US3828863A - Combined portable electric impact wrench and chipping hammer - Google Patents

Combined portable electric impact wrench and chipping hammer Download PDF

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Publication number
US3828863A
US3828863A US00376935A US37693573A US3828863A US 3828863 A US3828863 A US 3828863A US 00376935 A US00376935 A US 00376935A US 37693573 A US37693573 A US 37693573A US 3828863 A US3828863 A US 3828863A
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United States
Prior art keywords
tool holder
shaft
power tool
torque
torque transmitting
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
US00376935A
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English (en)
Inventor
W Schmid
K Wanner
R Hahner
G Hansel
M Bleicher
J Falchle
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F16H37/16—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types with a driving or driven member which both rotates or oscillates on its axis and reciprocates
    • 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
    • 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
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
    • B25D17/084—Rotating chucks or sockets
    • B25D17/088—Rotating chucks or sockets with radial movable locking elements co-operating with bit shafts specially adapted therefor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of 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
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0015—Tools having a percussion-only mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of 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
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/003—Details relating to chucks with radially movable locking elements
    • B25D2217/0038—Locking members of special shape
    • B25D2217/0042—Ball-shaped locking members

Definitions

  • Cl 173/48, 173/109, 1177330111282 is disengaged the user can rotate the tool holder at one of several speeds by way of the second transmis- [511 i Eozd 7/02 Ezlb 5/00 E216 3/02 sion.
  • the second transmission can drive the tool [58] Field of Search 173/48 47 holder at a selected speed while the clutch is engaged 'so that the tool holder moves axially and rotates about [56] References Cited its axis.
  • the second transmission embodies or is com- UNITED STATES PATENTS bined with a safety clutch which is disengaged when 3,114,423 12/ 1 3 Na lun 17 /48 X the tool holder offers excessive resistance to rotation.
  • PAIENIEDAUBWB f 3.828.863 sumu nrs I I Fig. 6
  • the present invention relates to portable power tools in general, especially to electrically operated power tools, and more particularly to improvements in multiple-purpose portable power tools. Still more particularly, the invention relates to improvements in portable power tools of the type wherein a holder for a screwdriver, chisel, drill or another material removing or material penetrating tool is movable axially and is also rotatable about its axis.
  • a presently known combined portable impact wrench and chipping hammer which is disclosed in Swiss Pat. No. 507,066 comprises a tool holder which can receive axial impulses from a pneumatic impeller and can be rotated at a single speed by way of a transmission which receives torque from the rotary output member of the prime mover.
  • the transmission is a stepdown transmission and the output shaft of the prime mover further serves to actuate the impeller.
  • a drawback of the just described power tool is that the tool holder can only be rotated at a single speed and that the impeller cannot be deactivated when the prime mover rotates its output member. This limits the utility of the power tool, i.e., the latter can be put to a very limited number of uses especially since it is not provided with means for permitting the attachment of a variety of differently dimensioned material removing or material penetrating tools.
  • U.S. Pat. No. 3,500,696 discloses a portable electric drill wherein the tool holder cannot move axially but can be rotated at two different speed. The utility of this power tool is also limited due to the absence of an impeller mechanism for the tool holder.
  • An object of the invention is to provide a portable power tool which is more versatile than presently known portable power tools because it can be readily converted from use as an impact wrench or the like, to use as a chipping hammer or the like, or to use as a simple power drill or the like.
  • Another object of the invention is to provide a portable power tool of the just outlined character which can be converted from one type of operation to a selected other type of operation while in actual use, which can rotate a tool at several speeds, and which embodies novel and improved safety features to prevent damage to its parts and/or an injury to the user.
  • a further object of the invention is to provide novel and improved means of transmitting motion from the prime mover to the axially movable rotary tool holder of a combined chipping hammer and impact wrench.
  • An additional object of the invention is to provide a portable power tool with a novel and improved multispeed transmission for rotating the tool holder.
  • Still another object of the invention is to provide a portable power tool with novel and improved control means for changing the speed ratio of and for deactivating the just outlined transmission.
  • the invention is embodied in a portable'power tool, particularly in a combined electric impact wrench and chipping hammer, which comprises a housing, a prime mover (preferably an electric motor) mounted in the housing and having a rotary output member, a tool LII holder which is rotatably and axially movably mounted in the housing and has'means for removably supporting a chisel, drill or another material penetrating and/or removing tool, impeller means (preferably operating with a cushion of compressed gaseous fluid) which is mounted in the housing and is actuatable to transmit to the tool holder recurring axial impluses, first transmission means which is mounted in the housing and has an input element receiving torque from the output member of the prime mover, a mobile output element for actuating the impeller means, and clutch means for moving the output element in response to rotation of the input element, first control means for disengaging the clutch means at the will of the operator to thereby deactivate the impeller means while the prime mover is free to rotate
  • a safety clutch which can form part of the second transmission means and serves to disconnect the prime mover from the tool holde when the latter offers excessive resistance to rotation, even when the second control means has been actuated by the operator to assume a position corresponding to one of the several speed ratios of the second transmission means.
  • FIG. 1 is a fragmentary longitudinal vertical sectional view of a portable power tool which embodies one form of the invention.
  • FIG. 2 is a sectional view as seen in the direction of arrows from the line II-II of FIG. 1;
  • FIG. 3 is a fragmentary sectional view as seen in the direction of arrows from the line III-III of FIG. 2;
  • FIG. 4 is a fragmentary partly elevational and partly longitudinal vertical sectional view of a second portable power tool
