EP0589337B1 - Hand tool machine, particularly a hammer drill - Google Patents

Hand tool machine, particularly a hammer drill Download PDF

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Publication number
EP0589337B1
EP0589337B1 EP93114799A EP93114799A EP0589337B1 EP 0589337 B1 EP0589337 B1 EP 0589337B1 EP 93114799 A EP93114799 A EP 93114799A EP 93114799 A EP93114799 A EP 93114799A EP 0589337 B1 EP0589337 B1 EP 0589337B1
Authority
EP
European Patent Office
Prior art keywords
hand tool
tool according
rotary element
powered hand
connecting channel
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
EP93114799A
Other languages
German (de)
French (fr)
Other versions
EP0589337A1 (en
Inventor
Manfred Bleicher
Otto Baumann
Markus Heckmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0589337A1 publication Critical patent/EP0589337A1/en
Application granted granted Critical
Publication of EP0589337B1 publication Critical patent/EP0589337B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M13/00—Crankcase ventilating or breathing
    • F01M13/04—Crankcase ventilating or breathing having means for purifying air before leaving crankcase, e.g. removing oil
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/26—Lubricating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/061—Swash-plate actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/185—Pressure equalising means between sealed chambers

Definitions

  • the invention relates to a hand tool, in particular a rotary hammer, according to the preamble of claim 1.
  • a hand tool is known from FR-A-2 546 802.
  • DE-A-33 29 005 and DE-A-40 00 822 describe a hand power tool in which the gear chamber is separated from the engine compartment by a housing part with a ball bearing for the pinion driven by the motor.
  • the ball bearing is provided with sealing washers on both sides and can also be provided on the side facing the transmission space with a centrifugal disc attached to the bearing inner ring in order to promote sealing of the transmission space from the engine compartment.
  • a drill hammer of the generic type is already known from FR-A-2 546 802, the gear chamber of which is vented to the atmosphere via a connecting channel.
  • an additional housing is provided which has openings to the gear chamber and covers the mouth of the connecting channel on the gear box side.
  • the hand tool according to the invention with the characterizing features of claim 1 has the advantage that the entry of lubricant into the connecting channel is prevented by the centrifugal forces generated during the rotation of the rotary element.
  • the connecting channel in particular the bore, which connects the transmission space to the atmosphere and / or the engine compartment, enables pressure to be reduced in the transmission space in a simple and inexpensive manner.
  • a motor-operated rotary hammer 1 is shown schematically, which is designed and works as described in detail in DE-A-33 29 005 and DE-A-40 00 822, to which expressly for the purpose the disclosure and to avoid unnecessary repetition.
  • the hammer drill 1 contains in a housing 2 an electric motor 3, a gear 4, a striking mechanism 5 designed as an air cushion percussion mechanism and one Tool holder 6 into which a tool 7 suitable for the respective application can be inserted.
  • the motor 3 has a pinion 8, which is always in engagement with an outer ring gear 9 of a clutch gear 10, which is part of a sleeve 30.
  • the gear wheel 10 has a toothing 11 on its end face.
  • the clutch gear 10 is supported in the wobble hub 29.
  • An intermediate shaft 17 runs inside the wobble hub 29 and sleeve 30.
  • a needle bearing 16 is pressed into the clutch gear 10, the clutch gear 10 and the intermediate shaft 17 being relatively displaceable in the region of the needle bearing 16.
  • the intermediate shaft 17 has a thickened central part 18, on the right side facing the clutch gear 10 of which a counter toothing 19 is arranged, which forms a clutch 11/19 with the toothing 11.
  • the left end of the intermediate shaft 17 is axially displaceably mounted in a needle bearing 22 seated in the housing 2.
  • a ball bearing 23 is pressed onto the middle part 18 following the longitudinal toothing 20, on the outer ring 24 of which a switching element 25 engages for the axial displacement of the intermediate shaft 17.
  • an engine compartment 31 is formed, in which the electric motor 3 is contained, and on the side adjoining on the left in FIG. 1, a transmission compartment 32, in which the transmission 4, the striking mechanism 5 and the other elements already explained are included.
  • the housing part 13 separates the engine compartment 31 from the gear compartment 32.
  • the pinion 8 extends through the Housing part 13 into the gear chamber 32 and is mounted within the housing part 13 by means of a ball bearing 26.
  • the ball bearing 26, as is not particularly emphasized, has sealing disks on both sides and, on the side facing the transmission space 32, also has a centrifugal disk 27 which is connected in a rotationally fixed manner to the inner ring of the ball bearing 26.
  • the ball bearing 26 is held with a sliding fit in the housing part 13, an O-ring 54 being arranged between the outer ring and the housing part 13.
  • This design of the ball bearing 26 with double-sided sealing disks, centrifugal disk 27 and O-ring 54 is intended to promote a seal of the gear chamber 32 to the engine compartment 31 in this area.
  • An O-ring 33 serves for further sealing.
  • the rotary hammer 1 has a pressure compensation device 34, which is shown in detail in particular in FIG. 2 and is explained in more detail below with reference to this.
  • the pressure compensation device 34 enables a reduction in the pressure generated in operation in the gear chamber 32 and thus pressure compensation.
  • heat develops during operation of the rotary hammer 1, especially in the gear chamber 32, in particular when the rotary hammer 1 operates in impact mode. Due to the heating in the gear chamber 32, a considerable excess pressure develops, which can be reduced by means of the pressure compensation device 34, and this advantageously with no loss of lubricant within the gear chamber 32.
  • the pressure compensation device 34 advantageously connects the gear chamber 32 to the engine compartment 31 and carries out a pressure compensation of the gear compartment 32 to the engine compartment 31.
  • the pressure compensation device 34 has at least one connecting channel 35 between the gear chamber 32 and the engine compartment 31.
  • Part of the pressure compensation device 34, in particular the connecting channel 35, is at least one bore 36 contained in the housing part 13, which ends at one end 37 in the gear chamber 32 and at the other end 38 in the engine compartment 31 and advantageously parallel to the axis of the pinion 8 through the Housing part 13 runs through.
  • the housing part 13 has in the area of the sleeve 30 with the coupling gear 10 at the end, the compression spring 12 and the intermediate shaft 17 a protrusion 28, for example a pin, which projects towards the gear chamber 32, which is an integral part of the housing part 13 and through which the at least one bore 36 runs , whose end 37 on the gearbox space ends in the region of the end face 39 of this projection 28.
  • a protrusion 28 for example a pin, which projects towards the gear chamber 32, which is an integral part of the housing part 13 and through which the at least one bore 36 runs , whose end 37 on the gearbox space ends in the region of the end face 39 of this projection 28.
  • gear chamber 32 can be vented to the outside, to the atmosphere.
