EP2047952B1 - Handtool machine with vibration balancing mass - Google Patents

Handtool machine with vibration balancing mass Download PDF

Info

Publication number
EP2047952B1
EP2047952B1 EP08105444A EP08105444A EP2047952B1 EP 2047952 B1 EP2047952 B1 EP 2047952B1 EP 08105444 A EP08105444 A EP 08105444A EP 08105444 A EP08105444 A EP 08105444A EP 2047952 B1 EP2047952 B1 EP 2047952B1
Authority
EP
European Patent Office
Prior art keywords
balancing mass
mass
spring
power tool
vibration
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.)
Active
Application number
EP08105444A
Other languages
German (de)
French (fr)
Other versions
EP2047952A1 (en
Inventor
Erwin Manschitz
Franz Popp
Franz Mössnang
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
Original Assignee
Hilti AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hilti AG filed Critical Hilti AG
Publication of EP2047952A1 publication Critical patent/EP2047952A1/en
Application granted granted Critical
Publication of EP2047952B1 publication Critical patent/EP2047952B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • B25D17/24—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
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted

Definitions

  • the invention refers to a hand tool with a striking mechanism, in particular a hammer drill, combination hammer or chisel hammer, with a vibration compensation mass, according to the preamble of claim 1 and as from EP 1415 768 A known.
  • a vibration balancing mass is a vibratory subsystem, which consists of an abstract vibratable mass, an abstract spring and an abstract damper, which must not be explicitly designed as a concrete component.
  • the abstract damper is often not realized as a concrete component and is still effective by practically always occurring friction and flow losses.
  • ordinary passive equalization masses which are exclusively self-excited, of actively controlled equalization compounds, which are deliberately externally excited by a mostly periodic excitation function.
  • the axially oscillating, passive vibration compensation mass is hollow-cylindrical; after EP1252976 arranged around the guide tube of the percussion and guided linearly along it.
  • the natural frequency of the vibration compensation mass corresponds as exactly as possible to the vibration frequency to be damped.
  • the natural frequency depends essentially on the mass of the balancing mass and the spring stiffness.
  • the object of the invention consists in the simple realization of respect to the natural frequency closely tolerated vibration compensation masses of hand tool machines in large quantities. Another aspect consists in the technologically simple production of different mass-based balancing weights for vibration compensation masses for various model platforms of hand tool machines.
  • a hand tool on an internal (eg gear cover housing) or external (eg outer housing) housing at least one vibration compensating mass with at least one axially oscillatable along a vibration axis, in itself rigid balancing mass, which is axially pressure-biased via at least one spring to the housing, wherein the inherently rigid leveling compound is formed in several parts.
  • the partial mass on an adjustment bore which can be done on the diameter of a technologically simple adjustment (via a mandrel used in the tool of different diameters) of the mass of the partial mass by this is reduced by the mass of the Justagezylinders.
  • the balancing mass composed of along the swing axis packetized masses, further advantageous with laser welding, plasma welding, sigma welding) welded together, which on the nature and number of packetized masses the mass of the balancing mass for vibration compensation masses for various model platforms of portable power tools is discreetly adjustable.
  • the balancing mass is advantageously composed of identical partial masses packed along the oscillating axis, as a result of which the masses are produced in bulk in very large quantities and are advantageously punched out of sheet metal and laser-welded. As a result, tight-tolerance leveling compounds can be produced in large quantities.
  • the formed / embossed stop surfaces can be made for the spring ends in a partial mass with high accuracy.
  • the spring is arranged with respect to its axial spring length completely within the balancing mass, whereby the total length of the vibration balancing mass is essentially determined by the balancing mass length. Since this is thus the greatest possible, the smallest possible resonance frequencies can be achieved with a fixed oscillation compensation ground length and spring constants.
  • the spring is arranged in a pocket-shaped, prismatic recess of the balancing mass, whereby it is at least partially positively guided in the recess and thus can not break across at pressure threshold stress.
  • the spring is arranged on both sides of the end face around a respective stop mandrel, which is further advantageous sleeve-shaped, whereby the spring via a mutually approaching displacement of the fixed to the housing stop pins is druckvorspannbar and thus allow axial limited oscillation of the balancing mass.
  • FIG. 1 has a with respect to a striking axis A axially beating and rotating hand tool 1 on a along the striking axis A vibrating housing 2 (shown on the outer housing, but analogous to a dashed shown to vibration isolated inner housing of a percussion 17) fixed vibration compensation mass 3 with a vibratory leveling compound 4, which is mounted axially resiliently via a spring 5 to the outer housing 2.
  • the mirror plane S with the axis of impact A mirror-symmetrical vibration compensation mass 3 is fixed by means of fixing means 6 in the form of screws on the housing 2 of the power tool 1 on the handle 7 opposite convex upper housing 8.
  • the matching concave trained, inherently rigid balancing mass 4 is disposed within a majority of these in the plane of representation transverse to the impact axis A (except for the housing top 8 facing sector) comprehensive Schwingungsaus GmbHsmassengephaseuse 9 and axially movable on this along the striking axis A extending guide surfaces 10 guided.
  • the exactly one spring 5 is arranged in a prismatic, pocket-shaped in the representation plane transverse to the impact axis A, recess 11 of the leveling compound 4.
  • Fig. 2a, 2b is in a variant of the vibration-compensating mass 3 ', the inherently rigid balancing mass 4' in several parts of many welded together, along the swing axis A packetized and (except for the two end-side) identical part masses 12th composed.
  • the two springs 5 with respect to their axial spring length completely within the plane mirrored to the mirror plane S with the striking axis A mirror-symmetrical compensating mass 4 'and on both sides at the front by one on the housing 2 (FIG. Fig. 1 ) arranged stop mandrel 16 around, which is itself formed sleeve-shaped.
  • the axially compressed stop pins 16 on the housing 2 ( Fig. 1 ) whereby the compensating mass 4 'with respect to the stop pins 16 and the housing 2 ( Fig. 1 ) is axially oscillatable.
  • FIG. 3 and FIG. 4 is formed mirror-symmetrical to the mirror plane S with the striking axis
  • a two-fold rotationally symmetrical Fig. 3 is the balancing mass 4 'composed of two diametrically oriented, identical partial masses 12' and spot welded together at welding points 13.
  • the two diametrically oriented, identical sub-masses 12 are formed shell-shaped as sheet-metal bent parts and riveted to one another with rivets 14.
  • the subassembly 12" has an adjustment bore 15.

