EP0474651B1 - Drill or percussion tool with coupling in the percussion drive - Google Patents

Drill or percussion tool with coupling in the percussion drive Download PDF

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Publication number
EP0474651B1
EP0474651B1 EP90906878A EP90906878A EP0474651B1 EP 0474651 B1 EP0474651 B1 EP 0474651B1 EP 90906878 A EP90906878 A EP 90906878A EP 90906878 A EP90906878 A EP 90906878A EP 0474651 B1 EP0474651 B1 EP 0474651B1
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EP
European Patent Office
Prior art keywords
coupling part
hammer
percussion
drill
control
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
EP90906878A
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German (de)
French (fr)
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EP0474651A1 (en
Inventor
Wolfgang Schmid
Jörg Faelchle
Walter Laubengaier
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0474651A1 publication Critical patent/EP0474651A1/en
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    • 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
    • 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

Definitions

  • the invention is based on a hammer drill or percussion hammer according to the preamble of claim 1.
  • a motor-driven rotary hammer is already known, the percussion mechanism of which is by means of a clutch between an intermediate shaft driven by the motor and the movement converting gear for generating the reciprocating piston movement can be switched off.
  • the clutch force is increased by a lever which is acted upon by the reaction forces of the striking mechanism.
  • the amplifying force exerted on the coupling is absorbed by a pin in the housing and a bearing of the intermediate shaft, which is supported in a special metal bearing bracket.
  • the effectiveness of the force amplification can be reduced by tolerances of the lever, the bearing pin and the bearing bracket.
  • the plastic housing can flow under very unfavorable conditions when heat is generated and the position of the pin can change.
  • a desired reduction in the contact pressure with such lever structures leads to an extension of the engagement path.
  • the hammer drill or percussion hammer according to the invention with the characterizing features of claim 1 has the advantage that both the contact pressure and the contact path for switching on the striking mechanism are reduced. This is achieved by a self-energizing clutch, which uses the motor power of the hammer to increase the clutch force.
  • the design of the hammer according to claims 5ff has the advantage that the effectiveness of the clutch force amplification is independent of reactions of non-associated components, such as housings, etc. This is achieved in that the intermediate shaft is free of clutch forces on the outside. This eliminates all tolerances originating from outside, i.e. from housing parts, levers or the like, which impair the function.
  • the plastic housing does not absorb any forces from the clutch force reinforcement.
  • the measures of claims 13 to 15 relate to a further exemplary embodiment which additionally has a braking device for faster disengagement.
  • FIG. 1 shows a longitudinal section through the front part of a rotary hammer in a first embodiment
  • FIG. 2 shows a longitudinal section through a hammer mechanism of a rotary hammer in a second exemplary embodiment.
  • the rotary hammer 2 is surrounded by a housing 3 made of plastic and has a tool holder 4 at the front into which a tool 5 can be inserted. Inside the housing 3 there is a motor, not shown, of which only the motor pinion 7 is visible. The pinion 7 meshes with a gear wheel 9 which is fixedly connected to a shaft 8.
  • the shaft 8, also referred to as an intermediate shaft, is mounted on both sides in bearings 10, 11 in the housing 3. Following the gear 9, a freely rotating but axially fixed coupling part 12 sits on the intermediate shaft, on which a swash plate is arranged as the drive member 13 of a movement conversion gear 14.
  • the design of the swash plate gear 14 and the hammer mechanism 15 driven thereby is described in detail in DE-A-35 06 695 (US-A-4 719 976).
  • the coupling part 12 has on the side facing away from the gear 9 an inner cone 17 with a conical surface standing at an acute angle to the shaft axis.
  • the coupling part 12 is axially fixed to the intermediate shaft 8 with a snap ring 18.
  • the outer cone 21 has a conical outer surface corresponding to the inner cone 17 and can be non-positively coupled with it.
  • the coupling part 20 has a radial annular stop surface 22 which points away from the fixed coupling part 12 and which is provided for engaging an actuating element for the coupling.
