WO2013108557A1 - Reciprocating tool - Google Patents

Reciprocating tool Download PDF

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Publication number
WO2013108557A1
WO2013108557A1 PCT/JP2012/083591 JP2012083591W WO2013108557A1 WO 2013108557 A1 WO2013108557 A1 WO 2013108557A1 JP 2012083591 W JP2012083591 W JP 2012083591W WO 2013108557 A1 WO2013108557 A1 WO 2013108557A1
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WO
WIPO (PCT)
Prior art keywords
reciprocating
output rod
cam
reciprocating tool
outer rotor
Prior art date
Application number
PCT/JP2012/083591
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French (fr)
Japanese (ja)
Inventor
靖史 小倉
鵜飼　智大
隆如 田原
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株式会社マキタ
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Publication of WO2013108557A1 publication Critical patent/WO2013108557A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D51/00—Sawing machines or sawing devices working with straight blades, characterised only by constructional features of particular parts; Carrying or attaching means for tools, covered by this subclass, which are connected to a carrier at both ends
    • B23D51/16—Sawing machines or sawing devices working with straight blades, characterised only by constructional features of particular parts; Carrying or attaching means for tools, covered by this subclass, which are connected to a carrier at both ends of drives or feed mechanisms for straight tools, e.g. saw blades, or bows
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for

