JPH02292550A - Integral type asymmetrical planetary gear - Google Patents
Integral type asymmetrical planetary gearInfo
- Publication number
- JPH02292550A JPH02292550A JP1113924A JP11392489A JPH02292550A JP H02292550 A JPH02292550 A JP H02292550A JP 1113924 A JP1113924 A JP 1113924A JP 11392489 A JP11392489 A JP 11392489A JP H02292550 A JPH02292550 A JP H02292550A
- Authority
- JP
- Japan
- Prior art keywords
- planetary
- outer shell
- gear
- planetary gear
- disk
- 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.)
- Pending
Links
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/02004—Gearboxes; Mounting gearing therein the gears being positioned relative to one another by rolling members or by specially adapted surfaces on the gears, e.g. by a rolling surface with the diameter of the pitch circle
-
- 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
Abstract
Description
この発明は、減速器、増速器として広い用途を持つ遊星
面車装置に関する。特に、遊星歯車に構造、外殻内歯歯
車の構造が非対称であって、遊星歯車が一体化されてい
る遊星歯車装置を与える。The present invention relates to a planetary trolley device that has wide applications as a speed reducer and a speed increaser. In particular, the present invention provides a planetary gear device in which the structure of the planetary gear and the structure of the outer shell internal gear are asymmetrical, and the planetary gear is integrated.
遊星歯車装置は、太陽歯車、３〜４個の遊星歯車、外殻
内歯歯車、キャリヤなどよりなる。
太陽歯車、遊星歯車、外殻内歯歯車の間での噛合点は６
または８点ある。噛合点が部材の数に比べて多すぎるの
で、伝達力が同一にならず、不均衡になりがちである。
噛み合いが不均衡であると、歯車同士が過度に深く噛合
うことになり、馨しい騒音、振動が発生する。エネルギ
ーのロスも大きくなる。
これを解決するために、遊星歯車や外殻内歯歯車の両側
または片側にピッチ円に等しい直径の円板やリングを取
り付けた遊星画車装置が提案されている。遊星歯車に取
り付けた円板と外殻内歯歯車に取り付けたリングとを接
触転動させる。
これにより歯先の過度の噛み込みを防ぐことができる。
これをピッチ円方式と呼ぶことにする。
第８図にこの方式の遊星歯車を示す。
この方式の遊星歯車装置は実に多い。それはピッチ円が
歯車にとって特別の円だからである。
ピッチ円に等しい直径の円板とリングを歯車と同回転さ
せたとき接触点で線速度が等しく、両者間に滑りがない
。だから伝達効率を損なわないし円板、リング自体の摩
滅も少ないからである。
しかしピッチ円は、歯底円と歯先円の中間の大きさを持
つ円であるので、部材の数が多くなり過ぎるという阜点
がある。ひとつの遊星歯車が３部材からなり、外殻内歯
歯車が３部材からなることになる。
部品点数が多いと、部品コストが増える。又外殻内歯歯
車が３部材からなると、３つの部材間での位置合わせの
不正という問題が生ずる。
そこで本出願人は歯先円方式の遊里歯車装置を発明した
（特願昭５６−１９３１１３ 、特開昭５８−９４６５
８、５８ ，６ ．４公開）。遊星歯車は歯先円より大
きい円板を両側に持つ。外殻内歯歯車は歯底円より大き
い直径のリング部を持つ。歯底円より大きいのでこれは
外殻内歯歯車のギヤ部に合体することができる。第７図
にこの方式の遊星歯車を示す。
そのためこの装置において外殻内歯歯車が一部材で作ら
れる。実際にはポリアセタールで成形する。
部品点数が２つ減る。部品コストが減少するだけでなく
、組み立てコストも削減される。
ただし円板とリングの接触転勤点がピッチ円からずれる
ので、果たして円滑に回転するかどうか疑問があった。
実際に作ってみると、抵抗なく滑らかに回転した。
これは歯車に関しては前後に対称であった。
本出願人はさらに前後に非対称である遊星歯車装置を発
明した。
ａ 特開昭ＧＯ−３４５５３、昭和６０年２月２２日公
開ｂ 特開昭ｆｌｉｐ−２５２８４５ 、昭和６０年１
２月１３日公開Ｃ 特開昭Ｇｌ−２７３３７、昭和６１
年２月６日公開ａは歯車の一方だけに円板を設けたもの
である。
ｂとＣは両方に円板、リングを付けている。しかしこれ
らは非対称であり、遊星歯車の片側の円板は歯先円より
大きく、もう一方の円板は歯底円より小さくしたもので
ある。
当然のことであるが外殻内歯歯車の片側のリング部は面
底円より大きく、もう一方のリング部は歯底円より小さ
い。
遊星面車の両側の円板、外殻内歯歯車の両側のリングで
、接触転勤点での線速度が異なるので、果たしてこのよ
うな遊星歯車装置が円滑に回転するかどうか疑問があっ
た。しかし実際に作ってみると、滑らかに回転した。
非対称遊星歯卓装置は組み立てた後に、太陽画車を側方
から差し込むことができる、という利点があった。
このように本出願人は多くの変則的な遊星歯車装置を発
明してきた。振動が少なく、伝達効率が高＜、シかも安
価であるものを摸索してきたということができる。The planetary gear system consists of a sun gear, three to four planetary gears, an outer shell internal gear, a carrier, and the like. The meshing points between the sun gear, planet gear, and outer shell internal gear are 6.
