WO2007061101A1 - Impact type working tool - Google Patents

Impact type working tool Download PDF

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Publication number
WO2007061101A1
WO2007061101A1 PCT/JP2006/323624 JP2006323624W WO2007061101A1 WO 2007061101 A1 WO2007061101 A1 WO 2007061101A1 JP 2006323624 W JP2006323624 W JP 2006323624W WO 2007061101 A1 WO2007061101 A1 WO 2007061101A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
tool holder
tool
rotational torque
impact
Prior art date
Application number
PCT/JP2006/323624
Other languages
French (fr)
Japanese (ja)
Inventor
Masanori Furusawa
Yoshihiro Kasuya
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 DE112006003186T priority Critical patent/DE112006003186T5/en
Publication of WO2007061101A1 publication Critical patent/WO2007061101A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—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
    • B25D16/003—Clutches specially adapted therefor
    • 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
    • B25D17/084—Rotating chucks or sockets
    • B25D17/088—Rotating chucks or sockets with radial movable locking elements co-operating with bit shafts specially adapted therefor
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • 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
    • B25D2217/003—Details relating to chucks with radially movable locking elements
    • B25D2217/0038—Locking members of special shape
    • B25D2217/0042—Ball-shaped locking members
    • 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
    • B25D2250/065—Details regarding assembling of the tool
    • 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
    • B25D2250/165—Overload clutches, torque limiters
    • 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
    • B25D2250/191—Ram catchers for stopping the ram when entering idling mode
    • 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
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the present invention relates to an impact-type work tool in which a tip tool performs a predetermined machining operation through a linear striking operation in the long axis direction and a rotation operation around the long axis direction.
  • German Patent No. 4009762 discloses a hammer drill.
  • a cylinder in which a piston and a striker are slidably disposed and a tool holder in which an impact bolt is slidably disposed and a hammer bit serving as a tip tool is divided. It is revered as a configuration.
  • the rotational movement of the cylinder driven by the motor is transmitted to the tool holder via a torque limiter.
  • a rotational torque exceeding a predetermined maximum value is applied between the cylinder and the tool holder, the torque is The limiter restricts the cylinder force and torque transmission to the tool holder.
  • An object of the present invention is to provide a technique that makes it easy to remove a tool holder from an impact type work tool in view of being applied.
  • An impact type work tool having a limiter, a tool holder internal mechanism part, and a rear load receiving part is configured.
  • the tip tool has a linear striking motion in the major axis direction,
  • a predetermined processing operation is performed through a rotation operation around the major axis direction.
  • the hitting operation and the rotating operation of the tip tool preferably include not only the mode in which they are performed simultaneously, but also the mode in which only the hitting operation is performed alone and the mode in which only the rotating operation is performed alone! .
  • the drive mechanism unit drives the tip tool to perform a striking operation.
  • the drive mechanism section includes a piston as a driving element that linearly moves in the cylinder, and a striker as a striking element that moves linearly through an air panel in accordance with the linear movement of the piston. Corresponds to this.
  • the cylinder accommodates the drive mechanism and rotates to rotate the tip tool.
  • the tool holder is configured separately from the cylinder and is connected to the long-axis tip region of the cylinder on the same axis.
  • the tool holder holds the tip tool in a state in which the relative movement in the circumferential direction is restricted while allowing the relative movement of the tip tool in the long axis direction.
  • the cylinder side rotational torque transmitting member is provided on the outer periphery of the cylinder so as to be relatively movable in the long axis direction of the cylinder and not relatively rotatable around the long axis direction of the cylinder.
  • the panel member is disposed on the outer periphery of the cylinder, and exerts an urging force so as to press the cylinder side rotational torque transmission member toward the tool holder.
  • the tool holder side rotational torque transmission member transmits the rotational torque from the cylinder to the tool holder by engaging with the cylinder side rotational torque transmission member pressed toward the tool holder by the panel member.
  • the torque limiter 1 includes a cylinder side rotational torque transmission member, a panel member, and a tool holder side rotational torque transmission member as constituent elements.
  • the cylinder force is against the urging force of the panel member, and the relationship between the cylinder side rotational torque transmission member and the tool holder side rotational torque transmission member. This cancels the transmission of the rotational force from the cylinder to the tool holder.
  • Tool holder An internal mechanism part is accommodated in a tool holder.
  • the internal structure of the tool holder typically corresponds to the impact bolt force as an intermediate that transmits the linear motion of the striker to the tip tool.
  • the rear load receiving portion is disposed in the cylinder, and receives a load acting in the direction opposite to the hammering operation of the tip tool in the cylinder direction from the tool holder internal mechanism portion.
  • the impact type work tool according to the present invention has, as a characteristic configuration, the tool holder, together with the housed holder internal mechanism, in the direction of the impact operation of the tip tool, the cylinder force is removed. It can be made freely. Further, the cylinder has a restricting portion that restricts the urging force of the panel member from acting forward beyond a predetermined position on the outer periphery of the cylinder. When the tool holder is removed from the cylinder, the panel member can be removed. It is configured to avoid interference.
  • the “regulator” in the present invention typically means a mode for restricting the tool holder side rotational torque transmitting member from moving to the tool holder side beyond a predetermined position on the cylinder outer periphery, or the cylinder side rotational torque.
  • the shift is preferably included.
  • the tool holder that accommodates the tool holder internal mechanism portion can also remove the cylinder force together with the tool holder internal mechanism.
  • the panel member's urging force acts forwardly beyond a predetermined position on the outer periphery of the cylinder because of the configuration that regulates the influence of the panel member. Cylinder force can be removed easily without receiving the tool holder.
  • FIG. 1 is a side cross-sectional view showing the overall configuration of the electric grease drill according to the present embodiment.
  • the hammer drill 101 according to the present embodiment is generally viewed as having a main body 103 that forms an outline of the hammer drill 101 and a hollow shape in a tip region (left side in the drawing) of the main body 103.
  • Nonmabit 119 which is detachably attached via the tool holder 137
  • the main body 103 is mainly composed of a handgrip 109 held by an operator connected to the opposite side of the hammer bit 119.
  • the non-mabit 119 is held by the tool holder 137 so that the linear movement in the major axis direction is possible and the relative rotation in the circumferential direction is restricted.
  • the hammer bit 119 corresponds to the “tip tool” in the present invention.
  • the hammer bit 119 side is the front and the handgrip 109 side is the rear.
  • the main body 103 includes a motor housing 105 that houses the drive motor 111, and a gear housing 107 that houses the motion changing structure 113, the striking element 115, and the power transmission mechanism 117.
  • the rotational output of the drive motor 111 is appropriately converted into linear motion by the motion mechanism 113 and then transmitted to the striking element 115, and the hammer bit 119 passes through the striking element 115 in the long axis direction (left-right direction in FIG. 1). Generates an impact force on. Further, the rotational output of the drive motor 111 is appropriately decelerated by the power transmission mechanism 117 and then transmitted to the non-bit bit 119, and the hammer bit 119 is rotated in the circumferential direction.
  • the hand grip 109 is formed in a substantially U shape in a side view, and the lower end side is connected to the lower end of the rear end of the motor housing 105, and the upper end side is connected to the rear end of the gear housing 107.
  • the drive motor 111 is energized and driven by a pulling operation of a trigger 109a disposed on the grip 109.
  • the motion conversion mechanism 113 is mainly configured by a gear 123 that is rotationally driven in a horizontal plane by a drive motor 111, a crank plate 125, a crank arm 127, and a cylindrical piston 129 as a driver, and the crank plate 125
  • the crank arm 127 and the cylindrical piston 129 constitute a crank mechanism.
  • the cylindrical piston 129 is slidably disposed in the cylinder 141, and performs a linear motion along the cylinder 141 when the drive motor 111 is energized.
  • the striking element 115 includes a striker 143 as a striker slidably disposed on the bore inner wall of the cylindrical piston 129 and a tool holder 137 slidably disposed. It is composed mainly of impact bolts 145 as mesons that transmit to the hammer bit 119.
  • the striker 143 is driven via the air panel of the air chamber 129a of the cylindrical piston 129 accompanying the sliding movement of the cylindrical piston 129, and the tool holder 13
  • the impact bolt 145 is slidably disposed on the impact bolt 145 (striking), and the impact force is transmitted to the hammer bit 119 via the impact bolt 145.
  • the cylindrical piston 129 and the strike force 143 correspond to the “drive mechanism” in the present invention.
  • FIG. 2 is a sectional view showing an enlarged state of the main part of the hammer drill 101.
  • the power transmission mechanism 117 is engaged with a small bevel gear 134 that is driven to rotate in a horizontal plane by a drive motor 111 via a gear (not shown), and engages with the small bevel gear 134 in a vertical plane.
  • a slide sleeve 147 that rotates in meshing engagement with the large bevel gear 135. Then, the rotation output of the slide sleeve 147 is transmitted from the cylinder 141 rotating together with the slide sleeve 147 to the tool holder 137 via the torque limiter 161. That is, the tool holder 137 is formed separately from the cylinder 141 and is concentrically disposed in the front end region of the cylinder 141.
  • the torque limiter 161 is disposed concentrically outside the cylinder 141. As shown in the exploded views of FIGS. 2 and 3, the torque limiter 161 brings the drive side ring 163 and the driven side ring 165, which are arranged opposite to each other in the axial direction, and the rings 163 and 165 close to each other. It is mainly composed of an urging panel 167 (compression coil spring) that urges in the direction in which it moves.
