JP2003094356A - Power tool with dynamic braking - Google Patents
Power tool with dynamic brakingInfo
- Publication number
- JP2003094356A JP2003094356A JP2001288109A JP2001288109A JP2003094356A JP 2003094356 A JP2003094356 A JP 2003094356A JP 2001288109 A JP2001288109 A JP 2001288109A JP 2001288109 A JP2001288109 A JP 2001288109A JP 2003094356 A JP2003094356 A JP 2003094356A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- dynamic braking
- tooth
- power tool
- rotor
- 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.)
- Pending
Links
Landscapes
- Portable Power Tools In General (AREA)
- Gear Transmission (AREA)
- Gears, Cams (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、騒音の発生を抑制
する発電制動付電動工具に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power tool with dynamic braking that suppresses noise generation.
【０００２】[0002]
【従来の技術】刃物等を駆動する電動工具については、
使用者がより安全に使用できることが要求されており、
スイッチを切ると電動機に発電制動力が生じ、停止時間
を短くできる発電制動付電動工具が広く使われるように
なってきた。2. Description of the Related Art Electric power tools for driving blades, etc.
It is required that the user can use it more safely,
When the switch is turned off, a dynamic braking force is generated in the electric motor, and electric tools with dynamic braking that can shorten the stop time have been widely used.
【０００３】この種の発電制動付電動工具をハスバ歯車
を用いた発電制動付の電気丸鋸を例に採り説明する。図
１は電気丸鋸の要部拡大断面図である。図に示す電気丸
鋸は電動機を内蔵し、その構成部品である回転子１は軸
受６により電動工具ハウジング１２に回転可能に取り付
けられている。回転子１の同軸上に軸受６より突出して
小歯車２が設けられる。小歯車２は回転子１の軸に直接
削成または成形され、場合によっては別部品として軸に
結合されている。この小歯車２と係合する大歯車４は出
力軸３に結合され、更に出力軸３の他端にはねじ９及び
２つのフランジ７、８によって鋸刃５が取り付けられ
る。回転子１の駆動力は小歯車２から大歯車４へ、更に
は鋸刃５へと伝達され、木材あるいは鋼管等を切断す
る。切断作業を終え、スイッチを切ると電動機に発電制
動力が生じ、短時間で回転が停止する機構となってい
る。An electric tool with dynamic braking of this kind will be described by taking an electric circular saw with dynamic braking using a helical gear as an example. FIG. 1 is an enlarged sectional view of a main part of an electric circular saw. The electric circular saw shown in the drawing has a built-in electric motor, and the rotor 1 as a component thereof is rotatably attached to a power tool housing 12 by a bearing 6. A small gear 2 is provided coaxially with the rotor 1 so as to project from the bearing 6. The pinion gear 2 is directly machined or formed on the shaft of the rotor 1, and is optionally connected to the shaft as a separate component. A large gear 4 that engages with the small gear 2 is connected to an output shaft 3, and a saw blade 5 is attached to the other end of the output shaft 3 by a screw 9 and two flanges 7 and 8. The driving force of the rotor 1 is transmitted from the small gear 2 to the large gear 4 and further to the saw blade 5 to cut wood, steel pipe or the like. When the cutting work is completed and the switch is turned off, a dynamic braking force is generated in the electric motor, and the rotation is stopped in a short time.
【０００４】[0004]
【発明が解決しようとする課題】電動工具は様々な使わ
れ方をされるので、長く使用している間に設計仕様以上
の衝撃負荷が加わることがある。上記した電気丸鋸の場
合であれば、木材によって鋸刃５が挟まれ丸鋸本体が急
速に戻される反発を生じたとき、木材中に入っている釘
を切断したとき、切断片が鋸刃５に巻き込まれたとき等
である。このような衝撃負荷が加わると、制動時に騒音
が発生し易い。Since the electric power tool is used in various ways, an impact load exceeding the design specifications may be applied during long use. In the case of the above-described electric circular saw, when the saw blade 5 is sandwiched by wood and the circular saw body is rapidly returned, when a nail contained in the wood is cut, the cutting piece is a saw blade. It is when it is caught in 5. When such an impact load is applied, noise is likely to occur during braking.
