JPH029150Y2 - - Google Patents
Info
- Publication number
- JPH029150Y2 JPH029150Y2 JP1985185344U JP18534485U JPH029150Y2 JP H029150 Y2 JPH029150 Y2 JP H029150Y2 JP 1985185344 U JP1985185344 U JP 1985185344U JP 18534485 U JP18534485 U JP 18534485U JP H029150 Y2 JPH029150 Y2 JP H029150Y2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- fixed
- driven gear
- teeth
- driven
- 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.)
- Expired
Links
- 238000005096 rolling process Methods 0.000 claims description 7
- 229910000831 Steel Inorganic materials 0.000 description 10
- 239000010959 steel Substances 0.000 description 10
- 230000002093 peripheral effect Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 3
- 239000004519 grease Substances 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Description
【考案の詳細な説明】
産業上の利用分野
本考案は歯車減速機構に係り、中間歯車とこれ
に噛合する固定歯車及び従動歯車を用いて減速を
行なう歯車減速機構に関する。[Detailed Description of the Invention] Industrial Application Field The present invention relates to a gear reduction mechanism, and more particularly, to a gear reduction mechanism that performs deceleration using an intermediate gear, a fixed gear meshing with the intermediate gear, and a driven gear.
従来の技術
第３図は従来の歯車減速機構の一例を示す。モ
ータで駆動される駆動軸１に偏心して取付けられ
た中間歯車２は固定歯車３の内周を公転する。固
定歯車３と所定の歯数差を有する従動歯車４は上
記中間歯車２の公転によつて固定歯車３に対しそ
の歯数差分だけ回転する。これによつて従動歯車
４に固定された出力回転軸５は、駆動軸１の回転
を減速して回転せしめられる。Prior Art FIG. 3 shows an example of a conventional gear reduction mechanism. An intermediate gear 2 eccentrically attached to a drive shaft 1 driven by a motor revolves around the inner circumference of a fixed gear 3. The driven gear 4, which has a predetermined difference in the number of teeth from the fixed gear 3, rotates with respect to the fixed gear 3 by the difference in the number of teeth due to the revolution of the intermediate gear 2. As a result, the output rotating shaft 5 fixed to the driven gear 4 is rotated while decelerating the rotation of the drive shaft 1.
考案が解決しようとする問題点
第３図示の従来機構においては、固定歯車３と
従動歯車４との周縁は接触し、従動歯車４が摺動
回転を行なう。この摺動時のすべり摩擦が大なる
ため、駆動軸１の回転を出力回転軸５に伝達する
効率が低下するという問題点があつた。また、従
来より、上記固定歯車３と従動歯車４との周縁を
互いに離間させ、出力回転軸５の軸受部６をラジ
アル軸受構造としたものがある。このものは効率
の低下はないが、ラジアル軸受構造部の出力回転
軸５に対する支持が高精度でなければならず、こ
の軸受構造が複雑かつ大型化してしまう。また中
間歯車２の回転により発生するノイズが外部に洩
れるという問題点があつた。Problems to be Solved by the Invention In the conventional mechanism shown in FIG. 3, the peripheral edges of the fixed gear 3 and the driven gear 4 are in contact, and the driven gear 4 performs sliding rotation. Since the sliding friction during this sliding becomes large, there is a problem in that the efficiency of transmitting the rotation of the drive shaft 1 to the output rotating shaft 5 decreases. Further, conventionally, there is a device in which the circumferential edges of the fixed gear 3 and the driven gear 4 are spaced apart from each other, and the bearing portion 6 of the output rotating shaft 5 has a radial bearing structure. Although this does not reduce efficiency, the radial bearing structure must support the output rotating shaft 5 with high precision, making the bearing structure complicated and large. Further, there was a problem in that noise generated by the rotation of the intermediate gear 2 leaked to the outside.
そこで、本考案は固定歯車と従動歯車との間に
ころがり軸受構造を設けることにより、上記の問
題点を解決した歯車減速機構を提供することを目
的とする。 Therefore, an object of the present invention is to provide a gear reduction mechanism that solves the above problems by providing a rolling bearing structure between the fixed gear and the driven gear.
