EP0552328A1 - Percussion drill. - Google Patents

Percussion drill.

Info

Publication number
EP0552328A1
EP0552328A1 EP92914235A EP92914235A EP0552328A1 EP 0552328 A1 EP0552328 A1 EP 0552328A1 EP 92914235 A EP92914235 A EP 92914235A EP 92914235 A EP92914235 A EP 92914235A EP 0552328 A1 EP0552328 A1 EP 0552328A1
Authority
EP
European Patent Office
Prior art keywords
guide tube
hammer
ring
tool holder
drill according
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
EP92914235A
Other languages
German (de)
French (fr)
Other versions
EP0552328B1 (en
Inventor
Manfred Bleicher
Ulrich Bohne
Volker Lasch
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0552328A1 publication Critical patent/EP0552328A1/en
Application granted granted Critical
Publication of EP0552328B1 publication Critical patent/EP0552328B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
    • B25D17/084—Rotating chucks or sockets
    • B25D17/088—Rotating chucks or sockets with radial movable locking elements co-operating with bit shafts specially adapted therefor
    • 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
    • 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
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/061—Swash-plate actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/003—Details relating to chucks with radially movable locking elements
    • B25D2217/0038—Locking members of special shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/003—Details relating to chucks with radially movable locking elements
    • B25D2217/0038—Locking members of special shape
    • B25D2217/0042—Ball-shaped locking members
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/003—Details relating to chucks with radially movable locking elements
    • B25D2217/0053—Devices for securing the tool retainer to the machine part
    • 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

