EP2429771B1 - Machine-outil portative, notamment machine-outil électrique portative - Google Patents

Machine-outil portative, notamment machine-outil électrique portative Download PDF

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Publication number
EP2429771B1
EP2429771B1 EP10717085.4A EP10717085A EP2429771B1 EP 2429771 B1 EP2429771 B1 EP 2429771B1 EP 10717085 A EP10717085 A EP 10717085A EP 2429771 B1 EP2429771 B1 EP 2429771B1
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EP
European Patent Office
Prior art keywords
handle
hand
power tool
held power
fastening component
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Application number
EP10717085.4A
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German (de)
English (en)
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EP2429771A1 (fr
Inventor
Joachim Schadow
Joerg Maute
Manfred Lutz
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2429771A1 publication Critical patent/EP2429771A1/fr
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    • 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

Definitions

  • the invention relates to a handheld power tool, in particular an electric handheld power tool, according to the preamble of claim 1 DE 10 2006 027 774 A1 forth.
  • the EP 1 533 084 A1 shows an electric hand drill with a tool housing, to which a bow-shaped handle connects in the rear area, the front ends of which are connected to the tool housing.
  • a base part which can be screwed onto the tool housing.
  • the bow-shaped handle has a bearing axis which is enclosed by a damping ring, the bearing axis being able to be supported with the damping ring in bearing shell sections which are located on the tool housing or on the base part.
  • the invention is based on the object of reducing the noticeable vibrations in a handheld power tool, that spread from a drive unit or arise during the machining of a workpiece and propagate into the housing of the hand tool.
  • a housing of a handheld power tool is provided with at least two separate housing parts to be connected to one another, wherein a housing part forms a handle housing for holding and guiding the hand machine tool.
  • a vibration reduction element is arranged between the housing parts.
  • the handle housing consists of at least two separately designed handle housing parts, which are designed as a handle and as a fastening component, the fastening component being connected on the one hand to the further housing part and on the other hand to the handle.
  • a vibration reduction element is arranged between the fastening component and the handle.
  • This embodiment has the advantage that the handle can be at least largely decoupled from oscillations and vibrations that originate from the drive unit or arise during the machining of a workpiece.
  • the handle is connected to the further housing part - which is usually the motor housing - at least in one spatial dimension via the fastening component.
  • the vibration reduction element is arranged between the fastening component and the handle, preferably in the axial direction in which the fastening component secures the handle.
  • the vibration reduction element lies in the transmission chain from the further housing component via the fastening element to the handle, so that the vibration transmission from the fastening component to the handle is at least reduced.
  • this version offers the possibility of designing the direct contact between the handle and the further housing part in such a way that no vibrations are transmitted, or only in a reduced manner, via this path.
  • Fasteners which connect the handle to the further housing part can be dispensed with. If necessary, such fastening means for fastening the handle to the further housing components can still be considered.
  • a further vibration reduction element is provided between the handle and the further housing component, which has a supporting effect since the handle is supported on the further housing part via this additional vibration reduction element. Despite the support, vibrations that spread in the further housing part are only transmitted to the handle in a reduced manner.
  • the division of the handle housing into a handle on the one hand and a fastening component on the other hand allows additional creative or constructive freedom and allows a variety of arrangement of vibration reduction elements between the fastening component and the further housing part and / or between the fastening component and the handle and possibly between the handle and the further housing part.
  • the further housing part is preferably a motor housing in which a drive unit, in particular an electric drive motor for driving the tool of the hand-held power tool, is accommodated. If necessary, further components are accommodated in the motor housing, for example electronic components, switches etc.
  • the handle housing forms, for example, a housing cover and, according to the invention, is made in two parts with the handle and the fastening component, the fastening component being connected directly to the motor housing, so that forces between the fastening component and are transferable to the motor housing. The fastening component also secures the handle in the desired position with respect to the motor housing.
  • the handle forms a grip sleeve which surrounds the further housing part, with the fastening component expediently forming the bottom or part of the bottom in this embodiment, so that the handle and the fastening component are designed together in a pot shape in the assembled state.
