EP0329852A2 - Clé à écrous à moteur - Google Patents
Clé à écrous à moteur Download PDFInfo
- Publication number
- EP0329852A2 EP0329852A2 EP88121554A EP88121554A EP0329852A2 EP 0329852 A2 EP0329852 A2 EP 0329852A2 EP 88121554 A EP88121554 A EP 88121554A EP 88121554 A EP88121554 A EP 88121554A EP 0329852 A2 EP0329852 A2 EP 0329852A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- coupling part
- output shaft
- latching
- coupling
- 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
Links
- 230000008878 coupling Effects 0.000 claims abstract description 74
- 238000010168 coupling process Methods 0.000 claims abstract description 74
- 238000005859 coupling reaction Methods 0.000 claims abstract description 74
- 230000001419 dependent effect Effects 0.000 claims description 6
- 230000000903 blocking effect Effects 0.000 claims description 5
- 230000036316 preload Effects 0.000 claims description 4
- 210000000078 claw Anatomy 0.000 description 10
- 230000005540 biological transmission Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
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
- B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
- B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
-
- 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 wrenches are known in which the speed, and thus also the torque, are switched as a function of the tightening torque can. This switchover can be carried out automatically. For example, it is known to measure the supply pressure in a power wrench driven by a hydraulic motor and to switch the power wrench to a higher torque if the supply pressure exceeds a certain limit value. In the case of an electrically driven power wrench, the tightening torque can be determined by the current drawn.
- the invention has for its object to provide a power wrench specified in the preamble of claim 1, which performs an automatic switch from low torque to high torque in a purely mechanical manner, without converting the torque into another physical quantity would have to, and that works reliably and with little wear.
- the force of the drive shaft is transmitted from a distributor shaft to the locking coupling in two different ways with different transmission ratios.
- a low screwing torque load torque
- the coupling part of the locking clutch engages with the first drive wheel, so that the output shaft is driven at a relatively high first speed, while the power transmission path from the second drive wheel to the locking clutch is interrupted.
- the coupling part engages either with the first drive wheel or with the second drive wheel.
- the coupling part is adjusted in that a force generated by the load torque counteracts the pretension of the coupling part.
- the coupling part can engage either only with the first or only with the second drive wheel, but never with both drive wheels at the same time.
- the preload of the coupling part can be applied by a spring device or also hydraulically. This preload 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.
- the coupling part is arranged to be longitudinally displaceable on the output shaft and it is pressed by the pretensioning device in the direction in which it is non-positively connected to the first drive wheel. If the load torque exceeds the limit value, the pretensioning device yields and the action of a guide curve results in an axial displacement of the coupling part in the direction of the second drive wheel. The frictional connection between the coupling part and the first drive wheel is released, while the frictional connection of the coupling part to the second drive wheel is established.
- One of the two locking couplings is preferably a claw coupling, while the other locking coupling is a ball coupling.
- the ball coupling In the ball coupling, entrainment takes place between a coupling body which is firmly connected to the first drive wheel and the coupling part by spring-loaded balls which are pressed against a non-circular path.
- 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 orbit is provided adjacent to a path of the coupling body which contains the recesses of the locking coupling and which receives the balls when the other locking coupling is engaged .
- the locking clutch provided with balls thus has two tracks arranged side by side, one of which represents a driving track and the other an idling track.
- the locking coupling is engaged; while the detent clutch is released when the balls are idling.
- the power wrench according to the invention enables a smooth and shock-free changeover from low torque to high torque or vice versa.
- the guide curve which, in conjunction with the preload, brings about the axial movement of the coupling part with respect to the output shaft as a function of the load torque, has the shape of an isosceles triangle. This results in a torque-dependent changeover of the gear ratio of the power wrench in both directions of rotation.
- the power wrench is designed like a hand drill. It has a drive device 10 which contains a (not shown) rotary motor which can be switched on by actuating a trigger lever 11. The direction of rotation can be set on the direction selector 12.
