EP1923176B1 - Hammer drill - Google Patents

Hammer drill Download PDF

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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)
French (fr)
Other versions
EP1923176A1 (en
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/en
Application granted granted Critical
Publication of EP1923176B1 publication Critical patent/EP1923176B1/en
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.

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

Description

Die Erfindung betrifft einen Bohrhammer mit den Merkmalen nach dem Oberbegriff des Anspruchs 1.The invention relates to a rotary hammer with the features according to the preamble of claim 1.

Bohrhämmer für den handgeführten Betrieb weisen in vorbekannter Bauform einen Antriebsmotor, eine vom Antriebsmotor drehend antreibbare Werkzeugspindel und ein Hammerwerk auf. Ein in einem Bohrfutter eingespannter Bohrer wird durch die Werkzeugspindel in Drehung versetzt. Der Antriebsmotor, der auch die Werkzeugspindel antreibt, betätigt darüber hinaus das Hammerwerk, welches axiale Hammerschläge auf den Bohrer ausübt. Beim Bohren in Stein oder vergleichbaren Materialien erzeugt der Bohrer ein Bohrloch unter gleichzeitiger Einwirkung seiner Drehbewegung und seiner axialen Hammerschläge.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. When drilling in stone or comparable materials, the drill produces a borehole under the simultaneous action of its rotary motion and its axial hammer blows.

Zur Erzeugung der kombinierten Dreh- und Schlagbewegung ist bei Bohrhämmern nach dem Stand der Technik eine zweite Welle parallel zur Werkzeugspindel angeordnet. Die Werkzeugspindel ist durch ein zweistufiges Getriebe vom Antriebsmotor angetrieben. Der Antriebsmotor treibt über eine erste Getriebestufe die zusätzliche Welle an, die ihrerseits die Werkzeugspindel über eine zweite Getriebestufe antreibt. Die zwischenliegende zweite Welle dient darüber hinaus als Antrieb für das Hammerwerk.In order to produce the combined turning and striking movement, 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.

Die parallele Anordnung von zwei Wellen, nämlich der Werkzeugspindel und der Antriebswelle des Hammerwerkes erfordert einen entsprechenden Bauraum. Das Gleiche gilt auch für das zweistufige Getriebe. Die Anordnung ist großvolumig, schwer und kostenintensiv.The parallel arrangement of two shafts, namely the tool spindle and the drive shaft of the hammer mill requires a corresponding space. The same applies to the two-stage gearbox. The arrangement is bulky, heavy and expensive.

Aus der DE 298 00 248 Ul ist ein Bohrhammer bekannt, dessen Werkzeugspindel und Hammerwerk jeweils mittels eines einstufigen Getriebes direkt von einer Motorwelle des Antriebsmotors angetrieben sind. Die Motorwelle weist hierzu zwei axial zueinander versetzte Verzahnungen auf, nämlich eine Stirnverzahnung zum Antrieb des Hammerwerkes, und eine Schneckenverzahnung zum Antrieb der Werkzeugspindel. Aus der Schneckenverzahnung folgt ein seitlich radialer Versatz der Motorwelle zur Werkzeugspindel, der in Verbindung mit dem axialen Versatz beider Verzahnungen an der Motorwelle einen entsprechend hohen Bauraum erfordert.From the DE 298 00 248 Ul is a rotary hammer known, the tool spindle and hammer mechanism are each driven by a single-stage gear directly from a motor shaft of the drive motor. For this purpose, 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.

Der Erfindung liegt die Aufgabe zugrunde, einen gattungsgemäßen Bohrhammer derart weiterzubilden, daß sein Bauvolumen verringert ist.The invention has the object of developing a generic rotary hammer such that its volume is reduced.

Diese Aufgabe wird durch einen Bohrhammer mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a hammer drill with the features of claim 1.

Dazu wird vorgeschlagen, daß die Werkzeugspindel und das Hammerwerk jeweils mittels eines einstufigen Getriebes direkt von einer Motorwelle des Antriebsmotors angetrieben sind. Die Anordnung ist spielfrei, kompakt, leichtgewichtig und kostengünstig herstellbar. Das angetriebene Zahnrad der Werkzeugspindel liegt nahe zum oder sogar am griffseitigen Ende der Werkzeugspindel. Auf eine Vorgelegewelle kann verzichtet werden, so dass das Getriebegehäuse im werkzeugnahen Bereich vergleichsweise schlank gestaltet werden kann. Dies vereinfacht Arbeiten unter räumlich beengten Bedingungen. Bei verringerter Teilezahl und insbesondere verringertem Gewicht ist der Schwerpunkt des Bohrhammers näher zum Handgriff verschoben, was die Ergonomie beim Arbeiten verbessert.For this purpose, it is proposed that 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.

