EP2457694B1 - Outil électrique - Google Patents

Outil électrique Download PDF

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Publication number
EP2457694B1
EP2457694B1 EP11188467.2A EP11188467A EP2457694B1 EP 2457694 B1 EP2457694 B1 EP 2457694B1 EP 11188467 A EP11188467 A EP 11188467A EP 2457694 B1 EP2457694 B1 EP 2457694B1
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EP
European Patent Office
Prior art keywords
mass
spring
machine tool
additional mass
striking
Prior art date
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Active
Application number
EP11188467.2A
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German (de)
English (en)
Other versions
EP2457694A2 (fr
EP2457694A3 (fr
Inventor
Peter Brugger
Dieter Profunser
Alexander Hoop
Hans Böni
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
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Hilti AG
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Publication of EP2457694A2 publication Critical patent/EP2457694A2/fr
Publication of EP2457694A3 publication Critical patent/EP2457694A3/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B25B21/026—Impact clutches

Definitions

  • the invention relates to a hand tool according to the preamble of claim 1.
  • a mechanical Tangentialtschtechnik as in the power tool of the type mentioned, for example, in an impact wrench allows comparatively large torques of the tool holder to provide, with only a comparatively small counter-torque required. This is for example when tightening screw or the setting of screw anchors in particularly solid ground advantage.
  • the tip torque which can be provided by the tangential impactor can far exceed a continuous torque that can be set by the drive of the handheld power tool.
  • the lowest possible counter-torque is of particular advantage to the user, since he usually has to provide the counter-torque on the handle of the hand-held power tool, such as an impact wrench. The lower the counter-torque, the easier it will be to handle the power tool.
  • a comparatively low holding torque is particularly desirable, as this is a major advantage of a percussive impact wrench, z. B. compared to a conventional screwdriver represents.
  • a percussive impact wrench z. B. compared to a conventional screwdriver represents.
  • a hand tool according to the preamble of claim 1 is made DE 11 96 587 known.
  • the invention begins, the object of which is to provide a hand tool machine in which an applicable torque range can be adapted in an improved manner.
  • an adaptation of a tangential impact mechanism should be implemented in an improved manner.
  • an adapted torque range should result in an overall increased applicable torque range.
  • the task relating to the power tool is achieved by a hand tool of the type mentioned, in the present invention, the features of the characterizing part of claim 1 are provided.
  • the tangential impact additionally provides an additional mass available that is releasably coupled to the main mass and is under the action of a second spring.
  • the additional mass is composed of the sum of the main mass and additional mass. This increases, if necessary, the deliverable torque of the tangential impact according to the concept of the invention.
  • the concept of the invention also provides that the additional mass is under the action of a second spring.
  • the concept of the invention also has the advantage that due to the largely constant beat frequency when adapting the tangential impact mechanism, an engine speed can also remain relatively constant. This advantageously allows an improved design of the drive both to a first operating state with only the main mass as a hammer and to a second operating state with increased Total mass of the hammer. At most, in the case of using an unregulated motor to drive the power tool when adapting the Tangentialzzitechniks the same speed due to the load also adapt.
  • the power tool in the context of a particularly advantageous development of the power tool, it can thus be operated in a first and a second operating state, it being possible to switch back and forth as required between the operating states mentioned.
  • a first operating state the main mass of the hammer and the anvil are axially movable under the action of force of a first spring and, while twisting the same, against each other tangentially against one another.
  • a second operating state the main mass and the additional mass of the hammer and anvil under the action of force of the first and second spring axially and while rotating the same against each other tangentially hitting against each other movable.
  • the additional mass can be detachably coupled to the main mass by means of a feed mechanism.
  • the feed mechanism advantageously has a preloaded second spring acting on the additional mass.
  • the feed mechanism is advantageous to operate by the user of the power tool, so that can be switched during operation of the power tool by pressing the feed mechanism between the first and second operating state.
  • the feed mechanism is movable along a control link.
  • the delivery mechanism may be movable by a user.
  • the feed mechanism is axially displaceable along a control link.
