EP2444204A1 - Werkzeugmaschine - Google Patents

Werkzeugmaschine Download PDF

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Publication number
EP2444204A1
EP2444204A1 EP11182099A EP11182099A EP2444204A1 EP 2444204 A1 EP2444204 A1 EP 2444204A1 EP 11182099 A EP11182099 A EP 11182099A EP 11182099 A EP11182099 A EP 11182099A EP 2444204 A1 EP2444204 A1 EP 2444204A1
Authority
EP
European Patent Office
Prior art keywords
gear
machine tool
driven gear
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Withdrawn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
EP11182099A
Other languages
German (de)
English (en)
French (fr)
Inventor
Ferdinand Kristen
Christoph Dieing
Rainer Ontl
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 EP2444204A1 publication Critical patent/EP2444204A1/de
Withdrawn legal-status Critical Current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
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/06—Composite materials
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/21—Metals
    • B25D2222/33—Copper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/21—Metals
    • B25D2222/42—Steel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/54—Plastics

Definitions

  • the present invention relates to a machine tool, in particular a hand-held lathe machine tool.
  • a pneumatic impactor and a rotary drive are typically driven by a common electric motor.
  • One of the electric motor periodically axially moving exciter piston drives a percussion piston via an air spring.
  • the strokes exerted by the percussion piston are transferred directly or indirectly to a drill bit.
  • the rotary drive is connected to the electric motor via a linkage and a transmission.
  • the power transmission to the drill bit is typically in a tool holder with locking elements which engage corresponding grooves on the drill bit.
  • the axial impacts of the drill bit are transmitted to the electric motor by the mechanical coupling of the rotational drive.
  • the bearings of the electric motor and the gearbox must be designed for the extra-axial loads.
  • a machine tool has a pneumatic striking mechanism which has a beater striking along a working axis.
  • a motor serves as a drive.
  • a transmission has a driving gear and a driven gear, wherein the driving gear meshes with the driven gear and at least the axis of rotation of the driven gear is inclined to the working axis.
  • the driving gear is made of metal and the driven gear is made of a carbon fiber reinforced plastic.
  • the power flow in the transmission is described starting from the engine.
  • the driving gear is in the power path closer to the engine than driven gear.
  • a combination of two intermeshing plastic gears fails under continuous load, even though they are reinforced with glass fibers.
  • the high torques to be transmitted can not be compensated by wider teeth.
  • a combination of a glass fiber reinforced plastic gear and a steel gear does not give satisfactory results either. Surprisingly, this tires the steel gear. Only the change to the use of carbon fibers for a gear and metal for the other gear results in a sufficiently resilient combination.
  • the gears should be manufactured with a high accuracy, ie small tolerance. Deviations in the dimensions of the teeth lead to higher wear and friction losses. Therefore, initially thermosets appear due to customary low manufacturing tolerances suitable. Under continuous load surprised a gear made of polyamide, a thermoplastic, despite larger tolerances with a higher stability.
  • An embodiment provides that the machine tool has a rotational drive for rotating a tool about the working axis and the driven gear of the carbon fiber reinforced plastic is coupled in a power flow path between the motor and the rotational drive.
  • the carbon fibers are aligned along a radial direction of the gear. This results in particularly good damping properties.
  • the carbon fibers may be radially or spirally aligned with the axis of rotation of the gear.
  • an outer diameter of the driven gear is at least three times larger than a diameter of a shaft on which the driven gear is mounted.
  • the shaft is preferably made of steel. In order for significant damping to be achieved, it turns out that the gear should be significantly larger than the steel core formed by the shaft.
  • the axis of rotation of the driven gear is preferably inclined between 70 degrees and 110 degrees to the working axis.
  • Fig. 1 1 schematically shows a hammer drill 1 with a drill bit 2 inserted .
  • a pneumatic impact mechanism 3 strikes the drill bit 2 along a direction of impact 4.
  • a rotary drive 5 continually rotates the drill bit 2 about its working axis 6. With the combined beating and rotating movement, the drill bit 2 chisels circular holes in mineral materials.
  • the hammer drill 1 is driven by an electric motor 7 , which drives both the pneumatic impact mechanism 3 and the rotary drive 5 .
  • a power supply of the electric motor 7 can be network-based or via batteries.
  • the powerful electric motor 7 is angled with its shaft 8 , for example, perpendicular to the pneumatic impact mechanism 3 and the working axis 6 .
  • a rotation axis 9 of the electric motor 7 and the working axis 6 are arranged correspondingly inclined to each other.
  • the electric motor 7 is, for example, an electrically commutated motor, for example a reluctance motor.
  • the pneumatic percussion mechanism 3 shown by way of example includes a guide tube 10, in which an excitation piston 11 and a percussion piston 12 are slidably mounted.
  • the excitation piston 11 and the percussion piston 12 include a pneumatic chamber 13 between them.
  • the excitation piston 11 is coupled via an eccentric 14 to the electric motor 7 , whereby the exciter piston 11 to a periodic movement along a Working axis 6 of the guide tube 10 is forced.
