WO2022244615A1 - 作業機 - Google Patents

作業機 Download PDF

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Publication number
WO2022244615A1
WO2022244615A1 PCT/JP2022/019286 JP2022019286W WO2022244615A1 WO 2022244615 A1 WO2022244615 A1 WO 2022244615A1 JP 2022019286 W JP2022019286 W JP 2022019286W WO 2022244615 A1 WO2022244615 A1 WO 2022244615A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
bearing
spindle
motor
drive shaft
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2022/019286
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
健悟 田村
康二 鈴木
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koki Holdings Co Ltd
Original Assignee
Koki Holdings Co Ltd
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 Koki Holdings Co Ltd filed Critical Koki Holdings Co Ltd
Priority to DE112022002666.9T priority Critical patent/DE112022002666T5/de
Priority to JP2023522594A priority patent/JP7622828B2/ja
Priority to CN202280035636.2A priority patent/CN117320845A/zh
Priority to US18/561,277 priority patent/US20240253203A1/en
Publication of WO2022244615A1 publication Critical patent/WO2022244615A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion

Definitions

  • the present invention relates to working machines.
  • a gear mechanism is provided on the front side of the rotating shaft of the motor, and the driving force of the motor is transmitted to the tip tool provided on the anvil by the gear mechanism.
  • the gear mechanism includes a spindle provided on the front side of the rotating shaft, a planetary gear rotatably supported by the spindle and meshed with a pinion gear of the rotating shaft, an outer gear meshed with the planetary gear, and a spindle capable of rotating. and a bearing that supports the That is, the gear mechanism is configured as a so-called planetary gear mechanism.
  • the bearings and the planetary gears are arranged side by side in the axial direction (front-rear direction) of the rotating shaft.
  • the bearing is arranged on the rear side in the axial direction (front-to-rear direction) of the rotating shaft with respect to the ring gear. Therefore, the size of the impact driver tends to increase in the axial direction of the rotating shaft. Further, in the operation of the impact driver, the operation is performed on the workpiece on the front side with respect to the impact driver. For this reason, if the size of the impact driver in the front-rear direction increases, the front-rear distance from the workpiece increases, which may reduce the workability of the impact driver.
  • An object of the present invention is to provide a work machine that can be downsized in consideration of the above facts.
  • One or more embodiments of the present invention comprise a motor having an axially extending drive shaft, a motor gear portion provided on the drive shaft, and a spindle provided on one axial side of the motor. and a transmission mechanism that is connected to the motor gear unit and transmits the rotational force of the drive shaft to the spindle to rotate the spindle, wherein the transmission mechanism is rotatably provided to the spindle, and the motor gear and a bearing that rotatably supports the spindle and is arranged radially outward of the drive shaft with respect to the idle gear.
  • the transmission mechanism includes a support portion formed on the other side of the spindle in the axial direction, the idle gear is rotatably provided on the support portion,
  • the bearing is a work machine configured to rotatably support the support section.
  • One or more embodiments of the present invention are a work machine in which the motor gear portion, the idle gear, and the bearing are arranged side by side in the radial direction of the drive shaft.
  • the support portion has a fitting portion fitted into the bearing, and the fitting portion and the idle gear are arranged in a circumferential direction of the drive shaft. It is a work machine arranged with
  • the transmission mechanism has a ring-shaped ring gear meshed with the idle gear, and the ring gear is arranged radially of the drive shaft with respect to the idle gear.
  • the working machine is arranged outside and arranged on the other side in the axial direction with respect to the bearing.
  • the support includes a first support that is rotatably supported by the bearing, and a first support that is disposed on the other side of the first support in the axial direction.
  • the working machine includes a second support portion, and a support shaft that spans the first support portion and the second support portion and rotatably supports the idle gear.
  • the bearing is fitted into a concave case opened to one side in the axial direction
  • the first support portion is provided with a restricting portion
  • a restricting portion restricts movement of the bearing to one side in the axial direction.
  • One or more embodiments of the present invention is a work machine in which the ring gear is arranged radially outward of the drive shaft with respect to the second support portion.
  • the idle gear includes a large-diameter gear portion meshed with the motor gear portion, a small-diameter gear portion meshed with the ring gear and having a smaller diameter than the large-diameter gear portion, It is a work machine configured including
  • One or more embodiments of the present invention is a work machine in which the bearing is arranged radially outward of the drive shaft with respect to the large diameter gear portion.
