive to transfer the turning force; a mechanism of multiplication of the rotating force in a housing including a transmitter of multiplication of the rotating force for all modes of torque from the lowest resistance to the highest resistance; and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable during all torque modes from the lowest resistance to the highest resistance.
83) Standard pneumatic impact wrenches hammer the screw with uncontrolled force with loud noise and excessive vibration. The HYTORC Z® Pisole is a precision torque multiplier that produces consistent power and measured in bolt after bolt without the uncontrolled force, loud noise and / or excess vibration of standard pneumatic impact wrenches. The Z® Pistol is the world's first pneumatic bolt-on tool with a precise torque reaction free arm in the world. It ensures uniform and precise screw loading. The Z® Gun incorporates a powerful impact mechanism and an accurate torque multiplier in the same tool, combining rapid descent with calibrated torque. It is operated by a trigger on the gun butt and includes a directional control key for tightening or loosening, a speed selection cable for high and low speeds and an automatic reaction socket drive that engages the Z® Washer under the nut. The impact mechanism closes or opens nuts, regardless of corrosion or imperfections in the thread. The torque multiplier mechanism breaks fixers or tightens them. It works with the Washer Z® without external reaction arm, without compression points and without improper lateral loads. It makes any fastening work faster, safer and better than before, all with one tool.
84) The Z® Pistol has built-in dual speed capability that is controlled by simply switching quickly from high speed descent mode to low speed torque power and vice versa. In high speed mode, the double socket rotates at several hundred revolutions per minute, but the torque is limited so that the tool cannot rotate or bounce off the operator's hand. Moving the selector upwards locks the tool in the power / torque mode and the nut or bolt is tightened to the desired torque automatically, based on the calibrated pneumatic fluid pressures.
85) Advantageously, the Z® Gun takes care of industrial problems and issues with hydraulic, pneumatic or electric torque intensifying tools. It maximizes the benefits and eliminates the losses of torque and tension; maximizes benefits and eliminates losses from HYTORC NUT ™, HYTORC WASHER ™, HYTORC® AVANTI®, HYTORC® XXI®, HYTORC® jGUN®, HYTORC® FLIPGun® and HYTORC® THRILL® - which can cause seizure due to threaded couplings lateral loading and accumulation of dry corrosion; minimizes operator exposure to vibration; provides higher inertia in intermittent force mode due to a higher mass of cooperation between the multiplication and impact mechanisms, which increases the torque output of the impact mechanism; lower and remove fasteners with higher speed without the use of a reaction arm, even when a torque higher than that absorbable by an operator is needed to overcome the adverse characteristics of the screwing application; loosens very tight and / or color-fastened fasteners stuck to their joints and fastens fasteners with the highest and most accurate torque desired using a coaxial reaction surface in the highest resistance torque mode. The vibration force mechanism can be activated while the nut is tightened to spray dry corrosion before applying full torque to the nut to loosen. This results in less torque needed to loosen the industrial threaded fastener and the sprayed dry grease does not accumulate or concentrate on portions of threads. In addition, during tightening and loosening, the nut is parallel to the face of the joint and the threads are not subjected to the enormous irregular lateral load making the face and thread friction more consistent. This guarantees a more uniform torque load and, thus, a uniform compression of the joint to prevent leaks and failure of the packing in the tightening. In addition, the use of the tool is simplified, reducing the risk of operator error and greater safety for the operator.
86) The industrial threaded fastener 20 is generally tightened using a torque, tension and / or torque and tension tool hydraulically, pneumatically or electrically activated. Figures 3A, 3B and 3C show a power tool free of reaction arm 10, the HYTORC® Z® gun, for tightening and / or loosening fastener 20. Tool 10 includes a motor to generate a turning force; a drive to transfer the turning force; a turning force multiplication mechanism in a housing including a turning force multiplication transmitter for all torque modes from lower resistance to higher 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. Note that tool 10 operates in a higher speed, lower torque (“HSLT”) mode, as shown as tool 10A in Figures 3A and 3B and a lower speed, higher torque (“LSHT”) mode, as shown as tool 10B in Figure 3C.
87) Tool 10A of Figures 3A and 3B and tool 10B of Figure 3C include: a drive input and output assembly 100; a rotating force multiplication set 200; a set of vibrating force 300; a 400 mode change set; and a double actuated output and reaction socket set 15, such as the HYTORC® Z® socket.
88) In HSLT mode, tool 10A: compress washer 1 between nut 36 in the preloaded fastener 20 at the pre-tightened joint 30 at a predetermined pre-tightening torque; decompress the washer 1 between the nut 36 in the unloaded fastener 20 at the loosened joint 30 of the predetermined pre-tightening torque; and / or the pressurized air-alley 1 vibrates between the tight nut 36 on the loaded fastener 20 at the tight joint 30 to properly spray the screw thread corrosion. In LSHT mode, tool 10B: pressurizes washer 1 between the tightened nut 36 on the loaded fastener 20 and the tightened joint 30 until a predetermined tightening torque; and / or com-prime the washer 1 between the nut seated 36 in the pre-loosened fastener 20 in the pre-loosened joint 30 from the pre-determined tightening torque.
89) In HSLT mode, tool 10A: lower nut 36 or nut 36 and washer 1 on fastener 20 with turning force in one direction to seat nut 36 and compress washer 1 on pre-loaded fastener 20 at the pre-tightened joint 30 to a pre-determined pre-tightening torque; raise the seated nut 36 or the seated nut 36 and the compressed washer 1 on the pre-loosened fastener 20 on the pre-loosened joint 30 with the turning force in the opposite direction of the predetermined pre-loosening torque; or vibrate (impact) the tight nut 36 on the pressurized washer 1 to apply vibration to properly spray the corrosion of the thread. In LSHT mode, tool 10B: tighten the nut 36 on the compressed washer 1 on the preloaded fastener 20 on the pre-tightened joint 30 with the turning force in one direction to the predetermined tightening torque and apply the reaction force in the opposite direction to the compressed washer 1; or loosen the tight nut 36 on the pressurized washer 1 in the loaded fastener 20 at the tight joint 30 with the turning force in the opposite direction from the predetermined tightening torque and apply the reaction force in one direction to the pressurized washer 1.
90) During operation, tool 10B in LSHT mode changes to tool 10A in HSLT mode after removing nut 36 and de-compressing washer 1 at the predetermined pre-loosening torque. During operation, tool 10A in HSLT mode changes to tool 10B in LSHT mode after nut 36 is set and decompress washer 1 at the predetermined pre-tightening torque; or adequate spraying of thread corrosion. Note that the operator uses the 400 mode change set to switch the tool from LSHT mode to HSLT mode or vice versa. It should be noted that the 400 mode change set is a manual switch, but it can be automatic. Similarly, note that the activation or deactivation of the vibration force set (impact) 300 can occur manually or automatically. It should be noted that the LSHT mode can be changed from the regulated torque to vibration assisted or vice versa and that the HSLT mode can be changed from vibration regulated to torque assisted or vice versa. It should be noted that the vibration force (impact) assembly 300 can continue to operate even if washer 1 starts or stops rotating. And it should be noted that the LSHT mode can be assisted by vibration to loosen nut 36 to help overcome chemical corrosion, heat and / or lubrication and prevent seizure of the screw thread.
91) Applying torque to a fastener creates facial friction, thread friction as well as screw loading. The friction and screw load are inversely proportional: as the friction increases, the amount of screw load generated decreases. The speed at which a fastener is tightened has a marked effect on the magnitude of the friction and thus the screw load generated in a joint to be closed. Advantageously, the Z® Gun is able to use the principle that coefficients of thread friction and under the head decrease as the speed of rotation increases.
92) The Pistol Z® works, for example, as follows. Suppose that for a job it is necessary to tighten 1% ”pins with 28/8“ nuts with torque of 520 feet-pounds using a Pistol-A1 Z®. The Pistol-A1 Z® is used for torque ranges from 300 to 1200 foot-pounds. The Z® Gun-A1 Pistol comes with a standard trigger size of 3/4 "square trigger and has the dimensions (L x W x H) of 11.92" by 3.29 "by 9.47" (30 x 8 x 24 cm). The drive outlet housing has a radius of 1.98 "(5 cm). The height and width of the cable are 6.94" and 2.12 "(17 and 5 cm), respectively. The descending and torque RPMs end vary approximately from 4000 to 7, respectively. The turning force of the tool is determined by the air pressure provided by a filter / regulator / lubricator (FRL). The operator consults the corresponding pressure / torque conversion table for this value. In this case, 520 foot-pounds of final torque corresponds to a pneumatic pressure of 50 psi, thus adjusting the air supply pressure of the FRL to 50 psi.
93) As shown in Figure 3B, tool 10A lowers nut 36 until it fits into the flange in HSLT mode. Washer 1 'is compressed between seated nut 36' and seated joint 30 '. In descent mode (HSLT), the selector (mode change set 400) is in the down position and tool 10A is held with both hands.
94) As shown in Figure 3C, to start applying torque in LSHT mode, the operator pulls selector 400 towards you in the up position. The seated nut 36 'is engaged, ensuring that the external reaction socket 17 completely surrounds the compressed washer 1'. Note the absence of compression points because both hands are safely out of the tightening zone around the seated nut 36 '. The operator presses the trigger until tool 10B stops and will no longer advance the internal drive socket 16. The operator applied 520 foot-pounds of torque to the tight nut 36 '' and the pressurized washer 1 '' and each other nut will receive the same clamping force as long as the FRL pressure is maintained. Figures 4A and 4B show a tight joint 30 ’’ that includes tight fastener 20 ’’, tight nut 36 ’’ and pressurized washer 1 ’’.
95) Note that the chamfered faces 8 assist washer 1 in removing weld fillets formed between flanges and pipes at joint 30 and other distance problems. Other chamfered faces 8 assist the external reaction socket in engaging and rotationally coupling with washer 1. The chamfered faces 8 can also accept modifications made to the external reaction socket 17 to allow use in inverted screwing applications.
96) The operator reverses the process for removing the 36 '' tight nut, this time starting in LSHT mode. The effects of weather and corrosion can make it more difficult to remove nuts and / or bolts than it was to tighten. Considering that obtaining a specific torque value is not a concern when loosening, the operator can raise the air pressure of the FRL to or near its maximum, giving the tool practically full power. A directional control is moved to release. The operator places the tool 10B in the application and places an internal drive socket 16 on the tight nut 36 '' and an external reaction socket 17 on the pressurized washer 1 ''. The operator pulls the speed selector 400 upwards, activates the tool 10B and proceeds to loosen the tight nut 36 '' until it can be manually turned and removed from the pressurized washers 1 ''. The operator moves the speed selector 400 to the HSLT position to remove nut 36. Remember that the vibration force mechanism can be activated while the nut is tightened to spray dry corrosion before applying full torque to the nut to loosen. This results in less torque needed to loosen the industrial threaded fastener and the sprayed dry grease does not accumulate or concentrate on portions of threads.
97) Please note that parts of this specification associated with Figures 16 to 23 provide a complete discussion of the HYTORC Z® Gun and related tools.
98) HYTORC® Z® Sockets The benefits of the Washer Z® are optimized when used with HYTORC® Z® Sockets with double actuation coaxial action and reaction. External gloves react on the Z® Washers and internal gloves rotate the nuts or screw heads adjacent (above) to the washers. Several dual socket systems of the present invention and proprietary HYTORC® do just that. Firstly, the Z® Pistol having a Z® Socket is the fastest and easiest way to obtain all the benefits of this reaction-free technology. Portions of the external socket surround the Z® washer and swivel in the grooves in the torque tool body. The internal socket connects to the tool drive and turns the nut. The impact action of the Z® Gun lowers the nut quickly and thus effortlessly switches to torque controlled mode while reacting against the Z® Washer. There are no external clamping points or unwanted side loads. For the first time, torque controlled with a pneumatic tool is possible, without sacrificing speed and flexibility. These proprietary socket sets exceed all applicable ANSI standards for strength and safety and come with a full range of inch and metric sizes for use in any job.
99) The applicant has revealed important features of the washers in its patent applications related to the HYTORC WAS-HER ™ washer. Washers positioned on the load path rotate with the nut (or screw head) or remain stationary; the washers will never rotate in the opposite direction like the nut due to facial friction and load compression. The applicant's innovation determined the effectiveness of reacting to remove in-line washers. Despite the frictional benefits of the threaded insert, the HYTORC WAS-HER ™ washer is viable because of this observation.
100) Generally, the joints to be closed of the present invention are tightened by means of a screw and a nut. The screw, having a hardened washer adjacent to the head of its screw, is inserted into the holes in the joint. The nut, having a geometrically adjoining hardened washer, is threaded onto the screw. An internal action socket turns the nut and tightens the gasket and an external reaction socket transfers the reaction force from the tool to the geometrically lockable hardened washer. As the action torque at the joint increases, the reaction force of the action torque increases proportionally. The rotationally coupled external socket is geometrically engaged in the hardened washer which eliminates the rotation of the tool in relation to the operator due to the reaction force.
101) Figures 5A, 5B and 5C are seen in perspective of the double actuation coaxial action and reaction set 15. Figure 5A is a perspective view of the assembled cross section. Figure 5B is an assembled perspective view. Figure 5C is an exploded perspective view. Figure 5D is a flat cross-sectional view of the double actuation coaxial action and reaction set 15 at the tight joint 30 ''.
102) In HSLT mode, as illustrated in Figures 3A and 3B, socket assembly 15 is substantially for transferring a vibrating form of turning force to nut 36 and washer 1 in one direction. In LSHT mode, as illustrated in Figure 3C, the results of which are shown in Figures 4A and 4B, the socket assembly 15 is substantially to transfer a multiplied shape of the turning force to nut 36 in one direction and the corresponding multiplied shape of a reaction force in another direction for washer 1, which acts as a stationary object.
103) Referring to Figure 5A, an inlet drive socket 16 includes an inner edge 52 with a nut engaging or screw head 51. The outer reaction socket 17 has an inner bottom edge 62 with a washer 1 engaging means 61 to engage the outer edge of washer 4 or external socket engaging means 9. Internal drive socket 16 is substantially disposed within external reaction socket 17. They are coupled via socket 18 coupling means. The sockets can be rotated cooperatively and relatively in opposite directions through the tool housing. The inner lower edge 62 and its engaging means 61 of the washer 1 and the outer edge 4 of the washer 1 and its outer socket engaging means 9 are substantially vertical. The outer reaction socket 17 includes an outer edge 63 having a tapered inwardly sloping surface towards a bottom of the inner bottom edge 62. A bottom face 54 of the inner socket 16 rotates on and / or on an upper face 64 from an inner bottom edge 65 of the external socket 17. Note that the socket 18 coupling means are designed for use with HYTORC® square drive hydraulic tools. Note that socket 18A coupling means are designed for use with HYTORC® pneumatic and electric torque guns, such as tool 10A (and 10B).
104) Washer 1 has, among other things, annular radius R1A, lobe radius R1L, projection radius R1K and center orifice radius R1V. Washer 1 has a height H1W, a first chamfer height H1Bi, a second chamfer height H1Bii, a projection height H1K and a chamfer angle ° 1. Nut 36 has a hexagonal radius R36N and height H36N. The external reaction socket 17 has a washer radius R17W that includes an outer washer / socket G1A that assists the external reaction socket 17 to facially engage the washer 1. A clearance 19 having separation height H1L provides distance enough between internal and external sockets 16 and 17. Internal socket 16 is free to rotate on the upper surface 64.
105) Please note that any suitable coupling geometry will be sufficient, as described in the HYTORC® patents and patent applications incorporated herein by reference. But note US patent No. 8,631,724, with grant date of January 21, 2014, entitled “FASTENING SOCKETS, WASHERS AND FASTENERS USED WITH THE WASHERS AND THE FASTENING SOCKETS”, the complete copy of which is incorporated by reference. The external socket engagement means of US Patent No. 8,631,724 do not engage the outer surface of a washer, but simply an "outer edge portion", thereby increasing the probabilities of failure.
