EP2425937A1 - Hand-held machine tool - Google Patents

Hand-held machine tool Download PDF

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Publication number
EP2425937A1
EP2425937A1 EP11176970A EP11176970A EP2425937A1 EP 2425937 A1 EP2425937 A1 EP 2425937A1 EP 11176970 A EP11176970 A EP 11176970A EP 11176970 A EP11176970 A EP 11176970A EP 2425937 A1 EP2425937 A1 EP 2425937A1
Authority
EP
European Patent Office
Prior art keywords
spring
mass body
hand tool
basic position
springs
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.)
Granted
Application number
EP11176970A
Other languages
German (de)
French (fr)
Other versions
EP2425937B1 (en
Inventor
Michael Wierer
Fabian Martin
Adrian Scherrer
Josef Althaus
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.)
Hilti AG
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Hilti AG
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Filing date
Publication date
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Publication of EP2425937A1 publication Critical patent/EP2425937A1/en
Application granted granted Critical
Publication of EP2425937B1 publication Critical patent/EP2425937B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • 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
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • 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
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted

Definitions

  • the hand tool e.g. a hand-held power tool with a pneumatic percussion mechanism, periodically gives the user a setback. Their amplitude can be attenuated by the absorber. An asymmetrically constructed Tilger can cause a higher damping effect in the power tool.
  • the spring stiffness may have a discontinuity or very strong change relative to the home position. The discontinuity results in a highly non-harmonic motion of the mass body and non-harmonic forces, which may be more appropriate to dampen the engine case.
  • the first spring stiffness is between five and ten times the second spring stiffness.
  • the ratio of the spring stiffnesses can be used to adjust the damping of the absorber to the non-return behavior of the power tool. The higher the ratio, the shorter and stronger the mass body is accelerated by the stiffer side.
  • An embodiment provides that the mass body in the second direction deflected from the basic position of at least one spring force-free and in the first direction deflected from the basic position of the at least one spring is subjected to force.
  • An embodiment provides that the mass body rests in the basic position on the spring. Rubbers with friction prove to be inefficient for use in hand tool machines. The coupling and decoupling of the spring and the resulting losses should be largely minimized. In the basic position, the other forces of the spring device cancel.
  • the mass body may be arranged in the basic position between two prestressed springs. An embodiment provides that the two prestressed springs are firmly connected to the mass body. Due to the fixed connection results in low losses in the springs due to plastic deformation or due to friction.
  • Fig. 1 shows as an embodiment a hammer drill 1 bz.
  • the hammer drill 1 bz has a tool holder 2bz for receiving a drill bit 3bz.
  • a striking mechanism 4bz of the hammer drill 1 bz strikes periodically along a working axis 5bz on the drill bit 3bz inserted in the tool holder 2bz and thereby drives it into a Underground.
  • a rotary drive 6bz can meanwhile rotate the drill bit 3bz about the working axis 5bz .
  • the striking mechanism 4bz and the rotary drive 6bz can be driven by a common motor 7bz, eg an electric motor.
  • a machine housing 8bz surrounds the striking mechanism 4bz, the rotary drive 6bz and the possibly common motor 7bz.
  • the Schlagtechnik 4bz is for example a pneumatic percussion.
  • An exciter 9bz and a club 10bz are movably guided in the pneumatic percussion mechanism 4bz along the working axis 5bz .
  • the exciter 9bz is coupled via an eccentric 11bz or a wobble finger to the motor 7bz and forced to a periodic, linear movement.
  • An air spring formed by a pneumatic chamber 12bz between exciter 9bz and racket 10bz couples a movement of the racket 10bz to the movement of the exciter 9bz .
  • the beater 10bz can strike directly on a rear end of the drill bit 3bz or indirectly transfer part of its momentum to the drill bit 3bz via a substantially stationary beater 13bz .
  • the user can perform the hammer drill 1 bz by hand by means of a handle 16bz .
  • the handle 16bz is attached to a side facing away from the tool holder 2bz side of the machine housing 8bz .
  • a longitudinal axis 17bz of the handle 16bz extends obliquely or perpendicular to the working axis 5bz.
  • the hammer drill 1 bz is, for example mirror-symmetrical to a plane of symmetry (corresponds to the plane of the drawing), which is spanned by the working axis 5bz and the longitudinal axis 17bz of the handle 16bz .
  • An axis perpendicular to the plane of symmetry is hereinafter referred to as the x-axis.
  • the y-axis is perpendicular to the x-axis and to the working axis 5bz.
  • the periodically operating impact mechanism 4bz causes vibrations in the engine case 8bz.
  • Spring suspensions 20Cz, 21bz of the handle 16bz on the machine housing 8bz partially suppress transmission of the vibrations to the handle 16bz to reduce the physiological stresses on the user.
  • the absorber 30Cz has a mass body 31 bz, which is connected by means of a spring device 32bz to the machine housing 8bz .
  • the oscillating machine housing 8bz stimulates the mass body 31 bz of the absorber 30Cz to resonate.
  • the system of mass body 31bz and a spring means 32bz is tuned to a natural frequency which is slightly larger than the excitation frequency through the machine housing 8bz, ie the repetition rate of the impact mechanism 4bz .
