US3760886A - Electrically-powered device for exerting rotational impact force to a fastener element - Google Patents

Electrically-powered device for exerting rotational impact force to a fastener element Download PDF

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Publication number
US3760886A
US3760886A US00198334A US3760886DA US3760886A US 3760886 A US3760886 A US 3760886A US 00198334 A US00198334 A US 00198334A US 3760886D A US3760886D A US 3760886DA US 3760886 A US3760886 A US 3760886A
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United States
Prior art keywords
drive member
output shaft
drive
respect
housing
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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
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US00198334A
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English (en)
Inventor
Y Mori
K Mizu
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.)
MATSUSHITO ELECTRIC IND CO Ltd
MATSUSHITO ELECTRIC INDUSTRIAL CO LTD JA
Original Assignee
MATSUSHITO ELECTRIC IND CO Ltd
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Filing date
Publication date
Priority claimed from JP10174470A external-priority patent/JPS4914520B1/ja
Priority claimed from JP7955671U external-priority patent/JPS5045751Y2/ja
Application filed by MATSUSHITO ELECTRIC IND CO Ltd filed Critical MATSUSHITO ELECTRIC IND CO Ltd
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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

Definitions

  • ABSTRACT A device for exerting impact force to a fastener such as a nut to tighten or loosen the nut with respect to an associated bolt.
  • the device has an axially movable and rotatable cylindrical drive member normally in engagement with an output shaft of the device having an outer end for engagement with a fastener.
  • An electrically actuated drive shaft extends into the drive member for relative rotational movement with respect to the drive member.
  • a formation comprising a plurality of balls is disposed between the drive member and shaft. The arrangement is such that the formation is depressed circumferentially of the drive member to expand axially thereof in response to the relative rotational movement between the drive member and the shaft whereby the drive member is disengaged from the output shaft.
  • a manually actuated tool such as a wrench is conventionally used to exert a rotational force to a fastener element such as a nut for tightening or loosening the same with respect to another fastener element such as a bolt associated with the nut.
  • a great magnitude of force is required to actuate such manual tool in rotating such fastener element and, particularly, in loosening a nut which is tightened with respect to an associated bolt.
  • a power-actuated tool such as a pressurized airactuated tool is also used for similar purposesbut requires a bulky and relatively complicated expensive pressurized air source such as an air compressor.
  • this type of device not only requires troublesome frequent maintenance but is noisy during operation due to the exhaust of spent pressurized air.
  • the device of this type moreover, requires a length of air supply conduit of a substantial diameter which limits the application of the device.
  • the pressurized air-actuated tool employs a impact force producing means which comprises hammers pivotally mounted on a hammer case and cam members on the hammer case for cooperating with the hammers to produce an impact force which is exerted on a fastener element to be rotated with respect to another fastener element associated therewith.
  • the device therefore, has a large number of parts which essentially increases the cost of manufacture of the the device.
  • the device is operable to produce a sufficient rotational impact force only when the device is operated at a high speed.
  • a rotational impact force producing means comprising an electrically actuated drive shaft and drive member and a clutch means for momentarily disengaging the drive member from an output shaft of the device so that the drive member intermittently exerts a rotational impact force of the same magnitude to the output shaft which transmits the impact force to a fastener element.
  • the device comprises a housing, a motor in said housing, means in driving connection with said motor for reducing the speed of the rotation of said motor, an impact force producing means within said housing and in operative connection with said speed reducing means, an output shaft rotatably extending outwardly from said housing and having a tool portion outside thereof for engagement with a fastener element, said output shaft having a portion within said housing having teeth formed thereon, said impact force producing means including a drive shaft in operative connection with said speed reducing means, a tubular hollow drive member loosely received on said drive shaft for rotation and axial movement with respect to said drive shaft and having teeth normally in engagement .with said teeth on said output shaft, means within said housing for biasing said drive member axially toward said output shaft to cause said teeth on said drive member to be engaged with said teeth on said output shaft, means between said drive shaft and said drive member for momentarily disengaging said teeth on said drive member from said teeth on said output shaft, said disengaging means being operative to axially shift said drive member away from said
  • the tubular hollow drive member has at least one axial bead extending radially inwardly therefrom.
  • the end of the drive member remote from the output shaft is preferably substantially closed by a radial wall through which the drive shaft extends rotatably and slidably.