Description

Die Erfindung bezeichnet eine Handwerkzeugmaschine mit einem Schlagwerk, insbesondere einen Bohrhammer, Kombihammer oder Meisselhammer, mit einer Schwingungsausgleichsmasse, nach dem Oberbegriff von Anspruch 1 und wie aus EP 1415 768 A bekannt.The invention refers to a hand tool with a striking mechanism, in particular a hammer drill, combination hammer or chisel hammer, with a vibration compensation mass, according to the preamble of claim 1 and as from EP 1415 768 A known.

Bei axial schlagenden Handwerkzeugmaschinen sind insbesondere Gehäuseschwingungen am Führungshandgriff zu vermeiden. Bedingt durch die axiale Spiegelsymmetrie üblicher Handwerkzeugmaschinen treten diese bevorzugt innerhalb einer Vibrationsebene in axialer Richtung sowie längs des Führungshandgriffs auf.In case of axially impacting hand tool machines, in particular housing vibrations on the guide handle are to be avoided. Due to the axial mirror symmetry of conventional hand tool machines, these preferably occur within a vibration plane in the axial direction and along the guide handle.

Eine Schwingungsausgleichsmasse ist ein schwingungsfähiges Teilsystem, welches aus einer abstrakten schwingbaren Masse, einer abstrakten Feder und einem abstrakten Dämpfer besteht, welche jeweils nicht explizit als konkretes Bauteil ausgeführt sein müssen. Insbesondere der abstrakte Dämpfer wird oft nicht als konkretes Bauteil realisiert und ist dennoch durch praktisch stets auftretende Reib- und Strömungsverluste wirksam. Man unterscheidet gewöhnliche passive Schwingungsausgleichsmassen, welche ausschliesslich selbst erregt sind, von aktiv gesteuerten Schwingungsausgleichsmassen, welche über eine zumeist periodische Erregungsfunktion gezielt fremderregt sind.A vibration balancing mass is a vibratory subsystem, which consists of an abstract vibratable mass, an abstract spring and an abstract damper, which must not be explicitly designed as a concrete component. In particular, the abstract damper is often not realized as a concrete component and is still effective by practically always occurring friction and flow losses. A distinction is made between ordinary passive equalization masses, which are exclusively self-excited, of actively controlled equalization compounds, which are deliberately externally excited by a mostly periodic excitation function.

