Device for tightening threaded fasteners

Abstract

The present disclosure relates to devices for tightening threaded fasteners. Specifically, the present disclosure relates to a pneumatic fluid pressure regulator assembly for use with a pneumatic torque tool for tightening and / or loosening threaded fasteners, comprising: a piston assembly; a regulator assembly; and a filter assembly. Additionally, the present disclosure relates to a pneumatic torque tool for tightening and / or loosening threaded fasteners, and an activation lockout safety assembly for use with a pneumatic torque tool for tightening and / or loosening threaded fasteners.

Description

[0001] This application is a divisional application of the invention patent application with the invention name “Device for tightening threaded fasteners”, the international application date is February 24, 2017, the international application number is PCT / US2017 / 019541, and the national application number is 201780024899.2.

[0002] CROSS-REFERENCE TO RELATED APPLICATIONS

[0003] This application claims priority to and / or constitutes a continuation or continuation-in-part of the following commonly owned and co-pending patent application, a copy of which is incorporated herein by reference in its entirety: U.S. Application No. 62 / 299,110, filed February 24, 2016, and entitled “APPARATUS FOR TIGHTENING THREADED FASTENERS.” Background Art

[0004] Torque power tools are known in the art and include pneumatic, electric and hydraulic powered tools.Torque power tools generate a rotational force to tighten and / or loosen threaded fasteners and an equal and opposite reaction force.

[0005] Over the years, the applicant has applied its in-depth understanding and innovation of torque power tools to handheld electric and pneumatic torque enhancement tools, including the development of Gun、FLASH TM and LITHIUM Series TM Product range and the drivers and tools used with them. By way of example, the development of these product lines is disclosed in the following U.S. patents and U.S. applications of the applicant: US6490952; US6609868; US6929439; US6883401; US6986298; US7003862; US7066053; US7125213; US7188552; US7207760; US7735397; US7641579; US7798038; US7832310; US7950309; US8042434; US D608,614; US13 / 577995; PCT / US2014 / 69996; PCT / US2014 / 71000; and US62 / 159,950, copies of which are incorporated herein by reference in their entirety.

[0006] The present invention addresses the evolving industrial bolting needs relative to applicant's product lines. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] Figure 1A 、 1B , 1C, 1D, 1E, 1F, 1G, 1H, 1I, 1J, 1K, 1L, 1M and 1N illustrate an integrated pneumatic flow pressure regulator assembly with and / or without a filter and / or a rotary joint according to the present disclosure.

[0008] Figure 2A1 、 2A2 , 2B1 and 2B2 illustrate activation or trigger lock safety assemblies according to the present disclosure.

[0009] Figure 3A 、 3B 3C illustrate a speed-sensing centrifugal multi-speed automatic shift assembly according to the present disclosure.

[0010] Figure 4A 、 4B , 4C, 4D, 4E, 4F, 4G, 4H and 4I illustrate torque sensing centrifugal multi-speed automatic shift assemblies according to the present disclosure.

[0011] Figure 5A 、 5B , 5C, 5D, 5E, 5F and 5G illustrate spiral cam or rocking rotational force multiplication assemblies according to the present disclosure.

[0012] Figure 6A 、 6B , 6C, 6D, 6E, 6F, 6G, 6H, 6I and 6J illustrate pneumatic pressure relief or burst valve assemblies according to the present disclosure.

[0013] Figure 7A 、 7B 7C illustrate a pneumatic fluid directional valve assembly according to the present disclosure.

[0014] Figure 8A and 8B A pneumatic fluid direction and activation or trigger lockout safety valve assembly according to the present disclosure is shown.

[0015] Figure 9A and 9B A pneumatic tool cycle counter or odometer assembly according to the present disclosure is shown. DETAILED DESCRIPTION

[0016] The disclosed inventions include:

[0017] ·according to Figure 1A 、 1B, 1C, 1D, 1E, 1F, 1G, 1H, 1I, 1J, 1K, 1L, 1M and 1N, with and / or without filters and / or swivel joints, for use with all of the applicant's pneumatic torque gun models;

[0018] ·according to Figure 2A1 、 2A2 , the activation or trigger lock safety assembly shown in 2B1 and 2B2 for all of the applicant's electric and pneumatic torque gun models;

[0019] Automatic torque gun shift assembly, which includes:

[0020] oAccording to Figure 3A 、 3B and the speed-sensing centrifugal multi-speed automatic shift assembly shown in 3C, for use with all of applicant's electric and pneumatic torque gun models;

[0021] oAccording to Figure 4A 、 4B , 4C, 4D, 4E, 4F, 4G, 4H and 4I shown as torque sensing centrifugal multi-speed automatic shift assemblies for use with all of applicant's electric and pneumatic torque gun models;

[0022] ·according to Figure 5A 、 5B , 5C, 5D, 5E, 5F and 5G, spiral cam or rocking torque multiplication assemblies for all of applicant's electric and pneumatic torque gun models;

[0023] ·according to Figure 6A 、 6B , 6C, 6D, 6E, 6F, 6G, 6H, 6I and 6J, which allow pressure relief to release a locked tool, for use with all models of pneumatic torque guns of the applicant;

[0024] ·according to Figure 7A 、 7B and the pneumatic fluid directional valve assembly shown in 7C, for use with all models of pneumatic torque guns owned by the applicant;

[0025] ·according to Figure 8A and 8B The pneumatic fluid direction and activation or trigger lockout safety valve assembly shown, for use with all of Applicant's pneumatic torque gun models; and

[0026] ·according to Figure 9A and 9B The illustrated pneumatic tool cycle counter or odometer assembly, which identifies tool actuation as a drop in pneumatic pressure, is used with all of the applicant's pneumatic torque gun models.

[0027] One-piece pneumatic flow pressure regulator assembly . refer to Figure 1A , by way of example, the Figure shows an exploded perspective view of an integrated pneumatic flow pressure regulator assembly 100, which is used in and forms part of several of the applicant's pneumatic torque guns, including torque gun 1 (not shown) for tightening and / or loosening industrial threaded fasteners.