  • One or more embodiments of the present invention comprise a motor having an axially extending drive shaft, a motor gear portion provided on the drive shaft, and a spindle provided on one axial side of the motor. and a transmission mechanism that is connected to the motor gear unit and transmits the rotational force of the drive shaft to the spindle to rotate the spindle, wherein the transmission mechanism is rotatably provided to the spindle, and the motor gear an idle gear meshed with a portion, a ring-shaped ring gear meshed with the idle gear, and a bearing that rotatably supports the spindle and is arranged on one side of the ring gear in the axial direction. It is a work machine composed of
  • One or more embodiments of the present invention is a work machine in which the bearing rotatably supports the spindle and is arranged radially outward of the drive shaft with respect to the idle gear.
  • the transmission mechanism includes a support portion formed on the other side of the spindle in the axial direction, the idle gear is rotatably provided on the support portion,
  • the bearing is a work machine configured to rotatably support the support section.
  • the idle gear includes a large-diameter gear portion meshed with the motor gear portion, a small-diameter gear portion meshed with the ring gear and having a smaller diameter than the large-diameter gear portion, It is a work machine configured including
  • One or more embodiments of the present invention is a work machine in which the bearing is arranged radially outward of the drive shaft with respect to the large diameter gear portion.
  • One or more embodiments of the present invention allow for miniaturization.
  • FIG. 1 is a longitudinal sectional view showing an impact wrench according to this embodiment
  • FIG. FIG. 2 is a longitudinal sectional view showing an enlarged speed reduction mechanism shown in FIG. 1
  • (A) is a cross-sectional view (cross-sectional view taken along line 3A-3A in FIG. 2) seen from the front side showing a meshing state between a small-diameter gear portion of a planetary gear and a ring gear of the speed reduction mechanism shown in FIG. 2
  • 3 is a cross-sectional view (cross-sectional view taken along line 3B-3B in FIG. 2) seen from the front side showing a meshing state between the large-diameter gear portion of the planetary gear shown in FIG. 2 and the pinion gear of the motor
  • FIG. FIG. 2 is a perspective view of the spindle shown in FIG. 1 as seen obliquely from the rear right
  • FIG. 3 is a longitudinal sectional view showing a modification of the speed reduction mechanism shown in FIG. 2;
  • An impact wrench 10 as a work machine according to the present embodiment will be described below with reference to the drawings.
  • An arrow UP, an arrow FR, and an arrow RH appropriately shown in the drawings indicate the upper side, the front side, and the right side of the impact wrench 10, respectively.
  • the vertical, front-rear, and left-right directions of the impact wrench 10 are indicated unless otherwise specified.
  • hatching is omitted.
  • the impact wrench 10 is configured as a tool for applying rotational force and impact force to an anvil 50 provided at the front end of the impact wrench 10 to perform tightening and the like.
  • the impact wrench 10 includes a housing 12 forming an outer shell of the impact wrench 10, a motor 30 housed in the housing 12, an impact mechanism 40, and a speed reduction mechanism 60 as a transmission mechanism.
  • a housing 12 forming an outer shell of the impact wrench 10
  • a motor 30 housed in the housing 12
  • an impact mechanism 40 housed in the housing 12
  • a speed reduction mechanism 60 as a transmission mechanism.
  • the housing 12 is formed in a substantially hollow I-shape when viewed from the right side. Specifically, the housing 12 includes an upper housing portion 12A that constitutes the upper end portion of the housing 12 and extends in the front-rear direction, and a handle portion that extends downward from the longitudinal middle portion of the upper housing portion 12A. 12B and a lower housing portion 12C forming the lower end portion of the housing 12. As shown in FIG.
  • the housing 12 is composed of a plurality of housing members, and the housing 12 is formed by assembling these housing members together.
  • a trigger 14 is provided at the upper end of the handle portion 12B, and the trigger 14 protrudes forward from the handle portion 12B and can be pulled rearward.
  • a switch mechanism 16 is provided behind the trigger 14 in the handle portion 12B. The switch mechanism 16 has a switch (not shown), and when the trigger 14 is pulled, the switch is switched from off to on.
  • a control section 18 is provided in the lower housing section 12C.
  • a switch of the switch mechanism 16 is electrically connected to the controller 18 , and an output signal corresponding to the operating state of the trigger 14 is output from the switch to the controller 18 .
  • a battery 20 is detachably attached to the lower housing portion 12C. The battery 20 is electrically connected to the controller 18 and supplies electric power to a motor 30 to be described later via the controller 18 .
