US3866692A - Power tools - Google Patents

Power tools Download PDF

Info

Publication number
US3866692A
US3866692A US328916A US32891673A US3866692A US 3866692 A US3866692 A US 3866692A US 328916 A US328916 A US 328916A US 32891673 A US32891673 A US 32891673A US 3866692 A US3866692 A US 3866692A
Authority
US
United States
Prior art keywords
tool
tool holder
driven
casing
driving
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
US328916A
Other languages
English (en)
Inventor
Charles R Stelljes
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.)
Boeing North American Inc
Original Assignee
Rockwell International Corp
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 Rockwell International Corp filed Critical Rockwell International Corp
Priority to US328916A priority Critical patent/US3866692A/en
Priority to GB217874A priority patent/GB1451258A/en
Priority to CH97774A priority patent/CH582302A5/xx
Priority to CA190,996A priority patent/CA1006718A/en
Priority to BR760/74A priority patent/BR7400760D0/pt
Priority to DE2404968A priority patent/DE2404968A1/de
Priority to FR7403608A priority patent/FR2216050B1/fr
Application granted granted Critical
Publication of US3866692A publication Critical patent/US3866692A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B45/00—Hand-held or like portable drilling machines, e.g. drill guns; Equipment therefor
    • B23B45/008—Gear boxes, clutches, bearings, feeding mechanisms or like equipment
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • E21B6/06—Drives for drilling with combined rotary and percussive action the rotation being intermittent, e.g. obtained by ratchet device
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/042—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D7/044—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth

Definitions

  • the present invention relates to power driven devices and, more particularly, to power driven devices for drilling holes in or otherwise working concrete, masonry, and the like by axially impacting a tool against the workpiece, either with or without intermittent rotation of the tool, depending upon the task and the material involved.
  • One primary object of the present invention resides in the provision of novel, improved power driven devices of the type just described. Such devices are commonly referred to as power hammers or power driven hammers; and this terminology will, accordingly, be employed herein with the understanding that it is intended to be only descriptive and not limiting.
  • these hammers include a mechanism of the character described in US. Pat. No. 3,650,336 issued Mar. 21, 1972, to Heinrich P. Koehler for POWER DRIVEN DEVICE for impacting a tool and a ratchet mechanism of the character therein disclosed for imparting intermittent rotation to the tool.
  • the motor of the device is connected through a rotary-toreciprocating motion converting mechanism to the impact producing mechanism, which consists ofa reciprocable piston in which a free-floating driver is slidably mounted.
  • the driver is dimensioned to strike a closed type tool holder to impart axial impacts to a tool in the holder. Controlled flow of air into and out of the piston on opposite sides of the driver produces positive forces for propelling the driver through its working and return strokes and provides cushions which prevent the driver from striking the ends of the piston as it moves backand-forth therein.
  • the tool socket and the tool mounted therein are rotatably advanced through an angle of preselected magnitude by a novel motion transmitting mechanism driven by the piston.
  • This mechanism is also torque responsive and interrupts the rotary drive connection between the piston and tool socket if the tool binds or sticks.
  • the rotary motion producing mechanism includes a drive member which is connected to the reciprocable piston by helical splines so that the drive member rotates back-and-forth as the piston reciprocates.
  • This motion of the drive member is converted to intermittent unidirectional rotary motion by a ratchet arrangement which has an input rotatable with the drive member just described.
  • the output member of the ratchet arrangement and, consequently, the tool holder and the tool mounted therein rotate or advance only as the drive member rotates in one of its two opposite directions.
  • my power driven hammers include a novel selector mechanism with an actuator accessible from the exterior of the casing for moving the input and output members of the ratchet mechanism out of engagement when axial impacting of the tool without rotation is wanted.
  • an actuator accessible from the exterior of the casing for moving the input and output members of the ratchet mechanism out of engagement when axial impacting of the tool without rotation is wanted.
  • the novel arrangement just described increases to a maximum the speed and ease with which power driven hammers can be shifted between the two modes of operation. And it also eliminates the need for two sets of tools with different shank configurations to produce the two modes of operation.
  • the selector mechanism I employ is simple and rugged and, therefore, has a long service life ant is relatively inexpensive to incorporate in a power hammer and to maintain.
  • novel power hammers of the present invention have the advantages .of being compact and relatively light and of having good balance due to the manner in which the motor is positioned with respect to the rotary-to-reciprocatory motion convering mechanism. They are also rugged, providing a long service life, and uncomplicated, making them comparatively inexpensive to manufacture and maintain.
  • novel hammers of the present invention are highly effective in drilling and like operations because of the intermittent rotation imparted to the tool in conjunction with axial impacts.
  • novel closed type tool holder employed in the hammers of the present invention has been found effective in preventing foreign matter from penetrating to the interior of the hammer casing. This also contributes to proper operation of the hammer and to long service life.
  • Another primary object of the present invention resides in the provision of power hammers with novel, improved mechanisms for providing a choice between axialhammering alone or axial hammering plus intermittent rotation of the tool.
  • FIG. 1 is a side view of a power driven hammer constructed in accord with the principles of the present invention and equipped with a selector mechanism in accord with that invention for providing a choice between axial hammering and intermittent rotary advance of a tool and axial hammering alone;
  • FIG. 2 is a longitudinal section through the front end of the power driven hammer of FIG. 1;
  • FIG. 3a is a fragmentary side view of the mechanism employed in the hammer of FIG. 1 to produce axial hammering and intermittent rotary advance of the tool;
  • FIG. 3b is a view similar to FIG. 3a but with the selector mechanism operated to interrupt the rotary advance of the tool so that it will only be axially impacted;
  • FIG. 4 is a pictorial view of a cup-shaped actuator employed in the selector mechanism
  • FIG. 5 is a section through the tool taken substantially along line 5-5 of FIG. 2;
  • FIG. 6 is a view similar to FIG. 2 of a hammer similar to that shown in FIG. 1, but equipped with an alternate form of selector mechanism;
  • FIG. 7 is a partially sectioned side view of the selector mechanism employed in the hammer of FIG. 6;