[0028] In this example, the regulator assembly 100 includes: a pressure regulator inlet 101; a center spring 102; a locking ring 103; a set screw 104; a ball bearing 105; an O-ring washer 106; a locking nut washer 107; a Lee spring 108; an O-ring 109; an adjusting ring 110; an internal locking nut 111; an Allen screw 112; a locking pin 113; a regulator cap 114; a Smalley retaining ring 115; an internal pressure relief valve 116; an internal pressure relief valve housing 117; a rubber disc 118; an O-ring 119; a valve housing 120; O-rings 121 and 122; a regulating valve washer 123; a rotor clamp 124; a piston 125; a Lee spring 126; and a retaining clamp 127.

[0029] Fluid pressure is adjusted, for example, by rotating the adjustment ring 110 of the assembly 100. An internal pressure relief valve 116, similar to a venturi valve, prevents overpressure during bolting operations, potentially damaging the torque gun 1. A display feature (not shown) is positioned on the rear of the applicant's torque gun to display the actual torque output and / or regulated air pressure. Advantageously, the regulator assembly 100: eliminates the traditional separate or in-line components of the FRL; and is integrally formed with, within, adjacent to, and / or in-line with the torque gun 1 and / or several of the applicant's other pneumatic torque guns.

[0030] Other features of the in-handle pneumatic flow pressure regulator assembly 100 shown in FIG1 that are mounted within or near the handle 10 of the torque gun 1 include an exhaust noise muffler assembly 150 having a noise filter 151 (not shown) and a mesh screen 152 (not shown). An end cap 160 holds all components within and / or near the handle 10 of the torque gun 1. It should be understood that many known types of components exist that can be used with the in-handle pneumatic flow pressure regulator assembly 100.

[0031] In addition, if Figure 1D 、 1EAs shown in FIG1F and FIG1F , as an example, a filter assembly 130 can be formed in or near the handle 10 of the in-handle pneumatic flow pressure regulator assembly 100 and / or the torque gun 1. The filter assembly 130 includes a filter unit 133 and an O-ring assembly 134 formed in a housing 131 closed by a cap 132. The filter assembly 130 filters, collects, absorbs, and / or dries compressed air by removing water, particulate matter, and / or oil.

[0032] In addition, if Figure 1F As shown in FIG, as an example, the rotary coupling assembly 140 can be formed within the handle adjacent the pneumatic fluid pressure regulator assembly 100, the filter assembly, and / or the handle 10 of the torque gun 1.

[0033] In other words, the in-handle pneumatic fluid pressure regulator assembly of the present invention comprises a piston valve in a cylinder cooperating with an adjustable spring-loaded diaphragm. The valve-diaphragm combination controls the flow of fluid from an inlet channel through an outlet conduit to rotate a motor, such as a turbine motor, within the torque gun 1. This serves to extend the venturi tube so that the valve-diaphragm combination withstands the pressure generated by the fluid flow through the outlet conduit. Compared to known external regulators, this in-handle pneumatic fluid pressure regulator assembly has a smaller size, a greater capacity or outlet flow rate, and a lower pressure drop.

[0034] The locking ring rotates coaxially on a resilient flange on the housing. The locking ring and flange work together to lock and release the adjusting knob for adjusting the spring pressure on the diaphragm. This design minimizes the possibility of the knob being accidentally rotated from its adjusted position.

[0035] like Figure 1G 、 1H As shown in FIG and 1I , by way of example, the pneumatic flow pressure regulator assembly of the present invention may include multiple regulator assemblies arranged side by side. As shown, the regulator assembly 100A is formed inline, but is not formed within the handle 10 of the tool 1. Alternatively, the multiple regulator assemblies may be formed in series, near or within the handle 10 of the tool 1, or without a handle.

[0036] As an example, Figure 1J 、 1K , 1L, 1M and 1N show other embodiments of the pneumatic flow pressure regulator assembly of the present invention. Figure 1J The pneumatic fluid pressure regulator assembly 100B includes: a piston assembly 160 ; a regulating assembly 170 ; and a filter assembly 180 .

[0037] Piston assembly 160 includes: valve housing 161; piston 162; coil spring 163; adjuster cap 164; seal 165; seal guide 166; piston seat or valve plate 167; gasket seal 168; O-rings 169A-D; and screw 169E. Adjustment assembly 170 includes: handle or threaded collar 171; friction O-ring 172; and washer 173. Filter assembly 180 includes: filter 181; and filter housing 182.

[0038] Pressurized fluid (e.g., compressed air) enters the regulator inlet 101 of the regulator assembly 100C and passes through a series of holes in the filter 181 and the valve plate 167. The filter 181 is secured in place using a press fit in the filter housing 182. The seal 165 and gasket 166 are secured to the valve plate 167 and the valve housing 161 with screws 169E.

[0039] When an unbalanced pressure condition exists between the force exerted by spring 163 on regulator piston 162 and O-ring 169C and the inlet pressure, air will pass through the hole in valve plate 167 if the inlet pressure is higher than the spring force on piston 162. Compressed air will continue to flow through regulator piston 162 via outlet port 164 until equilibrium is reached between the inlet pressure and spring 163. A second unbalanced condition may exist when the inlet pressure is less than the force exerted by spring 163 on regulator piston 162. In this case, pressurized fluid will vent to atmosphere until equilibrium is reached.

[0040] The spring 163 is adjusted using a threaded collar 171, which is sealed to the handle 10 of the tool 1 via an O-ring 169D, until a balanced state is reached. The fluid pressure is controlled by rotating the threaded collar 171 to increase or decrease the force on the spring 163. Several O-rings 169B, 169C, and 172 seal the regulator assembly 100B, producing negligible fluid leakage. A gasket 168 is formed between the outlet port of the valve housing 161 and the cap 164. The threaded cap 164 connects the regulator assembly 100B to the handle 10.

[0041] As an example, representative design parameters associated with the regulator assembly 100B include the following. In general, the regulator assembly 100B is intended to meet or exceed the flow characteristics of prior art regulators (such as the AW30 regulator from SMC Corporation of the United States). Specifically, compressed air is the intended pressurized fluid medium and includes water vapor, lubricant, and foreign particles. A filter 181 is located at the inlet port to remove water vapor, lubricant, and foreign particles larger than 2, 10, 20, 40, 70, or 100 microns. The inlet fluid pressure is 105 to 140 psig, and the outlet fluid pressure should be adjusted between 20 and 100 psig. At an outlet pressure of 20 to 90 psig and an inlet pressure of 105 to 140 psig, the flow rate can be 50 SCFM. When necessary, zero internal fluid leakage refers to having a tight cutoff to keep the downstream set point (i.e., exhaust directly discharged to the exhaust port of the torque gun) acceptable. Other design parameters include: 20 to 120°F ambient temperature; 3 / 8 NPT ports; wetted materials such as brass, CRES, Nitrile / Nitrile N; 1.25OD maximum envelope; field maintainability and / or repair; easy and accurate set point achievement via coarse / fine pressure adjustment; cycle life greater than 20k; etc.

