EP1391269B1 - Outil à main, notamment tournevis - Google Patents

Outil à main, notamment tournevis Download PDF

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Publication number
EP1391269B1
EP1391269B1 EP20030013591 EP03013591A EP1391269B1 EP 1391269 B1 EP1391269 B1 EP 1391269B1 EP 20030013591 EP20030013591 EP 20030013591 EP 03013591 A EP03013591 A EP 03013591A EP 1391269 B1 EP1391269 B1 EP 1391269B1
Authority
EP
European Patent Office
Prior art keywords
ring
ring gear
inclined surface
gear
locating
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
EP20030013591
Other languages
German (de)
English (en)
Other versions
EP1391269A2 (fr
EP1391269A3 (fr
Inventor
Bernd Fleischmann
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.)
Festool GmbH
Original Assignee
Festool 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 Festool GmbH filed Critical Festool GmbH
Publication of EP1391269A2 publication Critical patent/EP1391269A2/fr
Publication of EP1391269A3 publication Critical patent/EP1391269A3/fr
Application granted granted Critical
Publication of EP1391269B1 publication Critical patent/EP1391269B1/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
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings

Definitions

  • the invention relates to a power tool, such as screwdriver, with a machine engine and a drive from a drive motor to a rotational movement drivable, connectable with a tool drive shaft
  • the transmission contains at least one epicyclic gear with a rolling off in operation on the internal ring gear of a ring gear Getrieberädanördnung and wherein the ring gear is associated with a safety device which loaded by spring force to the ring gear, movably mounted detent balls which are in Verrastungseihgriff the occurrence of with respect to a turn-off torque smaller torques on the ring gear with the ring gear and hold it against rotation and upon reaching the Shut-off torque from the ring gear against the spring force are displaced from its engaged position, so that the ring gear can mecanicrehschen the locking balls ring gear is enclosed by a machine-mounted bearing ring, which on the Umfan g arranged distributed, in the radial direction through bearing recesses for receiving in each case a detent ball, wherein the wall
  • a safety device of the type mentioned can be provided, which operates depending on the torque.
  • the torque required for screwing is transmitted to the drive shaft by supporting the gear wheel arrangement on the ring gear.
  • the ring gear is held against rotation by the locking balls latched to it.
  • the turn-off torque exerted by the ring gear on the detent balls force is so large that the detent balls back against the spring force, so that the ring gear is no longer held but driven by the gear assembly to a rotary motion.
  • the present invention has for its object, the backup device as simple and inexpensive and in such a way to design that the turn-off torque can be adjusted by the user in handling simple manner and adapted to the particular application.
  • the bearing ring is enclosed by a support ring movable in the axial direction, which is loaded by the spring force in the axial direction and held by an oblique surface arrangement against the detent recesses protruding from the other and the ring gear resting balls, that the support ring rotatable from the outside to the power tool is arranged and that the inclined surface arrangement of distributed over the circumference, each associated with a detent ball and extending in the circumferential direction inclined surface areas is formed, within which viewed in cross-section oblique surface slope changes in the circumferential direction, so that depending on the rotational position of the support ring, the inclined surface areas with a rest on the rest of the detent balls.
  • the spring force exerted in the axial direction on the support ring is deflected so that the detent balls resting against the inclined surface areas are acted upon inwardly toward the ring gear.
  • the inclined surface pitch determines the force exerted on the detent balls. Therefore, the detent balls are held depending on the rotational position of the support ring with a different force against the ring gear. In this way, the turn-off torque can be changed and adapted to the particular application.
  • the handling is very simple, since the support ring only has to be twisted.
  • hand tool 1 is a screwdriver. However, it could also be, for example, a drill or other machine, with which a tool is driven to a rotational movement.
  • the power tool 1 includes a machine engine, not shown, and a drive shaft 2 drivable by the engine via a gear, which can be rotatably connected to a tool, not shown, for example, a screw-in tool in the form of a bit.
  • the drive shaft 2 performs a rotational movement with the tool about the axis of rotation of the drive shaft 2 corresponding Rotationsachsline 3 from.
  • the transmission includes an epicyclic gear stage 4 (there may be a plurality of gear stages connected in series), which is formed by a planetary gear with a central sun gear 5, three planet gears 6 distributed over the circumference and a ring gear 8 having an internal ring gear 7.
  • the sun gear 5 and the planetary gears 6, the respective external gears are not shown for simplicity, so that these wheels are drawn only as circles.
  • the sun gear 5 is non-rotatably mounted on the motor shaft 9 or another shaft driven by the machine motor and meshes with the planetary gears 6 arranged around the sun gear 5, which roll on the radially inner ring gear 7 of the ring gear 8.
  • the Planetenradachsen 10 are components of the otherwise not shown web of the planetary gear, via which the subsequent gear stage or the drive shaft 2 is driven.
  • the design and operation of such a planetary gear is well known, so that a further description is unnecessary. It is merely noted that in normal operation, the planetary gears 6, depending on the direction of rotation of the drive shaft 2, for example, in the direction of arrow 11 revolve around the sun gear 11. In this case, the transmitted via the Planetenradachsen 10 and the web of the planetary gear torque is absorbed by the ring gear 8.
