EP1307313B2 - Hand-operated machine tool - Google Patents

Hand-operated machine tool Download PDF

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Publication number
EP1307313B2
EP1307313B2 EP01943165A EP01943165A EP1307313B2 EP 1307313 B2 EP1307313 B2 EP 1307313B2 EP 01943165 A EP01943165 A EP 01943165A EP 01943165 A EP01943165 A EP 01943165A EP 1307313 B2 EP1307313 B2 EP 1307313B2
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EP
European Patent Office
Prior art keywords
disc
intermediate shaft
portable power
power tool
tool 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.)
Expired - Lifetime
Application number
EP01943165A
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German (de)
French (fr)
Other versions
EP1307313A1 (en
EP1307313B1 (en
Inventor
Peter Holzer
Robert Simm
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • 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
    • B25D2211/062—Cam-actuated impulse-driving mechanisms
    • B25D2211/064—Axial cams, e.g. two camming surfaces coaxial with drill spindle
    • 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
    • B25D2250/195—Regulation means
    • B25D2250/201—Regulation means for speed, e.g. drilling or percussion speed

Definitions

  • the invention relates to a hand tool according to the preamble of claim 1.
  • a hand tool of this type is known ( DE 198 03 454 A1 ).
  • a drivable from the drive motor drill spindle relative to the housing of the power tool is rotatably locked, so that a bolted to the drill spindle tool holder, z.
  • the locking device is arranged on an intermediate shaft, which can be coupled via two gear stages with the drill spindle. The locking device opens automatically in a torque transmission from the drive motor forth in the direction of the tool holder and locks automatically in a torque transmission from the tool holder forth to the drive motor.
  • the hand tool according to the invention with the features of claim 1 has the advantage that in the form of the torque-dependent safety coupling overload protection for the user in the abrupt blocking of the drill spindle, e.g. due to hooking of the drill, is created.
  • an overload protection is thus achieved, which protects the existing transmission and the locking device from overloading.
  • Due to the inclusion of the safety coupling in the locking device virtually no additional effort for the safety coupling is necessary. Also, it requires no additional space in the machine housing or a special adaptation of the machine housing to any required space for it.
  • the number of components required for the locking device or safety coupling is also as small as possible. Overall, despite the additionally provided safety coupling virtually no overhead on installation and costs necessary.
  • Fig. 1 schematically a hand tool in the form of a percussion drill 10 with a arranged in a machine housing 26, not shown drive motor for at least rotating drive of a tool holder 12 is shown.
  • the drive motor has a motor shaft 14 which is provided at the end with a drive pinion 15 or a similar toothing and rotatably mounted in a flange 27 by means of a bearing 29, eg ball bearing.
  • the flange 27 constitutes a separate component and is fixedly connected to the machine housing 26.
  • the drive motor is connected via the motor shaft 14 in gear connection with a drill spindle 13, with which the tool holder 12 is detachably connected, for. B. is screwed via a thread 35.
  • the drive pinion 15 meshes with a in Fig. 2 shown, to the intermediate shaft 17 coaxial gear 16 which is rotatable relative to the intermediate shaft 17.
  • the intermediate shaft 17 is rotatably mounted with an end-side shaft journal 46 by means of a needle bearing 48 in the flange 27.
  • the other shaft journal 47 is rotatably supported in the machine housing 26 by means of a needle bearing 49.
  • the intermediate shaft 17 has a toothing 18 and next to a rotatably connected thereto, z. B. hot pressed, gear 19, which are in engagement with gears 20 and 21, which are rotatably mounted on the drill spindle 13 and alternatively z. B.
  • a first gear (slow speed) is formed by the pair of teeth 18, 20 and a second gear (fast speed) through the pair of teeth 19, 21.
  • the gear ratio of these gear stages 18, 20 and 19, 21 is negative, that is, there is a translation of the intermediate shaft 17 on the drill spindle 13 in the slow.
  • Rastenschlagwerk 28 On a tool holder 12 facing away from the end of the drill spindle 13 sits a recorded in the flange 27 Rastenschlagwerk 28, applied over the known manner axial shocks on the drill spindle 13 can be.
  • the Rastenschlagwerk 28 is switched off in the usual way, so that the percussion drill 10 can also be used as a drill with two courses.
  • the tool holder 12 is z. B. formed as a jaw chuck, which by means of a sleeve 31 and a rotatably connected thereto cone nut adjustable chuck jaws 32, between which the shank of a tool is tensioned.
  • a base body 33 of the tool holder 12 is screwed on the thread 35 on a threaded pin 34 of the drill spindle 13 with high bias, so that the tool holder 12 and the drill spindle 13 in the application of the percussion drill 10 are rotatably connected to each other.
  • a dust collar 30 of the sleeve 31 projects into an opening of the machine housing 26.
  • the drill spindle 13 takes on the change of the tool a release or tightening torque and by means of a locking device 38 relative to the flange 27 of the machine housing 26 rotatably coupled.
  • the locking device 38 is disposed between the drill spindle 13 and a part of the machine housing 26 on the intermediate shaft 17.
  • Part of the locking device 38 is an approximately annular housing 43, which is held by means of radial projections 43a non-rotatably and positively in a part of the flange 27.
  • the housing 43 includes a coaxial to the intermediate shaft 17 cylindrical bore 53. In this there is a radially projecting driver 41 having disc 40 which is rotatably mounted on the intermediate shaft 17 relative to this and at least slightly axially.
  • the locking device 38 further includes the rotatable by the drive motor forth via the drive pinion 15, rotatable relative to the intermediate shaft 17 gear 16, on one of the disc 40 facing end side approximately parallel to each other and the disc 40 extending toward, approximately claw-like projections 39a, 39b ,
  • These projections 39a, 39b may be held in the form of cylindrical pins which fit into and circulate in the annulus formed between the bore 53 on the one hand and an outer peripheral surface 54 of the disc 40 on the other, diametrically opposed between the two Driver elements 41 extends.
  • the driver elements 41 are shaped in such a way that the disk 40 can be rotated in a limited manner between adjacent claws 39a, 39b.
