WO2020188994A1 - Electric tool - Google Patents

Electric tool Download PDF

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Publication number
WO2020188994A1
WO2020188994A1 PCT/JP2020/002019 JP2020002019W WO2020188994A1 WO 2020188994 A1 WO2020188994 A1 WO 2020188994A1 JP 2020002019 W JP2020002019 W JP 2020002019W WO 2020188994 A1 WO2020188994 A1 WO 2020188994A1
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WO
WIPO (PCT)
Prior art keywords
gear
planetary
gears
power tool
internal
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PCT/JP2020/002019
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French (fr)
Japanese (ja)
Inventor
政憲 中本
村上　弘明
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パナソニックＩｐマネジメント株式会社
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Publication of WO2020188994A1 publication Critical patent/WO2020188994A1/en

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    • 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
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
    • F16H3/36—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with a single gear meshable with any of a set of coaxial gears of different diameters

Definitions

  • This disclosure relates to a power tool equipped with a planetary gear device.
  • Patent Document 1 discloses a power tool provided with a traction drive type continuously variable transmission.
  • the solar roller on the input side and the thrust roller on the output side are pressed against a plurality of conical planetary rollers with a large force using a thrust mechanism, and the rolling contact obtained by this is used for power.
  • the speed change roller is pressed against the conical surface of the planetary roller, and the pressure contact position is displaced between the small diameter side and the large diameter side to change the contact diameter, thereby changing the output rotation speed steplessly. Shift gears.
  • Patent Document 1 Since the continuously variable transmission of Patent Document 1 requires a lubricant that forms an oil film on the pressure contact portion, it is necessary to take measures to prevent leakage of the lubricant. Further, since power is transmitted by pressure welding, if a large force is applied in the thrust direction, spin is likely to occur between the contact surfaces, and the power transmission efficiency may decrease.
  • the present disclosure has been made in view of such circumstances, and an object thereof is to provide a power tool equipped with a transmission mechanism.
  • the power tool of the present disclosure can rotate the drive shaft rotated by the motor, the sun gear fixed to the drive shaft, the internal gear, the planet body, and the planet body. It is provided with a planetary carrier that supports it and an output shaft that is directly or indirectly connected to the planetary carrier to which a tip tool can be mounted.
  • the driven gear and a plurality of gears having different numbers of teeth are coaxially arranged, the driven gear meshes with the sun gear, and one of the plurality of gears meshes with the internal gear.
  • FIG. 1 shows an example of the configuration of the power tool 1 according to the embodiment of the present disclosure.
  • the electric tool 1 is a rotary tool that uses a motor 2 as a drive source, and outputs a drive shaft 3 that is rotated by the motor 2, an output shaft 5 to which a tip tool can be mounted, and a rotary output of the drive shaft 3. It is provided with a power transmission mechanism 4 for transmitting to.
  • a tip tool such as a screwdriver that applies tightening torque to the screw member is attached to the output shaft 5. Electric power is supplied from the battery 13 built in the battery pack, and the motor 2 is driven by the motor drive unit 11.
  • the control unit 10 has a function of controlling the rotation of the motor 2.
  • the operation switch 12 is a trigger switch operated by the user, and the control unit 10 controls the on / off of the motor 2 by operating the operation switch 12, and also gives a drive instruction according to the operation amount of the operation switch 12 to the motor drive unit.
  • the motor drive unit 11 controls the applied voltage of the motor 2 according to the drive instruction supplied from the control unit 10 to adjust the motor rotation speed.
  • the power transmission mechanism 4 has a planetary gear reduction mechanism that meshes with a pinion gear attached to the drive shaft 3.
  • FIG. 2 shows the structure of the power transmission mechanism 4 provided with the planetary gear device.
  • the power transmission mechanism 4 includes a planetary gear device 20, and the planetary gear device 20 includes a sun gear 21 fixed to a drive shaft 3, an internal gear 22 non-rotatably attached to a housing 6, and a plurality of planets 23.
  • a planetary carrier 24 that rotatably supports a plurality of planetary bodies 23.
  • the planetary body 23 includes a first gear 30a, a second gear 30b, a third gear 30c, a fourth gear 30d, a fifth gear 30e, a sixth gear 30f, and a driven gear 31 arranged coaxially.
  • the driven gear 31 meshes with the sun gear 21.