  • a channel 36 ' which is only indicated by dashed lines, a hole in the housing part 13, which leads to the outside, possibly through the housing 2 or in some other way.
  • the channel 36 ′ adjoins the bore section of the bore 36 running to the left in FIG. 2.
  • the pressure compensation device 34 also has in the gear chamber 32 a continuously rotating rotary element 40, by means of which lubricant located in the gear chamber 32 can be thrown radially outwards as a result of centrifugal force.
  • the rotary element 40 is driven by means of the sleeve 30 of the transmission 4, which sleeve is constantly driven by the pinion 8, namely via the compression spring 12, the ends of which engage the sleeve 30 on the one hand and on the rotary element 40 on the other hand in a force-fitting and / or positive manner.
  • the compression spring 12 is e.g. with its last turn held non-positively and / or positively in a bore 41 of the sleeve 30, e.g.
  • the rotary element 40 is continuously driven via the sleeve 30, which is constantly driven by the pinion 8, and the compression spring 12, which is thus driven continuously in a rotating manner, both in the drilling working position and in the percussion drilling and chiseling working position of the rotary hammer 1.
  • the rotary element 40 is located thus always in rotation.
  • the rotary element 40 is spatially upstream of the end 37 of the connecting channel 35, in particular the bore 36, which opens out into the gear chamber 32, the rotary element 40 being able to cover this end 37 in the radial direction.
  • the rotation element 40 is formed from an approximately hat-shaped cover cap 42 which has an end wall 43, an adjoining, approximately cylindrical jacket 44 and an annular flange 45 adjoining the jacket 44.
  • the cover cap 42 engages over the projection 28 of the housing part 13 in the first embodiment with both an axial and a radial distance.
  • the end wall 43 radially covers the end 37 of the bore 36.
  • the cap 42 contains at least one passage 46, for example a bore, in the end wall 43. Dashed lines in FIG. 2 indicate that the cover cap 42 may additionally or instead also include a passage 47 in its jacket 44. Via the respective passage 46, 47, the gear chamber 32 communicates with the interior 48, which is enclosed by the cover cap 42, and via the interior 48 with the end 37 of the connecting channel 35, in particular the bore 36, opening out therein.
  • the considerable overpressure that forms during operation due to heating in the gear chamber 32 can be reduced through the passage 46, 47, the interior 48 and the bore 36 to the atmosphere or to the engine compartment 31, at the same time avoiding the lubricant contained in the gear chamber 32, in particular grease, can escape from the gear chamber 32 in this way and reach the atmosphere or the engine compartment 31, for example. It is thus achieved with simple means and in a cost-effective manner, a reliable sealing of the gear chamber 32 with simultaneous venting, wherein leakage of lubricant, in particular grease, and thus any loss of lubricant is avoided.
  • the rotary element 40 is part of the axial bearing 14, via which the compression spring 12 of the sleeve 30 is axially supported and rotatably supported with the right end in FIG. 2 on the housing part 13.
  • the axial bearing 14 is designed as a roller bearing, in particular a ball bearing. It contains 49 bearing bodies 50 in a bearing cage, e.g. in the form of balls.
  • the axial bearing 14 is supported on the housing part 13 by means of a bearing ring 51 on which the bearing bodies 50 run.
  • the rotary element 40 in particular the cover cap 42, forms a bearing surface 52 on the axial ring surface of the ring flange 45 facing the bearing bodies 50, which bearing surface essentially corresponds to that of the bearing ring 51 and on which the bearing bodies 50 run.
  • the rotary element 40 is instead formed from a disk.
  • the second exemplary embodiment differs from the first with regard to the design of the axial bearing 114, which is designed as a plain bearing in the second exemplary embodiment.
  • the axial bearing 114 has a sliding disc 160, which is axially supported on the housing part 113 via a sealing element 161.
  • the rotary element 140 in particular in the form of the cover cap 142, is axially supported and supported on the sliding disk 160 by the bearing surface 152 provided on the ring flange 145.
  • a sliding sleeve 162 is arranged, which is integral with the sliding washer 160 and centers the cover cap 142 on the projection 128.
  • the sliding disc 160 is pressed onto the projection 128 and the sealing element 161. As shown in FIG. 3, the bore 136, which connects the gear chamber 132 to the atmosphere or to the engine compartment 131, can be reduced to the smallest possible passage cross section in the region of the projection 128 and the centering sleeve 162.
  • the rotating element 140 has at least one radial or tangential groove 163 in the area of the bearing surface 152, which opens radially or tangentially outwards into the gear chamber 132. Furthermore, in the area of the bearing surface 152, the rotary element 140 has a centrifugal device 164 on its circumference, which is formed, for example, from an axially projecting, annular skirt 165.
  • the apron 165 is designed as a truncated cone ring, the inner surface 166 of which widens approximately in the shape of a truncated cone in the axial direction directed towards the housing part 113. Due to the groove 163 and the centrifugal device 164, the sealing and centrifugal effect is further increased.
  • the groove 163 serves as a return groove for any lubricant from the interior 148 radially outward back into the gear chamber 132.
  • the end face of the end wall 143 always remains free of lubricant, in particular grease, due to the centrifugal force during the rotation of the rotary element 140 .
  • lubricant contrary to expectations, pass through a passage 146, 147 in penetrate the interior 148, the lubricant is thrown outwards due to the rotation against the inner surface of the jacket 144, along which the lubricant travels to the axial bearing 114, in particular to the sliding disk 160.
  • the lubricant can then reach the outside radially via the at least one groove 163 and is thrown out and back into the gear chamber 132 via the approximately angular skirt 165. In this case, too, the lubricant penetrating into the interior 148 cannot get into the bore 136.
  • the configuration of the axial bearing 114 as a plain bearing in the second exemplary embodiment in FIG. 3 is even simpler and even more economical than the first exemplary embodiment.
  • the right end of the compression spring 112 is held on a shoulder 167 of larger diameter, the shoulder 167 being e.g. has radially directed driving surface 168 against which the end 169 of the spring 112 can bear in a form-fitting manner, so that the rotatingly driven spring 112 positively entrains and drives the rotary element 140 in one direction of rotation via this end 169 and the driving surface 168.
  • the right end of the compression spring 112 can also be clamped and thus non-positively connected to the rotary element 140 such that the continuously driven compression spring 112 drives the rotary element 140.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Handwerkzeugmaschine, insbesondere einen Bohrhammer, nach dem Oberbegriff des Anspruchs 1. Eine derartige Handwerkzeugmaschine ist aus der FR-A-2 546 802 bekannt.The invention relates to a hand tool, in particular a rotary hammer, according to the preamble of claim 1. Such a hand tool is known from FR-A-2 546 802.

