USRE33711E - Ratchet wrench - Google Patents

Ratchet wrench Download PDF

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Publication number
USRE33711E
USRE33711E US07/578,363 US57836390A USRE33711E US RE33711 E USRE33711 E US RE33711E US 57836390 A US57836390 A US 57836390A US RE33711 E USRE33711 E US RE33711E
Authority
US
United States
Prior art keywords
anvil
hammer
jaw
shaft
cam
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US07/578,363
Other languages
English (en)
Inventor
Akira Ono
Toshiro Iritani
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ingersoll Rand Co
Original Assignee
Ingersoll Rand Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ingersoll Rand Co filed Critical Ingersoll Rand Co
Application granted granted Critical
Publication of USRE33711E publication Critical patent/USRE33711E/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/004—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket

Definitions

  • This invention pertains to a powered ratchet wrench for tightening or removing threaded parts.
  • An impact clutch mechanism connects the ratchet mechanism with a rotary power source.
  • Conventional powered ratchet wrenches such as that disclosed in Japanese utility model gazette No. 1976-16,555, have a motor operated by compressed air in the base of the housing. When a throttle lever is pressed, compressed air flows to the motor, and the output shaft of the motor turns a transmission shaft by way of speed reducing gears. Slow speed and high torque are transmitted to the transmission shaft.
  • the eccentric rotation of a crankshaft at the front end of the transmission shaft oscillates a ratchet yoke.
  • the movement of the ratchet yoke causes the ratchet spindle or tool head of a ratchet mechanism to rotate so that a bolt, nut, or other threaded part is tightened or removed.
  • conventional powered ratchet wrenches are unsuitable for use in tight places where there is room for only one hand. Because the ratchet wrench cannot be gripped tightly in such cramped places, and since it is difficult to release the throttle lever at exactly the right time, the hand is often jerked or loses its grip. The operator's hand can be forcefully thrown against an obstruction and injured, or the ratchet wrench can forcefully strike a projecting part and be damaged.
  • This invention provides a powered ratchet wrench such that, when used to tighten or remove a part or fastener, an impact clutch mechanism provides the connection between the tool motor and the ratchet mechanism.
  • an impact clutch mechanism provides an initial direct connection between the motor and the ratchet mechanism to set or snug-up the fastener during "run down”.
  • the ratchet mechanism is thereafter rotated by a series of rotational impacts delivered by the impact clutch.
  • the impacts break the fastener loose, while the direct drive "runs up” the fastener. If the throttle lever is not released when fastener tightening is completed, only minimal torque reaction force is transmitted to the operator due to the impact clutch.
  • the tool can preform consistent tightening quickly and reliably, without manual assistance.
  • the ratchet wrench according to this invention is constructed so that the motor and ratchet mechanism are connected with an impact clutch rather than a speed reducing gear device, as in the conventional wrench.
  • the impact clutch allows the ratchet mechanism to rotate either under direct motor power or by rotational impacts. An impact can be produced rapidly and extremely smoothly during each motor rotation, so that the threaded part can be firmly tightened by the ratchet.
  • the connection between the motor and the ratchet is intermittently broken, so that the ratchet is rotating with minimum reaction to the operator.
  • This wrench is also suitable for use in tight places with room for only one hand on the tool. The hand won't be thrown against the work piece and injured, as could happen previously. Also, the danger of the ratchet wrench striking an obstruction and being damaged is avoided.
  • FIG. 1 shows a longitudinal cross section of the ratchet wrench.
  • FIG. 2 shows a perspective view of the base end of the anvil shaft, which is an essential part of the invention.
  • FIG. 3 shows a cross section along line III--III of FIG. 1, showing the hammer cage and cam ball of the impact clutch mechanism, which constitute essential parts of the invention.
  • FIG. 1 shows a longitudinal cross section through a preferred embodiment of the ratchet wrench.
  • the ratchet wrench 10 is constructed of several components which will first be described generally.
  • a throttle lever 20 controls the air flow to a rotary air motor 30.
  • the rotary output of the motor is transmitted to the hammer assembly 40 of an impact clutch mechanism.
  • a spring 50 biases an anvil shaft 60 into association with the hammer assembly 40.
  • the anvil shaft can be directly driven by the motor through the hammer assembly or can be driven intermittently by a series of rotational impacts from the hammer assembly.
  • the rotation of a crank on the anvil shaft causes the reversible ratchet mechanism 70 to rotate in the desired direction, thus tightening or removing a threaded part or fastener. Only a small reaction force is transmitted by the tool to the operator once the fastener is tight.
  • the tool 10 includes a motor housing 11 and a ratchet housing 12, secured together in fixed relation such as by a threaded coupling ring 13 and coupling nuts 14.
  • a throttle lever 20 opens and closes a throttle valve 22.