  • an inner case 22 is provided in the upper housing portion 12A as a case for housing a speed reduction mechanism 60, which will be described later.
  • the inner case 22 is formed in a substantially bottomed cylindrical shape that is open to the front side, and is mounted to the housing 12 so as to be disposed in the middle portion of the upper housing portion 12 ⁇ /b>A in the front-rear direction.
  • a motor bearing 24 for supporting a drive shaft 31 of a motor 30, which will be described later, is provided in the central portion of the bottom wall of the inner case 22. As shown in FIG. That is, a fixing hole for fixing the motor bearing 24 is formed in the bottom wall of the inner case 22 .
  • the side wall of the inner case 22 is formed in a substantially stepped cylindrical shape, and the diameter dimension of the front portion of the side wall is set larger than the diameter dimension of the rear portion of the side wall.
  • the inner space in the front portion of the inner case 22 is configured as a first accommodation portion 22A, and the internal space in the rear portion of the inner case 22 is configured as a second accommodation portion 22B.
  • the motor 30 As shown in FIG. 1, the motor 30 is accommodated in the rear end portion of the upper housing portion 12A and is electrically connected to the control portion 18. As shown in FIG. The motor 30 includes a drive shaft 31 whose axial direction is the front-rear direction, a rotor 32 connected to the drive shaft 31 so as to be rotatable together, and a substantially cylindrical stator 33 arranged radially outside the rotor 32 . is composed of
  • a rear end portion of the drive shaft 31 is rotatably supported by a motor bearing 26 fixed to the housing 12 .
  • the front end portion of the drive shaft 31 is rotatably supported by a motor bearing 24 fixed to the inner case 22 , and the front end portion of the drive shaft 31 is housed inside the inner case 22 .
  • a pinion gear 31A is formed as a motor gear portion at the front end of the drive shaft 31 .
  • a large-diameter gear portion 66A of a planetary gear 66 in a speed reduction mechanism 60 which will be described later, is meshed with the pinion gear 31A so that the rotational force of the motor 30 is transmitted to the spindle 42 by the speed reduction mechanism 60. Details of the speed reduction mechanism 60 will be described later.
  • the impact mechanism 40 is configured as a well-known impact mechanism that imparts rotational impact force to the anvil 50 provided at the front end of the upper housing portion 12A. Therefore, the configuration of the impact mechanism 40 will be briefly described below.
  • the impact mechanism 40 has a spindle 42 .
  • the spindle 42 is formed in a substantially stepped cylindrical shape whose axial direction is the front-rear direction.
  • the spindle 42 is rotatably accommodated in the upper housing portion 12A, and is arranged coaxially with the drive shaft 31 of the motor 30 and on the front side (one side in the axial direction) of the motor 30 .
  • the diameter of the front portion of the spindle 42 is set smaller than the diameter of the rear portion of the spindle 42 .
  • the rear end of the spindle 42 is integrally formed with a carrier portion 62 that constitutes a part of a speed reduction mechanism 60, which will be described later.
  • a substantially cylindrical hammer 44 is fitted to the front of the spindle 42 , and the hammer 44 is connected to the spindle 42 via a cam mechanism 46 .
  • An anvil 50 is provided on the front side of the spindle 42, and an end tool (not shown) is attached to the anvil 50. As shown in FIG. The driving force of the motor 30 is transmitted to the impact mechanism 40 by the deceleration mechanism 60, which will be described later.
  • the reduction mechanism 60 is accommodated in the upper housing portion 12A and arranged between the motor 30 and the impact mechanism 40. As shown in FIG. Specifically, the speed reduction mechanism 60 is arranged radially outside the pinion gear 31A of the motor 30 .
  • the speed reduction mechanism 60 is configured as a so-called planetary gear mechanism using the pinion gear 31A as a sun gear, reduces the speed of rotation of the motor 30, and transmits the speed to the impact mechanism 40.
  • the reduction mechanism 60 includes a carrier portion 62 as a support portion integrally provided at the rear end portion of the spindle 42, three planetary gears 66 as idle gears, a ring gear 68, and a bearing 70. It is
  • the carrier portion 62 includes a first carrier portion 62A as a first support portion and a second carrier portion 62B as a second support portion. consists of The first carrier portion 62A and the second carrier portion 62B are arranged facing each other with a predetermined gap in the front-rear direction, and are connected by a carrier connecting portion 62C.
  • the first carrier portion 62A has a base plate portion 62A1 forming a base portion of the first carrier portion 62A.