  • the absorber 30Cz can not quite follow the vibration of the machine housing 8bz and stabilizes in an antiphase oscillation.
  • the deviation of the natural frequency to the excitation frequency is preferably low, z. B. less than 10%, whereby an efficient energy transfer between the machine housing 8bz and absorber 30Cz is achieved.
  • Fig. 2 shows in detail an embodiment of the absorber 30Cz.
  • the absorber 30Cz has a housing 33bz, in which the mass body 31 bz is mounted longitudinally to a vibration axis 34bz .
  • An exemplary bearing 35bz includes round bars 36bz which are mounted in parallel to the vibration axis 34bz in the housing 33bz .
  • the mass body 31 bz has longitudinal bore 37bz or longitudinal grooves extending through the round rods 36bz .
  • the bearing 35bz is preferably low friction.
  • Other embodiments of linear bearings, eg with rolling bodies can also be used.
  • the mass body 31 bz can from a basic position 38bz (in Fig. 2 shown) along the vibration axis 34bz 30Cz be moved out in a first direction 39bz to a first end of the damper 40bz 30Cz and along the oscillation axis 34bz in an opposite, second direction 41 bz to a second end of the damper 42bz.
  • the spring device 32bz causes a restoring force on the mass body 31bz, as soon as it is deflected from the basic position 38bz .
  • the spring device 32bz is constructed asymmetrically to the basic position 38bz .
  • the exemplary spring means 32bz has first springs 44bz, second springs 45bz and a third spring 46bz.
  • the first springs 44bz are fastened to the first end of the housing 40bz 33bz and the mass body 31 bz, z. B. by clamping elements 47bz, 48bz.
  • the first springs 44bz push the mass body 31 bz deflected from the basic position 38bz in the second direction 41 bz.
  • the second springs 45bz are attached to the second end 42bz of the housing 33bz and to the mass body 31 bz .
  • the second springs 45bz of the mass body 31 bz is deflected from the basic position 38bz in the first direction 39bz kraftbeetzschlagt.
  • the first springs 44bz and second springs 45bz may be of the same design, eg with the same length and the same spring rigidity .
  • the first springs 44bz and second springs 45bz may be biased when the mass body 31 bz is in the home position 38bz .
  • the first springs 44bz and second springs 45bz may also be biased when the mass body 31 bz are deflected maximally in one or the other direction 39bz, 41 bz .
  • a load change of pressure load on tensile load of the springs 44bz, 45bz can be avoided.
  • the third spring 46bz is arranged only on one side of the mass body 31 bz, by way of example between the first end 40bz of the housing 33bz and the mass body 31 bz.
  • the third spring 46bz is fixedly connected to the housing 33bz, but only in the mass body 31 bz in whose basic position 38bz created.
  • the third spring 46bz is compressed.
  • the third spring 46bz detaches itself from the mass body 31 as soon as it exceeds the basic position 38bz .
  • the third spring 46bz fixedly connected to the mass body 31 bz and detaches from a seat 49bz on the housing 33bz.
  • the length of the third spring 46bz is equal to the distance of the mass body 31 bz selected to the seat 49bz .
  • the third spring 46bz is without bias when the mass body 31 bz is in the home position 38bz .
  • the spring stiffness of the spring means 32bz on the first side 50bz of the mass body 31 bz, ie in the first direction 39bz, can be five to ten times larger than the spring stiffness of the spring device 32bz on the second side 51 bz.
  • the third spring 46bz having three to eight times stiffness may be selected as the same first and second springs 45bz, 42bz .
  • the springs 44bz, 45bz, 46bz are, for example, coil springs made of steel.
  • the first springs 44bz and the second springs 45bz may be arranged coaxially with the round bars 36bz .
  • the swing axis 34bz is inclined parallel or at an angle of less than 5 degrees to the working axis 5bz of the portable power tool 1bz .
  • the spring device 32bz has a bending spring 60Cz, for example, leaf spring, which is aligned perpendicular to the swing axis 34bz .
  • the bending spring 60Cz is fixed with one end 61 bz to a seat 62bz in the housing 33bz of the damper 63bz .
  • At the other end 64bz of the mass body 31 bz is attached.
  • the mass body 31 bz oscillates along the swing axis 34bz, bending the bending spring 60Cz along its longitudinal extent .
  • a basic position 38bz of the mass body 31 bz results in a relaxed, unbent bending spring 60Cz.
  • a helical spring 65bz is arranged parallel to the oscillating axis 34bz on one side to the mass body 31 bz .
  • the coil spring 65bz touches the mass body 31 bz when it is in the normal position .
  • the coil spring 65bz In a deflection of the mass body 31 bz in the first direction 39bz , the coil spring 65bz is compressed.
  • On the mass body 31 bz act the restoring forces of the bending spring 60Cz and the coil spring 65bz.
  • a deflection of the mass body 31 bz in the opposite second direction 41 bz dissolves the mass body 31 bz of the coil spring 65bz. It acts only the restoring force of the bending spring 60Cz on the mass body 31 bz.

Abstract

The hand held tool has a damper (30) comprising a spring unit (32) for suspending a mass (31). The spring unit acts upon a deflection of the mass from an initial position in one direction (39) parallel to the working axis and upon a deflection of mass from a normal position in another direction (41). The spring stiffness in one direction is different from spring stiffness in another direction.

Description

GEBIET DER ERFINDUNGFIELD OF THE INVENTION

Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine.The present invention relates to a hand tool.