106) External reaction socket 17 of tool 10A is idle and inactive in HSLT mode. It is not engaged by a groove in the housing of the turning force multiplication set 200. Impact and / or vibration force transmitters of the turning force set 300 are grooved engaged on a drive shaft of output, which rotates the internal drive socket 16 to raise or lower nut 36 on fastener 20. The external reaction socket 17 of tool 10B, however, is rotationally coupled and geometrically engaged in washer 1 under nut 36. With the seating of the nut 36 ', the compressed washer 1' serves as a stationary object by which the housing of the turning force multiplication set 200 reacts by means of the reaction socket 17. With the housing of the turning force multiplication set assembly swing 300 kept at a standstill, the swing force multiplication transmitters tighten the seated nut 36 '' by means of the swing force output drive shaft.
107) During the operation of any modality of the tools having reaction socket assemblies of the present invention, the drive socket turns a nut or the head of a screw. During the operation of a modality of this tool, the reaction socket remains stopped during the HSLT mode. When operating another mode of this tool, the reaction socket rotates in the same direction as the drive socket in HSLT mode, but remains stationary in LSHT mode. And when operating another mode of this tool, the reaction socket remains stationary or rotates in the opposite direction with the drive socket in HSLT mode, but remains stationary in LSHT mode.
108) In other words, the drive socket is always operationally connected with the nut or the screw head during all torque modes from lower resistance to higher resistance. And the reaction socket is: operationally connected to the housing and the coaxial reaction surface to transfer a reaction force to the coaxial reaction surface during the highest resistance torque mode; connected operationally to the housing and coaxial reaction surface during the lowest resistance torque mode or the intermittent force mode; or operationally connected to the housing and operationally disconnected from the coaxial reaction surface during the lowest resistance torque mode or intermittent force mode.
109) In other words, a torque tool of the present invention includes: a drive means for connecting with a drive socket of a double actuation coaxial action and reaction socket assembly to turn a nut or head. screw; a reaction means for connecting a reaction socket of the coaxial action and reaction socket assembly to transmit the reaction force to a washer; a means of connection between the actuation and reaction means; at least two operating modes including a low torque and high speed mode and a high torque and low speed mode; the drive socket being rotated in one direction by the drive means during high torque and low speed mode and during low torque and high speed mode; the reaction socket being rotated in one direction when the connection medium between the actuation and reaction means is activated in low torque and high speed mode, but does not rotate the washer when the connection medium is deactivated in low speed and high torque. In other words, a torque tool of the present invention includes: a drive means for connecting a drive socket to a nut or screw head; a first reaction medium and a second reaction medium for connecting a reaction socket to a washer; at least two modes of operation - a low torque and high speed mode and a high torque and low speed mode; the actuating socket being rotated by the actuating means during both modes to rotate the nut or the screw head; the reaction socket being connected to a washer under the nut or the screw head; a first reaction medium that prevents said reaction socket from turning in high torque and low speed mode while the washer absorbs a greater magnitude reaction force and a second reaction medium that prevents the reaction socket from turning in torque mode low and high speed while an operator absorbs a reaction force of lesser magnitude. In this case, the grooved adapter in the housing of the rotating force multiplication housing assembly is the first reaction medium. And a switch arm of the mode change set having a scored adapter is the second reaction medium.
110) Dual sockets, particularly reaction gloves (sockets), of the present invention were developed for use in conjunction with all HYTORC® electrical, hydraulic and pneumatic torque / tension systems. It was necessary to reduce the outer diameters of the reaction gloves to provide maximum distance between the tool's reaction systems and the environments surrounding the fastener. Reducing the outer diameters of the reaction gloves required reducing the outer diameters of the action sockets as well.
111) Generally, various parts geometries have been developed for the gloves, sockets and adapter rings of the present invention. All possible components were developed using prototypes and evaluated experimentally at the HYTORC® research and development center. Quality tests included subjecting the parts to their application load in particular for countless cycles. Various alternatives of material and thermotreatment were also evaluated experimentally.
112) Note that parts of this specification associated with Figures 16 to 23 provide further discussion of the HYTORC Z® Sockets.
113) HYTORC® Z® Washer - Radial Coupling Differential for Fixer. In torque tools with traditional reaction fixings of the prior art, the reaction torque is the same and opposite to the action torque. However, the reaction force applied by the reaction arm is much greater on a stationary object in the vicinity. The reaction force is multiplied by the distance, by the length of the reaction arm. In fact, the lateral load, or reaction contact force, of a tool can vary between 2 and 4 times its torque output at the support points at a distance of, for example, 15 cm (1/2 foot), a from the rotating force axis of the drive. This greater reaction force is concentrated only at that location. Naturally, shorter reaction arms transfer a lower reaction contact force to the contact points closest to the axis of rotation of the drive. It is logical that an extremely short reaction arm would transfer a reaction contact force of similar magnitude, although slightly greater, than the torque tool output, because the fulcrum is extremely close to the rotating force axis of the drive. .
114) Irregularities in the threads produce adverse screwing characteristics. Among other damages, the lateral load causes the nut and bolt threads to engage with enormous force on the side where it is applied so that the dry grease accumulates in that place when the nut is turned. Often, only small fractions of the total areas of the thread surface are engaged between the bolt and the nut. This causes the screw threads to seize, which requires substantially more torque and therefore substantially more lateral load to loosen the nut. This chain of events often spoils the threads of screws and nuts. The fastener blocks or sticks at the point where all the turning force is used by the thread friction, which can cause the fastener or the tool that turns it to break.
115) The torque tool originally used to tighten the fastener is often insufficient to loosen the same corroded fastener. These corroded fasteners may need loosening torque values that vary between 2 and 4 times higher than the tightening torque, requiring a more powerful tool for loosening. High temperature bolting applications, such as turbines and housings, are generally critical, requiring stainless fasteners or precision manufactured fasteners with extremely high replacement costs. In addition, the use of thin threaded screws, which is already popular, multiplies this problem.
116) Similarly, the torque is equal and opposite to the action torque in the HYTORC® double actuated coaxial action and reaction socket set. But the reaction force intensification feature is also applicable. Referring again to the descriptions of HYTORC WASHER ™ and SMARTWASHERTM washers in the applicant's related patents, these washers had radius substantially similar to that of the nut. The reaction forces applied to these washers were of a magnitude similar to that of the same and opposite reaction torque. This helps to explain why HYTORC WASHER ™ eSMARTWASHERTM washers sometimes rotated with the nut or screw head.
117) Industrial screwing professionals recognized the need to use relatively similar fastener component sizes. In normal screwing operations, it does not matter whether the screw head or the nut is tightened. It is naturally assumed that the head of the screw and the face of the nut have the same diameter and the contact surfaces are the same to produce the same coefficient of friction. If they are not, it doesn't matter. Let's say the nut had flanges and the screw head didn't. If the tightening torque was determined on the assumption that the nut would have to be tightened, but instead, the screw head was subsequently tightened, the screw could be overloaded. Generally 50% of the torque is used to overcome the friction under the clamping surface. Therefore, a smaller friction radius will result in more torque entering the screw thread and thus over tightening. If the reverse were true, that is, the tightening torque was determined on the assumption that the screw head would have to be tightened, and then the nut was subsequently tightened, the screw would be less tightened.
118) In the same way that an extremely long reaction arm applies an extremely greater reaction force to a stationary object in the vicinity, an extremely short reaction arm applies a reaction support force of similar, although slightly greater, magnitude than the torque tool output. In this sense, the external reaction socket 17 can be considered a 360o reaction arm that applies that reaction support force of similar magnitude, although slightly larger than the torque tool's output infinitely around the outer edge 4 of the washer 1. In fact, the external reaction socket 17 applies a greater supporting force to the reaction washer 1 under nut 36. This can only be achieved by having a slightly larger washer 1 - geometric shape hitch of the external reaction socket 17 - than the nut 36 - geometrically shaped coupling of the inlet drive socket 16. The applicant's fundamental observation about washers associated with this new observation guarantees a stationary washer in which to react.
119) With reference to Figure 5D, the outer edge 4 of the pre-secured washer 1 '' extends beyond an outer edge 37 of the tightened nut 36 ''. Notably, a reaction force 92 acting in the other direction 94 received by the outer edge of the washer 4 is greater than an action torque 91 acting in a direction 93 received by the nut 36. The pressurized washer 1 '' absorbs the force reaction 92 of tool 10B so that tool 10B applies action torque 91 to seated nut 36 'and applies an opposite but slightly greater reaction force 92 to the outer edge of washer 4. The seated nut 1' rotates, but the compressed washer 1 'remains stationary. This relative positioning, that is, that the outer edge of the washer 4 is farther from the center of rotation, or from the turning force axis A10, than the outer edge of the nut 37, is an innovative aspect of the present invention. The reaction force 92 acts via the effective lever arm of the external socket 17, a distance R1A from the turning force axis A10 which tends to keep the washer 1 at a standstill. As a result of the radius differential of the external polygonal couplings, washer 1 remains stationary at joint 30, instead of turning with nut 36 when fastener 20 is tightened or loosened.
120) Treatment Means for Increasing the Coefficient of Friction of the HYTORC® Z® Washer. With reference to Figure 6, it shows a bottom-up view of the lower support face 3 formed with the treatment medium for increasing the friction coefficient 60. Nut 36 is shown with the smooth upper support face 2. The forces friction points are less between nut 36 and washer 1 when engaging smooth contact surfaces 2 and 38 than when engaging rough contact surface 3 and flange surface 30. Thus, nut 36 tends to turn and the washer 1 tends to remain stationary.
121) Figures 6B, 6C, 6D and 6E explain these phenomena. Figure 6B shows a nut 36 being tightened and compressed against the upper support face 2 of the washer 1. The upper support face 2 and a lower support face 38 of the nut 1 are smooth. During the tightening process, a frictional force 71r between nut 36 and washer 1 acts in a direction 92. A compressive force Fn of nut 36 acts on washer 1 in a downward direction along the force axis of rotation A10. A radius r is an effective friction radius or the distance from the turning force axis A10 to the center of the friction area 73r of the lower bearing face 38 of nut 36.
122) Figure 6C shows the washer 1 being compressed against the bearing face 35 of the joint 30. The bearing face 35 and the lower bearing face 3 of the washer 1 are engaged by friction and under load. During the tightening process, a frictional force 72R between the washer 1 and the joint 30 acts in the other direction 93. A compressive force Fn of the joint 30 acts on the washer 1 in an upward direction along the force axis of rotation A10. A radius R is an effective friction radius or the distance from the turning force axis A10 to the center of the friction area 74R of the lower bearing face 3 of washer 1.
123) Figure 6D shows a combination of Figures 6B and 6C. Figure 6E shows Fn and Fb. A compressive force Fc generated by the nut 36 pressing on the fastener 20 is the same on both sides of the airway 1 such that Fn = Fb = Fc. Frictional force (FR) = μ * Fc, where μ is the friction coefficient. Note that the effective friction radius of the treatment medium for increasing the friction coefficient 60, or R, is greater than the effective friction radius of nut 36, or r, such that Fc * R> Fc * r. This means that the torque to overcome the friction between the nut 36 and the washer 1 is less than the torque that would overcome the friction between the treatment medium to increase the friction coefficient 60 of the washer 1 and joint 30.
124) Referring again to the example in Figure 6A, the treatment medium for increasing the friction coefficient 60 is shown, for example, as a radial raised protrusion pattern 7 having an internal radius R7. The radial high protrusion pattern 7 is shown positioned as far as possible from the rotating force axis A10 at a substantially maximum radius, RMAX, to maximize torque (TRMAX) while still below a nut compression area 36. When the clamping force increases, the protrusion pattern 7 fits into the material on the face of the flange 35, thus resisting the attempt of the washer 1 to rotate with the nut 36. The friction coefficient, μ, remains constant and is multiplied by the constant compressive force Fc to produce a constant frictional force (Fb). The reaction torque (tR) is F * R. The maximum torque can be obtained with a substantially maximum radius, RMAX, such that tRMAX = F * RMAX. In other words, the effective friction radius, R, of washer 1, is greater than the effective friction radius, r, of nut 36. Generally, the effect friction radius of the Z® Washers of the present invention is greater than a radius of effective friction of the nuts or screw heads. Note that the principles of mechanics (static, dynamic, etc.) of describing traditional bolting applications and associated forces are well known in the art.
125) Explained in another way, the resistance of washer 1 to slide or rotate while the reaction torque is applied is due to the load and friction coefficient. The following expressions represent the relationship between the sliding force, friction, load and torque in a reaction washer.
126) Sliding Force Resistance = (Friction Coefficient) x (Load)
127) FR = μ * FN
128) where: FR = Force (Resistance), μ = Coefficient of e Friction and FN = Normal Force (Weight or Load).
129) In a threaded fastener the force to overcome the friction and create the slip or rotation is a function of the applied torque and the friction radius. Then, the force to create the landslide can be expressed as:
130) FS = (Torque) / (Friction Radius)
131) FS = T / rF
132) where: FR = Force (Slip), T = Torque and rF = Effective Friction Radius. Therefore, in a fixative:
133) FS = FR
134) T / rF = μ * FN, such that:
135) T = μ * rF * FN
136) The above expression shows that the slip resistance under torque is a function of the friction coefficient, load and radius of the friction surface. This effective friction radius is generally taken as the average radius of the central hole and the outer support face. When the friction radius increases, the resistance to sliding or turning increases. It should be understood, therefore, that a means for increasing the friction radius of the washer in relation to the friction radius of the nut or bolt anchors the washer in relation to the nut or bolt. Since they are equal and opposite torque forces, the reaction washers and nuts or bolts will always have identical bolt load torque forces applied. The friction coefficients are identical in the fasteners, when similar materials and lubricants are applied along them. By increasing the friction radius of the support face of the washer, it is therefore possible to ensure that the washers remain anchored in relation to the nut or bolt in all situations of screwing.
137) The friction radius of the washer is increased by tilting the supporting surface outward. This can be done by adding surface features to the outermost area of the bearing face while the innermost areas are neglected. Because of the high loads and the typical fit of the corresponding surfaces, only a slight selective conditioning of the surface is needed to effectively increase the friction radius.
138) The position and coverage area of the treatment medium to increase the friction coefficient, for example, the high protrusion characteristic and its relationship with the projection area of the nut or screw head ensure the efficiency of the System Z®. The lower surface of the washer includes treatments to increase the friction coefficient positioned outwards, defining a friction portion for engagement with the joint surface. The friction portion is arranged around an outer peripheral portion of the bottom surface and extends inward to a width less than the full width of the washer body. The surface with improved friction tends to block the nut while maintaining the bolt load, thus preventing involuntary loosening. In other words, the bottom surface of the washer is roughened to ensure substantial friction between the joint and the washer with the fastener tightening or loosening. The frictional forces developed between the washer and the gasket are substantial and reliably serve to prevent unwanted rotation of the washer after loading and during the initial unloading stage.
139) Experimentally unexpected repeatable performance is not possible if the improved friction surface 7 covers completely or is positioned in the central hole on the lower surface 3 of washer 1 or close to it. Most of the time, this configuration fails and washer 1 rotates with nut 36.
140) The concept of the Z® washer works in a similar way, only with an outer ring having treatment means to increase the friction coefficient. It is not necessary to have the smooth inner portion, that is, the inner surface 3A and also the rough outer portion. But different surface textures on the underside of the washer really help with the friction slope on the bottom surface as a whole and between the underside and top sides of the washer.