  • the grip sleeve encloses the further housing part and can be gripped in an ergonomically favorable manner by the operator for holding and guiding the handheld power tool.
  • the fastening component as the bottom of the pot-shaped housing cover, which forms the handle is positioned on the axial end of the motor housing and is expediently connected to the end of the motor housing.
  • non-positive, material and / or positive measures can be considered, for example screwing the fastening component onto the end face of the motor housing. If necessary, the fastening component can also be glued.
  • the vibration reduction element arranged between the fastening component and the handle acts in the axial direction and / or in the radial direction and dampens or reduces in this direction the vibrations to which the fastening component is subjected.
  • An optionally provided vibration reduction element between the further housing part and the fastening component also exerts its effect in the axial and / or in the radial direction.
  • the vibration reduction element is arranged in the axial direction between an end edge of the fastening component and the handle and is accordingly effective in the axial direction.
  • a further vibration reduction element can be arranged axially between an opposite end edge of the handle and a shoulder of the motor housing, so that the handle is delimited axially on opposite sides by a vibration reduction element in each case. This reduces both the transmission of vibrations from the fastening component to the handle and from the motor housing to the handle.
  • the vibration reduction element can be designed as a damping element be, which dissipates energy contained in the vibrations, so that vibrations are transmitted to the handle only in a reduced manner.
  • Vibration-reducing materials such as elastomers, rubber or rubber-like materials, foams, gels or the like are preferably used for this.
  • Material-damping components are preferably used, although movement-damping components can in principle also be used.
  • At least one vibration reduction element is designed as a spring element. Due to the spring action of the vibration reduction element, vibrations and vibrations that originate from a component are passed on to the adjacent component with respect to frequency and amplitude in reduced or modified form, whereby an effective reduction of the vibration load in the handle can also be achieved, in particular one Shift from critical to uncritical frequencies.
  • Separately designed spring elements can be used as the spring element, for example coil springs or leaf springs, which are arranged between the fastening component and the handle or are located between the motor housing and the fastening component or between the handle and the motor housing.
  • the spring elements can also be formed in one piece with a housing part, for example as a resilient projection which rises above the surface of a housing part and is in contact with a further housing part.
  • a combination of spring elements and damping elements may also be considered as vibration reduction elements.
  • the handle housing has a double-shell or double-walled design, in that the fastening component forms an inner grip sleeve which is directly connected to the motor housing, and the handle forms the outer grip sleeve which is located at a radial distance from the inner fastening component. so that an annular space is formed as an intermediate space between the sleeve-shaped, internal fastening component and the sleeve-shaped, external handle. At least one vibration reduction element is preferably arranged in the annular space, to at least weaken a vibration transmission from the motor housing via the internal fastening component to the external handle.
  • the internal fastening component can, on the other hand, be firmly connected to the motor housing, wherein vibrations transmitted to the fastening component do not lead to an increased vibration load on the operator due to the decoupling of the handle.
  • the intermediate space can advantageously be used to accommodate the vibration reduction elements, so that no additional installation space is required for the installation of vibration reduction elements.
  • vibration reduction elements can be arranged in the intermediate space. Both damping elements, in particular elements with material damping properties, are also considered, ie also spring elements that change the amplitude and the frequency of the transmitted vibrations. A mixed application of damping and spring elements can also be considered.
  • the vibration reduction element is designed as a gas pressure spring, in which a gas volume is enclosed by sealing elements which are arranged in the space between the fastening component and the handle.
  • the vibration reduction elements in the annular space cause vibration damping both in the radial direction and in the axial direction.
  • it may be expedient to align at least one vibration reduction element with an additional axial component in the intermediate space for example in such a way that a helical spring is positioned obliquely in the intermediate space, so that the spring axis both with the radial direction and with the axial direction encloses an angle.
  • a plurality of vibration reduction elements are expediently arranged in the annular intermediate space in order to ensure that there is uniform support of the outer handle on the inner fastening component over the axial length.
  • the external handle is preferably supported exclusively via vibration reduction elements in order to avoid vibration transmission bridges.
  • the outside handle is positively secured to the inside fastening component.
