EP2452782B1 - Hand tool - Google Patents

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Publication number
EP2452782B1
EP2452782B1 EP11185181.2A EP11185181A EP2452782B1 EP 2452782 B1 EP2452782 B1 EP 2452782B1 EP 11185181 A EP11185181 A EP 11185181A EP 2452782 B1 EP2452782 B1 EP 2452782B1
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EP
European Patent Office
Prior art keywords
absorbers
hand
machine tool
held machine
working axis
Prior art date
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Application number
EP11185181.2A
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German (de)
French (fr)
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EP2452782A3 (en
EP2452782A2 (en
Inventor
Oliver Ohlendorf
Jörg Martin
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Hilti AG
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Hilti AG
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Publication of EP2452782A3 publication Critical patent/EP2452782A3/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/006—Vibration damping means
    • 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
    • B25D2211/06—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
    • 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
    • B25D2250/275—Tools having at least two similar components
    • 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
    • B25D2250/371—Use of springs
    • B25D2250/381—Leaf springs

Definitions

  • the present invention relates to a hand tool with an absorber.
  • Examples are from the EP2072191A1 or US2010038105A1 known.
  • a hand tool has a linear drive for moving a tool along a working axis, e.g. a motorized pneumatic striking mechanism.
  • At least two dampers are provided in the hand tool for damping vibrations along the working axis.
  • a resonant excitation of an oscillation of the first damper along the working axis takes place at a first resonance frequency, which differs from a second resonance frequency of the second damper for the oscillation along the working axis.
  • the two resonance frequencies differ in a range from 2% to 5%, i.e. the first frequency is 1.02 to 1.05 times greater than the second resonance frequency.
  • each of the two absorbers has a pendulum arm and a mass body.
  • the mass body is resiliently attached to a housing of the handheld power tool by means of the pendulum arm.
  • the end of the pendulum arm that is distant from the mass body forms a bearing point around which the mass body executes a torsional vibration, guided by the pendulum arm.
  • the deflection preferably remains low, e.g. less than 30 degrees around the bearing point, whereby the movement of the mass body is considered approximately as along the working axis.
  • the pendulum arm or the bearing is designed to be very stiff against deflection out of the plane of rotation, which results in very high resonance frequencies. These high resonance frequencies should be at least an order of magnitude or 10 times higher than the resonance frequencies for excitation along the working axis in order not to be excitable.
  • the resonance frequencies of the two absorbers can be adjusted by the length of the pendulum arms, which can differ in a range from 4% to 10%.
  • the length denotes the distance from the center of gravity of the mass body to that Bearing point of the pendulum arm on the housing.
  • the mass of the mass bodies can differ by 4% to 10%.
  • the pendulum arm of a first of the two absorbers is arranged parallel to a pendulum arm of a second of the two absorbers.
  • the pendulum arms can be inclined at least 70 degrees to the working axis.
  • the pendulum arms can be designed as a leaf spring.
  • the leaf springs can be connected by a web at an end remote from the mass bodies.
  • the two leaf springs are manufactured as a stamped part.
  • the mass body can be attached to the pendulum arm.
  • One embodiment provides that a periodicity with which the linear drive moves the tool along the working axis lies between the resonance frequencies of the two absorbers.
  • the tool typically becomes very anharmonic, i.e. clearly not sinusoidal. Therefore, the term periodicity or repetition rate seems more appropriate to indicate how often the tool moves back and forth in a time standard.
  • the periodicity is measured as a frequency in Hertz. If a frequency is used in the application for the description of an anharmonic movement, this denotes the basic frequency.
  • Fig. 1 shows schematically a hammer drill 1.
  • the hammer drill 1 has a tool holder 2 , in which a drill bit 3 can be used as a tool.
  • a motor 4 which drives an impact mechanism 5 and an output shaft 6, forms a primary drive of the hammer drill 1 .
  • a user can guide the hammer drill 1 by means of a handle 7 and put the hammer drill 1 into operation by means of a system switch 8 .
  • the hammer drill 1 continuously rotates the drill bit 3 about a working axis 9 and can thereby strike the drill bit 3 along the working axis 9 into an underground.
  • the striking mechanism 5 is, for example, a pneumatic striking mechanism 5.
  • An exciter 10 and a striker 11 are movably guided in the striking mechanism 5 along the working axis 9 .
