EP1946892B1 - Clé à chocs - Google Patents

Clé à chocs Download PDF

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Publication number
EP1946892B1
EP1946892B1 EP20070022437 EP07022437A EP1946892B1 EP 1946892 B1 EP1946892 B1 EP 1946892B1 EP 20070022437 EP20070022437 EP 20070022437 EP 07022437 A EP07022437 A EP 07022437A EP 1946892 B1 EP1946892 B1 EP 1946892B1
Authority
EP
European Patent Office
Prior art keywords
impact
drive shaft
switch ring
output shaft
impact wrench
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.)
Active
Application number
EP20070022437
Other languages
German (de)
English (en)
Other versions
EP1946892A3 (fr
EP1946892A2 (fr
Inventor
Bernd Fleischmann
Jens Zieger
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.)
Protool GmbH
Original Assignee
Protool GmbH
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 Protool GmbH filed Critical Protool GmbH
Publication of EP1946892A2 publication Critical patent/EP1946892A2/fr
Publication of EP1946892A3 publication Critical patent/EP1946892A3/fr
Application granted granted Critical
Publication of EP1946892B1 publication Critical patent/EP1946892B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket

Definitions

  • the invention relates to a switchable from impact operation to non-impact operation impact wrench according to the preamble of claim 1.
  • a switchable from impact operation to non-impact operation impact wrench according to the preamble of claim 1.
  • Such a device is known from EP 1 574 294 A known.
  • Impact wrenches are used for tightening screws or loosening tightened screws.
  • the impact wrench is attached to the respective screw and in operated according to the tightening or loosening corresponding direction of rotation, so that in the impact mode when the limit counter-torque occurs consecutive, pulse-like blows in the circumferential direction on the output shaft and thus exerted on the screw.
  • One from the EP 1050381 A2 known impact wrench can be switched from the described impact mode to a non-impact operation by the output shaft is always connected to the drive shaft, regardless of the torque acting on them counter torque, so that the impact wrench works like a normal screwdriver, in which no impact function is integrated.
  • a drive shaft in the axial direction enforcing switching pin is present, which is advanced to switch from the impact mode to the non-impact mode, so that it comes into rotationally fixed engagement with the output shaft and this directly rotatably connected to the drive shaft.
  • the present invention has for its object to provide an impact wrench of the type mentioned, with a simple and stable structure and easy to handle manner of impact operation on the non-impact operation can be switched and allowed in non-impact operation, the transmission of relatively large torques.
  • the impactor is locked in non-impact mode on the switching ring with the drive shaft, so that the impactor no longer rotate relative to the drive shaft and thus can not shift axially. Therefore, the impactor can no longer dodge as it were and get out of engagement with the output shaft when acting on the output shaft of the limiting counter-torque. Therefore, the output shaft is always connected rotationally fixed to the drive shaft.
  • the switching ring may have a relatively large diameter, so that correspondingly large torques can be transmitted.
  • the impact wrench 1 is designed as a cordless device.
  • a receptacle for a battery pack is arranged at the bottom of the handle 7.
  • the impact wrench could also be operated with mains power.
  • a user-actuated push-button 10 is arranged at the front, via which a lying in the power supply operating switch 11 is actuated.
  • the output shaft 5 is at the front of the device housing 6 in front of this and can be connected to a turning tool for screwing or unscrewing a screw.
  • the protruding output shaft portion 12 is formed as a square shaft 13 and includes a polygonal recess 14 extending from its end face.
  • a conventional socket wrench can be attached to the square shaft 13 in a non-rotatable manner, which has a polygonal receptacle for the non-rotatable insertion of a polygonal screw head.
  • a socket wrench can also be attached to the square shank a header, on which in turn a turning tool can be set.
  • the polygonal recess 14, however, can be used for the rotationally fixed insertion of a bit-like turning tool.
  • the impact wrench 1 is switchable from a beating operation to a non-impact operation.
  • the output shaft 5 is independent of the applied torque or regardless of the incoming or ausuformenden from the screw acting on the output shaft counter torque non-rotatably connected without interruption to the drive shaft, so that the impact wrench 1 works like a conventional screwdriver without impact function.
  • the output shaft 5 can be selectively driven in both directions of rotation.
  • the output shaft 5 is rotatably supported relative to the drive shaft 4.
  • the drive shaft 4 on its output shaft 5 side facing a bearing extension 16 which engages in a bearing recess 15 of the output shaft 5 rotatably.