  • the base plate portion 62A1 is formed in a substantially annular plate shape with the plate thickness direction extending in the front-rear direction, extends radially outward from the rear end portion of the spindle 42, and extends inside the first accommodation portion 22A of the inner case 22. are placed.
  • a stepped portion 62A2 is formed on the outer peripheral portion of the front face of the base plate portion 62A1, and the stepped portion 62A2 is provided with a biasing spring 48 for biasing the hammer 44 of the impact mechanism 40 forward. is locked at its rear end.
  • Three fitting portions 62A3 are formed on the outer peripheral portion of the rear surface of the base plate portion 62A1.
  • the fitting portion 62A3 is formed in a substantially fan shape when viewed from the rear side, and protrudes rearward from the base plate portion 62A1.
  • an arc portion connecting two sides of the fitting portion 62A3 is arranged so as to form a concentric circle with the outer peripheral surface of the base plate portion 62A1 when viewed from the rear side, and the fitting portions 62A3 at three locations are connected to the spindle 42. are arranged at equal intervals (every 120 degrees) in the circumferential direction of the spindle 42 around the axis of the spindle 42 .
  • a gear housing portion 62A4 is formed in the first carrier portion 62A between the fitting portions 62A3 adjacent to each other in the circumferential direction of the spindle 42.
  • the gear housing portion 62A4 is formed in the shape of a groove that opens rearward and extends in the radial direction of the base plate portion 62A1.
  • the three gear housing portions 62A4 communicate with each other at the central portion of the base plate portion 62A1 and open radially outward of the base plate portion 62A1.
  • the outer peripheral portion of the base plate portion 62A1 (specifically, the portion arranged radially outside the fitting portion 62A3) is configured as a restricting portion 62A5.
  • the front portion of the pinion gear 31A in the motor 30 described above is arranged radially inside the first carrier portion 62A.
  • the second carrier portion 62B has a smaller diameter than the first carrier portion 62A and is formed in a substantially annular plate shape with the front-rear direction as the plate thickness direction.
  • the second carrier portion 62B is arranged coaxially with the first carrier portion 62A on the rear side of the first carrier portion 62A, and extends rearward from the fitting portion 62A3 of the first carrier portion 62A. It is connected to the first carrier portion 62A by a connecting portion 62C.
  • the second carrier portion 62B is arranged close to the front side of the bottom wall of the inner case 22 .
  • a rear end portion of the pinion gear 31A of the motor 30 is arranged radially inside the second carrier portion 62B.
  • the gear housing portion 62A4 is provided with a support shaft 64 that rotatably supports a planetary gear 66, which will be described later. That is, in this embodiment, three support shafts 64 are provided on the carrier portion 62 .
  • the support shaft 64 is formed in a substantially columnar shape whose axial direction is the front-rear direction. A front end portion of the support shaft 64 is fixed to the first carrier portion 62A, and a rear end portion of the support shaft 64 is fixed to the second carrier portion 62B. 2 carrier portion 62B.
  • the three support shafts 64 are arranged at equal intervals (every 120 degrees) in the circumferential direction of the spindle 42 .
  • the planetary gear 66 is configured as a two-stage gear whose axial direction is the front-rear direction, and is rotatably supported by the support shaft 64 of the carrier portion 62. As shown in FIG. Specifically, the planetary gear 66 includes a large-diameter gear portion 66A that constitutes the front portion of the planetary gear 66 and a small-diameter gear portion 66B that constitutes the rear portion of the planetary gear 66 .
  • the large-diameter gear portion 66A and the small-diameter gear portion 66B are formed in a substantially cylindrical shape with the longitudinal direction as the axial direction, and the diameter of the large-diameter gear portion 66A is set larger than the diameter of the small-diameter gear portion 66B.
  • External teeth composed of a plurality of teeth are formed on the outer peripheral portions of the large-diameter gear portion 66A and the small-diameter gear portion 66B, respectively. It is formed all around the direction.
  • the external teeth of the large-diameter gear portion 66A are meshed with the pinion gear 31A.
  • the large-diameter gear portion 66A is accommodated in the gear accommodating portion 62A4 of the carrier portion 62 and is arranged in the first accommodating portion 22A of the inner case 22.
  • the large-diameter gear portion 66A and the fitting portion 62A3 of the planetary gear 66 are alternately arranged side by side in the circumferential direction of the first carrier portion 62A (FIG. 3B). )reference).
  • the small-diameter gear portion 66B is arranged radially outside of the rear portion of the pinion gear 31A and inside the second accommodating portion 22B of the inner case 22 .