  • the exciter 10 is coupled to the motor 4 via an eccentric 12 or a wobble finger and is forced to perform a periodic, linear movement.
  • An air spring formed by a pneumatic chamber 13 between the exciter 10 and the striker 11 couples a movement of the striker 11 to the movement of the exciter 10 .
  • the striker 11 can strike directly onto a rear end of the drill bit 3 or indirectly transfer part of its impulse to the drill bit 3 via an essentially stationary intermediate striker 14 .
  • the striking mechanism 5 and preferably the further drive components are arranged within a machine housing 15 .
  • a first damper 20 and a second damper 21 are arranged within the machine housing 15 .
  • the first damper 20 hides the second damper 21.
  • the section in the plane II-II through the two damper 20 , 21 is in Fig. 2 shown.
  • the first absorber 20 has a first mass body 22 , which is connected via a leaf spring 23 to a rigid bearing point 24 on the housing 15 .
  • the leaf spring 23 In the rest position, the leaf spring 23 is arranged at an angle 25 of at least 70 degrees to the working axis 9 .
  • a movement of the machine housing 15 along the working axis 9 can stimulate the mass body 22 to perform the same movement along the working axis 9 .
  • the mass body 22 is guided by the leaf spring 23 , the mass body 22 follows a curved path 26.
  • the deflections of the mass body 22 are small compared to a length 27 of the leaf spring 23 , as a result of which the movement can be assumed to be approximately parallel to the working axis 9 .
  • the length 27 of the leaf spring 23 is measured from the attachment 24 to the center of gravity of the first mass body 22 .
  • the leaf spring 23 counteracts a deflection of the mass body 22 from its rest position by a restoring force.
  • the restoring spring force, the length 27 of the leaf spring 23 and the mass of the mass body 22 determine a resonance frequency of the first damper 20 .
  • the leaf spring 23 has a lower rigidity along the working axis 9 compared to the directions perpendicular to the working axis 9. An excitation of the leaf spring 23 perpendicular to the working axis 9 is therefore only possible at very high frequencies.
  • the second damper 21 is constructed essentially the same as the first damper 20 .
  • a second mass body 28 is connected to the machine housing 15 via a second leaf spring 29 .
  • the second leaf spring 29 is preferably arranged parallel to the first leaf spring 23 and also, in the rest position, inclined by at least 70 degrees to the working axis 9 .
  • the two leaf springs 22 , 29 preferably have the same spring constant and thickness, whereas a length 30 of the second leaf spring 29 is 4% to 10% longer than the length 27 of the first leaf spring 22.
  • a mass of the second mass body 28 is approximately equal to the mass of the first mass body 22.
  • the different lengths 30 , 29 bring about a 2% to 5% lower resonance frequency of the second absorber 21.
  • the mass bodies 22 , 28 have a mass that is 4% to 10% different.
  • the leaf springs 22 , 29 can be produced as a stamped sheet.
  • the two leaf springs 22 , 29 can be connected via a bridge 31 .
  • Fig. 3 shows the behavior of the two absorbers 20 , 21 for different excitation frequencies f, the deflection is plotted on the ⁇ -axis normalized to the maximum deflection (amplitude) of the mass bodies 22 , 28 along the working axis 9 .
  • Curve 32 indicates the excitation spectrum for the first absorber 20
  • curve 33 the excitation spectrum for the second absorber 21 .
  • the two absorbers 20 , 21 are out of tune with each other.
  • the detuning of the resonance frequency 34 of the first damper 20 is greater than the resonance frequency 35 of the second damper 21. Excitation of a damper with frequencies greater than its resonance frequency can lead to an oscillation of the damper in the hand tool 1 and causes vibrations to be eradicated instead of being desired Increase the vibrations. This actually speaks against the use of a second damper with a different frequency for the damping of vibrations along the working axis 9.
  • the two dampers 20 , 21 are only slightly out of tune with one another, they will probably couple to one another and the low-frequency damper 21 does not yet build up when the excitation frequency f by the linear drive 5 lies between the resonance frequencies 35 , 34 of the two absorbers 20 , 21 .
  • the resonance frequency 34 of the first damper 20 should lie within a frequency band 36 within which the excitation spectrum 32 of the second damper 21 drops to no more than a quarter (hatched area), preferably no more than half of the maximum amplitude.
  • the two absorbers 20 , 21 then couple strongly to one another. Overall, there is a broader response for the overall system from the two absorbers 20 , 21 .
  • the coupling of the two absorbers 20 , 21 can be increased by the elastic bridge 31 between the leaf springs 29 , 22 .
  • the resonance frequencies 34 , 35 are preferably set via the pendulum arms 23 , 29 and the mass bodies 22 , 28 so that a periodicity of the linear drive 5 lies between the resonance frequencies 34 , 35 .
  • the absorbers 20 , 21 can also be used in a jigsaw or a saber saw.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Description