  • FIG. 5 is a fragmentary longitudinal vertical sectional view of a third power tool
  • FIGS. 1 to 3 there is shown a spadehandle portable power tool which can be used as a chipping hammer and/or as an impact wrench.
  • the housing of the power tool comprises a front section 1, a median section 2 and a rear section 3 which latter is with a spade handle 3a (only partially shown).
  • the housing sections 1,2 and 3 are separably connected to each other by means of suitable bolts, screws or analogous fasteners, not shown.
  • the lower portion of the median housing section 2 receives a prime mover here shownas an electric motor 4 whose rotor 5 is connected with an output shaft 6 which is mounted in antifriction bearings provided therefor in the front and median housing-sections 1 and 2.
  • the front end portion of the output shaft 6 is rotatable in a front antifriction bearing 7 having roller-shaped rolling elements and being located in front of a fly wheel 6a.
  • the rear portion of the output shaft 6 is rotatable in a rear antifriction bearing 8 having spherical rolling elements.
  • the rearmostportion of the output shaft 6 constitutes or is rigidly connected to a pinion or gear 9 which is in mesh with a gear 11 secured to an intermediate shaft 10.
  • the front end portion of the intermediate shaft 10 is rotatable in a first antifriction bearing 10a which is mounted in an internal partition 2a of the section 2.
  • the rear portion of the intermediate shaft 10 is rotatable in a second antifriction bearing 1012 which is installed in a portion 3b of the rear housing section 3. That portion of the intermediate shaft 10 which extends between the front bearing 10a and the gear 11 carries a smaller gear 12 and a larger gear 13.
  • the gears 12 and 13 respectively mesh with a larger gear and a smaller gear 16 both rotatably mounted on a hollow shaft 14 which is rotatable in antifriction bearings 27 and 28 provided therefor in the housing section 2.
  • the gears 15 and 16 are immediately adjacent to each other and can be moved axially of the hollow shaft 14 by a shifter fork 17 shown in FIGS. 2 and 3.
  • the rear portion of the hollow shaft 14 is provided with an annulus of external torque receiving teeth 18 which can be moved into mesh with the internal torque transmitting teeth of the gear 15 or with the internal torquetransmitting teeth 21 of the gear 16.
  • the space 19 between the internal teeth 20 and 21 is wide enough to receive the external teeth 18 when the multi-speed transmission including the gears 12, 13, 15, 16 and hollow shaft 14 is in neutral position.
  • the sleeve 14 is provided with four equidistant external torque receiving teeth 18.
  • the shifter fork 17 for the gears 15 and 16 is recipro cable along a guide rod 22 (shown in FIGS. 2 and 3) which is mounted in the housing section 2,
  • the means for moving the shifter fork 17 lengthwise of the guide rod 22 comprises a substantially rectangular leaf spring 23 having two prongs 23a and 23b which flank an eccentric pin provided on a control shaft 24 having a portion extending from the housing section 2 immediately adjacent to the housing section 3 and being pro- .vided with a handle 26.
  • the handle 26 can be pivoted between three different positions including a lowerspeed setting of the multi-speed transmission, a higherspeed setting, and the aforementioned neutral position.
  • the shaft 24 extends substantially at right angles to a vertical portion or wall 2b of the intermediate housing section 2.
  • the parts 17 and 23-26 together constitute a control device which can be actuated by hand to select the speed and the neutral position of the transmission 9-16.
  • the rear antifriction bearing 28 for the hollow shaft 14 comprises roller-shaped rolling elements and the front antifiction bearing 27 for the hollow shaft 14 comprises spherical rolling elements.
  • the front bearing 27 is immediately adjacent to the front housing section 1.
  • An intermediate portion of the hollow shaft 14 between the bearings 27 and 28 is provided with several equidistant radially extending openings or cutouts 29 for spherical torque transmitting elements 30 forming part of a safety clutch.
  • the median portions of the torque transmitting elements 30 are normally held in the respective opening 29 by a pressure ring 31 which is biased forwardly by a strong helical spring 32 reacting against a retainer 33 which abuts against an external shoulder of the hollow shaft 14 in front of the rear bearing 28.
  • the front side of the pressure ring 31 is provided with two mutually inclined outwardly and forwardly flaring conical surfaces 34 and 34a.
  • the outermost portion of the spherical torque transmitting elements 30 are engaged by the inner conical surface 34, their innermost portions are caused to extend inwardly beyond the respective openings 29 so that they extend into axially parallel flutes 35 provided in a sleeve 36.
  • the outer conical surface 34a of the pressure ring 31 tapers to a greater extent that the inner conical surface 34 (i.e., the conical surface 34a makes with the axis of the hollow shaft 14 an acute angle which is larger than the actue angle between the axis of the shaft 14 and the inner conical surface 34) so that the surface 34a enables the torque transmitting elements 30 to move radially outwardly and to thereby abruptly disconnect the sleeve 36 from the hollow shaft 14 in response to a predetermined resistance which the rotary and axially movable tool holder 37 of the power tool offers to rotation.
  • the tool holder 37 has a rearwardly extending portion or shank 37a provided with axially parallel external grooves or flutes 39 for portions of balls 38 which are mounted in radially extending openings of the sleeve 36.
  • the balls 38 compel the sleeve 36 to rotate with the tool holder 37 or vice versa while the flutes 39 allow the shank 37a to move axially relative to the sleeve 36.
  • the front portion of the tool holder 37 is provided with internal threads 37b which can mesh with the external threads of a suitable tool T (see FIG. 4) such as a chisel, screwdriver or the like.
  • a first sealing ring 40 is interposed between the foremost portion of the sleeve 36 and the front housing section 1.
  • a second sealing element 41 is received in an internal groove of the sleeve 36 and engages the peripheral surface of the shank 37a.
  • the foremost portion of the sleeve 36 is further provided with a flange or collar 42 having an annulus of teeth 43 separated by axially parallel grooves each of which can receive a projection 45 provided on a transverse blocking shaft 44 which is rotatably mounted in the front housing section 1.
  • a portion of the blocking shaft 44 extends outwardly from the housing section 1 and is provided with a handle (not shown) similar to the handle 26 of FIG. 2 to enable an operator to move the projection 45 into or from engagement with the adjacent teeth 43 of the collar 42.
  • the multi-speed transmission 9-16 can rotate the tool holder 37 at two different speeds. Furthermore, and as explained above, the handle 26 of the control device 17, 23-26 can be moved to a position corresponding to the neutral position of the multi-speed transmission in which position the gears 15 and 16 can rotate relative to thehollow shaft 14 so that the tool holder 37 can be held by the projection 45 of the blocking shaft 44 against angular movement.
