US3179219A - Impact clutches - Google Patents

Impact clutches Download PDF

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Publication number
US3179219A
US3179219A US184013A US18401362A US3179219A US 3179219 A US3179219 A US 3179219A US 184013 A US184013 A US 184013A US 18401362 A US18401362 A US 18401362A US 3179219 A US3179219 A US 3179219A
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United States
Prior art keywords
impact
dog
anvil member
hammer mass
rotatable
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
US184013A
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English (en)
Inventor
Karden Karl Gosta
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
Priority to US184013A priority Critical patent/US3179219A/en
Priority to GB10309/63A priority patent/GB973333A/en
Priority to DEA42726A priority patent/DE1287529B/de
Priority to DK139463AA priority patent/DK112929B/da
Priority to CH413463A priority patent/CH414494A/de
Application granted granted Critical
Publication of US3179219A publication Critical patent/US3179219A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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 improvements in power operated impact tools such as wrenches for tightening or loosening nuts or bolts by power, and more particularly to a reversible impact clutch utilised in such impact tools for clutching and declutching the hammer member and the anvil member and for producing rotary blows to the anvil member.
  • a more specific object of the invention is to provide an improved impact clutch for power operated tools in which for simplicity of operation the clutching movement of the impacting clutch member is controlled by a positive cam action while the declutching movement is performed by means of a spring.
  • a further more specific object of the invention is to provide an improved impact clutch of the foregoing character in which the spring for safeguarding declutching movement is. a torsion spring arranged in a simple manner for effective operation over a long operable life and operable for rotation in both clockwise and counterclockwise directions.
  • FIG. 1 shows a longitudinal sectional i .view of an impact tool incorporating an impact clutch mechanism embodying the invention.
  • FIG. 2 is a transverse sectional view taken on the line 2-2 in 1.
  • FIG. 3 is a transverse sectional view on the line 3--3 in FIG. 1 and showing the impact clutch at the moment of impact.
  • FIG. 4 is a rear. View and section substantially on the line 4 i in FIG. 1.
  • FIG. 5 is a perspective view of a torsion spring incorporated in the impact clutch mechanism of FIG. 1.
  • FIG. 6 is a transverse sectional view corresponding to FIG. 3 but showing the impact clutch mechanism in declutching position immediately after impact.
  • FIG. 7 is a transverse sectional view corresponding to FIG.
  • FIG. 6 is a transverse sectional view corresponding to FIG. 7 but showing the impact dog in an angular position past said one cam ridge.
  • FIG. 9 shows a transverse sectional view corresponding to FIG. 8 but showing the impact dog in the other of its drive positions ready for riding over the other cam ridge of the anvil member.
  • FIG. 10 shows a transverse sectional view taken on the line lt'i1ll in FIG. 1 during rotation of the impact clutch in one direction with the impact dog in a position corresponding to FIG. 7.
  • the power operated impact tool illustrated in FIG. 1 incorporates an impact clutch according to the present invention and comprises a rear housing 2% having a handle portion 21 and a front housing 22.
  • the front housing 22 encloses the impact clutch proper and is proinvention will beice vided with a central opening 23 at its forward end through which an anvil member 25 protrudes.
  • the anvil member 25 is supported by a ball bearing 24 carried inside of and by the front housing 22.
  • a ring seal 26 is provided around the opening 23 and tightens against the anvil member 25.
  • a reversible rotary motor preferably as shown a pneumatic motor including a rotor or driving member 29 carrying radial vanes or blades 3i slidably supported within suitable grooves formed in the rotor.
  • a pneumatic motor including a rotor or driving member 29 carrying radial vanes or blades 3i slidably supported within suitable grooves formed in the rotor.
  • the driving member is driven by compressed air admitted to the motor in a conventional manner, preferably through the handle portion 21 and under control of a trigger valve, not shown, and the usual reversing valve 28.
  • the constructional features of the motor per se form no part of the present invention and may be carried out in any suitable conventional manner.
  • the driving member 253 has an axial bore 31 therethrough and is supported in the rear housing 2t) at its opposite ends by ball bearings 32 and 33.
  • the forward end of the driving member 29 extends through the ball bearing 32 and is formed with parallel splines 34, FIG. 4, on its protruding mantle portion.
  • the front end of the anvil member 25 carries a polygonal end portion 35 for receiving and carrying various removable tools, such as a socket wrench, not shown, which fits on the end portion 35'.
  • the anvil member 25 forms a cam portion 35 of substantially cylindrical configuration but provided with a pair of axially extending spaced apart cam ridges 39 and 4d.
  • the cam ridges 39, dill are provided with radially disposed opposite impact receiving faces 41 and 42, respectively, of which one, 41, is turned to receive impacts in clockwise direction, when looking from the rear housing 20 forwardly, while the other, is turned to receive impacts in counterclockwise direction.
