EP1990147A2 - Machine-outil vibrante dotée d'un élément antivibratoire - Google Patents

Machine-outil vibrante dotée d'un élément antivibratoire Download PDF

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Publication number
EP1990147A2
EP1990147A2 EP08103704A EP08103704A EP1990147A2 EP 1990147 A2 EP1990147 A2 EP 1990147A2 EP 08103704 A EP08103704 A EP 08103704A EP 08103704 A EP08103704 A EP 08103704A EP 1990147 A2 EP1990147 A2 EP 1990147A2
Authority
EP
European Patent Office
Prior art keywords
spring
external thread
spring wire
vibration
hand tool
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
EP08103704A
Other languages
German (de)
English (en)
Other versions
EP1990147A3 (fr
EP1990147B1 (fr
Inventor
Franz Mössnang
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
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Application filed by Hilti AG filed Critical Hilti AG
Publication of EP1990147A2 publication Critical patent/EP1990147A2/fr
Publication of EP1990147A3 publication Critical patent/EP1990147A3/fr
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Publication of EP1990147B1 publication Critical patent/EP1990147B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/006—Vibration damping means
    • 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
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • 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
    • B25D2250/361—Use of screws or threaded connections
    • 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
    • B25D2250/371—Use of springs

Definitions

  • the invention relates to a hand tool with a vibrating along a vibration axis assembly and a handle assembly, which is vibration decoupled via an anti-vibration element, in particular a drill or chisel hammer.
  • the handle is largely decoupled with respect to the transmission of vibrations by being connected to the vibrating assembly via an anti-vibration element.
  • the anti-vibration element may have both spring and damper properties.
  • each spring characteristic is linear, which is typical for low-loaded coil springs.
  • the spring characteristic becomes increasingly non-linear due to the material properties, especially when using elastomers.
  • suitable spring geometries such as leaf springs or other structural features such as one-sided contact constraints a spring.
  • the anti-vibration element is either completely realized as a hollow elastomeric cylinder or alternatively as a leaf spring hollow cylinder.
  • a disadvantage of an elastomeric hollow cylinder for use in the vibration damping of hand tool machines is its pronounced temperature and humidity dependence as well as the aging problem.
  • the metallic leaf spring hollow cylinder is a complicated to manufacture complex component.
  • DE102004031866 is for vibration damping of the handle of a vibrating hand tool an anti-vibration element with an axially non-linear spring characteristic already known, which consists of a spring wire coil, the two coil ends are each wound on a threaded dome, wherein the turns themselves Partially create only on one side of the external thread whose intermediate width is greater than the spring wire diameter.
  • the resulting axial non-linear spring characteristic goes smoothly in a progressively growing course after a linearly flat load area and then smoothly into a steeper linear course.
  • the core of the thread dome is tapered from the helical inner diameter axially on the spring side concave.
  • the object of the invention is the realization of a hand tool with an anti-vibration element with an axially non-linear spring characteristic, which has a steeper course on both sides of a linear flat middle load range.
  • Another aspect is the realization of a likewise non-linear spring characteristic with transverse load.
  • a handheld power tool includes a vibrating assembly along a vibration axis and a handle assembly that is vibration-decoupled via an anti-vibration member having a longitudinally oriented axis of the vibration spring coil having a plurality of windings on the unloaded anti-vibration element partially on a threaded dome with a Malawickenden over a biasing range External thread whose intermediate width is greater than the spring wire diameter of the spring wire coil, are screwed axially biased pressure.
  • the spring characteristic Due to the compressive bias of a portion of the spring wire coil and the external thread results in the spring characteristic on both sides of a flat linear center region in which all turns are exposed, each having an edge region with steeper characteristic, in which a part of the turns on the external thread and thus are no longer spring effective .
  • the spring characteristic In the low load range, where part of the windings are pressure-biased over the preload area, the spring characteristic is linearly steep because only the exposed windings are springy.
  • the spring characteristic In the high load range, in which an increasing part of the windings lie on the spring side on parts of the external thread within the preload area, the spring characteristic is progressively increasing, since fewer and fewer windings act resiliently.
  • the highest load range in which the windings within the preload area completely spring-side rest against the external thread, the spring characteristic is linearly steep, since only the exposed windings act resilient.
  • the pretensioning region which is delimited on the inside of the threaded end of the external thread, must be axially shorter than the coiled outer part of the unloaded spring wire filament.
  • the latter is thus on the outside of the inside contact surfaces of the threaded ends and thus biases the spring wire helix on the pressure side, until from the middle load range, this itself has shortened sufficiently and thus dissolves from a contact surface.
  • the spring wire helix is cylindrical and formed with a uniform pitch of the turns, whereby standard springs can be used.
  • the spring-side contact surface of the external thread on a non-linear slope whereby the spring characteristic in the high load range with respect to the progressive course is variable.
  • the external thread is a rectangular thread, whereby the contact surfaces (in longitudinal section) are axially oriented.
  • the radial height of the external thread is at least as large as the spring wire diameter, whereby the external thread forms axial contact surfaces even with combined transverse load.
  • the core of the thread dome starting from the helical inner diameter, is axially convexly tapered on the spring side, whereby, in the event of a transverse load, some turns radially engage the core of the thread dome and thus lead to a transverse progression.
  • FIG. 1 has a hand tool 12 shown only partially in the form of a chisel hammer on an anti-vibration element 1, which between a vibrating along a vibration axis A assembly 5 and a vibration-decoupled Handle assembly 6 is arranged.
  • the anti-vibration element 1 has a longitudinally oriented along the vibration axis A spring wire coil 7 with a plurality of turns 2, which are wound at a coil end on a threaded dome 3 with an external thread 4.
  • the anti-vibration element 1 is cylindrical and formed with a uniform pitch of the windings 2.
  • Fig. 2 lie in the illustrated load case of the anti-vibration element 1 without axial pressure load different turns 2 axially both spring-side and domed in a biasing V on the external thread 4 with axially two-sided contact surfaces 14, the intermediate Z is greater than the spring wire diameter D of the spring wire coil 7.
  • the spring wire coil 7 is located with different turns 7 on both contact surfaces 14 of the external thread 4.
  • the male thread 4 designed as a rectangular thread has a uniform pitch with respect to its spring-side contact surface 14 (analogously, a non-linear gradient is also possible, which is not explicitly shown).
  • the radial height H of the external thread 4 is greater than the spring wire diameter D.
  • the coaxially inner core of the threaded mandrel 3 is starting from the helical inner diameter S axially convexly tapered on the spring side.
  • Fig. 3 has the spring characteristic curve 13 (axial expansion X, axial force Fa) on both sides of a linearly flat middle region 9, in which all windings 2 (FIG. Fig. 2 ) are free, each having an edge region 8, 10 with a steeper characteristic, in which the turns 2 ( Fig. 2 ) only partially on the external thread 4 ( Fig. 2 ) abut axially.
  • the unloaded edge region 8 is the in the bias region V ( Fig. 2 ) prestressed part of the turns 2 ( Fig. 2 ) ineffective, so that results in a linear, steeper characteristic curve to overcome the bias.
  • the transition to the central region 9 forms a kink in the characteristic curve.
  • Fig. 4 has the spring characteristic 13 '(transverse strain Y, transverse force Fq) with increasing lateral load on a transverse progression by some turns 2 ( Fig. 2 ) down radially to the convex core of the threaded mandrel 3 ( Fig. 2 ) (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Springs (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP08103704A 2007-05-11 2008-04-24 Machine-outil vibrante dotée d'un élément antivibratoire Active EP1990147B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007000270A DE102007000270A1 (de) 2007-05-11 2007-05-11 Vibrierende Handwerkzeugmaschine mit Antivibrationselement