Durch eine geeignete Wahl der Federkonstanten und der Masse wird bei einer passiven Schwingungsausgleichsmasse dessen Eigenfrequenz entsprechend der zu dämpfenden Störfrequenz dimensioniert, in diesem Verwendungsfall der Vibration des Aussengehäuses der Handwerkzeugmaschine.By a suitable choice of the spring constants and the mass of a passive vibration compensation mass whose natural frequency is dimensioned according to the noise frequency to be damped, in this case of use, the vibration of the outer casing of the power tool.

Nach der FR2237734 werden bei schlagenden Handwerkzeugmaschinen zur Verminderung der Gehäuseschwingungen passive Schwingungsausgleichsmassen eingesetzt. Nach der DE815179 sind beidseitig lateral des Schlagwerks zwei axial schwingende, passive Schwingungsausgleichsmassen angeordnet.After FR2237734 are used in striking hand tool machines to reduce the housing vibrations passive vibration compensation compounds. After DE815179 are arranged on both sides laterally of the striking mechanism two axially oscillating, passive vibration compensation masses.

Nach der DE1281970 ist die axial schwingende, passive Schwingungsausgleichsmasse hohlzylinderförmig ausgebildet; nach der EP1252976 um das Führungsrohr des Schlagwerks herum angeordnet und längs dessen linear geführt.After DE1281970 the axially oscillating, passive vibration compensation mass is hollow-cylindrical; after EP1252976 arranged around the guide tube of the percussion and guided linearly along it.

Bei derartigen passiven Schwingungsausgleichsmassen ist es wichtig, dass die Eigenfrequenz der Schwingungsausgleichsmasse der zu dämpfenden Vibrationsfrequenz möglichst exakt entspricht. Die Eigenfrequenz hängt dabei wesentlich von der Masse der Ausgleichsmasse und der Federsteifigkeit ab.In the case of such passive vibration compensation masses, it is important that the natural frequency of the vibration compensation mass corresponds as exactly as possible to the vibration frequency to be damped. The natural frequency depends essentially on the mass of the balancing mass and the spring stiffness.

Die Aufgabe der Erfindung besteht in der einfachen Realisierung von bezüglich der Eigenfrequenz eng tolerierenden Schwingungsausgleichsmassen von Handwerkzeugmaschinen in hoher Stückzahl. Ein weiterer Aspekt besteht in der technologisch einfachen Herstellung von unterschiedlich massebehafteten Ausgleichsmassen für Schwingungsausgleichsmassen für verschiedene Modellplattformen von Handwerkzeugmaschinen.The object of the invention consists in the simple realization of respect to the natural frequency closely tolerated vibration compensation masses of hand tool machines in large quantities. Another aspect consists in the technologically simple production of different mass-based balancing weights for vibration compensation masses for various model platforms of hand tool machines.

Die Aufgabe wird im Wesentlichen durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen ergeben sich aus den Unteransprüchen.The object is essentially achieved by the features of claim 1. Advantageous developments emerge from the subclaims.

So weist eine Handwerkzeugmaschine an einem innenliegenden (bspw. Getriebedeckelgehäuse) oder aussenliegenden (bspw. Aussengehäuse) Gehäuse zumindest eine Schwingungsausgleichsmasse mit zumindest einer axial längs einer Schwingungsachse schwingbaren, in sich starren Ausgleichsmasse auf, welche über zumindest eine Feder zum Gehäuse axial druckvorgespannt ist, wobei die in sich starre Ausgleichsmasse mehrteilig ausgebildet ist.Thus, a hand tool on an internal (eg gear cover housing) or external (eg outer housing) housing at least one vibration compensating mass with at least one axially oscillatable along a vibration axis, in itself rigid balancing mass, which is axially pressure-biased via at least one spring to the housing, wherein the inherently rigid leveling compound is formed in several parts.