- the drive device 10 is accommodated in a separate housing to which the housing 13 containing the torque-dependent clutch 14 is fastened. At the opposite end of the housing 13, a housing 15 is attached, which contains a planetary gear 16.
- the output shaft 17th of the planetary gear has a head 18 to which a key nut for turning a screw can be attached.
- the shaft 19 of the motor projects into the interior of the housing 13 from the end wall of the housing of the drive device 10.
- the shaft 19 is supported by a ball bearing 21.
- the shaft 19 drives a gear 22, which is firmly seated on the distributor shaft 23.
- the distributor shaft 23 is supported at both ends in the housing 13 and there are two further gear wheels 24, 25 of different diameters.
- the larger gear 24 meshes with the teeth of the first drive wheel 26 and the gear 25 meshes with the teeth of the second drive wheel 27.
- Both drive wheels 26 and 27 are arranged coaxially with the output shaft 28 of the torque-dependent clutch 14. They are driven by the distributor shaft 23 at different speeds, the speed of the drive wheel 26 being greater than that of the second drive wheel 27.
- the first drive wheel 26 is mounted on the output shaft 28 with a ball bearing 29 and the second drive wheel 27 is with a roller bearing 30 mounted on a cylindrical projection 31 of the coupling body 32.
- a cup-shaped coupling body 33 extends from the first drive wheel 26 in the direction of the second drive wheel 27.
- the ball housing 34 of the coupling part 32 projects into the opening of the coupling body 33.
- a ring of claws 35 projects from the ball housing 34 in the direction of the second drive wheel 27. These claws 35 can engage claws 36, which are provided on the end face of the second drive wheel 27, when the clutch body 32 is displaced in the direction of the second drive wheel 27.
- the output end of the output shaft 28 is supported by a ball bearing 37 in the housing 13. On the rotating ring of the ball bearing 37, a spring 38 is supported, which presses the coupling part 32 in the direction of the first gear 26.
- each of the openings 39 has the shape of an isosceles triangle, the tip of which is directed parallel to the axis of the output shaft 28 against the bias applied by the spring 38.
- each guide curve 39 forms two inclined flanks 39a, 39b with opposite bevels (FIG. 3), along which the guide element 40 can slide. If the load torque occurring on the output shaft 28 exceeds the limit value, the guide element 40 disengages from the tips of the triangular guide curves 39 and slides along the flanks 39a or 39b, as a result of which the coupling part 32 disengages from and engages with the coupling body 33 Claws 35 come into engagement with the second drive wheel 27.
- Fig. 4 shows a cross section of the first locking clutch, which is formed from the coupling body 33 and the ball housing 34.
- the ball housing 34 contains a plurality of ball catches, each of which has a spring 43 contained in a radial blind bore 42 of the ball housing 34 and a ball 44 pressed outwards by the spring 43.
- the balls 44 run in a driving path 45, which is provided on the inside of the coupling body 33.
- This driving path 45 has a circumferentially varying diameter, i.e. it has recesses into which the balls 44 can penetrate.
- an idling path 46 Adjacent to the driving path 45, an idling path 46 is provided in the clutch body 33, the peripheral surface of which has no recesses but a constant diameter (FIG. 5).
- the coupling part 32 which is normally pressed in the direction of the drive wheel 26 by the spring 38, moves in the direction of the drive wheel 27 with compression of the spring 38, the balls 44 pass from the driving path 45 into the idle path 46.
- the coupling part 32 is uncoupled rotationally from the coupling body 33.
- the claws 35 and 36 engage in one another, so that the coupling part 32 is coupled to the drive wheel 27 and is rotated by the latter.
- This first gear stage has planet gears 48 which engage with the sun gear 47 with their toothings and roll on an internal toothing 49 of the housing 15.
- the planet gears 48 are supported on axles 50 which protrude from a bearing body 51 in which the end 52 of the output shaft 28 is also supported.