  • the wall 21; of the housing section 2 can be provided with indicia to facilitate the solution of a desired position for the handle 26. Analogous indicia (e.g., ON" and OFF can be provided on the front housing section 1 adjacent to the handle for the blocking shaft 44.
  • THe power tool of FIGS. 1 to 3 further comprise a second transmission serving to actuate at the will of the operator a pneumatic impeller which is installed in the hollow shaft 14 and is adapted to transmit to the shank 37a of the tool holder 37 recurrent axial impulses in a direction to the left, as viewed in FIG. 1, to thereby drive the top of a tool which is removably connected to the holder 37 by threads 37b into a workpiece, such as a piece of concrete, wood, brick or the like.
  • the impeller comprises a cylinder 61 which is movable axially in the interior of the hollow shaft 14 and receives a piston or plunger 62 which is adjacent to the rear end of the shank 37a. When the cylinder 61 is caused to move forwardly, the cushion of compressed air in its chamber 61a urges the piston 62 forwardly and causes it to strike against the rear end of the shank 37a.
  • the aforementioned transmissioned which serves to reciprocate the cylinder 61 of the impeller 61, 62 comprises an input element in the form of a bevel gear 46 which is secured to the intermediate shaft 10 adjacent to the gear 11 and is in permanent mesh with a second bevel gear 48 mounted on a hollow clutch shaft 47.
  • the shaft 47 is normal to the intermediate shaft 10 and has radially extending opening 51' for spherical torque transmitting elements 51 portions of which extend into axially parallel internal grooves or recesses 52 of the bevel gear 48 when the positive clutch including the hollow shaft 47, bevel gear 48 and spherical elements 51 is engaged.
  • Portions of the spherical elements 51 are normally held in the grooves or recesses 52 by a conical shoulder of a displacing member or bolt 54 which is movable axially in the hollow shaft 47 between the illustrated operative position and an inoperative position and is biased to the operative position of FIG. 1 by a helical spring 53 which reacts against an internal shoulder of the hollow shaft 47.
  • the control means for engaging or disengaging the positive clutch including the spherical elements 51 comprises a shaft 55 having an eccentric pin 56 which can move displacing member or bolt 54 upwardly, as viewed in FIG. 1, against the opposition of the spring 53 whereby the bolt 54 assumes its inoperative position and maintains its groove 57 in register with the spherical elements 51.
  • the upper end of the hollow shaft 47 carries a disk 58 provided with an eccentric pin 59 for a connecting rod 60 which constitutes a mobile output element of the transmission for the pneumatic impeller 61, 62 and is coupled to the cylinder 61 by a pin 60a.
  • the hollow shaft 47 is rotatable in a first antifriction bearing 49 provided therefor in the portion 3b of the rear housing section 3 below the disk 58, and in a second antifriction bearing 50 installed in the housing section 3 above the bevel gear 48.
  • the shaft 55 for the eccentric pin 56 extends from the housing section 3 and is provided with a handle (not shown) similar to the handle 26 of FIG. 2 which enables the operator to engage or disengage the positive clutch between the disk 58 and the bevel gear 46.
  • the piston 62 of the pneumatic impeller for the tool holder 37 is received in the cylinder 61 with minimal clearance.
  • the hollow shaft 14 can rotate about the cylinder 61.
  • the connecting rod 60 reciprocates the cylinder 61 and the piston 62 transmits recurrent axial impulses to the shank 37a so that the tip of a tool which is removably mounted in the holder 37 can be driven into a workpiece, such as a block of concrete or rock.
  • the projection 45 is first disengaged from the collar 42 and the shaft 24 for the eccentric pin 25 is rotated in a clockwise direction, as
  • the balls 38 rotate the shank 37a but the shank remains free to move axially under the action of the piston 62 and counter to such action when the connecting rod 60 retracts the cylinder 61.
  • the shank 37a moves rearwardly when the cylinder 61 moves rearwardly because the operator pushes the housing forwardly by way of the spade handle 3a.
  • the tool holder 37 offers excessive resistance to rotation with the hollow shaft 14.
  • the safety clutch including the spherical elements 30 then disengages the sleeve 36 from the hollow shaft 14 so that the shaft 14 can rotate with the gear 15 while the sleeve 36 and the tool holder 37 cease to rotate but the tool holder 37 remains free to move axially.
  • the pressure ring 31 of the safety clutch offers a relatively high resistance to axial movement in a direction toward the retainer 33 as long as the spherical elements 30 are engaged by its inner conical surface 34; however, once the resistance which the shank 37a offers to rotation increases to such an extent that the spherical elements 30 are partially expelled from the flutes 35 of the sleeves 36, they can rapidly travel along the outer'conical surface 34a to thus insure that the safety clutch is disengaged practically instantaneously orabruptly. This is desirable in order to avoid damage to or excessive wear upon the parts of the power tool.
  • the retainer 33 can be adjusted axially of the hollow shaft 14 to thereby select the exact resistance which the sleeve 36 must offer to rotation before the safety clutch is disengaged.
  • the spherical elements 30 are urged radially outwardly by the axially parallel ribs which separate the flutes 35 of the sleeve 36 from each other.
  • leaf spring 23 shown in FIG. 3 it enables the torque transmitting teeth or 21 of the gear 15 or 16 to move into mesh with the torque receiving teeth 18 of the hollow shaft 14 as soon as the teeth 18 move into register with the spaces between the teeth 20 or 21.
  • the shaft 24 is rotated clockwise or counterclockwise, as viewed in FIG. 3, at a time when the teeth 18 do not register with the spaces between the teeth 20 or 21, the corresponding prong 23b or 23a of the leaf spring 23 is deformed so that the spring 23 stores energy and is ready to propel the gears 15 and 16 axially of the hollow shaft 14 as soon as the spaces between the teeth 20 or 21 move into register with the teeth 18.
  • the gears 15 and 16 are rotated continuously by the gears 12 and 13 whenever the motor 4 is on.
  • the gears 15 and 16 are shifted in a direction to the left, as viewed in FIG. 1, so that .the torque receiving teeth 18 of the hollow shaft 14 move into mesh with the torque transmitting teeth 21 of the smaller gear 16 which is driven by the larger gear 13 of the intermediate shaft 10.
  • the shifting from higher to lower speed ratio, or vice versa, as well as from higher lower speed ratio to neutral position of the multi-speed transmission 9-16 can be effected while the motor 4 is on. It will be noted that the provision of the two control devices including the shafts 55 and 24 enables the operator to impart to the tool holder 37 axial impulses while the tool holder rotates or while thetool holder is held against rotation.