Definitions

  • the invention is based on a hammer according to the preamble of claim 1.
  • a rotary hammer is known in which, contrary to the otherwise conventional design, the guide tube for the striking mechanism and the tool holder are in two parts. The two parts are connected by locking elements which engage as balls in recesses in both parts, which results in a high selective loading of the parts. For this reason, the guide tube, like the tool holder, had to be tempered or hardened. Otherwise, the construction requires a high level of construction.
  • the hammer or hammer drill according to the invention with the characterizing features of claim 1 has the advantage that the high axial forces resulting from the striking mechanism are transmitted over a large area. This enables the use of an uncured guide tube, thereby avoiding delay in hardness and reworking on the guide tube. Last but not least, the lower weight of the components to be hardened is accompanied by a noticeable relief of the environment by omitting hardening steps.
  • the use of a resilient profile ring and corresponding grooves, preferably adapted in shape, in the guide tube and in the tool holder avoid shear stresses of the connecting element, so that the profile ring is only subjected to pressure and does not punctually, but only on the components to be connected Surface pressures occur between "hard” and "soft” components.
  • the grooves adapt exactly to the shape of the profile rings, so that they support with their entire surface.
  • the axial connection according to the invention has the further advantage that the hammer sleeve is easy to manufacture in a plug-in assembly and that the tool holder runs smoothly.
  • the contact surface In its inclined position with respect to the longitudinal axis, can be flat or also concavely curved in order to adapt to the external finish of the profile ring used.
  • the profile ring can in particular have a circular or oval, rectangular or other cross section.
  • a detent ring as a coupling part for a safety clutch, which is fastened by means of a plurality of rollers, which preferably lie linearly in three recesses. This makes the catch ring easily replaceable when worn. A good transmission of the torque between the catch ring and the guide sleeve is possible via the rollers with easy manufacturing possibilities.
  • a round ring can advantageously also be attached in the guide tube, which is on a slope of the detent ring may be under tension. The entire construction makes it possible to use a seamlessly drawn or welded soft piece of pipe as the guide tube, which considerably reduces the production costs.
  • the construction according to the invention has the further advantage that the connecting means between the guide tube and tool holder as well as the detent ring are very space-saving and enable a hammer sleeve which is also thin-walled in comparison to one-piece designs.
  • the connections therefore do not require any additional space, in contrast to the solution according to DE 38 28309 C2.
  • Figure 1 shows a longitudinal section through the front part of a rotary hammer
  • Figure 2 shows an axial connection in an enlarged view
  • Figure 3 shows a perspective view of a hammer sleeve.
  • Figure 4 shows a second embodiment.
  • a hammer drill has a housing 2 made of plastic, in which a motor, not shown, is housed, which drives an intermediate shaft 3.
  • a striking mechanism 4 is accommodated in the housing 2, at the front end of which a tool holder 5 is arranged.
  • the striking mechanism 4 lies within a three-part hammer sleeve 6, which consists of a guide tube 7, a tool holder 8 with a longitudinal axis 14 and a detent ring.
  • the striking mechanism 4 is guided in the guide tube 7 > which is mounted in the housing 2 and which is designed as a seamlessly drawn or welded uncured tube piece.
  • the tool holder 8 can rest against the guide tube 7 inside (as in FIG. 1) or outside.
  • the detent ring 9, which serves as part of a safety snap-in coupling 10, also sits on the guide tube 7.
  • the safety clutch 10 has rollers 11 as a driving body, which cooperate with locking troughs in the hardened locking ring 9 and with a gear wheel 12.
  • the gear wheel 12 is rotatable relative to the guide tube 7 and engages in a toothing 13 of the intermediate shaft 3.
  • the two parts 9 "UOd. 12 of the safety clutch 10 are pressed together by a compression spring 15, which determines the latching torque of the clutch.
  • the compression spring 15 is secured in a known manner by means of a support disk 18 held in the guide tube 7 by round rings 16, 17.
  • the striking mechanism 4 with a pot-shaped, reciprocally driven piston 20 and a striker 21 located therein.
  • the energy of the striker 21 driven by the piston 20 is applied to a dropper 22 and from there to a striker (not shown) Transfer tool.
  • the piston 20 is guided in the guide tube 7.
  • Guide tube 7 and tool holder 8 overlap in a certain area and are connected to one another there by means of a press fit. Careful machining of the easily accessible contact surfaces of the press fit connection simultaneously ensures good concentricity of the tool holder.
