EP1677950A1 - Percussion device for a hand machine tool - Google Patents

Percussion device for a hand machine tool

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Publication number
EP1677950A1
EP1677950A1 EP04762744A EP04762744A EP1677950A1 EP 1677950 A1 EP1677950 A1 EP 1677950A1 EP 04762744 A EP04762744 A EP 04762744A EP 04762744 A EP04762744 A EP 04762744A EP 1677950 A1 EP1677950 A1 EP 1677950A1
Authority
EP
European Patent Office
Prior art keywords
drive piston
gear
circular
driven
stroke
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04762744A
Other languages
German (de)
French (fr)
Other versions
EP1677950B1 (en
Inventor
Friedmar Dresig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1677950A1 publication Critical patent/EP1677950A1/en
Application granted granted Critical
Publication of EP1677950B1 publication Critical patent/EP1677950B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/10—Means for driving the impulse member comprising a cam mechanism
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body

Definitions

  • the invention relates to a striking mechanism for a hand tool, in particular for a hammer drill, hammer or impact drill, according to the preamble of claim 1.
  • the drive piston which is axially displaceable in the guide tube is connected by means of a connecting rod to a crank pin of a crankshaft which can be driven by the drive shaft of an electric motor via a pinion gear.
  • the crank mechanism sets the drive piston in a reciprocating motion.
  • the stroke of the drive piston over time shows an almost sinusoidal course.
  • the time course of the pressure in the compression chamber results from the relative path between the drive piston and racket and is determined by the sinusoidal course of the stroke of the drive piston.
  • the pressure curve is characterized by a briefly high peak value and a relatively long period of low pressure.
  • the basic pressure curve is shown in Fig. 3 curve a.
  • the high peak pressure in the compression space leads to a high load on the compression space and to a relatively high effort for sealing the compression space in the guide tube, which increases disproportionately with increasing pressure.
  • the pressure curve in the compression chamber caused by the sinusoidal stroke of the drive piston also means that the drive energy made available by the drive piston is not effectively used to evenly pressurize the club and therefore the optimum club speed for rapid drilling progress is not achieved.
  • the striking mechanism according to the invention for a hand machine tool with the features of claim 1 has the advantage that an almost arbitrary course of the stroke of the drive piston can be set by means of the non-circular gear pair, depending on how the pitch curves of the two gear wheels are designed.
  • the design of the pitch curves depends exclusively on the
  • the pitch curves can e.g. B. be calculated so that the racket receives a maximum speed with a minimal pressure load on the compression space. They can also be calculated in such a way that with a minimal pressure load in the compression chamber and at the same time high speed of the racket, only a minimal drive torque is required for the drive piston.
  • further optimization goals are possible through the design of the generating curve.
