WO2012045504A1 - Amortisseur de vibrations multidimensionnel - Google Patents

Amortisseur de vibrations multidimensionnel Download PDF

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Publication number
WO2012045504A1
WO2012045504A1 PCT/EP2011/063621 EP2011063621W WO2012045504A1 WO 2012045504 A1 WO2012045504 A1 WO 2012045504A1 EP 2011063621 W EP2011063621 W EP 2011063621W WO 2012045504 A1 WO2012045504 A1 WO 2012045504A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration
vibration damper
mass
power tool
balancing mass
Prior art date
Application number
PCT/EP2011/063621
Other languages
German (de)
English (en)
Inventor
Willy Braun
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
Priority to EP11740930.0A priority Critical patent/EP2625005A1/fr
Publication of WO2012045504A1 publication Critical patent/WO2012045504A1/fr

Links

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
    • 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

Definitions

  • the present invention relates to a vibration damper comprising a balance mass, which is provided for performing a counter-vibration, which counteracts a housing vibration of a power tool, and a power tool with a vibration damper according to the invention.
  • a vibration generating case vibration has a plurality of frequency components caused by different vibration sources.
  • the play between the individual components, non-linear elasticity courses, non-linear impact processes, only approximately harmonious reaction forces from a percussion mechanism, shock and recoil processes of a percussion chain or unbalanced mass forces of the drive come into question.
  • the main frequency is often significantly caused by a single source of vibration.
  • the main frequency is essentially derived from the periodic acceleration of the club. With such power tools is already a very good
  • a damper is a spring-mass system with a fixed resonant frequency that can achieve significant vibration reduction in a region near the resonant frequency.
  • absorbers are usually attached to a housing surface and act against the spatial direction in which the relevant vibration source acts.
  • Such absorbers show, for example, the documents EP 1 736 283 A2, EP 1 952 952 A2 and DE 20 2005 021 085 111, which disclose power tools with a striking mechanism.
  • the documents EP 1 736 283 A2 and EP 1 952 952 A2 disclose a damper which is arranged on the percussion mechanism housing cover, the EP 1 952 952 A2 providing a closed plastic housing for accommodating the absorber.
  • DE 20 2005 021 085 IM the absorber between the percussion mechanism housing and the housing shell of the power tool is arranged.
  • the document EP 1 770 979 A1 discloses a damping system consisting of two absorbers arranged on opposite sides of the hand-held power tool.
  • the absorbers disclosed here have in common that they have an absorber mass formed from a solid body with a cuboid, cylinder or plate-shaped geometry.
  • Such absorber systems are only unfavorable in a construction concept for a power tool can be integrated, as they usually greatly increase the rebuilding space.
  • the object of the invention is to provide a vibration reduction system for a power tool, which is very compact integrated into the power tool, so that it takes up very little space and the rebuild space of the power tool as little as possible increased, and at the same time an improved reduction of the housing oscillation of the power tool allows.
  • a vibration damper comprising a compensating mass, which is provided for exerting a counter-vibration, which counteracts a housing vibration of a housing of a power tool, wherein the balancing mass is formed from an open tube profile, or wherein the balancing mass formed from an open or closed tube profile is that vibrates in more than one spatial direction.
  • a pipe profile in the sense of the invention is a hollow body extending along a longitudinal direction and having in principle any but preferably area-symmetrical cross-section.
  • a tubular profile is rectangular or circular.
  • Such a tube profile is referred to below as closed tube profile.
  • An open tube profile according to the invention is a tube profile which is open on one side.
  • an open tube profile is U-shaped or partially circular.
  • Such an open or closed tube profile has the advantage that it can be manufactured inexpensively from a standard profile bar. Furthermore, it is better integrated on or in the housing of the power tool. Because in a preferred embodiment, the open or closed tube profile extends along major device surfaces.