  • the first gear 30a, the second gear 30b, the third gear 30c, the fourth gear 30d, the fifth gear 30e, and the sixth gear 30f (hereinafter, may be referred to as "gear 30" unless otherwise specified).
  • Each has a different number of teeth, and only one of the gears 30 meshes with the internal gear 22.
  • the output shaft 5 connects directly or indirectly to the planet carrier 24.
  • the planet carrier 24 rotatably supports the plurality of planets 23 in a direction inclined by a predetermined angle with respect to the axial direction of the drive shaft 3. In the illustrated example, two planets 23 are shown, but the number of planets 23 may be three or more.
  • the shaft portion provided at the end of the planetary body 23 is pivotally supported by the shaft support portion 33.
  • the internal gear 22 of the embodiment is non-rotatable with respect to the housing 6, but can move in the axial direction of the drive shaft 3. That is, the internal gear 22 is slidably mounted in the housing 6 in the axial direction.
  • the plurality of gears 30 in the planetary body 23 are provided at positions where the internal gears 22 mesh with the internal gears 22 when the internal gears 22 move in the axial direction.
  • the plurality of gears 30 are arranged so that only one gear meshes with the internal gear 22, and two or more gears 30 do not mesh with the internal gear 22 at the same time.
  • the first gear 30a meshes with the internal gear 22.
  • the planet 23 revolves while rotating, and the rotation output is transmitted to the output shaft 5.
  • the plurality of gears 30 in the planetary body 23 are coaxially stacked so that the number of teeth is in ascending or descending order.
  • the first gear 30a has the largest number of teeth
  • the sixth gear 30f has the smallest number of teeth.
  • the smaller the number of teeth of the gear 30, the lower the rotation speed of the output shaft 5 and the transmission. The torque increases. Therefore, when the first gear 30a meshes with the internal gear 22, the power tool 1 tightens the screw member at high speed and low torque.
  • FIG. 3 shows a state in which the internal gear 22 slides and meshes with the second gear 30b.
  • the internal gear 22 is disengaged from the first gear 30a and then meshes with the second gear 30b.
  • the internal gear 22 meshes with the inclined second gear 30b, so that the internal gear 22 and the gear 30 preferably have triangular teeth.
  • the internal gear 22 can easily mesh with the gear 30 from an oblique direction.
  • the rotation speed is relatively low and the transmission torque is relatively large as compared with the state where the internal gear 22 meshes with the first gear 30a.
  • FIG. 4 shows a state in which the internal gear 22 meshes with the sixth gear 30f.
  • the rotation speed of the power tool 1 is the lowest, but the transmission torque is the maximum.
  • the planetary body 23 of the embodiment is provided with 6 gears 30, but the larger the number of gears 30, the smoother the speed change can be realized.
  • the gear 30 having a large number of teeth rotates at high speed, but the transmission torque is small. Therefore, the gear 30 having a relatively large number of teeth may be formed thinner than the gear 30 having a relatively small number of teeth. That is, in the planetary body 23, the tooth width of the first gear 30a may be formed to be the thinnest. By forming the tooth width thin, it is possible to increase the number of gears 30 in a limited space.
  • the sun gear 21, the driven gear 31, the gear 30, and the internal gear 22 may be helical gears or bevel gears.
  • the power transmission mechanism 4 has the planetary gear device 20, but other types of mechanisms may be provided in addition to the planetary gear device 20.
  • the outline of the aspect of the present disclosure is as follows.
  • the power tool (1) of an aspect of the present disclosure includes a drive shaft (3) rotated by a motor (2), a sun gear (21) fixed to the drive shaft, an internal gear (22), and a driven gear.
  • a gear (31) and a plurality of gears (30) having different numbers of teeth are arranged coaxially, and the driven gear meshes with the sun gear and one gear meshes with the internal gear to rotate the planet body (23).
  • It includes a planetary carrier (24) that supports it as possible, and an output shaft (5) that is directly or indirectly connected to the planetary carrier and to which a tip tool can be mounted.
  • the planetary carrier (24) may rotatably support a plurality of planetary bodies (23) in a direction inclined by a predetermined angle with respect to the axial direction of the drive shaft.
  • the internal gear (22) is movable in the axial direction of the drive shaft, and the plurality of gears (30) in the planetary body (23) are provided at positions where the internal gear meshes with the internal gear when the internal gear moves in the axial direction. May be good.
