EP2234768B1 - Swash drive of a hand-held machine tool - Google Patents

Swash drive of a hand-held machine tool Download PDF

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Publication number
EP2234768B1
EP2234768B1 EP08861422A EP08861422A EP2234768B1 EP 2234768 B1 EP2234768 B1 EP 2234768B1 EP 08861422 A EP08861422 A EP 08861422A EP 08861422 A EP08861422 A EP 08861422A EP 2234768 B1 EP2234768 B1 EP 2234768B1
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EP
European Patent Office
Prior art keywords
wobble
drive shaft
drive
finger
power tool
Prior art date
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Application number
EP08861422A
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German (de)
French (fr)
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EP2234768A1 (en
Inventor
Gerd Schlesak
Juergen Lennartz
Stefan Holst
Klaus Kuespert
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2234768A1 publication Critical patent/EP2234768A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • 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
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven
    • 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
    • B25D2250/005—Adjustable tool components; Adjustable parameters
    • 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
    • B25D2250/331—Use of bearings

Definitions

  • the invention relates to a wobble drive a hand tool, in particular a drill and / or chisel hammer, according to the preamble of claim 1.
  • Such a wobble drive of a power tool designed as a hammer drill which has a drive shaft.
  • the wobble drive comprises a swash bearing arranged on the drive shaft and a swash plate mounted on the swash bearing.
  • At the swash plate two wobble fingers are provided with Taumelfingerachsen, which serve to drive a percussion piston and to drive a balancing mass, wherein the two wobble fingers are arranged diametrically opposite to the swash plate.
  • the wobble drive according to claim 1 provides that the axes of the wobble fingers form an angle ⁇ not equal to 180 °.
  • a "wobble drive” should be understood to mean, in particular, a drive which converts or converts a rotational movement of a drive-side element into an oscillating translational movement of an output-side element. This affects designed as a drive shaft, rotatably driven rotary member so on a swash plate of the wobble drive that the swash plate is driven back and forth about an axis of rotation and can put at least one further element in a linear translational movement via at least one wobble finger.
  • Tumbling drives are used, for example, in hand-held power tools, such as rotary hammers, to convert a rotary motion of a drive into an oscillatory translational motion of a striking piston which serves to build up pressure in an air cushion of a striking mechanism of the power tool, the pressure being used to apply impact to a tool is.
  • the wobble here represents an imbalance mass, which is noticeable especially at high speeds by vibrations or vibrations, noise and increased wear.
  • a targeted mass balance is known to be made on the power tool.
  • the mass balance can be positive or negative.
  • a positive mass balance by inserting balancing weights, which serve to adjust the center of gravity of the component to be balanced, in this case the swash plate so that it coincides with the center of the axis of rotation of the swash plate.
  • balancing weights which serve to adjust the center of gravity of the component to be balanced
  • the swash plate so that it coincides with the center of the axis of rotation of the swash plate.
  • the two main axes of inertia of the swash plate intersect with the axis of rotation.
  • a second wobble finger is provided on the swash plate, which converts the rotational movement of the drive shaft in a translational movement of a balancing mass.
  • at least one of the wobble fingers is arranged obliquely in space.
  • the axes of the wobble fingers form an angle ⁇ between 10 ° and 170 ° and / or 190 ° and 350 °.
  • the acceleration force which sets the hammer in oscillations or in reciprocating movements, composed of different components. These components mainly include inertial forces and a pressing force of the hammer drill and a pressing force of the operator of the hammer drill.
  • the angle ⁇ between the axes of the wobble fingers should preferably be between 10 ° and 170 ° and / or 190 ° and 350 °.
  • the angle between the axes of the wobble fingers is adjustable.
  • the compensation unit can be adjusted very fine, preferably continuously, and thus adapted to all load cases.
  • this also makes it possible to use the wobble drive in different hand tool machines, since this can be adapted to all hand tool machines due to the angular adjustment.
  • the adjustment of the angle ⁇ can be effected via a movable mounting of at least one wobble finger on the swash plate. This means a structurally simple, cost-effective way of angle adjustment.
  • the wobble finger converts a rotational movement of the drive shaft into a translatory movement of an element and the further wobble finger converts a rotational movement of the drive shaft into a translational and / or rotational movement of a further element.
  • an optimal phase angle between the movement of a first element and a movement of a second element can be realized, so that the vibrations of the power tool can be reduced to a minimum.
  • At least one element is linearly guided.
  • both elements are linearly guided, whereby an optimum balance of the forces acting during operation of the power tool can be achieved.
  • the elements are a piston of a percussion mechanism of the portable power tool and / or a compensation unit.
  • the compensation unit forms quasi a counterweight to the piston of the hammer mechanism and generates counter torques to the moving masses and moments occurring as a result of the movements of the piston.
  • the smoothness of the power tool is increased.
  • the piston is guided linearly and the compensation unit mounted linearly or rotationally.
  • the compensation unit is preferably guided substantially in the direction of a machining axis of the handheld power tool.
  • the term "substantially in the direction of a machining axis” should be understood in particular to mean that the guidance of the compensation unit relative to the machining axis has an angular deviation of less than 10 ° and preferably less than 5 °. This allows an optimal balance of the forces acting in the hand tool machine forces, as a result, the compensation unit an optimal counterweight to the also formed in the machining direction piston of the hammer mechanism. In addition, this facilitates the assembly of the power tool, since the individual components are only to be arranged in a main direction in a housing of the power tool.
  • the compensation unit can also be guided in the direction of an axis lying obliquely to the machining axis in space, which includes, for example with the machining axis an angle of 45 °, ie the compensation unit can be provided obliquely lying in space.
