JP3181099B2 - Planetary gear set - Google Patents
Planetary gear setInfo
- Publication number
- JP3181099B2 JP3181099B2 JP16476592A JP16476592A JP3181099B2 JP 3181099 B2 JP3181099 B2 JP 3181099B2 JP 16476592 A JP16476592 A JP 16476592A JP 16476592 A JP16476592 A JP 16476592A JP 3181099 B2 JP3181099 B2 JP 3181099B2
- Authority
- JP
- Japan
- Prior art keywords
- planetary gear
- gear
- planetary
- gears
- gear shaft
- 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 - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
- F16H1/2836—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planets relative to the planet carrier or by using free floating planets
Landscapes
- Retarders (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は各種産業用製品の増減速
装置に使用される遊星歯車装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear set used for a speed increasing and reducing device for various industrial products.
【０００２】[0002]
【従来の技術】（１） 従来の遊星歯車装置を図６乃至
図１０について説明する。図において、０１は複数の遊
星歯車、０２は遊星歯車軸、０３は遊星歯車０１のキヤ
リヤ、０５は内歯車、０６は太陽歯車である。図９は一
般的な遊星歯車装置の構成を示す斜視図、図６は遊星歯
車０１の軸支部分の断面図であり、図６に示すように遊
星歯車軸０２の両端をキヤリヤ０３に固定し、図７に示
すように内歯車０５を可撓継手０７で連結させるか、あ
るいは図８，図１０に示すように内歯車０５をさやばね
０４で支える等、遊星歯車軸０２以外の要素を工夫して
遊星歯車０１のそれぞれのかみあいに生ずる荷重の均等
化を計っている。 （２） 上記（１）項に示した遊星歯車における振動、
騒音を低減する技術として、遊星歯車の個数が偶数個の
場合に、相対する遊星歯車間のかみあい位相を歯数、圧
力角及び歯だけを調整する（遊星歯車の軸心は調整しな
い）ことで逆相とする方法が、文献「Ｗ．Ｅ．Ｐａｌｍ
ｅｒ ａｎｄ Ｒ．Ｒ．Ｆｕｅｈｒｅｒ“Ｎｏｉｓｅ
Ｃｏｎｔｒｏｌ Ｉｎ Ｐｌａｎｅｔａｖｙ Ｔｒａｎ
ｓｍｉｓｓｉｏｎｓ”ＳＡＥ ７７０５６１ １９７７
年」に記載されている。2. Description of the Related Art (1) A conventional planetary gear device will be described with reference to FIGS. In the figure, 01 is a plurality of planetary gears, 02 is a planetary gear shaft, 03 is a carrier of the planetary gear 01, 05 is an internal gear, and 06 is a sun gear. FIG. 9 is a perspective view showing the configuration of a general planetary gear device, and FIG. 6 is a sectional view of a shaft support portion of the planetary gear 01. As shown in FIG. 6, both ends of a planetary gear shaft 02 are fixed to a carrier 03. Elements other than the planetary gear shaft 02 are devised, such as connecting the internal gear 05 with a flexible joint 07 as shown in FIG. 7, or supporting the internal gear 05 with a sheath spring 04 as shown in FIGS. Thus, the loads generated in the meshing of the planetary gears 01 are equalized. (2) vibration in the planetary gear described in (1) above,
As a technology for reducing noise, when the number of planetary gears is an even number, the meshing phase between opposing planetary gears is adjusted by adjusting only the number of teeth, pressure angle, and teeth (the center of the planetary gears is not adjusted). The method of reverse phase is described in the document "WE Palm."
er and R.E. R. Fuehrer "Noise
Control In Planetary Tran
smissions "SAE 770561 1977
Year ".
【０００３】[0003]
【発明が解決しようとする課題】前述の従来技術には次
のような問題点がある。 （１） 図７，図８に示した可撓継手０７又はさやばね
０４は、共に内歯車０５の軸芯を調整するものであり、
個々の遊星歯車０１の軸芯及び歯当りを調整し、各遊星
歯車のかみあいに際して生ずる荷重を均等化することが
できない。 （２） 遊星歯車間のかみあい位相を逆相とする振動・
騒音の低減技術は、遊星歯車の個数が奇数個の場合には
適用することができない。The above-mentioned prior art has the following problems. (1) Both the flexible joint 07 and the sheath spring 04 shown in FIGS. 7 and 8 adjust the axis of the internal gear 05.