Definitions

  • the present invention relates to a reciprocating tool that converts a rotational output of a drive motor into a linear motion and outputs the linear motion.
  • the reciprocating tool include a reciprocating cutting tool called a reciprocating saw, a jigsaw, a hedge trimmer, a hammer, a hammer drill, and the like.
  • JP-A-2005-14111 discloses a reciprocating saw having a motion conversion mechanism such as a crank mechanism.
  • the motion conversion mechanism converts the rotational output of the drive motor built in the main body into a reciprocating motion, and reciprocates the output rod on which the blade is mounted in the axial direction.
  • the rotating shaft of the electric motor is arranged in parallel to the output rod.
  • the rotational output of the electric motor is decelerated by the bevel gear and transmitted to the crank plate.
  • JP 2009-241242 also discloses a reciprocating saw.
  • the rotating shaft of the electric motor is orthogonal to the output rod.
  • the rotation output of the electric motor is decelerated by the spur gear and transmitted to the crank plate.
  • the reciprocating motion generated by the revolution of the eccentric roller attached to the crank plate is transmitted as the reciprocating motion of the output rod.
  • the rotational output of the drive motor is decelerated by the gear. Thereafter, the rotational output is converted into a reciprocating motion by the motion converting mechanism and output as a reciprocating motion of the output rod. Therefore, the conventional general reciprocating saw has a number of parts because it has a motion conversion mechanism in addition to a speed reduction mechanism.
  • Some reciprocating saws are further equipped with an orbital mechanism or counterweight. Therefore, the reciprocating saw has a larger number of parts and a complicated structure.
  • the orbital mechanism provides a slight orbital motion to the output rod to increase the blade cutting efficiency.
  • the counterweight reciprocates in the opposite direction to the output rod in order to reduce vibration associated with the reciprocating movement of the output rod.
  • a reciprocating tool such as a reciprocating saw with a small number of parts is conventionally required.
  • the reciprocating tool has an electric motor as a drive source and a motion conversion mechanism.
  • the motion conversion mechanism converts the rotational output of the motor into the reciprocating motion of the output rod.
  • the electric motor is an outer rotor motor including an outer rotor that rotates on the outer peripheral side of the stator.
  • a motion conversion mechanism is interposed between the outer rotor and the output rod.
  • the outer rotor motor can rotate at low speed and output high torque.
  • the rotational power of the outer rotor of the outer rotor motor is output as a reciprocating motion of the output rod through the motion conversion mechanism. Therefore, the rotational output of the outer rotor motor is converted into the reciprocating motion of the output rod and output without passing through a speed reduction mechanism such as a conventional gear. Therefore, a speed reduction mechanism is unnecessary, the number of parts of the reciprocating tool can be reduced, and the reciprocating tool can be easily configured.
  • the motion conversion mechanism may comprise a cam mechanism.
  • the cam mechanism may have a cam body and a cam follower.
  • the cam body may be provided on the outer periphery of the rotating outer rotor.
  • the cam follower is provided on the output rod and engages with the cam groove of the cam body.
  • the motion conversion mechanism may comprise a cam mechanism having a cam groove and a follower that fits into the cam groove.
  • One of the cam groove and the follower may be provided on the outer peripheral surface of the outer rotor, and the other may be provided on the output rod.
  • one of the cam groove or the follower is directly provided on the outer peripheral surface of the outer rotor of the electric motor. Therefore, a reciprocating tool can be comprised simply. Or the increase in the number of parts of a reciprocating tool can be suppressed.
  • the motion conversion mechanism may have a structure in which the forward speed and the reverse speed of the output rod are different. Thereby, the working efficiency of the reciprocating tool can be improved.
  • the reciprocating tool may comprise a counterweight that reciprocates in the opposite direction to the output rod. Therefore, the vibration by the reciprocating motion of the output rod can be suppressed.
  • the counterweight can be supported coaxially on the output rod. Therefore, the counterweight can be supported by the output rod so as to be able to reciprocate. As a result, an increase in the number of parts can be suppressed, and the reciprocating tool can be simply configured.
  • the reciprocating tool may be provided with a structure in which the counterweight is turned back at a certain time with respect to the output rod. Therefore, the actual vibration accompanying the reciprocating motion of the output rod can be more effectively suppressed in accordance with the overall characteristics of the reciprocating tool.
  • the outer rotor may be provided with a cam portion for imparting orbital motion to the output rod. Therefore, slight orbital motion can be given to the output rod by utilizing the rotation of the outer rotor. Therefore, the structure can be provided while suppressing an increase in the number of parts of the reciprocating tool or suppressing the reciprocating tool from becoming complicated.
  • the reciprocating tool 1 is a reciprocating cutting tool called a so-called reciprocating saw.
  • the reciprocating tool 1 includes a tool body 2 and a handle 3.
  • the tool body 2 includes an electric motor 10 as a drive source.
  • the handle 3 is D-shaped and is provided at the rear part of the tool body 2.
  • a rechargeable battery pack 4 is attached to the lower part of the handle 3.
  • the battery pack 4 is a lithium ion battery.
  • the battery pack 4 can be removed from the tool body 2 and charged, thereby being used repeatedly.
  • the switch lever 5 provided on the handle 3 is pulled with a fingertip, the electric motor 10 is activated using the battery pack 4 as a power source.
  • a shoe 6 applied to the cutting material is provided at the front portion of the tool body 2. The shoe 6 protrudes forward from the front portion of the tool body 2.
  • the tool body 2 includes an electric motor 10, a motion conversion mechanism 20, and an output rod 7.
  • the electric motor 10 is a so-called outer rotor motor.
  • the outer rotor motor can rotate at a lower speed and output higher torque than the inner rotor motor.
  • the outer rotor motor includes a stator 11 that does not rotate and a cylindrical outer rotor 12.
  • the rotation of the outer rotor 12 is a rotation output of the electric motor 10.
  • the stator 11 is fixed to the main body housing 2a through the support shaft 13 so as not to rotate.
  • the outer rotor 12 is rotatably supported on the outer peripheral side of the stator 11 via the support shaft 13.
  • the outer rotor 12 can rotate about the axis J13 of the support shaft 13.
  • the reciprocating tool 1 has a cam mechanism 21 as a motion conversion mechanism 20.
  • the cam mechanism 21 includes a cam body (cylindrical groove cam) 22 and a cam follower 7a.
  • the cam body 22 can be integrally formed of the same member as the outer rotor 12.
  • the cam body 22 can be integrally provided along the periphery of the outer rotor 12. As shown in FIGS. 3 and 4, the cam body 22 (outer rotor 12) has a cylindrical shape. Cam grooves 23 and 24 are formed on the outer peripheral surface of the cam body 22.
  • the cam groove 23 located on the front side is used for reciprocating the output rod 7.
  • the cam groove 23 goes around the outer rotor 12 and is displaced in the direction of the axis J13.
  • the displacement in the direction of the axis J13 corresponds to the reciprocating distance of the output rod 7.
  • the cam groove 24 located on the rear side is used for reciprocating the counterweight 8.
  • the cam groove 24 goes around the outer rotor 12 and is displaced in the direction of the axis J13.
  • the displacement in the direction of the axis J13 corresponds to the reciprocating distance of the counterweight 8.
  • the displacement of the cam groove 24 in the direction of the axis J13 is opposite to the displacement of the cam groove 23 in the direction of the axis J13.
  • a cam follower 7a provided integrally with the output rod 7 is inserted.
  • the cam follower 8a of the counterweight 8 is inserted.
  • the counterweight 8 is supported on the rear part of the output rod 7.
  • the counterweight 8 is supported coaxially with the output rod 7 and relatively reciprocally movable in the axial direction.
  • the front and rear portions of the output rod 7 are attached to the main body housing 2a by bearings 15 and 16.