  • the percussion piston 12 follows the movement of the excitation piston 11 excited by the periodically compressed and decompressed pneumatic chamber 13, which acts as an air spring.
  • the percussion piston 12 abuts in the direction of impact 4 on an intermediate racket 15, which transfers the impact to the applied to the intermediate racket 15 drill bit 2 .
  • a gear 17 couples the output gear 16 with the rotary drive 5.
  • the illustrated gear 17 has a gear shaft 18 which is arranged parallel to the shaft 8 of the electric motor 7 .
  • a first gear 19 on the gear shaft 18 meshes with the output gear 16 of the electric motor 7.
  • a second gear 20 is arranged, which meshes with a ring gear 21 , for example.
  • the ring gear 21 is rotatably connected to the guide tube 10 which is rotated by the electric motor 7 and the gear 17 about the working axis 6 .
  • the second gear 20 and the ring gear 21 may be formed, for example, as bevel gears.
  • the rotational drive 5 is coupled, for example in the tool holder 22 to the rotating guide tube 10 .
  • the rotational drive 5 has, for example, a hollow sleeve into which the drill bit 2 can be inserted. In the cavity of the sleeve projecting elements, such as pins 23 engage in grooves of the drill bit 2 a.
  • the gear 17 can be coupled via a gear rod to the rotational drive 5 in the tool holder 22 .
  • the output pinion 16 of the motor 7 is made of steel and meshing with the output gear 16 end- shaped, first gear 19 made of carbon fiber-containing thermoplastic.
  • the axis of rotation 24 of the first gear 19 is perpendicular to the working axis 6.
  • the output pinion 16 of the electric motor 7 is preferably made of metal, in addition to steel are particularly copper-containing alloys, eg with a copper content of more than 50% suitable.
  • the second gear 20 on the shaft 18 may preferably be made of steel.
  • a branch of the transmission 17 for coupling the eccentric 14 to the motor 7 is preferably made entirely of steel gears. These are permanently the high repercussions starting from the hammer mechanism 3 grown.
  • the meshing with the output gear 16 of the motor 7 gear 25 may be made of carbon fiber-containing thermoplastic.
  • the shaft of the eccentric 14 is guided by one or more bearings 26 , which receive a large proportion of the radial shocks. The forwarded to the output gear 16 shocks can be sufficiently damped, so that the gear 25 made of plastic is able to cope with the forces occurring.
  • FIGS. 2, 3 and 4 show an exemplary construction of a damping gear 30 made of carbon fiber reinforced thermoplastic in plan view, cross-section and side view.
  • the damping gear 30 can be used for example as a first gear 19 .
  • the gear 30 has a disc-shaped base body 31 made of a carbon fiber reinforced thermoplastic.
  • the thermoplastic is preferably selected from the class of polyamides. With other fibers, such as glass fibers, no desired properties could be obtained.
  • the teeth 32 are formed in the periphery of the body teeth 32 .
  • the teeth 32 may be inclined relative to the axis of rotation 23 by an inclination angle 40 between 5 degrees and 25 degrees, for example 17 degrees.
  • the output gear 16 is formed with a same inclination angle for a more even transmission of the meshing teeth.
  • the damping gear 30 has a continuous hub opening 33 in the middle, which has a plurality of radially extending grooves 34 for improved torque transmission from a circular shape.
  • the preferably steel gear shaft 18 is pressed into the hub opening 33. Wings on the transmission shaft 18 engage in the grooves 34 a.
  • the structure of the disk-shaped main body 31 is designed with regard to a decoupling effect in the direction of impact 4 .
  • the carbon fibers preferably extend only in the radial direction, ie from the hub opening 33 straight to the periphery with the teeth 32, as in Fig. 2 indicated by individual carbon fibers 35 .
  • To the radially extending carbon fibers 35 are no transverse, for example, about the rotation axis 23 encircling, carbon fibers 35 are arranged.
  • the lack of networking proves to be surprisingly advantageous to attenuate the introduced via the transmission shaft 18 of the pneumatic percussion 3 radial shocks particularly efficient.
  • one Carbon fiber along its orientation is able to transmit the largest forces, the structure for a transfer of the beats seems to be advantageously inefficient.
  • the shock wave it is believed, can leak out in the matrix of thermoplastic.
  • the geometry of the main body 31 also shows ways to decouple the output pinion 16 from the beats.
  • the damping gear 30 preferably has a diameter 36 which is at least three times as large as an inner diameter 37 of the hub opening 33 and the transmission shaft 18 .
  • the diameter 36 is defined as the tip circle diameter, ie, a diameter of a circle circumscribing the damping gear 30 .
  • the disk-shaped base body 31 preferably has a thickness 38, perpendicular to the axis 23, which is between 4% and 8% of the diameter 36 .
  • the disc-shaped main body 31 in this case shows sufficient softness along the axis 23, which allows excitation by the shock waves of the beats. The radially introduced impacts can thus extend partially in the axial direction. Although the meshing gears are slightly shifted from one another, this proves to be more favorable than radial impacts on the shaft 8 of the motor 7.
  • the number of teeth 32 along the circumference of the first gear 30 is advantageously limited.
  • a ratio of the diameter 36 of the first gear 30 to its number of teeth 32 is in the range of 1.0 cm / per tooth to 1.25 cm / per tooth.
  • the teeth 32 have a relatively large base area 39 , whereby the blows are distributed over a larger segment of the main body 31 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Gears, Cams (AREA)
EP11182099A 2010-10-22 2011-09-21 Werkzeugmaschine Withdrawn EP2444204A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010042809A DE102010042809A1 (de) 2010-10-22 2010-10-22 Werkzeugmaschine