  • the faces 41, 42 are arcuate and formed by an axial partially cylindrical recess 43 formed in the cam portion 38 along an axis parallel to the axis of rotation of the anvil member 25. At its rearmost portion the anvil member 25 forms a slightly reduced cylindrical bearing portion 44.
  • a hammer mass 4-5 is arranged coaxially around the anvil member 25 and extends from the collar portion 36 thereof to the rear.
  • the hammer mass 45 is journalled by means of cylindrical bearing portions 46 and 47 on the collar 36 and the cylindrical bearing portion 44, respectively, for relative rotation with respect to the anvil member 25.
  • the hammer mass 45 preferably is of oval shape and is provided with a central bore 48 therein surrounding the cam portion 38 and allowing free rotation of the cam portion 3% and the cam ridges 39, 4d in the bore 43.
  • the rear portion of the hammer mass 45 is supported on the protruding end of the driving member 29.
  • the bore 51 is provided with longitudinally extending grooves 52 which receive the splines 34 of the driving member 29.
  • the grooves 52 are somewhat broader in circumferential direction than the corresponding splines 34, whereby a slight circumferential play or lost motion is created in the driving connection between the driving member 29 and the hammer mass 45 for a purpose to be explained further on.
  • An axial bore having a radius equal to the radius of the recess 43 of the anvil member 25 extends in parallel relation with the axis of the bore 48 and forms a partially cylindrical recess 53 in the hammer mass which recess 53 faces the cam portion 38 of the anvil member.
  • the recess 53 receives pivotally therein an impact transmitting dog 54 which is journalled in said recess by means of a partially cylindrical rear bearing portion 55 thereon.
  • the main portion of the impact dog 54 extending over the rear end of the anvil member 25 has a crescent shaped cross section and the dog 54- faces the cam portion 38 with the concave recess 56 defining the shorter arc of the crescent shaped cross section.
  • the concave recess 56 merges into the rear bearing portion 55 by a pair of spaced apart edges 57.
  • the concave recess 56 is provided in order to enable the impact dog 54 to rotate past and ride over the cam ridges 59, 45.
  • the rear portion 53 of the impact dog 54 is fully cylindrical and is journalled in a corresponding fully cylindrical rear part of the bore defining the recess 53. Adjacent and at opposite sides of the impact dog 54 the rear face of the hammer mass 45 forms abutments 59, FIG. 4-. On the rear portion 53 of the impact dog 54 there are provided corresponding angularly offset abutments 6t) cooperating with the abutments and defining the maximum swing of the impact dog 54 in both directions.
  • the rear portion 58 has a forwardly directed surface 61 which has formed thereon an axially and forwardly protruding pin 62 adjacent the periphery of the rear portion 53 and lying in the plane of symmetry of the concave recessed portion 56 of the impact dog 54.
  • the rear end of the hammer mass 45 rests against the inner ring of the ball bearing 32 while the impact dog 54 is kept in place axially between the outer ring of the ball bearing 32 and an end surface 63 provided in the hammer mass 45.
  • the rotor or driving member 29 carries at its splined end a pair of diametrically opposed projections 64, FIG. 10, each aligned with one of the splines 3
  • an elongated torsion spring 66 having a rectangular cross section and being bent in hair pin fashion.
  • the ends of the torsion spring 66 are bent at right angles and form shanks 67 and 68 extending in a transverse plane with respect to the axis of the spring 66 with the longer sides of the rectangular cross section of the shanks 67, 68 in parallel relation to said plane.
  • the arrangement of the spring 66 is such that when the spring 66 is inserted in the axial bore 31 the shanks 67, 63 will protrude radially between the rear face 50 of the anvil member 25 and the forward end of the driving member 25, the shanks 67, 68 extending alongside each other and embracing under a certain precompression or twisting of the torsion spring 66 opposed abutments on one of the projections 64 on the driving member 29 and diametrically opposed portions or abutments of the pin 62 on the impact dog 54, FIG. 10.
  • Such angularly offset position of the pin 62 is defined by the driving engagement between the splines 34 and the grooves 52 in the hammer mass and causes the impact dog to occupy the driving position 1 of FIG. 7 with the trailing edge 57 of the impact dog 54 inside of the cylindrical central bore 48 and the leading edge 57 outside of said bore 48.
  • the impact dog 54 and the anvil member 25 will remain in engagement so that the bolt is rotated constantly until it is run down and the resistance to rotation increases above some predetermined value.
  • the driving member 29 now quickly accelerates the hammer mass 45 by rotating it around the now stationary anvil member 25 until the mantle surface of the concave recess 56 and the trailing edge 57 of the impact dog forcefully run against the cam ridge of the cam portion 38, FIG. 9.
  • the pin 62 together with the impact dog 54 is now pivoted in a manner to bring the leading edge 57 of the impact dog 54 inside of the cylindrical central bore 48 while the trailing edge 57 is pivoted and accelerated radially away from the ridge 40, whereupon at the next moment the hammer mass delivers an impact against the recessed portion 43 of the cam ridge 59 by means of the rear bearing portion adjacent the leading edge 5'7 of the impact dog 54-, FIG. 3.