問題点を解決するための手段
本考案において、中間歯車は回転する駆動軸に
偏心して取付けられており、内歯の固定歯車に内
接噛合して上記駆動軸の歯車により回転及び公転
を行なう。また、中間歯車は固定歯車と同一径で
互いに周縁を接し歯数差を有する従動歯車に噛合
しており、従動歯車は上記歯数差に応じて減速回
転し、従動歯車に固定された出力回転軸が回転す
る。上記固定歯車の周縁と従動歯車の周縁との間
にはころがり軸受構造が設けられ従動歯車を支持
すると共に、従動歯車に固定された出力回転軸を
ブツシユで支持している。Means for Solving the Problems In the present invention, the intermediate gear is eccentrically attached to the rotating drive shaft, is internally meshed with the fixed internal gear, and is rotated and revolved by the gear of the drive shaft. In addition, the intermediate gear has the same diameter as the fixed gear, contacts the peripheral edges of each other, and meshes with a driven gear having a difference in the number of teeth.The driven gear rotates at a reduced speed according to the difference in the number of teeth, and the output rotation fixed to the driven gear The shaft rotates. A rolling bearing structure is provided between the periphery of the fixed gear and the periphery of the driven gear to support the driven gear, and also supports the output rotating shaft fixed to the driven gear by a bush.
作 用
本考案においては、固定歯車と従動歯車との間
のころがり軸受構造で従動歯車を支持しているた
め、従動歯車の回転に対する摩擦抵抗が小とな
る。Function In the present invention, since the driven gear is supported by a rolling bearing structure between the fixed gear and the driven gear, the frictional resistance against rotation of the driven gear is reduced.
実施例
第１図は本考案機構の一実施例の断面図を示
す。同図中、１１はモータ等により駆動される駆
動軸である。駆動軸１１の先端には偏心した位置
に孔が穿設され、この孔に中間歯車軸１２が圧入
固定されている。中間歯車１３は上記中間歯車軸
１２に回転自在に支持されており、その外周に設
けられた歯車の歯数は例えば「30」程度である。
固定歯車１４は駆動軸１１を中心とする内歯車で
あり、その歯数は例えば「99」である。この中間
歯車１３は固定歯車１４に対して転位した状態で
噛合し、駆動軸１１の回転により固定歯車１４の
内周を公転する。Embodiment FIG. 1 shows a sectional view of an embodiment of the mechanism of the present invention. In the figure, 11 is a drive shaft driven by a motor or the like. A hole is bored at an eccentric position at the tip of the drive shaft 11, and an intermediate gear shaft 12 is press-fitted into this hole. The intermediate gear 13 is rotatably supported by the intermediate gear shaft 12, and the number of teeth of the gear provided on its outer periphery is, for example, about 30.
The fixed gear 14 is an internal gear centered on the drive shaft 11, and has, for example, 99 teeth. This intermediate gear 13 meshes with the fixed gear 14 in a shifted state, and revolves around the inner periphery of the fixed gear 14 as the drive shaft 11 rotates.
従動歯車１５は内径及び外径寸法が略固定歯車
１４のそれと同一の内歯車であり、その歯数は固
定歯車１４より多く例えば「102」とされている。
従動歯車１５は駆動軸１１と軸中心が一致する出
力回転軸１６に固定されており、中間歯車１３は
従動歯車１５に対して転位なく噛合している。出
力回転軸１６は固定部１７に設けられたブツシユ
１８に軸承されている。 The driven gear 15 is an internal gear whose inner and outer diameter dimensions are substantially the same as those of the fixed gear 14, and the number of teeth thereof is greater than that of the fixed gear 14, for example, "102".
The driven gear 15 is fixed to an output rotating shaft 16 whose shaft center coincides with the drive shaft 11, and the intermediate gear 13 meshes with the driven gear 15 without displacement. The output rotating shaft 16 is supported by a bush 18 provided on the fixed part 17.
