US3610344A - Impact clutch - Google Patents

Impact clutch Download PDF

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Publication number
US3610344A
US3610344A US859155A US3610344DA US3610344A US 3610344 A US3610344 A US 3610344A US 859155 A US859155 A US 859155A US 3610344D A US3610344D A US 3610344DA US 3610344 A US3610344 A US 3610344A
Authority
US
United States
Prior art keywords
clutch
impact
anvil member
cam
hammer
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
US859155A
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English (en)
Inventor
Knut Christian Schoeps
Karl Gosta Karden
Sven Wilhelm Lundin
Klas Johan Astrom
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 US3610344A publication Critical patent/US3610344A/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
    • B25B21/02—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

  • This invention relates to impact clutches provided with a rotary anvil member, a hammer body carried coaxially rotatably with respect to the anvil member and a clutch dog movable relative to the anvil member and to the hammer body for taking respectively an impact position and an uncoupled position under the action of respectively cam means engaging the clutch dog and a power bias for constant actuation of the clutch dog.
  • the primary object of the invention is to provide a novel impact clutch design combining a small number of constituent details with a greatly improved axial compactness of the clutch.
  • a further object of the invention is to provide a dependable clutch design with good impact action and long operable life for the details thereof.
  • an impact clutch comprising a rotatable anvil member, a rotatable hammer mass coaxially supported with respect to said anvil member, rotatable driving means for said hammer mass, a clutch dog mounted on said hammer mass for conjoined rotation therewith and axially movably relative thereto, cooperating impact surfaces on said clutch dog and forwardly on said hammer body, a cavity in said hammer body, biasing means between said anvil member and said clutch dog for retracting the impact surfaces of said dog to uncoupled freely rotatable position into said cavity, and cam means between said hammer body and said clutch dog responsive to relative rotation therebetween for throwing said impact surfaces of said clutch dog from said cavity to impact position against said cooperating impact surfaces of said hammer body.
  • FIG. I is a longitudinal section through an impact clutch according to the invention substantially on the line ll in FIG. 2 and taking impact position.
  • FIG. 2 is a section on the line 2-2 in FIG. 1
  • FIG. 3 is a section on the line 3--3 in FIG. ll
  • FIG. 4 is a perspective view of a clutch dog also included in FIG. 1.
  • FIGS. 5-7 show diagrammatic functional illustrations of the main parts of the impact clutch. More particularly, FIG. 5 shows a plane development of the hammer body, the clutch dog, and the cam means of the impact clutch before delivering an impact and with the clutch dog is uncoupled position. FIG. 6 shows the details in FIG. 5 at the instant of impact with the clutch dog in the impact position. FIG. 7 shows the details in FIG. 5 immediately after the impact.
  • FIG. 8 shows a longitudinal section through a second embodiment of the impact clutch.
  • FIG. 9 is a cross section on the line 9-9 in FIG. 8.
  • FIG. I0 shows a third embodiment of the impact clutch.
  • FIG. 11 finally is a cross section on the line 11-11 in FIG. 10.
  • the impact clutch is shown encased in a motor-driven impact tool 15, preferably in hand-sustained impact wrench.
  • the impact tool 15 incorporates a motor, not shown in the figures, for example a pneumatic one, which produces reversible rotation of the driving shaft 17.
  • the impact clutch proper is encased between the housing 16 and a frontpiece 18 which supports rotatably a forwardly projecting anvil member 19.
  • the forward end of the anvil member 19 carries a square end 20 intended for carrying a removable tool such as a socket wrench, not shown.
  • the forward end of the drive shaft 17 has splines 22 thereon which are in engagement with cooperating internal splines 23 at the rear end of a hammer body 24.
  • a forward diametrically opposed inwardly directed lug 25 and an inwardly directed radial impact cam 21 the hammer body 24 bears rotatably against the intermediate portion of the anvil member 19.
  • the hammer body 24' is fonned as a hollow body with a large diameter circularly cylindrical cavity 26 disposed rearwardly of the impact cam 21 and the lug 25 and has furthermore a cylindrical guiding aperture 27 of smaller diameter arranged therebehind.
  • the hammer body 24 Rearwardly of the guiding aperture 27 the hammer body 24 has internally thereof an axial forwardly directed ball groove 28 shaped as an arc of a circle and taking up a ball 29 therein.
  • the ball 29 is maintained with limited peripheral freedom of movement in the ball groove 29 behind the flange portion of a flange sleeve 30 which is fixed in the hammer body 24 coaxially in front of the splines 23.
  • the ball groove 28 and ball 29 provide axial cam means within the hammer body 24.
  • the rear end of the anvil member 19 is rotatably joumaled, said rear end being formed as a short pivot 32.
  • a clutch dog 33 On the anvil member 19 a clutch dog 33, FIG. 4, is guided for conjoined rotation but axially movably.
  • the clutch dog 33 comprises a partly cylindrical shank portion 34 which is axially slidably guided in a partly cylindrical recess 35 equiform with the shank portion 34 and provided in the intermediate portion of the anvil member 19.
  • the surface of the shank portion 34 turned away from the anvil member 19 has a radius of curvature equal to the radii of the intermediate portion of the anvil member 19 and of the guiding aperture 27 of the hammer body 24.
  • the shank portion 34 is shaped as a full cylinder providing an integral radial impact cam 37.
  • the clutch dog 33 turns into an annular guiding portion 39 which surrounds the anvil member 19 slidably at a cylindrical portion 38 thereof in front of and adjacent the pivot 32.