  • the ridge of the drive shaft, the bead and radial wall of the drive member cooperate with the inner end face of the output shaft to define at least one radially, axially and circumferentially confined space in whch the disengaging means is operatiVely received.
  • the disengaging means may preferably comprise a formation of a plurality of balls so arranged within the space that the formation is circumferentially depressed by the ridge and bead to axially expand thereby urging the drive member away from the output shaft against the biasing means when the drive shaft is rotated with respect to the drive member.
  • the disengaging means may alternatively be a resilient ring-like element disposed in the space.
  • the drive member may preferably have a pair of circumferentially spaced flangesextending circumferentially of the drive member and projecting radially inwardly therefrom into the space.
  • the above-mentioned formation may include two balls which are aligned substantially circumferentially of the drive member.
  • the flanges are operative to limit the axial movement of the circumferentially aligned balls.
  • the device may preferably include a spring retainer mounted rotatably on the drive shaft.
  • the biasing means may preferably be a compression spring extending between the drive member and the spring retainer for normally urging the drive member against the outing, means in driving connection with said motor for reducing the speed of the rotation of said motor, an impact force producing means within said housing and in operative connection with said speed reducing means, an output shaft rotatably extending outwardly from said housing and having a tool portion outside thereof for engagement with a fastener element, said output shaft being adapted for interrupted driving connection with said impact force producing means so that the latter exerts a rotational impact force to said tool portion when said output shaft is in engagement with said impact force producing means, said housing including at least a pair of generally cylindrical hollow cover members coupled together at their adjacent ends against relative axial movement with respect to one another and for relative rotational movement with respect to one another, one of said covermembers having a portion rotatably extending into the adjacent end of other cover member, said portion of said one cover member having a pluralit
  • the mentioned portion of the one cover member may preferably have an annular groove formed in the peripheral surface of the portion.
  • Coupling means which preferably comprises a pair of semi-circular pieces secured to the inner surface of the other cover member are received in the annular groove for sliding movement therealong together with the other cover member.
  • the auxiliary handle preferably includes a sleeve member secured at one end to the other cover member and extending around the pin member.
  • a knob member may preferably be mounted on an extension of the pin member which extends out of the sleeve member.
  • the latter is preferably formed, in the peripheral surface thereof, with an L-shaped slot along which a stud on the pin member is slidable therewith axially and circumferentially of the sleeve member when the knob member is rotated or pulled with respect to the sleeve member.
  • FIG. 1 is a fragmentary partial axial sectional view of an embodiment of an electrically powered fastener rotating and tightening and loosening device according to the present invention with a part thereof broken away;
  • FIG. 2 is a cross-sectional view of the device taken substantialy along line II II in FIG. 1;
  • FIG. 3 is a view similar to FIG. 1 but illustrating another embodiment of the invention.
  • FIG. 4 is a cross-sectional view of the device shown in FIG. 3 taken substantially along line IV IV in FIG.
  • FIG. 5 diagrammatically illustrates in reduced scale the device of the present invention in its entirety
  • FIG. 6A-l is a perspective view of a modification of the means for disengaging the drive member from the output shaft as shown in FIGS. 1 and 3;
  • FIG. 6A-2 diagrammatically illustrates the function of the modified disengaging means shown in FIG. 6A-1;
  • FIG. 6B diagrammatically illustrates another modification of the disengaging means
  • FIG. 7A is an axial sectional view of the driving member of the embodiment shown in FIGS. 3 and 4 taken along line VII VII in FIG. 4 and illustrating the disengaging means in its inoperative position;
  • FIG. 7B is a view similar to FIG. 7A but illustrating the disengaging means in its operative position
  • FIG. 8 is a partial axial sectional view of a further embodiment of the device of the invention with a part removed;
  • FIG. 9 is a perspective view of a part of the device of the further embodiment with some elements shown in disassembled positions;
  • FIG. 10 is an enlarged axial sectional view of the auxiliary handle shown in FIG. 8.
  • FIG. 11 is a fragmentary view of the auxiliary handle taken along line XI XI in FIG. 10.
  • FIGS 1, 2 and 5 of the drawings there is shown an embodiment of an electrically powered fastener rotating and tightening and loosening device which comprises an electric motor 1 housed by a motor cover 5, a speed-reduction section 2 housed by a reduction section cover 6, an impact drive section 3 housed by a drive section cover 7, and an output or tool portion 4.
  • the covers 5, 6 and 7 and a handle portion 28 having a trigger type switch actuator 29 are assembled in an appropriate manner as shown in FIG. 5.
  • the motor 1 has its output shaft connected to a small gear 8 which is drivingly conncted to a drive shaft 12 through a series of reduction gears 9, l0 and l 1 of the speed reduction section 2.