  • the coupling part 20 also has a drum-shaped control sleeve 23, which surrounds the shaft 8 and has an essentially helical control surface 24 on its end face facing away from the cone surface 21.
  • the slope of the control surface 24 is not self-locking.
  • the control surface has a jump with a short axially directed section 25.
  • a separating spring 26 acts on the coupling part 20 in the sense of an opening of the coupling and is supported against the snap ring 18.
  • control surface 24 there is a corresponding control surface 27 of a control disk 28, which is fixedly or also integrally connected to the shaft 8.
  • the control surface 27 also has a jump with a short axially directed section 29.
  • the control disk 28 is connected in one piece to a spur gear 30 which engages in a gear 31 on the tool spindle 32 of the motor hammer and drives it permanently rotating.
  • an axial bearing 33 provided with rolling elements is arranged on the main spindle and can be pressed against the stop surface 22 of the coupling part 20.
  • the main spindle 32 is connected to the tool 5 via the tool holder 4 and is axially displaceable within limits.
  • the striking mechanism 15 is accommodated within the main spindle.
  • the motor is switched on, which drives the tool spindle via the gear wheels 7, 9, 30 and 31.
  • the coupling part 20 is urged by the spring 26 against the control disk 28, so that the control surfaces 24 and 27 are free from one another and sections 25 and 29 face each other. In this position, the coupling part 20 is rotatably carried along by the control disk 28 and does not move axially relative to the control disk 28.
  • the coupling part 20 is non-positively driven by the control disk 28 via the control surfaces 24 and 27 and at the same time is pressed axially against the force of the spring 26 against the coupling part 12.
  • the coupling part 20 is wedged between the fixed coupling part 12 and the control disk 28, which results in a self-amplification of the coupling force.
  • the coupling part 120 is rotatably supported in a needle bearing 140 and an axial bearing 141 on a control sleeve 123.
  • the coupling part 120 carries a lug 142 which, when the coupling is disengaged, can interact with an axially fixed brake plate 143.
  • the control sleeve 123 has in its inner bore 119 a control curve 124 in the form of a helical groove.
  • a corresponding groove is arranged as a cam 127 in the shaft 108.
  • Balls 144 are held in the grooves 124, 127 so that a ball screw is formed.
  • a pressure bracket 145 bears against the end face 122 of the control sleeve 123 and is connected via an axial bearing 133 to an axially displaceable tool spindle 132.
  • a gear 131 which meshes with a spur gear 130 on the shaft 108, is fastened on the tool spindle 132.
  • the function of the clutch 112/120 in the second embodiment corresponds to that of the first embodiment.
  • the pressure lever 145 presses against the control sleeve 123 and moves it in the direction of the coupling part 112.
  • the gear connection 123, 124, 127, 144 then takes effect the coupling part 112 in a position as shown in Figure 2.
  • the control sleeve 123 is braked with respect to the shaft 108 and moved in the direction of the fixed coupling part 112 because of the differential speed as a result of the ball screw 124, 127, 144.
  • the pressure lever 145 When the tool is lifted off the rock, the pressure lever 145 is also lifted off the end face 122 and the separating spring 126 and the gas forces of the striking mechanism 115, which exert tensile forces on the drive member in phases, release the clutch 112/120.
  • the clutch When the clutch is released, only the control sleeve 123 rotates with the shaft 108; the coupling part 120 rotates via the bearings 140, 141 relative to the control sleeve 123 and faces the striking mechanism 115. Switching off the striking mechanism is facilitated by the brake plate 143 on which the coupling part 120 is braked by stripes with its nose 142.
  • the invention is not limited to the exemplary embodiments. Rather, the individual features from the exemplary embodiments can also be combined with one another in another way or with features from the cited prior art, such as the arrangement of a needle bearing on the intermediate shaft for mounting the coupling part 12.
  • the clutch 12/20 or 112/120 can also be used instead of purely frictionally positive. B. with more or less flat claws in the axial direction.
  • the separating spring 26 can also be integrated in one of the coupling parts 12, 20, e.g. such that it consists of spring steel or has spring steel inserts.
  • the invention is also suitable for pure impact hammers. For this, e.g. only the gears 30 and 31 or 130 and 131 to be omitted.

