EP3065914A1 - Portable power tool - Google Patents

Portable power tool

Info

Publication number
EP3065914A1
EP3065914A1 EP14790626.7A EP14790626A EP3065914A1 EP 3065914 A1 EP3065914 A1 EP 3065914A1 EP 14790626 A EP14790626 A EP 14790626A EP 3065914 A1 EP3065914 A1 EP 3065914A1
Authority
EP
European Patent Office
Prior art keywords
catcher
impact
working axis
hand tool
tolerance
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14790626.7A
Other languages
German (de)
French (fr)
Other versions
EP3065914B1 (en
Inventor
Theo Kiesel
Helene KAPS
Matthias Keith
Olaf Koch
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
Priority to EP14790626.7A priority Critical patent/EP3065914B1/en
Publication of EP3065914A1 publication Critical patent/EP3065914A1/en
Application granted granted Critical
Publication of EP3065914B1 publication Critical patent/EP3065914B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • B25D17/11—Arrangements of noise-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
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • 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
    • B25D2250/191—Ram catchers for stopping the ram when entering idling mode
    • 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
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other
    • 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
    • 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
    • B25D2250/391—Use of weights; Weight properties of the tool

Definitions

  • the present invention relates to a hand tool with a hammer mechanism, in particular for use with chiseling tools.
  • a striking mechanism has several moving components that repeatedly move along a working axis and hit each other. This leads to a considerable noise. Precise guidance of the striking components parallel to the working axis prevents skewing of the striking components and rattling due to partial radial movement.
  • the hand tool of the invention has a tool holder, in which a tool on a working axis in a direction of impact is movable.
  • An impact mechanism has a beater coupled via a pneumatic chamber to a pathogen that is moved periodically along the working axis and an intermediate beater arranged in the direction of impact after the beater.
  • the intermediate beater is guided in a sliding bearing, with a tolerance coaxial to the working axis
  • the intermediate beater has an annular bead.
  • a hollow cylindrical catcher is arranged in the direction of impact in front of the bead. The catcher is movably guided on a sliding surface with a radial clearance along the working axis.
  • the radial clearance is at least three times as large as a tolerance of the guide of the intermediate racket in the sliding bearing.
  • the beating components are strictly managed as usual. In contrast, it may prove advantageous not to stringently guide a catcher for the intermediate bat. Although this can now move radially and thereby rattle, the overall noise is lower.
  • the impact of the intermediate impactor stimulates a radial vibration in the catcher, which also depends on the guidance.
  • the strict leadership proves to be unfavorable, since the resulting higher frequencies resonantly excite the housing.
  • One embodiment provides that the mass of the catcher is between 20% and 40% of the mass of the intermediate beater.
  • the catcher may be supported against the impact direction on a damping element. In particular, the catcher may be inserted between the damping element and a further damping element arranged in the direction of impact under prestressing.
  • An embodiment provides that a spring element spans a radial outer surface of the catcher.
  • the spring element centered the catcher to the working axis after an impact of the intermediate beater has occurred.
  • Fig. 1 a hammer drill
  • Fig. 2 shows a partial section of the hammer drill Same or functionally identical elements are indicated by the same reference numerals in the figures, unless stated otherwise.
  • FIG. 1 schematically shows a hammer drill 1 as an example of a chiseling hand tool.
  • the hammer 1 has a tool holder 2 in which a shank end 3 of a tool, eg a chisel 4, can be inserted.
  • a primary drive of the hammer drill 1 is a motor 5, which drives a striking mechanism 6 and an output shaft 7.
  • a battery pack 8 or a power line supplies the motor 5 with power.
  • a user can lead the hammer drill 1 by means of a handle 9 and take the hammer drill 1 by means of a system switch 10 in operation.
  • the hammer drill 1 rotates the drill 4 continuously about a working axis 11 and can beat the drill 4 in the direction of impact 12 along the working axis 11 in a substrate.
  • the percussion 6 is a pneumatic percussion 6.
  • An exciter piston 13 and a racket 14 are movably guided in a guide tube 15 in the striking mechanism 6 along the working axis 11.
  • the exciter piston 13 is connected to the motor 5 via an eccentric 16 coupled and forced to a periodic, linear motion.