  • the delivery mechanism may also be rotatable along a control link. Both are possible alone and in combination, for example, to switch between the aforementioned first operating and second operating state of the power tool.
  • the main mass and the additional mass are positively coupled to one another in a second operating state.
  • This has proven to be a comparatively simple mechanism for increasing the overall mass of the hammer.
  • the feed mechanism has a housing cage, in which said second spring is biased against the additional mass and the housing cage.
  • a housing cage is advantageous as a whole freely or according to a control link movable.
  • the feed mechanism thus has an intrinsically compact form which is safe to operate.
  • the feed mechanism is secured in a first operating state of a securing element against movement.
  • a securing element advantageously serves to prevent unintentional actuation of the feed mechanism.
  • a securing element can be designed to secure the feed mechanism for operation of the handheld power tool both in the first operating state and in a second operating state.
  • a securing element may be designed as a lever lock or the like against whose resistance the feed mechanism is to be actuated or which is also to be actuated by the user before actuation of the feed mechanism.
  • the tangential impact mechanism with a structurally suitable force-transmitting impact gear which acts on the hammer and / or the anvil.
  • a striking mechanism is advantageously used to move the hammer and / or anvil axially against one another according to a control contour and while twisting the same against each other tangentially.
  • Hammer and / or anvil advantageously each have a striking surface over which a Tangentialschlag is transferable to transmit a peak torque between the hammer and anvil.
  • the percussion gear can be formed in the form of a slotted guide with a thread-like control contour, which is formed on a spindle coupling the drive and the hammer.
  • a percussion gear may also be in the form of a knob arrangement with a slanted control contour formed on a cam and anvil coupling cam.
  • Other forms of impact gear are possible and not limited to the aforementioned advantageous developments.
  • the additional mass has a striking surface, which is coupled in the coupling Condition of additional mass and main mass extends axially equal to or beyond an extension of the main mass.
  • the impact surface of the additional mass alone or additionally formed to strike against an anvil impact surface for transmitting a Tangentialschlag. This can be used to a larger-scale design of the face of the additional mass and thus lower stress of the additional mass in carrying out the tangential impact.
  • the main mass has a striking surface which extends axially beyond an extension of the additional mass in the coupled state of additional mass and main mass.
  • the striking surface of the main mass is designed solely to strike against an anvil striking surface.
  • This second variant can advantageously be used to make the striking surfaces, in particular the anvil striking surface comparatively small. This can be used to advantage in reducing the total mass of the tangential impactor.
  • Fig. 2A and Fig. 2B schematically show the operation of an adaptive tangential impactor 10, wherein Fig. 2A the adaptive tangential impactor 10 in a first operating state and Fig. 2B shows the adaptive tangential impactor 10 in a second mode of operation.
  • the adaptive tangential impact mechanism 10 which for the sake of simplicity is also referred to as a tangential striking mechanism, has an anvil 60 assigned to the drive shaft 30 and a hammer 70 assigned to the drive 104 Fig. 2A
  • the hammer 70 is merely shown with its main mass 71.
  • the main mass 71 of the hammer 70 is movable axially against the anvil 60 solely under the action of a first external spring 81 and tangentially striking the anvil 60 while the main mass 71 is rotated.
  • the first - outboard - spring 81 is part of a in Fig. 2B
  • the first, outer spring 81 is supported against a fixed stop 83 and is biased in this manner against the main mass 71 of the hammer 70.
  • the first outer spring 81 has a first spring constant K1, which is achieved by means of its rigidity.
  • the main mass 71 of the hammer 70 has a weight designated M1.
  • the adaptive tangential impactor 10 may also be used in a second in accordance with the concept of the invention Fig. 2B shown operating state in which increases the deliverable torque and yet the natural frequency of the spring-mass system of hammer 70 and spring system 80 is kept substantially constant.
  • an additional mass 72 is additionally positively coupled to the main mass 71 of the hammer 70.
  • the weight of the additional mass 72 is referred to herein as M2.
  • the total mass of the hammer 70 is thus in the second in Fig. 2B shown operating state M1 + M2.
  • the equipped with this total mass hammer 70 is under the action of force of the spring system 80, which now in addition to the first, outer spring 81 has a second - extending within the outer spring spring 82.
  • the spring constant K2 of the second spring 82 is determined by its rigidity and may be greater or smaller than the stiffness of the first spring 81.