[0042] As an example, Figure 1K and 1L A pneumatic fluid pressure regulator assembly 100C is shown, comprising: a piston assembly 160; an adjustment assembly 170; a filter assembly 180; and a locking assembly 190. The locking assembly 190 comprises: a locking collar 191 having an upper splined engagement 191A; a lower splined engagement formed on the threaded collar 161; a shoulder screw 193; and a ball plunger 194. During operation of the tool 1, the external locking assembly 190 minimizes the possibility of accidental rotation of the threaded collar 161 from its adjusted position. The splines 191A engage the splines 192 and the locking collar 191 is axially held in place by the ball plunger 194, which allows the locking collar 191 to move from the adjusted position to the locked position. The locking collar 191 is rotationally constrained by the shoulder screw 193, which allows the locking collar 191 to slide axially along the groove but is rotationally fixed.

[0043] Figure 1M and 1N Regulator assembly 100C is shown, with and without rotational coupling assembly 140A, formed adjacent handle 10 of tool 1 .

[0044] It should be understood that there are many known types of components that can be used with the integrated pneumatic flow pressure regulator assemblies of the present invention, such as 100, 100A, 100B, and 100C.

[0045] Activate or trigger lock safety assemblyThe applicant attaches great importance to following the bolt connection industry safety standards and seeking ways to increase the safety of bolt connections. As an example, Figure 2A1 、 2A2 2B1 and 2B2 show perspective views of portions of torque guns 1A and 1B, respectively, having activation or trigger lock safety assemblies 200 and 250. Safety assemblies 200 and 250 are shown for applicant's pneumatic torque gun models, but may also be modified for applicant's electric torque gun models.

[0046] A trigger lockout safety assembly 200 is formed within and / or adjacent to the modified handle 10A near the rear of the tool 1A having the modified trigger 17A. In this example, the safety assembly 200 includes: a button 202; a retaining button 201; a locking lever 203; and a retaining spring 204. Before pneumatic fluid or electricity can be used to operate the torque gun 1A, the user must first depress the button 202. The safety assembly 200 prevents accidental activation of the torque gun 1A, which could result in serious injury to the user. The operator must maintain both hands on the tool 1A: one on the trigger 17A and one on the button 201.

[0047] The trigger lock safety assembly 200 locks the trigger 17A from being depressed by a recess in a locking bar 203 screwed into the trigger 17A. This recess in the locking bar 203 is occupied by a cylindrical portion of a button 202 captured in a hole perpendicular to the centerline of the locking bar 203, and a retaining button 201 screwed into the handle 10A. The button 202 is spring-loaded by a retaining spring 204 and has a circular recess adjacent to the cylindrical portion of the locking bar 203's retaining recess. To release the locked trigger 17A, the button 202 is pressed, shifting the position of the recess in the button 202 into direct alignment with the locking bar 203, thereby allowing the locking bar 203 to move rearward. After the trigger 17A is released, the locking bar 203 returns to its initial position, allowing the retaining button 201, preloaded by the retaining spring 204, to move back into the locked position.

[0048] In other words, the trigger 17A is locked from being depressed by the cylindrical portion of the button 202 being aligned with the groove in the locking bar 203. Conversely, the trigger 17A is allowed to be depressed by the cylindrical portion of the button 202 not being aligned with the groove in the locking bar 203.

[0049] A trigger lock safety assembly 250 is formed within and / or adjacent to the modified handle 10B, substantially between the trigger 17B and the rear portion of the torque gun 1B. In this example, the safety assembly 250 includes: a lever arm 251; a locking pin 252; a locking bolt 253; a lever housing 254; a lever stopper 255; a torsion spring 256; a trigger pin 257; a trigger spring 258; a lever screw 259; a set screw 260; and a cap 261. The safety assembly 250 is shown positioned so that the lever arm 251 is operated by the operator's left hand. A second version of the trigger lock safety mechanism 250 (not shown) includes similar components but is positioned so that the lever arm 251 is operated by the operator's right hand. Before pneumatic fluid or electricity can be used to operate the torque gun 1B, the user must first rotate the lever arm 251. The safety assembly 250 prevents accidental activation of the torque gun 1B, which could result in serious injury to the user. The operator must have both hands on tool 1B: one hand on trigger 17B and one hand on lever arm 251 .

[0050] The trigger 17B is locked in place via a trigger pin 250 that is screwed into the trigger 17B. The trigger 17B is spring loaded via a trigger spring 258 that is seated in a trigger pin 257. The trigger pin 250 has a radial groove at the end. A locking pin 252 is keyed into the groove to prevent rearward movement of the trigger pin 257.

[0051] To unlock the trigger 17B, the locking pin 257 has a release groove perpendicular to the centerline of the locking pin 252, as well as keyways at both ends. The release grooves at each end are cut at a specific angle to the two keyways, so that when the locking pin 252 is rotated at that specific angle, the release grooves align with the centerline of the trigger pin 250, allowing rearward movement. The locking pin 252 is rotated by a gear train consisting of a locking bolt 253 keyed to the end of the locking pin 252 and a lever tumbler 255. The lever tumbler 255 and locking bolt 253 are retained in the handle 10B via a lever housing 254, which is seated in a recess in the modified handle 10B and secured by a screw 260. The lever tumbler 255 rotates via a lever arm 251, which is keyed to the lever tumbler 255 and secured by a lever screw 259 and is also spring-loaded by a torsion spring 256. When lever arm 251 rotates upward (counterclockwise), this correspondingly rotates lever tumbler 255, which in turn rotates locking bolt 253 (clockwise), thereby rotating locking pin 252. The system's trajectory is limited by pin 262 in locking bolt 253. Pin 262 rides on a groove machined at a specific angular distance in lever housing 254, limiting the angular deflection of locking pin 253. The extreme counterclockwise movement of lever arm 251 positions the release slot in locking pin 251 to align with the centerline of trigger pin 257, allowing free rearward movement. When trigger 17B is released, trigger spring 258 pushes trigger pin 257 forward to its original position, with the radial groove directly aligned with locking pin 252. Torsion spring 256 forces the now freely movable lever tumbler 255 to rotate clockwise, rotating locking bolt 253 by rotating the release slot in locking pin 252 out of the path of trigger pin 257. This subsequently rotates locking pin 252 counterclockwise, thereby relocking it.