  • a radially inwardly projecting latching projection is formed on the handle, to which a radially outwardly facing latching projection is assigned on the outside of the fastening component.
  • the radial locking projections are axially slightly offset from one another, they can directly adjoin one another axially, so that it is reliably prevented that the handle is accidentally detached axially from the handheld power tool.
  • a bayonet lock can be used, for example.
  • the hand-held power tool has at least two separate housing parts to be connected to one another, one housing part forming a grip part for holding and guiding the hand-held power tool and a damping element being arranged between the housing parts.
  • the damping element is formed in one piece with a cable grommet, which encloses an electrical power cable, which is guided into the housing for the power supply of an electric drive motor of the hand-held power tool.
  • the cable grommet which usually consists of a material-damping material such as elastomer, is also used for vibration damping or vibration reduction, thereby simplifying the construction and reducing the number of components.
  • the damping element Since the power cable for power supply is usually inserted into the motor housing via the rear end, the damping element is also located on the rear end of the motor housing and can be connected to the handle in the sense of a fastening component, so that the handle is attached to the damping element and in one piece the damping element formed grommet is secured in at least one axial direction based on the motor housing.
  • Electric hand machine tool shown for example an angle grinder or an electric drill or screwdriver, has a housing, consisting of a motor housing 2, in which an electric drive motor 3 is arranged, and a handle housing 4, which is connected to the motor housing 2.
  • the handle housing 4 is constructed in two parts and consists of a handle 5 and a fastening component 6.
  • the handle 5 is designed as a grip sleeve which is pushed onto the rear section of the motor housing 2 and surrounds it in a ring.
  • the fastening component 6 is located on the rear axial end face 7 of the motor housing 2.
  • the sleeve-shaped handle 5 and the fastening component 6 together form a handle pot which is pushed onto the motor housing 2.
  • the fastening component 6 is designed in the form of a disk and has an axially projecting wall section 6a which extends in the direction of the handle 5.
  • the fastening component 6 is firmly connected to the rear end face 7 of the motor housing 2. In particular, the fastening component 6 lies directly on the end face 7.
  • the axially projecting section 6a of the fastening component 6 supports the handle 5 and applies an axial supporting force to it.
  • the free end face of the wall section 6a of the fastening component 6 is not in direct contact with the handle 5, but there is a damping element 8 between the handle 5 and the fastening component 6, which has the function of damping vibrations which arise from the motor housing 2 Spread out over the fastening component 6.
  • the damping element 8 is designed, for example, as a damping ring which extends along the outer jacket of the motor housing 2.
  • the damping element is not designed in the form of a ring, but rather only as a segment, in which variant a plurality of individual damping elements are preferably provided distributed over the circumference between the fastening component 6 and the handle 5.
  • the damping element 8 is seated in a contoured, ring-shaped circumferential seat 9, which is integrally formed on the outer casing of the motor housing 2.
  • the damping element 8 lies between the end face of the axial wall section 6a of the fastening component 6 and a radially inwardly extending extension 10 which is formed in one piece on the handle 5.
  • the damping element 8 transmits support forces in the axial direction and also unfolds its damping effect in the axial direction.
  • Various materials come into consideration as the material for the damping element, for example elastomers, rubber or gels or the like.
  • damping element 11 On the side axially opposite the first damping element 8 there is a further damping element 11 on the handle 5, which is clamped axially between a radially inwardly projecting extension 12 on the handle 5 and a shoulder 13 on the motor housing 2 and transmits supporting forces in the axial direction as well its damping effect unfolds in the axial direction.
  • the shoulder 13 on the motor housing 2 is designed in particular as a circumferential ring shoulder.
  • the damping element 11 is preferably designed as the damping element 8 as a damping ring.
  • the extent of the damping elements 8 and 11 is greater than the extent of the inwardly projecting extensions 10 and 12, so that the free end faces of the extensions 10 and 12 are not in contact with the outer lateral surface of the motor housing 2 and a direct contact between the handle 5 and the motor housing 2 is avoided. This ensures that there is no direct vibration transmission from the motor housing 2 to the handle 5.
