WO2007088821A1 - Outil a impact - Google Patents

Outil a impact Download PDF

Info

Publication number
WO2007088821A1
WO2007088821A1 PCT/JP2007/051415 JP2007051415W WO2007088821A1 WO 2007088821 A1 WO2007088821 A1 WO 2007088821A1 JP 2007051415 W JP2007051415 W JP 2007051415W WO 2007088821 A1 WO2007088821 A1 WO 2007088821A1
Authority
WO
WIPO (PCT)
Prior art keywords
striking
tool
motion
striker
impact
Prior art date
Application number
PCT/JP2007/051415
Other languages
English (en)
Japanese (ja)
Inventor
Masanori Furusawa
Original Assignee
Makita Corporation
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 Makita Corporation filed Critical Makita Corporation
Priority to EP07707646.1A priority Critical patent/EP1980371B1/fr
Publication of WO2007088821A1 publication Critical patent/WO2007088821A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • 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
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • 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
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0015—Tools having a percussion-only mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • 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
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0023—Pistons
    • B25D2217/0026—Double pistons
    • 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
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/275—Tools having at least two similar components

Definitions

  • the present invention relates to a striking tool that performs a predetermined machining operation by a striking operation of a tool bit in a long axis direction.
  • An electric hammer as a striking tool that performs a predetermined machining operation by a striking operation of a tool bit driven by a motor in the long axis direction is widely known.
  • Such an electric hammer is disclosed in, for example, Japanese Patent Application Laid-Open No. 2005-335046.
  • the rotation output of the motor is converted into a linear motion of the piston by the crank mechanism, and the striker linearly moves through the air panel that fluctuates due to the linear motion of the piston to strike the tool bit.
  • the present invention has an object to provide a technique effective in improving the working efficiency of a striking tool in view of the power.
  • the impact tool includes a motor, a first motion conversion mechanism, a first impact mechanism, a second motion conversion mechanism, a second impact mechanism, and a tip tool member.
  • the first motion mechanism is configured to convert the rotational output of the motor into linear motion
  • the first striking mechanism is configured to perform linear motion by being driven by the first motion mechanism.
  • Second The motion variation m «mechanism is configured to convert the rotational output of the motor into linear motion
  • the second striking mechanism is configured to perform linear motion by being driven by the second motion mechanism.
  • the tip tool member is struck by the first and second striking mechanisms and moves linearly to perform a predetermined machining operation on the workpiece.
  • the tip tool member is preferably struck alternately by each striking mechanism.
  • an electric hammer or a tip tool member that performs a hammering operation on a workpiece by performing only a straight striking motion in the long axis direction of the tip tool member is used.
  • first motion conversion mechanism and the “second motion conversion mechanism” in the present invention typically have a mechanism that converts the rotational output of the motor into a linear motion of the piston by the crank mechanism.
  • a mechanism that converts the rotational motion of the rotating body rotated by the motor into the swing motion of the swing member, and then converts the swing motion of the swing member into the linear motion of the piston or It preferably includes a mechanism for converting to linear movement of the piston using a swash plate rotated by a motor.
  • first striking mechanism and the “second striking mechanism” in the present invention typically include a striking element that performs a linear motion by a change in air pressure of an air chamber due to a linear linear motion of a piston, Furthermore, although it is set as the structure which has an intermediate
  • first and second motion conversion mechanisms means that there are at least two motion conversion mechanisms, and in addition to the first and second motion conversion mechanisms, a third motion conversion mechanism is included.
  • An embodiment having a conversion mechanism and further a fourth motion conversion mechanism is suitably included.
  • first and second striking mechanisms means that there are at least two striking mechanisms.
