[go: up one dir, main page]

EP0404035A2 - Tournevis motorisé - Google Patents

Tournevis motorisé Download PDF

Info

Publication number
EP0404035A2
EP0404035A2 EP90111491A EP90111491A EP0404035A2 EP 0404035 A2 EP0404035 A2 EP 0404035A2 EP 90111491 A EP90111491 A EP 90111491A EP 90111491 A EP90111491 A EP 90111491A EP 0404035 A2 EP0404035 A2 EP 0404035A2
Authority
EP
European Patent Office
Prior art keywords
clutch
gear
output shaft
power
torque
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.)
Granted
Application number
EP90111491A
Other languages
German (de)
English (en)
Other versions
EP0404035B1 (fr
EP0404035A3 (fr
Inventor
Wolfgang Koppatsch
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.)
Wagner Paul-Heinz
Original Assignee
Wagner Paul-Heinz
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 Wagner Paul-Heinz filed Critical Wagner Paul-Heinz
Publication of EP0404035A2 publication Critical patent/EP0404035A2/fr
Publication of EP0404035A3 publication Critical patent/EP0404035A3/fr
Application granted granted Critical
Publication of EP0404035B1 publication Critical patent/EP0404035B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/008—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with automatic change-over from high speed-low torque mode to low speed-high torque mode