  • the operator can decide to disengage the positive clutch between the bevel gear 46 and disk 58 of the transmission for the pneumatic impeller 61, 62 and to thereupon drive the tool holder 37 at the higher or lower speed so that the tool holder 37 rotates but does not perform any axial movements.
  • the positive clutch can be disengaged while the hollow shaft 14 rotates at a selected speed.
  • the tool holder 37 can accept a variety of different tools as well one or more adapters which enable it to accept further types or sizes of tools. This enhances the versatility of the power tool.
  • the portable power tool of FIG. 4 employs a modified positive clutch between the input element 60 and the output element 60 of the transmission for the pneumatic impeller including the cylinder 61 and piston 62.
  • This clutch is a claw clutch having an annulus of claws 67 on the right-hand (rear end face of the input element 66 (which corresponds to the gear 11 of FIG. 1 but is movable axially of the intermediate shaft 65) and an annulus of complementary claws 68 on the left-hand end face of a bevel gear 69 which is rotatable on the intermediate shaft 65.
  • the control means for engaging and disengaging the claws 67 and 68 comprises a suitable shifter having a handgrip portion 66a (indicated by broken lines) which extends from the housing of the power tool so that it can be manipulated by hand.
  • the bevel gear 69 is in permanent mesh with a bevel gear 69a which replaces the disk 58 of FIG. 1 and carries the pin 59 for the output element or connecting rod 60.
  • the bevel gear 69a is secured to a shaft 69b which is rotatable in antifriction bearings provided therefor in the rear housing section 3.
  • the intermediate shaft 65 is rotatable in two axially spaced antifriction bearings 65a, 65b having rollershaped rollings elements.
  • the construction of the multi-speed transmission which rotates the tool holder for the tool T is identical with that of the multi-speed transmission 9-16 of FIG. 1.
  • the control means 66a can be manipulated to engage or disengage the positive claw clutch 67, 68 while the multi-speed transmission is in neutral position or while the multi-speed transmission rotates the tool T at a selected speed.
  • the speed ratio of the multi-speed transmission can be changed or the multispeed transmission can be shifted to neutral while the claws 67 engage the claws 68.
  • FIG. 5 illustrates a portion of a third portable power tool which comprises modified control means for changing the speed ratio of the multi-speed transmission for the tool holder.
  • the intermediate shaft 10 carries two gears 12, 13 which'respectively mesh with gears 72 and 73, both freely rotatable on the hollow shaft 14.
  • the gears 72, 73 are respectively analogous to the gears 15, 16 of FIGS. 1 and 3.
  • the gears 72 and 73 are mounted on a cylindrical or sleevelike shifter 74 which is movable axially of the shaft 14.
  • the shifter 74 is provided with an annulus of external torque receiving teeth or projections 75 and serves to rotate the shaft 14'.
  • the teeth 75 are functional equivalents of teeth 18 on the shaft 14 of FIG. 1 and can be moved into mesh with internal torque transmitting teeth or projections 76 of the gear 72 or with internal torque transmitting teeth or projections of the gear 73, depending upon whether the user of the power tool wishes to drive the tool holder at a lower or higher speed.
  • the control means for moving the shifter 74 axially of the shaft 14' is preferably similar to or identical with the control means 17, 23, 24, 25, 26 of FIGS. 2 and 3.
  • the gears 72, 73 are held against axial movement.
  • the internal teeth 76 and 77 of the gears 72, 73 are separated from each other by a ring-shaped space 78 which is wide enough to accommodate the external teeth 75 of the shifter 74 when the user of the power tool wishes to maintain the multi-speed transmission for the tool holder in neutral position.
  • the portable power tool of FIG. 6 comprises a third embodiment of a disengageable positive clutch between the input element 46 and the output element 60 of the transmission for the pneumatic impeller 61, 62.
  • the clutch comprises a shaft 81 which carries at its upper end a disk 82 for the eccentric pin 59 and can receive torque from a sleeve-like clutch element 83 which is axially movably mounted thereon and is biased downwardly, as viewed in FIG. 6, by a helical spring 81a. The latter reacts against the inner race of an antifriction bearing 81b for the upper portion of the shaft 81.
  • the lower end face of the clutch element 83 carries an annulus of claws 84 which can be moved into mesh with similar claws 85 provided on the upper end face of a bevel gear 86 which is in permanent mesh with the bevel gear 46. The latter is secured to the intermediate shaft 10.
  • the clutch element 83 can be shifted axially by control means similar to that including the parts 17, 23, 24, 25, 26 shown in FIGS. 2 and 3.
  • the construction of the multi-speed transmission for the tool T is identical with that of the multi-speed transmission shown in FIGS. 1 to 3.
  • FIG. 7 illustrates a portable power tool which embodies a modified safety clutch for disengaging the tool holder 37 from the prime mover (not shown) when the tool holder offers excessive resistance to rotation with the hollow shaft 14".
  • the hollow shaft 14 is provided with axially parallel slots or openings 89 for rollershaped torque transmitting clutch elements 90 (only one shown) which extends into the adjacent flutes 35 of the sleeves 36 under the action of the spring 32.
  • the pressure ring 31 of FIG. 1 is replaced by two pressure rings 91, 92 the former of which abuts against a split ring 93 in a peripheral groove of the shaft 14".
  • the rear pressure'ring 92 is biased toward the pressure ring 91 by the spring 32.
  • the axes of the roller-shaped elements 90 are parallel with the axis of the hollow shaft 14".
  • Each of the pressure rings 91, 92 is provided with a conical surface (91a, 92a) into which a portion of each element 90 normally extends.
  • the pressure ring 92 yields and moves in a direction to the right to further stress the spring 32 when the sleeve 36 offers excessive resistance to rotation with the shaft 14". This allows the shaft 14 to rotate relative to the sleeve 36 and tool holder 37 but the parts of the power tool cannot be damaged because the tool ceases to rotate.
  • the construction of the power tool of FIG. 7 is identical with that of one of the power tools shown in FIG. 1, '4, or 6.
  • FIGS. 4 and 7, 5 and 7 or 6 and 7 can be incorporated in a single power tool.
  • a portable power tool particularly a combined electric impact wrench and chipping hammer, comprising a housing; a prime mover mounted in said housing and having a rotary output member; a tool holder rotatably and axially movably mounted in said housing; impeller means mounted in said housing and actuatable to transmit to said tool holder recurring axial impulses; first transmission means mounted in said housing and having an input element receiving torque from said output member, a mobile output element for actuating said impeller means, and clutch means for moving said output element in response to rotation of said input element; first control means for disengaging said clutch means at the will of the operator; multispeed second transmission means mounted in said housing between said tool holder and said output member and having a plurality of different speed ratios and a neutral position; and second control means actuatable independently of said first control means to select the speed ratio or the neutral position of said second transmission means so that said tool holder is movable axially by said impeller means while said second transmission means is in said neutral position or drives said tool holder
