JPS6227298B2 - - Google Patents
Info
- Publication number
- JPS6227298B2 JPS6227298B2 JP7790576A JP7790576A JPS6227298B2 JP S6227298 B2 JPS6227298 B2 JP S6227298B2 JP 7790576 A JP7790576 A JP 7790576A JP 7790576 A JP7790576 A JP 7790576A JP S6227298 B2 JPS6227298 B2 JP S6227298B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- tooth profile
- planetary gear
- tooth
- sun gear
- 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
- 239000002131 composite material Substances 0.000 description 4
- 230000013011 mating Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 230000002194 synthesizing effect Effects 0.000 description 1
Landscapes
- Gear Transmission (AREA)
- Retarders (AREA)
- Gears, Cams (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、遊星歯車機構において、その遊星歯
車の歯形を２つのサイクロイド系歯形を組合せた
複合歯形とし、内歯ならびに太陽歯車を共にピ
ン・ローラ（ピンのみでも可）歯形としたもので
ある。Detailed Description of the Invention [Field of Industrial Application] The present invention provides a planetary gear mechanism in which the tooth profile of the planetary gear is a composite tooth profile that combines two cycloid tooth profiles, and both the internal teeth and the sun gear are pin-shaped. It is a roller (pin only is also acceptable) with tooth profile.
従来、ピン・ローラよりなる歯形とサイクロイ
ド系歯形との噛合せの優秀性はサイクロ減速機
（登録商標）において実証されている。しかし内
歯と太陽の両歯車を円弧歯形とした遊星歯車機構
は存在しなかつた。これは遊星歯車を単一曲線よ
りなる歯形によつて形成することのみにとらわれ
ていたためである。
Conventionally, the superiority of the meshing between the pin roller tooth profile and the cycloidal tooth profile has been demonstrated in the Cyclo Reducer (registered trademark). However, there was no planetary gear mechanism in which both the internal gear and the sun gear had circular tooth shapes. This is because the planetary gears were only formed with tooth profiles consisting of a single curve.
本発明は、前記した従来の考え方を打破し、ピ
ン・ローラ歯形とサイクロイド系歯形のみで遊星
歯車機構を構成することを可能とし、その結果、
伝達効率ならびに伝達能力の向上と共に加工の容
易な遊星歯車機構を提供しようとするものであ
る。
The present invention breaks away from the conventional thinking described above and makes it possible to configure a planetary gear mechanism with only pin/roller tooth profiles and cycloid tooth profiles, and as a result,
The present invention aims to provide a planetary gear mechanism that has improved transmission efficiency and transmission capacity, and is easy to process.
本発明は、太陽歯車と遊星歯車ならびに内歯車
とで構成された遊星歯車機構の太陽歯車と内歯車
の歯形を共に円弧歯形とし、これらの両歯車と噛
合う遊星歯車の歯形を太陽歯車の円弧歯形に対応
させて創成したサイクロイド系歯形と内歯車の円
弧歯形に対応させて創成したサイクロイド系歯形
とを互に重ね合せて合成し、その内側の部分を遊
星歯車の歯形とし、歯元側が内歯車円弧歯形に噛
合し、歯先側が太陽歯車円弧歯形に噛合するサイ
クロイド系歯形を有する遊星歯車としたものであ
る。
In the present invention, the tooth profile of the sun gear and the internal gear of a planetary gear mechanism composed of a sun gear, a planet gear, and an internal gear are both circular arc tooth shapes, and the tooth profile of the planetary gear that meshes with these two gears is the circular arc tooth profile of the sun gear. The cycloid tooth profile created corresponding to the tooth profile and the cycloid tooth profile created corresponding to the circular arc tooth profile of the internal gear are superimposed and synthesized, and the inner part is the tooth profile of the planetary gear, and the tooth root side is the inner gear. The planetary gear has a cycloid tooth profile that meshes with the arc tooth profile of the gear, and the tooth tip side meshes with the arc tooth profile of the sun gear.
