EP1990147A2 - Vibrating hand machine tool with anti-vibration element - Google Patents

Vibrating hand machine tool with anti-vibration element Download PDF

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Publication number
EP1990147A2
EP1990147A2 EP08103704A EP08103704A EP1990147A2 EP 1990147 A2 EP1990147 A2 EP 1990147A2 EP 08103704 A EP08103704 A EP 08103704A EP 08103704 A EP08103704 A EP 08103704A EP 1990147 A2 EP1990147 A2 EP 1990147A2
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EP
European Patent Office
Prior art keywords
spring
external thread
hand tool
vibration
spring wire
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EP08103704A
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German (de)
French (fr)
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EP1990147B1 (en
EP1990147A3 (en
Inventor
Franz Mössnang
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Hilti AG
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Hilti AG
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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
    • B25D17/04—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
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/361—Use of screws or threaded connections
    • 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

Definitions

  • the invention relates to a hand tool with a vibrating along a vibration axis assembly and a handle assembly, which is vibration decoupled via an anti-vibration element, in particular a drill or chisel hammer.
  • the handle is largely decoupled with respect to the transmission of vibrations by being connected to the vibrating assembly via an anti-vibration element.
  • the anti-vibration element may have both spring and damper properties.
  • each spring characteristic is linear, which is typical for low-loaded coil springs.
  • the spring characteristic becomes increasingly non-linear due to the material properties, especially when using elastomers.
  • suitable spring geometries such as leaf springs or other structural features such as one-sided contact constraints a spring.
  • the anti-vibration element is either completely realized as a hollow elastomeric cylinder or alternatively as a leaf spring hollow cylinder.
  • a disadvantage of an elastomeric hollow cylinder for use in the vibration damping of hand tool machines is its pronounced temperature and humidity dependence as well as the aging problem.
  • the metallic leaf spring hollow cylinder is a complicated to manufacture complex component.
  • DE102004031866 is for vibration damping of the handle of a vibrating hand tool an anti-vibration element with an axially non-linear spring characteristic already known, which consists of a spring wire coil, the two coil ends are each wound on a threaded dome, wherein the turns themselves Partially create only on one side of the external thread whose intermediate width is greater than the spring wire diameter.
  • the resulting axial non-linear spring characteristic goes smoothly in a progressively growing course after a linearly flat load area and then smoothly into a steeper linear course.
  • the core of the thread dome is tapered from the helical inner diameter axially on the spring side concave.
  • the object of the invention is the realization of a hand tool with an anti-vibration element with an axially non-linear spring characteristic, which has a steeper course on both sides of a linear flat middle load range.
  • Another aspect is the realization of a likewise non-linear spring characteristic with transverse load.
  • a handheld power tool includes a vibrating assembly along a vibration axis and a handle assembly that is vibration-decoupled via an anti-vibration member having a longitudinally oriented axis of the vibration spring coil having a plurality of windings on the unloaded anti-vibration element partially on a threaded dome with a Malawickenden over a biasing range External thread whose intermediate width is greater than the spring wire diameter of the spring wire coil, are screwed axially biased pressure.
  • the spring characteristic Due to the compressive bias of a portion of the spring wire coil and the external thread results in the spring characteristic on both sides of a flat linear center region in which all turns are exposed, each having an edge region with steeper characteristic, in which a part of the turns on the external thread and thus are no longer spring effective .
  • the spring characteristic In the low load range, where part of the windings are pressure-biased over the preload area, the spring characteristic is linearly steep because only the exposed windings are springy.