  • the output shaft 5 is rotatably supported in the device housing 6 by means of a pivot bearing 17 arranged on its outer circumference.
  • the output shaft 5 also has at least one, advantageously a plurality of, in particular two diametrically opposed, radially outwardly projecting output drive projections 18, 19 (see in particular the FIGS. 2, 3 and 6 ), so that in the circumferential direction between the output driving projections 18, 19 spaces 20, 21 are formed.
  • a concentric with the drive shaft 4 arranged impactor 22 is mounted, which is in a manner to be described in driving connection with the drive shaft 4, but it can perform on the drive shaft 4 an axial movement with superimposed rotary motion.
  • the impactor 22 is acted upon by a spring force applied by a coil spring 23 in the direction of the output shaft 5 and takes except in the impact mode when acting on the limit counter-torque excess counter-torque under the spring force to the output shaft 5 down forward a forward position, which in the Drawing is shown. In this front position, the striker 22 is in rotational engagement with the output shaft 5.
  • the striker 22 at its output shaft 5 facing end in the number of output driving projections 18, 19 of the output shaft 5 corresponding drive driving projections 24, 25, the protrude in the axial direction of the impactor body 22 and engage in the front position of the impactor body 22 in each case in one of the intermediate spaces 20, 21 between the output drive projections 18, 19.
  • the driving entrainment projections 24, 25 have a smaller circumferential extent than the intermediate spaces 20, 21 between the driven entrainment projections 18, 19, so that the impactor body 22 and the output shaft 5 are relatively rotatable relative to one another. If the striking body is in its forward position, the driving entrainment projections 24, 25 lie in the direction of rotation of the drive shaft 4 on the driven entrainment projections 18, 19, so that the output shaft 5 is taken in the direction of rotation.
  • the impactor body 22 and the drive shaft 4 are connected to each other via two diametrically opposite cam assemblies 26, 27, each with associated and in the respective control cam assembly 26, 27 engaging control 28, 29 in the form of a control ball 30, 31.
  • two cam arrangements would suffice.
  • each control cam arrangement 26, 27 has a V-shaped extending control groove 32 on the outer circumference of the drive shaft 4, in which the respective control ball 30, 31 engages.
  • the tip of the V-shape of the cam groove 32 faces the output shaft 5.
  • the respective control ball 30, 31 protrudes from the relevant control groove 32 of the drive shaft 4 and abuts a respective control surface 33 on the inner periphery of the impactor 22.
  • FIG. 7 is the control surface 33 indicated by dash-dotted lines.
  • the control surface 33 is formed on the inner circumference of the impactor body 22 at the transition to an extension 34, facing the output shaft 5, of the inner cross-section of the impactor body 22.
  • the control surface 33 also has a V-shaped profile, wherein the tip of the V, however, faces away from the output shaft 5.
  • a control groove corresponding course could be provided on the inner periphery of the impactor 22.
  • the striking body 22 during impact operation when the output shaft 5 from the outside a larger counter-torque than the limit counter-torque is applied, against the spring force axial movement to the rear with superimposed Rotary movement relative to the drive shaft 4, so that the striking body 22 rotates past the output shaft 5 and then again under the spring force forward to the front position and thereby with its drive-driving projections 24, 25 in the spaces 20, 21 against the output driving projections 18, 19 of the output shaft 5 is moved, so that in the circumferential direction a blow to the output driving projections 18, 19 and thus exerted on the output shaft 5.
  • a switching ring 35 is present, which can be actuated by means of an actuating device 36 from the outside and between an impact position associated with the inoperative position and the non-impact operation associated effective position.
  • the switching ring 35 is arranged radially outside of the drive shaft 4 concentric with this.
  • the switching ring 35 is rotatably mounted on a rotatably connected to the drive shaft 4 switching ring bearing part 37 and axially displaceable. In its inoperative position ( Figures 2 . 4 and 5 ) is the switching ring 35 away from the impactor 22, so that the impactor 22 is unaffected by the switching ring 35.
  • the switching ring 35 moves you the switching ring 35, however, in its operative position toward the impactor 22 back, the switching ring 35 comes into rotationally fixed locking engagement with the impactor 22.
  • the switching ring 35 a plurality of distributed over the circumference, the impactor 22 projecting toward locking projections 38 on (in principle, only such a locking projection 38 could be present).
  • Each locking projection 38 is assigned a arranged at the facing end of the impactor 22 locking recess 39.