  • the outer peripheral surface 54 of the disc 40 has a cylindrical basic shape, wherein this cylindrical basic shape then passes approximately centrally between two adjacent driver elements 41 in each case a flat 42. In the area of the outer surface of the driver elements 41 between these and the bore 53 of the housing 43 only a slight movement play exists. In the adjoining region of the cylindrical peripheral surface 54 of the disc 40, a radial distance between the disc 40 and the bore 53 is provided, which is just sufficient to receive the projections 39a, 39b with little play. In the region of the respective flattening 42 there is a greater radial distance between the bore 53 and the flattening 42 of the disc.
  • a cylindrical rolling element 45 is accommodated with a small play of movement whose diameter exceeds the radial thickness of the approximately claw-shaped projections 39a, 39b.
  • the rolling elements 45 form pinch rollers.
  • the claw-like projections 39a, 39b may e.g. be circumferentially different lengths, each pair of diagonally opposite pairs 39a on the one hand and 39b on the other hand may each have the same length. Instead, the projections 39a, 39b may be the same size.
  • the driver elements 41 each have a torque-transmitting effect on the projections 39a, b. Because of their inertia, the rolling elements 45 are then urged toward the torque transmitting projections 39a, b, then they clamp between the flats 42 of the disc 40 and the bore 53 of the housing 43. As a result, the disc 40 is locked automatically fixed to the housing.
  • a safety clutch 58 is included, which is also disposed on the intermediate shaft 17.
  • the safety clutch 58 is z. B. designed as a slip clutch or front teeth having toothed coupling. It is arranged axially on the output side of the locking device 38. It provides overload protection for the user and for the locking device 38 and the transmission described is extremely simple and requires only a small space. Further, since the safety clutch 58 is integrated with the locking device 38, the number of components is reduced. Furthermore, a reduction of the assembly effort is achieved.
  • the safety clutch 58 is formed between the radial driver elements 41 having disc 40 on the one hand and an intermediate shaft fixed stop surface 59 on the other hand, which is formed here by the axial end face of the intermediate shaft 17 rotatably connected Zahnrades 19 of a gear stage. Against this abutment surface 59, the disc 40 is axially pressed with a facing end face 44 by means supported on the intermediate shaft 17 resilient axial force. On the intermediate shaft 17 sits one of these rotatable cylindrical sleeve 60 which extends on that side of the disc 40, which faces away from the stop surface 59.
  • the sleeve 60 is located with its disk 40 facing the end of the disk 40 axially and is pressed there to this. At the other, the disc 40 facing away from the end of the sleeve 60 attacks the resilient axial force.
  • at least one axial force generating spring 61 is arranged on the intermediate shaft 17.
  • a plurality of disc springs 61 are provided. These sit directly on the intermediate shaft 17.
  • the disc springs 61 are on the in Fig. 2 right side by means of a retaining washer 62 and a lock washer 63 axially supported with respect to the intermediate shaft 17.
  • the locking washer 63 is received positively in a groove 64 of the intermediate shaft 17.
  • the at least one spring here in the form of the disc springs 61, on the one hand axially supported on the intermediate shaft 17, while on the other hand resiliently acting on the facing end of the sleeve 60.
  • the sleeve 60 is thus in Fig. 2 acted upon axially resilient to the left.
  • the sleeve 60 With the end facing away from the disc 40 and thus facing the at least one spring 61, the sleeve 60 is axially above the in Fig. 2 right end of the gear 16 via.
  • the gear 16 is rotatably mounted on the sleeve 60. With the in Fig.
  • the rotatable on the intermediate shaft 17 and at least slightly axially displaceable disc 40 is pressed with its end face 44 against the associated abutment surface 59 of the gear 19, so that in this way the disc 40 torque transmitting with the gear 19 and this with the intermediate shaft 17 in Connection stands.
  • the disc 40 has a hub 67, which in Fig. 2 extends right to the facing end face of the sleeve 60 and the acted upon by the sleeve 60 end face 66 has.
  • these surfaces 59 and 44 may also surface elevations and surface depressions, in particular with one-piece front teeth, which cause a positive engagement.
  • the safety clutch 58 is designed as such a form-fitting coupling, in which the surfaces 44 and 59 in contact therewith have integral, non-illustrated front teeth.
  • the gear 19 is completely made as a sintered part, in which the front teeth are formed as parts of the safety clutch 58 equal in the production, whereby a significant cost savings is achieved.
  • the complete disk 40 together with its driver elements 41 and the integral hub 67 and the front teeth on the front side 44 is designed as a sintered part, so that the costs are also minimized.
  • the sleeve 60 as a further part of the safety coupling 58 is a simple, inexpensive component that does not require additional space.
  • the safety clutch 58 provides overload protection for the user as well as for the locking device 38 and the transmission. It is integrated in a cost-saving manner in the locking device 38, which is characterized also cost-effective, without a larger installation space is required by the arrangement of the safety clutch 58. Due to the reduced proportion of components and the assembly cost is reduced.
  • the safety clutch 58 is arranged axially next to the locking device 38 and on the output side thereof, which is predetermined by the disk 40, and thus at an axial distance from the locking device 38.
  • the disc 40 When transmitting the driving force from the motor shaft 14 via the gear 16 and the claw-like projections 39a, b on the driver elements 41, the disc 40 is driven, with effective safety clutch 58, the drive torque from the disc 40 to the gear 19 and thus to the intermediate shaft 17 is transmitted.
  • the safety clutch 58 responds in such a way that the disc 40 against the force of the at least one spring 61 axially in Fig. 2 is pressed to the right and thus the drive between the disc 40 and the gear 19 is disconnected. This protects the user against excessive machine return torques as well as any damage or damage Destruction of the locking device 38 avoided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Drilling And Boring (AREA)
  • Earth Drilling (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Transmission Devices (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Abstract