  • the spring characteristic In the high load range, in which an increasing part of the windings lie on the spring side on parts of the external thread within the preload area, the spring characteristic is progressively increasing, since fewer and fewer windings act resiliently.
  • the highest load range in which the windings within the preload area completely spring-side rest against the external thread, the spring characteristic is linearly steep, since only the exposed windings act resilient.
  • the pretensioning region which is delimited on the inside of the threaded end of the external thread, must be axially shorter than the coiled outer part of the unloaded spring wire filament.
  • the latter is thus on the outside of the inside contact surfaces of the threaded ends and thus biases the spring wire helix on the pressure side, until from the middle load range, this itself has shortened sufficiently and thus dissolves from a contact surface.
  • the spring wire helix is cylindrical and formed with a uniform pitch of the turns, whereby standard springs can be used.
  • the spring-side contact surface of the external thread on a non-linear slope whereby the spring characteristic in the high load range with respect to the progressive course is variable.
  • the external thread is a rectangular thread, whereby the contact surfaces (in longitudinal section) are axially oriented.
  • the radial height of the external thread is at least as large as the spring wire diameter, whereby the external thread forms axial contact surfaces even with combined transverse load.
  • the core of the thread dome starting from the helical inner diameter, is axially convexly tapered on the spring side, whereby, in the event of a transverse load, some turns radially engage the core of the thread dome and thus lead to a transverse progression.
  • FIG. 1 has a hand tool 12 shown only partially in the form of a chisel hammer on an anti-vibration element 1, which between a vibrating along a vibration axis A assembly 5 and a vibration-decoupled Handle assembly 6 is arranged.
  • the anti-vibration element 1 has a longitudinally oriented along the vibration axis A spring wire coil 7 with a plurality of turns 2, which are wound at a coil end on a threaded dome 3 with an external thread 4.
  • the anti-vibration element 1 is cylindrical and formed with a uniform pitch of the windings 2.
  • Fig. 2 lie in the illustrated load case of the anti-vibration element 1 without axial pressure load different turns 2 axially both spring-side and domed in a biasing V on the external thread 4 with axially two-sided contact surfaces 14, the intermediate Z is greater than the spring wire diameter D of the spring wire coil 7.
  • the spring wire coil 7 is located with different turns 7 on both contact surfaces 14 of the external thread 4.
  • the male thread 4 designed as a rectangular thread has a uniform pitch with respect to its spring-side contact surface 14 (analogously, a non-linear gradient is also possible, which is not explicitly shown).
  • the radial height H of the external thread 4 is greater than the spring wire diameter D.
  • the coaxially inner core of the threaded mandrel 3 is starting from the helical inner diameter S axially convexly tapered on the spring side.
  • Fig. 3 has the spring characteristic curve 13 (axial expansion X, axial force Fa) on both sides of a linearly flat middle region 9, in which all windings 2 (FIG. Fig. 2 ) are free, each having an edge region 8, 10 with a steeper characteristic, in which the turns 2 ( Fig. 2 ) only partially on the external thread 4 ( Fig. 2 ) abut axially.
  • the unloaded edge region 8 is the in the bias region V ( Fig. 2 ) prestressed part of the turns 2 ( Fig. 2 ) ineffective, so that results in a linear, steeper characteristic curve to overcome the bias.
  • the transition to the central region 9 forms a kink in the characteristic curve.
  • Fig. 4 has the spring characteristic 13 '(transverse strain Y, transverse force Fq) with increasing lateral load on a transverse progression by some turns 2 ( Fig. 2 ) down radially to the convex core of the threaded mandrel 3 ( Fig. 2 ) (not shown).

Abstract

The tool has a sub-assembly (5) that vibrates along a vibration axis. An anti-vibration element (1) vibrationally decouples a handle sub-assembly (6) from the sub-assembly (5) and has a coil spring (7) formed of a spring wire. A threaded plug (3) is provided with an outer thread (4). The coil spring (7) has a set of windings (2) extending along a preload region (V) and screwed on the outer thread under an axial compressive preload. The outer thread has an intermediate-channel width (Z) greater than diameter (D) of the wire, and has a spring-side contact surface having a non-linear pitch.