Das einstufige Getriebe zwischen der Motorwelle und der Werkzeugspindel ist ein Winkelgetriebe, welches durch ein Ritzel der Motorwelle und ein mit dem Ritzel in Eingriff stehendes Tellerrad der Werkzeugspindel gebildet ist. Das Ritzel der Motorwelle weist eine Stirnverzahnung auf, während das Tellerrad als Kronenrad ausgebildet ist. Die insbesondere als Geradverzahnung ausgeführte Stirnverzahnung des Ritzels ist kostengünstig herstellbar. Trotz der winkligen Anordnung des Tellerrades zum Ritzel führt dessen Ausbildung als Kronenrad zu einem sauberen, verschleißarmen Kämmen der ineinander greifenden Verzahnungen. Gleichzeitig ermöglicht die Ausbildung des Ritzels mit einer Stirnverzahnung den zusätzlichen Antrieb des Hammerwerkes mittels des gleichen Ritzels.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. Despite the angular arrangement of the ring gear to the pinion whose training as a crown wheel leads to a clean, low-wear combing the interlocking teeth. At the same time, the formation of the pinion with a spur gear allows the additional drive of the hammer mechanism by means of the same pinion.

Eine Drehachse des Hammerwerks liegt im wesentlichen parallel zur Motorachse, wobei das einstufige Getriebe zwischen der Motorwelle und dem Hammerwerk durch ein Stirnradgetriebe gebildet ist. Das Ritzel der Motorwelle mit der Stirnverzahnung steht sowohl im Eingriff mit dem Kronenrad der Werkzeugspindel als auch mit einem Stirnrad des Hammerwerks. An der Motorwelle bzw. deren Ritzel ist nur eine einzige Verzahnung anzubringen. Die Anordnung ist platzsparend und kostengünstig.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.

In bevorzugter Weiterbildung sind eine Motorachse der Motorwelle und eine Spindelachse der Werkzeugspindel in einem Winkel zueinander angeordnet, wobei der Winkel in einem Bereich von einschließlich 60° bis einschließlich 120° liegt und insbesondere etwa 90° beträgt. Die winklige Anordnung von Motorachse und Spindelachse ermöglicht eine kurze Bauform. In dem Winkelgetriebe mit Ritzel und Tellerrad kann mittels des nur einstufigen Getriebes die Drehzahl des Antriebsmotors hinreichend auf die gewünschte Drehzahl der Werkzeugspindel herabgesetzt werden.In a preferred embodiment, 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. In the angular gear with pinion and ring gear, 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.

In bevorzugter Weiterbildung steht das Ritzel der Motorwelle bezogen auf seine Achsrichtung in gleicher Höhe im Eingriff mit dem Kronenrad der Werkzeugspindel und mit dem Stirnrad des Hammerwerks. Insbesondere liegen Eingriffspunkte des Ritzels mit dem Tellerrad der Werkzeugspindel und dem Stirnrad des Hammerwerks bezogen auf die Achsrichtung der Motorwelle radial einander gegenüber. Die am Ritzel angreifenden, durch das Tellerrad und das gegenüberliegende Stirnrad hervorgerufenen Belastungen wirken symmetrisch und im wesentlichen frei von Exzentrizitäten auf die Motorwelle ein. Die Getriebe und die Motorlagerung unterliegen geringen Belastungen und können entsprechend klein, leicht und kostengünstig dimensioniert sein.In a preferred embodiment, 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. In particular, 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.