OFFENBARUNG DER ERFINDUNGDISCLOSURE OF THE INVENTION

Die erfindungsgemäße Handwerkzeugmaschine hat einen längs einer Arbeitsachse oszillierenden Antrieb und einen Tilger. Der Tilger weist einen in einer Federeinrichtung aufgehängten Massekörper auf. Die Federeinrichtung wirkt bei einer Auslenkung des Massenkörpers aus einer Grundstellung in eine erste Richtung parallel zu der Arbeitsachse mit einer ersten Federsteifigkeit und bei einer Auslenkung aus der Grundstellung in eine der ersten Richtung entgegengesetzten, zweiten Richtung mit einer zweiten Federsteifigkeit entgegen. Die erste Federsteifigkeit ist von der zweiten Federsteifigkeit verschieden.The hand tool according to the invention has a drive oscillating along a working axis and a absorber. The absorber has a suspended in a spring device mass body. The spring device acts in a deflection of the mass body from a basic position in a first direction parallel to the working axis with a first spring stiffness and at a deflection from the normal position in a direction opposite to the first direction, the second direction with a second spring stiffness. The first spring stiffness is different from the second spring stiffness.

Die Handwerkzeugmaschine, z.B. ein Handwerkzeugmaschine mit einem pneumatischen Schlagwerk, übt auf den Anwender periodisch einen Rückschlag aus. Deren Amplitude kann durch den Tilger abgeschwächt werden. Ein asymmetrisch aufgebauter Tilger kann eine höhere Dämpfwirkung bei der Handwerkzeugmaschine bewirken. Die Federsteifigkeit kann eine Diskontinuität oder sehr starke Änderung bezogen auf die Grundstellung aufweisen. Die Diskontinuität führt zu einer stark nicht-harmonischen Bewegung des Massekörpers und nicht-harmonischen Kräften, welche geeigneter sein können das Maschinengehäuse zu dämpfen.The hand tool, e.g. a hand-held power tool with a pneumatic percussion mechanism, periodically gives the user a setback. Their amplitude can be attenuated by the absorber. An asymmetrically constructed Tilger can cause a higher damping effect in the power tool. The spring stiffness may have a discontinuity or very strong change relative to the home position. The discontinuity results in a highly non-harmonic motion of the mass body and non-harmonic forces, which may be more appropriate to dampen the engine case.

Eine Ausgestaltung sieht vor, dass die erste Federsteifigkeit zwischen dem fünf und zehnfachen der zweiten Federsteifigkeit beträgt. Das Verhältnis der Federsteifigkeiten kann genutzt werden, um die Dämpfung des Tilgers an das Rückschlagverhalten der Handwerkzeugmaschine anzupassen. Je höher das Verhältnis ist, um so kürzer und stärker wird der Massenkörper durch die steifere Seite beschleunigt.One embodiment provides that the first spring stiffness is between five and ten times the second spring stiffness. The ratio of the spring stiffnesses can be used to adjust the damping of the absorber to the non-return behavior of the power tool. The higher the ratio, the shorter and stronger the mass body is accelerated by the stiffer side.

Eine Ausgestaltung sieht vor, dass der Massekörper in der zweiten Richtung ausgelenkt aus der Grundstellung von wenigstens einer Feder kraftfrei und in der ersten Richtung ausgelenkt aus der Grundstellung von der wenigstens einen Feder kraftbeaufschlagt ist. Die sich je nach Stellung des Massekörpers ankoppelnde und lösende Feder bewirkt die Asymmetrie des Tilgers.An embodiment provides that the mass body in the second direction deflected from the basic position of at least one spring force-free and in the first direction deflected from the basic position of the at least one spring is subjected to force. The Depending on the position of the mass body coupling and releasing spring causes the asymmetry of the absorber.

Eine Ausgestaltung sieht vor, dass der Massekörper in der Grundstellung an der Feder anliegt. Tilger mit Reibung erweisen sich als ineffizient für den Einsatz in Handwerkzeugmaschinen. Die Ankopplung und Abkopplung der Feder und die dabei entstehenden Verluste sollen weitgehend minimiert sein. In der Grundstellung heben sich die sonstigen Kräfte der Federeinrichtung auf. Der Massekörper kann in der Grundstellung zwischen zwei vorgespannten Federn angeordnet sein. Eine Ausgestaltung sieht vor, dass die zwei vorgespannten Federn mit dem Massekörper fest verbunden sind. Aufgrund der festen Anbindung ergeben sich geringe Verluste in den Federn aufgrund plastischer Deformation oder aufgrund von Reibung.An embodiment provides that the mass body rests in the basic position on the spring. Rubbers with friction prove to be inefficient for use in hand tool machines. The coupling and decoupling of the spring and the resulting losses should be largely minimized. In the basic position, the other forces of the spring device cancel. The mass body may be arranged in the basic position between two prestressed springs. An embodiment provides that the two prestressed springs are firmly connected to the mass body. Due to the fixed connection results in low losses in the springs due to plastic deformation or due to friction.

Eine Ausgestaltung sieht vor, dass der Massekörper an einer Biegefeder befestigt ist, die geneigt zu der Arbeitsrichtung angeordnet ist. Die Biegefeder ist entspannt, wenn der Massekörper in der Grundstellung ist.An embodiment provides that the mass body is attached to a spiral spring, which is arranged inclined to the working direction. The spiral spring is relaxed when the mass body is in the normal position.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Die nachfolgende Beschreibung erläutert die Erfindung anhand von exemplarischen Ausführungsformen und Figuren. In den Figuren zeigen:

Fig. 1
eine Handwerkzeugmaschine,
Fig. 2
ein Tilger,
Fig. 3 und 4
ein weiterer Tilger.
The following description explains the invention with reference to exemplary embodiments and figures. In the figures show:
Fig. 1
a hand tool,
Fig. 2
a mortar,
3 and 4
another absorber.

Gleiche oder funktionsgleiche Elemente werden durch gleiche Bezugszeichen in den Figuren indiziert, soweit nicht anders angegeben.Identical or functionally identical elements are indicated by the same reference numerals in the figures, unless stated otherwise.