  • said impeller means comprises a pneumatic cylinder and piston unit including a cylinder which is reciprocable by said output element of said first transmission means and a piston which is reciprocable in said cylinder and is arranged to impart said impulses to said tool holder.
  • a power tool as defined in claim I wherein said prime mover comprises an electric motor and said clutch means comprises a positive clutch.
  • said positive clutch comprises a hollow shaft arranged to transmit torque to said output element and having at least one opening, a torque transmitting element provided in said opening and movable between a first position in which it partly extends from said hollow shaft and is driven by said input element and a second position in the interior of said hollow shaft, and a displacing member movable in said shaft axially between an operative position in which said displacing member maintains said torque transmitting element in said first position and an inoperative position in which said torque transmitting element is free to assume said second position, said first control means being arranged to move said displacing member between said operative and inoperative positions.
  • said torque transmitting element is a sphere and said input element includes a gear having an internal recess which receives a portion of said sphere in said first position of said sphere, said displacing member comprising a bolt having a groove which receives a portion of said sphere in said second position of said sphere when said bolt assumes said inoperative position.
  • said positive clutch further comprises biasing means or permanently urging said bolt to one of said positions thereof and said first control means comprises an eccentric actuatable to move said bolt to the other of said positions against the opposition of said biasing means.
  • said positive clutch comprises a first annulus of claws driven by said input element and a second annulus of complementary claws arranged to move said output element, said first control means comprising means for moving one of said annuli of claws toward and away from the other annulus to thereby place the claws of said first annulus into and out of mesh with the claws of said second annulus.
  • said input element comprises a first gear which receives torque from said prime mover and said output element comprises or is movable by a second gear which is coaxial with said first gear one of said gears being movable axially toward and away from the other of said .gears and said first and second annuli of claws being respectively provided on said first and second gears and being located between said gears.
  • said positive clutch comprises a shaft which is arranged to drive said output element, a gear rotatably mounted on said shaft and receiving torque from said output member of said prime mover, a clutch element rotatable with and movable axially of said shaft toward and away from said gear, a first annulus of claws provided on said gear and facing said clutch element, and a second annulus of complementary claws provided on said clutch element and facing said gear, said first control means comprising means for moving said clutch element toward and away from said gear to thereby move said second annulus of claws into and from mesh with said first annulus of claws.
  • said second transmission means comprises a two-speed transmission including an intermediate shaft driven by said output member of said prime mover, a second shaft arranged to transmit torque to said tool holder, coaxial first and second gears rotatably mounted on said second shaft and being driven by said intermediate shaft at different speeds and respectively having first and second torque transmitting portions, and torque receiving means provided on said second shaft, said gears being movable axially of said second shaft and said second control means comprising shifter means actuatable to move said first or second torque transmit ting portion into engagement with said torque receiving means.
  • said second control means further comprises resilient means interposed between said eccentric and said shifter means so that said shifter means can move said gears axially when one of said first and second torque transmitting portions is ready to move into engagement with said torque receiving means of said second shaft.
  • said second transmission means comprises 'a' two-speed transmission including a first shaft driven by said output member of said prime mover, a second shaft arranged to drive said tool holder, a sleeve-like shifter movable axially of and rotatable with-said second shaft,
  • first and-second gears driven by said first shaft at different speeds and surrounding said shifter first and second torque transmitting portions respectively provided on said first and second gears, and torque receiving means provided on said shifter
  • said second control means comprising means for moving said shifter axially betweena first position in which said torque receiving means receives torque from said first torque transmitting portion, a second portion in which said torque receiving means receives torque from said second torque transmitting portion, and a third portion in which said torque receiving means is disengaged from said first and second torque transmitting portions.
  • said second control means comprises a manually operable eccentric for moving said shifter axially of said second shaft.
  • said second control means further comprises resilient means interposed between said shifter and said eccentric so that said shifter can move axially when said motion receiving means thereof registers with one of said first and second troque transmitting portions.
  • said safety clutch further comprises a sleeve arranged to rotate said tool holder and having a flute which normally receives a first portion of said torque transmitting element in said operative position thereof, said second transmission comprising a hollow shaft surrounding said flute and having a radial opening receiving a second portion of said torque transmitting element in said operative position thereof, said safety clutch further comprising a pressure transmitting member arranged to yieldably urge said torque transmitting element to said operative position and to permit said torque transmitting element to move to said inoperative position, in which latter position said first portion of said torque transmitting element is received in said opening, in response to said predetermined resistance of said tool holder to rotation with said shaft.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Boring (AREA)
US00376935A 1972-08-31 1973-07-06 Combined portable electric impact wrench and chipping hammer Expired - Lifetime US3828863A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2242944A DE2242944B2 (de) 1972-08-31 1972-08-31 Bohrhammer

