EP3271115B1 - Hand tool machine and mechanical impact mechanism - Google Patents
Hand tool machine and mechanical impact mechanism Download PDFInfo
- Publication number
- EP3271115B1 EP3271115B1 EP16707048.1A EP16707048A EP3271115B1 EP 3271115 B1 EP3271115 B1 EP 3271115B1 EP 16707048 A EP16707048 A EP 16707048A EP 3271115 B1 EP3271115 B1 EP 3271115B1
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- EP
- European Patent Office
- Prior art keywords
- power tool
- portable power
- tool according
- drive shaft
- shaped guide
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- 230000007246 mechanism Effects 0.000 title claims description 33
- 238000009527 percussion Methods 0.000 claims description 20
- 230000001154 acute effect Effects 0.000 claims description 4
- 230000008878 coupling Effects 0.000 description 6
- 238000010168 coupling process Methods 0.000 description 6
- 238000005859 coupling reaction Methods 0.000 description 6
- 230000002093 peripheral effect Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000005259 measurement Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
- B25B21/026—Impact clutches
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- 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
- B25D11/04—Portable percussive tools with electromotor or other motor drive in which the tool bit or anvil is hit by an impulse member
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- 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
- B25D11/102—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool
- B25D11/104—Means for driving the impulse member comprising a cam mechanism the rotating axis of the cam member being coaxial with the axis of the tool with rollers or balls as cam surface
Definitions
- the present invention relates to a portable power tool with a mechanical percussion mechanism, which has a drive shaft for the rotary drive of the impact mechanism associated with the mechanical striking mechanism.
- the invention has a mechanical percussion to the object, which has a provided with at least one drive cams impactor and provided with at least one output cam output shaft, wherein the at least one drive cam for the striking drive of the output cam is formed in a percussion mode of the mechanical percussion and the impactor cooperates with a drive shaft.
- a rotary impact tool in which a drive shaft is rotationally driven by a rotational drive power source, the drive shaft having an outer peripheral surface and a cam groove formed on the outer peripheral surface.
- a hammer is disposed coaxially with the drive shaft, the hammer having an inner peripheral surface and a cam groove formed on the inner peripheral surface.
- the rotary impact tool has an anvil engageable with the hammer along a rotational direction and a compression spring for axially biasing the hammer in the direction of the anvil or a corresponding tool holder.
- a ball For mechanical coupling between the drive shaft and the hammer a ball is provided, which engages in the cam groove of the drive shaft and in the cam groove of the hammer.
- the hammer is designed in such a way that it can rotate along a rotational location line defined by the cam groove of the drive shaft and the cam groove of the hammer.
- One form of a rotary locus of the hammer is in the advancing direction and the driven direction, respectively formed as a curve in which a pitch angle of the rotational location line changes continuously with the change of the hammer rotation angle.
- An object of the present invention is therefore to provide a hand tool with a hammer mechanism, in which the synchronization between a striker and a drive shaft is at least largely ensured in all operating conditions and which requires a reduced drive torque.
- a hand tool with a mechanical striking mechanism which has a drive shaft for the rotary drive of the impact mechanism associated with the mechanical striking mechanism.
- At least one V-shaped guide groove is provided on an outer circumference of the drive shaft, the baselines of which converge in a connecting section being configured concave-polygonal in the output direction at least in sections.
- the invention thus enables improved synchronization between the drive and driven cams of the mechanical percussion mechanism due to improved progression geometry of the V-shaped guide grooves, so that in particular the risk of wear-increasing, frontal or peripheral collisions between them is considerably reduced.
- the co-operating with the impactor drive shaft is preferably driven via a transmission for speed and torque adjustment of a mains or battery-powered electric motor.
- a driving ball is arranged in the at least one guide groove of the drive shaft, which engages in a driving cut-out formed on an inner circumference of a passage opening of the striking body.
- the connecting portion between the baselines of the V-shaped guide groove is curved at least substantially semicircular.
- the connecting portion has an enlarged radius.
- the baselines on both sides of the connecting portion each have a substantially rectilinear central portion with a first predetermined pitch angle, which is preferably greater than 45 °.
- a substantially rectilinear end section adjoins the two middle sections in each case with a second predetermined pitch angle, which is preferably less than 45 °.
- the first predetermined pitch angle is greater than the second predetermined pitch angle.
- two parallel spaced apart to each baseline of the V-shaped guide groove arranged contour lines converge at an acute point in a connection point.
- the at least one V-shaped guide groove has a substantially semicircular cross-sectional geometry.
- the at least one driving recess is formed in the shape of a hollow-ridge with a base line substantially corresponding to the baseline.
- a mechanical percussion mechanism which has a striker provided with at least one drive cam and an output shaft provided with at least one output cam, wherein the at least one drive cam for the striking drive of the output cam is formed in a percussion mode of the mechanical impact mechanism and the Impactor cooperates with a drive shaft, wherein at least one V-shaped guide groove is provided on an outer periphery of the drive shaft, which converges in a connecting portion Baseline in the output direction are formed at least partially concave-polygonal.
- the drive torque to be applied by a drive motor for operating the percussion mechanism can be reduced along with other positive effects and, consequently, significantly increase the service life of a particularly impact-fed impact wrench.
- there is an improved synchronization between the drive and the output cam of the impact mechanism which among other things leads to a reduction in wear and an increase in the life.
- Fig. 1 shows a hand tool 100, which is equipped with a tool holder 450 and a mechanical impact mechanism 200 according to the invention.
- the handheld power tool 100 has a housing 110 with a handle 126 and, according to one embodiment, is connected mechanically and electrically to a preferably exchangeable battery pack 130 for power supply independent of the mains.