AUSFÜHRUNGSFORMEN DER ERFINDUNGEMBODIMENTS OF THE INVENTION

Fig. 1 zeigt als eine Ausführungsform einen Bohrhammer 1 bz. Der Bohrhammer 1 bz hat eine Werkzeugaufnahme 2bz zur Aufnahme eines Bohrmeißel 3bz. Ein Schlagwerk 4bz des Bohrhammers 1 bz schlägt periodisch längs einer Arbeitsachse 5bz auf den in der Werkzeugaufnahme 2bz eingesetzten Bohrmeißel 3bz und treibt diesen dadurch in einen Untergrund. Ein Drehantrieb 6bz kann den Bohrmeißel 3bz währenddessen um die Arbeitsachse 5bz drehen.Fig. 1 shows as an embodiment a hammer drill 1 bz. The hammer drill 1 bz has a tool holder 2bz for receiving a drill bit 3bz. A striking mechanism 4bz of the hammer drill 1 bz strikes periodically along a working axis 5bz on the drill bit 3bz inserted in the tool holder 2bz and thereby drives it into a Underground. A rotary drive 6bz can meanwhile rotate the drill bit 3bz about the working axis 5bz .

Das Schlagwerk 4bz und der Drehantrieb 6bz können von einem gemeinsamen Motor 7bz, z.B. einem Elektromotor, angetrieben werden. Ein Maschinengehäuse 8bz umgibt das Schlagwerk 4bz, den Drehantrieb 6bz und den gegebenenfalls gemeinsamen Motor 7bz. The striking mechanism 4bz and the rotary drive 6bz can be driven by a common motor 7bz, eg an electric motor. A machine housing 8bz surrounds the striking mechanism 4bz, the rotary drive 6bz and the possibly common motor 7bz.

Das Schlagwerk 4bz ist beispielsweise ein pneumatisches Schlagwerk. Ein Erreger 9bz und ein Schläger 10bz sind in dem pneumatischen Schlagwerk 4bz längs der Arbeitsachse 5bz beweglich geführt. Der Erreger 9bz ist über einen Exzenter 11bz oder einen Taumelfinger an den Motor 7bz angekoppelt und zu einer periodischen, linearen Bewegung gezwungen. Eine Luftfeder gebildet durch eine pneumatische Kammer 12bz zwischen Erreger 9bz und Schläger 10bz koppelt eine Bewegung des Schlägers 10bz an die Bewegung des Erregers 9bz an. Der Schläger 10bz kann direkt auf ein hinteres Ende des Bohrmeißels 3bz aufschlagen oder mittelbar über einen im Wesentlichen ruhenden Zwischenschläger 13bz einen Teil seines Impuls auf den Bohrmeißel 3bz übertragen.The Schlagwerk 4bz is for example a pneumatic percussion. An exciter 9bz and a club 10bz are movably guided in the pneumatic percussion mechanism 4bz along the working axis 5bz . The exciter 9bz is coupled via an eccentric 11bz or a wobble finger to the motor 7bz and forced to a periodic, linear movement. An air spring formed by a pneumatic chamber 12bz between exciter 9bz and racket 10bz couples a movement of the racket 10bz to the movement of the exciter 9bz . The beater 10bz can strike directly on a rear end of the drill bit 3bz or indirectly transfer part of its momentum to the drill bit 3bz via a substantially stationary beater 13bz .

Die Werkzeugaufnahme 2bz hat beispielsweise eine Hülse 14bz, in welche der Bohrmeißel 3bz eingesetzt werden kann. Ein oder mehrere Verriegelungselemente 15bz, z.B. Kugeln, ragen in die Hülse 14bz und greifen in längs geschlossene Nuten des Bohrmeißels 3bz ein. Der Bohrmeißel 3bz kann entsprechend der Länge seiner Nuten in der Werkzeugaufnahme 2bz längs der Arbeitsachse 5bz gleiten. Der Drehantrieb 6bz dreht die Hülse 14bz um die Arbeitsachse 5bz. The tool holder 2bz has, for example, a sleeve 14bz into which the drill bit 3bz can be inserted. One or more locking elements 15bz, eg balls, protrude into the sleeve 14bz and engage in longitudinally closed grooves of the drill bit 3bz . The drill bit 3bz can slide according to the length of its grooves in the tool holder 2bz along the working axis 5bz . The rotary drive 6bz rotates the sleeve 14bz about the working axis 5bz.

Der Anwender kann den Bohrhammer 1 bz per Hand mittels eines Handgriffs 16bz führen. Der Handgriff 16bz ist an einer der Werkzeugaufnahme 2bz abgewandten Seite des Maschinengehäuses 8bz befestigt. Eine Längsachse 17bz des Handgriffs 16bz verläuft schräg oder senkrecht zu der Arbeitsachse 5bz. Der Bohrhammer 1 bz ist z.B. spiegelsymmetrisch zu einer Symmetrieebene (entspricht der Ebene der Zeichnung), die durch die Arbeitsachse 5bz und die Längsachse 17bz des Handgriffs 16bz aufgespannt wird. Eine Achse senkrecht zur der Symmetrieebene wird nachfolgend als x-Achse bezeichnet. Die y-Achse ist senkrecht zur x-Achse und zu der Arbeitsachse 5bz. The user can perform the hammer drill 1 bz by hand by means of a handle 16bz . The handle 16bz is attached to a side facing away from the tool holder 2bz side of the machine housing 8bz . A longitudinal axis 17bz of the handle 16bz extends obliquely or perpendicular to the working axis 5bz. The hammer drill 1 bz is, for example mirror-symmetrical to a plane of symmetry (corresponds to the plane of the drawing), which is spanned by the working axis 5bz and the longitudinal axis 17bz of the handle 16bz . An axis perpendicular to the plane of symmetry is hereinafter referred to as the x-axis. The y-axis is perpendicular to the x-axis and to the working axis 5bz.