GEBIET DER ERFINDUNGFIELD OF THE INVENTION

Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine mit einem Tilger. Beispiele sind aus der EP2072191A1 oder US2010038105A1 bekannt.The present invention relates to a hand tool with an absorber. Examples are from the EP2072191A1 or US2010038105A1 known.

OFFENBARUNG DER ERFINDUNGDISCLOSURE OF THE INVENTION

Eine erfindungsgemäße Handwerkzeugmaschine hat einen Linearantrieb zum Bewegen eines Werkzeugs längs einer Arbeitsachse, z.B. ein motorisch betriebenes, pneumatisches Schlagwerk. Wenigstens zwei Tilger sind in der Handwerkzeugmaschine zum Dämpfen von Schwingungen längs der Arbeitsachse vorgesehen. Eine resonante Anregung einer Schwingung des ersten Tilgers längs der Arbeitsachse erfolgt bei einer ersten Resonanzfrequenz, welche sich von einer zweiten Resonanzfrequenz des zweiten Tilgers für die Schwingung längs der Arbeitsachse unterscheidet. Die beiden Resonanzfrequenzen unterscheiden sich in einem Bereich von 2 % bis 5 %, d.h. die erste Frequenz ist um das 1,02-fache bis 1,05-fache größer als die zweite Resonanzfrequenz.A hand tool according to the invention has a linear drive for moving a tool along a working axis, e.g. a motorized pneumatic striking mechanism. At least two dampers are provided in the hand tool for damping vibrations along the working axis. A resonant excitation of an oscillation of the first damper along the working axis takes place at a first resonance frequency, which differs from a second resonance frequency of the second damper for the oscillation along the working axis. The two resonance frequencies differ in a range from 2% to 5%, i.e. the first frequency is 1.02 to 1.05 times greater than the second resonance frequency.

Eine Ausgestaltung sieht vor, dass jeder der zwei Tilger jeweils einen Pendelarm und einen Massekörper aufweist. Der Massekörper ist federnd mittels des Pendelarms an einem Gehäuse der Handwerkzeugmaschine befestigt. Das von dem Massekörper entfernte Ende des Pendelarm bildet einen Lagerpunkt, um den der Massekörper geführt durch den Pendelarm eine Drehschwingung ausführt. Die Auslenkung bleibt vorzugsweise gering, z.B. geringer als 30 Grad um den Lagerpunkt, wodurch die Bewegung des Massekörpers näherungsweise als längs der Arbeitsachse aufgefasst wird. Gegen eine Auslenkung aus der Drehebene heraus ist der Pendelarm oder das Lager sehr steif ausgebildet, was in sehr hohen Resonanzfrequenzen resultiert. Diese hohen Resonanzfrequenzen sollten wenigstens eine Größenordnung oder das 10-fache höher als die Resonanzfrequenzen für ein Anregung längs der Arbeitsachse sein, um nicht anregbar zu sein.One embodiment provides that each of the two absorbers has a pendulum arm and a mass body. The mass body is resiliently attached to a housing of the handheld power tool by means of the pendulum arm. The end of the pendulum arm that is distant from the mass body forms a bearing point around which the mass body executes a torsional vibration, guided by the pendulum arm. The deflection preferably remains low, e.g. less than 30 degrees around the bearing point, whereby the movement of the mass body is considered approximately as along the working axis. The pendulum arm or the bearing is designed to be very stiff against deflection out of the plane of rotation, which results in very high resonance frequencies. These high resonance frequencies should be at least an order of magnitude or 10 times higher than the resonance frequencies for excitation along the working axis in order not to be excitable.