  • the guide portion 39 slides in the guiding aperture 27 of the hammer body 24 and carries an integral rearwardly directed and peripherally double-sided axial cam 40 in alignment with the shank portion 34 of the clutch dog 33.
  • the cam 40 provides axial cam means on the clutch dog 33 and is pushed axially into the path of movement of the ball 29 by biasing or spring means such as helical springs 42.
  • the helical springs 42 are inserted in rearwardly pointing axial blind bores 41 in the anvil member 19 and bear against the guiding portion 39 such as to subject the clutch dog 33 constantly to a rearwardly directed power bias.
  • the fully cylindrical impact cam 37 of the clutch dog 33 forms tangentially facing impact surfaces 43, 44 which depending upon the rotational direction of the hammer body cooperate with the respective impact surfaces 45 and 46 provided at the opposite tangentially facing ends of the impact cam 21 on the hammer body 24, FIG. 2.
  • the fully cylindrical impact cam 37 of the clutch dog 33 will be subjected to a substantially tangential compressive force allowing a favorable impact force distribution between the hammer body 24 and the anvil member 19 and ensuring together with the per se favorable design solution a long operable life for the constituent details of the impact clutch.
  • FIGS. 8, 9 there is present a sleeve-shaped clutch dog 48 with three integral peripheral radially directed impact cams 49 coacting with three inwardly directed radial impact cams 50 on the hammer body 24.
  • the clutch dog 48 is provided with internal splines 51 in engagement with cooperating splines 52 on the anvil member 19. Between a forward flange 53 on the anvil member 19 and the clutch dog 48 is inserted a biasing means provided by a helical spring 54 surrounding the anvil member 19, which spring serves to retract the impact cams 49 into the cavity 26 and to move the cam 40 of the clutch dog 48 into the path of movement of the ball 29 of the hammer body 24.
  • the cam 40 is aligned with the annular portion of the sleeve forming the clutch dog 48.
  • a pivot 55 By means of a pivot 55 the rear end of the anvil member 19 is centered rotatably in the forward end of the drive shaft 17.
  • the ball 29 is kept in the ball groove 28 by the aid of an intermediate washer 56 sitting on the pivot 55 between the drive shaft 17 and the anvil member 19.
  • FIGS. 10 and 11 there is likewise provided a sleeve-shaped clutch dog 48 with radial impact earns 49 and actuated by a helical spring 58 projecting into the interior of the anvil member 19.
  • the clutch dog 48 has rearwardly an internal flange 59 against which the helical spring 58 bears.
  • the internal flange 59 is guided on a spacing sleeve 60 extending around an elongated centering pivot 55 passing through the washer 56 and extending through the interior of the anvil member 19, wherein the helical spring 58 is supported, onto the drive shaft 17.
  • FIGS. 8, 9 and in FIGS. 10, 11, respectively, are identical in their function with the embodiment in FIGS. l 7 and a repeated description of the function is therefore deemed unnecessary.
  • An impact clutch comprising a rotatable anvil member, a rotatable hammer means coaxially supported with respect to said anvil member, rotatable driving means for the hammer means, a clutch dog mounted on the anvil member for conjoint rotation therewith and axially movable relatively thereto, an elongated partly cylindrical shank portion on the clutch dog, a partly cylindrical axial recess in the anvil member, said recess being equiform with said shank portion and slidably receiving the clutch dog therein, cooperating impact surfaces on the clutch dog and forwardly on the said hammer means, said impact surfaces of the clutch dog being provided by a fully cylindrical radial impact cam and integral with the shank portion, the hammer means having a cavity, biasing means between said anvil member and the clutch dog for retracting the impact surfaces of said dog to uncoupled freely rotatable position into said cavity, cam means between the hammer means and the clutch dog responsive to relative rotation therebetween for throwing said impact surfaces of the clutch dog from the cavity to
  • An impact clutch comprising a rotatable anvil member, a rotatable hammer means coaxially supported with respect to said anvil member, rotatable driving means for the hammer means, a clutch sleeve axially slidably splined on the anvil member for conjoint rotation therewith, at least one radially inwardly directed cam at the forward end of the hammer body and integral therewith, at least one radial cam peripherally on and integral with the clutch sleeve for cooperation with said inwardly directed cam, the hammer body having a cavity, biasing means between the anvil member and said clutch sleeve for retracting the cam of the sleeve to uncoupled freely rotatable position into said cavity, and cam means between said hammer body and the clutch sleeve responsive to relative rotation therebetween for throwing said cam of the clutch dog from the cavity to impact-receiving position relative to said cooperating cam of the hammer body.
  • An impact clutch comprising a rotatable anvil member, a rotatable hammer means coaxially supported with respect to said anvil member, rotatable driving means for the hammer means, a one-piece clutch sleeve slidably mounted on the hammer means for conjoint rotation therewith, angularly spaced radially outwardly directed clutch teeth on the clutch sleeve and integral therewith, angularly spaced radially inwardly directed clutch teeth forwardly on the hammer body and integral therewith for impacting cooperation with said radially outwardly directed teeth, the hammer body having a cavity, spring means between the anvil member and the clutch sleeve for retracting the teeth of the sleeve to uncoupled freely rotatable position into the cavity, an axial peripherally doublesided cam integral with the clutch sleeve, a ball cooperating with the sides of the double-sided cam, an axial circularly arcshaped ball groove in said hammer body for receiving the ball therein