  • the plurality of gears (30) in the planetary body (23) may be arranged so that only one gear meshes with the internal gear.
  • the plurality of gears (30) in the planetary body (23) may be arranged coaxially so that the number of teeth is in ascending or descending order.
  • the internal gear and the gear in the planetary body may have triangular teeth. In a planetary body, a gear having a relatively large number of teeth may be formed thinner than a gear having a relatively small number of teeth.
  • This disclosure can be used for power tools equipped with planetary gears.

Abstract

An electric tool (1) includes: a sun gear (21) fixed to a drive shaft (3); an internal gear (22); planetary bodies (23); a planetary carrier (24) for rotatably supporting the planetary bodies (23); and an output shaft (5) directly or indirectly connected to the planetary carrier (24) to which a tip tool is attachable. Each planetary body (23) has a driven gear (31) and a plurality of gears (30) which are arranged coaxially. Each of the plurality of gears (30) has a different number of teeth. Each driven gear (31) meshes with the sun gear (21), and one of the plurality of gears (30) meshes with the internal gear (22).

Description

電動工具Electric tool
　本開示は、遊星歯車装置を備えた電動工具に関する。 This disclosure relates to a power tool equipped with a planetary gear device.
　特許文献１は、トラクションドライブ式の無段変速機を備えた動力工具を開示する。この無段変速機は、複数の円錐形の遊星ローラに、入力側の太陽ローラと出力側の推力ローラを推力機構を用いて大きな力で圧接し、これにより得られる転がり接触を利用して動力を伝達する。無段変速機は、遊星ローラの円錐面に変速ローラを圧接し、この圧接位置を小径側と大径側との間で変位させて接触径を変化させることで、出力回転数を無段階で変速する。 Patent Document 1 discloses a power tool provided with a traction drive type continuously variable transmission. In this continuously variable transmission, the solar roller on the input side and the thrust roller on the output side are pressed against a plurality of conical planetary rollers with a large force using a thrust mechanism, and the rolling contact obtained by this is used for power. To convey. In a continuously variable transmission, the speed change roller is pressed against the conical surface of the planetary roller, and the pressure contact position is displaced between the small diameter side and the large diameter side to change the contact diameter, thereby changing the output rotation speed steplessly. Shift gears.
特開２０１１－４５９７６号公報Japanese Unexamined Patent Publication No. 2011-45976
　特許文献１の無段変速機は、圧接部に油膜を形成する潤滑剤を必要とするため、潤滑剤の漏れ防止の対策をとる必要がある。また圧接による動力伝達のため、スラスト方向に大きな力が加わると、接触面間でスピンが起きやすく、動力伝達効率が低下することがある。 Since the continuously variable transmission of Patent Document 1 requires a lubricant that forms an oil film on the pressure contact portion, it is necessary to take measures to prevent leakage of the lubricant. Further, since power is transmitted by pressure welding, if a large force is applied in the thrust direction, spin is likely to occur between the contact surfaces, and the power transmission efficiency may decrease.
　本開示はこうした状況に鑑みなされたものであり、その目的は、変速機構を備えた電動工具を提供することにある。 The present disclosure has been made in view of such circumstances, and an object thereof is to provide a power tool equipped with a transmission mechanism.
　上記課題を解決するために、本開示のある態様の電動工具は、モータにより回転される駆動軸と、駆動軸に固定される太陽歯車と、内歯車と、遊星体と、遊星体を回転可能に支持する遊星キャリアと、遊星キャリアに直接的または間接的に接続して、先端工具を装着可能な出力軸とを備える。遊星体では、被駆動歯車と、歯数の異なる複数の歯車が同軸に配置され、被駆動歯車は太陽歯車に噛み合い、複数の歯車のうちの１つが内歯車に噛み合う。 In order to solve the above problems, the power tool of the present disclosure can rotate the drive shaft rotated by the motor, the sun gear fixed to the drive shaft, the internal gear, the planet body, and the planet body. It is provided with a planetary carrier that supports it and an output shaft that is directly or indirectly connected to the planetary carrier to which a tip tool can be mounted. In the planetary body, the driven gear and a plurality of gears having different numbers of teeth are coaxially arranged, the driven gear meshes with the sun gear, and one of the plurality of gears meshes with the internal gear.