  • a connecting rod connects the eccentric 16 with the excitation piston 13.
  • An air spring formed by a pneumatic chamber 17 between the excitation piston 13 and the racket 14 couples a movement of the racket 14 to the movement of the exciter piston 13.
  • the racket 14 indirectly transmits a portion of its momentum to the chisel 4 via a substantially stationary intermediate racket 18.
  • the percussion unit 6, and preferably the further drive components, are disposed within a machine housing 19.
  • the intermediate beater 18 has a substantially cylindrical base body 20.
  • the intermediate beater 18 is guided in a sliding bearing 21, 22 coaxial with the working axis 11.
  • the exemplary two-part sliding bearing 21, 22 encloses with a front sleeve 21 a machine-side end of the base body 20 and a rear sleeve 22, the tool-side end of the base body 20.
  • the diameter of the base body 20 deviates by a distance 23 of less than 50 ⁇ of the inner diameter the sleeves 21, 22 from. This corresponds to the typical for plain bearings 21, 22 tolerance H7 for the sleeves 21, 22 and g7 for the intermediate beater 18, each according to the ISO standard.
  • the tight tolerance ensures coaxial guidance, even with forces occurring in the range of 10 kN during impact.
  • the intermediate beater 18 is movable between a working position (upper half of FIG. 2) and an advanced position in the direction of impact 12 (lower half of FIG. 2).
  • the intermediate beater 18 has a relative to the base 20 radially projecting bead 24, which is preferably provided in a central portion of the intermediate beater 18.
  • the bead 24 bears against the impact direction 12 on a catcher 25 when the intermediate beater 18 is in the working position.
  • the catcher 25 has a hollow cylindrical shape with a radial outer surface 26.
  • the exemplary catcher 25 has a radially inwardly projecting collar 27, against which the bead 24 bears against the impact direction 12.
  • a length 28 of the catcher 25, in particular the radial outer surface 26 is in the range of 10% and 25% of the length 29 of the intermediate beater 18.
  • the movement of the intermediate beater 18 in the direction of impact 12 is stopped by a damped stop 30, if at this the bead 24th comes in the direction of impact 12 to concern.
  • the free path of the intermediate beater 18 from the working position to the stop 30 is small hammer drills in the range of 1 cm and 3 cm and large chisel in the range of 3 cm to 5 cm.
  • the catcher 25 is supported against the direction of impact 12 by a damping element 31 on the machine housing 19.
  • the catcher 25 shifts slightly over the Housing, when the intermediate beater 18 bounces against the catcher 25.
  • the catcher 25 also has a relative to the intermediate beater 18 is not negligible mass to reduce the bounce.
  • the mass of the catcher 25 is preferably in the range of 20% to 40% of the mass of the intermediate beater 18.
  • the large mass of the catcher 25 results from its axial dimension 28.
  • the catcher 25 is preferably between the damping element 31 and another in the direction of impact 12th arranged damping element 32 clamped.
  • the two damping elements 31, 32 are biased along the working axis 11.
  • the catcher 25 is held along the working axis 11 by the two damping or spring elements 31, 32 in a rest position.
  • the catcher 25 is coaxial with the working axis 11, i. coaxial with the intermediate beater 18, guided.
  • the axial guidance of the catcher 25 is effected by its cylindrical outer surface 26.
  • the axial dimension of the outer surface 26 is approximately equal to the length of the catcher 25.
  • the counterpart of the guide can be done for example by a cylindrical radial inner surface 33 of the machine housing 19.
  • the guide is provided with a clear radial play 34.
  • the clearance 34 should be at least 0.15 mm, ie more than three times the guide tolerance 23 of the sliding bearing 21, 22 for the intermediate beater 18.
  • the clearance 34 is in the radial direction between the metallic outer surface 26 of the catcher 25 and the leading metallic inner surface 33rd , here the machine housing 19 to determine.
  • the high tolerance proves to be favorable in order to reduce the noise of the collision of the impact pad 18 on the catcher 25.
  • the catcher 25 may be provided with radial spring elements 35 made of an elastomer, which surround the outer surface 26 and bear against the inner surface 33 of the guide 36.
  • the front sliding bearing 21 may have an inserted sealing ring 37, which the tolerance 23 is arranged balancing on the inside of the sleeve 21.
  • the sealing ring 37 strips off fine dust from the intermediate beater 18, and prevents penetration of the dust in the impact mechanism. 6
  • the guide tube 15 bz is a separate component to the machine housing 19 bz, which is arranged completely within the machine housing 19.
  • the guide tube 15 may also be partially exposed, ergo form part of the outer machine housing 19.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