  • the compensation unit is rotatable about an axis of rotation. This can be done in a simple and cost-effective manner, a reduction in the vibrations of the power tool by the first wobble the implementation of the rotational movement of the drive shaft in a translational movement of the first element and the second wobble finger, the implementation of the rotational movement of the drive shaft in at least one rotational movement of the other element he follows.
  • the compensation unit is designed as a disk-shaped and / or U-shaped component. This makes it possible to design the component with respect to the balancing effect individually by the component varies, for example, in its thickness.
  • the compensation unit surrounds a guide of the piston and / or the drive shaft at least partially or the compensation unit is penetrated by a guide of the piston and / or the drive shaft. This allows optimal adaptation of the wobble drive to existing structures, in particular the use of existing space.
  • FIGS. 1 and 3 show a partially sectioned view of a wobble drive 10 of a hand tool, not shown.
  • the hand tool is preferably a hammer drill.
  • the wobble drive 10 includes a swash bearing 14, rolling elements 38 and a swash plate 16 with wobble fingers 18, 20.
  • the hand tool has a drive shaft 12 on which the wobble drive 10 is attached to the swash bearing 14.
  • the swash bearing 14 is rotatably connected to the drive shaft 12.
  • the swash bearing 14 has an annular inner surface 40, which lies in a non-perpendicular to a rotational axis 42 of the drive shaft 12 level.
  • the swash plate 16 is arranged, which has on its inner side of the inner race 40 of the swash bearing 14 associated outer race 44. Between the inner race 40 and the outer race 44, the rolling elements 38, preferably balls, are arranged to be movable.
  • a first wobble finger 18 having a first wobble finger axis 22 and a second wobble finger 20 having a second wobble finger axis 24 are provided, which extend radially outwardly from the circumference of the swash plate 16.
  • the wobble fingers 18, 20 may in this case be formed integrally with the swash plate 16 as well as be attached to the swash plate 16 as separate components.
  • the axes 22, 24 of the wobble fingers 18, 20 form an angle ⁇ not equal to 180 °.
  • the angle ⁇ between the axes 22, 24 of the wobble fingers 18, 20 adjustable.
  • the adjustment of the angle ⁇ can take place via a movable mounting of at least one of the wobble fingers 18 or 20 on the swash plate 16, ie the wobble finger 18 or 20 is adjustable or adjustable arranged on the swash plate 16.
  • the axes 22, 24 of the wobble fingers 18, 20 form an angle ⁇ between 10 ° and 170 ° and / or 190 ° and 350 °.
  • the wobble fingers 18, 20 convert a rotational movement of the drive shaft 12 into a translational and / or rotational movement of at least one element 26, 28 by the wobble fingers 18, 20 being in operative connection with the respective element 26, 28, wherein at least one element 26 , 28 linearly guided, preferably positively guided.
  • the elements 26, 28 are, on the one hand, a piston 30 of a striking mechanism, not shown further, of the hand tool machine, which is linearly guided in the form of a hammer tube guide 36 in the direction of a machining axis 34, and, on the other hand, by a compensation unit 32.
  • One of the swash plate 16 facing away from the end of the first wobble finger 18 is connected via a piston pin 54 with the piston 30 of the striking mechanism in operative connection.
  • An end of the second wobble finger 20 facing away from the swash plate 16 is operatively connected to the compensation unit 32 via a recess 56 in the compensation unit 32.
  • the compensation unit 32a is linearly guided over two longitudinal guides designed as rods 46a, 48a in the direction of the machining axis 34a of the hand-held power tool, the compensation unit 32a being designed as a disc-shaped component in the present exemplary embodiment.
  • the rods 46a, 48a form a positive guide and are suitably held preferably at their ends in the power tool. They run essentially parallel to the drive shaft 12a.
  • the disc-shaped compensation unit 32a is penetrated by the guide 36a of the piston 30a and the drive shaft 12a, which is designed as a hammer tube, and contains two bores 50a and 52a, which respectively receive one of the rods 46a, 48a in a slidingly displaceable manner.
  • the drive shaft 12a is rotated together with the swash bearing 14a. Due to the inclined inner raceway surface 40a of the wobble bearing 14a, the rolling elements 38a revolving therein and, with them, the swash plate 16a, wobble offset, which is converted by the guidance of the elements 26a, 28a in a linear reciprocating movement of the elements 26a, 28a.
  • the first wobble finger 18a effects a conversion of the rotational movement of the drive shaft 12a into a reciprocating movement of the piston 30a in the hammer tube 36a of the impact mechanism along the machining axis 34a.
  • the second wobble finger 20a effects a conversion of the rotational movement of the drive shaft 12a into a reciprocating movement of the balance unit 32a parallel to the rotation axis 42a of the drive shaft 12a, the direction of the rotation axis 42a and the direction of the machining axis 34a being substantially coincident.
  • the compensation unit 32b rotatable about a rotation axis 58b, so that the wobble finger 18b converts a rotational movement of the drive shaft 12b in a translational movement of the piston 30b and the further tumble finger 20b, a rotational movement of the drive shaft 12b in a translational and / or rotational movement of the compensation unit 28b.
  • the drive shaft 12b is rotated together with the swash bearing 14b. Due to the inclined inner raceway surface 40b of the wobble bearing 14b, the rolling elements 38b revolving therein and, with them, the swash plate 16b are set in tumbling motion, which is guided by the guidance or mounting of the elements 26b, 28b in a linear reciprocating motion and / or rotational movement Elements 26b, 28b is converted.
  • the first wobble finger 18b effects a conversion of the rotational movement of the drive shaft 12b into a reciprocating movement of the piston 30b in the hammer tube 36b of the percussion mechanism along the machining axis 34b.
  • the second wobble finger 20b effects a conversion of the rotational movement of the drive shaft 12b into a movement about the rotation axis 58b and / or a movement of the compensation unit 32b reciprocating parallel to the rotation axis 42b of the drive shaft 12b, the direction of the rotation axis 42b and the direction of rotation Machining axis 34b substantially match.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Taumelantrieb einer Handwerkzeugmaschine, insbesondere einem Bohr- und/oder Meißelhammer, nach dem Oberbegriff des Anspruchs 1.The invention relates to a wobble drive a hand tool, in particular a drill and / or chisel hammer, according to the preamble of claim 1.

