JPH0610994A - Planetary gear device - Google Patents
Planetary gear deviceInfo
- Publication number
- JPH0610994A JPH0610994A JP4164765A JP16476592A JPH0610994A JP H0610994 A JPH0610994 A JP H0610994A JP 4164765 A JP4164765 A JP 4164765A JP 16476592 A JP16476592 A JP 16476592A JP H0610994 A JPH0610994 A JP H0610994A
- Authority
- JP
- Japan
- Prior art keywords
- planetary gear
- gear
- planetary
- gear shaft
- 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.)
- Granted
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)
Abstract
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 device used in a speed increasing / decreasing 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 structure of a general planetary gear device, and FIG. 6 is a cross-sectional view of the shaft supporting portion of the planetary gear 01. As shown in FIG. 6, both ends of the planetary gear shaft 02 are fixed to the carrier 03. The elements other than the planetary gear shaft 02 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. 8 and 10 are devised. Then, the load generated in each meshing of the planetary gears 01 is equalized. (2) Vibration in the planetary gears described in (1) above,
As a technology to reduce noise, if the number of planetary gears is an even number, adjust the meshing phase between opposing planetary gears by adjusting only the number of teeth, pressure angle, and teeth (the planetary gear axis is not adjusted). The method of reverse phase is described in the document “WE Palm.
er and R.E. R. Fuehler “Noise”
Control In Planetary Tran
missions "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) The flexible joint 07 or the sheath spring 04 shown in FIGS. 7 and 8 both adjust the axial center of the internal gear 05,
It is not possible to adjust the axial center and tooth contact of each planetary gear 01 to equalize the loads generated during the meshing of the planetary gears. (2) Vibration that makes the meshing phase between the planetary gears the opposite phase
The noise reduction technique 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。It is an object of the present invention to provide a planetary gear device that equalizes the load applied to each planetary gear and reduces the vibration and noise of the device.
【０００５】[0005]
【課題を解決するための手段】（１） 遊星歯車軸をキ
ヤリヤから片持ち固定し、遊星歯車軸と遊星歯車との間
に円筒状の第２の歯車軸を挿入し、挿入された第２歯車
軸を遊星歯車軸の自由端に固着する。なお、第２歯車軸
の内周面と、遊星歯車軸の外周面との間には空隙を設け
る。このようにして、各遊星歯車のかみあいにより生ず
る荷生を均等させる。 （２） 遊星歯車軸をキヤリヤに片持ち固定し、片持ち
固定された歯車軸をタイコ状に形成する。[Means for Solving the Problems] (1) A planetary gear shaft is cantilevered from a carrier, and a cylindrical second gear shaft is inserted between the planetary gear shaft and the planetary gear shaft. Secure the gear shaft to the free end of the planet gear shaft. A gap is provided between the inner peripheral surface of the second gear shaft and the outer peripheral surface of the planetary gear shaft. In this way, the loads caused by the meshing of the planetary gears are equalized. (2) The planetary gear shaft is cantilevered to the carrier, and the cantilevered gear shaft is formed in the shape of a drum.
【０００６】さらに円筒状の第２の歯車軸を上記のタイ
コ状の歯車軸に挿入すると共に抜け落ちない様にストッ
パを設ける。遊星歯車は上記第２の歯車軸に嵌め込んで
おく。このようにして、各遊星歯車のかみあいにより生
ずる荷重を均等させる。 （３） 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ＴZ ／ｎづつずらし（ｎ：遊星歯車の個数、
ＴZ ：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
減を計る。Further, the cylindrical second gear shaft is inserted into the above-mentioned Tyco gear shaft and a stopper is provided so as not to fall off. The planetary gear is fitted in the second gear shaft. In this way, the loads generated by the meshing of the planetary gears are equalized. (3) By adjusting the position of the planetary gears, the mutual phases of the planetary gears are shifted by T Z / n (n: number of planetary gears,
T Z: meshing cycle), by making the contact ratio ε ε ≒ 1 + (n- 1) / n, measuring the reduction of vibratory force between the planet gears and the internal gear.