Publications (3)

Publication Number Publication Date
EP1990147A2 true EP1990147A2 (fr) 2008-11-12
EP1990147A3 EP1990147A3 (fr) 2009-07-29
EP1990147B1 EP1990147B1 (fr) 2010-11-03

Family

ID=39590743

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08103704A Active EP1990147B1 (fr) 2007-05-11 2008-04-24 Machine-outil vibrante dotée d'un élément antivibratoire

Country Status (4)

Country Link
US (1) US8511658B2 (fr)
EP (1) EP1990147B1 (fr)
CN (1) CN101301747A (fr)
DE (2) DE102007000270A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007048887B4 (de) * 2007-10-11 2017-10-26 Andreas Stihl Ag & Co. Kg Handgeführtes Arbeitsgerät
CN106523566B (zh) * 2016-10-20 2018-08-03 许继电气股份有限公司 子母弹簧组件及其弹簧座
EP3501750A1 (fr) 2017-12-19 2019-06-26 Hilti Aktiengesellschaft Machine-outil portative à vibrations amorties
EP3599059B1 (fr) * 2018-07-25 2022-05-04 Andreas Stihl AG & Co. KG Outil de travail à main et procédé de montage d'un élément anti-vibratoire d'un outil de travail à main
US12021437B2 (en) 2019-06-12 2024-06-25 Milwaukee Electric Tool Corporation Rotary power tool
CN219311210U (zh) * 2021-05-14 2023-07-07 创科无线普通合伙 一种用于动力工具的手柄
TWI807998B (zh) * 2022-09-19 2023-07-01 施瑞源 限力減震裝置

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994016864A1 (fr) 1993-01-27 1994-08-04 Lord Corporation Isolateur de vibrations pour dispositifs vibrants tenus en main
DE102004031866A1 (de) 2004-07-01 2006-01-19 Andreas Stihl Ag & Co. Kg Handgeführtes Arbeitsgerät

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1404464A (en) * 1920-12-13 1922-01-24 Adolph F Meyer Spring
US3141660A (en) * 1961-03-08 1964-07-21 Woodhead Monroe Ltd Coil springs
US4712778A (en) * 1981-12-21 1987-12-15 North American Philips Corporation Helical spring holder assembly
DE10334906B4 (de) * 2002-07-30 2018-11-15 Andreas Stihl Ag & Co. Kg Antivibrationselement

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994016864A1 (fr) 1993-01-27 1994-08-04 Lord Corporation Isolateur de vibrations pour dispositifs vibrants tenus en main
DE102004031866A1 (de) 2004-07-01 2006-01-19 Andreas Stihl Ag & Co. Kg Handgeführtes Arbeitsgerät

Also Published As

Publication number Publication date
EP1990147A3 (fr) 2009-07-29
DE502008001685D1 (de) 2010-12-16
DE102007000270A1 (de) 2008-11-20
EP1990147B1 (fr) 2010-11-03
US20080277846A1 (en) 2008-11-13
US8511658B2 (en) 2013-08-20
CN101301747A (zh) 2008-11-12

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