EP0404035B1 - Tournevis motorisé - Google Patents

Tournevis motorisé Download PDF

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Publication number
EP0404035B1
EP0404035B1 EP19900111491 EP90111491A EP0404035B1 EP 0404035 B1 EP0404035 B1 EP 0404035B1 EP 19900111491 EP19900111491 EP 19900111491 EP 90111491 A EP90111491 A EP 90111491A EP 0404035 B1 EP0404035 B1 EP 0404035B1
Authority
EP
European Patent Office
Prior art keywords
coupling
power wrench
gear
output shaft
wrench according
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
EP19900111491
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German (de)
English (en)
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EP0404035A2 (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
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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

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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.
  • the supply pressure is measured and the screwdriver is switched to a higher torque when the supply pressure exceeds a certain limit.
  • the tightening torque is automatically switched 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 power wrench is known (DE 37 20 633 A1), which 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 fixed 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 on 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 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 must 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.
  • a power wrench with a torque-dependent manual transmission the type specified in the preamble of claim 1 is known from US-A-3 430 521.
  • the known power screwdriver has a first gear stage containing a planetary gear and a second gear stage arranged in series with the first gear stage.
  • the gear stages form two parallel drive branches that run continuously.
  • the first drive branch can be coupled to the output shaft of the power wrench via a first clutch and the second drive branch can be coupled to the output shaft via a second clutch.
  • the couplings have a coupling body which consists of two mutually coupled, counter-rotating coupling parts which are mounted on the output shaft so as to be displaceable in the axial direction and can be brought into engagement with corresponding coupling parts of the two coupling branches.
  • the coupling surfaces of the coupling parts are tooth-shaped.
  • the inner clutch part When a certain limit torque is exceeded, the inner clutch part is pushed back on the output shaft, so that one clutch is disengaged.
  • the outer clutch part which is coupled to the inner clutch part, is advanced so that the other clutch is engaged and the output shaft rotates at a lower speed and greater torque.
  • a disadvantage of the known power screwdriver is that a relatively complex mechanism is required in order to be able to switch the power screwdriver back from the gear position with lower speed and greater torque back to the gear position with higher speed and smaller torque.
  • 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.
  • two separate drive branches with different transmission ratios are available for transmission of the torque, which run continuously. 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 gearbox is always reduced regardless of the torque of the power wrench via a first gear stage. If 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. As soon as a certain limit torque is exceeded, 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.
  • planetary gears enable a compact tubular construction of the torque-dependent clutch with a low weight.
  • a guide curve is 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 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.
  • 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 a non-circular one Web are 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 carrier track 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 wrench 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 housed in a separate housing with a handle 3.
  • a torque-controlled 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-controlled 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 thereto 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 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 extension 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 extending 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 the 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.
  • 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 at 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. For each ball 34 there is a recess 61 and all recesses are arranged such that all balls 34 can be located in the associated recess at the same time, as shown in FIG. 5.
  • 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 into the blind bores 50 against the spring forces, increased security of the clutch against damage is achieved. Furthermore, drive shocks are prevented from being transmitted during the switching process.
  • the idle track 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 shifts 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 downstream planetary gear 26, 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.
  • Fig. 7 shows the functional diagram of a second embodiment of the torque-operated manual transmission.
  • 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 coupling 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 to the end of the pin 79 which projects into the interior of the housing.
  • the balls 83 located in the ball track 82 engage in recesses 84 of the movable coupling part.
  • the sliding piece 81 is moved against the force of the spring 46 towards 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 achieves a compact design of the torque-controlled 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 biased 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 moves in the axial direction, the claws 49, 49 'of the second coupling 48 engage and the balls 34 of the first coupling 32 slip 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 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, increased security of the clutch against damage is achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Structure Of Transmissions (AREA)
  • Transmission Devices (AREA)

Claims (13)