  • FIG. 8 is a pictorial view of two cam members which are components of the selector mechanism.
  • FIGS. 1 and 2 depict a power driven hammer 18 constructed in accord with the principles of the present invention.
  • the major components of hammer 18 include a casing 20 housing a motor drive-connected through a rotary-toreciprocable motion converting mechanism (neither shown) to the piston 26 of an impact imparting mechanism 28 which also includes a free-floating driver 20 slidably mounted in the piston.
  • Driver 30 is adapted to periodically strike and impart an impact to an axially movable tool holder 32 mounted in the forward end of casing 20 and thence to a tool 33 socketed in the tool holder and retained in place by a conventional spring type retainer 34.
  • the tool may also be intermittently rotated or advanced during each working stroke by the piston, which is drive-connected to too] holder 32 through a reciprocable to intermittent, undirectional, rotary motion converting drive mechanism 36.
  • Drive mechanism 36 is also designed to serve an overload function; i.e., to interrupt the drive connection between piston 26 and tool holder 32 if the rotation resisting torque exerted by the tool on the tool holder rises above a predetermined magnitude.
  • Hammer 18 also includes a novel selector mechanism 37 having an actuator 38 accessible from the exterior of casing 20. With the actuator in one of two positions drive mechanism 36 is operable to incrementally advance the tool 33 in tool holder 32. With the actuator in its other position, continuity in the drive mechanism is interrupted; and tool 33 is, therefore, axially impacted but not rotated.
  • Hammer 18 also has a pistol grip 39 supporting a switch 40 for controlling the operation of its motor.
  • switch 40 for controlling the operation of its motor.
  • piston 26 is supportedfor reciprocable, rectilinear movement in casing 20 by a piston guide which has not been shown because it is not part of the present invention and because it is described in detail in US. Pat. No. 3,650,336.
  • Free-floating driver 30, the other component of the axial impact producingmechanism, has a head 42 dimensioned for a sliding fitin the main body portion 44 of piston 26 and a smaller diameter stem '46 dimensioned for a sliding fit in the necked down forward portion 48 of the piston.
  • Driver 30 is extendible from one end of piston 26 into impacting engagement with tool holder 32 as piston 26 moves forwardly (i.e., toward the nose end of the hammer) and displaced toward the rearward end of the piston during the return stroke of the latter by the controlled ingress of air into piston 26 on opposite sides of driver head 42 and the controlled egress of air therefrom.
  • the tool holder 32 against which driver 30 impacts includes a cylindrical main body portion 50 in which a tool receiving socket 52 is formed and a closed rear wall 54, which prevents foreign matter from penetrating through the tool socket to the interior of casing 20.
  • Tool holder 32 is mounted for rectilinear movement in tool casing 20 with a flange 56 at its nose slidingly engaging the interior of the casing section.
  • An O-ring 58 disposed in a recess 60 formed in the tool holder nose portion prevents foreign matter from penetrating to the interior of the tool casing around the tool holder.
  • a ring 62 of resilient material is preferably disposed in the forward end of casing 20 in spaced relation to tool holder 32. This ring keeps tool holder 32 from striking and damaging the casing with motor of hammer 18 running and the hammer idling or with no tool in the tool holder.
  • the main body portion 50 of the tool holder extends into a bore 64 through the output or driven member 66 of a ratchet type, intermittent rotary motion producing mechanism 68 incorporated in motion converting drive mechanism 36.
  • Output member 66 is rotatably mounted in casing 20, but is fixed against axial movement by an annular ledge 70 in the casing and a retainer 72 fitted therein.
  • External splines 76 on the main body portion 50 of tool holder 32 and cooperating internal splines 78 in the bore 64 of driven member 66 connect the tool holder to ratchet output member 66 for rotation therewith.
  • the motion converting mechanism 36 also includes a motion converting component or drive member 80 having an internal bore 82 through which the forward end portion 48 of piston 26 extends (see FIGS. 2 and 5).
  • Member 80 is rotatably and axially movable in a bore 84 through an annular boss 86 in casing 20.
  • Helical external splines88 are formed on the forward end portion 48 of piston 26; and cooperating, internal, helical splines 90 are formed in the bore 82 of driven member 80. Accordingly, as piston 26 is reciprocated, it effects an oscillatory or to-and-fro rocking movement of drive member 80 through an angle determined by the configuration of cooperating splines 88 and 90.
  • the cylindrical input member 92 of a friction clutch 94 is journalled on and fixed to member 80 for rotation therewith.
  • the output member 96 of clutch 94 is similarly journalled on member 80, but is free to rotate rel ative to this member.
  • Clutch output member 96 is also the input or drive member of ratchet-mechanism 68.
  • Clutch members 92 and 96 are frictionally drive connected by Belleville washers 98 and 100 journalled on motion converting drive component 80 between the clutch elements and frictionally engaging the forward face 102 of input member 92 and the rear face 104 of output member 96.
  • the Belleville washers allow friction clutch output member 96 to slip relative to input member 92 when the tool sticks or is otherwise subjected to a restraining torque of more than a predetermined magnitude.