ところで、固定歯車１４の周縁面１４ａには回
転角度120度毎の計３箇所に、第２図に示す如き
円筒状の孔１４ｂが穿設されている。孔１４ｂに
はグリース等の潤滑剤が充填された後、孔１４ｂ
と同径の鋼球２０が挿入される。孔１４ｂの深さ
はその径の略1/2であり、鋼球２０は孔１４ｂよ
り突出している。従動歯車１５の周縁面１５ａに
は、駆動軸１１及び出力回転軸１６の軸中心より
鋼球２０の中心までの距離を半径とする溝１５ｂ
が穿設されている。溝１５ｂはその断面が鋼鉄球
２０の径より大径の円弧状で、深さは鋼球２０の
径の1/2未満である。従動歯車１５は溝１５ｂを
鋼球２０に当接させて、周縁面１５ａは周縁面１
４ａに僅かな距離で離間対向しており、鋼球２０
によるスラスト軸受構造が構成されている。 By the way, cylindrical holes 14b as shown in FIG. 2 are bored in the peripheral surface 14a of the fixed gear 14 at a total of three locations at every rotation angle of 120 degrees. After the hole 14b is filled with a lubricant such as grease, the hole 14b is filled with a lubricant such as grease.
A steel ball 20 with the same diameter is inserted. The depth of the hole 14b is approximately 1/2 of its diameter, and the steel ball 20 protrudes from the hole 14b. A groove 15b whose radius is the distance from the axial centers of the drive shaft 11 and the output rotating shaft 16 to the center of the steel ball 20 is formed on the peripheral surface 15a of the driven gear 15.
is drilled. The groove 15b has an arcuate cross section with a diameter larger than the diameter of the steel ball 20, and its depth is less than 1/2 of the diameter of the steel ball 20. The driven gear 15 has the groove 15b in contact with the steel ball 20, and the peripheral surface 15a is in contact with the peripheral surface 1.
4a at a small distance, and the steel ball 20
The thrust bearing structure is constructed by
ここで、駆動軸１１が回転して中間歯車１３が
固定歯車１４との噛合により自転及び公転を行な
う。中間歯車１３は同時に従動歯車１５とも噛合
しているため、従動歯車１５は中間歯車１３の１
公転につき歯数差（従動歯車１５と固定歯車１４
との歯数差）分だけ固定歯車１４に対して回転せ
しめられる。ところで、出力回転軸１６の駆動軸
１１に対する回転減速比ｉは次式の如く表わされ
る。 Here, the drive shaft 11 rotates, and the intermediate gear 13 engages with the fixed gear 14 to rotate and revolve. Since the intermediate gear 13 is also meshed with the driven gear 15 at the same time, the driven gear 15 is in mesh with one of the intermediate gears 13.
The difference in the number of teeth per revolution (driven gear 15 and fixed gear 14)
The fixed gear 14 is rotated by the difference in the number of teeth between the fixed gear 14 and the fixed gear 14. By the way, the rotational reduction ratio i of the output rotation shaft 16 with respect to the drive shaft 11 is expressed as in the following equation.
ｉ＝１−Z1／Z2
但し、Z1は固定歯車１４の歯数、Z2は従動歯車
１５の歯数である。 i=1-Z 1 /Z 2 where Z 1 is the number of teeth of the fixed gear 14 and Z 2 is the number of teeth of the driven gear 15.
これによつて、出力回転軸１６が減速回転す
る。このとき、固定歯車１４と従動歯車１５との
間は鋼球２０によるころがり軸受構造が設けられ
ているため、この間の摩擦が小さくなり駆動軸１
１の回転を出力回転軸１６に伝達する効率がほと
んど低下することがない。また、出力回転軸１６
はブツシユ１８で支持されているため構成が簡単
で小型化が可能であり、固定歯車１４と従動歯車
１５との間の隙間は極く僅かであるため中間歯車
１３の回転により発生するノイズの外部への洩れ
はほとんどない。 As a result, the output rotating shaft 16 rotates at a reduced speed. At this time, since a rolling bearing structure using steel balls 20 is provided between the fixed gear 14 and the driven gear 15, the friction between them is reduced and the drive shaft 1
The efficiency of transmitting one rotation to the output rotating shaft 16 hardly decreases. In addition, the output rotation shaft 16
is supported by the bush 18, so the structure is simple and can be made compact.Since the gap between the fixed gear 14 and the driven gear 15 is extremely small, the noise generated by the rotation of the intermediate gear 13 is eliminated from the outside. There is almost no leakage.
