EP2089192B1 - Massenschwingungseinheit für handwerkzeugmaschinen mit einer schlagwerkvorrichtung - Google Patents

Massenschwingungseinheit für handwerkzeugmaschinen mit einer schlagwerkvorrichtung Download PDF

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Publication number
EP2089192B1
EP2089192B1 EP07803568A EP07803568A EP2089192B1 EP 2089192 B1 EP2089192 B1 EP 2089192B1 EP 07803568 A EP07803568 A EP 07803568A EP 07803568 A EP07803568 A EP 07803568A EP 2089192 B1 EP2089192 B1 EP 2089192B1
Authority
EP
European Patent Office
Prior art keywords
unit
mass
counterweight
power tool
counter
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.)
Not-in-force
Application number
EP07803568A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2089192A1 (de
Inventor
Joachim Hecht
Klaus Kuespert
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2089192A1 publication Critical patent/EP2089192A1/de
Application granted granted Critical
Publication of EP2089192B1 publication Critical patent/EP2089192B1/de
Not-in-force 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
    • B25D17/24—Damping the reaction force
    • 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
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of 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
    • B25D2216/0069—Locking means
    • 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
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0084—Arrangements for damping of the reaction force by use of counterweights being fluid-driven
    • 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
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven
    • 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
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted
    • 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
    • B25D2250/231—Sleeve details