It is not possible to adjust the axial center and the tooth contact of the individual planetary gears 01 and to equalize the load generated when the respective planetary gears mesh with each other. (2) Vibration with the meshing phase between planetary gears reversed
The noise reduction technology cannot be applied when the number of planetary gears is an odd number.
【０００４】本発明は、各遊星歯車に加る荷重を均等化
し、また装置の振動、騒音を低減した遊星歯車装置を提
供することを目的とするものである。An object of the present invention is to provide a planetary gear device in which the loads applied to the respective planetary gears are equalized and the vibration and noise of the device are reduced.
【０００５】[0005]
【課題を解決するための手段】本発明は、遊星歯車の位
置を調整することで、遊星歯車相互の位相をＴ z ／ｎづ
つずらし（ｎ：遊星歯車の個数、Ｔ z ：かみあい周
期）、かみあい率εを ε≒１＋（ｎ−１）／ｎ とすることによって、遊星歯車と内歯車間の起振力の低
減を図る。SUMMARY OF THE INVENTION The present invention relates to a planetary gear.
By adjusting the position, the phase of the planetary gears can be shifted by T z / n.
Shift (n: number of planetary gears, T z : meshing circumference
Period), the contact ratio ε is set to ε ≒ 1 + (n−1) / n , thereby reducing the vibrating force between the planetary gear and the internal gear.
【０００６】[0006]
【作用】請求項１に記載された発明は、遊星歯車の個数
をｎ、かみあい周期をＴ z とした時に、各遊星歯車の位
置を調整して各遊星歯車相互のかみあい位相をＴ z ／ｎ
づつずらし、かみあい率ε≒１＋（ｎ−１）／ｎとする
ことにより、遊星歯車全体としての伝達荷重の変動がな
くなり、遊星歯車全体としての起振力が小さくなり、遊
星歯車装置の振動・騒音が大幅に低減する。 According to the present invention, the number of planetary gears is
The n, when the engagement period was T z, position of the planet gear
Adjust the location of the engagement phases of the planetary gears mutually T z / n
The contact ratio is ε ≒ 1 + (n−1) / n
As a result, there is no fluctuation in the transmission load of the entire planetary gear.
And the vibrating force of the entire planetary gear
The vibration and noise of the star gear device are greatly reduced.
【０００７】[0007]
【実施例】第１参考技術 まず始めに、 本発明の第１参考技術を図１について説明
する図において、１は遊星歯車、２は遊星歯車軸、３は
太陽歯車（図９の０６を参照）の軸線まわりに回転する
キヤリヤ、４は円筒状の第２の歯車軸、５，６はナット
である。DESCRIPTION OF THE PREFERRED EMBODIMENTS First Reference Technique First, referring to FIG. 1, which illustrates the first reference technique of the present invention, reference numeral 1 denotes a planetary gear, 2 denotes a planetary gear shaft, and 3 denotes a sun gear (see 06 in FIG. 9). ), 4 is a cylindrical second gear shaft, and 5 and 6 are nuts.
【０００８】図に示すように、遊星歯車軸２に設けられ
たフランジ部８をキャリヤ３に当接させた状態で、遊星
歯車軸２の一端とキャリヤ３とをナット５で固定し、遊
星歯車軸２と遊星歯車１との間に第２の歯車軸４を嵌入
して、遊星歯車軸２の自由端と歯車軸４の端部とをナッ
ト６で固定する。したがって、歯車軸２、４はキャリヤ
３に対して片持ち固定で、且つ軸を折り返した構造とな
っており、遊星歯車１を軸直角方向に変位可能に支持す
ることになる。As shown in the drawing, one end of the planetary gear shaft 2 and the carrier 3 are fixed with a nut 5 in a state in which the flange 8 provided on the planetary gear shaft 2 is in contact with the carrier 3, and the planetary gear The second gear shaft 4 is fitted between the shaft 2 and the planetary gear 1, and the free end of the planetary gear shaft 2 and the end of the gear shaft 4 are fixed with the nut 6. Therefore, the gear shafts 2 and 4 are cantilevered with respect to the carrier 3 and have a structure in which the shafts are turned back, thereby supporting the planetary gear 1 so as to be displaceable in a direction perpendicular to the axis.