【０００５】図８及び図９は従来の電気丸鋸の歯車部分
の動作状態を示す説明図であり、図８（Ａ）及び図９
（Ａ）は無負荷時又は通常切削時の負荷が加わったとき
の状態、図８（Ｂ）及び図９（Ｂ）は衝撃負荷が加わっ
たときの状態を示し、図中矢印は力の伝達方向を示す。
なお、図７は従来の電気丸鋸に使用される大歯車４の歯
１１を示す要部拡大斜視図である。FIGS. 8 and 9 are explanatory views showing the operating state of the gear portion of a conventional electric circular saw, and FIGS.
(A) shows a state when no load is applied or a load is applied during normal cutting, and FIGS. 8 (B) and 9 (B) show a state when an impact load is applied. In the figure, arrows indicate force transmission. Indicates the direction.
7. FIG. 7 is an enlarged perspective view of essential parts showing the teeth 11 of the large gear 4 used in the conventional electric circular saw.
【０００６】図８（Ａ）に示すように通常切削時の負荷
が加わっている状態では、小歯車２の歯１０と大歯車４
の歯１１とはほぼ歯幅全面で噛み合う。しかし、衝撃負
荷が加わると図８（Ｂ）に示すように片持ち支持される
小歯車２が軸受６を支点として撓み、歯１０は歯１１の
軸受６側で局部的に噛み合う（当接する）ことになる。
この小歯車２の歯１０と大歯車４の歯１１との局部的な
噛み合い（当接）によって、図９に示すように歯１０と
歯１１の歯面が変形し、駆動歯面１３と駆動歯面１４に
凹部１３ｂ、１４ｂが発生し、裏歯面１５と裏歯面１６
に凸部１５ｂ、１６ｂが発生してしまう。As shown in FIG. 8 (A), the teeth 10 of the small gear 2 and the large gear 4 are in a state where a load is applied during normal cutting.
It meshes with the teeth 11 of substantially the entire tooth width. However, when an impact load is applied, as shown in FIG. 8B, the cantilever-supported small gear 2 bends around the bearing 6 as a fulcrum, and the tooth 10 locally meshes (abuts) on the bearing 6 side of the tooth 11. It will be.
Due to the local meshing (contact) between the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4, the tooth surfaces of the teeth 10 and 11 are deformed as shown in FIG. Recesses 13b and 14b are formed in the tooth surface 14, and the back tooth surface 15 and the back tooth surface 16 are formed.
The convex portions 15b and 16b are generated.
【０００７】上記したように小歯車２の歯１０と大歯車
４の歯１１の歯面が変形すると、正転時、つまり小歯車
２から大歯車４へ回転力が伝達されるときは、図９
（Ａ）に示すように駆動歯面１３、１４が噛み合う（当
接する）ために騒音の発生等は認められないが、制動
時、つまり大歯車４から小歯車２へ回転力が伝達される
ときには、図９（Ｂ）に示すように正転時とは逆に、裏
歯面１５、１６の凸部１５ｂ、１６ｂ同士が噛み合う
（当接する）ことになり、歯１０と歯１１との噛み合い
（当接）が悪くなり、騒音が発生してしまう。前記した
騒音の発生は、図９に示されているように小歯車２の歯
１０の歯厚と大歯車４の歯１１の歯厚の関係が、歯１０
の歯厚よりも歯１１の歯厚が大きい寸法関係となってい
るが、上記したように凸部１５ｂ、１６ｂ同士が噛み合
う（当接する）ことにより、歯１０と歯１１との間の隙
間で小歯車２及び大歯車４が振動してしまうために発生
し、小歯車２及び大歯車４の裏歯面１５、１６にわずか
な変形が生じた場合でも噛み合いが悪く、騒音が悪化し
てしまうものである。When the tooth surfaces of the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4 are deformed as described above, when the normal rotation, that is, when the rotational force is transmitted from the small gear 2 to the large gear 4, 9
As shown in (A), since the drive tooth surfaces 13 and 14 mesh (contact) with each other, noise is not generated, but during braking, that is, when the rotational force is transmitted from the large gear 4 to the small gear 2. As shown in FIG. 9 (B), the convex portions 15b and 16b of the back tooth surfaces 15 and 16 mesh (contact) with each other, contrary to the normal rotation, and the meshing between the teeth 10 and 11 ( (Contact) becomes worse, and noise is generated. As shown in FIG. 9, the above-described noise is generated when the relationship between the tooth thickness of the tooth 10 of the small gear 2 and the tooth thickness of the tooth 11 of the large gear 4 is as follows.