Publications (1)

Publication Number Publication Date
US3828863A true US3828863A (en) 1974-08-13

Family

ID=5855161

Family Applications (1)

Application Number Title Priority Date Filing Date
US00376935A Expired - Lifetime US3828863A (en) 1972-08-31 1973-07-06 Combined portable electric impact wrench and chipping hammer

Country Status (10)

Country Link
US (1) US3828863A (hr)
JP (1) JPS5613596B2 (hr)
BR (1) BR7306718D0 (hr)
CH (1) CH560313A5 (hr)
DE (1) DE2242944B2 (hr)
ES (1) ES418342A1 (hr)
FR (1) FR2197680B1 (hr)
GB (1) GB1447867A (hr)
IT (1) IT993805B (hr)
NL (1) NL7311947A (hr)

Cited By (39)

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US3896888A (en) * 1973-04-05 1975-07-29 Kango Electric Hammers Ltd Electric hammer
US4114699A (en) * 1976-01-22 1978-09-19 Licentia Patent-Verwaltungs-Gmbh Pneumatic rotary hammer device
US4131165A (en) * 1976-04-28 1978-12-26 Robert Bosch Gmbh Hammer drill
US4276941A (en) * 1978-10-10 1981-07-07 Robert Bosch Gmbh Hand-held power tool
US4280359A (en) * 1974-10-16 1981-07-28 Robert Bosch Gmbh Rotary cam drive for impact tool
US4336847A (en) * 1980-06-27 1982-06-29 Hitachi Koki Company, Limited Percussion drill
US4366869A (en) * 1979-09-24 1983-01-04 Hilti Aktiengesellschaft Hammer drill
US4442906A (en) * 1980-11-18 1984-04-17 Black & Decker Inc. Percussive drills
US4446931A (en) * 1980-10-21 1984-05-08 Robert Bosch Gmbh Power driven hammer drill
US4487272A (en) * 1982-02-13 1984-12-11 Robert Bosch Gmbh Impacting drill
US4529044A (en) * 1983-03-28 1985-07-16 Hilti Aktiengesellschaft Electropneumatic hammer drill or chipping hammer
US4820962A (en) * 1986-10-31 1989-04-11 Hilti Aktiengesellschaft Arrangement for automatic working data set-up for driving implements
US4825961A (en) * 1985-07-29 1989-05-02 Hilti Aktiengesellschaft Drilling device
US5125461A (en) * 1990-04-27 1992-06-30 Black & Decker, Inc. Power tool
US5296768A (en) * 1991-11-14 1994-03-22 Hilti Aktiengesellschaft Revolutions per minute regulation device for a hand-held electric tool and method of its manufacture
US5373905A (en) * 1991-07-08 1994-12-20 Robert Bosch Gmbh Hammer drill
US5588496A (en) * 1994-07-14 1996-12-31 Milwaukee Electric Tool Corporation Slip clutch arrangement for power tool
US6015017A (en) * 1997-04-18 2000-01-18 Black & Decker Inc. Rotary hammer
US20030178211A1 (en) * 2002-03-23 2003-09-25 Andreas Stihl Ag & Co. Kg Portable drill having an internal combustion engine
US20040000414A1 (en) * 2002-04-11 2004-01-01 Karl Echtler Method of manufacturing a percussion mechanism of a hand-held power tool
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US20050284648A1 (en) * 2004-06-25 2005-12-29 Karl Frauhammer Device having a torque-limiting unit
US20060065417A1 (en) * 2004-09-30 2006-03-30 Hilti Aktiengesellschaft Drilling and/or chusel hammer
US20060137888A1 (en) * 2004-12-23 2006-06-29 Martin Soika Power tool
US20060201688A1 (en) * 2005-02-24 2006-09-14 Cheryl Jenner Hammer drill with a mode changeover mechanism
EP1726407A2 (en) 2005-05-26 2006-11-29 Matsushita Electric Works, Ltd. Hammer drill
US20070201748A1 (en) * 2006-02-03 2007-08-30 Black & Decker Inc. Housing and gearbox for drill or driver
CN100515687C (zh) * 2004-12-23 2009-07-22 百得有限公司 动力工具
US20090288851A1 (en) * 2008-05-26 2009-11-26 Max Co., Ltd. Driving tool
US20100000748A1 (en) * 2008-07-03 2010-01-07 Makita Corporation Hammer drill
US20100326689A1 (en) * 2006-12-27 2010-12-30 Gerhard Meixner Striking mechanism for a handheld electric power tool
US20110247848A1 (en) * 2008-12-16 2011-10-13 Robert Bosch Gmbh Hand-Held Power Tool
US20120261150A1 (en) * 2009-11-02 2012-10-18 Makita Corporation Power tool
CN104405793A (zh) * 2014-11-30 2015-03-11 重庆泽田汽车部件有限责任公司 一种保险离合器
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
CN108895120A (zh) * 2018-07-06 2018-11-27 甘肃省机械科学研究院有限责任公司 锥齿轮传动副啮合脱开装置
US20210114194A1 (en) * 2019-10-21 2021-04-22 Makita Corporation Power tool having hammer mechanism
US20220048177A1 (en) * 2020-08-12 2022-02-17 Robert Bosch Gmbh Hand-Held Power Tool
US20220362916A1 (en) * 2019-11-15 2022-11-17 Hilti Aktiengesellschaft Impact mechanism arrangement