The invention relates to a hand-operated machine tool with a tool mounting which may be driven, at least in a rotating manner, by means of a drive motor and a drilling spindle (13), comprising a chuck, for fixing tools, which may be actuated in the direction of rotation of the drilling spindle (13) and a locking device (38), by means of which the drilling spindle (13) can be fixed in a non-rotating manner to a part (27) of the machine housing (26), for the closing and opening of the chuck on the tool holder (12). Said locking device (38) automatically releases on a transfer of torque from the drive motor to the tool mounting (12) and which automatically locks on a transfer of torque from the tool mounting (12) to the drive motor and is arranged on an intermediate shaft (17), in combination with a safety clutch (58) which is also arranged on the intermediate shaft (17).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Handwerkzeugmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a hand tool according to the preamble of claim 1.

Eine Handwerkzeugmaschine dieser Art ist bekannt ( DE 198 03 454 A1 ). Mittels der Arretiervorrichtung ist eine vom Antriebsmotor her antreibbare Bohrspindel gegenüber dem Gehäuse der Handwerkzeugmaschine drehfest arretierbar, so dass ein mit der Bohrspindel verschraubter Werkzeughalter, z. B. ein Bohrfutter, von der Bohrspindel gelöst und/oder ein Werkzeug schlüssellos im Werkzeughalter eingespannt werden kann. Die Arretiervorrichtung ist auf einer Zwischenwelle angeordnet, die über zwei Getriebestufen mit der Bohrspindel koppelbar ist. Die Arretiervorrichtung öffnet selbsttätig bei einer Drehmomentübertragung vom Antriebsmotor her in Richtung zum Werkzeughalter und sperrt selbsttätig bei einer Drehmomentübertragung vom Werkzeughalter her zum Antriebsmotor.A hand tool of this type is known ( DE 198 03 454 A1 ). By means of the locking device, a drivable from the drive motor drill spindle relative to the housing of the power tool is rotatably locked, so that a bolted to the drill spindle tool holder, z. As a chuck, detached from the drill spindle and / or a tool can be clamped keyless in the tool holder. The locking device is arranged on an intermediate shaft, which can be coupled via two gear stages with the drill spindle. The locking device opens automatically in a torque transmission from the drive motor forth in the direction of the tool holder and locks automatically in a torque transmission from the tool holder forth to the drive motor.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Handwerkzeugmaschine mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass in Form der drehmomentabhängig arbeitenden Sicherheitskupplung ein Überlastschutz für den Anwender beim schlagartigen Blockieren der Bohrspindel, z.B. aufgrund Verhakens desBohrers, geschaffen ist. Zusätzlich ist damit eine Überlastsicherung erreicht, die das vorhandene Getriebe bzw. die Arretiervorrichtung vor Überlastung schützt. Aufgrund der Einbeziehung der Sicherheitskupplung in die Arretiervorrichtung ist praktisch kein zusätzlicher Aufwand für die Sicherheitskupplung notwendig. Auch bedarf es keines zusätzlichen Bauraumes im Maschinengehäuse bzw. einer besonderen Anpassung des Maschinengehäuses an einen etwaigen erforderlichen Bauraum dafür. Durch die Integration ist ferner die Anzahl erforderlichen Bauteile für die Arretiervorrichtung bzw. Sicherheitskupplung so klein wie möglich. Insgesamt wird trotz der zusätzlich vorgesehenen Sicherheitskupplung praktisch kein Mehraufwand an Montage und an Kosten nötig.The hand tool according to the invention with the features of claim 1 has the advantage that in the form of the torque-dependent safety coupling overload protection for the user in the abrupt blocking of the drill spindle, e.g. due to hooking of the drill, is created. In addition, an overload protection is thus achieved, which protects the existing transmission and the locking device from overloading. Due to the inclusion of the safety coupling in the locking device virtually no additional effort for the safety coupling is necessary. Also, it requires no additional space in the machine housing or a special adaptation of the machine housing to any required space for it. As a result of the integration, the number of components required for the locking device or safety coupling is also as small as possible. Overall, despite the additionally provided safety coupling virtually no overhead on installation and costs necessary.

Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Handwerkzeugmaschine möglich.The measures listed in the further claims advantageous refinements and improvements of the claim 1 hand tool are possible.

Zeichnungdrawing

Weitere Einzelheiten und Vorteile der Erfindung ergeben sich aus der nachfolgenden Zeichnungsbeschreibung und den Zeichnungen, in denen ein Ausführungsbeispiel der Erfindung dargestellt ist. Die Zeichnung, Beschreibung und die Ansprüche enthalten zahlreiche Merkmale in Kombination. Der Fachmann wird die Merkmale zweckmäßigerweise auch einzeln betrachten und zu sinnvollen weiteren Kombinationen zusammenfassen. Der Schutzumfang wird jedoch ansschliesslich durch die Patentansprüche definiert.Further details and advantages of the invention will become apparent from the following description of the drawings and the drawings, in which an embodiment of the invention is shown. The drawings, description and claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations. The scope of protection, however, is defined exclusively by the claims.

Es zeigen:

Fig. 1
einen Längsschnitt mit teilweiser Seitenansicht einer Schlagbohr-maschine,
Fig. 2
einen Schnitt entlang der Linie II - II der Einzelheit A in Fig. 1,
Fig. 3
einen Schnitt entlang der Linie III - III in Fig. 2.
Show it:
Fig. 1
a longitudinal section with partial side view of a percussion drill,
Fig. 2
a section along the line II - II of the detail A in Fig. 1 .
Fig. 3
a section along the line III - III in Fig. 2 ,

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Fig. 1 ist schematisch eine Handwerkzeugmaschine in Form einer Schlagbohrmaschine 10 mit einem in einem Maschinengehäuse 26 angeordneten, nicht näher dargestellten Antriebsmotor zum zumindest drehenden Antrieb eines Werkzeughalters 12 gezeigt. Der Antriebsmotor weist eine Motorwelle 14 auf, die endseitig mit einem Antriebsritzel 15 oder einer ähnlichen Verzahnung versehen und in einem Flansch 27 mittels eines Lagers 29, z.B. Kugellagers, drehbar gelagert ist. Der Flansch 27 stellt ein separates Bauteil dar und ist mit dem Maschinengehäuse 26 fest verbunden. Der Antriebsmotor steht über die Motorwelle 14 in Getriebeverbindung mit einer Bohrspindel 13, mit der der Werkzeughalter 12 lösbar verbunden ist, z. B. über ein Gewinde 35 verschraubt ist.In Fig. 1 schematically a hand tool in the form of a percussion drill 10 with a arranged in a machine housing 26, not shown drive motor for at least rotating drive of a tool holder 12 is shown. The drive motor has a motor shaft 14 which is provided at the end with a drive pinion 15 or a similar toothing and rotatably mounted in a flange 27 by means of a bearing 29, eg ball bearing. The flange 27 constitutes a separate component and is fixedly connected to the machine housing 26. The drive motor is connected via the motor shaft 14 in gear connection with a drill spindle 13, with which the tool holder 12 is detachably connected, for. B. is screwed via a thread 35.

Das Antriebsritzel 15 kämmt mit einem in Fig. 2 gezeigten, zur Zwischenwelle 17 koaxialen Zahnrad 16, das relativ zur Zwischenwelle 17 drehbar ist. Die Zwischenwelle 17 ist mit einem endseitigen Wellenzapfen 46 mittels ein es Nadellagers 48 im Flansch 27 drehbar gelagert. Der andere Wellenzapfen 47 ist mittels eines Nadellagers 49 im Maschinengehäuse 26 drehbar gelagert. Die Zwischenwelle 17 weist eine Verzahnung 18 und daneben ein damit drehfest verbundenes, z. B. warm aufgepresstes, Zahnrad 19 auf, die in Eingriff stehen mit Getrieberädern 20 bzw. 21, die auf der Bohrspindel 13 drehbar gelagert sind und alternativ z. B. mittels eines in einer Längsnut 22 der Bohrspindel 13 axial verschiebbaren Ziehkeils 23 mit der Bohrspindel 13 in einen drehmomentübertragenden Zustand versetzbar sind. Der Ziehkeil 23 bildet zusammen mit den Getrieberädern 20, 21 und einer hier nicht weiter dargestellten Betätigungsvorrichtung ein Schaltgetriebe 24 mit zwei Gängen. Ein erster Gang (langsame Drehzahl) wird durch die Zahnpaarung 18, 20 und ein zweiter Gang (schnelle Drehzahl) durch die Zahnpaarung 19, 21 gebildet. Das Übersetzungsverhältnis dieser Getriebestufen18, 20 bzw. 19, 21 ist negativ, d. h. es erfolgt eine Übersetzung von der Zwischenwelle 17 auf die Bohrspindel 13 ins Langsame.The drive pinion 15 meshes with a in Fig. 2 shown, to the intermediate shaft 17 coaxial gear 16 which is rotatable relative to the intermediate shaft 17. The intermediate shaft 17 is rotatably mounted with an end-side shaft journal 46 by means of a needle bearing 48 in the flange 27. The other shaft journal 47 is rotatably supported in the machine housing 26 by means of a needle bearing 49. The intermediate shaft 17 has a toothing 18 and next to a rotatably connected thereto, z. B. hot pressed, gear 19, which are in engagement with gears 20 and 21, which are rotatably mounted on the drill spindle 13 and alternatively z. B. by means of an axially slidable in a longitudinal groove 22 of the drill spindle 13 pull wedge 23 with the drill spindle 13 are displaceable in a torque-transmitting state. The pulling wedge 23, together with the gear wheels 20, 21 and an actuating device, not shown here, a manual transmission 24 with two gears. A first gear (slow speed) is formed by the pair of teeth 18, 20 and a second gear (fast speed) through the pair of teeth 19, 21. The gear ratio of these gear stages 18, 20 and 19, 21 is negative, that is, there is a translation of the intermediate shaft 17 on the drill spindle 13 in the slow.

