EP0590352A1 - Impact and/or drillhammer - Google Patents

Impact and/or drillhammer Download PDF

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Publication number
EP0590352A1
EP0590352A1 EP93114203A EP93114203A EP0590352A1 EP 0590352 A1 EP0590352 A1 EP 0590352A1 EP 93114203 A EP93114203 A EP 93114203A EP 93114203 A EP93114203 A EP 93114203A EP 0590352 A1 EP0590352 A1 EP 0590352A1
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EP
European Patent Office
Prior art keywords
shaft
eccentric
eccentric part
hammer drill
hammer
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
EP93114203A
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German (de)
French (fr)
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EP0590352B1 (en
Inventor
Manfred Bleicher
Ulrich Dipl.-Ing. Bohne (Fh)
Justus Dipl.-Ing. Lamprecht
Wilfried Dipl.-Ing. Kabatnik (Fh)
Joachim Dipl.-Ing. Hecht
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0590352A1 publication Critical patent/EP0590352A1/en
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Publication of EP0590352B1 publication Critical patent/EP0590352B1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • 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
    • B25D2250/005—Adjustable tool components; Adjustable parameters
    • B25D2250/021—Stroke length

Definitions

  • the invention is based on a hammer drill and / or percussion hammer according to the preamble of claim 1.
  • DE 41 21 279 A1 already discloses such a device in which the percussion mechanism is coupled to the idle device controlled by the tool via a claw coupling. A fixed part is connected to a rotating part via the claw coupling, which leads to wear and increased working noise.
  • the hammer and / or percussion hammer according to the invention with the characterizing features of claim 1 has the advantage that the coupling parts to be connected have the same rotational speed. The parts always remain in engagement with each other and are only rotated or shifted against each other. This leads to noiseless coupling processes without wear.
  • Figure 1 shows a longitudinal section through a hammer drill and Figure 2 shows a perspective section of Figure 1.
  • Figure 3 also shows a longitudinal section through a hammer in a second embodiment.
  • Figures 4, 5 and 6 show a perspective individual representation of eccentric parts and Figures 7 and 8 in processing schematically their function.
  • Figure 9 shows a third embodiment.
  • FIG. 1 shows a detail of a rotary hammer 1 with a housing 2 and a motor 3 at the rear.
  • the motor 3 drives a striking mechanism 5 via a shaft.
  • This has a racket 6, which acts via a striker 7 on a tool 9 received at the front in a tool holder 8.
  • the racket 6 is driven back and forth by a spring-stiff driver member 11. This is mounted such that it can be tilted about a tilt axis 12 and has a lever 14 coupled to a drive member 13.
  • the drive member 13 consists of a link sleeve 16 which has a downward extension 17 with an opening 18.
  • the opening 18 is shaped so that its surfaces facing the lever 14 are frustoconical on both sides with an elliptical base. The result is that the lever 14 is guided with little play in any possible eccentric position of the drive member 13 so that it ideally touches the opening 18 along a geometric line at the top and bottom.
  • the centerpiece of the drive is two eccentric parts 20, 21 which can be rotated relative to one another to a limited extent and which abut or engage in one another.
  • An inner eccentric part 20 is fixedly connected to the shaft 4 or is integrally formed therewith. It has an outer ring surface 22 which is cylindrical and extends coaxially but eccentrically to the axis of the shaft 4.
  • An outer eccentric part 21 has an inner ring surface 23 which surrounds the ring surface 22 and which likewise runs coaxially and eccentrically to the axis of the shaft 4.
  • the annular surface 23 is also eccentric to the peripheral surface 24 of the eccentric part 21, on which the articulation sleeve 16 is rotatably mounted via a needle bearing 25.
  • the articulation sleeve 16 is secured by a collar 26 on the eccentric part 21 and a spring-loaded spacer sleeve 27 which urges the entire drive member 13 towards the tool holder 8.
  • An axially limitedly movable hammer tube 29 connected to the tool holder 8 extends right up to the eccentric part 21.
  • a gear 30 for rotary drive is firmly connected, which meshes with a second gear 31 seated on the shaft 4.
  • the toothed wheel 30 On its end face facing the eccentric part 21, the toothed wheel 30 carries an axial bearing 32 which, with the interposition of a disk 33, is in contact with the end face of the eccentric part 21 on the collar.
  • the striker 7 tapering towards the striker 6 is guided in a guide sleeve 34 with a bore likewise tapering towards the striker in such a way that when the tool is pressed onto the striker 7 the hammer ear 29 moves in the direction of the eccentric part 21.
