EP1923176B1 - Marteau perforateur - Google Patents

Marteau perforateur Download PDF

Info

Publication number
EP1923176B1
EP1923176B1 EP07021608A EP07021608A EP1923176B1 EP 1923176 B1 EP1923176 B1 EP 1923176B1 EP 07021608 A EP07021608 A EP 07021608A EP 07021608 A EP07021608 A EP 07021608A EP 1923176 B1 EP1923176 B1 EP 1923176B1
Authority
EP
European Patent Office
Prior art keywords
motor shaft
tool spindle
hammer
pinion
hammer mechanism
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.)
Not-in-force
Application number
EP07021608A
Other languages
German (de)
English (en)
Other versions
EP1923176A1 (fr
Inventor
Roland Vögele
Rainer Kumpf
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.)
Techtronic Industries GmbH
Original Assignee
AEG Electric Tools 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 AEG Electric Tools GmbH filed Critical AEG Electric Tools GmbH
Publication of EP1923176A1 publication Critical patent/EP1923176A1/fr
Application granted granted Critical
Publication of EP1923176B1 publication Critical patent/EP1923176B1/fr
Not-in-force 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
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the invention relates to a rotary hammer with the features according to the preamble of claim 1.
  • Rotary hammers for hand-held operation have, in a previously known design, a drive motor, a tool spindle rotatably drivable by the drive motor and a hammer mechanism.
  • a drill clamped in a chuck is rotated by the tool spindle.
  • the drive motor which also drives the tool spindle, also operates the hammer mechanism, which applies axial hammer blows to the drill.
  • the drill produces a borehole under the simultaneous action of its rotary motion and its axial hammer blows.
  • a second shaft is arranged parallel to the tool spindle in rotary hammers according to the prior art.
  • the tool spindle is driven by a two-stage gearbox from the drive motor.
  • the drive motor drives the additional shaft via a first gear stage, which in turn drives the tool spindle via a second gear stage.
  • the Intermediate second shaft also serves as a drive for the hammer mill.
  • the tool spindle and hammer mechanism are each driven by a single-stage gear directly from a motor shaft of the drive motor.
  • the motor shaft has two axially mutually offset toothings, namely an end toothing for driving the hammer mechanism, and a worm toothing for driving the tool spindle. From the worm toothing follows a laterally radial offset of the motor shaft to the tool spindle, which requires a correspondingly high space in conjunction with the axial offset of both gears on the motor shaft.
  • the invention has the object of developing a generic rotary hammer such that its volume is reduced.
  • the tool spindle and the hammer mechanism each directly by means of a single-stage gearbox are driven by a motor shaft of the drive motor.
  • the arrangement is free of play, compact, lightweight and inexpensive to produce.
  • the driven gear of the tool spindle is close to or even at the handle end of the tool spindle.
  • On a countershaft can be omitted, so that the gear housing can be made comparatively slim in the tool-near area. This simplifies work in confined spaces. With reduced parts and in particular reduced weight of the center of gravity of the hammer is moved closer to the handle, which improves the ergonomics of working.
  • the single stage gearbox between the motor shaft and the tool spindle is an angular gear formed by a pinion of the motor shaft and a pinion gear of the tool spindle engaged with the pinion.
  • the pinion of the motor shaft has an end toothing, while the ring gear is formed as a crown wheel.
  • the particular designed as a straight tooth spur toothing of the pinion is inexpensive to produce.
  • the formation of the pinion with a spur gear allows the additional drive of the hammer mechanism by means of the same pinion.
  • An axis of rotation of the hammer mechanism is substantially parallel to the motor axis, wherein the single-stage gearbox between the motor shaft and the hammer mechanism by a spur gear is formed.
  • the pinion of the motor shaft with the face gear is both in engagement with the crown wheel of the tool spindle and with a spur gear of the hammer mill. At the motor shaft or its pinion only a single toothing is to be attached. The arrangement is space-saving and inexpensive.
  • a motor shaft of the motor shaft and a spindle axis of the tool spindle are arranged at an angle to each other, wherein the angle is in a range of including 60 ° to 120 ° inclusive and in particular is about 90 °.
  • the angular arrangement of motor axis and spindle axis allows a short design.