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

Abstract

A drill or percussion tool. In a percussion tool with a pneumatic percussion gear which may be switched on by pressing the percussion tool against the point to be processed, the effectiveness of the switching device is to be improved and the pressure to be applied by the operator is to be reduced. This is achieved by means of a self-reinforcing coupling (12/20), the coupling force of which is provided mainly by the intermediate shaft (8) via a control disc (28). Control surfaces (27) on the control disc (28 and 24) on the movable coupling component (20) convert the rotary movement into an axial coupling force.

Description

Die Erfindung geht aus von einem Bohr- oder Schlaghammer nach der Gattung des Anspruchs 1. Aus der DE-A-35 06 695 (= US-A-4 719 976) ist bereits ein motorisch angetriebener Bohrhammer bekannt, dessen Schlagwerk mittels einer Kupplung zwischen einer vom Motor angetriebenen Zwischenwelle und dem Bewegungswandlungsgetriebe zur Erzeugung der hin- und hergehenden Kolbenbewegung abschaltbar ist. Die Kupplungskraft wird dabei von einem Hebel verstärkt, der von den Reaktionskräften des Schlagwerks beaufschlagt ist. Die auf die Kupplung ausgeübte Verstärkungskraft wird dabei von einem Stift im Gehäuse und einem Lager der Zwischenwelle aufgenommen, das in einer besonderen Lagerbrücke aus Metall abgestützt ist. Die Wirksamkeit der Kraftverstärkung kann durch Toleranzen des Hebels, des Lagerstifts und der Lagerbrücke vermindert werden. Im Betrieb kann es unter sehr ungünstigen Bedingungen bei Hitzeentwicklung zum Fließen des Kunststoffgehäuses und damit zu einer Lageveränderung des Stiftes kommen. Außerdem führt eine erwünschte Verringerung der Anpreßkraft bei derartigen Hebelkonstruktionen zu einer Verlängerung des Einrückweges.The invention is based on a hammer drill or percussion hammer according to the preamble of claim 1. From DE-A-35 06 695 (= US-A-4 719 976) a motor-driven rotary hammer is already known, the percussion mechanism of which is by means of a clutch between an intermediate shaft driven by the motor and the movement converting gear for generating the reciprocating piston movement can be switched off. The clutch force is increased by a lever which is acted upon by the reaction forces of the striking mechanism. The amplifying force exerted on the coupling is absorbed by a pin in the housing and a bearing of the intermediate shaft, which is supported in a special metal bearing bracket. The effectiveness of the force amplification can be reduced by tolerances of the lever, the bearing pin and the bearing bracket. During operation, the plastic housing can flow under very unfavorable conditions when heat is generated and the position of the pin can change. In addition, a desired reduction in the contact pressure with such lever structures leads to an extension of the engagement path.

Der erfindungsgemäße Bohr- oder Schlaghammer mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß sowohl Anpreßkraft als auch Anpreßweg zum Einschalten des Schlagwerks verringert werden. Dies wird durch eine selbstverstärkende Kupplung erreicht, die zur Erhöhung der Kupplungskraft die Motorkraft des Hammers ausnutzt.The hammer drill or percussion hammer according to the invention with the characterizing features of claim 1 has the advantage that both the contact pressure and the contact path for switching on the striking mechanism are reduced. This is achieved by a self-energizing clutch, which uses the motor power of the hammer to increase the clutch force.

Durch die in den Unteransprüchen 2ff aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des in Anspruch 1 angegebenen Hammers möglich. Getriebeverbindungen mit in Axialrichtung schräg verlaufenden Steuerflächen- oder kurven ermöglichen eine Umwandlung der Drehbewegung der vom Motor angetriebenen Welle in eine Axialverschiebung einer Steuerhülse, solange diese eine Differenzdrehzahl zu der Welle aufweist. Das Merkmal in Anspruch 3 ermöglicht ein gezieltes Einkuppeln der Kupplung dann, wenn das Schlagwerk tatsächlich gebraucht wird.Advantageous further developments and improvements of the hammer specified in claim 1 are possible through the measures listed in subclaims 2ff. Gearbox connections with control surfaces or curves that run obliquely in the axial direction make it possible to convert the rotary movement of the shaft driven by the motor into an axial displacement of a control sleeve, as long as it has a differential speed to the shaft. The feature in claim 3 enables a targeted engagement of the clutch when the striking mechanism is actually needed.

Die Ausbildung des Hammers nach den Ansprüchen 5ff hat den Vorteil, daß die Wirksamkeit der Kupplungskraftverstärkung unabhängig von Rückwirkungen nicht zugehöriger Bauteile, wie Gehäuse usw. ist. Dies wird dadurch erreicht, daß die Zwischenwelle nach außen hin frei von Kupplungskräften ist. Damit entfallen alle von außerhalb, also von Gehäuseteilen, Hebeln oder dgl. herrührenden Toleranzen, die die Funktion beeinträchtigen. Das Kunststoffgehäuse nimmt keinerlei Kräfte aus der Kupplungskraftverstärkung auf. Die Maßnahmen der Ansprüche 13 bis 15 betreffen ein weiter Ausführungsbeispiel, das zum schnelleren Auskuppeln zusätzlich eine Bremseinrichtung aufweist.The design of the hammer according to claims 5ff has the advantage that the effectiveness of the clutch force amplification is independent of reactions of non-associated components, such as housings, etc. This is achieved in that the intermediate shaft is free of clutch forces on the outside. This eliminates all tolerances originating from outside, i.e. from housing parts, levers or the like, which impair the function. The plastic housing does not absorb any forces from the clutch force reinforcement. The measures of claims 13 to 15 relate to a further exemplary embodiment which additionally has a braking device for faster disengagement.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Figur 1 zeigt in einem ersten Ausführungsbeispiel einen Längsschnitt durch den vorderen Teil eines Bohrhammers, Figur 2 zeigt in einem zweiten Ausführungsbeispiel einen Längsschnitt durch ein Schlagwerk eines Bohrhammers.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. FIG. 1 shows a longitudinal section through the front part of a rotary hammer in a first embodiment, FIG. 2 shows a longitudinal section through a hammer mechanism of a rotary hammer in a second exemplary embodiment.