  • the eccentric part 21 When the tool 9 is pressed less strongly, the eccentric part 21 can move axially a little to the right relative to the eccentric part 20. It inevitably rotates along the curved tracks 37 with respect to the inner eccentric part 20, which reduces the overall eccentricity. If the tool 9 is completely removed from the workpiece, the outer eccentric part 21 comes into its front end position, as shown in FIG. 2, under pressure from the spring-loaded spacer sleeve 27. Since the total eccentricity of the drive member 13 is now zero, the articulation sleeve 16 remains without a deflection and the lever 14 stands still. The striking mechanism is thus switched off.
  • the second exemplary embodiment according to FIGS. 3 to 6 is constructed in principle like the first.
  • the functionally identical components shown in FIG. 3 are provided with reference numbers increased by 100. Unless mentioned below, the designations can be found in the first exemplary embodiment.
  • a drive member 113 comprises an inner eccentric part 120, which for assembly reasons consists of two members 120a, 120b. These are mutually immovable and fixed during operation, e.g. connected to shaft 104 by welding or pressing.
  • the eccentric part 120 has an eccentric outer ring surface 122 on which an inner ring surface 123 of an outer eccentric part 121 rests (see also FIGS. 4 to 6).
  • a pivot sleeve 116 is roller-mounted, which abuts a collar 126.
  • a driver member 111 engages in a known manner in an opening 118 of the articulation sleeve 116 provided with conical inner surfaces.
  • the inner eccentric part 120 has a circumferential groove 140 in its central region, which is delimited by two cam tracks 141 and 142 (see also development in FIGS. 7 and 8).
  • the cam tracks 141 and 142 are sawtooth-like, each with a steep flank 143 and a flat flank 144 per tooth 145.
  • the cam tracks 141 and 142 are congruent in the course, but offset in the circumferential direction.
  • a sawtooth-shaped annular bar 146 engages with play, which protrudes inwards from the outer eccentric part 121.
  • This also has sectionally steep sections 147 and sectionally flat sections 148.
  • the outer eccentric part 121 is axially displaceable.
  • a gear 130 fastened to a hammer tube 129 bears against it with its axial bearing 132.
  • the eccentric parts 120, 121 are shown in detail in FIGS. 4 to 6.
  • the eccentric member 120a is shifted to the left for the purpose of illustration.
  • FIG. 7 shows the disengaged state, in which the strip 146 of the outer eccentric part 121 bears against the eccentric member 120b against a stop. If the tool of the hammer drill 101 is now pressed onto a workpiece, the outer coupling part 121 is shifted backwards by the gear 130, that is to say to the left in FIGS. 3, 7 and 8.
  • the flat sections 148 of the bar 146 meet the flat flanks 144 of the eccentric member 120a. These slide against each other, so that the eccentric part 121 rotates relative to the eccentric part 120 by the amount B.
  • the strip 146 bears against the cam track 141 of the eccentric member 120a (see FIG. 8), the steep flanks 143 each forming stops which prevent the eccentric parts 120, 121 from rotating relative to one another.
  • the coupling is now fully engaged, which means that the total eccentricity has reached its maximum value.
  • This operating state is also shown in FIG. 3.
  • the spring 128 presses the eccentric part 121 forward via the spacer sleeve 127, that is to say to the right in FIG. 3, the eccentric part 121 rotating back in contact with the eccentric member 120b and the total eccentricity becoming zero .
  • the third exemplary embodiment according to FIG. 9 is constructed like the preceding ones. Compared to the first exemplary embodiment, functionally identical components are provided with reference numbers increased by 200 and the same designations. Since only the drive member 213 differs from the first embodiment, the description is limited to this.
  • An inner eccentric part 220 sits on a shaft 204. This has a cylindrical ring surface 222 which is inclined obliquely to the axis of the shaft 204.
  • An outer eccentric part 221 lies with its inner ring surface 223 on the ring surface 222.
  • the two eccentric parts 220 and 221 are secured against twisting by a wedge 250.
  • the inner eccentric part 220 carries a stop 251 on the right, against which the outer eccentric part 221 rests at zero eccentricity.
  • the outer eccentric part 221 is pushed backwards in the direction of the motor 203 by the gear 230 during the impact operation. In this position, the total eccentricity of the drive member 213 is maximum.
  • the ring surfaces 222 and 223 can be not only cylindrical, but also non-circular, for example square or equipped with another profile. In this case, the wedge 250 is also unnecessary.
  • the hammer mechanism coupling is also suitable for speed-independent control of the individual impact strength if required.
  • the total eccentricity and thus the deflection of the drive element change depending on the contact pressure of the machine at the machining point. A lower deflection leads to a lower single strike strength.