Definitions

  • the invention relates to a power wrench according to the preamble of claim 1.
  • Motor-driven power screwdrivers are known in which the speed and the torque associated with the speed can be switched over manually or automatically as a function of the screwing torque.
  • automatic wrenches with automatic changeover which are driven by a hydraulic motor, the supply pressure is measured and the power wrench is switched to a higher torque when the supply pressure exceeds a certain limit.
  • the torque is automatically switched over depending on the current consumed.
  • the required reduction of the high speed of the motor output shaft takes place via several conventional gear stages with toothed wheels which are offset laterally with respect to one another.
  • the gear stages have a relatively large space requirement and a relatively high weight.
  • a known power screwdriver of the type specified in the preamble of claim 1 (DE 37 20 633 A1) has three planetary gears arranged in series between an input shaft and an output shaft.
  • the ring gears of the input and output-side planetary gears are both axially displaceable and rotatably mounted in the housing of the power wrench, the ring gear of the input-side planetary gear being fixable by a clutch in a first position on the planet gear carrier and in a second position on the housing.
  • the clutch is in the first position, so that the ring gear of the input-side planetary gear is frictionally fixed to the planet carrier and rotates together with it at the same relatively high speed.
  • the clutch When a certain torque is exceeded, the clutch is moved into the second position by a spring-loaded cam mechanism. As a result, the ring gear of the input-side planetary gear is blocked against rotation in the housing and the clamping force between the ring gear and the planet carrier is released. The planet carrier consequently rotates at a relatively low speed. Furthermore, the power wrench also has a second clutch designed as a slip clutch, which interrupts the torque transmission when a maximum screwing torque is exceeded.
  • the switching mechanism for switching the gear ratio of the input-side gear stage is relatively complex.
  • the ring gears of the planetary gears are both rotatably and axially displaceably mounted in the housing and have to be shifted against each other by a complicated mechanism in such a way that the ring gear of the input-side planetary gear can be fixed either on the housing or on the planet carrier.
  • the clutch which fixes the ring gear of the input-side planetary gear on the planet carrier or on the housing, forms a structural unit with the planetary gear, so that the structure of the switching mechanism is relatively complicated.
  • the axially movable parts have to be manufactured with low manufacturing tolerances. There is a risk that the axially displaceable parts jam in their guides and block the switching mechanism.
  • the invention has for its object to provide a power wrench of the type specified in the preamble of claim 1, which has a simple structure and works without problems.
  • the second gear stage is contained in one of two parallel drive branches. Two separate drive branches with different transmission ratios are available to transmit the torque. Depending on the tightening torque, one or the other drive branch can then be accessed to drive the output shaft at a higher or lower speed.
  • Switching takes place via two clutches, one of which is arranged in a drive branch.
  • the common movable coupling part of both clutches is biased such that one of the two clutches is engaged and the other clutch is disengaged.
  • the speed of the drive shaft of the manual transmission is always reduced regardless of the torque of the power wrench via a first gear stage.
  • load torque When the tightening torque is low (load torque), the output of the first gear stage is connected directly to the output shaft, so that the output shaft is driven at a relatively high speed.
  • the power transmission via the other drive branch is interrupted.
  • the joint movable coupling part assumes the other position.
  • the transfer of the torque of the drive shaft now takes place via the second gear stage with a lower speed and higher torque.
  • the changeover takes place without external control by means of a changeover clutch or double clutch designed as an overload clutch, the clutch part of which is always coupled to one of the drive branches and thus never runs idle.
  • the gear stages are easy to set up, since they have a fixed transmission ratio and an elaborate control mechanism, which is prone to malfunctions, for changing the transmission ratio can be dispensed with at least one of the two transmission stages.
  • a guide curve is preferably provided on the output shaft, in which a guide element attached to the coupling part engages. If the limit torque is exceeded, the common coupling part is axially displaced against the preload.
  • the preload of the coupling part can be applied by a spring device or also hydraulically. This pretension can preferably be changed by external adjustment in order to be able to adjust the level of the load torque at which the switchover takes place.
  • One of the two couplings is advantageously designed as a ball coupling.
  • the coupling between a coupling body which is connected to the planet carrier of the first planetary gear and the movable coupling part takes place by spring-loaded balls which act against an un round path can be pressed.
  • Such a ball coupling forms a slip clutch in which the coupling body and the coupling part can move relative to one another.
  • a free idling path is provided adjacent to a driving path which contains the recesses of the ball coupling and which receives the balls when the coupling of the second drive branch is engaged .
  • the planet carrier of the first planetary gear advantageously has an output shaft which runs coaxially to the drive shaft and has an extension which extends beyond the second gear stage.
  • the output shaft can carry the sun gear of the second downstream planetary gear, while the shoulder is connected to the clutch body of the first clutch.
  • Fig. 1 shows the entire power screwdriver in a side view.
  • the power wrench is designed in the manner of a hand drill and has a drive device 1 which contains a rotary motor, not shown.
  • the rotary motor can be switched on by pressing the operating lever 2.
  • the drive device 1 is accommodated in a separate housing with a handle 3.