  • Ratchet teeth 106 are formed on the forward face 108 of clutch output/ratchet input member 96, and cooperating ratchet teeth 110 are formed on the rear face 112 of ratchet output member 66.
  • Clutch output mem* ber 96 and ratchet output member 66 are biased into driving relationship by a compression spring 114 having one end which abuts friction clutch input member 92. The other end of this spring engages an annular ledge 116 formed in casing 20.
  • clutch member 96 drives ratchet output member 66 when motion converting component 80 is oscillated or rotated by piston 26 in one direction. However, when output-input member 96 is rotated in the opposite direction by component 80, teeth 106 slide over the teeth 110; and no rotary motion is imparted to output member 66.
  • the rotary advance is transmitted to too] holder 32 as it is splined to ratchet output member 66.
  • the incremental advance is in turn transmitted to the tool 33 mounted in the tool socket by employing matching configurations in the tool socket and on the shank of tool 33 to connect them for concomitant rotary movement.
  • the selector mechanism 37 of hammer 18 includes a cup-shaped member 134 (See FIG. 4) surrounding ratchet mechanism input member 96.
  • An inwardly extending, radial flange 136 on member 134 engages the forward face 108 of input member 96 beyond the teeth 106 formed thereon as shown in FIG. 2.
  • Member 134 is moved toward the rear of hammer 18 to disengage teeth 106 from the teeth on ratchet mechanism output member 66 by rotating actuator 38 (which is a U-shaped hail) from the position shown in FIG. 3A to that shown in FIG. 3B.
  • Legs 140 of the bail extend through apertures 144 in two shafts or stems 146 (see FIGS. 2 and 5).
  • Stems 146 are mounted in axially aligned apertures 148 on opposite sides of casing 20 for rotation about an axis extending at right angles to the path along which ratchet input member 96 can move relative to output member 66.
  • stems 146 Fixed to or integral with and extending inwardly from stems 146 are eccentrics 150, which extend through slots 152 in member 134. Therefore, as bail 38 is displaced to the FIG. 3B position, the rotation of stems 146 displaces member 134 toward! the rear of hammer 18 against the force exerted by compression spring 114, disengaging ratchet input member 96 from output member 66. For the reasons discussed above, the tool holder 32 of hammer 18 and the tool 33 mounted in it then continue to be subjected to axial impacting, but do not rotate.
  • bail 38 is rotated back to the FIG. 3A position. As it is displaced, the cup-shaped member 134 moves forwardly; and ratchet teeth 106 and 110 re-engage so that the ratchet output member 66 and tool holder 32 will be rotatably advanced as piston 26 reciprocates.
  • a second form of selector mechanism 158 is employed in the hammer 160 shown in fragmentary form in FIG. 5. Because hammer 160 is the same as hammer 18 except for the selector mechanism, the former will be described only as necessary to make clear the construction and operation of the selector mechanism; and those components of hammer 160 common to it and hammer 18 will be identified by the same reference characters.
  • Selector mechanism 158 includes a ringlike fixed cam 162 surrounding ratchet output member 66. Adjacent fixed cam 162 is a second, also ringlike cam 164, which is both slidable and rotatable in casing 20. The rear face 166 of the movable cam is dimensioned to engage the forward face 108 of ratchet mechanism input member 96 beyond teeth 106.
  • Cams 1 64 and 162 have cam faces 168 and 170 so configured that, when cam 164 is rotated relative to the fixed cam, it will be displaced toward the rear of hammer 160 against the force exerted by compression spring 114. This displaces ratchet. input member 96 to the rear, disengaging the teeth 106 on the latter from the teeth 110 on ratchet mechanism output member 66 as in the embodiment of the invention described previously to keep rotary motion from being imparted to the tool holder 32 of hammer 160 or to the tool mounted in it.
  • Cam 164 is rotated to disengage the ratchet mechanism input and output members 96 and 66 in the manner just described by turning a knob 174 located exteriorly of casing 20.
  • a knob 174 located exteriorly of casing 20.
  • Fixed to or integral with knob 174 is a stem or shaft 176 mounted in casing 20 for rotation about an axis extending at right angles to the path along which ratchet input member 96 moves as it is disengaged from and engaged with output member 66.
  • Stem 176 is retained in place by a retainer ring 178 fitted in the stem and by a spring 180 between retaining ring 178 and a ledge 182 in casing 20'.
  • eccentric 184 which extends into a longitudinal slot 186 formed in the periphery of rotatable cam 164.
  • pin 188 With knob 174 in the position shown in FIG. 6, pin 188 is biased by spring 180 into a groove 190 in an arcuate boss 192 formed in casing 20, restraining knob 174 against rotation.
  • Ratchet members 96 and 66 are engaged, and the tool (not shown) in tool holder 32 is rotatably advanced as the piston 26 of the impact imparting mechanism reciprocates.
  • knob 174 When axial impact only is wanted, knob 174 is pulled away from casing 20, lifting pin 188 out of groove 190 and freeing knob 174 for rotation relative to the casing. The knob is then rotated until pin 188 is aligned with a second groove 194 in boss 192 and seated in the groove by spring 180 to again restrain the knob against rotation.
  • eccentric 184 rotates movable cam 164, causing one of the cam faces 168 formed on it to ride up the associated cam face 170 on fixed cam 162. This displaces cam member 164 toward the rear of the tool.
  • movable cam 164 will be rotated in the direction indicated by arrow 198, moving the cam rearwardly as shown by arrow 200.