  • the third striking mechanism and further the fourth striking mechanism is suitably included.
  • the “tip tool member” in the present invention suitably includes any of an aspect constituted by a single tool bit or an aspect constituted by a plurality of tool bits.
  • a mode in which a single tool bit is struck by a plurality of striking mechanisms, and a plurality of tool bits have the same number of striking mechanisms as the plurality of tool bits.
  • Any of a mode in which a plurality of tool bits are struck by a larger number of striking mechanisms than the plurality of tool bits, and a mode in which a plurality of tool bits are struck by a smaller number of striking mechanisms than the plurality of tool bits. Preferably included.
  • the first motion conversion mechanism and the first striking mechanism driven by the motor, and the second motion mechanism and the second striking mechanism driven by the motor can be hit to perform a predetermined processing operation. For this reason, the working efficiency is improved as compared with the conventional impact tool in which the tip tool member is driven by a single motion conversion mechanism and impact mechanism.
  • the rotational speed of the motor, the motion conversion mechanism driven by the motor, and the drive speed of the striking mechanism can be reduced. It is possible to reduce the wear of the sliding portion and improve the durability without reducing the working efficiency.
  • the first striking mechanism and the second striking mechanism in the striking tool are configured to perform a linear motion opposite to each other.
  • the other striking mechanism moves linearly in opposition to the one striking mechanism, so that it functions as a counterweight.
  • the vibration in the long axis direction of the tip tool member is reasonably reduced, which is effective for lowering the vibration of the impact tool in addition to improving work efficiency.
  • the first striking mechanism has a cylindrical first striking element that linearly moves to drive the tip tool member, and the second striking mechanism linearly moves to drive the tip tool member.
  • a second striker that is cylindrical and has approximately the same mass as the first striker.
  • the first striker and the second striker are configured to linearly move in opposition to each other.
  • the tip tool member is alternately struck by the first and second strikers and linearly moves, thereby increasing the number of strikes of the tip tool per unit time and further increasing the number of strikes from the first and second strikers.
  • the counterweight function between the two strikers can be further enhanced.
  • the first hitting mechanism and the second hitting mechanism are arranged in parallel in the vertical direction. This makes it possible to further improve the tool drive balance.
  • FIG. 1 is a side sectional view showing the overall configuration of the electric hammer according to the present embodiment.
  • the electric hammer 101 according to the present embodiment generally has a main body 103 that forms an outline of the electric hammer 101 and a tip region (left side in the drawing) of the main body 103.
  • the hammer bit 163 corresponds to the “tip tool member” in the present invention.
  • the hammer bit 163 side is referred to as the front
  • the hand grip 109 side is referred to as the rear.
  • the main body 103 constituting the tool main body includes a motor housing 105 containing a drive motor 111, first and second sets of crank mechanisms 113 and 115, and first and second sets of two.
  • a gear housing 107 that houses the striking elements 117 and 119 is formed.
  • the rotational output of the drive motor 111 is appropriately converted into linear motion by the first and second crank mechanisms 113, 115 and then transmitted to the first and second striking elements 117, 119, and the first and second An impact force in the major axis direction of the hammer bit 163 (left and right direction in FIG. 1) is generated via the second striking elements 117 and 119.
  • the drive motor 111 corresponds to the “motor” in the present invention.
  • the first crank mechanism 113 corresponds to the “first motion variable shelf” in the present invention
  • the second crank mechanism 115 corresponds to the “second motion variable structure” in the present invention
  • the first striking element 117 corresponds to the “first striking mechanism” in the present invention
  • the second striking element 119 corresponds to the “second striking mechanism” in the present invention.
  • the drive motor 111 is energized and driven by a pulling operation of a trigger 109a disposed on the handgrip 109.
  • FIG. 2 is a sectional view showing an enlarged state of the main part of the electric hammer 101