Description

Die Erfindung bezeichnet eine Handwerkzeugmaschine mit einer längs einer Vibrationsachse vibrierenden Baugruppe und einer Handgriffbaugruppe, die über ein Antivibrationselement schwingungsentkoppelt ist, insbesondere einen Bohr- oder Meisselhammer.The invention relates to a hand tool with a vibrating along a vibration axis assembly and a handle assembly, which is vibration decoupled via an anti-vibration element, in particular a drill or chisel hammer.

Üblicherweise wird bei vibrierenden Handwerkzeugmaschinen der Handgriff bezüglich der Übertragung von Vibrationen weitgehend entkoppelt, indem dieser über ein Antivibrationselement mit der vibrierenden Baugruppe verbunden ist. Dabei kann das Antivibrationselement sowohl Feder- als auch Dämpfereigenschaften aufweisen.Typically, in vibrating hand tool machines, the handle is largely decoupled with respect to the transmission of vibrations by being connected to the vibrating assembly via an anti-vibration element. In this case, the anti-vibration element may have both spring and damper properties.

Bei infinitesimalen Dehnungen ist jede Federkennlinie linear, was für gering belastete Schraubenfedern typisch ist. Bei grösseren Dehnungen wird die Federkennlinie auf Grund der Materialeigenschaften zunehmend nichtlinear, insbesondere bei Verwendung von Elastomeren. Zudem kann durch geeignete Federgeometrien wie Blattfedern oder weitere konstruktive Merkmale wie einseitige Kontaktzwänge eine Feder mit nichtlinearer Federkennlinie realisiert werden.At infinitesimal strains, each spring characteristic is linear, which is typical for low-loaded coil springs. For larger strains, the spring characteristic becomes increasingly non-linear due to the material properties, especially when using elastomers. In addition, can be realized by non-linear spring characteristic by suitable spring geometries such as leaf springs or other structural features such as one-sided contact constraints a spring.

Nach der W09416864 wird bei einer axial schlagenden Handwerkzeugmaschine zur Entkopplung des Handgriffs von der axial vibrierenden Baugruppe ein Antivibrationselement mit einer nichtlinearen Federkennlinie eingesetzt, die beidseitig eines linear flachen mittleren Belastungsbereiches glatt in einen progressiven Verlauf übergeht. Dazu ist das Antivibrationselement entweder komplett als ein Elastomerhohlzylinder oder alternativ als ein Blattfederhohlzylinder realisiert. Nachteilig bei einem Elastomerhohlzylinder zur Verwendung bei der Vibrationsdämpfung von Handwerkzeugmaschinen ist dessen ausgeprägte Temperatur- und Feuchtigkeitsabhängigkeit sowie die Alterungsproblematik. Der metallische Blattfederhohlzylinder hingegen ist ein aufwendig herzustellendes, komplexes Bauteil.After W09416864 is used in an axially striking hand tool for decoupling the handle of the axially vibrating assembly an anti-vibration element with a nonlinear spring characteristic, the smooth transition on both sides of a linear flat average load range in a progressive course. For this purpose, the anti-vibration element is either completely realized as a hollow elastomeric cylinder or alternatively as a leaf spring hollow cylinder. A disadvantage of an elastomeric hollow cylinder for use in the vibration damping of hand tool machines is its pronounced temperature and humidity dependence as well as the aging problem. The metallic leaf spring hollow cylinder, however, is a complicated to manufacture complex component.