  • the principle goal of the design of the pitch curves is to deliver a high amount of energy to the tool with a low power consumption, i.e. a significant increase in efficiency.
  • Advantageous further developments and improvements of the striking mechanism specified in claim 1 are possible through the measures listed in the further claims.
  • FIG. 2 is a perspective view of the drive piston and gear of the striking mechanism in FIG. 1,
  • Fig. 3 is a diagram of the pressure over time in the compression space of the striking mechanism in the prior art (curve a) and in the striking mechanism according to the invention (curve b).
  • the striking mechanism for a hand-held power tool for example, for a hammer drill, a hammer or an impact drill, shown partially in section in FIG .
  • the mutually facing end faces of drive piston 11 and striker 12 delimit a compression space 14 in the guide tube 13, in which an air cushion is enclosed.
  • the guide tube 13 is arranged in a housing of the handheld power tool, not shown here.
  • the axis of the guide tube 13 is aligned with the axis one Tool holder in which a tool, for example an impact drill, is partially held.
  • the tool either protrudes with its tool shaft into the guide tube 13 or, as here, is aligned axially to a firing pin 15 which is guided in the guide tube 13 so as to be axially displaceable.
  • An electric motor 16 is arranged in the housing of the hand-held power tool, which, via a gear 17, sets the drive piston 11 in a reciprocating, axial stroke movement in the guide tube 13.
  • the gear 17 has two intermeshing non-circular gears 18, 19, of which one non-circular gear 18 is a driving and the other non-circular gear 19 is a driven non-circular gear.
  • Each non-circular gear 18, 19 has an axis of rotation 20 and 21, respectively.
  • the two axes of rotation 20, 21 are arranged at a fixed distance a from one another.
  • the driving non-circular gear 18 is non-rotatably seated on a bearing in the housing
  • the driven non-circular gear 19 is rotatably mounted in the housing about its axis of rotation 21.
  • a piston rod 23 which acts as a crank or connecting rod, is articulated eccentrically with respect to the axis of rotation 21
  • Drive piston 11 is pivotally connected.
  • the end of the piston rod 23 on the piston side engages a pivot pin 24, which is received transversely to the axis of the guide tube 13 in the drive piston 11 at its end remote from the compression space 14.
  • the drive piston 11 is shown in its one stroke end position, in Fig. 2 in its other stroke end position.
  • the drive piston 11 When the electric motor 16 is switched on, the drive piston 11 is set into a reciprocating, axial lifting movement via the gear 17, the air cushion in the compression space 14 being alternately compressed and relaxed.
  • the club 12 is accelerated by the compression pressure and releases its energy to the tool via the firing pin 15.
  • the temporal The course of the pressure in the compression chamber 14 depends on the relative path between the drive piston 11 and the striker 12 and is essentially determined by the time course of the stroke of the drive piston 11.
  • the pitch curves 181 and 191 of the non-circular gear 18 and non-circular gear 19, which have the same number of teeth are designed in such a way that the stroke of the drive piston 11 shows the desired time profile.