【０００７】[0007]
【作用】歯形誤差、組立誤差等の誤差がなければ、複数
の遊星歯車のそれぞれのかみあいに生ずる荷重は均等に
なるが、実際はそれ等の誤差が存在するため、荷重は不
均一になる。この時、仮に装置の剛性が無限大であれば
誤差による荷重の不均一はそのまま残るが、剛性が小さ
く弾性的に変形しやすい構造であれば、遊星歯車、内歯
車、太陽歯車が、装置変形により、それぞれ均等にかみ
あうような位置に動き、不均一の度合が補正される。If there is no error such as a tooth profile error or an assembly error, the loads generated at the meshes of the plurality of planetary gears will be equal, but in reality, since there are such errors, the loads will be non-uniform. At this time, if the rigidity of the device is infinite, the unevenness of the load due to the error remains as it is, but if the structure is low and the structure is easily elastically deformed, the planetary gears, internal gears, and sun gears will be deformed. By this, the movements are made to evenly engage with each other, and the degree of non-uniformity is corrected.
【０００８】請求項１，２に記載された発明は、遊星歯
車軸を一方のキヤリヤに片持ち固定し、同遊星歯車軸の
外側に円筒状の第２の歯車軸を嵌装し、これ等の歯車軸
を可能な限り弾性的に変形しやすい構造にし、それによ
り遊星歯車が内歯車及び太陽歯車と均等にかみあうよう
な位置に動くことが可能になり、荷重の不均一を補正す
ることができる。According to the invention described in claims 1 and 2, the planetary gear shaft is cantilevered to one of the carriers, and the cylindrical second gear shaft is fitted on the outside of the planetary gear shaft. The structure of the gear shaft of the is made as elastic as possible as easily as possible, which allows the planetary gear to move to a position where it meshes evenly with the internal gear and sun gear, and it is possible to correct uneven loads. it can.
【０００９】請求項３に記載された発明は、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
大巾に低減する。According to a third aspect of the present invention, the meshing phases of the planetary gears are shifted by T Z / n, and the meshing ratio ε.
By setting ≈ 1 + (n-1) / n, fluctuations in the transmission load of the entire planetary gear are eliminated, the vibration force of the entire planetary gear is reduced, and vibration and noise of the planetary gear device are greatly reduced. To do.
【００１０】[0010]
第１実施例 本発明の第１実施例を図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。First Embodiment A first embodiment of the present invention will be described with reference to FIG. In the figure, 1 is a planetary gear, 2 is a planetary gear shaft, 3 is a carrier that rotates around the axis of the sun gear (see 06 in FIG. 9), 4
Is a cylindrical second gear shaft, and 5 and 6 are nuts.
【００１１】図に示すように、遊星歯車軸２の一端をキ
ヤリヤ３にナット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。従っ
て、歯車軸２，４はキヤリヤ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 figure, one end of a planetary gear shaft 2 is fixed to a carrier 3 with a nut 5, and a second gear shaft 4 is fitted between the planetary gear shaft 2 and the planetary gear 1 to form a planetary gear. A nut 6 fixes the free end of the shaft 2 and the end of the gear shaft 4. Therefore, the gear shafts 2 and 4 are cantilevered with respect to the carrier 3,
Moreover, the shaft is folded back, and the planetary gear 1 is supported so as to be displaceable in the direction perpendicular to the axis.
【００１２】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実施例 本発明の第２実施例を図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 in a direction perpendicular to the shaft. Can be easily elastically deformed. In the above embodiment, the nut 6 may be fixed by welding instead of the nut 6. Second Embodiment A second embodiment of the present invention will be described with reference to FIG.
【００１３】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 the figure, 1 is a planetary gear, 2a is a planetary gear shaft of a Tyco type (middle height), 3 is a carrier, 4a is a cylindrical second gear shaft, 5 is a nut, and 7 is a stopper.
The planetary gear shaft 2a is cantilevered to the carrier 3 as in the first embodiment. Further, the axial surface of the planetary gear shaft 2a is formed in a circular arc having a radius R in the shape of a drum. Due to the cantilever fixing, the planetary gear shaft 2a is easily elastically deformed, and the planetary gear 1 has the planetary gear 1 (see 05 in FIG. 9) and the sun gear (0 in FIG. 9).
(See 6) and move to a position that evenly engages. On the other hand, the cylindrical second gear shaft 4a is replaced with the planetary gear shaft 2a.
The planetary gear 1 is fitted in the gear shaft 4a.