Or there are 8 points. Since there are too many meshing points compared to the number of members, the transmitted forces tend to be unequal and unbalanced. If the meshing is unbalanced, the gears will mesh too deeply, causing noise and vibration. Energy loss also increases. To solve this problem, a planetary wheel device has been proposed in which a disk or ring having a diameter equal to the pitch circle is attached to either side or one side of a planetary gear or an external internal gear. A disk attached to a planetary gear and a ring attached to an outer shell internal gear are caused to contact and roll. This can prevent excessive biting of the tooth tips. This will be called the pitch circle method. Figure 8 shows a planetary gear of this type. There are many planetary gear devices of this type. This is because the pitch circle is a special circle for gears. When a disk and a ring with a diameter equal to the pitch circle are rotated at the same time as a gear, the linear velocity is equal at the point of contact, and there is no slippage between them. This is because the transmission efficiency is not impaired and there is less wear and tear on the disks and rings themselves. However, since the pitch circle is a circle with a size intermediate between the tooth root circle and the tooth tip circle, there is a problem that the number of members is too large. One planetary gear consists of three members, and an outer shell internal gear consists of three members. If the number of parts is large, the parts cost will increase. Furthermore, when the outer shell internal gear is composed of three members, a problem arises in that the three members are incorrectly aligned. Therefore, the present applicant invented a tip-circle type free-wheel gear device (Japanese Patent Application No. 56-193113, Japanese Unexamined Patent Publication No. 58-9465).
8, 58, 6. 4 published). Planetary gears have disks on both sides that are larger than the tooth tip circle. The outer shell internal gear has a ring portion with a diameter larger than the root circle. Since it is larger than the tooth root circle, it can be integrated into the gear part of the outer shell internal gear. Figure 7 shows a planetary gear of this type. Therefore, in this device, the outer shell internal gear is made of one piece. It is actually molded from polyacetal. The number of parts is reduced by two. Not only are component costs reduced, but assembly costs are also reduced. However, since the point of contact between the disc and the ring was shifted from the pitch circle, there was some doubt as to whether it would rotate smoothly. When I actually made it, it rotated smoothly without any resistance. This was symmetrical about the gears. The applicant has further invented a planetary gear train which is asymmetrical from front to back. a JP-A-34553, published on February 22, 1985 b JP-A flip-252845, 1, 1985
Published on February 13th C Unexamined Japanese Patent Publication No. 1983-27337, Showa 61
Published on February 6, 2015 A is a gear in which a disk is provided on only one side. B and C both have disks and rings attached. However, these are asymmetrical, with the disk on one side of the planetary gear being larger than the tip circle and the other disk being smaller than the root circle. Naturally, the ring portion on one side of the external shell internal gear is larger than the bottom circle of the face, and the other ring portion is smaller than the bottom circle. Since the linear speeds at the contact transfer points differ between the disks on both sides of the planetary wheel and the rings on both sides of the outer shell internal gear, there was some doubt as to whether such a planetary gear system would rotate smoothly. However, when I actually made it, it rotated smoothly. The asymmetrical planetary gear had the advantage that the sun wheel could be inserted from the side after assembly. The applicant has thus invented many irregular planetary gear systems. It can be said that we have been looking for something that has less vibration, high transmission efficiency, and is also inexpensive.