[0052] In other words, the trigger 17B is locked from being depressed by rotating the lever arm 251 to load the torsion spring 256. Conversely, the trigger 17B is allowed to be depressed by releasing the lever arm 251 to release the torsion spring 256.

[0053] In other embodiments (not shown), buttons, levers, and / or rods are located on both sides of the tool, requiring a specific hand positioning prior to operation. Once the trigger is pulled, the user can release the safety lever, and the tool remains powered as long as the trigger remains pulled. When the user releases the trigger, the lock automatically reengages. Thus, each time the trigger is pulled, the button and / or safety lever must first be disengaged. In one embodiment, the trigger lock is a blockage on a flat portion of the trigger bar that prevents the trigger from being pulled without disengaging the safety lever.

[0054] It should be understood that there are many known types of components that can be used with the trigger lock safety assemblies, such as 200 and 250, of the present invention.

[0055] Automatic torque gun shift assembly . Applicant places great importance on following bolting industry safety standards and seeking ways to improve bolting safety. The use of automatic clutch mechanisms with high-speed and high-torque bolting applications raises safety concerns. For example, an operator could be seriously injured by a pinch point between the reaction arm and the reaction surface of Applicant's torque gun when such a tool is transitioned between tightening and high-torque modes. The actual abrupt change between modes is dangerous to the operator. In high-speed mode, the reaction torque of Applicant's torque gun models ranges from minimal to no. Despite this, the reaction arm can also rotate in a dangerous manner. Conversely, in low-speed mode, the reaction torque of Applicant's torque gun models is very high, requiring the use of the reaction arm.

[0056] Applicants have also invented a multi-speed automatic shift assembly to automatically switch a torque gun having two (or more) speeds between a high-speed / low-torque ("HSLT") mode, a low-speed / high-torque ("LSHT") mode, and vice versa. Advantageously, the shift assembly of the present invention automatically switches applicants' torque gun between a fastener run-down or loosening function at speeds up to 4,000 rpm and a fastener tightening or loosening function at speeds as high as 150 rpm to as low as 4 rpm. A sensing mechanism determines when it is appropriate to shift between the modes.

[0057] The applicant shall The system is especially The gun is considered ideal for testing such a multi-speed automatic shift assembly because there is no external reaction clamp. However, it should be noted that the automatic shift assembly of the present invention can be used with all of the applicant's torque guns. The trigger lock safety assembly described previously and subsequently can be used to reduce the risk of injury to the operator during operation.

[0058] Speed-sensing centrifugal multi-speed automatic shift assembly . Figure 3A 、 3B Figures 3C and 3C illustrate, by way of example, an embodiment of a speed-sensing centrifugal multi-speed automatic mode shift assembly 300 of the present invention for use with an electrically or pneumatically operated torque gun. Assembly 300 may include: an outer LSHT clutch plate pack 301; an inner HSLT clutch plate pack 302; an outer pack spring 303; an assembly housing 304; ball bearings 305; a clutch carrier plate 306; a high-speed pressure plate 307; a retract pressure plate 308; a release bearing 309; and bearings 310 and 311.

[0059] Assembly 300 operates under the premise that speed and torque are inversely related in a tool: high speed means low torque, and low speed means high torque. Assembly 300 is generally formed within housing 304 and operates as follows. The outer LSHT clutch plate pack 301 is locked by outer set springs 303 by default for operation in LSHT mode. The outer set springs 303 lock the independent ring gears 322A for the first and second planetary gear stages 322 and 323 to the housing 304, allowing the tool to operate in LSHT mode.

[0060] When motor 330 reaches a predetermined speed, the ball bearings 305 adjacent to clutch carrier plates 306 on either side are forced apart due to the centrifugal forces from the rotational forces 332 and 333 of motor 330. These centrifugal forces force high-speed pressure plate 307 against inner HSLT clutch plate set 302, while simultaneously pushing retract pressure plate 308 against outer set of springs 303 via release bearing 309. This action at the HSLT causes outer set of springs 303 to release, allowing independent ring gear 322A to rotate freely on its supporting bearings 310 and 311. Simultaneously, inner HSLT clutch plate set 302 locks motor drive shaft 331 directly to independent ring gear 322A, essentially bypassing first and second stages 322 and 323 and driving third stage 324 directly from motor 330.

[0061] When the motor 330 slows down due to the increased seating resistance of the nut or bolt head, the ball bearings 305 in the carrier plate 306 retract, returning the inner and outer clutch plate sets 301 and 302 to their respective default states. In practice, the speed sensing centrifugal multi-speed automatic mode shift assembly 300 continuously shifts between the five (5) stage gearbox 320A and the three (3) stage gearbox 320B of the gearbox assembly 320 within the housing 321 at a speed of approximately 4000 rpm of the air motor 330.

[0062] Torque sensing centrifugal multi-speed automatic shift assembly As an example, Figure 4A An exploded perspective view of an embodiment of the present invention's torque sensing centrifugal multi-speed automatic shift assembly 400 for use with applicant's electrically or pneumatically operated torque guns is shown. Assembly 400 has elements that physically displace according to torque, and this displacement is used to shift a gear ratio changing mechanism. Figure 4B The assembly 400 is shown in HSLT mode. And Figure 4C The assembly 400 is shown in LSHT mode.

[0063] The torque sensing centrifugal multi-speed automatic shift assembly 400 may include: Smalley retaining rings 401, 402, 405, 417, 423, 424, and 431; bearings 403; a main housing 404; a lower thrust washer 406; first and second gear stage housings or ring gears 407; an inner friction material 408; an inner friction hub 409; and an outer friction material 410. Bearings 411 and 415; first gear stage sun gear or low speed drive 412; Smalley wave spring 413; external clutch material 414; external clutch housing 416; inner retaining ring 418; Smalley external wave ring 419; ball bearing 420; spiral cam input shaft 421; thrust needle roller bearings 422 and 425; top main housing 426; thrust needle roller washer 427; bearing spacer 428; bearing connector 429; and bearing 430.