  • the drive side ring 163 corresponds to the “cylinder side rotational torque transmission member” in the present invention
  • the driven side ring 165 corresponds to the “tool holder side rotational torque transmission member” in the present invention. As shown in FIG.
  • the drive-side ring 163 has a plurality of protrusions 163b protruding in the inner diameter direction on the inner peripheral surface thereof, and these protrusions 163b are formed in the axial direction formed on the outer peripheral surface of the cylinder 141. And are engaged with and engaged with a plurality of grooves 141b extending in the direction. Accordingly, the drive side ring 163 is configured to rotate integrally in the circumferential direction in a state where relative movement in the axial direction is allowed with respect to the cylinder 141.
  • the driven-side ring 165 is disposed on the outer peripheral surface of the cylinder 141 so as to be relatively rotatable, and the circlip 157 provided on the outer periphery of the cylinder 141 so as to be immovable in the major axis direction (the tool holder in the axial direction). 137 side) is restricted.
  • the circlip 157 corresponds to the “regulator” in the present invention.
  • the driving side ring 163 and the driven side ring 165 are respectively provided on axially facing end faces.
  • the teeth 163a and 165a are provided, and these teeth 163a and 165a are engaged with each other.
  • power can be transmitted from the drive side ring 163 to the driven side ring 165.
  • the axial end surface on the opposite side of the driving side ring 163 is opposed to the axial rear end surface of the tool holder 136.
  • the driven-side ring 165 and the tool holder 137 have teeth 165b and 137c on the axial end surfaces facing each other, and these teeth 165b and 137c are meshed and engaged with each other.
  • the biasing panel 167 is disposed behind the driving side ring 163 and is interposed between the spring receiving ring 168 fixedly fixed to the cylinder 141 and the driving side ring 163, and the driving side ring 163 Is biased in the direction approaching the driven ring 165.
  • the urging force of the urging panel 167 acts to press the driven ring 165 forward, which is the tool holder 137 side, but in this embodiment, as described above, the urging force is applied by the circlip 157.
  • the side ring 165 is restricted from moving forward beyond a predetermined position, whereby the biasing force of the biasing panel 167 does not act on the tool holder 137.
  • the rotational output of the cylinder 141 is transmitted to the tool holder 137 via the drive side ring 163 and the driven side ring 165 of the torque limiter 161.
  • the teeth 163a of the drive side ring 163 and the teeth 165a of the driven side ring 165 are engaged with each other via an engagement surface inclined at a predetermined angle in the axial direction in the circumferential direction.
  • the tool holder 137 includes a front holder part 137a and a rear holder part 137b!
  • the front holder portion 137a holds the hammer bit 119 and accommodates the impact bolt 145.
  • the rear holder portion 137b engages and engages with the teeth 165a of the driven side ring 165 of the torque limiter 161.
  • Have The front holder part 137a and the rear holder part 137b are fitted so that the front end part of the rear holder part 137b covers the rear end part of the front holder part 137a, and a predetermined amount relative to each other in the major axis direction. Circumference with movement allowed Are connected via a connecting ring 138 so as to rotate together.
  • the rear holder portion 137a is loosely fitted on the rear end side in the axial direction so as to be separable from the outer peripheral portion of the front end of the cylinder 141 in the forward direction (no, umbit 119 side).
  • the tool holder 137 is detachable from the cylinder 141, and in the assembled state, the tool holder 137 is moved forward by the stop ring 139 fixedly attached to the gear housing 107 (on the side of the nombit 119). ) Is restricted.
  • the meshing engagement between the teeth 165a of the driven ring 165 and the teeth 137c of the tool holder 137 is reliably maintained.
  • the impact bolt 145 accommodated in the tool holder 137 includes, in the axial direction, a large-diameter portion 145a that closely fits into the inner peripheral surface of the tool hole 137 and the inner peripheral surface of the tool holder 137.
  • a stepped structure having a small-diameter portion 145b having a predetermined large space therebetween, and a positioning member 151 is disposed on the outer peripheral side of the small-diameter portion 145b.
  • the hammer drill 101 performs a ware work in a state in which the user applies a forward pressing force to the main body 103 and presses the hammer bit 119 against the force-receiving material.
  • the impact bolt 145 is pushed backward together with the hammer bit 119 (to the cylindrical piston 129 side).
  • the impact bolt 145 is subjected to a reaction force when the hammer bit 119 is pressed against the workpiece during the machining operation, and the rearward movement of the impact bolt 145 by this reaction force causes the positioning member 151 to move.
  • the receiving ring 153 corresponds to the “rear load receiving portion” in the present invention
  • the impact bolt 137 and the positioning member 151 etc. accommodated in the tool holder 137 correspond to the “tool holder internal mechanism portion” in the present invention. . Therefore, when the tool holder 137 is removed from the cylinder 141, it is removed together with these “tool holder internal mechanism portions”.
  • the gear housing 107 is composed of a front housing part 107a and a rear housing part 107b which are divided into two in the axial direction.
  • the front housing portion 107a and the rear housing portion 107b are separated from each other by, for example, screws (not shown for convenience) in a butt-like joining region, and separated by removing the screws.
  • a stopper 139 for restricting the forward movement of the tool holder 137 is provided in the front housing portion 107a.
  • the hammer drill 101 configured as described above is used for pulling the trigger 109a by the user. Therefore, when the drive motor 111 is energized, the cylindrical piston 129 is slid linearly along the cylinder 141 via the motion conversion mechanism 113 mainly composed of a crank mechanism, and the associated cylindrical piston is moved accordingly.
  • the striker 143 moves linearly in the cylinder 141 by the pressure change of the air in the 129 air chambers 129a, that is, by the action of the air vane. When the striker 143 collides with the impact bolt 145, the kinetic energy is transmitted to the hammer bit 119.
  • the rotational output of the drive motor 111 is transmitted to the cylinder 141 via the power transmission mechanism 117.
  • the cylinder 141 is driven to rotate in the vertical plane
  • the tool holder 137 is driven to rotate from the cylinder 141 via the drive side ring 163 and the driven side ring 165 of the torque limiter 161.
  • the hammerbit 119 held in is rotated into a body shape.
  • the hammer bit 119 performs the hammering operation in the axial direction and the drilling operation in the circumferential direction, and drills the workpiece (concrete).
  • the hammer drill 101 is not limited to the hammer drill mode in which the hammer bit 119 performs the hammer operation and the circumferential drill operation, and the hammer bit 119 performs only the drill operation. It is possible to switch to working mode in drill mode. The operation mode is switched by sliding the slide sleeve 147 in the axial direction to release the tooth meshing engagement with the large bevel gear 135.
  • the so-called vario lock that restricts the free rotation of the tool holder 137 and the hammer bit 119, that is, fixes the hammer bit 119 in a predetermined direction (circumferential direction). I do.
  • the tooth lock 147a provided on the slide sleeve 147 is meshed and engaged with the tooth 149a of the lock ring 149 provided in a fixed state in the circumferential direction with respect to the gear housing 107. It is configured to do in. That is, the slide sleeve 147 is a single member but has a power transmission function and a vario-lock function at the time of mode switching. Note that the mode switching mechanism for sliding the slide sleeve 147 in the axial direction is not directly related to the present invention, and thus the description thereof is omitted.
  • the tool holder housed in the tool holder 137 In order to repair the impact bolt 145 and positioning member 151 as components constituting the internal mechanism, or to replace consumable parts such as O-rings 145c and 152 used in the impact bolt 145 and the positioning member 151, they are used in the main body 103. May be removed from.
  • the gear housing 107 is separated into a front housing part 107a and a rear housing part 107b. This separated state is shown in FIG.
  • the tool holder 137 is accompanied by the impact bolt 145 and the positioning member 1 51 accommodated in the tool holder 137. At the same time, they are moved away from the driven ring 165 of the cylinder 141 and the torque limiter 161 and removed.
  • the driven-side ring 165 of the torque limiter 161 does not move forward beyond a predetermined position with respect to the cylinder 141, that is, in the removal direction of the tool holder 137. Therefore, the urging force of the urging panel 167 does not act on the tool holder 137. That is, with respect to the connection between the tool holder 137 and the torque limiter 161, the torque limiter 161 and the tool holder 137 are engaged with each other through the teeth 165a and 137c in the circumferential direction, and the connection in the axial direction. It becomes a mutually independent form.
  • the tool holder 137 that does not receive the interference of the biasing panel 167 can be easily and easily removed from the cylinder 141.
  • this also applies to the repair work related to the constituent members of the internal structure of the tool holder or the assembly work performed after the replacement work.
  • the torque limiter 161 is disposed outside the cylinder 141, and the rotational force of the cylinder 141 is transmitted to the drive side ring 163 of the torque limiter 161, that is, the inner force is transmitted to the outside. It is assumed to be configured. As a result, power transmission to the tool holder 137 disposed so as to cover the outer surface end of the cylinder 141 can be performed structurally without difficulty, and the assembly of the torque limiter 161 to the cylinder 141 and the tool holder 137 can be assembled easily.
  • the impact bolt 145 and the positioning member 151 housed in the tool holder 137 are moved forward and removed. For this reason, during processing It is possible to remove the hammer bit 119 without receiving the interference of the receiving ring 153 that receives the pressing reaction force against the force-bearing material.
  • FIG. 1 is a side sectional view showing an overall configuration of a hammer drill according to an embodiment of the present invention.
  • FIG. 2 is a side view showing the main part of the hammer drill.
  • FIG. 3 is an exploded side view of the torque limiter.
  • FIG. 4 is a front view showing a drive side ring of the torque limiter.
  • FIG. 5 is a side sectional view showing a state where the gear housing is separated into a front housing part and a rear housing part.