  • the hammer mass 45 having delivered by means of the dog 54 a rotational blow to the anvil member 25, continues now rotation of the bolt to be tightened until, again, the cammmg force exerted by the cam ridge 39 on the impact dog 54 overcomes the force of the torsion spring 66 exerted by its shanks 68, whereupon the impact dog again overrides the cam ridge 39 and repeats the impact cycle.
  • the position of the impact dog 54 in FIG. 9 may also be occupied during running down of the nut.
  • the first impact which with increased resistance to rotation follows'upon such drive position will obviously be a weak one because of the angular nearness of the impact position.
  • the powerful blow received by the portions of the impact dog adjacent the trailing edge 57 after full acceleration from the position of FIG. 6 or FIG. 7 to the position of FIG. 9 is prevented from rocking the impact dog 54 and its pin 62 too far against the action of the spring shank 63 by s-,i 79,21 e
  • the driving member 29 when driving in the reverse direction or the direction of the arrow moves by means of the projection 64 and the spring shanks 67, 63 the pin 62 to an angular position offset in the direction of rotation with respect to the central plane through the axis of rotation of the hammer mass 45 and the pivotal axis of the impact dog 54-.
  • the pin 62 has now to counteract the spring action of the shank 67 of the torsion spring 56 during the rocking movement of the impact dog 54 into clutching or impact position as well as during overriding of the cam ridge 46.
  • the displacement of the pin 62 in the direction of rotation is attained by the circumferential play or lost motion in the drive connection between the splines 34 and the broad grooves 52, the width of which is calculated to give a play resulting in a suitable angle of attack of. the trailing edge portions of the impact dog and movement of the leading edge to a position outside of the central bore &8.
  • the diametrically opposed double arrangement of the projections 64 is provided for creating alternative positions during assembly of the impact clutch mechanism parts.
  • the spring 66 may alternatively be mounted in the hole 69 of the anvil member 25.
  • a tube not shown, into which the spring 66 may be inserted.
  • A11 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, an impact dog pivotally mounted on said hammer mass for rotation therewith and movable relative thereto in clutching and declutching direction about an axis offset from but parallel with the axis of rotation of said anvil member, cam means between said anvil member and said dog for positively pivoting the dog in the clutching direction, and a torsion spring extending axially of said clutch, said torsion spring being rotatable with said hammer mass for engaging and pivoting said impact dog in the declutching direction.
  • An impact clutch comprising a rotatable anvil memher, a rotatable hammer mass coaxially supported with respect to said anvil member, a rotatable driving member, a drive connection incorporating some degree of play for providing a constantly engaged direct drive between said driving member and said hammer mass except for said play, an impactdog pivotally mounted on said hamaxis offset from but parallel with the axis of rotation of i said anvil member, cam means between said anvil member and said dog for positively pivoting said dog in the clutching direction, and spring means rotatable by and with said hammer mass for engaging and pivoting said impact dog in the declutching direction.
  • 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 coaxiaily supported with respect to said hammer mass, an impact dog pivotally mounted on said hammer mass for rotation therewith and movable relative thereto in clutching and declutching direction about an axis offset from but parallel with the axis of rotation of said anvil member, a first abutment on said impact dog intermediate the pivotal axis of said impact dog and the axis of rotation of said hammer mass, a second abutment on said driving means adjacent said first abutment, cam means between said anvil member and said dog for positively pivoting said dog in the clutching direction, and spring means extending between said first and said second abutments and in engagement therewith for pivoting said impact dog in the declutching direction.
  • a reversible impact clutch comprising a rotatable anvil member, a rotatable hammer mass coaxially supported with respect to said anvil member, a rotatable driving member coaxially supported with respect to said hammer mass, a drive connection incorporating some degree of play for providing a constantly engaged direct drive between said driving member and said hammer mass except for said play, an impact dog pivotally mounted on said hammer mass for rotation therewith and movable relative thereto in clutching and declutching direction about an axis offset from but parallel with the axis of rotation of said anvil member, an extension on said impact dog forming a first pair of opposed abutment surfaces intermediate the pivotal axis of said impact dog and the axis of rotation of said hammer mass, an extension on said driving member adjacent said extension on said impact dog forming a second pair of abutment surfaces, cam means between said anvil member and said dog for positively pivoting said dog in the clutching direction, and a torsion spring extending between said first pair