In der DE-A-33 29 005 und DE-A-40 00 822 ist eine Handwerkzeugmaschine beschrieben, bei der der Getrieberaum durch einen Gehauseteil mit darin enthaltenem Kugellager für das vom Motor angetriebene Ritzel vom Motorraum getrennt ist. Das Kugellager ist beidseitig mit Dichtscheiben versehen und kann auf der dem Getrieberaum zugewandten Seite zusätzlich noch mit einer am Lagerinnenring befestigten Schleuderscheibe versehen sein, um eine Abdichtung des Getrieberaumes zum Motorraum hin zu fördern.DE-A-33 29 005 and DE-A-40 00 822 describe a hand power tool in which the gear chamber is separated from the engine compartment by a housing part with a ball bearing for the pinion driven by the motor. The ball bearing is provided with sealing washers on both sides and can also be provided on the side facing the transmission space with a centrifugal disc attached to the bearing inner ring in order to promote sealing of the transmission space from the engine compartment.

Durch Erwärmung im Betrieb der Handwerkzeugmaschine entwickelt sich im Getrieberaum ein erheblicher Überdruck, der bei der bekannten Handwerkzeugmaschine durch die vorhandenen Dichtelemente, insbesondere bei Schlagbetrieb, nicht ohne Verlust an Schmiermittel, insbesondere Fett, abgebaut werden kann.As a result of heating during operation of the hand-held power tool, a considerable overpressure develops in the gearbox, which in the known hand-held power tool due to the sealing elements present, in particular during impact operation, does not result in a loss of lubricant, in particular grease. can be broken down.

Aus der FR-A-2 546 802 ist bereits ein gattungsgemäßer Bohrhammer bekannt, dessen Getrieberaum über einen Verbindungskanal zur Atmosphäre hin entlüftet ist. Um zu vermeiden, daß Schmiermittel durch den Verbindungskanal nach außen dringen kann, ist ein zusätzliches Gehäuse vorgesehen, welches Öffnungen zum Getrieberaum aufweist und die getrieberaumseitige Mündung des Verbindungskanals abdeckt.A drill hammer of the generic type is already known from FR-A-2 546 802, the gear chamber of which is vented to the atmosphere via a connecting channel. In order to avoid that lubricant can penetrate through the connecting channel to the outside, an additional housing is provided which has openings to the gear chamber and covers the mouth of the connecting channel on the gear box side.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Handwerkzeugmaschine mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß durch die bei der Rotation des Rotationselements entstehenden Fliehkräfte ein Eintritt von Schmiermittel in den Verbindungskanal verhindert wird.The hand tool according to the invention with the characterizing features of claim 1 has the advantage that the entry of lubricant into the connecting channel is prevented by the centrifugal forces generated during the rotation of the rotary element.

Durch die in den abhängigen Ansprüchen 2 - 10 aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Handwerkzeugmaschine möglich. Der Verbindungskanal, insbesondere die Bohrung, die den Getrieberaum mit der Atmospähre und/oder dem Motorraum verbindet,ermöglicht in einfacher und kostengünstiger Weise einen Druckabbau im Getrieberaum.Advantageous developments and improvements of the hand-held power tool specified in claim 1 are possible through the measures listed in the dependent claims 2-10. The connecting channel, in particular the bore, which connects the transmission space to the atmosphere and / or the engine compartment, enables pressure to be reduced in the transmission space in a simple and inexpensive manner.

Zeichnungdrawing

Die Erfindung ist nachfolgend anhand von in den Zeichnungen gezeigten Ausführungsbeispielen näher erläutert. Es zeigen:

Fig. 1
einen schematischen Schnitt eines Bohrhammers gemäß einem ersten Ausführungsbeispiel,
Fig. 2
einen schematischen Schnitt einer Einzelheit des Bohrhammers in Fig. 1 in demgegenüber größerem Maßstab,
Fig. 3
einen schematischen Schnitt,etwa entsprechend demjenigen in Fig. 2,eines zweiten Ausführungsbeispieles.
The invention is explained in more detail below with reference to exemplary embodiments shown in the drawings. Show it:
Fig. 1
2 shows a schematic section of a rotary hammer according to a first exemplary embodiment,
Fig. 2
1 shows a schematic section of a detail of the hammer drill in FIG. 1 on a larger scale,
Fig. 3
a schematic section, approximately corresponding to that in Fig. 2, of a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Fig. 1 und 2 ist schematisch ein motorisch betriebener Bohrhammer 1 gezeigt, der so ausgebildet ist und arbeitet, wie in der DE-A-33 29 005 und DE-A-40 00 822 im einzelnen beschrieben ist, auf die ausdrücklich zum Zwecke der Offenbarung und zur Vermeidung unnötiger Wiederholungen verwiesen wird. Der Bohrhammer 1 enthält in einem Gehäuse 2 einen elektrischen Motor 3, ein Getriebe 4, ein als Luftpolsterschlagwerk ausgebildetes Schlagwerk 5 und eine Werkzeugaufnahme 6, in die ein für den jeweiligen Anwendungszweck geeignetes Werkzeug 7 einsetzbar ist. Der Motor 3 hat ein Ritzel 8, das stets in Eingriff mit einem äußeren Zahnkranz 9 eines Kupplungszahnrades 10 steht, das Teil einer Hülse 30 ist. Das Zahnrad 10 weist an seiner Stirnseite eine Verzahnung 11 auf. Es steht unter der Wirkung einer Druckfeder 12, die ihrerseits gegen ein an einem Gehäuseteil 13 anliegendes Axiallager 14 abgestützt ist. Die Verzahnung 11 am Ende der Hülse 30 kann in eine Gegenverzahnung 15 an einer Taumelnabe 29 des Schlagwerks 5 eingreifen und bildet mit dieser zusammen eine Kupplung 11/15.1 and 2, a motor-operated rotary hammer 1 is shown schematically, which is designed and works as described in detail in DE-A-33 29 005 and DE-A-40 00 822, to which expressly for the purpose the disclosure and to avoid unnecessary repetition. The hammer drill 1 contains in a housing 2 an electric motor 3, a gear 4, a striking mechanism 5 designed as an air cushion percussion mechanism and one Tool holder 6 into which a tool 7 suitable for the respective application can be inserted. The motor 3 has a pinion 8, which is always in engagement with an outer ring gear 9 of a clutch gear 10, which is part of a sleeve 30. The gear wheel 10 has a toothing 11 on its end face. It is under the action of a compression spring 12, which in turn is supported against an axial bearing 14 bearing against a housing part 13. The toothing 11 at the end of the sleeve 30 can engage in a counter toothing 15 on a wobble hub 29 of the striking mechanism 5 and together with this forms a coupling 11/15.