  • ratchet input member As cam member 164 engages the forward face of ratchet member 96, the ratchet input member also moves toward the rear of the tool. This separates ratchet teeth 106 from ratchet teeth 110, and the tool in tool holder 32 will be axially impacted but will not be rotated.
  • a power driven device comprising: a casing; a tool holder rotatably mounted in said casing; means which can be cycled through impacting and return strokes for imparting axial impacts to a tool mounted in said tool holder; means including a driving member and a driven member having means providing a drive connection therebetween for so connecting said impact imparting mechanism to said tool holder that said mechanism rotatably indexes said tool holder and the tool mounted therein during one of the strokes in each cycle thereof but does not effect rotation of the tool holder in the other of said strokes; and means selectively operable to effect a relative displacement between said driving and driven members which will interrupt the drive connection therebetween so that said tool can be axially impacted without rotating it, said driven member being connected to said tool holder for rotation therewith and being axially fixed relative to said casing, said tool holder and said driving member being axially movable relative to driven member, the means for connecting the impact imparting mechanism to said tool holder including means biasing said driving member toward said driven member to
  • the means for interrupting the drive connection between the driving and driven members by moving said driving member away from said driven member includes a member surrounding said driving member and having an inwardly directed flange engageable with said driving member on the side thereof nearest the driven member and means for displacing said flanged member relative to said driven member comprising a member journalled in said casing means for rotation about an axis normal to the path of movement of the flanged member and accessible from the exterior of the casing and an eccentric extending from the inward end of said pin and engaged with said flanged member, whereby said flanged member will be displaced as the member journalled in said casing is rotated.
  • the means for moving said driving member away from said driven member includes a fixed cam means, rotatable cam means between and engageable with said fixed cam means and that side of the driving member nearest the driven member, there being co-operating portions of said fixed and movable cam means so configured that said movable cam will be displaced relative to said fixed cam and move the driving member away from the driven member as said rotatable cam means is rotated relative to said fixed cam means.
  • the power driven member of claim 4, wherein the means for rotating said actuator comprises a member journalled in the casing for rotation about an axis normal to the path of movement of the driving member and accessible from the exterior of the casing and an inwardly extending eccentric engageable with said rotatably journalled member and said rotatable cam means.
  • the means for drive connecting the impact imparting mechanism to the tool holder includes a frictional drive connection providing means capable of transmitting only forces up to a selected maximum magnitude operatively connected between said impact imparting mechanism and the driving member, whereby the drive connection between the impact imparting mechanism and the tool holder is effectively interrupted while there is a rotation restraining force on said tool holder which exceeds the magnitude of the force which said frictional drive connection is capable of transmitting.
  • the means for drive connecting the impact imparting mechanism to the tool holder includes a ratchet means having said driving member as an input and said driven member as an output and means for rotating said driving member back and forth as said impact imparting mechanism moves through its impacting and return strokes, there being cooperating first and second means on said driving and driven members engageable when said driving member is rotated in one direction only to rotatably advance said driven member and said tool holder.
  • a power driven device comprising: a casing; a tool holder rotatably mounted in said casing which can be cycled through impacting and return strokes to impart axial impacts to a tool mounted in said tool holder; a mechanism for rotatably indexing said tool during only a selected part of the cycle of operation of the impact imparting mechanism which includes torque transmitting driving and driven members and means for disengaging said members when axial impact only is wanted and engaging them when both rotation and impacting is wanted; and a rotationtransmitting, torque release means in series with the mechanism for rotatably indexing the tool for keeping the torque imposed on said tool from exceeding a selected value.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • General Engineering & Computer Science (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Boring (AREA)
US328916A 1973-02-02 1973-02-02 Power tools Expired - Lifetime US3866692A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US328916A US3866692A (en) 1973-02-02 1973-02-02 Power tools
GB217874A GB1451258A (en) 1973-02-02 1974-01-17 Power tools
CH97774A CH582302A5 (fr) 1973-02-02 1974-01-24
CA190,996A CA1006718A (en) 1973-02-02 1974-01-25 Power tools
BR760/74A BR7400760D0 (pt) 1973-02-02 1974-02-01 Aperfeicoamentos em aparelho pneumaticamente acionado
DE2404968A DE2404968A1 (de) 1973-02-02 1974-02-01 Werkzeug mit eigenem kraftantrieb
FR7403608A FR2216050B1 (fr) 1973-02-02 1974-02-04