  • FIG. 3 shows a sectional structure based on the sectional instruction line of FIG.
  • the first and second clan The gear mechanisms 113 and 115 are arranged in parallel in the gear housing 107 in the vertical direction.
  • the first crank mechanism 113 includes a first crank plate 125 that is rotatable in a horizontal plane, a first eccentric shaft 127 that is shifted from the center of rotation to the first crank plate 125, and one end of the first eccentric shaft 127. Is connected to the other end of the first crank arm 129 via a first connecting shaft 131 so as to be relatively rotatable. Consists of the subject.
  • the first crank plate 125 is formed in a circular shape, and has a driven gear 125 a on the outer peripheral surface thereof.
  • the driven gear 125 a is engaged with and engaged with a drive gear 121 that is rotationally driven by the drive motor 111.
  • the first piston 133 is slidably disposed in the first bore 151a of the cylinder 151, and when the drive motor 111 is energized and driven, the long axis direction of the cylinder 151 (the non-mabit long axis direction) ) Perform a linear motion.
  • the second crank mechanism 115 includes a second crank plate 137 that is rotatable in a horizontal plane, a second eccentric shaft 139 that is arranged with a rotational center force shifted to the second crank plate 137, and a second eccentric shaft.
  • a second crank arm 141 one end of which is connected to the shaft 139 in a loose fit, and a second driver as a second driver attached to the other end of the second crank arm 141 via a second connecting shaft 143 so as to be relatively rotatable.
  • the second piston 145 is slidably disposed in the second bore 151b of the cylinder 151 !.
  • the first crank plate 125 and the second crank plate 137 are set so that their rotational axes are the same axis.
  • the shift amount of the first eccentric shaft 127 from the rotation center of the first crank plate 125 and the shift amount of the second eccentric shaft 139 from the rotation center of the second crank plate 137 are both set equal.
  • the first eccentric shaft 127 and the second eccentric shaft 139 are connected by a connecting member 147 so as to have a phase difference of approximately 180 degrees in the rotational direction of the first crank plate 125. That is, the second crank mechanism 115 is driven from the first crank mechanism 113 driven by the drive motor 111 via the connecting member 147, and the second piston 145 is substantially at a crank angle with respect to the first piston 133. It is configured to perform opposing linear motion with a delay of 180 degrees.
  • the first and second striking elements 117, 119 are arranged in parallel in the vertical direction.
  • the first striking element 117 includes a first striker 153 as a first striking element slidably disposed in the first bore 151a of the cylinder 151 and moving linearly in the longitudinal direction of the cylinder 151, and a cylindrical tool.
  • the holder 161 is slidably disposed, and is configured mainly with an impact bolt 157 as an intermediate that transmits the kinetic energy of the first striker 153 to the hammer bit 163.
  • the first striker 153 is driven through the fluctuation of the air pressure in the first air chamber 151c of the cylinder 151 accompanying the sliding movement of the first piston 133, that is, through the air panel, and collides (hits) with the impact bolt 157.
  • the striking force is transmitted to the non-mabit 163 held in the tool holder 161. That is, the first striking element 117 is driven by the first crank mechanism 113.
  • the second striking element 119 is slidably disposed in the second bore 151b of the cylinder 151, and the second striker 155 as a second striker that linearly moves in the longitudinal direction of the cylinder 151; No. impact bolt 157.
  • the second striker 155 is driven through the air panel of the second air chamber 151d of the cylinder 151 accompanying the sliding motion of the second piston 145, and collides with the impact bolt 157 to hit the impact bolt 157.
  • the striking force is transmitted to the retained non-mabit 163. That is, the second striking element 117 is driven by the second crank mechanism 115.
  • the impact bolt 157 receives a striking motion of the first striker 153 in the radially lower region of the rear end portion in the long axis direction and receives a striking motion of the second striker 155 in the radially upper region.
  • the impact surface 157a is as large as possible.
  • the cylinder 151 has a circular first bore 151a in which the first piston 133 and the first striker 153 are slidably arranged, and a circle in which the second piston 145 and the second striker 155 are slidably arranged.
