EP3271115B1 - Handwerkzeugmaschine sowie mechanisches schlagwerk - Google Patents

Handwerkzeugmaschine sowie mechanisches schlagwerk Download PDF

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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
Authority
EP
European Patent Office
Prior art keywords
power tool
portable power
tool according
drive shaft
shaped guide
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.)
Active
Application number
EP16707048.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3271115A1 (de
Inventor
Cheu Chyong Teh
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 EP3271115A1 publication Critical patent/EP3271115A1/de
Application granted granted Critical
Publication of EP3271115B1 publication Critical patent/EP3271115B1/de
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Classifications

    • 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
    • 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
    • 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
    • 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 ,

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Toys (AREA)
  • Drilling And Boring (AREA)
EP16707048.1A 2015-03-17 2016-02-24 Handwerkzeugmaschine sowie mechanisches schlagwerk Active EP3271115B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015204807.1A DE102015204807A1 (de) 2015-03-17 2015-03-17 Handwerkzeugmaschine sowie mechanisches Schlagwerk
PCT/EP2016/053842 WO2016146354A1 (de) 2015-03-17 2016-02-24 Handwerkzeugmaschine sowie mechanisches schlagwerk

Publications (2)

Publication Number Publication Date
EP3271115A1 EP3271115A1 (de) 2018-01-24
EP3271115B1 true EP3271115B1 (de) 2019-04-10

Family

ID=55446764

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16707048.1A Active EP3271115B1 (de) 2015-03-17 2016-02-24 Handwerkzeugmaschine sowie mechanisches schlagwerk

Country Status (5)

Country Link
US (1) US11185963B2 (zh)
EP (1) EP3271115B1 (zh)
CN (1) CN107405759B (zh)
DE (1) DE102015204807A1 (zh)
WO (1) WO2016146354A1 (zh)

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2712254A (en) * 1953-05-14 1955-07-05 Schodeberg Carl Theodore Power driven impact tool
DE1109107B (de) 1957-01-31 1961-06-15 Bosch Gmbh Robert Motorisch angetriebenes Drehschlaggeraet
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 (de) * 1962-07-03 1969-03-13 Bosch Gmbh Robert Motorisch angetriebenes Drehschlaggeraet
JP3653205B2 (ja) 2000-01-28 2005-05-25 株式会社マキタ オイルパルス回転工具
JP3678965B2 (ja) 2000-02-04 2005-08-03 株式会社マキタ 回転打撃工具
US6733414B2 (en) * 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
DE202006014850U1 (de) 2006-09-27 2006-11-23 Robert Bosch Gmbh Mechanisches Schlagwerk
EP2140976B1 (de) 2008-07-01 2011-11-16 Metabowerke GmbH Schlagschrauber
JP4600562B2 (ja) 2008-09-30 2010-12-15 パナソニック電工株式会社 インパクト回転工具
US7963430B2 (en) * 2008-10-15 2011-06-21 Chervon Limited Nailer device
CN201534323U (zh) 2009-09-10 2010-07-28 苏州宝时得电动工具有限公司 动力工具
DE102010029559A1 (de) 2010-06-01 2011-12-01 Robert Bosch Gmbh Handwerkzeugmaschine mit einem mechanischen Schlagwerk
US9505107B2 (en) * 2013-05-14 2016-11-29 Snap-On Incorporated Ball deflecting chamfer

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN107405759A (zh) 2017-11-28
CN107405759B (zh) 2021-03-19
US11185963B2 (en) 2021-11-30
WO2016146354A1 (de) 2016-09-22
US20180029206A1 (en) 2018-02-01
EP3271115A1 (de) 2018-01-24
DE102015204807A1 (de) 2016-09-22

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