Durch die mehrteilig ausgebildete, in sich starre Ausgleichsmasse ist diese bezüglich verschiedener (den verschiedenen Modellplattformen von Handwerkzeugmaschinen zugeordneten) Massen aus Teilmassen kombiniert zusammensetzbar, wobei die Teilmassen selbst technologisch einfach und eng tolerierend als Massenprodukt herstellbar sind.Due to the multi-part trained, inherently rigid balancing mass this is combined with respect to different (the various model platforms of hand tool machines) masses composed of sub-masses, the sub-masses even technologically simple and tight tolerances as a mass product can be produced.

Vorteilhaft weist die Teilmasse eine Justagebohrung auf, wodurch über deren Durchmesser eine technologisch einfache Justage (über einen in das Werkzeug eingesetzten Dorn verschiedenen Durchmessers) der Masse der Teilmasse erfolgen kann, indem diese um die Masse des Justagezylinders vermindert ist.Advantageously, the partial mass on an adjustment bore, which can be done on the diameter of a technologically simple adjustment (via a mandrel used in the tool of different diameters) of the mass of the partial mass by this is reduced by the mass of the Justagezylinders.

Vorteilhaft ist die Ausgleichsmasse aus längs der Schwingachse paketierten Teilmassen zusammengesetzt, weiter vorteilhaft mit Laser-Schweissen, Plasma-Schweissen, Sigma-Schweissen) untereinander verschweisst, wodurch über die Art und Anzahl der paketierten Teilmassen die Masse der Ausgleichsmasse für Schwingungsausgleichsmassen für verschiedene Modellplattformen von Handwerkzeugmaschinen diskret einstellbar ist.Advantageously, the balancing mass composed of along the swing axis packetized masses, further advantageous with laser welding, plasma welding, sigma welding) welded together, which on the nature and number of packetized masses the mass of the balancing mass for vibration compensation masses for various model platforms of portable power tools is discreetly adjustable.

Vorteilhaft ist die Ausgleichsmasse aus längs der Schwingachse paketierten identischen Teilmassen zusammengesetzt, wodurch die Teilmassen in sehr hohen Stückzahlen als Massenprodukt anfallen und vorteilhaft aus Metallblech herausgestanzt und laserverschweisst sind. Dadurch sind eng tolerierende Ausgleichsmassen in hoher Stückzahl herstellbar.The balancing mass is advantageously composed of identical partial masses packed along the oscillating axis, as a result of which the masses are produced in bulk in very large quantities and are advantageously punched out of sheet metal and laser-welded. As a result, tight-tolerance leveling compounds can be produced in large quantities.

Die umgeformten / geprägten Anschlagflächen können für die Federenden in einer Teilmasse mit hoher Genauigkeit hergestellt werden.The formed / embossed stop surfaces can be made for the spring ends in a partial mass with high accuracy.

Erfindungsgemäß ist die Feder bezüglich ihrer axialen Federlänge vollständig innerhalb der Ausgleichsmasse angeordnet, wodurch die Gesamtlänge der Schwingungsausgleichsmasse im Wesentlichen durch die Ausgleichsmassenlänge bestimmt wird. Da diese somit grösstmöglichst ist, sind bei fest vorgegebener Schwingungsausgleichsmassenlänge und Federkonstanten kleinstmöglichste Resonanzfrequenzen erzielbar.According to the invention, the spring is arranged with respect to its axial spring length completely within the balancing mass, whereby the total length of the vibration balancing mass is essentially determined by the balancing mass length. Since this is thus the greatest possible, the smallest possible resonance frequencies can be achieved with a fixed oscillation compensation ground length and spring constants.

Vorteilhaft ist die Feder in einer taschenförmigen, prismatischen Aussparung der Ausgleichsmasse angeordnet, wodurch diese zumindest teilweise in der Aussparung zwangsgeführt ist und somit bei Druckschwellbeanspruchung nicht quer ausbrechen kann.Advantageously, the spring is arranged in a pocket-shaped, prismatic recess of the balancing mass, whereby it is at least partially positively guided in the recess and thus can not break across at pressure threshold stress.