Der Bohrhammer 2 ist von einem Gehäuse 3 aus Kunststoff umgeben und weist vorne eine Werkzeughalterung 4 auf, in die ein Werkzeug 5 einsetzbar ist. Innerhalb des Gehäuses 3 befindet sich ein nicht gezeigte Motor, von dem nur das Mototrritzel 7 sichtbar ist. Das Ritzel 7 kämmt mit einem fest mit einer Welle 8 verbundenen Zahnrad 9. Die auch als Zwischenwelle bezeichnete Welle 8 ist beidseitig in Lagern 10,11 in dem Gehäuse 3 gelagert. Im Anschluß an das Zahnrad 9 sitzt auf der Zwischenwelle frei drehbar aber axial fest ein Kupplungsteil 12, auf dem als Antriebsglied 13 eines Bewegungswandlungsgetriebes 14 eine Taumelscheibe angeordnet ist. Die Ausbildung des Taumelscheiben-Getriebes 14 und des davon angetriebenen Schlagwerks 15 ist in der DE-A-35 06 695 (US-A-4 719 976) ausführlich beschrieben.The rotary hammer 2 is surrounded by a housing 3 made of plastic and has a tool holder 4 at the front into which a tool 5 can be inserted. Inside the housing 3 there is a motor, not shown, of which only the motor pinion 7 is visible. The pinion 7 meshes with a gear wheel 9 which is fixedly connected to a shaft 8. The shaft 8, also referred to as an intermediate shaft, is mounted on both sides in bearings 10, 11 in the housing 3. Following the gear 9, a freely rotating but axially fixed coupling part 12 sits on the intermediate shaft, on which a swash plate is arranged as the drive member 13 of a movement conversion gear 14. The design of the swash plate gear 14 and the hammer mechanism 15 driven thereby is described in detail in DE-A-35 06 695 (US-A-4 719 976).

Das Kupplungsteil 12 hat auf der dem Zahnrad 9 abgekehrten Seite einen Innenkonus 17 mit einer in spitzem Winkel zur Wellenachse stehenden Kegelmantelfläche. Das Kupplungsteil 12 ist mit einem Sprengring 18 an der Zwischenwelle 8 axial fixiert. Mit dem Kupplungsteil 12 ist ein auf der Welle 8 drehbares und axial verschiebbares Kupplungsteil 20 mit Außenkonus 21 kuppelbar. Der Außenkonus 21 weist eine dem Innenkonus 17 entsprechende Kegelmantelfläche auf und ist mit diesem kraftschlüssig kuppelbar. Das Kupplungsteil 20 hat eine von dem festen Kupplungsteil 12 wegweisende, radiale ringförmige Anschlagfläche 22, die zum Angriff eines Betätigungsgliedes für die Kupplung vorgesehen ist.The coupling part 12 has on the side facing away from the gear 9 an inner cone 17 with a conical surface standing at an acute angle to the shaft axis. The coupling part 12 is axially fixed to the intermediate shaft 8 with a snap ring 18. A coupling part 20 with an outer cone 21, which is rotatable and axially displaceable on the shaft 8, can be coupled to the coupling part 12. The outer cone 21 has a conical outer surface corresponding to the inner cone 17 and can be non-positively coupled with it. The coupling part 20 has a radial annular stop surface 22 which points away from the fixed coupling part 12 and which is provided for engaging an actuating element for the coupling.

Das Kupplungsteil 20 weist weiter eine trommelförmige, die Welle 8 umgebende Steuerhülse 23 auf, die an ihrer der Konusfläche 21 abgewandten Stirnseite eine im wesentlichen schraubenförmige Steuerfläche 24 hat. Die Steigung der Steuerfläche 24 ist nicht selbsthemmend. Die Steuerfläche weist einen Sprung mit einem kurzem axial gerichteten Abschnitt 25 auf. An dem Kupplungteil 20 greift eine im Sinne einer Öffnung der Kupplung wirkende Trennfeder 26 an, die gegen den Sprengring 18 abgestützt ist.The coupling part 20 also has a drum-shaped control sleeve 23, which surrounds the shaft 8 and has an essentially helical control surface 24 on its end face facing away from the cone surface 21. The slope of the control surface 24 is not self-locking. The control surface has a jump with a short axially directed section 25. A separating spring 26 acts on the coupling part 20 in the sense of an opening of the coupling and is supported against the snap ring 18.