Definitions

  • the invention relates to a handheld power tool impact device according to the preamble of claim 1.
  • a handheld power tool percussion device with a striking mechanism arrangement with at least one unit which is intended to generate a counterforce to a force resulting from the percussion mechanism, the unit being formed by a mass vibration unit is, wherein the mass vibration unit comprises a counterweight mass for striking mechanism arrangement, wherein the unit has a locking unit which is provided for securing the counterweight in an idle position, wherein the locking unit has at least one locking element and a fixing element and wherein for securing the counterweight in the axial direction of the Arresting element in a locking recess, which is arranged within the counter-vibration mass, is movable, wherein the fixing element is arranged movable within the locking element.
  • an advantageous reduction of vibrations on a housing of a hand tool machine with a hand tool machine impact device, which are caused by the generation of a shock pulse of the impact mechanism, can be achieved.
  • the generated counterforce and the force resulting from the hammer mechanism are preferably aligned in opposite directions, so that an advantageous and at least partial cancellation of the forces can be achieved in a vibration reduction and thus particularly advantageous a virtually vibration-free guidance for an operator of the power tool can be achieved.
  • the unit is intended to generate the counterforce within a large speed range of a drive unit or a high impact frequency range of Schlagwerkan instructive so that the counterforce generated in the direction and time can be advantageously matched to a compression force of Schlagtechnikan für a maximum vibration reduction can be achieved
  • the unit may be designed as a mechanical, an electrical and / or a magnetic and / or a pneumatic unit and / or as further, the expert appears reasonable unit and thereby a mechanical, electrical and / or magnetic, etc. counterforce to generate resultant force of the percussion arrangement.
  • the unit is formed by a mass vibration unit, which structurally simple means of a mechanical excitation, especially if the unit formed by the mass vibration unit has a counterweight, a counterforce generated by a counter-vibration to the compression force of the hammer mechanism can be achieved.
  • the unit has at least one spring means which supports the counterweight mass, whereby, after an excitation of the counterweight mass, an advantageous return of the counterweight mass to the rest position or starting position can be achieved and thus a renewed and in particular periodic excitation of the counterweight mass can be achieved.
  • the spring means supports the mating mass on a housing of the power tool.
  • the unit has at least one excitation means which can be driven by means of a drive means of the hammer mechanism, whereby a structurally simple adaptation or coupling of the generated counter-vibration or the generated counterforce to a rotational speed of the drive unit or to a beat frequency of the striking mechanism arrangement can be achieved.
  • the excitation means can be formed by an electrical, a magnetic and / or a mechanical excitation means and / or further excitation means which appear expedient to the person skilled in the art.
  • the countervibration mass can be excited by means of the excitation means counter to a drive direction of the striking mechanism arrangement, whereby an advantageous cancellation of the counterforce and the resulting force of the striking mechanism arrangement can be achieved.
  • the excitation means is formed by an eccentric wheel, so that in particular a periodic excitation of the countervibration mass is achieved can, wherein the eccentric wheel is preferably coupled to a beat frequency of the striking mechanism arrangement or a rotational speed of the drive unit.
  • the unit has a locking unit which is provided for securing the counterweight mass in an idling position.
  • a locking unit which is provided for securing the counterweight mass in an idling position.
  • a handheld power tool with a handheld power tool striking device is proposed, and thus an advantageous ease of operation with a low and / or particularly advantageous with a virtually vanishing resulting vibration of the power tool housing for an operator of the power tool is achieved.
  • FIG. 1 is a handheld power tool 36a shown with a handheld power tool impactor device 10a.
  • the handheld power tool impact device 10a ( FIG. 2 ) comprises a striking mechanism assembly 12a and a unit 14a formed by a mass vibration unit.
  • the percussion arrangement 12a is for generating a impact impulse for a tool 40a, which is located in a tool holder 42a of the handheld power tool 36a ( FIG. 1 ), and for this purpose has a piston 44a, a pneumatic element 46a, a racket 48a and a firing pin, not shown.
  • the percussion arrangement 12a comprises a hammer tube 32a, in which the piston 44a and the racket 48a along a drive direction 26a of the striking mechanism arrangement 12a are mounted axially movable. Between the piston 44a and the beater 48a, the pneumatic element 46a formed by an air cushion is arranged ( FIG. 2 ).
  • a drive torque is generated by a drive unit of the handheld power tool 36a (not shown here in detail and formed by an electric motor).
  • the drive unit transmits a drive torque to a drive means 38a formed by a drive shaft, which is oriented perpendicular to the drive direction 26a of the striking mechanism arrangement 12a ( FIG. 2 ).
  • a drive shaft which is oriented perpendicular to the drive direction 26a of the striking mechanism arrangement 12a ( FIG. 2 ).
  • this has an eccentric drive unit 52a with a non-rotatably connected to the drive shaft eccentric 54a and a bolt-shaped eccentric pin 56a.
  • the eccentric pin 56a is aligned perpendicular to a main extension surface 58a of the eccentric wheel 54a and perpendicular to the drive direction 26a of the hammer mechanism 12a and arranged in a region of the eccentric wheel 54a, which is arranged outside a drive shaft 60a of the eccentric wheel 54a formed by a rotation axis.