Nach der DE102004031866 ist zur Vibrationsdämpfung des Handgriffs einer vibrierenden Handwerkzeugmaschine ein Antivibrationselement mit einer axial nichtlinearen Federkennlinie vorbekannt, das aus einer Federdrahtwendel besteht, deren beide Wendelenden jeweils auf einen Gewindedom gewickelt sind, wobei die Windungen sich teilweise ausschliesslich an einer Seite am Aussengewinde anlegen, dessen Zwischengangweite grösser als der Federdrahtdurchmesser ist. Die sich daraus ergebende axiale nichtlineare Federkennlinie geht nach einem linear flachen Belastungsbereich glatt in einen progressiv wachsenden Verlauf und danach glatt in einen steileren linearen Verlauf über. Der Kern des Gewindedoms ist ausgehend vom Wendelinnendurchmesser axial federseitig konkav verjüngt.After DE102004031866 is for vibration damping of the handle of a vibrating hand tool an anti-vibration element with an axially non-linear spring characteristic already known, which consists of a spring wire coil, the two coil ends are each wound on a threaded dome, wherein the turns themselves Partially create only on one side of the external thread whose intermediate width is greater than the spring wire diameter. The resulting axial non-linear spring characteristic goes smoothly in a progressively growing course after a linearly flat load area and then smoothly into a steeper linear course. The core of the thread dome is tapered from the helical inner diameter axially on the spring side concave.

Die Aufgabe der Erfindung besteht in der Realisierung einer Handwerkzeugmaschine mit einem Antivibrationselement mit einer axial nichtlinearen Federkennlinie, die beidseitig eines linear flachen mittleren Belastungsbereiches einen steileren Verlauf aufweist. Ein weiterer Aspekt besteht in der Realisierung einer ebenfalls nichtlinearen Federkennlinie bei Querbelastung.The object of the invention is the realization of a hand tool with an anti-vibration element with an axially non-linear spring characteristic, which has a steeper course on both sides of a linear flat middle load range. Another aspect is the realization of a likewise non-linear spring characteristic with transverse load.

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 eine längs einer Vibrationsachse vibrierende Baugruppe und eine Handgriffbaugruppe auf, die über ein Antivibrationselement schwingungsentkoppelt ist, welches eine längs der Vibrationsachse orientierte Federdrahtwendel mit mehreren Windungen aufweist, die am unbelasteten Antivibrationselement teilweise auf einen Gewindedom mit einem sich über einen Vorspannbereich längs ersteckenden Aussengewinde, dessen Zwischengangweite grösser als der Federdrahtdurchmesser der Federdrahtwendel ist, axial druckvorgespannt aufgeschraubt sind.Thus, a handheld power tool includes a vibrating assembly along a vibration axis and a handle assembly that is vibration-decoupled via an anti-vibration member having a longitudinally oriented axis of the vibration spring coil having a plurality of windings on the unloaded anti-vibration element partially on a threaded dome with a ersteckenden over a biasing range External thread whose intermediate width is greater than the spring wire diameter of the spring wire coil, are screwed axially biased pressure.

Durch die Druckvorspannung eines Teils der Federdrahtwendel sowie dem Aussengewinde ergibt sich in der Federkennlinie beidseitig eines linear flachen Mittenbereiches, bei welchem alle Windungen frei liegen, jeweils ein Randbereich mit steilerer Kennlinie, bei welchem ein Teil der Windungen am Aussengewinde anliegen und somit nicht mehr federwirksam sind. Im niedrigen Belastungsbereich, bei dem ein Teil der Windungen über den Vorspannbereich druckvorgespannt sind, ist die Federkennlinie linear steil, da nur noch die freiliegenden Windungen federnd wirken. Im hohen Belastungsbereich, bei dem ein zunehmender Teil der Windungen innerhalb des Vorspannbereiches federseitig an Teilen des Aussengewindes anliegen, ist die Federkennlinie progressiv ansteigend, da zunehmend weniger Windungen federnd wirken. Im höchsten Belastungsbereich, bei dem die Windungen innerhalb des Vorspannbereiches federseitig vollständig am Aussengewinde anliegen, ist die Federkennlinie linear steil, da nur noch die freiliegenden Windungen federnd wirken.Due to the compressive bias of a portion of the spring wire coil and the external thread results in the spring characteristic on both sides of a flat linear center region in which all turns are exposed, each having an edge region with steeper characteristic, in which a part of the turns on the external thread and thus are no longer spring effective , In the low load range, where part of the windings are pressure-biased over the preload area, the spring characteristic is linearly steep because only the exposed windings are springy. In the high load range, in which an increasing part of the windings lie on the spring side on parts of the external thread within the preload area, the spring characteristic is progressively increasing, since fewer and fewer windings act resiliently. In the highest load range, in which the windings within the preload area completely spring-side rest against the external thread, the spring characteristic is linearly steep, since only the exposed windings act resilient.