A portable power tool has a tool holder 2 into which a tool 4 is insertable so as to be movable in a striking direction 12 on a working axis 11. A percussion mechanism 6 has a striker 14 coupled via a pneumatic chamber 17 to an exciter 13 that is movable periodically along the working axis 11, and an intermediate striker 18 arranged downstream of the striker 14 in the striking direction 12. The intermediate striker 18 is guided with a tolerance 23 in a plain bearing 21, 22 coaxial with the working axis 11. The intermediate striker 18 has an annular bead 24. A hollow-cylindrical backstop 25 is arranged upstream of the bead 24 in the striking direction 12. The backstop 25 is guided in a movable manner with radial play 34 along the working axis 11 on a sliding surface 33. The radial play 34 is at least three times as large as a tolerance of the guidance of the intermediate striker 18 in the plain bearing 21, 22.

Description

Handwerkzeugmaschine  Hand tool
GEBIET DER ERFINDUNG FIELD OF THE INVENTION
Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine mit einem Schlagwerk, insbesondere zu Verwendung mit meißelnden Werkzeugen. The present invention relates to a hand tool with a hammer mechanism, in particular for use with chiseling tools.
Ein Schlagwerk hat mehrere bewegte Komponenten, die sich wiederholt längs einer Arbeitsachse bewegen und aufeinander schlagen. Dies führt zu einer erheblichen Geräuschentwicklung. Eine präzise Führung der schlagenden Komponenten parallel zu der Arbeitsachse verhindern einen Schräglauf der schlagenden Komponenten und ein Klappern aufgrund einer teilweise radialen Bewegung. OFFENBARUNG DER ERFINDUNG A striking mechanism has several moving components that repeatedly move along a working axis and hit each other. This leads to a considerable noise. Precise guidance of the striking components parallel to the working axis prevents skewing of the striking components and rattling due to partial radial movement. DISCLOSURE OF THE INVENTION
Die erfindungsgemäße Handwerkzeugmaschine hat einen Werkzeughalter, in welchen ein Werkzeug auf einer Arbeitsachse in einer Schlagrichtung beweglich einsetzbar ist. Ein Schlagwerk hat einen über eine pneumatische Kammer an einen längs der Arbeitsachse periodisch bewegten Erreger gekoppelten Schläger und einen in Schlagrichtung nach dem Schläger angeordneten Zwischenschläger. Der Zwischenschläger ist in einem Gleitlager, mit einer Toleranz koaxial zu der Arbeitsachse geführt Der Zwischenschläger hat einen ringförmigen Wulst. Ein hohlzylindrischer Fänger ist in Schlagrichtung vor dem Wulst angeordnet. Der Fänger ist an einer Gleitfläche mit einem radialen Spiel längs der Arbeitsachse beweglich geführt. Das radiale Spiel ist wenigstens dreifach so groß wie eine Toleranz der Führung des Zwischenschlägers in dem Gleitlager,. Die schlagenden Komponenten werden wie üblich streng geführt. Im Gegensatz dazu kann es sich als vorteilhaft erweisen, einen Fänger für den Zwischenschläger nicht streng zu führen. Obwohl dieser sich nun radial bewegen und dadurch klappern kann, ist die gesamte Geräuschentwicklung geringer. Der Aufprall des Zwischenschlägers regt eine radiale Schwingung in dem Fänger an, welche auch von der Führung abhängt. Die strenge Führung erweist sich hierbei als ungünstiger, da die sich ergebenden höheren Frequenzen das Gehäuse resonant anregen. Eine Ausgestaltung sieht vor, dass die Masse des Fängers zwischen 20 % und 40 % der Masse des Zwischenschlägers beträgt. Der Fänger kann entgegen der Schlagrichtung an einem Dämpfelement abgestützt sein. Insbesondere kann der Fänger zwischen dem Dämpfelement und einem in Schlagrichtung angeordnetem weiteren Dämpfelement unter Vorspannung eingesetzt sein. The hand tool of the invention has a tool holder, in which a tool on a working axis in a direction of impact is movable. An impact mechanism has a beater coupled via a pneumatic chamber to a pathogen that is moved periodically along the working axis and an intermediate beater arranged in the direction of impact after the beater. The intermediate beater is guided in a sliding bearing, with a tolerance coaxial to the working axis The intermediate beater has an annular bead. A hollow cylindrical catcher is arranged in the direction of impact in front of the bead. The catcher is movably guided on a sliding surface with a radial clearance along the working axis. The radial clearance is at least three times as large as a tolerance of the guide of the intermediate racket in the sliding bearing. The beating components are strictly managed as usual. In contrast, it may prove advantageous not to stringently guide a catcher for the intermediate bat. Although this can now move radially and thereby rattle, the overall noise is lower. The impact of the intermediate impactor stimulates a radial vibration in the catcher, which also depends on the guidance. The strict leadership proves to be unfavorable, since the resulting higher frequencies resonantly excite the housing. One embodiment provides that the mass of the catcher is between 20% and 40% of the mass of the intermediate beater. The catcher may be supported against the impact direction on a damping element. In particular, the catcher may be inserted between the damping element and a further damping element arranged in the direction of impact under prestressing.