実施形態に係る電動工具の構成の一例を示す図である。It is a figure which shows an example of the structure of the power tool which concerns on embodiment. 動力伝達機構の構造を示す図である。It is a figure which shows the structure of a power transmission mechanism. 内歯車がスライドした状態を示す図である。It is a figure which shows the state which the internal gear slides. 内歯車がスライドした状態を示す図である。It is a figure which shows the state which the internal gear slides.
　図１は、本開示の実施形態に係る電動工具１の構成の一例を示す。電動工具１は、モータ２を駆動源とする回転工具であって、モータ２により回転される駆動軸３と、先端工具を装着可能な出力軸５と、駆動軸３の回転出力を出力軸５に伝達する動力伝達機構４とを備える。出力軸５には、ねじ部材に締付トルクを付与するドライバなどの先端工具が取り付けられる。電力はバッテリパックに内蔵されたバッテリ１３より供給され、モータ２はモータ駆動部１１により駆動される。 FIG. 1 shows an example of the configuration of the power tool 1 according to the embodiment of the present disclosure. The electric tool 1 is a rotary tool that uses a motor 2 as a drive source, and outputs a drive shaft 3 that is rotated by the motor 2, an output shaft 5 to which a tip tool can be mounted, and a rotary output of the drive shaft 3. It is provided with a power transmission mechanism 4 for transmitting to. A tip tool such as a screwdriver that applies tightening torque to the screw member is attached to the output shaft 5. Electric power is supplied from the battery 13 built in the battery pack, and the motor 2 is driven by the motor drive unit 11.
　制御部１０は、モータ２の回転を制御する機能を有する。操作スイッチ１２はユーザにより操作されるトリガスイッチであって、制御部１０は、操作スイッチ１２の操作によりモータ２のオンオフを制御するとともに、操作スイッチ１２の操作量に応じた駆動指示をモータ駆動部１１に供給する。モータ駆動部１１は、制御部１０から供給される駆動指示によりモータ２の印加電圧を制御して、モータ回転数を調整する。動力伝達機構４は、駆動軸３に取り付けられたピニオンギヤに噛み合う遊星歯車減速機構を有する。 The control unit 10 has a function of controlling the rotation of the motor 2. The operation switch 12 is a trigger switch operated by the user, and the control unit 10 controls the on / off of the motor 2 by operating the operation switch 12, and also gives a drive instruction according to the operation amount of the operation switch 12 to the motor drive unit. Supply to 11. The motor drive unit 11 controls the applied voltage of the motor 2 according to the drive instruction supplied from the control unit 10 to adjust the motor rotation speed. The power transmission mechanism 4 has a planetary gear reduction mechanism that meshes with a pinion gear attached to the drive shaft 3.
　図２は、遊星歯車装置を備えた動力伝達機構４の構造を示す。動力伝達機構４は、遊星歯車装置２０を備え、遊星歯車装置２０は、駆動軸３に固定される太陽歯車２１と、ハウジング６に回転不能に取り付けられる内歯車２２と、複数の遊星体２３と、複数の遊星体２３を回転可能に支持する遊星キャリア２４とを備える。遊星体２３は、同軸に配置された第１歯車３０ａ、第２歯車３０ｂ、第３歯車３０ｃ、第４歯車３０ｄ、第５歯車３０ｅ、第６歯車３０ｆおよび被駆動歯車３１を備える。被駆動歯車３１は太陽歯車２１に噛み合う。第１歯車３０ａ、第２歯車３０ｂ、第３歯車３０ｃ、第４歯車３０ｄ、第５歯車３０ｅ、第６歯車３０ｆ（以下、特に区別しない場合には「歯車３０」と呼ぶこともある）は、それぞれ異なる歯数を有し、いずれか１つの歯車３０のみが内歯車２２に噛み合う。出力軸５は、遊星キャリア２４に直接的または間接的に接続する。 FIG. 2 shows the structure of the power transmission mechanism 4 provided with the planetary gear device. The power transmission mechanism 4 includes a planetary gear device 20, and the planetary gear device 20 includes a sun gear 21 fixed to a drive shaft 3, an internal gear 22 non-rotatably attached to a housing 6, and a plurality of planets 23. , A planetary carrier 24 that rotatably supports a plurality of planetary bodies 23. The planetary body 23 includes a first gear 30a, a second gear 30b, a third gear 30c, a fourth gear 30d, a fifth gear 30e, a sixth gear 30f, and a driven gear 31 arranged coaxially. The driven gear 31 meshes with the sun gear 21. The first gear 30a, the second gear 30b, the third gear 30c, the fourth gear 30d, the fifth gear 30e, and the sixth gear 30f (hereinafter, may be referred to as "gear 30" unless otherwise specified). Each has a different number of teeth, and only one of the gears 30 meshes with the internal gear 22. The output shaft 5 connects directly or indirectly to the planet carrier 24.
