US3648784A - Rotary impact motor - Google Patents

Rotary impact motor Download PDF

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Publication number
US3648784A
US3648784A US73552A US3648784DA US3648784A US 3648784 A US3648784 A US 3648784A US 73552 A US73552 A US 73552A US 3648784D A US3648784D A US 3648784DA US 3648784 A US3648784 A US 3648784A
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US
United States
Prior art keywords
impact
anvil
cam
dog
hammer body
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
US73552A
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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
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Atlas Copco AB
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Publication date
Application filed by Atlas Copco AB filed Critical Atlas Copco AB
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Publication of US3648784A publication Critical patent/US3648784A/en
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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
    • B25B21/02—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
    • B25B21/026—Impact clutches

Definitions

  • ABSTRACT U In a bidirectionally operable impact motor for power driven U1] Appl' 73552 fastener setting tools an impact'dog is joumaled in a hammer body pivotally about an axis spaced from but parallel with the [30] Foreign Application Priority Data axis of rotation of the hammer body for taking impact and release positions with respect to opposed impact surfaces on a Sept. 26, 1969 Sweden ..l3304/69 rotamble anvil coaxial with the hammer body, one impact Sup face for each direction of rotation of the impact motor.
  • a driv Efnil ..173/9%g,58ill//2d3 ing member rotates the hammer body via the impact dog and ⁇ '58 ⁇ a 81/52 3, during rotation constantly biases the latter to the release position.
  • a cam body is pivotally supported coaxially on the anvil between two end positions.
  • This invention relates to a bidirectionally rotatable rotary impact motor with impacting action in either rotational direction thereof. More specifically the invention relates to rotary impact motors of the type with a hammer body coaxially rotatably supported with respect to the anvil, and an impact dog provided on the hammer body and pivotally arranged on the hammer body about an axis parallel with the rotational axis of the anvil for taking respectively impact and release positions with respect to the impact surfaces of the anvil under the action of cooperating cam means on the anvil, the impact dog, and on a driving member for rotating the hammer body via the impact dog.
  • the driving member usually constantly strives to pivot the impact dog back in the release direction so that the end of the impact dog trailing in the rotational direction during the relation rotation between the impact dog and anvil is forced to follow the periphery of the anvil.
  • Movement of the impact dog to an impact position is controlled by cam action and for purposes of promoting such action the impact surfaces of the anvil are placed peripherally as near as possible to one another, i.e., on a mutual distance cor-' responding to the width of the impact dog and the cam means of the anvil are correspondingly divided into two peripherally spaced opposed cam crests, one cam crest for each impact surface and direction of rotation.
  • the impact dog When the impact dog has to pass over the second cam crest after the pivotal movement to an impact position over the first one, the impact dog must be pivoted a second time. In order to attain a sufficiently large angle of acceleration prior to impact, it is desired to strike only once for each revolution, and therefore this second pivotal movement is allowed to take place without impacting.
  • This parasitic oscillation uses up energy and demands special radial depressions to be formed in the anvil in order to provide clearance for the pivotal oscillation of the impact dog, such measures increasing the cost of the anvil and weakening it.
  • a further object of the invention is to provide a simple and stable journaling of the hammer body and the other details of the rotary impact motor and to rely only on a minimum of details involved.