Eine Ausgestaltung sieht vor, dass ein Federelement eine radiale Außenfläche des Fängers umspannt. Das Federelement zentriert den Fänger zu der Arbeitsachse nachdem ein Aufprall des Zwischenschlägers erfolgt ist. An embodiment provides that a spring element spans a radial outer surface of the catcher. The spring element centered the catcher to the working axis after an impact of the intermediate beater has occurred.
KURZE BESCHREIBUNG DER FIGUREN BRIEF DESCRIPTION OF THE FIGURES
Die nachfolgende Beschreibung erläutert die Erfindung anhand von exemplarischen Ausführungsformen und Figuren. In den Figuren zeigen: The following description explains the invention with reference to exemplary embodiments and figures. In the figures show:
Fig. 1 einen Bohrhammer Fig. 1 a hammer drill
Fig. 2 einen Teilausschnitt aus dem Bohrhammer Gleiche oder funktionsgleiche Elemente werden durch gleiche Bezugszeichen in den Figuren indiziert, soweit nicht anders angegeben. Fig. 2 shows a partial section of the hammer drill Same or functionally identical elements are indicated by the same reference numerals in the figures, unless stated otherwise.
AUSFÜHRUNGSFORMEN DER ERFINDUNG Fig. 1 zeigt als Beispiel einer meißelnden Handwerkzeugmaschine schematisch einen Bohrhammer 1. Der Bohrhammer 1 hat eine Werkzeughalter 2, in welchen ein Schaftende 3 eines Werkzeug, z.B. eines Meißels 4, eingesetzt werden kann. Einen primären Antrieb des Bohrhammers 1 bildet ein Motor 5, welcher ein Schlagwerk 6 und eine Abtriebswelle 7 antreibt. Ein Batteriepaket 8 oder eine Netzleitung versorgt den Motor 5 mit Strom. Ein Anwender kann den Bohrhammer 1 mittels eines Handgriffs 9 führen und mittels eines Systemschalters 10 den Bohrhammer 1 in Betrieb nehmen. Im Betrieb dreht der Bohrhammer 1 den Bohrer 4 kontinuierlich um eine Arbeitsachse 11 und kann dabei den Bohrer 4 in Schlagrichtung 12 längs der Arbeitsachse 11 in einen Untergrund schlagen. Das Schlagwerk 6 ist ein pneumatisches Schlagwerk 6. Ein Erregerkolben 13 und ein Schläger 14 sind in einem Führungsrohr 15 in dem Schlagwerk 6 längs der Arbeitsachse 11 beweglich geführt. Der Erregerkolben 13 ist über einen Exzenter 16 an den Motor 5 angekoppelt und zu einer periodischen, linearen Bewegung gezwungen. Ein Pleuel verbindet den Exzenter 16 mit dem Erregerkolben 13. Eine Luftfeder gebildet durch eine pneumatische Kammer 17 zwischen dem Erregerkolben 13 und dem Schläger 14 koppelt eine Bewegung des Schlägers 14 an die Bewegung des Erregerkolbens 13 an. Der Schläger 14 überträgt mittelbar über einen im Wesentlichen ruhenden Zwischenschläger 18 einen Teil seines Impuls auf den Meißel 4. Das Schlagwerk 6 und vorzugsweise die weiteren Antriebskomponenten sind innerhalb eines Maschinengehäuses 19 angeordnet. EMBODIMENTS OF THE INVENTION FIG. 1 schematically shows a hammer drill 1 as an example of a chiseling hand tool. The hammer 1 has a tool holder 2 in which a shank end 3 of a tool, eg a chisel 4, can be inserted. A primary drive of the hammer drill 1 is a motor 5, which drives a striking mechanism 6 and an output shaft 7. A battery pack 8 or a power line supplies the motor 5 with power. A user can lead the hammer drill 1 by means of a handle 9 and take the hammer drill 1 by means of a system switch 10 in operation. In operation, the hammer drill 1 rotates the drill 4 continuously about a working axis 11 and can beat the drill 4 in the direction of impact 12 along the working axis 11 in a substrate. The percussion 6 is a pneumatic percussion 6. An exciter piston 13 and a racket 14 are movably guided in a guide tube 15 in the striking mechanism 6 along the working axis 11. The exciter piston 13 is connected to the motor 5 via an eccentric 16 coupled and forced to a periodic, linear motion. A connecting rod connects the eccentric 16 with the excitation piston 13. An air spring formed by a pneumatic chamber 17 between the excitation piston 13 and the racket 14 couples a movement of the racket 14 to the movement of the exciter piston 13. The racket 14 indirectly transmits a portion of its momentum to the chisel 4 via a substantially stationary intermediate racket 18. The percussion unit 6, and preferably the further drive components, are disposed within a machine housing 19.