  • the ring gear 8 is associated with a safety device.
  • This safety device has a machine-mounted, the ring gear 8 enclosing bearing ring 13, which distributed over the circumference, arranged in the radial direction bearing recesses 14 includes, each receiving a detent ball 15 movable in the radial direction.
  • the wall thickness of the bearing ring 13 is smaller than the diameter of the detent ball 15.
  • the detent balls 15 are in normal operation below the turn-off torque with the ring gear 8 in latching engagement, so that the ring gear 8 is held against rotation ( Figures 2, 3 and 9) ,
  • Each detent ball 15 is associated with such a recess 16.
  • the ring gear 8 has six bearing recesses 16. In contrast, only three locking balls 15 are present, so that only three locking recesses 16 are occupied by a detent ball 15.
  • the locking between the locking balls 15 and the recesses 16 is formed so that the ring gear 8 exerts an outwardly directed force on the locking balls 15.
  • the circumferentially opposite flanks 17, 18 of the recesses 16 are inclined accordingly.
  • the detent balls 15 are loaded by means of a spring force to the ring gear 8, so that they protrude when the machine and during normal operation under the spring force at the ring gear 8 facing inside of the bearing ring 13 from the bearing recesses 14 and engage in the recesses 16.
  • the spring force does not act directly but via a support ring 19 on the locking balls 15.
  • the support ring 19 surrounds the bearing ring 13 and is arranged to be movable in the axial direction. In this case, the support ring 19 is acted upon in the axial direction by the spring force.
  • the support ring 19 further has a locking balls 15 facing inclined surface arrangement 20, with which the support ring 19 abuts against the bearing balls 15.
  • the locking balls 15 are not only inside but also outside of the recesses 16, so that the inclined surface 20 can rest under the spring force in the axial direction of the locking balls 15. In this case, a force deflection takes place on the inclined surface arrangement 20, so that a radially directed force component acts on the locking balls 15.
  • the force with which the support ring 19 acts on the locking balls 15 and thus determines the turn-off torque depends not only on the spring force but also on the in cross-section ( Figures 3 to 10) seen slope of the inclined surface arrangement.
  • the turn-off torque is adjustable.
  • the support ring 19 is rotatably arranged on the hand tool 1 from the outside.
  • the oblique surface arrangement of distributed over the circumference, each associated with a detent ball 15 and extending in the circumferential direction inclined surface regions 21, 22, 23 are formed, within which in the circumferential direction seen in cross-section inclined surface pitch changed.
  • Figures 6 to 8 which show the support ring 19 at three within the same inclined surface region 21 at a distance in the circumferential direction to each other arranged locations.
  • the three inclined surface regions 21, 22, 23 are identical.
  • the inclined surface portions 21, 22, 23 depending on the rotational position of the support ring 19 with a different pitch on the locking balls 15. Accordingly, depending on the rotational position of the support ring 19, a different turn-off torque is required, in which the locking balls 15 move under axial displacement of the support ring 19 from the recesses 16.
  • the support ring 19 is rotationally fixed, but it is connected in the axial direction movable with a surrounding him adjusting ring 24, which is arranged accessible from the outside to the machine tool, as can be seen from Figure 1.
  • the adjusting ring 24 is rotatable and fixedly mounted in the axial direction on the machine housing.
  • the non-rotatable and thereby axially displaceable connection of the support ring 19 and the adjusting ring 24 with each other can be prepared, for example, that distributed on the outside of the support ring 19 distributed over the circumference, axially directed guide grooves 25 and the adjusting ring 24 in the guide grooves 25 engaging guide ribs 26.
  • the spring force holding the support ring 19 against the detent balls 15 is generated by a spring arrangement formed in the embodiment of several distributed over the circumference coil springs 27, which is supported in the axial direction on the one hand on the adjusting ring 24 and on the other hand on the support ring 19.
  • the adjusting ring 24 has a radially inwardly directed annular portion 28 on which the coil springs 27 are supported.
  • a retaining part 29 protruding toward the bearing ring 13 is arranged on the inner circumference of the support ring 19 between the inclined surface regions 21, 22, 23 in each case. Does the support ring 19 such a rotational position, in which the retaining parts 29 are above the locking balls 15, the retaining portions 29 prevent leakage of the locking balls 15 from the recesses 16 of the ring gear 8, so that the locking balls 15 regardless of the torque occurring on the ring gear 8 be held in their latched with the ring gear position.
  • the support ring 19 should move so fast as far in the axial direction that over the detent balls 15 sufficient space for their exit from the recesses 16 is created.
  • the path of movement of the support ring 19 is from the slope of the inclined surface arrangement measured with respect to the axial direction 20 dependent. The smaller this slope is, the longer is the path of movement of the support ring 19. A smaller pitch corresponds to a larger turn-off torque. Therefore, a safety device designed for larger turn-off torques, if no further measures are provided, switches more slowly than a safety device designed for smaller turn-off torques.
  • the planetary gear on three planet gears In the described embodiment, the planetary gear on three planet gears. It is understood that a different number of planetary gears could be present.
  • bearing recesses 16 and three locking balls 15 instead of six bearing recesses 16 and three locking balls 15, more or fewer bearing recesses or detent balls are also possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Retarders (AREA)
  • Rolling Contact Bearings (AREA)