以下添付図面を参照して本発明を実施例につい
て説明する。
Embodiments of the present invention will be described below with reference to the accompanying drawings.
第１図において、遊星歯車機構Ｐは太陽歯車
１、遊星歯車２、ならびに内歯車３とで構成され
ている。太陽歯車１と内歯形３は円弧歯形で、こ
れらと噛合う遊星歯車２は、そのピツチ円が内歯
車と太陽歯車の両ピツチ円が滑ることなく転つた
とき創成される歯形となつている。 In FIG. 1, a planetary gear mechanism P is composed of a sun gear 1, a planet gear 2, and an internal gear 3. The sun gear 1 and the internal tooth profile 3 are arc tooth profiles, and the pitch circle of the planetary gear 2 that meshes with them is a tooth profile created when both the pitch circles of the internal gear and the sun gear roll over without slipping.
ここで太陽歯車１の創成する歯形は、内歯車３
の創成する歯形と理論的に異つたものとなり、互
に干渉を起して歯形として成立し難いように見え
る。 Here, the tooth profile created by sun gear 1 is
It is theoretically different from the tooth profile created by the tooth profile, and it appears that they interfere with each other and are difficult to establish as a tooth profile.
しかし、本発明では、一般に噛合率の高くなる
内歯車３との噛合側の遊星歯車２の歯形を、サイ
クロイド系歯形の噛合率の低くなる谷部４を用
い、噛合率の低くなる太陽歯車１との噛合側の遊
星歯車２の歯形を噛合率の高くなるその外側の歯
先部５を用いている（第２図参照）。 However, in the present invention, the tooth profile of the planetary gear 2 on the meshing side with the internal gear 3, where the meshing ratio is generally high, is changed to the trough portion 4 where the meshing ratio is low, which is a cycloid tooth profile, and the sun gear 1, where the meshing ratio is low. For the tooth profile of the planetary gear 2 on the meshing side, the tooth tips 5 on the outside where the meshing ratio is high are used (see FIG. 2).
このように、谷部４と歯先部５との歯形形状が
異なる複合歯形によつて構成することにより、相
手歯車と内・外接噛合する遊星歯車の条件を十分
満足させることができる。 In this way, by constructing the gear with a composite tooth profile in which the tooth profile shapes of the trough portion 4 and the tooth tip portion 5 are different, the conditions for a planetary gear that meshes internally and externally with a mating gear can be fully satisfied.
さらに、内歯車３の円弧が、太陽歯車１の創成
する曲線を外側において干渉せずに離れていくた
めには、第３図に示す如く太陽歯車１の円弧中心
６を、そのピツチ円P1より内側にとる必要があ
る。 Furthermore, in order for the arc of the internal gear 3 to move away from the curve created by the sun gear 1 on the outside without interfering with it, the arc center 6 of the sun gear 1 must be set at its pitch circle P 1 as shown in FIG. It needs to be taken more inside.
従つて、例えば、第３図において、太陽歯車１
のピツチ円P1の半径r1＝50、遊星歯車２のピツチ
円P2の半径r2＝50、内歯車３のピツチ円P3の半径
r3＝150とする。 Therefore, for example, in FIG.
Radius of pitch circle P 1 of planetary gear 2 r 1 = 50, radius of pitch circle P 2 of planetary gear 2 r 2 = 50, radius of pitch circle P 3 of internal gear 3
Let r 3 = 150.
そして、太陽歯車１と内歯車３の創成歯形を重
ねるため、外接のピツチ円P1を第１図と異なり、
図の右側外方に出して示し、そこで、太陽歯車１
上の円弧中心６はピツチ円P1より６mm内側に転移
させている。 In order to overlap the generated tooth profiles of the sun gear 1 and the internal gear 3, the circumscribed pitch circle P 1 is different from that in Fig. 1.
It is shown outside on the right side of the figure, where the sun gear 1
The upper arc center 6 is moved 6 mm inside the pitch circle P1 .