　遊星キャリア２４は、複数の遊星体２３を、駆動軸３の軸線方向に対して所定角度傾斜した向きで回転可能に支持する。図示の例では２つの遊星体２３を示しているが、遊星体２３の個数は３つ以上であってもよい。遊星体２３の端部に設けられた軸部が、軸支部３３により軸支される。 The planet carrier 24 rotatably supports the plurality of planets 23 in a direction inclined by a predetermined angle with respect to the axial direction of the drive shaft 3. In the illustrated example, two planets 23 are shown, but the number of planets 23 may be three or more. The shaft portion provided at the end of the planetary body 23 is pivotally supported by the shaft support portion 33.
　実施形態の内歯車２２は、ハウジング６に対して回転不能とされるが、駆動軸３の軸線方向に移動可能である。つまり内歯車２２は、ハウジング６内で軸線方向にスライド可能に取り付けられている。遊星体２３における複数の歯車３０は、内歯車２２が軸線方向に移動すると、内歯車２２に噛み合う位置に設けられる。複数の歯車３０は、１つの歯車のみが内歯車２２と噛み合うように配置され、同時に２つ以上の歯車３０が内歯車２２と噛み合うことはない。内歯車２２が噛み合う歯車３０を変えることで、遊星歯車装置２０が変速機構として機能する。 The internal gear 22 of the embodiment is non-rotatable with respect to the housing 6, but can move in the axial direction of the drive shaft 3. That is, the internal gear 22 is slidably mounted in the housing 6 in the axial direction. The plurality of gears 30 in the planetary body 23 are provided at positions where the internal gears 22 mesh with the internal gears 22 when the internal gears 22 move in the axial direction. The plurality of gears 30 are arranged so that only one gear meshes with the internal gear 22, and two or more gears 30 do not mesh with the internal gear 22 at the same time. By changing the gear 30 in which the internal gear 22 meshes, the planetary gear device 20 functions as a speed change mechanism.
　図２に示す例では、第１歯車３０ａが内歯車２２に噛み合っている。モータ２が駆動軸３を回転すると、遊星体２３が自転しながら公転し、出力軸５に回転出力が伝達される。遊星体２３における複数の歯車３０は、同軸に、歯数が昇順または降順となるように積み重ねられる。複数の歯車３０において、第１歯車３０ａは最も歯数が多く、第６歯車３０ｆは最も歯数が少ない。内歯車２２に噛み合う歯車３０の歯数が多いほど、出力軸５の回転速度は高く、伝達トルクは小さくなり、一方で歯車３０の歯数が少ないほど、出力軸５の回転速度は低く、伝達トルクは大きくなる。そのため第１歯車３０ａが内歯車２２に噛み合っていると、電動工具１が、高速低トルクでねじ部材の締付を行う。 In the example shown in FIG. 2, the first gear 30a meshes with the internal gear 22. When the motor 2 rotates the drive shaft 3, the planet 23 revolves while rotating, and the rotation output is transmitted to the output shaft 5. The plurality of gears 30 in the planetary body 23 are coaxially stacked so that the number of teeth is in ascending or descending order. Among the plurality of gears 30, the first gear 30a has the largest number of teeth, and the sixth gear 30f has the smallest number of teeth. The larger the number of teeth of the gear 30 that meshes with the internal gear 22, the higher the rotation speed of the output shaft 5 and the smaller the transmission torque. On the other hand, the smaller the number of teeth of the gear 30, the lower the rotation speed of the output shaft 5 and the transmission. The torque increases. Therefore, when the first gear 30a meshes with the internal gear 22, the power tool 1 tightens the screw member at high speed and low torque.