Eine Anpassung der Resonanzfrequenzen der beiden Tilger kann durch die Länge der Pendelarme erfolgen, welche sich in einem Bereich von 4 % bis 10 % unterscheiden können. Die Länge bezeichnet dabei den Abstand des Schwerpunkts des Massenkörpers bis zu dem Lagerpunkt des Pendelarms am Gehäuse. Alternativ oder zusätzlich kann die Masse der Massekörper um 4 % bis10 % unterschiedlich sein.The resonance frequencies of the two absorbers can be adjusted by the length of the pendulum arms, which can differ in a range from 4% to 10%. The length denotes the distance from the center of gravity of the mass body to that Bearing point of the pendulum arm on the housing. Alternatively or additionally, the mass of the mass bodies can differ by 4% to 10%.

Eine Ausgestaltung sieht vor, dass der Pendelarm eines ersten der zwei Tilger parallel zu einem Pendelarm eines zweiten der zwei Tilger angeordnet ist. Die Pendelarme können unter wenigstens 70 Grad zu der Arbeitsachse geneigt angeordnet sind. Die Pendelarme können als Blattfeder ausgebildet sind. Die Blattfedern können an einem den Massekörpern entfernten Ende durch einen Steg verbunden sein. In einer Ausführungsform sind die beiden Blattfedern als ein Stanzteil hergestellt. Der Massekörper kann auf den Pendelarm aufgesteckt sein.One embodiment provides that the pendulum arm of a first of the two absorbers is arranged parallel to a pendulum arm of a second of the two absorbers. The pendulum arms can be inclined at least 70 degrees to the working axis. The pendulum arms can be designed as a leaf spring. The leaf springs can be connected by a web at an end remote from the mass bodies. In one embodiment, the two leaf springs are manufactured as a stamped part. The mass body can be attached to the pendulum arm.

Eine Ausgestaltung sieht vor, dass eine Periodizität mit der der Linearantrieb das Werkzeug längs der Arbeitsachse bewegt zwischen den Resonanzfrequenzen der beiden Tilger liegt. Das Werkzeug wird typischerweise stark anharmonisch, d.h. deutlich nicht sinusförmig bewegt. Daher erscheint der Begriff der Periodizität oder Wiederholungsrate geeigneter anzugeben, wie häufig sich das Werkzeug in einem Zeitnormal vor- und zurückbewegt. Die Periodizität wird gleich einer Frequenz in Hertz gemessen. Falls eine Frequenz in der Anmeldung zur Beschreibung für eine anharmonische Bewegung verwendet wird, bezeichnet diese die Grundfrequenz.One embodiment provides that a periodicity with which the linear drive moves the tool along the working axis lies between the resonance frequencies of the two absorbers. The tool typically becomes very anharmonic, i.e. clearly not sinusoidal. Therefore, the term periodicity or repetition rate seems more appropriate to indicate how often the tool moves back and forth in a time standard. The periodicity is measured as a frequency in Hertz. If a frequency is used in the application for the description of an anharmonic movement, this denotes the basic frequency.

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
Querschnitt durch einen Tilger in Fig. 1
Fig. 3
ein Anregungssprektrum des Tilgers von Fig. 2.
The following description explains the invention using exemplary embodiments and figures. The figures show:
Fig. 1
a hand tool,
Fig. 2
Cross section through an absorber in Fig. 1
Fig. 3
an excitation spectrum of the Tilger from Fig. 2 ,

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 symbols in the figures, unless stated otherwise.