前述の歯先円方式の場合でも、非対称の場合でも、遊星
歯車は３つの部材からなっている。
中央のギヤ部とこれを挟む２つの円板である。遊星歯車
は３〜４個有り、ひとつの遊星歯車が３つの部材からな
るので、部品コスト、組み立てコストともに高くなる。
もしも遊星歯車をひとつの部材で作ることができればコ
ストを大幅に削減できるであろう。
ピッチ円板を遊星歯車の両側に設けるものは３部材にな
っていた。２部材にする事は可能であろうがバランスの
点で問題がある。
歯先円方式のものは、遊星歯車が３部材にならざるを得
ない。ギヤ部の両側にギヤよりも大きい円板を有するか
らである。
本発明の目的のひとつは遊星歯車を一体化した遊星歯車
装置を与える事である。
もうひとつの目的は、外殻内歯歯車に材料的な工夫をし
て、より騒音、振動の少ない遊星歯車装置を与えること
である。A planetary gear consists of three members, whether in the case of the tip circle method described above or in the asymmetric case. It consists of a central gear part and two disks sandwiching it. There are three to four planetary gears, and one planetary gear is made up of three members, so both the parts cost and the assembly cost are high. If the planetary gear could be made from a single component, the cost would be significantly reduced. The pitch disk was provided on both sides of the planetary gear using three members. It would be possible to make it into two parts, but there would be a problem in terms of balance. In the tooth tip circle type, the planetary gear must have three members. This is because the gear portion has disks larger than the gear on both sides. One of the objects of the present invention is to provide a planetary gear system with integrated planetary gears. Another purpose is to provide a planetary gear system with less noise and vibration by improving the material of the outer shell internal gear.
【課題を解決するための手段】
本発明の遊星歯車装置は、一方に歯先円より大きい円板
を、もう一方に歯底円より小さい円板をギヤ部と一体に
形成した遊星歯車を用いる。ギヤ部と両側の円板部とを
一体化しているのであるこれが一つの特徴である。
つまり遊星歯車は中央にギヤ部、その側方に歯底円より
大きい遊星大円板部を、反対側に歯底円より小さい遊星
小円板部を有するが、これらが遊星ボス部とともに一体
化されている。
さらにもうひとつの特徴は外殻内歯歯車を、ナイロン６
８、ナイロン８、ボリプロビレンなど剛性の低い、柔軟
な材料で作るということである。
これにより振動、騒音を低減することができる。
遊星歯車の構造に対応して、外殻内画歯車は中央に外殻
ギヤ部を、側方に外殻内歯泪車の歯底円より大きい外殻
大内円筒部を、他方に外殻内歯歯車の歯先円より小さい
外殻小内円筒部を有する。
このような外殻内歯歯車の構造は前記の非対称遊星歯車
装置と同じである。[Means for Solving the Problems] The planetary gear device of the present invention uses a planetary gear in which a disk larger than a tooth tip circle is formed on one side and a disk smaller than a tooth bottom circle is formed integrally with a gear portion on the other side. . One of the features is that the gear part and the disk parts on both sides are integrated. In other words, a planetary gear has a gear part in the center, a large planetary disc part larger than the tooth root circle on the side, and a small planetary disc part smaller than the tooth root circle on the opposite side, but these are integrated with the planetary boss part. has been done. Another feature is that the outer shell internal gear is made of nylon 6
It is made of flexible materials with low rigidity such as nylon 8, polypropylene, etc. This allows vibration and noise to be reduced. Corresponding to the structure of the planetary gear, the inner-shell gear has an outer-shell gear part in the center, an outer-shell large inner cylindrical part larger than the tooth bottom circle of the outer-shell gear on the side, and an outer-shell inner cylindrical part on the other side. The outer shell has a small inner cylindrical portion that is smaller than the tip circle of the gear. The structure of such an external shell internal gear is the same as that of the asymmetric planetary gear device described above.