Aus der DE 198 51 888 A1 ist ein solcher Taumelantrieb einer als Bohrhammer ausgebildeten Handwerkzeugmaschine bekannt, die eine Antriebswelle aufweist. Der Taumelantrieb umfasst ein auf der Antriebswelle angeordnetes Taumellager und eine auf dem Taumellager gelagerte Taumelscheibe. An der Taumelscheibe sind zwei Taumelfinger mit Taumelfingerachsen vorgesehen, die zum Antrieb eines Schlagwerkkolbens und zum Antrieb einer Ausgleichsmasse dienen, wobei die beiden Taumelfinger einander diametral gegenüberliegend an der Taumelscheibe angeordnet sind.From the DE 198 51 888 A1 Such a wobble drive of a power tool designed as a hammer drill is known, which has a drive shaft. The wobble drive comprises a swash bearing arranged on the drive shaft and a swash plate mounted on the swash bearing. At the swash plate two wobble fingers are provided with Taumelfingerachsen, which serve to drive a percussion piston and to drive a balancing mass, wherein the two wobble fingers are arranged diametrically opposite to the swash plate.

Solcher Taumelantrieb ist auch in EP 1892 062A2 , Dokument gemäß Artikel 54(3), EPÜ, gezeigt.Such wobble drive is also in EP 1892 062A2 , Document according to Article 54 (3), EPC.

Vorteile der ErfindungAdvantages of the invention

Der Taumelantrieb nach Anspruch 1 sieht vor, dass die Achsen der Taumelfinger einen Winkel α ungleich 180° einschließen. Unter einem "Taumelantrieb" soll in diesem Zusammenhang insbesondere ein Antrieb verstanden werden, der eine Rotationsbewegung eines antriebsseitigen Elements in eine oszillierende Translationsbewegung eines abtriebsseitigen Elements umsetzt bzw. umwandelt. Hierbei wirkt ein als Antriebswelle ausgestaltetes, drehend angetriebenes Rotationselement derart auf eine Taumelscheibe des Taumelantriebs ein, dass die Taumelscheibe um eine Drehachse hin- und herkippend angetrieben wird und dabei über mindestens einen Taumelfinger mindestens ein weiteres Element in eine lineare Translationsbewegung versetzen kann. Taumelantriebe werden beispielsweise in Handwerkzeugmaschinen, wie beispielsweise Bohrhämmern, eingesetzt, um eine Rotationsbewegung eines Antriebs in eine oszillierende Translationsbewegung eines Schlagwerkkolbens umzuwandeln, welche zum Aufbau eines Drucks in einem Luftpolster eines Schlagwerks der Handwerkzeugmaschine dient, wobei der Druck zur Ausübung von Schlägen auf ein Werkzeug vorgesehen ist. Der Taumelfinger stellt hierbei eine Unwuchtmasse dar, die sich vor allem bei hohen Drehzahlen durch Vibrationen bzw. Schwingungen, Geräusche und erhöhten Verschleiß bemerkbar macht. Um diese Unwucht zu beseitigen bzw. auszugleichen, wird bekanntermaßen ein gezielter Massenausgleich an der Handwerkzeugmaschine vorgenommen. Der Massenausgleich kann dabei positiv oder negativ sein. In der Regel erfolgt ein positiver Massenausgleich durch Einsetzen von Ausgleichsmassen, welche dazu dienen, den Schwerpunkt des auszuwuchtenden Bauteils, in diesem Fall der Taumelscheibe, so einzustellen, dass er mit dem Mittelpunkt der Drehachse der Taumelscheibe zusammenfällt. Damit schneiden sich die beiden Hauptträgheitsachsen der Taumelscheibe mit der Drehachse. Im vorliegenden Ausführungsbeispiel ist hierfür ein zweiter Taumelfinger an der Taumelscheibe vorgesehen, der die Rotationsbewegung der Antriebswelle in eine Translationsbewegung einer Ausgleichsmasse umsetzt. Vorzugsweise ist hierbei mindestens einer der Taumelfinger schräg im Raum angeordnet. Die erfindungsgemäße Ausgestaltung nach Anspruch 1 ermöglicht, dass die durch die Massenkräfte hervorgerufenen Schwingungserscheinungen zumindest weitgehend eliminiert sind.The wobble drive according to claim 1 provides that the axes of the wobble fingers form an angle α not equal to 180 °. In this context, a "wobble drive" should be understood to mean, in particular, a drive which converts or converts a rotational movement of a drive-side element into an oscillating translational movement of an output-side element. This affects designed as a drive shaft, rotatably driven rotary member so on a swash plate of the wobble drive that the swash plate is driven back and forth about an axis of rotation and can put at least one further element in a linear translational movement via at least one wobble finger. Tumbling drives are used, for example, in hand-held power tools, such as rotary hammers, to convert a rotary motion of a drive into an oscillatory translational motion of a striking piston which serves to build up pressure in an air cushion of a striking mechanism of the power tool, the pressure being used to apply impact to a tool is. The wobble here represents an imbalance mass, which is noticeable especially at high speeds by vibrations or vibrations, noise and increased wear. To eliminate or compensate for this imbalance, a targeted mass balance is known to be made on the power tool. The mass balance can be positive or negative. In general, a positive mass balance by inserting balancing weights, which serve to adjust the center of gravity of the component to be balanced, in this case the swash plate so that it coincides with the center of the axis of rotation of the swash plate. Thus, the two main axes of inertia of the swash plate intersect with the axis of rotation. In the present embodiment, for this purpose, a second wobble finger is provided on the swash plate, which converts the rotational movement of the drive shaft in a translational movement of a balancing mass. Preferably, in this case at least one of the wobble fingers is arranged obliquely in space. The inventive design according to claim 1 allows that caused by the inertial forces vibration phenomena are at least largely eliminated.

