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US3703933A - Impact wrench with torque control means - Google Patents

Impact wrench with torque control means Download PDF

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Publication number
US3703933A
US3703933A US133647A US3703933DA US3703933A US 3703933 A US3703933 A US 3703933A US 133647 A US133647 A US 133647A US 3703933D A US3703933D A US 3703933DA US 3703933 A US3703933 A US 3703933A
Authority
US
United States
Prior art keywords
housing
cut
shaft
motor
impact wrench
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
US133647A
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English (en)
Inventor
Knut Christian Schoeps
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.)
Atlas Copco AB
Original Assignee
Atlas Copco AB
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 Atlas Copco AB filed Critical Atlas Copco AB
Application granted granted Critical
Publication of US3703933A publication Critical patent/US3703933A/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
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/145—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers
    • B25B23/1453—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers for impact wrenches or screwdrivers

Definitions

  • the invention relates to impact wrenches incorporating torque control means for controlling the tightening of threaded fasteners, for example screws and nuts, by means of such power driven tools. More particularly the invention relates to impact wrenches with torque control means of the type incorporating a drive motor, a cut-off means for the motor, a drive shaft in the motor, and a body operatively associated with the drive shaft which body in response to rotational resistance at each impact is displaced against the action of a return force. In such devices the body is subjected to inertial forces or rebound forces when impacting occurs.
  • an impact wrench with torque control means comprising a housing, a drive motor in said housing, cut-off means for said motor in said housing, a drive shaft in said motor, an anvil rotatably journalled in said housing and adapted to be connected to a workpiece, a rotary impact motor in said housing operatively interconnected between said drive shaft and said anvil for applying a succession of rotational impacts against said anvil and thereby to said workpiece, a body in said housing operatively associated with said drive shaft for being displaced at each impact relative to said drive shaft in response to rotational resistance of said anvil, means for producing a return force active against said body to cancel the displacements thereof, an adding mechanism in said housing for adding the lengths of displacement of said body, and means in said housing associated with said adding mechanism for activating said cut-ofi means at attainment in said adding mechanism of a predetermined sum total of said lengths of displacement.
  • FIG. 1 shows a fragmentary side view drawn partly in section of a wrench embodying the invention.
  • FIG. 2 is a cross section on the line 2-2 in FIG. 1.
  • FIG. 3 is a cross section on the line 3-3 in FIG. 1
  • FIG. 4 is a fragmentary section on the line 44 in FIG. 3.
  • FIG. 5 shows a fragmentary section on the line 5-5 in FIG. 3 and illustrates by broken lines an operating position of the elements covered by the section.
  • FIGS. 6 and 7 correspond to FIGS. 4 and 5 but show an alternative position of the elements involved.
  • FIG. 8 is a section on line 8-8 in FIG. 3.
  • FIG. 9 is. a rear end view drawn partly in section and seen on the line 9-9 in FIG. 1.
  • FIG. 10 is a section on the line 10-10 in FIG. 1.
  • FIG. 11 is a section on the line 11-11 in FIG. 1.
  • FIG. 12 shows an enlarged partial view of FIG. 8.
  • FIG. 13 is a section on the line 13-13 in 1 0.
  • rotor I As an example for the description has been chosen an application of the invention to a pneumatically driven impact wrench but the invention may also be applied with advantage in connection with electrically'or hydraulically driven impact wrenches.
  • the rotor 21 of a motor-preferably made as a vane motor.
  • the rotor 21 drives a conventional rotary impact motor, not shown, the anvil 23 of which projects from the front portion with a square end 24 intended-for taking up asocket wrench.
  • the socket wrench not shown, is brought into engagement a workpiece such as a nut to be tightened and the motor housing 20 is directed and ls dbyy y fshes
  • the motor housing 20 carries a backhead 26 having a cover 27, these parts enclosing the torque control means.
  • the main parts of the latter are formed by an in- The inertial or flywheel body 28 encloses in cap-like manner the rear end of the rotor 21 which is provided with cam means in the-form of oblique grooves 34 into which are inserted cam balls 35.