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

Abstract

Provided is an impact type working tool comprising a tip tool (119), drive mechanism portions (129, 143) for causing the tip tool to perform impacting actions, a cylinder (141) for rotating actions, a hollow tool holder (137), a torque limiter (161), tool holder internal mechanism portions (145, 151), and a backward load receiving portion (153). The tool holder (137) can be removed, together with the tool holder internal mechanism portions (145, 151) housed therein, in the impacting action direction of the tip tool (119) from the cylinder (141). This cylinder (141) is constituted to have a regulation portion (157) for regulating the biasing action of a spring member (167) of the torque limiter (161), not over a predetermined position on the outer circumference of that cylinder in the direction of the impacting action of the tip tool, so that the spring member (167) may be avoided from interfering, when the tool holder (137) is removed from the cylinder (141), with the removing action.

Description

明 細 書  Specification
衝撃式作業工具  Impact type work tool
技術分野  Technical field
[0001] 本発明は、先端工具が長軸方向への直線状の打撃動作、および当該長軸方向周 りの回転動作を介して所定の加工作業を行う衝撃式作業工具に関する。  The present invention relates to an impact-type work tool in which a tip tool performs a predetermined machining operation through a linear striking operation in the long axis direction and a rotation operation around the long axis direction.
背景技術  Background art
[0002] 独国特許第 4009762号公開公報には、ハンマドリルが開示されている。特許文献 1に記載のハンマドリルでは、ピストンおよびストライカが摺動自在に配置されるシリン ダと、インパクトボルトが摺動自在に配置されるとともに、先端工具としてのハンマビッ トを保持するツールホルダとを分割した構成として ヽる。そしてモータによって回転駆 動されるシリンダの回転動作は、トルクリミッターを介してツールホルダに伝達される 構成とされ、シリンダとツールホルダ間に予め定めた最大値以上の回転トルクが作用 したときには、トルクリミッタ一によりシリンダ力もツールホルダへのトルク伝達が規制さ れる。  [0002] German Patent No. 4009762 discloses a hammer drill. In the hammer drill described in Patent Document 1, a cylinder in which a piston and a striker are slidably disposed and a tool holder in which an impact bolt is slidably disposed and a hammer bit serving as a tip tool is divided. It is revered as a configuration. The rotational movement of the cylinder driven by the motor is transmitted to the tool holder via a torque limiter. When a rotational torque exceeding a predetermined maximum value is applied between the cylinder and the tool holder, the torque is The limiter restricts the cylinder force and torque transmission to the tool holder.
[0003] 上記ハンマドリルでは、トルクリミッターとツールホルダとは、その連結に関して互い に独立した形態となっておらず、ツールホルダをシリンダ力 の取り外す作業が行!ヽ にくい。  [0003] In the hammer drill, the torque limiter and the tool holder are not independent from each other in terms of their connection, and it is difficult to remove the tool holder from the cylinder force.
発明の開示  Disclosure of the invention
発明が解決しょうとする課題  Problems to be solved by the invention
[0004] 本発明は、力かる点に鑑み、衝撃式作業工具においてツールホルダを取り外しや すくする技術を提供することを目的とする。 An object of the present invention is to provide a technique that makes it easy to remove a tool holder from an impact type work tool in view of being applied.
課題を解決するための手段  Means for solving the problem
[0005] 上記課題を達成するため、各請求項に記載の発明が構成される。 [0005] In order to achieve the above object, the invention described in each claim is configured.
請求項 1に記載の発明によれば、先端工具と、駆動機構部と、シリンダと、ツールホ ルダと、シリンダ側回転トルク伝達部材と、パネ部材と、ツールホルダ側回転トルク伝 達部材と、トルクリミッターと、ツールホルダ内部機構部と、後方荷重受部とを有する 衝撃式作業工具が構成される。先端工具は、長軸方向への直線状の打撃動作、お よび当該長軸方向周りの回転動作を介して所定の加工作業を行う。なお先端工具の 打撃動作および回転動作は、それらが同時に行われる態様はもとより、打撃動作の みが単独で行われる態様、回転動作のみが単独で行われる態様の!/ヽずれも好適に 包含する。駆動機構部は、先端工具を打撃動作させるベく駆動する。駆動機構部と しては、典型的には、シリンダ内を直線状に動作する駆動子としてのピストン、および 当該ピストンの直線動作に伴い空気パネを介して直線状に動作する打撃子としての ストライカがこれに該当する。 According to the invention described in claim 1, the tip tool, the drive mechanism, the cylinder, the tool holder, the cylinder side rotational torque transmission member, the panel member, the tool holder side rotational torque transmission member, and the torque An impact type work tool having a limiter, a tool holder internal mechanism part, and a rear load receiving part is configured. The tip tool has a linear striking motion in the major axis direction, In addition, a predetermined processing operation is performed through a rotation operation around the major axis direction. In addition, the hitting operation and the rotating operation of the tip tool preferably include not only the mode in which they are performed simultaneously, but also the mode in which only the hitting operation is performed alone and the mode in which only the rotating operation is performed alone! . The drive mechanism unit drives the tip tool to perform a striking operation. Typically, the drive mechanism section includes a piston as a driving element that linearly moves in the cylinder, and a striker as a striking element that moves linearly through an air panel in accordance with the linear movement of the piston. Corresponds to this.
[0006] シリンダは、駆動機構部を収容するとともに、先端工具を回転駆動するべく回転動 作する。ツールホルダは、シリンダとは別体に構成されるとともに、当該シリンダの長 軸先端領域に同一軸線上にて連接される。またツールホルダは、先端工具の長軸方 向の相対移動を許容しつつ周方向の相対移動を規制した状態で当該先端工具を保 持する。シリンダ側回転トルク伝達部材は、シリンダの外周上に、当該シリンダの長軸 方向に相対移動可能かつ当該シリンダの長軸方向周りに相対回転不能に設けられ る。パネ部材は、シリンダの外周上に配置され、シリンダ側回転トルク伝達部材をツー ルホルダ側へと押圧するように付勢力を作用させる。ツールホルダ側回転トルク伝達 部材は、パネ部材によってツールホルダ側へと押圧されたシリンダ側回転トルク伝達 部材と係合することでシリンダからの回転トルクをツールホルダへ伝達する。  [0006] The cylinder accommodates the drive mechanism and rotates to rotate the tip tool. The tool holder is configured separately from the cylinder and is connected to the long-axis tip region of the cylinder on the same axis. The tool holder holds the tip tool in a state in which the relative movement in the circumferential direction is restricted while allowing the relative movement of the tip tool in the long axis direction. The cylinder side rotational torque transmitting member is provided on the outer periphery of the cylinder so as to be relatively movable in the long axis direction of the cylinder and not relatively rotatable around the long axis direction of the cylinder. The panel member is disposed on the outer periphery of the cylinder, and exerts an urging force so as to press the cylinder side rotational torque transmission member toward the tool holder. The tool holder side rotational torque transmission member transmits the rotational torque from the cylinder to the tool holder by engaging with the cylinder side rotational torque transmission member pressed toward the tool holder by the panel member.
[0007] トルクリミッタ一は、シリンダ側回転トルク伝達部材、パネ部材およびツールホルダ側 回転トルク伝達部材を構成要素とする。そしてシリンダ力もツールホルダへと予め設 定された最大値以上の回転トルクが作用した場合にパネ部材の付勢力に抗してシリ ンダ側回転トルク伝達部材どツールホルダ側回転トルク伝達部材との係合を解除し、 これによつてシリンダからツールホルダへの回転力の伝達を解除する。ツールホルダ 内部機構部は、ツールホルダ内に収容される。なおツールホルダ内部機構部は、典 型的には、打撃子の直線動作を先端工具に伝達する中間子としてのインパクトボルト 力 れに該当する。後方荷重受部は、シリンダ内に配置され、ツールホルダ内部機構 部からシリンダ方向へと先端工具の打撃動作と反対方向に作用する荷重を受ける。  [0007] The torque limiter 1 includes a cylinder side rotational torque transmission member, a panel member, and a tool holder side rotational torque transmission member as constituent elements. When the rotational force exceeding the preset maximum value is applied to the tool holder, the cylinder force is against the urging force of the panel member, and the relationship between the cylinder side rotational torque transmission member and the tool holder side rotational torque transmission member. This cancels the transmission of the rotational force from the cylinder to the tool holder. Tool holder An internal mechanism part is accommodated in a tool holder. The internal structure of the tool holder typically corresponds to the impact bolt force as an intermediate that transmits the linear motion of the striker to the tip tool. The rear load receiving portion is disposed in the cylinder, and receives a load acting in the direction opposite to the hammering operation of the tip tool in the cylinder direction from the tool holder internal mechanism portion.