Der Zwischenschläger 18 hat einen im wesentlichen zylindrischen Grundkörper 20. Der Zwischenschläger 18 ist in einem Gleitlager 21 , 22 koaxial zu der Arbeitsachse 11 geführt. Das beispielhafte zweiteiligen Gleitlager 21 , 22 umschließt mit einer vorderen Hülse 21 ein maschinenseitiges Ende des Grundkörpers 20 und mit einer hinteren Hülse 22 das werkzeugseitige Ende des Grundkörpers 20. Der Durchmesser des Grundkörpers 20 weicht um eine Distanz 23 von weniger als 50 μηι von dem Innendurchmesser der Hülsen 21 , 22 ab. Dies entspricht der für Gleitlager 21 , 22 typischen Toleranz H7 für die Hülsen 21 , 22 und g7 für den Zwischenschläger 18, jeweils nach der ISO-Norm. Die enge Toleranz gewährleistet eine koaxiale Führung, auch bei während des Schlages auftretenden Kräften im Bereich von 10 kN. Der Zwischenschläger 18 ist zwischen einer Arbeitsstellung (obere Bildhälfte Fig. 2) und einer in Schlagrichtung 12 vorgerückten Stellung (untere Bildhälfte Fig. 2) beweglich. Der Zwischenschläger 18 hat einen gegenüber dem Grundkörper 20 radial vorstehenden Wulst 24, welcher vorzugsweise in einem mittleren Abschnitt des Zwischenschlägers 18 vorgesehen ist. Der Wulst 24 liegt entgegen der Schlagrichtung 12 an einem Fänger 25 an, wenn der Zwischenschläger 18 in Arbeitsstellung ist. Der Fänger 25 hat eine hohlzylindrische Form mit einer radialen Außenfläche 26. Der beispielhafte Fänger 25 hat einen radial nach Innen vorstehenden Kragen 27, an welchem der Wulst 24 entgegen der Schlagrichtung 12 anliegt. Eine Länge 28 des Fängers 25, insbesondere der radialen Außenfläche 26 liegt im Bereich von 10 % und 25 % der Länge 29 des Zwischenschlägers 18. Die Bewegung des Zwischenschlägers 18 in Schlagrichtung 12 wird durch einen gedämpften Anschlag 30 gestoppt, wenn an diesem der Wulst 24 in Schlagrichtung 12 zum Anliegen kommt. Der freie Weg des Zwischenschlägers 18 von der Arbeitsstellung bis zu dem Anschlag 30 liegt bei kleinen Bohrhämmern im Bereich von 1 cm und 3 cm und bei großen Meißelhammern im Bereich von 3 cm bis 5 cm. The intermediate beater 18 has a substantially cylindrical base body 20. The intermediate beater 18 is guided in a sliding bearing 21, 22 coaxial with the working axis 11. The exemplary two-part sliding bearing 21, 22 encloses with a front sleeve 21 a machine-side end of the base body 20 and a rear sleeve 22, the tool-side end of the base body 20. The diameter of the base body 20 deviates by a distance 23 of less than 50 μηι of the inner diameter the sleeves 21, 22 from. This corresponds to the typical for plain bearings 21, 22 tolerance H7 for the sleeves 21, 22 and g7 for the intermediate beater 18, each according to the ISO standard. The tight tolerance ensures coaxial guidance, even with forces occurring in the range of 10 kN during impact. The intermediate beater 18 is movable between a working position (upper half of FIG. 2) and an advanced position in the direction of impact 12 (lower half of FIG. 2). The intermediate beater 18 has a relative to the base 20 radially projecting bead 24, which is preferably provided in a central portion of the intermediate beater 18. The bead 24 bears against the impact direction 12 on a catcher 25 when the intermediate beater 18 is in the working position. The catcher 25 has a hollow cylindrical shape with a radial outer surface 26. The exemplary catcher 25 has a radially inwardly projecting collar 27, against which the bead 24 bears against the impact direction 12. A length 28 of the catcher 25, in particular the radial outer surface 26 is in the range of 10% and 25% of the length 29 of the intermediate beater 18. The movement of the intermediate beater 18 in the direction of impact 12 is stopped by a damped stop 30, if at this the bead 24th comes in the direction of impact 12 to concern. The free path of the intermediate beater 18 from the working position to the stop 30 is small hammer drills in the range of 1 cm and 3 cm and large chisel in the range of 3 cm to 5 cm.
