EP3898117B1 - Machine-outil de burinage portative - Google Patents

Machine-outil de burinage portative Download PDF

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Publication number
EP3898117B1
EP3898117B1 EP19812801.9A EP19812801A EP3898117B1 EP 3898117 B1 EP3898117 B1 EP 3898117B1 EP 19812801 A EP19812801 A EP 19812801A EP 3898117 B1 EP3898117 B1 EP 3898117B1
Authority
EP
European Patent Office
Prior art keywords
segment
die
tool
axis
working 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.)
Active
Application number
EP19812801.9A
Other languages
German (de)
English (en)
Other versions
EP3898117A1 (fr
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
Publication of EP3898117A1 publication Critical patent/EP3898117A1/fr
Application granted granted Critical
Publication of EP3898117B1 publication Critical patent/EP3898117B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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 such as a hammer drill or an electric chisel.
  • a hammer drill according to the preamble of claim 1 is made, for example US 9,339,924 B2 known.
  • the hammer drill has an electro-pneumatic impact mechanism.
  • a user turns on an electric motor of the rotary hammer by pressing a button.
  • the percussion mechanism should only be activated when the user presses the hammer drill, more precisely a tool, against a substrate.
  • the electric motor continuously moves an exciter piston of the percussion mechanism.
  • a hammer of the hammer mechanism is coupled to the movement of the exciter piston via a pneumatic chamber when ventilation openings in the pneumatic chamber are closed.
  • the ventilation openings are controlled by a gun.
  • the die is placed on the working axis between the hammer and the tool.
  • the die When the percussion mechanism is pressed, the die is moved into a working position in the direction of the hammer. In the working position, the ventilation openings are closed and the impact mechanism is active. If there is no pressure, a hit of the club, a so-called empty shot, ensures that the deadbolt leaves the working position. The ventilation openings are released and the striking mechanism switches off.
  • the deadbolt moves in the direction of impact due to the empty shot.
  • a catcher catches the dopper.
  • the snapper comes to a standstill preferably through the catcher.
  • the striker may bounce off the catcher, slide back into the working position, and undesirably activate the hammer mechanism, closing the vents.
  • the next beat is a blank again.
  • the blank impacts represent a considerable burden for the hand-held power tool and the user, since the entire impact energy is absorbed within the hand-held power tool and is not directed into the ground as desired.
  • US 9,339,924 B2 describes a deadbolt with a front face that is eccentric relative to the catcher.
  • the eccentric face is intended to cause the die to rotate, thereby extracting kinetic energy from the die.
  • the Döpper then no longer reaches the working position.
  • the solution described depends on tolerance-free guidance of the die in order to ensure the eccentric arrangement.
  • the die and its guide are subject to a high level of wear due to the entry of dust and drill cuttings via the tool, which affects the accuracy of the guide.
  • the eccentric arrangement influences the efficiency of the transmission of the shock wave from the die to the axially arranged tool.
  • the chiseling hand tool has the features of claim 1, it has a tool holder, a striking mechanism and a blank impact catcher.
  • the tool holder can hold a tool and hold it movably on a working axis.
  • the hammer mechanism includes an exciter piston, a hammer, a beater and a guide for the beater.
  • the beater couples to the movement of the exciter piston via a pneumatic chamber.
  • the striker is arranged on the working axis in the direction of impact from the bat.
  • the guide guides the die on the working axis.
  • the deadbeat catcher for the deadlock has a conical inner surface facing the deadlock.
  • the die has an associated end face that is inclined relative to the working axis and points in the direction of impact.
  • the face abuts the conical inner surface when the striker is in its most advanced position in the direction of strike.
  • the face of the die has a first segment and a second segment in the circumferential direction. The second segment is offset in the direction of flap compared to the first segment. The offset in the two segments of the face causes the deadbolt to tilt when it comes into contact with the empty-blow catcher. The tilting leads to the die jamming in the guide tube. Simulations show additional deflection of the beater due to the axial offset between the opposing contact points of the beater and catcher. This increases the stopping effect of the catcher on the snap.