Auf einem dem Werkzeughalter 12 abgewandten Ende der Bohrspindel 13 sitzt ein im Flansch 27 aufgenommenes Rastenschlagwerk 28, über das in bekannter Weise axiale Schläge auf die Bohrspindel 13 aufgebracht werden können. Das Rastenschlagwerk 28 ist dabei in üblicher Weise abschaltbar, so dass die Schlagbohrmaschine 10 auch als Bohrmaschine mit zwei Gängen verwendbar ist.On a tool holder 12 facing away from the end of the drill spindle 13 sits a recorded in the flange 27 Rastenschlagwerk 28, applied over the known manner axial shocks on the drill spindle 13 can be. The Rastenschlagwerk 28 is switched off in the usual way, so that the percussion drill 10 can also be used as a drill with two courses.

Der Werkzeughalter 12 ist z. B. als Backenfutter ausgebildet, das mittels einer Hülse 31 und einer drehfest mit dieser verbundenen Konusmutter verstellbare Futterbacken 32 aufweist, zwischen denen der Schaft eines Werkzeugs spannbar ist. Ein Grundkörper 33 des Werkzeughalters 12 ist dabei über das Gewinde 35 auf einem Gewindezapfen 34 der Bohrspindel 13 mit hoher Vorspannung aufgeschraubt, so dass der Werkzeughalter 12 und die Bohrspindel 13 im Anwendungsfall der Schlagbohrmaschine 10 drehfest miteinander verbunden sind. Ein Staubkragen 30 der Hülse 31 ragt in eine Öffnung des Maschinengehäuses 26 hinein.The tool holder 12 is z. B. formed as a jaw chuck, which by means of a sleeve 31 and a rotatably connected thereto cone nut adjustable chuck jaws 32, between which the shank of a tool is tensioned. A base body 33 of the tool holder 12 is screwed on the thread 35 on a threaded pin 34 of the drill spindle 13 with high bias, so that the tool holder 12 and the drill spindle 13 in the application of the percussion drill 10 are rotatably connected to each other. A dust collar 30 of the sleeve 31 projects into an opening of the machine housing 26.

Die Bohrspindel 13 nimmt beim Wechsel des Werkzeuges ein Löse- bzw. Anziehdrehmoment auf und ist mittels einer Arretiervorrichtung 38 gegenüber dem Flansch 27 des Maschinengehäuses 26 drehfest koppelbar. Die Arretiervorrichtung 38 ist zwischen der Bohrspindel 13 und einem Teil des Maschinengehäuses 26 auf der Zwischenwelle 17 angeordnet. Bestandteil der Arretiervorrichtung 38 ist ein etwa ringförmiges Gehäuse 43, das mittels radialer Vorsprünge 43a undrehbar und formschlüssig in einem Teil des Flansches 27 gehalten ist. Das Gehäuse 43 enthält eine zur Zwischenwelle 17 koaxiale zylindrische Bohrung 53. In dieser befindet sich eine radial abstehende Mitnehmerelemente 41 aufweisende Scheibe 40, die auf der Zwischenwelle 17 relativ zu dieser drehbar und zumindest geringfügig axial verschiebbar angeordnet ist. Zur Arretiervorrichtung 38 gehört ferner das vom Antriebsmotor her über das Antriebsritzel 15 antreibbare, relativ zur Zwischenwelle 17 drehbare Zahnrad 16, das an der einen der Scheibe 40 zugewandten Stirnseite sich etwa parallel zueinander und zur Scheibe 40 hin erstreckende, etwa klauenartige Vorsprünge 39a, 39b aufweist. Diese Vorsprünge 39a, 39b können in Form zylindrischer Stifte gehalten sein, die in den Ringraum passen und in diesem umlaufen können, der zwischen der Bohrung 53 einerseits und einer äußeren Umfangsfläche 54 der Scheibe 40 andererseits gebildet ist, die sich zwischen den beiden einander diametral gegenüberliegenden Mitnehmerelementen 41 erstreckt. Die Mitnehmerelemente 41 sind derart geformt, dass die Scheibe 40 zwischen benachbarten Klauen 39a, 39b begrenzt verdrehbar ist. Die äußere Umfangsfläche 54 der Scheibe 40 hat zylindrische Grundform, wobei diese zylindrische Grundform dann etwa mittig zwischen zwei benachbarten Mitnehmerelementen 41 in jeweils eine Abflachung 42 übergeht. Im Bereich der Außenfläche der Mitnehmerelemente 41 ist zwischen diesen und der Bohrung 53 des Gehäuses 43 lediglich ein geringes Bewegungsspiel vorhanden. Im daran anschließenden Bereich der zylindrischen Umfangsfläche 54 der Scheibe 40 ist ein radialer Abstand zwischen der Scheibe 40 und der Bohrung 53 vorgesehen, der gerade ausreicht, die Vorsprünge 39a, 39b mit geringem Bewegungsspiel aufzunehmen. Im Bereich der jeweiligen Abflachung 42 liegt ein größerer radialer Abstand zwischen der Bohrung 53 und der Abflachung 42 der Scheibe vor. In diesem Bereich ist jeweils ein zylindrischer Wälzkörper 45 mit geringem Bewegungsspiel aufgenommen, dessen Durchmesser die radiale Dicke der etwa klauenförmigen Vorsprünge 39a, 39b übertrifft. Die Wälzkörper 45 bilden Klemmrollen. Die klauenartigen Vorsprünge 39a, 39b können z.B. in Umfangsrichtung unterschiedlich lang sein, wobei jeweils diagonal gegenüberliegende Paare 39a einerseits und 39b andererseits jeweils die gleiche Länge haben können. Statt dessen können die Vorsprünge 39a, 39b auch gleich groß sein.The drill spindle 13 takes on the change of the tool a release or tightening torque and by means of a locking device 38 relative to the flange 27 of the machine housing 26 rotatably coupled. The locking device 38 is disposed between the drill spindle 13 and a part of the machine housing 26 on the intermediate shaft 17. Part of the locking device 38 is an approximately annular housing 43, which is held by means of radial projections 43a non-rotatably and positively in a part of the flange 27. The housing 43 includes a coaxial to the intermediate shaft 17 cylindrical bore 53. In this there is a radially projecting driver 41 having disc 40 which is rotatably mounted on the intermediate shaft 17 relative to this and at least slightly axially. The locking device 38 further includes the rotatable by the drive motor forth via the drive pinion 15, rotatable relative to the intermediate shaft 17 gear 16, on one of the disc 40 facing end side approximately parallel to each other and the disc 40 extending toward, approximately claw-like projections 39a, 39b , These projections 39a, 39b may be held in the form of cylindrical pins which fit into and circulate in the annulus formed between the bore 53 on the one hand and an outer peripheral surface 54 of the disc 40 on the other, diametrically opposed between the two Driver elements 41 extends. The driver elements 41 are shaped in such a way that the disk 40 can be rotated in a limited manner between adjacent claws 39a, 39b. The outer peripheral surface 54 of the disc 40 has a cylindrical basic shape, wherein this cylindrical basic shape then passes approximately centrally between two adjacent driver elements 41 in each case a flat 42. In the area of the outer surface of the driver elements 41 between these and the bore 53 of the housing 43 only a slight movement play exists. In the adjoining region of the cylindrical peripheral surface 54 of the disc 40, a radial distance between the disc 40 and the bore 53 is provided, which is just sufficient to receive the projections 39a, 39b with little play. In the region of the respective flattening 42 there is a greater radial distance between the bore 53 and the flattening 42 of the disc. In this area, in each case a cylindrical rolling element 45 is accommodated with a small play of movement whose diameter exceeds the radial thickness of the approximately claw-shaped projections 39a, 39b. The rolling elements 45 form pinch rollers. The claw-like projections 39a, 39b may e.g. be circumferentially different lengths, each pair of diagonally opposite pairs 39a on the one hand and 39b on the other hand may each have the same length. Instead, the projections 39a, 39b may be the same size.