  • An impact clutch as set forth in claim 4 in which the ends of said torsion spring are provided with laterally protruding shanks extending in parallel relation to a transverse plane extending with respect to the axis of said spring and spaced from each other with said first and second pair of opposed abutment surfaces therebetween.
  • An impact clutch comprising a rotatable anvil memher, a rotatable hammer mass coaxially supported with respect to said anvil member, a rotatable driving member coaxially supported with respect to said hammer mass, a drive connection directly between said driving member and said hammer mass, an impact dog pivotally mounted on said hammer mass for rotation therewith and movable relative thereto in clutching and declutching direction about an axis oilset from but parallel with the axis of rotation of said anvil member, cam means between said anvil member and said dog for positively pivoting said dog in the clutching direction, and a torsion spring oriented coaxially with said anvil member and said driving member and arranged between said driving member and said impact dog for pivoting said impact dog in the declutching direction.
  • An impact clutch comprising a rotatable anvil memher, a rotatable hammer mass coaxially supported with respect to said anvil member, a rotatable driving member coaxially supported with respect to said hammer mass, a drive connection directly between said driving member and said hammer mass, a partially cylindrical axial recess in said hammer mass facing said anvil member, an impact transmitting dog having a partial cylindrical rear bearing portion thereon, said dog being journalled by said bearing portion in said hammer mass recess and supported therein for movement in clutching and declutching direction, a recessed front portion on said impact dog facing the anvil member and merging into said rear portion by a pair of spaced apart edges, cam means between said anvil member and one of said edges for pivoting said other edge in clutching direction, and a torsion spring oriented coaxially with said anvil member and said driv ing member and arranged between said driving member and said impact dog for pivoting said impact dog in the declutching direction.
  • a reversible impact clutch comprising a rotatable anvil member, a rotatable hammer mass coaxially supported with respect to said anvil member, a rotatable driving member coaxially supported with respect to said hammer mass, a drive connection incorporating some degree of play for providing a constantly engaged direct drive between said driving member and said hammer mass except for said play a partially cylindrical axial recess in said hammer mass facing said anvil member, an impact transmitting dog having a partially cylindrical rear bearing portion thereon, said dog being journalled by said bearing portion in said hammer mass recess and supported therein for movement in clutching and declutching direction, a recessed front portion on said impact dog facing the anvil member and merging into said rear portion by a pair of spaced apart edges, a pin on said impact dog intermediate the pivotal axis of said impact dog and the axis of rotation of said hammer mass forming a first pair of opposed abutment surfaces, at forwardly extending projection on said driving member adjacent said
  • An impact clutch as set forth in claim 10 in which the ends of said torsion spring form laterally parallel to a transverse plane through the axis of said spring and spaced from each other with protruding shanks extending in said first pair and second pair of opposed abutment surfaces disposed therebetween.
  • an impact clutch apparatus of the character de scribed having a reversible motor with a rotatable driving member extending therefrom, a rotatable anvil member c0- axially supported with'respect to said driving member and a rotatable hammer mass coaxially supported with respect to said anvil member, the combination which comprises a driving connection incorporating some degree of play for providing a constantly engaged direct drive between said driving member and said hammer mass except for said play, an impact dog pivotaliy mounted in said hammer mass about an axis offset from but parallel with the axis of rotation of said anvil member in a clutching and a declutching direction, a pin extending from said impact dog intermediate the pivotal axis thereof and the axis of said hammer mass forming a pair of opposed abutment surfaces, cam means disposed and operative between said anvil member and the trailing edge of said impact dog for positively pivoting the leading edge of said impact dog in a clutching direction, and spring means rotatable with said
  • said spring means comprises a torsion spring coaxially disposed in said driving member, and laterally protruding shanks extending in parallel to a transverse plane ex tending through the axis of said spring from the end thereof with said opposed abutment surfaces disposed therebetween.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
US184013A 1962-04-02 1962-04-02 Impact clutches Expired - Lifetime US3179219A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US184013A US3179219A (en) 1962-04-02 1962-04-02 Impact clutches
GB10309/63A GB973333A (en) 1962-04-02 1963-03-15 Improvements in impact clutches
DEA42726A DE1287529B (de) 1962-04-02 1963-03-27 Drehschlagwerkzeug
DK139463AA DK112929B (da) 1962-04-02 1963-03-28 Slagkobling.
CH413463A CH414494A (de) 1962-04-02 1963-04-02 Mit Schlagkupplung ausgerüstetes Schlagwerkzeug