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

Abstract

In the case of a drillhammer (hammer drill) (1), the percussive mechanism (5) is set in motion by pressure of the tool (9) against a place to be worked. In this process, the gearwheel (30) displaces an outer eccentric part (21) axially with respect to an inner eccentric part (20). As a result of a curved path (37) in the outer eccentric part (21) and a fixed guide pin (36) in the inner eccentric part (20), the two parts rotate to a limited degree relative to one another during axial displacement. With this rotation, the entire eccentricity of the drive member (13) changes from zero to a maximum value. The percussive-mechanism coupling constructed in this way has the advantage that it operates silently and with little wear. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Bohr- und/oder Schlaghammer nach dem Oberbegriff des Anspruchs 1. Aus der DE 41 21 279 A1 ist bereits ein solches Gerät bekannt, bei dem das Schlagwerk über eine Klauenkupplung mit der vom Werkzeug gesteuerten Leerlaufeinrichtung gekoppelt ist. Über die Klauenkupplung wird ein feststehendes mit einem rotierenden Teil verbunden, was zu Verschleiß und erhöhtem Arbeitsgeräusch führt.The invention is based on a hammer drill and / or percussion hammer according to the preamble of claim 1. DE 41 21 279 A1 already discloses such a device in which the percussion mechanism is coupled to the idle device controlled by the tool via a claw coupling. A fixed part is connected to a rotating part via the claw coupling, which leads to wear and increased working noise.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Bohr- und/oder Schlaghammer mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß die zu verbindenden Kupplungsteile gleiche Rotationsgeschwindigkeit aufweisen. Die Teile bleiben stets miteinander im Eingriff und werden nur gegeneinander verdreht oder verschoben. Dies führt zu geräuschlosen Kupplungsvorgängen ohne Verschleiß.The hammer and / or percussion hammer according to the invention with the characterizing features of claim 1 has the advantage that the coupling parts to be connected have the same rotational speed. The parts always remain in engagement with each other and are only rotated or shifted against each other. This leads to noiseless coupling processes without wear.

Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Bohr- und/oder Schlaghammers möglich.The measures listed in the dependent claims allow advantageous developments and improvements of the hammer drill and / or percussion hammer specified in claim 1.

Zeichnungdrawing

Drei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Figur 1 zeigt einen Längsschnitt durch einen Bohrhammer und Figur 2 einen perspektivischen Ausschnitt aus Figur 1. Figur 3 zeigt in einem zweiten Ausführungsbeispiel ebenfalls einen Längsschnitt durch einen Hammer. Figuren 4, 5 und 6 zeigen in perspektivischer Einzeldarstellung Exzenterteile und die Figuren 7 und 8 in Abwicklung schematisch deren Funktion. Figur 9 zeigt ein drittes Ausführungsbeispiel.Three embodiments of the invention are shown in the drawing and explained in more detail in the following description. Figure 1 shows a longitudinal section through a hammer drill and Figure 2 shows a perspective section of Figure 1. Figure 3 also shows a longitudinal section through a hammer in a second embodiment. Figures 4, 5 and 6 show a perspective individual representation of eccentric parts and Figures 7 and 8 in processing schematically their function. Figure 9 shows a third embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ausschnittsweise ein Bohrhammer 1 mit Gehäuse 2 und hintenliegendem Motor 3 gezeigt. Der Motor 3 treibt über eine Welle ein Schlagwerk 5 an. Dieses weist einen Schläger 6 auf, der über einen Döpper 7 auf ein vorne in einer Werkzeugaufnahme 8 aufgenommenes Werkzeug 9 einwirkt. Der Schläger 6 wird von einem federsteifen Treiberglied 11 hin- und hergehend angetrieben. Dieses ist um eine Kippachse 12 kippbar gelagert und weist einen mit einem Antriebsglied 13 gekoppelten Hebel 14 auf.FIG. 1 shows a detail of a rotary hammer 1 with a housing 2 and a motor 3 at the rear. The motor 3 drives a striking mechanism 5 via a shaft. This has a racket 6, which acts via a striker 7 on a tool 9 received at the front in a tool holder 8. The racket 6 is driven back and forth by a spring-stiff driver member 11. This is mounted such that it can be tilted about a tilt axis 12 and has a lever 14 coupled to a drive member 13.

Das Antriebsglied 13 besteht aus einer Anlenkhülse 16, die einen nach unten gerichteten Fortsatz 17 mit einem Durchbruch 18 aufweist. Der Durchbruch 18 ist so geformt, daß seine dem Hebel 14 zugewandten Flächen beidseitig kegelstumpfförmig mit elliptischer Grundfläche ausgebildet sind. Das führt dazu, daß der Hebel 14 in jeder möglichen Exzenterstellung des Antriebsgliedes 13 spielarm so geführt ist, daß er oben und unten idealerweise entlang je einer geometrischen Linie den Durchbruch 18 berührt.The drive member 13 consists of a link sleeve 16 which has a downward extension 17 with an opening 18. The opening 18 is shaped so that its surfaces facing the lever 14 are frustoconical on both sides with an elliptical base. The result is that the lever 14 is guided with little play in any possible eccentric position of the drive member 13 so that it ideally touches the opening 18 along a geometric line at the top and bottom.