Zur Erzielung der Druckvorspannung muss der an den Gewindeenden des Aussengewindes innenseitig begrenzte Vorspannbereich axial kürzer als der windungsgleiche aussenseitig begrenzte Teil der unbelasteten Federdrahtwendel sein. Letztere liegt somit aussenseitig an den innenseitigen Kontaktflächen der Gewindeenden an und spannt so die Federdrahtwendel druckseitig vor, bis ab dem mittleren Belastungsbereich diese sich selbst hinreichend verkürzt hat und somit von einer Kontaktfläche löst.To achieve the compressive prestressing, the pretensioning region, which is delimited on the inside of the threaded end of the external thread, must be axially shorter than the coiled outer part of the unloaded spring wire filament. The latter is thus on the outside of the inside contact surfaces of the threaded ends and thus biases the spring wire helix on the pressure side, until from the middle load range, this itself has shortened sufficiently and thus dissolves from a contact surface.

Vorteilhaft ist die Federdrahtwendel zylinderförmig sowie mit gleichmässiger Steigung der Windungen ausgebildet, wodurch Standardfedern verwendbar sind.Advantageously, the spring wire helix is cylindrical and formed with a uniform pitch of the turns, whereby standard springs can be used.

Vorteilhaft weist die federseitige Kontaktfläche des Aussengewindes eine nichtlineare Steigung auf, wodurch die Federkennlinie im hohen Belastungsbereich bezüglich des progressiven Verlaufs variierbar ist.Advantageously, the spring-side contact surface of the external thread on a non-linear slope, whereby the spring characteristic in the high load range with respect to the progressive course is variable.

Vorteilhaft ist das Aussengewinde ein Rechteckgewinde, wodurch die Kontaktflächen (im Längsschnitt) axial orientiert sind.Advantageously, the external thread is a rectangular thread, whereby the contact surfaces (in longitudinal section) are axially oriented.

Vorteilhaft ist die radiale Höhe des Aussengewindes zumindest so gross wie der Federdrahtdurchmesser, wodurch das Aussengewinde auch bei kombinierter Querbelastung axiale Kontaktflächen bildet.Advantageously, the radial height of the external thread is at least as large as the spring wire diameter, whereby the external thread forms axial contact surfaces even with combined transverse load.

Vorteilhaft ist der Kern des Gewindedoms ausgehend vom Wendelinnendurchmesser axial federseitig konvex verjüngt, wodurch bei einer Querbelastung sich einige Windungen radial an den Kern des Gewindedoms anlegen und somit zu einer Querprogression führen.Advantageously, the core of the thread dome, starting from the helical inner diameter, is axially convexly tapered on the spring side, whereby, in the event of a transverse load, some turns radially engage the core of the thread dome and thus lead to a transverse progression.

Die Erfindung wird bezüglich eines vorteilhaften Ausführungsbeispiels näher erläutert mit:

Fig. 1
einem Detail einer Handwerkzeugmaschine zur Vibrationsentkopplung
Fig. 2
einem unbelasteten Antivibrationselement im Längsschnitt gemäss Ebene II-II
Fig. 3
einer Federkennlinie bei Axialbelastung
Fig. 4
einer Federkennlinie bei Querbelastung
The invention will be explained in more detail with respect to an advantageous embodiment with:
Fig. 1
a detail of a hand tool for vibration decoupling
Fig. 2
an unloaded anti-vibration element in longitudinal section according to level II-II
Fig. 3
a spring characteristic under axial load
Fig. 4
a spring characteristic with lateral load

