EP0189769B1 - Perforateur rotatif ou à percussion - Google Patents

Perforateur rotatif ou à percussion Download PDF

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Publication number
EP0189769B1
EP0189769B1 EP86100313A EP86100313A EP0189769B1 EP 0189769 B1 EP0189769 B1 EP 0189769B1 EP 86100313 A EP86100313 A EP 86100313A EP 86100313 A EP86100313 A EP 86100313A EP 0189769 B1 EP0189769 B1 EP 0189769B1
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EP
European Patent Office
Prior art keywords
adjusting sleeve
spring
coupling
percussion
hammer drill
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.)
Expired - Lifetime
Application number
EP86100313A
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German (de)
English (en)
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EP0189769A1 (fr
Inventor
Willy Kress
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Individual
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Individual
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Publication date
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Publication of EP0189769A1 publication Critical patent/EP0189769A1/fr
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Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/003—Clutches specially adapted therefor

Definitions

  • the invention relates to a hammer drill or percussion hammer according to the preamble of claim 1.
  • a claw coupling is switched into the shaft that transmits the rotary drive to the tool, one coupling half of which is axially displaceably mounted on the shaft.
  • the shift takes place in that a first eccentric effect is exerted by a pin on a collar of the coupling half, the eccentric pin being driven by a rotary knob which can be operated manually from the outside (DE-A-3 018 633).
  • a second eccentric disc Forcibly coupled with this first eccentric pin, which causes the claw coupling to engage or disengage, is a second eccentric disc, which only releases the engagement of a locking pin in outer ring bores of the collar on the coupling half when the claw coupling is completely disengaged. It succeeds in this way, in chronological order First uncouple the drill drive, but not yet lock it, whereby the double eccentric releases the lock when the claw coupling is completely disengaged. The reverse process then takes place accordingly.
  • the problem of tooth-on-tooth standing is therefore eliminated in that the one claw side consists entirely of coupling teeth, which have the possibility of axially withdrawing, so that a complete approach of the two coupling halves, usually when the shaft is at a standstill, is fundamentally possible is that the coupling claws or coupling teeth of the sliding coupling half simply push back the opposing teeth or spring-loaded pins, with which they do not come into engagement during the subsequent turning operation.
  • the fixed clutch teeth then rest in one or the other direction of rotation on the remaining, that is not axially pushed away pins, so that a positive rotation is possible.
  • the problem with such a coupling may be that a constant disengagement pressure acts on the two coupling halves, generated by the spring-loaded pins pushed away, so that it is necessary to additionally lock the displaceable coupling half against axial movement in the engaged position. It is also cumbersome in this known coupling that a large number of axially displaceable driving pins are required, with a corresponding number of guide bores on the disk periphery of the one coupling half with respective compression springs which are inserted into the bore and which produce the spring preload, although it cannot be avoided, that when the direction of rotation is reversed, a certain amount of free movement, i.e. striking, is inevitable until the coupling teeth on the sliding coupling half engage on the opposite, protruding ones Create driving pin.
  • the intermediate shaft which is partially designed as a hollow shaft, is displaced axially against a coaxially internal spring so that the internal spline toothing of the hub body disengages from the external spline toothing of the intermediate shaft and reaches an undercut, as a result of which the hub body then remains without driving the intermediate shaft which continues to rotate and effects the drilling drive.
  • the intermediate shaft is displaced by rotating an actuating button, at the other end of which a switching eccentric is arranged, which presses on a crowned end of the intermediate shaft and displaces it.
  • the invention is therefore based on the object, in particular in the case of a rotary hammer or percussion hammer or a similar electric (hand) tool, to provide a simply constructed and therefore inexpensive coupling mechanism which, by external manual action, for example on a rotary knob, fully engages in the respectively disengaged or engaged position can be rotated without any obstacles resulting from a possible "tooth-on-tooth standing" and also without the need to constantly maintain pressure in one of the operating positions (engaged - disengaged) on the clutch.