  • the ring gear 68 is formed in the shape of an annular plate whose thickness direction is the front-rear direction.
  • the ring gear 68 is arranged coaxially with the drive shaft 31 of the motor 30 and arranged radially outside the drive shaft 31 with respect to the small diameter gear portion 66B of the planetary gear 66 . Further, the ring gear 68 is fitted into the second accommodating portion 22B of the inner case 22 and held by the inner case 22 so as not to move relative to it.
  • a plurality of internal teeth are formed on the inner peripheral portion of the ring gear 68 , and the internal teeth are formed along the entire circumference of the ring gear 68 in the circumferential direction.
  • the inner teeth of the ring gear 68 mesh with the outer teeth of the small-diameter gear portion 66B of the planetary gear 66 .
  • the planetary gear 66 revolves around the ring gear 68 while rotating around the support shaft 64 .
  • the rotational force of the motor 30 reduced in speed by the reduction mechanism 60 is transmitted to the carrier portion 62 so that the spindle 42 rotates around its own axis.
  • the bearing 70 is configured as a ball bearing.
  • the bearing 70 is fitted into the first accommodating portion 22A of the inner case 22 and held by the inner case 22 so as not to move relative to it.
  • a fitting portion 62A3 of the first carrier portion 62A in the carrier portion 62 is fitted into the bearing 70 from the front side, and the carrier portion 62 (spindle 42) is rotatably supported by the bearing 70.
  • a large-diameter gear portion 66A of the planetary gear 66 is arranged close to the bearing 70 with a predetermined gap therebetween.
  • the restricting portion 62A5 of the first carrier portion 62A is arranged adjacent to the radially inner portion of the bearing 70 on the front side, and the restricting portion 62A5 allows the bearing to rotate. It is configured to restrict the movement of 70 to the front side.
  • the bearing 70 is arranged on the front side in the axial direction of the ring gear 68 .
  • the motor 30 when the operator operates the trigger 14, the motor 30 is driven under the control of the control unit 18, and the drive shaft 31 of the motor 30 rotates.
  • the planetary gear 66 meshed with the pinion gear 31A of the drive shaft 31 rotates.
  • a small-diameter gear portion 66B of the planetary gear 66 is meshed with a ring gear 68, and the ring gear 68 is non-rotatably held by the inner case 22.
  • the planetary gear 66 revolves in the circumferential direction of the ring gear 68 while rotating around the support shaft 64 . This causes the carrier portion 62 (that is, the spindle 42) to rotate. Therefore, the impact mechanism 40 is actuated to apply a rotational impact force to the anvil 50 .
  • the speed reduction mechanism 60 includes a carrier portion 62 integrally formed with the rear end portion of the spindle 42 and a planetary gear 66 rotatably supported by the carrier portion 62.
  • the planetary gear 66 is meshed with the pinion gear 31A of the motor 30 .
  • the reduction mechanism 60 also has a bearing 70 that rotatably supports the carrier portion 62 , and the bearing 70 is arranged radially outside the drive shaft 31 of the motor 30 with respect to the planetary gear 66 . Therefore, compared to a configuration in which the carrier portion 62 is rotatably supported by the bearings 70 arranged on the front side or the rear side of the planetary gear 66, the size of the speed reduction mechanism 60 in the front-rear direction can be reduced.
  • the size of the impact wrench 10 in the front-rear direction can be reduced.
  • the front-to-rear distance between the workpiece positioned on the front side of the impact wrench 10 and the worker positioned on the rear side of the impact wrench 10 can be shortened. Therefore, workability of the impact wrench 10 can be improved.
  • the pinion gear 31A, the planetary gear 66, and the bearing 70 of the motor 30 are arranged side by side in the radial direction of the drive shaft 31 of the motor 30. As shown in FIG. That is, the pinion gear 31A, the planetary gear 66, and the bearing 70 are arranged at overlapping positions in the front-rear direction. Specifically, the working machine according to claim 9, wherein the bearing is arranged within a range from the front end to the rear end of the idle gear.
  • the speed reduction mechanism 60 also has a ring gear 68 , which is arranged radially outward of the drive shaft 31 with respect to the planetary gears 66 and rearward of the bearing 70 . Thereby, the ring gear 68 and the bearing 70 can be arranged side by side in the front-rear direction. The size of the speed reduction mechanism 60 in the front-rear direction can be further reduced.
  • the carrier portion 62 of the spindle 42 pivotally supports a first carrier portion 62A forming a front end portion of the carrier portion 62, a second carrier portion 62B forming a rear end portion of the carrier portion 62, and a planetary gear 66. and a support shaft 64 .