AUSFÜHRUNGSFORMEN DER ERFINDUNGEMBODIMENTS OF THE INVENTION

Fig. 1 zeigt schematisch einen Bohrhammer 1. Der Bohrhammer 1 hat eine Werkzeugaufnahme 2, in welche als Werkzeug ein Bohrmeißel 3 eingesetzt werden kann. Einen primären Antrieb des Bohrhammers 1 bildet ein Motor 4, welcher ein Schlagwerk 5 und eine Abtriebswelle 6 antreibt. Ein Anwender kann den Bohrhammer 1 mittels eines Handgriffs 7 führen und mittels eines Systemschalters 8 den Bohrhammer 1 in Betrieb nehmen. Im Betrieb dreht der Bohrhammer 1 den Bohrmeißel 3 kontinuierlich um eine Arbeitsachse 9 und kann dabei den Bohrmeißel 3 längs der Arbeitsachse 9 in einen Untergrund schlagen. Fig. 1 shows schematically a hammer drill 1. The hammer drill 1 has a tool holder 2 , in which a drill bit 3 can be used as a tool. A motor 4 , which drives an impact mechanism 5 and an output shaft 6, forms a primary drive of the hammer drill 1 . A user can guide the hammer drill 1 by means of a handle 7 and put the hammer drill 1 into operation by means of a system switch 8 . In operation, the hammer drill 1 continuously rotates the drill bit 3 about a working axis 9 and can thereby strike the drill bit 3 along the working axis 9 into an underground.

Das Schlagwerk 5 ist beispielsweise ein pneumatisches Schlagwerk 5. Ein Erreger 10 und ein Schläger 11 sind in dem Schlagwerk 5 längs der Arbeitsachse 9 beweglich geführt. Der Erreger 10 ist über einen Exzenter 12 oder einen Taumelfinger an den Motor 4 angekoppelt und zu einer periodischen, linearen Bewegung gezwungen. Eine Luftfeder gebildet durch eine pneumatische Kammer 13 zwischen Erreger 10 und Schläger 11 koppelt eine Bewegung des Schlägers 11 an die Bewegung des Erregers 10 an. Der Schläger 11 kann direkt auf ein hinteres Ende des Bohrmeißels 3 aufschlagen oder mittelbar über einen im Wesentlichen ruhenden Zwischenschläger 14 einen Teil seines Impuls auf den Bohrmeißel 3 übertragen. Das Schlagwerk 5 und vorzugsweise die weiteren Antriebskomponenten sind innerhalb eines Maschinengehäuses 15 angeordnet.The striking mechanism 5 is, for example, a pneumatic striking mechanism 5. An exciter 10 and a striker 11 are movably guided in the striking mechanism 5 along the working axis 9 . The exciter 10 is coupled to the motor 4 via an eccentric 12 or a wobble finger and is forced to perform a periodic, linear movement. An air spring formed by a pneumatic chamber 13 between the exciter 10 and the striker 11 couples a movement of the striker 11 to the movement of the exciter 10 . The striker 11 can strike directly onto a rear end of the drill bit 3 or indirectly transfer part of its impulse to the drill bit 3 via an essentially stationary intermediate striker 14 . The striking mechanism 5 and preferably the further drive components are arranged within a machine housing 15 .

Innerhalb des Maschinengehäuses 15 ist ein erster Tilger 20 und ein zweiter Tilger 21 angeordnet. In der Seitenansicht von Fig. 1 verdeckt der erste Tilger 20 den zweiten Tilger 21. Der Schnitt in der Ebene II-II durch die beiden Tilger 20, 21 ist in Fig. 2 dargestellt.A first damper 20 and a second damper 21 are arranged within the machine housing 15 . In the side view of Fig. 1 the first damper 20 hides the second damper 21. The section in the plane II-II through the two damper 20 , 21 is in Fig. 2 shown.