Das Kupplungszahnrad 10 ist in der Taumelnabe 29 gelagert. Innerhalb der Taumelnabe 29 und Hülse 30 verläuft eine Zwischenwelle 17. Im Kupplungszahnrad 10 ist ein Nadellager 16 eingepreßt, wobei das Kupplungszahnrad 10 und die Zwischenwelle 17 im Bereich des Nadellagers 16 relativ verschiebbar sind.
Die Zwischenwelle 17 weist einen verdickten Mittelteil 18 auf, an dessen dem Kupplungszahnrad 10 zugewandter rechter Seite eine Gegenverzahnung 19 angeordnet ist, die mit der Verzahnung 11 eine Kupplung 11/19 bildet. Am anderen Ende des Mittelteils 18 ist eine Längsverzahnung 20 angebracht, die mit ihrem dem Kupplungszahnrad 10 abgewandten linken Ende in eine drehfest mit dem Gehäuse 2 verbundene Zahnscheibe 21 einrückbar ist. Das linke Ende der Zwischenwelle 17 ist in einem im Gehäuse 2 sitzenden Nadellager 22 axial verschieblich gelagert. Auf das Mittelteil 18 ist im Anschluß an die Längsverzahnung 20 ein Kugellager 23 aufgepreßt, an dessen Außenring 24 ein Schaltstück 25 zur Axialverschiebung der Zwischenwelle 17 angreift.The clutch gear 10 is supported in the wobble hub 29. An intermediate shaft 17 runs inside the wobble hub 29 and sleeve 30. A needle bearing 16 is pressed into the clutch gear 10, the clutch gear 10 and the intermediate shaft 17 being relatively displaceable in the region of the needle bearing 16.
The intermediate shaft 17 has a thickened central part 18, on the right side facing the clutch gear 10 of which a counter toothing 19 is arranged, which forms a clutch 11/19 with the toothing 11. At the other end of the middle part 18 there is a longitudinal toothing 20 which, with its left end facing away from the clutch gearwheel 10, can be inserted into a toothed disk 21 which is connected to the housing 2 in a manner fixed against relative rotation. The left end of the intermediate shaft 17 is axially displaceably mounted in a needle bearing 22 seated in the housing 2. A ball bearing 23 is pressed onto the middle part 18 following the longitudinal toothing 20, on the outer ring 24 of which a switching element 25 engages for the axial displacement of the intermediate shaft 17.

Im Gehäuse 2 ist auf der in Fig. 1 rechten Seite ein Motorraum 31 ausgebildet, in dem der elektrische Motor 3 enthalten ist, und auf der in Fig. 1 sich links anschließenden Seite ein Getrieberaum 32, in dem das Getriebe 4, das Schlagwerk 5 und die übrigen bereits erläuterten Elemente enthalten sind. Der Gehäuseteil 13 trennt den Motorraum 31 vom Getrieberaum 32. Das Ritzel 8 erstreckt sich durch den Gehäuseteil 13 hindurch in den Getrieberaum 32 und ist innerhalb des Gehäuseteils 13 mittels eines Kugellagers 26 gelagert. Das Kugellager 26 weist, wie nicht besonders hervorgehoben ist, beidseitig Dichtscheiben auf und auf der zum Getrieberaum 32 weisenden Seite außerdem eine Schleuderscheibe 27, die drehfest mit dem Innenring des Kugellagers 26 verbunden ist. Ferner ist das Kugellager 26 mit Schiebesitz im Gehäuseteil 13 gehalten, wobei zwischen dem Außenring und dem Gehäuseteil 13 ein O-Ring 54 angeordnet ist. Diese Ausbildung des Kugellagers 26 mit beidseitigen Dichtscheiben, Schleuderscheibe 27 und O-Ring 54 soll in diesem Bereich eine Abdichtung des Getrieberaumes 32 zum Motorraum 31 hin fördern. Der weiteren Abdichtung dient ein O-Ring 33.In the housing 2, on the right side in FIG. 1, an engine compartment 31 is formed, in which the electric motor 3 is contained, and on the side adjoining on the left in FIG. 1, a transmission compartment 32, in which the transmission 4, the striking mechanism 5 and the other elements already explained are included. The housing part 13 separates the engine compartment 31 from the gear compartment 32. The pinion 8 extends through the Housing part 13 into the gear chamber 32 and is mounted within the housing part 13 by means of a ball bearing 26. The ball bearing 26, as is not particularly emphasized, has sealing disks on both sides and, on the side facing the transmission space 32, also has a centrifugal disk 27 which is connected in a rotationally fixed manner to the inner ring of the ball bearing 26. Furthermore, the ball bearing 26 is held with a sliding fit in the housing part 13, an O-ring 54 being arranged between the outer ring and the housing part 13. This design of the ball bearing 26 with double-sided sealing disks, centrifugal disk 27 and O-ring 54 is intended to promote a seal of the gear chamber 32 to the engine compartment 31 in this area. An O-ring 33 serves for further sealing.

