EP2669060A1 - Machine-outil de burinage - Google Patents

Machine-outil de burinage Download PDF

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Publication number
EP2669060A1
EP2669060A1 EP13168470.6A EP13168470A EP2669060A1 EP 2669060 A1 EP2669060 A1 EP 2669060A1 EP 13168470 A EP13168470 A EP 13168470A EP 2669060 A1 EP2669060 A1 EP 2669060A1
Authority
EP
European Patent Office
Prior art keywords
guide tube
tool according
hand tool
grooves
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.)
Granted
Application number
EP13168470.6A
Other languages
German (de)
English (en)
Other versions
EP2669060B1 (fr
Inventor
Orlaw Massler
Josef Fünfer
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 EP2669060A1 publication Critical patent/EP2669060A1/fr
Application granted granted Critical
Publication of EP2669060B1 publication Critical patent/EP2669060B1/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
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • 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
    • 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
    • B25D2250/065—Details regarding assembling of the tool
    • 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
    • B25D2250/185—Pressure equalising means between sealed chambers

Definitions

  • the present invention relates to a measuring element, e.g. an only pneumatic or rotary machine tool with a pneumatic impact mechanism.
  • a powered pneumatic percussion mechanism percussion piston in a guide tube is periodically accelerated by an air spring and impacts a tool or intermediate impactor at a point of impact.
  • the principle of the air spring requires an airtight guidance of the percussion piston in the guide tube. Due to the high mechanical load caused by the setbacks or the thermomechanical loads, the hammer mechanism should not heat up to over 100 degrees Celsius. Furthermore, the percussion piston must move smoothly in the guide tube in order not to suppress the relatively weak coupling of the motor drive via the air spring.
  • the hand tool of the invention has a pneumatic percussion.
  • the percussion includes a motor-driven exciter, a guide tube and a racket.
  • a formed inside the guide tube between the exciter and the bat air spring is circumferentially pressure sealed off from an inner surface of the guide tube.
  • the exciter and / or the club are formed as a piston guided by the inner surface.
  • exciters and clubs as a piston, the exciter as a piston and the racket rigidly connected to the guide tube cup-shaped, or the racket as a piston and the exciter can be rigidly connected to the guide tube.
  • An inner surface of the guide tube is provided with a plurality of molded-in recesses.
  • the inner surface is adapted in shape to the outer contour of the piston, so that it is clean and sealed pressure-tight. A slight deviation through depressions proves to be advantageous in terms of friction, without affecting the guide and in particular the pressure-tight closure essential for the concept of the pneumatic impact mechanism.
  • the depressions have a depth between 10 .mu.m and 100 .mu.m. Smaller depressions show no influence, it is assumed that the lubricating film compensates for these depressions. Larger depressions increased the abrasion of the sealing elements and thus reduced the life.
  • a dimension of the recess parallel to the working axis is preferably less than 200 ⁇ m.
  • the depressions have an area fraction between 1% and 10% of the inner surface.
  • An inner surface of the guide tube may be provided with a plurality of grooves running obliquely to the working axis and / or circular, square or diamond-shaped dents.
  • the grooves have a length at least an order of magnitude greater than width.
  • the dents are about the same length as they are wide.
  • An inner surface of the guide tube is provided with a plurality of grooves extending obliquely to the working axis.
  • the oblique grooves reduce the frictional force without, as initially feared, significantly worsening a seal of the pneumatic chamber for the air spring.
  • the efficiency of the hammer mechanism could be increased, i. the ratio of the impact energy delivered by the racket to the tool to the energy supplied by the motor via the exciter could be increased.
  • An embodiment provides that the grooves cross each other diamond-shaped.
  • One group of grooves has a different direction of rotation about the working axis than the grooves of another group.
  • An angle of inclination of the grooves with respect to the working axis is preferably in the range between 30 degrees and 50 degrees. This is especially true when the inclination of the grooves is constant over their entire length. In one embodiment, it is provided that the angle of inclination decreases along a direction of impact. The inclination angle is in the range of the impact point at 20 degrees to 40 degrees.