An der Steuerfläche 24 liegt eine korrespondierende Steuerfläche 27 einer Steuerscheibe 28, fest oder auch einstückig mit der Welle 8 verbunden ist. Die Steuerfläche 27 weist ebenfalls einen Sprung mit kurzem axial gerichteten Abschnitt 29 auf. Die Steuerscheibe 28 ist einstückig mit einem Stirnrad 30 verbunden, das in ein Zahnrad 31 an der Werkzeugspindel 32 des Motorhammers eingreift und diese permanent drehend antreibt. Neben dem Zahnrad 31 ist an der Hauptspindel ein mit Wälzkörpern versehenes Axiallager 33 angeordnet, das gegen die Anschlagfläche 22 des Kupplungsteils 20 preßbar ist. Die Hauptspindel 32 ist über die Werkzeughalterung 4 mit dem Werkzeug 5 verbunden und axial in Grenzen verschieblich. Innerhalb der Hauptspindel ist das Schlagwerk 15 untergebracht.On the control surface 24 there is a corresponding control surface 27 of a control disk 28, which is fixedly or also integrally connected to the shaft 8. The control surface 27 also has a jump with a short axially directed section 29. The control disk 28 is connected in one piece to a spur gear 30 which engages in a gear 31 on the tool spindle 32 of the motor hammer and drives it permanently rotating. In addition to the gear 31, an axial bearing 33 provided with rolling elements is arranged on the main spindle and can be pressed against the stop surface 22 of the coupling part 20. The main spindle 32 is connected to the tool 5 via the tool holder 4 and is axially displaceable within limits. The striking mechanism 15 is accommodated within the main spindle.

Zu Beginn eines Bohrvorganges wird der Motor eingeschaltet, der über die Zahnräder 7, 9, 30 und 31 die Werkzeugspindel antreibt. Das Kupplungsteil 20 wird von der Feder 26 gegen die Steuerscheibe 28 gedrängt, so daß die Steuerflächen 24 und 27 spaltfrei aneinander und die Abschnitte 25 und 29 einander gegenüber liegen. In dieser Stellung wird das Kupplungsteil 20 von der Steuerscheibe 28 drehend mitgenommen und verschiebt sich axial nicht gegenüber der Steuerscheibe 28.At the beginning of a drilling process, the motor is switched on, which drives the tool spindle via the gear wheels 7, 9, 30 and 31. The coupling part 20 is urged by the spring 26 against the control disk 28, so that the control surfaces 24 and 27 are free from one another and sections 25 and 29 face each other. In this position, the coupling part 20 is rotatably carried along by the control disk 28 and does not move axially relative to the control disk 28.

Sobald das Werkzeug 5 gegen die Bearbeitungsstelle gedrückt wird, verschiebt es die Werkzeugspindel 32 entsprechend ihrem Axialspiel nach innen. Dabei drängt das Axiallager 33 das verschiebliche Kupplungsteil 20 gegen das feste Kupplungsteil 12. Gleichzeitig entsteht ein Spalt zwischen den Steuerflachen 24 und 27. Sobald dieser Spalt breiter als die Länge der Axialabschnitte 25 bzw. 29 wird und die Konusflächen 17 und 21 sich berühren, wird das Kupplungsteil 20 von dem stillstehenden Kupplungsteil 12 abgebremst und die Getriebeverbindung 23, 24, 27, 28 wird zum Einrücken der Kupplung und zur Verstärkung der Kupplungskraft wirksam. Dabei verdrehen sich die Teile 20 und 28 gegeneinander, sodaß nun die über die Abschnitte 25 und 29 axial hinausstehenden Teile der Steuerflächen 24 und 27 einander berühren, wie dies in Figur 1 dargestellt ist. Das Kupplungsteil 20 wird kraftschlüssig über die Steuerflächen 24 und 27 von der Steuerscheibe 28 drehend angetrieben und gleichzeitig entgegen der Kraft der Feder 26 axial gegen das Kupplungsteil 12 gepreßt. Dabei verkeilt sich das Kupplungsteil 20 zwischen dem festen Kupplungsteil 12 und der Steuerscheibe 28, womit eine Selbstverstärkung der Kupplungskraft eintritt. Bei geschlossener Kupplung 12, 20 wird die Drehbewegung der Zwischenwelle 8 über das Stirnrad 30 und das Kupplungsteil 20 auf das zum Taumelgetriebe 14 gehörige Kupplungsteil 12 übertragen und das Schlagwerk 15 in Gang gesetzt.As soon as the tool 5 is pressed against the machining point, it moves the tool spindle 32 inwards in accordance with its axial play. The axial bearing 33 pushes the displaceable coupling part 20 against the fixed coupling part 12. At the same time, a gap is formed between the control surfaces 24 and 27. As soon as this gap becomes wider than the length of the axial sections 25 and 29 and the conical surfaces 17 and 21 touch the clutch part 20 is braked by the stationary clutch part 12 and the gear connection 23, 24, 27, 28 is effective for engaging the clutch and for increasing the clutch force. The parts 20 and 28 rotate against each other, so that the parts of the control surfaces 24 and 27 projecting axially beyond the sections 25 and 29 touch each other, as shown in FIG. The coupling part 20 is non-positively driven by the control disk 28 via the control surfaces 24 and 27 and at the same time is pressed axially against the force of the spring 26 against the coupling part 12. The coupling part 20 is wedged between the fixed coupling part 12 and the control disk 28, which results in a self-amplification of the coupling force. When the clutch 12, 20 is closed, the rotary movement of the intermediate shaft 8 is transmitted via the spur gear 30 and the clutch part 20 to the clutch part 12 belonging to the wobble mechanism 14 and the striking mechanism 15 is started.