Der Bohrhammer 1 weist eine Druckausgleichseinrichtung 34 auf, die insbesondere in Fig. 2 im Detail dargestellt und anhand dieser nachfolgend näher erläutert ist. Die Druckausgleichseinrichtung 34 ermöglicht einen Abbau des im Betrieb im Getrieberaum 32 entstehenden Druckes und somit einen Druckausgleich. Bekanntlich entwickelt sich im Betrieb des Bohrhammers 1 vor allem im Getrieberaum 32 Wärme, insbesondere dann, wenn der Bohrhammer 1 im Schlagbetrieb arbeitet. Durch die Erwärmung im Getrieberaum 32 entwickelt sich ein erheblicher Überdruck, der mittels der Druckausgleichseinrichtung 34 abgebaut werden kann, und dies mit Vorteil ohne Schmiermittelverlust innerhalb des Getrieberaumes 32.The rotary hammer 1 has a pressure compensation device 34, which is shown in detail in particular in FIG. 2 and is explained in more detail below with reference to this. The pressure compensation device 34 enables a reduction in the pressure generated in operation in the gear chamber 32 and thus pressure compensation. As is known, heat develops during operation of the rotary hammer 1, especially in the gear chamber 32, in particular when the rotary hammer 1 operates in impact mode. Due to the heating in the gear chamber 32, a considerable excess pressure develops, which can be reduced by means of the pressure compensation device 34, and this advantageously with no loss of lubricant within the gear chamber 32.

Die Druckausgleichseinrichtung 34 verbindet mit Vorteil den Getrieberaum 32 mit dem Motorraum 31 und nimmt einen Druckausgleich des Getrieberaumes 32 zum Motorraum 31 hin vor. Hierzu weist die Druckausgleichseinrichtung 34 mindestens einen Verbindungskanal 35 zwischen dem Getrieberaum 32 und dem Motorraum 31 auf. Teil der Druckausgleichseinrichtung 34, insbesondere des Verbindungskanales 35, ist mindestens eine im Gehäuseteil 13 enthaltene Bohrung 36, die mit einem Ende 37 in den Getrieberaum 32 und mit ihrem anderen Ende 38 in den Motorraum 31 ausmündet und vorteilhafterweise parallel zur Achse des Ritzels 8 durch den Gehäuseteil 13 hindurchläuft. Der Gehäuseteil 13 weist im Bereich der Hülse 30 mit endseitigem Kupplungszahnrad 10, der Druckfeder 12 und der Zwischenwelle 17 einen zum Getrieberaum 32 vorstehenden Vorsprung 28, z.B. Stift, auf, der einstückiger Teil des Gehäuseteils 13 ist und durch den die mindestens eine Bohrung 36 hindurchläuft, wobei deren getrieberaumseitiges Ende 37 im Bereich der Stirnseite 39 dieses Vorsprunges 28 ausmündet.The pressure compensation device 34 advantageously connects the gear chamber 32 to the engine compartment 31 and carries out a pressure compensation of the gear compartment 32 to the engine compartment 31. For this purpose, the pressure compensation device 34 has at least one connecting channel 35 between the gear chamber 32 and the engine compartment 31. Part of the pressure compensation device 34, in particular the connecting channel 35, is at least one bore 36 contained in the housing part 13, which ends at one end 37 in the gear chamber 32 and at the other end 38 in the engine compartment 31 and advantageously parallel to the axis of the pinion 8 through the Housing part 13 runs through. The housing part 13 has in the area of the sleeve 30 with the coupling gear 10 at the end, the compression spring 12 and the intermediate shaft 17 a protrusion 28, for example a pin, which projects towards the gear chamber 32, which is an integral part of the housing part 13 and through which the at least one bore 36 runs , whose end 37 on the gearbox space ends in the region of the end face 39 of this projection 28.

In Fig. 1 und 2 ist angedeutet,daß alternativ oder zusätzlich der Getrieberaum 32 nach außen,zur Atmosphäre, entlüftet sein kann. Hierzu dient ein nur gestrichelt angedeuteter Kanal 36', z.B. eine Bohrung, im Gehäuseteil 13, der nach außen führt, gegebenenfalls durch das Gehäuse 2 hindurch oder in sonstiger Weise. Der Kanal 36' schließt an den in Fig. 2 links davon verlaufenden Bohrungsabschnitt der Bohrung 36 an.1 and 2 it is indicated that, alternatively or additionally, the gear chamber 32 can be vented to the outside, to the atmosphere. A channel 36 ', which is only indicated by dashed lines, a hole in the housing part 13, which leads to the outside, possibly through the housing 2 or in some other way. The channel 36 ′ adjoins the bore section of the bore 36 running to the left in FIG. 2.

Die Druckausgleichseinrichtung 34 weist ferner im Getrieberaum 32 ein ständig umlaufend angetriebenes Rotationselement 40 auf, mittels dessen im Getrieberaum 32 befindliches Schmiermittel infolge Fliehkraft radial nach außen schleuderbar ist. Das Rotationselement 40 ist mittels der vom Ritzel 8 ständig angetriebenen Hülse 30 des Getriebes 4 angetrieben, und zwar über die Druckfeder 12, deren Enden an der Hülse 30 einerseits und am Rotationselement 40 andererseits kraftschlüssig und/oder formschlüssig angreifen. Mit dem in Fig. 2 linken Endbereich ist die Druckfeder 12 z.B. mit ihrer letzten Windung kraftschlüssig und/oder formschlüssig in einer Bohrung 41 der Hülse 30 gehalten, z.B. festgeklemmt. Das in Fig. 2 rechte,andere Ende der Druckfeder 12, z.B. deren letzte Windung oder ein Teil dieser, ist kraftschlüssig und/oder formschlüssig auf einem Abatz des Rotationselements 40 gehalten. Auf diese Weise wird über die vom Ritzel 8 ständig angetriebene Hülse 30 und die somit ständig umlaufend angetriebene Druckfeder 12 das Rotationselement 40 ständig angetrieben, und zwar sowohl in der Arbeitsstellung Bohren als auch in der Arbeitsstellung Schlagbohren und Meißeln des Bohrhammers 1. Das Rotationselement 40 befindet sich somit immer in Rotation.The pressure compensation device 34 also has in the gear chamber 32 a continuously rotating rotary element 40, by means of which lubricant located in the gear chamber 32 can be thrown radially outwards as a result of centrifugal force. The rotary element 40 is driven by means of the sleeve 30 of the transmission 4, which sleeve is constantly driven by the pinion 8, namely via the compression spring 12, the ends of which engage the sleeve 30 on the one hand and on the rotary element 40 on the other hand in a force-fitting and / or positive manner. With the left end region in Fig. 2, the compression spring 12 is e.g. with its last turn held non-positively and / or positively in a bore 41 of the sleeve 30, e.g. clamped. The other right end of the compression spring 12, e.g. the last turn or part thereof is held on a shoulder of the rotary element 40 in a force-fitting and / or form-fitting manner. In this way, the rotary element 40 is continuously driven via the sleeve 30, which is constantly driven by the pinion 8, and the compression spring 12, which is thus driven continuously in a rotating manner, both in the drilling working position and in the percussion drilling and chiseling working position of the rotary hammer 1. The rotary element 40 is located thus always in rotation.