  • the eccentric pin 56a is connected to the piston 44a via a drive rod 62a of the striking mechanism assembly 12a.
  • the mass vibration unit is disposed in a portion of the portable power tool 36a, that of the drive shaft From the perspective, the drive direction 26a of the hammer mechanism 12a is opposite.
  • the mass vibration unit has a counterweight 20a, a spring means 22a and an excitation means 24a formed by an eccentric wheel 28a.
  • the eccentric 28a is driven via the drive shaft of the drive unit, which is provided for driving the hammer mechanism assembly 12a, and is rotationally connected thereto.
  • the eccentric wheel 28a has a cam-shaped, asymmetrical shape of a main extension surface 64a, which, relative to a circular shape, in a center has a recess 66a for rotationally fixed attachment to the drive shaft ( FIG. 3 ).
  • the eccentric 28a and a drive cam 68a of the mass vibration unit and the eccentric 54a and the eccentric pin 56a of the striking mechanism 12a run in the direction of rotation 72a with a phase shift of 180 ° about the drive shaft, so that the drive cam 68a of the eccentric 28a of the mass vibration unit in one of Drive direction 26a opposite end position is when the eccentric pin 56a of the eccentric 54a of the percussion mechanism assembly 12a is in an in the drive direction 26a facing end position ( FIG. 2 ).
  • the counterweight 20a is moved counter to a drive direction 26a of the hammer mechanism 12a.
  • the counterweight 20a is moved counter to a spring force of a spring means 22a, wherein the spring means 22a, the counterweight 20a is supported on a housing 70a of the power tool 36a.
  • a maximum of a compression force acts formed force 18a of the percussion mechanism 12a against the drive direction 26a of the striking mechanism assembly 12a.
  • a counterforce 16a is generated which reaches a maximum, due to the arrangement of the mass vibration unit, almost simultaneously to the maximum resultant force 18a of the impact mechanism 12a.
  • the opposing force 16a of the mass vibration unit is in the opposite direction to the resultant force 18a of the percussion mechanism 12a, so that the resultant force 18a of the percussion mechanism 12a and the counterforce 16a in the area of the drive shaft cancel as far as possible and resulting oscillations of the handheld power tool 36a are at least reduced and / or avoided ( FIG. 2 ).
  • the spring means 22a of the mass vibration unit causes an automatic return of the counterweight 20a in the initial situation, the counterweight 20a after a periodic rotation about the axis of rotation of the drive shaft of the cam-shaped eccentric 28a again against the spring force of the spring means 22a and against the drive direction 26a of the striking mechanism 12a move.
  • the counterforce 16a of the mass vibration unit is adapted to a momentary impact frequency of the striking mechanism arrangement 12a or to a direction and time of the force 18a resulting from the impact mechanism arrangement 12a.
  • the spring means 22a causes an increased inertia when accelerating the counterweight 20a and the counterforce 16a thus acts over a longer period against the resulting force 18a of the impact mechanism assembly 12a.
  • FIGS. 4 to 12 Alternative examples or embodiments of the invention are shown. Substantially identical components, features and functions are basically numbered by the same reference numerals. To distinguish the examples, however, the reference numerals of the embodiments, the letters a to f are added. The following description is essentially limited to the differences from the example in FIGS FIGS. 1 to 3 , wherein with respect to the same components, features and functions on the description of the example in the FIGS. 1 to 3 can be referenced.
  • FIGS. 4 to 6 show an alternative portable power tool impactor apparatus 10b.
  • An eccentric 28b for exciting a counterweight 20b is also provided for driving a striking mechanism 12b.
  • the eccentric wheel 28b has two eccentric pins 56b, 74b which are arranged on mutually opposite edge regions 76b, 78b of the eccentric wheel 28b.
  • the eccentric pin 74b extends for excitation of the counterweight 20b on a side facing away from the eccentric pin 56b to drive the striking mechanism 12b side of the eccentric 28b perpendicular to a main extension surface 64b of the eccentric 28b.
  • another spring means 80b is arranged on a side facing in a drive direction 26b side.
  • the spring means 80b allows a muted coupling of the eccentric pin 74b to the counterweight mass 20b, wherein the eccentric pin 74b has a direction of movement in a direction of rotation 72b of the eccentric 28b and a drive shaft.
  • the eccentric pin 74b coupled to a Timing to the spring element 80b, in which a compression force is built up in the hammer mechanism assembly 12b.
  • a compression force or a resultant force 18b increases against the drive direction 26b in the striking mechanism arrangement 12b and at the same time the countervailing mass 20b is pressed counter to the drive direction 26b and thus a counterforce 16b is generated by an acceleration of the countervailing mass 20b.
  • a maximum force 18b results from the striking mechanism arrangement 12b against the drive direction 26b and from the mass vibration unit results in a maximum counterforce 16b in the direction of the drive direction 26b, wherein the force 18b and the counterforce 16b cancel each other at least partially.
  • the mass vibration unit on a stop means 82b which is arranged in the drive direction 26b of the striking mechanism assembly 12b after the other spring means 80b.
  • the stop means 82b prevents excessive back movement of the counterweight 20b by means of a spring means 22b and positions the counterweight 20b in a starting position for a renewed excitation by means of the eccentric wheel 28b.
  • the stop means 82b is additionally coupled to the counterweight 20b with a spring element 84b, to prevent undesirable abutment of the spring means 80b and / or the countermass 20b on the stop means 82b.