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

Abstract

The invention relates to a percussion device for a hand machine tool, in particular, a hammer drill, a paving breaker or an impact driller, comprising a drive piston (11), arranged for axial displacement in a guide tube, driven by motor in a reciprocating back and forth axial motion, by means of a gear (17) and a striker, acting on a tool, housed such as to be displaced axially in the guide tube and defining a compression chamber with an enclosed air cushion, along with the drive piston (11). According to the invention, a free configuration of the time course for the reciprocating motion of the drive piston (11), for the purposes of optimisation, for example, reduction of the peak pressure in the compression chamber, may be achieved, whereby the gear (17) comprises two engaging non-circular gearwheels (18, 19), the rotation axes (20, 21) of which are arranged at a fixed separation (a) from each other. The one driving non-circular gearwheel (18) is driven by motor and a connecting rod (23), connected to the drive piston (11), is connected, eccentrically to the rotation axis (21) of the non-circular gearwheel (19) as driven by the non-circular gearwheel (18).

Description

Schlagwerk für eine HandwerkzeugmaschineStriking mechanism for a hand machine tool
Stand der TechnikState of the art
Die Erfindung geht aus von einem Schlagwerk für eine Handwerkzeugmaschine, insbesondere für einen Bohrhammer, Schlaghammer oder eine Schlagbohrmaschine, nach dem Oberbegriff des Anspruchs 1.The invention relates to a striking mechanism for a hand tool, in particular for a hammer drill, hammer or impact drill, according to the preamble of claim 1.
Bei einer bekannten Handwerkzeugmaschine, z.B. Bohr- oder Schlaghammer (DE 35 11 437 A1) ist der im Führungsrohr axial verschiebliche Antriebskolben mittels eines Pleuels mit einem Kurbelzapfen einer Kurbelwelle verbunden, die über ein Ritzelgetriebe von der Antriebswelle eines Elektromotors antreibbar ist. Mit Einschalten des Elektromotors versetzt der Kurbeltrieb den Antriebskolben in eine hin- und hergehende Bewegung. Der Hubweg des Antriebskolbens über der Zeit zeigt dabei einen nahezu sinusförmigen Verlauf. Bei der Hubbewegung des Antriebskolbens entsteht im Kompressionsraum zwischen Antriebskolben und Schläger abwechselnd ein Über- und Unterdruck, wodurch der Schläger in Richtung des Werkzeugs beschleunigt wird. Der zeitliche Verlauf des Drucks im Kompressionsraum ergibt sich aus dem Relativweg zwischen Antriebskolben und Schläger und wird durch den sinusförmigen Verlauf des Hubs des Antriebskolbens bestimmt. Der Druckverlauf zeichnet sich durch einen kurzeitig hohen Spitzenwert und einen relativ langen Zeitabschnitt mit niedrigem Druck aus. Der prinzipielle Druckverlauf ist in Fig. 3 Kurve a dargestellt.In a known hand-held power tool, for example a hammer drill or percussion hammer (DE 35 11 437 A1), the drive piston which is axially displaceable in the guide tube is connected by means of a connecting rod to a crank pin of a crankshaft which can be driven by the drive shaft of an electric motor via a pinion gear. When the electric motor is switched on, the crank mechanism sets the drive piston in a reciprocating motion. The stroke of the drive piston over time shows an almost sinusoidal course. During the stroke movement of the drive piston, there is an alternating overpressure and underpressure in the compression space between the drive piston and the striker, which accelerates the striker in the direction of the tool. The time course of the pressure in the compression chamber results from the relative path between the drive piston and racket and is determined by the sinusoidal course of the stroke of the drive piston. The pressure curve is characterized by a briefly high peak value and a relatively long period of low pressure. The basic pressure curve is shown in Fig. 3 curve a.