141) This patent application aims to define, claim and protect a reaction type washer with friction area displaced outwards, for example, an external inclination of the friction radius of the reaction washer in relation to the nut. This produces a new, non-obvious displacement of the radius of the friction surface, preventing the washer from turning the nut. The prior art reaction washer without friction inclination tended to rotate, especially when used on hard surfaces. They performed marginally and worked only under ideal conditions on ideal surfaces. Turning unwanted type washers unwantedly caused damage to the flange faces, industrial bolting and inefficient system maintenance operations and economic loss. Stationary washers with ex-suit positioning of the treatment medium to increase the friction coefficient of the present invention keep flange faces intact, increase the efficiency of industrial bolting and system maintenance operations and minimize economic loss.
142) With reference again to Figure 5D, the relative differentials of radial engagement of the washer / fastener, that is, the outer edge 4 of the washer 1 is farther from the center of rotation, or from the turning force axis A10, than that the outer edge 37 of the nut 36 serves as another modality of treatment means for increasing the friction coefficient of the present invention. A surface area of the larger washer / flange with a longer engagement radius increases face friction in a surface area of the smaller nut / washer with a shorter engagement radius.
143) Explained otherwise, in screwing applications of the present invention, the friction torque generated by the interaction of the washer-flange surface area is greater than the friction torque generated by the interaction of the nut-washer surface area. The washer remains stationary so that it is possible to fix a retaining socket in a non-rotating way in relation to the tool housing. The retaining socket is placed in engagement with the outer polygonal edge of the washer while the clamping tool engages in an actionable way with the nut. After tightening, the washer is compressed under the nut and the tool housing is secured against rotation in relation to the washer. The washer absorbs the reaction moment and the reaction force of the tool housing which is opposite the tightening torque and deflects it into the compressed washer. There is no need for an external means of reaction.
144) Figures 7A, 7B and 7C show various dimensions and widths of the treatment medium to increase the friction coefficient of the washers, as protrusion strips. Figure 7A shows a washer 17A with an internal gap or central hole, 57A for use with a relatively small size M14 screw. The protrusion strip 77A covers most of the lower bearing face of the surface area 37A. However, the lower bearing face 37A has a smooth inner surface 3A7A adjacent to span 57A. In fact, the smooth internal surface 3A7A forms between the gap 57A, which accepts the fastener 20, and the protrusion strip 77A. Washer 17A has an internal radius, rin7A, an external radius, rout7A, an internal protrusion radius, rinK7A, an external protrusion radius, routK7A, and a lobe radius, rL7A. Similar dimensions are applicable, but are not shown in Figures 7B and 7C.
145) Remember that HYTORC WASHERs ™ and HYTORC SMARTWASHERs ™ washers added unnecessary height to bolting applications. The thicknesses of the Z® washers of the present invention are typically small compared to their outside diameters. For example, the average ratio of the thickness H1W to the outer diameter D1A of the washers shown in the drawings is about 0.08 and can vary from 0.04 to 0.12. Other reasons describe the Z® washers of the present invention, including: the average ratio of height H1W of the washer to height H36N of the nut is about 0.170 and can vary from 0.10 to 0.30; the average ratio of the diameter D1A of the washer and diameter D36 of the nut is about 1.10 and can vary from 0.80 to 1.40. These reasons are provided for descriptive purposes only.
146) Note the difficulty in quantifying the important characteristics of the friction slope of the Z® system. For example, relative surface areas of the washers and nuts (or screw heads) minimally affect the friction inclination results with the Z® system. In fact, relatively small threaded fasteners can have very different reasons than relatively large threaded fasteners.
147) The most informative data involve the calculation of the effective friction radius of the washer and the threaded fastener. Z® washers work so reliably because treatments to increase the friction coefficient are selectively tilted away from the central hole and towards 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 having a radial range of treatments to increase the friction coefficient on its underside is the center of that range. Note that this discussion correctly assumes the ideal case in which the screw load is evenly distributed under the nut or head of the screw due to the use of the Z® Washer.
148) Please note that friction improvements may not be necessary in many applications, although they ensure that the washer remains stationary in all applications, regardless of: the relative surface areas of the washer / fastener or hitch spokes; relative hardness of the fastener / joint material; and relative treatments of the fixer / joint surface as lubricants (molycoat, etc.) or coatings (paint, etc.). Friction improvements become important at the beginning of a tightening process when there is little or no load on the pin and / or nut. This slope of friction starts retaining the washer every time.
149) Alternatively, the means of treatments to increase the coefficient of friction includes: roughness, polygonal surfaces, grooves, protrusions, nails, grooves, cracks, protruding points or notches or others of said projections. Other options include press-enclosed projections, concentric or spiral rings, radial protrusions or teeth, wafer-like patterns, etc. Any operation that forces external surface areas to have a more aggressive interaction with the flange surface, such as selectively grinding, sanding, sandblasting, milling, machining, forging, casting, forming, shaping, roughing, stamping, recording, drilling, flexing or even relaxing the internal areas is sufficient. It should be noted that combinations of these means of treatment can be used to increase the friction coefficient. If the washer 1 - engagement of the external reaction socket 17 is slightly larger than the nut 36 - engagement of the internal drive socket 16, the treatment means for increasing the friction coefficient may not be necessary; can be positioned anywhere around the bottom surface of the washer; or it can be positioned substantially beyond an effective friction radius of the nut or bolt head around the bottom surface of the washer. To obtain the properties of the invention it is sufficient that the underside of the washer is uniform. The opposite friction surface, however, can also be tapered out, so the outer edge of the friction ring is thicker than the inner edge. However, if necessary, the washer, and therefore its underside, may also have a curvature. Particularly good results are obtained with a convex curve in the direction of the joint. This is revealed in US patent No. 7,462,007, the grant date of which is December 9, 2008, entitled “Reactive Biasing Fasteners”, the complete copy of which is incorporated herein by reference. It should be noted, however, that the washers of the present invention do not impart axial tilt strength to the elongated screw.
150) Generally, the reaction washers of the present invention for industrial bolting include: an external shape that allows rotational coupling with a torque application device; and a surface area of supporting friction on the underside that is discontinuous and selectively inclined in areas outside the central hole. These surface friction characteristics are selectively created on the underside of the washer and excluding any portion of the area close to the radius of the central hole. These surface friction characteristics can be created by knurling, blasting, milling, forging, casting, forming, shaping, roughing, stamping, engraving, drilling or bending. Surface friction characteristics can be created by simply relaxing the material close to the orifice of the reaction washer. The surface friction characteristics can also be: created with discontinuous surfaces and / or textures provided in an area or areas outside the hole; and / or positioned alone, randomly or in any array arrangement.
151) Alternative Z® Washer Geometries. Figures 8A to 8L show alternative shapes of the washer 1. The washers of the present invention can have an outer edge (and corresponding engagement means) formed with any geometry suitable for non-rotating engagement of an inner edge of an external socket ( and corresponding engagement means) formed with a suitable corresponding geometry or substantially identical geometry. The standard commercial shape of Z® 1 Washer is a "flower pattern" washer including concave portions extending inward and convex portions extending outward that are supplied, altered and repeatedly, in a radial direction around of an imaginary reference circle that is centered on a central point of the washer. Figures 8B, 8E, 8G, 8H and 8I are clear derivations of these flower-shaped washers. Note that Figure 8K shows a multilateral shaped hitch and Figure 8J shows a groove hitch, both of which can be considered to have a flower shape with increasing numbers of hitch teeth.
152) Other suitable geometries include shapes such as triangle, curvilinear triangle, square, rectangle, parallelogram, rhombus, trapezoid, trapezoid, rhombus, pentagon, hexagon, heptagon, octagon, eneagon, decagon, circle with external projections, ellipse or oval. It should be noted that the edges of the external side of any suitable shape can be curved, instead of angular, to intermediate the easy engagement with the Z sockets of the present invention.
153) Figures 8D1, 8D2 and 8D3 show the modality of Figure 8D, Washer Z® 18D for use with various power tools. Perspective views of the top and bottom faces and side, cross-sectional view of washer 18D, respectively, are shown. In general, washer 18D has a hexagonal annular shape having similar dimensions and characteristics as shown in Figures 1A, 1B and 1C, except for the subscript “8D”. The hexagonal shape of the washer 18D includes side corners that extend radially 68A forming a hexagonal type model. In general, an upper support face 28D is smooth with less surface friction and a lower support face 38D has sharp friction or bottom corners 78D with greater surface friction. Note that lubricants can be used on the upper support face 28D to reduce the surface friction between it and the threaded nut 36 or any other type of threaded fastener. The corners of the radial bottom 78D increase the surface friction of the lower support face 38D. The side corners 68D, although not shown, can include angled chamfer faces 88D formed between the upper bearing face 28D and the lateral bearing face 48D. These 88D beveled faces may constitute the portion of the outer edge that includes tapered surfaces and engagement teeth, the tapered surfaces being gradually angled outward and towards the lower support face 38D and lateral support face 48D.
154) Washer 18D has, inter alia, annular radius R8A, a radius of lobe R8L, a serrated radius R8K and a radius of span R8V. Washer 18D has a height H8, a first chamfer height H8Bi, a second chamfer height H8Bii, a projection height H8K and a chamfer angle ° 8. These chamfered faces 88A can assist washer 18A in releasing a corner radius from a flange and in other releasing issues. Other chamfered faces 8 assist the external reaction socket in engaging and rotating coupling with washer 1. The chamfered faces 8 can also accept modifications made to the external reaction socket 17 to allow for inverted bolting applications.
155) Alternative Placement of Treatment Means for Increasing Friction Coefficient of Z® Washer Figures 8D4 - 8D10 show washer 18D with several friction-inclined face iterations with relatively higher friction against the flange surface and relatively lower friction against the nut. In other words, washer 18D is shown with various types, sizes and locations of treatment means for increasing the friction coefficient. Note that these variations are shown with the 18D washer, but apply to all the reaction washers disclosed in the present invention. Figure 8D4 is shown with no friction improvements, just a smooth bottom side. Figure 8D5 is shown with friction improvements that are recesses formed inside the bottom face of the washer removing the material close to the central hole. Figure 8D6 shows a relatively thin range of friction improvements formed on a portion of the outer edge of the lower face. Figure 8D7 shows a relatively thick range of friction improvements formed equi-distant from a portion of the inner edge and portion of the outer edge of the underside. Figure 8D8 shows a relatively thin strip with 1X width of friction improvements formed at a distance 1X from the inner edge and 2X from the inner edge of the bottom face. Figure 8D9 shows means of improving friction, in this case a downward sloping ring having sharp edges formed on the outer edge of the lower face. The 18D5 washer, although shown curved, does not provide axial tilt strength to the elongated screw. Alternatively, the 18D5 washer may have no height variations, except at the sharp edges.
156) As shown in Figure 8D10, the washers of the present invention can also be provided with configurations for positive locking engagement with the external reaction socket. These positive locking couplings are cracks formed on the outer edge of the 18D airway. The external reaction socket would include matching latching means to allow hands-free operation and as soon as the nut is seated, hands-free operation in an inverted bolting application.
157) Revelations of reaction type washers for industrial bolting having friction surfaces of the prior art do not discuss the importance of the location or the scope of coverage of these friction surfaces. The applicant has found that the treatment medium for increasing the coefficient of friction located in the inner spokes of the washer near the screw or around the entire lower part of the alleyway tends in the direction of the washer's movement or rotation with the nut. These strategies have been marginally successful occasionally producing stationary washers. In other words, more friction treatments on larger, whole and / or inner portions of the bottom of the washers are substantially less efficient than friction treatments on smaller and / or outer portions.
158) Alternative Fixer and Z® Socket Types for use with Z® Washer. Figure 9A shows washer 18D for use with a screw provided with a screw head 20A threaded into a blind hole and HYTORC® 15 double actuated coaxial action and reaction socket assembly. Figure 9B shows washer 18D for use with a 20B socket head screw threaded into a blind hole and a 15C modified HYTORC® double actuated coaxial action and reaction socket set. Various fastener geometries can be used with Z® System tools, parts and accessories with corresponding design changes, as shown in Figure 9B. The modified socket assembly 15C includes a male fastener engagement means 16C instead of reaction socket 16.
159) Z® Washer Reduced Surface Area Figure 10 is similar to FIG. 5D, except that the outer edge 410A of a pressurized washer 110A "" cuts from the outer edge 37 of the tightened nut 36 ". Notably, a reaction torque force 9210A that acts in another direction 94 received by the outer edge of washer 410A may be less than the torque force of action 91 that acts in a direction 93 received by nut 36. Pressurized washer 110A '' absorbs reaction force 9210A from tool 10B so that tool 10B applies action torque 91 to seated nut 36 'and can apply less reaction force 9210A to the outer edge of washer 410A. Aggressive friction improvements 710A are required to prevent washer 110A from rotating from eating nut 36. Seated nut 36 'rotates, but compressed washer 110A' remains at rest. Relative positioning, ie, friction improvement 710A and therefore an effective friction radius of washer 110A is farther from the center of rotation, or the turning force axis A10, than an effective friction radius of the nut. 36 is an innovative aspect of the present invention. The reaction force 9210A acts via the external socket 17A a distance R10A approximately from the axis of turning force A10 which tends to keep the washer 110A at a standstill. As a result of the effective friction radius differential, washer 110A remains stationary at joint 30, instead of turning with nut 36 when fastener 20 is tightened or loosened. It should be noted that the lower face 54 of the internal socket 16 rotates on and / or on an upper face 64A of an internal lower edge 65A of the external socket 17A. In this case, the internal socket 16 and the external socket 17A may suffer additional facial friction due to a larger surface area of the upper face 64A.
160) In other words, washers with outer edges that have joint termination or reduce from an outer edge of the nut or screw head can be used with the HYTORC® Z® System. In such cases, it is necessary that the lower surface of the washer be formed with treatment means to increase the aggressive friction coefficient to ensure that the effective friction radius of the washer is greater than an effective friction radius of the nut or head. screw. Successful results are likely with aggressive friction improvements, even though the reaction force received by the outer edge of the washer is substantially equal to or less than the action torque received by a nut or the outer edge of the screw head. In these situations, these aggressive friction improvements may include roughness, polygonal surfaces, grooves, protrusions, nails, grooves, crevices, protruding points or other such projections. The displacement of aggressive means of treatment to increase the friction coefficient beyond R20 remains an important feature in this case. It should be noted that the modified external socket 17A requires a sophisticated design to engage and rotationally engage the washer 1. It should also be noted that the modified external socket 17A can allow for inverted screwing applications.
161) Alternative sizes of Socket Z®. Figures 11A, 11B and 11C show various reaction socket sizes, including external socket 1711A having straight walls and external sockets 1711B and 1711C having tapered walls. These variations allow threaded fasteners and HYTORC® Z® Washers of different sizes to be used with the same Z® Gun. Other settings can be used as needed.