【０００９】なお、遊星歯車軸２の外周面と第２の歯車
軸４の内周面とは接しない様に適当な空隙が設けてあ
り、歯車軸２，４は軸直角方向の荷重を受けて容易に弾
性変形することができる。上記実施例において、ナット
６の代りに溶接で固着してもよい。第２参考技術 本発明の第２参考技術を図２について説明する。An appropriate gap is provided so that the outer peripheral surface of the planetary gear shaft 2 and the inner peripheral surface of the second gear shaft 4 are not in contact with each other, and the gear shafts 2 and 4 receive a load perpendicular to the shaft. And can be easily elastically deformed. In the above embodiment, the nut 6 may be fixed by welding instead of the nut 6. Second Reference Technology A second reference technology of the present invention will be described with reference to FIG.
【００１０】図において、１は遊星歯車、２ａはタイコ
状（中高）の遊星歯車軸、３はキヤリヤ、４ａは円筒状
の第２の歯車軸、５はナット、７はストッパーである。
遊星歯車軸２ａは第１実施例と同様にキヤリヤ３に片持
ち固定させる。さらに、遊星歯車軸２ａの軸面を、半径
Ｒの円弧に、タイコ状に形成しておく。片持ち固定によ
り、遊星歯車軸２ａは弾性的に変形しやすく、遊星歯車
１が内歯車（図９の０５参照）及び太陽歯車（図９の０
６参照）と均等にかみあうような位置に動くことができ
る。他方、円筒状の第２の歯車軸４ａを遊星歯車軸２ａ
に嵌め込み、遊星歯車１は、歯車軸４ａに嵌め込まれて
いる。In FIG. 1, reference numeral 1 denotes a planetary gear, 2a denotes a planetary (medium-high) planetary gear shaft, 3 denotes a carrier, 4a denotes a cylindrical second gear shaft, 5 denotes a nut, and 7 denotes a stopper.
The planetary gear shaft 2a is fixed to the carrier 3 in the same manner as in the first embodiment. Further, the shaft surface of the planetary gear shaft 2a is formed in an arc shape having a radius R in a cocoon shape. Due to the cantilever fixation, the planetary gear shaft 2a is easily elastically deformed, and the planetary gear 1 is composed of an internal gear (see 05 in FIG. 9) and a sun gear (0 in FIG. 9).
6) and can be moved to a position where they mesh equally. On the other hand, the cylindrical second gear shaft 4a is connected to the planetary gear shaft 2a.
The planetary gear 1 is fitted to the gear shaft 4a.
【００１１】遊星歯車軸２ａには、図に示すように、半
径Ｒのクラウンを付けたので、歯車軸４ａの自由度が大
きくなり、歯車軸４ａの移動（変位）で歯当りの改善が
おこなわれる。２つの歯車軸２ａ，４ａ間は互いに抜け
落ちない様に適当なストッパー７が挿入されている。次
に、本発明の実施形態について、図３乃至図５に基づい
て説明する。Since the planetary gear shaft 2a is provided with a crown having a radius R as shown in the figure, the degree of freedom of the gear shaft 4a is increased, and the gear contact is improved by the movement (displacement) of the gear shaft 4a. It is. An appropriate stopper 7 is inserted between the two gear shafts 2a and 4a so as not to fall off from each other. Next
Next, an embodiment of the present invention will be described with reference to FIGS.
Will be explained.
【００１２】図３において、１Ａ，１Ｂ，１Ｃは遊星歯
車、０５は内歯車、０６は太陽歯車である。従来の遊星
歯車装置は、例えば図９において、各遊星歯車０１を等
間隔に配置しているが、本実施例では、図３に示すよう
に、各遊星歯車１Ａ，１Ｂ，１Ｃの位置を等間隔位置に
対してずらし、遊星歯車１Ａ，１Ｂ，１Ｃ相互のかみあ
い位相がＴz／ｎづつずれるように調整する。In FIG. 3, 1A, 1B and 1C are planetary gears, 05 is an internal gear, and 06 is a sun gear. In the conventional planetary gear device, for example, in FIG. 9, the respective planetary gears 01 are arranged at equal intervals, but in the present embodiment, as shown in FIG. 3, the positions of the respective planetary gears 1A, 1B, 1C are equal. The planetary gears 1A, 1B, and 1C are shifted with respect to the interval position so as to be shifted by T z / n each other.