  • a spring constant K2 - as well as the mass M2 of the additional mass 72 - be designed to a natural frequency of the spring Mass system of hammer 70 and spring system 80 in the second operating state in comparison to the first operating state to keep largely the same.
  • Both springs 81, 82 are in turn supported against the stop 83.
  • second operating state is the sum of the weights of the main mass 7 and additional mass 71, 71 of the hammer 70 under the action of the first and second spring 81, 82, so that the hammer 70 is axially and while twisting the same against the anvil 60 tangentially striking movable.
  • the hammer 70 has - in this case shown symbolically on the main mass 71 - hammer cam 73, which are provided for abutment with this also associated symbolically anvil cam 63.
  • a hammer cam 73 has a face 74 transverse to the circumferential direction of the hammer 70.
  • an anvil cam 63 may have a face 64, which is set transversely to the circumferential direction and is associated with the striking surface 74.
  • the striking surface can also be formed directly on the body of the anvil 60.
  • the axial and twisting movement of the hammer 70 is realized in the present case by a percussion gear in the form of a not shown in detail slotted guide on the spindle 20.
  • the slotted guide has a thread-like control contour which forcibly guides the hammer 70 with main mass 71 and 72 to a rotary movement under axial feed to the anvil 60, the movement being driven by the spring system 80.
  • Fig. 3A, Fig. 3B show - in each case in a cross section I and an axial section II already Fig. 2A, Fig. 2B explained operating states of a Tangentialtschtechniks 10A according to a particularly preferred first embodiment of the first further developing variant of the invention.
  • FIGS. 2A and 2B For identical or similar parts or parts of identical or similar function, in the present case the same reference numerals as in FIG FIGS. 2A and 2B used.
  • the mode of operation of the first variant of the adaptive tangential impact device 10A corresponds to the mode of operation as described with reference to FIG Fig. 2A, Fig. 2B was explained. In the following, reference is made in particular to the structural details of the tangential impact mechanism 10A and remainder to the description of the Fig. 2A, Fig. 2B directed.
  • the tangential impactor 10A is in the in Fig. 3A shown first operating mode operated only with the main mass 71, which is under the action of force only the first spring 81 and is moved axially and with rotation of the main mass 71 tangentially striking against the anvil 60.
  • the corresponding cam 73 of the main mass 71 is in the cross-sectional view I of Fig.
  • the moment of inertia of the main mass 71 in the present case is about I 1 40 000 gmm 2 .
  • the moment of inertia of the additional mass 72 in the present case is about I 2 100 000 gmm 2 .
  • the spring stiffness K1 of the first spring 81 is presently about 11 kN / m.
  • the spring stiffness K2 of the second spring 82 is present at 36 kN / m. Im in Fig. 3B shown second state, add the weights M1, M2 of the main mass 71 and the additional mass 72 to the total weight M1 + M2 of the hammer 70.
  • the spring stiffnesses K1, K2 of the first and second spring add up to a total spring stiffness K1, K2 of the spring system 80th the likewise adding moments of inertia I 1 , I 2 , the adaptive tangential impactor 10 A in the second operating state of the Fig. 3B a significantly increased transmissible torque.
  • the resonantly operable natural frequency of the spring-mass system of the adaptive tangential impactor 10A in the second operating state largely corresponds to that of the first operating state.
  • An effectively selectable beat frequency of the tangential impactor 10A thus remains largely the same although the transmittable torque is increased.
  • a housing frame 90 which is displaceable along the spindle 20 and rotatably mounted is realized.
  • the housing cage 90 is freely axially displaceable and rotatably mounted along a control link, not shown. That is, by rotating or moving the fixed to the housing cage and the housing 101 of the power tool 100 by cross-wheel 91 can be actuated the delivery mechanism as soon as the unintentional actuation preventing securing elements 92 are unlocked.
  • the securing elements 92 are formed in the form of tilting levers against the housing cage 90.
  • the housing cage 90 can be rotated or displaced beyond the resistance of the rocker arms.
  • the tilting levers attached to a housing 101 of the portable power tool are pushed away from the steering wheel 91 toward the housing.
  • the first spring 81 here supports an inner spring and against a stop 83.1 fastened to the spindle 20 and prestressed against the main mass 71.
  • the second spring 82 is here an outer spring and supported against a formed by the rear wall of the rear housing cage 90 stop 83.2 and biased against the additional mass 72.
  • the annular designed main mass 71 and additional mass 72 are present in any case partially concentric with each other.
  • the additional mass 72 surrounds the main mass annularly and positively in the second operating state, while the main mass 71 is guided by a control contour of a slotted guide on the spindle 20.
