EP3670096A1 - Machine-outil portative - Google Patents

Machine-outil portative Download PDF

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Publication number
EP3670096A1
EP3670096A1 EP18215055.7A EP18215055A EP3670096A1 EP 3670096 A1 EP3670096 A1 EP 3670096A1 EP 18215055 A EP18215055 A EP 18215055A EP 3670096 A1 EP3670096 A1 EP 3670096A1
Authority
EP
European Patent Office
Prior art keywords
striker
segment
tool
working axis
axis
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.)
Withdrawn
Application number
EP18215055.7A
Other languages
German (de)
English (en)
Inventor
Rory Britz
Rainer Ontl
Markus Hartmann
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.)
Hilti AG
Original Assignee
Hilti AG
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 Hilti AG filed Critical Hilti AG
Priority to EP18215055.7A priority Critical patent/EP3670096A1/fr
Priority to PCT/EP2019/083650 priority patent/WO2020126499A1/fr
Priority to US17/415,354 priority patent/US11858104B2/en
Priority to EP19812801.9A priority patent/EP3898117B1/fr
Priority to CN201980074739.8A priority patent/CN113165153A/zh
Publication of EP3670096A1 publication Critical patent/EP3670096A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • 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
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0015—Anvils
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0023—Pistons
    • 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
    • B25D2250/131—Idling mode of tools

