EP2655017A1 - Outil électrique portatif - Google Patents

Outil électrique portatif

Info

Publication number
EP2655017A1
EP2655017A1 EP11776804.4A EP11776804A EP2655017A1 EP 2655017 A1 EP2655017 A1 EP 2655017A1 EP 11776804 A EP11776804 A EP 11776804A EP 2655017 A1 EP2655017 A1 EP 2655017A1
Authority
EP
European Patent Office
Prior art keywords
hand tool
gear
electric hand
drive shaft
unit
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
EP11776804.4A
Other languages
German (de)
English (en)
Other versions
EP2655017B1 (fr
Inventor
Juergen Dietel
Christian Koepf
Andreas Schlegel
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 EP2655017A1 publication Critical patent/EP2655017A1/fr
Application granted granted Critical
Publication of EP2655017B1 publication Critical patent/EP2655017B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the invention relates to an electric hand tool, in particular a hammer drill, according to the preamble of the independent claim.
  • Input wheel an angle Wl of approximately, preferably approximately equal to 90 ° with the drive shaft.
  • the electric hand tool according to the invention with the features of the main claim has the advantage that a position, in particular a distance A of a center of gravity M of the power tool to a grip position on a main handle of the
  • Input wheel includes an angle Wl between 30 ° and 80 °, preferably between 50 ° and 70 °, more preferably of about 60 ° with the drive shaft.
  • the distance A to the grip position is advantageously minimized. If a transmission ratio IW between a rotational speed N R of the pinion and a rotational speed N E of the input gear in the angular gear in the range between 2 and 8, preferably between 2.5 and 7, so below required gear stages of
  • Transmission arrangement are made particularly small and lightweight, which also affects the location of the center of gravity M favorable. This will total one Achieved more ergonomic handling when used manually in the handle position of the electric hand tool.
  • Another advantage is to be considered that the electric hand tool is less top-heavy in the direction of the tool holder. In this way, an advantageously more compact design of the
  • the oriented at the angle Wl arrangement allows a space between the pinion and the input gear more efficient, for example, for an arrangement of a Hubantriebslagers in the
  • a crown gear in the electric hand tool according to the invention further has the advantage that a positional tolerance, in particular an axial clearance between a position of the pinion along the drive shaft and the position of the
  • a "standard motor” is to be understood as meaning, in particular, an electric motor not specifically intended for use in the electric hand tool according to the invention, this electric motor preferably taking the form of a DC motor or an electronically commutated electric motor.
  • the pinion is designed as a straight-toothed spur gear, wherein the input gear carries a complementary, in particular also a straight-toothed crown gear teeth.
  • This embodiment is particularly tolerant to the axial clearance between the position of the pinion along the drive shaft and the position of the crown gear teeth on the input gear.
  • the pinion is designed as a helical spur gear, wherein the input gear a complementary, in particular one also
  • helical crown gear teeth carries.
  • a supporting surface of the toothing is advantageously increased in particular held tooth width.
  • a module of the crown wheel toothing of the input wheel has a value between 0.5 and 3, preferably between 0.7 and 1.
  • the input wheel can be produced particularly cost-effectively and / or of high quality from an injection-molded, sintered, MIM or forged material.
  • a "forging material” is understood in particular to be a forgeable material.
  • Receiving the electric motor in the housing is achieved when the electric motor is biased relative to the housing with an elastic element at least axially in a direction along the drive shaft.
  • the electric motor with its inertial mass together with the elastic member advantageously as a mass-spring system for absorbing at least a portion of in the use unit occurring vibrations are used.
  • the angular alignment of the drive shaft additionally has the advantage that in particular advantageous proportions of axial and / or longitudinal vibrations in the working direction and perpendicular to this of the mass-spring system
  • absorbing can be absorbed.
  • an idle speed of the drive shaft is in an idling operation of the drive unit between 12,000 and 30,000 min '1 .
  • a control and / or regulating unit in particular an electronic unit to a controlling and / or regulating engagement in the drive unit - in particular for influencing a movement state of the drive shaft of the drive unit - provided.