  • the radial distance is determined on the one hand by the radial extent of the damping elements 8 and 11 and on the other hand by the radial extent of the seat 9, which is arranged on the outside of the motor housing 2 and serves to receive the damping element.
  • connection between the fastening component 6 and the end face 7 on the motor housing 2 takes place via common fastening measures, for example by screwing. It may be appropriate to arrange a further vibration reduction element between the end face 7 and the fastening component 6.
  • the vibration reduction elements are designed as damping elements 8 and 11.
  • spring elements can also be used instead of the damping element, which can also have a vibration-reducing effect, or at least a frequency shift in the direction of non-critical frequencies.
  • an absorber element 14 In the annular space between the outer casing of the motor housing 2 and the inside of the handle 5, which due to the radially projecting extensions 10 and 12 and the damping elements 8 and 11 is at a distance from the outer surface, there can be an absorber element 14.
  • the absorber element 14 is in particular firmly connected to the handle 5 and serves to increase the moment of inertia of the handle 5, as a result of which both the frequency and the amplitude of the vibrations acting on the handle 5 are changed. By choosing a corresponding damper element 14, the vibration load acting on the handle can be reduced in this way.
  • the absorber mass 14 is preferably fixedly and immovably connected to the handle 5. According to an alternative embodiment, however, it can also be expedient that the damper mass 14 is connected to the handle 5, but can perform a relative movement with respect to the handle 5. In this way, an oscillatable two-mass system with an intermediate spring element is achieved, which also changes both the frequency and the amplitude of the vibrations of the handle 5.
  • the sleeve-shaped handle 5 is connected to the axially rear end face 7 of the motor housing 2 by means of a spring element 15.
  • the spring element 15 is designed as a leaf spring, which is angular and extends with a section on the end face 7 of the motor housing 2 and with an angled section in the axial direction.
  • the angled section 15a has a radially outward projection in the region of its free end face, which protrudes into a groove on the inside of the handle 5, so that there is a positive connection in the axial direction between the section 15a of the spring element 15 and the handle 5 .
  • connection measures between the spring element 15 and the handle 5 can also be considered in order to secure the handle 5 in the axial direction or to achieve a vibration reduction in the axial direction and possibly also in the radial direction due to the spring action.
  • the fastening component 6 has the function of covering the end face 7.
  • the section 6a of the fastening component 6 which extends in the axial direction is expediently connected to the handle 5, a damping element being seen between the free one in the axial direction Front side of the section 6a and an extension projecting radially inwards on the inside of the handle 5 can be arranged.
  • spring elements 16, 17 and 18 are molded onto both the outer casing of the motor housing 2 and the rear, axial end face 7. These spring elements 16, 17 and 18 are formed in one piece with the motor housing and rise finger-shaped over the lateral surface or the rear end face of the motor housing.
  • the two spring elements 16 and 17 on the outer casing of the motor housing 2 act on the inside of the sleeve-shaped handle 5 and thereby transmit a clamping force in the radial direction.
  • the spring elements 16 and 17 can cooperate with a shaped seat on the inside of the handle 5, whereby a positive connection is achieved in the axial direction, so that forces can also be transmitted in the axial direction.
  • the free end face of the finger-shaped spring elements 16 and 17 extend in opposite directions, the rear spring element 17 being directed in the direction of the rear end face 7.
  • a further spring element 18 is formed on the rear end face 7 and acts axially on the fastening element 6.
  • the free end faces of the spring element 18 extend in the radial direction and lie in the assembled position in a latching recess which is delimited on the one hand by the inside of the lid-shaped fastening element 6 and on the other hand by a radially inwardly projecting extension 19.
  • the spring elements 16 and 17 on the outer surface of the motor housing 2 can extend in a ring in the circumferential direction on the outside of the motor housing. However, it is also possible to have a single, segmented spring element.
  • the fastening component 6 is designed as a base plate which is screwed to the end face 7 of the motor housing 2 by means of a screw 21.
  • the fastening component 6 acts in the axial direction on a spring element 20 which extends radially inwards on the inside of the sleeve-shaped handle 5 and is integrally formed on the handle 5.