第４図及び第５図は太陽歯車１と外接噛合する
遊星歯車２の創成曲線と内歯歯車３と内接噛合す
る遊星歯車２の創成曲線とを個別に表わしたもの
で、第４図は太陽歯車円弧歯形に対する遊星歯車
歯形の基曲線。 4 and 5 individually represent the generation curve of the planetary gear 2 that externally meshes with the sun gear 1 and the generation curve of the planetary gear 2 that internally meshes with the internal gear 3. Base curve of planetary gear tooth profile for sun gear arc tooth profile.
また、第５図は内歯円弧歯形に対する遊星歯車
歯形の基曲線である。 Further, FIG. 5 shows the base curve of the planetary gear tooth profile with respect to the internal circular arc tooth profile.
この第４図及び第５図から明らかな通り、両曲
線６′，７′は全体的に見れば全く異なるものであ
るが部分的に見れば近似する部分があるので、こ
の近似した部分を第３図に示したのと同様に重ね
あわせて合成して本発明の複合歯形を形成する。 As is clear from FIGS. 4 and 5, the two curves 6' and 7' are completely different when viewed as a whole, but when viewed partially, there are parts that are similar, so these approximated parts are The composite tooth profile of the present invention is formed by overlapping and synthesizing in the same manner as shown in Figure 3.
本発明によれば、相手歯車の歯形がピン又はロ
ーラ等の円弧歯形を有する太陽歯車１と内歯歯車
３と同時噛合する遊星歯車２の歯形形状を噛合率
の高くなる内歯歯車３とを噛合う部分を谷部４に
設け、噛合率の低くなる太陽歯車１と噛合う部分
を歯先部５に設けているので、内・外接同時噛合
する遊星歯車の噛合効率を向上させることができ
る。
According to the present invention, the tooth profile of the planetary gear 2 that simultaneously meshes with the sun gear 1 whose mating gear has a circular arc tooth profile such as a pin or roller, and the internal gear 3 which meshes simultaneously with the internal gear 3 with a high meshing ratio. Since the meshing part is provided in the valley part 4 and the part meshing with the sun gear 1, which has a low meshing ratio, is provided in the tooth tip part 5, it is possible to improve the meshing efficiency of the planetary gear that meshes internally and externally simultaneously. .
しかも、遊星歯車の相手歯形を円弧歯形として
も理想的な噛合を行なわせることが可能であるか
ら、
(a) 相手歯形をピン・ローラを組合せることによ
つて歯形を形成すれば良いから内歯車及び太陽
歯車の加工が容易に行なえる。 Furthermore, it is possible to achieve ideal meshing even if the mating tooth profile of the planetary gear is a circular arc tooth profile. Gears and sun gears can be easily processed.
(b) 相手歯形をピン・ローラの組合せにすれば良
いから、太陽歯車、内歯車の組立てはピン孔の
割出し精度のみに注意すれば良く、その精度が
向上する。(b) Since the mating tooth profile can be a combination of pins and rollers, when assembling the sun gear and internal gear, it is only necessary to pay attention to the indexing accuracy of the pin hole, which improves the accuracy.
(c) 遊星歯車が回転するピン又はローラとのころ
がり噛合いをするから、伝導効率が一段と向上
する。等、種々の利点を有している。(c) Transmission efficiency is further improved because the planetary gear engages in rolling engagement with the rotating pin or roller. It has various advantages such as.