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US328916A US3866692A (en) 1973-02-02 1973-02-02 Power tools

Publications (1)

Publication Number Publication Date
US3866692A true US3866692A (en) 1975-02-18

Family

ID=23283022

Family Applications (1)

Application Number Title Priority Date Filing Date
US328916A Expired - Lifetime US3866692A (en) 1973-02-02 1973-02-02 Power tools

Country Status (7)

Country Link
US (1) US3866692A (fr)
BR (1) BR7400760D0 (fr)
CA (1) CA1006718A (fr)
CH (1) CH582302A5 (fr)
DE (1) DE2404968A1 (fr)
FR (1) FR2216050B1 (fr)
GB (1) GB1451258A (fr)

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4044845A (en) * 1975-03-03 1977-08-30 Hilti Aktiengesellschaft Drilling tool with a two part input unit
US4158970A (en) * 1977-06-15 1979-06-26 Black & Decker Inc. Override arrangement and actuating knob for a shifting mechanism in portable tools
US4236588A (en) * 1977-06-27 1980-12-02 Hilti Aktiengesellschaft Hammer drill with a lockable tool holder
US4239143A (en) * 1979-05-21 1980-12-16 Olin Corporation Driver assembly for small-diameter fasteners
US4408668A (en) * 1980-02-20 1983-10-11 Koehring Gmbh Impact transfer device for power rams
DE3231902A1 (de) * 1982-08-27 1984-03-22 Robert Bosch Gmbh, 7000 Stuttgart Kraftangetriebene handwerkzeugmaschine fuer schlagende oder drehschlagende arbeitsweise
US5050687A (en) * 1988-09-23 1991-09-24 Prokhorov Ivan A Compression-vacuum action percussive machine
US5161624A (en) * 1990-03-19 1992-11-10 Hilti Aktiengesellschaft Tool for driving fastening elements into hard receiving materials
DE19654832A1 (de) * 1996-12-23 1998-06-25 Black & Decker Inc N D Ges D S Betätigungselement
US5871059A (en) * 1995-02-28 1999-02-16 Makita Corporation Mechanism for preventing idling strikes in power-driven striking tools
US6116352A (en) * 1998-03-10 2000-09-12 Robert Bosch Gmbh Drilling and/or percussion power tool
GB2407851A (en) * 2003-11-06 2005-05-11 Black & Decker Inc Slip clutch for rotary power tool
US20050274534A1 (en) * 2004-06-11 2005-12-15 Stefan Goetzfried Percussive power tool with flushing head
US20070181322A1 (en) * 2003-10-03 2007-08-09 Hansson Gunnar C Power tool with angle drive and pinion adjustment
EP1834736A1 (fr) * 2006-03-18 2007-09-19 Metabowerke GmbH Outil à main électrique
US20080210448A1 (en) * 2007-03-02 2008-09-04 Andre Ullrich Hand power tool
US20090129876A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-speed drill and transmission with low gear only clutch
US20090126957A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-mode drill with mode collar
US20090126956A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-mode hammer drill with shift lock
US20090126958A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-mode drill and transmission sub-assembly including a gear case cover supporting biasing
US20100084151A1 (en) * 2006-12-14 2010-04-08 Axel Kuhnle Electrical device with locked-on rotatable operating element
US7735575B2 (en) 2007-11-21 2010-06-15 Black & Decker Inc. Hammer drill with hard hammer support structure
US7770660B2 (en) 2007-11-21 2010-08-10 Black & Decker Inc. Mid-handle drill construction and assembly process
US7798245B2 (en) 2007-11-21 2010-09-21 Black & Decker Inc. Multi-mode drill with an electronic switching arrangement
CN103213103A (zh) * 2012-01-19 2013-07-24 南京德朔实业有限公司 紧固件工具
US20140190715A1 (en) * 2013-01-09 2014-07-10 Techtronic Power Tools Technology Limited Tool with rotatable head
US20150075830A1 (en) * 2011-12-28 2015-03-19 Positec Power Tools (Suzhou) Co., Ltd. Power tools
US9333637B2 (en) 2012-01-19 2016-05-10 Chevron (Hk) Limited Multi-tool for fasteners
CN105570333A (zh) * 2014-10-17 2016-05-11 楚天科技股份有限公司 半自动离合装置
US10260286B2 (en) * 2016-04-13 2019-04-16 Ningbo Ngp Industry Co., Ltd. Impact ice driller
US20210053806A1 (en) * 2019-08-21 2021-02-25 Rexon Industrial Corp., Ltd. Overload protection mechanism for winch
US20230086336A1 (en) * 2020-03-03 2023-03-23 Hilti Aktiengesellschaft Apparatus for adjusting a chisel

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3125454A1 (de) * 1981-06-29 1983-01-20 Hilti AG, 9494 Schaan Bohrhammer fuer bohr- und schlagbohrbetrieb
FI78158C (fi) * 1986-05-09 1989-06-12 Tampella Oy Ab Anordning vid en borrmaskin foer lagring av ett rotationsstycke.
CN103213107B (zh) * 2012-01-19 2015-12-02 南京德朔实业有限公司 紧固件工具的输出装置
DE102016224862A1 (de) * 2016-12-13 2018-06-14 Robert Bosch Gmbh Bohr- und/oder Meißelhammer
CN112593848B (zh) * 2020-12-24 2023-02-10 成都迪普金刚石钻头有限责任公司 一种pdc钻头复合冲击装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US720319A (en) * 1901-10-18 1903-02-10 William A Box Drill apparatus for drilling rock, mining, &c.
US875869A (en) * 1906-09-14 1908-01-07 Rolland S Trott Rock-drill.
US3323601A (en) * 1965-01-18 1967-06-06 Wacker Hermann Boring and breaking hammer with combustion engine or electromotor drive
US3334694A (en) * 1965-01-12 1967-08-08 Milwaukee Electric Tool Corp Rotary hammer
US3463246A (en) * 1966-12-28 1969-08-26 Metabowerke Kg Rotary percussive power tool with changeable drive
US3650336A (en) * 1970-05-05 1972-03-21 Rockwell Mfg Co Power driven device
US3720269A (en) * 1969-12-22 1973-03-13 Bosch Gmbh Robert Portable torque and impulse transmitting machine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO131358C (fr) * 1969-08-04 1975-05-14 Rockwell Mfg Co