  • a torque-dependent manual transmission 4 is fastened, the housing 5 of which is rotatably mounted relative to the housing of the drive device 1, so that the drive device 1 can be rotated with the handle 3 to any screw position.
  • the torque-dependent manual transmission 4 is followed by a planetary gear, which is inserted in the front housing part 6 of the power wrench.
  • the front housing part 6 On the output shaft of the planetary gear, a head 7 is attached, on which a key nut for turning a screw can be attached.
  • the front housing part 6 has a profile section 8 for fastening a support foot, not shown, which presses the front housing part and the housing 5 of the gearbox connected to it against a stationary abutment.
  • Fig. 2 shows the functional diagram of the torque-operated manual transmission 4.
  • the manual transmission has a first gear stage 21 ', the output shaft drives the output shaft 38 of the manual transmission via two individually switchable drive branches 11, 12.
  • One of the two drive branches contains a second gear stage 26 '.
  • Each of the two drive branches 11, 12 can be connected via a clutch 32, 48, one of the two clutches always being engaged and the other clutch being disengaged. Both clutches have a common coupling part 36. Is the on the output side of the second gear stage 26 'arranged clutch 48 is engaged, the output shaft 38 of the gearbox is driven with higher torque and lower speed than when the other clutch 32 is engaged and the torque without the second gear stage directly on the Output shaft 38 is transmitted.
  • FIG. 3 shows the torque-dependent manual transmission 4 constructed in accordance with the functional diagram from FIG. 2 in a sectional illustration.
  • the housing 5 of the gearbox 4 is rotatably supported with a ball bearing 18 relative to the housing of the drive device 1.
  • the drive shaft 19 driven by the rotary motor projects into the interior of the housing 5 from the end wall of the housing of the drive device 1.
  • the drive shaft 19 of the wave-shaped shoulder of a sun gear 20 of the first gear stage 21 'forming the first planetary gear 21 is rotatably connected.
  • the wavy shoulder of the sun gear 20 is mounted with the bearings 23, 23 'in the housing 5 of the gearbox.
  • the toothing of the sun gear 20 is in engagement with the toothing of the planet gears 22, which are arranged around the sun gear 20.
  • the planet gears 22 are mounted in a planet carrier 29, which also forms the output shaft 24 of the first gear 21. Furthermore, the planet carrier 29 carries the sun gear 25 of a second planetary gear 26, which is connected downstream of the first planetary gear 21 and which second gear stage 26 'forms. The sun gear 25 of the second planetary gear 26 drives the planet gears 27 which, like the planet gears 22 of the first planetary gear 21, engage in the internal toothing 17 of the housing 5.
  • the output shaft 24 of the planet carrier 29 has a wave-shaped extension 30 which extends coaxially in the housing 5 and extends beyond the second planetary gear 26.
  • the planet carrier 52 of the second planetary gear 26 is rotatably mounted on the shaft-shaped projection 30.
  • the coupling body 31 of the first coupling 32 is connected in a rotationally fixed manner to the wave-shaped extension 30.
  • the coupling body 31 contains a plurality of radially running blind bores 50, in which ball catches 33 are inserted. In the position shown in FIG. 1, the balls 34 of the ball catches 33 engage in a driving path 35 of a movable coupling part 36.
  • the coupling part 36 is surrounded by a cylindrical extension 37 of the output shaft 38, which with the ball bearing 54 on the shaft-shaped extension 30 and Ball bearing 53 is mounted in the housing 5.
  • two guide curves 39 are provided in the form of opposite triangular openings 40, which are shown in the top view in FIG. 4.
  • the ends of two pin-shaped guide elements 41 protrude into these openings.
  • the guide curves 39 and the guide elements 41 engaging therein ensure that the output shaft 38 always rotates with the coupling part 36, although slight relative rotations are possible within the openings formed by the guide curves 39 .
  • Each of the openings 40 has the shape of a isosceles triangle (Fig.4), the tip of which is directed to the output shaft 38.
  • the guide elements 41 connected to the movable coupling part 36 are pressed axially in the direction of the tips of the triangles by a spring 46 which is supported on the planet carrier 52 of the second planetary gear 26.
  • the balls 34 of the ball catches 33 run in the driving path 35 of the coupling part 36, so that the coupling body 31 and the coupling part 36 are engaged.
  • the triangular openings 40 are symmetrical with respect to the axis of the output shaft 38, so that each guide curve 39 forms two inclined flanks 40a, 40b with opposite bevels, along which the guide elements 41 can slide. If the load torque occurring at the output shaft 38 exceeds a certain limit value, the guide elements 41 disengage from the tips of the triangular guide curves 39 and slide along the flanks 40a or 40b, as a result of which the coupling part 36 counteracts the force of the spring 46 in the direction of the drive shaft 19 is moved. The balls 34 of the ball catches 33 slide into an idle track 47 provided on the side of the driving track 35 on the clutch part, so that the clutch part 36 is released from engagement with the clutch body 31.
  • a clutch body 55 is attached to the planet carrier 52 of the second planetary gear 26 and forms a second clutch 48 with the movable clutch part 36. If the movable coupling part 36 in the direction of the coupling body 55 of the load torque occurring on the output shaft 38 is exceeded second clutch 48 moves, the claws 49, 49 'of the second clutch 48 are engaged and the first clutch 32 is disengaged.
  • an axial bore 56 is provided, which runs through the sun gear 20 of the first planetary gear and the planet carrier 29 with the wave-shaped shoulder and the output shaft 38.
  • the coupling body 31 contains the ball catches 33, each of which has a spring 60 contained in the radial blind bore 50 of the coupling body 31 and the balls 34 pressed outwards by the spring 60.
  • the balls 34 run in the driving path 35, which is provided on the inside of the coupling body 31.
  • This driving path 35 has a circumferentially varying diameter, so that there are recesses 61 into which the balls 34 can penetrate.