Bei einer Drehmomentübertragung vom Antriebsmotor über die Motorwelle 14 mit Antriebsritzel 15 auf das Zahnrad 16 wirken die Vorsprünge 39a drehmomentübertagend auf die Mitnehmerelemente 41, wobei die Wälzkörper 45 aufgrund ihres Beharrungsvermögens dann vor den jeweils benachbarten Klauen 39b zu liegen kommen. Die benachbarten Klauen 39b halten dann die Wälzkörper 45 im Bereich der jeweiligen Abflachungen 42, so dass eine ungehinderte Drehmomentübertragung gewährleistet ist, bei diesem Beispiel und bei der Darstellung gemäß Fig. 3 im Uhrzeigersinn. Es versteht sich, dass bei einem dazu gegensinnigen Antrieb des Zahnrades 16 und gegensinniger Umlaufbewegung der klauenartigen Vorsprünge 39a, 39b die Vorsprünge 39b drehmomentübertragend auf die Mitnehmerelemente 41 wirken und dann die anderen Klauen 39a die Wälzkörper 45 so beaufschlagen, dass diese jeweils im Bereich der Abflachungen 42 verbleiben und eine ungehinderte Drehmomentübertragung in der anderen Drehrichtung gewährleistet ist.In a torque transmission from the drive motor via the motor shaft 14 with drive pinion 15 to the gear 16, the projections act 39a torque transfer to the driver elements 41, the rolling elements 45 then come to rest before their respective adjacent claws 39b due to their inertia. The adjacent claws 39b then hold the rolling elements 45 in the region of the respective flattenings 42, so that unimpeded torque transmission is ensured, in this example and in the illustration according to FIG Fig. 3 clockwise. It is understood that with an opposing drive of the gear 16 and reverse rotation of the claw-like projections 39a, 39b, the projections 39b torque-transmitting act on the driver elements 41 and then act on the other jaws 39a, the rolling elements 45 so that they each in the region of the flats 42 remain and unimpeded torque transmission is ensured in the other direction.

Bei einer Drehmomentübertragung, die statt der Einleitung über die Motorwelle 14 eingeleitet wird über die Bohrspindel 13 und die vom Werkzeughalter 12 ausgeht, wirken hingegen die Mitnehmerelemente 41 jeweils drehmomentübertragend auf die Vorsprünge 39a, b. Aufgrund ihres Beharrungsvermögens werden dann die Wälzkörper 45 in Richtung auf die drehmomentübertragenden Vorsprünge 39a, b gedrängt, wobei sie sich dann zwischen den Abflachungen 42 der Scheibe 40 und der Bohrung 53 des Gehäuses 43 festklemmen. Dadurch wird die Scheibe 40 selbsttätig gehäusefest arretiert. Dadurch ist es dann möglich, beim Spannen bzw. Lösen eines Werkzeuges im Werkzeughalter 12 oder auch beim Aufschrauben oder Abschrauben des Werkzeughalters 12 von der Bohrspindel 13 ein Gegenmoment auf die Bohrspindel 13 aufzubringen, und dies ohne dabei irgendeine besondere, von Hand auszulösende Arretiereinrichtung zu benötigen.In a torque transmission, which is initiated instead of the introduction via the motor shaft 14 via the drill spindle 13 and starting from the tool holder 12, on the other hand, the driver elements 41 each have a torque-transmitting effect on the projections 39a, b. Because of their inertia, the rolling elements 45 are then urged toward the torque transmitting projections 39a, b, then they clamp between the flats 42 of the disc 40 and the bore 53 of the housing 43. As a result, the disc 40 is locked automatically fixed to the housing. This makes it possible, when clamping or releasing a tool in the tool holder 12 or when screwing or unscrewing the tool holder 12 from the drill spindle 13 to apply a counter-torque on the drill spindle 13, and this without needing any special, manually triggered locking device ,

In diese zuvor beschriebene Arretiervorrichtung 38 ist eine Sicherheitskupplung 58 einbezogen, die ebenfalls auf der Zwischenwelle 17 angeordnet ist. Die Sicherheitskupplung 58 ist z. B. als Rutschkupplung oder Stirnzähne aufweisende Zahnkupplung ausgebildet. Sie ist axial an der Abtriebsseite der Arretiervorrichtung 38 angeordnet. Sie bietet einen Überlastschutz für den Anwender sowie für die Arretiervorrichtung 38 und das beschriebene Getriebe, ist außerordentlich einfach und benötigt nur einen geringen Bauraum. Da die Sicherheitskupplung 58 in die Arretiervorrichtung 38 integriert ist, wird ferner die Anzahl der Bauteile reduziert. Ferner ist eine Verringerung des Montageaufwandes erreicht.In this locking device 38 described above, a safety clutch 58 is included, which is also disposed on the intermediate shaft 17. The safety clutch 58 is z. B. designed as a slip clutch or front teeth having toothed coupling. It is arranged axially on the output side of the locking device 38. It provides overload protection for the user and for the locking device 38 and the transmission described is extremely simple and requires only a small space. Further, since the safety clutch 58 is integrated with the locking device 38, the number of components is reduced. Furthermore, a reduction of the assembly effort is achieved.