Es wird daher erfindungsgemäß in Anspruch 1 vorgeschlagen, dass die Achsen der Taumelfinger einen Winkel α zwischen 10° und 170° und/oder 190° und 350° einschließen. Insbesondere bei Bohrhämmern setzt sich die Beschleunigungskraft, welche den Bohrhammer in Schwingungen bzw. in Hin- und Herbewegungen versetzt, aus unterschiedlichen Komponenten zusammen. Diese Komponenten umfassen hauptsächlich Massenkräfte und eine Druckkraft des Bohrhammers sowie eine Andruckkraft des Bedieners des Bohrhammers. Um die Beschleunigungskraft in Gegenphase mit den Ausgleichsmassenkräften des Bohrhammers zu bringen, sollte der Winkel α zwischen den Achsen der Taumelfinger vorzugsweise zwischen 10° und 170° und/oder 190° und 350° betragen. Hierdurch kann ein optimaler Phasenwinkel zwischen der Bewegung des Kolbens und der Bewegung der Ausgleichseinheit realisiert werden, so dass die Schwingungen des Bohrhammers auf ein Minimum reduziert werden können. Vorteilhafterweise ist der Winkel zwischen den Achsen der Taumelfinger einstellbar. Hierdurch kann die Ausgleichseinheit sehr fein, vorzugsweise stufenlos eingestellt werden und somit an alle Belastungsfälle angepasst werden. Insbesondere besteht hierdurch auch die Möglichkeit, den Taumelantrieb in unterschiedlichen Handwerkzeugmaschinen einzusetzen, da dieser aufgrund der Winkeleinstellung an alle Handwerkzeugmaschinen angepasst werden kann.It is therefore proposed according to the invention in claim 1 that the axes of the wobble fingers form an angle α between 10 ° and 170 ° and / or 190 ° and 350 °. Particularly in rotary hammers, the acceleration force, which sets the hammer in oscillations or in reciprocating movements, composed of different components. These components mainly include inertial forces and a pressing force of the hammer drill and a pressing force of the operator of the hammer drill. In order to bring the acceleration force in antiphase with the balancing mass forces of the hammer drill, the angle α between the axes of the wobble fingers should preferably be between 10 ° and 170 ° and / or 190 ° and 350 °. In this way, an optimal phase angle between the movement of the piston and the movement of the compensation unit can be realized, so that the vibrations of the hammer drill can be reduced to a minimum. Advantageously, the angle between the axes of the wobble fingers is adjustable. As a result, the compensation unit can be adjusted very fine, preferably continuously, and thus adapted to all load cases. In particular, this also makes it possible to use the wobble drive in different hand tool machines, since this can be adapted to all hand tool machines due to the angular adjustment.

Vorzugsweise kann die Einstellung des Winkels α über eine bewegbare Lagerung mindestens eines Taumelfingers an der Taumelscheibe erfolgen. Dies bedeutet eine konstruktiv einfache, kostengünstige Möglichkeit der Winkeleinstellung.Preferably, the adjustment of the angle α can be effected via a movable mounting of at least one wobble finger on the swash plate. This means a structurally simple, cost-effective way of angle adjustment.

Erfindungsgemäß setzt der Taumelfinger eine Rotationsbewegung der Antriebswelle in eine Translationsbewegung eines Elements und der weitere Taumelfinger eine Rotationsbewegung der Antriebswelle in eine Translations- und/oder Rotationsbewegung eines weiteren Elements um. Hierdurch kann ein optimaler Phasenwinkel zwischen der Bewegung eines ersten Elements und einer Bewegung eines zweiten Elements realisiert werden, so dass die Schwingungen der Handwerkzeugmaschine auf ein Minimum reduziert werden können.According to the invention, the wobble finger converts a rotational movement of the drive shaft into a translatory movement of an element and the further wobble finger converts a rotational movement of the drive shaft into a translational and / or rotational movement of a further element. In this way, an optimal phase angle between the movement of a first element and a movement of a second element can be realized, so that the vibrations of the power tool can be reduced to a minimum.

Des Weiteren wird vorgeschlagen, dass mindestens ein Element linear geführt ist. Vorzugsweise sind beide Elemente linear geführt, wodurch eine optimale Austarierung der im Betrieb der Handwerkzeugmaschine wirkenden Kräfte erreichbar ist.Furthermore, it is proposed that at least one element is linearly guided. Preferably, both elements are linearly guided, whereby an optimum balance of the forces acting during operation of the power tool can be achieved.

Es wird vorgeschlagen, dass es sich bei den Elementen um einen Kolben eines Schlagwerks der Handwerkzeugmaschine und/oder um eine Ausgleichseinheit handelt. Vorteilhafterweise bildet die Ausgleichseinheit quasi ein Gegengewicht zum Kolben des Schlagwerks und erzeugt Gegenmomente zu den infolge der Bewegungen des Kolbens auftretenden bewegten Massen und Momenten. Hierdurch ist die Laufruhe der Handwerkzeugmaschine erhöht. Vorzugsweise ist der Kolben linear geführt und die Ausgleichseinheit linear oder rotatorisch gelagert.It is proposed that the elements are a piston of a percussion mechanism of the portable power tool and / or a compensation unit. Advantageously, the compensation unit forms quasi a counterweight to the piston of the hammer mechanism and generates counter torques to the moving masses and moments occurring as a result of the movements of the piston. As a result, the smoothness of the power tool is increased. Preferably, the piston is guided linearly and the compensation unit mounted linearly or rotationally.