  • the outer halves of the cam balls 35 project into internal oblique grooves in the inner portion of the inertial body 28 radially around the rear end of the rotor 21.
  • a piston 37 is axially slidably supported in the backhead 26 and abuts under the load of a helical spring 38 in axial direction against the outer side of the inertial body 28, producing a return force active to but the inertial body 28 against the end face of the rotor 21 whereby the' cam balls 35 are caused to take inner positions in the respective oblique grooves 34, 36, FIG. 7. Normally the inertial body rotates conjointly with the rotor 21 occupying the position illustrated in FIG. 7.
  • the rotor 21 is momentarily retarded by the rotational resistance while the inertial body 28 in response to such resistance persists in its rotational movement and forces the cam balls 35 to roll outwardly in the oblique grooves 34 and 36, respectively, to the position illustrated in FIG. 5.
  • the inertial body 28 is displaced axially relative to the rotor 21 a distance increasing with the I increased rotational resistance at impact and under compression of the helical spring 38 of the piston 37 and axial retraction of the latter.
  • the piston 37 is returned by the spring 38 towards the rotor 21 and the inertial body 28 and the cam balls 35 are simultaneously returned to the posi 1192 in F
  • the adding shaft 29 is journalled in the backhead 26 on suitable ball bearings in a plane perpendicular to the rotational axis of the rotor 21.
  • the adding shaft 29 is associated with means for transforming the axial movements of the inertial body 28 to unidirectional angular movement of the adding shaft 29, which means are provided by a pair of free-wheel-mechanisms 39,40 each comprising rollers or needle bodies 41 which at rotationin one direction are pressed by an outer ring 42 provided with cam surfacesinto non-rotary engagement with the adding shaft and at rotation in the opposite direction through the intermediary of a needle holder provided with resilient elements allow free rotation of the outer ring 42 relative to the adding shaft 29.
  • the outer ring 42 of thefree-wheel-mechanism 39 is carried non-rotatably by a ring shaped hub or driving member 43 which by means of a tooth 44 is in engagement with a ring groove 45 on the piston 37.
  • the other free wheel-mechanism 40 is received at the outer ring 42 thereof non-rotatably in a ring shaped hub 46 which by a locking plug 47 is non-rotatably locked in the backhead 26.
  • the locking direction of the two freewheel-mechanisms 39, 40 is chosen such, FIGS. 4,5 and 6,7, respectively, that during movement of the inertial body 28 axially away from the rotor 21, FIG. 5, the ring hub 43' will rotate freely in counter-clockwise direction with respect to the adding shaft which by the free-wheel-mechanism 40 is locked against rotation in counter-clockwise direction.
  • the adding shaft 29 is by means of a bevel gear 48 in engagement with a bevel gear 49 on a clutch shaft 30 which is supported on suitable ball bearings in the backhead 26 and the cover 27 thereof.
  • a gear 50 On the clutch shaft 30 is freely rotatably journalled a gear 50 the hub of which is formed as one half 51 of a conical friction clutch.
  • the cooperating other half 52 is carried slidably in axial direction on the clutch shaft 30 and is nonrotatably fixed thereto by a cross pin 53 traversing the clutch half 52 and the shaft 30, and being slidable axially in an axial groove 54 formed in the clutch shaft 30.
  • the clutch shaft is made hollow and carries a helical spring 55 bearing against the cross pin 53 and the cover 27 and striving to move the cross pin 53 and thus the clutch half 52 to such a position in the groove 54 as to release the clutch half 52 from the clutch half 51 of the gear 50.
  • the clutch shaft 30 is furthermore slidably supported an axial pin 56 for actuating the cross pin 53 which axial pin for purposes of engaging the clutch halves 52, 51 is actuatable by actuating means in response to actuation of the main control means of the impact wrench for the drive motor thereof. In electrically driven wrenches such actuation will be attained by application of a suitable solenoid.
  • a servo piston motor including a servo piston 57 affixed to the axial pin 56 is applied the servo piston 57 striving under the force bias of annular springs 58 to move the axial pin 56 to inactivated position in which the cross pin 53 is unaffected.
  • pressure fluid is supplied via a passage 59 to the cylinder 60 of the servo piston 57, the clutch halves 52, 51 are caused to engage by the axial pin 56 applying a thrust against the cross pin 53.
  • the passage 59 is pressurized or can be exhausted, respectively, by means of the reversing valve 61 of the wrench diagrammatically illustrated in FIGS.
