EP2918376A1 - Machine-outil portative de burinage - Google Patents

Machine-outil portative de burinage Download PDF

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Publication number
EP2918376A1
EP2918376A1 EP14159121.4A EP14159121A EP2918376A1 EP 2918376 A1 EP2918376 A1 EP 2918376A1 EP 14159121 A EP14159121 A EP 14159121A EP 2918376 A1 EP2918376 A1 EP 2918376A1
Authority
EP
European Patent Office
Prior art keywords
striker
impact
catcher
bearing
racket
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Withdrawn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
EP14159121.4A
Other languages
German (de)
English (en)
Inventor
Aaron Wiedner
Markus Hartmann
Udo Hauptmann
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 EP14159121.4A priority Critical patent/EP2918376A1/fr
Priority to EP15709154.7A priority patent/EP3116688B1/fr
Priority to CN201580006134.7A priority patent/CN105939820B/zh
Priority to US15/125,060 priority patent/US20170014983A1/en
Priority to PCT/EP2015/054919 priority patent/WO2015135916A1/fr
Publication of EP2918376A1 publication Critical patent/EP2918376A1/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • B25D2217/0019—Guide-sleeves
    • 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
    • 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
    • B25D2250/225—Serrations

Definitions

  • the present invention relates to a chiselling hand tool machine with Leerfordabsclien.
  • US 2002/0050191 A describes a generic hand tool with a coupled via an air spring to a pathogen racquet.
  • the striking mechanism has an anvil, which can move from a working position to a position that is advanced in the direction of impact when there is no clearance.
  • the racket can now also continue to advance in the direction of impact, thereby releasing the ventilation opening of the air spring.
  • the air spring remains deactivated until the striker is pushed back into the working position by a drill or chisel pressed against the ground. The case also shifted racket closes the vent and the air spring is activated again.
  • the hand tool has a tool holder for receiving a chiseling tool coaxial with a working axis.
  • a striking mechanism has a pathogen, a pneumatic chamber, a club and a striker on the working axis one after the other.
  • the pathogen is periodically forced by an engine.
  • the racket is guided coaxially to the working axis movable.
  • the pneumatic chamber is adapted for coupling movement of the racket to movement of the pathogen between the pathogen and the racket.
  • the striker is disposed in the direction of impact after the racket for indirectly transmitting a shock from the racket to a tool received in the tool holder.
  • the striker is arranged in a warehouse.
  • the striker has a lateral surface and a stop direction facing stop surface.
  • the bearing has a coaxially arranged to the working axis sleeve and a catcher.
  • the lateral surface of the striker is slidably guided on the inside of the sleeve.
  • the catcher is in the direction of impact from the stopper surface of the striker to limit movement of the striker Döppers arranged in the direction of impact.
  • a backdrop is for displacing the striker in a relative rotation with respect to the bearing when the striker moves in the direction of impact.
  • the scenery has a flank on the striker; and at the bearing a flank, wherein the two flanks abutting each other in the movement; rise in the direction of impact in the same circumferential direction.
  • the striker turns at the blank over the camp.
  • the conversion of the axial movement in the rotational movement proves to be very lossy, whereby advantageously the striker comes to a halt in the vicinity of the catcher.
  • the scenery may have a spur gear teeth on the end face of the striker and a spur gear teeth on the catcher.
  • the spur gears are preferably formed complementary to each other. When the striker hits the catcher, the serrations align with each other, causing the striker or catcher to rotate.
  • the bearing can be freely rotatably mounted in the machine housing about the working axis.
  • the bearing is decoupled from a drive shaft.
  • the freely rotatable catcher can rest in the direction of impact on an elastic damping element.
  • the friction between the damping element and the catcher stops the striker.
  • the damping element ensures that the catcher is always in its rear stop at the operating point and thus can perform an idle stroke axial movement direction tool, which is limited by the stop in the guide tube. By this additional impact process the striker is deprived of more energy.
  • the scenery may have a flank forming spiral groove in a cylindrical surface, the striker and engaging in the groove from the bearing runners.
  • the gate may equally comprise a flank forming helical groove in a cylindrical inner surface of the bearing and engaging in the groove from the striker rotor.