  • a slotted, resilient profile ring 24 is additionally inserted (see also FIG. 2). This is inserted under prestress into a mounting ring groove 25 in the tool holder 8, which can fully accommodate the profile ring 24.
  • the mounting ring groove 25 ends on one side in a contact surface 27 which is inclined at 30 ° -60 °, preferably 45 °, to the longitudinal axis 14.
  • the contact surface can also be rounded or concave, but in such a way that at least one part of the contact surface 27 that absorbs compressive forces is inclined approximately by the aforementioned angle to the longitudinal axis 14.
  • the guide tube 7 has an annular groove 28 which is preferably adapted to the respective profile of the hardened profile ring 24.
  • the profile ring 24 here has a circular cross section and the annular groove 28 has a semicircular cross section.
  • the detent ring 9 is connected to the guide tube 7 via three elongated rollers 30.
  • the rollers 30 lie in the guide tube 7 in three rectilinear notches 31 which run out at the ends and have a semicircular cross section (see FIG. 3, in which the rollers 30 have been omitted).
  • the detent ring 9 has three straight cutouts 3.
  • the rollers 30 are first inserted into the notches 31 and then the Rastenring 9 pushed over it.
  • an elastic round ring 34 is inserted into a groove in the guide tube 7 from the opposite side, that is to say from the rear.
  • the round ring 34 lies against a slope 35 of the detent ring 9.
  • the detent ring 9 can be dismantled by removing the round ring 34 and, if necessary, exchanged.
  • the hammer sleeve is in two parts and consists of a tool holder and a guide sleeve with an integrally formed detent ring for torque transmission.
  • the structure in particular with regard to the axial connection, is the same as the exemplary embodiment shown in the drawing.
  • a two-part design also has the advantage that a high-quality material only needs to be used for the tool holder and the guide tube does not have to be subjected to complete heat treatment. It also considerably simplifies and reduces the cost of manufacturing.
  • a further advantage is that the components located in the area of the striker can be mounted either from the front or from the rear with a two-part as well as with a three-part hammer sleeve. This is not possible with a one-piece version.
  • the profile ring 124 has a square cross section.
  • the mounting ring groove 125 with contact surface 127 is unchanged from the first embodiment.
  • the mounting position 126 of the profile ring 124 is shown in dashed lines.
  • the annular groove 128 also has a similar, flat, inclined contact surface 129 lying obliquely opposite the contact surface 127.
  • the annular groove 128 is so limited that it can not fully accommodate the profile ring 124, but only partially in an inclined position.
  • the axial connection with the profile ring 24/124 can, in reverse of the arrangement in the exemplary embodiments shown, also be designed such that the mounting ring groove is located in the outer tube part. Then the profile ring is inserted under prestress in the form of a pre-expansion and contracts again after the pipe parts have been joined together.

Abstract

Un marteau perforateur (3) présente une douille de guidage (6) en trois parties. Sur un tube de guidage (7) en acier non-trempé est fixé un porte-outil en acier trempé (8) au moyen de raccords axiaux (24, 25, 28). En outre, le tube de guidage (7) porte, pour l'établissement de la liaison avec le pignon de commande (12), une bague à crans (9). La bague à crans est fixée au tube de guidage (7) au moyen de trois rouleaux (30) permettant une bonne transmission du couple de rotation. Cette conception offre l'avantage qu'il ne faut plus tremper la douille tout entière (6), mais seulement le porte-outil (8) et la bague à crans (9). Le tube de guidage (7) peut être en acier doux. Les raccords (24, 25, 28) et (30, 31, 32) assurent une transmission de la force par une grande surface de contact, de manière à éviter, sur le tube de guidage doux, l'usure connue avec les techniques de liaison traditionnelles.A hammer drill (3) has a guide sleeve (6) in three parts. A hardened steel tool holder (8) is attached to a guide tube (7) of unhardened steel by means of axial connectors (24, 25, 28). In addition, the guide tube (7) carries, for establishing the connection with the control pinion (12), a notched ring (9). The notched ring is fixed to the guide tube (7) by means of three rollers (30) allowing good transmission of the torque. This design offers the advantage that it is no longer necessary to quench the entire bush (6), but only the tool holder (8) and the notch ring (9). The guide tube (7) can be made of mild steel. The fittings (24, 25, 28) and (30, 31, 32) ensure a transmission of the force by a large contact surface, so as to avoid, on the soft guide tube, the wear known with the techniques of traditional binding.