Der Fänger 25 ist entgegen der Schlagrichtung 12 durch ein Dämpfelement 31 an dem Maschinengehäuse 19 abgestützt. Der Fänger 25 verschiebt sich etwas gegenüber dem Gehäuse, wenn der Zwischenschläger 18 gegen den Fänger 25 prallt. Der Fänger 25 hat zudem eine gegenüber dem Zwischenschläger 18 nicht vernachlässige Masse, um den Prellschlag zu mindern. Die Masse des Fängers 25 liegt vorzugsweise im Bereich von 20 % bis 40 % der Masse des Zwischenschlägers 18. Die große Masse des Fängers 25 ergibt sich durch dessen axiale Abmessung 28. Der Fänger 25 ist vorzugsweise zwischen dem Dämpfelement 31 und einem weiteren in Schlagrichtung 12 angeordneten Dämpfelement 32 eingespannt. Die beiden Dämpfelemente 31 , 32 sind längs der Arbeitsachse 11 vorgespannt. Der Fänger 25 wird längs der Arbeitsachse 11 durch die beiden Dämpf- oder Federelemente 31 , 32 in einer Ruhestellung gehalten. The catcher 25 is supported against the direction of impact 12 by a damping element 31 on the machine housing 19. The catcher 25 shifts slightly over the Housing, when the intermediate beater 18 bounces against the catcher 25. The catcher 25 also has a relative to the intermediate beater 18 is not negligible mass to reduce the bounce. The mass of the catcher 25 is preferably in the range of 20% to 40% of the mass of the intermediate beater 18. The large mass of the catcher 25 results from its axial dimension 28. The catcher 25 is preferably between the damping element 31 and another in the direction of impact 12th arranged damping element 32 clamped. The two damping elements 31, 32 are biased along the working axis 11. The catcher 25 is held along the working axis 11 by the two damping or spring elements 31, 32 in a rest position.
Der Fänger 25 ist koaxial zu der Arbeitsachse 11 , d.h. koaxial zu dem Zwischenschläger 18, geführt. Die axiale Führung des Fängers 25 erfolgt durch dessen zylindrische Außenfläche 26. Die axiale Abmessung der Außenfläche 26 ist näherungsweise gleich der Länge des Fängers 25. Das Gegenstück der Führung kann beispielsweise durch eine zylindrische radiale Innenfläche 33 des Maschinengehäuses 19 erfolgen. Die Führung ist mit einem deutlichen radialen Spiel 34 versehen. Das Spiel 34 sollte wenigstens 0, 15 mm betragen, also mehr als dem Dreifachen der Führungstoleranz 23 des Gleitlagers 21 , 22 für den Zwischenschläger 18. Das Spiel 34 ist in radialer Richtung zwischen der metallischen Außenfläche 26 des Fängers 25 und der führenden metallischen Innenfläche 33, hier des Maschinengehäuses 19, zu bestimmen. Die hohe Toleranz erweist sich als günstig, um eine Geräuschentwicklung des beim Aufprall des Zwischenschlägers 18 auf den Fänger 25 zu verringern. The catcher 25 is coaxial with the working axis 11, i. coaxial with the intermediate beater 18, guided. The axial guidance of the catcher 25 is effected by its cylindrical outer surface 26. The axial dimension of the outer surface 26 is approximately equal to the length of the catcher 25. The counterpart of the guide can be done for example by a cylindrical radial inner surface 33 of the machine housing 19. The guide is provided with a clear radial play 34. The clearance 34 should be at least 0.15 mm, ie more than three times the guide tolerance 23 of the sliding bearing 21, 22 for the intermediate beater 18. The clearance 34 is in the radial direction between the metallic outer surface 26 of the catcher 25 and the leading metallic inner surface 33rd , here the machine housing 19 to determine. The high tolerance proves to be favorable in order to reduce the noise of the collision of the impact pad 18 on the catcher 25.
Der Fänger 25 kann mit radialen Federelementen 35 aus einem Elastomer versehen sein, welche dessen Außenfläche 26 umspannen und an der Innenfläche 33 der Führung 36 anliegen. The catcher 25 may be provided with radial spring elements 35 made of an elastomer, which surround the outer surface 26 and bear against the inner surface 33 of the guide 36.
Das vordere Gleitlager 21 kann einen eingesetzten Dichtring 37 aufweisen, welcher die Toleranz 23 ausgleichend an der Innenseite der Hülse 21 angeordnet ist. Der Dichtring 37 streift feinen Staub von dem Zwischenschläger 18 ab, und verhindert ein Eindringen des Staubes in das Schlagwerk 6. The front sliding bearing 21 may have an inserted sealing ring 37, which the tolerance 23 is arranged balancing on the inside of the sleeve 21. The sealing ring 37 strips off fine dust from the intermediate beater 18, and prevents penetration of the dust in the impact mechanism. 6
Bei der dargestellten Ausführungsform ist das Führungsrohr 15bz ein zu dem Maschinengehäuse 19bz separates Bauteil, welches vollständig innerhalb des Maschinengehäuses 19 angeordnet ist. Das Führungsrohr 15 kann auch abschnittsweise freiliegend sein, ergo einen Teil des äußeren Maschinengehäuses 19 bilden. In the illustrated embodiment, the guide tube 15 bz is a separate component to the machine housing 19 bz, which is arranged completely within the machine housing 19. The guide tube 15 may also be partially exposed, ergo form part of the outer machine housing 19.

