EP3501750A1 - Machine-outil portative à vibrations amorties - Google Patents

Machine-outil portative à vibrations amorties Download PDF

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Publication number
EP3501750A1
EP3501750A1 EP17208325.5A EP17208325A EP3501750A1 EP 3501750 A1 EP3501750 A1 EP 3501750A1 EP 17208325 A EP17208325 A EP 17208325A EP 3501750 A1 EP3501750 A1 EP 3501750A1
Authority
EP
European Patent Office
Prior art keywords
stiffness
vibration
compression spring
hand tool
rigidity
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Withdrawn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
EP17208325.5A
Other languages
German (de)
English (en)
Inventor
Adrian Steingruber
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 EP17208325.5A priority Critical patent/EP3501750A1/fr
Priority to PCT/EP2018/082028 priority patent/WO2019120837A1/fr
Priority to EP18801003.7A priority patent/EP3727762B1/fr
Priority to US16/757,737 priority patent/US11518017B2/en
Publication of EP3501750A1 publication Critical patent/EP3501750A1/fr
Withdrawn legal-status Critical Current

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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
    • B25D17/24—Damping the reaction force
    • 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 present invention relates to an electric hand tool machine comprising a percussion mechanism assembly vibrating along a vibration axis and a handle assembly that is vibration-decoupled via an anti-vibration unit, the anti-vibration unit having a multi-turn spring wire helix oriented along the vibration axis.
  • a hand tool is for example from the DE 10 2007 000 270 A1 known.
  • the spring wire coil is formed as a cylindrically progressive compression spring with two stiffness ranges of different stiffness.
  • a nonlinear spring characteristic of the spring wire coil can be achieved in a structurally simple and cost-effective manner.
  • the anti-vibration unit is free of a threaded dome, on which the spring wire coil is at least partially screwed.
  • the spring wire coil is formed as a cylindrically progressive compression spring with two stiffness ranges of different stiffness, a comparatively simple adaptation of the stiffness curve is possible, namely only by replacing the spring wire coil itself.
  • the spring wire coil provided as a cylindrically progressive compression spring is designed to be progressive on one side.
  • the higher stiffness range of stiffness sequentially joins the low stiffness range of stiffness.
  • the spring wire coil provided as a cylindrically progressive compression spring is progressively formed on both sides and preferably has a third stiffness range.
  • the third stiffness region has the same rigidity as the stiffness region having the lower stiffness.
  • the Stiffness range with the higher rigidity, along the vibration axis, between the stiffness ranges with the lower stiffness is provided.
  • the stiffness regions with the respectively low rigidity along the vibration axis have the same length.
  • the stiffness regions with the respective lower stiffness along the vibration axis can be shorter than a length of the stiffness region with the higher rigidity.
  • the compression spring has a constant outer diameter.
  • the compression spring in the unloaded state has a length between 65 and 75 mm.
  • the compression spring 66 has an outer diameter of between 19 and 23 mm.
  • FIG Fig. 1 A preferred embodiment of an electric hand tool 100 is shown in FIG Fig. 1 shown.
  • the electric hand tool 100 is provided as a hammer drill.
  • the hand tool 100 has a percussion mechanism assembly 10 vibrating longitudinally along the vibration axis A.
  • the striking mechanism assembly 10 includes an electric motor and a transmission, which are not shown here.
  • the electric hand tool 100 further has a handle assembly 20, which is vibration-decoupled via an anti-vibration unit 30.
  • the anti-vibration unit 30 in turn has a spring wire coil 35 oriented along the vibration axis A and having a plurality of turns.
  • Fig. 1 can be removed, the percussion unit 10 is slidably mounted via a slide 60 in a housing unit 90 of the power tool 100.
  • the housing 90 can in turn be handled via a rear handle 25 and a front handle 55.
  • the striking mechanism assembly 10 is connected to the housing unit 90 via an articulated arm 37 such that the striking mechanism assembly 10 can move along the vibration axis A.
  • the movement of the percussion mechanism assembly 10 is limited by a front stop buffer 70 and a rear stop buffer 73 relative to its movement along the vibration axis A.
  • the spring wire coil 35 is designed as a cylindrically progressive compression spring 36 with two stiffness ranges S1, S2 of different degrees of rigidity.
  • the spring wire coil 35 provided as a cylindrically progressive compression spring 36 is progressively formed on one side, with the higher stiffness portion S2 sequentially joining the lower stiffness portion S1.
  • Fig. 2 is the cylindrically progressive compression spring 36 of Fig. 1 shown in detail.
  • the cylindrically progressive compression spring 36 has two stiffness ranges S1, S2, which - in relation to the vibration axis - sequentially connect to each other.
  • the two stiffness regions S1, S2 have different stiffnesses.
  • the first rigidity region S1 has a lower rigidity than the second rigidity region S2.
  • a cylindrically progressive compression spring 36 which is progressively formed on both sides, is in Fig. 3 shown.
  • the compression spring 36 of Fig. 3 has three stiffness ranges S1, S2, S3.
  • first stiffness region S1 has a lower rigidity than the second rigidity region S2 having a high rigidity.
  • the third rigidity region S3 has the same rigidity as the first rigidity region S1, so both the first rigidity region S1 and the second rigidity region S3 each have a lower rigidity than the middle, second rigidity region S2.
  • the rigidity region S2 having the higher rigidity, along the vibration axis A, is located between the stiffness regions S1, S2 each having the low rigidity.
  • the stiffness regions S1, S3 with the respective lower rigidity have, along the vibration axis A, the same length LS1, LS3. This has the advantage that a risk of kinking the double-sided progressively formed cylindrical compression spring 36 is reduced.
  • the stiffness regions S1, S3 with the respective low stiffness along the vibration axis A are shorter than a length LS2 of the stiffness region S2 with the higher rigidity.
  • the compression spring 36 has a constant outer diameter.
  • Fig. 4 shows Fig. 4A the compression spring 36 in the unloaded state.
  • a nominal length of the compression spring 36 is about 69.55 mm.
  • Fig. 4B shows the state of the compression spring 36 in the installed and unactuated state.
  • the nominal length L1 of the unloaded compression spring 36 is about 56.50 mm, the associated spring force F1 for the unactuated state is about 132.5 N.
  • Fig. 4C finally shows the compression spring 36 in the installed and actuated state.
  • the nominal length L2 here is about 42.5 mm with an associated spring force F2 of about 310.1 N.
  • Fig. 5 shows further technical characteristics of the particularly preferred double-sided progressive compression spring 36 of Fig. 4 ,
  • the nominal lengths L0, L1, L2 or the spring force F1 assigned to the nominal length L1 and the spring force F2 assigned to the nominal length L2 have already been described with reference to FIG Fig. 4 described.
  • compression spring 36 has a wire diameter d of 2.8 mm and a mean turn diameter of the compression spring 36 Dm of about 18.2 mm.
  • the number of resilient turns n is calculated about 9.9 turns.
  • the total number of turns nt is calculated about 13.1 turns.
  • Fig. 6 shows a characteristic spring diagram for the preferred cylindrically progressive compression spring 36, which is progressively formed on both sides and has three stiffness ranges.
  • the relationship between the respective nominal lengths L0, L1, L2 and the associated lifting voltages F1, F2, etc. can be seen here.
  • the spring characteristic of the preferred compression spring 36 is the Fig. 3 to 6 shown.
  • a stroke tension F in N is plotted against the spring travel s in mm. It can be clearly seen that the spring characteristic curve increases linearly up to a stroke voltage Fx of approximately 213.42 N in order to bend off from this point (bending point of the spring characteristic curve) towards a steeper spring characteristic curve section.
  • the spring characteristic of the compression spring 36 thus has a total of a progressive behavior.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP17208325.5A 2017-12-19 2017-12-19 Machine-outil portative à vibrations amorties Withdrawn EP3501750A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP17208325.5A EP3501750A1 (fr) 2017-12-19 2017-12-19 Machine-outil portative à vibrations amorties
PCT/EP2018/082028 WO2019120837A1 (fr) 2017-12-19 2018-11-21 Machine-outil portative à amortissement des vibrations
EP18801003.7A EP3727762B1 (fr) 2017-12-19 2018-11-21 Machine-outil portative à vibrations amorties
US16/757,737 US11518017B2 (en) 2017-12-19 2018-11-21 Vibration-damped hand-held power tool