In einer zweckmäßigen Ausführung sind der Antriebsmotor, die Werkzeugspindel und das Hammerwerk zwischen zwei Gehäuseschalen aus Kunststoff angeordnet, wobei zumindest ein Lager der Motorwelle und zumindest ein Lager des Hammerwerks in einem gemeinsamen Lagersteg insbesondere aus Leichtmetall gehalten sind, und wobei der Lagersteg zwischen den beiden Gehäuseschalen fixiert ist. Der gemeinsame Lagersteg erzeugt eine erhöhte Steifigkeit der Lagerung und damit eine verbesserte Genauigkeit der gegenseitigen Ausrichtung der verschiedenen Komponenten. Insbesondere ist die Präzision der gegenseitigen Ausrichtung von der Motorwelle und dem direkt davon angetriebenen Hammerwerk verbessert. Für eine kompakte Bauform kann der Achsabstand von Motorwelle und Hammerwerk verringert werden. Außerdem wird die erforderliche Steifigkeit der Lagerung alleine durch den Lagersteg aufgebracht, so dass für das Getriebegehäuse ein vergleichsweise weicher, schlagzäher Kunststoff eingesetzt werden kann. Der Lagersteg kann gemeinsam mit den restlichen Teilen wie Motoranker, Werkzeugspindel, Hammerwerk, elektrische Komponenten oder dergleichen in die Kunststoffschalen eingelegt und zwischen den beiden Schalen formschlüssig bzw. klemmend fixiert werden. Die Montage ist einfach und kostengünstig. Der Ausschuss bei der Montage ist verringert. Die Lebensdauer des Bohrhammers ist vergrößert.In an expedient embodiment, 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. In particular, the precision of the mutual alignment of the motor shaft and the directly driven hammer mechanism is improved. For a compact design, the center distance of the motor shaft and hammer mill can be reduced. In addition, 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.

Das Hammerwerk ist vorteilhaft ein pneumatisches Hammerwerk mit einem durch ein Exzenterrad und ein Pleuel angetriebenen Druckkolben.The hammer mechanism is advantageously a pneumatic hammer mechanism with a pressure piston driven by an eccentric wheel and a connecting rod.

Ein Ausführungsbeispiel der Erfindung ist im Folgenden anhand der Zeichnung näher beschrieben. Es zeigen:

Fig. 1
eine Längsschnittdarstellung durch einen erfindungsgemäß ausgeführten Bohrhammer mit einer Übersichtsdarstellung der gegenseitigen Anordnung von Antriebsmotor, Werkzeugspindel und Hammerwerk;
Fig. 2
eine vergrößerte Detailansicht der Anordnung nach Fig. 1 im Antriebsbereich der Werkzeugspindel und des Hammerwerkes mit Einzelheiten der jeweils hierzu vorgesehenen einstufigen Getriebe.
An embodiment of the invention is described below with reference to the drawing. Show it:
Fig. 1
a longitudinal sectional view through an inventively designed rotary hammer with an overview of the mutual arrangement of drive motor, tool spindle and hammer mechanism;
Fig. 2
an enlarged detail of the arrangement according to Fig. 1 in the drive range of the tool spindle and the hammer mechanism with details of each provided for this purpose single-stage gearbox.

Fig. 1 zeigt eine Längsschnittdarstellung durch einen erfindungsgemäß ausgeführten Bohrhammer. Der Bohrhammer weist einen elektrischen Antriebsmotor 1, eine vom Antriebsmotor 1 drehend antreibbare Werkzeugspindel 2 und ein Hammerwerk 3 auf. Der elektrische Antriebsmotor 1 ist zur Versorgung mit Netzspannung vorgesehen. Es kann auch ein Akkubetrieb oder dergleichen zweckmäßig sein. Anstelle des elektrischen Antriebsmotors 1 kann auch ein Verbrennungsmotor vorgesehen sein. 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.

Der Bohrhammer ist in seiner gewöhnlichen Betriebsposition gezeigt, in der er vom Benutzer mit der Hand gehalten und geführt wird. Hierbei liegt eine Spindelachse 8 etwa horizontal, während eine Motorwelle 6 des Antriebsmotors 1 mit ihrer Motorachse 7 etwa vertikal angeordnet ist. Die Motorachse 7 und die Spindelachse 8 liegen im gezeigten Ausführungsbeispiel in einem Winkel α von 90° zueinander. Der Winkel α liegt vorteilhaft in einem Bereich von einschließlich 60° bis einschließlich 120°.The hammer drill is shown in its usual operating position, in which it is held and guided by the user by hand. Here, 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 α of 90 ° to each other. The angle α is advantageously in a range of including 60 ° to 120 ° inclusive.