  • throttle valve 22 When throttle valve 22 is in the open position, compressed air enters the tool at air inlet 24 which is connected to a suitable compressed air source. The compressed air flows into the rotary air motor 30 and transfers its energy to the rotor. The spent air is exhausted from exhaust 26.
  • the rotary motor 30 is located in the motor housing 11.
  • an air motor is shown, but any rotary power source such as a hydraulic or electric motor could also be used.
  • Air motor 30 has a rotor 34 and an extending output shaft 31.
  • the two ends of rotor 34 are supported by bearings 33 which in turn are supported by end plates 32.
  • the rotor is mounted for rotation in the cylinder 35, the open ends of which are covered by the end plates 32.
  • the cylinder has an eccentric bore, as is typical of conventional air motors.
  • a plurality of vanes 36 are slidably mounted in radial slots in the rotor. The vanes slide radially back and forth in the slots as the rotor turns due to centrifugal force and the eccentric inner surface of cylinder 35. As the inlet air pushes against vanes 36, it causes rotor 34 to rotate, thus causing output shaft 31 to rotate therewith.
  • Numeral 41 designates the hammer cage. It is cup shaped, having a cylindrical wall portion and a base portion which together form an inner surface designated by numeral 44. Within the hammer cage on the inner surface 44 are two diametrically opposed axial grooves. The axial grooves extend only part way down the cylindrical wall portion, forming semi-circular shoulders at a specified distance above the base portion.
  • the hammer cage 41 in this preferred embodiments is directly driven by the output shaft 31, as for example by a splined connection. Alternatively, however, the hammer cage could be gear driven.
  • a circular raceway 47 Formed in the base portion of the hammer cage is a circular raceway 47, which is concentric about the axis of rotation. Coinciding with the raceway, but extending for only a limited number of degrees, is a larger-dimensioned cam ball pocket 46.
  • the cam ball pocket typically describes an arc in the range of 45 to 180 degrees.
  • a cam ball 43 is held in the pocket and rolls freely through the arc.
  • the anvil shaft 60 carries an axially extending cam 62.
  • the cam 62 is preferably a one-sided cam and projects axially from the end of the anvil shaft.
  • the cam forms a cam peak with preferably one gradually rising inclined surface adjacent the cam peak and one sharply falling surface adjacent the other side of the peak.
  • the inclined surface occupies about a 90 degree arc on the anvil shaft. The sharp surface facilitates escape of the cam.
  • the cam 62 and the raceway 47 are dimensioned so that when the hammer cage rotates with the cam extending into the raceway, the hammer cage rotates freely without interference from the cam. In other words, as the raceway rotates relative to the cam, the raceway permits the cam to extend into it without interference.
  • the anvil shaft carries at least one, and preferably two anvil jaws 63.
  • the anvil jaws are diametrically opposed and radially extending.
  • the outer radial surfaces of the anvil jaws are dimensioned so that the inner chamber 44 of the hammer cage can rotate freely about the anvil jaws.
  • the anvil shaft also carries an eccentric crank 61 at the shaft end opposite the cam 62.
  • the anvil shaft 60 is supported by needle bearing 54 so that it slides freely in the axial direction as well as freely rotates.
  • the anvil shaft is also journaled for rotation and axial movement by a bore in hammer cage top 42.
  • Numeral 50 designates a helical coil biasing spring of a size to fit around a reduced diameter portion of the anvil shaft 60 and abut against a shoulder on the shaft. This biasing spring normally urges the anvil shaft 60 toward the base portion of the hammer cage 41, such that the extending cam 62 normally projects into the raceway 47.
  • At least one, and preferably two hammer jaws 45 are received in the axial grooves of the hammer cage 41.
  • the hammer jaws are harden pins and when in place are half embedded in the cylindrical wall portion and half exposed in the inner chamber 44.
  • the hammer jaws rest on the shoulders of the axial grooves so as not to extend to the base portion of the hammer cage.
  • An uninterrupted cylindrical surface is provided below the shoulders at the base of the inner chamber 44. This surface allows the hammer cage 41 to rotate relative to the anvil jaws 63 when the biasing spring urges the anvil shaft toward the base portion of the hammer cage without impacting on the anvil jaws.
  • the hammer cage top 42 has a short, snug-fitting, reduced diameter portion that is inserted into the inner chamber 44 of the hammer cage.
  • the cage top also has two diametrically opposite pilot bores that axially align with the axial grooves of the hammer cage.
  • the hammer jaws 45 are also received into these pilot bores to fix the hammer jaws in an axial position and to lock the hammer cage and hammer cage top together against relative rotation.
  • FIG. 1 illustrates the ratchet wrench in a position when the biasing spring 50 is extended and the cam 62 is positioned in the raceway 47.
  • the anvil jaws 63 are biased by the spring toward the base of the hammer cage such that during rotation of the hammer cage, the hammer jaws 45 do not intercept the anvil jaws 63.
  • the uninterrupted cylindrical portion of the hammer cage 41 that portion located below the hammer jaws, rotates radially adjacent to the anvil jaws.
  • Eccentric crank 61 is positioned at the end of the anvil shaft 60 opposite the cam 62.
  • the crank slides axially in the bore of a drive bushing 52 so as to allow for the axial movement of the anvil shaft.