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17208325.5A EP3501750A1 (fr) 2017-12-19 2017-12-19 Machine-outil portative à vibrations amorties

Publications (1)

Publication Number Publication Date
EP3501750A1 true EP3501750A1 (fr) 2019-06-26

Family

ID=60673931

Family Applications (2)

Application Number Title Priority Date Filing Date
EP17208325.5A Withdrawn EP3501750A1 (fr) 2017-12-19 2017-12-19 Machine-outil portative à vibrations amorties
EP18801003.7A Active EP3727762B1 (fr) 2017-12-19 2018-11-21 Machine-outil portative à vibrations amorties

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP18801003.7A Active EP3727762B1 (fr) 2017-12-19 2018-11-21 Machine-outil portative à vibrations amorties

Country Status (3)

Country Link
US (1) US11518017B2 (fr)
EP (2) EP3501750A1 (fr)
WO (1) WO2019120837A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI807998B (zh) * 2022-09-19 2023-07-01 施瑞源 限力減震裝置

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DE102007000270A1 (de) 2007-05-11 2008-11-20 Hilti Aktiengesellschaft Vibrierende Handwerkzeugmaschine mit Antivibrationselement
EP2848370A1 (fr) * 2013-09-12 2015-03-18 HILTI Aktiengesellschaft Machine-outil manuelle

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10334906A1 (de) * 2002-07-30 2004-02-26 Andreas Stihl Ag & Co. Kg Antivibrationselement
DE202004013670U1 (de) * 2004-09-01 2004-11-04 Wacker Construction Equipment Ag Hammer mit abgefederter Schutzhaube
US20070277992A1 (en) * 2006-05-30 2007-12-06 Hilti Aktiengesellschaft Percussion hand-held power tool with axially displaceable percussion mechanism
DE102007000270A1 (de) 2007-05-11 2008-11-20 Hilti Aktiengesellschaft Vibrierende Handwerkzeugmaschine mit Antivibrationselement
EP2848370A1 (fr) * 2013-09-12 2015-03-18 HILTI Aktiengesellschaft Machine-outil manuelle

Also Published As

Publication number Publication date
EP3727762B1 (fr) 2023-10-18
US20210187721A1 (en) 2021-06-24
EP3727762A1 (fr) 2020-10-28
US11518017B2 (en) 2022-12-06
WO2019120837A1 (fr) 2019-06-27

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