Kernstück des Antriebs sind zwei begrenzt gegeneinander verdrehbare Exzenterteile 20, 21, die aneinander anliegen bzw. ineinandergreifen. Ein inneres Exzenterteil 20 ist fest mit der Welle 4 verbunden bzw. mit dieser einstückig ausgebildet. Es weist eine äußere Ringfläche 22 auf, die zylindrisch ausgebildet ist und sich koaxial aber exzentrisch zur Achse der Welle 4 erstreckt. Ein äußeres Exzenterteil 21 weist eine die Ringfläche 22 umgreifende innere Ringfläche 23 auf, die ebenfalls koaxial und exzentrisch zur Achse der Welle 4 verläuft. Die Ringfläche 23 ist außerdem exzentrisch zur Umfangsfläche 24 des Exzenterteils 21, auf der über ein Nadellager 25 die Anlenkhülse 16 drehbar gelagert ist. Gesichert ist die Anlenkhülse 16 durch einen Bund 26 am Exzenterteil 21 und eine federbelastete Abstandshülse 27, die das gesamte Antriebsglied 13 nach vorne in Richtung Werkzeugaufnabme 8 drängt.The centerpiece of the drive is two eccentric parts 20, 21 which can be rotated relative to one another to a limited extent and which abut or engage in one another. An inner eccentric part 20 is fixedly connected to the shaft 4 or is integrally formed therewith. It has an outer ring surface 22 which is cylindrical and extends coaxially but eccentrically to the axis of the shaft 4. An outer eccentric part 21 has an inner ring surface 23 which surrounds the ring surface 22 and which likewise runs coaxially and eccentrically to the axis of the shaft 4. The annular surface 23 is also eccentric to the peripheral surface 24 of the eccentric part 21, on which the articulation sleeve 16 is rotatably mounted via a needle bearing 25. The articulation sleeve 16 is secured by a collar 26 on the eccentric part 21 and a spring-loaded spacer sleeve 27 which urges the entire drive member 13 towards the tool holder 8.

Ein mit dem Werkzeughalter 8 fest verbundenes axial begrenzt bewegliches Hammerrohr 29 reicht bis unmittelbar an das Exzenterteil 21 heran. Mit ihm ist ein Zahnrad 30 zum Drehantrieb fest verbunden, welches mit einem auf der Welle 4 sitzenden zweiten Zahnrad 31 kämmt. Auf seiner dem Exzenterteil 21 zugewandten Stirnseite trägt das Zahnrad 30 ein Axiallager 32, welches unter Zwischenlage einer Scheibe 33 in Kontakt mit der bundseitigen Stirnfläche des Exzenterteils 21 steht. Der sich zum Schläger 6 hin verjüngende Döpper 7 ist in einer Führungshülse 34 mit sich ebenfalls zum Schläger hin verjüngender Bohrung so geführt, daß beim Andrücken des Werkzeugs an den Döpper 7 das Hammerohr 29 sich in Richtung auf das Exzenterteil 21 verschiebt.An axially limitedly movable hammer tube 29 connected to the tool holder 8 extends right up to the eccentric part 21. With it, a gear 30 for rotary drive is firmly connected, which meshes with a second gear 31 seated on the shaft 4. On its end face facing the eccentric part 21, the toothed wheel 30 carries an axial bearing 32 which, with the interposition of a disk 33, is in contact with the end face of the eccentric part 21 on the collar. The striker 7 tapering towards the striker 6 is guided in a guide sleeve 34 with a bore likewise tapering towards the striker in such a way that when the tool is pressed onto the striker 7 the hammer ear 29 moves in the direction of the eccentric part 21.

In Figur 2 ist die Welle 4 mit den Exzenterteilen 20 und 21 gezeigt. In die Ringfläche 22 des inneren Exzenterteils 20 sind gleichmäßig über dem Umfang verteilt zwei bis vier kurze Führungsstifte 36 eingesetzt. Diese greifen in zugeordnete schraubenförmige Kurvenbahnen 37 in den Ringflächen 23 des äußeren Exzenterteils 21 ein. In Figur 2 stehen die Führungsstifte 36 am linken Ende der zugeordneten Kurvenbahn 37 auf Anschlag; das Exzenterteil 21 befindet sich in der Drehstellung, in der sich die Exzentrizitäten beider Teile 20, 21, die gleichgroß sind, gerade aufheben. Somit läuft die Umfangsfläche 24 gegenüber der Achse der Welle 4 rund.In Figure 2, the shaft 4 with the eccentric parts 20 and 21 is shown. Two to four short guide pins 36 are inserted into the annular surface 22 of the inner eccentric part 20, evenly distributed over the circumference. These engage in associated helical cam tracks 37 in the annular surfaces 23 of the outer eccentric part 21. In Figure 2, the guide pins 36 are at the left end of the associated cam track 37 on the stop; the eccentric part 21 is in the rotational position in which the eccentricities of both parts 20, 21, which are of the same size, just cancel each other out. Thus, the peripheral surface 24 runs round with respect to the axis of the shaft 4.