Description

BohrhammerHammer drill
St nd der TechnikState of the art
Die Erfindung geht aus von einem Hammer nach dem Oberbegriff des Anspruchs 1. Aus der DE 3828309 C2 ist ein Bohrhammer bekannt, bei dem entgegen der sonst üblichen Bauweise das Führungsrohr für das Schlagwerk und die Werkzeugaufnahme zweiteilig sind. Die Verbindung beider Teile erfolgt durch Verriegelungselemente, die als Kugeln in Ausnehmungen beider Teile eingreifen, was eine hohe punktuelle Be¬ lastung der Teile mit sich bringt. Aus diesem Grund mußte das Füh¬ rungsrohr, genauso wie die Werkzeugaufnahme vergütet beziehungsweise gehärtet werden. Im übrigen erfordert die Konstruktion einen hohen baulichen Aufwand.The invention is based on a hammer according to the preamble of claim 1. From DE 3828309 C2 a rotary hammer is known in which, contrary to the otherwise conventional design, the guide tube for the striking mechanism and the tool holder are in two parts. The two parts are connected by locking elements which engage as balls in recesses in both parts, which results in a high selective loading of the parts. For this reason, the guide tube, like the tool holder, had to be tempered or hardened. Otherwise, the construction requires a high level of construction.
Vorteile der ErfindungAdvantages of the invention
Der erfindungsgemäße Schlag- oder Bohrhammer mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß die vom Schlagwerk herrührenden hohen Axialkräfte großflächiger übertragen werden. Dies ermöglicht die Verwendung eines ungehärteten Führungs¬ rohrs, wodurch Härteverzug und Nacharbeit am Führungsrohr vermieden werden. Nicht zuletzt geht mit dem geringeren Gewicht der zu härten¬ den Bauteile auch eine merkliche Entlastung der Umwelt durch weg¬ fallende Härtungsschritte einher. Die Verwendung eines federnden Profilrings und entsprechender, vor¬ zugsweise in ihrer Form angepaßter Nuten im Führungsrohr und in der Werkzeugaufnahme vermeiden Scherbeanspruchungen des Verbindungs¬ elements, so daß der Profilring nur noch auf Druck beansprucht wird und an den zu verbindenden Bauteilen keine punktuellen, sondern nur flächige Pressungen zwischen "harten" und "weichen" Bauteilen auf¬ treten. Spätestens durch Einlaufen während des Betriebs passen sich die Nuten genau der Form der Profilringe an, so daß sie mit ihrer gesamten Fläche tragen. Die erfindungsgemäße Axialverbindung hat den weiteren Vorteil, daß die Hammerhülse leicht in Steckmontage zu fer¬ tigen ist und daß ein einwandfreier Rundlauf des Werkzeughalters ge¬ geben ist.The hammer or hammer drill according to the invention with the characterizing features of claim 1 has the advantage that the high axial forces resulting from the striking mechanism are transmitted over a large area. This enables the use of an uncured guide tube, thereby avoiding delay in hardness and reworking on the guide tube. Last but not least, the lower weight of the components to be hardened is accompanied by a noticeable relief of the environment by omitting hardening steps. The use of a resilient profile ring and corresponding grooves, preferably adapted in shape, in the guide tube and in the tool holder avoid shear stresses of the connecting element, so that the profile ring is only subjected to pressure and does not punctually, but only on the components to be connected Surface pressures occur between "hard" and "soft" components. At the latest by running in during operation, the grooves adapt exactly to the shape of the profile rings, so that they support with their entire surface. The axial connection according to the invention has the further advantage that the hammer sleeve is easy to manufacture in a plug-in assembly and that the tool holder runs smoothly.
Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Bohrhammers möglich. Die Anlagefläche kann in ihrer Schräglage zur Längsachse eben oder auch konkav gewölbt sein, um sich der Außenkoritur des verwendeten Profilrings anzupassen. Der Profilring kann insbesondere kreisrunden oder auch ovalen, recht¬ eckigen oder sonstigen Querschnitt haben.Advantageous further developments and improvements of the rotary hammer specified in claim 1 are possible through the measures listed in the dependent claims. In its inclined position with respect to the longitudinal axis, the contact surface can be flat or also concavely curved in order to adapt to the external finish of the profile ring used. The profile ring can in particular have a circular or oval, rectangular or other cross section.
Besonders vorteilhaft ist es, das an der Werkzeugaufnahme erforder¬ liche Drehmoment über einen Preßsitz zu übertragen, da über den Pro¬ filring in Umfangsrichtung nur begrenzt Kräfte übertragen werden können. Weiter vorteilhaft ist ein Rastenring als Kupplungsteil für eine Sicherheitskupplung, der mittels mehrerer Walzen befestigt ist, die in vorzugsweise drei Aussparungen linienförmig anliegen. Damit ist der Rastenring bei Verschleiß leicht austauschbar. Über die Walzen ist bei leichter Fertigungsmoglichkeit eine gute Übertragung des Drehmoments zwischen dem Rastenring und der Führungshülse mög¬ lich. Zur axialen Sicherung kann vorteilhafterweise zusätzlich ein Rundring in dem Führungsrohr angebracht sein, der an einer Schräge des Rastenrings gegebenenfalls unter Vorspannung anliegt. Die ge¬ samte Konstruktion ermöglicht es, als Führungsrohr ein nahtlos ge¬ zogenes oder geschweißtes weiches Rohrstück zu verwenden, was die Fertigungskosten erheblich reduziert.It is particularly