[0064] The general operation of the torque-sensing centrifugal multi-speed automatic shift assembly 400, powered by motor 440, is as follows. In HSLT mode, the spiral camshaft 421 is urged into a neutral position by the Smalley wave spring 413. The internal friction material 408 is forced into engagement between the ring gear or first and second gear stage housings 407 and the internal friction hub 409. This eliminates rotation of the low-speed drive 412. In this example, the ring gear 407 rotates and produces a final high-speed output ratio of approximately 67:1, rather than a low-speed ratio of approximately 1291:1.

[0065] In LSHT mode, the spiral camshaft 421 forces the inner hub 409 and outer clutch housing 416 into engagement via the outer friction material 410. These components engage the main housing 404 and the low-speed drive 412, which activates the first and second planetary gear stages 432 and 433. In this example, a gear reduction ratio of approximately 19:1 is achieved.

[0066] As an example, Figure 4D 、 4E 4F and 4G, 4H and 4I show side and horizontal views and vertical cross-sections, respectively, of another embodiment of the torque sensing centrifugal multi-speed automatic shift assembly 450 of the present invention for use with applicant's electrically or pneumatically operated torque guns. Assembly 450 utilizes an over-eccentric type mechanism that results in clean, rapid changes in shifter position. Figure 4D 、 4E 4F shows the assembly 450 in HSLT mode. And Figure 4G 、 4H 4I and 4I show the assembly 450 in LSHT mode.

[0067] Generally, the torque sensing centrifugal multi-speed automatic shift assembly 450 may include many of the same components as the torque sensing centrifugal multi-speed automatic shift assembly 400. Some of the different components may include: one or more flanges; one or more spring housings; one or more spring cups; and one or more thrust cups.

[0068] Specifically, the torque sensing centrifugal multi-speed automatic shift assembly 450 includes: an intermediate housing 451; a bearing connector 452; a bracket 453; first and second planetary stage sun gears 454A and 454B; a spring flange 455; a first and second stage housing or ring gear 456; a sun gear fixing screw 457; a thrust bearing flange 458; a spring sleeve 459; a motor shaft 460; a flange 461; a thrust race 462; ball bearings 463 and 464; a steel ball 465; a retaining ring 466, 467 and 468; a drive coupling ball 469; a needle thrust bearing 470 and 471; a thrust washer 472; a retaining ring 473 and 474; a ball bearing 475; an outer wave spring 476; an inner wave spring 477; a ball bearing 478; and a retaining ring 479.

[0069] The torque-sensing centrifugal multi-speed automatic shift assembly 450, powered by motor 440, operates as follows. Rotation of carrier 453 drives ring gear 456 via drive coupling balls 469. As torque increases, drive coupling balls 469 ascend the ramp of carrier 453, pushing spring sleeve 459 upward, compressing wave spring 476. Drive coupling balls 469 move radially outward within the V-groove of carrier 453. Once the center of drive coupling balls 469 passes the straight section of the Y-groove of ring gear 456, they transfer to the angled section of the Y-groove. Drive coupling balls 469 quickly tilt away and become lodged between the Y-groove of ring gear 456 and intermediate housing 451. Intermediate housing 451 is coupled to ring gear 456, and carrier 453 disengages from ring gear 456. Ball 465, along with spring flange 455 and spring 477, acts as an overrunning clutch in the event that ball 469, when pushed out by bracket 453, strikes the top of the wedge-shaped profile of intermediate housing 451. This jamming condition causes ball 465 to move out of the ball slot in spring flange 455, pushing spring flange 455 upward until the next available ball slot rotates past and ball 465 drops into place.

[0070] In other words, in HSLT mode, motor shaft 460 is directly coupled to and drives ring gear 456, bypassing the first and second stage planetary gears. Bypassing the first and second stages causes the second stage planetary gearset to rotate at motor speed. In LSHT mode, carrier gear 453 is disengaged from ring gear 456, and intermediate housing 451 is coupled to ring gear 456. The gear ratio between input and output increases by the ratio of the first and second stages.

[0071] It should be understood that there are many known types of components that can be used with the automatic mode shift assemblies, such as 300 , 400 , and 450 , of the present invention.

[0072] Swing force multiplier assembly Applicants have also invented a rocking torque multiplication assembly for use with Applicants' torque guns having two (or more) speeds, including HSLT and LSHT modes. Advantageously, the rocking torque multiplication assembly of the present invention has a particularly compact and robust design and produces very high reduction ratios in a single stage, for example, from about 10:1 to about 3000:1.

[0073] As an example, Figure 5A and 5B A perspective view and a side cross-sectional view of the rocking turning force multiplication assembly 500 in the gearbox assembly 590 are shown. Figure 5C A perspective view of a first stage assembly 510 of assembly 500 is shown. Figure 5D A perspective view of the second stage assembly 560 of the assembly 500 is shown. Figure 5E and 5F Exploded perspective views of first and second stage assemblies 510 and 560 are shown. Figure 5G An exploded perspective view of the rocking turning force multiplication assembly 500 is shown.

[0074] In this example, the first stage eccentric gear assembly 510 includes: an intermediate housing 511; an eccentric gear 512; a ring gear 513 having a sun gear drive extension 521; a planetary gear assembly 514; a flange bearing 515; a drive input shaft 516; a needle bearing 517; a sleeve bearing 518; a locating pin 519; and a steel ball bearing 520. The drive input shaft 516 operatively connects the motor (not shown) to the first stage assembly 510. The sun gear drive extension 521 operatively connects the first stage assembly 510 to the planetary gear housing 561 of the second stage assembly 560.

[0075] In this example, the eccentric gear 512 has 43 teeth; the ring gear 513 with the sun gear extension 521 has 44 teeth and 12 teeth respectively; each planet gear of the planetary gear assembly 514 has 24 teeth; and the drive input shaft 516 has 12 teeth. In fact, a very high reduction ratio is obtained during operation because the eccentric gear 512 is essentially rocked within the ring gear 513 with the sun gear drive extension 521.