  • the second bore 151b is attached to the gear housing 107 in a state where movement in the long axis direction and the circumferential direction is restricted.
  • FIG. 3 shows the cross-sectional structure of the cylinder 151.
  • the tool holder 161 is attached to the distal end portion of the gear housing 107 in a state where movement in the long axis direction and the circumferential direction is restricted.
  • the hammer bit 163 is held by the tool holder 161 in a state where relative movement in the major axis direction is allowed.
  • the first air chamber 151c is caused to fluctuate in the air pressure in the first air chamber 151c.
  • the striker 153 moves linearly in the cylinder 151. Then, the first striker 153 collides with the impact bolt 157 to transmit the kinetic energy (striking force) to the hammer bit 163, which causes the hammer bit 163 to slide in the tool holder 161 and to be covered. Perform hammering work on the workpiece.
  • the second eccentric shaft 139 is connected to the second eccentric shaft 139 via the connecting member 147 in conjunction with the rotating operation of the first eccentric shaft 127 accompanying the rotation of the first crank plate 125.
  • Crank plate 137 circulates around the center of rotation.
  • the second crank arm 141 swings and the second piston 145 slides in the second bore 151b of the cylinder 151.
  • the first eccentric shaft 127 and the second eccentric shaft 139 have a phase difference of approximately 180 degrees in terms of crank angle. Therefore, the second piston 145 is slid linearly within the second bore 151b of the cylinder 151 with a delay of about 180 degrees with respect to the first piston 133.
  • a single hammer bit 163 can be struck twice by one crank rotation. For this reason, the number of hits of the hammer bit 163 is doubled when the number of revolutions of the drive motor 111 is set to be equal to that of a conventional electric hammer that performs a single hitting operation with one crank rotation. Work efficiency is improved. In other words, when the number of hammer bits 163 hit per unit time is set to the same level as the conventional one, the rotational speed of the drive motor 111 and the first and second cranks driven by the drive motor 111 are changed.
  • the driving speed of the mechanisms 113, 115 and the first and second striking elements 117, 119 can be reduced at low speeds, resulting in a sliding part without reducing work efficiency.
  • Durability can be improved by reducing wear on sliding parts such as materials or O-rings.
  • the first piston 133 and the second piston 145 are configured to be driven with a phase difference of approximately 180 degrees in terms of crank angle.
  • the first striker 153 and the second striker 155 perform linear movements that face each other. Therefore, when one, for example, the first strike force 153 linearly moves to the side hitting the hammer bit 163 (front), the other, for example, the second striker 155 goes straight to the side away from the hammer bit 163 (rear). In operation, it functions as a counterweight. As a result, the vibration in the long axis direction of the hammer bit that occurs during the carpentry work is reasonably reduced, which is effective in reducing the vibration of the electric hammer 101.
  • the electric hammer 101 according to the second embodiment is a two-bit type using the first hammer bit 173 and the second hammer bit 175 as the tip tool members, and is the same as that described above except for the configuration related thereto.
  • the configuration is the same as that of the first embodiment. Therefore, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.
  • the first hammer bit 173 corresponds to the “first tool bit” in the present invention
  • the second hammer bit 175 corresponds to the “second tool bit” in the present invention.
  • FIG. 4 shows the overall configuration of the electric hammer 101
  • FIG. 5 shows the configuration of the main part.
  • the tool holder 171 of the second embodiment has two cylindrical holes for attaching the first hammer bit 173 and the second hammer bit 175, and the tip of the gear housing 107. Mounted on the side (front end side) in a state where movement in the long axis direction and circumferential direction of the hammer bit is restricted. The first hammer bit 173 and the second hammer bit 175 are held by the tool holder 171 in a state where relative movement in the major axis direction is allowed.
  • the first striking element 117 is slidable in the tool holder 171 and the first striker 153 as a first striking element that linearly moves in the first bore 151a of the cylinder 151 in the longitudinal direction of the hammer bit. Arranged to transmit the kinetic energy of the first striker 153 to the first hammer bit 173. It is mainly composed of a first impact bolt 177 as a meson. The first striker 153 is driven through the air panel of the first air chamber 151c of the cylinder 151 as the first piston 133 slides, and collides (hits) with the first impact bolt 177. The striking force is transmitted to the first hammer bit 173 held by the tool holder 171.