Nach Fig. 1 weist eine nur ausschnittsweise dargestellte Handwerkzeugmaschine 12 in Form eines Meisselhammers ein Antivibrationselement 1 auf, welches zwischen einer längs einer Vibrationsachse A vibrierenden Baugruppe 5 und einer vibrationsentkoppelten Handgriffbaugruppe 6 angeordnet ist. Das Antivibrationselement 1 weist eine längs der Vibrationsachse A orientierte Federdrahtwendel 7 mit mehreren Windungen 2 auf, welche an einem Wendelende auf einen Gewindedom 3 mit einem Aussengewinde 4 aufgewickelt sind. Die Antivibrationselement 1 ist zylinderförmig sowie mit gleichmässiger Steigung der Windungen 2 ausgebildet.To Fig. 1 has a hand tool 12 shown only partially in the form of a chisel hammer on an anti-vibration element 1, which between a vibrating along a vibration axis A assembly 5 and a vibration-decoupled Handle assembly 6 is arranged. The anti-vibration element 1 has a longitudinally oriented along the vibration axis A spring wire coil 7 with a plurality of turns 2, which are wound at a coil end on a threaded dome 3 with an external thread 4. The anti-vibration element 1 is cylindrical and formed with a uniform pitch of the windings 2.

Nach Fig. 2 liegen im dargestellten Belastungsfall des Antivibrationselements 1 ohne axiale Druckbelastung verschiedene Windungen 2 axial sowohl federseitig als auch domseitig in einem Vorspannbereich V am Aussengewinde 4 mit axial beidseitigen Kontaktflächen 14 an, dessen Zwischengangweite Z grösser als der Federdrahtdurchmesser D der Federdrahtwendel 7 ist. Dabei liegt die Federdrahtwendel 7 mit verschiedenen Windungen 7 an beiden Kontaktflächen 14 des Aussengewindes 4 an. Das als Rechteckgewinde ausgebildete Aussengewinde 4 weist bezüglich seiner federseitigen Kontaktfläche 14 eine gleichmässige Steigung auf (analog ist auch eine nichtlineare Steigung möglich, was nicht explizit dargestellt ist). Die radiale Höhe H des Aussengewindes 4 ist grösser als der Federdrahtdurchmesser D. Der koaxial innenliegende Kern des Gewindedoms 3 ist ausgehend vom Wendelinnendurchmesser S axial federseitig konvex verjüngt.To Fig. 2 lie in the illustrated load case of the anti-vibration element 1 without axial pressure load different turns 2 axially both spring-side and domed in a biasing V on the external thread 4 with axially two-sided contact surfaces 14, the intermediate Z is greater than the spring wire diameter D of the spring wire coil 7. In this case, the spring wire coil 7 is located with different turns 7 on both contact surfaces 14 of the external thread 4. The male thread 4 designed as a rectangular thread has a uniform pitch with respect to its spring-side contact surface 14 (analogously, a non-linear gradient is also possible, which is not explicitly shown). The radial height H of the external thread 4 is greater than the spring wire diameter D. The coaxially inner core of the threaded mandrel 3 is starting from the helical inner diameter S axially convexly tapered on the spring side.