遊星画車の遊星ギヤ部と、外殻内歯歯車の外殻ギヤ部が
噛合する。遊星面車の遊星大円板部と、外殻内歯歯車の
外殻大内円筒部とが転勤接触する。遊星歯車の遊星小円
板部と、外殻内歯歯車の外殻小内円筒部とが転勤接触す
る。
回転トルクはギヤ部同士で伝達される。半径方向の過度
の力は、遊星歯車の円板部と外殻内歯歯車の円部の転勤
接触により防ぐことができ、歯車同士が過度に噛合うと
いう事がない。
転勤接触点において、円板や円筒部の線速度が異なるの
であるが゛、これらは円滑な回転を妨げない。円板や円
筒にはある程度の公差を付けるので常時これらが転勤接
触しているのではなく、むしろほとんどの時間これらは
離れている。であるから線速度の違いが、回転の妨げと
はならないのである。
遊星歯車が一体化されているので、部品コストや組み立
てコストが低減される。
外殻内歯歯車がナイロン６８、ナイロン８、ポリプロピ
レンであるので、柔軟であり、騒音，振動が軽減される
。The planetary gear portion of the planetary wheel meshes with the outer shell gear portion of the outer shell internal gear. The planetary large disk portion of the planetary surface wheel and the outer shell large inner cylindrical portion of the outer shell internal gear come into rolling contact. The small planetary disk portion of the planetary gear and the small inner cylindrical portion of the outer shell of the outer internal gear come into rolling contact. Rotational torque is transmitted between the gear parts. Excessive force in the radial direction can be prevented by rolling contact between the disk portion of the planetary gear and the circular portion of the outer shell internal gear, and the gears do not mesh excessively with each other. Although the linear velocities of the disk and cylinder differ at the rolling contact point, these do not hinder smooth rotation. Since a certain degree of tolerance is attached to the disks and cylinders, they are not always in contact with each other; rather, they are separated most of the time. Therefore, the difference in linear velocity does not hinder rotation. Since the planetary gears are integrated, component costs and assembly costs are reduced. Since the outer shell internal gear is made of nylon 68, nylon 8, or polypropylene, it is flexible and reduces noise and vibration.
以下、実施例を示す図面により本発明の一体型非対称遊
星画車装置を説明する。
第１図は本発明の実施例に係る遊星歯車装置の一部切り
欠き正面図、第２図は一部切り欠き背面図、第３図は第
１図中のＩＩＩ−［断面図である。
遊星歯車装置は、太陽歯車１、遊星歯車２、外殻内歯歯
車３、キャリヤ４などよりなる。
中心に太陽歯車１がある。これを囲みこれと噛合う４つ
の遊星歯車２がある。遊星歯車は３であっても良い。こ
れら全ての遊星歯車２を囲んで、これらと噛合する外殻
内爾歯車３がある。
キャリヤ４は、主キャリヤ盤４ａと副キャリヤ盤４ｂと
を組み合わせたものである。キャリヤ４は遊星軸５によ
って、遊星歯車２を回転自在に支持するものである。
主キャリヤ盤４ａは、内歯に４つ（または３つ）の第１
凸部１０を有する。これに対応し副キャリヤ盤４ｂは内
歯に４つ（または３つ）の第２凸部１１を有する。