　図３は、内歯車２２がスライドして第２歯車３０ｂに噛み合った状態を示す。内歯車２２は、モータ２に近付く方向にスライドされると、第１歯車３０ａとの噛み合いが外れた後、第２歯車３０ｂに噛み合う。図示されるように、内歯車２２は、傾斜した第２歯車３０ｂに噛み合うため、内歯車２２および歯車３０は、三角歯を有することが好ましい。互いに先端を尖らせた三角歯形状をもつことで、内歯車２２が斜め方向から歯車３０と容易に噛み合うことができる。内歯車２２が第２歯車３０ｂに噛み合った状態では、内歯車２２が第１歯車３０ａと噛み合った状態と比べて、回転速度は相対的に低く、伝達トルクは相対的に大きくなっている。 FIG. 3 shows a state in which the internal gear 22 slides and meshes with the second gear 30b. When the internal gear 22 is slid in the direction approaching the motor 2, the internal gear 22 is disengaged from the first gear 30a and then meshes with the second gear 30b. As shown, the internal gear 22 meshes with the inclined second gear 30b, so that the internal gear 22 and the gear 30 preferably have triangular teeth. By having triangular tooth shapes with sharpened tips, the internal gear 22 can easily mesh with the gear 30 from an oblique direction. In the state where the internal gear 22 meshes with the second gear 30b, the rotation speed is relatively low and the transmission torque is relatively large as compared with the state where the internal gear 22 meshes with the first gear 30a.
　図４は、内歯車２２が第６歯車３０ｆに噛み合った状態を示す。内歯車２２が第６歯車３０ｆに噛み合った状態では、電動工具１の回転速度が最も低いが、伝達トルクが最大となる。 FIG. 4 shows a state in which the internal gear 22 meshes with the sixth gear 30f. When the internal gear 22 meshes with the sixth gear 30f, the rotation speed of the power tool 1 is the lowest, but the transmission torque is the maximum.
　実施形態の遊星体２３は、６段の歯車３０を備えているが、歯車３０の段数が多いほど、なめらかな変速を実現できる。遊星体２３において、歯数が多い歯車３０は、高速回転する一方で、伝達トルクは小さい。そのため歯数の相対的に多い歯車３０は、歯数の相対的に少ない歯車３０よりも薄く形成されてよい。つまり遊星体２３においては、第１歯車３０ａの歯幅が最も薄く形成されてよい。歯幅を薄く形成することで、限られたスペースにおける歯車３０の段数を増やすことが可能となる。 The planetary body 23 of the embodiment is provided with 6 gears 30, but the larger the number of gears 30, the smoother the speed change can be realized. In the planetary body 23, the gear 30 having a large number of teeth rotates at high speed, but the transmission torque is small. Therefore, the gear 30 having a relatively large number of teeth may be formed thinner than the gear 30 having a relatively small number of teeth. That is, in the planetary body 23, the tooth width of the first gear 30a may be formed to be the thinnest. By forming the tooth width thin, it is possible to increase the number of gears 30 in a limited space.
　以上、本開示を実施形態をもとに説明した。この実施形態は例示であり、それらの各構成要素あるいは各処理プロセスの組合せにいろいろな変形例が可能なこと、またそうした変形例も本開示の範囲にあることは当業者に理解されるところである。 The present disclosure has been described above based on the embodiment. It will be appreciated by those skilled in the art that this embodiment is exemplary and that various modifications are possible for each of these components or combinations of processing processes, and that such modifications are also within the scope of the present disclosure. ..
　太陽歯車２１、被駆動歯車３１、歯車３０および内歯車２２は、はすば歯車またはやまば歯車であってよい。実施形態では動力伝達機構４が遊星歯車装置２０を有しているが、遊星歯車装置２０に加えて他の種類の機構を備えてもよい。 The sun gear 21, the driven gear 31, the gear 30, and the internal gear 22 may be helical gears or bevel gears. In the embodiment, the power transmission mechanism 4 has the planetary gear device 20, but other types of mechanisms may be provided in addition to the planetary gear device 20.
　本開示の態様の概要は、次の通りである。
　本開示のある態様の電動工具（１）は、モータ（２）により回転される駆動軸（３）と、駆動軸に固定される太陽歯車（２１）と、内歯車（２２）と、被駆動歯車（３１）と、歯数の異なる複数の歯車（３０）が同軸に配置され、被駆動歯車が太陽歯車に噛み合い、１つの歯車が内歯車に噛み合う遊星体（２３）と、遊星体を回転可能に支持する遊星キャリア（２４）と、遊星キャリアに直接的または間接的に接続して、先端工具を装着可能な出力軸（５）とを備える。 The outline of the aspect of the present disclosure is as follows.