  • the fitting portion 62A3 of the first carrier portion 62A is fitted into the bearing 70 and is rotatably supported by the bearing 70. As shown in FIG. More specifically, in the first carrier portion 62A, the fitting portions 62A3 and the planetary gears 66 are alternately arranged in the circumferential direction. It meshes with 30 pinion gears 31A.
  • the carrier portion 62 (spindle 42 ) is supported by the bearing 70 while the planetary gear 66 is arranged in the carrier portion 62 . It can be rotatably supported.
  • the bearing 70 is held by the inner case 22 that is open to the front side. Furthermore, the restricting portion 62A5 of the first carrier portion 62A is arranged adjacent to the front side of the radially inner portion of the bearing 70 to restrict the movement of the bearing 70 to the front side. As a result, the bearing 70 held by the inner case 22 can be well maintained by utilizing the carrier portion 62 .
  • a ring gear 68 is arranged radially outside the second carrier portion 62B.
  • the ring gear 68 can be arranged radially outward of the drive shaft 31 with respect to the planetary gears 66 while the planetary gears 66 are arranged on the carrier portion 62 .
  • the planetary gear 66 of the reduction mechanism 60 includes a large-diameter gear portion 66A meshed with the pinion gear 31A and a small-diameter gear portion 66B meshed with the ring gear 68 .
  • the rotation of the motor 30 can be reduced by the reduction mechanism 60 and transmitted to the spindle 42 . This can contribute to miniaturization of the motor 30 . Therefore, the impact wrench 10 can be effectively miniaturized.
  • the planetary gear 66 of the speed reduction mechanism 60 is configured as a two-stage gear, but the configuration of the planetary gear 66 is not limited to this.
  • the planetary gear 66 may be configured as a one-stage gear by omitting the small-diameter gear portion 66B.
  • the diameter of the ring gear 68 may be made larger than in the present embodiment, and the outer teeth of the rear portion of the planetary gear 66 may mesh with the inner teeth of the ring gear 68 .
  • the bearing 70 is arranged radially outward of the drive shaft 31 with respect to the planetary gear 66, compared with the configuration in which the bearing 70 is arranged on the front side or the rear side of the planetary gear 66, the The size of the speed reduction mechanism 60 can be reduced.
  • the pinion gear 31A is formed integrally with the drive shaft 31 of the motor 30, but the pinion gear 31A and the drive shaft 31 may be formed separately so that the pinion gear 31A can rotate integrally with the drive shaft 31. may be connected to
  • SYMBOLS 10 Impact wrench (work machine), 22... Inner case (case), 30... Motor, 31... Drive shaft, 31A... Pinion gear (motor gear part), 42... Spindle, 60... Reduction mechanism (transmission mechanism), 62... Carrier Part (supporting part) 62A... First carrier part (first supporting part) 62A3... Fitting part 62A5... Regulating part 62B... Second carrier part (second supporting part) 64... Support shaft 66... Planetary gear (idle gear) 66A large diameter gear portion 66B small diameter gear portion 68 ring gear 70 bearing

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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PCT/JP2022/019286 2021-05-19 2022-04-28 作業機 Ceased WO2022244615A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE112022002666.9T DE112022002666T5 (de) 2021-05-19 2022-04-28 Arbeitsmaschine
JP2023522594A JP7622828B2 (ja) 2021-05-19 2022-04-28 作業機
CN202280035636.2A CN117320845A (zh) 2021-05-19 2022-04-28 作业机
US18/561,277 US20240253203A1 (en) 2021-05-19 2022-04-28 Work machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021084586 2021-05-19
JP2021-084586 2021-05-19

Publications (1)

Publication Number Publication Date
WO2022244615A1 true WO2022244615A1 (ja) 2022-11-24

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PCT/JP2022/019286 Ceased WO2022244615A1 (ja) 2021-05-19 2022-04-28 作業機

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US (1) US20240253203A1 (https=)
JP (1) JP7622828B2 (https=)
CN (1) CN117320845A (https=)
DE (1) DE112022002666T5 (https=)
WO (1) WO2022244615A1 (https=)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023132345A1 (de) * 2022-11-24 2024-05-29 Makita Corporation Kraftwerkzeug

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007507361A (ja) * 2003-10-03 2007-03-29 アトラス・コプコ・ツールス・アクチボラグ 遊星型減速歯車装置を備えた動力工具
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