  • the tangential impact mechanism 10A is fastened to the housing 101 of the handheld power tool 100 with screw connections 107.
  • the screw connections 107 hold a bearing block 108, which on the drive side comprises the bearings 109 for the spindle 20.
  • the additional mass 72 has a cross-sectional view I of FIG Fig. 3B apparent striking surface 74 on a hammer cam 75 thereof, which extends in the coupled state of additional mass 72 and main mass 71 over an axial extent of the main mass 71 axially out or - in a modification - can extend to the same height thereof.
  • at least the striking surface 74 of the additional mass 72 serves - in a modification by the striking surface of the main mass 71 - for abutment against an anvil striking surface on an anvil cam 63.
  • Both the main mass 71 and the additional mass 72 can therefore have suitable cams 73 with impact surface 74 for the execution of a tangential impact on the anvil 60.
  • the striking surface 74 may be formed by a cam 75 of the additional mass 72 or - in the modification - both by a cam 73 of the main mass and by a cam 75 of the additional mass 72. Especially in the latter case increases the total available impact surface 74 for tangential impact on the anvil 60 so that the tangential impact torque distribution is distributed over a relatively large area. This ultimately leads to less wear of the cams 73, 75 on the main mass 71 and additional mass 72.
  • the face of the cam 75 of the additional mass 72 projects slightly relative to the cam 73 of the main mass, so that only the cam 75 of the additional mass 72 has contact with the anvil 60 during tangential impact.
  • the main mass 71 and the additional mass 72 are positively connected to each other by the described feed mechanism.
  • Both the main mass and the additional mass 72 and the first spring 81 and the second spring 82 are available for torque transmission at the tangential 10 A in Fig. 3B shown second operating mode available. Accordingly, the deliverable torque increases in the adaptive tangential impactor 10A. Due to the second spring 82, the release torque of the tangential impactor is also increased. However, this holds in a relatively limited range, so that the handling of a hand tool 100 with the adaptive tangential impactor 10 is practically not affected.
  • FIGS. 3A and 3B show a second embodiment of an adaptive tangential impactor 10B in one FIGS. 3A and 3B analog representation.
  • identical reference numerals are used herein for identical or similar parts or parts of identical or similar function.
  • the design of the adaptive tangential impactor 10B is broadly similar to that of the adaptive tangential impactor 10A. In the following, only the differences between the two tangential impact devices are referred to. The essential difference is by comparison of the cross-sectional representation I in FIGS. 4A and 4B recognizable.
  • the main mass 71 has a striking surface 74 or a cam 73 which is exclusively-that is to say in FIG Fig. 4A shown first operating state as well as in Fig. 4B shown second operating state - Contact with the anvil 60 has Tangentialschlag.
  • the concentric and form-fitting coupled to each other main mass and additional mass 71, 72 to form the hammer 70 only with the two cams 73 of the main mass 71 are equipped.
  • the additional mass 72 has no cams.
  • the impact surfaces of the anvil 60 can thereby be carried out to a lesser extent.
  • the entire spring-mass system of the adaptive percussion mechanism 10B can be made smaller in mass.
  • the additional mass 72 thus has a lower weight than the main mass. Accordingly, the moment of inertia difference between the main mass and the additional mass is not as great as in the adaptive tangential impactor 10A.
  • the spring stiffness for forming the spring constant K1 of the first spring is selected here with 11 KN / m.
  • the spring stiffness for forming the spring constant K2 of the second spring is presently formed with 24 KN / m.
  • the second spring constant K2 in the spring system is thus greater than the first spring constant K1.
  • the preferred impact frequency of the tangential impactor 10A, 10B, that is the natural frequency of the total spring-mass system, in the first and second operating state is approximately equal.
  • Fig. 5 shows on an equal scale the torque peaks transmitted between hammer 70 and anvil 60 over an equal period of time in an adaptive tangential impactor 10A or 10B.
  • view A it can be seen that an average amount of transmitted torque peak in the first operating state corresponds to only about half of an average amount of a torque peak in the second operating state.
  • the first operating state only the main mass 71 of the hammer 70 is moved tangentially striking the anvil 60 under the force of the first spring 81 while twisting it.
  • both the main mass 71 and the additional mass 72 of the hammer 70 are moved axially against the anvil 60 by twisting the first and second springs 81, 82, while twisting the same.
  • the illustrations also show that the beat frequency of an adaptive tangential impactor 10A, 10B is substantially equal and fairly constant in the first and second modes of operation.