Claims

PATENTANSPRÜCHE
1. Handwerkzeugmaschine mit 1. Hand tool with
einem Werkzeughalter (2), in welchen ein Werkzeug (4) auf einer Arbeitsachse (11) in einer Schlagrichtung (12) beweglich einsetzbar ist,  a tool holder (2) in which a tool (4) is movably insertable on a working axis (11) in a direction of impact (12),
einem Schlagwerk (6), das einen über eine pneumatische Kammer (17) an einen längs der Arbeitsachse (1 1) periodisch bewegten Erreger (13) gekoppelten Schläger (14) und einen in Schlagrichtung (12) nach dem Schläger (14) angeordneten Zwischenschläger (18) aufweist,  a percussion mechanism (6), which has a via a pneumatic chamber (17) to a along the working axis (1 1) periodically moved exciter (13) coupled racket (14) and in the direction of impact (12) after the racket (14) arranged intermediate racket (18),
wobei der Zwischenschläger (18) in einem Gleitlager (21 , 22) mit einer Toleranz (23) koaxial zu der Arbeitsachse (1 1) geführt ist, und wobei der Zwischenschläger (18) einen ringförmigen Wulst (24) aufweist,  wherein the intermediate beater (18) in a sliding bearing (21, 22) with a tolerance (23) is guided coaxially to the working axis (1 1), and wherein the intermediate beater (18) has an annular bead (24),
einem hohlzylindrischen Fänger (25), der in Schlagrichtung (12) vor dem Wulst (24) angeordnet ist,  a hollow cylindrical catcher (25), which is arranged in the direction of impact (12) in front of the bead (24),
einer Gleitfläche (33), in welcher der Fänger (25) mit einem radialen Spiel (34) längs der Arbeitsachse (1 1) beweglich geführt ist,  a sliding surface (33) in which the catcher (25) with a radial clearance (34) along the working axis (1 1) is movably guided,
wobei das radiale Spiel (34) wenigstens dreifach so groß wie eine Toleranz der Führung des Zwischenschlägers (18) in dem Gleitlager (21 , 22) ist.  wherein the radial play (34) is at least three times greater than a tolerance of the guide of the intermediate beater (18) in the sliding bearing (21, 22).
2. Handwerkzeugmaschine nach Anspruch 1 , dadurch gekennzeichnet, dass die Masse des Fängers (25) zwischen 20 % und 40 % der Masse des Zwischenschlägers (18) beträgt. 2. Hand tool according to Claim 1, characterized in that the mass of the catcher (25) is between 20% and 40% of the mass of the intermediate beater (18).
3. Handwerkzeugmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Fänger (25) entgegen der Schlagrichtung (12) an einem Dämpfelement (31) abgestützt ist. 3. Hand tool according to Claim 1 or 2, characterized in that the catcher (25) is supported against the direction of impact (12) on a damping element (31).
4. Handwerkzeugmaschine nach Anspruch 3, dadurch gekennzeichnet, dass der Fänger (25) zwischen dem Dämpfelement (31) und einem in Schlagrichtung (12) angeordnetem weiteren Dämpfelement (32) unter Vorspannung eingesetzt ist. 4. Hand tool according to Claim 3, characterized in that the catcher (25) between the damping element (31) and a direction of impact (12) arranged further damping element (32) is inserted under bias.
5. Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein Federelement (35) eine radiale Außenfläche (26) des Fängers (25) umspannt. 5. Hand tool according to one of the preceding claims, characterized in that a spring element (35) spans a radial outer surface (26) of the catcher (25).
6. Handwerkzeugmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Fänger (25) aus Stahl ist. 6. Hand tool according to one of the preceding claims, characterized in that the catcher (25) is made of steel.
EP14790626.7A 2013-11-06 2014-10-30 Manual tool machine Active EP3065914B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14790626.7A EP3065914B1 (en) 2013-11-06 2014-10-30 Manual tool machine