- the bearing body 51 also forms the sun gear 53 of the second gear stage 16b, the planet gears 54 of which also engage with the internal toothing 49 of the housing 15.
- the planet gears 54 are mounted on axles 55 which protrude from the bearing body 56.
- the bearing body 56 is connected in one piece to the output shaft 17, which is mounted in a bearing 57 at the end of the housing 15.
- the bearing 57 is accommodated in a head piece 58, which has an outer profile 59 for attaching an external support element (not shown) in order to divert the reaction force that arises when a screw is turned onto a stationary replacement bearing.
- a nut is placed on the head 18 of the output shaft 17, which is connected to the screw to be rotated.
- the drive device 10 rotates the distributor shaft 23, as a result of which the drive wheels 26 and 27 are rotated simultaneously, but at different speeds.
- the spring 38 presses the coupling part 32 against the drive wheel 26, so that the balls 44 are in the driving path and the drive wheel 26 takes the coupling part 32 along via the coupling body 33. Since the claws 35.36 in this State are disengaged, the drive wheel 27 rotates empty on the coupling part 32.
- the output shaft 28 is therefore driven at the high speed and correspondingly low torque.
- the rotation of the output shaft 28 is reduced by the planetary gear 16 and transmitted to the screw via the output shaft 17.
- the load-dependent clutch 14 is located between the drive device 10 and the planetary gear 16, where the torques to be transmitted are relatively low, so that the clutch 14 can be made small.
- the coupling part 32 moves with the guide element 40 along the flanks 39a of the guide curve 39, so that the coupling part 32 moves against the drive wheel 27.
- the balls 44 move from the carrier track 45 into the idle track 46 and at the same time the claws 35 and 36 come into mutual engagement.
- the output shaft 28 is driven via the gears 25 and 27 at a lower speed and higher torque. This drive with higher torque and lower speed continues until the screw is tightened. So there is no constant switching back and forth between high and low speed.
- the axis of the planetary gear 16 runs coaxially to that of the output shaft 28.
- the shaft 19 of the rotary drive 10, in contrast, is laterally offset.
- the snap coupling according to FIGS. 2 to 5 also have a blocking device 60, which makes it possible to hold the movable coupling part 32 in the load position after the limit speed has been exceeded against the bias of the spring 38.
- a blocking device 60 which makes it possible to hold the movable coupling part 32 in the load position after the limit speed has been exceeded against the bias of the spring 38.
- the blocking device 60 is used. This has a rotatable hand lever 61 which is fastened to a shaft 62 mounted in the housing 13.
- a cam section 63 is provided on the shaft 62, against which a pin 64 abuts, which is arranged to be longitudinally displaceable in a bore of the output shaft 28.
- This pin 64 abuts a cross pin 65, the ends of which protrude from the output shaft 28 and engage in a sleeve 66 surrounding the output shaft.
- the clutch body 32 is pressed against this sleeve 66 by the spring 38.
- the pin 64 is advanced as a result of the cam part 63, as a result of which the sleeve 66 presses the coupling part 32 into the position which corresponds to the high load torque and in which the claws 35, 36 are in mutual engagement, while the first latching clutch 33 , 34 is solved.
- the hand lever 61 can be rotated without overcoming a greater counterforce, so that the sleeve 66 follows the coupling part 32. Since the power transmission via the shaft 62, the cam part 63 and the pin 64 is self-locking, the pressure of the spring 38 means that the coupling part 32 cannot be moved back into the overdrive position unless the hand lever 61 has been manually rotated into a position beforehand which the sleeve 66 has been moved by the spring 38. If necessary, a locking device 67 can be provided with which the hand lever 61 is held in the effective position and in the ineffective position.
- Fig. 6 shows another embodiment which is the same as that of the first embodiment, except that the blocking device 60 is omitted and is replaced by a locking device.