  • the counterweight 20b is positioned by means of the spring means 22b for support on the housing 70b of the power tool and the spring element 84b in a starting position for a new excitation.
  • a handheld power tool impactor device 10c is shown with a locking unit 34c which is provided for securing a counterweight mass 20c in an idling position.
  • the locking unit 34c has a spring element 86c, a locking element 88c, a fixing element 90c and a retaining ring 92c arranged on a hammer tube 32c.
  • the spring element 86c supports the locking element 88c on a housing 70c of a hand-held power tool and is arranged in a chiseling operation in a prestressed position.
  • the fixing element 90c is fixedly connected to the retaining ring 92c with an end 94c pointing in a drive direction 26c and movably arranged with the other end 96c within the locking element 88c.
  • the locking element 88c has a recess 98c, which tapers in a direction which extends counter to the drive direction 26c, in which the fixing element 90c is arranged to be axially movable.
  • the spring element 86c causes a displacement of the fixing element 90c in the drive direction 26c or a displacement of the tapered recess 98c Moving the locking member 88c upward or a movement of the locking member 88c, which is directed away from the housing 70c of the power tool.
  • the locking element 88c moves into a locking recess 102c, which is arranged inside the counterweight 20c, so that the counterweight 20c is secured in the axial direction 100c.
  • the idle position is coupled to an idle position of a striking mechanism 12c.
  • the hammer tube 32c In the idling position of the striking mechanism arrangement 12c, the hammer tube 32c is displaced together with the retaining ring 92c in a drive direction 26c, and thus the fixing element 90c moves in the axial direction 100c out of the tapering recess 98c of the locking element 88c ( FIG. 7 ).
  • the locking unit 34c in FIG. 8 differs from the locking unit 34c in FIG. 7 by a direct arrangement of the fixing element 90c on the hammer tube 32c, which has a holding element 104c for this purpose.
  • a portable power tool impactor device 10d having a counterweight 20d which is cylindrically disposed around a hammer tube 32d of a striking mechanism assembly 12d.
  • the counterweight 20d is thereby excited counter to a drive direction 26d of the impact mechanism 12d to a counter vibration, which generates a counter force 16d to a resultant force 18d of the impact mechanism 12d.
  • the counterweight 20d is supported by a spring means 22d on a housing 70d of a hand tool, wherein the spring means 22d is arranged on one of the drive direction 26d of the hammer mechanism 12d opposite end 124d of the counterweight 20d.
  • a stop means 126d arranged on the housing 70d of a hand tool that stops the counterweight 20d in a swing back to a starting position for a new excitation and prevents unwanted further movement of the counterweight 20d in the direction of the drive direction 26d.
  • the counterweight 20d arranged around the hammer tube 32d is excited to counter oscillations via an eccentric gear 28d different from an eccentric gear 54d for driving the hammer mechanism 12d.
  • the counterweight 20d is excited via an excitation rod 128d, which is set into an axial movement via the eccentric wheel 28d.
  • the counterweight 20d arranged around the hammer tube 32d is driven via the eccentric gear 28d to drive the hammer mechanism 12d.
  • the excitation rod 128d has an axial guide 130d aligned in the drive direction 26d for exciting the counterweight 20d.
  • FIG. 11 shows a portable power tool impact device 10e with a counterweight 20e of a mass vibration unit formed by a hammer tube 32e.
  • An operation and an excitation of the counterweight 20e correspond to the example in FIG. 9 ,
  • FIG. 12 shows a portable power tool impact device 10f with an excitation means 24f formed by a pneumatic means 30f.
  • a counterweight 20f of a mass vibration unit in a housing 110f of the mass vibration unit.
  • the housing 110f of the mass vibration unit has a cylindrical shape with two valves 132f, 134f.
  • the counterweight 20f which is disk-shaped, is excited to counter vibrations of a hammer mechanism 12f, so that the counterweight 20f generates a counterforce 16f to a resultant force 18f of the hammer mechanism 12f.
  • the counterweight 20f is supported on the housing 110f by means of a spring means 22f thereon.
  • the two valves 132f, 134f are disposed on opposite housing walls 136f, 138f of the housing 110f, one of the two valves 132f for supplying air and the other of the two valves 134f for discharging air.
  • the valve 132f for supplying Air is connected to a pneumatic element 46f of the impact mechanism assembly 12f via an air line 140f. Air is conducted via the air line 140f or the valve 132f by means of an overpressure in the pneumatic element 46f of the striking mechanism arrangement 12f into the housing 110f of the mass vibration unit and an overpressure is generated in the mass vibration unit.
  • the positive air pressure in the housing 110f of the mass vibration unit pushes the counterweight 20f counter to a drive direction 26f of the hammer mechanism 12f against a spring force of the spring means 22f against the housing 110f, so as to produce a counter force 16f generated to the hammer mechanism 12f.
  • the valve 134f for discharging air from the counterweight 20f is uncovered within a portion 142f of the housing 110f with the overpressure , air can be discharged into the hand tool.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
EP07803568A 2006-11-10 2007-09-20 Massenschwingungseinheit für handwerkzeugmaschinen mit einer schlagwerkvorrichtung Not-in-force EP2089192B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006053105A DE102006053105A1 (de) 2006-11-10 2006-11-10 Handwerkzeugmaschinenschlagwerkvorrichtung
PCT/EP2007/059988 WO2008055743A1 (de) 2006-11-10 2007-09-20 Massenschwingungseinheit für handwerkzeugmaschinen mit einer schlagwerkvorrichtung