【００１３】なおかみあい率は、従来では任意に選ぶと
ころを、本実施例では、ε＝１＋（ｎ−１）／ｎとなる
ように選ぶ。次に本実施例の作用を説明する。平歯車の
伝達荷重の変動は、図４のような特性を示す。かみあい
周期をＴzとすると、図に示すように、平歯車は２歯か
みあいと１歯かみあいとが周期的にくり返され、その時
のかみあい枚数の変化が図に示すような伝達荷重の変動
を引き起こす。In the present embodiment, the contact ratio is arbitrarily selected, but is selected so that ε = 1 + (n−1) / n. Next, the operation of the present embodiment will be described. The fluctuation of the transmission load of the spur gear shows a characteristic as shown in FIG. Assuming that the meshing period is T z , as shown in the figure, the spur gear has two teeth and one tooth meshed periodically, and the change in the number of meshes at that time causes the change in the transmission load as shown in the figure. cause.
【００１４】２歯かみあい領域は、かみあい率をεとす
れば、（ε−１）Ｔzで与えられる。今、図５に示すよ
うに、遊星歯車の個数ｎがｎ＝３で与えられる遊星歯車
装置において、歯車対全体としての伝達荷重の変動が、
図５右側の４に示すようになくなるようにする方法を考
える。[0014] 2 teeth meshing region, if the contact ratio and epsilon, is given by (ε-1) T z. Now, as shown in FIG. 5, in a planetary gear device in which the number n of the planetary gears is given by n = 3, the fluctuation of the transmission load of the entire gear pair is
Consider a method for eliminating the color as shown by 4 on the right side of FIG.
【００１５】そのためには図５の遊星歯車１Ａ，１Ｂ，
１Ｃと内歯車０５のかみあい１，２，３の位相をＴz／
３づつずらし、それぞれのかみあいの２歯かみあい領域
を２／３・Ｔz，即ち、かみあい率にして、 ε＝１＋２／３＝１＋（３−１）／３ （２） とすれば良い。For this purpose, the planetary gears 1A, 1B,
1C and the internal gear 05 are engaged with each other, and the phase of 1, 2, 3 is T z /
3 shifting increments, 2 teeth meshing area 2/3 · T z of the respective mating, i.e., in the contact ratio, ε = 1 + 2/3 = 1 + (3-1) / 3 may be set to (2).
【００１６】遊星歯車の個数がｎ個の場合は、かみあい
対の位相をＴz／ｎづつずらし、かみあい率εを ε＝１＋（ｎ−１）／ｎ とすれば、歯車対全体としての伝達荷重の変動はなくな
る。一般に歯車装置では、図４に示す伝達荷重の変動が
起振力となって、装置の振動・騒音を発生させる。しか
し、先に述べたように、遊星歯車装置のかみあい対の位
相をＴz／ｎづつずらし、かみあい率εを ε＝１＋（ｎ−１）／ｎ とすれば、歯車対全体としての伝達荷重の変動がなくな
り、歯車対全体としての起振力が小さくなるので、遊星
歯車装置の振動・騒音の大幅低減が計れる。If the number of planetary gears is n, the phase of the meshing pair is shifted by T z / n and the meshing ratio ε is ε = 1 + (n−1) / n. There is no change in load. In general, in a gear device, the fluctuation of the transmission load shown in FIG. 4 becomes a vibrating force to generate vibration and noise of the device. However, as described above, if the phase of the meshing pair of the planetary gear device is shifted by T z / n and the meshing ratio ε is ε = 1 + (n−1) / n, the transmission load of the entire gear pair is And the vibration force of the planetary gear set can be greatly reduced since the vibration force of the entire gear pair is reduced.