The tooth thickness of the tooth 11 is larger than the tooth thickness of the tooth 11. However, as described above, the convex portions 15b and 16b are meshed with (abutted against) each other, so that the gap between the tooth 10 and the tooth 11 is increased. This occurs because the small gear 2 and the large gear 4 vibrate, and even if the back tooth surfaces 15 and 16 of the small gear 2 and the large gear 4 are slightly deformed, the meshing is poor and the noise is deteriorated. It is a thing.
【０００８】上記問題点を解決する策として、歯面に変
形が起こり難いように歯車のモジュールを大きくする、
あるいは小歯車２を撓み難くする等の策があるが、電動
工具の小形化とは逆行する構成となるので、これらの策
は実施し難かった。As a measure to solve the above problems, the gear module is enlarged so that the tooth surface is less likely to be deformed.
Alternatively, there are measures such as making the small gear 2 difficult to bend, but these measures are difficult to implement because the structure is contrary to the downsizing of the electric tool.
【０００９】本発明の課題は、上記問題点を解消し、発
電制動時に発生する騒音を抑制することができる発電制
動付電動工具を提供することである。An object of the present invention is to solve the above problems and provide a power tool with dynamic braking capable of suppressing noise generated during dynamic braking.
【００１０】[0010]
【課題を解決するための手段】上記目的は、小歯車又は
大歯車の、発電制動時に噛み合う歯面の回転子軸受側に
歯厚が小さくなる方向に傾斜した傾斜面を設けることに
より達成される。The above object is achieved by providing an inclined surface inclined in a direction in which the tooth thickness becomes smaller on the rotor bearing side of the tooth surface of a small gear or a large gear that meshes during dynamic braking. .
【００１１】[0011]
【発明の実施の形態】本発明発電制動付電動工具につい
てハスバ歯車を用いた発電制動付電気丸鋸を例に採り説
明する。電気丸鋸の動力伝達部の概略は図１に示す従来
の電気丸鋸と同じであり、それぞれの部位についての説
明は省略する。BEST MODE FOR CARRYING OUT THE INVENTION An electric power tool with dynamic braking according to the present invention will be described by taking an electric circular saw with dynamic braking using a helical gear as an example. The outline of the power transmission section of the electric circular saw is the same as that of the conventional electric circular saw shown in FIG. 1, and the description of each part is omitted.
【００１２】図２及び図３は本発明電気丸鋸の歯車部分
の動作状態を示す説明図であり、図２（Ａ）及び図３
（Ａ）は無負荷時又は通常切削時の負荷が加わったとき
の状態、図２（Ｂ）は衝撃負荷が加わったときの状態、
図３（Ｂ）は発電制動時の状態を示し、図中矢印は力の
伝達方向を示す。2 and 3 are explanatory views showing the operating state of the gear portion of the electric circular saw of the present invention, and FIG. 2 (A) and FIG.
(A) is a state when no load is applied or a load is applied during normal cutting, and FIG. 2 (B) is a state when an impact load is applied,
FIG. 3B shows the state during dynamic braking, and the arrows in the figure show the direction of force transmission.
【００１３】図２に示すように、大歯車４の歯１０の制
動時に噛み合う歯面である裏歯面１６の回転子軸受６側
には歯１０の歯厚が小さくなる方向に傾斜した傾斜部１
６ａが設けられている。As shown in FIG. 2, on the rotor bearing 6 side of the back tooth surface 16 which is the tooth surface that meshes with the teeth 10 of the large gear 4 at the time of braking, an inclined portion that is inclined in the direction in which the tooth thickness of the teeth 10 becomes smaller. 1
6a is provided.