- the hand tool 100 is exemplified as a cordless rotary impact wrench. It should be noted, however, that the present invention is not limited to cordless impact wrenches, but rather may be applied to various power tools in which a tool is rotated and an impact mechanism according to the invention is used, e.g. in a percussion drill, etc., regardless of whether the power tool is independent of the mains with a battery pack or network-dependent operable. In addition, it should be understood that the present invention is not limited to power tool hand tools.
- the drive motor 114 can be actuated, for example via a manual switch 128, ie switched on and off, and can be any type of motor, such as an electronically commutated motor or a DC motor.
- the drive motor 114 is so electronically controlled or controlled that both a reversing operation, as well as specifications with respect to a desired rotational speed can be realized.
- the functioning and the structure of a suitable Drive motor are well known in the art and therefore will not be further described here for the sake of brevity of the description.
- the drive motor 114 is preferably connected via an associated motor shaft 116 to the transmission 118, which converts rotation of the motor shaft 116 into rotation of a drive shaft 120 provided between the transmission 118 and impact mechanism 200. This conversion is preferably such that the drive shaft 120 rotates relative to the motor shaft 116 with increased torque but reduced rotational speed.
- the drive motor 114 is illustratively arranged in a motor housing 115 and the gear 118 in a gear housing 119, wherein the gear housing 119 and the motor housing 115 are arranged in the housing 110 by way of example.
- mechanical percussion 200 is an example arranged in an optional impact mechanism housing 220 rotational or rotational impact, which has a striking body 300 which performs sudden high-intensity rotation pulses and an output cam assembly 410 to an output shaft 400, for example a Output spindle, transmits.
- optional percussion gear housing 220 is merely exemplary in nature and is not intended to limit the invention. This can also be found in striking mechanisms without separate impact mechanism housing application, for example, are arranged directly in the housing 110 of the power tool 100.
- the tool holder 450 is preferably provided, which is preferably designed for receiving insert tools and according to one embodiment, at least with an insert tool 140 with outer polygon coupling 142, but preferably also with an insert tool with polygon socket coupling, eg a socket wrench connectable is.
- the Insert tool 140 is exemplified as a screwdriver bit with the external polygon coupling 142, illustratively a hexagonal coupling formed, which is arranged in a suitable internal receptacle of the tool holder 450.
- Such a screwdriver bit and a suitable socket wrench are sufficiently known from the prior art, so that is omitted here for the purpose of scarcity of the description to a detailed description.
- the impactor 300 is preferably axially biased in the direction of the tool holder 450 and the output shaft 400 by means of a compression spring, not shown.
- the output shaft 400 with the tool holder 450, as well as the striking mechanism 200, the drive shaft 120, the gear 118, the motor shaft 116 and the drive motor 114 are illustratively arranged along a longitudinal central axis 150 in the housing 110 of the power tool 100.
- Fig. 2 shows the drive shaft 120 of Fig. 1 which according to one embodiment has two at least substantially V-shaped guide grooves 162, 164.
- These V-shaped guide grooves 162, 164 are preferably in a preferably cylindrical outer periphery 160 of at least partially hollow cylindrical executed according to an embodiment and coaxial with the longitudinal central axis 150 of Fig. 1 extending drive shaft 120 is formed.
- the hollow cylindrical portion of the drive shaft 120 serves, for example, for receiving a guide element or guide pin of the output shaft 400 of Fig. 1 ,
- the V-shaped guide grooves 162, 164 preferably each have a substantially C-shaped and preferably semicircular cross-sectional geometry.
- each driver ball 166, 168 is added in each guide groove 162, 164 .
- the two driver balls 166, 168 are preferably each to preferably maximally to their respective Equatorialumffiten in the V-shaped guide grooves 162, 164th
- Fig. 3 shows the drive shaft 120 of Fig. 2 to illustrate the formed according to one embodiment, V-shaped guide groove 162 of Fig. 2 .
- the V-shaped guide groove 162 preferably has two baselines 170, 172, which preferably converge in an arcuate, preferably at least approximately semicircular, connecting portion 174 which points in an output direction 176 of the drive shaft 120.
- the connecting portion 174 illustratively has a radius R 1 .
- the symmetrical to the longitudinal center axis 150 of Fig. 1 extending baselines 170, 172 each have one, on both sides of the connecting portion 174 subsequent, preferably at least approximately rectilinear central portion 180, 182 on. At each of these preferably in turn preferably at least approximately rectilinear end portion 184, 186 at a deviating from 180 °, obtuse or elongated angle ⁇ 1 connects.
- the baselines 170, 172 thus have, according to the invention, an at least sectionally concave-polygonal course, ie, the baselines 170, 172 represent two traverses which are "curved" toward one another in the direction of the longitudinal central axis 150 or run towards one another.
- Parallel to each of the two baselines 170, 172 of the V-shaped guide groove 162 extends in each case a contour line 190, 192, which preferably converge at an acute angle in a connection point P 1 opposite the connecting portion 174.
- Fig. 4 shows the preferred cylindrical solid impactor 300 of Fig. 1 which according to one embodiment has a preferably cylindrical passage opening 302. This encloses the longitudinal central axis 150 of Fig. 1 preferably coaxial.
- an inner circumference 304 of the through hole 302 are preferably two driving recesses 306, 308 embedded, preferably each an approximately C- or L-shaped, preferably semi-circular cross-sectional geometry for receiving a respective Mitauerkugel 166.168 of Fig. 2 to preferably at most to their Equatorialumfticianen.
- two drive cams 312, 314 designed in the manner of axial projections are preferably integrally formed, which according to one embodiment are positioned on both sides of the passage opening 302 and diametrically opposite one another.