162) Z® System Applied to HYTORC® Torque Tools. HYTORC® developed grooved adapters and reaction plates to adapt the Z® System to its set of torque tool models operated electrically, hydraulically and pneumatically for regular distance, low distance and screw connection applications. Figure 12A shows socket coupling means or grooved adapters 18 and 18A, as discussed with respect to Figures 5A, 5B, 5C and 5D. The 18A grooved adapter is designed for use with HYTORC® pneumatic and electric torch guns, such as the Pistol Z® 10A (and 10B), as shown again in Figure 12B. It has an annular ring shape equipped with grooved couplings on its internal and external sides. The internal drive socket 16 and the external reaction socket 17 of the double drive socket 15 are coupled cooperatively and relatively rotatable in opposite directions in LSHT mode by means of the tool housing and / or other known means and / or by means of coupling means 18A.
163) As shown in Figure 12C, the grooved adapter 18 is designed for use with the applicant's hydraulic torque tools, such as HYTORC® ICE® 10C and HYTORC® AVANTI® 10D and other such tools. It is shaped like a staggered annular ring with an upper and lower fused portion having a different radius. The upper ring has a smaller radius and inner grooved hooks for non-rotating engagement with the grooved reaction support portions 19A and 19B of tools 10C and 10D. The lower ring has a longer radius and grooved outer couplings for non-rotating engagement of the grooved portions on the external reaction socket 16. The internal drive socket 16 and the external reaction socket 17 of the external socket. double actuation 15A are coupled cooperatively and relatively rotating in opposite directions by means of the tool housings and / or other known and / or proprietary means by means of coupling 18.
164) Figures 13A and 13B show the reaction block Z® 17B for use with HYTORC® STEALTH® 10E designed primarily for low distance bolting applications. The reaction block 17B is shaped to fit the dimensions of the STEALTH® 10E and is fixed non-swiveling in the tool housing by means of pins or screws. Reaction block Z® 17B engages non-rotatingly with Washer Z® 1.
165) Z® System Applied to the HYTORC® Displaced Connection. The benefits of the Z® System can be obtained with proprietary double-actuated displaced connections, such as, for example, device 80. Connection 80 is driven by HYTORC®'s proprietary coaxial action and reaction torque tools, such as , for example, the hydraulic torque tool HYTORC® ICE® 10C or pneumatic torque multiplier of the HYTORC® Z® 10B (or 10A) gun. Other tools of this type include Single Speed jGUN® owned by HYTORC®, Dual Speed jGUN® Plus, AVANTI® 10D and / or STEALTH® 10E. These proprietary interchangeable, double-actuated displaced connections are described completely in the following jointly owned copending applications, the complete copies of which are hereby incorporated by reference: Patent Cooperation Treaty Order Serial Number PCT / US2014 / 035375, with filing date of 24 April 2014, entitled "APPARATUS FOR TIGHTENING THREADED FASTE-NERS" and US Patent Application No. 61 / 940,919, with filing date of February 18, 2014, entitled "APPARATUS FOR TIGHTENING THREADED FASTENERS ''.
166) Figures 14A and 14B show top and bottom perspective views of the displaced drive connection set 80, for transmission and torque multiplication of the HYTORC® ICE® 10C to tighten or loosen a threaded fastener (not shown) on Washer Z ® 1. Connection 80 includes a drive power input assembly 81; a set of drive force output 82 and a set of reaction force 83.
167) Generally during a tightening operation, a bottom relief face of Washer Z® 1 rests on a joint to be closed while a bottom face of a nut or screw head to be tightened rests on an upper smooth face of the Arru-ela Z® 1. The outer edges of the Washer Z® 1 engage in a non-rotating manner and react in a recess in an ex-suit reaction socket of reaction force set 83. However, a socket drive power outlet assembly 82 tightens the nut or bolt head on Washer Z® 1.
168) Advantageously, the displacement connection set allows access to fasteners previously unattainable due, for example, to projected threads, limited distances and obstructions; it makes previously unusable electrical, hydraulic, manual and / or pneumatic devices viable, enables previously unusable advanced materials, such as, for example, aeronautical grade aluminum, creates modular components, such as, for example, hexagonal drive reduction and increase, male and female drive adapters to meet the screwing application characteristics; produces precise and personalized torque multiplication; controls the application of the driving force and the reaction force; overcomes problems of corrosion, screw and facial deformation; prevents chafing of the screw thread; cancels the side load; ensures balanced screw load for compression of the symmetrical joint; simplifies the use of the connection and the tool; minimizes the risk of operator error and maximizes screwing safety.
169) The HYTORC® Z® System Used with a HYTORC® Double Sided Friction Washer. According to Figures 15A to 15, it may be necessary to prevent the locknut or screw head from turning depending on the relative friction conditions in play when using the HYTORC® Z® System. If necessary, the operator inserts a proprietary double-sided friction washer HYTORC® 85 under the locknut or head of the screw 22. Its two faces with improved friction 86 and 87 prevent the head of the screw 22 from turning, especially as soon as the load starts to be applied to screw 24. Generally, discussions about friction related to Washer Z® 1 apply to faces with improved friction 86 and 87. Similar benefits are obtained, as in the face of lower support 3 of Washer Z® 1 for the strategic placement of friction improvements on faces 86 and 87.
170) In other words, a proprietary HYTORC® washer system, or double locking washer system includes a first washer provided with means of external reaction force coupling and a friction face for use under a nut or head. screw to be tightened or loosened (such as Washer Z® 1) and a second washer provided with two friction faces for use under a nut or screw head on the other side of the joint (such as double-sided friction washer 85). This duplex plunger washer system prevents the pin or screw from rotating together in order to control friction on the thread and face of the fastener to obtain the best torque translation for screw loading. It should be noted that any treatments for increasing the friction coefficient discussed in relation to the HYTORC® Z® Washer apply to the HYTORC® 85 Double Sided Friction Washer.
171) It should be noted that this double locking washer system can be used with any portion, any combination or all elements of the HYTORC® Z® System. Remember that the torque has unknown friction and the tension has unknown screw relaxation. This washer system can come in a set to eliminate uncontrollable facial friction and uncontrollable side loading to improve the accuracy of the torque and tension screw load.
172) The HYTORC® Z® Pistol (in detail). Referring to Figures 16A and 16B as an example, they are seen in perspective of tools 10A and 10B, originally shown in Figures 3A-3C as the HYTORC Z® Gun. Tools 10A and 10B include: drive input and output set 100; rotating force multiplication set 200; vibrating force set 300; mode change set 400; and double reaction socket and double drive output 15, or the HYTORC® Z® socket.
173) Referring to Figure 17A as an example, a cross-sectional, side view of tool 10A in LSHT mode is shown. Referring to Figure 17B as an example, a cross-sectional, side view of tool 10B in HSLT mode is shown.
174) Figures 17A and 17B show a drive input and output assembly 100 for tools 10A and 10B. The drive input components include the drive housing of the tool 101 containing a drive generator mechanism 102, handle assembly 103 and a switching mechanism 104. Drive generator mechanism 102 generates torque turning force 91 in one direction 93 to rotate the nut 36 and is shown constituted as a means of driving the motor which may include a hydraulic, pneumatic, electric or manual motor. The drive housing of the tool 101 is generally shown as a cylindrical body with cable assembly 103 that is held by an operator. The cable assembly 103 includes a switching mechanism 104 for switching the drive generating mechanism 102 between an inoperative position and an operating position and vice versa. A turning force input shaft 121 connects drive input components of drive input and output assembly 100 to the turning force multiplication set 200 and vibration force set 300 and transfers the force of rotation 91 between them. A turning force output shaft 122 includes a drive part 123 which can be formed, for example, as a square drive. The rotating force output shaft 122 connects drive output components of drive input and output set 100 to the rotating force multiplication set 200 and vibrating force set 300 and transfers a multiplied shape or rotating force vibrated 91 between them and the double actuation reaction and output socket assembly 15. In one operating mode, a grooved reaction force adapter 443 receives torque reaction force 92 in the opposite direction 94 .
175) Figure 18 is a cross-sectional, side view of the turning force multiplication set 200 and vibrating force set 300 of the tool 10A in LSHT mode. Figure 18 also shows portions of drive input and output assembly 100. Components not shown otherwise in other figures include 19% swing force output reduction gear. Figure 19 is a perspective view, in cross section of the drive tool housing assembly 101, drive tool cable assembly 103 and related internal components of tool 10A and tool 10B. Figure 19 shows portions of the drive input and output assembly 100. The components shown include: a rear cable cover 131; a gasket 137 adjacent to the rear cover 131 and the rear part of the housing 101; engine assembly 102; and an air valve assembly 132 having an external air valve 133 and an internal air valve 134 held in place by a dowel pin 135. The rear cover 131 attaches to the rear and is secured to these components in the housing 101 by means of BHCS 136 torque screws. A trigger assembly 150 includes: switching mechanism 104; springs 151; a trigger shaft bushing 152; and a trigger rod 153. Cable 103 includes: a control valve assembly 155 with a control valve 157 and a pin pin 156; a conical spring 161; a regulator valve spacer 162; O-rings 163, one formed between the control valve assembly 155 and an internal regulator housing 164 and one formed between the internal regulator housing 164 and bottom plate 173. A mesh screen 171 is formed between the control plate bottom 173 and a noise filter 172. A cap screw and socket head 174 connects these components and the bottom plate 173 having a gasket 176 on the cable assembly 103. An air connection 175 is extruded from the bottom plate 173 and connects to the internal regulator housing 164. A pushbutton assembly on cable 180 (not shown) allows an operator to change the direction of the pivoting force and includes: a cable insert with pushbutton 181; a rack with push-button 182; a spring 183 and connectors 184.
176) The swing force multiplication set 200 includes: a swing force multiplier mechanism 210 in a housing of the swing force multiplier mechanism 201 substantially for the LSHT mode including a plurality of sets of multiplication transmitters of rotating force. In the modalities shown in Figures 17A and 17B, the force multiplier set 200 includes 5 (five) sets of multiplication transmitters 211, 212, 213, 214 and 215. It should be understood that there are several known types of force multiplier mechanisms. Generally, the rotating force multiplication transmitter sets 211 to 215 constitute the rotating force multiplier mechanism 210 and a system of compound epicyclic gears. It can include a plurality of external planetary gears that revolve around a central sun gear. The planetary gears can be mounted on mobile conveyors that can themselves rotate in relation to the solar gear. These composite epicyclic gear systems may include outer ring gears that engage with planetary gears. Simple epicyclic gear systems have a sun, a ring, a conveyor and a planetary assembly. Composite epicyclic gear systems may include interlaced planetary structures, staggered planetary structures and / or multi-stage planetary structures. Compared to simple epicyclic gear systems, composite epicyclic gear systems have the advantages of a higher reduction ratio, greater torque to weight ratio and more flexible configurations.
177) Rotating force multiplication transmitter sets 211 to 215 may include: gear cages; planetary gears; ring gears; solar gears; oscillatory gears; cycloidal gears; epicyclic gears; connectors; spacers; displacement rings; retaining rings; bushings; bearings; lids; transmission gears; transmission shafts; positioning pins; drive wheels; springs or any combination or portion thereof. Rotating force multiplier transmitters, such as 211 to 215, may include other similar components known as well. It should be noted that the turning force input shaft 121 can also be considered a turning force multiplication transmitter; specifically, it is a first stage solar motor gear for the 211 swing force multiplier transmitter. The swing force multiplier sets are well known and revealed and described. An example is disclosed and described in Applicant's US Patent No. 7,950,309, the entire copy of which is incorporated herein by reference.
178) Figure 18 shows more details of portions of the rotation force multiplication set 200 than Figures 17A and 17B. Rotating force multiplication set of components 200 shown in Figure 18 and not in Figures 17A and 17B include: a locknut 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 and lower inner retaining ring 251; an upper and lower ball bearing 246; a double sealed bearing 244; and an inner retaining ring 245.
179) The vibration force assembly 300 includes a vibration force mechanism 310 in a housing of the vibration force mechanism 301 substantially for HSLT mode including one or a plurality of vibration transmitters. In the modality shown in Figures 17A and 17B, the vibration force set 300 includes two vibration transmitters, specifically impact 311 and 312. It should be understood that there are several known vibration force mechanisms and often involve mechanisms impact force consisting of a stop and a rotating hammer. The hammer is rotated by the engine and the stop has a rotating resistance. Each impact provides a hammer force that is passed on to the output drive.
180) Generally, vibration force sets can include vibration force mechanisms, such as ultrasonic force mechanisms including ultrasonic force transmitters; mass unbalance force mechanisms including mass unbalance force transmitters, or any other time-varying force mechanism (load, displacement, spin or speed) including time-varying force disturbance transmitters (load, displacement, turn or speed). Additional vibrating power sets may include: hammers; stops; connectors; spacers; displacement rings; retaining rings; bushings; bearings; lids; transmission gears; transmission shafts; positioning pins; drive wheels; springs or any combination thereof. Vibration transmitters like 311 and 312 can include other similar components known as well. Figure 18 also shows a dowel pin 320.
181) Generally, the RPMs of tools 10A and 10B decrease when the torque output increases. The activation or deactivation of the vibration force mechanism 310 may alternatively be such that when the RPMs fall or increase beyond a predetermined number, the vibration force mechanism 310 becomes inefficient or effective. In HSLT mode, the vibration force mechanism 310 provides a turning force to the nut. In LSHT mode, the vibration force mechanism 310 acts as an extension to transfer the turning force from one part of the tool to another. It should be noted that the vibration force mechanism 310 may be located close to the tool motor, close to the tool output drive or anywhere in between.
182) In HSLT mode, the vibration force mechanism 310 always receives a rotating and rotating force; the housing may or may not receive a turning force; and the torque output is relatively low, which is because the housing does not need to react. It should be noted that in the modalities of Figures 17A and 17B, the vibration force mechanism 310 is operable only in a higher speed mode, such as the HSLT mode. This, in turn, means that with a lower speed, when the torque-intensifying mechanism is operable, such as the LSHT mode, there is no impact and / or minimal vibration. During HSLT mode, at least two multiplication transmitters are unitary and rotate with the hammer to increase inertia and assist in the hammer movement of the impact mechanism. It should be noted that when a fastener shows little or no corrosion, thread and facial deformation and / or thread seizure, the 310 vibration force mechanism may not be required in HSLT mode.
183) Sliding action mode change set 400 is substantially for switching 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 slide action mode change set 400 includes: a displacer base 401; a displacer collar 442; a grooved displacer pivot 443; a grooved ring of the displacer 445; an outer displacement ring 456 and an inner displacement set 450. The inner displacement set 450, as illustrated in Figures 17A and 17B includes: an inner displacement bushing 452; an inner displacement ring 453 and coupling ball bearings 454.
184) Sliding action mode change set 400 may include: manual sets (sequential, unsynchronized or preselector manual) or automatic sets (pneumatic, semi-automatic, electro-hydraulic, saxomatic, double or continuously variable clutches); torque converters; bombs; planetary gears; clutches; tracks; valves; connectors; spacers, displacement rings; retaining rings; bushings; bearings; necklaces; blocking spheres; lids; transmission gears; transmission shafts; synchronizers; positioning pins; drive wheels; springs or any combination or portion thereof. The mode change components can include other similar components known as well. It should be understood that there are several well-known shifting sets and often involve shifting components consisting of necklaces, rings and locking spheres.
185) Figure 18 shows more details of portions of the slide action mode change set 400 than Figures 17A or 17B. Additional components of shift set 400 shown in Figure 18 and not shown in Figures 17A and 17B include: internal retaining rings 451, 457 and 459; a lower bushing and an upper bushing 446 and 447; and displacer ring reaction plugs 458. Figure 20 is a perspective view of the 400 mode change assembly of tool 10A and tool 10B. Figure 20 shows substantial external portions of the 400 mode shift assembly. Components not otherwise shown in other Figures include: a locking shaft cover 402; a 403 cable insert; a handle of the 404 cable; a cable for pulling 405; an actuator pin and displacer pin 406; a pivot pin 407; a displacement extension support 410; SHCS 411; a set of shifter fixer 430; a connection of the upper and lower displacer 441; a corrugated spring 448 and a support slot 449.