Definitions

  • the present invention relates to a chiseling hand tool, e.g. a hammer drill or an electric chisel.
  • a chiseling hand tool e.g. a hammer drill or an electric chisel.
  • a hammer drill is out, for example US 9,339,924 B2 known.
  • the hammer drill has an electro-pneumatic hammer mechanism.
  • a user switches on an electric motor of the rotary hammer by pressing a button.
  • the striking mechanism should only be activated when the user presses the hammer drill, more precisely a tool, against a surface.
  • the electric motor continuously moves an exciter piston of the striking mechanism.
  • a striker of the striking mechanism is coupled to the movement of the exciter piston via a pneumatic chamber when the ventilation openings of the pneumatic chamber are closed.
  • the ventilation openings are controlled by an anvil.
  • the striker is located on the working axis between the racket and the tool.
  • the striking mechanism When the striking mechanism is pressed on, the striker is moved into a working position in the direction of the racket. In the working position, the ventilation openings are closed and the striking mechanism is active. If there is no pressure, a blow from the racket, a so-called empty blow, ensures that the striker leaves the working position. The ventilation openings are released and the striking mechanism switches off.
  • the striker moves in the direction of impact due to the blank stroke.
  • a catcher catches the striker.
  • the striker preferably comes to a standstill through the catcher.
  • the striker can bounce off the catcher, slide back into the working position and, undesirably, the ventilation openings can activate the striking mechanism.
  • the next stroke is an empty stroke.
  • the empty blows represent a considerable burden for the handheld power tool and the user, since the entire impact energy is absorbed within the handheld power tool and is not passed into the ground as desired.
  • US 9,339,924 B2 describes a striker with an end surface that is eccentric to the catcher.
  • the eccentric end face is intended to cause the striker to rotate, thereby removing kinetic energy from the striker. The striker then no longer reaches the Working position.
  • the solution described depends on tolerance-free guidance of the striker in order to ensure the eccentric arrangement.
  • the anvil and its guidance are subject to high wear due to the entry of dust and drillings through the tool, which affects the accuracy of the guidance.
  • the eccentric arrangement influences the efficiency of the transmission of the shock wave from the die to the axially arranged tool.
  • the chiseling hand machine tool has a tool holder, an electric motor, a striking mechanism and an empty stroke catcher.
  • the tool holder can hold a tool and hold it movably on a working axis.
  • the striking mechanism includes an exciter piston, a racket, a striker and a guide for the striker.
  • the exciter piston is coupled to the electric motor.
  • the racket couples to the movement of the exciter piston via a pneumatic chamber.
  • the striker is arranged in the striking direction of the racket on the working axis.
  • the guide guides the striker on the working axis.
  • the empty flap catcher for the striker has a conical inner surface facing the striker.
  • the striker has an associated end surface that is inclined with respect to the working axis and points in the direction of impact.
  • the end face lies against the conical inner surface when the striker is in its most advanced position in the direction of impact.
  • the end face of the striker has a first segment and a second segment in the circumferential direction. The second segment is offset from the first segment in the direction of impact.
  • the offset in the two segments of the end face means that the striker tilts when it bears against the empty stroke catcher. The tilting leads to jamming of the striker in the guide tube. Simulations show an additional bending of the anvil due to the axial offset between the opposing contact points of the anvil and catcher. This increases the catch effect of the catcher on the striker.
  • Fig. 1 shows schematically a hammer drill as an example of a chiseling hand machine tool 1 .
  • the hammer drill has a tool holder 2 , in which a tool 3 can be inserted and locked.
  • the tools 3 can be, for example, drills for the chiseling processing of mineral building materials, such as concrete or stone, or chisels for the purely chiseling processing of the same building materials.
  • the hammer drill 1 contains a pneumatic hammer mechanism 4 , which periodically strikes the tool 3 in the direction of impact 5 during operation.
  • the hammer drill 1 contains an output shaft 6 , which rotates the tool holder 2 and thus the tool 3 about a working axis 7 during operation.
  • the striking mechanism 4 and the output shaft 6 are driven by a motor 8 , for example an electric motor.
  • the output shaft 6 can be switched off in chiseling hand machine tools 1 or in purely chiseling hand machine tools 1 without an output shaft.
  • the hand tool 1 has a handle 9 , by means of which the user can hold and guide the hand tool 1 in operation.
  • the handle 9 is attached to a machine housing 10 .
  • the handle 9 is preferably arranged at an end of the handheld power tool 1 or of the machine housing 10 remote from the tool holder 2 .