  • a bidirectionally rotatable rotary impact motor with impacting action in either rotational direction thereof comprising a housing, an anvil rotatably journaled in said housing, a pair of peripherally opposed impact surfaces on said anvil each corresponding to one of said rotational directions, a hammer body rotatably carried in said housing coaxially with respect to the axis of rotation of said anvil, an impact dog supported on said hammer body for pivotal movement about an axis spaced from but parallel with said axis of rotation for taking respectively impact or release positions relative to said impact surfaces, cam means on said impact dog, a rotatable driving member in said housing in camming engagement with said impact dog for rotating said hammer body in either direction and pivoting said impact dog to said release position, and a cam body cooperating with said cam means and supported movably in a peripheral direction on said anvil between two end positions thereon for pivoting in each of them said impact dog to an
  • FIG. II is a longitudinal section through a rotary impact motor according to the invention with the details included therein shown in impact position.
  • FIG. 2 is a section on the line 2-2 in FIG. I restricted to the details in the hammer body of the impact motor.
  • FIG. 3 is a corresponding section on the line 3--3 in FIG. I.
  • FIG. 4 is a perspective view of an impact dog in FIG. I together with the cam means of the anvil cooperating therewith.
  • FIG. 5 is a section corresponding to FIG. 2 but of the impact motor in release position immediately after impacting.
  • FIG. 6 is a section corresponding to FIG. 3 but with the appurtenant details in release position.
  • FIG. 7 and FIG. 8 are sequential] sections showing the details in FIG. 5 during acceleration up to a position immediately prior to the impact position illustrated in FIG. 2.
  • FIG. 9 shows the details in FIG. 2 in impact position upon reversal of the rotating and impacting direction of the impact motor.
  • FIG. 10 shows a fragmentary rear end view of an anvil with a modified impact dog and modified cam means therefor.
  • FIG. lll finally shows a perspective view corresponding to FIG. 4 but ofthe cam means and of the impact dog in FIG. 10.
  • the impact clutch is shown as fitted in a hand sustained impact wrench 15 which includes a housing I6 and for example a reversible pneumatic motor, not shown in the figures, the motor causing rotationin the desired rotational direction of a drive shaft 17 journaled in the housing.
  • the impact motor or impact clutch mechanism proper is interposed between the housing 16 and a front piece 18 which within a journal bore 19 rotatably supports a forwardly projecting anvil 20.
  • the forward end of the anvil 20 carries a driving end 21 intended for removably carrying a tool thereon, not shown, usually a socket wrench.
  • the drive shaft 17 is forwardly provided with splines and spline grooves 22 and receives in an inner bore rotatably a centering pivot 23 which is fixed centrally in the rear end portion 24 at the rear end face of the anvil 20.
  • the end portion 24 is circularly cylindrical and provided with an axial partly cylindrical recess 25, the radially outwardly projecting outer portions of which form a pair of opposed impact surfaces 26, 27, FIG. 7.
  • a hammer body 28 is coaxially rotatably journaled on the end portion 24 of the anvil.
  • a partly cylindrical journaling recess 30 which slidably receives an impact dog 32 the latter being arched arcuately in cross section.
  • the impact dog 32 has a convex, partly cylindrical back portion 33 which in its entire length is slidably supported by the cylindrical surface of the journaling recess 30 for pivotal movement about an axis parallel with the rotational axis of the hammer body 28 and of the anvil 20.
  • the impact dog 32 has a recess 34 directed towards the end portion 24 which in a position of symmetry of the impact dog 32 within the hammer body 28, FIGS.
  • the impact dog 32 carries at the rear end thereof a single lobed cam body 35 being formed symmetrical with respect to the central longitudinal plane thereof and in one piece therewith and having a radially inwardly directed crest. Rearwardly the journal bore 29 of the hammer body 23 is transformed into an enlarged cylindrical journal portion 36.
  • a driving element 38 On the splines and spline grooves 22 of the drive shaft 17 fits a driving element 38 by cooperating splines and spline grooves 37, the driving element slidably cooperating by a front cam flange 39 with the cylindrical journaling portion 36 of the hammer body 28.