Das Rotationselement 40 ist dem in den Getrieberaum 32 ausmündenden Ende 37 des Verbindungskanals 35, insbesondere der Bohrung 36, räumlich mit axialem Abstand davon vorgelagert, wobei das Rotationselement 40 dieses Ende 37 in Radialrichtung überdecken kann.The rotary element 40 is spatially upstream of the end 37 of the connecting channel 35, in particular the bore 36, which opens out into the gear chamber 32, the rotary element 40 being able to cover this end 37 in the radial direction.

Das Rotationselement 40 ist aus einer etwa hutförmigen Abdeckkappe 42 gebildet, die eine Stirnwand 43, einen sich daran anschließenden, etwa zylindrischen Mantel 44 und einen an den Mantel 44 anschließenden Ringflansch 45 aufweist. Die Abdeckkappe 42 übergreift den Vorsprung 28 des Gehäuseteils 13 beim ersten Ausführungsbeispiel mit sowohl axialem als auch radialem Abstand. Die Stirnwand 43 überdeckt radial das Ende 37 der Bohrung 36. Bei Rotation des ständig angetriebenen Rotationselements 40 in Gestalt der Abdeckkappe 42 bleibt die zum Getrieberaum 32 weisende Seite der Stirnwand 43 in Folge der Fliehkraft ständig schmiermittelfrei, z.B. fettfrei. Das Schmiermittel wird aufgrund der Rotation auf der Stirnwand 43 radial nach außen geschleudert.The rotation element 40 is formed from an approximately hat-shaped cover cap 42 which has an end wall 43, an adjoining, approximately cylindrical jacket 44 and an annular flange 45 adjoining the jacket 44. The cover cap 42 engages over the projection 28 of the housing part 13 in the first embodiment with both an axial and a radial distance. The end wall 43 radially covers the end 37 of the bore 36. When the continuously driven rotary element 40 in the form of the cover cap 42 rotates, the side of the end wall 43 facing the gear chamber 32 remains constantly lubricant-free, e.g. fat free. The lubricant is thrown radially outward due to the rotation on the end wall 43.

Die Abdeckkappe 42 enthält in der Stirnwand 43 mindestens einen Durchlaß 46, z.B. eine Bohrung. Gestrichelt ist in Fig. 2 angedeutet, daß die Abdeckkappe 42 zusätzlch oder statt dessen auch in ihrem Mantel 44 einen Durchlaß 47 enthalten kann. Über den jeweiligen Durchlaß 46, 47 steht der Getrieberaum 32 mit dem Innenraum 48, der von der Abdeckkappe 42 umschlossen ist, und über den Innenraum 48 mit dem darin ausmündenden Ende 37 des Verbindungskanals 35, insbesondere der Bohrung 36, in Verbindung. Somit kann der im Betrieb aufgrund Erwärmung im Getrieberaum 32 sich bildende erhebliche Überdruck über den Durchlaß 46,47,den Innenraum 48 und die Bohrung 36 zur Atmosphäre oder zum Motorraum 31 hin abgebaut werden, wobei zugleich vermieden ist, daß im Getrieberaum 32 enthaltenes Schmiermittel, insbesondere Fett,auf diesem Wege aus dem Getrieberaum 32 entweichen und etwa in die Atmosphäre bzw. in den Motorraum 31 gelangen kann. Es ist somit mit einfachen Mitteln und auf kostengünstige Weise eine zuverlässige Abdichtung des Getrieberaumes 32 bei gleichzeitiger Entlüftung dieses erreicht, wobei ein Austritt von Schmiermittel, insbesondere Fett, und somit ein etwaiger Schmiermittelverlust, vermieden ist. Sollte im Betrieb Schmiermittel evtl. doch durch den Durchlaß 46,47 in den Innenraum 48 eindringen, so wird das Schmiermittel aufgrund des ständig rotierenden Rotationselementes 40 und somit aufgrund der Fliehkraft innerhalb der Abdeckkappe 42 gegen die Innenseite des Mantels 44 geschleudert, wobei das Schmiermittel allenfalls entlang des Mantels 44 bis hin zum Axiallager 14 gelangen kann und dort radial aufgrund der Fliehkraft wieder in den Getrieberaum 32 zurückgefördert wird. Auf keinen Fall kann Schmiermittel, welches über den Durchlaß 46,47 in den Innenraum 48 gelangt, in die Bohrung 36 eindringen.The cap 42 contains at least one passage 46, for example a bore, in the end wall 43. Dashed lines in FIG. 2 indicate that the cover cap 42 may additionally or instead also include a passage 47 in its jacket 44. Via the respective passage 46, 47, the gear chamber 32 communicates with the interior 48, which is enclosed by the cover cap 42, and via the interior 48 with the end 37 of the connecting channel 35, in particular the bore 36, opening out therein. Thus, the considerable overpressure that forms during operation due to heating in the gear chamber 32 can be reduced through the passage 46, 47, the interior 48 and the bore 36 to the atmosphere or to the engine compartment 31, at the same time avoiding the lubricant contained in the gear chamber 32, in particular grease, can escape from the gear chamber 32 in this way and reach the atmosphere or the engine compartment 31, for example. It is thus achieved with simple means and in a cost-effective manner, a reliable sealing of the gear chamber 32 with simultaneous venting, wherein leakage of lubricant, in particular grease, and thus any loss of lubricant is avoided. Should lubricant possibly penetrate through the passage 46, 47 into the interior 48 during operation, the lubricant will be caused by the constantly rotating Rotation element 40 and thus thrown due to the centrifugal force within the cap 42 against the inside of the shell 44, the lubricant can possibly reach along the shell 44 up to the thrust bearing 14 and is radially returned to the gear chamber 32 due to the centrifugal force. Under no circumstances can lubricant, which enters the interior 48 via the passage 46, 47, penetrate into the bore 36.