  • the coupling body 31 is in engagement with the coupling part 36 and the cylindrical extension of the output shaft 38 is carried along via the guide element 41. Since the clutch 32 can slip even when the balls 34 are in the driving path and are pressed against the spring forces into the blind holes 50, an increased security of the clutch against damage is achieved. Furthermore, drive shocks are prevented from being transmitted during the switching process.
  • the idle path 47 has a constant diameter and has no recesses distributed around the circumferential surface.
  • the power screwdriver described according to FIGS. 1-6 works as follows: To tighten a screw, a nut is placed on the head 7 of the power screwdriver, which is connected to the screw to be turned. The drive device 1 rotates the drive shaft 19, whereby the planet gears 22 of the first planetary gear 21 are driven. As long as the tightening torque is still low, the first clutch is engaged and the torque is transmitted via the planet carrier 29 of the first planetary gear 21 directly to the output shaft 38 of the torque-dependent manual transmission 4. The output shaft 38 drives the third downstream planetary gear, which is located in the front housing part 6 and moves the head 7 at a relatively high speed and a low torque.
  • the common clutch part 36 of the two clutches 32, 48 moves and the first clutch disengages.
  • the second clutch 48 is engaged.
  • the torque is now transmitted with the interposition of the second planetary gear 26, the planet carrier of which Coupling part 36 takes the output shaft 38 of the manual transmission.
  • the rotation of the planet carrier 29 of the first planetary gear 21 is further reduced by the second planetary gear 26 connected downstream, so that the head 7 of the power wrench is driven via the output shaft 38 at a lower speed but with a higher torque. This drive with higher torque and lower speed continues until the screw is tightened. There is no constant switching back and forth between high and low speed.
  • the manual transmission of the second exemplary embodiment also has two planetary gears 21, 26 and two clutches 32, 48.
  • the only difference between the two manual transmissions is that in the manual transmission according to the second exemplary embodiment, the second clutch 48 is not arranged on the output side of the second planetary gear 26, but rather on the drive side thereof.
  • Fig. 8 shows a section through the manual transmission according to the second embodiment.
  • the drive shaft 19 protruding from the drive device 1 carries the sun gear 20 of the first planetary gear 21.
  • the external toothing of the sun gear 20 engages with the internal teeth of the planet gears 22, which move the planet carrier 29.
  • the planet carrier 29 drives, via the first clutch 32 with the ball catches 33, a shaft 64 which is axially rotatable in the gearbox and whose end piece facing away from the drive shaft 19 is toothed with the output shaft 38.
  • the output shaft 38 is followed by the third planetary gear 76, which is located in the front housing part 6 of the power wrench.
  • the coupling piece 36 of the first clutch 32 is displaced so that the first clutch disengages and the claws 49, 49 'of the second clutch 48 come into engagement, as a result of which the sun gear 25 of the second planetary gear 26 is taken away.
  • the sun gear 25 engages in the external toothing of the planet gears 27 of the second planetary gear 26.
  • the sun gear 75 of the third planetary gear 76 is driven by the planet carrier 52 of the second planetary gear 26.
  • the planet carrier 52 has a shoulder 73 which surrounds the shaft 64 and has internal teeth. The internal toothing of the shoulder 73 is in engagement with the external toothing of the shaft 64, so that the shaft 64 rotates freely.
  • the output shaft 38 rotates at a relatively high speed and low torque. If the first clutch is disengaged by shifting the clutch part 36 and the second clutch 48 is engaged, the second planetary gear 26 is connected downstream of the first planetary gear and the output shaft 38 is moved at a lower speed and higher torque.
  • the figures 9 and 10 show a locking device 77 with which the movable coupling part 36 can be blocked, so that the second coupling 48 is always engaged and the first coupling 32 is disengaged and the power wrench works with a relatively high torque and low speed in the load gear.
  • a sliding piece 81 with a ball track 82 is attached.
  • the balls 83 located in the ball track 82 engage in recesses 84 in the movable coupling part.
  • the sliding piece 81 is moved against the force of the spring 46 onto the coupling piece 55 of the second coupling 48, so that the claws 49, 49 'of the second coupling mesh.
  • the sliding piece 81 is blocked by the locking device 77.
  • the balls 83 can roll on the sliding piece 81, so that the coupling part 36 can move freely.
  • FIGS. 11 and 12 show another embodiment of the first clutch 32 of the torque-dependent manual transmission in a sectional view.
  • the coupling 32 differs from the couplings described with reference to FIGS. 5 and 6 in that the coupling body 31 with the springs 60 is arranged axially to the drive shaft. This results in a compact design of the torque-dependent manual transmission.
  • the axially arranged clutch body 31 of the first clutch 32 forms, together with the springs 60 and the balls 34, the common axially displaceable clutch part 36 for the first and the second clutch 32, 48.
  • the common clutch part 36 is biased into the overdrive position shown in Fig. 11, in which the claws 49,49 'of the second clutch 48 are disengaged and the first clutch 32 is engaged.
  • the balls 34 of the first clutch 32 which are preloaded by the springs 60, engage in hemispherical recesses 85 in a ring piece 86 which takes the output shaft of the power wrench with them. If the limit value of the load torque is exceeded, the common coupling part 36 shifts in the axial direction, the claws 49, 49 'of the second coupling 48 engaging and the balls 34 of the first coupling 32 slipping out of the recesses 85 of the ring piece 86, so that the first clutch 32 is disengaged.
  • the first clutch 32 can slip even when the balls 34 are located in the recesses 85 of the ring piece 86 and are pressed against the spring forces into the blind bores 50 of the clutch body 31, an increased security of the clutch against damage is achieved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Structure Of Transmissions (AREA)
  • Transmission Devices (AREA)
EP19900111491 1989-06-22 1990-06-19 Tournevis motorisé Expired - Lifetime EP0404035B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3920471 1989-06-22
DE19893920471 DE3920471C1 (fr) 1989-06-22 1989-06-22