Publications (2)

Publication Number Publication Date
EP2089192A1 EP2089192A1 (de) 2009-08-19
EP2089192B1 true EP2089192B1 (de) 2011-03-23

Family

ID=38829021

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07803568A Not-in-force EP2089192B1 (de) 2006-11-10 2007-09-20 Massenschwingungseinheit für handwerkzeugmaschinen mit einer schlagwerkvorrichtung

Country Status (6)

Country Link
EP (1) EP2089192B1 (zh)
CN (1) CN101535007B (zh)
AT (1) ATE502732T1 (zh)
DE (2) DE102006053105A1 (zh)
RU (1) RU2466856C2 (zh)
WO (1) WO2008055743A1 (zh)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008044219A1 (de) * 2008-12-01 2010-06-02 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
DE102009027423A1 (de) * 2009-07-02 2011-01-05 Robert Bosch Gmbh Vorrichtung zur Reduktion und/oder Kompensation von Vibrationen, insbesondere für eine Handwerkzeugmaschine und zur Verwendung in Handwerkzeugmaschinen
DE102009044941A1 (de) * 2009-09-24 2011-03-31 Robert Bosch Gmbh Gegenschwinger, der zum Ausgleich von Gehäusevibrationen eines Elektrowerkzeugs in diesem vorsehbar ist
DE102009047106A1 (de) * 2009-11-25 2011-05-26 Robert Bosch Gmbh Variation der Eigenfrequenz von Schwingungsmitteln in Elektrowerkzeugen
DE102010039787A1 (de) * 2010-08-26 2012-03-01 Robert Bosch Gmbh Handwerkzeugmaschine
DE102012221517A1 (de) * 2012-11-26 2014-05-28 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
CN109404514B (zh) * 2017-08-14 2021-06-11 苏州宝时得电动工具有限公司 偏心轮的支撑结构、传动机构和电动工具
US10814468B2 (en) 2017-10-20 2020-10-27 Milwaukee Electric Tool Corporation Percussion tool
CN214723936U (zh) 2018-01-26 2021-11-16 米沃奇电动工具公司 冲击工具
EP3626398A1 (de) * 2018-09-19 2020-03-25 Hilti Aktiengesellschaft Zwangserregter biharmonischer tilger

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU130449A1 (ru) * 1959-12-18 1960-11-30 Е.В. Александров Электромолоток
GB2129733A (en) * 1982-10-27 1984-05-23 Jean Walton More-vibration-free concrete breakers and percussion drills
DE10021355B4 (de) * 2000-05-02 2005-04-28 Hilti Ag Schlagendes Elektrohandwerkzeuggerät mit schwingungsentkoppelten Baugruppen
CN2600223Y (zh) * 2002-12-11 2004-01-21 林青田 往复式气动工具的减震装置
EP1710052B1 (en) * 2003-03-21 2014-11-19 Black & Decker, Inc. Power hammer comprising a vibration reduction means
JP4527468B2 (ja) * 2004-08-17 2010-08-18 株式会社マキタ 電動工具

Also Published As

Publication number Publication date
WO2008055743A1 (de) 2008-05-15
DE502007006800D1 (de) 2011-05-05
CN101535007B (zh) 2011-10-05
DE102006053105A1 (de) 2008-05-15
CN101535007A (zh) 2009-09-16
RU2466856C2 (ru) 2012-11-20
RU2009121814A (ru) 2010-12-20
ATE502732T1 (de) 2011-04-15
EP2089192A1 (de) 2009-08-19

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