  • a "controlling and / or regulating intervention” is to be understood as meaning, in particular, an active intervention in at least one parameter, such as, for example, quantities of the energy consumption and / or power output of the drive unit.
  • Under a state of motion of the drive shaft is in particular a rotational movement about a longitudinal axis with a speed, for example, a currently applied actual speed understood.
  • the housing is a first
  • the first control element may be designed in particular as a main switch, main switch or a so-called throttle lever.
  • the second control element is preferably designed as a rotary or slide switch with at least two switching positions for each direction of rotation.
  • a "direction of rotation” is understood to mean, in particular, a direction of rotation of a shaft about its axis of rotation.
  • the second control also have at least a third switching position - neutral or secure position - in which a startup of the electric hand tool is prevented or blocked.
  • the use unit is at least designed as a striking mechanism, in particular as a pneumatic percussion.
  • the preferred pneumatic striking mechanism comprises a guide sleeve with an axially movably mounted in the guide sleeve piston unit and an axially movably mounted
  • the guide sleeve is designed as a hammer tube.
  • the gear arrangement of this preferred embodiment has at least one means for at least partial conversion of the rotational movement of the drive shaft into an oscillating movement of the piston unit.
  • the gear arrangement of the electric hand tool according to the invention comprises a rotary gear stage for a
  • Rotary drive of the use unit which is preferably designed as a spur gear.
  • the gear arrangement of the electric hand tool according to the invention comprises at least one coupling unit, by which the movement of the use unit in an operating state of the drive unit can be controlled, in particular selectively activated or deactivated.
  • the "operating state” is understood in particular to be an activated state of the drive unit, in which the drive shaft is driven to rotate
  • Coupling arrangement is then in particular a torque transmission from an input side to an output side can be braked or interrupted.
  • Coupling units such as Ein Wegkupplungen or snap-in couplings known, which have at least one pair of coupling members by means of selectable detachable, positive and / or non-positive connections a torque from a first coupling member to a second coupling member of
  • the coupling device is designed as a friction clutch.
  • a first, the first coupling member forming friction contour is preferably provided at the input gear of the gear assembly, while a second, complementary friction contour is provided as a second coupling member on a bearing sleeve of the Hubantriebslagers, in particular the swash bearing device.
  • At least one actuating means for actuating the coupling arrangement is provided on the housing of the electric hand tool according to the invention, then, in an advantageous further development, one may be provided by a user of the
  • Electric hand tool selectable mode switching can be displayed. Also are the expert in connection with multi-stage manual transmissions and / or
  • Mode selectors in electric hand tools a variety of possible designs known.
  • such an actuating means is designed as an at least two-stage rotary or slide switch.
  • electronic and / or sensory elements such as pushbutton elements, non-contact sensors or acoustic sensors, as actuating means.
  • FIG. 1 shows a schematic partial section of a hammer drill according to the invention
  • FIG. 2 shows a detail of the gear arrangement according to FIG. 1
  • FIG. 3 is a schematic representation of the transmission arrangement according to FIG. 2
  • FIG. 1 shows a schematic partial section of a hammer drill 10 as an example of an electric hand tool 11 according to the invention.
  • the electric hand tool 10, 11 in this case comprises a housing 12, at its one end end 14
  • Tool holder 16 is arranged, which has a receiving opening 20 extending along an axis 18 for receiving a tool, not shown, in particular a tool shank.
  • a handle device 22 is provided, in particular connected to the housing 12, preferably in one piece with the
  • the handle device 22 has a gripping area 24, which can be grasped by a user's hand, and a main operating element 26 for putting the electric hand tool 10, 11 into operation.
  • the handle assembly 22 includes an actuator 28 for selecting or setting a mode or operating condition of the electric hand tool 10, 11.
  • the tool holder 16 is intended to be rotationally driven or at least rotationally driven in at least one mode of the electric hand tool 10, 11