Beim Abheben des Werkzeugs 5 von der Bearbeitungsstelle entfällt der Andruck des Axiallagers 33 auf das Kupplungsteil 12. Wenn sich nun das Schlagwerk 15 in der Schubphase befindet, also nicht von der Zwischenwelle 8 aktiv angetrieben wird, sondern beim Rückhub seinerseits kurzzeitig die Zwischenwelle treibt, fällt kurzzeitig auch die Selbstverstärkungswirkung der Steuerflächen 24 und 27 weg. In diesem Moment reicht die Kraft der Feder 26, die Kupplungsteile 12 und 20 auseinanderzutreiben und damit die Kupplung zu lösen, was zu dem erwünschten Stillstand des Schlagwerks 15 führt.When the tool 5 is lifted from the machining point, the thrust of the axial bearing 33 on the coupling part 12 is eliminated. If the striking mechanism 15 is now in the overrun phase, that is to say it is not actively driven by the intermediate shaft 8, but instead on the return stroke drives the intermediate shaft for a short time, the self-reinforcing effect of the control surfaces 24 and 27 also ceases for a short time. At this moment, the force of the spring 26 is sufficient to drive the coupling parts 12 and 20 apart and thus to release the coupling, which leads to the desired stoppage of the striking mechanism 15.

Bei dem in Figur 2 gezeigten Ausführungsbeispiel sind Teile, die denen im ersten Ausführungsbeispiel entsprechen, mit um 100 erhöhten Bezugsziffern versehen. Die Drehung des Motorritzels 107 wird auf die Welle 108 über ein fest mit dieser verbundenes, zum Beispiel aufgeschweißtes Zahnrad 109 übertragen. Die Welle 108 ist in zwei Lagern 110 und 111 parallel zur Achse des Motorritzel 107 gelagert. Das Zahnrad 109 bildet gleichzeitig ein axial feststehendes Kupplungsteil 112 mit einem als Kupplungsfläche dienenden Innenkonus 117. Mit dem Innenkonus 117 wirkt ein Außenkonus 121 an einem axial beweglichen Kupplungsteil 120 zusammen. An dem Kupplungsteil 120 ist ein Antriebsglied 113 des Bewegungswandlungsgetriebes 114 angeordnet, mit dem das Schlagwerk 115 angetrieben wird. Das Kupplungsteil 120 ist drehbar in einem Nadellager 140 und einem Axiallager 141 auf einer Steuerhülse 123 gelagert. Das Kupplungsteil 120 trägt eine Nase 142 die in ausgekuppeltem Zustand der Kupplung mit einem axial feststehenden Bremsblech 143 zusammenwirken kann.In the exemplary embodiment shown in FIG. 2, parts which correspond to those in the first exemplary embodiment are provided with reference numerals increased by 100. The rotation of the motor pinion 107 is transmitted to the shaft 108 via a gearwheel 109 which is firmly connected to it, for example welded on. The shaft 108 is supported in two bearings 110 and 111 parallel to the axis of the motor pinion 107. The gearwheel 109 simultaneously forms an axially stationary coupling part 112 with an inner cone 117 serving as a coupling surface. The inner cone 117 cooperates with an outer cone 121 on an axially movable coupling part 120. On the coupling part 120, a drive member 113 of the motion converting gear 114 is arranged, with which the striking mechanism 115 is driven. The coupling part 120 is rotatably supported in a needle bearing 140 and an axial bearing 141 on a control sleeve 123. The coupling part 120 carries a lug 142 which, when the coupling is disengaged, can interact with an axially fixed brake plate 143.

Die Steuerhülse 123 weist in ihrer inneren Bohrung 119 eine Steuerkurve 124 in Form einer schraubenlinienförmigen Rille auf. Eine dazu korrespondierende Rille ist als Steuerkurve 127 in der Welle 108 angeordnet. In den Rillen 124, 127 sind Kugeln 144 gehalten so daß sich ein Kugelgewinde bildet. An der Stirnfläche 122 der Steuerhülse 123 liegt ein Andruckbügel 145 an, der über ein Axiallager 133 mit einer axial verschieblichen Werkzeugspindel 132 in Verbindung steht. Auf der Werkzeugspindel 132 ist ein Zahnrad 131 befestigt, das mit einem Stirnrad 130 auf der Welle 108 kämmt.The control sleeve 123 has in its inner bore 119 a control curve 124 in the form of a helical groove. A corresponding groove is arranged as a cam 127 in the shaft 108. Balls 144 are held in the grooves 124, 127 so that a ball screw is formed. A pressure bracket 145 bears against the end face 122 of the control sleeve 123 and is connected via an axial bearing 133 to an axially displaceable tool spindle 132. A gear 131, which meshes with a spur gear 130 on the shaft 108, is fastened on the tool spindle 132.