[0008] 本発明に係る衝撃式作業工具は、特徴的構成として、ツールホルダは、収容したッ ールホルダ内部機構部とともに、先端工具の打撃動作方向へと、シリンダ力 取り外 し自在とされる。さらにシリンダは、パネ部材の付勢力が当該シリンダ外周上の所定 位置以上に前方へと作用するのを規制する規制部を有し、ツールホルダがシリンダ から取り外される場合にパネ部材が当該取り外し作業に干渉することを回避するよう に構成されている。なお本発明における「規制部」とは、典型的には、ツールホルダ 側回転トルク伝達部材がシリンダ外周上の所定位置以上にツールホルダ側へと移動 するのを規制する態様、あるいはシリンダ側回転トルク伝達部材がシリンダ外周上の 所定位置以上にツールホルダ側回転トルク伝達部材へと移動するのを規制する態様 、更にはパネ部材が所定位置以上にシリンダ側回転トルク伝達部材へと移動するの を規制する態様の 、ずれをも好適に包含する。 [0008] The impact type work tool according to the present invention has, as a characteristic configuration, the tool holder, together with the housed holder internal mechanism, in the direction of the impact operation of the tip tool, the cylinder force is removed. It can be made freely. Further, the cylinder has a restricting portion that restricts the urging force of the panel member from acting forward beyond a predetermined position on the outer periphery of the cylinder. When the tool holder is removed from the cylinder, the panel member can be removed. It is configured to avoid interference. The “regulator” in the present invention typically means a mode for restricting the tool holder side rotational torque transmitting member from moving to the tool holder side beyond a predetermined position on the cylinder outer periphery, or the cylinder side rotational torque. A mode in which the transmission member is restricted from moving to a tool holder side rotational torque transmission member beyond a predetermined position on the cylinder outer periphery, and further a panel member is restricted from moving to a cylinder side rotational torque transmission member beyond a predetermined position. In this embodiment, the shift is preferably included.
ツールホルダ内部機構部を構成する構成部材としての、例えばインパクトボルト、あ るいは当該インパクトボルトとツールホルダの内壁面間に介在されるオーリング等に つき、修理あるいは交換が必要とされた場合、それら構成部材をツールホルダ力も取 り外すことになる。本発明によれば、ツールホルダ内部機構部を収容するツールホル ダを当該ツールホルダ内部機構とともにシリンダ力も取り外すことができる。そしてッ ールホルダの取り外しの際、パネ部材の付勢力が当該シリンダ外周上の所定位置以 上に前方へと作用するのを、シリンダに設けた規制部によって規制する構成のため、 パネ部材の影響を受けることなぐツールホルダをシリンダ力 容易に取り外すことが できる。  If repair or replacement is required for a component constituting the tool holder internal mechanism, such as an impact bolt or an O-ring interposed between the impact bolt and the inner wall surface of the tool holder, These components will also be removed from the tool holder force. According to the present invention, the tool holder that accommodates the tool holder internal mechanism portion can also remove the cylinder force together with the tool holder internal mechanism. When removing the tool holder, the panel member's urging force acts forwardly beyond a predetermined position on the outer periphery of the cylinder because of the configuration that regulates the influence of the panel member. Cylinder force can be removed easily without receiving the tool holder.
発明の効果  The invention's effect
[0009] 本発明によれば、衝撃式作業工具にぉ 、てツールホルダを取り外しやすくする技 術が提供されることとなった。  [0009] According to the present invention, there has been provided a technique that makes it easy to remove a tool holder from an impact-type work tool.
発明を実施するための最良の形態  BEST MODE FOR CARRYING OUT THE INVENTION
[0010] 以下、本発明の実施形態につき、図 1〜図 5を参照しつつ詳細に説明する。本実 施の形態は、衝撃式作業工具の一例として電動式のハンマドリルを用いて説明する 。図 1は本実施の形態に係る電動式ノヽンマドリルの全体構成を示す側断面図である 。図 1に示すように、本実施の形態に係るハンマドリル 101は、概括的に見て、ハンマ ドリル 101の外郭を形成する本体部 103と、当該本体部 103の先端領域（図示左側） に中空状のツールホルダ 137を介して着脱自在に取付けられたノヽンマビット 119と、 本体部 103のハンマビット 119の反対側に連接された作業者が握るハンドグリップ 10 9とを主体として構成されている。ノヽンマビット 119は、ツールホルダ 137によってその 長軸方向への相対的な直線動作が可能に、かつその周方向への相対的な回動が 規制された状態で保持される。ハンマビット 119は、本発明における「先端工具」に対 応する。なお説明の便宜上、ハンマビット 119側を前、ハンドグリップ 109側を後とい Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS. 1 to 5. This embodiment will be described using an electric hammer drill as an example of an impact-type work tool. FIG. 1 is a side cross-sectional view showing the overall configuration of the electric grease drill according to the present embodiment. As shown in FIG. 1, the hammer drill 101 according to the present embodiment is generally viewed as having a main body 103 that forms an outline of the hammer drill 101 and a hollow shape in a tip region (left side in the drawing) of the main body 103. Nonmabit 119, which is detachably attached via the tool holder 137, The main body 103 is mainly composed of a handgrip 109 held by an operator connected to the opposite side of the hammer bit 119. The non-mabit 119 is held by the tool holder 137 so that the linear movement in the major axis direction is possible and the relative rotation in the circumferential direction is restricted. The hammer bit 119 corresponds to the “tip tool” in the present invention. For convenience of explanation, the hammer bit 119 side is the front and the handgrip 109 side is the rear.
[0011] 本体部 103は、駆動モータ 111を収容したモータハウジング 105と、運動変 «構 113、打撃要素 115および動力伝達機構 117を収容したギアハウジング 107とによつ て構成されている。駆動モータ 111の回転出力は、運動変 構 113によって直線 運動に適宜変換された上で打撃要素 115に伝達され、当該打撃要素 115を介して ハンマビット 119の長軸方向（図 1における左右方向）への衝撃力を発生する。また 駆動モータ 111の回転出力は、動力伝達機構 117によって適宜減速された上でノヽン マビット 119に伝達され、当該ハンマビット 119が周方向に回転動作される。ハンドグ リップ 109は、側面視で概ねコの字形に形成されるとともに、下端側がモータハウジン グ 105の後端下部に連接され、上端側がギアハウジング 107の後端に連接されてい る。なお駆動モータ 111は、グリップ 109に配置されたトリガ 109aの引き操作によって 通電駆動される。 The main body 103 includes a motor housing 105 that houses the drive motor 111, and a gear housing 107 that houses the motion changing structure 113, the striking element 115, and the power transmission mechanism 117. The rotational output of the drive motor 111 is appropriately converted into linear motion by the motion mechanism 113 and then transmitted to the striking element 115, and the hammer bit 119 passes through the striking element 115 in the long axis direction (left-right direction in FIG. 1). Generates an impact force on. Further, the rotational output of the drive motor 111 is appropriately decelerated by the power transmission mechanism 117 and then transmitted to the non-bit bit 119, and the hammer bit 119 is rotated in the circumferential direction. The hand grip 109 is formed in a substantially U shape in a side view, and the lower end side is connected to the lower end of the rear end of the motor housing 105, and the upper end side is connected to the rear end of the gear housing 107. The drive motor 111 is energized and driven by a pulling operation of a trigger 109a disposed on the grip 109.
[0012] 運動変換機構 113は、駆動モータ 111によって水平面内にて回転駆動されるギア 123、クランク板 125、クランクアーム 127、および駆動子としての筒状ピストン 129を 主体として構成され、クランク板 125、クランクアーム 127、筒状ピストン 129によって クランク機構が構成されている。筒状ピストン 129は、シリンダ 141内に摺動自在に配 置されており、駆動モータ 111が通電駆動されることに伴い当該シリンダ 141に沿つ て直線動作を行う。  The motion conversion mechanism 113 is mainly configured by a gear 123 that is rotationally driven in a horizontal plane by a drive motor 111, a crank plate 125, a crank arm 127, and a cylindrical piston 129 as a driver, and the crank plate 125 The crank arm 127 and the cylindrical piston 129 constitute a crank mechanism. The cylindrical piston 129 is slidably disposed in the cylinder 141, and performs a linear motion along the cylinder 141 when the drive motor 111 is energized.