  • the hammer drill or percussion hammer according to the invention with the characterizing features of the main claim and has the advantage that, based on the coupling process, in which mechanical positive connections are to be made effectively, even if the coupling conditions are not ideal at any given time are (tooth-on-tooth standing), in any case can be fully engaged from the actuator actuation side and then the clutch mechanism automatically engages when the ever-occurring relative angular shifts offer the opportunity to do so.
  • the engagement process is smooth and without ratcheting.
  • a further advantage of an embodiment of the present invention becomes apparent when one considers the displacement of the adjusting sleeve for engaging or disengaging on the countershaft in connection with a particularly simple actuator design for the manual actuation which brings about the changeover; a driving lug engages on an intermediate sliding member carrying out a linear displacement from the actuator into an annular groove of the adjusting sleeve and can move it axially in the desired direction, the actual rotary handle element, on which the user manually engages, in each case fully rotated into one or the other position can be without, even in the worst case, obstacles or blocking effects for switching.
  • the basic idea of the present invention is to equip the axially displaceable for effecting the clutch engagement on the countershaft, which is always in spline engagement with the sliding sleeve or clutch adjusting sleeve, hereinafter only referred to as the adjusting sleeve, even with axially displaceable driving pins, preferably by a ring spring trained and at least in partial groove areas on the adjusting sleeve bias spring loaded axially in the coupling direction, so that it is possible from the manual actuator, the coupling sleeve to fully shift into their clutch position, even if the clutch is not immediately applied, because the distance to go is absorbed by the axially shifting driving pins and their pre-tensioning spring (s) and automatically at a later point in time, e.g. when the machine goes into idle mode is engaged without the need for manual intervention or any other action by the user.
  • the housing can be divided in the usual manner in the longitudinal direction, that is, it can be designed as a double-shell housing, with at least one axial intersection or separation point, which is designated by A; with longitudinal screws 11 and 12 (cf. FIG. 2), which are inserted into corresponding lateral recesses in the rear housing half 10a and screwed into the inner projections of the front housing half 10b and clamped.
  • the drive motor with fan wheel 13, rotor 14 with motor drive shaft 15, carbon guides 16a, 16b and ball bearings 17 and 18 on both sides is shown at 12; further down in the handle are some electronic or electrical switching elements u. Like., which are designated together with 19 and which will not be discussed in the following because they are not part of the invention.
  • the drive pinion 20 of the motor shaft 15 is in engagement with a gearwheel 21, which is fixedly arranged on an intermediate or countershaft 22 for the percussion drive and the drive of a drill spindle sleeve 23 (cf. also the partial representation of FIG. 3, which in particular the Area of the countershaft and the impact drive shows more precisely).
  • a gearwheel 21 which is fixedly arranged on an intermediate or countershaft 22 for the percussion drive and the drive of a drill spindle sleeve 23 (cf. also the partial representation of FIG. 3, which in particular the Area of the countershaft and the impact drive shows more precisely).
  • 24 denotes a multitude of bearing and guiding tasks
  • the cylinder flange is made of aluminum and can be manufactured by injection molding or die casting and forms an inner guide sliding bore 25 for slidably supporting the over an eccentric effect driven, reciprocating in the guide bore 25 working or drive piston 26.
  • a gear twin 30 axially displaceable but non-rotatably in a suitable embodiment, for example, longitudinally displaceable by longitudinal grooves, the longitudinal displaceability of the two gear wheels 30a, 30b serving to change gear.
  • the countershaft 22 is stationary on both sides via needle bearings 31, 32 in the housing, but of course rotatably mounted and in the region of the gear twin 30 has a corresponding gear pair from the gears 32a, 32b, which is rotationally fixed and axially immovable the countershaft 22 are attached.
  • a second switchover option - how the switchover or the actuators provided for this switchover of the machine elements and parts moved here by an axial displacement will be explained in more detail below - then results from the additionally provided possibility that seen in itself with such hammer drills, it is also known to optionally switch the percussion drive on or off.