  • the setting drum 31, 65 includes a drum portion 31 which is rotatably journalled on a base portion 65, FIG.
  • a clockwork spring 67 is tensioned between a groove 68 in the base portion 65 and a pin 69 in the drum portion 31, FIG. 10.
  • the clockwork spring 67 is pre-stressed striving to but a pin 70 on the drum portion 31 against a tooth 64, FIG. 10, arranged on the base portion 65 on the rim of a flange thereon.
  • the base portion 65 is adjustably affixed to the cover 27 in a manner to prevent rotation between these parts
  • a cogwheelshaped locking plate 71 is axially slidably but nonrotatably mounted in the base portion 65 on a cross pin 72 engaging an axial groove 73 in the locking plate 71 and is depressable against the action of helical springs 74 which are inserted between the base portion 65 and the interior of the lockingplate 71 to urge the latter outwardly into locking position, FIG. 1.
  • the locking plate 71 mates with a toothed ring 75 which by means of screws is afiixed to the cover 27, FIG. 9.
  • the locking plate When the locking plate is depressed axially towards thebase portion 65, it will be released from the toothed ring 75 so that the locking plate 71 by a suitable tool insertable into axial bores 76 in the plate. 71 may be turned together with the base portion 65 and the drum portion 31 to the desired angular position in the cover 27, whereupon the plate 71 is permitted to spring out into'locking engagement with the toothed ring 75, the base portion 65 thus becoming locked in the desired angular position.
  • the drum portion 31 carries an abutment embodied by a release pin 77 for activating the motor cut-off means 32.
  • the motor cut-0E 32 is formed by a cut-off valve provided with a closing head which is slidable in a bore 80 in the backhead 26 through the intermediary of a base shaped as a piston 79 of equal size with the head 32.
  • a helical spring 81 is inserted between the cover 27 and the piston 79 and strives to move the cut-off 32 in a direction away from the cover 27 to but against the bottom 82 of the bore 80 in which position both faces of the closing head of the cut-off 32 are pressurized.
  • a bell crank lever 84 is pivotally journalled on a pivot 83 adjacent the piston 79 between the cover 27 and the backhead 26 and is actuated by a turning spring 85 to latch in the bottom butting position of the cut-off 32 under the action of the turning spring 85 behind an annular shoulder 86 on the piston 79, thus locking the cut-off 32 in inactivated position between the lever 84 and the shoulder 82, FIG. 13.
  • the bore 80 is supplied with pressure fluid from the reversing valve 61 via a passage 87 and the pressure fluid flows from the bore 80 past the cut-off 32 via a passage 88 to the motor inlet 89 in the motor housing 20, FIG. 1. By pressure in the bore 80 acting against the piston 79, the cutoff 32 is biased in the direction of the cover 27.
  • the release pin 77 of the setting drum 31 cooperates with the lever 84 and is capable of applying a thrust against the arm 90 thereof remote from the shoulder 86 whereby the lever 84 is turned against the action of the turning spring 85 away from the ring shoulder 86.
  • the pressure in the bore 80 will displace the piston 79 towards the cover 27 so that the head of the cut-off 32 engages the central part of the bore 80 thus closing off the supply of pressure fluid from the passage 87 to the passage 88 whereby the drive motor of the wrench is stopped.
  • the cut-off preferably will be embodied by a conventional solenoid-actuated switch for the main current with the solenoid striving to displace the switch member past the lever 84 when the latter is released by the release pin 77 acting against the arm 90.
  • the base portion 65 of the setting drum 31, 65 is first adjusted to the desired angular starting position in the backhead 26. This means that one selects by way of adjustment of the base portion 65 the desired angular starting position of the release pin 77, FIG. 11, and of the tooth 64 of the base portion 65, against which the pin 70 is butted by the clockwork spring 67 in the starting position. Thereupon the locking plate 21 is allowed to spring out into locking engagement with the toothed ring 75 so that the position of the base portion 65 is fixed.
  • the wrench is connected to a suitable pressure fluid supply, for example to a source of compressed air.
  • the throttle valve 62 of the handle 25 is depressed so that the reversing valve 61, set to cause clockwise rotation of the motor 21 when the tool is viewed from the rear in FIG. 1, is pressurized as is the case with the passages 87,59.
  • the pressure fluid From the passage 59 the pressure fluid enters the cylinder 60 actuating the servo piston 57 to bring the clutch halves 52, 51 of the clutch shaft into frictional engagement.