  • Drive bushing 52 slides vertically in a bushing pocket 72 of ratchet yoke 71 so as to accommodate the up and down movement of the crank 61 as it rotates.
  • the oscillating movement of the ratchet yoke is transferred to the ratchet mechanism 70.
  • the ratchet mechanism rotates a ratchet spindle or tool head 73 in a conventional manner as is well known in the prior art.
  • the ratchet reverse knob 74 By turning the ratchet reverse knob 74 to the appropriate setting, the direction of rotation of the ratchet spindle can be determined.
  • the tool can be operated to tighten or remove a fastener by setting the ratchet reverse knob 74.
  • the ratchet mechanism is first simply directly driven by the motor through the impact clutch to rotate or "run down" the fastener to a snug position.
  • impacts are applied by the impact clutch mechanism to further rotate the ratchet mechanism and further torque the fastener.
  • FIG. 1 illustrates the "run down" position of the tool.
  • the anvil shaft 60 is in its normal axial position, that is biased toward the base portion of the hammer cage with the one-sided cam 62 extending into the raceway 47.
  • the cam ball 43 is contained in the limited arc cam ball pocket 46.
  • output shaft 31 causes hammer cage 41 to rotate with it due to the splined connection.
  • the trailing shoulder of the rotating cam ball pocket engages and drives the cam ball in the direction of rotation directly of the hammer cage.
  • the cam ball next engages but does not roll up the inclined surface of the one-sided cam 62.
  • the rotating cam ball imparts rotation to the anvil shaft 60.
  • the gradual inclined surface of the cam 62 begins to ride up on the cam ball 43 due to the continued rotation of the cam ball with the hammer cage.
  • the anvil shaft and the attached anvil jaws 63 are moved axially forward away from the base portion of the hammer cage.
  • the cam ball cooperates with the cam to move the cam and attached anvil shaft axially forward as the cam rides up on the cam ball as it revolves within the cam ball pocket and rotates with the hammer cage.
  • This impact drives the anvil shaft 60 in the direction of rotation of the hammer cage until sufficient resistance is met.
  • This resistance is the resistance the fastener encounters as it tightens and is transferred from the fastener through the ratchet mechanism to the anvil shaft 60.
  • the anvil shaft stops rotating and the hammer jaws and anvil jaws will begin to disengage.
  • the force in the compressed biasing spring 50 overcomes the axial momentum of the anvil shaft and begins to push the cam back towards the hammer cage base.
  • the steep escape surface adjacent the cam peak kicks the cam ball in the direction of the leading edge of the cam ball pocket. The cam peak then again enters the raceway 47.
  • the cam 62 once again encounters the cam ball 43.
  • the cam ball rotates in the cam ball pocket with the cam until the ball reaches the trailing edge of the pocket. If there still is sufficient resistance due to fastener tension, the cam ball will again force the cam to ride up on the cam ball and the impact sequence will be repeated until the fastener can not be further tightened.
  • the cam ball thus times the impacts.
  • the impact clutch mechanism will continue to cause the hammer to impact on the anvil.
  • the ratchet mechanism will not provide any more tightening torque to the fastener. However, the tool operator will not experience any torque reaction due to the tool turning on the tightened fastener. Rather the operator will experience only the minimal reactions due to the impact clutch.
  • anvil shaft 60 can be constructed of two pieces to facilitate the manufacture and assembly of the tool.
  • a separate cam portion having the cam peak and anvil jaws can be positioned inside the inner chamber 44 of the hammer cage and splined to a shaft portion extending through the bore of the hammer cage top.
  • biasing spring 50 can be positioned anywhere along the shaft portion of the anvil shaft 60.
  • the biasing spring can be positioned on the splined connection between the cam portion and the shaft portion.
  • the purpose of the impact clutch mechanism is to translate rotary motion to interrupted rotary motion having less torque reaction.
  • the impact clutch mechanism described in connection with the preferred embodiment can be broadly categorized as a unique embodiment of a cam engage, spring disengage impact clutch. Other embodiments of the cam engage, spring disengage type impact clutch are also considered to be within the scope of this invention.
  • the anvil shaft moves axially.
  • An alternate embodiment can provide for the hammer jaws to move axially rather than the anvil shaft.
  • One advantage of this invention over the prior art includes minimizing the torque reaction to the tool operator when a fastener is tight and the tool continues to run. This allows the tool to be safely operated with one hand and also in confined and awkward situations. The tool will also produce a consistent tightening torque. The operator will not have to stop the tool before the fastener is tight and manually tighten the fastener out of concern for his own safety and well-being. Additionally, the tool allows a faster "run-down" of the fasteners than prior art powered ratchets.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
US07/578,363 1985-05-15 1990-09-04 Ratchet wrench Expired - Lifetime USRE33711E (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP60103158A JPH0635115B2 (ja) 1985-05-15 1985-05-15 ラチエットレンチのハンマ構造
JP60-103158 1985-05-15