Nach Fig. 3 weist die Federkennlinie 13 (Axialdehnung X, Axialkraft Fa) beidseitig eines linear flacheren Mittenbereiches 9, bei welchem alle Windungen 2 (Fig. 2) frei liegen, jeweils einen Randbereich 8, 10 mit steilerer Kennlinie auf, bei welchem die Windungen 2 (Fig. 2) nur teilweise am Aussengewinde 4 (Fig. 2) axial anliegen. Im unbelasteten Randbereich 8 ist der im Vorspannbereich V (Fig. 2) vorgespannte Teil der Windungen 2 (Fig. 2) unwirksam, so dass sich bis zur Überwindung der Vorspannung eine lineare, steilere Kennlinie ergibt. Der Übergang zum Mittenbereich 9 bildet einen Knick in der Kennlinie aus. Im hochbelasteten Randbereich 10 lagert sich stetig ein Teil der Windungen 2 (Fig. 2) axial an das Aussengewinde 4 (Fig. 2) an, so dass sich eine progressiv ansteigende Federkennlinie ergibt. Im höchsten Belastungsbereich 11, bei dem die Windungen 2 (Fig. 2) im Vorspannbereich V (Fig. 2) vollständig an der federseitigen Kontaktfläche 14 des Aussengewindes 4 (Fig. 2) anliegen, ist die Federkennlinie linear steil, da nur noch der freiliegende Teil der Windungen 2 (Fig. 2) federnd wirkt.To Fig. 3 has the spring characteristic curve 13 (axial expansion X, axial force Fa) on both sides of a linearly flat middle region 9, in which all windings 2 (FIG. Fig. 2 ) are free, each having an edge region 8, 10 with a steeper characteristic, in which the turns 2 ( Fig. 2 ) only partially on the external thread 4 ( Fig. 2 ) abut axially. In the unloaded edge region 8 is the in the bias region V ( Fig. 2 ) prestressed part of the turns 2 ( Fig. 2 ) ineffective, so that results in a linear, steeper characteristic curve to overcome the bias. The transition to the central region 9 forms a kink in the characteristic curve. In the heavily loaded edge region 10, a part of the turns 2 is continuously stored ( Fig. 2 ) axially to the external thread 4 ( Fig. 2 ), so that there is a progressively increasing spring characteristic. In the highest load range 11, in which the turns 2 ( Fig. 2 ) in the preamble area V ( Fig. 2 ) completely on the spring-side contact surface 14 of the external thread 4 ( Fig. 2 ) abut, the spring characteristic is linearly steep, since only the exposed part of the turns 2 ( Fig. 2 ) acts resiliently.

Nach Fig. 4 weist die Federkennlinie 13' (Querdehnung Y, Querkraft Fq) mit wachsender Querbelastung eine Querprogression auf, indem sich einige Windungen 2 (Fig. 2) unten radial an den konvexen Kern des Gewindedoms 3 (Fig. 2) anlegen (nicht dargestellt).To Fig. 4 has the spring characteristic 13 '(transverse strain Y, transverse force Fq) with increasing lateral load on a transverse progression by some turns 2 ( Fig. 2 ) down radially to the convex core of the threaded mandrel 3 ( Fig. 2 ) (not shown).

Claims (6)