第１図は、本発明を実施した遊星歯車機構Ｐを
示す概略図。第２図は、第１図における遊星歯車
２の拡大詳細図。第３図は、本発明に係る複合歯
形の詳細図。第４図は、太陽歯車円弧歯形に対す
る遊星歯車歯形の基曲線図。第５図は、内歯歯車
円弧歯形に対する遊星歯車歯形の基曲線図であ
る。
図において：― Ｐ…遊星歯車機構、１…太陽
歯車、２…遊星歯車、３…内歯車、４…内歯車と
の噛合部、５…太陽歯車との噛合部、６…（太陽
歯車の）円弧中心、７…（内歯車の）円弧中心、
P1，P2，P3…太陽歯車、遊星歯車、内歯車の各ピ
ツチ円。
FIG. 1 is a schematic diagram showing a planetary gear mechanism P in which the present invention is implemented. FIG. 2 is an enlarged detailed view of the planetary gear 2 in FIG. 1. FIG. 3 is a detailed view of the composite tooth profile according to the present invention. FIG. 4 is a base curve diagram of a planetary gear tooth profile with respect to a sun gear arc tooth profile. FIG. 5 is a base curve diagram of a planetary gear tooth profile with respect to an internal gear circular arc tooth profile. In the figure: - P...Planetary gear mechanism, 1...Sun gear, 2...Planetary gear, 3...Internal gear, 4...Meshing part with internal gear, 5...Meshing part with sun gear, 6...(of sun gear) Center of arc, 7... Center of arc (of internal gear),
P 1 , P 2 , P 3 ... Pitch circles of sun gear, planet gear, and internal gear.
Claims (1)
された遊星歯車機構において、太陽歯車と内歯車
の歯形を共に円弧歯形とし、これらの両歯車と噛
合う遊星歯車の歯形を太陽歯車の円弧歯形に対応
させて創成したサイクロイド系歯形と内歯車の円
弧歯形に対応させて創成したサイクロイド系歯形
とを互に重ね合せて合成し、その内側の部分を遊
星歯車の歯形とし、歯元側が内歯車円弧歯形に噛
合し、歯先側が太陽歯車円弧歯形に噛合するサイ
クロイド系歯形を有する遊星歯車としたことを特
徴とする遊星歯車機構。 ２ 太陽歯車の円弧中心をそのピツチP1より内側
にとつて遊星歯車の山部が形成されていることを
特徴とする特許請求の範囲第１項に記載の遊星歯
車機構。[Scope of Claims] 1. In a planetary gear mechanism composed of a sun gear, a planet gear, and an internal gear, the tooth profiles of the sun gear and the internal gear are both circular arc tooth profiles, and the tooth profile of the planet gear that meshes with these two gears is A cycloidal tooth profile created corresponding to the circular arc tooth profile of the sun gear and a cycloidal tooth profile created corresponding to the circular arc tooth profile of the internal gear are superimposed and synthesized, and the inner part thereof is used as the tooth profile of the planetary gear, A planetary gear mechanism characterized in that the planetary gear has a cycloidal tooth profile in which the root side meshes with the circular arc tooth profile of the internal gear and the tooth tip side meshes with the circular arc tooth profile of the sun gear. 2. The planetary gear mechanism according to claim 1, wherein the mountain portion of the planetary gear is formed with the arc center of the sun gear located inside the pitch P1 .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7790576A JPS535362A (en) | 1976-07-02 | 1976-07-02 | Planetary gear mechanism with internally and outernally contacted cycloid gears |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7790576A JPS535362A (en) | 1976-07-02 | 1976-07-02 | Planetary gear mechanism with internally and outernally contacted cycloid gears |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS535362A JPS535362A (en) | 1978-01-18 |
| JPS6227298B2 true JPS6227298B2 (en) | 1987-06-13 |
Family
ID=13647080
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7790576A Granted JPS535362A (en) | 1976-07-02 | 1976-07-02 | Planetary gear mechanism with internally and outernally contacted cycloid gears |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS535362A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS576146A (en) * | 1980-06-11 | 1982-01-13 | Sumitomo Heavy Ind Ltd | Planetary gear mechanism with inscribed/circumscribed cycloidal tooth |
| JP2646270B2 (en) * | 1989-11-28 | 1997-08-27 | 日立粉末冶金株式会社 | Planetary gear set |
| CN102252058B (en) * | 2011-07-01 | 2014-10-08 | 重庆大学 | Cycloid planetary transmission gear based on line-surface conjugation |
-
1976
- 1976-07-02 JP JP7790576A patent/JPS535362A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS535362A (en) | 1978-01-18 |
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