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
US18814388A Continuation 1988-04-29 1988-04-29
US07/363,419 Reissue US4919022A (en) 1988-04-29 1989-06-05 Ratchet wrench

Publications (1)

Publication Number Publication Date
USRE33711E true USRE33711E (en) 1991-10-08

Family

ID=14346693

Family Applications (1)

Application Number Title Priority Date Filing Date
US07/578,363 Expired - Lifetime USRE33711E (en) 1985-05-15 1990-09-04 Ratchet wrench

Country Status (5)

Country Link
US (1) USRE33711E (fr)
EP (1) EP0202130B1 (fr)
JP (1) JPH0635115B2 (fr)
CA (1) CA1281920C (fr)
DE (1) DE3674634D1 (fr)

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5890848A (en) * 1997-08-05 1999-04-06 Cooper Technologies Company Method and apparatus for simultaneously lubricating a cutting point of a tool and controlling the application rate of the tool to a work piece
US6082986A (en) 1998-08-19 2000-07-04 Cooper Technologies Reversible double-throw air motor
US6105595A (en) 1997-03-07 2000-08-22 Cooper Technologies Co. Method, system, and apparatus for automatically preventing or allowing flow of a fluid
US6241500B1 (en) 2000-03-23 2001-06-05 Cooper Brands, Inc. Double-throw air motor with reverse feature
US6742609B2 (en) 2001-05-11 2004-06-01 United Diamond Ltd. Rotational impact drill assembly
US20040149469A1 (en) * 2003-01-31 2004-08-05 Ingersoll-Rand Company Rotary tool
US20060053979A1 (en) * 2004-09-10 2006-03-16 Sp Air Kabusiki Kaisha Corporation Hand tool with impact drive and speed reducing mechanism
USD554460S1 (en) 2006-04-18 2007-11-06 Ingersoll-Rand Company Air tool
USD578852S1 (en) 2006-05-01 2008-10-21 Ingersoll-Rand Company Air tool
US20100064864A1 (en) * 2008-09-15 2010-03-18 Sp Air Kabushiki Kaisha Double Hammer Clutch Impact Wrench
US20100101815A1 (en) * 2008-10-27 2010-04-29 Sp Air Kabushiki Kaisha Jumbo hammer clutch impact wrench
USD617620S1 (en) 2009-06-04 2010-06-15 Ingersoll-Rand Company Power ratchet wrench
USD623033S1 (en) 2009-09-23 2010-09-07 Ingersoll-Rand Company Grinder
US20100326243A1 (en) * 2009-06-30 2010-12-30 Ingersoll Rand Company Ratchet wrench with collar-actuated reversing mechanism
US20130239753A1 (en) * 2012-03-16 2013-09-19 Basso Industry Corporation Pneumatic driven ratchet wrench
US20140083256A1 (en) * 2012-09-21 2014-03-27 Basso Industry Corp. Pneumatic ratchet wrench having a shrunk head section
US20150165603A1 (en) * 2013-12-17 2015-06-18 Ming-Ta Cheng Power device with a unicorn impact unit
US9272400B2 (en) 2012-12-12 2016-03-01 Ingersoll-Rand Company Torque-limited impact tool
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US9737978B2 (en) 2014-02-14 2017-08-22 Ingersoll-Rand Company Impact tools with torque-limited swinging weight impact mechanisms
US20230051397A1 (en) * 2021-08-10 2023-02-16 Panasonic Intellectual Property Management Co., Ltd. Impact rotary tool
US20240286254A1 (en) * 2023-02-23 2024-08-29 Ju He Industry Co., Ltd. Impact powered torque wrench
US12076839B2 (en) * 2018-12-24 2024-09-03 Js Products, Inc. Power ratchet