  • the spring element 20 generates an axial force, which is directed against the contact pressure, which with the aid of the screw 21 over the fastening component 6 is reached.
  • the axial force presses the handle 5 axially against the shoulder 13 on the motor housing 2, so that the handle 5 is secured in the axial direction in both directions via the fastening component 6.
  • the radially rising spring elements 16 and 17 integrally formed on the outer casing of the motor housing 2 act on the handle 5 in the radial direction.
  • the spring element 20 formed on the inside of the handle 5 is expediently not annular, but extends only over a limited angular section.
  • a groove is formed on the inside of the handle 5, into which the edge region of the plate-shaped fastening component 6 projects.
  • a power cable 23 is arranged on the rear axial end face 7 of the motor housing 2 and is used in the interior of the motor housing to supply power to the electric drive motor placed there.
  • the power cable 23 is surrounded by a cable grommet 22, which consists of a resilient material that has vibration-damping properties.
  • a damping element 24 is formed in one piece with the cable grommet 22, which is disk-shaped or ring-shaped and whose radial outside lies in contact with the inner wall of the handle 5 in the region of the free end face of the handle.
  • an extension 10 is also formed, which is acted upon axially by the damping element 24.
  • the cover or plate-shaped fastening component 6 is inserted, which is screwed to the end face of the motor housing 2 via a screw 21.
  • the fastening component 6 acts on the damping element 24 in the axial direction and presses it in the direction of the front side 7 of the motor housing against the extension 10 on the inside of the handle 5.
  • the cable grommet 22 which surrounds the power cable 23, and the damping element 24 are formed as separate components. Both the cable grommet 22 and the damping element 24, which are each arranged on the end face 7, are clamped axially by the plate-shaped fastening component 6, which is screwed onto the end face 7 of the motor housing 2 by means of the screw 21. The cable grommet 22 and the damping element 24 are pressed axially by the pressure of the fastening element 6 against the radially inwardly projecting extension 10 formed on the inside of the handle 5.
  • damping element 24 On the side facing away from the damping element 24 there is a further damping element 25, which is ring-shaped, between the extension 10, which rotates in a ring on the inside of the handle 5, and the end face 7 of the motor housing 2.
  • the handle housing is also divided into two, however, the fastening component 6 forms an inner, pot-shaped handle sleeve which rests directly on the motor housing 2 or is connected to it.
  • the handle 5 forms an outer grip sleeve which has a larger diameter than the fastening component 6 and is pushed onto the fastening component 6.
  • an annular space 26 is formed, which serves to accommodate vibration reduction elements.
  • damping elements 8 are arranged in the space 26 as vibration reduction elements, the damping elements 8 each consisting of a material with vibration-damping properties. A plurality of such damping elements 8 are distributed over the axial length.
  • the damping elements 8 can either be ring-shaped and extend over the circumference of the intermediate space 26 or, according to an alternative embodiment, can be segment-shaped.
  • the vibration reduction elements 8 in the space 26 of the Figures 7 to 15 on the one hand assume a vibration-damping function in order to relieve the outer handle 5 of vibrations which originate from the motor housing 2 and propagate into the fastening component 6.
  • the vibration reduction elements also take on a supporting function in order to fix the sleeve-shaped handle 5 in the radial and possibly also in the axial direction in the desired installation position.
  • locking projections 27 and 28 are formed on the inside of the handle 5 and the outside of the fastening component 6, respectively, which extend in the radial direction, the dimensions of the locking projections 27 and 28 in Radial direction are selected so that a positive connection is established in the axial direction.
  • the locking projection 27 formed on the inside of the handle 5 is found at a greater axial distance from the end face of the hand tool than the second locking projection 28, which is molded onto the fastening component 6, so that the handle 5 cannot be released axially.
  • Fig. 8 consist of the vibration reduction elements, which are arranged in the intermediate space 26 between the fastening component 6 and the handle 5, each of a spring element, for example a coil spring, which is subjected to pressure.
  • the spring axis extends according to Fig. 8 in the radial direction. Due to the spring action in the radial direction, corresponding vibrations are changed according to their frequency and amplitude such that the overall vibration load in the handle 5 is reduced.