- the drive cams 312, 314 act in a suitable manner with two output cams, not shown, of the impact mechanism to create the output cam assembly 410 of Fig. 1 together.
- Fig. 5 shows the impactor 300 of Fig. 4 to illustrate the driving cutout 306 formed according to one embodiment of FIG Fig. 4 , This is preferably in the inner circumference 304 of preferably centric to the longitudinal central axis 150 extending through hole 302 formed in the impactor 300.
- the driving recess 306 is preferably corresponding to the cooperating with them V-shaped guide groove 162 and 164 of Fig. 2 formed and has an arcuate, preferably at least approximately semicircular connecting portion 320 having a radius R 2 , to which on both sides in each case a base line 322, 324 connected.
- the latter in each case has a rectilinear middle section 326, 328, which preferably merges into a similarly rectilinear end section 330, 332 at a blunt or extended angle ⁇ 2 , which differs from 180 °.
- the radii R 1 of the V-shaped guide grooves (see. Fig. 2 and Fig. 3 ) and the radii R 2 of the driving recesses 306, 308 are preferably the same size.
- Fig. 6 shows a measurement diagram in which a resulting by the guide groove according to the invention axial displacement S ( ⁇ ) of the impactor 300 of 4 and FIG. 5 in response to a rotational angle ⁇ between the drive shaft 120 of Fig. 2 and Fig. 3 and the impactor 300 each for a conventional linear guide groove and the inventive concave-polygonal guide groove 162 and 164 of Fig. 2 and Fig. 3 is applied.
- ⁇ axial displacement S ( ⁇ ) of the impactor 300 of 4 and FIG. 5 in response to a rotational angle ⁇ between the drive shaft 120 of Fig. 2 and Fig. 3 and the impactor 300 each for a conventional linear guide groove and the inventive concave-polygonal guide groove 162 and 164 of Fig. 2 and Fig. 3 is applied.
- the course of the graph 600 results from the above-described guide groove geometry of the concave-polygonal guide grooves 162 and 164 of FIG Fig. 2 and Fig. 3 and accordingly also has an arcuate connecting portion 602 with a radius R 3 , which corresponds to the connecting portion 174 of FIG Fig. 3 and to each of which an at least approximately rectilinear middle section 604, 606 adjoins, wherein these central sections 604, 606 correspond to the central sections 180, 182 of FIG Fig. 3 correspond.
- An angle ⁇ 1 between an illustrative horizontal axis 612, or a first parallel line drawn illustratively to the horizontal coordinate axis, and both middle sections 604, 606 is preferably greater than 45 ° and is illustratively approximately 55 ° in each case.
- This angle ⁇ 1 is preferably greater than an angle ⁇ 2 between a corresponding horizontal axis 614, or a second parallel line drawn illustratively to the horizontal coordinate axis, and two end sections 608, 610 corresponding to the end sections 184, 186 of FIG Fig. 3 which is preferably less than 45 ° and illustratively about 43 °.
- the radius R 3 preferably corresponds to the radii R 1, 2 of the V-shaped and concave-polygonal guide grooves 162 and 164, respectively Fig. 2 and Fig. 3 the drive shaft 120 of Fig. 2 or the takeaway savings 306,308 of Fig. 4 of the impactor 300 of 4 and FIG. 5 , The same applies to the three angles ⁇ 1, 2, 3 (see in particular. Fig. 3 and Fig. 5 ).
- FIG. 5 illustrates another measuring diagram in which an axial velocity v (t) of the impactor body 300 of FIG. 4 resulting from the guide groove geometry according to the invention is shown in FIG 4 and FIG. 5 depending on the time t in each case for a common linear guide groove and the concave-polygonal guide groove 162 or 164 of Fig. 2 and Fig. 3 is applied.
- v (t) of the impactor body 300 of FIG. 4 resulting from the guide groove geometry according to the invention is shown in FIG 4 and FIG. 5 depending on the time t in each case for a common linear guide groove and the concave-polygonal guide groove 162 or 164 of Fig. 2 and Fig. 3 is applied.
- a dotted graph 700 - compared to the present invention at least partially concave polygonal guide groove 162 and 164 of Fig. 2 and Fig.
- a dashed curve 800 As indicated by a dashed curve 800 - depending on the time plotted on a horizontal coordinate axis t always a lower axial velocity v (t) of the impactor 300 of 4 and FIG. 5 established.
- the section 802, the sections 804, 806 and the sections 808, 810 of the Graphs 800 correspond to the connecting section 602, the middle sections 604, 606 and the end sections 608, 610 of the graph 600 of FIG Fig. 6 ,
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Description
Die vorliegende Erfindung betrifft eine Handwerkzeugmaschine mit einem mechanischen Schlagwerk, die eine Antriebswelle zum drehenden Antrieb eines dem mechanischen Schlagwerk zugeordneten Schlagkörpers aufweist. Darüber hinaus hat die Erfindung ein mechanisches Schlagwerk zum Gegenstand, das einen mit mindestens einem Antriebsnocken versehenen Schlagkörper und eine mit mindestens einem Abtriebsnocken versehene Abtriebswelle aufweist, wobei der mindestens eine Antriebsnocken zum schlagenden Antrieb des Abtriebsnockens in einem Schlagbetrieb des mechanischen Schlagwerks ausgebildet ist und der Schlagkörper mit einer Antriebswelle zusammenwirkt.The present invention relates to a portable power tool with a mechanical percussion mechanism, which has a drive shaft for the rotary drive of the impact mechanism associated with the mechanical striking mechanism. In addition, the invention has a mechanical percussion to the object, which has a provided with at least one drive cams impactor and provided with at least one output cam output shaft, wherein the at least one drive cam for the striking drive of the output cam is formed in a percussion mode of the mechanical percussion and the impactor cooperates with a drive shaft.