186) Referring again to Figures 5A to 5D, they show a perspective and cross-sectional view of a set of drive output and reaction socket 15 of tool 10A and tool 10B and the set of double drive output and socket reaction 15A of tool 10C and tool 10D.
187) In LSHT mode, the double actuated output and reaction socket assembly 15 is substantially to transfer a multiplied form of turning force 91 to nut 36 in one direction 93 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 drive output and reaction socket 15 assembly is substantially to transfer a vibrating form of turning force 91 to nut 36 or nut 36 and washer 1 in a direction 93. In the embodiment shown in Figures 17A and 17B, the double drive output set and reaction socket 15 includes an internal drive socket 16 and an ex-suit reaction socket 17. The external reaction socket 17 is non-switchable on the grooved displacer pivot of reaction force 443 during LSHT mode. It should be understood that there are several known coupling mechanisms for transferring turning and reaction forces to threaded fasteners and nuts and washers, including denticulation, groove and other geometries.
188) Tool 10A operates according to the following in LSHT mode. The operator pulls the base of the displacer 401 towards a rear position. The coupling / locking ball bearings 454 disengage from the housing of the rotating force multiplier mechanism 201 and engage the grooved ring of the displacer 445 within the pivot of the grooved reaction force displacer 443. The displacer base 401 is coupled to the housing of the displacement swing force multiplier mechanism 201. swing force multiplier transmitters 211 to 215 are unlocked and free to rotate relative to each other. When the operator pulls the base of the displacer 401 towards a rear position, he also engages the grooved vibration force (impact) ring of the change set 453 in the housing of the vibration force (impact) mechanism 301. This locks the vibration force (impact) transmitters 311 and 312 and thus the vibration force (impact) set 300. This allows the rotating force output drive shaft 120 to be driven by the fifth gear cage of the rotating force multiplication transmitter 215, which is engaged in the groove of the vibration force (impact) mechanism housing 301. The grooved displacer pivot 443 is engaged in the groove of the reaction socket 17. And the reaction 17 is geometrically engaged in washer 1 under nut 36. With the nut 36 in place, the washer of the compressed locking disc 1 serves as a stationary object by which the housing of the rotating force multiplication mechanism 201 reacts outside the socket and reaction 17. With the rotating force multiplication set 201 housing held still, the rotating force multiplication transmitters 211 to 215 tighten the seated nut 36 by means of the power output drive shaft. of rotation 120.
189) Generally, the operation of tool 10B requires activation or deactivation of the impact mechanism 310. The slide action mode change set 400 can change the tool 10A between: the multiplication mechanism 210; impact mechanism 310; part of the multiplication mechanism 210 (such as, for example, one of the plurality of multiplication transmitters); part of the impact mechanism 310 (such as, for example, one of the plurality of impact transmitters); or any combination thereof.
190) Tool 10B works as follows in HSLT mode. The operator pushes the base of the displacer 401 towards a forward position. The coupling / locking ball bearings 454 engage the housing of the rotating force multiplying mechanism 201 and the housing of the vibrating force (impact) mechanism 301. The grooved ring of the displacer 445 disengages from the pivot dislocator groove of internal reaction force 443, thus making it idle and inactive. Therefore, the reaction socket 17 is idle and inactive because it is not engaged by a groove in the housing of the swing force multiplication mechanism 201. With the coupling / locking ball bearings 454 engaged in the housing of the swing force multiplication mechanism 301, the rotating force multiplication transmitters 211 to 215 are blocked and unable to rotate relative to each other. Thus, the rotating force multiplication set 200 rotates as a unit mass through the rotating force input shaft 121. Motor 102 rotates the rotating force input shaft 121 which includes the primary motor gear -first stage of the rotating force multiplication transmitter 211. When the operator pushes the base of the displacer 401 towards a forward position, he also disengages the slotted vibration force (impact) ring of the change set 453 of the housing- vibration force (impact) mechanism 301. This locks the vibration force (impact) transmitters 311 and 312 and thus the vibration force (impact) set 300. The housing of the vibration force (impact) mechanism vibration (impact) 301 is engaged by groove in the fifth gear cage of the rotating force multiplier transmitter 215. The vibration force (impact) transmitter 312 (stop) is engaged by groove in the power output drive shaft of rotation 120, which raises or lower nut 36 on pin 23 by the impact of the vibration force transmitter (impact) 311 (hammer).
191) Referring again to Figures 3A to 3C and Figures 4A-4B, generally and from the perspective of nut 36, tool 10A tightens, loosens or tightens and loosens nut 36 in LSHT mode. And tool 10B raises, lowers or raises and lowers nut 36 in HSLT mode. Generally, from the perspective of washer 1, tool 10A, in LSHT mode: pressurizes washer 1 '' between the tightened nut 36 '' on the loaded pin 23 '' and the tightened joint 30 '' at the predetermined tightening torque; and / or compress the washer 1 'between the nut seated 36' on the pre-loosened pin 23 'on the pre-loosened joint 30' from the predetermined tightening torque. Generally, from the perspective of the washer 1, the tool 10B, in HSLT mode: compresses the washer 1 'between the nut seated 21' on the preloaded pin 23 'on the pre-tightened joint 30' at the predetermined pre-tightening torque; decompress washer 1 between nut 36 on pin 23 at the loosened joint 30 of the predetermined pre-tightening torque; the pressurized washer vibrates 1 '' between the tight nut 21 '' on the loaded pin 23 '' on the tight joint 30 '' to properly spray the screw thread corrosion. It should be noted that the reference numbers with 'and' 'represent similar magnitudes of force.
192) During HSLT mode, tool 10B: lower nut 36 or nut 36 and washer 1 on pin 23 with turning force 91 in a direction 93 to seat nut 36 'and compress washer 1' on pin preloaded 23 'in the pre-tightened joint 30' up to a predetermined pre-tightening torque; raise the seated nut 36 'or the seated nut 36' and the compressed washer 1 'on the pre-loosened pin 23' on the pre-loosened joint 30 'with the turning force 92 in an opposite direction 94 of the predetermined pre-loosening torque ; or vibrate (im- pacta) the tight nut 36 '' on the pressurized washer 1 '' to apply vibration to properly spray the corrosion of the thread. During LSHT mode, tool 10A: tighten the nut 36 'on the compressed washer 1' on the preloaded screw 23 'on the pre-tightened joint 30' with the turning force 91 in an opposite direction 93 to the predetermined tightening torque and applies reaction force 92 in an opposite direction 93 to the compressed washer 1 '; or loosen the tight nut 36 '' on the pressurized washer 1 '' on the loaded pin 23 '' on the tight joint 30 '' with the turning force 92 in the opposite direction 94 from the predetermined tightening torque and apply reaction force 91 in a 93 direction to the 1 '' pressurized washer. It should be noted that the reference numbers with 'and' 'represent similar magnitudes of force.
193) During operation, tool 10A changes from LSHT mode to tool 10B in HSLT mode after removing nut 36 and de-compressing washer 1 at the predetermined pre-loosening torque. During operation, tool 10B changes from HSLT mode to tool 10A in LSHT mode after nut 36 is installed and decompress washer 1 at the predetermined pre-tightening torque; or adequate spraying of thread corrosion. It should be noted that the operator uses the 400 mode change set to switch the tool from LSHT mode to HSLT mode or vice versa, but that switching may include other similar components known as well. It should be noted that the 400 mode change set is a manual switch, but it can be automatic. Similarly, note that the activation or deactivation of the set of vibration force (impact) 300 can occur manually or automatically. It should be noted that the LSHT mode can be switched from the regulated torque to assisted by vibration or vice versa and that the HSLT mode can be changed from regulated by vibration to assisted by torque or vice versa. It should be noted that the vibration force (impact) assembly 300 can continue to operate even if washer 1 starts or stops rotating. And it should be noted that the LSHT mode can be assisted by vibration to loosen nut 36 to help overcome chemical corrosion, heat and / or lubrication and prevent seizure of the screw thread.
194) It should be noted that power tools for tightening and loosening industrial fasteners with reduced grip according to the present invention can also be characterized by the fact that: the housing of the rotating force multiplication mechanism 201 is operationally connected to at least one rotating force multiplication transmitter 211 to 215; during LSHT mode, at least two multiplication transmitters 211 to 215 rotate relative to each other; and during HSLT mode at least two multiplication transmitters 211 to 215 are unitary to assist the hammering movement provided by the swing force impact mechanism 310. During HSLT mode, the power output drive shaft of rotation 120 and the combination of the rotation force multiplication set 200 including its housing rotate as a unit mass in the same direction. This creates inertia that improves the torque output of the impact mechanism to overcome corrosion, thread and face deformation and to prevent seizure of the screw thread.
195) Tightening and loosening methods with reduced seizure of two parts are revealed with reciprocal industrial fasteners 20 of the type that has nut 36, washer 1 and pin 23 with an electric tool (10A and 10B) of the type having: motor 102 to generate a turning force; a drive (122 and 123) for transferring turning force 91; swing force multiplication mechanism 210 in housing swing force multiplication mechanism 201 for LSHT mode including swing force multiplication transmitters 211 to 215; vibration force mechanism 310 for HSLT including vibration transmitters 311, 312; drive socket 16 operatively connected to nut 36; reaction socket 17; during LSHT mode, operationally connected to washer 1 to transfer reaction force 92 to washer 1; and during HSLT mode, operationally connected or operationally disconnected from washer 1. This method including, where tightening includes: placing washer 1 on a free end of pin 25; place nut 36 on washer 1 at the free end of pin 25; lower, in HSLT mode, nut 36 or nut 36 and washer 1 at the free end of pin 25 to a predetermined pre-tightening torque to seat nut 36 and compress washer 1; switch from HSLT mode to LSHT mode; and tighten with torque application, in LSHT mode, the nut 36 seated to a predetermined tightening torque and pressurize the washer 1 between the tight nut 36 and the tight joint 30; loosening includes: placing tool 10A on tight nut 36 and pressurized washer 1; loosen by applying the torque, in LSHT mode, the tightened nut 36 on the pressurized washer 1 to a predetermined loosening torque; switch from LSHT mode to HSLT mode; and raise, in HSLT mode, the seated nut 36 or seated nut 36 and the compressed washer 1 at the free end of pin 25. The loosening method also includes: vibrating, in the HSLT mode, the tight nut 36 on the pressurized washer 1 to apply vibration to spray the screw thread corrosion and switch from HSLT mode to LSHT mode.
196) Tools 10A and 10B above and tools 10F, 10G, 10H and 10I below, are generally described as power tools for tightening and loosening with reduced grip, an industrial threaded type fastener having a coaxial reaction surface, a pin and a threadable nut with the pin or pin head connected to the pin. The tools 10A, 10B, 10F, 10G, 10H and 10I include: a motor to generate a turning force; a drive to transfer the turning force; a turning force multiplication mechanism in a housing including a turning force multiplication transmitter for all torque modes from the lowest resistance to the highest resistance; and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable during all torque modes from the lowest resistance to the highest resistance.
197) Alternatively, tools 10A and 10B above and tools 10F, 10G, 10H and 10I below are described as electric tools for tightening and loosening with grip reduction an industrial fastener of the type having a nut, washer and a pin, the tools including: a motor to generate a turning force; a drive to transfer the turning force; a rotating force multiplying mechanism in a housing including a rotating force multiplying transmitter for a continuous torque mode; a vibration force mechanism including a vibration transmitter for: an intermittent torque mode; an intermittent force mode; or both intermittent torque and intermittent force modes.
198) With reference to Figure 21A, as an example, a cross-sectional view of a modality of the present invention such as the 10F tool, an electric tool for tightening, loosening or both tightening and loosening, with flu reduction is shown. - gem, an industrial threaded fastener 801 of the type provided with a pin and nut that can be threaded with the pin. The 10F tool includes: a drive input and output set 810; a set of rotation force multiplication 820; a set of vibrating force 830; a 840 mode change set; and a set of drive output socket and reaction arm 850.
199) With reference to Figure 21B, as an example, a cross-sectional view of a modality of the present invention as a 10G tool is shown. The 10F and 10G tools are similar, as noted by the doubling of the reference numbers. The 10G tool is a reaction tool with a free arm for tightening, loosening or both tightening and loosening, with reduced grip, an 802 threaded type industrial fastener having a coaxial reaction surface, such as a HYTORC® Washer Z® 1, a pin and nut that can be threaded with the pin. The 10G tool includes: a set of drive input and output 810; a rotating force multiplication set 820; a set of vibrating force 830; a 840 mode change set; and 855 double-action outlet and reaction socket set, which is similar to the HYTORC® Z® 15 socket.
200) The 10F and 10G tools include a rotating force multiplying mechanism with one or a plurality of gear stages. A vibration force mechanism includes: a rotating force impact mechanism having a hammer and a stop; and an intermittent force mechanism 860 of an ultrasonic force mechanism including an ultrasonic force transmitter; a mass imbalance force mechanism including a mass imbalance force transmitter, or any other time-varying disturbance force transmitter (load, displacement, spin or speed). Tool 10F represents a modified HYTORC® THRILL® Gun including 860 intermittent force mechanism. Tool 10G represents a modified HYTORC® Z® Gun including 860 intermittent force mechanism.
201) With reference to Figure 22A, as an example, a cross-sectional view of a modality of the present invention is shown, such as the 10H tool, an electric tool for tightening, loosening or both tightening and loosening, with reduction of flu. - gem, an industrial threaded fastener 901 of the type equipped with a pin and nut that can be threaded with the pin. The 10H tool includes: a 910 drive input and output assembly; a turning force multiplication set 920; a set of vibrating force 960; a 940 mode change set; and a 950 drive output socket and reaction arm assembly.
202) With reference to Figure 22B, as an example, a cross-sectional view of a modality of the present invention such as tool 10I is shown. The 10H and 10I tools are similar, as noted by the doubling of the reference numbers. The 10I tool is a power tool with a free arm to tighten, loosen or both tighten and loosen, with reduced grip, an industrial threaded fastener type 901 having a coaxial reaction surface, such as, for example, a HYTORC® Washer Z® 1, a pin and nut that can be threaded with the pin. Tool 10I includes: a set of 910 drive input and output; a rotating force multiplication set 920; a set of vibrating force 960; a 950 mode change set; and 955 double-action outlet and reaction socket set, which is similar to the HYTORC® Z® 15 socket.
203) Tools 10H and 10I include a rotating force multiplying mechanism with one or a plurality of gear stages. A 960 vibration force mechanism includes 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 force transmitter (load, displacement, turn or speed) including a time-varying force transmitter (load, displacement, turn or speed). The 10H tool represents a modified HYTORC® jGUN® Dual Speed Gun including 960 intermittent force mechanism. The 10I tool represents a modified HYTORC® jGUN® Dual Speed Gun including 960 intermittent force mechanism and a dual actuation and output assembly. reaction socket 955, which is similar to Socket HYTORC® Z®15.
204) In addition to tools 10A, 10B, 10G and 10I, the drive socket is connected to the nut in an operational manner. The reaction socket can be operationally connected to the housing and the coaxial reaction surface during the highest resistance torque mode to transfer a reaction force to the coaxial reaction surface. Alternatively, the reaction socket can be operationally connected to the coaxial reaction surface and housing or operationally connected to the housing and operationally disconnected from the coaxial reaction surface during the lowest resistance torque mode. or the inmittent force mode. The drive socket is shown as an internal socket and the reaction socket is shown as an external socket.
205) The following discussion refers to tools 10A, 10B, 10F, 10G, 10H and 10I. It should be noted that in order to facilitate the description, any reference to a "nut" or "fixer" includes the possibility of: a pin head fixed to a pin; a nut and washer on and / or on a pin; a pin head attached to the pin and a washer on the pin. It should be noted that any suitable fastener geometry can be used with the present invention, such as, for example: an allen key connection; a socket cam screw head ("SSC"; a socket head button screw head ("SHBS"); a hexagon cap screw head ("HHCS"); a round screw head and slotted ("RHSS"); a flat torx screw head ("FHTS"); a socket adjusting screw head ("SSS"); or a cap screw head with socket head "(SHCS ").