  • the first striking element 117 corresponds to the “first striking mechanism” in the present invention.
  • the second striking element 119 is slidable in the tool holder 171 and a second striker 155 as a second striking element that linearly moves in the second bore 151b of the cylinder 151 in the longitudinal direction of the hammer bit.
  • the second impact bolt 179 as a second meson that is arranged and transmits the kinetic energy of the second striker 155 to the second hammer bit 175 is mainly configured.
  • the second striker 155 is driven through the air panel of the second air chamber 151d of the cylinder 151 accompanying the sliding movement of the second piston 145 and collides (hits) with the second impact bolt 179.
  • the striking force is transmitted to the second hammer bit 175 held by the tool holder 171.
  • the second striking element 119 corresponds to the “second striking mechanism” in the present invention.
  • the first crank mechanism 113 that drives the first striking element 117 and the second crank mechanism 115 that drives the second striking element 119 are configured in the same manner as in the first embodiment described above. Therefore, when the drive motor 111 is energized, the first striking element 117 is driven by the first crank mechanism 113, and the second striking element 119 is driven by the second crank mechanism 115. For this reason, the first hammer bit 173 and the second hammer bit 175 perform one hitting operation each time the crank rotates. That is, the total number of hitting operations by the first hammer bit 173 and the second hammer bit 175 is performed twice in one rotation of the crank, and work efficiency can be improved as in the first embodiment.
  • the rotational speed of the driving motor 111 and the first and second driving motors 111 are driven.
  • the driving speed of the crank mechanisms 11 3, 115 and the first and second striking elements 117, 119 can be reduced, so that the sliding parts such as sliding members or O-rings can be moved without reducing the working efficiency. Wear can be reduced and durability can be improved.
  • the first piston 133 of the first crank mechanism 113 and the second piston 145 of the second crank mechanism 115 are configured to linearly move in the cylinder 151 with a phase difference of 180 degrees in terms of crank angle. Yes.
  • the vibration in the long axis direction of the hammer bit that occurs during the machining operation can be rationally reduced, and this is effective in reducing the vibration of the electric hammer 101.
  • the construction work is performed using the first and second two hammer bits 173 and 175, so that a wide range is simultaneously checked as compared with the case of one. be able to.
  • crank mechanisms 113 and 115 are employed as means for converting the rotational output of the drive motor 111 into the linear motion of the pistons 133 and 145.
  • the present invention is not limited to this, and for example, the drive motor 111 After the rotating motion of the rotating body rotated by is converted into the swinging motion of the swinging member, the swinging motion of this swinging member is converted to the linear motion of the pistons 133, 145 or rotated by the drive motor 111.
  • a mechanism that converts the pistons 133 and 145 into linear motion using a swash plate may be used.
  • the case where the two crank mechanisms 113 and 115 and the two striking elements 117 and 119 are provided has been described. However, these may be further added.
  • the present embodiment is not limited to the force described with the electric hammer 101 as an example of a striking tool, and the umbilits 163, 173, and 175 are not limited to the striking motion in the long axis direction. It can be applied to a hammer drill that performs rotational movement.
  • FIG. 1 is a side sectional view showing an overall configuration of an electric hammer according to a first embodiment of the present invention.
  • FIG. 2 is a side sectional view showing a main part of the electric hammer.
  • FIG. 3 is a longitudinal sectional view based on the line AA in FIG.
  • FIG. 4 is a side sectional view showing an overall configuration of an electric hammer according to a second embodiment of the present invention.
  • FIG. 5 is a side sectional view showing a main part of the electric hammer.
  • FIG. 6 is a cross-sectional view based on the line BB in FIG.
  • FIG. 7 is a cross-sectional view based on the line CC in FIG.