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Gripping On Spindles (AREA)
US859155A 1968-09-24 1969-09-18 Impact clutch Expired - Lifetime US3610344A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE12892/68A SE320334B (sv) 1968-09-24 1968-09-24

Publications (1)

Publication Number Publication Date
US3610344A true US3610344A (en) 1971-10-05

Family

ID=20296477

Family Applications (1)

Application Number Title Priority Date Filing Date
US859155A Expired - Lifetime US3610344A (en) 1968-09-24 1969-09-18 Impact clutch

Country Status (7)

Country Link
US (1) US3610344A (sv)
CA (1) CA926325A (sv)
DE (1) DE1947215A1 (sv)
FR (1) FR2018753A1 (sv)
GB (1) GB1230539A (sv)
NL (1) NL6914405A (sv)
SE (1) SE320334B (sv)

Cited By (17)

* 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
US3804180A (en) * 1972-07-07 1974-04-16 M Gelfand Impact wrench
US3952814A (en) * 1975-03-14 1976-04-27 Mikhail Lvovich Gelfand Impact wrench
US4243108A (en) * 1977-11-21 1981-01-06 Galimov Anas G Pneumatic inpact wrench having rotatable and axially translatable components
US4867250A (en) * 1986-08-18 1989-09-19 Ritt Corporation Pneumatic impact imparting tool
US5836403A (en) * 1996-10-31 1998-11-17 Snap-On Technologies, Inc. Reversible high impact mechanism
US6047779A (en) * 1997-07-29 2000-04-11 Chicago Pneumatic Tool Company Twin lobe impact mechanism
US6135212A (en) * 1998-07-28 2000-10-24 Rodcraft Pneumatic Tools Gmbh & Co. Kg Hammering screwdriver with disengagable striking mechanism
US6158526A (en) * 1999-03-09 2000-12-12 Snap-On Tools Company Reversible impact mechanism with structure limiting hammer travel
US20060118316A1 (en) * 2004-12-02 2006-06-08 One World Technologies Limited Stepped shaft
US20060225903A1 (en) * 2005-04-07 2006-10-12 Sterling Robert E Rotary impact tool, shock attenuating coupling device for a rotary impact tool, and rotary impact attenuating device
US20070187125A1 (en) * 2006-01-27 2007-08-16 Sterling Robert E Shock attenuating device for a rotary impact tool
US20110048751A1 (en) * 2008-05-07 2011-03-03 Elger William A Drive assembly for a power tool
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US9308636B2 (en) 2012-02-03 2016-04-12 Milwaukee Electric Tool Corporation Rotary hammer with vibration dampening
US20160193726A1 (en) * 2014-12-04 2016-07-07 Black & Decker Inc. Drill
US10328558B2 (en) 2014-12-04 2019-06-25 Black & Decker Inc. Drill

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0621220D0 (en) * 2006-10-25 2006-12-06 Mason Stephen J Shuttle driver