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

Claims (12)

  1. Machine-outil manuelle (100), en particulier sous forme de visseuse à percussion, comportant :
    - un porte-outil monté sur un arbre d'entraînement (30) pour recevoir un outil, en particulier un tournevis,
    - dans laquelle l'arbre d'entraînement (30) peut réaliser un mouvement de rotation et de percussion en partie tangentielle au moyen d'un mécanisme de percussion tangentielle (10, 10A, 10B) pouvant être entraîné par un mécanisme d'entraînement (104), en particulier un moteur (105) et/ou un bloc d'engrenages (106),
    - dans laquelle le mécanisme de percussion tangentielle (10, 10A, 10B) comporte une enclume (60) associée à l'arbre d'entraînement (30) et un marteau (70) associé au mécanisme d'entraînement (104), lesquels enclume et marteau peuvent, sous l'action de la force d'au moins un premier ressort (81), se déplacer l'un par rapport à l'autre et venir se percuter axialement l'un contre l'autre de manière tangentielle lorsqu'ils sont mis en rotation,
    - dans laquelle le marteau (70) comporte une masse principale (71), et
    - dans laquelle une masse additionnelle (72) peut être accouplée à la masse principale (71), laquelle masse additionnelle est soumise à l'action de la force d'un second ressort (82),
    caractérisée en ce que la masse additionnelle (72) peut être accouplée à la masse principale (71) de manière séparable.
  2. Machine-outil manuelle (100) selon la revendication 1, caractérisée en ce que dans un premier état de fonctionnement, la masse principale (71) du marteau (70) et l'enclume (60) seule peuvent, sous l'action de la force d'un premier ressort (81), se déplacer l'une par rapport à l'autre et venir se percuter axialement l'une contre l'autre de manière tangentielle lorsqu'elles sont mises en rotation.
  3. Machine-outil manuelle (100) selon la revendication 1 ou 2, caractérisée en ce que dans un second état de fonctionnement, la masse principale (71) et la masse additionnelle (72) du marteau (70) et de l'enclume (60) peuvent, sous l'action de la force des premier et second ressorts (81, 82), se déplacer l'une par rapport à l'autre et venir se percuter axialement l'une contre l'autre de manière tangentielle lorsqu'elles sont mises en rotation.
  4. Machine-outil manuelle (100) selon la revendication 1 ou 2, caractérisée en ce que la masse additionnelle (72) peut être accouplée à la masse principale (71) de manière séparable au moyen d'un mécanisme d'avance, dans laquelle le mécanisme d'avance comporte un second ressort (82) préchargé agissant sur la masse additionnelle (72).
  5. Machine-outil manuelle (100) selon l'une des revendications 1 à 4, caractérisée en ce que le mécanisme d'avance peut être déplacé axialement le long d'une coulisse de guidage et/ou peut être mis en rotation, en particulier par un utilisateur.
  6. Machine-outil manuelle (100) selon l'une des revendications 1 à 5, caractérisée en ce que la masse principale (71) et la masse additionnelle (72) sont accouplées par complémentarité de formes dans un second état de fonctionnement.
  7. Machine-outil manuelle (100) selon l'une des revendications 1 à 6, caractérisée en ce que la masse additionnelle (72) comporte une surface d'impact qui, lorsque la masse additionnelle (72) et la masse principale (71) sont accouplées, s'étend axialement jusqu'à ou au-delà d'une extension de la masse principale (71) pour venir en butée contre une surface d'impact de l'enclume.
  8. Machine-outil manuelle (100) selon l'une des revendications 1 à 7, caractérisée en ce que la masse principale (71) comporte une masse de percussion qui, lorsque la masse additionnelle (72) et la masse principale (71) sont accouplées, s'étend axialement au-delà d'une extension de la masse additionnelle (72) pour venir en butée contre une surface d'impact de l'enclume.
  9. Machine-outil manuelle (100) selon l'une des revendications 1 à 8, caractérisée en ce que le mécanisme d'avance comporte une cage de boîtier (90) dans laquelle le second ressort (82) est préchargé contre la masse additionnelle (72) et la cage de boîtier (90).
  10. Machine-outil manuelle (100) selon l'une des revendications 1 à 9, caractérisée en ce qu'un mouvement du mécanisme d'avance est empêché dans un premier état de fonctionnement par un élément de blocage (92).
  11. Machine-outil manuelle (100) selon l'une des revendications 1 à 10, caractérisée en ce que les poids des masses (71, 72) et les raideurs des ressorts (81, 82) sont configurés de telle sorte qu'une fréquence de résonance du mécanisme de percussion tangentielle (10, 10A, 10B) est sensiblement égale dans un premier état et un second état de fonctionnement.
  12. Machine-outil manuelle (100) selon l'une des revendications 1 à 11, caractérisée en ce que le mécanisme de percussion tangentielle (10, 10A, 10B) comporte un bloc d'engrenages de percussion transmettant une force et agissant sur le marteau (70) et/ou l'enclume (60), bloc d'engrenages de percussion au moyen duquel le marteau (70) et/ou l'enclume (60) peuvent être déplacés l'un par rapport à l'autre en suivant un contour de guidage et venir se percuter axialement l'un contre l'autre de manière tangentielle lorsque le bloc d'engrenages est mis en rotation.
EP11188467.2A 2010-11-26 2011-11-09 Outil électrique Active EP2457694B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010062014A DE102010062014B3 (de) 2010-11-26 2010-11-26 Handwerkzeugmaschine