[0013] 打撃要素 115は、筒状ピストン 129のボア内壁に摺動自在に配置された打撃子とし てのストライカ 143と、ツールホルダ 137に摺動自在に配置されるとともに、ストライカ 143の運動エネルギをハンマビット 119に伝達する中間子としてのインパクトボルト 1 45とを主体として構成される。ストライカ 143は、筒状ピストン 129の摺動動作に伴う 当該筒状ピストン 129の空気室 129aの空気パネを介して駆動され、ツールホルダ 13 7に摺動自在に配置されたインパクトボルト 145に衝突（打撃）し、当該インパクトボル ト 145を介してハンマビット 119に打撃力を伝達する。筒状ピストン 129およびストライ 力 143は、本発明における「駆動機構部」に対応する。 [0013] The striking element 115 includes a striker 143 as a striker slidably disposed on the bore inner wall of the cylindrical piston 129 and a tool holder 137 slidably disposed. It is composed mainly of impact bolts 145 as mesons that transmit to the hammer bit 119. The striker 143 is driven via the air panel of the air chamber 129a of the cylindrical piston 129 accompanying the sliding movement of the cylindrical piston 129, and the tool holder 13 The impact bolt 145 is slidably disposed on the impact bolt 145 (striking), and the impact force is transmitted to the hammer bit 119 via the impact bolt 145. The cylindrical piston 129 and the strike force 143 correspond to the “drive mechanism” in the present invention.
[0014] 図 2にはハンマドリル 101の主要部を拡大した状態が断面図で示される。動力伝達 機構 117は、駆動モータ 111によって図示省略のギアを介して水平面内にて回転駆 動される小べベルギア 134、当該小べベルギア 134に嚙み合!、係合して鉛直面内 にて回転する大べベルギア 135、当該大べベルギア 135に嚙み合い係合して回転 するスライドスリーブ 147を主体として構成される。そしてスライドスリーブ 147の回転 出力は、当該スライドスリーブ 147とともに回転するシリンダ 141からトルクリミッター 1 61を経てツールホルダ 137に伝達される。すなわち、ツールホルダ 137は、シリンダ 141とは別体に形成されるとともに、当該シリンダ 141の前端領域に同心状に配置さ れている。 FIG. 2 is a sectional view showing an enlarged state of the main part of the hammer drill 101. The power transmission mechanism 117 is engaged with a small bevel gear 134 that is driven to rotate in a horizontal plane by a drive motor 111 via a gear (not shown), and engages with the small bevel gear 134 in a vertical plane. And a slide sleeve 147 that rotates in meshing engagement with the large bevel gear 135. Then, the rotation output of the slide sleeve 147 is transmitted from the cylinder 141 rotating together with the slide sleeve 147 to the tool holder 137 via the torque limiter 161. That is, the tool holder 137 is formed separately from the cylinder 141 and is concentrically disposed in the front end region of the cylinder 141.
[0015] トルクリミッター 161は、シリンダ 141の外側に同心状に配置されている。トルクリミツ ター 161は、図 2および図 3の分解図に示されるように、軸方向において、互いに対 向状に配置される駆動側リング 163と被動側リング 165、および両リング 163, 165を 互いに接近する方向に付勢する付勢パネ 167 (圧縮コイルスプリング)を主体として 構成されている。駆動側リング 163は、本発明における「シリンダ側回転トルク伝達部 材」に対応し、被動側リング 165は、本発明における「ツールホルダ側回転トルク伝達 部材」に対応する。駆動側リング 163は、図 4に示すように、その内周面に内径方向 へと突出する複数の突部 163bを有し、これらの突部 163bがシリンダ 141の外周面 に形成された軸方向に延びる複数の溝 141bに嚙み合 、係合されて 、る。これにより 、駆動側リング 163は、シリンダ 141に対して軸方向への相対移動が許容された状態 で周方向には一体に回転する構成とされる。被動側リング 165は、シリンダ 141の外 周面に相対回転可能に配置されるとともに、当該シリンダ 141の外周に長軸方向へ の移動不能に設けられたサークリップ 157によって軸方向前端側（ツールホルダ 137 側)への移動が規制されている。サークリップ 157は、本発明における「規制部」に対 応する。  The torque limiter 161 is disposed concentrically outside the cylinder 141. As shown in the exploded views of FIGS. 2 and 3, the torque limiter 161 brings the drive side ring 163 and the driven side ring 165, which are arranged opposite to each other in the axial direction, and the rings 163 and 165 close to each other. It is mainly composed of an urging panel 167 (compression coil spring) that urges in the direction in which it moves. The drive side ring 163 corresponds to the “cylinder side rotational torque transmission member” in the present invention, and the driven side ring 165 corresponds to the “tool holder side rotational torque transmission member” in the present invention. As shown in FIG. 4, the drive-side ring 163 has a plurality of protrusions 163b protruding in the inner diameter direction on the inner peripheral surface thereof, and these protrusions 163b are formed in the axial direction formed on the outer peripheral surface of the cylinder 141. And are engaged with and engaged with a plurality of grooves 141b extending in the direction. Accordingly, the drive side ring 163 is configured to rotate integrally in the circumferential direction in a state where relative movement in the axial direction is allowed with respect to the cylinder 141. The driven-side ring 165 is disposed on the outer peripheral surface of the cylinder 141 so as to be relatively rotatable, and the circlip 157 provided on the outer periphery of the cylinder 141 so as to be immovable in the major axis direction (the tool holder in the axial direction). 137 side) is restricted. The circlip 157 corresponds to the “regulator” in the present invention.
[0016] 駆動側リング 163と被動側リング 165は、互いに対向する軸方向の端面にそれぞれ 歯 163a、 165aを有し、これら歯 163a, 165aが互いに嚙み合い係合されている。こ れにより駆動側リング 163から被動側リング 165への動力の伝達が可能とされる。ま た被動側リング 165は、駆動側リング 163の反対側の軸方向端面がツールホルダ 13 7の軸方向後端面と対向している。そして被動側リング 165とツールホルダ 137は、そ れぞれ対向する軸方向端面に歯 165b, 137cを有し、これら歯 165b, 137cが互い に嚙み合い係合されている。これにより被動側リング 165からツールホルダ 137への 動力の伝達が可能とされる。付勢パネ 167は、駆動側リング 163の後方に配置される とともに、シリンダ 141に固定状に止着されたバネ受リング 168と、駆動側リング 163と の間に介在され、当該駆動側リング 163を被動側リング 165に近接する方向へと押 圧付勢している。このため、付勢パネ 167の付勢力は、被動側リング 165をツールホ ルダ 137側である前方へと押圧するように作用するが、本実施の形態では、前述した ように、サークリップ 157によって被動側リング 165が所定位置以上に前方へ移動す ることが規制されており、これにより付勢パネ 167の付勢力がツールホルダ 137には 作用しない構成とされる。 [0016] The driving side ring 163 and the driven side ring 165 are respectively provided on axially facing end faces. The teeth 163a and 165a are provided, and these teeth 163a and 165a are engaged with each other. As a result, power can be transmitted from the drive side ring 163 to the driven side ring 165. Further, in the driven side ring 165, the axial end surface on the opposite side of the driving side ring 163 is opposed to the axial rear end surface of the tool holder 136. The driven-side ring 165 and the tool holder 137 have teeth 165b and 137c on the axial end surfaces facing each other, and these teeth 165b and 137c are meshed and engaged with each other. As a result, power can be transmitted from the driven ring 165 to the tool holder 137. The biasing panel 167 is disposed behind the driving side ring 163 and is interposed between the spring receiving ring 168 fixedly fixed to the cylinder 141 and the driving side ring 163, and the driving side ring 163 Is biased in the direction approaching the driven ring 165. For this reason, the urging force of the urging panel 167 acts to press the driven ring 165 forward, which is the tool holder 137 side, but in this embodiment, as described above, the urging force is applied by the circlip 157. The side ring 165 is restricted from moving forward beyond a predetermined position, whereby the biasing force of the biasing panel 167 does not act on the tool holder 137.
[0017] シリンダ 141の回転出力は、トルクリミッター 161の駆動側リング 163、被動側リング 165を経てツールホルダ 137に伝達される。駆動側リング 163の歯 163aと被動側リン グ 165の歯 165aは、周方向において、軸方向に所定の角度で傾斜する係合面を介 して係合している。このことにより、駆動側リング 163と被動側リング 165との間、すな わちシリンダ 141とツールホルダ 137間に所定値を超えるトルクが作用したときは、傾 斜状の係合面間に滑りが生じ、駆動側リング 163が付勢パネ 167の付勢力に抗して 被動側リング 165から離間する方向へと移動し、これにより駆動側リング 163の歯 16 3aと被動側リング 165の歯 165aの係合が解除されて動力の伝達が遮断される。  The rotational output of the cylinder 141 is transmitted to the tool holder 137 via the drive side ring 163 and the driven side ring 165 of the torque limiter 161. The teeth 163a of the drive side ring 163 and the teeth 165a of the driven side ring 165 are engaged with each other via an engagement surface inclined at a predetermined angle in the axial direction in the circumferential direction. As a result, when a torque exceeding a predetermined value is applied between the drive side ring 163 and the driven side ring 165, that is, between the cylinder 141 and the tool holder 137, the slippage occurs between the inclined engagement surfaces. And the drive side ring 163 moves away from the driven ring 165 against the biasing force of the biasing panel 167, whereby the teeth 163a of the drive side ring 163 and the teeth 165a of the driven side ring 165 are moved. Is disengaged and power transmission is interrupted.