【００１４】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。 第３実施例 本発明の第３実施例を図３乃至図５について説明する。As shown in the figure, since the planetary gear shaft 2a is provided with a crown having a radius R, the degree of freedom of the gear shaft 4a is increased and the tooth contact is improved by the movement (displacement) of the gear shaft 4a. Be done. An appropriate stopper 7 is inserted between the two gear shafts 2a and 4a so as not to slip off from each other. Third Embodiment A third embodiment of the present invention will be described with reference to FIGS.
【００１５】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, the planetary gears 01 are arranged at equal intervals in FIG. 9, but in the present embodiment, as shown in FIG. 3, the positions of the planetary gears 1A, 1B, 1C are equal. It is shifted with respect to the distance position and adjusted so that the meshing phases of the planetary gears 1A, 1B, 1C are shifted by T Z / n.
【００１６】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繰り返えされ、その
時のかみ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。The contact ratio is arbitrarily selected in the prior art, but in this embodiment, ε = 1 + (n-1) / n. Next, the operation of this embodiment will be described. The fluctuation of the transmission load of the spur gear shows the characteristic as shown in FIG. Assuming that the meshing cycle is T Z , as shown in the figure, the spur gear has two teeth meshing and one tooth meshing repeated periodically, and the change in the meshing number at that time is the variation of the transmission load as shown in the figure. cause.
【００１７】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。The two-tooth meshing region is given by (ε-1) T Z, where ε is the meshing ratio. Now, as shown in FIG. 5, in a planetary gear device in which the number n of planetary gears is given as n = 3, the fluctuation of the transmission load of the entire gear pair is
Let us consider a method of eliminating the loss as shown at 4 on the right side of FIG.
【００１８】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 that purpose, the planetary gears 1A, 1B shown in FIG.
1C and the phase of meshing 1, 2 and 3 of the internal gear 05 is T Z /
It is sufficient to shift by 3 and set the two-tooth meshing area of each meshing to 2/3 · T Z , that is, the meshing ratio, and set ε = 1 + 2/3 = 1 + (3-1) / 3 (2).
【００１９】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。When 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. Load fluctuations disappear. Generally, in a gear device, the fluctuation of the transmission load shown in FIG. 4 serves as 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 Is eliminated and the vibration force of the gear pair as a whole is reduced, so that the vibration and noise of the planetary gear device can be greatly reduced.
【００２０】[0020]
【発明の効果】（１） 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、
前記太陽歯車の軸線まわりに回転するキヤリヤに遊星歯
車軸を片持ち固定し、前記遊星歯車軸と遊星歯車の間に
円筒状の第２の歯車軸を嵌入すると共に、同第２の歯車
軸を前記遊星歯車軸に対して軸直角方向に変形可能とし
たことにより、各遊星歯車の荷重を均一化し、歯当りを
改善することができる。 （２） 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。(1) The present invention provides a planetary gear device in which a plurality of planetary gears are arranged between a sun gear and an internal gear,
A planetary gear shaft is cantilevered and fixed to a carrier that rotates around the axis of the sun gear, a cylindrical second gear shaft is inserted between the planetary gear shaft and the planetary gear, and the second gear shaft is attached to the carrier. By allowing the planetary gear shaft to be deformed in the direction perpendicular to the shaft, the load of each planetary gear can be made uniform and tooth contact can be improved. (2) According to the present invention, in a planetary gear device in which a plurality of planetary gears are arranged between a sun gear and an internal gear, when the number of planetary gears is n and the meshing period is T Z , the position of each planetary gear is adjusted. And the meshing phase of each planetary gear is T Z / n
By sequentially shifting and setting the contact ratio ε≈1 + (n-1) / n, the vibration force of the planetary gear device can be reduced, and vibration and noise can be reduced.
【図１】本発明の第１実施例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 embodiment of the present invention.
【図２】本発明の第２実施例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 embodiment of the present invention.
【図３】本発明の第３実施例の原理を示す図である。FIG. 3 is a diagram showing the principle of the third 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 transmission load and time in gear noise.
【図５】本発明の第３実施例における作用を示す図であ
る。FIG. 5 is a diagram showing the operation of the third 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.