Das periodisch arbeitende Schlagwerk 4bz führt zu Schwingungen oder Vibrationen in dem Maschinengehäuse 8bz. Federnde Aufhängungen 20Cz, 21 bz des Handgriffs 16bz an dem Maschinengehäuse 8bz unterdrücken teilweise eine Übertragung der Schwingungen auf den Handgriff 16bz, um die physiologischen Belastungen des Anwenders zu verringern.The periodically operating impact mechanism 4bz causes vibrations in the engine case 8bz. Spring suspensions 20Cz, 21bz of the handle 16bz on the machine housing 8bz partially suppress transmission of the vibrations to the handle 16bz to reduce the physiological stresses on the user.

Eine weitere Verringerung der Belastungen für den Anwender wird durch einen Tilger 30Cz erreicht, welche in dem Maschinengehäuse 8bz angeordnet ist. Der Tilger 30Cz hat einen Massekörper 31 bz, der mittels eine Federeinrichtung 32bz an dem Maschinengehäuse 8bz angebunden ist. Das schwingende Maschinengehäuses 8bz regt den Massekörper 31 bz des Tilgers 30Cz zum Mitschwingen an. Das System aus Massekörper 31bz und einer Federeinrichtung 32bz ist auf eine Eigenfrequenz abgestimmt, die etwas größer als die Anregungsfrequenz durch Maschinengehäuse 8bz, d.h. die Repetitionsrate des Schlagwerks 4bz ist. Der Tilger 30Cz kann der Schwingung des Maschinengehäuses 8bz nicht ganz folgen und stabilisiert sich in einer gegenphasigen Schwingung. Die Abweichung der Eigenfrequenz zur Anregungsfrequenz ist vorzugsweise gering, z. B. geringer als 10 %, wodurch eine effiziente Energieübertragung zwischen Maschinengehäuse 8bz und Tilger 30Cz erreicht wird.Further reduction of the burden on the user is achieved by a wiper 30Cz disposed in the machine housing 8bz . The absorber 30Cz has a mass body 31 bz, which is connected by means of a spring device 32bz to the machine housing 8bz . The oscillating machine housing 8bz stimulates the mass body 31 bz of the absorber 30Cz to resonate. The system of mass body 31bz and a spring means 32bz is tuned to a natural frequency which is slightly larger than the excitation frequency through the machine housing 8bz, ie the repetition rate of the impact mechanism 4bz . The absorber 30Cz can not quite follow the vibration of the machine housing 8bz and stabilizes in an antiphase oscillation. The deviation of the natural frequency to the excitation frequency is preferably low, z. B. less than 10%, whereby an efficient energy transfer between the machine housing 8bz and absorber 30Cz is achieved.

Fig. 2 zeigt im Detail eine Ausführungsform des Tilgers 30Cz. Der Tilger 30Cz hat ein Gehäuse 33bz, in dem der Massekörper 31 bz längs zu einer Schwingungsachse 34bz gelagert ist. Ein beispielhaftes Lager 35bz beinhaltet Rundstäbe 36bz, welche parallel zu der Schwingungsachse 34bz ausgerichtet in dem Gehäuse 33bz befestigt sind. Der Massekörper 31 bz hat Längsbohrung 37bz oder Längsnuten durch die Rundstäbe 36bz verlaufen. Das Lager 35bz ist vorzugsweise reibungsarm. Andere Ausgestaltungen von Linearlagern, z.B. mit Rollkörpern können ebenfalls verwendet werden. Fig. 2 shows in detail an embodiment of the absorber 30Cz. The absorber 30Cz has a housing 33bz, in which the mass body 31 bz is mounted longitudinally to a vibration axis 34bz . An exemplary bearing 35bz includes round bars 36bz which are mounted in parallel to the vibration axis 34bz in the housing 33bz . The mass body 31 bz has longitudinal bore 37bz or longitudinal grooves extending through the round rods 36bz . The bearing 35bz is preferably low friction. Other embodiments of linear bearings, eg with rolling bodies can also be used.

Der Massekörper 31 bz kann von einer Grundstellung 38bz (in Fig. 2 dargestellt) aus längs der Schwingungsachse 34bz in eine erste Richtung 39bz zu einem ersten Ende 40bz des Tilgers 30Cz und längs der Schwingungsachse 34bz in eine gegenläufige, zweite Richtung 41 bz zu einem zweiten Ende 42bz des Tilgers 30Cz verschoben werden. Die Federeinrichtung 32bz bewirkt eine Rückstellkraft auf den Massekörper 31bz, sobald dieser aus der Grundstellung 38bz ausgelenkt ist. Die Federeinrichtung 32bz ist asymmetrisch zu der Grundstellung 38bz aufgebaut. In dem dargestellten Beispiel fällt die Grundstellung 38bz mit einer geometrischen Mitte der Federeinrichtung 32bz oder des Tilgers 30Cz zusammen und somit ist die Federeinrichtung 32bz asymmetrisch zu einer Ebene 43bz, die senkrecht zur Arbeitsachse 5bz ist und durch die geometrische Mitte der Federeinrichtung 32bz verläuft. Auf den Massekörper 31 bz wirkt größere Rückstellkraft, wenn dieser um einen Hub in die erste Richtung 39bz aus der Grundstellung 38bz ausgelenkt, als wenn der Massekörper 31 bz um den selben Hub in die entgegengesetzte zweite Richtung 41bz aus der Grundstellung 38bz ausgelenkt ist.The mass body 31 bz can from a basic position 38bz (in Fig. 2 shown) along the vibration axis 34bz 30Cz be moved out in a first direction 39bz to a first end of the damper 40bz 30Cz and along the oscillation axis 34bz in an opposite, second direction 41 bz to a second end of the damper 42bz. The spring device 32bz causes a restoring force on the mass body 31bz, as soon as it is deflected from the basic position 38bz . The spring device 32bz is constructed asymmetrically to the basic position 38bz . In the illustrated example, the home position 38bz coincides with a geometric center of the spring means 32bz or the absorber 30cz and thus the spring means 32bz is asymmetrical to a plane 43bz which is perpendicular to the working axis 5bz and passes through the geometric center of the spring means 32bz . On the mass body 31 bz greater restoring force acts when deflected by a stroke in the first direction 39bz from the basic position 38bz , as if the mass body 31 bz is deflected bzz to the same stroke in the opposite second direction 41bz from the basic position 38bz .