[0018] ツールホルダ 137は、前側ホルダ部 137aと後側ホルダ部 137bから構成されて!、る 。そして前側ホルダ部 137aがハンマビット 119を保持するとともに、インパクトボルト 1 45を収容し、後側ホルダ部 137bがトルクリミッター 161の被動側リング 165の歯 165 aと嚙み合 、係合する歯 137cを有して 、る。前側ホルダ部 137aと後側ホルダ部 137 bは、前側ホルダ部 137aの後端部に後側ホルダ部 137bの前端部が被さるように嵌 合されるとともに、互いに長軸方向への所定量の相対移動が許容された状態で周方 向には一体となって回転するように、連結リング 138を介して連接されている。また後 側ホルダ部 137aは、軸方向の後端側において、シリンダ 141の前端外周部に対し 前方向（ノ、ンマビット 119側）への分離可能に遊嵌状に嵌合されている。すなわち、 ツールホルダ 137は、シリンダ 141に対して取り外し自在とされており、組付け状態に あっては、ギアハウジング 107に固定状に止着されたストップリング 139によって前方 向（ノ、ンマビット 119側）への移動が規制されている。これにより、被動側リング 165の 歯 165aとツールホルダ 137の歯 137cとの嚙み合い係合が確実に維持される。 [0018] The tool holder 137 includes a front holder part 137a and a rear holder part 137b! The front holder portion 137a holds the hammer bit 119 and accommodates the impact bolt 145. The rear holder portion 137b engages and engages with the teeth 165a of the driven side ring 165 of the torque limiter 161. Have The front holder part 137a and the rear holder part 137b are fitted so that the front end part of the rear holder part 137b covers the rear end part of the front holder part 137a, and a predetermined amount relative to each other in the major axis direction. Circumference with movement allowed Are connected via a connecting ring 138 so as to rotate together. The rear holder portion 137a is loosely fitted on the rear end side in the axial direction so as to be separable from the outer peripheral portion of the front end of the cylinder 141 in the forward direction (no, umbit 119 side). In other words, the tool holder 137 is detachable from the cylinder 141, and in the assembled state, the tool holder 137 is moved forward by the stop ring 139 fixedly attached to the gear housing 107 (on the side of the nombit 119). ) Is restricted. Thus, the meshing engagement between the teeth 165a of the driven ring 165 and the teeth 137c of the tool holder 137 is reliably maintained.
[0019] ツールホルダ 137に収容されるインパクトボルト 145は、軸方向において、ツールホ ルダ 137の筒孔内周面に密接状に嵌合する大径部 145aと、ツールホルダ 137の筒 孔内周面との間に所定大の空間を有する小径部 145bを有する段付構造とされ、当 該小径部 145bの外周側に位置決め部材 151が配置されている。ハンマドリル 101 は、使用者が本体部 103に前方への押圧力を加えてハンマビット 119を被力卩ェ材に 押し付けた状態でカ卩工作業を行う。このとき、インパクトボルト 145は、ハンマビット 11 9とともに後方 (筒状ピストン 129側）へと押し込まれる。つまり、インパクトボルト 145に は、加工作業を行う際にハンマビット 119を被加工材に押し付けたときの反力が作用 するが、この反力によるインパクトボルト 145の後方への移動は、位置決め部材 151 がシリンダ 141に設けた受リング 153に当接することで受けられる。この受リング 153 は、本発明における「後方荷重受部」に対応し、またツールホルダ 137に収容される インパクトボルト 137および位置決め部材 151等は、本発明における「ツールホルダ 内部機構部」に対応する。したがって、ツールホルダ 137は、シリンダ 141から取り外 す際、これら「ツールホルダ内部機構部」とともに、取り外される。  [0019] The impact bolt 145 accommodated in the tool holder 137 includes, in the axial direction, a large-diameter portion 145a that closely fits into the inner peripheral surface of the tool hole 137 and the inner peripheral surface of the tool holder 137. A stepped structure having a small-diameter portion 145b having a predetermined large space therebetween, and a positioning member 151 is disposed on the outer peripheral side of the small-diameter portion 145b. The hammer drill 101 performs a ware work in a state in which the user applies a forward pressing force to the main body 103 and presses the hammer bit 119 against the force-receiving material. At this time, the impact bolt 145 is pushed backward together with the hammer bit 119 (to the cylindrical piston 129 side). In other words, the impact bolt 145 is subjected to a reaction force when the hammer bit 119 is pressed against the workpiece during the machining operation, and the rearward movement of the impact bolt 145 by this reaction force causes the positioning member 151 to move. Is received by contacting a receiving ring 153 provided on the cylinder 141. The receiving ring 153 corresponds to the “rear load receiving portion” in the present invention, and the impact bolt 137 and the positioning member 151 etc. accommodated in the tool holder 137 correspond to the “tool holder internal mechanism portion” in the present invention. . Therefore, when the tool holder 137 is removed from the cylinder 141, it is removed together with these “tool holder internal mechanism portions”.
[0020] ツールホルダ 137の取り外しのために、ギアハウジング 107は、軸方向において 2 分割された前側ハウジング部 107aと後側ハウジング部 107bから構成されて 、る。前 側ハウジング部 107aと後側ハウジング部 107bとは、突合せ状の接合領域にぉ 、て 、例えばネジ (便宜上図示を省略する）によって分離可能に接合され、当該ネジを外 すことによって分離される。そしてツールホルダ 137の前方への移動を規制するストツ プリング 139は、前側ハウジング部 107aに設けられている。  [0020] For the removal of the tool holder 137, the gear housing 107 is composed of a front housing part 107a and a rear housing part 107b which are divided into two in the axial direction. The front housing portion 107a and the rear housing portion 107b are separated from each other by, for example, screws (not shown for convenience) in a butt-like joining region, and separated by removing the screws. . A stopper 139 for restricting the forward movement of the tool holder 137 is provided in the front housing portion 107a.
[0021] 上記のように構成されるハンマドリル 101は、使用者によるトリガ 109aの引き操作に よって駆動モータ 111が通電駆動されると、クランク機構を主体に構成される運動変 換機構 113を介して筒状ピストン 129がシリンダ 141に沿って直線状に摺動動作され 、それに伴う筒状ピストン 129の空気室 129a内の空気の圧力変化、すなわち空気バ ネの作用により、ストライカ 143はシリンダ 141内を直線運動する。ストライカ 143は、 インパクトボルト 145に衝突することで、その運動エネルギをハンマビット 119に伝達 する。 The hammer drill 101 configured as described above is used for pulling the trigger 109a by the user. Therefore, when the drive motor 111 is energized, the cylindrical piston 129 is slid linearly along the cylinder 141 via the motion conversion mechanism 113 mainly composed of a crank mechanism, and the associated cylindrical piston is moved accordingly. The striker 143 moves linearly in the cylinder 141 by the pressure change of the air in the 129 air chambers 129a, that is, by the action of the air vane. When the striker 143 collides with the impact bolt 145, the kinetic energy is transmitted to the hammer bit 119.
[0022] 一方、駆動モータ 111の回転出力は、動力伝達機構 117を介してシリンダ 141に 伝達される。これにより、シリンダ 141が鉛直面内にて回転駆動されるとともに、当該 シリンダ 141からトルクリミッター 161の駆動側リング 163、および被動側リング 165を 介してツールホルダ 137力回転駆動され、更にツールホルダ 137にて保持されるハ ンマビット 119がー体状に回転される。力くして、ハンマビット 119が軸方向のハンマ 動作と周方向のドリル動作を行い、被加工材 (コンクリート）に穴開け作業を遂行する  On the other hand, the rotational output of the drive motor 111 is transmitted to the cylinder 141 via the power transmission mechanism 117. As a result, the cylinder 141 is driven to rotate in the vertical plane, and the tool holder 137 is driven to rotate from the cylinder 141 via the drive side ring 163 and the driven side ring 165 of the torque limiter 161. The hammerbit 119 held in is rotated into a body shape. The hammer bit 119 performs the hammering operation in the axial direction and the drilling operation in the circumferential direction, and drills the workpiece (concrete).