Bei an eine Bearbeitungsstelle fest angedrücktem Werkzeug 9, wie dies in Figur 1 gezeigt ist, liegt das äußere Exzenterteil 21 auf Anschlag an der Abstandshülse 27 an, sodaß es sich gegenüber dem inneren Exzenterteil 20 nicht weiter verschieben oder verdrehen kann. Die von beiden Exzenterteilen 20 und 21 hevorgerufene Gesamtexzentrizität des Antriebsglieds 13 hat nun ihren Maximalwert erreicht. Das heißt, der Hebel 14 des Treiberglieds 11 wird mit maximaler Amplitude auf und ab bewegt. Damit ist das Schlagwerk 5 auf maximale Schlagstärke eingestellt.When the tool 9 is firmly pressed onto a processing point, as shown in FIG. 1, the outer eccentric part 21 abuts against the spacer sleeve 27 so that it cannot move or twist relative to the inner eccentric part 20. The total eccentricity of the drive member 13 caused by both eccentric parts 20 and 21 has now reached its maximum value. That is, the lever 14 of the driver member 11 is moved up and down with maximum amplitude. The striking mechanism 5 is thus set to maximum impact strength.

Bei weniger stark angedrücktem Werkzeug 9 kann sich das Exzenterteil 21 gegenüber dem Exzenterteil 20 axial ein Stück nach rechts bewegen. Dabei verdreht es sich zwangsläufig entlang der Kurvenbahnen 37 gegenüber dem inneren Exzenterteil 20, womit sich die Gesamtexzentrizität verringert. Wird das Werkzeug 9 ganz vom Werkstück weggenommen, so gelangt das äußere Exzenterteil 21 auf Druck der federbelasteten Abstandshülse 27 in seine vordere Endstellung, wie sie in Figur 2 gezeigt ist. Da nun die Gesamtexzentrizität des Antriebsglieds 13 Null ist, bleibt die Anlenkhülse 16 ohne Ausschlag und der Hebel 14 steht still. Das Schlagwerk ist somit abgeschaltet.When the tool 9 is pressed less strongly, the eccentric part 21 can move axially a little to the right relative to the eccentric part 20. It inevitably rotates along the curved tracks 37 with respect to the inner eccentric part 20, which reduces the overall eccentricity. If the tool 9 is completely removed from the workpiece, the outer eccentric part 21 comes into its front end position, as shown in FIG. 2, under pressure from the spring-loaded spacer sleeve 27. Since the total eccentricity of the drive member 13 is now zero, the articulation sleeve 16 remains without a deflection and the lever 14 stands still. The striking mechanism is thus switched off.

Das zweite Ausführungsbeispiel nach den Figuren 3 bis 6 ist im Prinzip wie das erste aufgebaut. Die in Figur 3 gezeigten funktionsgleichen Bauteile sind mit um 100 erhöhten Bezugszahlen versehen. Die Bezeichnungen sind, soweit nachfolgend nicht erwähnt, dem ersten Ausführungsbeispiel zu entnehmen.The second exemplary embodiment according to FIGS. 3 to 6 is constructed in principle like the first. The functionally identical components shown in FIG. 3 are provided with reference numbers increased by 100. Unless mentioned below, the designations can be found in the first exemplary embodiment.

Ein Antriebsglied 113 umfaßt ein inneres Exzenterteil 120, das aus Montagegründen aus zwei Gliedern 120a, 120b besteht. Diese sind im Betrieb gegeneinander unverschieblich und fest, z.B. durch Schweißen oder Aufpressen mit der Welle 104 verbunden. Das Exzenterteil 120 weist eine exzentrische äußere Ringfläche 122 auf, auf der eine innere Ringfläche 123 eines äußeren Exzenterteils 121 aufliegt (s. auch Figuren 4 bis 6). Auf einer äußeren Umfangsfläche 124 des Exzenterteils 121 ist, wie im ersten Ausführungsbeispiel, eine Anlenkhülse 116 wälzgelagert, die an einem Bund 126 anliegt. In einen mit kegelstumfförmigen Innenflächen versehenen Durchbruch 118 der Anlenkhülse 116 greift in bekannter Weise ein Treiberglied 111 ein.A drive member 113 comprises an inner eccentric part 120, which for assembly reasons consists of two members 120a, 120b. These are mutually immovable and fixed during operation, e.g. connected to shaft 104 by welding or pressing. The eccentric part 120 has an eccentric outer ring surface 122 on which an inner ring surface 123 of an outer eccentric part 121 rests (see also FIGS. 4 to 6). On the outer circumferential surface 124 of the eccentric part 121, as in the first exemplary embodiment, a pivot sleeve 116 is roller-mounted, which abuts a collar 126. A driver member 111 engages in a known manner in an opening 118 of the articulation sleeve 116 provided with conical inner surfaces.