- This latching device consists of a latching recess 39c in the guide curve 39. In the load position, the guide element 40 latches in the latching recess 39c according to FIG. 6. The latching in the latching recess 39c requires less force than the latching out of this latching recess. In this way, the switching behavior of the clutch receives a hysteresis. This means that when the load torque increases, the switchover to a lower speed of the output shaft takes place at a low torque than when the load torque decreases, the switchover to the higher output speed occurs. In this way, a constant switching of the clutch is avoided in the limit range of the critical load torque.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3801972A DE3801972A1 (de) | 1988-01-23 | 1988-01-23 | Kraftschrauber |
DE3801972 | 1988-01-23 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0329852A2 true EP0329852A2 (fr) | 1989-08-30 |
EP0329852A3 EP0329852A3 (en) | 1990-09-05 |
EP0329852B1 EP0329852B1 (fr) | 1993-08-11 |
Family
ID=6345877
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP88121554A Expired - Lifetime EP0329852B1 (fr) | 1988-01-23 | 1988-12-23 | Clé à écrous à moteur |
Country Status (5)
Country | Link |
---|---|
US (1) | US4966057A (fr) |
EP (1) | EP0329852B1 (fr) |
JP (1) | JP2867031B2 (fr) |
DE (2) | DE3801972A1 (fr) |
ES (1) | ES2042703T3 (fr) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0404035A2 (fr) * | 1989-06-22 | 1990-12-27 | Wagner, Paul-Heinz | Tournevis motorisé |
FR2658889A1 (fr) * | 1990-02-23 | 1991-08-30 | Atlas Copco Tools Ab | Transmission de puissance a deux vitesses, pour un outil a moteur, notamment sous l'action d'air comprime. |
DE4333599A1 (de) * | 1992-10-01 | 1994-04-07 | Makita Corp | Schraubeneindrehwerkzeug |
EP0787931A1 (fr) * | 1996-01-31 | 1997-08-06 | Black & Decker Inc. | Transmission automatique variable pour outil à main |
EP1092896A1 (fr) * | 1996-09-05 | 2001-04-18 | Black & Decker Inc. | Transmission automatique variable pour outil à main |
FR2996484A1 (fr) * | 2012-10-05 | 2014-04-11 | Renault Georges Ets | Dispositif de vissage comprenant au moins une roue-libre solidaire du carter |
WO2018011203A1 (fr) * | 2016-07-11 | 2018-01-18 | Robert Bosch Gmbh | Système de machine-outil portative |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5361853A (en) * | 1991-11-29 | 1994-11-08 | Ryobi Limited | Power tool |
US5681329A (en) * | 1991-12-16 | 1997-10-28 | Callicrate; Michael P. | Method and apparatus for castration using an endless elastic loop |
US5236434A (en) * | 1991-12-16 | 1993-08-17 | Callicrate Michael P | Method and apparatus for ligating a body part |
DE9312303U1 (de) * | 1993-08-18 | 1994-12-15 | Robert Bosch Gmbh, 70469 Stuttgart | Vorrichtung zum Anziehen von Schraubverbindungen |
JP2756245B2 (ja) * | 1996-05-30 | 1998-05-25 | 前田金属工業株式会社 | ボルト・ナット締付機 |
DE19845024C2 (de) * | 1998-09-30 | 2000-08-03 | Fein C & E | Kraftgetriebener Schrauber |
US6093128A (en) * | 1999-03-12 | 2000-07-25 | Ingersoll-Rand Company | Ratchet wrench having self-shifting transmission apparatus |