  • the spring elements 15 also bring about a stabilization of the handle 5 in the axial direction.
  • a plurality of such spring elements 15 are arranged in the intermediate space 26 distributed over the axial length.
  • the embodiment according to Fig. 9 differs from the previous one in that the spring elements 15 are arranged at an angle and inclined in the intermediate space 26, in such a way that the longitudinal axis of the spring assumes an angle both in relation to the axial direction of the housing and in relation to the radial direction. Distributed over the axial length, possibly also distributed over the circumference, several such spring elements 15 are provided, axially spaced spring elements 15 being inclined at an angle in such a way that the radially inner end face of the spring elements 15, each coupled to the fastening element 6 is directed in the direction of the respective axial end face of the fastening component.
  • the vibration reduction elements in the intermediate space 26 between the fastening component 6 and the handle 5 are each formed as leaf springs with a different geometric shape.
  • a first spring element 16 is designed as a U-shaped leaf spring, a second spring element 17 has a wave shape.
  • the U-shaped spring element 16 is only clamped in the intermediate space 26, it being possible in this case to dispense with additional fastening measures for the firm connection to the outside of the fastening component 6 or the inside wall of the handle 5; nevertheless, it may be appropriate to provide such fasteners.
  • the second, wave-shaped spring element 17 is connected via a fastening element to the wall of the fastening component 6 or the wall of the handle 5.
  • the vibration reduction element is also designed as a spring element which is arranged in the intermediate space 26. Shown is a wave-shaped spring element 17, which is molded onto the inner wall of the handle 5 and is thus formed in one piece with the handle 5. On the fastening component 6 side, the spring element 17 is connected with the aid of a fastening means, for example with the aid of a screw.
  • the space 26 is sealed gas-tight, so that the gas volume located in the space 26 is effective in the manner of a gas spring.
  • the gas-tight closure is on the part of the free
  • the end face of the fastening component 6 and the handle 5 is reached by means of an annular damping element 8 arranged adjacent to the shoulder 13 on the motor housing 2.
  • the gas volume stabilizes the handle 5 in the desired position in relation to the motor housing 2 and the fastening component 6 and also causes vibration damping.
  • fluid cushions 30 which have the function of vibration reduction elements and also support the handle 5 radially and in the axial direction.
  • the fluid cushions 30 can be filled with compressed gas, which results in a good elasticity of the fluid cushions. In principle, however, filling with liquid is also possible.
  • the fluid cushions 30 can be used in groove-shaped guide parts which are formed on the outside of the fastening component 6 or the inside of the handle 5 and in particular define the axial position of the fluid cushion 30 in a form-fitting manner.
  • sealing rings 6a, 6b and 5a there are two separately formed gas volumes 31 and 32 in the intermediate space 26, which are separated or sealed off from one another or axially outward by sealing rings 6a, 6b and 5a.
  • the sealing rings 6a, 6b and 5a are formed in one piece with the fastening component 6 or the handle 5 and are each designed as radially rising rings. Basically, separately formed sealing rings can also be considered.
  • the three rings 6a, 6b and 5a are axially spaced from one another, so that a first gas volume 31 is enclosed between the ring 6a and the ring 5a and a second gas volume 32 is enclosed between the ring 5a and the ring 6b.
  • Fig. 15 corresponds essentially to that Fig. 14 with the difference that a throttle channel 33 connecting the two fluid volumes 31 and 32 is guided through the sealing ring 5a.
  • An exchange of the respective fluid volumes is possible via the throttle channel 33, with the throttling effect being able to achieve speed damping with regard to the axial movement of the handle 5 relative to the fastening component 6.