Das innere Exzenterteil 120 weist in seinem Mittelbereich eine umlaufende Nut 140 auf, die von zwei Kurvenbahnen 141 und 142 begrenzt wird (s. auch Abwicklung in den Figuren 7 und 8). Die Kurvenbahnen 141 und 142 sind sägezahnartig mit je einer steilen Flanke 143 und einer flachen Flanke 144 je Zahn 145 ausgebildet. Die Kurvenbahnen 141 und 142 sind im Verlauf deckungsgleich, jedoch in Umfangsrichtung versetzt angeordnet. In die Nut 140 greift mit Spiel eine im Profil ebenfalls sägezahnförmige ringförmige Leiste 146 ein, die von dem äußeren Exzenterteil 121 nach innen wegsteht. Diese weist ebenfalls stückweise steile Abschnitte 147 und stückweise flache Abschnitte 148 auf. Das äußere Exzenterteil 121 ist, wie im ersten Beispiel, axial verschieblich. An ihm liegt ein an einem Hammerrohr 129 befestigtes Zahnrad 130 mit seinem Axiallager 132 an.The inner eccentric part 120 has a circumferential groove 140 in its central region, which is delimited by two cam tracks 141 and 142 (see also development in FIGS. 7 and 8). The cam tracks 141 and 142 are sawtooth-like, each with a steep flank 143 and a flat flank 144 per tooth 145. The cam tracks 141 and 142 are congruent in the course, but offset in the circumferential direction. In the groove 140, a sawtooth-shaped annular bar 146 engages with play, which protrudes inwards from the outer eccentric part 121. This also has sectionally steep sections 147 and sectionally flat sections 148. As in the first example, the outer eccentric part 121 is axially displaceable. A gear 130 fastened to a hammer tube 129 bears against it with its axial bearing 132.

Die Exzenterteile 120, 121 sind in allen Einzelheiten in den Figuren 4 bis 6 dargestellt. In Figur 6 ist zu Darstellungszwecken das Exzenterglied 120a nach links verschoben.The eccentric parts 120, 121 are shown in detail in FIGS. 4 to 6. In FIG. 6, the eccentric member 120a is shifted to the left for the purpose of illustration.

Die Funktion der von den Exzenterteilen 120, 121 gebildeten Schlagwerkskupplung ist am besten aus den Figuren 7 und 8 ersichtlich.The function of the striking mechanism coupling formed by the eccentric parts 120, 121 can best be seen from FIGS. 7 and 8.

Figur 7 zeigt den ausgekuppelten Zustand, bei dem die Leiste 146 des äußeren Exzenterteils 121 an dem Exzenterglied 120b auf Anschlag anliegt. Wird nun das Werkzeug des Bohrhammers 101 an ein Werkstück angedrückt, so wird das äußere Kupplungsteil 121 von dem Zahnrad 130 nach hinten, das heißt in den Figuren 3, 7 und 8 nach links verschoben. Dabei treffen die flachen Abschnitte 148 der Leiste 146 auf die flachen Flanken 144 des Exzenterglieds 120a. Diese gleiten aneinander ab, so daß sich das Exzenterteil 121 gegenüber dem Exzenterteil 120 um den Betrag B verdreht. Am Ende des Schaltvorgangs liegt die Leiste 146 an der Kurvenbahn 141 des Exzenterglieds 120a an (siehe Figur 8 ), wobei die steilen Flanken 143 jeweils Anschläge bilden, die weiteres Verdrehen der Exzenterteile 120, 121 gegeneinander verhindern. Nun ist die Kupplung voll eingekuppelt, das heißt, die Gesamtexzentrizität hat ihren Maximalwert erreicht. Dieser Betriebszustand ist auch in Figur 3 dargestellt.FIG. 7 shows the disengaged state, in which the strip 146 of the outer eccentric part 121 bears against the eccentric member 120b against a stop. If the tool of the hammer drill 101 is now pressed onto a workpiece, the outer coupling part 121 is shifted backwards by the gear 130, that is to say to the left in FIGS. 3, 7 and 8. The flat sections 148 of the bar 146 meet the flat flanks 144 of the eccentric member 120a. These slide against each other, so that the eccentric part 121 rotates relative to the eccentric part 120 by the amount B. At the end of the switching process, the strip 146 bears against the cam track 141 of the eccentric member 120a (see FIG. 8), the steep flanks 143 each forming stops which prevent the eccentric parts 120, 121 from rotating relative to one another. The coupling is now fully engaged, which means that the total eccentricity has reached its maximum value. This operating state is also shown in FIG. 3.

Wird der Hammer wieder von der Bearbeitungsstelle weggenommen, so drückt die Feder 128 das Exzenterteil 121 über die Abstandshülse 127 nach vorne, das heißt in Figur 3 nach rechts, wobei sich gleichzeitig das Exzenterteil 121 im Kontakt mit dem Exzenterglied 120b zurückdreht und die Gesamtexzentrizität Null wird.If the hammer is removed again from the processing point, the spring 128 presses the eccentric part 121 forward via the spacer sleeve 127, that is to say to the right in FIG. 3, the eccentric part 121 rotating back in contact with the eccentric member 120b and the total eccentricity becoming zero .

Das dritte Ausführungsbeispiel nach Figur 9 ist im Prinzip wie die vorangegangenen aufgebaut. Funktionsgleiche Bauteile sind gegenüber dem ersten Ausführungsbeispiel mit um 200 erhöhten Bezugszahlen und den gleichen Bezeichnungen versehen. Da nur das Antriebsglied 213 vom ersten Ausführungsbeispiel abweicht, beschränkt sich die Beschreibung auf dieses.In principle, the third exemplary embodiment according to FIG. 9 is constructed like the preceding ones. Compared to the first exemplary embodiment, functionally identical components are provided with reference numbers increased by 200 and the same designations. Since only the drive member 213 differs from the first embodiment, the description is limited to this.