  • an eccentric shaft 37 is rotatably mounted transversely to the countershaft 22 in a bearing 36 fastened to the cylinder flange 24, the eccentric shaft 37 supporting an eccentric pivot pin 39 at its upper end and a helical gear 40 at its lower end, which meshes with another gear 41, which is freely rotatable, but axially immovable on the countershaft 22.
  • a coupling sleeve or adjusting sleeve 42 is provided for driving the eccentric shaft 37 in rotation, which results in the impact effect in a manner which will be explained briefly below, which is shown in greater detail in the illustration of FIGS. 5a, b and c.
  • the adjusting sleeve 42 as it will only be referred to below, is non-rotatably arranged on the countershaft 22, but is axially displaceable, for example by means of a corresponding spline toothing, and can be moved in the direction of the freely rotating gear 41.
  • the adjusting sleeve 42 has at least one, preferably two or possibly even more, driving pins 43, 44 which are diametrically opposed in the case of only two driving pins.
  • a connecting rod 45 acting like a connecting rod is between the eccentric pin 39 is provided on the eccentric shaft 37 and the working or drive piston 26 which slides in the guide bore 25 of the cylinder flange 24.
  • An essential feature of the present invention is the special clutch mechanism for taking the percussion drive 37, 39, 45, 26, 46 as it is formed by the adjusting sleeve 42 in the area of the countershaft.
  • FIG. 5a shows at 43a and 44a in this exemplary embodiment two guide bores offset from the center, in which the driving pins 43, 44, or in general terms, the driving elements, since of course no round pin shape is required and these are also rectangular or with any Cross section in the bores 43a, 44a can be guided, axially displaceable.
  • the guide bores 43a, 44a are each offset, so form at 70 inwardly projecting ring shoulders, so that it is ensured that the correspondingly complementary driving pins 43, 44 cannot fall through the guide bores in the coupling direction, that is to say in the plane of the drawing in FIG. 3, to the right .
  • the axial securing on the other side and at the same time the resilient bias that is exerted for the clutch engagement on the driving pins 43, 44 is generated by the fact that on the rear end, that is the left end of the driving pin in the plane of the drawing an axial prestressing force is exerted on an annular spring seated on the adjusting sleeve 42.
  • This ring spring is designated 71 and in this particularly simple, inexpensive and equally reliable embodiment consists of a closed ring made of a suitable elastomeric material, which is inserted into an adjacent groove 72 in the adjusting sleeve.
  • This ring spring 71 is preferably a so-called O-ring known per se; to accommodate it, the adjusting sleeve, as can best be seen from the illustration in FIGS. 5b and 5c, forms a projection 73 on the left in the plane of the drawing, which merges into a widened head part 74, so that the receiving groove 72 for the ring spring 71 is formed;
  • this groove is only present where the cantilevered head part does not hinder the free, spring-loaded mobility of the driving pins 43, 44; in other words, where the guide bores 44a, 43a are located, the overlap of the annular groove 72 or the head part is left out cut away so that the in the remaining groove areas - these can best be seen in the view of Fig.
  • the ring spring 71 bulges in this case at the points not covered by the ring groove 72 to the rear, but is held unchanged by the groove areas, also because of its own radial prestress, and exerts constant axial pressure on the driving pins 43, 44 therein Quasi coupling position of the adjusting sleeve 42. If the electric motor is rotated in this position, for example by actuating a starter push handle on the rotary hammer, then the gears involved in this coupling process automatically set themselves correctly at some point, and the driving pins snap into the corresponding recesses on the counter gear 41, or with each other relative displacement between gear 41 and adjusting sleeve 42, caused in whatever way.
  • the ring spring 71 also any other suitable configuration and can have any other suitable structure, provided that it can sit radially in the receiving groove 72 of the adjusting sleeve 42 and can exert corresponding axial forces on the driving pins, which can otherwise remain comparatively small, since it is only necessary to place them in the corresponding counter-openings of the gear 41 to axially press in and no retroactive forces occur while maintaining this (engaged) operating state.
  • annular spring 71 also made of a suitable metallic material, for example a tension spring forming a self-contained ring, that is to say constructed of individual spring bonds, as is any and all exerting the required axial engagement pressure on the driving pins the adjusting sleeve 42 can be fastened spring is suitable for this.
  • a suitable metallic material for example a tension spring forming a self-contained ring, that is to say constructed of individual spring bonds, as is any and all exerting the required axial engagement pressure on the driving pins the adjusting sleeve 42 can be fastened spring is suitable for this.