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP20130191708 EP2871030A1 (en) 2013-11-06 2013-11-06 Manual tool machine
PCT/EP2014/073304 WO2015067517A1 (en) 2013-11-06 2014-10-30 Portable power tool
EP14790626.7A EP3065914B1 (en) 2013-11-06 2014-10-30 Manual tool machine

Publications (2)

Publication Number Publication Date
EP3065914A1 true EP3065914A1 (en) 2016-09-14
EP3065914B1 EP3065914B1 (en) 2019-12-04

Family

ID=49518827

Family Applications (2)

Application Number Title Priority Date Filing Date
EP20130191708 Withdrawn EP2871030A1 (en) 2013-11-06 2013-11-06 Manual tool machine
EP14790626.7A Active EP3065914B1 (en) 2013-11-06 2014-10-30 Manual tool machine

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP20130191708 Withdrawn EP2871030A1 (en) 2013-11-06 2013-11-06 Manual tool machine

Country Status (4)

Country Link
US (1) US10286537B2 (en)
EP (2) EP2871030A1 (en)
CN (1) CN105705300A (en)
WO (1) WO2015067517A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3000560A1 (en) * 2014-09-25 2016-03-30 HILTI Aktiengesellschaft Driving device with gas spring
EP3231560A1 (en) * 2016-04-13 2017-10-18 HILTI Aktiengesellschaft Handheld machine tool
EP3822036A1 (en) * 2019-11-12 2021-05-19 Hilti Aktiengesellschaft Impact device assembly

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2844109A1 (en) 1978-10-10 1980-04-24 Bosch Gmbh Robert HAND MACHINE, IN PARTICULAR DRILLING AND / OR HAMMER
PT1238759E (en) * 2001-03-07 2004-04-30 Black & Decker Inc HAMMER
DE102005000042A1 (en) 2005-04-25 2006-10-26 Hilti Ag Chisel or chisel
DE102006000209A1 (en) 2006-05-05 2007-11-15 Hilti Ag Hand tool machine with impact tool holder
DE102006000533A1 (en) 2006-12-18 2008-06-19 Hilti Ag Hand-held tool with pneumatic hammer action, for chiseling or drilling, includes loose impact bush between external collars on header component
JP5147488B2 (en) * 2008-03-27 2013-02-20 株式会社マキタ Work tools

Also Published As

Publication number Publication date
EP2871030A1 (en) 2015-05-13
US20160279778A1 (en) 2016-09-29
CN105705300A (en) 2016-06-22
EP3065914B1 (en) 2019-12-04
US10286537B2 (en) 2019-05-14
WO2015067517A1 (en) 2015-05-14

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