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DE2709946C2 (de) * 1977-03-08 1982-12-23 Novopress GmbH Pressen und Presswerkzeuge & Co KG, 4000 Düsseldorf Tragbares Handwerkzeug
DE2757008C2 (de) * 1977-12-21 1982-04-01 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Pneumatischer Bohrhammer
DE2759136C2 (de) * 1977-12-30 1982-10-28 Wacker-Werke Gmbh & Co Kg, 8077 Reichertshofen Kurbeltrieb für motorisch angetriebene, schlagend wirkende Arbeitsgeräte
DE3028464A1 (de) * 1980-07-26 1982-03-18 C. & E. Fein Gmbh & Co, 7000 Stuttgart Tragbares schlagwerkzeug
JPS5783311A (en) * 1980-10-31 1982-05-25 Hitachi Koki Co Ltd Air-cushion-type impact tool
JPS5827554U (ja) * 1981-07-31 1983-02-22 トヨタ自動車株式会社 エンジンの減速時燃料制御装置
DE3319934A1 (de) * 1982-06-02 1983-12-15 Black & Decker, Inc. (eine Gesellschaft n.d.Ges.d. Staates Delaware), 19711 Newark, Del. Schlagbohrmaschine
GB2121717B (en) * 1982-06-02 1985-09-18 Black & Decker Inc Improvements in or relating to rotary percussive drills
DE3235544A1 (de) * 1982-09-25 1984-03-29 Robert Bosch Gmbh, 7000 Stuttgart Bohrhammer
JPS6176205A (ja) * 1984-09-25 1986-04-18 Matsushita Electric Works Ltd 振動ドリル
JPS6310296U (hr) * 1986-07-04 1988-01-23
DE3625535C2 (de) * 1986-07-29 1994-05-11 Festo Kg Exzentertellerschleifer
DE3633675A1 (de) * 1986-10-03 1988-04-14 Hilti Ag Bohrhammer mit schlagwerk
DE3634591A1 (de) * 1986-10-10 1988-04-14 Black & Decker Inc Bohrhammer mit einem luftpolsterschlagwerk
JPH0785842B2 (ja) * 1988-07-15 1995-09-20 松下電工株式会社 ハンマードリル
JPH0616963B2 (ja) * 1988-07-15 1994-03-09 松下電工株式会社 ハンマードリル
JPH0653327B2 (ja) * 1988-04-25 1994-07-20 松下電工株式会社 ハンマードリル
DE3821594A1 (de) * 1988-06-27 1989-12-28 Hilti Ag Motorisch betriebenes handwerkzeug
JPH0295582A (ja) * 1988-09-30 1990-04-06 Hitachi Koki Co Ltd インパクトドリル
DE4401664B4 (de) * 1994-01-21 2008-12-18 Robert Bosch Gmbh Bohrhammer mit einer elektronischen Regeleinrichtung und einem Betriebsartenschalter
DE102007062248A1 (de) * 2007-12-21 2009-06-25 Robert Bosch Gmbh Handwerkzeugmaschine mit einer, mindestens eine drehbar gelagerte Zwischenwelle umfassenden Getriebevorrichtung
DE102012214938B4 (de) * 2012-08-22 2016-11-10 Metabowerke Gmbh Getriebeanordnung für eine angetriebene Werkzeugmaschine sowie Werkzeugmaschine mit einer solchen Getriebeanordnung
CN104653711A (zh) * 2014-12-16 2015-05-27 天津市诚田丰金属制品有限公司 一种冲击钻的动力结构
JP2020119298A (ja) 2019-01-24 2020-08-06 キオクシア株式会社 メモリシステム
CN117571581B (zh) * 2024-01-16 2024-03-22 山西八建集团有限公司 建筑外墙渗水检测装置

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DE651027C (de) * 1934-11-07 1937-10-06 Union Handels Akt Ges Bisher S Schlag- und Bohrwerkzeug mit elektrischem Antrieb und zwei verschieden schnell umlaufenden Wellen
US3203490A (en) * 1963-06-27 1965-08-31 Black & Decker Mfg Co Compact rotary hammer
GB1195505A (en) * 1967-07-31 1970-06-17 Hilti Ag Hammer Drill
DE1948055A1 (de) * 1969-09-23 1971-04-01 Impex Essen Vertrieb Elektrisch betriebener Bohrhammer