Die beispielhafte Federeinrichtung 32bz hat erste Federn 44bz, zweite Federn 45bz und eine dritte Feder 46bz. Die ersten Federn 44bz sind an dem ersten Ende 40bz des Gehäuses 33bz und an dem Massekörper 31 bz befestigt, z. B. durch Klemmelemente 47bz, 48bz. Die ersten Federn 44bz drücken den Massekörper 31 bz ausgelenkt aus der Grundstellung 38bz in die zweite Richtung 41 bz. Die zweiten Federn 45bz sind an dem zweiten Ende 42bz des Gehäuses 33bz und an dem Massekörper 31 bz befestigt. Durch die zweiten Federn 45bz ist der Massekörper 31 bz ausgelenkt aus der Grundstellung 38bz in die erste Richtung 39bz kraftbeaufschlagt. Die ersten Federn 44bz und zweiten Federn 45bz können gleich ausgebildet, z.B. mit gleicher Länge und gleicher Federsteifigkeit, sein. Die ersten Federn 44bz und zweiten Federn 45bz können vorgespannt sein, wenn der Massekörper 31 bz in der Grundstellung 38bz ist. Weiters können die ersten Federn 44bz und zweiten Federn 45bz auch vorgespannt sein, wenn der Massekörper 31 bz in die eine oder andere Richtung 39bz, 41 bz maximal ausgelenkt sind. Hierdurch kann ein Lastwechsel von Druckbelastung auf Zugbelastung der Federn 44bz, 45bz vermieden werden.The exemplary spring means 32bz has first springs 44bz, second springs 45bz and a third spring 46bz. The first springs 44bz are fastened to the first end of the housing 40bz 33bz and the mass body 31 bz, z. B. by clamping elements 47bz, 48bz. The first springs 44bz push the mass body 31 bz deflected from the basic position 38bz in the second direction 41 bz. The second springs 45bz are attached to the second end 42bz of the housing 33bz and to the mass body 31 bz . By the second springs 45bz of the mass body 31 bz is deflected from the basic position 38bz in the first direction 39bz kraftbeaufschlagt. The first springs 44bz and second springs 45bz may be of the same design, eg with the same length and the same spring rigidity . The first springs 44bz and second springs 45bz may be biased when the mass body 31 bz is in the home position 38bz . Furthermore, the first springs 44bz and second springs 45bz may also be biased when the mass body 31 bz are deflected maximally in one or the other direction 39bz, 41 bz . As a result, a load change of pressure load on tensile load of the springs 44bz, 45bz can be avoided.

Die dritte Feder 46bz ist nur auf einer Seite des Massekörpers 31 bz angeordnet, beispielhaft zwischen dem ersten Ende 40bz des Gehäuses 33bz und dem Massekörper 31 bz. Die dritte Feder 46bz ist fest mit dem Gehäuse 33bz verbunden, jedoch nur an den Massekörper 31 bz in dessen Grundstellung 38bz angelegt. Wenn sich der Massekörper 31 bz von der Grundstellung 38bz aus in die erste Richtung 39bz bewegt wird die dritte Feder 46bz komprimiert. Bei einer Bewegung in die zweite Richtung 41 bz löst sich die dritte Feder 46bz von dem Massekörper 31 bz sobald dieser die Grundstellung 38bz überschreitet. Alternativ ist die dritte Feder 46bz mit dem Massekörper 31 bz fest verbunden und löst sich aus einem Sitz 49bz an dem Gehäuse 33bz. Die Länge der dritten Feder 46bz ist gleich dem Abstand des Massekörpers 31 bz bis zu dem Sitz 49bz gewählt. Die dritte Feder 46bz ist ohne Vorspannung, wenn der Massekörper 31 bz in der Grundstellung 38bz ist.The third spring 46bz is arranged only on one side of the mass body 31 bz, by way of example between the first end 40bz of the housing 33bz and the mass body 31 bz. The third spring 46bz is fixedly connected to the housing 33bz, but only in the mass body 31 bz in whose basic position 38bz created. When the mass body 31 moves from the basic position 38bz in the first direction 39bz , the third spring 46bz is compressed. Upon movement in the second direction 41 bz , the third spring 46bz detaches itself from the mass body 31 as soon as it exceeds the basic position 38bz . Alternatively, the third spring 46bz fixedly connected to the mass body 31 bz and detaches from a seat 49bz on the housing 33bz. The length of the third spring 46bz is equal to the distance of the mass body 31 bz selected to the seat 49bz . The third spring 46bz is without bias when the mass body 31 bz is in the home position 38bz .