Nachfolgend sind Einzelheiten der Sicherheitskupplung 58 einschließlich weiterer Details der damit getrieblich verbundenen Arretiervorrichtung 38 erläutert. Die Sicherheitskupplung 58 ist zwischen der die radialen Mitnehmerelemente 41 aufweisenden Scheibe 40 einerseits und einer zwischenwellenfesten Anschlagfläche 59 andererseits ausgebildet, die hier durch die axiale Stirnfläche des mit der Zwischenwelle 17 drehfest verbundenen Zahnrades19 der einen Getriebestufe gebildet ist. Gegen diese Anschlagfläche 59 ist die Scheibe 40 axial mit einer zugewandten Stirnseite 44 mittels an der Zwischenwelle 17 abgestützter federnder Axialkraft anpressbar. Auf der Zwischenwelle 17 sitzt eine dieser gegenüber drehbare zylindrische Hülse 60, die sich auf derjenigen Seite der Scheibe 40 erstreckt, die der Anschlagfläche 59 abgewandt ist. Die Hülse 60 liegt mit ihrem der Scheibe 40 zugewandten Ende an der Scheibe 40 axial an und wird dort an diese angepresst. Am anderen, der Scheibe 40 abgewandten Ende der Hülse 60 greift die federnde Axialkraft an. Hierzu ist auf der Zwischenwelle 17 mindestens eine die Axialkraft erzeugende Feder 61, insbesondere Tellerfeder, angeordnet. Beim gezeigten Ausführungsbeispiel sind mehrere Tellerfedern 61 vorgesehen. Diese sitzen unmittelbar auf der Zwischenwelle 17. Die Tellerfedern 61 sind auf der in Fig. 2 rechten Seite mittels einer Haltescheibe 62 und einer Sicherungsscheibe 63 axial in Bezug auf die Zwischenwelle 17 abgestützt. Die Sicherungsscheibe 63 ist in einer Nut 64 der Zwischenwelle 17 formschlüssig aufgenommen. Zwischen den Tellerfedern 61 und der zugewandten Stirnseite der Hülse 60 sind Ausgleichsscheiben 65 angeordnet. Aufgrund der beschriebenen Anordnung ist die mindestens eine Feder, hier in Form der Tellerfedern 61, einerseits an der Zwischenwelle 17 axial abgestützt, wobei sie andererseits auf das zugewandte Ende der Hülse 60 federnd einwirkt. Die Hülse 60 ist somit in Fig. 2 nach links hin axial federnd beaufschlagt. Mit dem Ende, das der Scheibe 40 abgewandt ist und somit der mindestens einen Feder 61 zugewandt ist, steht die Hülse 60 axial über die in Fig. 2 rechte Stirnseite des Zahnrades 16 über. Das Zahnrad 16 ist auf der Hülse 60 drehbar gelagert. Mit dem in Fig. 2 linken Ende steht die Hülse 60 über die dortige Stirnseite des Zahnrades 16 ebenfalls über, wobei die Hülse 60 mit dieser Stirnseite axial an die zugewandte Stirnseite 66 der Scheibe 40 angepresst ist. Dadurch wird die auf der Zwischenwelle 17 drehbare und zumindest geringfügig axial verschiebbare Scheibe 40 mit ihrer Stirnseite 44 gegen die zugeordnete Anschlagfläche 59 des Zahnrades 19 angepresst, so dass in dieser Weise die Scheibe 40 drehmomentübertragend mit dem Zahnrad 19 und über dieses mit der Zwischenwelle 17 in Verbindung steht. Die Scheibe 40 weist eine Nabe 67 auf, die in Fig. 2 rechts bis zur zugewandten Stirnseite des Hülse 60 reicht und die von der Hülse 60 beaufschlagte Stirnseite 66 hat.Details of the safety coupling 58, including further details of the locking device 38 operatively connected thereto, are explained below. The safety clutch 58 is formed between the radial driver elements 41 having disc 40 on the one hand and an intermediate shaft fixed stop surface 59 on the other hand, which is formed here by the axial end face of the intermediate shaft 17 rotatably connected Zahnrades 19 of a gear stage. Against this abutment surface 59, the disc 40 is axially pressed with a facing end face 44 by means supported on the intermediate shaft 17 resilient axial force. On the intermediate shaft 17 sits one of these rotatable cylindrical sleeve 60 which extends on that side of the disc 40, which faces away from the stop surface 59. The sleeve 60 is located with its disk 40 facing the end of the disk 40 axially and is pressed there to this. At the other, the disc 40 facing away from the end of the sleeve 60 attacks the resilient axial force. For this purpose, at least one axial force generating spring 61, in particular plate spring, is arranged on the intermediate shaft 17. In the illustrated embodiment, a plurality of disc springs 61 are provided. These sit directly on the intermediate shaft 17. The disc springs 61 are on the in Fig. 2 right side by means of a retaining washer 62 and a lock washer 63 axially supported with respect to the intermediate shaft 17. The locking washer 63 is received positively in a groove 64 of the intermediate shaft 17. Between the disc springs 61 and the facing end face of the sleeve 60 shims 65 are arranged. Due to the described arrangement, the at least one spring, here in the form of the disc springs 61, on the one hand axially supported on the intermediate shaft 17, while on the other hand resiliently acting on the facing end of the sleeve 60. The sleeve 60 is thus in Fig. 2 acted upon axially resilient to the left. With the end facing away from the disc 40 and thus facing the at least one spring 61, the sleeve 60 is axially above the in Fig. 2 right end of the gear 16 via. The gear 16 is rotatably mounted on the sleeve 60. With the in Fig. 2 left end is the sleeve 60 on the local front side of the gear 16 also over, wherein the sleeve 60 is pressed with this end face axially against the facing end face 66 of the disc 40. Thus, the rotatable on the intermediate shaft 17 and at least slightly axially displaceable disc 40 is pressed with its end face 44 against the associated abutment surface 59 of the gear 19, so that in this way the disc 40 torque transmitting with the gear 19 and this with the intermediate shaft 17 in Connection stands. The disc 40 has a hub 67, which in Fig. 2 extends right to the facing end face of the sleeve 60 and the acted upon by the sleeve 60 end face 66 has.