In besonders einfacher Ausgestaltung ist das Rotationselement 40 Teil des Axiallagers 14, über das die Druckfeder 12 der Hülse 30 mit dem in Fig. 2 rechten Ende axial am Gehäuseteil 13 abgestützt und drehbar gelagert ist. Beim ersten Ausführungsbeispiel gemäß Fig. 1 und 2 ist das Axiallager 14 als Wälzlager, insbesondere Kugellager, ausgebildet. Es enthält in einem Lagerkäfig 49 Lagerkörper 50,z.B. in Form von Kugeln. Am Gehäuseteil 13 ist das Axiallager 14 mittels eines Lagerringes 51, auf dem die Lagerkörper 50 laufen, abgestützt. Das Rotationselement 40, insbesodere die Abdeckkappe 42, bildet auf der den Lagerkörpern 50 zugewandten axialen Ringfläche des Ringflansches 45 eine Lagerfläche 52, die derjenigen des Lagerringes 51 im wesentlichen entspricht und auf der die Lagerkörper 50 laufen.In a particularly simple embodiment, the rotary element 40 is part of the axial bearing 14, via which the compression spring 12 of the sleeve 30 is axially supported and rotatably supported with the right end in FIG. 2 on the housing part 13. 1 and 2, the axial bearing 14 is designed as a roller bearing, in particular a ball bearing. It contains 49 bearing bodies 50 in a bearing cage, e.g. in the form of balls. The axial bearing 14 is supported on the housing part 13 by means of a bearing ring 51 on which the bearing bodies 50 run. The rotary element 40, in particular the cover cap 42, forms a bearing surface 52 on the axial ring surface of the ring flange 45 facing the bearing bodies 50, which bearing surface essentially corresponds to that of the bearing ring 51 and on which the bearing bodies 50 run.

Bei einem anderen, nicht gezeigten Ausführungsbeispiel ist das Rotationselement 40 statt dessen aus einer Scheibe gebildet.In another embodiment, not shown, the rotary element 40 is instead formed from a disk.

Bei dem in Fig. 3 gezeigten zweiten Ausführungsbeispiel sind für die Teile, die dem ersten Ausführungsbeispiel gemäß Fig. 1 und 2 entsprechen, um 100 größere Bezugszeichen verwendet, so daß dadurch zur Vermeidung von Wiederholungen auf die Beschreibung des ersten Ausführungsbeispieles Bezug genommen ist.In the second exemplary embodiment shown in FIG. 3, 100 larger reference numerals are used for the parts which correspond to the first exemplary embodiment according to FIGS. 1 and 2, so that reference is made to the description of the first exemplary embodiment in order to avoid repetition.

Das zweite Ausführungsbeispiel unterscheidet sich vom ersten hinsichtlich der Ausbildung des Axiallagers 114, das beim zweiten Ausführungsbeispiel als Gleitlager ausgebildet ist. Das Axiallager 114 weist eine Gleitscheibe 160 auf, die über ein Dichtelement 161 axial am Gehäuseteil 113 abgestützt ist. Das Rotationselement 140, insbesondere in Gestalt der Abdeckkappe 142, ist mit der am Ringflansch 145 vorgesehenen Lagerfläche 152 an der Gleitscheibe 160 axial abgestützt und gelagert. Im Radialraum zwischen dem Vorsprung 128, z.B. Stift, des Gehäuseteils 113 und dem Mantel 144 der Abdeckkappe 142 ist eine Gleithülse 162 angeordnet, die mit der Gleitscheibe 160 einstückig ist und die Abdeckkappe 142 auf dem Vorsprung 128 zentriert. Die Gleitscheibe 160 ist auf den Vorsprung 128 und das Dichtelement 161 gepreßt. Wie Fig. 3 zeigt, kann die Bohrung 136, die den Getrieberaum 132 mit der Atmospähre oder mit dem Motorraum 131 verbindet, im Bereich des Vorsprunges 128 und der zentrierenden Hülse 162 auf den kleinstmöglichen Durchlaßquerschnitt reduziert werden.The second exemplary embodiment differs from the first with regard to the design of the axial bearing 114, which is designed as a plain bearing in the second exemplary embodiment. The axial bearing 114 has a sliding disc 160, which is axially supported on the housing part 113 via a sealing element 161. The rotary element 140, in particular in the form of the cover cap 142, is axially supported and supported on the sliding disk 160 by the bearing surface 152 provided on the ring flange 145. In the radial space between the projection 128, e.g. Pin, the housing part 113 and the jacket 144 of the cover cap 142, a sliding sleeve 162 is arranged, which is integral with the sliding washer 160 and centers the cover cap 142 on the projection 128. The sliding disc 160 is pressed onto the projection 128 and the sealing element 161. As shown in FIG. 3, the bore 136, which connects the gear chamber 132 to the atmosphere or to the engine compartment 131, can be reduced to the smallest possible passage cross section in the region of the projection 128 and the centering sleeve 162.

Das Rotationselement 140 weist im Bereich der Lagerfläche 152 zumindest eine radiale oder tangentiale Nut 163 auf, die radial oder tangential nach außen in den Getrieberaum 132 ausmündet. Ferner weist das Rotationselement 140 im Bereich der Lagerfläche 152 auf seinem Umfang eine Schleudereinrichtung 164 auf, die z.B. aus einer axial überstehenden, ringförmigen Schürze 165 gebildet ist. Die Schürze 165 ist als Kegelstumpfring ausgebildet, dessen innere Fläche 166 sich in der zum Gehäuseteil 113 gerichteten Achsrichtung etwa kegelstumpfförmig erweitert. Aufgrund der Nut 163 und der Schleudereinrichtung 164 wird der Dicht- und Schleudereffekt noch gesteigert. Die Nut 163 dient als Rückfördernut für etwaiges Schmiermittel aus dem Innenraum 148 radial nach außen zurück in den Getrieberaum 132. Auch bei diesem zweiten Ausführungsbeispiel bleibt die Stirnseite der Stirnwand 143 in Folge der Fliehkraft bei der Rotation des Rotationselements 140 stets frei von Schmiermittel, insbesondere Fett. Sollte Schmiermittel wider Erwarten doch durch einen Durchlaß 146, 147 in den Innenraum 148 eindringen, so wird das Schmiermittel aufgrund der Rotation nach außen geschleudert gegen die Innenfläche des Mantels 144, längs der das Schmiermittel zum Axiallager 114, insbesondere zur Gleitscheibe 160,wandert. Das Schmiermittel kann sodann über die mindestens eine Nut 163 radial nach außen gelangen und wird über die etwa winkelige Schürze 165 heraus und zurück in den Getrieberaum 132 geschleudert. Somit kann auch in diesem Fall das in den Innenraum 148 eindringende Schmiermittel nicht in die Bohrung 136 gelangen.The rotating element 140 has at least one radial or tangential groove 163 in the area of the bearing surface 152, which opens radially or tangentially outwards into the gear chamber 132. Furthermore, in the area of the bearing surface 152, the rotary element 140 has a centrifugal device 164 on its circumference, which is formed, for example, from an axially projecting, annular skirt 165. The apron 165 is designed as a truncated cone ring, the inner surface 166 of which widens approximately in the shape of a truncated cone in the axial direction directed towards the housing part 113. Due to the groove 163 and the centrifugal device 164, the sealing and centrifugal effect is further increased. The groove 163 serves as a return groove for any lubricant from the interior 148 radially outward back into the gear chamber 132. In this second exemplary embodiment too, the end face of the end wall 143 always remains free of lubricant, in particular grease, due to the centrifugal force during the rotation of the rotary element 140 . Should lubricant, contrary to expectations, pass through a passage 146, 147 in penetrate the interior 148, the lubricant is thrown outwards due to the rotation against the inner surface of the jacket 144, along which the lubricant travels to the axial bearing 114, in particular to the sliding disk 160. The lubricant can then reach the outside radially via the at least one groove 163 and is thrown out and back into the gear chamber 132 via the approximately angular skirt 165. In this case, too, the lubricant penetrating into the interior 148 cannot get into the bore 136.