  • a main device surface is, for example, a housing surface bounding an interior of the power tool or a housing surface. ne device component limiting surface or the power tool to the outside limiting housing surface.
  • the open or closed tube profile extends over at least two or more major device surfaces. Compared to a balancing mass that extends only along one main surface of the device, there are therefore several main device surfaces available for the open or closed tube profile.
  • the leveling compound is therefore of a shallower construction so that it less increases the functional space of the electrical tool.
  • the open or closed tube profile due to its multi-dimensional extent and better in the space of the power tool can be arranged, in which no other components of the power tool are arranged. The power tool is therefore more compact overall.
  • the center of gravity of the balancing mass is arranged outside the balancing mass.
  • the center of mass of the open or closed pipe profile is arranged in the converted interior of the pipe profile.
  • the balancing mass preferably has a recess in which an elastic force means is arranged. Since the elastic force means is arranged in a recess of the balancing mass, it requires no additional space.
  • the balancing mass is preferably provided so that it oscillates against the force of the elastic force means in and against a first spatial direction.
  • an elastic force means is preferably a metal spring, more preferably provided a steel spring, which is formed for example as a cylindrical coil spring or as a torsion spring. Such a spring has a high efficiency and therefore causes a good decoupling.
  • the elastic force agent made of elastomeric materials, especially preferred zugt made of closed-cell elements made of polyurethane.
  • Such an elastomer spring has the advantage that it can be loaded in several spatial directions, so that only an elastomeric spring for vibration damping in all directions required and the vibration damper is therefore very simple.
  • Very particularly preferably combined as elastic force means metal spring elements with spring elements made of elastomeric materials. Then, preferably, a metal spring element counteracts the relevant vibration source, while an elastomeric spring element acts at least in the other spatial directions.
  • the vibration absorber preferably comprises a guide rail extending in the first spatial direction.
  • the first spatial direction is preferably the spatial direction in which the relevant vibration-causing source oscillates.
  • the guide rail is resiliently mounted in a second spatial direction and / or a third spatial direction, which extend in each case transversely to the first spatial direction.
  • second and third elastic force means are preferably provided, for the material formation of which the same embodiments already described above apply, as for the elastic force means.
  • This resilient mounting allows the vibration damper further degrees of freedom of movement in a second and a third spatial direction, which are arranged in particular transversely to the first spatial direction and transverse to each other, with the same balancing mass.
  • the degrees of freedom of movement are decoupled from each other by means of the elastic force means.
  • the vibration damper is therefore not only better integrated into the spatial concept of the power tool, but with the same leveling compound is also a Vibrationstilgung achieved in several directions.
  • the elastomeric spring elements, in particular the second and third elastic force means are preferably used for the eradication of further less significant vibration-causing sources.
  • the balancing mass comprises two recesses, in each of which an elastic force means is arranged, and the vibration damper two guide rails, which are arranged on opposite sides of the balancing mass.
  • the recesses and the guide rails are arranged symmetrically to a center plane, so that the bearing forces occurring on the guide rail evenly distributed.
  • the object is further achieved with a power tool with a vibration damper according to the invention.
  • the power tool has a striking mechanism.
  • the power tool is a Bohrhamnmer.
  • the vibration absorber according to the invention can also be integrated into other power tools.
  • the vibration absorber is preferably provided as close as possible to a relevant vibration source, so that the power flow path between the vibration source and the vibration reduction system is small. Therefore, it is preferred that the center of gravity of the balancing mass is arranged close to or on a striking mechanism axis of the hammer mechanism. Particularly preferably, the first spatial direction extends along the striking mechanism axis. Furthermore, it is preferred that the balancing mass at least partially transverse to Schlagtechniksachse extends, so that a very effective vibration damping in particular caused by the impact mechanism as a significant vibration source housing vibration is possible.