[0023] なお本実施の形態に係るハンマドリル 101は、上述したハンマビット 119にハンマ 動作と周方向のドリル動作とを行わせる、ハンマドリルモードでの作業態様のほか、 ハンマビット 119にドリル動作のみを行わせる、ドリルモードでの作業態様に切り換え ることが可能とされている。この動作モードの切り換えは、スライドスリーブ 147を軸方 向にスライドさせて大べベルギア 135に対する歯の嚙み合 ヽ係合を解除することで 行われる。そしてハンマモードでハンマビット 119を駆動するときは、ツールホルダ 13 7およびハンマビット 119の自由回転を規制する、つまりハンマビット 119を所定の向 き (周方向）に定めて固定する、いわゆるバリオロックを行う。本実施の形態では、この ノ リオロックについて、スライドスリーブ 147に設けた歯 147aを、ギアハウジング 107 に対して周方向に固定状態に設けられたロックリング 149の歯 149aに嚙み合い係合 することで行う構成としている。つまり、スライドスリーブ 147は、単一部材でありながら 、動力伝達機能とモード切換時のバリォロック機能とを有する構成とされる。なおスラ イドスリーブ 147を軸方向にスライドさせるためのモード切 «構については、本発 明に直接関係しないため、その説明を省略する。 [0023] The hammer drill 101 according to the present embodiment is not limited to the hammer drill mode in which the hammer bit 119 performs the hammer operation and the circumferential drill operation, and the hammer bit 119 performs only the drill operation. It is possible to switch to working mode in drill mode. The operation mode is switched by sliding the slide sleeve 147 in the axial direction to release the tooth meshing engagement with the large bevel gear 135. When driving the hammer bit 119 in the hammer mode, the so-called vario lock that restricts the free rotation of the tool holder 137 and the hammer bit 119, that is, fixes the hammer bit 119 in a predetermined direction (circumferential direction). I do. In the present embodiment, the tooth lock 147a provided on the slide sleeve 147 is meshed and engaged with the tooth 149a of the lock ring 149 provided in a fixed state in the circumferential direction with respect to the gear housing 107. It is configured to do in. That is, the slide sleeve 147 is a single member but has a power transmission function and a vario-lock function at the time of mode switching. Note that the mode switching mechanism for sliding the slide sleeve 147 in the axial direction is not directly related to the present invention, and thus the description thereof is omitted.
[0024] さて、ハンマドリル 101においては、ツールホルダ 137に収容されたツールホルダ 内部機構部を構成する構成部材としての、インパクトボルト 145、および位置決め部 材 151の修理、あるいはそれに用いられるオーリング 145c, 152等の消耗部品の交 換等のために、それらを本体部 103内から取り外すことがある。このために、ギアハウ ジング 107は、前側ハウジング部 107aと後側ハウジング部 107bとに分離されるが、 この分離状態が図 5に示される。図示のように、ギアハウジング 107が前側ハウジング 部 107aと後側ハウジング部 107bとに分離されると、それに伴いツールホルダ 137は 、当該ツールホルダ 137内に収容されたインパクトボルト 145および位置決め部材 1 51とともに、シリンダ 141およびトルクリミッター 161の被動側リング 165からそれぞれ 離間する前方向へと移動されて取り外される。 Now, in the hammer drill 101, the tool holder housed in the tool holder 137 In order to repair the impact bolt 145 and positioning member 151 as components constituting the internal mechanism, or to replace consumable parts such as O-rings 145c and 152 used in the impact bolt 145 and the positioning member 151, they are used in the main body 103. May be removed from. For this purpose, the gear housing 107 is separated into a front housing part 107a and a rear housing part 107b. This separated state is shown in FIG. As shown in the figure, when the gear housing 107 is separated into the front housing part 107a and the rear housing part 107b, the tool holder 137 is accompanied by the impact bolt 145 and the positioning member 1 51 accommodated in the tool holder 137. At the same time, they are moved away from the driven ring 165 of the cylinder 141 and the torque limiter 161 and removed.
[0025] この場合、本実施の形態においては、前述したように、トルクリミッター 161の被動 側リング 165は、シリンダ 141に対し所定位置以上に前方向、すなわちツールホルダ 137の取り外し方向へ移動しないようにサークリップ 157によって規制され、これによ り付勢パネ 167の付勢力がツールホルダ 137に作用しな!/、構成として!/、る。すなわち 、ツールホルダ 137とトルクリミッター 161との連結に関し、トルクリミッター 161とツー ルホルダ 137とは、周方向においては歯 165a, 137cを介して嚙み合い係合される 力 軸方向についてはその連結に関して互いに独立した形態となってなる。このため 、付勢パネ 167の干渉を受けることなぐツールホルダ 137をシリンダ 141から容易、 かつ楽に取り外すことが可能になった。このことは、当然のことながら、ツールホルダ 内部機構部の構成部材に関する修理作業ある 、は交換作業後に行われる組付け作 業時においても同様である。 In this case, in the present embodiment, as described above, the driven-side ring 165 of the torque limiter 161 does not move forward beyond a predetermined position with respect to the cylinder 141, that is, in the removal direction of the tool holder 137. Therefore, the urging force of the urging panel 167 does not act on the tool holder 137. That is, with respect to the connection between the tool holder 137 and the torque limiter 161, the torque limiter 161 and the tool holder 137 are engaged with each other through the teeth 165a and 137c in the circumferential direction, and the connection in the axial direction. It becomes a mutually independent form. For this reason, the tool holder 137 that does not receive the interference of the biasing panel 167 can be easily and easily removed from the cylinder 141. As a matter of course, this also applies to the repair work related to the constituent members of the internal structure of the tool holder or the assembly work performed after the replacement work.
[0026] また本実施の形態においては、トルクリミッター 161をシリンダ 141の外側に配置し 、シリンダ 141の回転力がトルクリミッター 161の駆動側リング 163に伝達される構成、 つまり内側力 外側へと伝達される構成としている。その結果、シリンダ 141の外面端 部に被さるように配置されたツールホルダ 137に対する動力伝達を構造的に無理な く行うことができるとともに、シリンダ 141に対するトルクリミッター 161の組付け、およ びツールホルダ 137の組付けを楽に行うことができる。  In the present embodiment, the torque limiter 161 is disposed outside the cylinder 141, and the rotational force of the cylinder 141 is transmitted to the drive side ring 163 of the torque limiter 161, that is, the inner force is transmitted to the outside. It is assumed to be configured. As a result, power transmission to the tool holder 137 disposed so as to cover the outer surface end of the cylinder 141 can be performed structurally without difficulty, and the assembly of the torque limiter 161 to the cylinder 141 and the tool holder 137 can be assembled easily.
[0027] また本実施の形態では、ツールホルダ 137内に収容されるインパクトボルト 145、位 置決め部材 151を、前方へと移動させて取り外す構成である。このため、加工作業時 のハンマビット 119の被力卩ェ材に対する押し付け反力を受ける受リング 153の干渉を 受けることなぐ取り外すことができる。 In the present embodiment, the impact bolt 145 and the positioning member 151 housed in the tool holder 137 are moved forward and removed. For this reason, during processing It is possible to remove the hammer bit 119 without receiving the interference of the receiving ring 153 that receives the pressing reaction force against the force-bearing material.
図面の簡単な説明  Brief Description of Drawings
[0028] [図 1]本発明の実施の形態に係るハンマドリルの全体構成を示す側断面図である。  FIG. 1 is a side sectional view showing an overall configuration of a hammer drill according to an embodiment of the present invention.
[図 2]ハンマドリルの主要部を示す側面図である。  FIG. 2 is a side view showing the main part of the hammer drill.
[図 3]トルクリミッターを分解して示す側面図である。  FIG. 3 is an exploded side view of the torque limiter.
[図 4]トルクリミッターの駆動側リングを示す正面図である。  FIG. 4 is a front view showing a drive side ring of the torque limiter.
[図 5]ギアハウジングを前側ハウジング部と後側ハウジング部に分離した状態を示す 側断面図である。  FIG. 5 is a side sectional view showing a state where the gear housing is separated into a front housing part and a rear housing part.
符号の説明  Explanation of symbols
[0029] 101 ハンマドリル (衝撃式作業工具） [0029] 101 Hammer drill (impact work tool)
103 本体部  103 Body
105 モータハウジング  105 Motor housing
107 ギアハウジング  107 Gear housing
109 グリップ  109 grip
109a トリガ  109a trigger
11 1 駆動モータ  11 1 Drive motor
113 運動変換機構  113 Motion conversion mechanism
115 打撃要素  115 Stroke element
117 動力伝達機構  117 Power transmission mechanism
119 ハンマビット (先端工具）  119 hammer bit (tip tool)
123 ギア  123 gear
125 クランク板  125 Crank plate
127 クランクアーム  127 crank arm
129 筒状ピストン (駆動機構部）  129 Cylindrical piston (drive mechanism)
129a 空気室  129a Air chamber
134 小べベルギア  134 Small Bevel Gear
135 大ベべノレギア 137 ツーノレホノレダ 135 Great Benore Gear 137 Tsunore Honoreda
137a 前側ホルダ部 137a Front holder
137b 後側ホルダ部 137b Rear holder
137c 歯 137c teeth
138 連結リング 138 Connecting ring
139 ストップリング 139 Stop ring
141 シリンダ 141 cylinders
141b 溝 141b groove
143 ストライカ (駆動機構部）  143 striker (drive mechanism)
145 インパクトボルト（ツールホルダ内部機構部） 145 Impact bolt (Tool holder internal mechanism)
145a 大径部 145a Large diameter part
145b 小径部  145b Small diameter part
145c オーリング  145c O-ring
147 スライドスリーブ  147 Slide sleeve
147a 歯  147a teeth
151 位置決め部材 (ツールホルダ内部機構部）  151 Positioning member (Internal mechanism of tool holder)
152 オーリング  152 O-ring
153 受リング (後方荷重受部）  153 Receiving ring (rear load receiving part)
157 サークリップ (規制部）  157 Circlip (Regulation Department)
161 トルクリミッター  161 Torque limiter
163 駆動側リング (シリンダ側回転トルク伝達部材） 163a 困  163 Drive side ring (cylinder side rotational torque transmission member) 163a
163b 突部 163b protrusion
165 被動側リング (ツールホルダ側回転トルク伝達部材) 165a 困  165 Driven ring (Tool holder side rotational torque transmission member) 165a
165b 困 165b
167 付勢パネ (パネ部材）  167 Biasing panel (panel material)
168 バネ受リング 168 Spring bearing ring