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2850128A (en) * 1952-08-01 1958-09-02 Rotor Tool Company Rotary impact clutch
US2881884A (en) * 1955-01-12 1959-04-14 Chicago Pneumatic Tool Co Impact clutch
US3001429A (en) * 1959-04-16 1961-09-26 Master Power Corp Rotary impact wrench
US3001428A (en) * 1960-02-23 1961-09-26 Master Power Corp Rotary impact wrench
US3174597A (en) * 1961-12-19 1965-03-23 Chicago Pneumatic Tool Co Impact clutch
US3389756A (en) * 1965-08-09 1968-06-25 Kawamoto Mitsugi Impact wrench
US3414065A (en) * 1967-04-26 1968-12-03 Rockwell Mfg Co Rotary impact tool

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2850128A (en) * 1952-08-01 1958-09-02 Rotor Tool Company Rotary impact clutch
US2881884A (en) * 1955-01-12 1959-04-14 Chicago Pneumatic Tool Co Impact clutch
US3001429A (en) * 1959-04-16 1961-09-26 Master Power Corp Rotary impact wrench
US3001428A (en) * 1960-02-23 1961-09-26 Master Power Corp Rotary impact wrench
US3174597A (en) * 1961-12-19 1965-03-23 Chicago Pneumatic Tool Co Impact clutch
US3389756A (en) * 1965-08-09 1968-06-25 Kawamoto Mitsugi Impact wrench
US3414065A (en) * 1967-04-26 1968-12-03 Rockwell Mfg Co Rotary impact tool

Cited By (24)

* 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
US3804180A (en) * 1972-07-07 1974-04-16 M Gelfand Impact wrench
US3952814A (en) * 1975-03-14 1976-04-27 Mikhail Lvovich Gelfand Impact wrench
US4243108A (en) * 1977-11-21 1981-01-06 Galimov Anas G Pneumatic inpact wrench having rotatable and axially translatable components
US4867250A (en) * 1986-08-18 1989-09-19 Ritt Corporation Pneumatic impact imparting tool
US5836403A (en) * 1996-10-31 1998-11-17 Snap-On Technologies, Inc. Reversible high impact mechanism
US6047779A (en) * 1997-07-29 2000-04-11 Chicago Pneumatic Tool Company Twin lobe impact mechanism
US6135212A (en) * 1998-07-28 2000-10-24 Rodcraft Pneumatic Tools Gmbh & Co. Kg Hammering screwdriver with disengagable striking mechanism
US6158526A (en) * 1999-03-09 2000-12-12 Snap-On Tools Company Reversible impact mechanism with structure limiting hammer travel
US6227308B1 (en) 1999-03-09 2001-05-08 Snap-On Tools Company Reversible impact mechanism with structure limiting hammer travel
US7207393B2 (en) 2004-12-02 2007-04-24 Eastway Fair Company Ltd. Stepped drive shaft for a power tool
US20060118316A1 (en) * 2004-12-02 2006-06-08 One World Technologies Limited Stepped shaft
US20060225903A1 (en) * 2005-04-07 2006-10-12 Sterling Robert E Rotary impact tool, shock attenuating coupling device for a rotary impact tool, and rotary impact attenuating device
US20070158090A1 (en) * 2005-04-07 2007-07-12 Exhaust Technologies, Inc. Rotary impact tool, shock attenuating coupling device for a rotary impact tool, and rotary impact attenuating device
US20070187125A1 (en) * 2006-01-27 2007-08-16 Sterling Robert E Shock attenuating device for a rotary impact tool
US7438140B2 (en) 2006-01-27 2008-10-21 Exhaust Technologies, Inc. Shock attenuating device for a rotary impact tool
US8505648B2 (en) 2008-05-07 2013-08-13 Milwaukee Electric Tool Corporation Drive assembly for a power tool
US20110048751A1 (en) * 2008-05-07 2011-03-03 Elger William A Drive assembly for a power tool
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US9308636B2 (en) 2012-02-03 2016-04-12 Milwaukee Electric Tool Corporation Rotary hammer with vibration dampening
US10195730B2 (en) 2012-02-03 2019-02-05 Milwaukee Electric Tool Corporation Rotary hammer
US20160193726A1 (en) * 2014-12-04 2016-07-07 Black & Decker Inc. Drill
US10328559B2 (en) * 2014-12-04 2019-06-25 Black & Decker Inc. Drill
US10328558B2 (en) 2014-12-04 2019-06-25 Black & Decker Inc. Drill

Also Published As

Publication number Publication date
FR2018753A1 (sv) 1970-06-26
NL6914405A (sv) 1970-03-26
CA926325A (en) 1973-05-15
SE320334B (sv) 1970-02-02
DE1947215A1 (de) 1970-06-25
GB1230539A (sv) 1971-05-05

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