  • the output rod 7 is supported so as to be able to reciprocate in the direction of the axis J7 with respect to the main body housing 2a.
  • the bearing 15 located on the front side supports the output rod 7 so as to be tiltable up and down at a constant angle.
  • the bearing 16 located on the rear side is supported by the main body housing 2 a so as to be movable up and down, and is urged downward by a compression spring 17.
  • An orbital roller 18 is attached to the outer periphery of the bearing 16.
  • the orbital roller 18 is placed on a lift cam portion 25 (see FIGS. 3 and 4) provided at the rear portion of the outer rotor 12 (cam body 22).
  • the outer rotor 12 is pressed against the lift cam portion 25 by the compression spring 17.
  • the lift cam portion 25 is rotated by the rotation of the cam body 22, and the lift cam portion 25 moves the orbital roller 18 up and down.
  • the output rod 7 reciprocates in the direction of the axis J7, and the rear portion of the output rod 7 moves up and down.
  • a so-called orbital motion is given to the output rod 7.
  • the one-touch detachable clamping device 9 is attached to the front end of the output rod 7.
  • the blade B is attached to the front end of the output rod 7 by the clamping device 9.
  • the electric motor 10 is activated, and the cam body 22 (outer rotor 12) rotates about the axis J13.
  • a cam follower 7 a of the output rod 7 is engaged with the cam groove 23 of the cam body 22, and a cam follower 8 a of the counterweight 8 is engaged with the cam groove 24. Therefore, when the cam body 22 rotates, the output rod 7 reciprocates in the direction of the axis J7, and the counterweight 8 reciprocates in the direction opposite to the output rod 7.
  • the cam grooves 23 and 24 have forward end positions (turning points) 23a and 24a and backward end positions (turning points) 23b and 24b, respectively.
  • the forward end position 24a has a difference in the angle ⁇ in the direction opposite to the rotation direction of the outer rotor 12 (the arrow direction in FIG. 4) and the reverse end position 23b.
  • the backward end position 24b has a difference in angle ⁇ in the direction opposite to the rotational direction than the forward end position 23a. For this reason, after the output rod 7 reaches the forward end, the counterweight 8 reaches the backward end with a slight time difference. After the output rod 7 reaches the backward end, the counterweight 8 reaches the forward end with a slight time difference.
  • the electric motor 10 as a drive source is an outer rotor motor that can rotate at low speed and output high torque.
  • the rotational power of the outer rotor 12 of the electric motor 10 is converted into the reciprocating motion of the output rod 7 by the motion conversion mechanism 20.
  • the rotational output of the electric motor 10 is converted into the reciprocating motion of the output rod 7 without passing through a speed reduction mechanism using a conventional gear or the like.
  • the reciprocating tool 1 does not have a speed reduction mechanism. Therefore, the reciprocating tool 1 has a simple structure with a small number of parts. Alternatively, the reciprocating tool 1 has a short length in the axis J7 direction of the output rod 7. Alternatively, the reciprocating tool 1 has a small operation sound and excellent durability. Alternatively, the reciprocating tool 1 has high power transmission efficiency.
  • the electric motor 10 is an outer rotor motor, a large inertia force of the outer rotor 12 is generated.
  • the inertial force is converted into an axially reciprocating motion of the output rod 7 that varies greatly. Therefore, the outer rotor 12 can produce a flywheel effect in a reciprocating motion.
  • a cam groove 23 for reciprocating output rod and a cam groove 24 for reciprocating counterweight are directly provided on the outer periphery of the outer rotor 12.
  • the outer rotor 12 is integrally provided with a cam body 22. Therefore, the structure of the reciprocating tool 1 can be simplified.
  • the output rod 7 reciprocates by the cam mechanism 21 in which the cam follower 7a is engaged with the cam groove 23 of the cam body 22. Therefore, by appropriately setting the cam curve of the cam groove 23, the moving speed at the time of forward movement and the moving speed at the time of backward movement can be made different. For example, in the path from the forward end position 23a of the cam groove 23 to the backward end position 23b (the upper half circumference range in FIG. 4 and the backward movement range of the output rod 7), the inclination angle of the cam groove with respect to the circumferential direction is increased. Thereby, the retreating speed of the output rod 7 and the blade B can be increased. On the other hand, in the path from the backward end position 23b to the forward end position 23a (the lower half circumference range in FIG.
  • the forward movement range of the output rod 7), the inclination angle of the cam groove with respect to the circumferential direction is reduced.
  • the forward speed of the output rod 7 and the blade B can be made slower.
  • the working efficiency of the reciprocating tool 1 can be further increased.
  • Counterweight 8 reciprocates in the opposite direction as the output rod 7 reciprocates. Thereby, the vibration of the output rod 7 can be absorbed or reduced.
  • the counterweight 8 reciprocates on the output rod 7. Therefore, the increase in the number of parts of the reciprocating tool 1 is suppressed, and the structure of the reciprocating tool 1 can be simplified.
  • the moving speed of the counterweight 8 and the reciprocating timing can be set in accordance with the characteristics of the reciprocating tool 1 and the work content.
  • the counterweight 8 changes between forward and reverse, and the moving speed of the counterweight 8 becomes zero.
  • the output rod 7 changes between forward movement and reverse movement, and the moving speed of the output rod 7 becomes zero.
  • the forward end position 24a and the backward end position 24b are positioned so as to be delayed from the backward end position 23b and the forward end position 23a by an angle ⁇ in the rotation angle of the cam body 22, respectively. Thereby, the generation of vibration accompanying the reciprocating motion of the output rod 7 can be absorbed or suppressed more efficiently in accordance with the characteristics of the reciprocating tool 1.
  • the cam body 22 is provided with a lift cam portion 25 in addition to the cam grooves 23 and 24.
  • the lift cam portion 25 can give orbital motion to the output rod 7. Thereby, the cutting capability or work efficiency of the reciprocating tool 1 can be improved.
  • the cam body 22 is provided integrally with the outer rotor 12.
  • a cam groove 23, a cam groove 24, and a lift cam portion 25 are integrally provided on the cam body 22.
  • the cam groove 23 is used for reciprocating the output rod 7.
  • the cam groove 24 is used for reciprocating the counterweight 8.
  • the lift cam portion 25 is used for orbital movement of the output rod 7 along an elliptical locus. Therefore, the number of parts of the reciprocating tool 1 is suppressed, and the internal structure of the reciprocating tool 1 can be simplified.
  • the cam mechanism 21 may have cam grooves 23 and 24 formed in the cam body 22 as described above, and cam followers 7a and 8a inserted into the cam grooves 23 and 24, respectively.
  • the cam mechanism may have a cam convex portion formed on the cam body 22 and a roller follower that engages with the cam convex portion.
  • the cam projection has the same path as the cam grooves 23 and 24.
  • Each of the output rod and the counterweight is provided with a pair of roller followers.
  • a cam projection is installed between the pair of roller followers.
  • the cam body can have irregularities opposite to the irregularities of the cam body 22 described above.
  • the motion conversion mechanism 20 may have a crank mechanism instead of the cam mechanism 21 described above.
  • the electric motor is arranged vertically, and the crank plate is integrally provided on the outer rotor.
  • An eccentric roller provided on the crank plate is engaged with the output rod, and the output rod reciprocates.
  • a speed reduction mechanism such as a gear train can be omitted, and the reciprocating tool can be simplified.
  • the electric motor 10 may be a DC power supply type or an AC power supply type.
  • the reciprocating tool 1 may be a battery type reciprocating saw or an AC power source type reciprocating saw as described above.
  • the reciprocating tool 1 may be a reciprocating saw (reciprocating cutting tool) as described above, or may be another reciprocating tool that converts the rotation output of the electric motor into a reciprocating motion of the rod by a motion converting mechanism and outputs the reciprocating motion.
  • a jigsaw, hedge trimmer, hammer, hammer drill or the like may be used.