  • the cam flange 39 is provided with cut-out cam member consisting of opposite radially disposed cam surfaces 40,41 at opposite sides of the cam body 35 of the impact dog 32 and directed for cooperation with the radially outwardly disposed base portion thereof.
  • an intermediate washer 43 rotatably fitted onto the centering pivot 23.
  • a single lobed anvil cam body 44 on the anvil 20 is pivotally journaled on said same centering pivot 23 surrounded by the cam flange 39 radially spaced therefrom and the cam body 44 is countered by said washer and inserted between the face of end portion 24 and the intermediate washer 43.
  • the rear end or end portion 24 of the anvil 20 at the face thereof is provided with an axial preferably cylindrical recess 45 into which recess is inserted the base portion of the cam body 44 which has a lug 46 thereon.
  • the base portion and the lug 46 are carried pivotally in the recess 45 between two end positions symmetrical to one another, respectively FIG. 2 and FIG. 9, in which end position the cam body 44 is arrested by an abutment in the form of a pin 47 cooperating with the lug 46.
  • the pin 47 is press-fitted into a bore at the periphery of the recess 45 to such a depth that it can be freely passed by a cam crest 48 on the cam lobe of cam body 44 during pivotal movement of the cam body 44.
  • the cam crest 48 lies axially outside of the recess 45 and projects radially into the path of movement of the impact dog cam body 35 for cooperation with the crest of the latter.
  • the anvil cam body 44 is circumscribed by the path of movement of the cam means on the driving element 38, that is to say of the cam surfaces 40,41 and is likewise circumscribed by the path of movement of the impact dog cam body 35.
  • the rotation of the driving element 38 is transmitted at the cam surface 40 to the cam body 35 of the impact dog 32 and thus the hammer body 28 is rotated while the impact dog rotates the anvil 20, the socket wrench, and the screw by engagement with the impact surface 26. Rotation goes on continuously until the screw has been screwed down and the resistance to rotation is increased.
  • the cam body 35 of the impact dog 32 hits the crest 48 of the anvil cam body 44 which causes an instant turning of the impact dog 32 to the impact position for meeting the impact surface 26 of the anvil 20, FIG. 2.
  • theanvil cam body 44 is kept immovable relative to theend portion 24 by the abutment pin 47.
  • the impact dog 32 by its back portion 32 delivers an impact under full velocity against the impact surface 26 and transmits the kinetic energy of the hammer body 28 and of the impact dog 32 to the end portion 24 of the anvil 20 in the form of a rotational impact.
  • the impact dog 32 recoils back and at such instant can hit the crest 48 of the anvil cam body 44 by a blow directed in the opposite counterclockwise direction.
  • the rear end of the anvil presents a substantially triangular recess 49 rounded at the comers and with a flat side surface 50 which is perpendicular to the plane through the axes of rotation of the anvil 20 and the impact dog 32 at the instant of impact.
  • the anvil cam body 44 has an angularly shaped lug 51 with flanks 52, 53.
  • the lug 51 is countered arrestingly by the side surface 50 and applies itself thereagainst either by one flank 52 thereof or by the other flank 53 and thereby defines the end position of the cam body 44 respectively during rotation in a clockwise, FIG.
  • the cooperating impact dog 32 is reinforced at the cam body 35 by a fully cylindrical reinforcing portion 54 between the cam body 35 and the recess 34 of the impact dog 32.
  • a bidirectionally rotatable rotary impact motor with impacting action in either rotational direction thereof comprising a housing, an anvil rotatably journaled in said housing, a pair of peripherally opposed impact surfaces on said anvil each corresponding to one of said rotational directions, a hammer body rotatably carried in said housing coaxially with respect to the axis of rotation of said anvil, an impact dog supported on said hammer body for pivotal movement about an axis spaced from but parallel with said axis of rotation for taking respectively impact or release positions relative to said impact surfaces, cam means on said impact dog, a rotatable driv ing member in said housing in camming engagement with said impact dog for rotating said hammer body in either direction and pivoting said impact dog to said release position, and a cam body cooperating with said cam means and supported movably in a peripheral direction on said anvil between two end positions thereon for pivoting in each of them said impact dog to impact an position against the one of said impact surfaces corresponding to the chosen rotational direction of