副キャリヤ盤４ｂの第２凸部１１の先にはプラグ部１２
が形成されている。主キャリヤ盤４ａの第１凸部１０に
はこれに対応してソケット穴１３が穿たれている。
キャリ４を組み立てるには、副キャリヤ盤４ｂのプラグ
部１２を、主キャリヤ盤４ａのソケット穴１３に挿入に
、先端を窪み２９の外に出す。そしてプラグ部工２の先
端をかしめる。かしめ端部２８の作用により主キャリヤ
盤４ａと副キャリヤ盤４ｂとが一体化される。
これは主キャリヤ盤４ａ１副キャリヤ盤４ｂが焼結合金
、アルミダイキャストで作られている場合である。
主キャリヤ盤４ａ１副キャリヤ盤４ｂがプラスチックで
できている場合は、超音波溶着法によりプラグ部１２の
端部２８をソケット穴１３に対して固着する。
主キャリヤ盤４ａの裏面には、遊星軸止穴１６を穿った
第３凸部１８が、４つ（または３つ）形成されている。
第３凸部１８は隣接するふたつの第１凸部１０の中間に
設けられる。副キャリヤ盤４ｂの裏面には、遊星軸止穴
１８を穿った第４凸部１９が４つ（または３つ）形成さ
れている。
遊星軸５の両端は、主キャリヤ盤４ａと副キャリヤ盤４
ｂの遊星軸止穴１８、１６によって固定される。
本発明のひとつの特徴が遊星歯車の形状にあるので、第
４図の拡大正面図と、遊星歯車だけの拡大正面図である
第５図により、更に詳し《説明する。
遊星歯車２は中央に遊星ギヤｇ８を有し、左右に遊星小
円板部６と遊里大円板部７とを有する。
つまり遊星歯車２は非対称の構造をしている。
遊里ギャ部８の内方が遊星ボス部９となっており、ここ
に軸通し穴２１が穿たれている。遊星軸５は、遊星ボス
部９の軸通し穴２１に挿通されている。
遊星小円板部６は、遊星歯車の歯底円より小さい。遊星
大円板部７は、遊星歯車の面先円より大きい。
しかも遊星ギヤ部８と遊星小円板部８、遊星大円板部７
とが遊星ボス部９とともに一体として作られている。
三つの部材として分かれているのではない。ひとつの部
材である。ここが新規な点のひとつである。プラスチッ
ク射出成形や、焼結によりこのような非対称の遊星歯車
を作ることができる。
遊星歯車２に対応して、外殻内歯歯車３も３つの部分を
持つ。
外殻内歯歯車３は、中央に外殻ギヤ部２５を、左右に外
殻小内円筒部２６と外殻小内円筒部２６とを有する。
外殻ギヤ部２５は遊星歯車２の遊星ギヤ部８と噛み合い
、回転トルクを伝達する。
外殻小内円筒部２６に、遊星面車２の遊星小円板部６が
接触転動する。転勤面にはもちろんギャプがあり、両者
が接触することもあり、非接触のこともある。
同様に、外殻大内円筒部２７には、遊星歯車２の遊星大
円板部７が転勤接触する。この転勤面にもギャップがあ
り、両者が接触することもあり、非接触のこともある。
外殻小内円筒部２６と遊星小円板部６の接触、および外
殻大内円筒部２７と遊星大円板部７の接触によって、半
径方向の力が、遊星歯車２から外殻内歯歯車３に伝えら
れる。
太陽面車１には太陽軸孔１４があって、スプライン、セ
レーションあるいＤ型穴が形成されている。
キャリヤ４の主キャリヤ盤４ａのボス部は肉厚になって
おり、軸方向にキャリヤ軸孔１５が穿たれている。キャ
リヤ軸孔１５にもスプライン、セレーション等の廻り止
め機構が形成されている。
これを減速器として使用する場合は、太陽軸孔１４に入
力軸を、キャリヤ軸孔１５に出力軸を挿入する。増速器
として使用するときは太陽軸孔１４に出力軸を、キャリ
ヤ軸孔１５の入力軸を挿入する。
外殻内歯歯車３は、ケーシング等に固定しなければなら
ない。廻り止めするため、この例では外殻内ｍｔＢ車３
の外周は平坦な円筒部３２の上に、いくつかの廻り止め
突部３１が形成してある。これは一例にすぎない。
外殻内歯歯車３を固定するため、その他の構造を任意に
採用することができる。軸方向に穴の形成して、ネジ止
め、ピン止めできるようにしても良い。
図示した例では、廻り止め凸部３１が、中心線より外れ
た位置にある。トルクの掛かる面と、廻り止め突部の存
在する面とが離れている。この間で、外殻内歯歯車が捻
じれる。このため突然の大きいショックを吸収できると
いう効果がある。
さらに外殻内歯画車３は一体として、ナイロン６８、ナ
イロン６またはポリプロピレンで成形スる。これはポリ
アセタールより柔軟であり、振動や騒音を抑制する上で
効果的である。
第３図の例では、遊星歯車２の軸方向の変位を抑えるた
めに、遊星ボス部９の両側に膨出した第３凸部１６、第
４凸部１９を設けている。
太陽歯車１は遊星歯車２の遊星大円板部７によって抜け
どめされている。
太陽歯車１の反対側は、膨出した主キャリヤ盤４ａの内
ボス部２２によって、軸方向の変位が禁じられる。こう
して太陽歯車１は軸方向に正しい位置に保たれる。
この例では、主キャリヤ盤４ａを外殻内歯画車３の外殻
小内円筒部２６より大きくして、キャリヤ４が外殻内歯
歯車３から、左方へ抜けるのを防いでいる。
第６図は他の実施例を示す遊星歯車装置の一部縦断面図
である。基本的な構造は前記の例と同じである。
これは遊星歯車２の軸方向の変位を防ぐために主キャリ