  • Fig. 1 schematically shows a hammer drill 1 as an example of a chiseling hand tool .
  • the hammer drill 1 has a tool holder 2, in which a shank end 3 of a tool, for example one of the drill 4, can be used.
  • a primary drive of the hammer drill 1 is a motor 5, which drives a pneumatic impact mechanism 3 and an output shaft 6 .
  • a battery pack 7 or a power line provide the motor 5 with power.
  • a user can guide the hammer drill 1 by means of a handle 8 and take means of a system switch 9, the hammer drill 1 is in operation.
  • the hammer drill 1 rotates the drill 4 continuously about a working axis 10 and can beat the drill 4 in the direction of impact 11 along the working axis 10 in a substrate.
  • the striking mechanism 3 and preferably the further drive components are arranged within a machine housing 12 .
  • the pneumatic impact mechanism 3 has a piston-shaped exciter 13, a pneumatic chamber 14, a piston-shaped racket 15 and an anvil 16, which are successively arranged in the direction of impact 11 on the working axis 10 and guided along the working axis 10 .
  • the exciter 13 and the racket 15 are arranged for example in a stationary guide tube 17 .
  • the racket may also be arranged in a cup-shaped exciter whose tubular wall forms the guide tube for the racket; analogously, the racket can be designed cup-shaped.
  • the exciter 13 is connected to the motor 5 via a gear unit, which converts the rotational movement of the motor 5 into a periodic linear forward and backward movement of the exciter 13 along the working axis 10 .
  • the gear unit includes an eccentric 18 driven by the motor 5 , which is connected to the exciter 13 by a connecting rod 19 .
  • the gear unit may also contain a wobble drive.
  • the pneumatic chamber 14 is closed by the exciter 13 and the racket 15 .
  • the motor-driven periodic movement of the exciter 13 increases the air pressure in the pneumatic chamber 14 from the ambient pressure.
  • the freely movable racket 15 is accelerated away from the exciter 13 by the increased air pressure, accelerated in the direction of impact 11 or accelerated towards the exciter 13 at reduced air pressure.
  • the movement of the racket 15 is coupled to the movement of the exciter 13 through the pneumatic chamber 14, also referred to as an air spring.
  • the racket 15 oscillates in operation between a front inflection point, in which the exciter 13 and the racket 15 compress the pneumatic chamber 14 maximum, and a rear inflection point (impact point), in which the racket 15 strikes the striker 16 .
  • the striker 16 is held in operation by a pressed-on the substrate tool 4 in a working position, which tunes the distance between the turning points such that the periodicity of the movement of the racket 15 with the periodicity of movement of the exciter 13 matches. Missing the contact pressure of the tool 4, for example, because the user lifts the hammer drill 1 from the ground, the striker 16 leaves the working position in the direction of impact 11. The bat 15 flies over the impact point in the direction of impact 11 addition. In this case, a ventilation opening 20 is released, which allows an exchange of air of the pneumatic chamber 14 with the environment and thus deactivates the air spring. The racket 15 is no longer coupled to the exciter 13 and the striking mechanism 3 switches off automatically. The striker 16 preferably remains outside the working position. Once the user presses the tool 4 back to the ground, the striker 16 is moved to the working position and the vent opening 20 is closed. The Schlagtechnik 3 turns itself on again.
  • the exemplary ventilation openings 20 are in radial openings in the guide tube 17, which seals the racket 15 with respect to the pneumatic chamber 14 in operation.
  • the ventilation openings 20 are offset in the direction of impact 11 to the pneumatic chamber 14 when the racket 15 is in the direction of impact 11 before the impact point.
  • the pneumatic chamber 14 extends to the ventilation openings 20 and is ventilated.
  • the ventilation openings 20 can also be opened or closed by sleeves which actuate the racket 15 or the striker 16 .
  • the striker 16 has a substantially cylindrical core 21 and a collar 22 surrounding a central portion of the core 21 .
  • the core 21 is along the working axis 10 through in Essentially to the working axis 10 vertical end faces 23, 24 completed.
  • the end faces 23, 24 form the impact-absorbing face 23 on which the racket 15 strikes w. the impact-releasing face 24, which strikes the drill 4 .
  • the striking surfaces 23, 24 may be slightly convex.
  • the collar 22 has a cylindrical lateral surface 25 and is closed along the working axis 10 by end faces 26, 27 , which are inclined relative to the working axis 10 .
  • the racket 15 facing, front end face 26 is conical.