206) These discussions describe the coaxial reaction surface as a washer. In some cases, however, the washer may be integrally formed or be joined to a joint to be tightened or loosened. In other cases, the coaxial reaction surface is a portion of the pin that extends beyond the nut. In still other instances, a coaxial reaction arm rests on a viable and accessible stationary object for tightening and loosening with reduced grip.
207) Washer 1 is usually shown as a flower washer with a serrated bottom face to provide the reaction torque. According to Figures 8A to 8L, note that almost any external shape that engages without rotation in the reaction sockets, plates and connections of the present invention is suitable. It should also be noted that almost any surface characteristic that increases facial friction is adequate. Examples of external shapes include: any suitable geometric shape such as pentagon, hexagon, octagonal, etc .; protrusions, cutouts, pressed holes, dentications, etc. Examples of improved surface friction characteristics include: patterns; finishes; treatments; coatings; leafings; roughness, etc. In an inventive way, even before the nut and / or the screw head is seated, the coaxial reaction surface becomes a viable and accessible coaxial stationary object on which the reaction forces of the tools are transferred.
208) Generally, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following during the inmittent force mode. Tools can descend through the nut or nut and washer with intermittent turning force in one direction. Tools can move up the nut or nut and washer with intermittent turning force in the opposite direction. Either tools can impact, vibrate or both impact and vibrate the nut or nut and washer with an intermittent turning force to apply vibration and rotation in the opposite direction, the intermittent vibrating force to apply vibration, or both.
209) More specifically, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following during intermittent force mode. Tools can descend through the nut or nut and washer with intermittent turning force in one direction to set the nut in a restrictively rotating state with significant adverse bolting application characteristics to a predetermined pre-tightening torque state and compress the washer between a joint to be tightened and the seated nut. Tools can move up the nut or nut and washer with the intermittent turning force in the opposite direction to remove the nut from the predetermined pre-tightening torque state to the restrictively rotating state with significant adverse bolting application characteristics and decompress the washer between the joint to be loosened and the nut removed. Either tools can impact, vibrate or both, the nut or nut and washer with an intermittent turning force to apply vibration and rotation in the opposite direction, the intermittent vibrating force to apply vibration, or both, from a corrosive state inappropriately sprayed thread to a properly sprayed thread corrosion state. For example, tools can generate ultrasonic sound waves through an ultrasonic wave generator, such as a 960 vibration force mechanism to vibrate the fastener at ultra-high speeds to spray thread corrosion.
210) Often, intermittent force (impact, vibration, ultrasonic, etc.) is required when descending to firmly compress the washer between the nut and the face of the flange. Absent this compression caused by impact, the washer may not assume the reaction force due to two frictions on the two washer faces. When properly compressed, the face of the washer that rests on the nut receives a rotating friction in a clockwise direction because of the torque output of the tool and an equal and opposite rotating friction in a counterclockwise direction because of the reaction force. As such, the turning friction of the washer face that touches the flange face prevents the washer from turning. In other words, the tool is designed to keep the washer stationary during the rotation of the nut, which eliminates the usual side load and differences in surface from nut to nut. Better control of surface friction and thread is obtained for better torque translation for the fastener load.
211) Generally, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following during the highest resistance torque mode. Tools can tighten the nut at a lower speed, greater torque turning force in one direction and apply a reaction force in a direction opposite to the washer. And / or tools can loosen the nut at a lower speed, greater torque turning force in the opposite direction and apply the reaction force in the opposite direction to the washer.
212) More specifically, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following during the highest resistance torque mode. The tools can tighten the nut at a lower speed, greater 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 direction opposite the washer to pressurize the washer between the loosened joint and the tight nut. And / or tools can tighten the nut down with the lowest speed, higher torque turning force in the opposite direction to loosen the nut from the predetermined pre-tightening torque state to a predetermined tightening torque state and apply the reaction force in one direction to the washer to depressurize the washer between the loosened joint and the loosened nut.
213) Generally, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following during the lowest resistance torque mode. Tools can descend through the nut or nut and washer with a higher speed rotating force and lower torque in one direction. And / or the tools can go up through the nut or nut and washer with the highest speed rotating force and the lowest torque in the opposite direction.
214) More specifically, tools 10A, 10B, 10F, 10G, 10H and 10I can do any of the following during the lowest resistance torque mode. Tools can descend through the nut or nut and washer with the highest rotating force and lowest torque in one direction to set the nut in a freely rotating state with negligible adverse bolting application characteristics to the pre torque state - predetermined tightening and compress the washer between the joint to be tightened and the seated nut. And / or the tools can rise through the nut or nut and washer with the highest speed rotating force and lowest torque in the opposite direction to remove the nut from the predetermined pre-tightening torque state to the freely rotating state with characteristics of application of insignificant warning screws and decompress the washer between the joint to be loosened and the nut removed.
215) Generally, tools 10A, 10B, 10F, 10G, 10H and 10I can tighten, loosen or tighten and loosen the nut in the highest resistance torque mode. Tools can rise, fall or impact the nut or nut and washer in intermittent torque mode or in the lower resistance torque mode. The tools can change from the intermittent torque mode to the higher resistance torque mode after seating the nut and compressing the washer to the predetermined pre-tightening torque state and / or proper spraying of the thread corrosion. The tools can switch from the higher resistance torque mode to the intermittent torque mode and / or the lower resistance torque mode by removing the nut and decompressing the washer in the predetermined pre-loosening torque state. The tools can change from the lowest resistance torque mode to the highest resistance torque mode after seating the nut and compressing the washer to the predetermined pre-tightening torque state.
216) In operation, tools can change: from the highest resistance torque mode to the intermittent torque mode; from the highest resistance torque mode to the lowest resistance torque mode; from the lowest resistance torque mode to the intermittent torque mode; from the lowest resistance torque mode to the highest resistance torque mode; from intermittent torque mode to the highest resistance torque mode; or from blinking mode to the lowest resistance torque mode.
217) The activation or deactivation of the vibration mechanism or the torque multiplication mechanism can occur manually or automatically. In this way, the switching mechanism can be manual or automatic. In addition, the switching mechanism and therefore any mode or combination of modes and corresponding mechanisms can be activated automatically according to the load on the fastener. For example, a seized reduction power tool of the present invention may need vibration and / or impact to spray corrosion onto a tightened fastener and raise or lower the nut at high speed. The nut tightened with torque cannot only rotate with vibration and / or impact. An operator may need to activate vibration and / or impact to spray dry corrosion onto the torque tightened nut, which may occur independently or in combination with the torque multiplication mechanism. As noted, the torque required to loosen the nut is greater than the initial tightening torque because lubrication has dried or disappeared, corrosion is present and the pin is still loaded and extended. In other words: higher torque values are needed to unload and release the pin. As soon as the nut is loosened it can be turned at a higher or higher speed during the lower resistance torque mode and / or intermittent torque mode. However, the nut may have to get rid of corroded and / or damaged or defective pin threads. This often requires vibration and / or intermittent force in combination with the torque multiplication mechanism. When descending, the nut is turned at a higher speed during the lower resistance torque mode and / or intermittent torque mode. Here, too, the lower resistance torque mode alone may not be sufficient to overcome problems with corroded and / or damaged or defective pin threads. Similarly, vibration or intermittent force and / or intermittent force combined with the torque multiplying mechanism is often required for this purpose. The present invention solves these problems.
218) Generally, methods are described for tightening and / or loosening, with reduction of seizure, an industrial threaded fastener of the type that has a coaxial reaction surface, a pin and a nut that can be threaded into the pin or a head. pin connected to the pin with a free-arm electric reaction tool of the type it has: a motor to generate a turning force; a drive to transfer the turning force; a rotating force multiplying mechanism in a housing including a rotating force multiplying transmitter for all torque modes from the lowest resistance to the highest resistance; and at least one vibration force mechanism including a vibration transmitter for an intermittent force mode operable during all torque modes from the lowest resistance to the highest resistance. The tightening method includes: descending in one direction by the nut, the pin head, the nut and the coaxial reaction surface or the pin head and the coaxial reaction surface; and firmly tighten the nut or the pin head in one direction while reacting in the opposite direction off the coaxial reaction surface. The loosening method includes: loosening with torque in the opposite direction to the nut or pin head while reacting in one direction of the coaxial reaction surface; and raising in the opposite direction, the nut, the pinhead, the nut and the coaxial reaction surface or the pinhead and the coaxial reaction surface;
219) The discussion that follows refers to the configurations of the electric reaction tools with free arm to tighten and loosen, with reduced grip, industrial fasteners according to the present invention. Note that similar items are interchangeable, such as: intensifier, multiplier and multiplication; impact and impact.
220) More specifically, in an impact mode mode, the tool housing and gear stages remain stationary while the impact hits. When the impact mechanism is far from the motor, the motor axis passes through the center of the multipliers to the impact mechanism and from there to the output drive. When the impact mechanism is immediately after the engine and in front of the multipliers, the engine activates the impact mechanism and the axis passes through the impact mechanism through the center of the multipliers and goes to the output drive.
221) In another mode of the impact mode, the tool housing and the gear stages rotate in unison while the impact hits blocking the gear stages. This can be accomplished by connecting: the solar gear to the ring gear; the solar gear with the gear cage; or the gear cage with the ring gear of a planar stage. In each case, all the gear cages and the housing act as an extension of rotation from the motor to the impact mechanism or from the impact mechanism until the tool output drive.
222) In another mode of impact mode, the tool housing remains stationary and the gear cages rotate in unison while the impact hits blocking the gear cages together. When the impact mechanism is away from the engine, the gear cage (s) acts (s) as an extension within the engine housing to the impact mechanism. When the impact mechanism is immediately after the engine and in front of the multipliers, the gear cages act as an extension within the impact mechanism housing to the tool's output drive.
223) Generally, during LSHT mode, at least two multiplication transmitters rotate in relation to each other. In multiplier mode, the tool housing always rotates in opposition to the solar gears and the output shaft of the multipliers, which is why the tool housing has to react. When the torque is intensified 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's output trigger, the impact mechanism will not impact if it rotates with the last solar gear. If the impact mechanism is located before the multiplier and close to the engine, the impact mechanism rotates at high speed and needs to be blocked.
224) In a modality in which the impact mechanism is far from the engine, the following occurs: the impact mechanism remains stopped while the multipliers rotate; the motor output shaft goes to the multiplier to multiply the torque; and the last solar gear extends through the impact mechanism to the output drive. When the impact mechanism is immediately after the engine and in front of the multipliers, the motor drive shaft passes through the impact mechanism to the multiplier for torque multiplication and the last solar gear extends to the output drive.
225) In another mode, the impact mechanism rotates at the speed of the last solar gear of the force multipliers. When the impact mechanism is far from the motor, the motor output shaft goes to the multiplier for torque multiplication and the last solar gear rotates the impact mechanism which rotates the tool output shaft. When the impact mechanism is immediately after the engine and in front of the multipliers, turning the impact mechanism to rotate the multipliers would result in an impact, which should be avoided. On the other hand, the impact mechanism can be blocked by locking the hammer with the impact housing or locking the hammer with the stop. The impact mechanism acts as an extension between the motor output drive and the first multiplier solar gear.
226) The speed of the last solar gear in the multiplier may be high enough to operate the impact mechanism. The impact of the tool output shaft can be avoided by blocking the hammer with the impact housing, the hammer with the impact stop with the tool housing or the hammer with the tool housing.
227) In a specific LSHT mode, the multiplication mechanism is close to the engine and before the impact mechanism. The motor bypasses the multiplication mechanism and extends its output force through at least part of the multiplication mechanism by means of a pin in the direction of the output drive. In a specific modality of the LSHT mode, the impact mechanism is close to the engine and before the multiplication mechanism. The impact mechanism extends its output force through at least part of the multiplication mechanism by means of a pin in the direction of the output drive.
228) The power tool for tightening and loosening industrial fasteners with seizure reduction according to the present invention is described here as having two or three modes, higher torque mode and lower speed, lower torque mode and speed higher and intermittent force mode. It must be understood that the at least two modes described here are merely exemplary. Other modes can be added to either mode and / or to the input and / or output means. It should be understood that the present invention is not limited to just two speeds, but can have multiple speeds. For example, known torque-intensifying tools are usually driven by pneumatic or electric motors. Often, the power output and rotation speeds of these engines are increased or decreased by means of planetary gears or the like, which can become part of the engine. Often, known torque boosting tools eliminate one or more boosting means to increase the rotational speed of the tool motor. Other known torque-enhancing tools use gear intensification and / or reduction mechanisms as stand-alone components or adjacent to the engine to increase and / or decrease shaft rotation speeds. The present invention can also include these gear intensification and / or reduction mechanisms as stand-alone components, as multiplication transmitters and part of the multiplication mechanism 210 or as vibration transmitters and part of the 310 vibration mechanism. multiplication 200 can be configured to have multiple multiplication transmitters contained in multiple housings in the multiplication set.
229) It should be understood that each of the elements described above, or two or more together, can also find a useful application in other types of constructions other than the types described above. The characteristics revealed in the preceding description, or in the claims that follow, or in the accompanying drawings, expressed in their specific forms or in terms of a means to perform the revealed function, or a method or process to achieve the revealed result, as the case may be , can, separately or in any combination of these characteristics, be used to carry out the invention in different ways. It should be noted that the descriptions of numbered components may differ slightly in the specification.
230) Although the invention has been illustrated and described as being carried out on a hydraulic control tool, it is not intended to be limited to the details illustrated, since various structural modifications and alterations can be made without escaping in any way from the scope of the present invention.
231) Without further analysis, the description above reveals so completely the essence of the present invention that others, applying current knowledge, will be able to readily adapt it for various applications without omitting characteristics that, from the point of view of the previous technique. later, clearly constitute the essential characteristics of the generic or specific aspects of this invention.
232) When used in this report and in the claims, the terms “comprising”, “including”, “having” and variations thereof mean that the characteristics, steps or integers are included. The terms should not be interpreted in such a way as to exclude the presence of other characteristics, stages or components.