  • the pressure fluid passes through the passage 87 and the bore 80 past the motor cut-off 32 and thence to the passage 88 and to the motor inlet 89 to rotate the rotor 21 in clockwise direction.
  • the screw rotates until it has been driven down against the workpiece whereupon the anvil 23 stops and the rotary impact motor starts impacting.
  • the inertial or flywheel body 28 Prior to each impact the inertial or flywheel body 28 is in the state of rapid rotation and when the anvil 29 at impact causes the rotor 21 to stop, the inertial body 28 will continue its rotation performing, by reason of the oblique grooves 34, 36 and the cam balls 35, an axial rearwardly directed stroke for each impact delivered.
  • the piston 37 for each impact delivered is firstly displaced freely rearwardly, FIG. 5, and thereafter returned in forward direction under the bias of the spring 38 entraining the adding shaft 29.
  • the uni-directional angular movements of the adding shaft 29 are transmitted directly to the clutch shaft 30 and via the clutch halves 52,51 to the gear 50.
  • the adding shaft 29 sums up the length of displacement by uni-directional rotation and turning of the gear 50, the rotation of the latter being transmitted via the gear rim 63 to the drum portion 31.
  • the turning motion forces the pin of the setting drum 31 to leave the tooth 64 and as the increment lengths of the displacements generate tuming movement of the adding shaft 29 and the setting drum 31, the pin 77 will be successively displaced towards the arm 90.
  • the release pin 77 hits the arm 90 the lever 84 is unlatched and the motor cut-off is released so that it can fall into the middle portion of the bore thus closing the air supply to the motor inlet 89.
  • the throttle valve 62 Upon cut-off the operator has to release the throttle valve 62, the latter being preferably made such as to exhaust in the released position thereof the passages 87 and 59 and the reversing valve 61 via the throttle valve 62.
  • the closing bias acting against the piston 79 disappears and the spring 81 of the cut-off 32 is thus in the position to return the cut-off to open position supported against the bottom of the hole 82.
  • Relief of the passage 59 relieves the servo piston 57 and the annular springs 58 thereof displace the axial pin 56 away from the cross pin 53.
  • This allows the tensioned clockwork spring 67 to return the setting drum back to the starting position, the pin 70 thus being returned against the tooth 64 and the release pin 77 to its starting position.
  • the first impact in the exemplary embodiment only represents a fraction of the total turning movement of the adding shaft up to activation of the cut-off, and an excessively long first displacement of the inertial or flywheel body, therefore, will be unable to have any adverse effects on the resulting final torque.
  • An impact wrench with torque control means comprising a housing, a drive motor in said housing, cut-off means for said motor in said housing, a drive shaft in said motor, an anvil rotatably journalled in said housing and adapted to be connected to a workpiece, a rotary impact motor in said housing operatively interconnected between said drive shaft and said anvil for applying a succession of rotational impacts against said I anvil and thereby to said workpiece, a body in said housing operativelyassociated with said drive shaft for being displaced at each impact relative to said drive shaft in response to rotational resistance of said anvil, means for producing a return force .active against said body to cancel the displacements thereof, an adding mechanism in said housing for adding the lengths of displacement of said body, and means in said housing associated with said adding mechanism for activating said cut-off means at attainment in said adding mechanism of a predetermined sum total of said lengths of displacement.
  • An impact wrench accordingto claim 4 in which a clutch is provided for connecting said drum portion to said adding shaft, and means for disengaging said said startin means.
  • An im pact wrench in which said motor is actuated pneumatically, a passage in said housing for supplying compressed air to said motor, said cut-off means being a normally open cut-off valve in said passage, means for biasing said valve to the cutoff portion thereof, a locking arm pivotally mounted in said housing and cooperating with said cut-off valve to releasably arrest said cut-off valve in the open position thereof, and said member on said drum portion cooperating with said locking arm for releasing movement of said cut-off valve to the cut-off position thereof.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
US133647A 1970-04-24 1971-04-13 Impact wrench with torque control means Expired - Lifetime US3703933A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE05745/70A SE350426B (it) 1970-04-24 1970-04-24