【００１４】無負荷時又は通常切削時の負荷が加わると
きには、図２（Ａ）に示すように小歯車２の歯１０と大
歯車４の歯１１とはほぼ歯幅全面で噛み合う（当接す
る）。図２（Ｂ）に示すように、木材によって鋸刃５が
挟まれ丸鋸本体が急速に戻される反発を生じる、木材中
に入っている釘を切断する、切断片が鋸刃５に巻き込ま
れる等の理由により衝撃負荷が加わると、片持ち支持で
ある小歯車２が軸受６を支点として撓み、歯１０と歯１
１とが軸受６側で局部的に噛み合う（当接する）ことに
なる。この小歯車２の歯１０と大歯車４の歯１１との局
部的な噛み合い（当接）によって、図３に示すように小
歯車２及び大歯車４の駆動歯面１３、１４に凹部１３
ａ、１４ｂが発生すると共に、小歯車２の裏歯面１５に
凸部１５ａが発生してしまう。しかし、歯１０と歯１１
との局部的な噛み合い（当接）によって大歯車４の裏歯
面１６にも変形が生じるものの、上記したように大歯車
４の裏歯面１６の回転子軸受６側に歯厚が小さくなるよ
うに傾斜した傾斜部１６ａを設けた構成としたため、歯
１１の裏歯面１６の歯筋方向よりも変形部が突出してし
まうことを抑制することができる。なお、図３中の１６
ａ’は変形後の傾斜面である。このため、発電制動時、
つまり大歯車４から小歯車２へ回転力が伝達される際に
は、過大な衝撃負荷は加わらないので図３（Ｂ）に示す
ように小歯車２の撓みは非常に小さく、小歯車２の裏歯
面１５の凸部１５ａが大歯車４の裏歯面１６に接触する
ことはなく、歯１０と歯１１とはほぼ歯幅全面で噛み合
う（当接する）ため、騒音が発生することを抑制するこ
とができる。なお、大歯車４の歯１１の裏歯面１６の傾
斜面１６ａの傾斜角は小歯車２の裏歯面１５に生じる凸
部１５ａよりも十分に大きく設計する必要がある。When no load is applied or a load is applied during normal cutting, as shown in FIG. 2A, the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4 mesh (contact) with each other over substantially the entire tooth width. . As shown in FIG. 2 (B), the saw blade 5 is sandwiched by the wood and the circular saw body is rapidly returned, cutting the nail contained in the wood, and a cutting piece is caught in the saw blade 5. When an impact load is applied for some reason, the small gear 2, which is cantilevered, bends around the bearing 6 as a fulcrum, and the teeth 10 and the teeth 1
1 and 1 locally mesh (contact) with each other on the bearing 6 side. Due to the local meshing (contact) between the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4, the recesses 13 are formed in the drive tooth surfaces 13, 14 of the small gear 2 and the large gear 4 as shown in FIG.
A and 14b are generated, and a convex portion 15a is generated on the back tooth surface 15 of the small gear 2. However, tooth 10 and tooth 11
Although the back tooth surface 16 of the large gear 4 is also deformed due to the local meshing (contact) with the back tooth surface 16, the tooth thickness becomes smaller on the rotor bearing 6 side of the back tooth surface 16 of the large gear 4 as described above. Since the inclined portion 16a is provided as described above, it is possible to prevent the deformed portion from protruding beyond the tooth trace direction of the back tooth surface 16 of the tooth 11. In addition, 16 in FIG.
a'is a slanted surface after deformation. Therefore, during dynamic braking,
That is, when the rotational force is transmitted from the large gear 4 to the small gear 2, an excessive impact load is not applied, so that the flexure of the small gear 2 is very small as shown in FIG. The convex portion 15a of the back tooth surface 15 does not come into contact with the back tooth surface 16 of the large gear 4, and the teeth 10 and the teeth 11 mesh (contact) with each other over substantially the entire tooth width, thus suppressing noise generation. can do. The inclination angle of the inclined surface 16a of the back tooth surface 16 of the tooth 11 of the large gear 4 needs to be designed to be sufficiently larger than the convex portion 15a generated on the back tooth surface 15 of the small gear 2.
【００１５】上記したように大歯車４の発電制動時に噛
み合う歯面である裏歯面１６の回転子軸受６側に歯厚が
小さくなる方向に傾斜した傾斜面１６ａを設けたことに
より、図２（Ｂ）に示すように工具作業時に衝撃負荷が
加わった際に片持ち支持である小歯車２が軸受６を支点
として撓み、小歯車２の歯１０と大歯車４の歯１１との
局部的な噛み合い（当接）によって大歯車４の裏歯面１
６に変形が生じたとしても、発電制動時に歯１０の裏歯
面１６と歯１１の裏歯面１５とが局部的に噛み合う（当
接する）ことを抑制することができるため、発電制動時
に発生する騒音を抑制することができ、発電制動付電動
工具を長く使用したとしても発電制動時に発生する騒音
の悪化を抑制することができる。As described above, by providing the inclined surface 16a which is inclined in the direction in which the tooth thickness becomes smaller on the rotor bearing 6 side of the back tooth surface 16 which is the tooth surface which meshes with the large gear 4 at the time of dynamic braking, FIG. As shown in (B), when a shock load is applied during the tool work, the small gear 2, which is cantilevered, bends around the bearing 6 as a fulcrum, and the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4 are locally formed. Back tooth surface 1 of the large gear 4 due to the meshing (contact)
Even if 6 is deformed, it is possible to prevent the back tooth surface 16 of the tooth 10 and the back tooth surface 15 of the tooth 11 from locally engaging (contacting) with each other during power generation braking. Noise can be suppressed, and even if the electric tool with dynamic braking is used for a long time, it is possible to suppress deterioration of noise generated during dynamic braking.
