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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