[0076] In this example, second stage eccentric gear assembly 560 includes: planet gear housing 561; planet gear assembly 562; planet gear bushing 563; ring gear / square drive extension 564 having square drive extension 568; eccentric gear 565; locating pin 566; and inner retaining ring 567. Square drive extension 564 operatively connects second stage assembly 560 to a drive socket (not shown).

[0077] In this example, eccentric gear 565 has 32 teeth; ring gear 564 with sun gear extension 568 has 33 teeth; each planet gear of planetary gear assembly 562 has 12 teeth; and sun gear extension 521 has 12 teeth. In practice, a very high reduction ratio is achieved during operation because eccentric gear 565 essentially rocks within ring gear 564 with square drive extension 568.

[0078] The first and second stage assemblies 510 and 560 are located within a gearbox assembly 590. The gearbox assembly 590 may include: a gearbox housing 591; a gearbox housing adapter 591; a ball bearing assembly 593; a gearbox assembly connector 594; first and second bearing gearbox bearings 595A and 595B; a lock washer 596; a lock nut 597; a retaining ring 598; and a flange bearing 599.

[0079] During operation of the rocking force multiplication assembly 500, input shaft 516 drives planetary gear assembly 514. Planetary gear assembly 514 has an offset counterbore, which causes eccentric (cycloidal sun) gear 512 to rotate on an eccentric path. This eccentric rotation produces a ratio of EQ-1, for example, [ring gear / (ring gear - eccentric gear)], which causes intermediate (sun gear) housing 511 to rotate at a reduced speed. Sun gear drive extension 521 is driven at a reduced ratio, which in turn drives planetary gear assembly 562, utilizing the same eccentric path and ratio as shown in EQ-1. This final output drives ring gear 564, which is concentric with gearbox housing 591, to transmit output force to square drive extension 568.

[0080] It should be understood that there are many known types of force multiplication mechanisms or compound epicyclic gear systems that can be used for the swing-rotating force multiplication assembly 500. These can include multiple outer planetary gears that rotate around a central sun gear. The planetary gears can be mounted on a movable bracket, which can itself rotate relative to the sun gear. Such a compound epicyclic gear system can include an outer ring gear that meshes with the planetary gears. A simple epicyclic gear system has a sun gear, a ring gear, a bracket and a planetary gear set. A compound epicyclic gear system can include a meshed planetary structure, a stepped planetary structure and / or a multi-stage planetary structure. Compared to a simple epicyclic gear system, a compound epicyclic gear system has the advantages of a larger reduction ratio, a higher torque-to-weight ratio and more flexible configuration.

[0081] The turning force multiplication transmission assembly of the present invention may include: a gear carrier; planetary gears; a ring gear; a sun gear; a rocking gear; a cycloidal gear; an epicyclic gear; a connector; a spacer; a shift ring; a retaining ring; a bushing; a bearing; a cap; a transmission gear; a transmission shaft; a locating pin; a drive wheel; a spring; any combination or portion thereof; and / or other known similar components. It should be noted that turning force input shaft 516 may also be considered a turning force multiplication transmission; specifically, it is the first stage motor sun gear of first stage 510. Turning force multiplication assemblies are well known and have been disclosed and described. An example is disclosed and described in Applicant's U.S. Patent No. 7,950,309, a copy of which is incorporated herein by reference in its entirety.

[0082] Pneumatic pressure relief or burst valve assemblies . The gun, along with all of the applicant's electric and pneumatic torque gun models, is not immune to becoming wedged in place between the fastener and the point where the tool reacts. In some cases, the pneumatic torque gun is stopped and its air motor is positioned so that torque is still applied to the fastener and force exists between the reaction arm and the reaction surface. Freeing such a stuck tool is difficult, and current products and methods result in a significant loss of bolt load upon removal.

[0083] Figure 6A 、 6B 6C, and 6D illustrate various views of the pneumatic pressure relief valve assembly 600 of the present invention. It is integrated into the applicant's pneumatic torque gun models and their control systems to facilitate removal of such guns after tightening a fastener. If the tool becomes stuck during tightening, the relief valve assembly 600 reverses the direction of pneumatic flow and, consequently, tool rotation, allowing the tool to move slightly regardless of bolt load. In effect, the tool rotates slightly in the loosening direction. This releases the opposing forces applied to the tool by the recently tightened fastener and the reaction point.

[0084] Generally, the release valve assembly 600 includes: an outer pneumatic valve portion 602; an intermediate pneumatic directional valve portion 603; an inner pneumatic valve portion 604; a pneumatic reverse valve portion 608; and a button 609. The release valve assembly 600 also includes: a key bar 601 on the outer pneumatic valve portion 602; a detent pin 605; a Smalley peak-to-peak spring 606; and an inner retaining ring 607. The components of the valve assembly 600 are integrated into and / or formed adjacent to a modified handle 10C and / or a modified tool handle rear cover 3C of a torque gun 1C and / or one of several other pneumatic torque guns of the applicant.

[0085] Advantageously, the release valve assembly 600 releases the force applied to the tool's reaction point by activating a single control button, which reverses the tool's rotation without loosening the fastener while simultaneously providing a short, controlled burst of air. This burst of air, directed to the motor 16C, is delivered via the reverse side of the valve. As described below, the release valve assembly 600 receives this air even when the tool is still configured for operation in the forward direction. In effect, it reverses the direction of the torque gun 1C without requiring the use of a modified trigger 17C, typically used as an on / off pneumatic valve.

[0086] As an example, Figures 6F-6J The operation of the release valve assembly 600 is shown. Figure 6F A button 609 is shown on the cover 3C for actuating the release valve assembly 600. An inlet port 691 from the tool handle 17C is used to reverse the direction of the motor 16C. An air passage 692 connects to the reverse valve 608. An air passage 694 connects the reverse valve 608 to the rear cover passage 695. The directional valve 603 also serves as an air sleeve 693 and helps open and close the port to reverse the direction of the motor 16C.

[0087] Figure 6G The front side of the reversing valve assembly 600 is shown. Reversing valve 608 is closed and exhaust port 621 is closed. To redirect air to the reverse side of the valve assembly 600, various ports and channels need to be opened and closed. This is achieved via directional valve 603, which is moved by pressing button 609. When the drive port 624 is open, directional valve 603 is positioned for clockwise rotation or tightening. In this view, the valve assembly 600 is deactivated. Handle inlet port 623 is open, allowing air to flow to motor 16C when trigger 17C is pressed. Air sleeve 693 is in its normal operating position.