Die Ausgestaltung des Axiallagers 114 als Gleitlager beim zweiten Ausführungsbeispiel in Fig. 3 ist im Vergleich zum ersten Ausführungsbeispiel noch einfacher und noch kostengünstiger.The configuration of the axial bearing 114 as a plain bearing in the second exemplary embodiment in FIG. 3 is even simpler and even more economical than the first exemplary embodiment.

Beim zweiten Ausführungsbeispiel in Fig. 3 ist das dort rechte Ende der Druckfeder 112 auf einem im Durchmesser größeren Absatz 167 gehalten, wobei der Absatz 167 eine z.B. radial gerichtete Mitnahmefläche 168 aufweist, an der das Ende 169 der Feder 112 formschlüssig anliegen kann, so daß die umlaufend angetriebene Feder 112 über dieses Ende 169 und die Mitnahmefläche 168 das Rotationselement 140 in der einen Drehrichtung formschlüssig mitnimmt und antreibt. Statt dessen kann z.B. so wie beim ersten Ausführungsbeispiel in Fig. 1 und 2 das rechte Ende der Druckfeder 112 auch klemmend und somit kraftschlüssig mit dem Rotationselement 140 derart verbunden sein, daß darüber die ständig angetriebene Druckfeder 112 das Rotationselement 140 antreibt.In the second embodiment in FIG. 3, the right end of the compression spring 112 is held on a shoulder 167 of larger diameter, the shoulder 167 being e.g. has radially directed driving surface 168 against which the end 169 of the spring 112 can bear in a form-fitting manner, so that the rotatingly driven spring 112 positively entrains and drives the rotary element 140 in one direction of rotation via this end 169 and the driving surface 168. Instead, e.g. 1 and 2, the right end of the compression spring 112 can also be clamped and thus non-positively connected to the rotary element 140 such that the continuously driven compression spring 112 drives the rotary element 140.

Claims (10)

  1. Powered hand tool, particularly a hammer drill, having a housing (2) and an electric drive motor (3), contained in a motor space (31, 131) of the housing (2), for driving a pinion (8; 108) which extends through a housing part (13; 113) into a gear space (32; 132) and meshes there with a gear (4) for driving a tool holder (6), and also a pressure-compensating device (34; 134) which reduces a pressure arising in the gear space (32; 132) during operation and has a connecting channel (35; 135) for venting the gear space (32; 132), one end (37; 137) of the connecting channel (35; 135), which end (37; 137) leads out into the gear space (32; 132), being covered by a cover (42; 142) which has at least one passage (46, 47; 146, 147) leading to the connecting channel (35; 135), characterized in that the cover (42; 142) is designed as a rotary element (40; 140) which can be driven in a rotating manner relative to the housing (2).
  2. Powered hand tool according to Claim 1, characterized in that the connecting channel (35; 135) leads with its other end (38; 138) into the atmosphere and/or into the motor space (31; 131).
  3. Powered hand tool according to Claim 1 or 2, characterized in that the connecting channel (35; 135) is provided as a bore (36, 36'; 136) having a bore section running approximately parallel to the axis of the pinion (8; 108) through the housing part (13; 113).
  4. Powered hand tool according to one of the preceding claims, characterized in that the rotary element (40; 140) is located spatially at an axial distance in front of the end (37; 137), leading out into the gear space (32; 132), of the connecting channel (35; 135), in particular the bore (36, 36'; 136), and covers this end (37; 137) in the radial direction.
  5. Powered hand tool according to one of the preceding claims, characterized in that the cover (42; 142) is formed by a roughly hat-shaped cover cap, and the connecting channel (35; 135) is accommodated in a, for example pin-shaped, projection (28, 128) of the housing part (13; 113).
  6. Powered hand tool according to one of the preceding claims, characterized in that the rotary element (40; 140) is mounted relative to the housing part (13; 113) in an axial bearing surface (52; 152).
  7. Powered hand tool according to Claim 6, characterized in that the rotary element (140) has at least one groove (163) in the area of the bearing surface (152), which groove (163) leads radially or tangentially outwards into the gear space (132).
  8. Powered hand tool according to Claim 6 or 7, characterized in that the rotary element (140) has a centrifugual device (164) on its periphery in the area of the bearing surface (152).
  9. Powered hand tool according to Claim 8, characterized in that the centrifugal device (164) is formed from an axially projecting annular apron (165).
  10. Powered hand tool according to one of the preceding claims, characterized in that the rotary element (40; 140) can be driven by means of a compression spring (12; 112), the ends of which act in a frictional and/or positive-locking manner on the rotary element (40; 140) on the one hand and on a sleeve (30; 130) which can be driven by the drive pinion (8; 108) on the other hand.
EP93114799A 1992-09-24 1993-09-15 Hand tool machine, particularly a hammer drill Expired - Lifetime EP0589337B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4231987 1992-09-24
DE4231987A DE4231987A1 (en) 1992-09-24 1992-09-24 Hand tool, in particular rotary hammer

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EP0589337A1 EP0589337A1 (en) 1994-03-30
EP0589337B1 true EP0589337B1 (en) 1996-08-21

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DE59303491D1 (en) 1996-09-26
DE4231987A1 (en) 1994-03-31
EP0589337A1 (en) 1994-03-30

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