  • a rotary impact motor according to claim 1 in which said cam body and cam means both are cooperating single lobed cams, said driving member having opposed cam surfaces engageable with opposite sides of said impact dog cam.
  • a rotary impact motor according to claim 1 in which said cam body of said anvil is supported at the rear end of said anvil pivotally about a pivot thereon and coaxial therewith.
  • a rotary impact motor in which there is provided an axial recess around said pivot in said anvil, a base portion on said cam body extending into said axial recess, a lug on said base portion, and abutment means on said anvil in said recess and cooperating with said lug for defining said end positions of said cam body.
  • a rotary impact motor in which said impact dog cam is symmetrical with respect to a central plane of symmetry for the impact dog, the end positions of said anvil cam being symmetrical with respect to a central plane of symmetry for said impact surfaces on said anvil.
  • a rotary impact motor according to claim 5 in which said impact surfaces of said anvil are provided by an axial recess in a circularly cylindrical rear end portion of said anvil about which the impact dog has its path of movement, said hammer body by means of a central axial joumaling bore therein being rotatably supported on said end portion.
  • a bidirectionally rotatable rotary impact motor with impacting action in either rotational direction thereof comprising a housing, an anvil rotatably journaled in said housing, a pair of peripherally opposed impact surfaces on said anvil each corresponding to one of said rotational directions, a hammer body rotatably carried in said housing coaxially with respect to the axis of rotation of said anvil, an impact dog supported on said hammer body for pivotal movement about an axis spaced from but parallel with said axis of rotation for taking respectively impact or release positions relative to said impact surfaces, a single lobed cam on said impact dog, a rotatable driving member in said housing, opposed cam surfaces on said driving member engageable with opposite sides of said impact dog cam for rotating said hammer body in either direction and pivoting said impact dog to said release position, a cam body cooperating with said impact dog cam and supported movably in a peripheral direction on said anvil between two end positions thereon for pivoting in each of them said impact dog to an impact position against the one of said impact surfaces
  • a rotary impact motor according to claim 7 in which said cam surfaces are provided on a ring shaped cam flange on said driving member, said cam flange surrounding said anvil cam body and rotatably fitting in a cylindrical joumaling portion in and rearwardly of said hammer body.
  • a rotary impact motor in which said impact surfaces of said anvil are provided by an axial recess in a circularly cylindrical rear end portion of said anvil about which the impact dog has its path of movement, said hammer body by means ofa central axial joumaling bore therein being rotatably supported on said end portion, and said anvil cam body being supported at the rear face of said end portion about a pivot coaxial with said anvil.
  • a bidirectionally rotatable rotary impact motor with impacting action in either rotational direction thereof comprising a housing, an anvil rotatably journaled in said housing, a pair of peripherally opposed semi cylindrical impact surfaces on said anvil each corresponding to one of said rotational directions, a hammer body rotatably carried in said housing coaxially with respect to and around said anvil, a semi cylindrical impact dog supported on said hammer body for pivotal movement about an axis spaced from but parallel with said axis of rotation for taking respectively impact or release positions relative to said impact surfaces, a cam on said impact dog, a rotatable driving member in said housing rearwardly of said hammer body, opposed cam surfaces on said driving member engageable with opposite sides of said impact dog cam for rotating said hammer body in either direction and biasing the trailing end of said impact dog towards said anvil and said release position of said impact dog, and a cam body cooperating with said impact do cam and supported movably in a peripheral direction on sat anvil between two end positions