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US184013A US3179219A (en) 1962-04-02 1962-04-02 Impact clutches

Publications (1)

Publication Number Publication Date
US3179219A true US3179219A (en) 1965-04-20

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ID=22675242

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Application Number Title Priority Date Filing Date
US184013A Expired - Lifetime US3179219A (en) 1962-04-02 1962-04-02 Impact clutches

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US (1) US3179219A (da)
CH (1) CH414494A (da)
DE (1) DE1287529B (da)
DK (1) DK112929B (da)
GB (1) GB973333A (da)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3648784A (en) * 1969-09-26 1972-03-14 Atlas Copco Ab Rotary impact motor
US3789934A (en) * 1971-04-07 1974-02-05 Atlas Copco Ab Rotary impact motor
US4347902A (en) * 1979-12-18 1982-09-07 Chicago Pneumatic Tool Company Rotary impact wrench clutch
US6318479B1 (en) * 1999-10-01 2001-11-20 Chicago Pneumatic Tool Company Vibration isolated impact wrench
US6321853B2 (en) * 1999-10-01 2001-11-27 Chicago Pneumtic Tool Company Vibration isolated impact wrench
US6527060B1 (en) 1998-02-03 2003-03-04 Atlas Copco Tools Ab Portable power tool with separate pistol-type handle
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
US20080066941A1 (en) * 2006-09-18 2008-03-20 Sp Air Kabushiki Kaisha Reversible valve assembly for a pneumatic tool
US20210379738A1 (en) * 2016-08-25 2021-12-09 Milwaukee Electric Tool Corporation Impact tool