  • the speed of the drive motor can be sufficiently reduced to the desired speed of the tool spindle by means of only single-stage gearbox.
  • the pinion of the motor shaft is related to its axial direction at the same height in engagement with the crown gear of the tool spindle and the spur gear of the hammer mill.
  • engagement points of the pinion with the ring gear of the tool spindle and the spur gear of the hammer mill are radially opposite each other with respect to the axial direction of the motor shaft.
  • the forces acting on the pinion, caused by the ring gear and the opposite spur loads act symmetrically and substantially free of eccentricities on the motor shaft.
  • the gearbox and the engine mount are subject to low loads and can be correspondingly small, lightweight and cost-effective dimensioned.
  • the drive motor, the tool spindle and the hammer mechanism are arranged between two housing shells made of plastic, wherein at least one bearing of the motor shaft and at least one bearing of the hammer mechanism are held in a common bearing web, in particular made of light metal, and wherein the bearing web between the two housing shells is fixed.
  • the common bearing bar generates an increased rigidity of the bearing and thus an improved Accuracy of the mutual alignment of the various components.
  • the precision of the mutual alignment of the motor shaft and the directly driven hammer mechanism is improved.
  • the center distance of the motor shaft and hammer mill can be reduced.
  • the required rigidity of the bearing is applied solely by the bearing web, so that for the gear housing, a comparatively soft, impact-resistant plastic can be used.
  • the bearing bar can be inserted together with the remaining parts such as motor armature, tool spindle, hammer mechanism, electrical components or the like in the plastic shells and fixed in a form-fitting or clamping between the two shells.
  • the assembly is simple and inexpensive. The committee during assembly is reduced. The life of the hammer drill is increased.
  • the hammer mechanism is advantageously a pneumatic hammer mechanism with a pressure piston driven by an eccentric wheel and a connecting rod.
  • Fig. 1 shows a longitudinal section through an inventively executed hammer drill.
  • the hammer drill has an electric drive motor 1, a tool spindle 2, which can be driven in rotation by the drive motor 1, and a hammer mechanism 3.
  • the electric drive motor 1 is provided for supply with mains voltage. It can also be a battery operation or the like appropriate. Instead of the electric drive motor 1, an internal combustion engine may also be provided.
  • the hammer drill is shown in its usual operating position, in which it is held and guided by the user by hand.
  • a spindle axis 8 is approximately horizontal, while a motor shaft 6 of the drive motor 1 with its motor shaft 7 is arranged approximately vertically.
  • the motor shaft 7 and the spindle axis 8 are in the illustrated embodiment at an angle ⁇ of 90 ° to each other.
  • the angle ⁇ is advantageously in a range of including 60 ° to 120 ° inclusive.
  • the tool spindle 2 is driven directly by the motor shaft 6 of the drive motor 1 by means of a single-stage gear 4.
  • a pinion 9 is formed integrally with the motor shaft 6, while a ring gear 10 rotatably with the rotatably mounted tool spindle 2 at its handle end or in the immediate vicinity is connected.
  • the pinion 9 and the ring gear 10 together form a single-stage reduction gear in the form of an angular gear in which the pinion 9 of the motor shaft 6 is directly in engagement with the ring gear 10 of the tool spindle 10.
  • the single-stage gear 4 is a reduction gear, in which the operating speed of the drive motor 1 is reduced to a reduced speed of the tool spindle 2.
  • a chuck 27 is arranged for a drill, not shown.
  • the chuck 27 is rotatably connected to the tool spindle 2 and transmits the rotational movement of the tool spindle 2 on the clamped drill.
  • a further single-stage transmission 5 is provided, by means of which the hammer mechanism 3 is driven directly by the motor shaft 6 of the drive motor 1.
  • the hammer mechanism 3 an eccentric 22 with a molded spur gear 14 which meshes directly with the pinion 9 of the motor shaft 6.
  • the single-stage gear 5 between the motor shaft 6 and the hammer mechanism 3 is a geared spur gear, which is formed from the pinion 9 and the spur gear 14.
  • the tool spindle 2 is designed as a hollow tube, in the rear of the chuck 27, a plunger 26, a striker 25 and a pressure piston 24 in the direction of the spindle axis 8 longitudinally displaceable are guided.