Claims (6)

  1. Outil à main, en particulier tournevis, avec un moteur de machine et un arbre d'entraînement pouvant être entraîné depuis le moteur de machine par l'intermédiaire d'un mécanisme et pouvant être relié à un outil, dans lequel le mécanisme comprend au moins un étage d'engrenage planétaire avec un ensemble d'engrenages roulant en service sur la couronne dentée intérieure d'une roue creuse et dans lequel un dispositif de sécurisation est associé à la roue creuse, dispositif qui présente des billes de crantage montées mobiles et contraintes par un ressort en direction de la roue creuse, billes qui, si le couple de rotation sur la roue creuse est inférieur à un couple de rotation d'arrêt, se placent en prise de crantage avec la roue creuse et tiennent celle-ci d'une manière fixe en rotation et qui, quand on atteint le couple de rotation d'arrêt, sont repoussées par la roue creuse hors de leur position de prise contre la force du ressort, de sorte que la roue creuse peut passer devant les billes de crantage, la roue creuse (8) étant entourée d'une bague palier (13) placée fixe sur la machine, qui présente des évidements de soutien (14) répartis sur la circonférence continus dans la direction radiale afin de recevoir chacun une bille de crantage (15), l'épaisseur de paroi de la bague palier (13) étant inférieure au diamètre des billes de crantage (15), des évidements de crantage (16) associés aux billes de crantage (15) étant placés sur la circonférence extérieure de la roue creuse (8), caractérisé en ce que la bague palier (13) est entourée d'une bague de soutien (19) mobile dans la direction axiale, qui est contrainte dans la direction axiale par la force d'un ressort et est tenue par l'intermédiaire d'un ensemble à surfaces obliques (20) contre les billes de crantage (15) dépassant des évidements de crantage (16) et s'appuyant d'autre part contre ia roue creuse (8), en ce que la bague de soutien (19) est placée sur l'outil à main de manière à pouvoir être tournée de l'extérieur et en ce que l'ensemble de surfaces obliques (20) est formé par des zones de surface oblique (21, 22, 23) réparties sur la circonférence, associée chacune à une bille de crantage (15) et s'étendant dans la direction circonférentielle, à l'intérieur desquelles l'inclinaison des surfaces obliques vue en coupe transversale change dans la direction circonférentielle, de sorte que, selon la position de rotation de la bague de soutien (19), les zones de surface oblique (21, 22, 23) s'appuient avec une pente différente contre les billes de crantage (15).
  2. Outil à main selon la revendication 1, caractérisé en ce que, dans la direction axiale, les zones de surface oblique (21, 22, 23) sont suivies à chaque fois d'une zone de surface inclinée (30) s'étendant dans la direction circonférentielle le long de la zone de surface oblique concernée, les zones de surface inclinée (30) présentant dans la direction axiale une inclinaison plus grande que les zones de surface oblique (21, 22, 23).
  3. Outil à main selon la revendication 1 ou 2, caractérisé en ce que la bague de soutien (19) présente, dans la direction axiale à la suite des zones de surface oblique (21, 22, 23) resp. des zones de surface inclinée (30), une partie annulaire (32) en saillie dans la direction axiale, en tant que sécurité contre une chute des billes de crantage (15).
  4. Outil à main selon l'une des revendications 1 à 3, caractérisé en ce que sur la circonférence intérieure de la bague de soutien (19), dans la direction circonférentielle entre les zones de surface oblique (21, 22, 23), est placée à chaque fois une partie de retenue (29) formant saillie en direction de la bague palier (13), de sorte que, les parties de retenue (29) étant tournées sur les billes de crantage (15), les billes de crantage (15) sont tenues dans les évidements de crantage (16) de la roue creuse (8) indépendamment du couple de rotation présent sur la roue creuse (8).
  5. Outil à main selon l'une des revendications 1 à 4, caractérisé en ce que la bague de soutien (19) est reliée de manière fixe en rotation, mais mobile axialement, à une bague de réglage (24) l'entourant, accessible de l'extérieur, pouvant tourner et montée fixe axialement, un système de ressort (27) produisant la force de ressort s'appuyant d'un côté sur la bague de réglage (24) et de l'autre côté sur la bague de soutien (19).
  6. Outil à main selon la revendication 5, caractérisé en ce qu'à l'extérieur sur la bague de soutien (19) ou à l'intérieur sur la bague de réglage sont placées des rainures de guidage (26) orientées axialement et réparties sur la circonférence, et sur la bague de réglage (24) ou la bague de soutien sont placées des membrures de guidage (26) s'engageant dans les rainures de guidage (25).
EP20030013591 2002-08-21 2003-06-14 Outil à main, notamment tournevis Expired - Lifetime EP1391269B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10239483 2002-08-21
DE2002139483 DE10239483B3 (de) 2002-08-21 2002-08-21 Handwerkzeugmaschine, beispielsweise Schrauber