Ferner wird vorgeschlagen, dass die Ausgleichseinheit vorzugsweise im Wesentlichen in Richtung einer Bearbeitungsachse der Handwerkzeugmaschine geführt ist. Dabei soll unter "im Wesentlichen in Richtung einer Bearbeitungsachse" insbesondere verstanden werden, dass die Führung der Ausgleichseinheit zur Bearbeitungsachse eine Winkelabweichung kleiner 10° und vorzugsweise kleiner 5° aufweist. Dies ermöglicht eine optimale Austarierung der in der Handwerkzeugmaschine wirkenden Kräfte, da hierdurch die Ausgleichseinheit ein optimales Gegengewicht zu dem ebenfalls in Bearbeitungsrichtung geführten Kolben des Schlagwerks bildet. Zudem erleichtert dies die Montage der Handwerkzeugmaschine, da die einzelnen Bauteile nur mehr in einer Hauptrichtung in einem Gehäuse der Handwerkzeugmaschine anzuordnen sind. Alternativ hierzu kann die Ausgleichseinheit auch in Richtung einer schräg zur Bearbeitungsachse im Raum liegenden Achse geführt sein, welche beispielsweise mit der Bearbeitungsachse einen Winkel von 45° einschließt, d.h. die Ausgleichseinheit kann schräg im Raum liegend vorgesehen sein.Furthermore, it is proposed that the compensation unit is preferably guided substantially in the direction of a machining axis of the handheld power tool. In this case, the term "substantially in the direction of a machining axis" should be understood in particular to mean that the guidance of the compensation unit relative to the machining axis has an angular deviation of less than 10 ° and preferably less than 5 °. This allows an optimal balance of the forces acting in the hand tool machine forces, as a result, the compensation unit an optimal counterweight to the also formed in the machining direction piston of the hammer mechanism. In addition, this facilitates the assembly of the power tool, since the individual components are only to be arranged in a main direction in a housing of the power tool. Alternatively, the compensation unit can also be guided in the direction of an axis lying obliquely to the machining axis in space, which includes, for example with the machining axis an angle of 45 °, ie the compensation unit can be provided obliquely lying in space.

Alternativ wird vorgeschlagen, dass die Ausgleichseinheit um eine Drehachse drehbar ist. Hierdurch kann auf einfache und kostengünstige Weise eine Reduktion der Schwingungen der Handwerkzeugmaschine erfolgen, indem über den ersten Taumelfinger die Umsetzung der Rotationsbewegung der Antriebswelle in eine Translationsbewegung des ersten Elements und über den zweiten Taumelfinger die Umsetzung der Rotationsbewegung der Antriebswelle in mindestens eine Rotationsbewegung des weiteren Elements erfolgt.Alternatively, it is proposed that the compensation unit is rotatable about an axis of rotation. This can be done in a simple and cost-effective manner, a reduction in the vibrations of the power tool by the first wobble the implementation of the rotational movement of the drive shaft in a translational movement of the first element and the second wobble finger, the implementation of the rotational movement of the drive shaft in at least one rotational movement of the other element he follows.

Vorteilhafterweise ist die Ausgleichseinheit als scheibenförmiges und/oder U-förmiges Bauteil ausgebildet. Hierdurch besteht die Möglichkeit, das Bauteil in Bezug auf die Ausgleichswirkung individuell auszugestalten, indem das Bauteil beispielsweise in seiner Dicke variiert.Advantageously, the compensation unit is designed as a disk-shaped and / or U-shaped component. This makes it possible to design the component with respect to the balancing effect individually by the component varies, for example, in its thickness.

Besonders vorteilhaft umgibt die Ausgleichseinheit eine Führung des Kolbens und/oder die Antriebswelle mindestens teilweise bzw. ist die Ausgleichseinheit von einer Führung des Kolbens und/oder der Antriebswelle durchdrungen. Dies ermöglicht eine optimale Anpassung des Taumelantriebs an bestehende Konstruktionen, insbesondere die Verwendung von vorhandenem Bauraum.Particularly advantageously, the compensation unit surrounds a guide of the piston and / or the drive shaft at least partially or the compensation unit is penetrated by a guide of the piston and / or the drive shaft. This allows optimal adaptation of the wobble drive to existing structures, in particular the use of existing space.

Zeichnungdrawing

Weitere Vorteile ergeben sich aus der folgenden Zeichnungsbeschreibung. In der Zeichnung sind zwei Ausführungsbeispiele der Erfindung dargestellt. Die Zeichnung, die Beschreibung und die Ansprüche enthalten zahlreiche Merkmale in Kombination. Der Fachmann wird die Merkmale zweckmäßigerweise auch einzeln betrachten und zu sinnvollen weiteren Kombinationen zusammenfassen.Further advantages emerge from the following description of the drawing. In the drawing, two embodiments of the invention are shown. The drawing, the description and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations.