Schlagwerke sind aus
Aus der
Nachteilig an diesem Stand der Technik ist unter anderem, dass aufgrund der Geometrie der Kurvennuten eine verschleißerhöhende stirn- oder randseitige Kollision zwischen den Hammernocken und den Ambossnocken möglich ist. Dies bedeutet, dass der Hammer und der Amboss in Abhängigkeit vom Betriebszustand des Drehschlagwerkzeugs in dessen Betrieb häufiger nicht zueinander synchronisiert sind, d.h. außer Eingriff stehen.A disadvantage of this prior art, inter alia, that due to the geometry of the cam grooves, a wear-increasing frontal or edge-side collision between the hammer cam and the anvil cam is possible. This means that the hammer and the anvil are more often not synchronized with each other depending on the operating condition of the rotary impact tool in its operation, i. out of engagement.
Eine Aufgabe der vorliegenden Erfindung ist es daher, eine Handwerkzeugmaschine mit einem Schlagwerk anzugeben, bei dem die Synchronisation zwischen einem Schlagkörper und einer Antriebswelle zumindest weitgehend in allen Betriebszuständen gewährleistet ist und das ein reduziertes Antriebsdrehmoment erfordert.An object of the present invention is therefore to provide a hand tool with a hammer mechanism, in which the synchronization between a striker and a drive shaft is at least largely ensured in all operating conditions and which requires a reduced drive torque.
Dieses Problem wird gelöst durch eine Handwerkzeugmaschine mit einem mechanischen Schlagwerk, die eine Antriebswelle zum drehenden Antrieb eines dem mechanischen Schlagwerk zugeordneten Schlagkörpers aufweist. An einem Außenumfang der Antriebswelle ist mindestens eine V-förmige Führungsnut vorgesehen, deren in einem Verbindungsabschnitt zusammenlaufende Grundlinien in Abtriebsrichtung zumindest abschnittsweise konkav-polygonal ausgebildet sind.This problem is solved by a hand tool with a mechanical striking mechanism, which has a drive shaft for the rotary drive of the impact mechanism associated with the mechanical striking mechanism. At least one V-shaped guide groove is provided on an outer circumference of the drive shaft, the baselines of which converge in a connecting section being configured concave-polygonal in the output direction at least in sections.
Die Erfindung ermöglicht somit aufgrund einer verbesserten Verlaufsgeometrie der V-förmigen Führungsnuten eine verbesserte Synchronisation zwischen Antriebs- und Abtriebsnocken des mechanischen Schlagwerks, so dass insbesondere die Gefahr von verschleißerhöhenden, stirn- oder randseitigen Kollisionen zwischen diesen erheblich reduziert wird. Darüber hinaus reduziert sich ein zum Betrieb des Schlagwerks notwendiges, mechanisches Antriebsdrehmoment. Die mit dem Schlagkörper zusammenwirkende Antriebswelle wird vorzugsweise über ein Getriebe zur Drehzahl- und Drehmomentanpassung von einem netz- oder akkugespeisten Elektromotor angetrieben.The invention thus enables improved synchronization between the drive and driven cams of the mechanical percussion mechanism due to improved progression geometry of the V-shaped guide grooves, so that in particular the risk of wear-increasing, frontal or peripheral collisions between them is considerably reduced. In addition, reduces a necessary for the operation of the impact mechanism, mechanical drive torque. The co-operating with the impactor drive shaft is preferably driven via a transmission for speed and torque adjustment of a mains or battery-powered electric motor.
Vorzugsweise ist in der mindestens einen Führungsnut der Antriebswelle eine Mitnehmerkugel angeordnet, die in eine an einem Innenumfang einer Durchgangsöffnung des Schlagkörpers ausgebildete Mitnahmeaussparung eingreift.Preferably, a driving ball is arranged in the at least one guide groove of the drive shaft, which engages in a driving cut-out formed on an inner circumference of a passage opening of the striking body.
Somit ist eine zuverlässige mechanische Kopplung zwischen der Antriebswelle und dem Schlagkörper unter Aufrechterhaltung einer notwendigen relativen Beweglichkeit zur Erzeugung von im Betrieb erforderlichen, pulsierenden Drehschlägen gegeben.Thus, a reliable mechanical coupling between the drive shaft and the striker while maintaining a necessary relative mobility for generating required in operation, pulsating rotational shocks is given.
Im Fall einer vorteilhaften Ausgestaltung ist der Verbindungsabschnitt zwischen den Grundlinien der V-förmigen Führungsnut zumindest im Wesentlichen halbkreisförmig gekrümmt.In the case of an advantageous embodiment, the connecting portion between the baselines of the V-shaped guide groove is curved at least substantially semicircular.
Durch den vergrößerten Radius des Verbindungsabschnitts erfolgt eine Reduzierung der axialen Geschwindigkeit des Schlagkörpers.Due to the increased radius of the connecting portion, the axial velocity of the impactor is reduced.
Gemäß einer Weiterbildung weist der Verbindungsabschnitt einen vergrößerten Radius auf.According to a development, the connecting portion has an enlarged radius.
Aufgrund des vergleichsweise großen Radius ergibt sich ein verbesserter zeitlicher Verlauf der Bewegungsgeschwindigkeit des Schlagkörpers.Due to the comparatively large radius results in an improved time course of the movement speed of the impactor.