Der hohe Spitzendruck im Kompressionsraum führt zu einer hohen Belastung des Kompressionsraums und zu einem relativ hohen Aufwand für die Abdichtung des Kompressionsraums im Führungsrohr, der mit zunehmendem Druck überproportional anwächst. Der durch den sinusförmigen Hub des Antriebskolbens bedingte Druckverlauf im Kompressionsraum führt außerdem dazu, dass die vom Antriebskolben zur Verfügung gestellte Antriebsenergie nicht effektiv zu einer gleichmäßigen Druckbeaufschlagung des Schlägers genutzt wird und damit die optimale Schlägergeschwindigkeit für einen schnellen Bohrfortschritt nicht erreicht wird.The high peak pressure in the compression space leads to a high load on the compression space and to a relatively high effort for sealing the compression space in the guide tube, which increases disproportionately with increasing pressure. The pressure curve in the compression chamber caused by the sinusoidal stroke of the drive piston also means that the drive energy made available by the drive piston is not effectively used to evenly pressurize the club and therefore the optimum club speed for rapid drilling progress is not achieved.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Schlagwerk für eine Handwerkzeugmaschine mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass mittels des Unrundzahnrad- Paars ein nahezu beliebiger Verlauf des Hubwegs des Antriebskolbens eingestellt werden kann, je nachdem, wie die Wälzkurven der beiden Zahnräder ausgelegt werden. Die Auslegung der Wälzkurven hängt dabei ausschließlich von demThe striking mechanism according to the invention for a hand machine tool with the features of claim 1 has the advantage that an almost arbitrary course of the stroke of the drive piston can be set by means of the non-circular gear pair, depending on how the pitch curves of the two gear wheels are designed. The design of the pitch curves depends exclusively on the
Optimierungsziel ab. Die Wälzkurven können z. B. so berechnet werden, dass der Schläger bei einer minimalen Druckbelastung des Kompressionsraums eine maximale Geschwindigkeit erhält. Sie können auch so berechnet werden, dass bei einer minimalen Druckbelastung im Kompressionsraum bei gleichzeitig hoher Geschwindigkeit des Schlägers nur ein minimales Antriebsmoment für den Antriebskolben gefordert wird. Neben diesen Beispielen sind weitere Optimierungsziele durch die Wälzkurvenauslegung möglich. Prinzipielles Ziel der Auslegung der Wälzkurven ist die Abgabe einer hohen Energie an das Werkzeug bei einer niedrigen Leistungsaufnahme, also eine deutliche Erhöhung des Wirkungsgrads. Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Schlagwerks möglich.Optimization target. The pitch curves can e.g. B. be calculated so that the racket receives a maximum speed with a minimal pressure load on the compression space. They can also be calculated in such a way that with a minimal pressure load in the compression chamber and at the same time high speed of the racket, only a minimal drive torque is required for the drive piston. In addition to these examples, further optimization goals are possible through the design of the generating curve. The principle goal of the design of the pitch curves is to deliver a high amount of energy to the tool with a low power consumption, i.e. a significant increase in efficiency. Advantageous further developments and improvements of the striking mechanism specified in claim 1 are possible through the measures listed in the further claims.
Zeichnungdrawing
Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiels in der nachfolgenden Beschreibung näher erläutert. Es zeigen in prinzipieller Darstellung:The invention is explained in more detail in the following description with reference to an embodiment shown in the drawing. In principle, they show:
Fig. 1 ein Schlagwerk für eine Handwerkzeugmaschine, teilweise geschnitten,1 a striking mechanism for a hand tool, partially cut,
Fig. 2 eine perspektivische Darstellung von Antriebskolben und Getriebe des Schlagwerks in Fig. 1 ,2 is a perspective view of the drive piston and gear of the striking mechanism in FIG. 1,
Fig. 3 ein Diagramm des zeitlichen Druckverlaufs im Kompressionsraum des Schlagwerks beim Stand der Technik (Kurve a) und bei dem erfindungsgemäßen Schlagwerk (Kurve b).Fig. 3 is a diagram of the pressure over time in the compression space of the striking mechanism in the prior art (curve a) and in the striking mechanism according to the invention (curve b).