  • the volumes 31 and 32 are in accordance with the exemplary embodiment 14 and 15 not filled with gas, but with a liquid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Portable Power Tools In General (AREA)
  • Motor Or Generator Frames (AREA)
  • Vibration Prevention Devices (AREA)

Claims (15)

  1. Machine-outil portative, en particulier machine-outil électrique portative, comportant un boîtier qui comprend au moins deux parties de boîtier (2, 4) séparées et à relier les unes aux autres, une partie de boîtier formant un boîtier de préhension (4) pour retenir et guider la machine-outil portative (1) et un élément de réduction de vibrations (8, 11, 15, 16, 17, 18, 24, 25) étant disposé entre les parties de boîtier (2, 4), caractérisée en ce que le boîtier de préhension (4) est constitué d'au moins deux parties de boîtier de préhension formées séparément, qui sont formées en tant que poignée (5) et en tant que composant de fixation (6), le composant de fixation (6) étant un couvercle de sécurité s'appuyant axialement ou du côté frontal contre l'autre partie de boîtier (2), en ce que le composant de fixation (6) est relié d'une part à l'autre partie de boîtier (2) et d'autre part à la poignée (5) et en ce qu'un élément de réduction de vibrations (24) est disposé entre le composant de fixation (6) et la poignée (5), la poignée (5) étant réalisée en tant que manchon de préhension entourant l'autre partie de boîtier (2).
  2. Machine-outil portative selon la revendication 1, caractérisée en ce qu'un élément de réduction de vibrations (24) est disposé axialement entre la poignée (5) et le composant de fixation (6).
  3. Machine-outil portative selon la revendication 1 ou 2, caractérisée en ce qu'un élément de réduction de vibrations (8, 11, 15, 16, 17, 18, 24, 25) est disposé axialement entre la poignée (5) et l'autre partie de boîtier (2).
  4. Machine-outil portative selon l'une des revendications 1 à 3, caractérisée en ce qu'un élément de réduction de vibrations (8, 11, 15, 16, 17, 18, 24, 25) est disposé radialement entre la poignée (5) et l'autre partie de boîtier (2).
  5. Machine-outil portative selon l'une des revendications 1 à 4, caractérisée en ce qu'au moins un élément de réduction de vibrations (8, 11, 15, 16, 17, 18, 24, 25) est réalisé en tant qu'élément d'amortissement (8, 11, 24, 25).
  6. Machine-outil portative selon l'une des revendications 1 à 5, caractérisée en ce qu'au moins un élément de réduction de vibrations (8, 11, 15, 16, 17, 18, 24, 25) est réalisé en tant qu'élément ressort (15, 16, 17, 18, 20).
  7. Machine-outil portative selon la revendication 6, caractérisée en ce que l'élément ressort (15, 16, 17, 18, 20) est formé d'un seul tenant avec une partie de boîtier (2, 4).
  8. Machine-outil portative selon l'une des revendications 1 à 7, caractérisée en ce qu'au moins un élément de réduction de vibrations est formé en tant que ressort à pression de gaz (31, 32).
  9. Machine-outil portative selon la revendication 8, caractérisée en ce que le ressort à pression de gaz est formé par un volume de gaz (31, 32) qui est renfermé entre des éléments d'étanchéité (5a, 6a, 6b) dans l'espace intermédiaire (26) limité par la poignée (5) et le composant de fixation (6).
  10. Machine-outil portative selon l'une des revendications 1 à 9, caractérisée en ce qu'une partie de boîtier forme un carter de moteur (2) servant à la réception d'un moteur d'entraînement (3).
  11. Machine-outil portative selon l'une des revendications 5 à 10, caractérisée en ce que l'élément d'amortissement (8, 11, 24, 25) est formé d'un seul tenant avec un passe-câble (22) d'un câble d'alimentation électrique (23) servant à l'alimentation en courant d'un moteur d'entraînement électrique (3).
  12. Machine-outil portative selon la revendication 11, caractérisée en ce que l'élément d'amortissement (8, 11, 24, 25) s'appuie par le passe-câble (22) contre un côté frontal de l'autre partie de boîtier (2).
  13. Machine-outil portative selon la revendication 11 ou 12, caractérisée en ce que l'élément d'amortissement (8, 11, 24, 25) est de forme annulaire.
  14. Machine-outil portative selon l'une des revendications 11 à 13, caractérisée en ce que la fixation à l'autre partie de boîtier (2) est réalisée au moyen de l'élément d'amortissement (8, 11, 24, 25).