  • the locking projections 38 engage in the locking recesses 39, so that the striking body 22 is rotatably connected to the switching ring 35.
  • the arrangement could also be made so that the locking projections on the striker and the locking recesses are arranged on the switching ring.
  • Another advantage of the impact wrench 1 is that the impactor body 22 in the inoperative position of the switching ring 35 automatically off such a rotational position relative to the switching ring 35 assumes that the locking recesses 39 of the impactor 22 in the axial direction in alignment with the locking projections 38 of the switching ring 35 are arranged so that the switching ring 35 immediately enters his locking into the operative position with its locking projections 38 in the locking recesses 39 of the impactor body 22 and no further manipulations are required to bring the locking projections 38 and the locking recesses 39 in an aligned position.
  • the end face regions 40, 41 of the striking body 22 arranged between two respective locking recesses 39 have a course which is recessed with respect to the mouths of the locking recesses 39, so that the aforementioned end face regions 40, 41 form depressions on the end face of the striking body 22. In this way it is avoided that the latching projections 38 of the switching ring 35 can collide with the end face of the impactor 22 in impact mode.
  • the transmission unit 3 includes a drive shaft 4 driving planetary gear.
  • this planetary gearset includes a set of planetary gears 42 distributed over the circumference, which radially inwardly mesh with a sun gear 43 driven by the drive motor 2 and radially outwardly with a ring gear 44 enclosing the set of planetary gears 42.
  • the planetary gears 42 are each rotatably mounted on a Planetenradwelle 45 which project from an annular peripheral web body 46 which is arranged on the impactor 22 side facing the planetary gear 42.
  • the drive shaft 4 is rotatably and axially fixedly connected to the web body 46, so that the drive shaft 4 is driven via the planetary gear.
  • the planetary gear mechanism is a multi-stage, switchable planetary gear.
  • the planetary gear mechanism has a web body facing the striking body 22, that is, the web body 46.
  • This web body 46 is designed such that it also forms the switching ring bearing part 37.
  • the switching ring 35 is rotatably mounted on the outer circumference of the web body 46 and axially displaceable. In this way, no separate switching ring bearing part is required, so that results in a low-part arrangement.
  • the web body 46 has a smaller diameter than the impactor 22, so that the web body 46, as shown in FIGS. 4 and 5 it can be seen, a piece immersed in the impactor 22.
  • groove-like, axially directed guideways 47 are arranged on the outer periphery of the web body 46.
  • the arrangement is suitably made so that the locking projections 38 of the switching ring 35 run radially inward in the guideways 47 and engage in the non-impact operation with its radially outer region in the locking recesses 39 of the impactor body 22.
  • the striker 22 acting on the front coil spring 23 is supported with its rear end on the web body 46, which is arranged fixed in the axial direction.
  • the coil spring 23 rotates during operation of the impact wrench 1 with.
  • the impactor 22 has an open towards the rear, annular circumferential recess 48 into which engages the coil spring 23 and is mounted with the respective end.
  • the web body 46 also forms an annular circumferential recess 49, which is open towards the front and receives the rear end of the coil spring 23. This contributes to the space-saving design. In principle, only one of the two recesses 48, 49, expediently the recess 48 in the impactor 22, could be present.
  • the actuating device 36 with which the switching ring 35 can be displaced, has an externally on the device housing 6 movably arranged actuating element 50, from the movement of the axial displacement movement of the switching ring 35 is derived.
  • the switching ring 35 on its outer circumference on a circumferential annular groove 51 into which a suitably U-like switching bracket 52 engages, which preferably consists of wire material.
  • the switch bracket 52 is movable in the axial direction and is actuated by means of the actuating element 50.
  • the switching bracket 52 During operation of the impact wrench 1, the switching bracket 52 remains in the direction of rotation, and the switching ring 35 rotates past the switching bracket 52.
  • the actuating element 50 is formed in the expedient embodiment of an annular, rotatably mounted on the housing 6 rotary valve 53 which is connected to the switch bracket 52 so that its rotational movement is converted into the axial displacement movement of the switching ring 35.
  • This movement conversion takes place by means of a flat shape having deflecting part 54, on the one hand carries the switching bracket 52 and on the other hand with the rotary valve 53 in engagement is that the switching bracket 52 and with this the switching ring 35 moves in the axial direction when the rotary valve 53 is rotated.