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

Abstract

A reciprocating tool (1) has an electric motor (10) as drive source, and a motion conversion mechanism (20). The motion conversion mechanism (20) converts the rotary output of the motor (10) to the reciprocating motion of an output rod (7). The electric motor (10) is an outer rotor motor provided with an outer rotor (12) that rotates on the outer periphery of a stator (11). The motion conversion mechanism (20) is disposed between the outer rotor (12) and the output rod (7).

Description

往復動工具Reciprocating tool
　本発明は、駆動モータの回転出力を直線運動に変換して出力する往復動工具に関する。往復動工具は、例えばレシプロソーと称される往復動切断工具、ジグソー、ヘッジトリマ、ハンマ、ハンマドリル等が含まれる。 The present invention relates to a reciprocating tool that converts a rotational output of a drive motor into a linear motion and outputs the linear motion. Examples of the reciprocating tool include a reciprocating cutting tool called a reciprocating saw, a jigsaw, a hedge trimmer, a hammer, a hammer drill, and the like.
　特開２００５－１４１１１号公報には、クランク機構等の運動変換機構を有するレシプロソーが開示される。運動変換機構は、本体に内装された駆動モータの回転出力を往復運動に変換し、ブレードが装着された出力ロッドを軸方向に往復運動させる。電動モータの回転軸は、出力ロッドに平行に配置される。電動モータの回転出力は、ベベルギヤによって減速されてクランク板に伝達される。 JP-A-2005-14111 discloses a reciprocating saw having a motion conversion mechanism such as a crank mechanism. The motion conversion mechanism converts the rotational output of the drive motor built in the main body into a reciprocating motion, and reciprocates the output rod on which the blade is mounted in the axial direction. The rotating shaft of the electric motor is arranged in parallel to the output rod. The rotational output of the electric motor is decelerated by the bevel gear and transmitted to the crank plate.
　特開２００９－２４１２４２号公報にもレシプロソーが開示される。電動モータの回転軸は、出力ロッドに直交する。電動モータの回転出力は、平歯車によって減速されてクランク板に伝達される。上記２つのレシプロソーでは、クランク板に取付けた偏心ローラの公転によって生じる往復動が出力ロッドの往復動として伝達される。上述するように一般的なレシプロソーでは、駆動モータの回転出力がギヤによって減速される。その後、回転出力が運動変換機構によって往復動に変換され、出力ロッドの往復動として出力される。したがって従来の一般的なレシプロソーは、減速機構に加えて運動変換機構を有するため部品点数が多い。 JP 2009-241242 also discloses a reciprocating saw. The rotating shaft of the electric motor is orthogonal to the output rod. The rotation output of the electric motor is decelerated by the spur gear and transmitted to the crank plate. In the two reciprocating saws, the reciprocating motion generated by the revolution of the eccentric roller attached to the crank plate is transmitted as the reciprocating motion of the output rod. As described above, in a general reciprocating saw, the rotational output of the drive motor is decelerated by the gear. Thereafter, the rotational output is converted into a reciprocating motion by the motion converting mechanism and output as a reciprocating motion of the output rod. Therefore, the conventional general reciprocating saw has a number of parts because it has a motion conversion mechanism in addition to a speed reduction mechanism.
　レシプロソーは、さらにオービタル機構またはカウンタウエイトを備えるものもある。したがって該レシプロソーは、部品点数がさらに多く、複雑な構造を有する。オービタル機構は、ブレードの切断効率を高めるために出力ロッドに対して僅かなオービタル運動を与える。カウンタウエイトは、出力ロッドの往復動に伴う振動を低減するために出力ロッドと反対方向に往復動する。 Some reciprocating saws are further equipped with an orbital mechanism or counterweight. Therefore, the reciprocating saw has a larger number of parts and a complicated structure. The orbital mechanism provides a slight orbital motion to the output rod to increase the blade cutting efficiency. The counterweight reciprocates in the opposite direction to the output rod in order to reduce vibration associated with the reciprocating movement of the output rod.
　したがって部品点数が少ないレシプロソー等の往復動工具が従来必要とされている。 Therefore, a reciprocating tool such as a reciprocating saw with a small number of parts is conventionally required.
　本発明の１つの特徴によると往復動工具は、駆動源としての電動モータと運動変換機構を有する。運動変換機構は、モータの回転出力を出力ロッドの往復運動に変換する。電動モータは、ステータの外周側にて回転するアウタロータを備えるアウタロータモータである。アウタロータと出力ロッドとの間に運動変換機構が介在される。 According to one feature of the present invention, the reciprocating tool has an electric motor as a drive source and a motion conversion mechanism. The motion conversion mechanism converts the rotational output of the motor into the reciprocating motion of the output rod. The electric motor is an outer rotor motor including an outer rotor that rotates on the outer peripheral side of the stator. A motion conversion mechanism is interposed between the outer rotor and the output rod.
　アウタロータモータは、低速回転かつ高トルクを出力可能である。アウタロータモータのアウタロータの回転動力は、運動変換機構を介して出力ロッドの往復動として出力される。したがって従来のギヤ等の減速機構を経ることなくアウタロータモータの回転出力が出力ロッドの往復動に変換されて出力される。そのため減速機構が不要であり、往復動工具の部品点数を少なくでき、往復動工具が簡易に構成され得る。 The outer rotor motor can rotate at low speed and output high torque. The rotational power of the outer rotor of the outer rotor motor is output as a reciprocating motion of the output rod through the motion conversion mechanism. Therefore, the rotational output of the outer rotor motor is converted into the reciprocating motion of the output rod and output without passing through a speed reduction mechanism such as a conventional gear. Therefore, a speed reduction mechanism is unnecessary, the number of parts of the reciprocating tool can be reduced, and the reciprocating tool can be easily configured.
　本発明の他の特徴によると運動変換機構がカム機構を備え得る。例えばカム機構は、カム体とカムフォロワを有し得る。カム体は、回転するアウタロータの外周に設けられ得る。カムフォロワは、出力ロッドに設けられてカム体のカム溝に係合する。カム溝のカム曲線を適切に設定することにより、アウタロータの回転をカム機構を経て出力ロッドの往復運動に変換できる。 According to another feature of the invention, the motion conversion mechanism may comprise a cam mechanism. For example, the cam mechanism may have a cam body and a cam follower. The cam body may be provided on the outer periphery of the rotating outer rotor. The cam follower is provided on the output rod and engages with the cam groove of the cam body. By appropriately setting the cam curve of the cam groove, the rotation of the outer rotor can be converted into the reciprocating motion of the output rod through the cam mechanism.
　本発明の他の特徴によると運動変換機構は、カム溝とカム溝に嵌合するフォロワを有するカム機構を備え得る。カム溝とフォロワの一方がアウタロータの外周面に設けられ、他方が出力ロッドに設けられ得る。 According to another feature of the invention, the motion conversion mechanism may comprise a cam mechanism having a cam groove and a follower that fits into the cam groove. One of the cam groove and the follower may be provided on the outer peripheral surface of the outer rotor, and the other may be provided on the output rod.
　したがってカム溝またはフォロワの一方が電動モータのアウタロータの外周面に直接設けられる。これにより往復動工具は、簡易に構成され得る。あるいは往復動工具の部品点数の増大を抑制し得る。 Therefore, one of the cam groove or the follower is directly provided on the outer peripheral surface of the outer rotor of the electric motor. Thereby, a reciprocating tool can be comprised simply. Or the increase in the number of parts of a reciprocating tool can be suppressed.
　本発明の他の特徴によると運動変換機構は、出力ロッドの前進速度と後退速度を相違させる構造を有し得る。これにより往復動工具の作業効率を高め得る。 According to another feature of the present invention, the motion conversion mechanism may have a structure in which the forward speed and the reverse speed of the output rod are different. Thereby, the working efficiency of the reciprocating tool can be improved.
　本発明の他の特徴によると往復動工具は、出力ロッドと反対方向に往復動するカウンタウエイトを備え得る。これにより出力ロッドの往復動による振動を抑制し得る。 According to another feature of the invention, the reciprocating tool may comprise a counterweight that reciprocates in the opposite direction to the output rod. Thereby, the vibration by the reciprocating motion of the output rod can be suppressed.