The power tool (1) of an aspect of the present disclosure includes a drive shaft (3) rotated by a motor (2), a sun gear (21) fixed to the drive shaft, an internal gear (22), and a driven gear. A gear (31) and a plurality of gears (30) having different numbers of teeth are arranged coaxially, and the driven gear meshes with the sun gear and one gear meshes with the internal gear to rotate the planet body (23). It includes a planetary carrier (24) that supports it as possible, and an output shaft (5) that is directly or indirectly connected to the planetary carrier and to which a tip tool can be mounted.
　遊星キャリア（２４）は、複数の遊星体（２３）を、駆動軸の軸線方向に対して所定角度傾斜した向きで回転可能に支持してもよい。内歯車（２２）は、駆動軸の軸線方向に移動可能であり、遊星体（２３）における複数の歯車（３０）は、内歯車が軸線方向に移動すると、内歯車に噛み合う位置に設けられてもよい。遊星体（２３）における複数の歯車（３０）は、１つの歯車のみが内歯車と噛み合うように配置されてもよい。遊星体（２３）における複数の歯車（３０）は、同軸に、歯数が昇順または降順となるように配置されてもよい。内歯車および遊星体における歯車は、三角歯を有してもよい。遊星体において、歯数の相対的に多い歯車は、歯数の相対的に少ない歯車よりも薄く形成されてもよい。 The planetary carrier (24) may rotatably support a plurality of planetary bodies (23) in a direction inclined by a predetermined angle with respect to the axial direction of the drive shaft. The internal gear (22) is movable in the axial direction of the drive shaft, and the plurality of gears (30) in the planetary body (23) are provided at positions where the internal gear meshes with the internal gear when the internal gear moves in the axial direction. May be good. The plurality of gears (30) in the planetary body (23) may be arranged so that only one gear meshes with the internal gear. The plurality of gears (30) in the planetary body (23) may be arranged coaxially so that the number of teeth is in ascending or descending order. The internal gear and the gear in the planetary body may have triangular teeth. In a planetary body, a gear having a relatively large number of teeth may be formed thinner than a gear having a relatively small number of teeth.
　本開示は、遊星歯車装置を備えた電動工具に利用できる。 This disclosure can be used for power tools equipped with planetary gears.
１・・・電動工具、２・・・モータ、３・・・駆動軸、４・・・動力伝達機構、５・・・出力軸、６・・・ハウジング、２０・・・遊星歯車装置、２１・・・太陽歯車、２２・・・内歯車、２３・・・遊星体、２４・・・遊星キャリア、３０・・・歯車、３１・・・被駆動歯車、３３・・・軸支部。 1 ... Electric tool, 2 ... Motor, 3 ... Drive shaft, 4 ... Power transmission mechanism, 5 ... Output shaft, 6 ... Housing, 20 ... Planetary gear device, 21 ... Sun gear, 22 ... Internal gear, 23 ... Planetary body, 24 ... Planet carrier, 30 ... Gear, 31 ... Driven gear, 33 ... Shaft branch.

Claims (7)

  1. 　モータにより回転される駆動軸と、
    　前記駆動軸に固定される太陽歯車と、
    　内歯車と、
    　被駆動歯車と、歯数の異なる複数の歯車が同軸に配置され、前記被駆動歯車が前記太陽歯車に噛み合い、１つの歯車が前記内歯車に噛み合う遊星体と、
    　前記遊星体を回転可能に支持する遊星キャリアと、
    　遊星キャリアに直接的または間接的に接続して、先端工具を装着可能な出力軸と、
    　を備えたことを特徴とする電動工具。     The drive shaft rotated by the motor and
    The sun gear fixed to the drive shaft and
    With internal gears
    A planetary body in which a driven gear and a plurality of gears having different numbers of teeth are coaxially arranged, the driven gear meshes with the sun gear, and one gear meshes with the internal gear.
    A planetary carrier that rotatably supports the planetary body,
    With an output shaft that can be directly or indirectly connected to the planetary carrier to mount a tip tool,
    A power tool characterized by being equipped with.