[0088] Figure 6H The reverse side of valve assembly 600 is shown. It is not activated in this view. Exhaust port 626 is open in the normal operating position, and directional valve 603 is positioned for clockwise rotation. Inlet port 627 for counterclockwise operation is closed by directional valve 603. Reverse valve 608 remains closed. Air sleeve 693 is in the normal operating position.

[0089] Figure 6I The front side of the valve assembly 600 is shown again, this time with the button 610 depressed. Pressing the button 610 moves the air sleeve 693 forward, opening the reverse port 622 by opening the reverse valve 608. This occurs while the air inlet 623 from the trigger 17C is in the closed position. The air sleeve 693 is now in reverse mode. Exhaust ports 628 through 615 allow air to flow from the reverse port 622 through the reverse port passage 641. The normal exhaust port 621 remains closed by the directional valve 603 because it has not yet been rotated.

[0090] Figure 6J The reverse side of the valve assembly 600 is shown when the button 609 is pressed. The air sleeve 693 is pushed forward, sending air to the reverse side. When the reverse valve 608 is opened, the exhaust slot 631 closes, which moves the air sleeve 693 to the closed position. The air is forced in the reverse direction through the motor 16B and out of the exhaust port 621 on the front side, thereby reversing the tool 1C slightly. It should be noted that five (5) exhaust ports 631 are shown.

[0091] It should be noted that any suitable number of inlets and exhaust ports, slots, faces, channels, sleeves, sizes, materials, etc. may be used to control and optimize airflow through the torque wrench.

[0092] Figure 6E Another modified back cover 3C1 is shown, featuring a custom human / electronic device interface system designed by the applicant and an associated computer program. This simplifies tool operation and provides a user-friendly method for making necessary adjustments and tool configuration changes. It should be noted that the modified back cover 3C1 and its components can be used with any of the applicant's electric, hydraulic, and / or pneumatic torque guns.

[0093] Pneumatic fluid directional valve assemblies . The gun and all of the applicant's electric and pneumatic torque gun models are required to tighten and loosen threaded fasteners in both forward and reverse directions. Figure 7A 、 7B As shown in Figures 7 and 7C , applicants have further improved their pneumatic torque gun models by developing a pneumatic fluid directional valve assembly 700, as an example, to enhance the ease of directional control of such tools. Generally, directional valve assembly 700 includes: an outer pneumatic valve portion 702; an inner pneumatic valve portion 704; and a push-button lever assembly 706. It should be noted that the components of directional valve assembly 700 are integrated into and / or formed adjacent to a modified handle 10D of a torque gun 1D and / or one of several other pneumatic torque guns of applicants. It should be noted that directional valve assembly 700 utilizes similar concepts found in pressure relief valve assembly 600, which operates in a similar manner.

[0094] The operator changes the directional flow of pneumatic fluid by depressing the button lever assembly 706. A rack and pinion connection between the inner pneumatic valve portion 704 and the button lever assembly 706 opens and / or closes the various ports and channels of the directional valve assembly 700, thereby allowing the operator to control the flow of pneumatic fluid. Springs 706A and 706B bias the button lever assembly 706 and help lock it in place once the operator selects the tool direction. Any suitable number of ports, channels, faces, sizes, materials, etc. can be used to optimize the directional flow through the torque wrench.

[0095] The outer pneumatic valve portion 702 is press-fitted into the modified handle 10D of the torque gun 1D. The outer portion 702 has six independent ports (713, 714, 715, 716, 717, and 718). The inner pneumatic valve portion 704 has three distinct faces (710, 711, and 712). When the operator pushes the button lever assembly 706 in one direction 720, face 711 allows air to flow from port 713 to port 718, causing the air motor to rotate clockwise. Exhaust air passes through port 717 and is directed by face 712 to port 714, exiting the handle 10D. When the button lever assembly 706 is pushed in the other direction 721, face 710 allows air to flow from port 713 to port 715, causing the air motor to rotate counterclockwise. Exhaust air passes through port 716 and is directed by face 712 to port 716. It should be noted that any suitable number of ports, channels, sizes, materials, etc. may be used to optimize airflow through the torque wrench.

[0096] Pneumatic fluid directional and activation or trigger lock safety assembly . The guns and all of the applicant's electric and pneumatic torque gun models are required to tighten and loosen threaded fasteners in both forward and reverse directions. They must also follow and advance industry safety standards. Figure 8A and 8B As shown in , applicants have further improved their pneumatic torque gun models to enhance the ease of directional control of the tool by developing, as an example, a pneumatic fluid directional valve and activation or trigger lockout safety assembly 800. Generally, pneumatic fluid directional valve and trigger lockout safety assembly 800 includes: an outer pneumatic valve portion 802; an inner pneumatic valve portion 804; a button lever assembly 808; a button 810; and a trigger protrusion 814. It should be noted that the components of pneumatic fluid directional valve and trigger lockout safety assembly 800 are integrated into and / or formed adjacent to a modified handle 10E of a torque gun 1E and / or one of several other pneumatic torque guns of applicants. It should be noted that pneumatic fluid directional valve and trigger lockout safety assembly 800 utilizes similar concepts found in pressure relief valve assembly 600 and directional valve assembly 700, which operate in a similar manner.

[0097] The operator changes the directional flow of the pneumatic fluid by depressing the button lever assembly 808. A rack and pinion connection between the inner pneumatic valve portion 804 and the button lever assembly 808 opens and / or closes the various ports and passages of the pneumatic fluid directional valve and the trigger lock safety assembly 800, thereby allowing the operator to control the flow of the pneumatic fluid. Springs 806A and 806B bias the button lever assembly 809 and help lock it in place once the operator has selected the tool direction. Any suitable number of inlet and exhaust ports, grooves, faces, passages, sleeves, sizes, materials, etc. can be used to optimize the directional flow through the torque wrench.