advantageous to transmit the torque required on the tool holder via a press fit, since only limited forces can be transmitted in the circumferential direction via the profile ring. Also advantageous is a detent ring as a coupling part for a safety clutch, which is fastened by means of a plurality of rollers, which preferably lie linearly in three recesses. This makes the catch ring easily replaceable when worn. A good transmission of the torque between the catch ring and the guide sleeve is possible via the rollers with easy manufacturing possibilities. For axial securing, a round ring can advantageously also be attached in the guide tube, which is on a slope of the detent ring may be under tension. The entire construction makes it possible to use a seamlessly drawn or welded soft piece of pipe as the guide tube, which considerably reduces the production costs.
Die erfindungsgemäße Konstruktion hat den weiteren Vorteil, daß die Verbindungsmittel zwischen Führungsrohr und Werkzeugaufnähme sowie Rastenring sehr platzsparend sind und eine im Vergleich zu einteili¬ gen Ausführungen ebenso dünnwandige Hammerhülse ermöglichen. Die Verbindungen benötigen also keinen zusätzlichen Platz im Gegensatz zu der Lösung gemäß der DE 38 28309 C2.The construction according to the invention has the further advantage that the connecting means between the guide tube and tool holder as well as the detent ring are very space-saving and enable a hammer sleeve which is also thin-walled in comparison to one-piece designs. The connections therefore do not require any additional space, in contrast to the solution according to DE 38 28309 C2.
Zeichnungdrawing
Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dar¬ gestellt und in der nachfolgenden Beschreibung erläutert. Figur 1 zeigt einen Längsschnitt durch den vorderen Teil eines Bohrhammers, Figur 2 zeigt in vergrößerter Darstellung eine AxialVerbindung und Figur 3 zeigt eine perspektivische Ansicht einer Hammerhülse. Figur 4 zeigt ein zweites Ausführungsbeispiel.Two exemplary embodiments of the invention are shown in the drawing and explained in the following description. Figure 1 shows a longitudinal section through the front part of a rotary hammer, Figure 2 shows an axial connection in an enlarged view and Figure 3 shows a perspective view of a hammer sleeve. Figure 4 shows a second embodiment.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Ein Bohrhammer weist ein Gehäuse 2 aus Kunststoff auf, in dem ein nicht gezeigter Motor untergebracht ist, der eine Zwischenwelle 3 antreibt. Außerdem ist in dem Gehäuse 2 ein Schlagwerk 4 unter¬ gebracht, an dessen vorderem Ende ein Werkzeughalter 5 angeordnet ist. Das Schlagwerk 4 liegt innerhalb einer dreiteiligen Hammerhülse 6, die aus einem Führungsrohr 7» einer Werkzeugaufnahme 8 mit Längs¬ achse 14 nnd einem Rastenring besteht. Das Schlagwerk 4 ist ge¬ führt in dem im Gehäuse 2 gelagerten Führungsrohr 7> das als nahtlos gezogenes oder geschweißtes ungehärtetes Rohrstück ausgebildet ist. Mit dem Führungsrohr 7 ist die im wesentlichen ebenfalls rohrförmige Werkzeugaufnahme 8 verbunden, die zum Werkzeughalter 5 gehört und in die ein nicht gezeigtes Werkzeug unmittelbar eingesteckt wird. Die Werkzeugaufnahme 8 kann innerhalb (wie in Figur 1 ) oder auch außer¬ halb an dem Führungsrohr 7 anliegen. Weiter sitzt auf dem Führungs¬ rohr 7 der Rastenring 9» der als Teil einer Sicherheitsüberrastkupp- lung 10 dient. Die Sicherheitskupplung 10 weist in bekannter Weise als Mitnahmekδrper Walzen 11 auf, die mit Rastmulden in dem gehärte¬ ten Rastenring 9 nnd mit einem Zahnrad 12 zusammenarbeiten. Das Zahnrad 12 ist gegenüber dem Führungsrohr 7 drehbar und greift in eine Verzahnung 13 der Zwischenwelle 3 ein. Die beiden Teile 9 "U-O-d. 12 der Sicherheitskupplung 10 werden durch eine Druckfeder 15, die das Überrastmoment der Kupplung bestimmt, zusammengepreßt. Die Druckfeder 15 ist in bekannter Weise mittels einer durch Rundringe 16, 17 in dem Führungsrohr 7 gehaltenen Stützscheibe 18 gesichert.A hammer drill has a housing 2 made of plastic, in which a motor, not shown, is housed, which drives an intermediate shaft 3. In addition, a striking mechanism 4 is accommodated in the housing 2, at the front end of which a tool holder 5 is arranged. The striking mechanism 4 lies within a three-part hammer sleeve 6, which consists of a guide tube 7, a tool holder 8 with a longitudinal axis 14 and a detent ring. The striking mechanism 4 is guided in the guide tube 7 > which is mounted in the housing 2 and which is designed as a seamlessly drawn or welded uncured tube piece. The essentially likewise tubular tool holder 8, which belongs to the tool holder 5 and into which a tool, not shown, is inserted directly, is connected to the guide tube 7. The tool holder 8 can rest against the guide tube 7 inside (as in FIG. 1) or outside. The detent ring 9, which serves as part of a safety snap-in coupling 10, also sits on the guide tube 7. In a known manner, the safety clutch 10 has rollers 11 as a driving body, which cooperate with locking troughs in the hardened locking ring 9 and with a gear wheel 12. The gear wheel 12 is rotatable relative to the guide tube 7 and engages in a toothing 13 of the intermediate shaft 3. The two parts 9 "UOd. 12 of the safety clutch 10 are pressed together by a compression spring 15, which determines the latching torque of the clutch. The compression spring 15 is secured in a known manner by means of a support disk 18 held in the guide tube 7 by round rings 16, 17.