Beschreibung des AusführungsbeispielsDescription of the embodiment
Das in Fig. 1 als Prinzipskizze teilweise geschnitten dargestellte Schlagwerk für eine Handwerkzeugmaschine, z.B. für einen Bohrhammer, einen Schlaghammer oder eine Schlagbohrmaschine, weist einen Antriebskolben 11 und einen Schläger 12 auf, die axial hintereinander in einem Führungsrohr 13 aufgenommen und darin axial verschieblich geführt sind. Die einander zugekehrten Stirnseiten von Antriebskolben 11 und Schläger 12 begrenzen einen Kompressionsraum 14 im Führungsrohr 13, in dem ein Luftpolster eingeschlossen ist. Das Führungsrohr 13 ist in einem hier nicht dargestellten Gehäuse der Handwerkzeugmaschine angeordnet. Die Achse des Führungsrohr 13 fluchtet mit der Achse einer Werkzeugaufnahme, in dem ein Werkzeug, z.B. ein Schlagbohrer, teilweise gehalten ist. Das Werkzeug ragt entweder mit seinem Werkzeugschaft in das Führungsrohr 13 hinein oder ist - wie hier - axial fluchtend zu einem Schlagbolzen 15 ausgerichtet, der im Führungsrohr 13 axial verschieblich geführt ist.The striking mechanism for a hand-held power tool, for example, for a hammer drill, a hammer or an impact drill, shown partially in section in FIG , The mutually facing end faces of drive piston 11 and striker 12 delimit a compression space 14 in the guide tube 13, in which an air cushion is enclosed. The guide tube 13 is arranged in a housing of the handheld power tool, not shown here. The axis of the guide tube 13 is aligned with the axis one Tool holder in which a tool, for example an impact drill, is partially held. The tool either protrudes with its tool shaft into the guide tube 13 or, as here, is aligned axially to a firing pin 15 which is guided in the guide tube 13 so as to be axially displaceable.
Im Gehäuse der Handwerkzeugmaschine ist ein Elektromotor 16 angeordnet, der über ein Getriebe 17 den Antriebskolben 11 in eine hin- und hergehende, axiale Hubbewegung im Führungsrohr 13 versetzt. Das Getriebe 17 weist zwei miteinander kämmende Unrundzahnräder 18 , 19 auf, von denen das eine Unrundzahnrad 18 ein treibendes und das andere Unrundzahnrad 19 ein angetriebenes Unrundzahnrad ist. Jedes Unrundzahnrad 18, 19 besitzt eine Drehachse 20 bzw. 21. Die beiden Drehachsen 20, 21 sind in einem festen Abstand a voneinander angeordnet. In dem dargestellten Ausführungsbeispiel sitzt das treibende Unrundzahnrad 18 drehfest auf einer im Gehäuse gelagertenAn electric motor 16 is arranged in the housing of the hand-held power tool, which, via a gear 17, sets the drive piston 11 in a reciprocating, axial stroke movement in the guide tube 13. The gear 17 has two intermeshing non-circular gears 18, 19, of which one non-circular gear 18 is a driving and the other non-circular gear 19 is a driven non-circular gear. Each non-circular gear 18, 19 has an axis of rotation 20 and 21, respectively. The two axes of rotation 20, 21 are arranged at a fixed distance a from one another. In the illustrated embodiment, the driving non-circular gear 18 is non-rotatably seated on a bearing in the housing
Vorgelegewelle 25 und zwischen der Abtriebswelle 22 des Elektromotors 16 und . der Vorlegewelle 25 ist ein Zwischengetriebe 26 angeordnet. Das angetriebene Unrundzahnrad 19 ist im Gehäuse um seine Drehachse 21 drehbar gelagert. An dem angetriebenen Unrundzahnrad 19 ist exzentrisch zur Drehachse 21 eine als Kurbel oder Pleuel wirkende Kolbenstange 23 angelenkt, die mit demLayshaft 25 and between the output shaft 22 of the electric motor 16 and. the intermediate shaft 25, an intermediate gear 26 is arranged. The driven non-circular gear 19 is rotatably mounted in the housing about its axis of rotation 21. On the driven non-circular gear 19, a piston rod 23, which acts as a crank or connecting rod, is articulated eccentrically with respect to the axis of rotation 21
Antriebskolben 11 schwenkbeweglich verbunden ist. Das kolbenseitige Ende der Kolbenstange 23 greift hierzu an einem Drehbolzen 24 an, der quer zur Achse des Führungsrohrs 13 im Antriebskolben 11 an dessen vom Kompressionsraum 14 abgekehrten Ende aufgenommen ist. In Fig. 1 ist der Antriebskolben 11 in seiner einen Hubendstellung, in Fig. 2 in seiner anderen Hubendstellung dargestellt.Drive piston 11 is pivotally connected. For this purpose, the end of the piston rod 23 on the piston side engages a pivot pin 24, which is received transversely to the axis of the guide tube 13 in the drive piston 11 at its end remote from the compression space 14. In Fig. 1, the drive piston 11 is shown in its one stroke end position, in Fig. 2 in its other stroke end position.