  • the hammer mechanism 3 is a pneumatic hammer mechanism, in which the pressure piston 24 carries out an oscillating movement via a connecting rod 23 through the rotationally driven eccentric wheel 22 in the direction of the spindle axis 8. About an air cushion in the hollow tool spindle, this oscillating motion is transmitted to the striker 25, which transmits its impact kinetic energy 26 by the plunger 26 on the clamped, not shown drill when hitting the plunger.
  • the impact movement and the rotational movement of the drill is generated via the two single-stage gear 4, 5 directly from the common pinion 9 of the drive motor 1.
  • Fig. 2 shows an enlarged detail view of the arrangement according to Fig. 1 in the region of the two gear 4, 5.
  • the pinion 9 has a continuous up to the free end spur toothing 11, which is designed in the embodiment shown as a straight toothing. It can also be a helical helical gearing appropriate.
  • the ring gear 10 of the tool spindle 2 is designed as a crown gear 13, the teeth of which engage in the spur toothing 11 at an engagement point 15.
  • the engagement point 15 lies on the chuck 27 ( Fig. 1 ) facing side of the motor shaft. 6
  • the spur gear 14 has on its peripheral side on a straight toothing, not shown, the meshing at an engagement point 16 with the spur toothing 11 of the pinion 9 in engagement stands. Diameter and number of teeth of the spur gear 14 are a multiple of the pinion 9, so that the transmission 5 is a reduction gear, in which the operating speed of the drive motor 1 is reduced to a reduced input rotational speed of the hammer unit 3.
  • the hammer mechanism 3 including its eccentric wheel 22 with the integrally formed spur gear 14 is on the chuck 27 ( Fig. 1 ) facing away from the motor shaft 6 is arranged such that the engagement point 16 is based on the axial direction of the motor shaft 7 at the same height with the engagement point 15 of the transmission 4.
  • the two engagement points 15, 16 of the two single-stage gear 4, 5 are relative to the motor axis 7 opposite each other.
  • the spur toothing 11 is in this case both in engagement with the crown gear 13 at the engagement point 15, as well as in engagement with the spur gear 14 at the engagement point 16th
  • the pinion 9 has the spur toothing 11 in the lower region and a conical toothing in the upper region near the free end.
  • a hub 30 is integrally formed, with the eccentric 22 is rotatably mounted to form a bearing 20 on a bearing pin 29.
  • a central axis of the bearing journal 29 forms an axis of rotation 12 of the hammer mechanism 3, which is parallel to the motor shaft 7 of the motor shaft 6.
  • the Eccentric 22 carries a schematically indicated crank pin 32 which engages in a connecting rod 31 of the connecting rod 23. When driven by the drive motor 1 rotation of the eccentric wheel 22 about the axis of rotation 12 of the crank pin 32 performs a circular path corresponding to an arrow 33.
  • the connecting rod eye 31 experiences an oscillating movement between two end positions indicated by 31 'and 31 ", which are transmitted via the connecting rod 23 to the pressure piston 24 which carries out a corresponding oscillating axial movement and is applied to the striker 25 (FIG. Fig. 1 ) transmits.
  • a machine housing which comprises two housing shells 17, 18 made of plastic.
  • a machine housing which comprises two housing shells 17, 18 made of plastic.
  • a section of an open housing shell 17 is shown, while a second, substantially symmetrical thereto formed housing shell 18 closes the arrangement.
  • a schematically indicated bearing web 21 made of metal, advantageously made of light metal and in particular made of aluminum positively or clamped fixed.
  • the designed as an electric motor drive motor 1 has on its motor shaft 6 on an armature 35, on whose the gear 4, 5 facing end face, a fan 34 is mounted co-rotating.
  • the bearing bar 21 is arranged on the gear 4, 5 facing side of the fan 34.
  • the bearing bar 21 carries the bearing pin 29 of the bearing 20 from the hammer mechanism 3. Furthermore, designed as a rolling bearing 19 for supporting the motor shaft 6 is arranged close to the pinion 9, which is also held in the bearing web 21.
  • the formation of the bearing web 21 of light metal provides a viable and positionally accurate fixation of the bearings 19, 20 against each other at a small radial distance safe. It may also be expedient to fix a gear-near bearing of the tool spindle 2 and / or an axial abutment shoulder of the crown wheel 13 on the bearing web 21.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Boring (AREA)