【００１６】次に本発明電機丸鋸の他の実施形態を図４
〜図６を用いて説明する。なお、図４は本発明電気丸鋸
の大歯車４の歯１１を示す要部拡大斜視図、図５及び図
６は本発明電気丸鋸の歯車部分の動作状態を示す説明図
であり、図５（Ａ）及び図６（Ａ）は無負荷時又は通常
切削時の負荷が加わったときの状態、図５（Ｂ）は衝撃
負荷が加わったときの状態、図６（Ｂ）は発電制動時の
状態を示し、図中矢印は力の伝達方向を示す。Next, another embodiment of the circular saw of the present invention will be described with reference to FIG.
~ It demonstrates using FIG. FIG. 4 is an enlarged perspective view of a main portion showing the teeth 11 of the large gear 4 of the electric circular saw of the present invention, and FIGS. 5 and 6 are explanatory views showing the operating state of the gear portion of the electric circular saw of the present invention. 5 (A) and FIG. 6 (A) are states when no load or load is applied during normal cutting, FIG. 5 (B) is a state when impact load is applied, and FIG. 6 (B) is dynamic braking. In the figure, the arrow indicates the direction of force transmission.
【００１７】本実施形態は、上記実施形態で示した大歯
車４の歯１１の裏歯面１６の回転子軸受６側に傾斜面１
６ａを設けると共に、傾斜面１６ａと対向する駆動歯面
１４に傾斜面１６ａと同様に歯厚が小さくなる方向に傾
斜する傾斜面１４ａを設けた構成をしたものである。In this embodiment, the inclined surface 1 is provided on the rotor bearing 6 side of the back tooth surface 16 of the tooth 11 of the large gear 4 shown in the above embodiment.
6a, and the drive tooth surface 14 facing the inclined surface 16a is provided with an inclined surface 14a that is inclined in a direction in which the tooth thickness becomes smaller, similar to the inclined surface 16a.
【００１８】上記した構成とすることにより、上記実施
形態と同様に発電制動時に発生する騒音を抑制すること
ができるという効果を得られるものであると共に、図５
（Ｂ）に示すように工具作業時に衝撃負荷が加わった際
に片持ち支持である小歯車２が軸受６を支点として撓ん
だとしても小歯車２の歯１０と大歯車４の歯１１とが局
部的な噛み合い（当接）を起こすことを抑制することが
できるものである。これによって、小歯車２の歯１０と
大歯車４の歯１１の発電制動時に噛み合う歯面である裏
歯面１５、１６に発生する変形を抑制することができ、
発電制動時に発生する騒音を更に抑制することができる
ものである。なお、図６中の１６ａ’は変形後の傾斜
面、１４ａ’は変形後の傾斜面を示す。With the above-mentioned structure, it is possible to obtain the effect that the noise generated during the dynamic braking can be suppressed as in the case of the above-mentioned embodiment, and in addition, as shown in FIG.
As shown in (B), even if the small gear 2, which is cantilevered, bends around the bearing 6 as a fulcrum when an impact load is applied during tool work, the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4 are It is possible to suppress the occurrence of local meshing (contact). As a result, it is possible to suppress the deformation of the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4 that occur on the back tooth surfaces 15 and 16 that are tooth surfaces that mesh with each other during dynamic braking.
The noise generated during dynamic braking can be further suppressed. In addition, 16a 'in FIG. 6 shows an inclined surface after deformation, and 14a' shows an inclined surface after deformation.
【００１９】なお、上記実施形態では、大歯車４の歯１
１の歯面１４、１６の回転子軸受６側に歯厚が小さくな
る方向に傾斜した傾斜面１４、１６を設けた構成とした
が、小歯車２の歯１０の裏歯面１５の回転子軸受６側に
歯厚が小さくなる方向に傾斜する傾斜面を設けた構成、
該裏歯面傾斜面にの加えて駆動歯面１３の回転子軸受６
側に歯厚が小さくなる方向に傾斜する傾斜面を設けた構
成としても上記実施形態と同様の効果を得ることができ
るものである。In the above embodiment, the teeth 1 of the gear wheel 4 are
Although the inclined surfaces 14 and 16 inclined in the direction in which the tooth thickness becomes smaller are provided on the tooth bearing surfaces 14 and 16 of the first rotor on the side of the rotor bearing 6, the rotor of the back tooth surface 15 of the tooth 10 of the pinion 2 is described. A configuration in which an inclined surface that is inclined in the direction in which the tooth thickness decreases is provided on the bearing 6 side,
In addition to the back tooth surface inclined surface, the rotor bearing 6 of the drive tooth surface 13
The same effect as in the above embodiment can be obtained even if the side surface is provided with an inclined surface that is inclined in the direction in which the tooth thickness decreases.