Der erste Tilger 20 hat einen ersten Massenkörper 22, der über eine Blattfeder 23 mit einem starren Lagerpunkt 24 an dem Gehäuse 15 verbunden ist. Die Blattfeder 23 ist, in Ruhelage, unter einem Winkel 25 von wenigstens 70 Grad zu der Arbeitsachse 9 angeordnet. Eine Bewegung des Maschinengehäuses 15 längs der Arbeitsachse 9 kann den Massenkörper 22 zu einer ebensolchen Bewegung längs der Arbeitsachse 9 anregen. Aufgrund der Führung des Massenkörpers 22 durch die Blattfeder 23 folgt der Massenkörper 22 einer gekrümmten Bahn 26. Die Auslenkungen des Massenkörpers 22 sind gering verglichen zu einer Länge 27 der Blattfeder 23, wodurch die Bewegung näherungsweise als parallel zu der Arbeitsachse 9 angenommen werden kann. Die Länge 27 der Blattfeder 23 wird von der Befestigung 24 bis zum Schwerpunkt des ersten Massekörpers 22 gemessen. Die Blattfeder 23 wirkt einer Auslenkung des Massenkörpers 22 aus seiner Ruhelage durch eine Rückstellkraft entgegen. Die rückstellende Federkraft, die Länge 27 der Blattfeder 23 und die Masse des Massekörpers 22 legen eine Resonanzfrequenz des ersten Tilgers 20 fest.The first absorber 20 has a first mass body 22 , which is connected via a leaf spring 23 to a rigid bearing point 24 on the housing 15 . In the rest position, the leaf spring 23 is arranged at an angle 25 of at least 70 degrees to the working axis 9 . A movement of the machine housing 15 along the working axis 9 can stimulate the mass body 22 to perform the same movement along the working axis 9 . Because the mass body 22 is guided by the leaf spring 23 , the mass body 22 follows a curved path 26. The deflections of the mass body 22 are small compared to a length 27 of the leaf spring 23 , as a result of which the movement can be assumed to be approximately parallel to the working axis 9 . The length 27 of the leaf spring 23 is measured from the attachment 24 to the center of gravity of the first mass body 22 . The leaf spring 23 counteracts a deflection of the mass body 22 from its rest position by a restoring force. The restoring spring force, the length 27 of the leaf spring 23 and the mass of the mass body 22 determine a resonance frequency of the first damper 20 .

Die Blattfeder 23 hat eine geringere Steifigkeit längs der Arbeitsachse 9 verglichen zu den Richtungen senkrecht zu der Arbeitsachse 9. Eine Anregung der Blattfeder 23 senkrecht zu der Arbeitsachse 9 ist somit nur mit sehr hohen Frequenzen möglich.The leaf spring 23 has a lower rigidity along the working axis 9 compared to the directions perpendicular to the working axis 9. An excitation of the leaf spring 23 perpendicular to the working axis 9 is therefore only possible at very high frequencies.

Der zweite Tilger 21 ist im wesentlichen gleich zu dem ersten Tilger 20 aufgebaut. Ein zweiter Massekörper 28 ist über eine zweite Blattfeder 29 mit dem Maschinengehäuse 15 verbunden. Die zweite Blattfeder 29 ist vorzugsweise parallel zu der ersten Blattfeder 23 angeordnet und ebenfalls, in Ruhelage, um wenigstens 70 Grad zu der Arbeitsachse 9 geneigt. Die beiden Blattfedern 22, 29 haben vorzugsweise die gleiche Federkonstante und Stärke, eine Länge 30 der zweiten Blattfeder 29 ist hingegen um 4 % bis 10 % länger als die Länge 27 der ersten Blattfeder 22. Eine Masse des zweiten Massekörpers 28 etwa gleich der Masse des ersten Massekörpers 22. Die unterschiedlichen Längen 30, 29 bewirken eine 2 % bis 5 % geringere Resonanzfrequenz des zweiten Tilgers 21. In einer weitere Ausgestaltung haben die Massekörper 22, 28 eine um 4 % bis 10 % unterschiedliche Masse.The second damper 21 is constructed essentially the same as the first damper 20 . A second mass body 28 is connected to the machine housing 15 via a second leaf spring 29 . The second leaf spring 29 is preferably arranged parallel to the first leaf spring 23 and also, in the rest position, inclined by at least 70 degrees to the working axis 9 . The two leaf springs 22 , 29 preferably have the same spring constant and thickness, whereas a length 30 of the second leaf spring 29 is 4% to 10% longer than the length 27 of the first leaf spring 22. A mass of the second mass body 28 is approximately equal to the mass of the first mass body 22. The different lengths 30 , 29 bring about a 2% to 5% lower resonance frequency of the second absorber 21. In a further embodiment, the mass bodies 22 , 28 have a mass that is 4% to 10% different.

Die Blattfedern 22, 29 können als ein gestanztes Blech hergestellt werden. Die beiden Blattfedern 22, 29 können über eine Brücke 31 zusammenhängen.The leaf springs 22 , 29 can be produced as a stamped sheet. The two leaf springs 22 , 29 can be connected via a bridge 31 .