  • the drive shaft 12 is secured at one end to the first reduction gear 11 for rotation therewith and is rotatably supported at a portion intermediary of the ends thereof by a ball bearing 20 mounted on that portion 51 of the cover 6 which is snugly received in and secured to the rear end of the cover 7.
  • a collar 24 is mounted on the shaft 12 in abutment with one end face of the bearing 20.
  • the impact drive section 3 includes a cylindrical drive member 13 having a disc-like end wall 13' which is slidably received on the drive shaft 12 so that the drive member 13 is rotatable and axially slidable with respect to the shaft 12.
  • the drive member 13 has a pair of diametrically opposite axially forwardly extending teeth 15 formed on the forward end face of the drive member 13.
  • the tool portion 4 includes an output shaft 16 rotatably extending through a bushing 25 received in and scured to the inner surface of-a bore 7 formed in the forward end of the cover 7.
  • the output shaft 16 is coaxial with the drive shaft 12 and has an inner or rear portion 160 of an increased diameter which loosely extends rearwardly into the drive member 13 and which rotatably receives a forward extension 18 of the drive shaft 12 in an axial bore 19 formed in the rear portion 16a.
  • the output shaft 16 also has formed thereon a flange 16b on which are formed a pair of diametrically opposite axially rearwardly extending teeth 17 adapted to be engaged and disengaged by the teeth on the drive member 13.
  • a compression coil spring 21 extends around a rear reduced diameter portion of the drive member 13 and an intermediate portion of the drive shaft 12.
  • the coil spring 21 has an end in pressure contact with an annular shoulder 6' provided by a forward portion of the cover 6 received in the cover 7.
  • the other end of the coil spring 21 is in pressure contact with another shoulder provided by the rear reduced diameter portion of the drive member 13.
  • the compression coil spring 21 normally forwardly biases the drive member '13 to urge the teeth 15 thereof into engagement with the teeth 17 of the output shaft 16.
  • FIG. 3 illustrates another embodiment of the invention which is modified to employ a thrust bearing 23 mounted on the drive shaft 12 adjacent the collar 24.
  • the thrust bearing 24 bears a thrust from a disclike spring retainer 22 which is rotatably mounted partly on the drive shaft 12 and partly on the thrust bearing 24 and which receives the rear end of the compression coil spring 21 at the marginal edge portion.
  • a disclike spring retainer 22 which is rotatably mounted partly on the drive shaft 12 and partly on the thrust bearing 24 and which receives the rear end of the compression coil spring 21 at the marginal edge portion.
  • the disengaging means comprises two sets of four balls of a hard material such as steel.
  • the disengaging means are disposed in spaces 14, 14 defined in radial and axial directions by the inner surface 131 of the drive member 13, the rear wall 13' thereof, the outer surface of the shaft 12 and the rear end surface of the rear portion 16a of the output shaft 16.
  • FIG. 2 is a cross-sectional view of the embodiment shown in FIG. 1 illustrating the spaces 14, 14 as seen in a direction perpendicular to that in which the spaces are seen in FIG. 1.
  • FIG. 4 is a cross-sectional view similar to FIG. 2 but illustrating the spaces 14, 14 in the modified embodiment shown in FIG. 3. From the illustrations in FIGS. 2 and 4, it will be understood that each of the embodiments has a pair of generally arcuate diametrically opposite spaces 14, 14 defined in the circumferential direction by a pair of diametrically opposite beads 27, 27 projecting radially inwardly from the drive member 13 and by a pair of diametrically opposite ridges 26, 26 radially outwardly extending from the drive shaft 12.
  • the side faces of the ridges 26, 26 and beads 27, 27 are formed to provide arcuately concave profiles to accommodate the spherical surfaces of the balls received in the spaces 14, 14.
  • FIG. 4 is substantially identical with the embodiment shown in FIG. 2 except for the provision of a pair of diametrically opposite flanges 132, 132 extending radially inwardly beyond the ridges 27, 27 and extending circumferentially between the spaces 14, 14 at the ends thereof adjacent the rear end face of the output shaft portion 16a as best seen in FIGS. 7A and 7B which are taken substantially along line VII VII inFIG. 4. It will be seen in FIGS. 7A and 78 that four balls 141, 142, 143 and 144 are received in each space 14.
  • the diameter D1 of the shaft 12 the diameter D2 of a circle of revolution of the inner surfaces 131, 131 of the drive member 13, the diameter D3 of a circle of revolution of the outer surfaces of the ridges 26, 26 and the diameter d of each of the balls 141 through 144 be of the following relationship:
  • the four balls 141 through 144 are disposed at the four apexes of a diamond.
  • the axially aligned balls 141 and 144 contact each other while the other circumferentially aligned two balls 142 and 143 are spaced from one another as shown in FIG. 7A.
  • the drive member 13 is biased forwardly by the coil spring 21 so that the teeth 15 of the drive member 13 are in meshing engagement with the teeth 17 of the output shaft '16.
  • the process is repeated to give the tool portion 4 an interrupted rotational impact force of the same magnitude which in turn may be exerted to a fastener such as a nut to tighten the same with respect to a cooperating bolt and against a workpiece through which the bolt extends.