  • leaf springs which, as indicated by dashed lines at 76, can be embodied at 76a are fixed, for example by spot welding, to the adjusting sleeve 42 and hold the driving pin in position by axial pressure.
  • a particularly advantageous embodiment of the present invention finally results in connection with the actuator described in the schematic representation of FIGS. 6 and 7, which is the manual Switching from the outside is made possible by the user.
  • the actuator In order to carry out the engagement movement or any switch-over adjustment movements in electric (hand) tools, the actuator is designed as schematically explained with reference to the representations of FIGS. 6 and 7, which will be discussed below.
  • the rotary handle element accessible to an external manual actuation is designated by 50; it can be rotated, but is otherwise immovably mounted in a suitable manner in the housing, in a preferred embodiment such that either a projecting edge flange on the rotary handle element 50 is at least partially by itself 6, a housing ring projection 51 engages in an at least partially circumferential outer ring groove 52 on the rotary handle element 50.
  • a particularly preferred embodiment can then arise in a further development of the present invention in that the twist grip element is used where there is a housing interface A, where two housing part halves 10a, 10b to be connected to one another for final assembly are connected to one another in the longitudinal direction or laterally to form a dividing line or joint, and are joined together.
  • partial circle cutouts 55a, 55b are provided at the point at which the rotary handle elements for the actuator are to be arranged in the adjoining housing halves (at least in the case of a round rotary handle element), which complement one another when the housing is assembled to form a cut-out full circle.
  • twist grip element only needs to have a lower projecting ring flange, as is indicated in the illustration in FIG. 1 (this will be discussed further below), since the axial locking and securing against falling out is of course possible while being pressed in by others Parts is prevented safely.
  • an intermediate sliding member 56 is arranged adjacent to it within the housing, which is slidably mounted in a suitable, completely free manner, if appropriate by suitable or correspondingly arranged housing projections and ribs, so that this is a sliding movement can only perform in the double direction of arrows B and C, as shown in FIG. 6.
  • there is an engagement pin 57 on the rotary handle element 50 which engages in an elongated hole 58 on the intermediate sliding member 56, which extends in the transverse direction to the desired displacement direction generating the adjustment movement.
  • This subcomponent can therefore be, for example, the adjusting sleeve 42 shown in more detail in FIG. 3, but also the axially displaceable twin gearwheel 30 for changing gear.
  • twist grip elements 50a, 50b inserted centrally on both sides of the housing separation point A are guided on their outer ring edge to carry out the rotary adjustment movement through the housing ring cutout here and engage behind 61 ring recesses or simply housing cutout end areas with inner ring flanges, the respective engagement pin 57a, 57b depending on the extent the desired adjustment movement is mounted more or less eccentrically;
  • the twist grip elements 50a, 50b inserted centrally on both sides of the housing separation point A are guided on their outer ring edge to carry out the rotary adjustment movement through the housing ring cutout here and engage behind 61 ring recesses or simply housing cutout end areas with inner ring flanges, the respective engagement pin 57a, 57b depending on the extent the desired adjustment movement is mounted more or less eccentrically;
  • the center line A is provided as in the case of the engagement movement 42 of the adjusting sleeve 42, which requires only a small displacement path - the two intermediate sliding members 56a, 56b can be of quite different shape, the intermediate sliding member 56a responsible for the gear changeover initially engaging over the smaller gear 30b of the twin gear 30 and then in the groove arranged between the two gears 30a, 30b engages for adjustment.
  • the lower intermediate sliding member has a driving lug 59b arranged in the central region, which engages in the annular groove 62 of the adjusting sleeve 42 enlarged in FIG. 5. As shown in FIG.
  • the twist grip elements can be inserted into the housing of the electric (hand) tool in such a way that they do not protrude beyond the outline of the housing, so that the entire device acquires a pleasing appearance, with corresponding recessed grips 63, for example with an intermediate bridge, for smooth adjustment.
  • the twist grip elements with ring flanges 64 overlapping the outer housing ring regions, so that a secure hold for the twist grip elements is achieved together with the inner projecting ring flanges or ring grooves receiving housing ring flanges.