权利要求:
Claims (22)
[0001]
1. “REACTION WASHER” to receive the opposite torque generated due to the tightening or loosening of a threaded fastener, characterized by the fact that it includes: - An outer edge (6) having a geometric shape that allows the rotating coupling with a power tool (10); and - A lower surface (3) having treatments (7) to increase the coefficient of friction inclined in outward areas from a central hole (5).
[0002]
2. “REACTION WASHER”, according to claim 1, characterized by the fact that the treatments (7) to increase the friction coefficient are selectively inclined towards the outer edge (6).
[0003]
3. “REACTION WASHER” according to claim 1, comprising an effective friction radius RIK of the washer (1) is greater than the effective friction radius of the threaded fastener (20) for use with a fixing socket assembly (15) including: - An internal socket (16) having an internal edge with means of engaging nut (36) or screw head (22); - an external socket (17) having an inner edge with a reaction washer engaging means for engaging the outer edge (6) of the reaction washer (1); characterized in that the inner socket (16) is substantially disposed within the outer socket (17) and the inner socket (16) and the outer socket (17) are coupled to a mechanism that allows the inner socket (16) and the outer socket (17) are rotated, cooperatively or relatively, in opposite directions.
[0004]
4. "REACTION WASHER" according to claim 3, characterized by the fact that the outer edge (6) of the washer (1) extends substantially beyond the outer edge of the threaded fastener (20).
[0005]
5. “REACTION WASHER”, according to claim 4, characterized by the fact that a reaction supporting force received by the outer edge (6) of the washer (1) is slightly larger than an action torque received by an outer edge of the threaded fastener (20).
[0006]
6. “REACTION WASHER”, according to claim 1, characterized by the fact that the treatments (7) for increasing the friction coefficient are positioned substantially beyond an effective friction radius of a nut (36) or head ( 1) screw (20) around the lower surface (3) of the washer (1).
[0007]
7. “REACTION WASHER” according to claim 1, characterized by the fact that the bottom surface (3) includes a smooth surface (3) The one formed between the central hole (5) to accept the screw (20) and treatments (7) to increase the friction coefficient.
[0008]
8. "REACTION WASHER" according to claim 3, characterized by the fact that the outer edge (6) of the washer (1) and its engaging means that are substantially vertical engage with an inner edge of an external socket ( 17) and their coupling means which are substantially vertical.
[0009]
9. “REACTION WASHER” according to claim 3, characterized by providing suitable geometries that include: - Concave portions (6) extending inward and convex portions extending outward that are supplied, alternately and repeatedly in a radial direction around a central point of the washer (1); or - Any geometric shape such as triangle, curvilinear triangle, square, rectangle, parallelogram, rhombus, trapezoid, trapezoid, rhombus, pentagon, hexagon, heptagon, octagon, eneagon, decagon, circle with external projections, ellipse or oval.
[0010]
10. “REACTION WASHER”, according to claim 1, characterized by the fact that it includes a conical lower edge portion (8) formed between the outer edge (6) and the lower surface (3) and extending to in relation to an outer edge of the threaded fastener (20) and downwards in relation to the outer edge.
[0011]
11. “REACTION WASHER” according to claim 3, characterized by the fact that it includes a conical lower edge portion (8) extending inwardly in relation to an outer edge of the nut (36) or the head ( 22) screw (20), formed between the outer edge (6) and the bottom surface.
[0012]
12. “FIXING SOCKET ASSEMBLY” including: - An internal socket (16) having an internal edge with a nut (36) or pin head (22) coupling means (20); and - an outer socket (17) having an inner edge with a reaction washer engaging means (1) for engaging the outer edge of the reaction washer (1) of claims 1 to 11, characterized by the fact that the inner socket (16) is substantially disposed within the outer socket (17), the inner socket (16) and the outer socket (17) being coupled together with a mechanism that allows the inner socket (16) and the outer socket (17 ) are rotated, cooperatively and relatively, in opposite directions.
[0013]
13. "FIXING SOCKET ASSEMBLY", according to claim 12, characterized by the fact that the inner edge of the outer socket (17) and its coupling means and the outer edge (6) of the washer (1) and its engagement means are substantially vertical.
[0014]
14. "FIXING SOCKET ASSEMBLY" according to claim 12, characterized by the fact that the outer socket (17) includes an outer lower edge having a tapered inward surface towards the bottom of a lower inner edge.
[0015]
15. “FIXING SOCKET ASSEMBLY”, according to claim 12, characterized by the fact that the external socket is formed as a Reaction Block.
[0016]
16. “FIXING SOCKET ASSEMBLY”, according to claim 12 integrated in a Displacement Connection, characterized by the fact that it has a set of drive force input; an internal socket (16) formed as a set of driving force output; and the external socket (17) formed as a set of reaction force.
[0017]
17. “THREADED FIXER FOR FIXING OBJECTS”, characterized by the fact that it includes: - One pin (20); - A nut (36) to be tightened or loosened by means of threads interlockable on the pin (20) or on the head (22) of the pin (20) to be tightened or loosened, connected to the pin; and - the reaction washer (1) disposed between one of the objects (30) and the nut (36) or the screw head (22) (20).
[0018]
18. "THREADED FASTENER" according to claim 17, including a Double Sided Friction Washer (85) disposed between the other objects (30) and another part of the fastener (20) that must not be rotated, characterized by the fact that the friction washer (85) has upper (86) and lower (87) faces, each formed with treatments (7) to increase the friction coefficient to prevent the other part of the fastener (20) from rotating.
[0019]
19. "THREADED FIXER" according to either claim 17 or 18, characterized by the fact that it must be tightened and / or loosened by the fixing socket assembly (15) of any claim 12 to 16.
[0020]
20. “REACTION TORQUE ELECTRIC TOOL WITH FREE ARM TO TIGHTEN, LOOSE OR TIGHTEN AND LOOSE A THREADED FIXER” according to any one of claims 17 to 19, characterized by the fact that it includes: - A rotating force generating mechanism ( 100); - A drive to transfer the turning force (200); and - A fixing socket assembly (15) of any of claims 12 to 16.
[0021]
21. “ELECTRICAL TOOL”, according to claim 20, characterized by the fact that it is driven electrically, hydraulically or pneumatically.
[0022]
22. "OBJECT FIXING SYSTEM", characterized by the fact that it includes: - A threaded fastener (20), according to any claim 17 to 19; and - A torque electric tool (10), according to any of claims 20 to 22.