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
US73552A 1969-09-26 1970-09-18 Rotary impact motor Expired - Lifetime US3648784A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE13304/69A SE333906B (fr) 1969-09-26 1969-09-26

Publications (1)

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US3648784A true US3648784A (en) 1972-03-14

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Application Number Title Priority Date Filing Date
US73552A Expired - Lifetime US3648784A (en) 1969-09-26 1970-09-18 Rotary impact motor

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Country Link
US (1) US3648784A (fr)
JP (1) JPS4922759B1 (fr)
BE (1) BE756623A (fr)
CH (1) CH515100A (fr)
DE (1) DE2046783A1 (fr)
FR (1) FR2062535A5 (fr)
GB (1) GB1279052A (fr)
NL (1) NL168156C (fr)
SE (1) SE333906B (fr)
ZA (1) ZA706452B (fr)

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3789934A (en) * 1971-04-07 1974-02-05 Atlas Copco Ab Rotary impact motor
US4002212A (en) * 1974-10-02 1977-01-11 Atlas Copco Aktiebolag Rotary impact mechanism
US4243109A (en) * 1979-06-07 1981-01-06 Marquette Metal Products Company Bi-directional rotary impact tool for applying a torque force
US20100071923A1 (en) * 2008-09-25 2010-03-25 Rudolph Scott M Hybrid impact tool
US20100071924A1 (en) * 2006-10-13 2010-03-25 Knut Christian Schoeps Impact wrench with a lubricated impact mechanism
US7806198B2 (en) 2007-06-15 2010-10-05 Black & Decker Inc. Hybrid impact tool
US20100276168A1 (en) * 2009-04-30 2010-11-04 Sankarshan Murthy Power tool with impact mechanism
US20110152029A1 (en) * 2009-12-23 2011-06-23 Scott Rudolph Hybrid impact tool with two-speed transmission
US20110232930A1 (en) * 2010-03-23 2011-09-29 Qiang Zhang Spindle bearing arrangement for a power tool
US8251158B2 (en) 2008-11-08 2012-08-28 Black & Decker Inc. Multi-speed power tool transmission with alternative ring gear configuration
US20150196997A1 (en) * 2014-01-16 2015-07-16 Ingersoll-Rand Company Controlled Pivot Impact Tools
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US20190375078A1 (en) * 2018-06-12 2019-12-12 Tranmax Machinery Co., Ltd. Impact block, carrier member and impact tool using sames
US20190375085A1 (en) * 2018-06-12 2019-12-12 Tranmax Machinery Co., Ltd. Impact block, carrier member and impart tool using sames
GB2577109A (en) * 2018-09-14 2020-03-18 Design Prototype Mft And Supply Limited Impact wrench
US11318589B2 (en) 2018-02-19 2022-05-03 Milwaukee Electric Tool Corporation Impact tool
US11484997B2 (en) * 2018-12-21 2022-11-01 Milwaukee Electric Tool Corporation High torque impact tool
US11511400B2 (en) * 2018-12-10 2022-11-29 Milwaukee Electric Tool Corporation High torque impact tool
USD971706S1 (en) 2020-03-17 2022-12-06 Milwaukee Electric Tool Corporation Rotary impact wrench
US11701759B2 (en) * 2019-09-27 2023-07-18 Makita Corporation Electric power tool
US11806855B2 (en) 2019-09-27 2023-11-07 Makita Corporation Electric power tool, and method for controlling motor of electric power tool
US12048988B2 (en) 2020-12-08 2024-07-30 Snap-On Incorporated Impact mechanism for a rotary impact tool
US12157208B2 (en) 2020-02-24 2024-12-03 Milwaukee Electric Tool Corporation Impact tool

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2940566A (en) * 1958-02-17 1960-06-14 Master Pneumatic Tool Company Impact clutch
US3179219A (en) * 1962-04-02 1965-04-20 Atlas Copco Ab Impact clutches
US3321043A (en) * 1964-03-24 1967-05-23 Ingersoll Rand Co Oil bath lubrication for mechanism
US3557884A (en) * 1969-06-24 1971-01-26 Ingersoll Rand Co Impact wrench mechanism

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2940566A (en) * 1958-02-17 1960-06-14 Master Pneumatic Tool Company Impact clutch
US3179219A (en) * 1962-04-02 1965-04-20 Atlas Copco Ab Impact clutches
US3321043A (en) * 1964-03-24 1967-05-23 Ingersoll Rand Co Oil bath lubrication for mechanism
US3557884A (en) * 1969-06-24 1971-01-26 Ingersoll Rand Co Impact wrench mechanism

Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3789934A (en) * 1971-04-07 1974-02-05 Atlas Copco Ab Rotary impact motor
US4002212A (en) * 1974-10-02 1977-01-11 Atlas Copco Aktiebolag Rotary impact mechanism
US4243109A (en) * 1979-06-07 1981-01-06 Marquette Metal Products Company Bi-directional rotary impact tool for applying a torque force
US7938195B2 (en) 2006-10-13 2011-05-10 Atlas Copco Tools Ab Impact wrench with a lubricated impact mechanism
US20100071924A1 (en) * 2006-10-13 2010-03-25 Knut Christian Schoeps Impact wrench with a lubricated impact mechanism
US7806198B2 (en) 2007-06-15 2010-10-05 Black & Decker Inc. Hybrid impact tool
US8794348B2 (en) 2008-09-25 2014-08-05 Black & Decker Inc. Hybrid impact tool
US10513021B2 (en) 2008-09-25 2019-12-24 Black & Decker Inc. Hybrid impact tool
US20100071923A1 (en) * 2008-09-25 2010-03-25 Rudolph Scott M Hybrid impact tool
US9193053B2 (en) 2008-09-25 2015-11-24 Black & Decker Inc. Hybrid impact tool
US8251158B2 (en) 2008-11-08 2012-08-28 Black & Decker Inc. Multi-speed power tool transmission with alternative ring gear configuration
US8434564B2 (en) 2008-11-08 2013-05-07 Black & Decker Inc. Power tool
US8631880B2 (en) 2009-04-30 2014-01-21 Black & Decker Inc. Power tool with impact mechanism
US20100276168A1 (en) * 2009-04-30 2010-11-04 Sankarshan Murthy Power tool with impact mechanism
US8460153B2 (en) 2009-12-23 2013-06-11 Black & Decker Inc. Hybrid impact tool with two-speed transmission
USRE46827E1 (en) 2009-12-23 2018-05-08 Black & Decker Inc. Hybrid impact tool with two-speed transmission
US20110152029A1 (en) * 2009-12-23 2011-06-23 Scott Rudolph Hybrid impact tool with two-speed transmission
US8584770B2 (en) 2010-03-23 2013-11-19 Black & Decker Inc. Spindle bearing arrangement for a power tool
US20110232930A1 (en) * 2010-03-23 2011-09-29 Qiang Zhang Spindle bearing arrangement for a power tool
US9216504B2 (en) 2010-03-23 2015-12-22 Black & Decker Inc. Spindle bearing arrangement for a power tool
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US9539715B2 (en) * 2014-01-16 2017-01-10 Ingersoll-Rand Company Controlled pivot impact tools
US20150196997A1 (en) * 2014-01-16 2015-07-16 Ingersoll-Rand Company Controlled Pivot Impact Tools
US11318589B2 (en) 2018-02-19 2022-05-03 Milwaukee Electric Tool Corporation Impact tool
US20220250216A1 (en) * 2018-02-19 2022-08-11 Milwaukee Electric Tool Corporation Impact tool
US20240269808A1 (en) * 2018-02-19 2024-08-15 Milwaukee Electric Tool Corporation Impact tool
US11964368B2 (en) * 2018-02-19 2024-04-23 Milwaukee Electric Tool Corporation Impact tool
US20190375078A1 (en) * 2018-06-12 2019-12-12 Tranmax Machinery Co., Ltd. Impact block, carrier member and impact tool using sames
US20190375085A1 (en) * 2018-06-12 2019-12-12 Tranmax Machinery Co., Ltd. Impact block, carrier member and impart tool using sames
EP3581333A1 (fr) * 2018-06-12 2019-12-18 Tranmax Machinery Co., Ltd. Bloc d'impact, élément porteur et outil d'impact les utilisant
EP3581334A1 (fr) * 2018-06-12 2019-12-18 Tranmax Machinery Co., Ltd. Bloc d'impact, élément porteur et outil d'impact les utilisant
GB2577109A (en) * 2018-09-14 2020-03-18 Design Prototype Mft And Supply Limited Impact wrench
US11511400B2 (en) * 2018-12-10 2022-11-29 Milwaukee Electric Tool Corporation High torque impact tool
US11597061B2 (en) * 2018-12-10 2023-03-07 Milwaukee Electric Tool Corporation High torque impact tool
US11938594B2 (en) * 2018-12-21 2024-03-26 Milwaukee Electric Tool Corporation High torque impact tool
US20230080957A1 (en) * 2018-12-21 2023-03-16 Milwaukee Electric Tool Corporation High torque impact tool
US20240227131A1 (en) * 2018-12-21 2024-07-11 Milwaukee Electric Tool Corporation High torque impact tool
US11484997B2 (en) * 2018-12-21 2022-11-01 Milwaukee Electric Tool Corporation High torque impact tool
US11701759B2 (en) * 2019-09-27 2023-07-18 Makita Corporation Electric power tool
US11806855B2 (en) 2019-09-27 2023-11-07 Makita Corporation Electric power tool, and method for controlling motor of electric power tool
US12157208B2 (en) 2020-02-24 2024-12-03 Milwaukee Electric Tool Corporation Impact tool
USD971706S1 (en) 2020-03-17 2022-12-06 Milwaukee Electric Tool Corporation Rotary impact wrench
US12048988B2 (en) 2020-12-08 2024-07-30 Snap-On Incorporated Impact mechanism for a rotary impact tool

Also Published As

Publication number Publication date
GB1279052A (en) 1972-06-21
BE756623A (fr) 1971-03-01
DE2046783A1 (de) 1971-04-08
SE333906B (fr) 1971-03-29
CH515100A (de) 1971-11-15
JPS4922759B1 (fr) 1974-06-11
ZA706452B (en) 1971-05-27
NL168156C (nl) 1982-03-16
NL7013984A (fr) 1971-03-30
FR2062535A5 (fr) 1971-06-25

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