  • a working axis 7 parallel to the striking direction 5 and running centrally through the tool holder 2 preferably runs through the handle 9 when it can be gripped with one hand.
  • the handle 9 can be partially decoupled from the machine housing 10 by damping elements in order to dampen vibrations of the striking mechanism 4 .
  • the user can put the handheld power tool 1 into operation by means of a button 12 . Pressing the button 12 activates the motor 8 .
  • the button 12 is preferably arranged on the handle 9 , whereby this can be actuated by the hand gripping the handle 9 .
  • the striking mechanism 4 has an excitation piston 13 , a racket 14 and a striker 15 .
  • the excitation piston 13 , the striker 14 and the striker 15 are arranged in the striking direction 5 in succession on the working axis 7 .
  • the excitation piston 13 is coupled to engine 8 via a gear train.
  • the gear train converts the rotary movement of the motor 8 into a periodic forward and backward movement of the excitation piston 13 on the working axis 7 .
  • An exemplary gear train is based on an eccentric wheel 16 and a connecting rod 17 . Another version is based on a wobble drive.
  • the racket 14 is coupled to the movement of the excitation piston 13 by a pneumatic chamber 18 , also referred to as an air spring.
  • the pneumatic chamber 18 is closed along the working axis 7 on the drive side by the exciter piston 13 and on the tool side by the striker 14 .
  • the racket 14 is designed as a piston.
  • the pneumatic chamber 18 is closed in the radial direction by a guide tube 19 .
  • the excitation piston 13 and the striker 14 slide air-tight against the inner surface of the guide tube 19 .
  • the exciter piston can be cup-shaped.
  • the racket slides within the exciter piston.
  • the racket can be cup-shaped, the exciter piston sliding within the racket.
  • the striker 14 coupled via the pneumatic chamber 18, moves periodically parallel to the striking direction 5 between a reversal point on the drive side and a reversal point on the tool side.
  • the tool-side reversal point is predetermined by the striker 15 , on which the striker 14 strikes in the tool-side reversal point.
  • the striker 15 is movably guided parallel to the striking direction 5 between a stop 20 and the tool 3 .
  • the user presses the tool 3 against the striker 15 and indirectly the striker 15 against the stop 20 when pressing the tool 3 against a surface.
  • the position of the striker 15 adjacent to the stop 20 is referred to as the working position.
  • the striker 14 preferably strikes the striker 15 when the striker 15 is in the working position.
  • the striker 15 serves as an agent for the impact of the striker 14 on the tool 3 . Damping the shock by the striker 15 is not desirable.
  • Fig. 2 shows an exemplary embodiment of the striker 15 .
  • the striker 15 slides in a tubular guide 21 on the working axis 7 .
  • the working axis 7 is predetermined by the cylindrical inner surface 22 of the guide 21 .
  • the inner surface 22 is arranged coaxially to the working axis 7 .
  • the anvil 15 has a cylindrical lateral surface 23 which bears against the inner surface 22 .
  • the lateral surface 23 typically defines the largest diameter of the striker 15 .
  • the lateral surface 23 defines a longitudinal axis or anvil axis 24 of the anvil 15 .
  • the striking axis 24 corresponds to the axis of symmetry of the Lateral surface 23 . Due to the guide 21 of the striker 15 over the leading lateral surface 23 , the striker axis 24 lies on the working axis 7 .
  • the striker 15 has a striking surface 25 which points in the direction of the striker 14 .
  • the bat 14 strikes the striking surface 25 .
  • the area of the striking surface 25 is typically less than the area of a cross section in the region of the leading lateral surface 23 .
  • the striking surface 25 is preferably rotationally symmetrical to the striking axis 24 .
  • the bat 14 thus strikes the center of the striking surface 25 , which ensures more efficient energy transmission.
  • the striking surface 25 can be flat, a spherical configuration is preferred. In the embodiment shown, the striking surface 25 is adjoined by a cylindrical section whose diameter corresponds to the diameter of the striking surface 25 .
  • the striker 15 has an abutting surface 26 which points in the direction of the tool 3 , ie in the direction of impact 5 and is remote from the striker 14 .
  • the anvil 15 is with the abutment surface 26 on the tool 3 or to impacts on the tool 3 with the abutment surface 26th
  • the surface area of the abutting surface 26 is typically less than the surface area of a cross section in the region of the leading lateral surface 23 .
  • the striking surface 25 is rotationally symmetrical to the striking axis 24 .
  • An impact transfer from the striker 15 to the tool 3 takes place centrally from the impact surface 26 .
  • the butt surface 26 can be flat or crowned. In the embodiment shown, the abutting surface 26 is followed by a cylindrical section 27 , the diameter of which corresponds to the diameter of the abutting surface 26 .
  • the striker 15 bears against the stop 20 in the working position.
  • the stop 20 can for example be designed as a ring.
  • the ring has an inner diameter that is slightly larger than the diameter of the striking surface 25 .
  • the striker 15 has a (bump) surface 28 .