  • the racket 15 facing away from the rear end face 27 has a cone-shaped envelope.
  • the mean inclination 28 of the end faces 26, 27 is in the range between 30 degrees and 70 degrees.
  • the striker 16 is guided in a bearing 29 on the working axis 10 .
  • the exemplary bearing 29 includes a sleeve 30 against which the cylindrical surface 25 of the collar 22 of the striker 23 abuts.
  • the cylindrical jacket surface 31 of the core 21 for axially guiding the beatpiece 23 can rest on the sleeve 30 .
  • the bearing 29 limits the axial movement in the direction of impact 11 by a catcher 32 and counter to the direction of impact 11 by a base 33.
  • the example annular socket 33 is in the direction of impact 11 in front of the collar 22 of the striker 23.
  • the core 21 may be in the opening of the Moving pedestal 33 freely, the inner diameter of the base 33 is designed to be a game greater than the diameter of the impact-absorbing face 24 .
  • the diameter of the collar 22 is greater than the inner diameter of the base 33, consequently, the collar 22 may rest against the base 33 against impact direction 11 .
  • the pressed drill 4 presses the collar 22, that is, the racket 15 facing end face 26, against the base 33, which corresponds to the working position of the striker 23 during operation.
  • the impact-absorbing face 24 defines in the working position the point of impact of the striking mechanism 3.
  • the catcher 32 is located in the direction of impact 11 in front of the collar 22 .
  • the catcher 32 is annularly formed with an inner diameter which is larger than the diameter of the impact-releasing impact surface 24 and less than the diameter of the collar 22 .
  • the pointing in the direction of impact 11 end face 27 of the collar 22 may rest in the direction of impact 11 on the catcher 32 , since they overlap in the radial direction.
  • the striker 16 is stopped by the catcher 32 after the racket 15 strikes the striker 16 in the absence of contact pressure of the tool 4 .
  • the catcher 32 may be formed as a constriction of the sleeve 30 as shown or like the example socket 33 may be formed as a separate component.
  • the catcher 32 preferably has an axial play in the machine housing 12.
  • the catcher 32 is supported on the machine housing 12 in the direction of impact 11 by means of a damping element 34 .
  • the catcher 32 preferably absorbs the kinetic energy of the striker 23 to prevent the striker 16 from sliding back to the operative position by itself due to the recoil.
  • the striker 16 and its bearings 29 are provided with a link 35 which causes the striker 16 in its movement in the direction of impact 11 in a rotational movement.
  • the rotational movement proves to be an effective measure, the striker 16 to escape its kinetic energy during impact with the catcher 32 .
  • the striker 16 thus remains close to the catcher 32 and does not accidentally slip back into the working position.
  • the link 35 includes, for example the catcher 32 facing spur gear teeth 36 on the rear end surface 27 of the collar 22 and the collar 22 facing the spur gear toothing 37 at the catcher 32.
  • the two end teeth 36, 37 are complementary to each other.
  • the spur toothing 36 of the collar 22 may be formed as a bevel gear 36
  • the complementary spur toothing 37 of the catcher 32 is concave.
  • the striker 16 is freely rotatable about the working axis 10 in the bearing 29 . The angular orientation of the two end faces 26, 27 is therefore largely random. As soon as the striker 16 strikes the catcher 32 , the two end faces 26 are oriented towards one another.
  • the striker 16 rotates by a quarter of the width of the teeth 38 of the spur gear 36 with respect to the catcher 32 until the two spur gears 36, 37 are aligned with each other.
  • the gate 35 proves to be highly attenuating. Presumably results in the strong damping due to a dynamic inhibition, which arises after the two serrations 36, 37 are aligned.
  • the spur gears 36, 37 now move apart due to the rotational movement of the striker 23 along the working axis 10 , against the pulse of the striker 16 in the direction of impact 11th
  • the spur toothing 36 of the collar 22 has a plurality of identical teeth 38, which are arranged in the circumferential direction 39 successively distributed equidistant.
  • the number of teeth 38 depends on the size of the striker 16, for example, the number is between 15 and 40.
  • the head line 40 of the tooth 38 is rectilinear and lies with the working axis 10 in a plane. When formed as a bevel gear spur gear 36 of the collar 22 , the head line 40 between 30 degrees and 70 degrees with respect to the working axis 10 is inclined.
  • the head line may be skewed in another embodiment with the working axis 10, wherein the head line monotonically from one end to the other end of the working axis 10 degrees. Alternatively, the head line may be formed spirally.