  • a fastener such as a nut to tighten the same with respect to a cooperating bolt and against a workpiece through which the bolt extends.
  • FIGS. 2 and 4 are operable substantially in the same manner. It will, however, be appreciated that the embodiment shown in FIG. 4 is more advantageous in that the circumferentially and radially inwardly extending flanges 132, 132 of the embodiment shown in FIG. 4 assure controlled or axially limited operations of the circumferentially aligned balls 142 and 143 for the reliable engagement between the sets of the teeth and 17 and their disengagement from each other. On the contrary with the embodiment shown in FIG.
  • the inner surfaces 131 of the drive member 13 in both embodiments shown in FIGS. 2 and 4 have complex curvatures.
  • the drive member 13 of the embodiment shown in FIG. 4 has circumferentially and radially inwardly extending flanges 132, 132.
  • the rear wall portion 13 thereof is advantageously a disclike member which is fitted into and secured to a cylindrical hollow member to complete the drive member 13.
  • FIGS. 3 and 4 For convenience, the embodiment shown in FIGS. 3 and 4 is illustrated and has been described as employing both of the disc-like spring retainer and thrust bearing assembly 22 and 23 and the radially inwardly and circumferentially extending flanges 132 and 132. It is, however, to be understood that the scope of the present invention includes a device which does not have such a spring retainer and thrust bearing assembly but employs such flanges. It is also to be understood that a device which has such a spring retainer and thrust bearing assembly but does not include such flanges is also included in the scope of the invention.
  • the above-described device of the invention is operable per se. It is, however, difficult for the device to be supported in position at the handle 28 alone during operation.
  • the device of another embodiment therefore, may preferably be equipped with accessories which will be described hereunder with reference to FIGS. 8 to l l of the drawings.
  • the reduction section cover 6 and the handle portion 28 are provided thereon with brackets 30 and 30', respectively.
  • the device is provided with a suspension belt 31 connected at the opposite ends to the brackets 30 and 30 so that the device can be supported from a shoulder of an operator by means of the suspension belt 31.
  • An auxiliary handle 38 is mounted on the cover 7 at a portion adjacent the rear end thereof.
  • Numeral 52 indicates a socket mounted on the tool portion 4.
  • Numeral 53 denotes an electric lead line connected to the handle portion 28 and electrically connected to a switch (not shown) associated with the actuator 29.
  • portion 51 of the reduction section cover 6 which is received in the rear end portion of the cover 7 is formed with an annular groove 33 in the peripheral surface thereof.
  • the groove 33 rotatably receives a split ring comprising a pair of semi-circular pieces 34, 34 having formed therein threaded holes 35, 35.
  • the cover 7 is rotatably coupled to the cover 6 by means of screws 37 extending inwardly through apertures 36 in the cover 7 into the threaded holes 35, 35 in the split ring pieces 34, 34 slidable along the groove 33.
  • a plurality of spaced holes 39 are formedlin the peripheral surface of the portion 51 of the cover 6.
  • the holes 39 are arranged in a radial plane which is parallel to the annular groove 33 and includes the axis of the auxiliary handle 32.
  • the latter has a pin 38 which extends slidably through the wall of the cover 7 into a selected one of the apertures 39 to determine the angular position of the auxiliary handle with respect to the device as will be described later in more detail.
  • the auxiliary handle 32 comprises a sleeve 40 in which the above-mentioned pin 38 is received for relative sliding movement with respect to the sleeve 40.
  • a collar 45 is fitted into the bottom end of the sleeve 40 and is secured thereto by means of a set screw 46.
  • a flange 41 At the intermediary portion between the ends of the pin 38 is provided a flange 41 with which a compression coil spring 42 is in pressure contact at one end to hold the pin 38 in engagement with the selected one of the apertures 39 in the cover 6, the other end of the spring 42 being retained by the collar 45.
  • the pin 38 has mounted on the periphery thereof a stud 43 which is slidably received in an L-shaped slot 44, as shown in FIG. 11, formed in the peripheral wall of the sleeve 40 so that the stud 43 and the slot 44 cooperate together to limit the axial movement of the pin 38 with respect to the sleeve 40.
  • a knob 47 is secured to the bottom end of the pin 38 by means of a set screw 48.
  • the sleeve 40 and the knob 47 are covered with rugged covers 49 and 50, respectively, to make it easy for an operator to grip the auxiliary handle 32.
  • the stud 43 is normally positioned at an upper end portion A of the slot 44.
  • the stud 43 is moved along the slot 44 to a central portion B thereof and, when the knob 47 is rotated in a direction, the stud 43 is further moved to the other end portion C of the slot 44.
  • the pin 38 is removed from the hole 39 in the forward end portion 51 of the cover 6 and is maintained in this position by the cooperation of the stud 43 and the circumferential section of the slot 44 even if the pulling force is removed from the knob 47.
  • the drive section cover 7 is rotatable together with the split ring pieces 34, 34 with respect to the reduction section cover 6.
  • the knob 47 may be rotated in the other direction to allow the pin 38 to be urged into the selected aperture 39 by the compression spring 42 so that the auxiliary handle 32 is angularly firmly repositioned with respect to the device.