ヤ盤４ａと副キャリヤ盤４ｂの裏面に周回突条３８、３
７を設けたものである。遊星歯車２の遊星小円板部８、
遊星大円板部７の側面が、キャリヤ４の周回突条３８、
３７に接触するから、遊星歯車２は軸方向の正しい位置
に保たれる。
またこの例では、外殻内歯歯車には軸方向にボルト穴３
８が穿たれている。ここにボルトを通して外殻内歯歯車
３をケ〜シングに固定する。
太陽歯車１は、プラスチック、焼結合金、亜鉛または鉄
などで作ることができる。
遊星歯車２は、プラスチックまたは焼結合金で作られる
。異形の歯車であるが、金型によって作ることができる
。
キャリヤ４は、プラスチック、アルミ、アルミ合金、焼
結合金、亜鉛、鉄などによって作ることができる。
外殻内歯歯車３は、ナイロン６８、ナイロン６またはポ
リプロピレンで作ることができる。
第１図〜第６図の例では、太陽歯車１が抜けないように
、主キャリヤ盤４ａに近い方に遊星小円板部６が、副キ
ャリヤ盤４ｂに近い方に遊星大円板部７が設けられてい
る。
これらの関係は逆にしても良い。もしも逆にすると、組
み立てて後でも太陽歯車１は自由に着脱できるようにな
る。
寸法的なこについて述べる。
遊星歯車２の遊星小円板部６の半径は、遊星歯車の歯底
円半径より、０〜２モジュール小さい。
遊星歯車２の遊星大円板部７の半径は、遊星歯車の面先
円半径より、０〜２モジュール大きい。
外殻内歯歯車３の外殻小内円筒部２６の半径は外殻内歯
歯車の画先円半径より、０〜２モジュール小さい。
外殻内歯歯車３の外殻大内円筒部２７の半径は外殻内歯
面車の歯底円半径より０〜２モジュール大きい。
次に組み立ての工程についてのべる。
１ 第２凸部１１が上向きになるように、副キャリヤ盤
４ｂをテーブルの上に置く。
遊星軸５を遊星軸止穴１６に差し込む。
遊星大円板部７が下になるように、遊星歯車２を遊星軸
５に入れる。
外殻大内円箇部２７が下になるように、外殻内歯歯車３
を遊星歯車２の外側に入れる。
太陽歯車１を少し回しながら、遊星歯車２の中央に入れ
る。
主キャリヤ盤４ａを、位置合わせしながら、副キャリヤ
盤４ｂに嵌込む。
プラグ部１２が窪み２９から突出しているので、これを
上から抑圧してかしめる。DESCRIPTION OF THE PREFERRED EMBODIMENTS The integrated asymmetric planetary wheel device of the present invention will be described below with reference to drawings showing embodiments. 1 is a partially cutaway front view of a planetary gear device according to an embodiment of the present invention, FIG. 2 is a partially cutaway rear view, and FIG. 3 is a sectional view taken along line III in FIG. 1. The planetary gear device includes a sun gear 1, a planet gear 2, an outer shell internal gear 3, a carrier 4, and the like. There is a sun gear 1 in the center. There are four planetary gears 2 surrounding this and meshing with it. The number of planetary gears may be three. Surrounding all these planetary gears 2 is an in-shell gear 3 that meshes with them. The carrier 4 is a combination of a main carrier board 4a and a sub carrier board 4b. The carrier 4 rotatably supports the planetary gear 2 by means of a planetary shaft 5. The main carrier plate 4a has four (or three) first
It has a convex portion 10. Correspondingly, the sub-carrier disk 4b has four (or three) second convex portions 11 on its internal teeth. A plug portion 12 is provided at the tip of the second convex portion 11 of the sub-carrier board 4b.