  • the hammer drill has a tool holder 2, in which a tool 3 can be used and locked.
  • the tools 3 can, for example, be drill bits for turning and chiseling processing of mineral building materials, such as concrete or rock, or chisels for purely chiseling processing of the same building materials.
  • the rotary hammer 1 contains a pneumatic percussion mechanism 4 which periodically exerts impacts on the tool 3 in the impact direction 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 percussion 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 handheld power tools 1 or in purely chiseling handheld power tools 1 are without an output shaft.
  • the hand-held power tool 1 has a handle 9, by means of which the user can hold and guide the hand-held power tool 1 during operation.
  • the handle 9 is attached to a machine housing 10 .
  • the handle 9 is preferably arranged at an end of the hand-held power tool 1 or of the machine housing 10 which is remote from the tool holder 2 .
  • a working axis 7 parallel to the direction of impact 5 and running centrally through the tool holder 2 preferably runs through the handle 9 if it is to 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 percussion mechanism 4 .
  • the user can start up the hand-held power tool 1 using a button 12 . Pressing the button 12 activates the motor 8.
  • the button 12 is preferably arranged on the handle 9 , as a result of which it can be actuated by the hand gripping the handle 9 .
  • the percussion mechanism 4 has an exciter piston 13, a hammer 14 and a striker 15.
  • the exciter piston 13, the hammer 14 and the striker 15 are arranged one after the other on the working axis 7 in the direction of impact 5 .
  • the exciter piston 13 is coupled to the motor 8 via a gear train.
  • the gear train converts the rotational movement of the motor 8 into a periodic forward and backward movement of the exciter piston 13 on the working axis 7 .
  • An exemplary gear train is based on an eccentric wheel 16 and a connecting rod 17. Another embodiment is based on a wobble drive.
  • the beater 14 is coupled to the movement of the exciter 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 hammer 14 .
  • the beater 14 is designed as a piston.
  • the pneumatic chamber 18 is closed off in the radial direction by a guide tube 19 .
  • the exciter piston 13 and the beater 14 slide airtightly against the inner surface of the guide tube 19.
  • the exciter piston can be cup-shaped.
  • the beater slides inside the exciter piston.
  • the racquet can be cup-shaped, with the exciter piston sliding within the racquet.
  • the beater 14 moves, coupled via the pneumatic chamber 18 , periodically parallel to the impact direction 5 between a drive-side reversal point and a tool-side reversal point.
  • the reversal point on the tool side is specified by the snap die 15 , on which the beater 14 strikes at the reversal point on the tool side.
  • the die 15 is movably guided parallel to the impact direction 5 between a stop 20 and the tool 3 .
  • the user presses the tool 3 against the die 15 and indirectly the die 15 against the stop 20.
  • the position of the die 15 resting against the stop 20 is referred to as the working position.
  • the impact of the beater 14 on the die 15 preferably takes place when the die 15 is in the working position.
  • the striker 15 serves as an intermediary for the impact of the hammer 14 on the tool 3. A damping of the impact by the striker 15 is not desirable.
  • the die 15 slides in a tubular guide 21 on the working axis 7.
  • the working axis 7 is defined by the cylindrical inner surface 22 of the guide 21 .
  • the inner surface 22 is arranged coaxially to the working axis 7 .
  • the die 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 die 15.
  • the lateral surface 23 defines a longitudinal axis or die axis 24 of the die 15.
  • the die axis 24 corresponds to the axis of symmetry of the die Lateral surface 23. Due to the guidance 21 of the die 15 via the leading lateral surface 23 , the die axis 24 lies on the working axis 7.
  • the striker 15 has a striking surface 25 which points in the direction of the racquet 14 .
  • the racquet 14 hits the striking surface 25 .
  • the surface area of the striking surface 25 is typically less than the surface area of a cross section in the area of the leading lateral surface 23.
  • the striking surface 25 is preferably rotationally symmetrical to the die axis 24.
  • the hammer 14 thus strikes the striking surface 25 in the middle , which ensures more efficient energy transfer.
  • the striking surface 25 can be of planar design; a crowned design is preferred. In the illustrated embodiment, the striking surface 25 is followed by a cylindrical section whose diameter corresponds to the diameter of the striking surface 25 .