  • the stud 43 is also returned to its initial position A in the slot 44.
  • auxiliary handle 32 can be set at a position most suited for easy operation of the device to facilitate improved working efficiency.
  • An electrically-powered device for exerting intermittent rotational impact force to a first fastener element to move the same with respect to a second fastener element associated therewith, said device comprising a housing, a motor in said housing, means in driving connection with said motor for reducing the speed of the rotation of said motor, an impact force producing means within said housing and in operative connection with said speed reducing means, an output shaft rotatably extending outwardly from said housing and having a tool portion outside thereof for engagement with said first fastener element, said output shaft having a portion within said housing having teeth formed thereon, said impact force producing means including a drive shaft in operative connection with said speed reducing means, a tubular hollow drive member loosely received on said drive shaft for rotation and axial movement with respect to said drive shaft and having teeth normally in engagement with said teeth on said output shaft, means within said housing for biasing said drive member axially toward said output shaft to cause said teeth on said drive member to be engaged with said teeth on said output shaft, means between said drive shaft and said drive
  • said drive shaft has formed thereon at least one radially outwardly and axially extending ridge, said tubular hollow drive member having at least one axial bead extending radially inwardly therefrom, the end of said drive member remote from said output shaft being substantially closed by a radial wall through which said drive shaft extends rotatably and slidably, said ridge on said drive shaft, said bead and radial wall of said drive member cooperating with the inner end face of said output shaft to define at least one'radially, axially and circumferentially confined space in which said disengaging means are operatively received.
  • said disengaging means comprises a formation of a plurality of balls so arranged within said space that the formation is depressed circumferentially of said drive member by said ridge and bead to expand axially of said drive member for thereby urging said drive member away from said output shaft against said biasing means when said drive shaft is rotated withrespect to said drive member.
  • said disengaging means comprises a resilient ring-like element disposed within said space, said resilient element'being adapted to be depressed circumferentially of said drive member by said ridge and bead to expand axially of said drive member for thereby urging said drive member away from said output shaft against said biasing meanS when said drive shaft is rotated with respect to said drive member.
  • a spring retainer mounted rotatably on said drive shaft, said biasing means comprising a compression spring extending between said drive member and said spring retainer for normally urging said drive member against said output shaft.
  • An electrically powered device for exerting intermittent rotational impact force to a first fastener element totighten the same with respect to a second fastener element associated therewith, said device comprising a housing, a motor in said housing, means in driving connection with said motor for reducing the speed of the rotation of said motor, an impact force producing means within said housing and in operative connection with said speed reducing means, an output shaft rotatably extending outwardly from said housing and having a tool portion outside thereof for engagement with said first fastener element, said output shaft being adapted for interrupted driving connection with said impact force producing means so that the latter exerts a rotational impact force to said tool portion when said output shaft is in engagement with said impact force producing means, said housing including at least a pair of generally cylindrical hollow cover members coupled together at their adjacent ends against relative axial movement with respect to one another and for relsubstantially radially therefrom, said auxiliary handle including a pin member mounted therein for axial sliding movement with respect to said auxiliary handle, said pin member having an end portion extending slidably
  • said portion of said one cover member has an annular groove formed in the peripheral surface thereof, coupling means received in said annular groove for sliding movement therealong and secured to said other cover member for rotation therewith with respect to said one cover member.
  • said auxiliary handle includes a sleeve member secured at one end to said other cover member and extending around said pin member, the latter having an extension projecting out of the other end of said sleeve member, a knob member mounted on said extension of said pin member, said sleeve member having an L-shaped slot formed in the peripheral wall thereof, said pin member having a stud radially projecting therefrom and extending into said slot for movement therealong, said slot having a portion extending axially of said sleeve member and another portion extending circumferentially thereof.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
US00198334A 1970-11-16 1971-11-12 Electrically-powered device for exerting rotational impact force to a fastener element Expired - Lifetime US3760886A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP10174470A JPS4914520B1 (nl) 1970-11-16 1970-11-16
JP7955671U JPS5045751Y2 (nl) 1971-09-01 1971-09-01