  • the grooves advantageously extend over at least the track swept by the racquet during the beating operation.
  • One embodiment provides that grooves of a group with a common direction of rotation run parallel to one another.
  • the guide tube is bent from a sheet metal strip.
  • Sheet metal strips are produced by rolling processes. This will make the surface typically very smooth and even.
  • An embossing or scribing of the grooves proves to be particularly advantageous for shaped sheet metal guide tubes.
  • the sheet metal strip may be connected at its two opposite edges by a continuous positive connection or a seam to form a pressure-tight tube. The pressure-tight fit is ensured by a toothing.
  • 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 4 , for example one of the drill bit, can be used.
  • a primary drive of the hammer drill 1 is a motor 5 , which drives a striking mechanism 6 and an output shaft 7 .
  • 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 bit 4 continuously about a working axis 10 and can beat the drill bit 4 in the direction of impact 11 along the working axis 10 in a substrate.
  • the striking mechanism 6 is, for example, a pneumatic impact mechanism 6 .
  • An exciter 12 and a racket 13 are movably guided in the striking mechanism 6 along the working axis 10 .
  • the exciter 12 is coupled via an eccentric 14 or a wobble finger to the motor 5 and forced to a periodic, linear movement.
  • An air spring formed by a pneumatic chamber 15 between exciter 12 and racket 13 couples a movement of the racket 13 to the movement of the exciter 12 at.
  • the racket 13 can strike directly on a rear end of the drill bit 4 or indirectly transfer part of its pulse to the drill bit 4 via a substantially resting intermediate racket 16 .
  • the striking mechanism 6 and preferably the further drive components are arranged within a machine housing 17 .
  • the exemplary exciter 12 is designed as a piston which is moved back and forth in a cylindrical guide tube 18 .
  • the racket 13 is also designed as a piston. Both the exciter 12 and the racket 13 close with their radial outer surfaces airtight with an inner surface 19 of the guide tube 18 from.
  • the racket 13 is provided with a sealing ring 20 , which typically proves necessary to achieve a pressure in the range between 10 bar and 20 bar due to remaining manufacturing tolerances.
  • the sealing ring 20 is preferably made of natural or synthetic rubber.
  • the exciter 12 may be rigidly connected to the guide tube 18 to form a pot-shaped exciter 12 in which the racket 13 is running.
  • the guide tube 18 may extend to a bearing block 21 for the intermediate beater 16 .
  • the guide tube 18 has a plurality of radial to the working axis 10 openings.
  • First of the openings 22 allow an adiabatic pressure equalization of the air spring in a warming device.
  • Second of the openings 23 aerate the pneumatic chamber 15 and deactivate the air spring as soon as the striking mechanism 6 beats empty.
  • the friction losses of the exciter 12 on the inner surface 19 of the guide tube 18 should be as minimal as possible.
  • a first reduction in friction is achieved by a lubricating film.
  • a structured inner surface 19 additionally proves to be advantageous over a smooth inner surface 19 .
  • the inner surface 19 is provided with obliquely to the working axis 10 extending grooves 24 .
  • Fig. 3 shows the unrolled inner surface 19 of the guide tube 18th
  • the grooves 24 have a depth 25 of more than 10 microns (microns) and a depth 25 of less than 100 microns.
  • a width 26 of the grooves 24 is in the region of the depth 25th
  • the grooves 24 are about one to five times as wide as they are deep.
  • the depth 25 is the dimension of the groove 24 in the radial direction, the width 26 the smallest dimension of the groove 24 on the inner surface 19 and the length is the largest dimension on the inner surface 19th
  • the grooves 24 may extend over the entire length 27 of the guide tube 18 .
  • the grooves 24 extend helically along the inner surface 19th An inclination of the grooves 24 with respect to the working axis 10 preferably remains constant over its length.
  • a first group 28 of the grooves 24 extends in a positive direction of rotation and a second group 29 of the grooves 24 extends in a negative direction of rotation.
  • the grooves 24 of the two groups 28 , 29 intersect alternately.
  • Adjacent grooves 24 , a group 28 , 29 are arranged offset to one another at a distance between 5 000 .mu.m to 20 000 .mu.m along the working axis 10 .