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

Claims (12)

  1. Clé à chocs commutable du mode de frappe au mode de non frappe, comportant un arbre d'entraînement (4) pouvant être entraîné par moteur, un arbre de sortie (5) logé de manière rotative par rapport à l'arbre d'entraînement (4), disposé de manière coaxiale par rapport à l'arbre d'entraînement (4) et un corps de frappe (22) logé de manière concentrique par rapport à l'arbre d'entraînement sur celui-ci, en liaison de propulsion avec l'arbre d'entraînement (4) et sollicité par une force de ressort dans le sens axial vers l'arbre de sortie (5), lequel corps de frappe (22) est en engagement d'entraînement rotatif avec l'arbre de sortie (5) dans une position avant avancée vers l'arbre de sortie (5) et est relié par au moins un agencement de cames de commande (26, 27) et un élément de commande (28, 29) s'engageant dans celui-ci avec l'arbre d'entraînement (4) de telle manière qu'en mode de frappe, le corps de frappe (22) occupe sa position avant si aucun couple antagoniste ou un plus petit couple antagoniste agit de l'extérieur comme un couple antagoniste limite sur l'arbre de sortie (5), et si le couple antagoniste limite agit de l'extérieur sur l'arbre de sortie (5), réalise un mouvement axial vers l'arrière dans le sens contraire de la force de ressort avec un mouvement rotatif superposé par rapport à l'arbre d'entraînement (4), se tourne devant l'arbre de sortie (5) puis parvient de nouveau dans sa position avant sous la force de ressort et exerce une frappe dans le sens périphérique sur l'arbre de sortie (5), le dispositif de commutation pour la commutation du mode de frappe au mode de non frappe contenant un anneau de commutation (35) actionnable de l'extérieur au moyen d'un dispositif d'actionnement (36), réglable entre une position inactive associée au mode de frappe et une position active associée au mode de non frappe, qui est disposé radialement en dehors de l'arbre d'entraînement (4) de manière concentrique à celui-ci, caractérisée en ce que l'anneau de commutation (35) est logé de manière mobile dans le sens axial et solidaire en rotation sur une partie de palier d'anneau de commutation (37) reliée de manière solidaire en rotation à l'arbre d'entraînement (4) et parvient en engagement de verrouillage fixe en rotation avec le corps de frappe (22) lors du déplacement de sa position inactive n'influençant pas le corps de frappe (22) dans sa position active.
  2. Clé à chocs selon la revendication 1, caractérisée en ce que l'engagement de verrouillage est effectué au moyen d'au moins une saillie de verrouillage (38) sur l'anneau de commutation (35) ou sur le corps de frappe (22) et d'au moins un évidement de verrouillage (39) sur le corps de frappe (22) ou sur l'anneau de commutation (35), le corps de frappe (22) occupant automatiquement dans la position inactive de l'anneau de commutation (35) en cas de clé à chocs désactivée, une telle position rotative par rapport à l'anneau de commutation (35), dans laquelle au moins un évidement de verrouillage (39) ou au moins une saillie de verrouillage est disposée sur le corps de frappe (22) en alignement dans le sens axial avec au moins une saillie de verrouillage (38) ou au moins un évidement de verrouillage (39) sur l'anneau de commutation (35).
  3. Clé à chocs selon la revendication 2, caractérisé en ce qu'au moins un agencement de cames de commande (26, 27) présente une forme en V et en ce que l'élément de commande (28, 29) est formé par une sphère de commande (30, 31) de sorte que la sphère de commande (30, 31) soit disposée dans la position rotative de départ sur la pointe du V respectif.
  4. Clé à chocs selon la revendication 2 ou 3, caractérisé en ce que le corps de frappe (22) présente plusieurs évidements de verrouillage (39) répartis sur la périphérie sur son côté avant tourné vers l'anneau de commutation (35) et en ce que les zones de côté avant (40, 41) du corps de frappe (22) disposées entre respectivement deux évidements de verrouillage (39) présentent un tracé en retrait par rapport aux ouvertures des évidements de verrouillage (39).
  5. Clé à chocs selon l'une quelconque des revendications 1 à 4, caractérisée en ce que l'arbre d'entraînement (4) est entraîné par un engrenage planétaire présentant un corps de traverse (46) tourné vers le corps de frappe (22), relié de manière fixe en rotation et fixe dans le sens axial à l'arbre d'entraînement (4), qui est réalisé comme une partie de palier d'anneau de commutation (37) logeant de manière mobile dans le sens axial et fixe en rotation l'anneau de commutation (35) sur sa périphérie extérieure.
  6. Clé à chocs selon l'une quelconque des revendications 1 à 5, caractérisée en ce que la force de ressort appliquée sur le corps de frappe (22) est appliquée par un ressort cylindrique (23).
  7. Clé à chocs selon la revendication 6, caractérisée en ce que le ressort cylindrique (23) s'appuie contre le corps de traverse (46).
  8. Clé à chocs selon la revendication 7, caractérisée en ce que le corps de frappe (22) et/ou le corps de traverse (46) présente sur son côté avant tourné vers le corps de traverse (46) ou le corps de frappe (22), un évidement rotatif en forme d'anneau (48 ou 49) pour le logement du ressort cylindrique (23).
  9. Clé à chocs selon l'une quelconque des revendications 5 à 8, caractérisée en ce que le corps de traverse (46) présente un diamètre plus petit que celui du corps de frappe (22) et s'enfonce un peu plus loin dans le corps de frappe (22).
  10. Clé à chocs selon l'une quelconque des revendications 1 à 9, caractérisée en ce que le dispositif d'actionnement (36) présente un élément d'actionnement (50) disposé de manière mobile à l'extérieur sur le boîtier de la clé à chocs, du mouvement duquel est dérivé le mouvement axial de l'anneau de commutation (35).
  11. Clé à chocs selon la revendication 10, caractérisée en ce que l'anneau de commutation (35) présente une rainure annulaire rotative (51) sur sa périphérie extérieure, dans laquelle s'engage un étrier de commutation (52) pouvant être actionné à l'aide de l'élément d'actionnement (50), mobile dans le sens axial.
  12. Clé à chocs selon la revendication 11, caractérisée en ce que l'élément d'actionnement (50) est formé par un tiroir rotatif (53) annulaire, logé de manière rotative sur le boîtier (6) de la clé à chocs, qui est relié à l'étrier de commutation (52) de sorte que son mouvement rotatif soit converti en mouvement axial de l'anneau de commutation (35).
EP20070022437 2007-01-20 2007-11-20 Clé à chocs Active EP1946892B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710003037 DE102007003037A1 (de) 2007-01-20 2007-01-20 Schlagschrauber