　本発明の他の特徴によるとカウンタウエイトが出力ロッドに同軸に支持され得る。したがってカウンタウエイトが出力ロッドによって往復動可能に支持され得る。これにより部品点数の増大が抑制され、往復動工具が簡易に構成され得る。 According to another feature of the invention, the counterweight can be supported coaxially on the output rod. Therefore, the counterweight can be supported by the output rod so as to be able to reciprocate. As a result, an increase in the number of parts can be suppressed, and the reciprocating tool can be simply configured.
　本発明の他の特徴によるとカウンタウエイトの移動速度がゼロになる往復動の折返し時がある。出力ロッドの移動速度がゼロになる往復動の折返し時がある。往復動工具は、カウンタウエイトの折返し時が出力ロッドの折返し時に対して一定時間の遅れとなる構造を備え得る。したがって出力ロッドの往復動に伴う現実の振動を往復動工具の全体特性に合わせてより効果的に抑制できる。 According to another feature of the present invention, there is a turn-back time of the reciprocating motion in which the counterweight moving speed becomes zero. There are times when the output rod moves back and forth when it moves to zero. The reciprocating tool may be provided with a structure in which the counterweight is turned back at a certain time with respect to the output rod. Therefore, the actual vibration accompanying the reciprocating motion of the output rod can be more effectively suppressed in accordance with the overall characteristics of the reciprocating tool.
　本発明の他の特徴によると出力ロッドにオービタル運動を与えるためのカム部がアウタロータに設けられ得る。したがってアウタロータの回転を利用して出力ロッドに僅かなオービタル運動が与えられ得る。そのため該構造は、往復動工具の部品点数の増大を抑制しつつ、または往復動工具が複雑になることを抑制しつつ、設けられ得る。 According to another aspect of the present invention, the outer rotor may be provided with a cam portion for imparting orbital motion to the output rod. Therefore, slight orbital motion can be given to the output rod by utilizing the rotation of the outer rotor. Therefore, the structure can be provided while suppressing an increase in the number of parts of the reciprocating tool or suppressing the reciprocating tool from becoming complicated.
出力ロッドが前進端に到達した時点における往復動工具の縦断面図である。It is a longitudinal cross-sectional view of the reciprocating tool when the output rod reaches the forward end. 出力ロッドが後退端に到達した時点における往復動工具の縦断面図である。It is a longitudinal cross-sectional view of the reciprocating tool when the output rod reaches the retracted end. 運動変換機構としてカム機構を構成するカム体の斜視図である。It is a perspective view of the cam body which comprises a cam mechanism as a motion conversion mechanism. カム体の展開図である。It is an expanded view of a cam body.
　本発明の実施形態を図１～４に基づいて説明する。往復動工具１は、いわゆるレシプロソーと称される往復動切断工具である。往復動工具１は、工具本体２とハンドル３を備える。工具本体２は、駆動源として電動モータ１０を内装する。ハンドル３は、Ｄ形であって、工具本体２の後部に設けられる。ハンドル３の下部に充電式のバッテリパック４が装着される。バッテリパック４は、リチウムイオンバッテリである。バッテリパック４は、工具本体２から取外され充電され、これにより繰り返し使用され得る。ハンドル３に設けられたスイッチレバー５を指先で引き操作すると、バッテリパック４を電源として電動モータ１０が起動する。工具本体２の前部には、切断材に当てられるシュー６が設けられる。シュー６は、工具本体２の前部から前方へ突き出す。 Embodiments of the present invention will be described with reference to FIGS. The reciprocating tool 1 is a reciprocating cutting tool called a so-called reciprocating saw. The reciprocating tool 1 includes a tool body 2 and a handle 3. The tool body 2 includes an electric motor 10 as a drive source. The handle 3 is D-shaped and is provided at the rear part of the tool body 2. A rechargeable battery pack 4 is attached to the lower part of the handle 3. The battery pack 4 is a lithium ion battery. The battery pack 4 can be removed from the tool body 2 and charged, thereby being used repeatedly. When the switch lever 5 provided on the handle 3 is pulled with a fingertip, the electric motor 10 is activated using the battery pack 4 as a power source. A shoe 6 applied to the cutting material is provided at the front portion of the tool body 2. The shoe 6 protrudes forward from the front portion of the tool body 2.
　工具本体２は、電動モータ１０と運動変換機構２０と出力ロッド７を備える。電動モータ１０は、いわゆるアウタロータモータである。アウタロータモータは、インナロータモータに比して低速回転かつ高トルクを出力できる。アウタロータモータは、回転しないステータ１１と、円筒形のアウタロータ１２を備える。アウタロータ１２の回転は、電動モータ１０の回転出力である。 The tool body 2 includes an electric motor 10, a motion conversion mechanism 20, and an output rod 7. The electric motor 10 is a so-called outer rotor motor. The outer rotor motor can rotate at a lower speed and output higher torque than the inner rotor motor. The outer rotor motor includes a stator 11 that does not rotate and a cylindrical outer rotor 12. The rotation of the outer rotor 12 is a rotation output of the electric motor 10.
　ステータ１１は、支軸１３を介して本体ハウジング２ａに回転不能に固定される。アウタロータ１２は、支軸１３を介してステータ１１の外周側に回転可能に支持される。アウタロータ１２は、支軸１３の軸線Ｊ１３回りに回転できる。 The stator 11 is fixed to the main body housing 2a through the support shaft 13 so as not to rotate. The outer rotor 12 is rotatably supported on the outer peripheral side of the stator 11 via the support shaft 13. The outer rotor 12 can rotate about the axis J13 of the support shaft 13.
　往復動工具１は、運動変換機構２０としてカム機構２１を有する。カム機構２１は、カム体（円筒溝カム）２２とカムフォロワ７ａを備える。カム体２２は、アウタロータ１２と同一部材にて一体に構成され得る。カム体２２は、アウタロータ１２の周囲に沿って一体に設けられ得る。図３，４に示すようにカム体２２（アウタロータ１２）は、円筒形状を有する。カム体２２の外周面には、カム溝２３，２４が形成される。 The reciprocating tool 1 has a cam mechanism 21 as a motion conversion mechanism 20. The cam mechanism 21 includes a cam body (cylindrical groove cam) 22 and a cam follower 7a. The cam body 22 can be integrally formed of the same member as the outer rotor 12. The cam body 22 can be integrally provided along the periphery of the outer rotor 12. As shown in FIGS. 3 and 4, the cam body 22 (outer rotor 12) has a cylindrical shape. Cam grooves 23 and 24 are formed on the outer peripheral surface of the cam body 22.
　前側に位置するカム溝２３は、出力ロッド７を往復動させるために利用される。カム溝２３は、アウタロータ１２を一周しかつ軸線Ｊ１３方向に変位する。軸線Ｊ１３方向の変位は、出力ロッド７の往復動距離に相当する。後ろ側に位置するカム溝２４は、カウンタウエイト８を往復動させるために利用される。カム溝２４は、アウタロータ１２を一周しかつ軸線Ｊ１３方向に変位する。軸線Ｊ１３方向の変位は、カウンタウエイト８の往復動距離に相当する。カム溝２４の軸線Ｊ１３方向の変位は、カム溝２３の軸線Ｊ１３方向の変位と逆向きである。 The cam groove 23 located on the front side is used for reciprocating the output rod 7. The cam groove 23 goes around the outer rotor 12 and is displaced in the direction of the axis J13. The displacement in the direction of the axis J13 corresponds to the reciprocating distance of the output rod 7. The cam groove 24 located on the rear side is used for reciprocating the counterweight 8. The cam groove 24 goes around the outer rotor 12 and is displaced in the direction of the axis J13. The displacement in the direction of the axis J13 corresponds to the reciprocating distance of the counterweight 8. The displacement of the cam groove 24 in the direction of the axis J13 is opposite to the displacement of the cam groove 23 in the direction of the axis J13.
　カム溝２３には、出力ロッド７に一体に設けられたカムフォロワ７ａが挿入される。カム溝２４には、カウンタウエイト８のカムフォロワ８ａが挿入される。カウンタウエイト８は、出力ロッド７の後部に支持される。カウンタウエイト８は、出力ロッド７に同軸でかつ相対的に軸方向に往復動可能に支持される。 In the cam groove 23, a cam follower 7a provided integrally with the output rod 7 is inserted. In the cam groove 24, the cam follower 8a of the counterweight 8 is inserted. The counterweight 8 is supported on the rear part of the output rod 7. The counterweight 8 is supported coaxially with the output rod 7 and relatively reciprocally movable in the axial direction.