  • the inner surface 19 between the adjacent grooves 24 is preferably smooth. Smooth means that a roughness of the inner surface 19 between the grooves 24 is at least an order of magnitude smaller than the depth 25 of the grooves 24th
  • An amount of the inclination angle 30 of the grooves 24 with respect to the working axis 10 is in the range between 30 degrees and 50 degrees.
  • the relationship of the inclination in the interplay with the racket 13 , the sealing ring 20 , the lubricating film and the periodically changing temperature and pressure conditions is not fully understood. Tilt angles 30 out of range, both smaller and larger, however, result in greater losses of impact mechanism 6 .
  • the inclination angle 30 of the helical grooves 24 is the difference of the angle of 90 degrees.
  • the guide tube 18 is made of a bent sheet metal strip 31 , which is closed by a seam and / or a toothed closure along the working axis 10 ( Figure 3 ).
  • the opposite edges 32 of the sheet-metal strip 31 may be provided with a toothing, which engage in the bent to the guide tube 18 sheet metal strip 31 .
  • the toothing 33 may additionally be hermetically sealed by a weld. Alternatively, the teeth may be hermetically sealed with a plastic.
  • the grooves 24 are preferably rolled in the sheet metal strip 31 or introduced by another non-cutting method.
  • the inner surface 19 thus remains free of burrs.
  • the guide tube 18 longer than the track 34 of the racket 13 during operation.
  • the racket 13 periodically moves between a beating point and a rear turning point.
  • the impact point is defined by the intermediate beater 16 and its end facing the racket 13 .
  • the rear reversal point results from the air spring 15 , which decelerates the racket 13 to a stop and then accelerates in the direction of the impact point.
  • the rear reversal point is approximately at the level at which the exciter 12 has covered halfway between its two turning points.
  • a first vent 22 for adiabatic pressure equalization is preferably stamped in the sheet metal strip 31 . Further, preferably second ventilation opening 23 are punched for stopping the striking mechanism 6 in the sheet metal strip 31 .
  • the punching device is on the inner surface 19th
  • the ventilation openings 22 , 23 are outside the path 34 .
  • the second ventilation openings 23 preferably directly adjoin the track 34 .
  • the grooves 24 end in the vicinity of the second ventilation openings 23 , that is, on a section of the guide tube 18 adjoining the track 34 in the direction of impact 11 . Increased friction may favor stopping of the racket 13 when the racket 13 slides past the point of impact, for example, in the event of a blank strike.
  • a further embodiment provides for a variation of the angle of inclination 30 along the working axis 10 .
  • the inclination angle 30 relative to the working axis 10 increases in the direction of impact 11 .
  • the guide tube 18 must be tight against the high air pressure in the pneumatic chamber 15 .
  • vertical grooves 24 are preferred.
  • this orientation of the grooves 24 probably create a greater frictional resistance than parallel to the working axis 10 grooves 24th
  • the inclination angle 30 is in the range of the rear reversal point between 40 degrees and 60 degrees and decreases towards the impact point between 20 degrees and 30 degrees.
  • An embodiment may have different depth grooves 24 .
  • every fifth to tenth groove 24 may have a depth 25 to five times as great as the others.
  • the few and deeper grooves 24 with, for example, a depth 25 between 50 microns and 100 microns can pick up dust grains that pass through the seals and the intermediate beater 16 .
  • the number of deep grooves 24 is kept small in order to ensure a sufficiently pressure-tight closure of the racket 13 on the inner surface 19 .
  • the dents 35 have a depth 25 between 10 microns and 100 microns.
  • a diameter 36 of the dents 35 is approximately in the region of its depth 25th
  • the dents 35 are preferably arranged regularly, for example on nodes of a grid with rectangular or diamond-shaped cells.
  • the entire surface of the dimples 35 is significantly smaller than the inner surface 19 , for example less than 10%.
  • the remaining inner surface 19 is preferably smooth, ie has a roughness of significantly less than 10 microns.
  • the racket 13 touches the remaining smooth inner surface 19th
  • the dents 35 can be embossed, for example, with a stamp in the inner surface 19 .
  • the Aufsch embossing can be leveled by a subsequent rolling or stamping.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Surgical Instruments (AREA)
EP13168470.6A 2012-05-29 2013-05-21 Machine-outil à main de burinage Active EP2669060B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012208986A DE102012208986A1 (de) 2012-05-29 2012-05-29 Meißelnde Werkzeugmaschine