Vorteilhaft ist die Feder beidseitig stirnseitig um je einen Anschlagsdorn herum angeordnet, welcher weiter vorteilhaft hülsenförmig ausgebildet ist, wodurch die Feder über eine sich gegenseitig annährende Versetzung der am Gehäuse fixierten Anschlagsdorne druckvorspannbar ist und somit eine axiale begrenzte Schwingung der Ausgleichsmasse ermöglichen.Advantageously, the spring is arranged on both sides of the end face around a respective stop mandrel, which is further advantageous sleeve-shaped, whereby the spring via a mutually approaching displacement of the fixed to the housing stop pins is druckvorspannbar and thus allow axial limited oscillation of the balancing mass.

Die Erfindung wird bezüglich eines vorteilhaften Ausführungsbeispiels näher erläutert mit:

  • Fig. 1 als Handwerkzeugmaschine
  • Fig. 2a als Schwingungsausgleichsmasse (im nicht schwingfähigen, uneingebauten Zustand) der Handwerkzeugmaschine nach Fig. 1
  • Fig. 2b als Längsschnitt nach der Linie IIb - lib in Fig. 2a (im nicht schwingfähigen, uneingebauten Zustand)
  • Fig. 3 als weitere Variante der Ausgleichsmasse
  • Fig. 4 als weitere Variante der Ausgleichsmasse
The invention will be explained in more detail with respect to an advantageous embodiment with:
  • Fig. 1 as a hand tool machine
  • Fig. 2a as vibration compensation mass (in non-oscillatory, uninstalled state) of the power tool according to Fig. 1
  • Fig. 2b as a longitudinal section along the line IIb - lib in Fig. 2a (in non-oscillatory, uninstalled state)
  • Fig. 3 as another variant of the balancing mass
  • Fig. 4 as another variant of the balancing mass

Nach Fig. 1 weist eine bezüglich einer Schlagachse A axial schlagende und drehende Handwerkzeugmaschine 1 eine am längs der Schlagachse A vibrierenden Gehäuse 2 (dargestellt am Aussengehäuse, doch analog auch an einem gestrichelt dargestellten dazu schwingungsisolierten Innengehäuse eines Schlagwerks 17) festgelegte Schwingungsausgleichsmasse 3 mit einer schwingbaren Ausgleichsmasse 4 auf, welche über eine Feder 5 zum aussenliegenden Gehäuse 2 axial federnd gelagert ist. Die zur Spiegelebene S mit der Schlagachse A spiegelsymmetrisch ausgebildete Schwingungsausgleichsmasse 3 ist über Festlegungsmittel 6 in Form von Schrauben formschlüssig am Gehäuse 2 der Handwerkzeugmaschine 1 auf der dem Handgriff 7 gegenüberliegenden konvexen Gehäuseoberseite 8 festgelegt. Die dazu passend konkav ausgebildete, in sich starre Ausgleichsmasse 4 ist innerhalb eines diese in der Darstellungsebene quer zur Schlagachse A mehrheitlich (bis auf den zur Gehäuseoberseite 8 zugewandten Sektor) umfassenden Schwingungsausgleichsmassengehäuse 9 angeordnet und an diesem über längs der Schlagachse A verlaufende Führungsflächen 10 axial beweglich geführt. Die genau eine Feder 5 ist in einer prismatischen, in der Darstellungsebene quer zur Schlagachse A taschenförmigen, Aussparung 11 der Ausgleichsmasse 4 angeordnet.To Fig. 1 has a with respect to a striking axis A axially beating and rotating hand tool 1 on a along the striking axis A vibrating housing 2 (shown on the outer housing, but analogous to a dashed shown to vibration isolated inner housing of a percussion 17) fixed vibration compensation mass 3 with a vibratory leveling compound 4, which is mounted axially resiliently via a spring 5 to the outer housing 2. The mirror plane S with the axis of impact A mirror-symmetrical vibration compensation mass 3 is fixed by means of fixing means 6 in the form of screws on the housing 2 of the power tool 1 on the handle 7 opposite convex upper housing 8. The matching concave trained, inherently rigid balancing mass 4 is disposed within a majority of these in the plane of representation transverse to the impact axis A (except for the housing top 8 facing sector) comprehensive Schwingungsausgleichsmassengehäuse 9 and axially movable on this along the striking axis A extending guide surfaces 10 guided. The exactly one spring 5 is arranged in a prismatic, pocket-shaped in the representation plane transverse to the impact axis A, recess 11 of the leveling compound 4.