  • the tooth 38 has a flank 42 pointing only in the right-handed circumferential direction 41 and an edge pointing only in the left-handed circumferential direction 39 43.
  • the two flanks 42, 43 run in the direction of impact 11 towards each other and in the head line 40 together.
  • the tooth 38 tapers in the direction of impact 11.
  • An inclination 44 of the right-hand flank 42 is determined relative to a reference plane 45 .
  • the reference plane 45 is spanned by the working axis 10 and the point on the flank 42 at which the slope 44 is to be determined.
  • the slope 44 is preferably in the range between 30 degrees and 60 degrees.
  • the inclination 46 of the left-handed flank 43 with respect to the reference plane 45 is preferably equal to the inclination 44 of the right-hand flank 42.
  • the two flanks 42, 43 can converge toward one another in the direction of the working axis 10 .
  • the tooth 38 is thus wider on its outside than closer to the working axis 10.
  • the width of the tooth 38 preferably increases in proportion to the distance from the working axis 10.
  • the angular width of the tooth 38 is thus constant along the radial direction.
  • a height 47 of the teeth 38, ie the dimension of the flanks 42, 43 along the working axis 10, is in the range between 2 mm and 5 mm.
  • the spur toothing 37 of the catcher 32 is constructed to be complementary to the spur toothing 36 of the collar 22 .
  • the spaces between the teeth 48 of the catcher 32 correspond in shape and number to the teeth 38 of the collar 22.
  • a left-hand flank 49 of the tooth 48 on the catcher 32 is largely congruent with the right-hand flank 42 of the tooth 38 on the collar 22;
  • a right-hand flank of the tooth 48 on the catcher 32 is largely congruent with the left-hand flank 43 of the tooth 38 on the collar 22nd
  • the catcher 32 may be freely rotatable about the working axis 10 in the machine housing 12 .
  • the catcher 32 is decoupled from the output shaft 6 .
  • both rotate relative to each other.
  • the rotational energy transmitted by the striker 16 into the catcher 32 is removed from the striking mechanism 3 .
  • the damping element 34 is preferably rotationally fixed in the machine housing 12, whereby the catcher 32 moves relative to the damping element 34 .
  • the friction between the rubber-containing damping element 34 and the catcher 32 extracts the kinetic energy from the striker 16 .
  • a link 50 on a lateral surface 25, 31 of the striker 23 engage to convert the striker 16 in a rotational movement.
  • the exemplary gate 50 has a groove 51 extending spirally in the lateral surface 31.
  • the bearing 29 is provided with a rotor 52 , which engages in the groove 51 .
  • the rotor 52 is connected in the bearing 29 such that the rotor 52 relative to the bearing 29 along the working axis 10 and in the circumferential direction 41 is immovable.
  • the rotor 52 may be, for example, a ball that is enclosed in the bearing 29 .
  • the ball can rotate in the socket about its center.
  • the rotor 52 is located with a flank on an obliquely to the working axis 10 extending edge 53 of the groove 51 at.
  • the movement of the striker 23 along the working axis 10 forces a relative rotational movement of striker 16 and bearing 29.
  • the groove 51 may have a constant pitch 54 along the working axis 10 .
  • the length of the entire groove 51 corresponds to the free path of the striker 23 between the base 33 and the catcher 32, typically in the range between 20 mm and 50 mm.
  • the groove 51 is parallel to the working axis 10 at an end facing the racket 15 and the pitch 54 increases in the direction of impact 11.
  • the parallel section may be between 4 mm and 10 mm in length.
  • the slope 54 at the tool-side end of the groove 51 is between 30 degrees and 60 degrees.
  • the ball can equally be caught in the lateral surface 31 of the striker 23 and the groove 30 may be arranged in the inner surface of the sleeve.
  • a plurality of identical grooves 51 may be provided around the working axis 10 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP14159121.4A 2014-03-12 2014-03-12 Machine-outil portative de burinage Withdrawn EP2918376A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP14159121.4A EP2918376A1 (fr) 2014-03-12 2014-03-12 Machine-outil portative de burinage
EP15709154.7A EP3116688B1 (fr) 2014-03-12 2015-03-10 Machine-outil portative de burinage
CN201580006134.7A CN105939820B (zh) 2014-03-12 2015-03-10 凿削的手持式工具机
US15/125,060 US20170014983A1 (en) 2014-03-12 2015-03-10 Chiseling handheld power tool
PCT/EP2015/054919 WO2015135916A1 (fr) 2014-03-12 2015-03-10 Machine-outil portative de burinage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14159121.4A EP2918376A1 (fr) 2014-03-12 2014-03-12 Machine-outil portative de burinage