Die Federsteifigkeit der Federeinrichtung 32bz auf der ersten Seite 50bz des Massekörpers 31 bz, d.h. in die erste Richtung 39bz, kann fünf bis zehnmal so groß gewählt werden die sein wie die Federsteifigkeit der Federeinrichtung 32bz auf der zweiten Seite 51 bz. In dem gezeigten Beispiel mit zwei ersten Federn 44bz und einer dritten Feder 46bz auf der ersten Seite 50bz und zwei zweiten Federn 45bz auf der zweiten Seite 50bz kann die dritte Feder 46bz mit der drei bis achtfachen Steifigkeit wie die gleichen ersten und zweite Federn 45bz, 42bz gewählt werden.The spring stiffness of the spring means 32bz on the first side 50bz of the mass body 31 bz, ie in the first direction 39bz, can be five to ten times larger than the spring stiffness of the spring device 32bz on the second side 51 bz. In the example shown two first springs 44bz and a third spring 46bz on the first side 50bz and two second springs 45bz on the second side 50bz , the third spring 46bz having three to eight times stiffness may be selected as the same first and second springs 45bz, 42bz .

Bei dem vorgestellten Bohrhammer 1 bz ist der Tilger 30Cz mit der ersten Richtung 39bz auf das Werkzeug 3bz, d.h. in Schlagrichtung 25, weisend angeordnet. Beim Schlag des Schlägers 10bz auf das Werkzeug 3bz und dessen Eintreiben in den Untergrund ergibt sich ein kurzer Rückstoss mit hoher Amplitude, welche besser an die steifere Seite des Tilgers 30Cz ankoppelt. Ein zweiter schwächerer und zeitlich länger wirkender Rückschlag ergibt sich, wenn der Schläger 10bz von dem Erreger 9bz über das Luftpolster abgestoßen wird. Dieser weichere Rückschlag koppelt besser an die weichere Seite des Tilgers 30Cz an.In the presented hammer drill 1 bz the absorber 30Cz with the first direction 39bz on the tool 3bz, that is arranged in the direction of impact 25, facing . At the beat of the Racket 10bz on the tool 3bz and its driving into the ground results in a short recoil with high amplitude, which better couples to the stiffer side of the damper 30Cz. A second weaker and longer acting kickback occurs when the bat 10bz is repelled by the exciter 9bz over the air cushion. This softer kick connects better to the softer side of the 30Cz Tiller .

Die Federn 44bz, 45bz, 46bz sind beispielsweise Schraubenfedern aus Stahl. Die ersten Federn 44bz und die zweiten Federn 45bz können koaxial zu den Rundstäben 36bz angeordnet sein.The springs 44bz, 45bz, 46bz are, for example, coil springs made of steel. The first springs 44bz and the second springs 45bz may be arranged coaxially with the round bars 36bz .

In einer weiteren Ausführungsform kann die Federeinrichtung 32bz mit nur einer Feder auf jeder Seite 50bz, 51 bz des Massekörpers 31 bz ausgebildet sein, wobei die Federn 45bz, 46bz eine verschieden Federsteifigkeit aufweisen. Die weichere Feder 45bz ist vorzugsweise soweit vorgespannt, dass sie in jeder Stellung des Massekörpers 31 bz an diesem anliegt. Die härtere Feder 46bz löst sich von dem Massekörper 31 bz, wenn sich dieser aus der Grundstellung entgegen die weichere Feder 45bz bewegt.In a further embodiment, the spring device 32bz may be formed with only one spring on each side 50bz, 51bz of the mass body 31bz, the springs 45bz, 46bz having a different spring rigidity. The softer spring 45bz is preferably biased so far that it rests in each position of the mass body 31 bz to this. The harder spring 46bz detaches from the mass body 31bz as it moves from the home position against the softer spring 45bz.

Die Schwingachse 34bz ist parallel oder unter einem Winkel von weniger als 5 Grad zur Arbeitsachse 5bz der Handwerkzeugmaschine 1bz geneigt.The swing axis 34bz is inclined parallel or at an angle of less than 5 degrees to the working axis 5bz of the portable power tool 1bz .

Fig. 3 und 4 zeigen eine weitere Ausführungsform. Die Federeinrichtung 32bz hat eine Biegefeder 60Cz, z.B. Blattfeder, welche senkrecht zur Schwingachse 34bz ausgerichtet ist. Die Biegefeder 60Cz ist mit einem Ende 61 bz an einem Sitz 62bz in dem Gehäuse 33bz des Tilgers 63bz befestigt. An dem anderen Ende 64bz ist der Massekörper 31 bz befestigt. Der Massekörper 31 bz pendelt längs der Schwingachse 34bz, wobei die Biegefeder 60Cz entlang ihrer Längsausdehnung verbogen wird. Eine Grundstellung 38bz des Massekörpers 31 bz ergibt sich bei entspannter, unverbogener Biegefeder 60Cz. 3 and 4 show a further embodiment. The spring device 32bz has a bending spring 60Cz, for example, leaf spring, which is aligned perpendicular to the swing axis 34bz . The bending spring 60Cz is fixed with one end 61 bz to a seat 62bz in the housing 33bz of the damper 63bz . At the other end 64bz of the mass body 31 bz is attached. The mass body 31 bz oscillates along the swing axis 34bz, bending the bending spring 60Cz along its longitudinal extent . A basic position 38bz of the mass body 31 bz results in a relaxed, unbent bending spring 60Cz.

