JPS6220415B2 - - Google Patents
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- Publication number
- JPS6220415B2 JPS6220415B2 JP55099330A JP9933080A JPS6220415B2 JP S6220415 B2 JPS6220415 B2 JP S6220415B2 JP 55099330 A JP55099330 A JP 55099330A JP 9933080 A JP9933080 A JP 9933080A JP S6220415 B2 JPS6220415 B2 JP S6220415B2
- Authority
- JP
- Japan
- Prior art keywords
- radius
- tooth profile
- gear
- planetary gear
- pitch circle
- 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
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Description
【発明の詳細な説明】
従来外接噛合において、円弧歯形の相手歯形が
トロコイド平行曲線となる事はピン歯車として良
く知られている。又太陽歯車と内歯車を円弧歯形
とし、遊星歯車歯形をトロコイド曲線の複合歯形
とした遊星歯車装置についても知られている（特
開昭53−5362）。DETAILED DESCRIPTION OF THE INVENTION In conventional external meshing, it is well known that the mating tooth profile of a circular arc tooth profile is a trochoidal parallel curve as a pin gear. Also known is a planetary gear device in which the sun gear and internal gear have circular arc tooth shapes, and the planetary gear tooth profile has a compound tooth shape of a trochoid curve (Japanese Patent Laid-Open No. 5362-1983).
本発明は遊星歯車機構における遊星歯車にピン
とローラよりなる円弧歯形を用いる事により、太
陽歯車と遊星歯車、遊星歯車と内歯車の各々噛合
を転がり接触とし、かつ内歯車の歯形を円弧歯形
とする事により、従来その加工が困難であつた大
形高精度の内歯車を容易に加工可能にし、大形高
精度の遊星歯車減速機を低コストにて提供できる
ようにし、かくして高速大馬力に適した長寿命で
コンパクトな高性能遊星歯車減速機を低コストに
て提供しようとするものである。以下実施例につ
いて説明する。 The present invention uses an arcuate tooth profile made of pins and rollers for the planetary gear in a planetary gear mechanism, so that the meshing of the sun gear and the planetary gear, and the planetary gear and the internal gear is in rolling contact, and the tooth profile of the internal gear is an arcuate tooth profile. This makes it possible to easily machine large, high-precision internal gears, which were previously difficult to machine, and to provide large, high-precision planetary gear reducers at low cost, making them suitable for high-speed, large-horsepower applications. The objective is to provide a compact, high-performance planetary gear reducer with a long life and at a low cost. Examples will be described below.
図は本発明に係る遊星歯車減速機の歯形部分の
噛合状態を示し、太陽歯車１の歯数zi＝12、遊星
歯車Ｐの歯数zp＝24、内歯車４の歯数zi＝60の
場合を示す。 The figure shows the meshing state of the teeth of the planetary gear reducer according to the present invention, where the number of teeth of the sun gear 1 zi = 12, the number of teeth of the planetary gear P zp = 24, and the number of teeth zi of the internal gear 4 = 60. shows.
遊星歯車Ｐはピン３とローラ２の組合わせより
なり、ローラ２はピン３との間で自由に回転する
事が出来る。またピン列のピツチ半径ｅは遊星歯
車のピツチ半径ｂより小さくしてある。 The planetary gear P consists of a combination of a pin 3 and a roller 2, and the roller 2 can freely rotate between the pin 3 and the roller 2. Further, the pitch radius e of the pin row is smaller than the pitch radius b of the planetary gear.
太陽歯車１の歯形は外接噛合における円弧歯形
の相手歯形として求められるトロコイド平行曲線
である。 The tooth profile of the sun gear 1 is a trochoidal parallel curve obtained as the counterpart tooth profile of the circular arc tooth profile in circumscribed meshing.
内歯車４は半径ｃを有する内歯車のピツチ円７
よりも径の小さな半径ｄの円９上に中心を持ち、
各々の半径がｇ＝ｆ＋ｈである円弧となつてい
る。すなわち（遊星歯車ローラの半径）に（内歯
車ピツチ円半径と円弧のピツチ円半径の差）を加
えた半径の円弧を等ピツチに配した歯形となつて
いる。 The internal gear 4 has a pitch circle 7 of the internal gear with a radius c.
It has a center on a circle 9 with a radius d smaller than
Each arc has a radius of g=f+h. In other words, the tooth profile has circular arcs with a radius equal to (the radius of the planetary gear roller) plus (the difference between the pitch circle radius of the internal gear and the pitch circle radius of the circular arc) arranged at equal pitches.
上記の場合内歯車４の円弧歯形は、遊星歯車円
弧歯形に対する内接噛合における理論相手歯形と
は異なるが、内歯車４と遊星歯車Ｐの荷重伝達に
よる弾性変形により、円滑な動力伝達を行なう近
似歯形となつている。 In the above case, the circular arc tooth profile of the internal gear 4 is different from the theoretical mating tooth profile in internal meshing with the circular arc tooth profile of the planetary gear, but it is an approximation that allows smooth power transmission due to elastic deformation due to load transmission between the internal gear 4 and the planetary gear P. It has a tooth shape.
以上の構成であるから、
(1) 遊星歯車Ｐに対する太陽歯車１の歯形は歯車
の機構学的な歯形の条件を満足し理論噛合をさ
せることがきる。 With the above configuration, (1) the tooth profile of the sun gear 1 with respect to the planetary gear P satisfies the mechanical tooth profile conditions of the gear and can achieve theoretical meshing.
(2) 遊星歯車Ｐに対する内歯車４の歯形は近似歯
形であるが、内接噛合であるので、荷重伝達に
よる弾性変形により噛合率１以上の円滑な動力
伝達を行なう。(2) The tooth profile of the internal gear 4 with respect to the planetary gear P is an approximate tooth profile, but since it is internally meshed, smooth power transmission with a meshing ratio of 1 or more is achieved by elastic deformation due to load transmission.