Publications (3)

Publication Number Publication Date
EP0404035A2 true EP0404035A2 (fr) 1990-12-27
EP0404035A3 EP0404035A3 (fr) 1991-09-04
EP0404035B1 EP0404035B1 (fr) 1994-08-31

Family

ID=6383343

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900111491 Expired - Lifetime EP0404035B1 (fr) 1989-06-22 1990-06-19 Tournevis motorisé

Country Status (3)

Country Link
EP (1) EP0404035B1 (fr)
JP (1) JPH03117568A (fr)
DE (1) DE3920471C1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0787931A1 (fr) * 1996-01-31 1997-08-06 Black & Decker Inc. Transmission automatique variable pour outil à main
NL2000620C2 (nl) * 2006-04-28 2008-10-07 Unex Corp Aangedreven koppelversterker.
US7806198B2 (en) 2007-06-15 2010-10-05 Black & Decker Inc. Hybrid impact tool
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver
US8460153B2 (en) 2009-12-23 2013-06-11 Black & Decker Inc. Hybrid impact tool with two-speed transmission
US8584770B2 (en) 2010-03-23 2013-11-19 Black & Decker Inc. Spindle bearing arrangement for a power tool
US8631880B2 (en) 2009-04-30 2014-01-21 Black & Decker Inc. Power tool with impact mechanism
US8794348B2 (en) 2008-09-25 2014-08-05 Black & Decker Inc. Hybrid impact tool
US9604354B2 (en) 2012-02-27 2017-03-28 Black & Decker Inc. Tool having multi-speed compound planetary transmission
CN111941054A (zh) * 2020-09-11 2020-11-17 意华控股集团有限公司 一种螺丝自动锁紧装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4328599C2 (de) * 1992-08-25 1998-01-29 Makita Corp Rotations-Schlagwerkzeug
US6938526B2 (en) * 2003-07-30 2005-09-06 Black & Decker Inc. Impact wrench having an improved anvil to square driver transition
US7314097B2 (en) 2005-02-24 2008-01-01 Black & Decker Inc. Hammer drill with a mode changeover mechanism
DE102007047611A1 (de) * 2007-10-04 2009-04-09 Grohmann Engineering Gmbh Schrauberwerkzeug

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3430521A (en) * 1967-06-19 1969-03-04 Ingersoll Rand Co Power-operated tool having two-speed rotary output
DE1478973A1 (de) * 1962-11-23 1969-07-03 Licentia Gmbh Umschaltbares Getriebe mit Ratschenscheiben fuer motorisch angetriebene Handwerkzeuge
EP0092127A2 (fr) * 1982-04-21 1983-10-26 Wagner, Paul-Heinz Outil rotatif
EP0329852A2 (fr) * 1988-01-23 1989-08-30 Wagner, Paul-Heinz Clé à écrous à moteur

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3618024A1 (de) * 1986-05-28 1987-12-03 Hilti Ag Elektrowerkzeug mit schaltkupplung
SE450354B (sv) * 1986-06-24 1987-06-22 Atlas Copco Ab Motordrivet tvahastighetsverktyg
DE3636026A1 (de) * 1986-10-23 1988-04-28 Hilti Ag Handgeraet mit werkzeughalter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1478973A1 (de) * 1962-11-23 1969-07-03 Licentia Gmbh Umschaltbares Getriebe mit Ratschenscheiben fuer motorisch angetriebene Handwerkzeuge
US3430521A (en) * 1967-06-19 1969-03-04 Ingersoll Rand Co Power-operated tool having two-speed rotary output
EP0092127A2 (fr) * 1982-04-21 1983-10-26 Wagner, Paul-Heinz Outil rotatif
EP0329852A2 (fr) * 1988-01-23 1989-08-30 Wagner, Paul-Heinz Clé à écrous à moteur