　出力ロッド７の前後部は、軸受け１５，１６によって本体ハウジング２ａに取付けられる。出力ロッド７は、本体ハウジング２ａに対して軸線Ｊ７方向に往復動可能に支持される。前側に位置する軸受け１５は、出力ロッド７を一定角度で上下に傾動可能に支持する。後ろ側に位置する軸受け１６は、本体ハウジング２ａに上下動可能に支持され、圧縮ばね１７によって下方に付勢される。 The front and rear portions of the output rod 7 are attached to the main body housing 2a by bearings 15 and 16. The output rod 7 is supported so as to be able to reciprocate in the direction of the axis J7 with respect to the main body housing 2a. The bearing 15 located on the front side supports the output rod 7 so as to be tiltable up and down at a constant angle. The bearing 16 located on the rear side is supported by the main body housing 2 a so as to be movable up and down, and is urged downward by a compression spring 17.
　軸受け１６の外周には、オービタルローラ１８が取付けられる。オービタルローラ１８は、アウタロータ１２（カム体２２）の後部に設けたリフトカム部２５（図３，４参照）に載せられる。アウタロータ１２は、圧縮ばね１７によってリフトカム部２５に押付けられる。カム体２２の回転によってリフトカム部２５が回転し、リフトカム部２５がオービタルローラ１８を上下動させる。オービタルローラ１８の上下動により軸受け１６が上下動し、出力ロッド７の後部が上下動する。したがって出力ロッド７は、軸線Ｊ７方向の往復動し、かつ出力ロッド７の後部が上下動する。これにより出力ロッド７にいわゆるオービタル運動が与えられる。 An orbital roller 18 is attached to the outer periphery of the bearing 16. The orbital roller 18 is placed on a lift cam portion 25 (see FIGS. 3 and 4) provided at the rear portion of the outer rotor 12 (cam body 22). The outer rotor 12 is pressed against the lift cam portion 25 by the compression spring 17. The lift cam portion 25 is rotated by the rotation of the cam body 22, and the lift cam portion 25 moves the orbital roller 18 up and down. As the orbital roller 18 moves up and down, the bearing 16 moves up and down, and the rear portion of the output rod 7 moves up and down. Accordingly, the output rod 7 reciprocates in the direction of the axis J7, and the rear portion of the output rod 7 moves up and down. As a result, a so-called orbital motion is given to the output rod 7.
　出力ロッド７の前端にワンタッチ脱着式のクランプ装置９が取付けられる。クランプ装置９によって出力ロッド７の前端にブレードＢが装着される。 The one-touch detachable clamping device 9 is attached to the front end of the output rod 7. The blade B is attached to the front end of the output rod 7 by the clamping device 9.
　使用者がハンドル３を把持し、手の指先でスイッチレバー５を引き操作する。これにより電動モータ１０が起動し、カム体２２（アウタロータ１２）が軸線Ｊ１３回りに回転する。カム体２２のカム溝２３には出力ロッド７のカムフォロワ７ａが係合され、カム溝２４にはカウンタウエイト８のカムフォロワ８ａが係合されている。したがってカム体２２が回転すると、出力ロッド７が軸線Ｊ７方向に往復動し、カウンタウエイト８が出力ロッド７と反対方向に往復動する。 The user grips the handle 3 and pulls the switch lever 5 with the fingertip of the hand. As a result, the electric motor 10 is activated, and the cam body 22 (outer rotor 12) rotates about the axis J13. A cam follower 7 a of the output rod 7 is engaged with the cam groove 23 of the cam body 22, and a cam follower 8 a of the counterweight 8 is engaged with the cam groove 24. Therefore, when the cam body 22 rotates, the output rod 7 reciprocates in the direction of the axis J7, and the counterweight 8 reciprocates in the direction opposite to the output rod 7.
　カム体２２が回転すると、リフトカム部２５によって出力ロッド７の後部を支持する軸受け１６が上下動する。これにより出力ロッド７にオービタル運動が与えられる。図２に示すように出力ロッド７が後退端に至ると出力ロッド７の後部が最も上方に位置する。図３に示すように出力ロッド７が前進端に至ると出力ロッド７の後部が最も下方に位置する。このため出力ロッド７とブレードＢは、図１、２において時計回りに楕円軌跡に沿って往復動する。 When the cam body 22 rotates, the bearing 16 that supports the rear portion of the output rod 7 is moved up and down by the lift cam portion 25. Thereby, an orbital motion is given to the output rod 7. As shown in FIG. 2, when the output rod 7 reaches the retracted end, the rear portion of the output rod 7 is located at the uppermost position. As shown in FIG. 3, when the output rod 7 reaches the forward end, the rear portion of the output rod 7 is positioned at the lowest position. For this reason, the output rod 7 and the blade B reciprocate along the elliptical locus clockwise in FIGS.
　図４に示すようにカム溝２３，２４は、それぞれ前進端位置（折返し点）２３ａ，２４ａと後退端位置（折返し点）２３ｂ，２４ｂを有する。前進端位置２４ａは、後退端位置２３ｂよりもアウタロータ１２の回転方向（図４の矢印方向）と逆方向への角度θの差を有する。後退端位置２４ｂは、前進端位置２３ａよりも回転方向と逆方向への角度θの差を有する。このため出力ロッド７が前進端に至った後に、僅かな時間差をおいてカウンタウエイト８が後退端に至る。出力ロッド７が後退端に至った後に、僅かな時間差をおいてカウンタウエイト８が前進端に至る。 As shown in FIG. 4, the cam grooves 23 and 24 have forward end positions (turning points) 23a and 24a and backward end positions (turning points) 23b and 24b, respectively. The forward end position 24a has a difference in the angle θ in the direction opposite to the rotation direction of the outer rotor 12 (the arrow direction in FIG. 4) and the reverse end position 23b. The backward end position 24b has a difference in angle θ in the direction opposite to the rotational direction than the forward end position 23a. For this reason, after the output rod 7 reaches the forward end, the counterweight 8 reaches the backward end with a slight time difference. After the output rod 7 reaches the backward end, the counterweight 8 reaches the forward end with a slight time difference.
　以上のように駆動源としての電動モータ１０は、低速回転かつ高トルクを出力できるアウタロータモータである。電動モータ１０のアウタロータ１２の回転動力は、運動変換機構２０によって出力ロッド７の往復動に変換される。このため従来のギヤ等による減速機構を経ることなく電動モータ１０の回転出力が出力ロッド７の往復動に変換される。 As described above, the electric motor 10 as a drive source is an outer rotor motor that can rotate at low speed and output high torque. The rotational power of the outer rotor 12 of the electric motor 10 is converted into the reciprocating motion of the output rod 7 by the motion conversion mechanism 20. For this reason, the rotational output of the electric motor 10 is converted into the reciprocating motion of the output rod 7 without passing through a speed reduction mechanism using a conventional gear or the like.
　したがって往復動工具１は、減速機構を有しない。そのため往復動工具１は、部品点数が少なく、簡易な構造である。あるいは往復動工具１は、出力ロッド７の軸線Ｊ７方向の長さが短い。あるいは往復動工具１は、動作音が小さく、耐久性にも優れる。あるいは往復動工具１は、高い動力伝達効率を有する。 Therefore, the reciprocating tool 1 does not have a speed reduction mechanism. Therefore, the reciprocating tool 1 has a simple structure with a small number of parts. Alternatively, the reciprocating tool 1 has a short length in the axis J7 direction of the output rod 7. Alternatively, the reciprocating tool 1 has a small operation sound and excellent durability. Alternatively, the reciprocating tool 1 has high power transmission efficiency.
　電動モータ１０は、アウタロータモータであるため、アウタロータ１２の大きな慣性力を生じる。該慣性力は、大きく変化する出力ロッド７の軸方向の往復運動に変換される。したがってアウタロータ１２は、往復運動においてフライホイール効果を生じ得る。 Since the electric motor 10 is an outer rotor motor, a large inertia force of the outer rotor 12 is generated. The inertial force is converted into an axially reciprocating motion of the output rod 7 that varies greatly. Therefore, the outer rotor 12 can produce a flywheel effect in a reciprocating motion.
　アウタロータ１２の外周に出力ロッド往復動用のカム溝２３とカウンタウエイト往復動用のカム溝２４が直接設けられる。同アウタロータ１２にはカム体２２が一体に設けられる。したがって往復動工具１の構造は、簡略化され得る。 A cam groove 23 for reciprocating output rod and a cam groove 24 for reciprocating counterweight are directly provided on the outer periphery of the outer rotor 12. The outer rotor 12 is integrally provided with a cam body 22. Therefore, the structure of the reciprocating tool 1 can be simplified.