Die zwischenwellenfeste Anschlagfläche 59 des mit der Zwischenwelle 17 drehfest verbundenen Zahnrades 19 einerseits und die dieser zugeordnete Stirnseite 44 der Scheibe 40 andererseits können auf den einander zugewandten und mittels der mindestens einen Feder 61 federnd aneinandergepressten Stirnseiten einen Reibschluss bildende Flächenteile, z. B: Reibflächen, aufweisen. Statt dessen können diese Flächen 59 und 44 auch Oberflächenerhöhungen und Oberflächenvertiefungen, insbesondere damit einstückige Stirnzähne, aufweisen, die einen formschlüssigen Eingriff bewirken. Beim gezeigten Ausführungsbeispiel ist die Sicherheitskupplung 58 als eine derartige formschlüssige Kupplung gestaltet, bei der die miteinander in Berührung stehenden Flächen 44 und 59 damit einstückige, nicht weiter dargestellte Stirnzähne aufweisen. In einfacher Weise ist das Zahnrad 19 komplett als Sinterteil gefertigt, bei dem die Stirnzähne als Teile der Sicherheitskupplung 58 gleich bei der Herstellung mit gebildet sind, wodurch eine erhebliche Kostenersparnis erzielt ist. In vorteilhafter Weise ist ferner auch die komplette Scheibe 40 mitsamt ihren Mitnehmerelementen 41 und der damit einstückigen Nabe 67 und den Stirnzähnen auf der Stirnseite 44 als Sinterteil gestaltet, so dass auch dafür die Kosten minimiert sind. Die Hülse 60 als weiterer Teil der Sicherheitskupplung 58 stellt ein einfaches, kostengünstiges Bauteil dar, das keinen zusätzlichen Bauraum benötigt. Die Sicherheitskupplung 58 bietet einen Überlastschutz für den Anwender sowie für die Arretiervorrichtung 38 und das Getriebe. Sie ist in kostensparender Weise in die Arretiervorrichtung 38 integriert, die dadurch ebenfalls kostengünstig gestaltet ist, ohne dass durch die Anordnung der Sicherheitskupplung 58 ein größerer Einbauraum benötigt wird. Aufgrund reduzierter Anteil der Bauteile ist auch der Montageaufwand reduziert.The intermediate shaft fixed stop surface 59 of the intermediate shaft 17 rotatably connected gear 19 on the one hand and this associated end face 44 of the disc 40 on the other hand, on the facing and by means of at least one spring 61 resiliently pressed together end faces a frictionally engaging surface parts, z. B: friction surfaces, exhibit. Instead, these surfaces 59 and 44 may also surface elevations and surface depressions, in particular with one-piece front teeth, which cause a positive engagement. In the embodiment shown, the safety clutch 58 is designed as such a form-fitting coupling, in which the surfaces 44 and 59 in contact therewith have integral, non-illustrated front teeth. In a simple way, the gear 19 is completely made as a sintered part, in which the front teeth are formed as parts of the safety clutch 58 equal in the production, whereby a significant cost savings is achieved. In an advantageous manner, furthermore, the complete disk 40 together with its driver elements 41 and the integral hub 67 and the front teeth on the front side 44 is designed as a sintered part, so that the costs are also minimized. The sleeve 60 as a further part of the safety coupling 58 is a simple, inexpensive component that does not require additional space. The safety clutch 58 provides overload protection for the user as well as for the locking device 38 and the transmission. It is integrated in a cost-saving manner in the locking device 38, which is characterized also cost-effective, without a larger installation space is required by the arrangement of the safety clutch 58. Due to the reduced proportion of components and the assembly cost is reduced.

Es ist erkennbar, dass die Sicherheitskupplung 58 axial neben der Arretiervorrichtung 38 und auf der Abtriebsseite dieser, die durch die Scheibe 40 vorgegeben ist, angeordnet ist und somit in axialem Abstand von der Arretiervorrichtung 38.It can be seen that the safety clutch 58 is arranged axially next to the locking device 38 and on the output side thereof, which is predetermined by the disk 40, and thus at an axial distance from the locking device 38.

Bei der Übertragung der Antriebskraft von der Motorwelle 14 über das Zahnrad 16 und dessen klauenartige Vorsprünge 39a, b auf die Mitnehmerelemente 41 wird die Scheibe 40 angetrieben, wobei bei wirksamer Sicherheitskupplung 58 das Antriebsmoment von der Scheibe 40 auf das Zahnrad 19 und damit auf die Zwischenwelle 17 übertragen wird. Im Falles eines Antriebsmomentes, das das zulässige Moment der Sicherheitskupplung 58 übersteigt, spricht die Sicherheitskupplung 58 in der Weise an, dass die Scheibe 40 gegen die Kraft der mindestens einen Feder 61 axial in Fig. 2 nach rechts gedrückt wird und damit der Antrieb zwischen der Scheibe 40 und dem Zahnrad 19 getrennt wird. Dadurch wird der Anwender vor zu hohen Rückdrehmomenten der Maschine geschützt sowie eine etwaige Beschädigung oder Zerstörung der Arretiervorrichtung 38 vermieden.When transmitting the driving force from the motor shaft 14 via the gear 16 and the claw-like projections 39a, b on the driver elements 41, the disc 40 is driven, with effective safety clutch 58, the drive torque from the disc 40 to the gear 19 and thus to the intermediate shaft 17 is transmitted. In the case of a drive torque exceeding the allowable torque of the safety clutch 58, the safety clutch 58 responds in such a way that the disc 40 against the force of the at least one spring 61 axially in Fig. 2 is pressed to the right and thus the drive between the disc 40 and the gear 19 is disconnected. This protects the user against excessive machine return torques as well as any damage or damage Destruction of the locking device 38 avoided.

Erfolgt ein gegensinniger Antrieb vom Werkzeughalter 12 und von der Bohrspindel 13 her auf die Zwischenwelle 17, so wird bei eingerückter Sicherheitskupplung 58 dieses Moment von der Scheibe 40 aufgenommen, da in diesem Fall die Arretiervorrichtung 38 die Scheibe 40 blockiert durch Festklemmen der Wälzkörper 45 zwischen der Bohrung 53 des Gehäuses 43 und den Abflachungen 42 der Scheibe 40. Die Sicherheitskupplung 58 ist hinsichtlich ihres übertragbaren Moments so eingestellt, dass in diesem Zustand der Verklemmung durch die Wälzkörper 45 die Sicherheitskupplung 58 noch nicht im Sinne einer Entkupplung anspricht, da das in die Bohrspindel 13 eingeleitete Moment z. B. zum Wechsel des Werkzeuges oder Lösen des Werkzeughalters 12 geringer ist als das zulässige übertragbare Moment der Sicherheitskupplung 58. Erst dann, wenn ein demgegenüber unzulässiges höheres Moment über die Bohrspindel 13 eingeleitet wird, kann auch dann die Sicherheitskupplung 58 im Entkuppelsinn ansprechen, um auch dann eine Beschädigung oder Zerstörung der Arretiervorrichtung 38 und des Getriebes zu vermeiden.If an opposing drive from the tool holder 12 and the drill spindle 13 forth on the intermediate shaft 17, so this torque is absorbed by the disc 40 when the safety clutch 58, since in this case the locking device 38, the disc 40 blocked by clamping the rolling elements 45 between the Bore 53 of the housing 43 and the flats 42 of the disc 40. The safety clutch 58 is adjusted in terms of their transmittable torque that in this state of jamming by the rolling elements 45, the safety clutch 58 is not yet in the sense of decoupling responds, as in the drill spindle 13 initiated moment z. B. for changing the tool or releasing the tool holder 12 is less than the allowable transmissible torque of the safety clutch 58. Only then, when a contrary inadmissible higher torque is introduced via the drill spindle 13, then the safety clutch 58 can also respond in Entkuppelsinn then to avoid damage or destruction of the locking device 38 and the transmission.