Innerhalb des Führungsrohrs 7 befindet sich das Schlagwerk 4 mit einem topffδrmigen, hin- und hergehend angetriebenen Kolben 20 und einem darin befindlichen Schläger 21. Die Energie des vom dem Kolben 20 angetriebenen Schlägers 21 wird auf einen Dδpper 22 und von dort aus auf ein nicht gezeigtes Werkzeug übertragen. Der Kolben 20 ist in dem Führungsrohr 7 geführt.Within the guide tube 7 there is the striking mechanism 4 with a pot-shaped, reciprocally driven piston 20 and a striker 21 located therein. The energy of the striker 21 driven by the piston 20 is applied to a dropper 22 and from there to a striker (not shown) Transfer tool. The piston 20 is guided in the guide tube 7.
Führungsrohr 7 und Werkzeugaufnahme 8 überlappen sich in einem ge¬ wissen Bereich und sind dort mittels eines Preßsitzes miteinander verbunden. Eine sorgfältige Bearbeitung der gut zugänglichen Kon¬ taktflächen der Preßsitzverbindung gewährleistet gleichzeitig einen guten Rundlauf des Werkzeughalters. Zur insbesondere axialen Siche¬ rung der beiden Teile ist zusätzlich ein geschlitzter, federnder Profilring 24 eingelegt (vergleiche auch Figur 2). Dieser wird unter Vorspannung in eine Montageringnut 25 in der Werkzeugaufnahme 8 ein¬ gesetzt, die den Profilring 24 voll in sich aufnehmen kann. Siehe hierzu die gestrichelt gezeichnete Montagestellung 26 des Profil¬ rings. Die Montageringnut 25 läuft einseitig in einer Anlagefläche 27 aus, die um 30° - 60°, vorzugsweise 45° schräg zur Längsachse 14 geneigt ist. Bei einem Profilring 24 mit rundem Querschnitt kann die Anlagefläche auch gerundet, bzw. konkav sein, jedoch so, daß zumin¬ dest ein Druckkräfte aufnehmender Teil der Anlagefläche 27 etwa um den genannten Winkel zur Längsachse 14 geneigt ist. Das Führungsrohr 7 weist eine vorzugsweise dem jeweiligen Profil des gehärteten Pro¬ filrings 24 angepaßte Ringnut 28 auf. Der Profilring 24 hat hier einen kreisförmigen Querschnitt und die Ringnut 28 einen halbkreis¬ förmigem Querschnitt. Bei fertigmontierter Hammerhülse 6 weitet sich der Profilring 24 ans, so daß er in der Ringnut 28 formschlüssig anliegt und eine flächige Kraftübertragung erfolgen kann. Mit seiner inneren Seite liegt der Profilring an der Anlagefläche 27 an (siehe Kraftpfeil F1) .Guide tube 7 and tool holder 8 overlap in a certain area and are connected to one another there by means of a press fit. Careful machining of the easily accessible contact surfaces of the press fit connection simultaneously ensures good concentricity of the tool holder. For the axial securing of the two parts in particular, a slotted, resilient profile ring 24 is additionally inserted (see also FIG. 2). This is inserted under prestress into a mounting ring groove 25 in the tool holder 8, which can fully accommodate the profile ring 24. Please refer the assembly position 26 of the profile ring shown in dashed lines. The mounting ring groove 25 ends on one side in a contact surface 27 which is inclined at 30 ° -60 °, preferably 45 °, to the longitudinal axis 14. In the case of a profile ring 24 with a round cross-section, the contact surface can also be rounded or concave, but in such a way that at least one part of the contact surface 27 that absorbs compressive forces is inclined approximately by the aforementioned angle to the longitudinal axis 14. The guide tube 7 has an annular groove 28 which is preferably adapted to the respective profile of the hardened profile ring 24. The profile ring 24 here has a circular cross section and the annular groove 28 has a semicircular cross section. When the hammer sleeve 6 is fully assembled, the profile ring 24 widens so that it lies in a form-fitting manner in the annular groove 28 and a flat force transmission can take place. The inner side of the profile ring lies against the contact surface 27 (see force arrow F1).
Im Betrieb des Schlagwerks 5 treten insbesondere beim Übergang in den Leerlauf an der Axialverbindung hohe Momentanbelastungen in Richtung des Pfeiles F in Figur 2 auf. Aufgrund der Neigung der An¬ lagefläche 27 führt dies zu einer Druckbeanspruchung in Richtung des Pfeiles F1. Dadurch wird das weiche Führungsrohr 7 nicht hauptsäch¬ lich an der empfindlichen Kante der Ringnut 28, sondern vorwiegend weiter im Nutgrund beansprucht. Auch eine Scherbeanspruchung des Profilrings 24 wird mit dieser Bauweise vermieden.During operation of the striking mechanism 5, high instantaneous loads in the direction of the arrow F in FIG. 2 occur in particular in the transition to idling at the axial connection. Due to the inclination of the contact surface 27, this leads to a pressure load in the direction of arrow F1. As a result, the soft guide tube 7 is not primarily stressed on the sensitive edge of the annular groove 28, but predominantly further in the groove base. Shear stress on the profile ring 24 is also avoided with this design.