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EP2457694A2 EP2457694A2 (fr) 2012-05-30
EP2457694A3 EP2457694A3 (fr) 2018-03-14
EP2457694B1 true EP2457694B1 (fr) 2019-05-15

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US (1) US8950508B2 (fr)
EP (1) EP2457694B1 (fr)
JP (1) JP6009756B2 (fr)
DE (1) DE102010062014B3 (fr)

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EP2985118A1 (fr) 2014-08-12 2016-02-17 HILTI Aktiengesellschaft Procéde optimisé pour une ancre extensible
EP2985117A1 (fr) * 2014-08-12 2016-02-17 HILTI Aktiengesellschaft Procéde optimisé pour une ancre extensible
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JP6397325B2 (ja) * 2014-12-22 2018-09-26 株式会社Ｔｊｍデザイン 回転工具
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WO2018080786A1 (fr) * 2016-10-11 2018-05-03 Ingersoll-Rand Company Clé à chocs ayant des composants d'entraînement accordés de manière dynamique et procédé associé
JP6995591B2 (ja) * 2017-11-30 2022-01-14 株式会社マキタ インパクト工具
JP7386027B2 (ja) * 2019-09-27 2023-11-24 株式会社マキタ 回転打撃工具
JP7320419B2 (ja) 2019-09-27 2023-08-03 株式会社マキタ 回転打撃工具
JP7373376B2 (ja) * 2019-12-02 2023-11-02 株式会社マキタ インパクト工具
JP2022106194A (ja) * 2021-01-06 2022-07-19 株式会社マキタ インパクト工具

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Also Published As

Publication number Publication date
JP2012111035A (ja) 2012-06-14
EP2457694A2 (fr) 2012-05-30
JP6009756B2 (ja) 2016-10-19
DE102010062014B3 (de) 2012-05-10
US8950508B2 (en) 2015-02-10
US20120132452A1 (en) 2012-05-31
EP2457694A3 (fr) 2018-03-14

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