Die Werkzeugspindel 2 ist direkt von der Motorwelle 6 des Antriebsmotors 1 mittels eines einstufigen Getriebes 4 angetrieben. Hierzu ist einteilig mit der Motorwelle 6 ein Ritzel 9 ausgeformt, während ein Tellerrad 10 drehfest mit der drehbar gelagerten Werkzeugspindel 2 an ihrem griffseitigen Ende oder in unmittelbarer Nähe dazu verbunden ist. Das Ritzel 9 und das Tellerrad 10 bilden zusammen ein einstufiges Untersetzungsgetriebe in Form eines Winkelgetriebes, bei dem das Ritzel 9 der Motorwelle 6 mit dem Tellerrad 10 der Werkzeugspindel 10 direkt in Eingriff steht. Durch Drehung der Motorwelle 6 wird die Werkzeugspindel 2 über das einstufige Getriebe 4 um die Spindelachse 8 drehend angetrieben. Das einstufige Getriebe 4 ist ein Untersetzungsgetriebe, in dem die Arbeitsdrehzahl des Antriebsmotors 1 auf eine verringerte Drehzahl der Werkzeugspindel 2 herabgesetzt wird.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. For this purpose, 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. By rotation of the motor shaft 6, the tool spindle 2 is driven to rotate about the spindle axis 8 via the single-stage gear 4. 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.

Am freien Arbeitsende der Werkzeugspindel 2 ist ein Spannfutter 27 für einen nicht dargestellten Bohrer angeordnet. Das Spannfutter 27 ist drehfest mit der Werkzeugspindel 2 verbunden und überträgt die Drehbewegung der Werkzeugspindel 2 auf den eingespannten Bohrer.At the free end 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.

Zusätzlich zum Getriebe 4 ist ein weiteres einstufiges Getriebe 5 vorgesehen, mittels dessen das Hammerwerk 3 direkt von der Motorwelle 6 des Antriebsmotors 1 angetrieben ist. Hierzu weist das Hammerwerk 3 ein Exzenterrad 22 mit einem angeformten Stirnrad 14 auf, welches direkt mit dem Ritzel 9 der Motorwelle 6 kämmt. Das einstufige Getriebe 5 zwischen der Motorwelle 6 und dem Hammerwerk 3 ist ein untersetzendes Stirnradgetriebe, welches aus dem Ritzel 9 und dem Stirnrad 14 gebildet ist.In addition to the transmission 4, 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. For this purpose, 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.

Die Werkzeugspindel 2 ist als hohles Rohr ausgeführt, in dem rückwärtig des Spannfutters 27 ein Stößel 26, ein Döpper 25 und ein Druckkolben 24 in Richtung der Spindelachse 8 längsverschiebbar geführt sind. Das Hammerwerk 3 ist ein pneumatisches Hammerwerk, bei dem der Druckkolben 24 über ein Pleuel 23 durch das drehend angetriebene Exzenterrad 22 in Richtung der Spindelachse 8 eine oszillierende Bewegung ausführt. Über ein Luftpolster in der hohlen Werkzeugspindel wird diese oszillierende Bewegung auf den Döpper 25 übertragen, der beim Auftreffen auf den Stößel 26 seine kinetische Schlagenergie durch den Stößel 26 auf den eingespannten, nicht dargestellten Bohrer überträgt. Die Schlagbewegung und die Drehbewegung des Bohrers wird über die beiden einstufigen Getriebe 4, 5 direkt vom gemeinsamen Ritzel 9 des Antriebsmotors 1 erzeugt.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 zeigt eine vergrößerte Detailansicht der Anordnung nach Fig. 1 im Bereich der beiden Getriebe 4, 5. Es ist zu erkennen, daß das Ritzel 9 eine bis zum freien Ende durchgehende Stirnverzahnung 11 aufweist, die im gezeigten Ausführungsbeispiel als Geradverzahnung ausgeführt ist. Es kann auch eine spiralige Schrägverzahnung zweckmäßig sein. Das Tellerrad 10 der Werkzeugspindel 2 ist als Kronenrad 13 ausgeführt, dessen Zähne in die Stirnverzahnung 11 an einem Eingriffspunkt 15 eingreifen. Alternativ kann es auch zweckmäßig sein, das Ritzel 9 im Bereich des Eingriffspunktes 15 als Kegelritzel auszuführen, wobei dann das Tellerrad 10 in geeigneter Weise als Kegelrad ausgeführt ist. Der Eingriffspunkt 15 liegt auf der dem Spannfutter 27 (Fig. 1) zugewandten Seite der Motorwelle 6. Fig. 2 shows an enlarged detail view of the arrangement according to Fig. 1 in the region of the two gear 4, 5. It can be seen that 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. Alternatively, it may also be expedient to perform the pinion 9 in the region of the engagement point 15 as a bevel pinion, in which case the ring gear 10 is designed in a suitable manner as a bevel gear. The engagement point 15 lies on the chuck 27 ( Fig. 1 ) facing side of the motor shaft. 6

Das Stirnrad 14 weist auf seiner Umfangseite eine nicht näher dargestellte Geradverzahnung auf, die an einem Eingriffspunkt 16 mit der Stirnverzahnung 11 des Ritzels 9 kämmend in Eingriff steht. Durchmesser und Zähnezahl des Stirnrades 14 betragen ein Vielfaches vom Ritzel 9, so daß das Getriebe 5 ein Untersetzungsgetriebe ist, bei dem die Arbeitsdrehzahl des Antriebsmotors 1 auf eine verringerte Antriebsdrehzahl des Hammerwerks 3 herabgesetzt wird.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.