  1. Tournevis motorisé avec un mécanisme de changement de vitesse actionné en fonction du couple de rotation, comprenant :
    - un premier étage de transmission (21') avec un rapport de transmission fixe, qui comprend un premier train d'engrenages planétaires (21),
    - un second étage de transmission (26'), placé en série avec le premier étage de transmission (21'), et qui se trouve dans l'un de deux branchements d'entraînement parallèles (11, 12), les deux étant entraînés en permanence
    - et un premier et un second embrayages (32, 48) avec une partie d'embrayage (36), qui peut prendre deux positions, qui est précontrainte sur l'une de ces positions et qui prend l'autre position lors du dépassement d'un couple de rotation limite, dans lequel la sortie du premier étage de transmission (21') peut être accouplée à la prise de force (38) à travers le premier branchement d'entraînement (12) contenant le premier embrayage (32) et à travers le second branchement d'entraînement (11) contenant le second embrayage (48) et le second étage de transmission (26'), et dans lequel seulement l'un des deux embrayages (32, 48) est enclenché pour chacune des deux positions de la partie d'embrayage (36)
       caractérisé en ce que,
       la partie d'embrayage commune (36) est accouplée à la prise de force (38) par au moins un élément de guidage (41) s'engageant dans une courbe de guidage (39), de telle façon que la partie d'embrayage commune (36), lors du dépassement d'un couple limite, soit déplacée axialement par la courbe de guidage (39) pour l'accouplement du second embrayage (48).
  2. Tournevis motorisé selon la revendication 1, caractérisé en ce que la courbe de guidage (39) délimite une ouverture triangulaire (40), contre un angle de laquelle est appuyé l'élément de guidage (41) par une tension initiale axiale et qui est symétrique par rapport à l'axe de la prise de force (38).
  3. Tournevis motorisé selon la revendication 1 ou 2, caractérisé en ce que la courbe de guidage (39) est prévue sur la prise de force (38) et l'élément de guidage est prévu sur la partie d'embrayage (36).
  4. Tournevis motorisé selon l'une des revendications 1 à 3, caractérisé en ce que le second embrayage (48) dans le second branchement d'entraînement est disposé du côté de la prise de force du second étage de transmission (26').
  5. Tournevis motorisé selon l'une des revendications 1 à 3, caractérisé en ce que le second embrayage (48) dans le second branchement d'entraînement est disposé du côté de l'entraînement du second étage de transmission (26').
  6. Tournevis motorisé selon l'une des revendications 1 à 5, caractérisé en ce que le premier embrayage (32) comprend au moins un encliquetage à bille (33) prévu sur la partie d'embrayage (36), et dont la bille (34) s'engage dans une glissière d'entraînement (35), pourvue d'évidements (61), d'un corps d'embrayage (31) relié à la cage de transmission planétaire (29) du premier train d'engrenages planétaires (21).
  7. Tournevis motorisé selon la revendication 6, caractérisé en ce que le premier embrayage (32) présente une glissière de marche à vide (47) adjacente à la glissière d'entraînement (35) du corps d'embrayage (31), qui reçoit les billes (34), quand le second embrayage (48) est enclenché.
  8. Tournevis motorisé selon la revendication 6 ou 7, caractérisé en ce que la cage de transmission planétaire (29) du premier train d'engrenages planétaires présente un arbre de sortie (24) s'étendant coaxialement par rapport à l'arbre d'entraînement (19), lequel arbre de sortie présente une saillie (30) s'étendant au-delà du second étage de transmission, et sur laquelle le corps d'embrayage (31) est fixé.
  9. Tournevis motorisé selon l'une des revendications 1 à 8, caractérisé en ce que le second étage de transmission (26') est formé par un deuxième train d'engrenages planétaires (26) et en ce que les roues planétaires (22, 27) des premier et deuxième trains d'engrenages planétaires (21, 26) engrènent avec la denture intérieure (17) d'une couronne commune de train planétaire.
  10. Tournevis motorisé selon la revendication 9, caractérisé en ce que la couronne de train planétaire est constituée par la carcasse (5) du tournevis motorisé.
  11. Tournevis motorisé selon la revendication 10, caractérisé en ce que la carcasse (5) du tournevis motorisé est montée rotative sur palier, et en ce que la carcasse (5) présente un tronçon profilé (8) pour la fixation d'un pied d'appui, qui soutient la carcasse en prenant un appui solide fixe.
  12. Tournevis motorisé selon l'une des revendications 1 à 11, caractérisé en ce que la prise de force (38) porte la roue solaire d'un troisième train d'engrenages planétaires (76) placé en aval du mécanisme de changement de vitesse.
  13. Tournevis motorisé selon l'une des revendications 1 à 12, caractérisé en ce qu'il est prévu, dans le mécanisme de changement de vitesse (4), un dispositif d'arrêt (77) bloquant la partie d'embrayage mobile (36) dans l'une des deux positions .
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 EP0404035A2 (fr) 1990-12-27
EP0404035A3 EP0404035A3 (fr) 1991-09-04
EP0404035B1 true EP0404035B1 (fr) 1994-08-31

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EP19900111491 Expired - Lifetime EP0404035B1 (fr) 1989-06-22 1990-06-19 Tournevis motorisé

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

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US9193053B2 (en) 2008-09-25 2015-11-24 Black & Decker Inc. Hybrid impact tool
US8631880B2 (en) 2009-04-30 2014-01-21 Black & Decker Inc. Power tool with impact mechanism
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
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

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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
DE3801972A1 (de) * 1988-01-23 1989-08-03 Wagner Paul Heinz Kraftschrauber

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7314097B2 (en) 2005-02-24 2008-01-01 Black & Decker Inc. Hammer drill with a mode changeover mechanism
US9233461B2 (en) 2012-02-27 2016-01-12 Black & Decker Inc. Tool having multi-speed compound planetary transmission
US10195731B2 (en) 2012-02-27 2019-02-05 Black & Decker Inc. Tool having compound planetary transmission

Also Published As

Publication number Publication date
EP0404035A2 (fr) 1990-12-27
JPH03117568A (ja) 1991-05-20
DE3920471C1 (fr) 1990-09-27
EP0404035A3 (fr) 1991-09-04

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