Fig. 3 zeigt das Verhalten der beiden Tilger 20, 21 für verschiedene Anregungsfrequenzen f, über die γ-Achse ist die Auslenkung normiert auf die maximale Auslenkung (Amplitude) der Massenkörper 22, 28 längs der Arbeitsachse 9 aufgetragen. Die Kurve 32 gibt das Anregungsspektrum für den ersten Tilger 20, die Kurve 33 das Anregungsspektrum für den zweiten Tilger 21 an. Fig. 3 shows the behavior of the two absorbers 20 , 21 for different excitation frequencies f, the deflection is plotted on the γ-axis normalized to the maximum deflection (amplitude) of the mass bodies 22 , 28 along the working axis 9 . Curve 32 indicates the excitation spectrum for the first absorber 20 , curve 33 the excitation spectrum for the second absorber 21 .

Die beiden Tilger 20, 21 sind zueinander verstimmt. Die Verstimmung der Resonanzfrequenz 34 des ersten Tilgers 20 ist größer als die Resonanzfrequenz 35 des zweiten Tilgers 21. Eine Anregung eines Tilgers mit Frequenzen größer als dessen Resonanzfrequenz kann zu einem Aufschaukeln des Tilgers in der Handwerkzeugmaschine 1 führen und bewirkt statt eines gewünschten Tilgens von Vibrationen ein Verstärken der Vibrationen. Dies spricht eigentlich gegen den Einsatz eines zweiten Tilgers mit einer anderen Frequenz für das Tilgen von Schwingungen längs der Arbeitsachse 9. Es wurde jedoch erkannt, dass wenn die beiden Tilger 20, 21 nur etwas zueinander verstimmt sind, diese wohl aneinander ankoppeln und der niederfrequente Tilger 21 sich noch nicht aufschaukelt, wenn die Anregungsfrequenz f durch den Linearantrieb 5 zwischen den Resonanzfrequenzen 35, 34 der beiden Tilger 20, 21 liegt. Die Resonanzfrequenz 34 des ersten Tilgers 20 sollte dabei innerhalb eines Frequenzbandes 36 liegen, innerhalb welchem das Anregungsspektrum 32 des zweiten Tilgers 21 auf nicht mehr als ein Viertel (schraffierte Fläche), vorzugsweise nicht mehr als die Hälfte der Maximalamplitude abfällt. Die beiden Tilger 20, 21 koppeln dann stark aneinander an. Insgesamt ergibt sich für das Gesamtsystem aus den zwei Tilgern 20, 21 eine breitere Resonanz. Das Ankoppeln der beiden Tilger 20, 21 kann durch die elastische Brücke 31 zwischen den Blattfedern 29, 22 noch gesteigert werden. Die Resonanzfrequenzen 34, 35 werden vorzugsweise über die Pendelarme 23, 29 und die Massenkörper 22, 28 so eingestellt, dass eine Periodizität des Linearantriebs 5 zwischen den Resonanzfrequenzen 34, 35 liegt.The two absorbers 20 , 21 are out of tune with each other. The detuning of the resonance frequency 34 of the first damper 20 is greater than the resonance frequency 35 of the second damper 21. Excitation of a damper with frequencies greater than its resonance frequency can lead to an oscillation of the damper in the hand tool 1 and causes vibrations to be eradicated instead of being desired Increase the vibrations. This actually speaks against the use of a second damper with a different frequency for the damping of vibrations along the working axis 9. However, it was recognized that if the two dampers 20 , 21 are only slightly out of tune with one another, they will probably couple to one another and the low-frequency damper 21 does not yet build up when the excitation frequency f by the linear drive 5 lies between the resonance frequencies 35 , 34 of the two absorbers 20 , 21 . The resonance frequency 34 of the first damper 20 should lie within a frequency band 36 within which the excitation spectrum 32 of the second damper 21 drops to no more than a quarter (hatched area), preferably no more than half of the maximum amplitude. The two absorbers 20 , 21 then couple strongly to one another. Overall, there is a broader response for the overall system from the two absorbers 20 , 21 . The coupling of the two absorbers 20 , 21 can be increased by the elastic bridge 31 between the leaf springs 29 , 22 . The resonance frequencies 34 , 35 are preferably set via the pendulum arms 23 , 29 and the mass bodies 22 , 28 so that a periodicity of the linear drive 5 lies between the resonance frequencies 34 , 35 .