Der Rastenring 9 ist mit dem Führungsrohr 7 über drei längliche Wal¬ zen 30 verbunden. Die Walzen 30 liegen in dem Führungsrohr 7 in drei geradlinigen, an den Enden auslaufenden Einkerbungen 31 mit halb¬ kreisförmigen Querschnitt an (siehe Figur 3, in der die Walzen 30 weggelassen wurden). Der Rastenring 9 weist entsprechend drei ge¬ radlinige Aussparungen 3 auf. Bei der Montage werden zunächst die Walzen 30 in die Einkerbungen 31 eingelegt und anschließend der Rastenring 9 darubergeschoben. Zur axialen Fixierung des Rastenrings wird von der Gegenseite, also von hinten, ein elastischer Rundring 34 in eine Nut in dem Führungsrohr 7 eingesetzt. Der Rundring 34 liegt an einer Schräge 35 des Rastenrings 9 an. Der Rastenring 9 kann bei dieser Konstruktion durch Herausnehmen des Rundrings 34 demontiert und gegebenenfalls ausgetauscht werden.The detent ring 9 is connected to the guide tube 7 via three elongated rollers 30. The rollers 30 lie in the guide tube 7 in three rectilinear notches 31 which run out at the ends and have a semicircular cross section (see FIG. 3, in which the rollers 30 have been omitted). Correspondingly, the detent ring 9 has three straight cutouts 3. During assembly, the rollers 30 are first inserted into the notches 31 and then the Rastenring 9 pushed over it. To axially fix the detent ring, an elastic round ring 34 is inserted into a groove in the guide tube 7 from the opposite side, that is to say from the rear. The round ring 34 lies against a slope 35 of the detent ring 9. In this construction, the detent ring 9 can be dismantled by removing the round ring 34 and, if necessary, exchanged.
In einem anderen, nicht gezeigten Ausführungsbeispiel ist die Hammerhülse zweiteilig und besteht aus einer Werkzeugaufnahme und einer Führungshülse mit angeformtem Rastenring für die Drehmoment- Übertragung. Im übrigen ist der Aufbau insbesondere auch bezüglich der Axialverbindung mit dem in der Zeichnung gezeigten Ausführungs¬ beispiel gleich. Auch eine zweiteilige Ausführung hat den Vorteil, daß nur für die Werkzeugaufnahme ein hochwertiger Werkstoff verwen¬ det zu werden braucht und das Führungsrohr keiner vollständigen Wär¬ mebehandlung unterzogen werden muß. Außerdem wird die Fertigung dadurch schon erheblich vereinfacht und verbilligt. Ein weiterer Vorteil liegt darin, daß die im Bereich des Döppers gelegenen Bau¬ teile bei einer zweiteiligen wie auch schon bei einer dreiteiligen Hammerhülse entweder von vorne oder von hinten montiert werden können. Dies ist bei einer einteiligen Ausführung nicht möglich.In another embodiment, not shown, the hammer sleeve is in two parts and consists of a tool holder and a guide sleeve with an integrally formed detent ring for torque transmission. For the rest, the structure, in particular with regard to the axial connection, is the same as the exemplary embodiment shown in the drawing. A two-part design also has the advantage that a high-quality material only needs to be used for the tool holder and the guide tube does not have to be subjected to complete heat treatment. It also considerably simplifies and reduces the cost of manufacturing. A further advantage is that the components located in the area of the striker can be mounted either from the front or from the rear with a two-part as well as with a three-part hammer sleeve. This is not possible with a one-piece version.
Im zweiten Ausführungsbeispiel nach Figur 4 hat der Profilring 124 einen quadratischen Querschnitt. Die Montageringnut 125 mit Anlage¬ fläche 127 ist gegenüber dem ersten Ausführungsbeispiel unverändert. Die Montagestellung 126 des Profilrings 124 ist gestrichelt einge¬ zeichnet. Die Ringnut 128 weist schräg gegenüberliegend zu der An¬ lagefläche 127 ebenfalls eine gleichartige, ebene, geneigte Anlage¬ fläche 129 auf. Im übrigen ist die Ringnut 128 so begrenzt, daß sie den Profilring 124 nicht voll, sondern nur in Schräglage teilweise aufnehmen kann. Dies führt bei der Montage der Axialverbindung zwangsläufig zu einem erwünschten Kippen des Profilrings 124, so daß dieser, wie im ersten Ausführungsbeispiel, schräg zur Trennfuge 133 zwischen Führungsrohr 107 und Werkzeugaufnahme 108, in Richtung der Kraft F1 beansprucht wird. In gleicher Weise werden die Nuten 125 und 128 bei axialen Schlägen auf den Werkzeughalter 108 nicht hauptsächlich an ihren empfindlichen Rändern sondern weiter im Nut rund beansprucht.In the second exemplary embodiment according to FIG. 4, the profile ring 124 has a square cross section. The mounting ring groove 125 with contact surface 127 is unchanged from the first embodiment. The mounting position 126 of the profile ring 124 is shown in dashed lines. The annular groove 128 also has a similar, flat, inclined contact surface 129 lying obliquely opposite the contact surface 127. In addition, the annular groove 128 is so limited that it can not fully accommodate the profile ring 124, but only partially in an inclined position. During the assembly of the axial connection, this inevitably leads to a desired tilting of the profile ring 124, so that, as in the first exemplary embodiment, the latter is inclined to the parting line 133 between the guide tube 107 and the tool holder 108, in the direction of the force F1. In the same way, the grooves 125 and 128 are subjected to axial stresses on the tool holder 108, not mainly at their sensitive edges, but also in the groove.
Die AxialVerbindung mit dem Profilring 24/124 kann in Umkehrung der Anordnung bei den gezeigten Ausführungsbeispielen auch so gestaltet sein, daß die Montageringnut sich im äußeren Rohrteil befindet. Dann wird der Profilring unter Vorspannung in Form einer Vordehnung ein¬ gesetzt und zieht sich nach dem Zusammenfügen der Rohrteile wieder zusammen. The axial connection with the profile ring 24/124 can, in reverse of the arrangement in the exemplary embodiments shown, also be designed such that the mounting ring groove is located in the outer tube part. Then the profile ring is inserted under prestress in the form of a pre-expansion and contracts again after the pipe parts have been joined together.