Handwerkzeugmaschine mit einer längs einer Vibrationsachse (A) vibrierenden Baugruppe (5) und einer Handgriffbaugruppe (6), die über ein Antivibrationselement (1) schwingungsentkoppelt ist, welches eine längs der Vibrationsachse (A) orientierte Federdrahtwendel (7) mit mehreren Windungen (2) aufweist, die teilweise auf einen Gewindedom (3) mit einem sich längs ersteckenden Aussengewinde (4) aufgeschraubt ist, dadurch gekennzeichnet, dass am Antivibrationselement (1) die sich über einen Vorspannbereich (V) längs ersteckenden Windungen (2) axial druckvorgespannt auf das Aussengewinde (4) aufgeschraubt sind, wobei das Aussengewinde (4) eine Zwischengangweite (Z) aufweist, die grösser als der Federdrahtdurchmesser (D) der Federdrahtwendel (7) ist.Hand tool with a vibration axis (A) vibrating assembly (5) and a handle assembly (6) via an anti-vibration element (1) is vibration-decoupled, which is along the vibration axis (A) oriented spring wire coil (7) with several turns (2) which is partially screwed onto a threaded dome (3) with a male thread (4) which extends longitudinally, characterized in that the antivibration element (1) has the windings (2) extending longitudinally over a preload region (V) axially biased onto the external thread (4) are screwed, wherein the external thread (4) has an intermediate width (Z), which is greater than the spring wire diameter (D) of the spring wire coil (7). Handwerkzeugmaschine nach Anspruch 1, dadurch gekennzeichnet, dass die Federdrahtwendel (7) zylinderförmig sowie mit gleichmässiger Steigung der Windungen (2) ausgebildet ist.Powered hand tool according to claim 1, characterized in that the spring wire coil (7) is cylindrical and formed with a uniform pitch of the turns (2). Handwerkzeugmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die federseitige Kontaktfläche (14) des Aussengewindes (4) eine nichtlineare Steigung aufweist.Powered hand tool according to claim 1 or 2, characterized in that the spring-side contact surface (14) of the external thread (4) has a non-linear slope. Handwerkzeugmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass das Aussengewinde (4) ein Rechteckgewinde ist.Hand tool according to one of claims 1 to 3, characterized in that the external thread (4) is a rectangular thread. Handwerkzeugmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die radiale Höhe (H) des Aussengewindes (4) zumindest so gross wie der Federdrahtdurchmesser (D) ist.Hand tool according to one of claims 1 to 4, characterized in that the radial height (H) of the external thread (4) is at least as large as the spring wire diameter (D). Handwerkzeugmaschine nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Kern des Gewindedoms (3) ausgehend von einem Wendelinnendurchmesser (S) axial federseitig konvex verjüngt ist.Hand tool according to one of claims 1 to 5, characterized in that the core of the threaded mandrel (3), starting from a helical inner diameter (S) is axially convexly tapered on the spring side.
EP08103704A 2007-05-11 2008-04-24 Vibrating hand machine tool with anti-vibration element Active EP1990147B1 (en)

Applications Claiming Priority (1)

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DE102007000270A DE102007000270A1 (en) 2007-05-11 2007-05-11 Vibrating hand tool with anti-vibration element

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EP1990147A2 true EP1990147A2 (en) 2008-11-12
EP1990147A3 EP1990147A3 (en) 2009-07-29
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EP (1) EP1990147B1 (en)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007048887B4 (en) * 2007-10-11 2017-10-26 Andreas Stihl Ag & Co. Kg Hand-held implement
CN106523566B (en) * 2016-10-20 2018-08-03 许继电气股份有限公司 Primary and secondary spring assembly and its spring base
EP3501750A1 (en) 2017-12-19 2019-06-26 Hilti Aktiengesellschaft Vibration-dampened hand-held machine tool
EP3599059B1 (en) * 2018-07-25 2022-05-04 Andreas Stihl AG & Co. KG Hand-held working device and method for mounting an antivibration element of a hand-held working device
TWI807998B (en) * 2022-09-19 2023-07-01 施瑞源 force limiting shock absorber

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WO1994016864A1 (en) 1993-01-27 1994-08-04 Lord Corporation Vibration isolator for hand-held vibrating devices
DE102004031866A1 (en) 2004-07-01 2006-01-19 Andreas Stihl Ag & Co. Kg Hand-held implement

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US1404464A (en) * 1920-12-13 1922-01-24 Adolph F Meyer Spring
US3141660A (en) * 1961-03-08 1964-07-21 Woodhead Monroe Ltd Coil springs
US4712778A (en) * 1981-12-21 1987-12-15 North American Philips Corporation Helical spring holder assembly
DE10334906B4 (en) * 2002-07-30 2018-11-15 Andreas Stihl Ag & Co. Kg Anti-vibration element

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WO1994016864A1 (en) 1993-01-27 1994-08-04 Lord Corporation Vibration isolator for hand-held vibrating devices
DE102004031866A1 (en) 2004-07-01 2006-01-19 Andreas Stihl Ag & Co. Kg Hand-held implement

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US8511658B2 (en) 2013-08-20
CN101301747A (en) 2008-11-12
US20080277846A1 (en) 2008-11-13
EP1990147B1 (en) 2010-11-03
DE102007000270A1 (en) 2008-11-20
EP1990147A3 (en) 2009-07-29

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