Publications (1)

Publication Number Publication Date
EP2444204A1 true EP2444204A1 (de) 2012-04-25

Family

ID=44651471

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11182099A Withdrawn EP2444204A1 (de) 2010-10-22 2011-09-21 Werkzeugmaschine

Country Status (4)

Country Link
US (1) US20120097409A1 (zh)
EP (1) EP2444204A1 (zh)
CN (1) CN102451928A (zh)
DE (1) DE102010042809A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3756802A1 (de) * 2019-06-26 2020-12-30 Hilti Aktiengesellschaft Verbundzahnrad für einen elektropneumatischen bohrhammer

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2910336A1 (de) * 2014-02-21 2015-08-26 HILTI Aktiengesellschaft Handwerkzeugmaschine
CN105291672B (zh) * 2015-12-02 2017-10-31 上海电机学院 锡杯撞花机
CN107336198B (zh) * 2017-07-24 2021-01-12 苏州艾乐蒙特机电科技有限公司 一种变行程的冲击电锤
EP3632624A1 (de) * 2018-10-04 2020-04-08 Hilti Aktiengesellschaft Exzenterantrieb für eine handwerkzeugmaschine
CN112296947A (zh) * 2020-02-27 2021-02-02 杨新军 一种滑块撞击式冲击电钻

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19532722A1 (de) * 1995-09-05 1997-03-06 Danfoss As Getriebe für eine hydraulische Kolbenmaschine
EP1391637A2 (de) * 2002-08-23 2004-02-25 IMS Gear GmbH Zahnradanordnung
GB2392966A (en) * 2002-09-13 2004-03-17 Black & Decker Inc Power tool with overload clutch and an arrangement for detecting tool bit blocking

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3556778A (en) * 1968-10-14 1971-01-19 American Potash & Chem Corp Ternary damping alloy
JPS543643A (en) * 1977-06-10 1979-01-11 Tsugio Kobayashi Gear comosed of carbon fiber
JPS5850356A (ja) * 1981-09-16 1983-03-24 Sumitomo Electric Ind Ltd 複合歯車
US4413860A (en) * 1981-10-26 1983-11-08 Great Lakes Carbon Corporation Composite disc
JPH04312256A (ja) * 1991-04-12 1992-11-04 Asahi Chem Ind Co Ltd 長繊維強化熱可塑性樹脂よりなる歯車及びカム
US5596905A (en) * 1994-01-21 1997-01-28 Asahi Kogaku Kogyo Kabushiki Kaisha Oscillation damping gear
DE29715257U1 (de) * 1997-08-26 1997-12-04 Atlas Copco Electric Tools Mitnahmevorrichtung
JP2001304379A (ja) * 2000-04-20 2001-10-31 Unisia Jecs Corp 合成樹脂製歯車及びその製造方法
JP2007222998A (ja) * 2006-02-24 2007-09-06 Kyocera Chemical Corp ラッピングキャリア及びその製造方法
DE102006035417B4 (de) * 2006-11-09 2016-12-01 Hilti Aktiengesellschaft Handwerkzeugmaschine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19532722A1 (de) * 1995-09-05 1997-03-06 Danfoss As Getriebe für eine hydraulische Kolbenmaschine
EP1391637A2 (de) * 2002-08-23 2004-02-25 IMS Gear GmbH Zahnradanordnung
GB2392966A (en) * 2002-09-13 2004-03-17 Black & Decker Inc Power tool with overload clutch and an arrangement for detecting tool bit blocking

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3756802A1 (de) * 2019-06-26 2020-12-30 Hilti Aktiengesellschaft Verbundzahnrad für einen elektropneumatischen bohrhammer
WO2020260081A1 (de) * 2019-06-26 2020-12-30 Hilti Aktiengesellschaft Verbundzahnrad für einen elektropneumatischen bohrhammer

Also Published As

Publication number Publication date
US20120097409A1 (en) 2012-04-26
DE102010042809A1 (de) 2012-04-26
CN102451928A (zh) 2012-05-16

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