US6165096A (en) * | 1999-03-12 | 2000-12-26 | Ingersoll-Rand Company | Self-shifting transmission apparatus |
DE10161356B4 (de) * | 2001-12-13 | 2013-03-07 | Hilti Aktiengesellschaft | Schraubgerät |
JP2005299883A (ja) * | 2004-04-15 | 2005-10-27 | Omi Kogyo Co Ltd | 歯車伝動機構及び電動工具 |
US7980324B2 (en) | 2006-02-03 | 2011-07-19 | Black & Decker Inc. | Housing and gearbox for drill or driver |
ES2334081B2 (es) * | 2006-04-28 | 2011-12-12 | Unex Corporation | Intensificador de par de torsion motorizado. |
US8303449B2 (en) * | 2006-08-01 | 2012-11-06 | Techtronic Power Tools Technology Limited | Automatic transmission for a power tool |
SE0700264L (sv) * | 2007-02-05 | 2008-05-13 | Atlas Copco Tools Ab | Mutterdragare med svivlat växelhus |
JP5117258B2 (ja) * | 2008-04-01 | 2013-01-16 | 株式会社マキタ | 自動変速式動力工具 |
US8911320B2 (en) | 2009-08-28 | 2014-12-16 | Makita Corporation | Power tool |
US9186808B2 (en) | 2009-08-28 | 2015-11-17 | Makita Corporation | Power tool with continuously-variable transmission traction drive |
US20120080285A1 (en) * | 2010-10-01 | 2012-04-05 | Ho-Tien Chen | Clutch device for a screw driver |
EP2635410B1 (fr) | 2010-11-04 | 2016-10-12 | Milwaukee Electric Tool Corporation | Outil à chocs avec embrayage réglable |
DE102016124694B4 (de) * | 2016-12-16 | 2020-06-10 | Peter Müller | Fügeelemente-Bereitstellungsvorrichtung sowie zugehörige Robotervorrichtung |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB794045A (en) * | 1954-07-28 | 1958-04-30 | Eduard Wille | Motor-driven screwing-in tool for screwing-in and tightening screws or nuts |
US3319494A (en) * | 1964-10-22 | 1967-05-16 | Ingersoll Rand Co | Dual-speed fastener driving tool |
US3430521A (en) * | 1967-06-19 | 1969-03-04 | Ingersoll Rand Co | Power-operated tool having two-speed rotary output |
FR2394373A1 (fr) * | 1977-06-15 | 1979-01-12 | Black & Decker Mfg Co | Instrument motorise faisant fonction de perceuse ou de tournevis |
GB2025290A (en) * | 1978-07-14 | 1980-01-23 | Cooper Ind Inc | Toruque responsive speed shift mechanism for power tool |
DE3720633A1 (de) * | 1986-06-24 | 1988-01-14 | Atlas Copco Ab | Motorisch angetriebenes werkzeug, insbesondere schraub- oder bohrwerkzeug |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1289056A (fr) * | 1970-12-22 | 1972-09-13 | ||
JPS5811462Y2 (ja) * | 1974-09-13 | 1983-03-04 | リョービ株式会社 | デンドウコウグノ ニダンヘンソクソウチ |
JPS546158U (fr) * | 1977-06-14 | 1979-01-16 | ||
JPS54117466U (fr) * | 1978-02-06 | 1979-08-17 | ||
US4328871A (en) * | 1980-01-28 | 1982-05-11 | Sps Technologies, Inc. | Power tool speed and torque control mechanism |
DE3049200C2 (de) * | 1980-12-27 | 1984-04-26 | Volkswagenwerk Ag, 3180 Wolfsburg | Mit einem Wechselstrom-Antriebsmotor ausgerüsteter Schrauber |
DE3214842A1 (de) * | 1982-04-21 | 1983-10-27 | Wagner, Paul-Heinz, 5203 Much | Drehwerkzeug |
DE3342880C2 (de) * | 1983-11-26 | 1987-02-05 | Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt | Einstellbare Drehmomentenbegrenzung für Elektrowerkzeuge |
DE3432376A1 (de) * | 1984-09-03 | 1986-03-13 | Hilti Ag, Schaan | Motorisch betriebenes schraubgeraet |
DE3618024A1 (de) * | 1986-05-28 | 1987-12-03 | Hilti Ag | Elektrowerkzeug mit schaltkupplung |