  • the die 15 has an impact surface 26 which points in the direction of the tool 3 , ie in the direction of impact 5 and is averted from the hammer 14 .
  • the striker 15 bears against the tool 3 with the abutting surface 26 or hits the tool 3 with the abutting surface 26 .
  • the surface area of impact surface 26 is typically less than the surface area of a cross-section in the area of leading lateral surface 23.
  • Impact surface 25 is rotationally symmetrical to die axis 24. Impact transmission from die 15 to tool 3 takes place centrally from impact surface 26.
  • Impact surface 26 can be flat or crowned.
  • the abutment surface 26 is adjoined by a cylindrical section 27 whose diameter corresponds to the diameter of the abutment surface 26 .
  • the snap die 15 rests against the stop 20 in the working position.
  • the stop 20 can be designed as a ring, for example.
  • the ring has an inside diameter that is slightly larger than the diameter of the face 25 .
  • the snap die 15 has a (rebound impact) surface 28 .
  • the impact surface 28 preferably has a conical shape.
  • the diameter of the die 15 increases uniformly along the die axis 24 from the smaller diameter of the striking face 25 to the diameter of the leading lateral surface 23.
  • the bounce face 28 is rotationally symmetrical to the die axis 24.
  • An inclination of the bounce face 28 relative to the die axis 24 and thus also in relation to the working axis 7 is preferably constant along the die axis 24 .
  • the stop 20 can also have a conical surface facing the rebound 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 snap die 15 moves only slightly out of its working position. After the beater 14 hits the die 15, the die 15 moves as far as the tool 3 moves out of the tool holder 2 at most. Due to the contact pressure exerted by the user, the tool 3 is pushed back into the tool holder until the snap die 15 rests against the stop 20 .
  • a (blank strike) catcher 30 stops the striker 15 in the direction of impact 5.
  • the striker 15 strikes the catcher 30 with an end face 31 .
  • the snap die 15 is then in its most advanced position in the direction of impact 5 .
  • the die 15 is tilted somewhat in relation to the guide 21 when the die 15 hits the blank strike catcher 30 , ie the die axis 24 is tilted in relation to the working axis 7 .
  • the tilting causes the die 15 to jam in the guide 21, as a result of which kinetic energy of the die 15 is reduced and the die 15 preferably comes to a standstill.
  • the tilting is achieved by a special asymmetry of the end face 31 of the snap die 15 .
  • the end face 31 points in the direction of impact 5 and is inclined relative to the die axis 24 .
  • the impact surface 25 connects the lateral surface 23 with the impact surface 26.
  • the diameter of the die 15 reduces from the maximum diameter of the leading lateral surface 23 to the diameter of the impact 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 in the direction of impact 5 in relation to the second segment 34 .
  • the two segments 33, 34 are inclined relative to the die axis 24 and the working axis 7 .
  • the offset is reflected in the fact that for a section of the end face 31 at a constant radial distance from the working axis 7, the portion of the section associated with the first segment 33 is closer to the abutment surface 26 than the portion of the section associated with the second segment 34
  • the first segment 33 thus strikes first in the direction of impact 5 .
  • a portion of the first segment 33 ranges from 200 degrees to 270 degrees.
  • the second segment 34 is preferably cone-shaped.
  • An axis of the full cone forming the second segment 34 preferably coincides with the die axis 24 .
  • the first segment 33 can also be cone-shaped. One corresponding axis does not coincide with the die axis 24 .
  • the axis can be offset parallel to the die axis 24 or canted.
  • 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 proportion of the circumference than the steeper second segment 34.
  • the blank firing 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 impact surface 26 of the die 15 but less than the diameter of the lateral surface 23 of the die 15 .
  • the constriction has a conical inner surface 37 which faces towards 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.
  • die 15 is tilted or bent. Both effects lead to efficient braking of the die 15. This also occurs when the guide 21 of the die 15 parallel to the working axis 7 already has greater play due to wear.
  • the guide 21 can be rigidly anchored in the machine housing 10 .
  • the exemplary guide 21 is suspended in a damped manner in the impact direction 5 .
  • the guide 21 can be located 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 by the nose 41 in the impact direction 5 .
  • 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.