Mit Einschalten des Elektromotors 16 wird der Antriebskolben 11 über das Getriebe 17 in eine hin- und hergehende, axiale Hubbewegung versetzt, wobei das Luftpolster im Kompressionsraum 14 abwechselnd komprimiert und entspannt wird. Durch den Kompressionsdruck wird der Schläger 12 beschleunigt und gibt seine Energie über den Schlagbolzen 15 an das Werkzeug ab. Der zeitliche Verlauf des Drucks im Kompressionsraum 14 hängt dabei vom Relativweg zwischen Antriebskolben 11 und Schläger 12 ab und wird im wesentlichen durch den zeitlichen Verlauf des Hubs des Antriebskolbens 11 bestimmt. Um einen optimierten Weg-Zeit-Verlauf des Antriebskolbens 11 darstellen zu können, sind die Wälzkurven 181 und 191 von Unrundzahnrad 18 und Unrundzahnrad 19, die die gleiche Zähnezahl tragen, so gestaltet, dass der Hubweg des Antriebskolbens 11 den gewünschten zeitlichen Verlauf zeigt. Eine Optimierungsmöglichkeit besteht darin, die Wälzkurven 181 , 191 der beiden Unrundzahnräder 18, 19 so zu berechnen, dass bei minimaler Druckbelastung im Kompressionsraum der Schläger 12 eine maximale Geschwindigkeit erhält. In Fig. 3 zeigt die Kurve b den zeitlichen Druckverlauf im Kompressionsraum 14 bei einer solchen Auslegung der beiden Unrundzahnräder 18, 19. Wie deutlich zu sehen ist, sind gegenüber dem Druckverlauf gemäß Kurve a, der bei einer herkömmlichen nahezu sinusförmigen Hubbewegung des Antriebskolbens 11 nach dem Stand der Technik erreicht wird, die Druckspitzen abgebaut und wird eine gleichmäßigere Druckverteilung über eine längeren Zeitraum erzielt. Die hohe Schlägergeschwindigkeit bleibt dabei erhalten.When the electric motor 16 is switched on, the drive piston 11 is set into a reciprocating, axial lifting movement via the gear 17, the air cushion in the compression space 14 being alternately compressed and relaxed. The club 12 is accelerated by the compression pressure and releases its energy to the tool via the firing pin 15. The temporal The course of the pressure in the compression chamber 14 depends on the relative path between the drive piston 11 and the striker 12 and is essentially determined by the time course of the stroke of the drive piston 11. In order to be able to represent an optimized path-time profile of the drive piston 11, the pitch curves 181 and 191 of the non-circular gear 18 and non-circular gear 19, which have the same number of teeth, are designed in such a way that the stroke of the drive piston 11 shows the desired time profile. One possibility for optimization is to calculate the pitch curves 181, 191 of the two non-circular gears 18, 19 in such a way that the racket 12 receives a maximum speed with a minimal pressure load in the compression space. In FIG. 3, curve b shows the pressure curve over time in the compression chamber 14 in the case of such a configuration of the two non-circular gears 18, 19. As can clearly be seen, compared to the pressure curve according to curve a, the drive piston 11 follows after a conventional almost sinusoidal stroke movement the prior art is achieved, the pressure peaks are reduced and a more uniform pressure distribution is achieved over a longer period of time. The high racquet speed is maintained.
Mit dem neuartigen Getriebe lässt sich durch entsprechende Auslegung der Wälzkurven 181 , 191 der Unrundzahnräder 18, 19 je nach Optimierungsziel ein guter Bohrfortschritt bzw. Meißelabtrag, eine geringere Leistungsaufnahme und eine gleichmäßigere Stromaufnahme erreichen. Die Handwerkzeugmaschine zeigt insgesamt eine geringere Vibration. With the new type of gear, depending on the optimization goal, a good drilling progress or chisel removal, a lower power consumption and a more uniform power consumption can be achieved by appropriate design of the rolling curves 181, 191 of the non-circular gears 18, 19. The handheld machine tool shows a lower vibration overall.