Publications (3)

Publication Number Publication Date
EP1946892A2 EP1946892A2 (fr) 2008-07-23
EP1946892A3 EP1946892A3 (fr) 2009-06-03
EP1946892B1 true EP1946892B1 (fr) 2011-05-04

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Family Applications (1)

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EP20070022437 Active EP1946892B1 (fr) 2007-01-20 2007-11-20 Clé à chocs

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EP (1) EP1946892B1 (fr)
DE (2) DE102007003037A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9193053B2 (en) * 2008-09-25 2015-11-24 Black & Decker Inc. Hybrid impact tool
CN102019608B (zh) * 2009-09-10 2013-07-03 苏州宝时得电动工具有限公司 动力工具
WO2012002578A1 (fr) * 2010-06-30 2012-01-05 Hitachi Koki Co., Ltd. Outil à percussion
DE102015209406A1 (de) * 2015-05-22 2016-11-24 Robert Bosch Gmbh Handwerkzeugmaschine mit einem mechanischen Drehschlagwerk
DE102017101948A1 (de) 2017-02-01 2018-08-02 Festool Gmbh Schlagschrauber
DE102018118196A1 (de) * 2018-07-27 2020-01-30 Festool Gmbh Hand-Werkzeugmaschine, insbesondere Schlagschrauber

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2828640B2 (ja) * 1988-11-15 1998-11-25 松下電工株式会社 回転衝撃工具
DE4301610C2 (de) * 1993-01-22 1996-08-14 Bosch Gmbh Robert Schlagschrauber
JP3911905B2 (ja) 1999-04-30 2007-05-09 松下電工株式会社 インパクト回転工具
JP4405900B2 (ja) * 2004-03-10 2010-01-27 株式会社マキタ インパクトドライバ
US20060237205A1 (en) * 2005-04-21 2006-10-26 Eastway Fair Company Limited Mode selector mechanism for an impact driver

Also Published As

Publication number Publication date
DE102007003037A1 (de) 2008-07-24
EP1946892A3 (fr) 2009-06-03
DE502007007112D1 (de) 2011-06-16
EP1946892A2 (fr) 2008-07-23

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