  • the impact face 28 preferably has a conical shape. In the area of the impact face 28 , the diameter of the striking surface 15 increases uniformly along the striking axis 24 from the smaller diameter of the striking surface 25 to the diameter of the leading lateral surface 23 .
  • the impact face 28 is rotationally symmetrical to the striking axis 24 .
  • An inclination of the impact face 28 with respect to the striking axis 24 and thus also with respect to the working axis 7 is preferably constant along the striking axis 24 .
  • the stop 20 can have a likewise conical surface facing the impact surface 28 .
  • the stop 20 can be supported in the machine housing 10 via a damping element 29 , for example an elastic O-ring.
  • the striker 15 moves only slightly out of its working position in chiseling operation. After a stroke of the racquet 14 to the anvil 15, the anvil 15 is moved a maximum as far as the tool 3 moves out of the tool holder. 2 Due to the contact pressure of the user, the tool 3 is pushed back into the tool holder until the striker 15 bears against the stop 20 .
  • a (empty stroke) catcher 30 stops the striker 15 in the striking direction 5 .
  • the anvil 15 strikes the catcher 30 with an end face 31 .
  • the striker 15 is then in its most advanced position in the striking direction 5 .
  • the striker 15 is tilted slightly relative to the guide 21 when the striker 15 strikes against the empty stroke catcher 30 , ie the striker axis 24 is tilted relative to the working axis 7 .
  • the tilting causes the striker 15 to jam in the guide 21 , as a result of which kinetic energy of the striker 15 is reduced and the striker 15 preferably comes to a standstill.
  • the tilting is achieved by a special asymmetry of the end face 31 of the striker 15 .
  • the end face 31 points in the direction of impact 5 and is inclined with respect to the striking axis 24 .
  • the striking surface 25 connects the outer surface 23 to the abutting surface 26 .
  • the diameter of the anvil 15 is reduced from the maximum diameter of the leading lateral surface 23 to the diameter of the abutting surface 26 .
  • the special feature of the end face 31 is its subdivision in the circumferential direction 32 into a first segment 33 and a second segment 34 .
  • both segments 33 , 34 can be conical.
  • the first segment 33 is offset from the second segment 34 in the impact direction 5 .
  • the two segments 33 , 34 are inclined with respect to the striking axis 24 and working axis 7 .
  • the offset shows that for a section of the end face 31 with a constant radial distance from the working axis 7 , the proportion of the section belonging to the first segment 33 is closer to the abutment surface 26 than the proportion of the section belonging to the second segment 34 .
  • the first segment 33 thus strikes first in the direction of impact 5 .
  • a portion of the first segment 33 is in the range from 200 degrees to 270 degrees.
  • the second segment 34 is preferably conical.
  • An axis of the complete cone, which forms the second segment 34 preferably coincides with the striking axis 24 .
  • the first segment 33 can also be conical.
  • a corresponding axis does not coincide with the striking axis 24 .
  • the axis can be offset or tilted parallel to the striking axis 24 .
  • a radius of curvature r1 of the first segment 33 is larger than the radius of curvature r2 of the second segment.
  • the flatter first segment 33 can take up a larger portion of the circumference than the steeper second segment 34 .
  • the empty space catcher 30 is formed, for example, by a conical narrowing of the guide 21 .
  • the constriction has an inner diameter which is larger than the diameter of the abutment surface 26 of the striker 15 but smaller than the diameter of the outer surface 23 of the striker 15 .
  • the constriction has a conical inner surface 37 which points in the direction of the die 15 .
  • the conical inner surface 37 is preferably rotationally symmetrical to the working axis 7 .
  • the front, first segment 34 causes a larger radial force component compared to the flat segment 33 .
  • the die 15 is tilted or bent. Both effects lead to an efficient braking of the striker 15 . This also occurs if the guide 21 of the striker 15 already has a larger play parallel to the working axis 7 due to wear.
  • the guide 21 can be rigidly anchored in the machine housing 10 .
  • the exemplary guide 21 is suspended damped in the direction of impact 5 .
  • the guide 21 can lie in a slide bearing 38 .
  • a damping element 39 for example an elastomer, is clamped between a stop 40 fixed to the housing and a nose 41 .
  • the stop 40 is arranged in the direction 5 of the nose 41 .
  • the first segment 33 can be formed by a flat or almost flat bevel.
  • a radius of curvature r1 of the first segment 33 is correspondingly very large.
  • the first segment 33 has a smaller proportion of the circumference, for example between 30 degrees and 45 degrees.
EP18215055.7A 2018-12-21 2018-12-21 Machine-outil portative Withdrawn EP3670096A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP18215055.7A EP3670096A1 (fr) 2018-12-21 2018-12-21 Machine-outil portative
PCT/EP2019/083650 WO2020126499A1 (fr) 2018-12-21 2019-12-04 Machine-outil portative
US17/415,354 US11858104B2 (en) 2018-12-21 2019-12-04 Portable power tool
EP19812801.9A EP3898117B1 (fr) 2018-12-21 2019-12-04 Machine-outil de burinage portative
CN201980074739.8A CN113165153A (zh) 2018-12-21 2019-12-04 便携式动力工具