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US720319A (en) * 1901-10-18 1903-02-10 William A Box Drill apparatus for drilling rock, mining, &c.
US875869A (en) * 1906-09-14 1908-01-07 Rolland S Trott Rock-drill.
US3334694A (en) * 1965-01-12 1967-08-08 Milwaukee Electric Tool Corp Rotary hammer
US3323601A (en) * 1965-01-18 1967-06-06 Wacker Hermann Boring and breaking hammer with combustion engine or electromotor drive
US3463246A (en) * 1966-12-28 1969-08-26 Metabowerke Kg Rotary percussive power tool with changeable drive
US3720269A (en) * 1969-12-22 1973-03-13 Bosch Gmbh Robert Portable torque and impulse transmitting machine
US3650336A (en) * 1970-05-05 1972-03-21 Rockwell Mfg Co Power driven device

Cited By (53)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4044845A (en) * 1975-03-03 1977-08-30 Hilti Aktiengesellschaft Drilling tool with a two part input unit
US4158970A (en) * 1977-06-15 1979-06-26 Black & Decker Inc. Override arrangement and actuating knob for a shifting mechanism in portable tools
US4236588A (en) * 1977-06-27 1980-12-02 Hilti Aktiengesellschaft Hammer drill with a lockable tool holder
US4239143A (en) * 1979-05-21 1980-12-16 Olin Corporation Driver assembly for small-diameter fasteners
US4408668A (en) * 1980-02-20 1983-10-11 Koehring Gmbh Impact transfer device for power rams
DE3231902A1 (de) * 1982-08-27 1984-03-22 Robert Bosch Gmbh, 7000 Stuttgart Kraftangetriebene handwerkzeugmaschine fuer schlagende oder drehschlagende arbeitsweise
US5050687A (en) * 1988-09-23 1991-09-24 Prokhorov Ivan A Compression-vacuum action percussive machine
US5161624A (en) * 1990-03-19 1992-11-10 Hilti Aktiengesellschaft Tool for driving fastening elements into hard receiving materials
US5871059A (en) * 1995-02-28 1999-02-16 Makita Corporation Mechanism for preventing idling strikes in power-driven striking tools
DE19654832A1 (de) * 1996-12-23 1998-06-25 Black & Decker Inc N D Ges D S Betätigungselement
US6116352A (en) * 1998-03-10 2000-09-12 Robert Bosch Gmbh Drilling and/or percussion power tool
US20070181322A1 (en) * 2003-10-03 2007-08-09 Hansson Gunnar C Power tool with angle drive and pinion adjustment
US7963346B2 (en) * 2003-10-03 2011-06-21 Atlas Copco Tools Ab Power tool with angle drive and pinion adjustment
GB2407851A (en) * 2003-11-06 2005-05-11 Black & Decker Inc Slip clutch for rotary power tool
US20050274534A1 (en) * 2004-06-11 2005-12-15 Stefan Goetzfried Percussive power tool with flushing head
US7252155B2 (en) * 2004-06-11 2007-08-07 Hilti Aktiengesselschaft Percussive power tool with flushing head
CN101036983B (zh) * 2006-03-18 2013-01-23 梅塔波沃克有限公司 手持式电动工具机
EP1834736A1 (fr) * 2006-03-18 2007-09-19 Metabowerke GmbH Outil à main électrique
US8327948B2 (en) * 2006-03-18 2012-12-11 Guenther Stark Electrical hand tool device
US20070215369A1 (en) * 2006-03-18 2007-09-20 Metabowerke Gmbh Electrical hand tool device
US20090126959A1 (en) * 2006-03-18 2009-05-21 Guenther Stark Electrical Hand Tool Device
US20100084151A1 (en) * 2006-12-14 2010-04-08 Axel Kuhnle Electrical device with locked-on rotatable operating element
US7891438B2 (en) * 2007-03-02 2011-02-22 Robert Bosch Gmbh Hand power tool
US20080210448A1 (en) * 2007-03-02 2008-09-04 Andre Ullrich Hand power tool
US7987920B2 (en) 2007-11-21 2011-08-02 Black & Decker Inc. Multi-mode drill with mode collar
US20090129876A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-speed drill and transmission with low gear only clutch
US7735575B2 (en) 2007-11-21 2010-06-15 Black & Decker Inc. Hammer drill with hard hammer support structure
US7762349B2 (en) 2007-11-21 2010-07-27 Black & Decker Inc. Multi-speed drill and transmission with low gear only clutch
US7770660B2 (en) 2007-11-21 2010-08-10 Black & Decker Inc. Mid-handle drill construction and assembly process
US20100206591A1 (en) * 2007-11-21 2010-08-19 Black & Decker Inc. Multi-mode drill with mode collar
US7798245B2 (en) 2007-11-21 2010-09-21 Black & Decker Inc. Multi-mode drill with an electronic switching arrangement
US20100300714A1 (en) * 2007-11-21 2010-12-02 Trautner Paul K Multi-mode drill with an electronic switching arrangement
US7854274B2 (en) 2007-11-21 2010-12-21 Black & Decker Inc. Multi-mode drill and transmission sub-assembly including a gear case cover supporting biasing
US7717191B2 (en) 2007-11-21 2010-05-18 Black & Decker Inc. Multi-mode hammer drill with shift lock
US20090126958A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-mode drill and transmission sub-assembly including a gear case cover supporting biasing
US20090126956A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-mode hammer drill with shift lock
US8109343B2 (en) 2007-11-21 2012-02-07 Black & Decker Inc. Multi-mode drill with mode collar
US8292001B2 (en) 2007-11-21 2012-10-23 Black & Decker Inc. Multi-mode drill with an electronic switching arrangement
US20090126957A1 (en) * 2007-11-21 2009-05-21 Black & Decker Inc. Multi-mode drill with mode collar
US7717192B2 (en) 2007-11-21 2010-05-18 Black & Decker Inc. Multi-mode drill with mode collar
US8555998B2 (en) 2007-11-21 2013-10-15 Black & Decker Inc. Multi-mode drill with mode collar
US20150075830A1 (en) * 2011-12-28 2015-03-19 Positec Power Tools (Suzhou) Co., Ltd. Power tools
US9821430B2 (en) * 2011-12-28 2017-11-21 Positec Power Tools (Suzhou) Co., Ltd. Power tools
CN103213103A (zh) * 2012-01-19 2013-07-24 南京德朔实业有限公司 紧固件工具
CN103213103B (zh) * 2012-01-19 2015-07-15 南京德朔实业有限公司 紧固件工具
US9333637B2 (en) 2012-01-19 2016-05-10 Chevron (Hk) Limited Multi-tool for fasteners
US20140190715A1 (en) * 2013-01-09 2014-07-10 Techtronic Power Tools Technology Limited Tool with rotatable head
US9956676B2 (en) * 2013-01-09 2018-05-01 Techtronic Power Tools Technology Limited Tool with rotatable head
CN105570333A (zh) * 2014-10-17 2016-05-11 楚天科技股份有限公司 半自动离合装置
CN105570333B (zh) * 2014-10-17 2018-06-29 楚天科技股份有限公司 半自动离合装置
US10260286B2 (en) * 2016-04-13 2019-04-16 Ningbo Ngp Industry Co., Ltd. Impact ice driller
US20210053806A1 (en) * 2019-08-21 2021-02-25 Rexon Industrial Corp., Ltd. Overload protection mechanism for winch
US20230086336A1 (en) * 2020-03-03 2023-03-23 Hilti Aktiengesellschaft Apparatus for adjusting a chisel