Claims

請求の範囲  The scope of the claims
長軸方向への直線状の打撃動作、および当該長軸方向周りの回転動作を介して 所定の加工作業を行う先端工具と、  A tip tool for performing a predetermined machining operation through a linear striking motion in the major axis direction and a rotation motion around the major axis direction;
前記先端工具を打撃動作させるための駆動機構部と、  A drive mechanism for striking the tip tool;
前記駆動機構部を収容するとともに、前記先端工具を回転駆動するべく回転動作 するシリンダと、  A cylinder that houses the drive mechanism and rotates to drive the tip tool;
前記シリンダとは別体に構成されるとともに、前記シリンダの長軸先端領域に同一 軸線上にて連接され、前記先端工具の長軸方向の相対移動を許容しつつ周方向の 相対移動を規制した状態で前記先端工具を保持する中空状のツールホルダと、 前記シリンダの外周上に、当該シリンダの長軸方向に相対移動可能かつ当該シリ ンダの長軸方向周りに相対回転不能に設けられたシリンダ側回転トルク伝達部材と、 前記シリンダの外周上に配置され、前記シリンダ側回転トルク伝達部材を前記ツー ルホルダ側へと押圧するように付勢力を作用させるパネ部材と、  The cylinder is configured separately from the cylinder, and is connected to the long-axis tip region of the cylinder on the same axis, and restricts the relative movement in the circumferential direction while allowing the relative movement of the tip tool in the long-axis direction. A hollow tool holder for holding the tip tool in a state, and a cylinder provided on the outer periphery of the cylinder so as to be relatively movable in the long axis direction of the cylinder and not relatively rotatable around the long axis direction of the cylinder A side rotational torque transmitting member, a panel member disposed on the outer periphery of the cylinder, and applying a biasing force to press the cylinder side rotational torque transmitting member toward the tool holder;
前記シリンダ外周上に配置されるとともに、前記パネ部材によって前記ツールホル ダ側へと押圧された前記シリンダ側回転トルク伝達部材と係合することで前記シリン ダからの回転トルクを前記ツールホルダへ伝達するツールホルダ側回転トルク伝達 部材と、  The rotational torque from the cylinder is transmitted to the tool holder by being engaged with the cylinder-side rotational torque transmitting member that is disposed on the outer periphery of the cylinder and pressed toward the tool holder by the panel member. Tool holder side torque transmission member,
前記シリンダ側回転トルク伝達部材、パネ部材およびツールホルダ側回転トルク伝 達部材を構成要素とするとともに、前記シリンダ力も前記ツールホルダへと予め設定 された最大値以上の回転トルクが作用した場合に前記パネ部材の付勢力に抗して 前記シリンダ側回転トルク伝達部材と前記ツールホルダ側回転トルク伝達部材との係 合を解除し、これによつて前記シリンダ力 前記ツールホルダへの回転力の伝達を解 除するトルクリミッターと、  The cylinder side rotational torque transmission member, the panel member, and the tool holder side rotational torque transmission member are constituent elements, and the cylinder force is also applied when a rotational torque of a preset maximum value or more is applied to the tool holder. The engagement between the cylinder-side rotational torque transmitting member and the tool holder-side rotational torque transmitting member is released against the biasing force of the panel member, thereby transmitting the rotational force to the cylinder force and the tool holder. Torque limiter to be released,
前記ツールホルダ内に収容されたツールホルダ内部機構部と、  A tool holder internal mechanism housed in the tool holder;
前記シリンダ内に配置され、前記ツールホルダ内部機構部力 前記シリンダ方向へ と前記先端工具の打撃動作と反対方向に作用する荷重を受ける後方荷重受部と、を 有する衝撃式作業工具であって、  An impact-type work tool having a rear load receiving portion that is disposed in the cylinder and receives a load acting in the direction opposite to the striking operation of the tip tool in the direction of the cylinder in the tool holder internal mechanism.
前記ツールホルダは、収容した前記ツールホルダ内部機構部とともに、前記先端ェ 具の打撃動作方向へと、前記シリンダ力 取り外し自在とされ、 The tool holder, together with the tool holder internal mechanism portion accommodated therein, has the tip end portion. The cylinder force can be removed in the direction of the tool's impact movement,
さらに前記シリンダは、前記パネ部材の付勢力が当該シリンダ外周上の所定位置 以上に前記先端工具の打撃動作方向へと作用するのを規制する規制部を有し、前 記ツールホルダが前記シリンダから取り外される場合に前記パネ部材が当該取り外し 作業に干渉することを回避するように構成されて!ヽることを特徴とする衝撃式作業ェ 具。  Further, the cylinder has a restricting portion that restricts the biasing force of the panel member from acting in the striking operation direction of the tip tool beyond a predetermined position on the outer periphery of the cylinder, and the tool holder is moved from the cylinder. An impact-type work tool characterized by being configured to avoid the panel member from interfering with the removal work when removed.
[2] 請求項 1に記載の衝撃式作業工具であって、  [2] The impact type work tool according to claim 1,
前記シリンダ側回転トルク伝達部材およびツールホルダ側回転トルク伝達部材は、 それぞれ前記シリンダの外周上に同心状かつ互いに対向状に配置されるリング状部 材によって構成されるとともに、  The cylinder-side rotational torque transmitting member and the tool holder-side rotational torque transmitting member are each configured by ring-shaped members that are concentrically arranged on the outer periphery of the cylinder and opposed to each other.
互いに対向する軸方向の端面にそれぞれ歯を有し、これらの歯が互いに係合され ることで前記シリンダ側回転トルク伝達部材力 前記ツールホルダ側回転トルク伝達 部材へと動力の伝達が行われることを特徴とする衝撃式作業工具。  Each end face in the axial direction facing each other has teeth, and these teeth are engaged with each other so that the cylinder side rotational torque transmission member force is transmitted to the tool holder side rotational torque transmission member. An impact-type work tool characterized by
[3] 請求項 2に記載の衝撃式工具であって、 [3] The impact tool according to claim 2,
前記シリンダ側回転トルク伝達部材および前記ツールホルダ側回転トルク伝達部 材の各歯は、周方向において、軸方向に所定の角度で傾斜する係合面を介して係 合するように構成され、  Each tooth of the cylinder side rotational torque transmission member and the tool holder side rotational torque transmission member is configured to engage with each other via an engagement surface inclined at a predetermined angle in the axial direction in the circumferential direction,
前記シリンダと前記ツールホルダ間に前記所定の最大値以上の回転トルクが作用 した場合に、前記傾斜状の係合面間に滑りが生じ、前記シリンダ側回転トルク伝達部 材が前記パネ部材の付勢力に抗して前記ツールホルダ側回転トルク伝達部材から 離間する方向へと前記シリンダの長軸方向に移動し、これによつて前記シリンダ側回 転トルク伝達部材および前記ツールホルダ側回転トルク伝達部材の各歯の係合が解 除されて動力の伝達が遮断されることを特徴とする衝撃式作業工具。  When a rotational torque greater than the predetermined maximum value acts between the cylinder and the tool holder, slip occurs between the inclined engaging surfaces, and the cylinder-side rotational torque transmission member is attached to the panel member. The cylinder side rotational torque transmission member and the tool holder side rotational torque transmission member are moved in the long axis direction of the cylinder in a direction away from the tool holder side rotational torque transmission member against the force. The impact-type work tool is characterized in that the engagement of each tooth is disengaged and the transmission of power is cut off.
[4] 請求項 2または 3に記載の衝撃式作業工具であって、 [4] The impact type work tool according to claim 2 or 3,
前記シリンダ側回転トルク伝達部材は、リング内周面に内径方向へと突出する突部 を有し、  The cylinder side rotational torque transmission member has a protrusion protruding in the inner diameter direction on the inner peripheral surface of the ring,
前記シリンダは、その外周面に長軸方向に伸びる溝を有し、  The cylinder has a groove extending in a major axis direction on an outer peripheral surface thereof,
前記突部が前記溝に係合することにより、前記シリンダ側回転トルク伝達部材は、 前記シリンダに対して、軸方向への相対移動が許容された状態で周方向には一体に 回転する構成とされることを特徴とする衝撃式作業工具。 When the protrusion engages with the groove, the cylinder-side rotational torque transmission member is An impact-type work tool characterized by being configured to rotate integrally in the circumferential direction in a state in which relative movement in the axial direction is allowed with respect to the cylinder.
[5] 請求項 1から 4までの 、ずれか一項に記載の衝撃式作業工具であって、  [5] The impact type work tool according to any one of claims 1 to 4, wherein:
前記規制部は、前記シリンダの外周上に固定されたサークリップによって構成され 前記ツールホルダ側回転トルク伝達部材が、前記サークリップによって所定位置以 上に前方へ移動することが規制されることにより、前記パネ部材の付勢力が前記先 端工具の打撃動作方向へと作用するのを規制することを特徴とする衝撃式作業工具  The restricting portion is constituted by a circlip fixed on the outer periphery of the cylinder, and the tool holder side rotational torque transmitting member is restricted by the circlip from moving forward beyond a predetermined position, An impact-type work tool for restricting the biasing force of the panel member from acting in the striking motion direction of the tip tool
[6] 請求項 1から 4までの 、ずれか一項に記載の衝撃式作業工具であって、 [6] The impact type work tool according to any one of claims 1 to 4, wherein
前記ツールホルダ内部機構部は、前記駆動機構部の打撃力を前記先端工具に伝 達するインパクトボルトを有し、  The tool holder internal mechanism has an impact bolt that transmits the impact force of the drive mechanism to the tip tool;
前記後方荷重受部は、前記シリンダ内に配置されるとともに、前記インパクトボルト が前記シリンダ側へと前記先端工具力も反力を受ける場合に、当該インパクトボルト に作用する前記先端工具の打撃動作と反対方向に作用する荷重を受けるリング状 部材によって構成されることを特徴とする衝撃式作業工具。  The rear load receiving portion is arranged in the cylinder and is opposite to the impact operation of the tip tool acting on the impact bolt when the impact bolt receives the reaction force of the tip tool force toward the cylinder side. An impact type work tool comprising a ring-shaped member that receives a load acting in a direction.
PCT/JP2006/323624 2005-11-28 2006-11-27 Impact type working tool WO2007061101A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112006003186T DE112006003186T5 (en) 2005-11-28 2006-11-27 Electric shock tool

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005341846A JP4751706B2 (en) 2005-11-28 2005-11-28 Impact type work tool
JP2005-341846 2005-11-28

Publications (1)

Publication Number Publication Date
WO2007061101A1 true WO2007061101A1 (en) 2007-05-31

Family

ID=38067322

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2006/323624 WO2007061101A1 (en) 2005-11-28 2006-11-27 Impact type working tool

Country Status (3)

Country Link
JP (1) JP4751706B2 (en)
DE (1) DE112006003186T5 (en)
WO (1) WO2007061101A1 (en)

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EP2551062A1 (en) * 2011-07-26 2013-01-30 Black & Decker Inc. Hammer

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KR101764054B1 (en) 2015-12-18 2017-08-01 류욱현 Pile driver with compressed air

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JP2001239473A (en) * 2000-02-10 2001-09-04 Robert Bosch Gmbh Portable power tool

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JPH1058352A (en) * 1996-05-30 1998-03-03 Robert Bosch Gmbh Tool holder change device for hand-held machine tool
JP2001239473A (en) * 2000-02-10 2001-09-04 Robert Bosch Gmbh Portable power tool

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2551062A1 (en) * 2011-07-26 2013-01-30 Black & Decker Inc. Hammer
US9339924B2 (en) 2011-07-26 2016-05-17 Black & Decker Inc. Hammer
EP3260241A1 (en) * 2011-07-26 2017-12-27 Black & Decker Inc. Hammer

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JP4751706B2 (en) 2011-08-17
DE112006003186T5 (en) 2008-10-02

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