なお、固定歯車１４と従動歯車１５間の鋼球２
０は４個以上用いても良く、更にスラスト軸受構
造に限らずラジアル軸受構造を含むころがり軸受
構造であれば良く、上記実施例に限定されない。 Note that the steel ball 2 between the fixed gear 14 and the driven gear 15
Four or more zeros may be used, and any rolling bearing structure may be used, including not only a thrust bearing structure but also a radial bearing structure, and is not limited to the above embodiment.
考案の効果
上述の如く、本考案になる歯車減速機構は、固
定歯車と従動歯車との間にころがり軸受構造を設
けたため、従動歯車の摩擦抵抗が小となり駆動軸
の回転を出力回転軸に伝達する効率がほとんど低
下することがなく、構成が簡単で小型化が可能で
あり、ノズルの洩れがほとんどない等の特長を有
している。Effects of the invention As mentioned above, the gear reduction mechanism according to the invention has a rolling bearing structure between the fixed gear and the driven gear, so the frictional resistance of the driven gear is reduced and the rotation of the drive shaft is transmitted to the output rotating shaft. It has features such as there is almost no decrease in efficiency, the structure is simple and can be made compact, and there is almost no leakage from the nozzle.
第１図は本考案機構の一実施例の断面図、第２
図は第１図示の機構の一部の拡大断面図、第３図
は従来機構の一例の断面図である。
１１……駆動軸、１３……中間歯車、１４……
固定歯車、１５……従動歯車、１６……出力回転
軸、２０……鋼球。
Figure 1 is a sectional view of one embodiment of the mechanism of the present invention;
The figure is an enlarged sectional view of a part of the mechanism shown in the first figure, and FIG. 3 is a sectional view of an example of the conventional mechanism. 11... Drive shaft, 13... Intermediate gear, 14...
Fixed gear, 15... Driven gear, 16... Output rotating shaft, 20... Steel ball.
Claims (1)
内歯の固定歯車に内接噛合させて自転及び公転さ
せると共に、該中間歯車を該固定歯車と同一径で
互いに周縁を接し歯数差を有する従動歯車に噛合
させて、該従動歯車を該歯数差に応じて減速回転
せしめる歯車減速機構において、該固定歯車の周
縁と従動歯車の周縁との間に該従動歯車を支持す
るころがり軸受構造を設け、該従動歯車に固定さ
れた出力回転軸をブツシユで支持してなる歯車減
速機構。 An intermediate gear mounted eccentrically on a rotating drive shaft is internally meshed with a fixed gear of internal teeth to rotate and revolve, and the intermediate gear has the same diameter as the fixed gear and contacts each other at the periphery and has a difference in the number of teeth. In a gear reduction mechanism that meshes with a gear and causes the driven gear to rotate at a reduced speed according to the difference in the number of teeth, a rolling bearing structure is provided between the periphery of the fixed gear and the periphery of the driven gear to support the driven gear. , a gear reduction mechanism in which an output rotating shaft fixed to the driven gear is supported by a bush.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985185344U JPH029150Y2 (en) | 1985-11-29 | 1985-11-29 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985185344U JPH029150Y2 (en) | 1985-11-29 | 1985-11-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6292338U JPS6292338U (en) | 1987-06-12 |
| JPH029150Y2 true JPH029150Y2 (en) | 1990-03-06 |
Family
ID=31133883
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985185344U Expired JPH029150Y2 (en) | 1985-11-29 | 1985-11-29 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH029150Y2 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58178045A (en) * | 1982-03-26 | 1983-10-18 | アドヴアンスト・エナジ−・コンセプツ「あ」８１リミテツド | Planet type power gearing with drive element of roller freely rolling |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4717075U (en) * | 1971-03-31 | 1972-10-27 |
-
1985
- 1985-11-29 JP JP1985185344U patent/JPH029150Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58178045A (en) * | 1982-03-26 | 1983-10-18 | アドヴアンスト・エナジ−・コンセプツ「あ」８１リミテツド | Planet type power gearing with drive element of roller freely rolling |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6292338U (en) | 1987-06-12 |
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