JPH0639899Y2 (ja) * | 1986-08-08 | 1994-10-19 | 株式会社マキタ | 回転電動工具におけるトルク調整装置 |
-
1988
- 1988-01-23 DE DE3801972A patent/DE3801972A1/de not_active Withdrawn
- 1988-12-23 EP EP88121554A patent/EP0329852B1/fr not_active Expired - Lifetime
- 1988-12-23 DE DE8888121554T patent/DE3883205D1/de not_active Expired - Lifetime
- 1988-12-23 ES ES88121554T patent/ES2042703T3/es not_active Expired - Lifetime
-
1989
- 1989-01-19 JP JP1010970A patent/JP2867031B2/ja not_active Expired - Fee Related
-
1990
- 1990-04-09 US US07/507,094 patent/US4966057A/en not_active Expired - Lifetime
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB794045A (en) * | 1954-07-28 | 1958-04-30 | Eduard Wille | Motor-driven screwing-in tool for screwing-in and tightening screws or nuts |
US3319494A (en) * | 1964-10-22 | 1967-05-16 | Ingersoll Rand Co | Dual-speed fastener driving tool |
US3430521A (en) * | 1967-06-19 | 1969-03-04 | Ingersoll Rand Co | Power-operated tool having two-speed rotary output |
FR2394373A1 (fr) * | 1977-06-15 | 1979-01-12 | Black & Decker Mfg Co | Instrument motorise faisant fonction de perceuse ou de tournevis |
GB2025290A (en) * | 1978-07-14 | 1980-01-23 | Cooper Ind Inc | Toruque responsive speed shift mechanism for power tool |
DE3720633A1 (de) * | 1986-06-24 | 1988-01-14 | Atlas Copco Ab | Motorisch angetriebenes werkzeug, insbesondere schraub- oder bohrwerkzeug |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0404035A2 (fr) * | 1989-06-22 | 1990-12-27 | Wagner, Paul-Heinz | Tournevis motorisé |
EP0404035A3 (fr) * | 1989-06-22 | 1991-09-04 | Wagner, Paul-Heinz | Tournevis motorisé |
FR2658889A1 (fr) * | 1990-02-23 | 1991-08-30 | Atlas Copco Tools Ab | Transmission de puissance a deux vitesses, pour un outil a moteur, notamment sous l'action d'air comprime. |
DE4333599A1 (de) * | 1992-10-01 | 1994-04-07 | Makita Corp | Schraubeneindrehwerkzeug |
US5372206A (en) * | 1992-10-01 | 1994-12-13 | Makita Corporation | Tightening tool |
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 |
EP1092896A1 (fr) * | 1996-09-05 | 2001-04-18 | Black & Decker Inc. | Transmission automatique variable pour outil à main |
FR2996484A1 (fr) * | 2012-10-05 | 2014-04-11 | Renault Georges Ets | Dispositif de vissage comprenant au moins une roue-libre solidaire du carter |
WO2018011203A1 (fr) * | 2016-07-11 | 2018-01-18 | Robert Bosch Gmbh | Système de machine-outil portative |
US11148275B2 (en) | 2016-07-11 | 2021-10-19 | Robert Bosch Gmbh | Hand-held power-tool device |
EP4008488A1 (fr) * | 2016-07-11 | 2022-06-08 | Robert Bosch GmbH | Dispositif de machine-outil à main |
Also Published As
Publication number | Publication date |
---|---|
JP2867031B2 (ja) | 1999-03-08 |
EP0329852B1 (fr) | 1993-08-11 |
JPH01234175A (ja) | 1989-09-19 |
DE3883205D1 (de) | 1993-09-16 |
EP0329852A3 (en) | 1990-09-05 |
US4966057A (en) | 1990-10-30 |
ES2042703T3 (es) | 1993-12-16 |
DE3801972A1 (de) | 1989-08-03 |
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Legal Events
Date | Code | Title | Description |
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