Publications (1)

Publication Number Publication Date
US3703933A true US3703933A (en) 1972-11-28

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US133647A Expired - Lifetime US3703933A (en) 1970-04-24 1971-04-13 Impact wrench with torque control means

Country Status (10)

Country Link
US (1) US3703933A (it)
BE (1) BE766175A (it)
CA (1) CA926161A (it)
CH (1) CH526371A (it)
DE (1) DE2119273C3 (it)
FR (1) FR2090618A5 (it)
GB (1) GB1312435A (it)
NL (1) NL173609C (it)
SE (1) SE350426B (it)
ZA (1) ZA712338B (it)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3908766A (en) * 1973-05-23 1975-09-30 Bosch Gmbh Robert Impact wrench
US3974883A (en) * 1975-05-19 1976-08-17 Standard Pressed Steel Co. Tightening system
US4416340A (en) * 1981-12-24 1983-11-22 Smith International, Inc. Rotary drilling head
US5836403A (en) * 1996-10-31 1998-11-17 Snap-On Technologies, Inc. Reversible high impact mechanism
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
US6105595A (en) * 1997-03-07 2000-08-22 Cooper Technologies Co. Method, system, and apparatus for automatically preventing or allowing flow of a fluid
US6155355A (en) * 1996-12-16 2000-12-05 Atlas Copco Tools Ab Torque impulse tool with automatic power shut-off comprising two inertia bodies
WO2003095151A1 (en) * 2002-05-09 2003-11-20 Snap-On Incorporated Air auto shut-off mechanism for a pneumatic torque-applying tool
US20040007370A1 (en) * 2002-07-09 2004-01-15 Giardino David A. Retrofit kit for a modular control apparatus for a power impact tool
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US20040149469A1 (en) * 2003-01-31 2004-08-05 Ingersoll-Rand Company Rotary tool
US20070221022A1 (en) * 2006-03-07 2007-09-27 Makita Corporation Power tool
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
US20160184983A1 (en) * 2013-08-08 2016-06-30 Atlas Copco Industrial Technique Ab Power tool with flywheel and gear for accelerating said flywheel
US20160354905A1 (en) * 2015-06-05 2016-12-08 Ingersoll-Rand Company Power tools with user-selectable operational modes
US9737978B2 (en) 2014-02-14 2017-08-22 Ingersoll-Rand Company Impact tools with torque-limited swinging weight impact mechanisms
US10099351B2 (en) 2013-08-08 2018-10-16 Atlas Copco Industrial Technique Ab Torque delivering power tool with flywheel
US10145199B2 (en) * 2010-11-20 2018-12-04 Halliburton Energy Services, Inc. Remote operation of a rotating control device bearing clamp and safety latch
US11260517B2 (en) 2015-06-05 2022-03-01 Ingersoll-Rand Industrial U.S., Inc. Power tool housings
US11602832B2 (en) 2015-06-05 2023-03-14 Ingersoll-Rand Industrial U.S., Inc. Impact tools with ring gear alignment features
US11784538B2 (en) 2015-06-05 2023-10-10 Ingersoll-Rand Industrial U.S., Inc. Power tool user interfaces

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE794782A (fr) * 1972-02-04 1973-05-16 Atlas Copco Ab Cle a percussion a arret automatique
DE2441457C2 (de) * 1974-08-29 1983-05-26 Robert Bosch Gmbh, 7000 Stuttgart Druckluftschlagschrauber
DE2516951C3 (de) * 1975-04-17 1981-09-03 Robert Bosch Gmbh, 7000 Stuttgart Steuereinrichtung zum Abschalten des Antriebsmotors eines elektrisch betriebenen Schraubers
SU810472A1 (ru) * 1976-08-23 1981-03-07 Всесоюзный Научно-Исследовательскийи Проектно-Конструкторский Институтмеханизированного И Ручногостроительно-Монтажного Инструмента,Вибраторов И Строительно-Отделочныхмашин Ударный гайковерт
CN101695830B (zh) * 2009-09-27 2011-04-20 华中科技大学 一种水压冲击扳手
CN112077796B (zh) * 2019-06-14 2024-10-01 苏州东成工具科技有限公司 冲击电动工具