  • FIG. 1 shows a power tool, here a hammer drill, in a side view with a vibration damper according to the invention
  • FIG. 2 shows a partial section A-A through the hammer drill of FIG. 1 in a plan view from above
  • Fig. 3 shows a partial section C-C of the hammer drill of Fig. 2 in one
  • FIG. 3 (a) shows the vibration damper of FIGS. 1, 2, 4 and 5, and FIG. 3 (b) shows another embodiment of a vibration damper according to the invention
  • FIG. 4 shows a side view of that disclosed in FIGS. 1 and 2
  • FIG. 5 shows a sectional view B-B of FIG. 2 of a bearing of a guide rail of the vibration damper disclosed in FIGS. 1 and 2.
  • FIG. 1 shows a power tool 3, in this case a hammer drill, in a side view with a vibration damper 1 according to the invention.
  • the terms power tool 3 and hammer drill are used synonymously below.
  • the vibration damper 1 has a balancing mass 2, which is displaceably mounted along a guide rail 7 in and against a first spatial direction, which is characterized here by an arrow 1 1.
  • a balancing mass 2 which is displaceably mounted along a guide rail 7 in and against a first spatial direction, which is characterized here by an arrow 1 1.
  • the leveling compound 2 against the force of an elastic member 61 which is designed here as a helical spring, moved.
  • the terms elastic element and coil spring are used synonymously.
  • the helical spring 61 is arranged in a recess 5 of the balancing mass 2.
  • FIG. 2 shows a partial section A-A through the hammer drill 3 of FIG. 1 in a plan view from above.
  • 4 shows a side view of the vibration damper disclosed in FIGS. 1 and 2
  • FIG. 5 shows a sectional view B-B of FIG. 2 of a bearing of a guide rail of the vibration damper disclosed in FIGS. 1 and 2.
  • the leveling compound 2 is formed by an open, here U-shaped, tubular profile.
  • balancing mass 2 and pipe profile are used synonymously.
  • the tube profile 2 has on two opposite sides 21, 23 legs and a leg 21, 23 connecting bottom 22.
  • opposite sides 21, 23 of the balancing weight and legs are used synonymously. It is mounted on the two opposite legs 21, 23 on guide rails 7 translationally displaceable in the first spatial direction 11, in which extend the guide rails. Namely, the recess 5 is provided in both legs 21, 23 of the balancing mass 2, in which the helical spring 61 is arranged.
  • the helical spring 61 is fixed to the balancing mass 2 with a first end 61 1 and is supported on the guide rail 7 at a second end 612, so that it is compressed when the balancing mass 2 is displaced against the first spatial direction 11.
  • the coil spring 61 When moving in the first spatial direction 1 1, the coil spring 61, however, decompressed. In a swinging motion, the coil springs 61 are alternately supported on the guide rail 7 and the leveling compound 2.
  • the guide rails 7 are provided here as two symmetrical to a median plane 9 arranged separate components. But they are also summarized to a single component. Furthermore, they can be combined with a cover (not shown), chips the vibration damper 1 is dust-free encapsulated.
  • the vibration damper 1, in particular the leveling compound 2, is arranged symmetrically overall with respect to the median plane 9, in which a hammer mechanism axis 81 of the hammer drill 3 also extends. Therefore, the percussion axis 81 extends transversely through the bottom 23 of the balancing mass 2. Since the vibration damper 1 is symmetrical to the median plane 9, in which the striking mechanism axis 81 is arranged, the center of mass of the balancing mass 2 is on a line M, which extends transversely to the hammer axis 81 and this cuts.
  • the legs 21, 23 of the balancing mass 2 each extend essentially along a side surface 821, 823 of a percussion mechanism housing 82 of the hammer drill 3.
  • the base 22 of the balancing mass 2 extends substantially along an end face 822 of the striking mechanism housing 82.
  • the side surfaces 821, 823 and the end face 822 of the percussion mechanism housing 82 main surfaces of the device. Therefore, the shown vibration absorber 1 according to the invention extends along three main surfaces 821, 822, 823. It is therefore much flatter than a vibration absorber with a balancing mass of the same material and weight, which extends only along a single device main surface (not shown).