Nach Fig. 2a, 2b ist bei einer Variante der Schwingungsausgleichsmasse 3' die in sich starre Ausgleichsmasse 4' mehrteilig aus vielen untereinander verschweissten, längs der Schwingachse A paketierten und (bis auf die beiden stirnseitigen) identischen Teilmassen 12 zusammengesetzt. Dabei sind die beiden Federn 5 bezüglich ihrer axialen Federlänge vollständig innerhalb der zur Spiegelebene S mit der Schlagachse A spiegelsymmetrisch ausgebildeten Ausgleichsmasse 4' sowie beidseitig stirnseitig um je einen am Gehäuse 2 (Fig. 1) festgelegten Anschlagsdorn 16 herum angeordnet, welcher selbst hülsenförmig ausgebildet ist. Im nicht dargestellten eingebauten Zustand werden die dann axial zusammengedrückten Anschlagsdorne 16 am Gehäuse 2 (Fig. 1) festgelegt, wodurch die Ausgleichsmasse 4' gegenüber den Anschlagsdornen 16 und dem Gehäuse 2 (Fig. 1) axial schwingfähig ist.To Fig. 2a, 2b is in a variant of the vibration-compensating mass 3 ', the inherently rigid balancing mass 4' in several parts of many welded together, along the swing axis A packetized and (except for the two end-side) identical part masses 12th composed. In this case, the two springs 5 with respect to their axial spring length completely within the plane mirrored to the mirror plane S with the striking axis A mirror-symmetrical compensating mass 4 'and on both sides at the front by one on the housing 2 (FIG. Fig. 1 ) arranged stop mandrel 16 around, which is itself formed sleeve-shaped. In the installed state, not shown, then the axially compressed stop pins 16 on the housing 2 ( Fig. 1 ), whereby the compensating mass 4 'with respect to the stop pins 16 and the housing 2 ( Fig. 1 ) is axially oscillatable.

Nach Fig. 3 und Fig. 4 ist die zur Spiegelebene S mit der Schlagachse A spiegelsymmetrisch ausgebildeten Ausgleichsmasse 4" bezüglich der Schwingachse A zweizählig rotationssymmetrisch ausgebildet. Nach Fig. 3 ist die Ausgleichsmasse 4' aus zwei diametral orientierten, identischen Teilmassen 12' zusammengesetzt sowie an Schweisspunkten 13 miteinander punktverschweisst. Nach Fig. 4 sind die zwei diametral orientierten, identischen Teilmassen 12" schalenförmig als Blechbiegeteile ausgebildet sowie mit Nieten 14 miteinander vernietet. Zudem weist die Teilmasse 12" eine Justagebohrung 15 auf.To FIG. 3 and FIG. 4 is formed mirror-symmetrical to the mirror plane S with the striking axis A balancing mass 4 "with respect to the swing axis A two-fold rotationally symmetrical Fig. 3 is the balancing mass 4 'composed of two diametrically oriented, identical partial masses 12' and spot welded together at welding points 13. To Fig. 4 the two diametrically oriented, identical sub-masses 12 "are formed shell-shaped as sheet-metal bent parts and riveted to one another with rivets 14. In addition, the subassembly 12" has an adjustment bore 15.