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3318390A (en) * 1964-10-28 1967-05-09 Reed Roller Bit Co Mechanism for controlling tension in fasteners
CH460669A (de) * 1967-03-30 1968-07-31 Reed International Inc Motorbetriebenes Werkzeug
US3643749A (en) * 1970-07-14 1972-02-22 Ingersoll Rand Co Signal inhibitor for impact wrench

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3318390A (en) * 1964-10-28 1967-05-09 Reed Roller Bit Co Mechanism for controlling tension in fasteners
CH460669A (de) * 1967-03-30 1968-07-31 Reed International Inc Motorbetriebenes Werkzeug
US3643749A (en) * 1970-07-14 1972-02-22 Ingersoll Rand Co Signal inhibitor for impact wrench

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3908766A (en) * 1973-05-23 1975-09-30 Bosch Gmbh Robert Impact wrench
US3974883A (en) * 1975-05-19 1976-08-17 Standard Pressed Steel Co. Tightening system
US4416340A (en) * 1981-12-24 1983-11-22 Smith International, Inc. Rotary drilling head
US5836403A (en) * 1996-10-31 1998-11-17 Snap-On Technologies, Inc. Reversible high impact mechanism
US6155355A (en) * 1996-12-16 2000-12-05 Atlas Copco Tools Ab Torque impulse tool with automatic power shut-off comprising two inertia bodies
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
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
WO2003095151A1 (en) * 2002-05-09 2003-11-20 Snap-On Incorporated Air auto shut-off mechanism for a pneumatic torque-applying tool
US20030226674A1 (en) * 2002-05-09 2003-12-11 Putney Gordon A. Air auto shut-off
US6883617B2 (en) 2002-05-09 2005-04-26 Snap-On Incorporated Air auto shut-off
US20040007370A1 (en) * 2002-07-09 2004-01-15 Giardino David A. Retrofit kit for a modular control apparatus for a power impact tool
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
US20070221022A1 (en) * 2006-03-07 2007-09-27 Makita Corporation Power tool
US7712546B2 (en) * 2006-03-07 2010-05-11 Makita Corporation Power tool having torque limiter
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US10145199B2 (en) * 2010-11-20 2018-12-04 Halliburton Energy Services, Inc. Remote operation of a rotating control device bearing clamp and safety latch
US9272400B2 (en) 2012-12-12 2016-03-01 Ingersoll-Rand Company Torque-limited impact tool
US10099351B2 (en) 2013-08-08 2018-10-16 Atlas Copco Industrial Technique Ab Torque delivering power tool with flywheel
US20160184983A1 (en) * 2013-08-08 2016-06-30 Atlas Copco Industrial Technique Ab Power tool with flywheel and gear for accelerating said flywheel
US9737978B2 (en) 2014-02-14 2017-08-22 Ingersoll-Rand Company Impact tools with torque-limited swinging weight impact mechanisms
US20160354905A1 (en) * 2015-06-05 2016-12-08 Ingersoll-Rand Company Power tools with user-selectable operational modes
US11260517B2 (en) 2015-06-05 2022-03-01 Ingersoll-Rand Industrial U.S., Inc. Power tool housings
US11491616B2 (en) * 2015-06-05 2022-11-08 Ingersoll-Rand Industrial U.S., Inc. Power tools with user-selectable operational modes
US11602832B2 (en) 2015-06-05 2023-03-14 Ingersoll-Rand Industrial U.S., Inc. Impact tools with ring gear alignment features
US11707831B2 (en) 2015-06-05 2023-07-25 Ingersoll-Rand Industrial U.S., Inc. Power tool housings
US11784538B2 (en) 2015-06-05 2023-10-10 Ingersoll-Rand Industrial U.S., Inc. Power tool user interfaces

Also Published As

Publication number Publication date
SE350426B (it) 1972-10-30
BE766175A (fr) 1971-09-16
NL173609B (nl) 1983-09-16
NL7105554A (it) 1971-10-26
CA926161A (en) 1973-05-15
NL173609C (nl) 1984-02-16
DE2119273C3 (de) 1974-10-17
FR2090618A5 (it) 1972-01-14
DE2119273A1 (de) 1971-11-11
CH526371A (de) 1972-08-15
GB1312435A (en) 1973-04-04
ZA712338B (en) 1972-01-26

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