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62246480A (ja) * 1986-04-16 1987-10-27 信濃空圧工業株式会社 締め付け装置
US4791836A (en) * 1987-04-01 1988-12-20 Chicago Pneumatic Tool Company Ratchet mechanism
JPS63256373A (ja) * 1987-04-14 1988-10-24 信濃空圧工業株式会社 締め付け装置
SE504620C2 (sv) * 1995-04-26 1997-03-17 Atlas Copco Tools Ab Pneumatiskt momentimpulsverktyg
DE10309012B3 (de) * 2003-03-01 2004-08-12 Hilti Ag Steuerverfahren einer axial schlagenden und drehenden Elektrohandwerkzeugmaschine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3212590A (en) * 1963-07-29 1965-10-19 Reed Roller Bit Co Impact wrench
US3414066A (en) * 1966-08-31 1968-12-03 Chicago Pneumatic Tool Co Impact wrench
US3428137A (en) * 1967-10-12 1969-02-18 Chicago Pneumatic Tool Co Impact wrench
US4063601A (en) * 1976-08-23 1977-12-20 Dresser Industries, Inc. Rotary impact tool
US4184552A (en) * 1977-05-17 1980-01-22 Marquette Metal Products Company Manually actuated impact tool
US4346630A (en) * 1979-12-17 1982-08-31 Rodac Pneumatic Tools Ratchet wrench
US4382476A (en) * 1981-12-03 1983-05-10 Swenson Oscar J Manual torque magnifying impact tool

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3174597A (en) 1961-12-19 1965-03-23 Chicago Pneumatic Tool Co Impact clutch
JPS5435380Y2 (fr) * 1971-04-13 1979-10-27
JPS5235708B2 (fr) * 1971-09-27 1977-09-10
JPS4918313U (fr) * 1972-05-17 1974-02-16
US4313505A (en) * 1979-08-27 1982-02-02 Rodac Pneumatic Tools Rotary impact clutch

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3212590A (en) * 1963-07-29 1965-10-19 Reed Roller Bit Co Impact wrench
US3414066A (en) * 1966-08-31 1968-12-03 Chicago Pneumatic Tool Co Impact wrench
US3428137A (en) * 1967-10-12 1969-02-18 Chicago Pneumatic Tool Co Impact wrench
US4063601A (en) * 1976-08-23 1977-12-20 Dresser Industries, Inc. Rotary impact tool
US4184552A (en) * 1977-05-17 1980-01-22 Marquette Metal Products Company Manually actuated impact tool
US4346630A (en) * 1979-12-17 1982-08-31 Rodac Pneumatic Tools Ratchet wrench
US4382476A (en) * 1981-12-03 1983-05-10 Swenson Oscar J Manual torque magnifying impact tool