Eine Schraubenfeder 65bz ist parallel zu der Schwingachse 34bz einseitig zu dem Massekörper 31 bz angeordnet. Die Schraubenfeder 65bz berührt den Massekörper 31 bz, wenn dieser in der Grundstellung ist. Bei einer Auslenkung des Massekörpers 31 bz in die erste Richtung 39bz wird die Schraubenfeder 65bz komprimiert. Auf den Massekörper 31 bz wirken die Rückstellkräfte der Biegefeder 60Cz und der Schraubenfeder 65bz. Bei einer Auslenkung des Massekörpers 31 bz in die gegenläufige zweite Richtung 41 bz (Fig. 4) löst sich der Massekörper 31 bz von der Schraubenfeder 65bz. Es wirkt nur die Rückstellkraft der Biegefeder 60Cz auf den Massekörper 31 bz. A helical spring 65bz is arranged parallel to the oscillating axis 34bz on one side to the mass body 31 bz . The coil spring 65bz touches the mass body 31 bz when it is in the normal position . In a deflection of the mass body 31 bz in the first direction 39bz , the coil spring 65bz is compressed. On the mass body 31 bz act the restoring forces of the bending spring 60Cz and the coil spring 65bz. In a deflection of the mass body 31 bz in the opposite second direction 41 bz ( Fig. 4 ) dissolves the mass body 31 bz of the coil spring 65bz. It acts only the restoring force of the bending spring 60Cz on the mass body 31 bz.

Claims (8)

Handwerkzeugmaschine mit einem längs einer Arbeitsachse oszillierenden Antrieb und einem Tilger (30Cz), der einen in einer Federeinrichtung (32bz) aufgehängten Massekörper (31 bz) aufweist, wobei die Federeinrichtung (32bz) bei einer Auslenkung des Massenkörpers (31 bz) aus einer Grundstellung in eine erste Richtung (39bz) parallel zu der Arbeitsachse (5bz) mit einer ersten Federsteifigkeit und bei einer Auslenkung aus der Grundstellung in eine der ersten Richtung (39bz) entgegengesetzten, zweiten Richtung (41bz) mit einer zweiten Federsteifigkeit entgegenwirkt und die erste Federsteifigkeit von der zweiten Federsteifigkeit verschieden ist. Hand tool with a longitudinally oscillating on a working axis drive and a damper (30Cz) having a in a spring device (32bz) suspended mass body (31 bz) , wherein the spring means (32bz) at a deflection of the mass body (31 bz) from a basic position in a first direction (39bz) parallel to the working axis (5bz) with a first spring stiffness and at a deflection from the home position in a first direction (39bz) opposite, second direction (41bz) counteracts with a second spring stiffness and the first spring stiffness of the second spring stiffness is different. Handwerkzeugmaschine nach Anspruch 1, dadurch gekennzeichnet, dass die erste Federsteifigkeit zwischen dem fünf und zehnfachen der zweiten Federsteifigkeit beträgt.Powered hand tool according to claim 1, characterized in that the first spring stiffness is between five and ten times the second spring stiffness. Handwerkzeugmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Massekörper (31 bz) in der zweiten Richtung (41 bz) ausgelenkt aus der Grundstellung von wenigstens einer Feder (46bz; 65bz) kraftfrei und in der ersten Richtung (39bz) ausgelenkt aus der Grundstellung von der wenigstens einen Feder (46bz; 65bz) kraftbeaufschlagt ist.Hand tool according to claim 1 or 2, characterized in that the mass body (31 bz) in the second direction (41 bz) deflected from the basic position of at least one spring (46bz; 65bz) without force and in the first direction (39bz) deflected out of the Basic position of the at least one spring (46bz; 65bz) is subjected to a force. Handwerkzeugmaschine nach Anspruch 3, dadurch gekennzeichnet, dass der Massekörper (31 bz) in der Grundstellung an der Feder (46bz, 65bz) anliegt. Powered hand tool according to claim 3, characterized in that the mass body (31 bz) in the basic position of the spring (46bz, 65bz) rests. Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Massekörper (31 bz) in der Grundstellung zwischen zwei vorgespannten Federn (44bz, 45bz) angeordnet ist.Hand tool according to one of the preceding claims, characterized in that the mass body (31 bz) in the basic position between two prestressed springs (44bz, 45bz) is arranged. Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche, dass die zwei vorgespannten Federn (44bz, 46bz) mit dem Massekörper (31 bz) fest verbunden sind. Hand tool according to one of the preceding claims, that the two prestressed springs (44bz, 46bz) with the mass body (31 bz) are firmly connected. Handwerkzeugmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Massekörper (31 bz) an einer Biegefeder (60Cz) befestigt ist, die geneigt zu der Arbeitsrichtung (5bz) angeordnet ist.Powered hand tool according to one of claims 1 to 4, characterized in that the mass body (31 bz) on a bending spring (60Cz) is fixed, which is inclined to the working direction (5bz) is arranged. Handwerkzeugmaschine nach Anspruch 7, dadurch gekennzeichnet, dass die Biegefeder (60Cz) entspannt ist, wenn der Massekörper (31 bz) in der Grundstellung ist. Powered hand tool according to claim 7, characterized in that the bending spring (60Cz) is relaxed when the mass body (31 bz) is in the normal position .
EP20110176970 2010-09-02 2011-08-09 Hand-held machine tool Active EP2425937B1 (en)

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DE102010040173A1 (en) 2012-03-08
US8985236B2 (en) 2015-03-24
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ES2532738T3 (en) 2015-03-31
CN102380854A (en) 2012-03-21

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