Auf einer Welle 204 sitzt ein inneres Exzenterteil 220. Dieses weist eine zylindrische Ringfläche 222 auf, die schräg zur Achse der Welle 204 geneigt ist. Ein äußeres Exzenterteil 221 liegt mit seiner inneren Ringfläche 223 auf der Ringfläche 222 auf. Die beiden Exzenterteile 220 und 221 sind durch einen Keil 250 gegen gegenseitiges Verdrehen gesichert. Das innere Exzenterteil 220 trägt rechts einen Anschlag 251, an dem das äußere Exzenterteil 221 bei Exzentrizität Null anliegt. Das äußere Exzenterteil 221 wird während des Schlagbetriebs durch das Zahnrad 230 nach hinten in Richtung Motor 203 gedrückt. In dieser Stellung ist die Gesamtexzentrizität des Antriebsglieds 213 maximal. Bei von der Bearbeitungsstelle abgehobenem Bohrhammer wird das äußere Exzenterteil 221 durch die Feder 228 nach vorn verschoben, wobei sich infolge der schräg verlaufenden Ringflächen 222 und 223 die Exzentrizität allmählich bis auf den Wert Null verringert. Die Ringflächen 222 und 223 können außer zylindermantelförmig auch unrund, zum Beispiel vierkantig oder mit einem sonstigen Profil ausgestattet sein. In diesem Fall erübrigt sich auch der Keil 250.An inner eccentric part 220 sits on a shaft 204. This has a cylindrical ring surface 222 which is inclined obliquely to the axis of the shaft 204. An outer eccentric part 221 lies with its inner ring surface 223 on the ring surface 222. The two eccentric parts 220 and 221 are secured against twisting by a wedge 250. The inner eccentric part 220 carries a stop 251 on the right, against which the outer eccentric part 221 rests at zero eccentricity. The outer eccentric part 221 is pushed backwards in the direction of the motor 203 by the gear 230 during the impact operation. In this position, the total eccentricity of the drive member 213 is maximum. When the rotary hammer is lifted from the machining point, the outer eccentric part 221 is moved forward by the spring 228, the eccentricity gradually being reduced to zero as a result of the oblique ring surfaces 222 and 223. The ring surfaces 222 and 223 can be not only cylindrical, but also non-circular, for example square or equipped with another profile. In this case, the wedge 250 is also unnecessary.

Die Schlagwerkskupplung eignet sich bei Bedarf auch zur drehzahlunabhängigen Steuerung der Einzelschlagstärke. Abhängig von der Anpreßkraft der Maschine an die Bearbeitungsstelle ändert sich die Gesamtexzentrizität und damit der Ausschlag des Antriebsgliedes. Ein geringerer Ausschlag führt zu einer geringeren Einzelschlagstärke.The hammer mechanism coupling is also suitable for speed-independent control of the individual impact strength if required. The total eccentricity and thus the deflection of the drive element change depending on the contact pressure of the machine at the machining point. A lower deflection leads to a lower single strike strength.

Claims (11)