１ 遊星歯車 ２ 遊星歯車軸 ３ キヤリヤ ４ 第２の歯車軸 1 planetary gear 2 planetary gear shaft 3 carrier 4 second gear shaft
Claims (3)
を配置した遊星歯車装置において、前記太陽歯車の軸線
まわりに回転するキヤリヤに遊星歯車軸を片持ち固定
し、前記遊星歯車軸と遊星歯車の間に円筒状の第２の歯
車軸を嵌入すると共に、同第２の歯車軸を前記遊星歯車
軸の自由端に固着させたことを特徴とする遊星歯車装
置。1. In a planetary gear device in which a plurality of planetary gears are arranged between a sun gear and an internal gear, a planetary gear shaft is cantilevered and fixed to a carrier that rotates around the axis of the sun gear. A planetary gear device in which a cylindrical second gear shaft is fitted between the planetary gears and the second gear shaft is fixed to the free end of the planetary gear shaft.
を配置した遊星歯車装置において、前記太陽歯車の軸線
まわりに回転するキヤリヤに遊星歯車軸を片持ち固定し
且つ同遊星歯車軸の軸面をタイコ状に形成し、前記遊星
歯車軸と遊星歯車の間に円筒状の第２の歯車軸を嵌入す
ると共に、同第２の歯車軸の脱落を防止するストッパを
設けたことを特徴とする遊星歯車装置。2. A planetary gear device in which a plurality of planetary gears are arranged between a sun gear and an internal gear, wherein a planetary gear shaft is cantilevered and fixed to a carrier rotating about the axis of the sun gear. A shaft surface is formed in a Tyco shape, a cylindrical second gear shaft is fitted between the planetary gear shaft and the planetary gear, and a stopper is provided to prevent the second gear shaft from falling off. And planetary gear system.
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。3. A planetary gear device in which a plurality of planetary gears are arranged between a sun gear and an internal gear, wherein the position of each planetary gear is adjusted when the number of planetary gears is n and the meshing period is T Z. A planetary gear device characterized in that the meshing phases of the respective planetary gears are shifted by T Z / n so that the meshing 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 true JPH0610994A (en) | 1994-01-21 |
| JP3181099B2 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) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010123964A1 (en) * | 2009-04-23 | 2010-10-28 | The Timken Company | Epicyclic gear system with semi-integrated flexpin assemblies |
| EP2241780A3 (en) * | 2009-04-14 | 2011-05-11 | Kawasaki Jukogyo Kabushiki Kaisha | Planetary reduction gear apparatus |
| JP4829967B2 (en) * | 2005-07-08 | 2011-12-07 | オルビタル２ リミテッド | Gear mounting body |
| US8348803B2 (en) | 2008-04-17 | 2013-01-08 | Kawasaki Jukogyo Kabushiki Kaisha | Planetary reduction gear apparatus |
| DE102010019976B4 (en) * | 2010-05-10 | 2016-10-13 | Schaeffler Technologies AG & Co. KG | Planet wheel and planetary gear |
| KR20210037798A (en) * | 2019-09-27 | 2021-04-07 | 엘지전자 주식회사 | Geared inwheel motor |
| DE102021116909A1 (en) | 2021-06-30 | 2023-01-05 | Renk Gmbh | planetary gear |
-
1992
- 1992-06-23 JP JP16476592A patent/JP3181099B2/en not_active Expired - Lifetime
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4829967B2 (en) * | 2005-07-08 | 2011-12-07 | オルビタル２ リミテッド | Gear mounting body |
| US8348803B2 (en) | 2008-04-17 | 2013-01-08 | Kawasaki Jukogyo Kabushiki Kaisha | Planetary reduction gear apparatus |
| EP2241780A3 (en) * | 2009-04-14 | 2011-05-11 | Kawasaki Jukogyo Kabushiki Kaisha | Planetary reduction gear apparatus |
| WO2010123964A1 (en) * | 2009-04-23 | 2010-10-28 | The Timken Company | Epicyclic gear system with semi-integrated flexpin assemblies |
| US8920284B2 (en) | 2009-04-23 | 2014-12-30 | 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 |
| KR20210037798A (en) * | 2019-09-27 | 2021-04-07 | 엘지전자 주식회사 | Geared inwheel motor |
| DE102021116909A1 (en) | 2021-06-30 | 2023-01-05 | Renk Gmbh | planetary gear |
| DE102021116909B4 (en) | 2021-06-30 | 2023-06-07 | Renk Gmbh | planetary gear |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3181099B2 (en) | 2001-07-03 |
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