Claims (12)

  1. Perforateur rotatif ou à percussion ou outil électrique équivalent avec un embrayage réalisé à griffes, comprenant une douille de réglage (42) pour accoupler un type de marche, en particulier une commande de percussion ou un entraînement rotatif habituelle, la douille de réglage étant placée sur un arbre intermédiaire ou de renvoi (22), solidaire en rotation et en même temps déplaçable axialement par rapport à une contrepièce (41) sous l'effet d'un déplacement d'une pièce de réglage externe (50) et une prise d'actionnement par interpénétration de forme produit la mise en rotation par rapprochement mutuel entre la douille de réglage (42) et la contrepièce (41), caractérisé par
    a) au moins un goujon d'entraînement (43, 44) connu en soi inséré dans la douille de réglage (42), décentré et axialement déplaçable contre l'action d'un ressort, qui
    b) par commande de l'élément de réglage d'embrayage extérieur (50) est renvoyé dans une position d'attente non accouplée contre l'action de ressort, jusqu'à la butée finale d'embrayage total, dans laquelle les deux pièces d'embrayage (douille de réglage 42 et contrepièce 41) sont transportées dans la position finale axiale d'embrayage,
    (c) position d'attente à partir de laquelle au moins l'un des tenons d'entraînement (43, 44) s'engage dans les ouvertures de réception sur la contrepièce (41) par un mouvement de rotation relatif des deux parties d'embrayage (douille de réglage 42, contrepièce 41) l'un par rapport à l'autre de sorte que, grâce au positionnement initial dent sur dent des pièces d'embrayage, le mouvement de l'élément de réglage de l'embrayage est réalisable complètement jusqu'à la butée finale, en avançant en même temps l'engagement effectif de l'embrayage.
  2. Perforateur rotatif ou à percussion selon la revendication 1, caractérisé en ce qu'un élément élastique (71) exerçant la tension du ressort sur au moins un goujon d'entraînement (43, 44) est un ressort annulaire en direction radiale, maintenu fixe sur la douille de réglage (42), ressort contre lequel repose axialement le goujon d'entraînement (43, 44).
  3. Perforateur rotatif ou à percussion selon la revendication 2, caractérisé en ce que le ressort annulaire est composé d'un matériau en élastomère fermé de forme annulaire.
  4. Perforateur rotatif ou à percussion selon une des revendications 2 ou 3, caractérisé en ce que le ressort annulaire est un anneau taurique.
  5. Perforateur rotatif ou à percussion selon la revendication 2, caractérisé en ce que le ressort annulaire est un ressort de traction fermé de forme annulaire, se composant de spirales successives.
  6. Perforateur rotatif ou à percussion selon la revendication 5, caractérisé en ce que le ressort de traction comportant une forme annulaire fermée est composé de spirales en fil métallique.
  7. Perforateur rotatif ou à percussion selon la revendication 1, caractérisé en ce qu'un élément de élastique exerçant la tension du ressort sur la douille de réglage (42) est constitué d'un ressort à lames placé sur sa face frontale côté arrière à la manière d'un sécante, ressort qui exerce une tension axiale sur l'extrémité arrière d'au moins un goujon d'entraînement (43, 44).
  8. Perforateur rotatif ou à percussion selon une ou plusieurs des revendications 1 à 7, caractérisé en ce que le ressort annulaire (71) est inséré dans une rainure annulaire partielle de réception (72) formée par une collerette annulaire saillante vers l'extérieur, évitant toutefois les zones des alésages de guidage (43a, 44a) des goujons d'entraînement (43, 44) et produit en addition à sa tension radiale, dirigée vers l'intérieur, la tension résultant de ce qui précède agissant axialement sur les extrémités des goujons d'entraînement (43, 44) logés dans leurs alésages de guidage (43a, 43b), avec la possibilité de reculer du plan de rainure de réception (72) dans la zone des goujons d'entraînement (43, 44) et de préparer l'engagement de l'embrayage en atteignant sa position finale de la douille de réglage (42).
  9. Perforateur rotatif ou à percussion selon une des revendications 1à 8, caractérisé en ce que les alésages de guidage (43a, 44a) des goujons d'entraînement dans la douille de réglage (42) sont décalés en formant des épaulements annulaires (70) radiaux agissant comme butées.
  10. Perforateur rotatif ou à percussion selon une des revendications 1 à 9, caractérisé en ce que la contrepièce (41) par rapport à la douille de réglage (42) est formée d'une contre roue dentée pouvant tourner librement sur l'arbre de renvoi (22), roue dentée qui engrène par une denture oblique avec une roue dentée (40) décalée de 90° d'une transmission à excentrique (37, 39) pour la commande de percussion pneumatique et en ce que sont disposées dans la contre roue dentée les butées ou contre ouvertures, dans lesquelles s'insèrent les goujons d'entraînement (43, 44) dans la position embrayée.
  11. Perforateur rotatif ou à percussion selon une des revendications 1 à 9, caractérisé en ce que la douille de réglage (42) comporte une rainure annulaire moyenne (62), dans laquelle engrène le taquet d'entraînement (59) d'un élément coulissant intermédiaire (56) guidé droit par un moyen du boîtier, lequel élément est commandé par un élément de poignée rotative (50) accessible à une manoeuvre manuelle extérieure, laquelle poignée s'encliquète par un goujon d'engagement (57) dans un trou oblong (56) sur l'élément coulissant intermédiaire (56).
  12. Perforateur rotatif ou à percussion selon la revendication 11, caractérisé en ce que le trou oblong (58) sur l'élément coulissant intermédiaire se développe perpendiculairement à la direction de déplacement de l'embrayage sur la douille de réglage (42).
EP86100313A 1985-01-31 1986-01-11 Perforateur rotatif ou à percussion Expired - Lifetime EP0189769B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3503172 1985-01-31
DE19853503172 DE3503172A1 (de) 1985-01-31 1985-01-31 Bohr- oder schlaghammer