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18215055.7A EP3670096A1 (fr) 2018-12-21 2018-12-21 Machine-outil portative

Publications (1)

Publication Number Publication Date
EP3670096A1 true EP3670096A1 (fr) 2020-06-24

Family

ID=64755368

Family Applications (2)

Application Number Title Priority Date Filing Date
EP18215055.7A Withdrawn EP3670096A1 (fr) 2018-12-21 2018-12-21 Machine-outil portative
EP19812801.9A Active EP3898117B1 (fr) 2018-12-21 2019-12-04 Machine-outil de burinage portative

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP19812801.9A Active EP3898117B1 (fr) 2018-12-21 2019-12-04 Machine-outil de burinage portative

Country Status (4)

Country Link
US (1) US11858104B2 (fr)
EP (2) EP3670096A1 (fr)
CN (1) CN113165153A (fr)
WO (1) WO2020126499A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2918376A1 (fr) * 2014-03-12 2015-09-16 HILTI Aktiengesellschaft Machine-outil portative de burinage
US9339924B2 (en) 2011-07-26 2016-05-17 Black & Decker Inc. Hammer

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Publication number Priority date Publication date Assignee Title
US3952813A (en) * 1975-02-07 1976-04-27 Nikolai Prokhorovich Chepurnoi Percussive device for driving holes in soil
JPS6347494A (ja) * 1986-08-18 1988-02-29 株式会社　リツト 空気衝撃工具
JPH09103970A (ja) * 1995-10-03 1997-04-22 Nippon Electric Ind Co Ltd 電動インパクトレンチ
US5906244A (en) * 1997-10-02 1999-05-25 Ingersoll-Rand Company Rotary impact tool with involute profile hammer
DE102004031866B4 (de) * 2004-07-01 2015-09-10 Andreas Stihl Ag & Co. Kg Handgeführtes Arbeitsgerät
US7249638B2 (en) * 2005-01-07 2007-07-31 Black & Decker Inc. Impact wrench anvil and method of forming an impact wrench anvil
DE102005000042A1 (de) 2005-04-25 2006-10-26 Hilti Ag Bohr-oder Meisselhammer
AU2009244208B2 (en) * 2008-05-07 2014-10-09 Milwaukee Electric Tool Corporation Anvil assembly for a power tool
DE102008043136A1 (de) * 2008-10-23 2010-04-29 Robert Bosch Gmbh Schlaghammer mit linearmotorischem Antrieb
CN102114624A (zh) * 2009-12-31 2011-07-06 南京德朔实业有限公司 一种电动工具
DE102010006152B4 (de) * 2010-01-29 2014-07-03 Aeg Electric Tools Gmbh Handgeführter Bohrhammer
DE102010029915A1 (de) * 2010-06-10 2011-12-15 Hilti Aktiengesellschaft Werkzeugmaschine und Steuerungsverfahren
KR101263885B1 (ko) * 2011-06-21 2013-05-13 윤무영 회전력 전달장치
DE102012220886A1 (de) * 2012-11-15 2014-05-15 Hilti Aktiengesellschaft Werkzeugmaschine
JP2014166667A (ja) * 2013-02-28 2014-09-11 Hitachi Koki Co Ltd 打撃工具
US10260711B2 (en) 2014-05-30 2019-04-16 Osram Sylvania Inc. Light control films and lighting devices including same

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9339924B2 (en) 2011-07-26 2016-05-17 Black & Decker Inc. Hammer
EP2918376A1 (fr) * 2014-03-12 2015-09-16 HILTI Aktiengesellschaft Machine-outil portative de burinage

Also Published As

Publication number Publication date
WO2020126499A1 (fr) 2020-06-25
EP3898117B1 (fr) 2022-11-16
EP3898117A1 (fr) 2021-10-27
US11858104B2 (en) 2024-01-02
CN113165153A (zh) 2021-07-23
US20220063078A1 (en) 2022-03-03

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