  • the actuator 28 may be provided in particular to select a direction of rotation of the tool holder 16 selectable.
  • Fig. 1 forms an end portion 30 of
  • Handle device 22 with a motor segment 32 of the housing 12 a closed frame around a passage opening 34 for a particular penetration of fingers of the user's hand.
  • the end region 30 is preferably connected to the motor segment 32 via a connecting bridge 36 that extends essentially parallel to the axis 18.
  • Connecting bridge 30 is a power supply unit 38, in particular a battery or battery pack 40 arranged, preferably releasably, interchangeably arranged, by means of which the electric hand tool 10, 11 can be supplied with electrical energy for commissioning.
  • the battery or battery pack 40 preferably comprises at least one lithium-ion or lithium polymer cell, not shown here.
  • a supply voltage provided by the battery pack 40 is less than 20V, preferably less than 18V.
  • the battery pack 40 is less than 20V, preferably less than 18V.
  • Power supply unit 38 but also a fuel cell or a
  • Connection device for connection to an external power source such as a power supply include.
  • a motor segment 32 of the housing 12 which is designed as an electric motor 42
  • the electric motor 42 is preferably designed as a DC motor or an electronically commutated electric motor, which preferably has an idling speed NO between 12,000 and 30,000 min '1 . However, it can also be provided a corresponding universal electric motor.
  • Electric motor 42 closes as shown in FIG. 1 a preferred angle Wl of about 60 ° with the axis 18 a.
  • the angle Wl between 30 ° and 80 °, preferably between 50 ° and 70 °.
  • the electric motor 42 contributes with its inertial mass up to a quarter
  • the position of a center of gravity M of the electric hand tool 10, 11 is shown schematically in FIG. 1 and is therefore strongly influenced by the arrangement of the electric motor 42.
  • the angle Wl shifts in particular an axial position with respect to a longitudinal extension L with decreasing angle Wl towards the handle device 22. From angles Wl of about 50 °, the position of the center of gravity M also shifts noticeably perpendicular to the axis 18 to this.
  • the elastic element 50 in the example according to FIG. 1 has an essentially annular design and surrounds the drive shaft 46. It is supported on the one hand via a motor section 32 substantially immovable, preferably connected to the motor segment 32 or at this supporting
  • a pinion 62 designed as a spur gear 60 is arranged as shown in FIG. 1, in particular at least rotationally fixed with the
  • Drive shaft 46 connected, preferably rigidly connected to the drive shaft 46 or even integrally executed with this.
  • the spur gear 60 is connected to a provided with a crown gear 64 input gear 66 of a gear assembly 68 in operative connection, at least it is arranged engageable with this operatively connected.
  • the input gear 66 is at least rotationally fixed, preferably fixed on an input shaft 70th Gear assembly 68 is arranged, which is substantially parallel to the axis 18, so that the drive shaft 46 and input shaft 70 include an angle W2, which is substantially equal to the angle Wl.
  • the input gear 66 therefore has with respect to its crown gear teeth 64 a conical arrangement of the teeth with an opening angle WK, which corresponds to twice the angle Wl.
  • the crown gear toothing 64 according to FIG. 1 is manufactured with a module between 0.5 and 3, preferably between 0.7 and 1.
  • input wheels 66 of this type can be easily manufactured by injection molding, sintering, MIM techniques or forging.
  • the pinion 62 forms with the input gear 66 a first gear stage 72 in the form of an angular gear 73 of the gear assembly 68 with a gear ratio in the range between 2 and 8, preferably between 2.5 and 7, more preferably between 3 and 5. Therefore, typical idling speeds are Nl the input shaft 70 between 2,000 and 10,000 min '1 , preferably between 2,500 and 5,500 min ' 1 .
  • the gear arrangement 68 of the electric hand tool 10, 11 according to FIG. 1 is shown in FIG. 2 for the sake of clarity in a partially enlarged view.
  • Input shaft 70 of the gear assembly 68 is shown in FIG. 2 as a for
  • the intermediate or countershaft 70, 74 is in a first end portion 74a and in a second end portion 74b, each with a bearing device 75a, 75b relative to the housing 12 at least rotatably decoupled housed in the housing 12, wherein the input gear 66 in the vicinity of the first end portion 74a preferably rotatably on the intermediate or countershaft 70, 74 is arranged.
  • On the intermediate or countershaft 74 in the direction of the second end portion 74b is in front of the