Das Hammerwerk 3 einschließlich seines Exzenterrades 22 mit dem angeformten Stirnrad 14 ist auf der dem Spannfutter 27 (Fig. 1) abgewandten Seite der Motorwelle 6 derart angeordnet, daß der Eingriffspunkt 16 bezogen auf die Achsrichtung der Motorachse 7 auf gleicher Höhe mit dem Eingriffspunkt 15 des Getriebes 4 liegt. Die beiden Eingriffspunkte 15, 16 der beiden einstufigen Getriebe 4, 5 liegen bezogen auf die Motorachse 7 einander gegenüber. Die Stirnverzahnung 11 liegt hierbei sowohl im Eingriff mit dem Kronenrad 13 am Eingriffspunkt 15, als auch im Eingriff mit dem Stirnrad 14 am Eingriffspunkt 16.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

Es kann auch eine Ausführung zweckmäßig sein, bei der das Ritzel 9 im unteren Bereich die Stirnverzahnung 11 und im oberen Bereich nahe dem freien Ende eine Kegelverzahnung aufweist. In diesem Falle liegt dann der Eingriffspunkt 15 des als Kegelrad ausgeführten Tellerrades 10 oberhalb des Eingriffspunktes 16 vom Stirnrad 14.It may also be expedient embodiment, in which the pinion 9 has the spur toothing 11 in the lower region and a conical toothing in the upper region near the free end. In this case, then the point of engagement 15 of the ring gear designed as a bevel gear 10 above the engagement point 16 of the spur gear 14th

Am Exzenterrad 22 ist eine Nabe 30 einteilig angeformt, mit der das Exzenterrad 22 unter Bildung eines Lagers 20 drehend auf einem Lagerzapfen 29 gelagert ist. Eine Mittelachse des Lagerzapfens 29 bildet eine Drehachse 12 des Hammerwerks 3, die parallel zur Motorachse 7 der Motorwelle 6 liegt. Das Exzenterrad 22 trägt einen schematisch angedeuteten Kurbelzapfen 32, der in ein Pleuelauge 31 des Pleuels 23 eingreift. Bei einer durch den Antriebsmotor 1 angetriebenen Drehung des Exzenterrades 22 um die Drehachse 12 führt der Kurbelzapfen 32 eine Kreisbahn entsprechend einem Pfeil 33 aus. Bezogen auf die Achsrichtung der Spindelachse 8 erfährt das Pleuelauge 31 eine oszillierende Bewegung zwischen zwei mit 31' und 31" angegebenen Endpositionen. Diese werden über das Pleuel 23 auf den Druckkolben 24 übertragen, der eine entsprechende oszillierende Axialbewegung ausführt und auf den Döpper 25 (Fig. 1) überträgt.On the eccentric 22, 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. Relative to the axial direction of the spindle axis 8, 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.

Die gesamte Anordnung des Antriebsmotors 1, der Werkzeugspindel 2, des Hammerwerks 3 und weiterer, nicht näher beschriebener Komponenten ist in einem Maschinengehäuse angeordnet, welches zwei Gehäuseschalen 17, 18 aus Kunststoff umfaßt. Der besseren Übersichtlichkeit halber ist nur ein Ausschnitt einer geöffneten Gehäuseschale 17 gezeigt, während eine zweite, im wesentlichen symmetrisch dazu ausgebildete Gehäuseschale 18 die Anordnung verschließt. Im montierten Zustand der beiden Gehäuseschalen 17, 18 ist zwischen diesen ein schematisch angedeuteter Lagersteg 21 aus Metall, vorteilhaft aus Leichtmetall und insbesondere aus Aluminium formschlüssig bzw. klemmend fixiert. Der als Elektromotor ausgeführte Antriebsmotor 1 weist auf seiner Motorwelle 6 einen Anker 35 auf, an dessen den Getrieben 4, 5 zugewandten Stirnseite ein Lüfterrad 34 mitdrehend befestigt ist. Der Lagersteg 21 ist auf der den Getrieben 4, 5 zugewandten Seite des Lüfterrades 34 angeordnet.The entire arrangement of the drive motor 1, the tool spindle 2, the hammer mechanism 3 and further, unspecified components is arranged in a machine housing, which comprises two housing shells 17, 18 made of plastic. For better clarity, only a section of an open housing shell 17 is shown, while a second, substantially symmetrical thereto formed housing shell 18 closes the arrangement. In the assembled state of the two housing shells 17, 18 between these 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.