Es zeigen:

Fig. 1
eine Seitenansicht eines erfindungsgemäßen Taumelantriebs einer Handwerkzeugmaschine in einer ersten Ausführungsform,
Fig. 2
eine Vorderansicht des erfindungsgemäßen Taumelantriebs gemäß Fig. 1,
Fig. 3
eine Seitenansicht eines erfindungsgemäßen Taumelantriebs einer Handwerkzeugmaschine in einer zweiten Ausführungsform und
Fig. 4
eine Vorderansicht des erfindungsgemäßen Taumelantriebs gemäß Fig. 3.
Show it:
Fig. 1
a side view of a wobble drive according to the invention a hand tool in a first embodiment,
Fig. 2
a front view of the wobble drive according to the invention Fig. 1 .
Fig. 3
a side view of a wobble drive according to the invention a hand tool in a second embodiment and
Fig. 4
a front view of the wobble drive according to the invention Fig. 3 ,

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die Figuren 1 und 3 zeigen eine teilweise geschnittene Darstellung eines Taumelantriebs 10 einer nicht näher dargestellten Handwerkzeugmaschine. Bei der Handwerkzeugmaschine handelt es sich vorzugsweise um einen Bohrhammer. Der Taumelantrieb 10 umfasst ein Taumellager 14, Wälzkörper 38 und eine Taumelscheibe 16 mit Taumelfingern 18, 20. Die Handwerkzeugmaschine besitzt eine Antriebswelle 12, auf welcher der Taumelantrieb 10 mit dem Taumellager 14 befestigt ist. Das Taumellager 14 ist mit der Antriebswelle 12 drehfest verbunden. Das Taumellager 14 weist eine ringförmige Innenlauffläche 40 auf, die in einer nicht senkrecht zu einer Drehachse 42 der Antriebswelle 12 stehenden Ebene liegt. Um das Taumellager 14 ist die Taumelscheibe 16 angeordnet, die auf ihrer Innenseite eine der Innenlauffläche 40 des Taumellagers 14 zugeordnete Außenlauffläche 44 aufweist. Zwischen der Innenlauffläche 40 und der Außenlauffläche 44 sind die Wälzkörper 38, vorzugsweise Kugeln, beweglich angeordnet.The FIGS. 1 and 3 show a partially sectioned view of a wobble drive 10 of a hand tool, not shown. The hand tool is preferably a hammer drill. The wobble drive 10 includes a swash bearing 14, rolling elements 38 and a swash plate 16 with wobble fingers 18, 20. The hand tool has a drive shaft 12 on which the wobble drive 10 is attached to the swash bearing 14. The swash bearing 14 is rotatably connected to the drive shaft 12. The swash bearing 14 has an annular inner surface 40, which lies in a non-perpendicular to a rotational axis 42 of the drive shaft 12 level. To the swash bearing 14, the swash plate 16 is arranged, which has on its inner side of the inner race 40 of the swash bearing 14 associated outer race 44. Between the inner race 40 and the outer race 44, the rolling elements 38, preferably balls, are arranged to be movable.

Gemäß den Figuren 2 und 4 sind an einem Umfang der Taumelscheibe 16 ein erster Taumelfinger 18 mit einer ersten Taumelfingerachse 22 und ein zweiter Taumelfinger 20 mit einer zweiten Taumelfingerachse 24 vorgesehen, die sich radial vom Umfang der Taumelscheibe 16 aus nach außen erstrecken. Die Taumelfinger 18, 20 können hierbei sowohl einstückig mit der Taumelscheibe 16 ausgebildet sein als auch als separate Bauteile an der Taumelscheibe 16 angebracht sein.According to the Figures 2 and 4 At a periphery of the swash plate 16, a first wobble finger 18 having a first wobble finger axis 22 and a second wobble finger 20 having a second wobble finger axis 24 are provided, which extend radially outwardly from the circumference of the swash plate 16. The wobble fingers 18, 20 may in this case be formed integrally with the swash plate 16 as well as be attached to the swash plate 16 as separate components.

Erfindungsgemäß schließen die Achsen 22, 24 der Taumelfinger 18, 20 einen Winkel α ungleich 180° ein. Vorteilhafterweise ist der Winkel α zwischen den Achsen 22, 24 der Taumelfinger 18, 20 einstellbar. Die Einstellung des Winkels α kann über eine bewegbare Lagerung mindestens eines der Taumelfinger 18 oder 20 an der Taumelscheibe 16 erfolgen, d.h. der Taumelfinger 18 oder 20 ist verstellbar bzw. justierbar an der Taumelscheibe 16 angeordnet. Vorzugsweise schließen die Achsen 22, 24 der Taumelfinger 18, 20 einen Winkel α zwischen 10° und 170° und/oder 190° und 350° ein.According to the invention, the axes 22, 24 of the wobble fingers 18, 20 form an angle α not equal to 180 °. Advantageously, the angle α between the axes 22, 24 of the wobble fingers 18, 20 adjustable. The adjustment of the angle α can take place via a movable mounting of at least one of the wobble fingers 18 or 20 on the swash plate 16, ie the wobble finger 18 or 20 is adjustable or adjustable arranged on the swash plate 16. Preferably, the axes 22, 24 of the wobble fingers 18, 20 form an angle α between 10 ° and 170 ° and / or 190 ° and 350 °.

Die Taumelfinger 18, 20 setzen eine Rotationsbewegung der Antriebswelle 12 in eine Translations- und/oder Rotationsbewegung jeweils mindestens eines Elements 26, 28 um, indem die Taumelfinger 18, 20 in Wirkverbindung mit dem jeweiligen Element 26, 28 stehen, wobei mindestens ein Element 26, 28 linear geführt, vorzugsweise zwangsgeführt ist. Bei den Elementen 26, 28 handelt es sich zum einen um einen Kolben 30 eines nicht weiter dargestellten Schlagwerks der Handwerkzeugmaschine, der in einer als Hammerrohr ausgebildeten Führung 36 in Richtung einer Bearbeitungsachse 34 linear geführt ist, und zum anderen um eine Ausgleichseinheit 32.The wobble fingers 18, 20 convert a rotational movement of the drive shaft 12 into a translational and / or rotational movement of at least one element 26, 28 by the wobble fingers 18, 20 being in operative connection with the respective element 26, 28, wherein at least one element 26 , 28 linearly guided, preferably positively guided. The elements 26, 28 are, on the one hand, a piston 30 of a striking mechanism, not shown further, of the hand tool machine, which is linearly guided in the form of a hammer tube guide 36 in the direction of a machining axis 34, and, on the other hand, by a compensation unit 32.