Bevorzugt weisen die Grundlinien beidseits des Verbindungsabschnitts jeweils einen im Wesentlichen geradlinigen Mittelabschnitt mit einem ersten vorgegebenen Steigungswinkel auf, der bevorzugt größer als 45° ist.Preferably, the baselines on both sides of the connecting portion each have a substantially rectilinear central portion with a first predetermined pitch angle, which is preferably greater than 45 °.
Somit ergibt sich eine hohe axiale Beschleunigung des Schlagkörpers und damit einhergehend eine hohe Schlagenergie.This results in a high axial acceleration of the impactor and, consequently, a high impact energy.
Vorzugsweise schließt sich an die beiden Mittelabschnitte jeweils ein im Wesentlichen geradliniger Endabschnitt mit einem zweiten vorgegebenen Steigungswinkel an, der bevorzugt kleiner als 45° ist.Preferably, a substantially rectilinear end section adjoins the two middle sections in each case with a second predetermined pitch angle, which is preferably less than 45 °.
Hierdurch wird die Wahrscheinlichkeit, dass die Antriebsnocken und die Abtriebsnocken miteinander stirn- oder randseitig kollidieren, erheblich reduziert. Bei einer vorteilhaften Ausgestaltung ist der erste vorgegebene Steigungswinkel größer als der zweite vorgegebene Steigungswinkel.As a result, the probability that the drive cam and the output cam collide with each other frontally or peripherally, significantly reduced. In an advantageous embodiment, the first predetermined pitch angle is greater than the second predetermined pitch angle.
Hierdurch ergeben sich optimale Betriebseigenschaften des Schlagwerks im Schlagbetrieb.This results in optimum operating characteristics of the hammer mechanism in impact mode.
Nach Maßgabe einer günstigen Ausgestaltung laufen zwei parallel beabstandet zu jeder Grundlinie der V-förmigen Führungsnut angeordnete Höhenlinien in einem Verbindungspunkt spitzwinklig zusammen.According to a favorable embodiment, two parallel spaced apart to each baseline of the V-shaped guide groove arranged contour lines converge at an acute point in a connection point.
Infolgedessen ergibt sich eine verringerte Reibung der Mitnehmerkugeln innerhalb der Führungsnut beim Passieren des Verbindungspunktes.As a result, there is a reduced friction of the Mitnehmerkugeln within the guide when passing the connection point.
Bevorzugt weist die mindestens eine V-förmige Führungsnut eine im Wesentlichen halbkreisförmige Querschnittsgeometrie auf.Preferably, the at least one V-shaped guide groove has a substantially semicircular cross-sectional geometry.
Hierdurch ergibt sich ein linienhafter, d.h. ein maximal großflächiger Kontakt zwischen der Mitnehmerkugel und der zugehörigen Führungsnut bzw. Mitnehmerausnehmung.This results in a linear, i. a maximum large-area contact between the Mitnehmerkugel and the associated guide or Mitnehmerausnehmung.
Nach Maßgabe einer vorteilhaften Weiterbildung ist die mindestens eine Mitnahmeaussparung hohlkehlförmig mit einer im Wesentlichen korrespondierend zur Grundlinie verlaufenden Basislinie ausgebildet.In accordance with an advantageous further development, the at least one driving recess is formed in the shape of a hollow-ridge with a base line substantially corresponding to the baseline.
Infolgedessen ist im Zusammenwirken mit der V-förmigen Führungsnut eine zuverlässige Führung der Mitnehmerkugeln zwischen der Antriebswelle und dem Schlagkörper gewährleistet.As a result, a reliable guidance of the driving balls between the drive shaft and the impactor is ensured in cooperation with the V-shaped guide groove.
Das Eingangs genannte Problem wird zudem gelöst durch ein mechanisches Schlagwerk, das einen mit mindestens einem Antriebsnocken versehenen Schlagkörper und eine mit mindestens einem Abtriebsnocken versehene Abtriebswelle aufweist, wobei der mindestens eine Antriebsnocken zum schlagenden Antrieb des Abtriebsnockens in einem Schlagbetrieb des mechanischen Schlagwerks ausgebildet ist und der Schlagkörper mit einer Antriebswelle zusammenwirkt, wobei an einem Außenumfang der Antriebswelle mindestens eine V-förmige Führungsnut vorgesehen ist, deren in einem Verbindungsabschnitt zusammenlaufende Grundlinien in Abtriebsrichtung zumindest abschnittsweise konkav-polygonal ausgebildet sind.The problem mentioned at the outset is also solved by a mechanical percussion mechanism which has a striker provided with at least one drive cam and an output shaft provided with at least one output cam, wherein the at least one drive cam for the striking drive of the output cam is formed in a percussion mode of the mechanical impact mechanism and the Impactor cooperates with a drive shaft, wherein at least one V-shaped guide groove is provided on an outer periphery of the drive shaft, which converges in a connecting portion Baseline in the output direction are formed at least partially concave-polygonal.
Aufgrund der erfindungsgemäß polygonal-konkaven Führungsnuten lässt sich neben anderen positiven Effekten das von einem Antriebsmotor zum Betrieb des Schlagwerks aufzubringende Antriebsdrehmoment reduzieren und damit einhergehend die Betriebsdauer eines insbesondere akkugespeisten Schlagschraubers signifikant steigern. Darüber hinaus ergibt sich eine verbesserte Synchronisierung zwischen den Antriebs- und den Abtriebsnocken des Schlagwerks, was unter anderem zu einer Verschleißminderung und einer Erhöhung der Lebensdauer führt.Because of the polygonal-concave guide grooves according to the invention, the drive torque to be applied by a drive motor for operating the percussion mechanism can be reduced along with other positive effects and, consequently, significantly increase the service life of a particularly impact-fed impact wrench. In addition, there is an improved synchronization between the drive and the output cam of the impact mechanism, which among other things leads to a reduction in wear and an increase in the life.