Cited By (64)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3896888A (en) * 1973-04-05 1975-07-29 Kango Electric Hammers Ltd Electric hammer
US4280359A (en) * 1974-10-16 1981-07-28 Robert Bosch Gmbh Rotary cam drive for impact tool
US4456076A (en) * 1974-10-16 1984-06-26 Robert Bosch Gmbh Power-driven hand tool
US4537264A (en) * 1974-10-16 1985-08-27 Robert Bosch Gmbh Power-driven hand tool
US4114699A (en) * 1976-01-22 1978-09-19 Licentia Patent-Verwaltungs-Gmbh Pneumatic rotary hammer device
US4131165A (en) * 1976-04-28 1978-12-26 Robert Bosch Gmbh Hammer drill
US4276941A (en) * 1978-10-10 1981-07-07 Robert Bosch Gmbh Hand-held power tool
US4366869A (en) * 1979-09-24 1983-01-04 Hilti Aktiengesellschaft Hammer drill
US4336847A (en) * 1980-06-27 1982-06-29 Hitachi Koki Company, Limited Percussion drill
US4446931A (en) * 1980-10-21 1984-05-08 Robert Bosch Gmbh Power driven hammer drill
US4442906A (en) * 1980-11-18 1984-04-17 Black & Decker Inc. Percussive drills
US4487272A (en) * 1982-02-13 1984-12-11 Robert Bosch Gmbh Impacting drill
US4529044A (en) * 1983-03-28 1985-07-16 Hilti Aktiengesellschaft Electropneumatic hammer drill or chipping hammer
US4825961A (en) * 1985-07-29 1989-05-02 Hilti Aktiengesellschaft Drilling device
US4820962A (en) * 1986-10-31 1989-04-11 Hilti Aktiengesellschaft Arrangement for automatic working data set-up for driving implements
US5125461A (en) * 1990-04-27 1992-06-30 Black & Decker, Inc. Power tool
US5159986A (en) * 1990-04-27 1992-11-03 Black & Decker, Inc. Power tool
US5373905A (en) * 1991-07-08 1994-12-20 Robert Bosch Gmbh Hammer drill
US5296768A (en) * 1991-11-14 1994-03-22 Hilti Aktiengesellschaft Revolutions per minute regulation device for a hand-held electric tool and method of its manufacture
US5588496A (en) * 1994-07-14 1996-12-31 Milwaukee Electric Tool Corporation Slip clutch arrangement for power tool
US6015017A (en) * 1997-04-18 2000-01-18 Black & Decker Inc. Rotary hammer
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US20030178211A1 (en) * 2002-03-23 2003-09-25 Andreas Stihl Ag & Co. Kg Portable drill having an internal combustion engine
US20040000414A1 (en) * 2002-04-11 2004-01-01 Karl Echtler Method of manufacturing a percussion mechanism of a hand-held power tool
US20050284648A1 (en) * 2004-06-25 2005-12-29 Karl Frauhammer Device having a torque-limiting unit
US8136607B2 (en) * 2004-06-25 2012-03-20 Robert Bosch Gmbh Device having a torque-limiting unit
US20060065417A1 (en) * 2004-09-30 2006-03-30 Hilti Aktiengesellschaft Drilling and/or chusel hammer
US20060137888A1 (en) * 2004-12-23 2006-06-29 Martin Soika Power tool
CN100515687C (zh) * 2004-12-23 2009-07-22 百得有限公司 动力工具
US7306049B2 (en) * 2004-12-23 2007-12-11 Black & Decker Inc. Mode change switch for power tool
US7314097B2 (en) 2005-02-24 2008-01-01 Black & Decker Inc. Hammer drill with a mode changeover mechanism
US20060201688A1 (en) * 2005-02-24 2006-09-14 Cheryl Jenner Hammer drill with a mode changeover mechanism
US20060266536A1 (en) * 2005-05-26 2006-11-30 Matsushita Electric Works, Ltd. Hammer drill
EP1726407A3 (en) * 2005-05-26 2008-10-22 Matsushita Electric Works, Ltd. Hammer drill
EP1726407A2 (en) 2005-05-26 2006-11-29 Matsushita Electric Works, Ltd. Hammer drill
US7694750B2 (en) 2005-05-26 2010-04-13 Panasonic Electric Works Co., Ltd. Hammer drill
US7828074B2 (en) 2005-05-26 2010-11-09 Panasonic Electric Works Co., Ltd. Hammer drill
US20110220379A1 (en) * 2006-02-03 2011-09-15 Black & Decker Inc. Housing and gearbox for drill or driver
US10987793B2 (en) 2006-02-03 2021-04-27 Black & Decker Inc. Power tool with tool housing and output spindle housing
US9579785B2 (en) 2006-02-03 2017-02-28 Black & Decker Inc. Power tool with transmission cassette received in clam shell housing
US20070201748A1 (en) * 2006-02-03 2007-08-30 Black & Decker Inc. Housing and gearbox for drill or driver
US8205685B2 (en) 2006-02-03 2012-06-26 Black & Decker Inc. Housing and gearbox for drill or driver
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver
US20100326689A1 (en) * 2006-12-27 2010-12-30 Gerhard Meixner Striking mechanism for a handheld electric power tool
US8096369B2 (en) * 2006-12-27 2012-01-17 Robert Bosch Gmbh Striking mechanism for a handheld electric power tool
US20090288851A1 (en) * 2008-05-26 2009-11-26 Max Co., Ltd. Driving tool
US7921933B2 (en) * 2008-05-26 2011-04-12 Max Co., Ltd. Impact driving tool
US7931095B2 (en) * 2008-07-03 2011-04-26 Makita Corporation Hammer drill
US20100000748A1 (en) * 2008-07-03 2010-01-07 Makita Corporation Hammer drill
US9010456B2 (en) * 2008-12-16 2015-04-21 Robert Bosch Gmbh Hand-held power tool
US20110247848A1 (en) * 2008-12-16 2011-10-13 Robert Bosch Gmbh Hand-Held Power Tool
US20120261150A1 (en) * 2009-11-02 2012-10-18 Makita Corporation Power tool
US9339923B2 (en) * 2009-11-02 2016-05-17 Makita Corporation Power tool
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
CN104405793A (zh) * 2014-11-30 2015-03-11 重庆泽田汽车部件有限责任公司 一种保险离合器
CN104405793B (zh) * 2014-11-30 2023-07-14 重庆泽田汽车部件有限责任公司 一种保险离合器
CN108895120A (zh) * 2018-07-06 2018-11-27 甘肃省机械科学研究院有限责任公司 锥齿轮传动副啮合脱开装置
US11529727B2 (en) 2019-10-21 2022-12-20 Makita Corporation Power tool having hammer mechanism
US20210114194A1 (en) * 2019-10-21 2021-04-22 Makita Corporation Power tool having hammer mechanism
US11826891B2 (en) * 2019-10-21 2023-11-28 Makita Corporation Power tool having hammer mechanism
US20220362916A1 (en) * 2019-11-15 2022-11-17 Hilti Aktiengesellschaft Impact mechanism arrangement
US12115637B2 (en) * 2019-11-15 2024-10-15 Hilti Aktiengesellschaft Impact mechanism arrangement
US20220048177A1 (en) * 2020-08-12 2022-02-17 Robert Bosch Gmbh Hand-Held Power Tool
US11981012B2 (en) * 2020-08-12 2024-05-14 Robert Bosch Gmbh Hand-held power tool

Also Published As

Publication number Publication date
GB1447867A (en) 1976-09-02
IT993805B (it) 1975-09-30
JPS4968367A (hr) 1974-07-02
FR2197680B1 (hr) 1976-11-12
DE2242944A1 (de) 1974-03-14
NL7311947A (hr) 1974-03-04
CH560313A5 (hr) 1975-03-27
BR7306718D0 (pt) 1974-06-27
AU5984873A (en) 1975-03-06
JPS5613596B2 (hr) 1981-03-30
DE2242944B2 (de) 1981-04-23
FR2197680A1 (hr) 1974-03-29
ES418342A1 (es) 1976-03-16

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