Ein der Taumelscheibe 16 abgewandtes Ende des ersten Taumelfingers 18 steht über einen Kolbenbolzen 54 mit dem Kolben 30 des Schlagwerks in Wirkverbindung. Ein der Taumelscheibe 16 abgewandtes Ende des zweiten Taumelfingers 20 steht über eine Ausnehmung 56 in der Ausgleichseinheit 32 mit der Ausgleichseinheit 32 in Wirkverbindung.One of the swash plate 16 facing away from the end of the first wobble finger 18 is connected via a piston pin 54 with the piston 30 of the striking mechanism in operative connection. An end of the second wobble finger 20 facing away from the swash plate 16 is operatively connected to the compensation unit 32 via a recess 56 in the compensation unit 32.

Im ersten Ausführungsbeispiel gemäß den Figuren 1 und 2 ist die Ausgleichseinheit 32a über zwei als Stäbe 46a, 48a ausgebildete Längsführungen in Richtung der Bearbeitungsachse 34a der Handwerkzeugmaschine linear geführt, wobei die Ausgleichseinheit 32a im vorliegenden Ausführungsbeispiel als scheibenförmiges Bauteil ausgebildet ist. Die Stäbe 46a, 48a bilden eine Zwangsführung und sind auf geeignete Weise vorzugsweise an ihren Enden in der Handwerkzeugmaschine gehalten. Sie verlaufen im Wesentlichen parallel zur Antriebswelle 12a. Die scheibenförmige Ausgleichseinheit 32a ist von der als Hammerrohr ausgebildeten Führung 36a des Kolbens 30a und der Antriebswelle 12a durchdrungen und enthält zwei Bohrungen 50a und 52a, die jeweils einen der Stäbe 46a, 48a gleitend verschiebbar aufnehmen. Hierdurch ist die Ausgleichseinheit 32a in der Handwerkzeugmaschine parallel zur Drehachse 42a der Antriebswelle 12a hin- und her verschiebbar angeordnet, so dass der Taumelfinger 18a eine Rotationsbewegung der Antriebswelle 12a in eine Translationsbewegung des Kolbens 30a und der weitere Taumelfinger 20a eine Rotationsbewegung der Antriebswelle 12a in eine Translationsbewegung der Ausgleichseinheit 28a umsetzt.In the first embodiment according to the FIGS. 1 and 2 the compensation unit 32a is linearly guided over two longitudinal guides designed as rods 46a, 48a in the direction of the machining axis 34a of the hand-held power tool, the compensation unit 32a being designed as a disc-shaped component in the present exemplary embodiment. The rods 46a, 48a form a positive guide and are suitably held preferably at their ends in the power tool. They run essentially parallel to the drive shaft 12a. The disc-shaped compensation unit 32a is penetrated by the guide 36a of the piston 30a and the drive shaft 12a, which is designed as a hammer tube, and contains two bores 50a and 52a, which respectively receive one of the rods 46a, 48a in a slidingly displaceable manner. As a result, the compensation unit 32a in the portable power tool parallel to the rotation axis 42a of the drive shaft 12a back and forth arranged displaceable, so that the wobble finger 18a a rotational movement of the drive shaft 12a in a translational movement of the piston 30a and the further tumble finger 20a, a rotational movement of the drive shaft 12a in a Translational movement of the compensation unit 28a converts.

Im Betrieb der Handwerkzeugmaschine wird die Antriebswelle 12a zusammen mit dem Taumellager 14a gedreht. Aufgrund der schräg liegenden Innenlauffläche 40a des Taumellagers 14a werden die darin umlaufenden Wälzkörper 38a und mit ihnen die Taumelscheibe 16a in eine Taumelbewegung versetzt, die durch die Führung der Elemente 26a, 28a in eine lineare Hin- und Herbewegung der Elemente 26a, 28a umgewandelt wird. Der erste Taumelfinger 18a bewirkt eine Umwandlung der Rotationsbewegung der Antriebswelle 12a in eine entlang der Bearbeitungsachse 34a hin- und hergehende Bewegung des Kolbens 30a in dem Hammerrohr 36a des Schlagwerks. Gleichzeitig bewirkt der zweite Taumelfinger 20a eine Umwandlung der Rotationsbewegung der Antriebswelle 12a in eine parallel zur Drehachse 42a der Antriebswelle 12a hin- und hergehende Bewegung der Ausgleichseinheit 32a, wobei die Richtung der Drehachse 42a und die Richtung der Bearbeitungsachse 34a im Wesentlichen übereinstimmen.In operation of the power tool, the drive shaft 12a is rotated together with the swash bearing 14a. Due to the inclined inner raceway surface 40a of the wobble bearing 14a, the rolling elements 38a revolving therein and, with them, the swash plate 16a, wobble offset, which is converted by the guidance of the elements 26a, 28a in a linear reciprocating movement of the elements 26a, 28a. The first wobble finger 18a effects a conversion of the rotational movement of the drive shaft 12a into a reciprocating movement of the piston 30a in the hammer tube 36a of the impact mechanism along the machining axis 34a. At the same time, the second wobble finger 20a effects a conversion of the rotational movement of the drive shaft 12a into a reciprocating movement of the balance unit 32a parallel to the rotation axis 42a of the drive shaft 12a, the direction of the rotation axis 42a and the direction of the machining axis 34a being substantially coincident.