Publications (2)

Publication Number Publication Date
EP0189769A1 EP0189769A1 (fr) 1986-08-06
EP0189769B1 true EP0189769B1 (fr) 1991-05-08

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EP86100313A Expired - Lifetime EP0189769B1 (fr) 1985-01-31 1986-01-11 Perforateur rotatif ou à percussion

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DE (2) DE3503172A1 (fr)

Families Citing this family (8)

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Publication number Priority date Publication date Assignee Title
DE4003029A1 (de) * 1990-02-02 1991-08-08 Bosch Gmbh Robert Handgefuehrte werkzeugmaschine mit radialgeblaese
DE4016774A1 (de) * 1990-05-25 1991-11-28 Bosch Gmbh Robert Von hand fuehrbare elektrische werkzeugmaschine
DE4205840C2 (de) * 1992-02-26 1996-10-24 Kress Elektrik Gmbh & Co Bohrhammer mit Meißelfunktion
DE4305965C2 (de) * 1993-02-26 1997-08-21 Kress Elektrik Gmbh & Co Schaltvorrichtung zur Spindelarretierung für Elektrowerkzeuge
DE102007062248A1 (de) * 2007-12-21 2009-06-25 Robert Bosch Gmbh Handwerkzeugmaschine mit einer, mindestens eine drehbar gelagerte Zwischenwelle umfassenden Getriebevorrichtung
DE102008055057A1 (de) * 2008-12-22 2010-06-24 Robert Bosch Gmbh Werkzeugmaschine, insbesondere handgehaltene Werkzeugmaschine
CN103240443B (zh) * 2013-04-17 2016-08-10 河海大学 弹簧直角型钢桥裂纹修复钻孔机
CN111376213A (zh) * 2018-12-28 2020-07-07 南京德朔实业有限公司 电动榔头

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Publication number Priority date Publication date Assignee Title
US2966974A (en) * 1958-07-28 1961-01-03 Walter B Paskowski Clutch
US3837409A (en) * 1973-02-26 1974-09-24 Skil Corp Rotary hammer power tool
DE2728961C2 (de) * 1977-06-27 1991-08-08 Hilti Ag, Schaan Bohrhammer mit arretierbarem Werkzeughalter
DE3018633A1 (de) * 1980-05-16 1981-11-19 Wacker-Werke Gmbh & Co Kg, 8077 Reichertshofen Elektrobohrhammer mit abschaltbarem bohrantrieb
DE3213672C2 (de) * 1982-04-14 1984-07-12 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Stellglied zum Umschalten einer Hammerbohrmaschine mit einem durch einen Taumelscheibenantrieb betätigbaren pneumatischen Schlagwerk vom Betriebszustand "Bohren" in den Betriebszustand "Hammerbohren"
DE3224050A1 (de) * 1982-06-28 1983-12-29 Black & Decker, Inc. (eine Gesellschaft n.d.Ges.d. Staates Delaware), 19711 Newark, Del. Antriebsvorrichtung fuer das schlagwerk eines schlag- oder bohrhammers
DE3310145C2 (de) * 1983-03-21 1993-10-21 Hilti Ag Elektropneumatischer Bohrhammer mit austauschbarem Schlagwerk
DE3311263A1 (de) * 1983-03-28 1984-10-04 Hilti Ag, Schaan Handgeraet mit zweiganggetriebe

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Publication number Publication date
DE3679073D1 (de) 1991-06-13
EP0189769A1 (fr) 1986-08-06
DE3503172A1 (de) 1986-08-07

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