Die Erfindung ist anhand von in den Zeichnungen dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Es zeigen:
- Fig. 1
- eine schematische Darstellung einer Handwerkzeugmaschine, die mit einer Werkzeugaufnahme und einem erfindungsgemäßen mechanischen Schlagwerk ausgestattet ist,
- Fig. 2
- eine perspektivische Teilansicht einer Antriebswelle mit zwei V-förmigen Führungsnuten,
- Fig. 3
- eine Draufsicht auf eine V-förmige Führungsnut der Antriebswelle von
Fig. 2 , - Fig. 4
- eine perspektivische Ansicht eines Schlagkörpers mit einer Durchgangsöffnung,
- Fig. 5
- eine perspektivische Teilansicht des Schlagkörpers von
Fig. 4 mit einer Mitnahmeaussparung, - Fig. 6
- ein Messdiagramm, in dem eine durch die erfindungsgemäße Führungsnutgeometrie resultierende Axialverschiebung des Schlagkörpers von
Fig. 4 und Fig. 5 in Abhängigkeit von einem Drehwinkel zwischen der Antriebswelle vonFig. 2 und Fig. 3 und dem Schlagkörper jeweils für eine gebräuchliche, lineare Führungsnut und eine erfindungsgemäße, konkav-polygonale Führungsnut aufgetragen ist, und - Fig. 7
- ein Messdiagramm, in dem die durch die erfindungsgemäße Führungsnutgeometrie resultierende Axialgeschwindigkeit des Schlagkörpers von
Fig. 4 und Fig. 5 in Abhängigkeit von der Zeit t jeweils für die gebräuchliche, lineare Führungsnut und die erfindungsgemäße, konkav-polygonale Führungsnut illustriert ist.
- Fig. 1
- a schematic representation of a hand tool, which is equipped with a tool holder and a mechanical impact mechanism according to the invention,
- Fig. 2
- a partial perspective view of a drive shaft with two V-shaped guide grooves,
- Fig. 3
- a plan view of a V-shaped guide groove of the drive shaft of
Fig. 2 . - Fig. 4
- a perspective view of a striking body with a through hole,
- Fig. 5
- a partial perspective view of the impactor of
Fig. 4 with a driving cut, - Fig. 6
- a measurement diagram in which a resulting by the guide groove according to the invention axial displacement of the impactor of
4 and FIG. 5 depending on a rotation angle between the drive shaft ofFig. 2 and Fig. 3 and the striker respectively for a common, linear guide groove and a concave-polygonal guide groove according to the invention is applied, and - Fig. 7
- a measurement diagram in which the resultant by the Führungsnutgeometrie invention axial velocity of the impactor of
4 and FIG. 5 depending on the time t in each case for the conventional, linear guide groove and the inventive, concave-polygonal guide groove is illustrated.
Die Handwerkzeugmaschine 100 ist beispielhaft als Akku-Drehschlagschrauber ausgebildet. Es wird jedoch darauf hingewiesen, dass die vorliegende Erfindung nicht auf Akku-Drehschlagschrauber beschränkt ist, sondern vielmehr bei unterschiedlichen Elektrowerkzeugen Anwendung finden kann, bei denen ein Werkzeug in Drehungen versetzt wird und ein erfindungsgemäßes Schlagwerk Anwendung findet, z.B. bei einer Schlagbohrmaschine etc., unabhängig davon, ob das Elektrowerkzeug netzunabhängig mit einem Akkupack oder netzabhängig betreibbar ist. Darüber hinaus wird darauf hingewiesen, dass die vorliegende Erfindung nicht auf motorbetriebene Handwerkzeugmaschinen beschränkt ist.The
In dem Gehäuse 110 sind ein von dem Akkupack 130 mit Strom versorgter, elektrischer Antriebsmotor 114, ein Getriebe 118 und das Schlagwerk 200 angeordnet. Der Antriebsmotor 114 ist z.B. über einen Handschalter 128 betätigbar, d.h. ein- und ausschaltbar, und kann ein beliebiger Motortyp sein, z.B. ein elektronisch kommutierter Motor oder ein Gleichstrommotor. Vorzugsweise ist der Antriebsmotor 114 derart elektronisch steuer- bzw. regelbar, dass sowohl ein Reversierbetrieb, als auch Vorgaben hinsichtlich einer gewünschten Drehgeschwindigkeit realisierbar sind. Die Funktionsweise und der Aufbau eines geeigneten Antriebsmotors sind aus dem Stand der Technik hinreichend bekannt und werden deshalb hier zwecks Knappheit der Beschreibung nicht weiter beschrieben.In the
Der Antriebsmotor 114 ist bevorzugt über eine zugeordnete Motorwelle 116 mit dem Getriebe 118 verbunden, das eine Drehung der Motorwelle 116 in eine Drehung einer zwischen Getriebe 118 und Schlagwerk 200 vorgesehenen Antriebswelle 120 umwandelt. Diese Umwandlung erfolgt bevorzugt derart, dass die Antriebswelle 120 sich relativ zur Motorwelle 116 mit vergrößertem Drehmoment, aber verringerter Drehgeschwindigkeit dreht. Der Antriebsmotor 114 ist illustrativ in einem Motorgehäuse 115 angeordnet und das Getriebe 118 in einem Getriebegehäuse 119, wobei das Getriebegehäuse 119 und das Motorgehäuse 115 beispielhaft in dem Gehäuse 110 angeordnet sind.The