【００２０】また、小歯車２及び大歯車４のそれぞれの
歯１０、１１の裏歯面１３、１５の回転子軸受６側に歯
厚が小さくなる方向に傾斜した傾斜面を設けた構成とし
た場合には、歯１０、歯１１の歯面の変形を更に抑制す
ることができると共に、発電制動時の騒音の発生を更に
抑制することができるものである。Further, the back gear surfaces 13 and 15 of the teeth 10 and 11 of the small gear 2 and the large gear 4, respectively, are provided on the rotor bearing 6 side with inclined surfaces inclined in the direction in which the tooth thickness decreases. In this case, the deformation of the tooth surfaces of the teeth 10 and 11 can be further suppressed, and the generation of noise during dynamic braking can be further suppressed.
【００２１】なお、上記した小歯車あるいは大歯車の歯
面に設けられる傾斜面は、本実施形態では図２（Ｂ）及
び図５（Ｂ）に示すように片持ち支持である小歯車２が
軸受６を支点として撓んだとしても小歯車２の歯１０と
大歯車４の歯１１とが局部的な噛み合い（当接）を起こ
すことを抑制する目的から図４に示すように円弧形状と
したが、直線形状としても良いものである。In the present embodiment, the inclined surface provided on the tooth surface of the small gear or the large gear is a cantilever-supported small gear 2 as shown in FIGS. 2 (B) and 5 (B). Even if the bearing 6 is bent about the fulcrum, the teeth 10 of the small gear 2 and the teeth 11 of the large gear 4 have a circular arc shape as shown in FIG. 4 for the purpose of suppressing local meshing (contact). However, a linear shape is also possible.
【００２２】なお、上記実施形態では、歯車としてハス
バ歯車を例に採り説明したが、平歯車であっても上記実
施形態と同様に発電制動時の騒音を抑制することができ
るものである。In the above embodiment, the helical gear has been described as an example of the gear. However, even a spur gear can suppress noise during dynamic braking as in the above embodiment.
【００２３】次に本発明電気丸鋸の騒音低減の定量的効
果について説明する。本発明電気丸鋸の歯車は、モジュ
ール０．８で歯幅１２ｍｍの大歯車４において、円弧は
片持ち支持である小歯車２の軸受け側端面から３ｍｍの
位置から歯幅端面まで歯厚が暫時小さくなる方向に片歯
面０．０５ｍｍの円弧を駆動歯面及び裏歯面に形成した
ものとした。またそれ以外の影響を少なくするために、
同一の本体を用いた。これら歯車を組み込んだ本体で、
鋸刃５にある一定の衝撃荷重を加えた。なお騒音測定は
鋸刃方向１ｍの位置からのマイクによるものである。そ
の結果、ブレーキ音で従来歯車を組み込んだ本体が９８
ｄＢＡであったのに対し、本発明歯車では８８ｄＢＡと
なり、１０ｄＢＡもの騒音低減効果が得られた。ここで
衝撃荷重を加えた後での小歯車２及び大歯車４の噛み合
いピッチ円系直径上の歯筋方向の変形量は、それぞれ従
来が６０μｍ、本発明では１５μｍで駆動歯面が凹み、
裏歯面で同量で凸形状となっている。騒音低減の要因
は、本発明歯車は同衝撃荷重において従来の電気丸鋸の
歯車に対し、大歯車４の歯筋方向に円弧を有しているこ
とから、小歯車２の変形した歯面と接触しないことによ
るもので、それにより衝撃荷重による歯面変形の影響を
受けないためである。Next, the quantitative effect of noise reduction of the electric circular saw of the present invention will be described. The gear of the electric circular saw of the present invention is a module 0.8 and a large gear 4 having a tooth width of 12 mm. An arc of 0.05 mm on one tooth surface was formed on the drive tooth surface and the back tooth surface in the direction of decreasing. In addition, in order to reduce other effects,
The same body was used. With the body incorporating these gears,
A certain impact load was applied to the saw blade 5. The noise measurement was performed by a microphone from a position 1 m in the saw blade direction. As a result, the brake sound makes 98
In contrast to dBA, the gear of the present invention has 88 dBA, and a noise reduction effect of 10 dBA was obtained. Here, the amount of deformation in the tooth trace direction on the meshing pitch circle system diameter of the small gear 2 and the large gear 4 after applying the impact load is 60 μm in the conventional case and 15 μm in the present invention, and the drive tooth surface is dented,
The back tooth surface has the same amount and a convex shape. The reason for the noise reduction is that the gear of the present invention has an arc in the tooth trace direction of the large gear 4 in comparison with the gear of the conventional electric circular saw under the same impact load, so that the tooth surface of the small gear 2 is deformed. This is because they do not come into contact with each other, so that they are not affected by tooth surface deformation due to impact load.