Publications (1)

Publication Number Publication Date
EP2918376A1 true EP2918376A1 (fr) 2015-09-16

Family

ID=50289393

Family Applications (2)

Application Number Title Priority Date Filing Date
EP14159121.4A Withdrawn EP2918376A1 (fr) 2014-03-12 2014-03-12 Machine-outil portative de burinage
EP15709154.7A Not-in-force EP3116688B1 (fr) 2014-03-12 2015-03-10 Machine-outil portative de burinage

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP15709154.7A Not-in-force EP3116688B1 (fr) 2014-03-12 2015-03-10 Machine-outil portative de burinage

Country Status (4)

Country Link
US (1) US20170014983A1 (fr)
EP (2) EP2918376A1 (fr)
CN (1) CN105939820B (fr)
WO (1) WO2015135916A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3670096A1 (fr) * 2018-12-21 2020-06-24 Hilti Aktiengesellschaft Machine-outil portative

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1796371A (en) * 1928-12-04 1931-03-17 Nordiska Armaturfab Ab Arrangement in striking tool
US2831462A (en) * 1951-03-30 1958-04-22 Atlas Copco Ab Hammer pistons and percussion apparatuses provided with such hammer pistons
US20020050191A1 (en) 2000-04-18 2002-05-02 Oliver Muhr Electric hand tool device with idle strike cutoff
US20040194987A1 (en) * 2001-03-07 2004-10-07 Andreas Hanke Hammer
US20120223491A1 (en) * 2011-03-02 2012-09-06 Hilti Aktiengesellschaft Chuck

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DE3304916A1 (de) * 1983-02-12 1984-08-16 Robert Bosch Gmbh, 7000 Stuttgart Bohrhammer
US4561507A (en) * 1984-03-06 1985-12-31 Liou Mou T Tool adapter
US4745980A (en) * 1985-03-30 1988-05-24 Chung Te Shun Auto-hammer driver
NO300702B1 (no) * 1996-02-19 1997-07-07 Bakke Oil Tools As Orienteringsanordning, særlig for boreverktöy eller brönnutstyr
DE19726383A1 (de) * 1997-06-21 1998-12-24 Bosch Gmbh Robert Elektrowerkzeugmaschine
US6467547B2 (en) * 2000-12-11 2002-10-22 Weatherford/Lamb, Inc. Hydraulic running tool with torque dampener
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US6745836B2 (en) * 2002-05-08 2004-06-08 Jeff L. Taylor Down hole motor assembly and associated method for providing radial energy
DE10261030A1 (de) * 2002-12-24 2004-07-08 Robert Bosch Gmbh Bohrhammer
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GB2423044A (en) * 2005-02-10 2006-08-16 Black & Decker Inc Hammer with cam-actuated driven member
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DE102010044011A1 (de) * 2010-11-16 2012-05-16 Hilti Aktiengesellschaft Handwerkzeugmaschine
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Publication number Priority date Publication date Assignee Title
US1796371A (en) * 1928-12-04 1931-03-17 Nordiska Armaturfab Ab Arrangement in striking tool
US2831462A (en) * 1951-03-30 1958-04-22 Atlas Copco Ab Hammer pistons and percussion apparatuses provided with such hammer pistons
US20020050191A1 (en) 2000-04-18 2002-05-02 Oliver Muhr Electric hand tool device with idle strike cutoff
US20040194987A1 (en) * 2001-03-07 2004-10-07 Andreas Hanke Hammer
US20120223491A1 (en) * 2011-03-02 2012-09-06 Hilti Aktiengesellschaft Chuck

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3670096A1 (fr) * 2018-12-21 2020-06-24 Hilti Aktiengesellschaft Machine-outil portative
WO2020126499A1 (fr) * 2018-12-21 2020-06-25 Hilti Aktiengesellschaft Machine-outil portative
CN113165153A (zh) * 2018-12-21 2021-07-23 喜利得股份公司 便携式动力工具
US11858104B2 (en) 2018-12-21 2024-01-02 Hilti Aktiengesellschaft Portable power tool
CN113165153B (zh) * 2018-12-21 2024-05-24 喜利得股份公司 便携式动力工具

Also Published As

Publication number Publication date
CN105939820B (zh) 2017-12-29
WO2015135916A1 (fr) 2015-09-17
EP3116688A1 (fr) 2017-01-18
US20170014983A1 (en) 2017-01-19
EP3116688B1 (fr) 2018-01-31
CN105939820A (zh) 2016-09-14

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