Das mit der Antriebswelle 120 gekoppelte, mechanische Schlagwerk 200 ist beispielhaft ein in einem optionalen Schlagwerkgehäuse 220 angeordnetes Dreh- bzw. Rotationsschlagwerk, das einen Schlagkörper 300 aufweist, der schlagartige Drehimpulse mit hoher Intensität ausführt und über eine Abtriebsnockenanordnung 410 auf eine Abtriebswelle 400, z.B. eine Abtriebsspindel, überträgt. Es sei jedoch darauf hingewiesen, dass die Verwendung des optionalen Schlagwerkgehäuses 220 lediglich beispielhaften Charakter hat und nicht als Einschränkung der Erfindung dient. Diese kann vielmehr auch bei Schlagwerken ohne separate Schlagwerkgehäuse Anwendung finden, die z.B. unmittelbar im Gehäuse 110 der Handwerkzeugmaschine 100 angeordnet sind. Darüber hinaus sind die Funktionsweise und der Aufbau eines geeigneten Schlagwerks aus dem Stand der Technik, z.B. aus der
An der Abtriebswelle 400 ist bevorzugt die Werkzeugaufnahme 450 vorgesehen, die vorzugsweise zur Aufnahme von Einsatzwerkzeugen ausgebildet ist und gemäß einer Ausführungsform zumindest mit einem Einsatzwerkzeug 140 mit Außenmehrkant-Kupplung 142, aber bevorzugt auch mit einem Einsatzwerkzeug mit Innenmehrkant-Kupplung, z.B. einem Steckschlüssel, verbindbar ist. Das Einsatzwerkzeug 140 ist beispielhaft als Schrauberbit mit der Außenmehrkant-Kupplung 142, illustrativ einer Sechskant-Kupplung, ausgebildet, die in einer geeigneten Innenaufnahme der Werkzeugaufnahme 450 angeordnet ist. Ein derartiges Schrauberbit sowie ein geeigneter Steckschlüssel sind hinreichend aus dem Stand der Technik bekannt, sodass hier zwecks Knappheit der Beschreibung auf eine eingehende Beschreibung verzichtet wird.On the
Der Schlagkörper 300 ist bevorzugt in Richtung der Werkzeugaufnahme 450 bzw. der Abtriebswelle 400 mittels einer nicht dargestellten Druckfeder axial vorgespannt. Die Abtriebswelle 400 mit der Werkzeugaufnahme 450, sowie das Schlagwerk 200, die Antriebswelle 120, das Getriebe 118, die Motorwelle 116 und der Antriebsmotor 114 sind illustrativ entlang einer Längsmittelachse 150 im Gehäuse 110 der Handwerkzeugmaschine 100 angeordnet.The
Die V-förmigen Führungsnuten162, 164 weisen bevorzugt jeweils eine im Wesentlichen C-förmige und vorzugsweise halbkreisförmige Querschnittsgeometrie auf. In jeder Führungsnut 162, 164 ist jeweils eine Mitnehmerkugel 166, 168 aufgenommen. Die beiden Mitnehmerkugeln 166, 168 liegen vorzugsweise jeweils bis bevorzugt maximal zu ihren jeweiligen Äquatorialumfängen in den V-förmigen Führungsnuten 162, 164.The V-shaped
Die symmetrisch zur Längsmittelachse 150 von
An einer illustrativ kreisringförmigen Stirnseite 310 des Schlagkörpers 300 sind bevorzugt zwei nach Art von axialen Vorsprüngen ausgebildete Antriebsnocken 312, 314 vorzugsweise integral ausgebildet, die gemäß einer Ausführungsform beidseits der Durchgangsöffnung 302 und diametral zueinander positioniert sind. Die Antriebsnocken 312, 314 wirken in geeigneter Weise mit zwei nicht dargestellten Abtriebsnocken des Schlagwerks unter Schaffung der Abtriebsnockenanordnung 410 von
Die Mitnahmeaussparung 306 ist bevorzugt korrespondierend zu der mit ihr zusammenwirkenden V-förmigen Führungsnut 162 bzw. 164 von
Entsprechendes gilt für den geometrischen Verlauf der hier verdeckten zweiten, bevorzugt diametral zur Mitnahmeaussparung 306 angeordneten Mitnahmeaussparung 308 von
Der Verlauf des Graphen 600 ergibt sich aufgrund der oben beschriebenen Führungsnutengeometrie der konkav-polygonalen Führungsnuten 162 bzw. 164 von
Insbesondere resultiert aus den erfindungsgemäß zumindest abschnittsweise polygonal-konkaven Führungsnuten 162 bzw. 164 von
Claims (11)
- Portable power tool (100) having a mechanical percussion mechanism (200), said power tool (100) having a drive shaft (120) for driving a percussion body (300) assigned to the percussion mechanism (200) in rotation, wherein, on an outer circumference (160) of the drive shaft (120), at least one V-shaped guide slot (162, 164) is provided, the bottom lines (170, 172) of which that converge in a connecting portion (174) are formed at least partially in a concave-polygonal manner in the output direction (176).
- Portable power tool according to Claim 1, characterized in that, in the at least one guide slot (162, 164) of the drive shaft (120), a driver ball (166, 168) is arranged, which engages in an entrainment cutout (306, 308) formed on an inner circumference (304) of a through-opening (302) of the percussion body (300).
- Portable power tool according to Claim 1 or 2, characterized in that the connecting portion (174) between the bottom lines (170, 172) of the V-shaped guide slot (162, 164) is curved at least substantially in a semicircular manner.
- Portable power tool according to one of the preceding claims, characterized in that the connecting portion (174) has an increased radius (R1).