  • Input wheel 66 a Hubantriebslager 76 in the form of a swash bearing device 78 of a use unit 79 rotatably, preferably freely rotatable relative to the intermediate or countershaft 70, 74 arranged.
  • the swash bearing device 78 includes a bearing sleeve 80 and a, a
  • Taumelfinger 82 having bearing ring 84 which is mounted on a wobble bearing, not shown here, preferably wobble bearings relative to the bearing sleeve.
  • the wobble roller bearing has a tilted in a known manner, at least against a vertical relative to the intermediate or countershaft 70, 74
  • Countershaft 70, 74 oscillates axially oscillating.
  • 74 far end of the wobble finger 82 engages a receiving pin 86 of a piston unit 88 a.
  • the piston unit 88 is axially displaceably mounted in a guide sleeve 92 designed as a hammer tube 90.
  • 92 a not shown here also axially movably mounted impactor is added, which by a provided between the piston unit 88 and the impactor air cushion over the
  • the oscillating movement of the piston unit is set in motion in a known manner.
  • the impactor is in turn provided to impart shock pulses to a tool received in the tool holder 16 transferable or produce.
  • the guide sleeve 90, 92, the piston unit 88 and the impactor thus form a simple embodiment of a pneumatic percussion mechanism 94.
  • pneumatic percussion devices 94 are known in the art, which may be advantageous under some circumstances used.
  • the striking body is guided axially displaceably in the piston unit 88, which in turn is accommodated axially displaceably in the guide sleeve 90, 92.
  • Impact body and a tool end be arranged as a pulse transformer.
  • Rotary gear stage 98 arranged as a further component of the use unit 79. It can be provided both that the first spur gear 96, as shown in Fig. 2, rotationally fixed, in particular arranged integrally with intermediate or countershaft 70, 74 and executed, as well as that the first spur gear 96 via coupling means not shown here with the intermediate or countershaft 70, 74 is FDverbindbar.
  • a second spur gear 100 of the rotary gear stage 98 is shown in FIG. 2 on the guide sleeve 90, 92 and preferably rotatably connected thereto.
  • Fig. 3 shows a schematic sectional view of the gear assembly 68 of FIG. 2, in this illustration, particularly the schematic structure of
  • Tumble bearing device 78 and a coupling unit 102 can be seen.
  • the coupling unit 102 is provided for transferring a drive torque generated by the drive unit 42, 44 on the drive shaft 46, 48 and transmitted via the bevel gear 73 to the intermediate or countershaft 70, 74 to the use unit, in particular the swash bearing device 78.
  • the coupling unit 102 is preferably designed as a friction clutch 104.
  • a conical ring 110 is provided, preferably formed, around a rotation axis 108 of the intermediate or countershaft 70, 74.
  • the conical ring 110 has a cone-shaped outer circumferential surface 112 directed essentially radially outward.
  • the input gear 66 which is preferably in the form of a crown wheel, has an annular friction contour 116 on its side surface 114, which has an inner circumferential surface 118 which is directed inwards in a direction substantially radially in the direction of the rotation axis 108.
  • the outer circumferential surface 112 and the inner lateral surface 118 are each in the form of friction surfaces 120, in particular as complementary to one another, in the
  • Substantially surface-engageable friction surfaces 122 are formed.
  • the opening angles Ol and 02 of the outer and inner lateral surface 112, 118 are approximately the same, so that upon engagement of the two conical surfaces 112, 118 caused by frictional force-locking connection, in particular clamping or spline connection is formed.
  • Preferred opening angles lie in the range between 1 ° and 30 °, in particular between 5 ° and 15 °, angle differences preferably being smaller than 5 °, in particular smaller than 2 °.
  • the friction surfaces 120, 122 thus form the coupling means 124 of the coupling unit 102, wherein the input gear 66 with the friction contour 116, the first coupling member 126 and the bearing sleeve 80 with cone ring 110 form the second coupling member 128 of the coupling unit 102.
  • At least one restoring element 130 is provided between the two coupling members 126, 128 according to the preferred embodiment according to FIG. 3, which spans the two coupling members 126, 128 into a disengaged position in a rest position as shown in FIG. Only by an axial
  • Mode switch and a corresponding in the housing corresponding switching mechanism comprises, wherein by selecting a corresponding switching position of the mode switch, the switching mechanism acts on the coupling unit 102 so that the coupling members 126, 128 engage.
  • an idle arrangement may be provided which engages the coupling members 126, 128 upon contact of the tool with a workpiece.