　出力ロッド７は、カム体２２のカム溝２３にカムフォロワ７ａを係合させたカム機構２１により往復動する。したがってカム溝２３のカム曲線を適切に設定することにより、前進時の移動速度と後退時の移動速度を異ならせ得る。例えば、カム溝２３の前進端位置２３ａから後退端位置２３ｂに至る経路（図４において上側半周の範囲、出力ロッド７の復動範囲）では、カム溝の周方向に対する傾斜角度を大きくする。これにより出力ロッド７及びブレードＢの後退速度を速くできる。一方、後退端位置２３ｂから前進端位置２３ａに至る経路（図４において下側半周の範囲、出力ロッド７の往動範囲）では、カム溝の周方向に対する傾斜角度を小さくする。これにより出力ロッド７及びブレードＢの前進速度をより遅くできる。出力ロッド７の前進速度と後退速度を異ならせることで、往復動工具１の作業効率を一層高めることができる。 The output rod 7 reciprocates by the cam mechanism 21 in which the cam follower 7a is engaged with the cam groove 23 of the cam body 22. Therefore, by appropriately setting the cam curve of the cam groove 23, the moving speed at the time of forward movement and the moving speed at the time of backward movement can be made different. For example, in the path from the forward end position 23a of the cam groove 23 to the backward end position 23b (the upper half circumference range in FIG. 4 and the backward movement range of the output rod 7), the inclination angle of the cam groove with respect to the circumferential direction is increased. Thereby, the retreating speed of the output rod 7 and the blade B can be increased. On the other hand, in the path from the backward end position 23b to the forward end position 23a (the lower half circumference range in FIG. 4, the forward movement range of the output rod 7), the inclination angle of the cam groove with respect to the circumferential direction is reduced. Thereby, the forward speed of the output rod 7 and the blade B can be made slower. By making the forward speed and the reverse speed of the output rod 7 different, the working efficiency of the reciprocating tool 1 can be further increased.
　出力ロッド７の往復動に合わせてカウンタウエイト８が反対方向に往復動する。これにより出力ロッド７の振動が吸収あるいは低減され得る。カウンタウエイト８が出力ロッド７上を往復動する。そのため往復動工具１の部品点数の増大が抑制され、往復動工具１の構造が簡略され得る。 ¡Counterweight 8 reciprocates in the opposite direction as the output rod 7 reciprocates. Thereby, the vibration of the output rod 7 can be absorbed or reduced. The counterweight 8 reciprocates on the output rod 7. Therefore, the increase in the number of parts of the reciprocating tool 1 is suppressed, and the structure of the reciprocating tool 1 can be simplified.
　カム溝２４をカム溝２３に対して適切に設定することで、往復動工具１の特性や作業内容に合わせてカウンタウエイト８の移動速度と往復動のタイミングを設定できる。 By appropriately setting the cam groove 24 with respect to the cam groove 23, the moving speed of the counterweight 8 and the reciprocating timing can be set in accordance with the characteristics of the reciprocating tool 1 and the work content.
　前進端位置２４ａと後退端位置２４ｂでは、カウンタウエイト８が前進と後進の間で変わり、カウンタウエイト８の移動速度がゼロになる。後退端位置２３ｂと前進端位置２３ａでは、出力ロッド７が前進と後進の間で変わり、出力ロッド７の移動速度がゼロになる。前進端位置２４ａと後退端位置２４ｂは、後退端位置２３ｂと前進端位置２３ａからそれぞれカム体２２の回転角度において角度θだけ遅れるように位置する。これにより出力ロッド７の往復動に伴う振動の発生が、往復動工具１の特性に合わせてより効率よく吸収または抑制され得る。 At the forward end position 24a and the backward end position 24b, the counterweight 8 changes between forward and reverse, and the moving speed of the counterweight 8 becomes zero. At the backward end position 23b and the forward end position 23a, the output rod 7 changes between forward movement and reverse movement, and the moving speed of the output rod 7 becomes zero. The forward end position 24a and the backward end position 24b are positioned so as to be delayed from the backward end position 23b and the forward end position 23a by an angle θ in the rotation angle of the cam body 22, respectively. Thereby, the generation of vibration accompanying the reciprocating motion of the output rod 7 can be absorbed or suppressed more efficiently in accordance with the characteristics of the reciprocating tool 1.
　カム体２２には、カム溝２３，２４に加えてリフトカム部２５が設けられる。リフトカム部２５は、出力ロッド７にオービタル運動を与え得る。これにより往復動工具１の切断能力または作業効率が高められ得る。 The cam body 22 is provided with a lift cam portion 25 in addition to the cam grooves 23 and 24. The lift cam portion 25 can give orbital motion to the output rod 7. Thereby, the cutting capability or work efficiency of the reciprocating tool 1 can be improved.
　アウタロータ１２にカム体２２が一体に設けられる。カム体２２にはカム溝２３とカム溝２４とリフトカム部２５が一体に設けられる。カム溝２３は、出力ロッド７を往復動させるために用いられる。カム溝２４は、カウンタウエイト８を往復動させるために用いられる。リフトカム部２５は、出力ロッド７を楕円軌跡に沿ってオービタル運動させるために用いられる。したがって往復動工具１の部品点数が抑制され、往復動工具１の内部構造が簡略され得る。 The cam body 22 is provided integrally with the outer rotor 12. A cam groove 23, a cam groove 24, and a lift cam portion 25 are integrally provided on the cam body 22. The cam groove 23 is used for reciprocating the output rod 7. The cam groove 24 is used for reciprocating the counterweight 8. The lift cam portion 25 is used for orbital movement of the output rod 7 along an elliptical locus. Therefore, the number of parts of the reciprocating tool 1 is suppressed, and the internal structure of the reciprocating tool 1 can be simplified.
　本発明の形態を上記構造を参照して説明したが、本発明の目的を逸脱せずに多くの交代、改良、変更が可能であることは当業者であれば明らかである。したがって本発明の形態は、添付された請求項の精神と目的を逸脱しない全ての交代、改良、変更を含み得る。例えば本発明の形態は、前記特別な構造に限定されず、下記のように変更が可能である。 Although the embodiments of the present invention have been described with reference to the above structure, it will be apparent to those skilled in the art that many substitutions, improvements, and changes can be made without departing from the object of the present invention. Accordingly, aspects of the invention may include all alterations, modifications, and changes that do not depart from the spirit and scope of the appended claims. For example, the form of the present invention is not limited to the special structure, and can be modified as follows.
　カム機構２１は、上述するようにカム体２２に形成されたカム溝２３，２４と、カム溝２３，２４のそれぞれに挿入されるカムフォロワ７ａ，８ａを有しても良い。これに代えてカム機構は、カム体２２に形成されたカム凸部と、カム凸部に係合するローラフォロワを有していても良い。カム凸部は、カム溝２３，２４と同じ経路を有する。出力ロッドとカウンタウエイトのそれぞれには、各一対のローラフォロワが設けられる。一対のローラフォロワの間にカム凸部が設置される。すなわちカム体は、上述するカム体２２の凹凸に対して逆の凹凸を有し得る。 The cam mechanism 21 may have cam grooves 23 and 24 formed in the cam body 22 as described above, and cam followers 7a and 8a inserted into the cam grooves 23 and 24, respectively. Instead of this, the cam mechanism may have a cam convex portion formed on the cam body 22 and a roller follower that engages with the cam convex portion. The cam projection has the same path as the cam grooves 23 and 24. Each of the output rod and the counterweight is provided with a pair of roller followers. A cam projection is installed between the pair of roller followers. In other words, the cam body can have irregularities opposite to the irregularities of the cam body 22 described above.
　運動変換機構２０は、上述のカム機構２１に代えてクランク機構を有していても良い。例えば電動モータが縦置きに配置され、アウタロータにクランク板が一体に設けられる。クランク板に設けた偏心ローラが出力ロッドに係合され、出力ロッドが往復動する。この構成によってもギヤ列等の減速機構が省略され、往復動工具が簡略され得る。 The motion conversion mechanism 20 may have a crank mechanism instead of the cam mechanism 21 described above. For example, the electric motor is arranged vertically, and the crank plate is integrally provided on the outer rotor. An eccentric roller provided on the crank plate is engaged with the output rod, and the output rod reciprocates. Also with this configuration, a speed reduction mechanism such as a gear train can be omitted, and the reciprocating tool can be simplified.
　電動モータ１０は、直流電源式でも良いし、交流電源式でも良い。 The electric motor 10 may be a DC power supply type or an AC power supply type.
　往復動工具１は、上述するようにバッテリ式のレシプロソーでも良いし、交流電源式のレシプロソーでも良い。 The reciprocating tool 1 may be a battery type reciprocating saw or an AC power source type reciprocating saw as described above.
　往復動工具１は、上述するようにレシプロソー（往復動切断工具）でも良いし、電動モータの回転出力を運動変換機構によってロッドの往復運動に変換して出力する他の往復動工具でも良い。例えばジグソー、ヘッジトリマ、ハンマ、ハンマドリル等でも良い。 The reciprocating tool 1 may be a reciprocating saw (reciprocating cutting tool) as described above, or may be another reciprocating tool that converts the rotation output of the electric motor into a reciprocating motion of the rod by a motion converting mechanism and outputs the reciprocating motion. For example, a jigsaw, hedge trimmer, hammer, hammer drill or the like may be used.