Die Funktion der Kupplung 112/120 im zweiten Ausführungsbeispiel entspricht der des ersten Ausführungsbeispiels. Sobald die Werkzeugspindel 132 durch Andruck eines Werkzeugs gegen eine Bearbeitungsstelle entsprechend ihrem Axialspiel nach innen verschoben wird, drückt der Andruckhebel 145 gegen die Steuerhülse 123 und verschiebt sie in Richtung auf das Kupplungsteil 112. Unter Wirksamwerden der Getriebeverbindung 123, 124, 127, 144 gelangt dann das Kupplungsteil 112 in eine Stellung wie dies in Figur 2 gezeigt ist. Dabei wird die Steuerhülse 123 gegenüber der Welle 108 abgebremst und wegen der Differenzdrehzahl in Folge des Kugelgewindes 124, 127, 144 in Richtung auf das feststehende Kupplungsteil 112 bewegt.The function of the clutch 112/120 in the second embodiment corresponds to that of the first embodiment. As soon as the tool spindle 132 is moved inwards by pressing a tool against a machining point in accordance with its axial play, the pressure lever 145 presses against the control sleeve 123 and moves it in the direction of the coupling part 112. The gear connection 123, 124, 127, 144 then takes effect the coupling part 112 in a position as shown in Figure 2. The control sleeve 123 is braked with respect to the shaft 108 and moved in the direction of the fixed coupling part 112 because of the differential speed as a result of the ball screw 124, 127, 144.

Beim Abheben des Werkzeugs vom Gestein wird auch der Andrückhebel 145 von der Stirnfläche 122 abgehoben und die Trennfeder 126 sowie die Gaskräfte des Schlagwerks 115 die phasenweise Zugkräfte auf das Antriebsglied ausüben, führen zu einem Lösen der Kupplung 112/120. Bei gelöster Kupplung dreht sich nur noch die Steuerhülse 123 mit der Welle 108 mit; das Kupplungsteil 120 dreht sich über die Lager 140, 141 relativ zur Steuerhülse 123 und steht gegenüber dem Schlagwerk 115. Das Abschalten des Schlagwerks wird erleichtert durch das Bremsblech 143 an dem das Kupplungsteil 120 durch Streifen mit seiner Nase 142 abgebremst wird.When the tool is lifted off the rock, the pressure lever 145 is also lifted off the end face 122 and the separating spring 126 and the gas forces of the striking mechanism 115, which exert tensile forces on the drive member in phases, release the clutch 112/120. When the clutch is released, only the control sleeve 123 rotates with the shaft 108; the coupling part 120 rotates via the bearings 140, 141 relative to the control sleeve 123 and faces the striking mechanism 115. Switching off the striking mechanism is facilitated by the brake plate 143 on which the coupling part 120 is braked by stripes with its nose 142.

Die Erfindung beschränkt sich nicht auf die Ausführungsbeispiele. Vielmehr sind die einzelnen Merkmale aus den Ausführungsbeispielen auch in anderer Weise miteinander oder mit Merkmalen aus dem zitierten Stand der Technik kombinierbar, wie z.B. die Anordnung eines Nadellagers auf der Zwischenwelle zur Lagerung des Kupplungsteils 12.The invention is not limited to the exemplary embodiments. Rather, the individual features from the exemplary embodiments can also be combined with one another in another way or with features from the cited prior art, such as the arrangement of a needle bearing on the intermediate shaft for mounting the coupling part 12.

Die Kupplung 12/20 bzw. 112/120 kann auch statt rein kraftschlüssig formschlüssig z. B. mit mehr oder weniger flachen Klauen in Axialrichtung ausgebildet werden.The clutch 12/20 or 112/120 can also be used instead of purely frictionally positive. B. with more or less flat claws in the axial direction.

Die Trennfeder 26 kann auch in eines der Kupplungsteile 12, 20 integriert sein, z.B. derart, daß dieses aus Federstahl besteht oder Federstahleinlagen aufweist.The separating spring 26 can also be integrated in one of the coupling parts 12, 20, e.g. such that it consists of spring steel or has spring steel inserts.

Die Erfindung ist auch für reine Schlaghämmer geeignet. Dazu brauchten z.B. nur die Zahnräder 30 und 31 bzw. 130 und 131 fortgelassen zu werden.The invention is also suitable for pure impact hammers. For this, e.g. only the gears 30 and 31 or 130 and 131 to be omitted.