【００２４】本来、回転数の高い小歯車２に本発明歯車
を適用することが有効であるが、今回のような構造の小
歯車の場合、切削では被加工物と工具が干渉しやすいこ
とから加工困難である。このような場合には塑性加工の
転造等型による成形加工が有効である。一方大歯車４に
ついては、切削、成形とも可能である。Originally, it is effective to apply the gear of the present invention to the small gear 2 having a high rotational speed. However, in the case of the small gear having the structure as described above, the workpiece and the tool are likely to interfere with each other during cutting. It is difficult to process. In such a case, the forming work by the rolling isomorphism of plastic working is effective. On the other hand, the large gear 4 can be cut and formed.
【００２５】[0025]
【発明の効果】本発明によれば、上記したように、小歯
車又は大歯車の、発電制動時に噛み合う歯面の回転子軸
受側に歯厚が小さくなる方向に傾斜した傾斜面を設けた
ことにより、発電制動時に発生する騒音を抑制すること
ができる発電制動付電動工具を提供することができるよ
うになる。According to the present invention, as described above, the small gear or the large gear is provided with the inclined surface which is inclined in the direction of decreasing the tooth thickness on the rotor bearing side of the tooth surface meshed during the dynamic braking. As a result, it is possible to provide a power tool with dynamic braking that can suppress noise generated during dynamic braking.
【図１】発電制動付電動工具の要部拡大断面図。FIG. 1 is an enlarged cross-sectional view of essential parts of a power tool with dynamic braking.
【図２】本発明発電制動付電動工具の一実施形態を構成
する歯車部分の動作状態を示す説明図。FIG. 2 is an explanatory diagram showing an operating state of a gear portion that constitutes an embodiment of the electric power tool with dynamic braking of the present invention.
【図３】本発明発電制動付電動工具の一実施形態を構成
する歯車部分の動作状態を示す説明図。FIG. 3 is an explanatory diagram showing an operating state of a gear portion that constitutes an embodiment of the electric power tool with dynamic braking of the present invention.
【図４】本発明発電制動付電動工具を構成する歯車の他
の実施形態を示す要部拡大斜視図。FIG. 4 is an enlarged perspective view of essential parts showing another embodiment of a gear that constitutes the electric power tool with dynamic braking of the present invention.
【図５】本発明発電制動付電動工具の他の実施形態を構
成する歯車部分の動作状態を示す説明図。FIG. 5 is an explanatory diagram showing an operating state of a gear portion that constitutes another embodiment of the electric power tool with dynamic braking of the present invention.
【図６】本発明発電制動付電動工具の他の実施形態を構
成する歯車部分の動作状態を示す説明図。FIG. 6 is an explanatory diagram showing an operating state of a gear portion that constitutes another embodiment of the electric power tool with dynamic braking of the present invention.
【図７】従来の電動工具の歯車の一例を示す要部拡大斜
視図。FIG. 7 is an enlarged perspective view of an essential part showing an example of a gear of a conventional electric power tool.
【図８】従来の発電制動付電動工具の歯車部分の動作状
態を示す説明図。FIG. 8 is an explanatory diagram showing an operating state of a gear portion of a conventional power tool with dynamic braking.
【図９】従来の発電制動付電動工具の歯車部分の動作状
態を示す説明図。FIG. 9 is an explanatory diagram showing an operating state of a gear portion of a conventional power tool with dynamic braking.