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0787931A1 (fr) * 1996-01-31 1997-08-06 Black & Decker Inc. Transmission automatique variable pour outil à main
US5897454A (en) * 1996-01-31 1999-04-27 Black & Decker Inc. Automatic variable transmission for power tool
US7980324B2 (en) 2006-02-03 2011-07-19 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
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
NL2000620C2 (nl) * 2006-04-28 2008-10-07 Unex Corp Aangedreven koppelversterker.
US7806198B2 (en) 2007-06-15 2010-10-05 Black & Decker Inc. Hybrid impact tool
US9193053B2 (en) 2008-09-25 2015-11-24 Black & Decker Inc. Hybrid impact tool
US8794348B2 (en) 2008-09-25 2014-08-05 Black & Decker Inc. Hybrid impact tool
US10513021B2 (en) 2008-09-25 2019-12-24 Black & Decker Inc. Hybrid impact tool
US8631880B2 (en) 2009-04-30 2014-01-21 Black & Decker Inc. Power tool with impact mechanism
USRE46827E1 (en) 2009-12-23 2018-05-08 Black & Decker Inc. Hybrid impact tool with two-speed transmission
US8460153B2 (en) 2009-12-23 2013-06-11 Black & Decker Inc. Hybrid impact tool with two-speed transmission
US9216504B2 (en) 2010-03-23 2015-12-22 Black & Decker Inc. Spindle bearing arrangement for a power tool
US8584770B2 (en) 2010-03-23 2013-11-19 Black & Decker Inc. Spindle bearing arrangement for a power tool
US9604354B2 (en) 2012-02-27 2017-03-28 Black & Decker Inc. Tool having multi-speed compound planetary transmission
US10926398B2 (en) 2012-02-27 2021-02-23 Black & Decker Inc. Tool having compound planetary transmission
US11738439B2 (en) 2012-02-27 2023-08-29 Black & Decker Inc. Power tool with planetary transmission
CN111941054A (zh) * 2020-09-11 2020-11-17 意华控股集团有限公司 一种螺丝自动锁紧装置

Also Published As

Publication number Publication date
EP0404035B1 (fr) 1994-08-31
DE3920471C1 (fr) 1990-09-27
JPH03117568A (ja) 1991-05-20
EP0404035A3 (fr) 1991-09-04

Similar Documents

Publication Publication Date Title
EP0329852B1 (fr) Clé à écrous à moteur
DE69400262T2 (de) Motorgetriebenes Gerät und Mechanismus dafür
EP0401548B1 (fr) Dispositif à outil de vissage
DE4236819C2 (de) Motorisch angetriebene Drehwerkzeugeinrichtung
EP0990488B1 (fr) Tournevis motorisé
DE69533521T2 (de) Ratschen schraubenschlüssel
EP0404035B1 (fr) Tournevis motorisé
DE10202263A1 (de) 360 DEG Kupplungskragen
EP0092127A2 (fr) Outil rotatif
EP0612588A1 (fr) Dispositif de commande pour outils électriques
DE19717466B4 (de) Mehrganggetriebe für Elektrowerkzeugmaschinen
DE19809135A1 (de) Elektrohandwerkzeugmaschine
EP0577981B1 (fr) Tête pour une pièce à main médicale ou dentaire comportant un outil de traitement oscillant
DE3235544A1 (de) Bohrhammer
EP0666212B1 (fr) Transmission manoevrable de pédalier pour une bicyclette ou similaires
DE2433995A1 (de) Ueberlastkupplung zur begrenzung eines uebertragenen drehmomentes
DE4024722A1 (de) Elektrischer schraubendreher
DE4444952A1 (de) Kontinuierlich-variables Reibrollengetriebe
DE4105405A1 (de) Zweiganggetriebe fuer ein motorisch angetriebenes werkzeug
DE3505323C2 (fr)
DE3431630C2 (de) Elektrowerkzeug zum wahlweisen Bohren oder Schrauben
DE4310847C2 (de) Antriebseinrichtung für eine Küchenmaschine
DE3919648C2 (de) Winkelschrauber
DE19809131A1 (de) Elektrohandwerkzeugmaschine
DE3330337C2 (de) Kraftdrehvorrichtung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): ES FR GB IT SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): ES FR GB IT SE

17P Request for examination filed

Effective date: 19920111

17Q First examination report despatched

Effective date: 19930319

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): ES FR GB IT SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19940831

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.SCRIBED TIME-LIMIT

Effective date: 19940831

Ref country code: ES

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19940831

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19941102

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19941130

EN Fr: translation not filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19970616

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980619

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19980619