(3) 太陽歯車１と遊星歯車Ｐ、遊星歯車Ｐと内歯
車４の噛合は、遊星歯車Ｐのピンローラによ
り、滑りが吸収される事により転がり接触を行
なわせることができる。(3) In the meshing between the sun gear 1 and the planetary gear P, and the planetary gear P and the internal gear 4, slippage is absorbed by the pin roller of the planetary gear P, so that rolling contact can be achieved.
……等の諸特性を有し、寿命が長く、しかもコン
パクトな遊星歯車減速機を得ることができる。It is possible to obtain a planetary gear reducer that has the following characteristics, has a long life, and is compact.
図は本発明に係る遊星歯車減速機を示す。
図において；−１……太陽歯車、２……遊星歯
車ローラ、３……遊星歯車ピン、４……内歯車、
５……太陽歯車ピツチ円、６……遊星歯車ピツチ
円、７……内歯車ピツチ円、８……遊星歯車ピン
列のピツチ円、９……内歯車円弧中心のピツチ
円、ａ……太陽歯車ピツチ円半径、ｂ……遊星歯
車ピツチ円半径、ｃ……内歯車ピツチ円半径、ｄ
……内歯車円弧中心のピツチ円半径、ｅ……遊星
歯車ピン列のピツチ円半径、ｆ……遊星歯車ロー
ラの半径、ｇ……内歯車円弧の半径、ｈ……（内
歯車のピツチ円半径と内歯車円弧中心のピツチ円
半径の差）ｈ＝ｃ−ｄ、Ｐ……遊星歯車。
The figure shows a planetary gear reducer according to the invention. In the figure: -1...Sun gear, 2...Planetary gear roller, 3...Planetary gear pin, 4...Internal gear,
5... Sun gear pitch circle, 6... Planet gear pitch circle, 7... Internal gear pitch circle, 8... Planet gear pin row pitch circle, 9... Internal gear pitch circle at center of arc, a... Sun Gear pitch circle radius, b...Planetary gear pitch circle radius, c...Internal gear pitch circle radius, d
... Pitch circle radius at the center of the internal gear arc, e... Pitch circle radius of the planetary gear pin row, f... Radius of the planetary gear roller, g... Radius of the internal gear arc, h... (Pitch circle of the internal gear Difference between the radius and the radius of the pitch circle at the center of the internal gear arc) h = c - d, P... Planetary gear.
Claims (1)
る。 (ロ) 太陽歯車の歯形は外接噛合における円弧歯形
の相手歯形として求められるトロコイド平行歯
形で構成する。 (ハ) 遊星歯車の歯形はピンとローラとより成る円
弧歯形となつている。そしてピン列のピツチ円
半径ｅを遊星歯車のピツチ円半径ｂより小さく
している。 (ニ) 内歯車の歯形は、内歯車の歯車としてのピツ
チ円半径ｃより小さなピツチ円半径ｄの円上に
中心を持ち、各々の半径ｇが遊星歯車ローラの
半径ｆに内歯車のピツチ円半径ｃと前記のピツ
チ円半径ｄとの差ｈを加えた半径の円弧を等ピ
ツチに配した歯形とし、遊星歯車円弧歯形に対
して内接噛合する内歯車４を円滑な動力伝達を
行なう近似歯形とした。[Claims] 1. A planetary gear reducer comprising the following (a) to (d). (a) It consists of a sun gear, a planetary gear, and an internal gear. (b) The tooth profile of the sun gear is composed of a trochoidal parallel tooth profile, which is determined as the counterpart tooth profile of the circular arc tooth profile in circumscribed meshing. (c) The tooth profile of the planetary gear is an arc tooth profile made up of pins and rollers. The pitch circle radius e of the pin row is made smaller than the pitch circle radius b of the planetary gear. (d) The tooth profile of the internal gear has its center on a circle with a pitch circle radius d smaller than the pitch circle radius c of the internal gear, and each radius g is the same as the pitch circle of the internal gear with the radius f of the planetary gear roller. An approximation in which circular arcs with a radius equal to the difference h between the radius c and the pitch circle radius d are arranged at equal pitches, and the internal gear 4 that internally meshes with the planetary gear circular arc tooth profile performs smooth power transmission. It was made into a tooth shape.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9933080A JPS5725548A (en) | 1980-07-22 | 1980-07-22 | Circular profile planetary gear speed reduction device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9933080A JPS5725548A (en) | 1980-07-22 | 1980-07-22 | Circular profile planetary gear speed reduction device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5725548A JPS5725548A (en) | 1982-02-10 |
| JPS6220415B2 true JPS6220415B2 (en) | 1987-05-07 |
Family
ID=14244620
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9933080A Granted JPS5725548A (en) | 1980-07-22 | 1980-07-22 | Circular profile planetary gear speed reduction device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5725548A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0332318U (en) * | 1989-08-04 | 1991-03-28 | ||
| CN1329469C (en) * | 2005-08-04 | 2007-08-01 | 上海应用技术学院 | Modified urea formaldehyde binding agent and its preparation method |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100945192B1 (en) * | 2009-06-10 | 2010-03-03 | 주식회사 세진아이지비 | A transmission device for converting a torque |
-
1980
- 1980-07-22 JP JP9933080A patent/JPS5725548A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0332318U (en) * | 1989-08-04 | 1991-03-28 | ||
| CN1329469C (en) * | 2005-08-04 | 2007-08-01 | 上海应用技术学院 | Modified urea formaldehyde binding agent and its preparation method |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5725548A (en) | 1982-02-10 |
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