Claims (7)

  1. Marteau perforateur avec un moteur d'entraînement (1) en particulier électrique, une broche d'outil (2) apte à être entraînée en rotation par le moteur d'entraînement (1), et un mécanisme de percussion (3), la broche d'outil (2) et le mécanisme de percussion (3) étant entraînés chacun à l'aide d'un engrenage à simple démultiplication (4, 5), directement par un arbre (6) du moteur d'entraînement (1),
    caractérisé en ce que l'engrenage à simple démultiplication (4) entre l'arbre de moteur (6) et la broche d'outil (2) est constitué par un engrenage d'angle qui est formé par un pignon (9) de l'arbre de moteur (6) à denture cylindrique (11) et par une couronne dentée (13) de la broche (2) qui est en prise avec le pignon (9), en ce qu'un axe de rotation (12) du mécanisme de percussion (3) est globalement parallèle à l'axe de moteur (7), l'engrenage à simple démultiplication (5) entre l'arbre de moteur (6) et le mécanisme de percussion (3) étant formé par un engrenage cylindrique, et en ce que le pignon (9) de l'arbre de moteur (6) à denture cylindrique (11) est en prise à la fois avec la couronne dentée (13) de la broche d'outil (2) et avec une roue dentée (14) du mécanisme de percussion (3).
  2. Marteau perforateur selon la revendication 1, caractérisé en ce qu'un axe de moteur (7) de l'arbre de moteur (6) et un axe de broche (8) de la broche d'outil (2) sont disposés suivant un angle (α) l'un par rapport à l'autre, l'angle (α) étant situé dans une plage de 60° inclus à 120° inclus et étant en particulier d'environ 90°.
  3. Marteau perforateur selon la revendication 1 ou 2, caractérisé en ce que la denture cylindrique (11) du pignon (9) de l'arbre de moteur (6) est constituée par une denture droite.
  4. Marteau perforateur selon l'une des revendications 1 à 3, caractérisé en ce que le pignon (9) de l'arbre de moteur (6), par rapport à son sens axial, est en prise à la même hauteur avec la couronne dentée (13) de la broche d'outil (2) et avec la roue cylindrique (14) du mécanisme de percussion (3).
  5. Marteau perforateur selon l'une des revendications 1 à 4, caractérisé en ce que les points de prise (15, 16) du pignon (9) avec la couronne dentée (13) de la broche d'outil (2) et avec la roue cylindrique (14) du mécanisme de percussion (3) se font face radialement par rapport au sens axial de l'arbre de moteur (6).
  6. Marteau perforateur selon l'une des revendications 1 à 5, caractérisé en ce que le moteur d'entraînement (1), la broche d'outil (2) et le mécanisme de percussion (3) sont disposés entre deux coques de boîtier (17, 18) en matière plastique, au moins un palier (19) de l'arbre de moteur (6) et au moins un palier (20) du mécanisme de percussion (3) étant supportés dans une branche de montage commune (21) en métal léger, et la branche de montage (21) étant fixée entre les deux coques de boîtier (17, 18).
  7. Marteau perforateur selon l'une des revendications 1 à 6, caractérisé en ce que le mécanisme de percussion (3) est constitué par un mécanisme de percussion pneumatique avec un piston de pression (24) entraîné par une roue d'excentrique (22) et par une bielle (23).
EP07021608A 2006-11-17 2007-11-07 Marteau perforateur Not-in-force EP1923176B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006054288A DE102006054288A1 (de) 2006-11-17 2006-11-17 Bohrhammer

Publications (2)

Publication Number Publication Date
EP1923176A1 EP1923176A1 (fr) 2008-05-21
EP1923176B1 true EP1923176B1 (fr) 2009-09-16

Family

ID=39102931

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07021608A Not-in-force EP1923176B1 (fr) 2006-11-17 2007-11-07 Marteau perforateur

Country Status (4)

Country Link
US (1) US7661485B2 (fr)
EP (1) EP1923176B1 (fr)
CN (1) CN101181783B (fr)
DE (2) DE102006054288A1 (fr)

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DE102008022461B4 (de) 2008-05-08 2010-01-28 Aeg Electric Tools Gmbh Bohrhammer
DE102008022455B4 (de) 2008-05-08 2014-06-26 Aeg Electric Tools Gmbh Bohrhammer
DE102008022454B4 (de) 2008-05-08 2014-06-26 Aeg Electric Tools Gmbh Bohrhammer
DE102008054458A1 (de) 2008-12-10 2010-06-17 Robert Bosch Gmbh Handwerkzeugmaschine
CN102476222B (zh) * 2010-11-24 2014-12-10 南京德朔实业有限公司 用于振荡工具上的开孔器
DE102010063069A1 (de) * 2010-12-14 2012-06-14 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Bohrmaschine oder Schraubbohrmaschine
DE102011077220A1 (de) * 2010-12-21 2012-06-21 Robert Bosch Gmbh Elektrohandwerkzeug
DE102012103604A1 (de) * 2012-04-24 2013-10-24 C. & E. Fein Gmbh Handführbare Werkzeugmaschine mit Gehäuse
DE102013221108A1 (de) * 2013-10-17 2015-05-07 Robert Bosch Gmbh Werkzeugmaschinenvorrichtung
CN104708600A (zh) * 2015-03-18 2015-06-17 江苏源通电气有限公司 一种保护钻头的多用钻孔机
CN108979097B (zh) * 2017-05-05 2020-10-02 杭州富阳鼎杰石材有限公司 一种建筑室内装潢使用的地板锤
US10994399B2 (en) 2017-07-31 2021-05-04 Ryan Duggan Hammer drill and set tool device
EP3461593A1 (fr) * 2017-09-30 2019-04-03 Positec Power Tools (Suzhou) Co., Ltd Outil de percussion
US11613929B2 (en) 2019-11-08 2023-03-28 Xr Dynamics Llc Dynamic drilling systems and methods

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Also Published As

Publication number Publication date
US20080115952A1 (en) 2008-05-22
US7661485B2 (en) 2010-02-16
CN101181783A (zh) 2008-05-21
DE102006054288A1 (de) 2008-05-21
CN101181783B (zh) 2010-09-29
EP1923176A1 (fr) 2008-05-21
DE502007001531D1 (de) 2009-10-29

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