Publications (3)

Publication Number Publication Date
EP1391269A2 EP1391269A2 (fr) 2004-02-25
EP1391269A3 EP1391269A3 (fr) 2006-05-10
EP1391269B1 true EP1391269B1 (fr) 2007-03-14

Family

ID=30775569

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20030013591 Expired - Lifetime EP1391269B1 (fr) 2002-08-21 2003-06-14 Outil à main, notamment tournevis

Country Status (2)

Country Link
EP (1) EP1391269B1 (fr)
DE (2) DE10239483B3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE502005004301D1 (de) 2005-11-18 2008-07-10 Metabowerke Gmbh Elektromotorisch angetriebenes Schraub-oder Bohrwerkzeuggerät mit Planetengetriebe
CN101396811B (zh) * 2007-09-28 2012-04-25 苏州宝时得电动工具有限公司 动力工具
CN102748443B (zh) * 2012-06-01 2015-08-26 李飞宇 行星齿轮过载保护装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1860599U (de) * 1962-08-10 1962-10-18 Metabowerke Kg Elektrisch betriebenes schraubwerkzeug.
DE2409815A1 (de) * 1974-03-01 1975-09-11 Bosch Gmbh Robert Kraftschrauber mit abschalteinrichtung
US4448098A (en) * 1982-03-10 1984-05-15 Katsuyuki Totsu Electrically driven screw-driver
DE3636301A1 (de) * 1986-10-24 1988-04-28 Steinel Gmbh & Co Kg Handwerkszeug
NL9101335A (nl) * 1991-08-02 1993-03-01 Emerson Electric Co Transmissie voor elektrisch aangedreven gereedschap.
US5897454A (en) * 1996-01-31 1999-04-27 Black & Decker Inc. Automatic variable transmission for power tool
DE19902187A1 (de) * 1998-03-04 1999-09-16 Scintilla Ag Gangumschaltbares Planetengetriebe

Also Published As

Publication number Publication date
DE10239483B3 (de) 2004-03-04
EP1391269A2 (fr) 2004-02-25
DE50306785D1 (de) 2007-04-26
EP1391269A3 (fr) 2006-05-10

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