１は回転子、２は小歯車、３は出力軸、４は大歯車、５
は鋸刃、６は軸受、７、８はフランジ、９はねじ、１０
は小歯車２の歯、１１は大歯車４の歯、１２は電動工具
ハウジング、１３、１４は駆動歯面、１５、１６は大歯
車４の裏歯面、１４ａ、１５ａ、１６ａは傾斜面、１４
ａ’、１５ａ’、１６ａ’は変形後の傾斜面である。1 is a rotor, 2 is a small gear, 3 is an output shaft, 4 is a large gear, 5
Is a saw blade, 6 is a bearing, 7 and 8 are flanges, 9 is a screw, 10
Is a tooth of the small gear 2, 11 is a tooth of the large gear 4, 12 is a power tool housing, 13 and 14 are drive tooth surfaces, 15 and 16 are back tooth surfaces of the large gear 4, 14a, 15a and 16a are inclined surfaces, 14
Reference numerals a ', 15a', and 16a 'are inclined surfaces after deformation.
───────────────────────────────────────────────────── フロントページの続き Ｆターム(参考） 3J009 DA06 DA11 EA04 EA12 EA21 EA32 EA43 EB02 FA11 3J030 AB02 BA05 BB09 CA10 ─────────────────────────────────────────────────── ─── Continued front page F term (reference) 3J009 DA06 DA11 EA04 EA12 EA21 EA32 EA43 EB02 FA11 3J030 AB02 BA05 BB09 CA10
Claims (3)
と、該回転子の同軸上に該回転子の軸受より突出して設
けられた小歯車と、該小歯車と係合する大歯車とを備え
た発電制動付電動工具であって、前記小歯車又は前記大
歯車の、発電制動時に噛み合う歯面の前記回転子軸受側
に歯厚が小さくなる方向に傾斜した傾斜面を設けたこと
を特徴とする発電制動付電動工具。1. A rotor of an electric motor having a dynamic braking function, a small gear provided coaxially with the rotor so as to project from a bearing of the rotor, and a large gear engaged with the small gear. A power tool with dynamic braking, characterized in that an inclined surface that is inclined in a direction in which the tooth thickness becomes smaller is provided on the rotor bearing side of the tooth surface of the small gear or the large gear that meshes during dynamic braking. Power tool with dynamic braking.
の双方に設けたことを特徴とする請求項１記載の発電制
動付電動工具。2. The power tool with dynamic braking according to claim 1, wherein the inclined surface is provided on both the small gear and the large gear.
前記小歯車及び前記大歯車の無負荷回転時に噛み合う歯
面の前記回転子軸受側に歯厚が小さくなる方向に傾斜し
た傾斜面を設けたことを特徴とする請求項１あるいは請
求項２記載の発電制動付電動工具。3. An inclined surface inclined in a direction in which the tooth thickness becomes smaller is provided on the rotor bearing side of a tooth surface of the small gear or the large gear, or a tooth surface of the small gear and the large gear that mesh with each other during no-load rotation. The power tool with dynamic braking according to claim 1 or 2, characterized in that.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001288109A JP2003094356A (en) | 2001-09-21 | 2001-09-21 | Power tool with dynamic braking |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001288109A JP2003094356A (en) | 2001-09-21 | 2001-09-21 | Power tool with dynamic braking |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003094356A true JP2003094356A (en) | 2003-04-03 |
Family
ID=19110808
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001288109A Pending JP2003094356A (en) | 2001-09-21 | 2001-09-21 | Power tool with dynamic braking |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003094356A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008232383A (en) * | 2007-03-23 | 2008-10-02 | Enplas Corp | Resin double helical gear |
| JP4949248B2 (en) * | 2005-07-28 | 2012-06-06 | 武蔵精密工業株式会社 | Gear design method and gear using CAD system |
| JP2012241865A (en) * | 2011-05-23 | 2012-12-10 | Sumitomo Heavy Ind Ltd | Flexible meshing-type type gear device and method of manufacturing external gear or the like used for the same |
-
2001
- 2001-09-21 JP JP2001288109A patent/JP2003094356A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4949248B2 (en) * | 2005-07-28 | 2012-06-06 | 武蔵精密工業株式会社 | Gear design method and gear using CAD system |
| US8250941B2 (en) | 2005-07-28 | 2012-08-28 | Musashi Seimitsu Kogyo Kabushiki Kaisha | Method of designing gear using CAD system, and gear |
| JP2008232383A (en) * | 2007-03-23 | 2008-10-02 | Enplas Corp | Resin double helical gear |
| JP2012241865A (en) * | 2011-05-23 | 2012-12-10 | Sumitomo Heavy Ind Ltd | Flexible meshing-type type gear device and method of manufacturing external gear or the like used for the same |
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