类似技术:

---

公开号 | 公开日 | 专利标题

---

BR112016014225B1|2021-04-27|REACTION WASHER, FIXING SOCKET ASSEMBLY, THREADED FIXER FOR OBJECT FIXING, REACTION TORQUE POWER TOOL WITH FREE ARM TO TIGHTEN, LOOSE OR TIGHTEN AND LOOSE A THREADED FASTENER AND TIGHTENING, TIGHTENING, TIGHTENING, TIGHTENING, TIGHTENING, TIGHTENING AND TIGHTENING GRIPPING

---

CN108349072B|2021-08-10|Reaction washer and its fastening sleeve

---

US20160375563A1|2016-12-29|Apparatus for tightening threaded fasteners

---

US20210095710A1|2021-04-01|Apparatus for tightening threaded fasteners

---

US20130202384A1|2013-08-08|Apparatus for tightening threaded fasteners

---

WO2018160230A1|2018-09-07|Two-part tapered thread nut assembly

---

US20190003512A1|2019-01-03|Apparatus for tightening threaded fasteners

---

US20210372442A1|2021-12-02|Apparatus for tightening threaded fasteners

---

RU53962U1|2006-06-10|WRENCH WITH KEY HEAD

同族专利:

---

公开号 | 公开日

---

AU2014370184A1|2016-07-21|

---

EP3083146B1|2020-07-15|

---

CN106030128B|2019-11-26|

---

CO2017002155A2|2017-04-28|

---

AP2016009275A0|2016-06-30|

---

PE20161186A1|2016-10-27|

---

CN106030128A|2016-10-12|

---

ES2837373T3|2021-06-30|

---

EA201691082A1|2016-11-30|

---

US20170021478A1|2017-01-26|

---

CA2934325A1|2015-07-02|

---

CL2016001517A1|2017-06-16|

---

TW202033892A|2020-09-16|

---

WO2015095425A3|2015-11-12|

---

CN111075826A|2020-04-28|

---

WO2015100115A2|2015-07-02|

---

EA036723B1|2020-12-11|

---

MX2016008104A|2017-03-27|

---

JP2017508105A|2017-03-23|

---

AU2020286246A1|2021-01-14|

---

WO2015095425A2|2015-06-25|

---

PL3083146T3|2021-01-25|

---

PH12016501187A1|2016-07-25|

---

KR20160098473A|2016-08-18|

---

EP3083146A2|2016-10-26|

---

TWI685619B|2020-02-21|

---

DK3083146T3|2020-10-12|

---

TW201537047A|2015-10-01|

---

AU2018247220A1|2018-11-01|

---

JP6702870B2|2020-06-03|

---

PE20211486A1|2021-08-09|

---

WO2015100115A3|2015-11-12|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

US2832395A|1954-01-25|1958-04-29|Swayne Robinson & Co|Metal working vise with bending rollers|

---

US2856799A|1957-05-13|1958-10-21|Curtis Frank De|Support for small tools|

---

US3351116A|1965-12-20|1967-11-07|Marvin J Madsen|Lock washer|

---

JPS4429215Y1|1965-12-28|1969-12-03|

---

US3581383A|1967-12-13|1971-06-01|Taisei Corp|Method for tightening a nut and bolt assembly|

---

US4034788A|1975-12-19|1977-07-12|Elco Industries, Inc.|Fastener assembly|

---

US4134438A|1977-07-21|1979-01-16|Frieberg Bengt O|Locking device for threaded fasteners|

---

JPS57200716A|1981-06-04|1982-12-09|Yukiyoshi Kawabata|Locking device for screw clamping elastic body|

---

US4706526A|1985-08-21|1987-11-17|Junkers John K|Fluid operated wrench|

---

US4671142A|1985-08-21|1987-06-09|Junkers John K|Fluid operated wrench|

---

USRE33951E|1987-09-29|1992-06-09|Fluid operated wrench|

---

US5016502A|1990-03-30|1991-05-21|Junkers John K|Power wrench|

---

US5499558A|1992-05-07|1996-03-19|Junkers; John K.|Fluid operated tool for elongating and relaxing a threaded connector|

---

US5318397A|1992-05-07|1994-06-07|Junkers John K|Mechanical tensioner|

---

CN2154379Y|1993-04-08|1994-01-26|段英贤|Emboss taper spring washer|

---

JP2527130B2|1993-05-31|1996-08-21|上田朱美|Screw locking device|

---

US5539970A|1994-10-21|1996-07-30|Junkers John K|Method of and device for elongating and relaxing a stud|

---

US5640749A|1994-10-21|1997-06-24|Junkers; John K.|Method of and device for elongating and relaxing a stud|

---

US5538379A|1995-02-15|1996-07-23|Junkers John K|Mechanical tensioner for and method of elongating and relaxing a stud and the like|

---

US5946789A|1995-10-18|1999-09-07|Junkers; John K.|Method of and device for elongating and relaxing a stud|

---

US6230589B1|1998-06-29|2001-05-15|John K. Junkers|Power tool|

---

US6253642B1|1998-09-22|2001-07-03|John K. Junkers|Power tool|

---

AU5426600A|1999-06-14|2001-01-02|Masaki Yamazaki|Screw mechanism|

---

US6298752B1|1999-06-25|2001-10-09|John K. Junkers|Continuous fluid-operated wrench|

---

US6152243A|1999-08-05|2000-11-28|Junkers; John K.|Universal torque power tool|

---

US6490952B2|1999-08-05|2002-12-10|John K. Junkers|Fastening device|

---

US6254323B1|1999-10-22|2001-07-03|John K. Junkers|Bolt for connecting two parts with one another, and fastening device provided with the bolt|

---

AUPQ611800A0|2000-03-09|2000-03-30|Smolarek, Hanna Maria|Washer and threaded fastener assembly incorporating same|

---

AU5878601A|2000-05-19|2001-11-26|Eisuke Ishida|Structure for preventing loosening of threaded fasteners|

---

US6461093B1|2000-09-05|2002-10-08|John K. Junkers|Threaded fastener|

---

JP2002181026A|2000-12-12|2002-06-26|Taiwan Hoashi Kigyo Kofun Yugenkoshi|Tightening bolt set|

---

US6749386B2|2001-08-20|2004-06-15|Maclean-Fogg Company|Locking fastener assembly|

---

US7125213B2|2001-12-06|2006-10-24|Junkers John K|Washer, fastener provided with a washer, method of and power tool for fastening objects|

---

US7207760B2|2001-12-06|2007-04-24|Junkers John K|Washer and fastener provided with a washer|

---

US6609868B2|2001-12-06|2003-08-26|John K. Junkers|Washer, fastener provided with a washer, and method of fastening with the use of the washer|

---

US7066053B2|2002-03-29|2006-06-27|Junkers John K|Washer, fastener provided with a washer|

---

DE20206373U1|2002-04-23|2002-08-08|Textron Verbindungstechnik|Self-locking fastening device|

---

US20040131445A1|2003-01-06|2004-07-08|Carl Kjellberg|Nut, a fastener provided with a nut, and a fastening device therefor|

---

USD500060S1|2003-05-05|2004-12-21|John K. Junkers|Bolting machine|

---

AU2003903340A0|2003-07-01|2003-07-17|Eznut Pty Ltd|Elastic joint element and threaded fastener assembly incorporating same|

---

AU2004203297A1|2003-08-12|2005-03-03|John Kurt Junkers|Socket for tightening, loosening or holding a hexagonal part underneath an equally sized hexagonal nut|

---

US20050155461A1|2004-01-15|2005-07-21|Junkers John K.|Washer, fastener provided with a washer, method of and power tool for fastening objects|

---

US20070157736A1|2004-01-21|2007-07-12|Nippon Telegraph And Telephone Corporation|Screwdriver device and screw|

---

US7857566B2|2005-07-14|2010-12-28|Reactive Spring Fasteners, Llc|Reactive fasteners|

---

US7462007B2|2004-07-14|2008-12-09|Paul Sullivan|Reactive biasing fasteners|

---

US7062992B2|2004-10-29|2006-06-20|Norwolf Tool Works|Constant rotation rotary torque multiplier|

---

AU2006200183A1|2005-03-15|2006-10-05|Unex Corporation|A washer, a fastener provided with the washer, and method of and a tool for fastening with the use of the washer|

---

US7188552B1|2005-10-14|2007-03-13|Jetyd Corp.|Holding socket for a threaded fastener|

---

ES2334081B2|2006-04-28|2011-12-12|Unex Corporation|MOTORIZED TORQUE INTENSIFIER.|

---

GB0617579D0|2006-09-07|2006-10-18|Rencol Tolerance Rings Ltd|Combination mounting ring|

---

AU2008200632B2|2007-02-09|2011-06-30|Kangas, Eila Anneli|Locking washer|

---

US7641579B2|2007-04-19|2010-01-05|Junkers John K|Eccentric gear mechanism and method of transfering turning force thereby|

---

US7735397B2|2007-06-01|2010-06-15|Junkers John K|Fluid operated torque tool for and a method of tightening a nut on a plate on railroad crossings|

---

US7765895B2|2007-10-29|2010-08-03|Junkers John K|Fluid-operated torque wrench for and method of tightening or loosening fasteners|

---

US7798038B2|2007-10-29|2010-09-21|Junkers John K|Reaction arm for power-driven torque intensifier|

---

US20090142155A1|2007-12-03|2009-06-04|Tu-Global Co., Ltd.|Anti-loosening unit|

---

US8042434B2|2008-01-24|2011-10-25|Junkers John K|Safety torque intensifying tool|

---

US7832310B2|2008-07-18|2010-11-16|Junkers John K|Torque power tool|

---

DE202008011371U1|2008-08-26|2008-10-23|Acument Gmbh & Co. Ohg|Washer, screw or nut with increased coefficient of friction|

---

USD608614S1|2008-12-18|2010-01-26|John Junkers|Power operated torque tool|

---

US8079795B2|2009-03-23|2011-12-20|Junkers John K|Washer for tightening and loosening threaded connectors|

---

US20160375563A1|2011-05-23|2016-12-29|HYTORC Division Unex Corporation|Apparatus for tightening threaded fasteners|

---

JP5440766B2|2009-07-29|2014-03-12|日立工機株式会社|Impact tools|

---

EA030710B1|2010-02-09|2018-09-28|Хайторк Дивижн Юнекс Корпорейшн|Apparatus for tightening threaded joints|

---

EP2361722B1|2010-02-18|2013-01-16|Aktiebolaget SKF|Rod tensioning device.|

---

CN102233555B|2010-04-27|2015-01-28|阿尼泰特株式会社|Sleeve for connection and washer for supporting used reacting force and connecting structure|

---

JP5787350B2|2010-04-27|2015-09-30|ユニタイト株式会社|Fastening structure, reaction force washer used therefor, and fastening socket|

---

US9657766B2|2010-09-14|2017-05-23|Enduralock, Llc|Tools and ratchet locking mechanisms for threaded fasteners|

---

US8925646B2|2011-02-23|2015-01-06|Ingersoll-Rand Company|Right angle impact tool|

---

US20120266560A1|2011-04-21|2012-10-25|Illinois Tool Works Inc.|Self-counterboring, screw-threaded headed fastener with enlarged flanged portion or wings having cutting teeth thereon, and cutting wrench/screw gun sockets|

---

US10215217B2|2015-04-17|2019-02-26|Enduralock, Llc|Locking fastener with deflectable lock|

---

CA3033078A1|2015-09-08|2017-03-16|Enduralock, Llc|Locking mechanisms with deflectable washer members|EP3423236A1|2016-03-02|2019-01-09|Hytorc Division Unex Corporation|Threaded fastener with friction coefficient increasing treatments|

---

EP3288715A2|2015-04-28|2018-03-07|Hytorc Division Unex Corporation|Reaction washer and threaded fasterner comprising such washer|

---

US10107325B2|2015-11-04|2018-10-23|The Reaction Washer Company|Multifunction reaction washer and stack accessed by slim reaction socket|

---

CN105328650B|2015-11-24|2017-07-11|同济大学|A kind of electronic installation tool of split Nested-type single-side bolt fastener|

---

CN105317815A|2015-11-26|2016-02-10|申益|Self-reactive force coaxial washer|

---

CN105269504B|2015-11-26|2018-03-06|申益|One kind is used for fastener active force and is co-axially mounted method with the reaction arm of force|

---

EP3419790B1|2016-02-24|2021-12-22|Hytorc Division Unex Corporation|Apparatus for tightening threaded fasteners|

---

TWI603815B|2016-04-13|2017-11-01|優鋼機械股份有限公司|Rotatable fastening device|

---

CN105782216A|2016-05-16|2016-07-20|蔡文斌|Torque rotating and floating load anti-loosening gasket|

---

WO2018104075A1|2016-12-05|2018-06-14|Atlas Copco Industrial Technique Ab|Torque impulse wrench|

---

RU2661640C2|2016-12-19|2018-07-18|Акционерное общество "Концерн "Научно-производственное объединение "Аврора"|Reinforced fastener|

---

WO2018181078A1|2017-03-31|2018-10-04|彰善 増澤|Washer-equipped wheel nut and tightener for washer-equipped wheel nut|

---

JP6460555B2|2017-03-31|2019-01-30|彰善 増澤|Wheel nut with washer, and wheel nut tightening machine with washer|

---

US20190176280A1|2017-12-11|2019-06-13|Lam Research Corporation|Knurling edge driving tool|

---

RU188408U1|2018-05-21|2019-04-11|федеральное государственное бюджетное образовательное учреждение высшего образования "Самарский государственный технический университет"|ULTRASONIC WIPER|

---

US20210239151A1|2018-08-07|2021-08-05|Bolt Engineer Co.|Lock washer and fastening structure|

---

WO2020092932A2|2018-11-01|2020-05-07|HYTORC Division Unex Corporation|Apparatus for tightening threaded fasteners|

---

CN109590512B|2018-11-22|2020-07-03|台州三麟精密工具股份有限公司|Expansion bolt loosening machine|

---

US11168729B2|2019-03-12|2021-11-09|Earl Allen Size, JR.|Multi-piece anti-vibration locking fastener|

---

US11236778B2|2019-03-12|2022-02-01|Earl Allen Size, JR.|Multi-piece anti-vibration locking fastener having coaxially arranged inner and outer opposite threaded bolts in combination with successive and opposite threaded profiles within a thickened base layer|

---

RU206777U1|2021-06-19|2021-09-28|Дмитрий Олегович Кирюхин|Prefabricated sheet material|

法律状态:
2018-01-23| B11A| Dismissal acc. art.33 of ipl - examination not requested within 36 months of filing|

---

2018-05-15| B04C| Request for examination: application reinstated [chapter 4.3 patent gazette]|

---

2020-03-24| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

---

2021-03-16| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

---

2021-04-27| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 17/12/2014, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

---

申请号 | 申请日 | 专利标题

---

US201361916926P| true| 2013-12-17|2013-12-17|

---

US61/916,926|2013-12-17|

---

US201461940919P| true| 2014-02-18|2014-02-18|

---

US61/940,919|2014-02-18|

---

PCT/US2014/035375|WO2014176468A1|2013-04-24|2014-04-24|Apparatus for tightening threaded fasteners|

---

USPCT/US2014/035375|2014-04-24|

---

US201462012009P| true| 2014-06-13|2014-06-13|

---

US62/012,009|2014-06-13|

---

PCT/US2014/070996|WO2015100115A2|2013-12-17|2014-12-17|Apparatus for tightening threaded fasteners|

---