Der Lagersteg 21 trägt den Lagerzapfen 29 des Lagers 20 vom Hammerwerk 3. Des weiteren ist ein als Wälzlager ausgebildetes Lager 19 zur Lagerung der Motorwelle 6 nahe am Ritzel 9 angeordnet, welches ebenfalls im Lagersteg 21 gehalten ist. Die Ausbildung des Lagersteges 21 aus Leichtmetall stellt eine tragfähige und lagegenaue Fixierung der Lager 19, 20 gegeneinander bei geringem radialem Abstand zueinander sicher. Es kann auch zweckmäßig sein, ein getriebenahes Lager der Werkzeugspindel 2 und/oder eine axiale Anlageschulter des Kronenrades 13 am Lagersteg 21 zu fixieren.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.

Claims (7)

  1. Hammer drill with an in particular electric drive motor (1), with a tool spindle (2) capable of being driven to rotate by the drive motor (1) and with a hammer mechanism (3), wherein the tool spindle (2) and the hammer mechanism (3) are directly driven by a motor shaft (6) of the drive motor (1) by means of single-stage gearboxes (4, 5),
    characterised in that the single-stage gearbox (4) between the motor shaft (6) and the tool spindle (2) is a bevel gear system comprising a pinion (9) of the motor shaft (6) with spur toothing (11) and a crown wheel (13) of the tool spindle (2) in engagement with the pinion (9), in that an axis of rotation (12) of the hammer mechanism (3) extends substantially parallel to the motor axis (7), wherein the single-stage gearbox (5) between the motor shaft (6) and the hammer mechanism (3) is a spur gear system, and in that the pinion (9) of the motor shaft (6), which is provided with the spur toothing (11), is in engagement both with the crown wheel (13) of the tool spindle (2) and with a spur gear (14) of the hammer mechanism (3).
  2. Hammer drill according to claim 1,
    characterised in that a motor axis (7) of the motor shaft (6) and a spindle axis (8) of the tool spindle (2) are arranged at an angle (α) relative to one another, the angle (α) lying within a range from 60° to 120° inclusive, being in particular approximately 90°.
  3. Hammer drill according to claim 1 or 2,
    characterised in that the spur toothing (11) of the pinion (9) of the motor shaft (6) comprises straight teeth.
  4. Hammer drill according to any of claims 1 to 3,
    characterised in that the pinion (9) of the motor shaft (6) is in engagement with the crown wheel (13) of the tool spindle (2) and with the spur gear (14) of the hammer mechanism (3) at the same level relative to its axial direction.
  5. Hammer drill according to any of claims 1 to 4,
    characterised in that points of engagement (15, 16) of the pinion (9) with the crown wheel (13) of the tool spindle (2) and with the spur gear (14) of the hammer mechanism (3) are positioned radially opposite one another relative to the axial direction of the motor shaft (6).
  6. Hammer drill according to any of claims 1 to 5,
    characterised in that the drive motor (1), the tool spindle (2) and the hammer mechanism (3) are placed between two housing shells (17, 18) made of plastic, wherein at least one bearing (19) of the motor shaft (6) and at least one bearing (20) of the hammer mechanism (3) are held in a common light alloy bearing web (21) and wherein the bearing web (21) is attached between the two housing shells (17, 18).
  7. Hammer drill according to any of claims 1 to 6,
    characterised in that the hammer mechanism (3) is a pneumatic hammer mechanism with a ram (24) driven by a cam gear (22) and a connecting rod (23).
EP07021608A 2006-11-17 2007-11-07 Hammer drill Not-in-force EP1923176B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006054288A DE102006054288A1 (en) 2006-11-17 2006-11-17 Rotary Hammer

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EP1923176A1 EP1923176A1 (en) 2008-05-21
EP1923176B1 true EP1923176B1 (en) 2009-09-16

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US (1) US7661485B2 (en)
EP (1) EP1923176B1 (en)
CN (1) CN101181783B (en)
DE (2) DE102006054288A1 (en)

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

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