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US3760886A true US3760886A (en) 1973-09-25

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US00198334A Expired - Lifetime US3760886A (en) 1970-11-16 1971-11-12 Electrically-powered device for exerting rotational impact force to a fastener element

Country Status (6)

Country Link
US (1) US3760886A (nl)
CA (1) CA935492A (nl)
DE (1) DE2156665C3 (nl)
FR (1) FR2114699A5 (nl)
GB (1) GB1360472A (nl)
NL (1) NL165094C (nl)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3848680A (en) * 1973-12-26 1974-11-19 Skil Corp Impact clutch mechanism
US4232750A (en) * 1978-10-26 1980-11-11 Antipov Georgy A Impact wrench with a rotary tool drive
US5836403A (en) * 1996-10-31 1998-11-17 Snap-On Technologies, Inc. Reversible high impact mechanism

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IL266295B2 (en) 2019-04-28 2024-02-01 Ham Let Israel Canada Ltd key

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2753965A (en) * 1951-10-03 1956-07-10 Thor Power Tool Co Impact tools
US2756853A (en) * 1955-04-01 1956-07-31 Albertson & Co Inc Rotary impact tool
US2808916A (en) * 1953-10-09 1957-10-08 Ingersoll Rand Co Impact wrench
US3198303A (en) * 1964-01-06 1965-08-03 Ingersoll Rand Co Rotary impact tool
US3369615A (en) * 1966-05-27 1968-02-20 Black & Decker Mfg Co Impact wrench
US3414066A (en) * 1966-08-31 1968-12-03 Chicago Pneumatic Tool Co Impact wrench

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2753965A (en) * 1951-10-03 1956-07-10 Thor Power Tool Co Impact tools
US2808916A (en) * 1953-10-09 1957-10-08 Ingersoll Rand Co Impact wrench
US2756853A (en) * 1955-04-01 1956-07-31 Albertson & Co Inc Rotary impact tool
US3198303A (en) * 1964-01-06 1965-08-03 Ingersoll Rand Co Rotary impact tool
US3369615A (en) * 1966-05-27 1968-02-20 Black & Decker Mfg Co Impact wrench
US3414066A (en) * 1966-08-31 1968-12-03 Chicago Pneumatic Tool Co Impact wrench

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3848680A (en) * 1973-12-26 1974-11-19 Skil Corp Impact clutch mechanism
US4232750A (en) * 1978-10-26 1980-11-11 Antipov Georgy A Impact wrench with a rotary tool drive
US5836403A (en) * 1996-10-31 1998-11-17 Snap-On Technologies, Inc. Reversible high impact mechanism

Also Published As

Publication number Publication date
NL165094C (nl) 1981-03-16
DE2156665B2 (de) 1974-07-25
GB1360472A (en) 1974-07-17
FR2114699A5 (nl) 1972-06-30
NL165094B (nl) 1980-10-15
CA935492A (en) 1973-10-16
DE2156665A1 (nl) 1972-06-15
DE2156665C3 (de) 1975-03-13
NL7115718A (nl) 1972-05-18

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