  • an arrangement of the balancing mass 2 is also preferred, in which these extend from the side surfaces 821, 823 along the rear end face 822, starting from the side surfaces 821, 823 above the striking mechanism housing 82 extends.
  • the leveling compound 2 extends along further main surfaces of the device.
  • the guide rails 7 are fixed to the striking mechanism housing 82. In this embodiment, however, only housing vibrations can be compensated, which oscillate in the first spatial direction 1 1.
  • the guide rail 7 shown here is instead mounted resiliently by means of a bearing member 71 to a guide housing 78, wherein the guide housing 78 in turn is resiliently mounted in a guide bearing 83 of the percussion mechanism housing 82.
  • the bearing component 71 which is cylindrical (see Fig. 5), recesses in which second elastic force means 62 are supported.
  • the arrangement of the second elastic force means 62 in the guide housing 78 is visible above all in a section of FIG. 5.
  • the guide housing 78 has a U-shaped cross-section and is provided such that the second elastic force means 62 are each supported on a leg 781 of the guide housing 78 (see FIG. 3 (a)), and thus a frictional connection between the bearing component 71 and cause the guide housing 78.
  • the guide rail 7 By means of the second elastic force means 62, the guide rail 7 and thus also the leveling compound 2 in and against a second spatial direction, which is shown here as arrow 12, slidably mounted.
  • the bearing component 71 allows a rotary rotational movement relative to the housing 78.
  • the guide bearing 83 is also provided in U-shaped cross-section in the striking mechanism housing 82. Between the guide bearing 83 and the guide housing 78 third elastic force means 63 are provided, which are supported on the guide bearing 83 and the guide housing 78, so that this in and gene a third spatial direction, which here is the Maschinenquimmight, and is shown by an arrow 13, is displaceable.
  • the legs 781 of the guide housing 78 slide along legs 831 of the guide bearing 83, so that the guide bearing 83 is provided at the same time for supporting and guiding the guide housing 78.
  • FIG. 2 shows a partial section CC of the hammer drill of FIG. 2 in a view from the end face 33 (see FIG. 2) of the hammer drill 3, wherein FIG. 3 (a) shows the vibration damper 1 of FIGS. 4 and 5, and wherein FIG. 3 (b) shows a further embodiment of a vibration damper 1 according to the invention.
  • 3 (a) shows the bearing of the guide rail 7. Visible is the arrangement of the guide rail 7 on the bearing component 71, the means of the second elastic force means 62 caused resilient mounting of the bearing member 71 in the guide housing 78 and the caused by the third elastic force means 63 resilient mounting of the guide housing 78 in the guide bearing 83 of the percussion mechanism housing 82nd
  • Impact mechanism (not shown) of the hammer drill 3 extends.
  • the second and third force means 62, 63 are formed in the context of Fig. 2, 3a and 5 as coil springs.
  • Fig. 3 (b) shows an embodiment of the vibration absorber 1 in which the second and third elastic force means 62 ', 63' are each formed as an elastomeric spring. Due to their geometric configuration and support, forces and moments can be transmitted via the elastomer springs 62 ', 63' at the same time, so that the leveling compound 2 nevertheless remains rigidly coupled to the striking mechanism housing 82.
  • the second elastic force means 62 'designed as an elastomer spring also replaces that in the embodiment of FIG. 3 (b).
  • Required bearing component 71 The formed as an elastomer spring third elastic force means 63 'replaces in this embodiment, the required in the embodiment of Fig. 3 (b) guide housing 78.
  • This embodiment is therefore in terms of the number of components and the assembly cost is very inexpensive.
  • the vibration damper 1 according to the invention is not only very compact in a construction concept of a power tool 3 can be integrated without significantly increase the converted functional space of the power tool 3. But it is also very effective in terms of the compensation of the housing vibrations. Because it not only vibrates in the spatial direction 1 1, in which vibrates the vibration responsible for the largest proportion of vibration largely responsible. Instead, it vibrates in all three spatial directions 11, 12, 13, so that other vibrations, which are not caused in particular by this authoritative source, can be compensated with the vibration damper 1 according to the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