Landscapes

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

Abstract

La présente invention concerne un outil à impact (101) qui comprend un moteur (111), un premier mécanisme de conversion de mouvement (113) pour convertir la sortie rotative du moteur (111) en mouvement linéaire, un premier mécanisme à impact (117) entraîné par le premier mécanisme de conversion de mouvement (113) pour réaliser des mouvements linéaires, un second mécanisme de conversion de mouvement (115) pour convertir la sortie rotative du moteur (111) en mouvement linéaire, un second mécanisme à impact (119) entraîné par le second mécanisme de conversion de mouvement (115) pour réaliser des mouvements linéaires, et un élément d'outil d'extrémité (163) forcé par les premier et second mécanismes à impact (117, 119) à réaliser des actions d'impacts alternés. Avec ces impacts alternés par les premier et second mécanismes à impact (117, 119), le nombre d'impacts de l'élément d'outil d'extrémité (163) par temps unitaire est augmenté, et le premier mécanisme à impact (117) et le second mécanisme à impact (119) fonctionnent en alternance en tant que contrepoids.
PCT/JP2007/051415 2006-01-31 2007-01-29 Outil a impact WO2007088821A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07707646.1A EP1980371B1 (fr) 2006-01-31 2007-01-29 Outil à impact

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006-022446 2006-01-31
JP2006022446A JP2007203388A (ja) 2006-01-31 2006-01-31 打撃工具

Publications (1)

Publication Number Publication Date
WO2007088821A1 true WO2007088821A1 (fr) 2007-08-09

Family

ID=38327394

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/051415 WO2007088821A1 (fr) 2006-01-31 2007-01-29 Outil a impact

Country Status (3)

Country Link
EP (1) EP1980371B1 (fr)
JP (1) JP2007203388A (fr)
WO (1) WO2007088821A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2127820A1 (fr) * 2008-05-26 2009-12-02 Max Co., Ltd. Outil d'enfoncement

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITPN20110067A1 (it) * 2011-10-11 2013-04-12 Giovanni Zago Apparecchiatura di perforazione-demolizione pluri-cilindrica ad azione elettro-pneumatica
DE102015203487A1 (de) * 2015-02-26 2016-09-01 Ecoroll Ag Werkzeugtechnik Festhammervorrichtung zum Beeinflussen von Werkstücken und zugehöriges Verfahren
US20230027574A1 (en) * 2021-07-26 2023-01-26 Makita Corporation Striking tool

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS308287Y1 (fr) * 1953-01-17 1955-06-15
JPS4963601A (fr) * 1972-10-21 1974-06-20
JPS516583U (fr) * 1974-07-02 1976-01-17
JPS6033636B2 (ja) * 1979-07-04 1985-08-03 日立工機株式会社 電気ハンマ

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE830332C (de) * 1950-02-11 1952-02-04 Moenninghoff Maschf Druckluftbetriebener Abbauhammer
DE967868C (de) * 1955-03-31 1957-12-19 Robel & Co G Schlaggeraet
JPS6033636A (ja) * 1983-08-04 1985-02-21 Nec Corp 推論装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS308287Y1 (fr) * 1953-01-17 1955-06-15
JPS4963601A (fr) * 1972-10-21 1974-06-20
JPS516583U (fr) * 1974-07-02 1976-01-17
JPS6033636B2 (ja) * 1979-07-04 1985-08-03 日立工機株式会社 電気ハンマ

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2127820A1 (fr) * 2008-05-26 2009-12-02 Max Co., Ltd. Outil d'enfoncement
US7921933B2 (en) 2008-05-26 2011-04-12 Max Co., Ltd. Impact driving tool

Also Published As

Publication number Publication date
EP1980371A1 (fr) 2008-10-15
JP2007203388A (ja) 2007-08-16
EP1980371B1 (fr) 2014-03-19
EP1980371A4 (fr) 2010-06-16

Similar Documents

Publication Publication Date Title
JP4593387B2 (ja) 電動工具
JP4195818B2 (ja) 電動ハンマ
JP4863942B2 (ja) 打撃工具
RU2510326C2 (ru) Ударный инструмент
RU2434733C2 (ru) Ручная машина, прежде всего перфоратор и/или отбойный молоток
JP6441588B2 (ja) 打撃工具
US8016047B2 (en) Electrical power tool with anti-vibration mechanisms of different types
JP4793755B2 (ja) 電動工具
EP2428323B1 (fr) Outil à impact
WO2013111460A1 (fr) Outil de frappe
WO2009154171A1 (fr) Outil de travail
WO2014034862A1 (fr) Outil à percussion
RU2009128742A (ru) Электрическая ручная машина
US6739405B2 (en) Hammer
WO2007088821A1 (fr) Outil a impact
CN107206584B (zh) 作业工具
JP2007175836A (ja) 打撃工具
WO2012144568A1 (fr) Outil à percussion
JP4805288B2 (ja) 電動ハンマ
WO2013061835A1 (fr) Outil de frappe
JP5058726B2 (ja) 打撃工具
JP5913009B2 (ja) 打撃工具
JP7412135B2 (ja) 打撃工具
JP5913010B2 (ja) 打撃工具
JP2007175837A (ja) 打撃工具

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application
NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2007707646

Country of ref document: EP