- Portable power tool according to one of the preceding claims, characterized in that the bottom lines (170, 172) on either side of the connecting portion (174) each have a substantially rectilinear middle portion (180, 182) with a first predefined gradient angle (α1), which is preferably greater than 45°.
- Portable power tool according to Claim 5, characterized in that the two middle portions (180, 182) are each adjoined by a substantially rectilinear end portion (184, 186) with a second predefined gradient angle (α2), which is preferably less than 45°.
- Portable power tool according to Claim 6, characterized in that the first predefined gradient angle (α1) is greater than the second predefined gradient angle (α2).
- Portable power tool according to one of the preceding claims, characterized in that two top lines (190, 192), arranged parallel to and at a distance from each bottom line (170, 172) of the V-shaped guide slot (162, 164), converge at an acute angle at a connecting point (P1).
- Portable power tool according to Claim 8, characterized in that the at least one V-shaped guide slot (162, 164) has a substantially semicircular cross-sectional geometry.
- Portable power tool according to one of Claims 2 to 9, characterized in that the at least one entrainment cutout (306, 308) is formed in a groove-like manner with a base line (322, 324) extending in a manner substantially corresponding to the bottom line.
- Mechanical percussion mechanism (200) which has a percussion body (300) provided with at least one drive cam (312, 314), and an output shaft (400) provided with at least one output cam (312, 314), wherein the at least one drive cam (312, 314) is configured for percussively driving the output cam in percussion operation of the mechanical percussion mechanism (200) and the percussion body (300) cooperates with a drive shaft (120), wherein, on an outer circumference (160) of the drive shaft (120), at least one V-shaped guide slot (162, 164) is provided, the bottom lines (170, 172) of which that converge in a connecting portion (174) are formed at least partially in a concave-polygonal manner in the output direction (176).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015204807.1A DE102015204807A1 (en) | 2015-03-17 | 2015-03-17 | Hand tool and mechanical percussion |
PCT/EP2016/053842 WO2016146354A1 (en) | 2015-03-17 | 2016-02-24 | Hand-held power tool and mechanical percussion mechanism |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3271115A1 EP3271115A1 (en) | 2018-01-24 |
EP3271115B1 true EP3271115B1 (en) | 2019-04-10 |
Family
ID=55446764
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16707048.1A Active EP3271115B1 (en) | 2015-03-17 | 2016-02-24 | Hand tool machine and mechanical impact mechanism |
Country Status (5)
Country | Link |
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US (1) | US11185963B2 (en) |
EP (1) | EP3271115B1 (en) |
CN (1) | CN107405759B (en) |
DE (1) | DE102015204807A1 (en) |
WO (1) | WO2016146354A1 (en) |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2712254A (en) * | 1953-05-14 | 1955-07-05 | Schodeberg Carl Theodore | Power driven impact tool |
DE1109107B (en) * | 1957-01-31 | 1961-06-15 | Bosch Gmbh Robert | Motor-driven rotary impact device |
US3054312A (en) * | 1960-02-02 | 1962-09-18 | Zengerer Hans | Rotary-impact type hand tool |
US3001428A (en) * | 1960-02-23 | 1961-09-26 | Master Power Corp | Rotary impact wrench |
DE1478807A1 (en) * | 1962-07-03 | 1969-03-13 | Bosch Gmbh Robert | Motor-driven rotary impact device |
JP3653205B2 (en) * | 2000-01-28 | 2005-05-25 | 株式会社マキタ | Oil pulse rotating tool |
JP3678965B2 (en) * | 2000-02-04 | 2005-08-03 | 株式会社マキタ | Rotating hammer tool |
US6733414B2 (en) * | 2001-01-12 | 2004-05-11 | Milwaukee Electric Tool Corporation | Gear assembly for a power tool |
DE202006014850U1 (en) | 2006-09-27 | 2006-11-23 | Robert Bosch Gmbh | Mechanical beater for manual machine tool has impact body mounted axially movable and rotationally secured on drive shaft and an elastomer axial stop as ring-shaped spring element also mounted on drive shaft |
EP2140976B1 (en) * | 2008-07-01 | 2011-11-16 | Metabowerke GmbH | Impact wrench |
JP4600562B2 (en) | 2008-09-30 | 2010-12-15 | パナソニック電工株式会社 | Impact rotary tool |
US7963430B2 (en) * | 2008-10-15 | 2011-06-21 | Chervon Limited | Nailer device |
CN201534323U (en) * | 2009-09-10 | 2010-07-28 | 苏州宝时得电动工具有限公司 | Power tool |
DE102010029559A1 (en) * | 2010-06-01 | 2011-12-01 | Robert Bosch Gmbh | Hand tool with a mechanical percussion |
US9505107B2 (en) * | 2013-05-14 | 2016-11-29 | Snap-On Incorporated | Ball deflecting chamfer |
-
2015
- 2015-03-17 DE DE102015204807.1A patent/DE102015204807A1/en not_active Withdrawn
-
2016
- 2016-02-24 CN CN201680016507.3A patent/CN107405759B/en active Active
- 2016-02-24 US US15/554,322 patent/US11185963B2/en active Active
- 2016-02-24 EP EP16707048.1A patent/EP3271115B1/en active Active
- 2016-02-24 WO PCT/EP2016/053842 patent/WO2016146354A1/en active Application Filing
Non-Patent Citations (1)
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EP3271115A1 (en) | 2018-01-24 |
WO2016146354A1 (en) | 2016-09-22 |
CN107405759B (en) | 2021-03-19 |
DE102015204807A1 (en) | 2016-09-22 |
CN107405759A (en) | 2017-11-28 |
US11185963B2 (en) | 2021-11-30 |
US20180029206A1 (en) | 2018-02-01 |
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