Bohr- und/oder Schlaghammer mit in einem Gehäuse (2) untergebrachtem Motor (3) und einem Schlagwerk (5), dessen Schläger (6) von einem Treiberglied (11) etwa in seiner axialen Richtung beschleunigt wird und der periodisch direkt oder indirekt axial auf den Schaft eines Werkzeugs (9) auftrifft, welches Treiberglied (11) um eine Kippachse (12) kippbar ist und von einem Antriebsglied (13) mit Exzenter (20, 21) hin- und hergehend angetrieben wird, das seinerseits von einer Welle (4) in Drehung versetzt wird, dadurch gekennzeichnet, daß das Antriebsglied (13) zwei ineinandergreifende Exzenterteile (20, 21) aufweist, von denen das erste (20) mit der Welle (4) undrehbar verbunden und das zweite (21) gegenüber der Welle (4) axial verschieblich ist, wobei beide Exzenterteile (20, 21) mit jeweils die Welle (4) umgebenden, gegenüber dieser unsymmetrisch angeordneten miteinander in Kontakt stehenden Ringflächen (22, 23) versehen sind, die so gegeneinander versetzbar sind, daß die resultierende, auf das Treiberglied (11) einwirkende Exzentrizität des Antriebsgliedes (13) gegenüber der Welle (4) zwischen Null und einem Maximalwert einstellbar ist.Hammer drill and / or percussion hammer with a motor (3) housed in a housing (2) and a percussion mechanism (5), the striker (6) of which is accelerated approximately in its axial direction by a driver member (11) and which is periodically directly or indirectly axially strikes the shank of a tool (9), which driver member (11) can be tilted about a tilt axis (12) and is driven to and fro by a drive member (13) with an eccentric (20, 21), which in turn is driven by a shaft ( 4) is set in rotation, characterized in that the drive member (13) has two interlocking eccentric parts (20, 21), of which the first (20) is non-rotatably connected to the shaft (4) and the second (21) with respect to the shaft (4) is axially displaceable, both eccentric parts (20, 21) being provided with ring surfaces (22, 23) which surround the shaft (4) and are arranged asymmetrically with respect to one another and are displaceable relative to one another in such a way that the result The eccentricity of the drive member (13) acting on the driver member (11) relative to the shaft (4) can be set between zero and a maximum value. Bohr- und/oder Schlaghammer nach Anspruch 1, dadurch gekennzeichnet, daß das Treiberglied (11) mit dem Antriebsglied (13) ständig in Eingriff steht.Hammer drill and / or percussion hammer according to claim 1, characterized in that the driver member (11) is in constant engagement with the drive member (13). Bohr- und/oder Schlaghammer nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das zweite Exzenterteil (21) entlang der Ringfläche (22) des ersten (20) axial verschieblich ist.Hammer drill and / or percussion hammer according to claim 1 or 2, characterized in that the second eccentric part (21) is axially displaceable along the ring surface (22) of the first (20). Bohr- und/oder Schlaghammer nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Ringflächen (22, 23) sich koaxial zur Achse der Welle (4) erstrecken.Hammer drill and / or percussion hammer according to one of claims 1 to 3, characterized in that the annular surfaces (22, 23) extend coaxially to the axis of the shaft (4). Bohr- und/oder Schlaghammer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Ringflächen (22, 23) zylindermantelförmig sind.Hammer drill and / or percussion hammer according to one of the preceding claims, characterized in that the annular surfaces (22, 23) are cylindrical in shape. Bohr- und/oder Schlaghammer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das zweite Exzenterteil (21, 121) an einer Kurvenbahn (37, 141, 142) geführt ist und sich bei axialer Verschiebung entlang der Welle (4) gegenüber dem ersten Exzenterteil (20, 120) verdreht.Hammer drill and / or percussion hammer according to one of the preceding claims, characterized in that the second eccentric part (21, 121) is guided on a cam track (37, 141, 142) and is axially displaced along the shaft (4) with respect to the first Eccentric part (20, 120) twisted. Bohr- und/oder Schlaghammer nach Anspruch 6, dadurch gekennzeichnet, daß die Kurvenbahn (37) schraubenlinienförmig und in einem der beiden Exzenterteile (20, 21) angeordnet ist.Hammer drill and / or percussion hammer according to claim 6, characterized in that the cam track (37) is arranged helically and in one of the two eccentric parts (20, 21). Bohr- und/oder Schlaghammer nach Anspruch 6, dadurch gekennzeichnet, daß in beiden Exzenterteilen (120, 121) miteinander zusammenarbeitende Kurvenbahnen (141, 142, 146) angeordnet sind.Hammer drill and / or percussion hammer according to Claim 6, characterized in that cam tracks (141, 142, 146) which cooperate with one another are arranged in the two eccentric parts (120, 121). Bohr- und/oder Schlaghammer nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Ringflächen (222, 223) sich schräg zur Achsrichtung der Welle (204) hin erstrecken.Hammer drill and / or percussion hammer according to one of claims 1 to 3, characterized in that the annular surfaces (222, 223) extend obliquely to the axial direction of the shaft (204). Bohr- und/oder Schlaghammer nach Anspruch 9, dadurch gekennzeichnet, daß die Ringflächen (222, 223) unrund sind.Hammer drill and / or percussion hammer according to claim 9, characterized in that the annular surfaces (222, 223) are out of round. Bohr- und/oder Schlaghammer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Antriebsglied (13) einen Durchbruch (18) zum Eingriff des Treibergliedes (11) aufweist, der zum Treiberglied (11) hin beidseitig kegelstumpförmig ausgebildet ist, sodaß in jeder möglichen Exzenterstellung des Antriebsgliedes (13) das Treiberglied (11) idealerweise an Zwei Linien den Durchbruch (18) spielarm berührt.Hammer drill and / or percussion hammer according to one of the preceding claims, characterized in that the drive member (13) has an opening (18) for engaging the driver member (11) which is frustoconical on both sides towards the driver member (11), so that in each possible eccentric position of the drive member (13) ideally touches the driver member (11) on two lines the opening (18) with little play.
EP93114203A 1992-09-24 1993-09-04 Impact and/or drillhammer Expired - Lifetime EP0590352B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4231986 1992-09-24
DE4231986A DE4231986A1 (en) 1992-09-24 1992-09-24 Hammer and / or percussion hammer

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EP0590352A1 true EP0590352A1 (en) 1994-04-06
EP0590352B1 EP0590352B1 (en) 1997-04-09

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DE (2) DE4231986A1 (en)

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EP0590352B1 (en) 1997-04-09
DE59306096D1 (en) 1997-05-15
US5337835A (en) 1994-08-16
DE4231986A1 (en) 1994-03-31

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