Claims

Ansprüche Expectations
1. Schlagwerk für eine Handwerkzeugmaschine, insbesondere Bohrhammer, Schlaghammer oder Schlagbohrmaschine, mit einem in einem Führungsrohr (13) axial verschieblich angeordneten Antriebskolben (11), der motorisch über ein Getriebe (17) in eine hin- und hergehende, axiale Hubbewegung versetzbar ist, mit einem auf ein Werkzeug wirkenden Schläger (12), der im Fuhrungsrohr (13) axial verschieblich aufgenommen . ist, und mit einem von Antriebskolben (11) und Schläger (12) begrenzten Kompressionsraum (14), in dem ein Luftpolster eingeschlossen ist, dadurch gekennzeichnet, dass das Getriebe (17) zwei miteinander kämmende Unrundzahnräder (18, 19) aufweist, deren Drehachsen (20, 21 ) in einem festen Abstand (a) voneinander angeordnet sind, und dass das eine, treibende Unrundzahnrad (18) motorisch antreibbar ist und an dem anderen, vom treibenden Unrundzahnrad (18) angetriebenen Unrundzahnrad (19) eine mit dem Antriebskolben (11 ) verbundene Kolbenstange (23) exzentrisch zu dessen Drehachse (21) angelenkt ist.1. striking mechanism for a hand-held power tool, in particular rotary hammer, hammer or hammer drill, with a drive piston (11) which is axially displaceably arranged in a guide tube (13) and which can be set in a reciprocating axial stroke movement by means of a gear (17), with a racket (12) acting on a tool which is axially displaceably received in the guide tube (13). and with a compression space (14) delimited by drive piston (11) and racket (12), in which an air cushion is enclosed, characterized in that the gear (17) has two intermeshing non-circular gears (18, 19), the axes of rotation of which (20, 21) are arranged at a fixed distance (a) from each other, and that one driving non-circular gear (18) can be driven by a motor and on the other non-circular gear (19) driven by the driving non-circular gear (18) one with the drive piston ( 11) connected piston rod (23) is articulated eccentrically to its axis of rotation (21).
2. Schlagwerk nach Anspruch 1 , dadurch gekennzeichnet, dass die Wälzkurven (181 , 191) der beiden Unrundzahnräder (18, 19) so gestaltet sind, dass der Hubweg des Antriebskolbens (11) einen gewünschten zeitlichen Verlauf hat. 2. Impact mechanism according to claim 1, characterized in that the pitch curves (181, 191) of the two non-circular gears (18, 19) are designed so that the stroke of the drive piston (11) has a desired time profile.
3. Schlagwerk nach Anspruch 2, dadurch gekennzeichnet, dass der zeitliche Verlauf des Hubwegs des Antriebskolbens (11) so festgelegt ist, dass eine hohe Schlägergeschwindigkeit bei minimalem Kompressionsdruck im Kompressionsraum (14) erzielbar ist.3. Percussion mechanism according to claim 2, characterized in that the time course of the stroke of the drive piston (11) is set such that a high racket speed can be achieved with minimal compression pressure in the compression space (14).
4. Schlagwerk nach Anspruch 2, dadurch gekennzeichnet, dass der zeitliche Verlauf des Hubwegs des Antriebskolbens (11) so festgelegt ist, dass eine hohe Schlägergeschwindigkeit bei minimaler aufgenommener elektrischer Energie erzielbar ist.4. percussion mechanism according to claim 2, characterized in that the time course of the stroke of the drive piston (11) is set so that a high racket speed can be achieved with minimal electrical energy absorbed.
5. Schlagwerk nach einem der Ansprüche 1 - 4, dadurch gekennzeichnet, dass die beiden Unrundzahnräder (18, 19) eine gleiche Zähnezahl aufweisen. 5. Impact mechanism according to one of claims 1-4, characterized in that the two non-circular gears (18, 19) have the same number of teeth.
EP04762744A 2003-10-17 2004-09-03 Percussion device for a hand machine tool Expired - Lifetime EP1677950B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10348397A DE10348397A1 (en) 2003-10-17 2003-10-17 Schlagwerk for a hand tool
PCT/DE2004/001957 WO2005044521A1 (en) 2003-10-17 2004-09-03 Percussion device for a hand machine tool

Publications (2)

Publication Number Publication Date
EP1677950A1 true EP1677950A1 (en) 2006-07-12
EP1677950B1 EP1677950B1 (en) 2007-03-07

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04762744A Expired - Lifetime EP1677950B1 (en) 2003-10-17 2004-09-03 Percussion device for a hand machine tool

Country Status (6)

Country Link
US (1) US20060260830A1 (en)
EP (1) EP1677950B1 (en)
CN (1) CN1867429A (en)
DE (2) DE10348397A1 (en)
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US20060260830A1 (en) 2006-11-23
DE502004003181D1 (en) 2007-04-19
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EP1677950B1 (en) 2007-03-07
CN1867429A (en) 2006-11-22
WO2005044521A1 (en) 2005-05-19

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