[0098] The components of the trigger lock safety assembly include: first and second notches 808A and 808B of the button lever assembly 806; and trigger protrusion 814. Tool 1E is inactive by default. To activate Tool 1E, the operator must align first or second notch 808A or 808B with trigger protrusion 814, depending on the desired orientation. It should be noted that the operator must use two hands to activate Tool 1E: one hand to operate the button lever assembly 806 and the other hand to operate the trigger 17E. It should be noted that any suitable number of inlets and outlets, slots, surfaces, channels, sleeves, notches, protrusions, sizes, materials, etc., can be used to optimize airflow and torque wrench safety.

[0099] Air tool cycle counter or odometer assembly .recall Figure 6E , which shows a modified back cover 3C1. This is an example of the integration of modern electronic devices with industrial bolt systems that the applicant has recently focused on. Figure 9A and 9B As shown in FIG, the applicant has further modified the rear cover of its pneumatic tool models (e.g., tool 1F). This simplifies the operation of the tool and provides a user-friendly method for making necessary adjustments and configuration changes. One such improvement includes a pneumatic tool cycle counter or odometer assembly 900.

[0100] Generally, odometer assembly 900 comprises: a pressure sensor / transducer assembly 901; a portion of a microcomputer assembly 902 with an associated computer program; and a human / electronic device interface assembly 903. Once tool 1E is activated, microcomputer assembly 902 processes the data output by pressure sensor assembly 901. The principle of pneumatic tool cycle counter assembly 900 is based on the fact that, upon activation, when the trigger is pulled, the internal pressure of tool 1E rapidly drops over a short period of time. Microcomputer assembly 902 is programmed to recognize and record each such rapid pressure drop. These rapid pressure drops are associated with trigger pulls, or cycles, of tool 1E. Human / electronic device interface assembly 903 displays a running total of these cycles on an LCD display.

[0101] In other words, pressurized air enters the air supply assembly 990 of the tool 1E through the air supply connector assembly 991. The pressurized air passes through the air supply tube 992 and enters the pressure transducer air supply channel 993. The pressure sensor / transducer assembly 901 supplies a DC voltage signal to the electronic circuitry of the microcomputer assembly 902. When the trigger 17F is engaged and the air motor rotates, the internal pressure of the torque gun 1E drops. This differential pressure is processed and recorded by a computer program built into the microcomputer assembly 902 and displayed on the human / electronic device interface assembly 903.

[0102] As an example, representative design parameters associated with the odometer assembly 900 include the following. Actuation is defined as a small pressure drop (load pressure) within a predetermined range based on the tool pressure prior to operator use. Relatively large pressure drops such as free-running pressure and / or hose disconnects are ignored, as are relatively small pressure drops such as fluid line "noise". The effective pressure drop range for a given pressure is between the load pressure drop and free-running pressure drop values. Pressure changes after effective actuation are ignored until the current pressure returns to a value close to the pre-activation level. All pressure increases are ignored. The detent count value is in the range of 0 to 99,999, but the counter will continue to count beyond 99,999. The complete actuation counter value can be retrieved and / or reset to 0 using any suitable digital connection (e.g., USB, Bluetooth, WLAN, SMS, etc.). The current count is maintained even when the microcomputer assembly 902 is turned off or powered off.

[0103] Final Thoughts . It should be understood that each of the above elements or combinations of two or more elements may also find effective application in other types of constructions different from the types described above. The features disclosed in the foregoing description or the appended claims or the drawings are expressed in their specific forms or in the form of devices for performing the disclosed functions or methods or processes for obtaining the disclosed results, as appropriate. Such features may be used independently or in any combination of such features to implement the present invention in its various forms. It should be noted that the descriptions of the numbered components in the specification may be slightly different.

[0104] While the present invention has been illustrated and described as embodied in a fluid-handling tool, it is not intended to be limited to the details shown, since various variations and structural modifications may be made without departing in any way from the spirit of the invention.

[0105] Without further analysis, the foregoing will sufficiently disclose the subject matter of the invention so that others, by applying present knowledge, may readily adapt it to various applications without neglecting the features which, from the point of view of the prior art, constitute the essential characteristics of the invention in general or in its specific application.

[0106] When used in this specification and claims, the terms "comprises", "comprising", "having" and variations thereof mean that the specified features, steps or integers are included. The terms should not be interpreted as excluding the presence of other features, steps or components.

Claims

1. A pneumatic pressure relief or burst valve assembly for use with a pneumatic torque tool for tightening and / or loosening threaded fasteners, the pneumatic pressure relief or burst valve assembly comprising: External pneumatic valve part; intermediate pneumatic directional valve part; internal pneumatic valve part; pneumatic reverse valve part; and buttons, The outer pneumatic valve portion, the middle pneumatic directional valve portion, the inner pneumatic valve portion, and the pneumatic reversing valve portion are formed as a unit that can rotate relative to each other and is actuated by the button, and include various inlet and exhaust ports, grooves, surfaces, channels, and sleeves to control and optimize the air flow through the pneumatic torque tool, so that the pneumatic torque tool can be reversed by activating the button without loosening the threaded fastener and simultaneously providing a short, controlled burst of air to relieve the force applied to the reaction point of the pneumatic torque tool.

2. A pneumatic torque tool for tightening and / or loosening threaded fasteners, the pneumatic torque tool comprising a pneumatic pressure relief or burst valve assembly according to claim 1, the pneumatic pressure relief or burst valve assembly being integrated with and / or formed within the pneumatic torque tool.

3. A pneumatic fluid directional and trigger lockout safety valve assembly for use with a pneumatic torque tool for tightening and / or loosening threaded fasteners, the pneumatic fluid directional and trigger lockout safety valve assembly comprising: External pneumatic valve part; internal pneumatic valve part; button rod assembly; Button; and the trigger protrusion, wherein the outer pneumatic valve portion and the inner pneumatic valve portion are formed as a unit capable of relative rotation actuated by the button and the button lever assembly, including various inlet and exhaust ports, grooves, surfaces, channels and sleeves to allow an operator to control and optimize the directional airflow through the pneumatic torque tool; and wherein first and second notches formed on the button lever assembly and the trigger protrusion require an operator to align the first and second notches with the trigger protrusion in a desired direction in order to activate the pneumatic torque tool.

4. A pneumatic torque tool for tightening and / or loosening threaded fasteners, the pneumatic torque tool comprising a pneumatic fluid directional and trigger lock safety valve assembly according to claim 3, the pneumatic fluid directional and trigger lock safety valve assembly being integrated with and / or formed within the pneumatic torque tool.

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