Die Tilger 20, 21 können auch in einer Stichsäge oder ein Säbelsäge eingesetzt werden.The absorbers 20 , 21 can also be used in a jigsaw or a saber saw.

Claims (10)

  1. Hand-held machine tool with a linear drive for moving a tool along a working axis (9) and two absorbers (20, 21), the resonance frequencies of which differ for a movement along the working axis (9), wherein the resonance frequency of the first of the two absorbers (20) lies within a frequency band, within which the stimulated second of the two absorbers (21) oscillates with a deflection, which corresponds to at least a quarter of a deflection with resonant stimulation of the second absorber (21).
  2. Hand-held machine tool according to claim 1, characterised in that the resonance frequencies of the absorbers (20, 21) vary by at least 2%.
  3. Hand-held machine tool according to claim 1 or 2, characterised in that each of the two absorbers (20, 21) has a pendulum arm (23, 29) and a mass body (22, 28), which is fastened to a housing (15) of the hand-held machine tool (1) in a resilient way by means of the pendulum arm (23, 29).
  4. Hand-held machine tool according to claim 3, characterised in that a length (27, 30) of the pendulum arms (23, 29) and/or a mass of the mass bodies (22, 28) differs in a range from 4% to 10%.
  5. Hand-held machine tool according to claim 3 or 4, characterised in that the pendulum arm (23, 29) of a first of the two absorbers (20, 21) is arranged parallel to the pendulum arm (29, 23) of a second of the two absorbers (21, 20).
  6. Hand-held machine tool according to claim 3, characterised in that the pendulum arms (23, 29) are arranged inclined to the working axis by least 70 degrees.
  7. Hand-held machine tool according to claim 3, characterised in that the pendulum arms (23, 29) are made as leaf springs.
  8. Hand-held machine tool according to claim 7, characterised in that the leaf springs are connected to an end away from the mass bodies (22, 28) by a bar.
  9. Hand-held machine tool according to one of the previous claims, characterised in that a resonance frequency for stimulation of the two absorbers (20, 21) into a movement perpendicular to the working axis is higher than the resonance frequency for the movement along the working axis by at least one order of magnitude.
  10. Hand-held machine tool according to one of the previous claims, characterised in that a periodicity, with which the linear drive (5) moves the tool along the working axis (9), lies between the resonance frequencies (34, 35) of both absorbers (20, 21).
EP11185181.2A 2010-11-12 2011-10-14 Hand tool Active EP2452782B1 (en)

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DE102010043810A DE102010043810A1 (en) 2010-11-12 2010-11-12 Hand tool

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Publication number Priority date Publication date Assignee Title
JP2014069293A (en) * 2012-09-28 2014-04-21 Hitachi Koki Co Ltd Impact tool
EP2848370A1 (en) * 2013-09-12 2015-03-18 HILTI Aktiengesellschaft Manual tool machine
EP2886261A1 (en) * 2013-12-18 2015-06-24 HILTI Aktiengesellschaft Manual tool machine
CN106457543B (en) * 2014-04-30 2019-11-19 工机控股株式会社 Power tool
EP3028818A1 (en) 2014-12-03 2016-06-08 HILTI Aktiengesellschaft Power tool

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54127080A (en) * 1978-03-25 1979-10-02 Makoto Nandate Vibration isolation device in handle of machine in which vibration is formed
JP4157382B2 (en) * 2001-04-11 2008-10-01 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング Hand-held machine tool with vibration-damping handgrip
JP4793755B2 (en) * 2006-03-07 2011-10-12 日立工機株式会社 Electric tool
BRPI0808724A2 (en) * 2007-05-01 2015-11-24 Hitachi Koki Kk reciprocating tools
US7806201B2 (en) * 2007-07-24 2010-10-05 Makita Corporation Power tool with dynamic vibration damping
DE102007060636A1 (en) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Electric hand tool, in particular a drill and / or chisel hammer, with a Tilgereinheit
DE102007055843A1 (en) * 2007-12-17 2009-06-25 Hilti Aktiengesellschaft Hand tool with vibration compensator
DE102008000625A1 (en) * 2008-03-12 2009-09-17 Robert Bosch Gmbh Hand tool

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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DE102010043810A1 (en) 2012-05-16
US20120125649A1 (en) 2012-05-24
EP2452782A2 (en) 2012-05-16

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