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

Claims (6)

  1. Machine-outil de burinage à main (1) comprenant
    un porte-outil (2) destiné à maintenir un outil (3) sur un axe de travail (7), un mécanisme de percussion (4) qui comporte un piston excitateur (13), un percuteur (14), une chambre pneumatique (18) fermée par le piston excitateur (13) et le percuteur (14) et destinée à coupler un mouvement du percuteur (14) au piston excitateur (13) et une matrice (15) disposée en aval du percuteur (14) dans la direction de percussion (5) et destinée à transmettre une percussion du percuteur (14) à l'outil (3),
    un guide (21) destiné à la matrice (15) pour guider la matrice (15) sur l'axe de travail (7),
    un récupérateur de percussion à vide (30) destiné à la matrice (15), le récupérateur (30) comportant une surface intérieure conique (37) dirigée vers la matrice (15), et la matrice (15) comportant une surface frontale (31) qui pointe dans la direction de percussion (5), qui est inclinée par rapport à l'axe de travail (7) et qui vient en appui sur la surface intérieure conique (37) lorsque la matrice (15) est dans sa position la plus avancée dans la direction de percussion (5),
    caractérisé en ce que
    la surface frontale (31) de la matrice (15) comporte un premier segment (33) et un deuxième segment (34) dans la direction circonférentielle (32), le deuxième segment (34) étant décalé du premier segment (33) dans la direction de percussion (5).
  2. Machine-outil de burinage à main (1) selon la revendication 1, caractérisée en ce que, dans une vue en coupe perpendiculaire à l'axe de travail (7), le premier segment (33) a un premier rayon de courbure (r1) et le deuxième segment (34) a un deuxième rayon de courbure (r2), et le premier rayon de courbure (r1) étant supérieur au deuxième rayon de courbure (r2).
  3. Machine-outil de burinage à main (1) selon la revendication 1 ou 2, caractérisé en ce que le premier segment (33) est décrit par un cône dont l'axe est décalé de l'axe de travail (7).
  4. Machine-outil de burinage à main (1) selon la revendication 3, caractérisé en ce que le deuxième segment (34) est décrit par un cône dont l'axe est coaxial à l'axe de travail (7).
  5. Machine-outil de burinage à main (1) selon la revendication 5, caractérisé en ce que le cône du premier segment (33) est décalé du cône du deuxième segment (34) suivant l'axe de travail (7).
  6. Machine-outil de burinage à main (1) selon l'une des revendications précédentes, caractérisé en ce que l'inclinaison du premier segment (33) par rapport à l'axe de travail (7) est égale à l'inclinaison du deuxième segment (34) par rapport à l'axe de travail (7).
EP19812801.9A 2018-12-21 2019-12-04 Machine-outil de burinage portative Active EP3898117B1 (fr)

Applications Claiming Priority (2)

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

Publications (2)

Publication Number Publication Date
EP3898117A1 EP3898117A1 (fr) 2021-10-27
EP3898117B1 true EP3898117B1 (fr) 2022-11-16

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 Before (1)

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

Country Status (4)

Country Link
US (1) US11858104B2 (fr)
EP (2) EP3670096A1 (fr)
CN (1) CN113165153B (fr)
WO (1) WO2020126499A1 (fr)

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* Cited by examiner, † Cited by third party
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
WO2009137690A1 (fr) * 2008-05-07 2009-11-12 Milwaukee Electric Tool Corporation Ensemble enclume pour outil motorisé
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
GB201112829D0 (en) 2011-07-26 2011-09-07 Black & Decker Inc Hammer
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
EP2918376A1 (fr) * 2014-03-12 2015-09-16 HILTI Aktiengesellschaft Machine-outil portative de burinage
WO2015184456A1 (fr) 2014-05-30 2015-12-03 Osram Sylvania Inc. Films de commande de lumière et dispositifs d'éclairage comprenant lesdits films

Also Published As

Publication number Publication date
US20220063078A1 (en) 2022-03-03
US11858104B2 (en) 2024-01-02
WO2020126499A1 (fr) 2020-06-25
CN113165153A (zh) 2021-07-23
EP3670096A1 (fr) 2020-06-24
EP3898117A1 (fr) 2021-10-27
CN113165153B (zh) 2024-05-24

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