Claims (14)

  1. Portable power tool, in particular a drilling or percussion drilling machine, having a machine housing (26), having a drive motor for the at least rotary drive of a drilling spindle (13), having a tool holder (12), e.g. in the form of a drill chuck, wherein the drilling spindle (13) receives a releasing or tightening torque during the changing of the tool and can be coupled in a rotationally fixed manner relative to a part (27) of the machine housing (26) by means of a locking device (38) which is arranged between the drilling spindle (13) and a part (27) of the machine housing (26) on an intermediate shaft (17) which is rotationally connected to the drilling spindle (13) and can be coupled to the latter via at least one gearing stage (18/20 or 19/21), said locking device (38) opening automatically during a torque transmission from the drive motor to the tool holder (12) and locking automatically during a torque transmission from the tool holder (12) in the opposite direction, a safety clutch (58) included in the locking device (38) being arranged on the intermediate shaft (17), characterized in that the safety clutch (58) is arranged axially on the output side of the locking device (38).
  2. Portable power tool according to Claim 1, characterized in that the safety clutch (58) is formed between a disc (40), having radially projecting driver elements (41), of the locking device (38) and a stop surface (59) which is fixed relative to the intermediate shaft and against which the disc (40) can be pressed axially by means of an elastic axial force bearing on the intermediate shaft (17).
  3. Portable power tool according to either of Claims 1 and 2, characterized in that the disc (40) is arranged on the intermediate shaft (17) in such a way as to be rotatable and at least slightly axially displaceable, if need be by means of a hub (67) in one piece with said disc (40), relative to the intermediate shaft (17).
  4. Portable power tool according to one of Claims 1 to 3, characterized in that a sleeve (60) is arranged on the intermediate shaft (17), said sleeve (60) extending on that side of the disc (40) which faces away from the stop surface (59) which is fixed relative to the intermediate shaft.
  5. Portable power tool according to Claim 4, characterized in that the sleeve (60) bears axially against the disc (40) with the end face which faces the disc (40).
  6. Portable power tool according to Claim 4 or 5, characterized in that the axial force acts on the other end of the sleeve (60) facing away from the disc (40).
  7. Portable power tool according to one of Claims 1 to 6, characterized in that at least one spring (61) producing the axial force, in particular a disc spring, is arranged on the intermediate shaft (17).
  8. Portable power tool according to Claim 7, characterized in that the at least one spring (61) is axially supported on one side on the intermediate shaft (17) and acts elastically on the other side on the facing side of the sleeve (60).
  9. Portable power tool according to one of Claims 1 to 8, characterized in that a gear (16) which can be driven from the drive motor is rotatably arranged on the intermediate shaft (17), in particular on the sleeve (60), and this gear (16) has, as part of the locking device (38), projections (39a, 39b) on an end face facing the disc (40), said projections (39a, 39b) extending approximately parallel to one another and to the disc (40).
  10. Portable power tool according to one of Claims 4 to 9, characterized in that the sleeve (60) projects axially beyond the gear (16) with the end which faces away from the disc (40).
  11. Portable power tool according to one of Claims 1 to 10, characterized in that the stop surface (59) fixed relative to the intermediate shaft is formed by an axial end face of a gear (19) of a gearing stage (19/21), which gear (19) is arranged on the intermediate shaft (17) in a rotationally fixed manner, e.g. is pressed in place thereon.
  12. Portable power tool according to one of Claims 1 to 11, characterized in that the stop surface (59) fixed relative to the intermediate shaft, in particular the gear (19), on the one hand and the disc (40) on the other hand, on the end faces (59, 44) facing one another and pressed against one another, have surface parts contacting one another and forming a friction grip and/or a form fit, e.g. are provided with surface prominences and/or surface recesses, in particular radial teeth.
  13. Portable power tool according to one of Claims 9 to 12, characterized in that the locking device (38) has a housing (43) which is held in a part (27), e.g. a flange part, of the machine housing (26) and in which the projections (39a, 39b) of the gear (16) are arranged and in which the radial driver elements (41) of the disc (40) are arranged at circumferential angular distances apart and in which a rolling body (45), in particular a clamping roller, is arranged in the circumferential direction between two respective projections (39a, 39b) of a projection pair (39a, 39b) extending in the circumferential direction between two driver elements (41), wherein, during a torque transmission from the drive motor in the direction of the tool holder (12), the projections (39a, 39b) release the rolling bodies (45) in such a way that the latter revolve in the housing (43), and, during a torque transmission from the tool holder (12) in the direction of the drive motor, the driver elements (41) lock the rolling bodies (45) in position relative to the housing (43).
  14. Portable power tool according to one of Claims 1 to 13, characterized in that the disc (40) having the driver elements (41) and the end face (44) of the safety clutch (58) and/or the gear (19) which is fixed relative to the intermediate shaft and has the stop surface (59) of the safety clutch (58) are/is designed as a sintered part.
EP01943165A 2000-08-03 2001-05-29 Hand-operated machine tool Expired - Lifetime EP1307313B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10037808 2000-08-03
DE10037808A DE10037808A1 (en) 2000-08-03 2000-08-03 Hand tool
PCT/DE2001/002035 WO2002011933A1 (en) 2000-08-03 2001-05-29 Hand-operated machine tool

Publications (3)

Publication Number Publication Date
EP1307313A1 EP1307313A1 (en) 2003-05-07
EP1307313B1 EP1307313B1 (en) 2007-08-01
EP1307313B2 true EP1307313B2 (en) 2009-08-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP01943165A Expired - Lifetime EP1307313B2 (en) 2000-08-03 2001-05-29 Hand-operated machine tool

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Country Link
US (1) US6793023B2 (en)
EP (1) EP1307313B2 (en)
JP (1) JP2004524168A (en)
CN (1) CN1211176C (en)
DE (2) DE10037808A1 (en)
WO (1) WO2002011933A1 (en)

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Also Published As

Publication number Publication date
EP1307313A1 (en) 2003-05-07
EP1307313B1 (en) 2007-08-01
US20030173097A1 (en) 2003-09-18
JP2004524168A (en) 2004-08-12
CN1446139A (en) 2003-10-01
DE10037808A1 (en) 2002-02-14
CN1211176C (en) 2005-07-20
US6793023B2 (en) 2004-09-21
DE50112797D1 (en) 2007-09-13
WO2002011933A1 (en) 2002-02-14

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