  15. Machine-outil portative selon l'une des revendications 11 à 14, caractérisée en ce que l'élément d'amortissement (8, 11, 24, 25) est relié à la partie de préhension (4).
EP10717085.4A 2009-05-11 2010-04-15 Machine-outil portative, notamment machine-outil électrique portative Active EP2429771B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009002970A DE102009002970A1 (de) 2009-05-11 2009-05-11 Handwerkzeugmaschine, insbesondere Elektrohandwerkzeugmaschine
PCT/EP2010/054921 WO2010130519A1 (fr) 2009-05-11 2010-04-15 Machine-outil portative, notamment machine-outil électrique portative

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EP2429771B1 true EP2429771B1 (fr) 2020-06-10

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EP (1) EP2429771B1 (fr)
CN (1) CN102421569B (fr)
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WO (1) WO2010130519A1 (fr)

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DE102008001829A1 (de) * 2008-05-16 2009-11-19 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere Akku-Schrauber bzw. Akku-Bohrer
JP5395531B2 (ja) * 2009-06-19 2014-01-22 株式会社マキタ 作業工具
DE102012103587A1 (de) * 2012-04-24 2013-10-24 C. & E. Fein Gmbh Handführbare Werkzeugmaschine mit Außengehäuse
CN109807835A (zh) * 2012-04-26 2019-05-28 苏州宝时得电动工具有限公司 摆动动力工具
US20140262402A1 (en) * 2013-03-14 2014-09-18 Robert Bosch Gmbh Power Hand Tool with Vibration Isolation
US20150068783A1 (en) 2013-09-06 2015-03-12 Blount, Inc. Pole-attached power tool systems
DE102014103856A1 (de) * 2014-03-20 2015-09-24 C. & E. Fein Gmbh Handwerkzeug mit einem Außengehäuse und einem Innengehäuse
EP2942158A1 (fr) * 2014-05-09 2015-11-11 HILTI Aktiengesellschaft Machine-outil portative
CN105881464A (zh) * 2015-02-15 2016-08-24 苏州宝时得电动工具有限公司 动力工具
CN106965132A (zh) * 2016-01-14 2017-07-21 苏州宝时得电动工具有限公司 动力工具
JP6703417B2 (ja) * 2016-02-19 2020-06-03 株式会社マキタ 作業工具
CN107097184B (zh) * 2016-02-19 2021-08-31 株式会社牧田 作业工具
CN109883463B (zh) * 2019-03-08 2021-04-13 深圳市福伦达精工技术有限公司 一种重载车辆诊断仪
EP3745563A1 (fr) * 2019-05-31 2020-12-02 Soler & Palau Research, S.L. Moyens d'amortissement d'un moteur électrique d'un appareil de génération d'écoulement d'air et ledit appareil comprenant les moyens d'amortissement
JP7350523B2 (ja) * 2019-06-10 2023-09-26 株式会社マキタ 動力工具
US11396078B2 (en) * 2019-06-10 2022-07-26 Makita Corporation Grinder
CN216442260U (zh) 2019-06-12 2022-05-06 米沃奇电动工具公司 电动工具
CN114007810B (zh) * 2019-06-27 2023-10-31 阿特拉斯·科普柯工业技术公司 手持式动力工具
CN112427967B (zh) * 2019-08-26 2022-11-11 南京泉峰科技有限公司 电动工具
JP2022127768A (ja) * 2021-02-22 2022-09-01 株式会社マキタ 打撃工具
CH718506B1 (de) * 2021-04-02 2024-05-31 Xenaki Georg Gerät, insbesondere für Massage- und Behandlungszwecke.
JP2024011112A (ja) * 2022-07-14 2024-01-25 株式会社マキタ 打撃工具

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CN102421569B (zh) 2015-04-01
WO2010130519A1 (fr) 2010-11-18
US20120111595A1 (en) 2012-05-10
US9168652B2 (en) 2015-10-27
DE102009002970A1 (de) 2010-11-18
CN102421569A (zh) 2012-04-18
EP2429771A1 (fr) 2012-03-21

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