Claims (8)

  1. 　往復動工具であって、
    　駆動源としての電動モータと、前記モータの回転出力を出力ロッドの往復運動に変換する運動変換機構を有し、
    　前記電動モータは、ステータの外周側にて回転するアウタロータを備えるアウタロータモータであり、前記アウタロータと前記出力ロッドとの間に前記運動変換機構が介在される往復動工具。     A reciprocating tool,
    An electric motor as a drive source, and a motion conversion mechanism that converts the rotational output of the motor into a reciprocating motion of an output rod;
    The electric motor is an outer rotor motor including an outer rotor that rotates on an outer peripheral side of a stator, and the reciprocating tool in which the motion conversion mechanism is interposed between the outer rotor and the output rod.
  2. 　請求項１に記載の往復動工具であって、
    　前記運動変換機構がカム機構を備える往復動工具。     The reciprocating tool according to claim 1,
    A reciprocating tool in which the motion conversion mechanism includes a cam mechanism.
  3. 　請求項１又は２に記載の往復動工具であって、
    　前記運動変換機構は、カム溝と前記カム溝に嵌合するフォロワを有するカム機構を備え、前記カム溝と前記フォロワの一方が前記アウタロータの外周面に設けられ、他方が前記出力ロッドに設けられる往復動工具。     The reciprocating tool according to claim 1 or 2,
    The motion conversion mechanism includes a cam mechanism having a cam groove and a follower that fits into the cam groove, and one of the cam groove and the follower is provided on an outer peripheral surface of the outer rotor, and the other is provided on the output rod. Reciprocating tool.
  4. 　請求項１～３の何れか１つに記載の往復動工具であって、
    　前記運動変換機構は、前記出力ロッドの前進速度と後退速度を相違させる構造を有する往復動工具。     Reciprocating tool according to any one of claims 1 to 3,
    The motion conversion mechanism is a reciprocating tool having a structure in which a forward speed and a reverse speed of the output rod are different.
  5. 　請求項１～４の何れか１つに記載の往復動工具であって、
    　前記出力ロッドと反対方向に往復動するカウンタウエイトを備える往復動工具。     Reciprocating tool according to any one of claims 1 to 4,
    A reciprocating tool comprising a counterweight that reciprocates in a direction opposite to the output rod.
  6. 　請求項５に記載の往復動工具であって、
    　前記カウンタウエイトが前記出力ロッドに同軸に支持される往復動工具。     The reciprocating tool according to claim 5,
    A reciprocating tool in which the counterweight is coaxially supported by the output rod.
  7. 　請求項５または６に記載の往復動工具であって、
    　前記カウンタウエイトの移動速度がゼロになる往復動の折返し時が、前記出力ロッドの移動速度がゼロになる往復動の折返し時に対して一定時間の遅れとなる構造を備える往復動工具。     The reciprocating tool according to claim 5 or 6,
    A reciprocating tool comprising a structure in which a reciprocating motion when the counterweight moving speed becomes zero is delayed by a fixed time from a reciprocating time when the output rod moving speed becomes zero.
  8. 　請求項１～７の何れか１つに記載した往復動工具であって、
    　前記出力ロッドにオービタル運動を与えるためのカム部が前記アウタロータに設けられる往復動工具。     Reciprocating tool according to any one of claims 1 to 7,
    A reciprocating tool in which a cam portion for giving orbital motion to the output rod is provided in the outer rotor.
PCT/JP2012/083591 2012-01-16 2012-12-26 Reciprocating tool WO2013108557A1 (en)

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JP2015027716A (en) * 2013-07-30 2015-02-12 日立工機株式会社 Electric tool
CN107442855A (en) * 2016-05-30 2017-12-08 南京德朔实业有限公司 Electric saw

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JP2000291762A (en) * 1999-04-13 2000-10-20 Makita Corp Reciprocating mechanism and electric tool using the same
JP2002079417A (en) * 2000-09-08 2002-03-19 Hitachi Koki Co Ltd Cutting mechanism of saber saw
JP2005014111A (en) * 2003-06-23 2005-01-20 Makita Corp Reciprocating power tool
JP2006150571A (en) * 2004-12-01 2006-06-15 Nidec Shibaura Corp Power tool
JP2007098562A (en) * 2005-09-07 2007-04-19 Yokota Kogyo Kk Electric impact tightening tool
JP2011156629A (en) * 2010-02-02 2011-08-18 Makita Corp Motor control device, electric power tool, and program

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015027716A (en) * 2013-07-30 2015-02-12 日立工機株式会社 Electric tool
CN107442855A (en) * 2016-05-30 2017-12-08 南京德朔实业有限公司 Electric saw
CN107442855B (en) * 2016-05-30 2019-03-08 南京德朔实业有限公司 Electric saw

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