Im zweiten Ausführungsbeispiel gemäß den Figuren 3 und 4 ist die Ausgleichseinheit 32b um eine Drehachse 58b drehbar, so dass der Taumelfinger 18b eine Rotationsbewegung der Antriebswelle 12b in eine Translationsbewegung des Kolbens 30b und der weitere Taumelfinger 20b eine Rotationsbewegung der Antriebswelle 12b in eine Translations- und/oder Rotationsbewegung der Ausgleichseinheit 28b umsetzt.In the second embodiment according to the Figures 3 and 4 is the compensation unit 32b rotatable about a rotation axis 58b, so that the wobble finger 18b converts a rotational movement of the drive shaft 12b in a translational movement of the piston 30b and the further tumble finger 20b, a rotational movement of the drive shaft 12b in a translational and / or rotational movement of the compensation unit 28b.

Im Betrieb der Handwerkzeugmaschine wird die Antriebswelle 12b zusammen mit dem Taumellager 14b gedreht. Aufgrund der schräg liegenden Innenlauffläche 40b des Taumellagers 14b werden die darin umlaufenden Wälzkörper 38b und mit ihnen die Taumelscheibe 16b in eine Taumelbewegung versetzt, die durch die Führung bzw. Lagerung der Elemente 26b, 28b in eine lineare Hin-und Herbewegung und/oder Rotationsbewegung der Elemente 26b, 28b umgewandelt wird. Der erste Taumelfinger 18b bewirkt eine Umwandlung der Rotationsbewegung der Antriebswelle 12b in eine entlang der Bearbeitungsachse 34b hin- und hergehende Bewegung des Kolbens 30b in dem Hammerrohr 36b des Schlagwerks. Gleichzeitig bewirkt der zweite Taumelfinger 20b eine Umwandlung der Rotationsbewegung der Antriebswelle 12b in eine Bewegung um die Drehachse 58b und/oder eine parallel zur Drehachse 42b der Antriebswelle 12b hin- und hergehende Bewegung der Ausgleichseinheit 32b, wobei die Richtung der Drehachse 42b und die Richtung der Bearbeitungsachse 34b im Wesentlichen übereinstimmen.During operation of the power tool, the drive shaft 12b is rotated together with the swash bearing 14b. Due to the inclined inner raceway surface 40b of the wobble bearing 14b, the rolling elements 38b revolving therein and, with them, the swash plate 16b are set in tumbling motion, which is guided by the guidance or mounting of the elements 26b, 28b in a linear reciprocating motion and / or rotational movement Elements 26b, 28b is converted. The first wobble finger 18b effects a conversion of the rotational movement of the drive shaft 12b into a reciprocating movement of the piston 30b in the hammer tube 36b of the percussion mechanism along the machining axis 34b. At the same time, the second wobble finger 20b effects a conversion of the rotational movement of the drive shaft 12b into a movement about the rotation axis 58b and / or a movement of the compensation unit 32b reciprocating parallel to the rotation axis 42b of the drive shaft 12b, the direction of the rotation axis 42b and the direction of rotation Machining axis 34b substantially match.

Claims (9)

  1. Wobble drive (10) for a portable power tool, in particular a rotary and/or demolition hammer, which has a drive shaft (12), having a wobble bearing (14) arranged on the drive shaft (12) and having a wobble plate (16) mounted on the wobble bearing (14), at least two wobble fingers (18, 20) having wobble finger axes (22, 24) being provided on said wobble plate (16), wherein the wobble finger (18) converts a rotary movement of the drive shaft (12) into a translatory movement of one element (26) and the further wobble finger (20) converts a rotary movement of the drive shaft (12) into a translatory and/or rotary movement of a further element (28), characterized in that the axes (22, 24) of the wobble fingers (18, 20) enclose an angle (α) of between 10° and 170° and/or 190° and 350°.
  2. Wobble drive according to Claim 1, characterized in that the angle (α) between the axes (22, 24) of the wobble fingers (18, 20) is settable.
  3. Wobble drive according to Claim 2, characterized in that the angle (α) is set via a movable bearing of at least one wobble finger (18, 20) on the wobble plate (16).
  4. Wobble drive according to Claim 1, characterized in that at least one element (26, 28) is guided linearly.
  5. Wobble drive according to one of the preceding claims, characterized in that the elements (26, 28) are a piston (30) of a percussion mechanism of the portable power tool and/or a compensating unit (32).
  6. Wobble drive according to Claim 5, characterized in that the compensating unit (32) is guided substantially in the direction of a machining axis (34) of the portable power tool and/or in the direction of an axis located spatially at an angle to a machining axis (34) of the portable power tool.
  7. Wobble drive according to Claim 5, characterized in that the compensating unit (32) is rotatable about a rotation axis (58).
  8. Wobble drive according to one of Claims 5 to 7, characterized in that the compensating unit (32) is in the form of a disc-shaped and/or U-shaped component.
  9. Wobble drive according to one of Claims 5 to 8, characterized in that the compensating unit (32) at least partially surrounds a guide (36) for the piston (30) and/or the drive shaft (12).
EP08861422A 2007-12-19 2008-10-22 Swash drive of a hand-held machine tool Active EP2234768B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007061716A DE102007061716A1 (en) 2007-12-19 2007-12-19 Tumbling drive of a hand tool machine
PCT/EP2008/064254 WO2009077241A1 (en) 2007-12-19 2008-10-22 Swash drive of a hand-held machine tool

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EP2234768A1 EP2234768A1 (en) 2010-10-06
EP2234768B1 true EP2234768B1 (en) 2012-12-12

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EP (1) EP2234768B1 (en)
CN (1) CN101903133B (en)
DE (1) DE102007061716A1 (en)
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WO2009077241A1 (en) 2009-06-25
DE102007061716A1 (en) 2009-06-25
CN101903133A (en) 2010-12-01
US20100270046A1 (en) 2010-10-28
CN101903133B (en) 2013-05-08
EP2234768A1 (en) 2010-10-06
RU2010129101A (en) 2012-01-27
RU2497653C2 (en) 2013-11-10
US8403075B2 (en) 2013-03-26
US20130213682A1 (en) 2013-08-22

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