Claims (15)

  1. Hammer drill or percussion hammer (2) comprising a tool spindle (32) and a preferably pneumatic percussion mechanism which is accommodated therein and which can be put into action by means of a releasable coupling (20, 12) arranged between the motor and a movement transforming transmission mechanism (14) for the production of a reciprocating piston movement and having two coupling parts (12, 20) which are held apart by a separating spring (26) and of which one (12) is arranged axially fast and the other coupling part (20) axially displaceably on a shaft (8) driven by the motor, for rotation relative to said shaft (8), characterized in that the axially displaceable coupling part (20, 120) is connected to the shaft (8, 108) by means of a transmission connection (23, 24, 27, 28; 123, 124, 127, 144) which transmits parts of the torque of the shaft (8, 108) in the form of an axially directed closing force to the coupling part (20, 120).
  2. Hammer drill or percussion hammer according to Claim 1, characterized in that a control surface (27, 127) extending obliquely in the axial direction is made fast to the shaft (8, 108) and cooperates with a corresponding, likewise obliquely extending control surface (24, 124) provided on a control sleeve (23, 123) and connected to the axially displaceable coupling part (20, 120), and the coupling (12/20, 112/120) can be brought into engagement by helical displacement of the control sleeve (23, 123) along the control cams (24, 27, 124, 127).
  3. Hammer drill or percussion hammer according to Claim 2, characterized in that the displaceable control sleeve (23, 123) can be moved in the closing direction by the axially displaceable tool spindle (32, 132) of the drill or hammer.
  4. Hammer drill or percussion hammer according to Claim 3, characterized in that a friction-reducing thrust bearing (33, 133) is arranged between the tool spindle (32, 132) and the control sleeve (23, 123).
  5. Hammer drill or percussion hammer according to one of the preceding claims, characterized in that the axially fixed coupling part (12) is rotatable relative to the shaft (8) and the control surface (27) is arranged on a control disc (28).
  6. Hammer drill or percussion hammer according to one of the preceding claims, characterized in that by means of the rotation of the axially displaceable coupling part (20) relative to the control disc (28) the coupling part (20) comes into operative contact both with the axially fast coupling part (12) and with the control disc (28) for the transmission of a torque.
  7. Hammer drill or percussion hammer according to one of the preceding claims, characterized in that the displaceable coupling part (20) is pressed against the control surface (24) by the action of the separating spring (26).
  8. Hammer drill or percussion hammer according to one of the preceding claims, characterized in that the axially fast coupling part (12) is arranged on the drive member (13) of the movement transforming transmission mechanism (14).
  9. Hammer drill or percussion hammer according to one of the preceding claims, characterized in that the control disc (28) is connected to a spur gear for the rotational driving of the tool spindle (32) of the drill or hammer.
  10. Hammer drill or percussion hammer according to one of the preceding claims, characterized in that the control surfaces (24, 27) each have a break having an axially extending portion (25, 29) for rotational driving, said portions lying opposite one another when the coupling (12, 20) is disengaged.
  11. Hammer drill or percussion hammer according to one of the preceding claims, characterized in that between the coupling parts (12, 20) a spring (26) forcing them apart is arranged.
  12. Hammer drill or percussion hammer according to one of Claims 1 to 10, characterized in that one of the coupling parts (12, 20) is resilient in the axial direction or has resilient regions which develop an opening force when the coupling is closed.
  13. Hammer drill or percussion hammer according to one of Claims 1 to 4, in which the axially fixed coupling part is also made radially fast to the shaft, characterized in that the axially displaceable coupling part (120) is rotatable relative to the control sleeve (123).
  14. Hammer drill or percussion hammer according to Claim 13, characterized in that the shaft (108) and the control sleeve (123) each have spiral grooves as control cams (124, 127), in which balls (144) are held.
  15. Hammer drill or percussion hammer according to Claim 13 or 14, characterized by a brake device having a fixed brake plate (143) against which the coupling part (120) comes to bear and is braked in the uncoupled axial position.
EP90906878A 1989-05-31 1990-05-12 Drill or percussion tool with coupling in the percussion drive Expired - Lifetime EP0474651B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE3917644 1989-05-31
DE3917644 1989-05-31
DE3931329 1989-09-20
DE3931329A DE3931329C1 (en) 1989-05-31 1989-09-20
PCT/DE1990/000341 WO1990014929A1 (en) 1989-05-31 1990-05-12 Drill or percussion tool with coupling in the percussion drive

Publications (2)

Publication Number Publication Date
EP0474651A1 EP0474651A1 (en) 1992-03-18
EP0474651B1 true EP0474651B1 (en) 1994-08-24

Family

ID=25881420

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90906878A Expired - Lifetime EP0474651B1 (en) 1989-05-31 1990-05-12 Drill or percussion tool with coupling in the percussion drive

Country Status (6)

Country Link
US (1) US5277259A (en)
EP (1) EP0474651B1 (en)
JP (1) JP2930711B2 (en)
BR (1) BR9007403A (en)
DE (2) DE3931329C1 (en)
WO (1) WO1990014929A1 (en)

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Also Published As

Publication number Publication date
JPH04506036A (en) 1992-10-22
DE3931329C1 (en) 1990-06-28
BR9007403A (en) 1992-06-16
WO1990014929A1 (en) 1990-12-13
DE59006913D1 (en) 1994-09-29
EP0474651A1 (en) 1992-03-18
US5277259A (en) 1994-01-11
JP2930711B2 (en) 1999-08-03

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