Claims (7)

  1. Power tool with at least one vibration-balancing mass (3, 3') attached to a housing (2), with at least one intrinsically rigid balancing mass (4, 4', 4") which is axially vibratable along a vibration axis (A) and is axially resiliently mounted with respect to the housing (2) by means of at least one spring (5), the intrinsically rigid balancing mass (4, 4', 4") being made up of rigidly connected partial masses (12, 12', 12"), characterized in that the spring (5) is arranged with its axial spring length completely within the balancing mass (4, 4', 4").
  2. Power tool according to Claim 1, characterized in that the partial mass (12") has an adjustment hole (15).
  3. Power tool according to Claim 1, characterized in that the balancing mass (4') is composed of partial masses (12) stacked along the vibration axis (A).
  4. Power tool according to Claim 3, characterized in that the balancing mass (4') is composed of identical partial masses (12) stacked along the vibration axis (A).
  5. Power tool according to Claim 1, characterized in that the spring (5) is arranged inside a V-shaped pocket-like recess (11) in the balancing mass (4, 4', 4").
  6. Power tool according to any one of Claims 1 to 5, characterized in that the spring (5) is arranged around a stop boss (16) at each end.
  7. Power tool according to Claim 1, characterized in that the balancing mass is composed of two identical half-shells (12') arranged opposite each other on either side of the vibration axis (A).
EP08105444A 2007-10-09 2008-09-26 Handtool machine with vibration balancing mass Active EP2047952B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007000837A DE102007000837A1 (en) 2007-10-09 2007-10-09 Hand tool with vibration compensation mass

Publications (2)

Publication Number Publication Date
EP2047952A1 EP2047952A1 (en) 2009-04-15
EP2047952B1 true EP2047952B1 (en) 2012-08-22

Family

ID=40001439

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08105444A Active EP2047952B1 (en) 2007-10-09 2008-09-26 Handtool machine with vibration balancing mass

Country Status (4)

Country Link
US (1) US20090090528A1 (en)
EP (1) EP2047952B1 (en)
CN (1) CN101407051B (en)
DE (1) DE102007000837A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9555554B2 (en) 2013-05-06 2017-01-31 Milwaukee Electric Tool Corporation Oscillating multi-tool system

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4647957B2 (en) * 2004-08-27 2011-03-09 株式会社マキタ Work tools
US8056747B2 (en) * 2007-10-12 2011-11-15 General Electric Company Removable tank for laundry bulk dispenser system
DE102009054723A1 (en) * 2009-12-16 2011-06-22 Robert Bosch GmbH, 70469 Hand tool
DE102009054728A1 (en) * 2009-12-16 2011-06-22 Robert Bosch GmbH, 70469 Hand tool
DE102009054708A1 (en) * 2009-12-16 2011-06-22 Robert Bosch GmbH, 70469 Hand machine tool device
DE102010002262A1 (en) * 2010-02-23 2011-08-25 Robert Bosch GmbH, 70469 External absorber
DE102010041938A1 (en) * 2010-10-04 2012-04-05 Robert Bosch Gmbh Material distribution unit
US10232500B2 (en) * 2012-12-17 2019-03-19 Swerea Ivf Ab Impact machine
WO2015193284A1 (en) * 2014-06-16 2015-12-23 Swerea Ivf Ab An impact machine
CN215617869U (en) * 2018-04-04 2022-01-25 米沃奇电动工具公司 Rotary hammer suitable for applying axial impact to tool head

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2127821A1 (en) * 2008-05-27 2009-12-02 AEG Electric Tools GmbH Electric tool with vibration dampener