【００１７】[0017]
【発明の効果】以上説明したように、本発明は、太陽歯
車と内歯車の間に複数の遊星歯車を配置した遊星歯車装
置において、遊星歯車の個数をｎ、かみあい周期をＴz
とした時に、各遊星歯車の位置を調整して各遊星歯車相
互のかみあい位相をＴz／ｎづつずらし、かみあい率ε
≒１＋（ｎ−１）／ｎとしたことにより、遊星歯車装置
の起振力を減少させ、振動及び騒音を低減することがで
きる。 As described above, according to the present invention, the planetary gear unit in which a plurality of planet gears between sun gear and the internal gear, the number of planetary gears n, the meshing periods T z
, The position of each planetary gear is adjusted to shift the meshing phase of each planetary gear by T z / n, and the meshing ratio ε
By setting ≒ 1 + (n−1) / n, it is possible to reduce the vibrating force of the planetary gear device and reduce vibration and noise.
【図面の簡単な説明】[Brief description of the drawings]
【図１】 本発明の第１参考技術の遊星歯車軸部分の断
面図である。FIG. 1 is a sectional view of a planetary gear shaft portion according to a first reference technology of the present invention.
【図２】 本発明の第２参考技術の遊星歯車軸部分の断
面図である。FIG. 2 is a sectional view of a planetary gear shaft portion according to a second reference technology of the present invention.
【図３】 本発明の実施形態の原理を示す図である。FIG. 3 is a diagram illustrating the principle of an embodiment of the present invention.
【図４】 歯車騒音における伝達荷重・時間の関係を示
す線図である。FIG. 4 is a diagram showing a relationship between transmitted load and time in gear noise.
【図５】 本発明の実施形態における作用を示す図であ
る。FIG. 5 is a diagram showing an operation in the embodiment of the present invention.
【図６】 従来の遊星歯車装置の遊星歯車軸部分の断面
図である。FIG. 6 is a sectional view of a planetary gear shaft portion of a conventional planetary gear device.
【図７】 従来の遊星歯車装置における荷重均等化手段
を示す断面図である。FIG. 7 is a sectional view showing a load equalizing means in a conventional planetary gear device.
【図８】 他の荷重均等化手段を示す側面図である。FIG. 8 is a side view showing another load equalizing means.
【図９】 従来の遊星歯車装置の歯車部分の斜視図であ
る。FIG. 9 is a perspective view of a gear portion of a conventional planetary gear device.
【図１０】 図８の内歯車全体を示す斜視図である。FIG. 10 is a perspective view showing the entire internal gear of FIG. 8;
１ 遊星歯車 ２ 遊星歯車軸 ３ キヤリヤ ４ 第２の歯車軸 Reference Signs List 1 planetary gear 2 planetary gear shaft 3 carrier 4 second gear shaft
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭51−2869（ＪＰ，Ａ) 特開 昭56−90145（ＪＰ，Ａ) 実開 昭53−159468（ＪＰ，Ｕ) 実開 昭60−3342（ＪＰ，Ｕ) 実開 平１−143447（ＪＰ，Ｕ) 特公 昭42−9168（ＪＰ，Ｂ１) 仙波 正荘「歯車 第１巻」（昭32− ８−15）日刊工業新聞社 Ｐ．158−164 仙波 正荘「歯車 第10巻」（昭42− 11−30）日刊工業新聞社 Ｐ．3972 (58)調査した分野(Int.Cl.7，ＤＢ名) F16H 1/28 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-51-2869 (JP, A) JP-A-56-90145 (JP, A) Fully open Showa 53-159468 (JP, U) Really open Showa 60- 3342 (JP, U) JP-A 1-143447 (JP, U) JP-B Sho 42-9168 (JP, B1) Masanori Senba "Gears Volume 1" (Showa 32-8-15) Nikkan Kogyo Shimbun P . 158-164 Masanori Senba, “Gears, Volume 10” (Showa 42-11-30), Nikkan Kogyo Shimbun 3972 (58) Field surveyed (Int.Cl. 7 , DB name) F16H 1/28
Claims (1)
を配置した遊星歯車装置において、遊星歯車の個数を
ｎ、かみあい周期をＴzとした時に、各遊星歯車の位置
を調整して各遊星歯車相互のかみあい位相をＴz／ｎづ
つずらし、かみあい率ε≒１＋（ｎ−１）／ｎとしたこ
とを特徴とする遊星歯車装置。1. A planetary gear unit in which a plurality of planet gears between the inner and the sun gear gear, the number of planetary gears n, when the engagement period was T z, by adjusting the position of each planet gear the meshing phases of the planetary gears mutually shifted T z / n increments, planetary gear unit, characterized in that the contact ratio ε ≒ 1 + (n-1 ) / n.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16476592A JP3181099B2 (en) | 1992-06-23 | 1992-06-23 | Planetary gear set |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16476592A JP3181099B2 (en) | 1992-06-23 | 1992-06-23 | Planetary gear set |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0610994A JPH0610994A (en) | 1994-01-21 |