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE755276A (fr) * 1969-08-25 1971-02-01 Maurer Spencer B Clef rotopercutante et son mecanisme d'accouplement

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2219883A (en) * 1937-06-05 1940-10-29 Chicago Pneumatic Tool Co Impact wrench
US2343596A (en) * 1941-12-12 1944-03-07 Cleveland Pneumatic Tool Co Nut setter
US2768546A (en) * 1954-04-26 1956-10-30 Chicago Pneumatic Tool Co Torque control for impact wrenches

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2285638A (en) * 1939-11-22 1942-06-09 Chicago Pneumatic Tool Co Impact clutch
US2718803A (en) * 1954-08-16 1955-09-27 Ingersoll Rand Co Impact wrench
US2801718A (en) * 1956-04-05 1957-08-06 Thor Power Tool Co Impact clutch mechanism

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2219883A (en) * 1937-06-05 1940-10-29 Chicago Pneumatic Tool Co Impact wrench
US2343596A (en) * 1941-12-12 1944-03-07 Cleveland Pneumatic Tool Co Nut setter
US2768546A (en) * 1954-04-26 1956-10-30 Chicago Pneumatic Tool Co Torque control for impact wrenches

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3648784A (en) * 1969-09-26 1972-03-14 Atlas Copco Ab Rotary impact motor
US3789934A (en) * 1971-04-07 1974-02-05 Atlas Copco Ab Rotary impact motor
US4347902A (en) * 1979-12-18 1982-09-07 Chicago Pneumatic Tool Company Rotary impact wrench clutch
US6527060B1 (en) 1998-02-03 2003-03-04 Atlas Copco Tools Ab Portable power tool with separate pistol-type handle
US6318479B1 (en) * 1999-10-01 2001-11-20 Chicago Pneumatic Tool Company Vibration isolated impact wrench
US6321853B2 (en) * 1999-10-01 2001-11-27 Chicago Pneumtic Tool Company Vibration isolated impact wrench
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
US20080066941A1 (en) * 2006-09-18 2008-03-20 Sp Air Kabushiki Kaisha Reversible valve assembly for a pneumatic tool
US20080066937A1 (en) * 2006-09-18 2008-03-20 Sp Air Kabushiki Kaisha Reversible Valve Assembly for a Pneumatic Tool
US7802633B2 (en) * 2006-09-18 2010-09-28 Sp Air Kabushiki Kaisha Reversible valve assembly for a pneumatic tool
US8020631B2 (en) 2006-09-18 2011-09-20 Sp Air Kabushiki Kaisha Reversible valve assembly for a pneumatic tool
US20210379738A1 (en) * 2016-08-25 2021-12-09 Milwaukee Electric Tool Corporation Impact tool
US11897095B2 (en) * 2016-08-25 2024-02-13 Milwaukee Electric Tool Corporation Impact tool
US20240181609A1 (en) * 2016-08-25 2024-06-06 Milwaukee Electric Tool Corporation Impact tool with collapsible member to compensate for thermal expansion
US12304034B2 (en) * 2016-08-25 2025-05-20 Milwaukee Electric Tool Corporation Impact tool with collapsible member to compensate for thermal expansion

Also Published As

Publication number Publication date
CH414494A (de) 1966-05-31
GB973333A (en) 1964-10-21
DK112929B (da) 1969-01-27
DE1287529B (de) 1969-01-16

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