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1845825A (en) * 1927-07-22 1932-02-16 Chicago Pneumatic Tool Co Spring handle attachment for rock drills
US1868626A (en) * 1928-02-04 1932-07-26 Chicago Pneumatic Tool Co Shock absorbing handle
DE815179C (en) 1949-11-17 1951-10-01 Franz Dr-Ing Bollenrath Pneumatic hammer with mass balancing
US3230831A (en) * 1963-06-07 1966-01-25 Giddings & Lewis Vibration damper for machine tools
DE1281970B (en) 1964-06-25 1968-10-31 Reichsbahn Vertreten Durch Den Vibration damper for hammer
US3522864A (en) * 1968-05-08 1970-08-04 Cincinnati Milling Machine Co Tuned vibration damper assembly for machine tools
FR2237734A1 (en) 1973-07-16 1975-02-14 Inst Nal Rech Securite Oscillating mass shock absorbers for pneumatic drill - two sliding masses sprung above and below flank drill casing
DE3122979A1 (en) * 1981-06-10 1983-01-05 Hilti AG, 9494 Schaan DRILLING OR CHISEL HAMMER
US4612429A (en) * 1984-08-13 1986-09-16 Westinghouse Electric Corp. Multiple-impact shock absorbing means for circuit interrupter and other apparatus
US5471969A (en) * 1993-09-28 1995-12-05 Mcdonald, Jr.; Norman J. Stabilizers adapted to be connected to a bow
GB0109747D0 (en) 2001-04-20 2001-06-13 Black & Decker Inc Hammer
US6719503B1 (en) * 2001-09-07 2004-04-13 Unova Ip Corp Tuned damped absorber support
EP1415768A1 (en) 2002-10-31 2004-05-06 Atlas Copco Electric Tools GmbH Oscillation damper
DE602004026134D1 (en) * 2003-04-01 2010-05-06 Makita Corp power tool
DE10332637A1 (en) * 2003-07-18 2005-02-03 Andreas Stihl Ag & Co. Kg Anti-vibration element
WO2005105386A1 (en) * 2004-04-30 2005-11-10 Makita Corporation Working tool
GB2414702A (en) * 2004-06-04 2005-12-07 Black & Decker Inc Vibration Reduction Apparatus for Power Tool

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2127821A1 (en) * 2008-05-27 2009-12-02 AEG Electric Tools GmbH Electric tool with vibration dampener

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9555554B2 (en) 2013-05-06 2017-01-31 Milwaukee Electric Tool Corporation Oscillating multi-tool system

Also Published As

Publication number Publication date
EP2047952A1 (en) 2009-04-15
CN101407051B (en) 2012-12-05
US20090090528A1 (en) 2009-04-09
DE102007000837A1 (en) 2009-04-16
CN101407051A (en) 2009-04-15

Similar Documents

Publication Publication Date Title
EP2047952B1 (en) Handtool machine with vibration balancing mass
EP1952952B1 (en) Oscillation mass damper for hand tools
EP2425937B1 (en) Hand-held machine tool
EP1952950A2 (en) Portable power tool with an oscillation damper
EP1422029B1 (en) Vibration decoupled percussion mechanism assembly
EP1882559A1 (en) Hand tool with decoupling arrangement
EP1151827B1 (en) Hand tool with electrical percussion system
DE102007060636A1 (en) Electric hand tool, in particular a drill and / or chisel hammer, with a Tilgereinheit
EP2119537A1 (en) Electric hand tool
DE102007055843A1 (en) Hand tool with vibration compensator
EP2089192B1 (en) Mass oscillating unit for hand-held machine tools with a striking device
EP3227058B1 (en) Control method for a hand-held power tool
EP2379282B1 (en) Hand tool having counter-oscillator
EP3227056B1 (en) Hand-held power tool
EP1752259B1 (en) Electric hand tool
EP1787761B1 (en) Motor-driven hammer drill
EP2452782B1 (en) Hand tool
EP2127821B1 (en) Electric tool with vibration dampener
EP1674210B1 (en) Tool with main handle mechanically decoupled
EP1886767A2 (en) Hand tool machine with pneumatic striking mechanism
EP1862266B1 (en) Hammer hand tool with axially flexible impact mechanism
EP2822734B1 (en) Hand-machine tool device
WO2009043627A1 (en) Auxiliary handle device
WO2011000609A1 (en) Device for reducing and/or compensating vibrations, in particular for a hand machine tool, and for application in hand machine tools
EP3626398A1 (en) Forcibly energised biharmonic damper

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

17P Request for examination filed

Effective date: 20091015

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20100526

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 571700

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120915

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502008008002

Country of ref document: DE

Effective date: 20121018

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20120822

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

Effective date: 20120822

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121122

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121222

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121123

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121224

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

BERE Be: lapsed

Owner name: HILTI AKTIENGESELLSCHAFT

Effective date: 20120930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121203

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120930

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20130523

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120926

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120930

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121122

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008008002

Country of ref document: DE

Effective date: 20130523

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120822

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120926

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080926

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 571700

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130926

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130926

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20190926

Year of fee payment: 12

Ref country code: SE

Payment date: 20190918

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20190919

Year of fee payment: 12

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200930

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200927

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200930

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230830

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20230920

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230920

Year of fee payment: 16