Also Published As

Publication number Publication date
FR2216050A1 (fr) 1974-08-30
CH582302A5 (fr) 1976-11-30
DE2404968A1 (de) 1974-08-15
CA1006718A (en) 1977-03-15
BR7400760D0 (pt) 1974-10-29
FR2216050B1 (fr) 1977-09-16
GB1451258A (en) 1976-09-29

Similar Documents

Publication Publication Date Title
US3866692A (en) Power tools
US3650336A (en) Power driven device
US3847229A (en) Portable impact wrench
US4236588A (en) Hammer drill with a lockable tool holder
US3828863A (en) Combined portable electric impact wrench and chipping hammer
US3837409A (en) Rotary hammer power tool
US5653294A (en) Impact mechanism for a hammer drill
US3685594A (en) Rotary hammer or the like
US3867988A (en) Power tools
US7383893B2 (en) Electric hammer drill
US6223833B1 (en) Spindle lock and chipping mechanism for hammer drill
EP1832393B1 (fr) Machine-outil
US3305031A (en) Power hammer
DE60302283D1 (de) Bohrhammer mit Überlastkupplung
GB2424249A (en) Power tool with overload clutch mounted in cavity in gear-cog
JP2004276227A (ja) 動力式工具
US7296635B2 (en) Rotary hammer with mode change ring
US3585817A (en) Adjustable clutch construction
US3463246A (en) Rotary percussive power tool with changeable drive
US11318596B2 (en) Power tool having hammer mechanism
US3876014A (en) Rotary hammer with rotation stop control trigger
US3170523A (en) Rotary hammer
US3269466A (en) Impact tool
US3845826A (en) Rotary disconnect for a rotary hammer tool
GB2102718A (en) Improvements in or relating to rotary percussive drills