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6105595A (en) 1997-03-07 2000-08-22 Cooper Technologies Co. Method, system, and apparatus for automatically preventing or allowing flow of a fluid
US5890848A (en) * 1997-08-05 1999-04-06 Cooper Technologies Company Method and apparatus for simultaneously lubricating a cutting point of a tool and controlling the application rate of the tool to a work piece
US6082986A (en) 1998-08-19 2000-07-04 Cooper Technologies Reversible double-throw air motor
US6217306B1 (en) 1998-08-19 2001-04-17 Cooper Technologies Company Reversible double-throw air motor
US6241500B1 (en) 2000-03-23 2001-06-05 Cooper Brands, Inc. Double-throw air motor with reverse feature
US6742609B2 (en) 2001-05-11 2004-06-01 United Diamond Ltd. Rotational impact drill assembly
US20040149469A1 (en) * 2003-01-31 2004-08-05 Ingersoll-Rand Company Rotary tool
US6889778B2 (en) 2003-01-31 2005-05-10 Ingersoll-Rand Company Rotary tool
US20060053979A1 (en) * 2004-09-10 2006-03-16 Sp Air Kabusiki Kaisha Corporation Hand tool with impact drive and speed reducing mechanism
US7080578B2 (en) * 2004-09-10 2006-07-25 Sp Air Kabusiki Kaisha Corporation Hand tool with impact drive and speed reducing mechanism
USD554460S1 (en) 2006-04-18 2007-11-06 Ingersoll-Rand Company Air tool
USD578852S1 (en) 2006-05-01 2008-10-21 Ingersoll-Rand Company Air tool
US20100064864A1 (en) * 2008-09-15 2010-03-18 Sp Air Kabushiki Kaisha Double Hammer Clutch Impact Wrench
US20100101815A1 (en) * 2008-10-27 2010-04-29 Sp Air Kabushiki Kaisha Jumbo hammer clutch impact wrench
US8261849B2 (en) * 2008-10-27 2012-09-11 Sp Air Kabushiki Kaisha Jumbo hammer clutch impact wrench
USD617620S1 (en) 2009-06-04 2010-06-15 Ingersoll-Rand Company Power ratchet wrench
US20100326243A1 (en) * 2009-06-30 2010-12-30 Ingersoll Rand Company Ratchet wrench with collar-actuated reversing mechanism
US8051746B2 (en) 2009-06-30 2011-11-08 Ingersoll Rand Company Ratchet wrench with collar-actuated reversing mechanism
USD623033S1 (en) 2009-09-23 2010-09-07 Ingersoll-Rand Company Grinder
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US20130239753A1 (en) * 2012-03-16 2013-09-19 Basso Industry Corporation Pneumatic driven ratchet wrench
US8757031B2 (en) * 2012-03-16 2014-06-24 Basso Industry Corp. Pneumatic driven ratchet wrench
US20140083256A1 (en) * 2012-09-21 2014-03-27 Basso Industry Corp. Pneumatic ratchet wrench having a shrunk head section
US9713866B2 (en) * 2012-09-21 2017-07-25 Basso Industry Corp. Pneumatic ratchet wrench having a shrunk head section
US9272400B2 (en) 2012-12-12 2016-03-01 Ingersoll-Rand Company Torque-limited impact tool
US20150165603A1 (en) * 2013-12-17 2015-06-18 Ming-Ta Cheng Power device with a unicorn impact unit
US9737978B2 (en) 2014-02-14 2017-08-22 Ingersoll-Rand Company Impact tools with torque-limited swinging weight impact mechanisms
US12076839B2 (en) * 2018-12-24 2024-09-03 Js Products, Inc. Power ratchet
US20230051397A1 (en) * 2021-08-10 2023-02-16 Panasonic Intellectual Property Management Co., Ltd. Impact rotary tool
US11865689B2 (en) * 2021-08-10 2024-01-09 Panasonic Intellectual Property Management Co., Ltd. Impact rotary tool
US20240286254A1 (en) * 2023-02-23 2024-08-29 Ju He Industry Co., Ltd. Impact powered torque wrench
US12337444B2 (en) * 2023-02-23 2025-06-24 Ju He Industry Co., Ltd. Impact powered torque wrench

Also Published As

Publication number Publication date
DE3674634D1 (de) 1990-11-08
CA1281920C (fr) 1991-03-26
JPS61260982A (ja) 1986-11-19
EP0202130B1 (fr) 1990-10-03
JPH0635115B2 (ja) 1994-05-11
EP0202130A1 (fr) 1986-11-20

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