L'invention concerne un amortisseur de vibrations (1) qui comprend une masse d'équilibrage (2) servant à exercer une contre-vibration, qui agit à l'encontre d'une vibration d'un carter (4) d'un outil électrique (3). Selon l'invention, la masse d'équilibrage (2) est constituée d'un profilé tubulaire ouvert ou bien la masse d'équilibrage (2) est constituée d'un profilé tubulaire ouvert ou fermé, qui vibre dans plus d'une direction spatiale. La présente invention concerne par ailleurs un outil électrique (3) équipé de l'amortisseur de vibrations (1) selon l'invention.
PCT/EP2011/063621 2010-10-04 2011-08-08 Amortisseur de vibrations multidimensionnel WO2012045504A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11740930.0A EP2625005A1 (fr) 2010-10-04 2011-08-08 Amortisseur de vibrations multidimensionnel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010041928.1 2010-10-04
DE102010041928A DE102010041928A1 (de) 2010-10-04 2010-10-04 Mehrdimensionaler Schwingungstilger

Publications (1)

Publication Number Publication Date
WO2012045504A1 true WO2012045504A1 (fr) 2012-04-12

Family

ID=44513233

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/063621 WO2012045504A1 (fr) 2010-10-04 2011-08-08 Amortisseur de vibrations multidimensionnel

Country Status (3)

Country Link
EP (1) EP2625005A1 (fr)
DE (1) DE102010041928A1 (fr)
WO (1) WO2012045504A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170043466A1 (en) * 2014-04-30 2017-02-16 Hitachi Koki Co., Ltd. Work tool

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6362931A (ja) * 1986-09-04 1988-03-19 Nippon Kokan Kk <Nkk> 動吸振器
EP1736283A2 (fr) 2005-06-23 2006-12-27 Black & Decker, Inc. Mécanisme d'amortissement de vibrations pour un marteau perforateur
DE202005021085U1 (de) 2004-08-27 2007-01-25 Makita Corp., Anjo Kraftwerkzeug
EP1770979A2 (fr) 2005-09-30 2007-04-04 Pitney Bowes, Inc. Système de détection des copies utilisant corrélations de modeles de détection des copies
EP1787761A1 (fr) * 2005-11-16 2007-05-23 Metabowerke GmbH Perçeuse motorisée à percussion
EP1952952A2 (fr) 2007-01-31 2008-08-06 HILTI Aktiengesellschaft Réducteur de vibrations pour machine-outil manuelle

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6362931A (ja) * 1986-09-04 1988-03-19 Nippon Kokan Kk <Nkk> 動吸振器
DE202005021085U1 (de) 2004-08-27 2007-01-25 Makita Corp., Anjo Kraftwerkzeug
EP1736283A2 (fr) 2005-06-23 2006-12-27 Black & Decker, Inc. Mécanisme d'amortissement de vibrations pour un marteau perforateur
EP1770979A2 (fr) 2005-09-30 2007-04-04 Pitney Bowes, Inc. Système de détection des copies utilisant corrélations de modeles de détection des copies
EP1787761A1 (fr) * 2005-11-16 2007-05-23 Metabowerke GmbH Perçeuse motorisée à percussion
EP1952952A2 (fr) 2007-01-31 2008-08-06 HILTI Aktiengesellschaft Réducteur de vibrations pour machine-outil manuelle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170043466A1 (en) * 2014-04-30 2017-02-16 Hitachi Koki Co., Ltd. Work tool
US10632605B2 (en) * 2014-04-30 2020-04-28 Koki Holdings Co., Ltd. Work tool

Also Published As

Publication number Publication date
DE102010041928A1 (de) 2012-04-05
EP2625005A1 (fr) 2013-08-14

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