Landscapes

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

Abstract

L'invention concerne un outil électrique portatif, en particulier un marteau perforateur, comprenant un boîtier (12, 32) qui renferme au moins une unité d'entraînement (42, 44) munie d'un arbre d'entraînement (46, 48) et d'un pignon (60, 62) disposé dans une partie d'extrémité (58) de l'arbre d'entraînement (46, 48), et un système de transmission (68) muni d'une roue d'entrée (66) formant avec le pignon (60, 62) un engrenage angulaire (73). Le système de transmission permet de convertir un mouvement de rotation de l'arbre d'entraînement (46, 48) en au moins un mouvement, de préférence en au moins un mouvement d'oscillation, d'une unité de travail (79) présentant un logement d'outil (20) pour le raccordement, de préférence détachable, à un outil. Selon l'invention, la roue d'entrée (66) comporte une denture de couronne dentée (64) engrenant avec le pignon (60, 62), un arbre d'entrée de la roue d'entrée (66) formant un angle W1 compris entre 30° et 80°, de préférence entre 50° et 70°, avec l'arbre d'entraînement (46, 48), et présentant un rapport de multiplication IW entre une vitesse de rotation NR du pignon (60, 62) et une vitesse de rotation NE de la roue d'entrée (66) compris entre 2 et 8, de préférence entre 2,5 et 7.
EP11776804.4A 2010-12-21 2011-11-02 Outil électrique portatif Active EP2655017B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010063620 2010-12-21
DE102011077220A DE102011077220A1 (de) 2010-12-21 2011-06-08 Elektrohandwerkzeug
PCT/EP2011/069221 WO2012084316A1 (fr) 2010-12-21 2011-11-02 Outil électrique portatif

Publications (2)

Publication Number Publication Date
EP2655017A1 true EP2655017A1 (fr) 2013-10-30
EP2655017B1 EP2655017B1 (fr) 2020-06-17

Family

ID=44903244

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11776804.4A Active EP2655017B1 (fr) 2010-12-21 2011-11-02 Outil électrique portatif

Country Status (3)

Country Link
EP (1) EP2655017B1 (fr)
DE (1) DE102011077220A1 (fr)
WO (1) WO2012084316A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6510250B2 (ja) * 2015-01-29 2019-05-08 株式会社マキタ 作業工具
DE102017209832A1 (de) * 2017-06-12 2018-12-13 Robert Bosch Gmbh Handwerkzeugmaschine
EP4008486A1 (fr) * 2020-12-04 2022-06-08 Hilti Aktiengesellschaft Machine-outil à deux moteurs

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3623648A1 (de) * 1986-07-12 1988-01-14 Hilti Ag Bohrhammer mit schlagwerk
DE4101665A1 (de) * 1990-01-13 1991-11-21 Licentia Gmbh Handgefuehrte elektrowerkzeugmaschine
DE4216808A1 (de) * 1992-05-21 1993-11-25 Hilti Ag Bohr- und Meisselgerät
DE19719923C2 (de) * 1997-05-13 1999-03-18 Atlas Copco Electric Tools Bohr-, Bohrschraub- oder Schlagbohrmaschine
DE10355812A1 (de) * 2003-11-28 2005-06-09 Robert Bosch Gmbh Elektrowerkzeugmaschine
DE102005062861A1 (de) * 2005-12-29 2007-07-05 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Bohr- und/oder Meißelhammer
DE102006054288A1 (de) * 2006-11-17 2008-05-21 A & M Electric Tools Gmbh Bohrhammer
DE102008022454B4 (de) * 2008-05-08 2014-06-26 Aeg Electric Tools Gmbh Bohrhammer
DE102008022455B4 (de) * 2008-05-08 2014-06-26 Aeg Electric Tools Gmbh Bohrhammer

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012084316A1 *

Also Published As

Publication number Publication date
EP2655017B1 (fr) 2020-06-17
WO2012084316A1 (fr) 2012-06-28
DE102011077220A1 (de) 2012-06-21

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