| JP3181099B2 true JP3181099B2 (en) | 2001-07-03 |
Family
ID=15799505
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16476592A Expired - Lifetime JP3181099B2 (en) | 1992-06-23 | 1992-06-23 | Planetary gear set |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3181099B2 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2413836B (en) * | 2005-07-08 | 2006-04-12 | Orbital 2 Ltd | A gear mounting |
| US8348803B2 (en) | 2008-04-17 | 2013-01-08 | Kawasaki Jukogyo Kabushiki Kaisha | Planetary reduction gear apparatus |
| CA2682454C (en) * | 2009-04-14 | 2013-11-26 | Kawasaki Jukogyo Kabushiki Kaisha | Planetary reduction gear apparatus |
| EP2422111B1 (en) | 2009-04-23 | 2013-10-16 | The Timken Company | Epicyclic gear system with semi-integrated flexpin assemblies |
| DE102010019976B4 (en) * | 2010-05-10 | 2016-10-13 | Schaeffler Technologies AG & Co. KG | Planet wheel and planetary gear |
| KR102276982B1 (en) * | 2019-09-27 | 2021-07-13 | 엘지전자 주식회사 | Geared inwheel motor |
| DE102021116909B4 (en) | 2021-06-30 | 2023-06-07 | Renk Gmbh | planetary gear |
-
1992
- 1992-06-23 JP JP16476592A patent/JP3181099B2/en not_active Expired - Lifetime
Non-Patent Citations (2)
| Title |
|---|
| 仙波 正荘「歯車 第１０巻」（昭４２−１１−３０）日刊工業新聞社 Ｐ．３９７２ |
| 仙波 正荘「歯車 第１巻」（昭３２−８−１５）日刊工業新聞社 Ｐ．１５８−１６４ |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0610994A (en) | 1994-01-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5221146A (en) | Structure of bearing of geared shaft | |
| EP0305535B1 (en) | Epicyclic reduction gear | |
| US10060517B2 (en) | Strain wave gearing, frictional engagement wave device, and wave generator | |
| JP3387935B2 (en) | Planetary gear set | |
| JP3181099B2 (en) | Planetary gear set | |
| EP0559626A1 (en) | Planetary reduction unit | |
| US5108353A (en) | Crossed-axis gear differential | |
| GB2270359A (en) | A gear transmission with an anti-rattle system | |
| JP2000179629A (en) | Small backlash planetary gear device | |
| JPH0788878B2 (en) | Planetary gearbox with two sets of floating carriers | |
| JPH0534538B2 (en) | ||
| JPH06257660A (en) | Geared transmission mechanism | |
| EP1296847B1 (en) | Geared transmissions | |
| JP3034617B2 (en) | Double-row internal gear planetary gear structure | |
| US9644728B2 (en) | Strain wave device | |
| JP2726699B2 (en) | Planetary gear unit with backlash adjustment mechanism | |
| CA2440705C (en) | Compound differential planetary gear assembly | |
| JPH1151156A (en) | Gear, gear device, and backlash adjusting method of the gear device | |
| CA2256147A1 (en) | Gear-drive assembly | |
| KR102336717B1 (en) | Reducer having dual eccentric rotating shaft | |
| JPH07508825A (en) | Gear assembly structure of differential gear device | |
| GB2211900A (en) | Gear box comprising drum rotatable about inclined axis and bevel gears | |
| JPH10299841A (en) | Inscribed meshing epicyclic gear structure | |
| JPH07301288A (en) | Planetary gear drive without internal gear | |
| KR940701518A (en) | Multi-stage torque distribution differential |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20000620 |
|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20010321 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080420 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090420 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100420 Year of fee payment: 9 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110420 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130420 Year of fee payment: 12 |
|
| EXPY | Cancellation because of completion of term | ||
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130420 Year of fee payment: 12 |