Publications (2)

Publication Number Publication Date
EP2669060A1 true EP2669060A1 (fr) 2013-12-04
EP2669060B1 EP2669060B1 (fr) 2017-02-22

Family

ID=48444231

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13168470.6A Active EP2669060B1 (fr) 2012-05-29 2013-05-21 Machine-outil à main de burinage

Country Status (4)

Country Link
US (1) US9527199B2 (fr)
EP (1) EP2669060B1 (fr)
CN (1) CN103447580B (fr)
DE (1) DE102012208986A1 (fr)

Cited By (1)

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EP3281747A1 (fr) * 2016-08-09 2018-02-14 HILTI Aktiengesellschaft Machine-outil portative

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DE102011007660A1 (de) * 2011-04-19 2012-10-25 Hilti Aktiengesellschaft Handwerkzeugmaschine und Herstellungsverfahren
WO2013178246A1 (fr) * 2012-05-29 2013-12-05 Hilti Aktiengesellschaft Appareil de pose actionné par combustion interne
EP2842696B1 (fr) * 2013-08-30 2016-06-01 HILTI Aktiengesellschaft Outil électrique
EP2857150A1 (fr) * 2013-10-03 2015-04-08 HILTI Aktiengesellschaft Machine-outil manuelle
GB201321894D0 (en) * 2013-12-11 2014-01-22 Black & Decker Inc Hammer drive mechanism
US20150343616A1 (en) * 2014-06-03 2015-12-03 Soartec Industrial Corp. Hammering set for an impact tool
JP6325360B2 (ja) * 2014-06-12 2018-05-16 株式会社マキタ 打撃工具
CN106903804B (zh) * 2017-03-23 2018-12-04 灵武市伟畅机械科技有限公司 一种用于建筑装潢的钻孔装置
CN106903805B (zh) * 2017-03-23 2018-12-04 宁夏百畅万通矿山机械有限公司 一种装修用打孔器
WO2020056654A1 (fr) * 2018-09-20 2020-03-26 博世电动工具（中国）有限公司 Machine-outil à percussion
US11945087B2 (en) 2019-03-29 2024-04-02 Tien-I Industrial Co., Ltd. Impact tool head
US11498198B2 (en) * 2019-08-20 2022-11-15 The Boeing Company Ergonomic handle for a power tool
DE102020209356A1 (de) 2020-07-24 2022-01-27 Robert Bosch Gesellschaft mit beschränkter Haftung Schlagwerkvorrichtung für eine Handwerkzeugmaschine
JP2022134644A (ja) * 2021-03-03 2022-09-15 株式会社マキタ 回転打撃工具

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FR1485579A (fr) * 1966-03-14 1967-06-23 Rockwell Mfg Co Outil à main d'impacts rotatifs notamment un marteau perforateur
DE19929183A1 (de) * 1999-06-25 2001-01-04 Wacker Werke Kg Luftfederschlagwerk mit hohlem Schlagkolben
EP1674205A1 (fr) * 2004-12-23 2006-06-28 BLACK & DECKER INC. Mécanisme d'entraînement pour outil motorisé
EP2514569A1 (fr) * 2011-04-19 2012-10-24 HILTI Aktiengesellschaft Machine-outil manuelle et procédé de fabrication

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3281747A1 (fr) * 2016-08-09 2018-02-14 HILTI Aktiengesellschaft Machine-outil portative
WO2018029025A1 (fr) * 2016-08-09 2018-02-15 Hilti Aktiengesellschaft Machine-outil portative
US11123853B2 (en) 2016-08-09 2021-09-21 Hilti Aktiengesellschaft Hand-held power tool

Also Published As

Publication number Publication date
CN103447580B (zh) 2017-04-12
CN103447580A (zh) 2013-12-18
US20130319712A1 (en) 2013-12-05
DE102012208986A1 (de) 2013-12-05
US9527199B2 (en) 2016-12-27
EP2669060B1 (fr) 2017-02-22

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