  2. 　前記遊星キャリアは、複数の前記遊星体を、前記駆動軸の軸線方向に対して所定角度傾斜した向きで回転可能に支持する、
    　ことを特徴とする請求項１に記載の電動工具。     The planetary carrier rotatably supports a plurality of the planetary bodies in a direction inclined by a predetermined angle with respect to the axial direction of the drive shaft.
    The power tool according to claim 1.
  3. 　前記内歯車は、前記駆動軸の軸線方向に移動可能であり、
    　前記遊星体における前記複数の歯車は、前記内歯車が軸線方向に移動すると、前記内歯車に噛み合う位置に設けられる、
    　ことを特徴とする請求項１または２に記載の電動工具。     The internal gear is movable in the axial direction of the drive shaft, and is movable.
    The plurality of gears in the planetary body are provided at positions where the internal gears mesh with the internal gears when the internal gears move in the axial direction.
    The power tool according to claim 1 or 2, wherein the power tool.
  4. 　前記遊星体における前記複数の歯車は、１つの歯車のみが前記内歯車と噛み合うように配置される、
    　ことを特徴とする請求項３に記載の電動工具。     The plurality of gears in the planetary body are arranged so that only one gear meshes with the internal gear.
    The power tool according to claim 3, wherein the power tool is characterized in that.
  5. 　前記遊星体における前記複数の歯車は、同軸に、歯数が昇順または降順となるように配置される、
    　ことを特徴とする請求項１から４のいずれかに記載の電動工具。     The plurality of gears in the planetary body are coaxially arranged so that the number of teeth is in ascending or descending order.
    The power tool according to any one of claims 1 to 4, wherein the power tool.
  6. 　前記内歯車および前記遊星体における歯車は、三角歯を有する、
    　ことを特徴とする請求項１から５のいずれかに記載の電動工具。     The internal gear and the gear in the planetary body have triangular teeth.
    The power tool according to any one of claims 1 to 5, wherein the power tool.
  7. 　前記遊星体において、歯数の相対的に多い歯車は、歯数の相対的に少ない歯車よりも薄く形成される、
    　ことを特徴とする請求項１から６のいずれかに記載の電動工具。     In the planetary body, a gear having a relatively large number of teeth is formed thinner than a gear having a relatively small number of teeth.
    The power tool according to any one of claims 1 to 6, characterized in that.
PCT/JP2020/002019 2019-03-20 2020-01-22 Electric tool WO2020188994A1 (en)

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50118149A (en) * 1974-03-04 1975-09-16
JPS521367A (en) * 1975-06-24 1977-01-07 Kazumi Ishikawa Change gear device of multiple stage planetary gear
JPS53122579U (en) * 1977-03-07 1978-09-29
JPH0510399A (en) * 1991-07-08 1993-01-19 Toshiba Corp Planetary gears
JPH0868461A (en) * 1994-08-26 1996-03-12 Matsushita Electric Works Ltd Speed change gear
JP2005016732A (en) * 2004-10-22 2005-01-20 Futofumi Nagao Transmission and its gear shifting method
JP2009535583A (en) * 2006-04-30 2009-10-01 トマクテック・アクティーゼルスカブ transmission
CN101761615A (en) * 2008-10-30 2010-06-30 苏州宝时得电动工具有限公司 Speed change tool
JP2011511912A (en) * 2008-02-12 2011-04-14 スー ユン、ケウン Power transmission device using planetary gears having multiple gear trains

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50118149A (en) * 1974-03-04 1975-09-16
JPS521367A (en) * 1975-06-24 1977-01-07 Kazumi Ishikawa Change gear device of multiple stage planetary gear
JPS53122579U (en) * 1977-03-07 1978-09-29
JPH0510399A (en) * 1991-07-08 1993-01-19 Toshiba Corp Planetary gears
JPH0868461A (en) * 1994-08-26 1996-03-12 Matsushita Electric Works Ltd Speed change gear
JP2005016732A (en) * 2004-10-22 2005-01-20 Futofumi Nagao Transmission and its gear shifting method
JP2009535583A (en) * 2006-04-30 2009-10-01 トマクテック・アクティーゼルスカブ transmission
JP2011511912A (en) * 2008-02-12 2011-04-14 スー ユン、ケウン Power transmission device using planetary gears having multiple gear trains
CN101761615A (en) * 2008-10-30 2010-06-30 苏州宝时得电动工具有限公司 Speed change tool

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