Claims

Ansprüche Expectations
1. Motorisch angetriebener Hammer mit einem Gehäuse (2) und einer darin gelagerten mehrteiligen Hammerhülse (6), die mindestens ein Führungsrohr (7) und eine damit verbundene Werkzeugaufnahme (8) aufweist, die insbesondere über ein Zahnrad (12) von einem Motor drehend angetrieben ist, dadurch gekennzeichnet, daß die Werkzeug¬ aufnahme (8) an der Hammerhülse (6) mittels einer Axialverbindung befestigt ist, die einen federnden geschlitzten Profilring (24) auf¬ weist, der in seiner Montagestellung unter radialer Vorspannung vollständig in eine Montageringnut (25) vorzugsweise an der Werk¬ zeugaufnahme (8) einsetzbar ist und bei der fertig montierten Hammerhülse (6) in eine Ringnut (28) am zu verbindenden Bauteil, vorzugsweise am Führungsrohr (7)» einrastet und daß die Montage¬ ringnut (25) eine gegenüber einer Normalen zur Längsachse (14) der Werkzeugaufnahme (8) schräg gestellte Anlagefläche (27) aufweist, an der der Profilring (24) bei fertigmontierter Hammerhülse (6) an¬ liegt.1. Motor-driven hammer with a housing (2) and a multi-part hammer sleeve (6) mounted therein, which has at least one guide tube (7) and an associated tool holder (8), which rotates in particular via a gear (12) from a motor is driven, characterized in that the tool holder (8) is fastened to the hammer sleeve (6) by means of an axial connection which has a resilient, slotted profile ring (24) which, in its assembled position, is completely inserted into a mounting ring groove (radial bias) 25) can preferably be used on the tool holder (8) and, when the hammer sleeve (6) is fully assembled, engages in an annular groove (28) on the component to be connected, preferably on the guide tube (7), and that the assembly annular groove (25) has a contact surface (27) which is inclined relative to a normal to the longitudinal axis (14) of the tool holder (8), on which the profile ring (24) when the hammer sleeve (6 ) is present.
2. Hammer nach Anspruch 1, dadurch gekennzeichnet, daß die An¬ lagefläche (27) im wesentlichen eben ist und in einem Winkel von 30β - 60°, vorzugsweise 45° schräg zur Längsachse (14) der Werkzeug¬ aufnahme (8) steht. 2. Hammer according to claim 1, characterized in that the An¬ contact surface (27) is substantially flat and at an angle of 30 β - 60 °, preferably 45 ° to the longitudinal axis (14) of the tool holder (8) .
3. Hammer nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Anlagefläche (27) der Außenkontur eines Profilrings (24) mit Kreis¬ querschnitt angepaßt ist.3. Hammer according to claim 1 or 2, characterized in that the contact surface (27) of the outer contour of a profile ring (24) is adapted with a circular cross-section.
4. Hammer, insbesondere Bohrhammer, nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Werkzeugaufnahme (8) und das Führungsrohr (7) durch Preßsitz drehfest verbunden sind.4. Hammer, in particular rotary hammer, according to any one of the preceding claims, characterized in that the tool holder (8) and the guide tube (7) are rotatably connected by a press fit.
5. Hammer nach einem der vorhergehenden Ansprüche, dadurch gekenn¬ zeichnet, daß mit dem Führungsrohr (7) ein Rastenring (9) mittels mehrerer Walzen (30) verbunden ist, die in vorzugsweise drei Aus¬ sparungen (32) des Rastenrings (9) linienfδrmig anliegen.5. Hammer according to one of the preceding claims, characterized gekenn¬ characterized in that with the guide tube (7) a detent ring (9) is connected by means of several rollers (30), which preferably three recesses (32) of the detent ring (9) line-like.
6. Bohrhammer nach einem der vorhergehenden Ansprüche, dadurch ge¬ kennzeichnet, daß der Rastenring (9) axial durch einen Rundring (34) an dem Führungsrohr (7) gehalten ist und daran mit einer Schräge (35) anliegt.6. Hammer drill according to one of the preceding claims, characterized ge indicates that the detent ring (9) is held axially by a round ring (34) on the guide tube (7) and bears against it with a slope (35).
7. Bohrhammer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Verbindungselemente (24, 30) flächig an dem Führungsrohr (7) in dessen Ringnut (28) bzw. Einkerbungen (31) anliegen.7. Hammer drill according to one of the preceding claims, characterized in that the connecting elements (24, 30) rest flat on the guide tube (7) in the annular groove (28) or notches (31).
8. Bohrhammer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Rastenring (9) Teil einer Sicherheits-Über- rastkupplung (10) ist.8. Hammer drill according to one of the preceding claims, characterized in that the detent ring (9) is part of a safety snap-in coupling (10).
9. Bohrhammer nach einem der vorhergehenden Ansprüche, dadurch ge¬ kennzeichnet, daß das Führungsrohr (7) aus "weichem" ungehärtetem Stahl gefertigt ist. 9. hammer drill according to one of the preceding claims, characterized ge indicates that the guide tube (7) is made of "soft" unhardened steel.
10. Bohrhammer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Führungsrohr (7) ein nahtloses gezogenes Rohr ist.10. Hammer drill according to one of the preceding claims, characterized in that the guide tube (7) is a seamless drawn tube.
11. Bohrhammer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Führungsrohr (7) ein geschweißtes Rohr ist, 11. Hammer drill according to one of the preceding claims, characterized in that the guide tube (7) is a welded tube,
EP92914235A 1991-07-08 1992-07-06 Percussion drill Expired - Lifetime EP0552328B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4122516 1991-07-08
DE4122516 1991-07-08
DE4215288 1992-05-09
DE4215288A DE4215288A1 (en) 1991-07-08 1992-05-09 DRILLING HAMMER
PCT/DE1992/000559 WO1993001027A1 (en) 1991-07-08 1992-07-06 Percussion drill

Publications (2)

Publication Number Publication Date
EP0552328A1 true EP0552328A1 (en) 1993-07-28
EP0552328B1 EP0552328B1 (en) 1995-10-11

Family

ID=25905294

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92914235A Expired - Lifetime EP0552328B1 (en) 1991-07-08 1992-07-06 Percussion drill

Country Status (4)

Country Link
US (1) US5373905A (en)
EP (1) EP0552328B1 (en)
DE (2) DE4215288A1 (en)
WO (1) WO1993001027A1 (en)

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Also Published As

Publication number Publication date
DE4215288A1 (en) 1993-01-14
DE59203993D1 (en) 1995-11-16
US5373905A (en) 1994-12-20
EP0552328B1 (en) 1995-10-11
WO1993001027A1 (en) 1993-01-21

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