is formed. A corresponding socket hole 13 is bored in the first convex portion 10 of the main carrier plate 4a. To assemble the carrier 4, insert the plug portion 12 of the sub-carrier board 4b into the socket hole 13 of the main carrier board 4a, and bring the tip out of the recess 29. Then, caulk the tip of the plug part 2. By the action of the caulking end portion 28, the main carrier plate 4a and the sub carrier plate 4b are integrated. This is the case where the main carrier plate 4a1 and the sub carrier plate 4b are made of sintered alloy or die-cast aluminum. When the main carrier plate 4a1 and the sub carrier plate 4b are made of plastic, the end portion 28 of the plug portion 12 is fixed to the socket hole 13 by ultrasonic welding. Four (or three) third convex portions 18 are formed on the back surface of the main carrier disk 4a, each having a planetary shaft fixing hole 16 formed therein. The third protrusion 18 is provided between two adjacent first protrusions 10. Four (or three) fourth convex portions 19 having planetary shaft fixing holes 18 are formed on the back surface of the sub-carrier disk 4b. Both ends of the planetary shaft 5 are connected to a main carrier plate 4a and a sub carrier plate 4.
It is fixed by the planetary shaft fixing holes 18 and 16 of b. Since one of the features of the present invention is the shape of the planetary gear, it will be explained in more detail with reference to the enlarged front view of FIG. 4 and FIG. 5, which is an enlarged front view of only the planetary gear. The planetary gear 2 has a planetary gear g8 in the center, and has a small planetary disk part 6 and a large planetary disk part 7 on the left and right sides. In other words, the planetary gear 2 has an asymmetric structure. The inside of the free gear part 8 is a planetary boss part 9, in which a shaft hole 21 is bored. The planetary shaft 5 is inserted into a shaft through hole 21 of the planetary boss portion 9. The small planetary disk portion 6 is smaller than the root circle of the planetary gear. The large planetary disk portion 7 is larger than the face tip circle of the planetary gear. Moreover, the planetary gear part 8, the small planetary disc part 8, and the large planetary disc part 7
are made integrally with the planetary boss portion 9. It is not separated into three parts. It is one member. This is one of the new points. Such asymmetric planetary gears can be made by plastic injection molding or sintering. Corresponding to the planetary gear 2, the outer shell internal gear 3 also has three parts. The outer shell internal gear 3 has an outer shell gear part 25 at the center, and an outer shell small inner cylindrical part 26 and an outer shell small inner cylindrical part 26 on the left and right sides. The outer shell gear portion 25 meshes with the planetary gear portion 8 of the planetary gear 2 to transmit rotational torque. The small planetary disk part 6 of the planetary wheel 2 contacts and rolls on the small inner cylindrical part 26 of the outer shell. Of course, there are gaps in the transfer aspect, and there are times when the two parties come into contact, and times when there is no contact. Similarly, the large planetary disk portion 7 of the planetary gear 2 comes into contact with the outer shell large inner cylindrical portion 27 . There is also a gap in this transfer aspect, and sometimes there is contact between the two parties, and sometimes there is no contact. Due to the contact between the outer shell small inner cylindrical portion 26 and the planetary small disk portion 6 and the contact between the outer shell large inner cylindrical portion 27 and the planetary large disk portion 7, radial force is applied from the planetary gear 2 to the outer shell inner tooth. This is transmitted to gear 3. The sun rover 1 has a sun shaft hole 14 formed with splines, serrations, or a D-shaped hole. The boss portion of the main carrier plate 4a of the carrier 4 is thick, and a carrier shaft hole 15 is bored in the axial direction. A rotation prevention mechanism such as a spline or serration is also formed in the carrier shaft hole 15. When using this as a decelerator, insert the input shaft into the sun shaft hole 14 and the output shaft into the carrier shaft hole 15. When used as a speed increaser, the output shaft is inserted into the sun shaft hole 14 and the input shaft of the carrier shaft hole 15 is inserted. The outer shell internal gear 3 must be fixed to a casing or the like. In order to prevent rotation, in this example, mtB vehicle 3 in the outer shell
Several anti-rotation protrusions 31 are formed on a cylindrical portion 32 whose outer periphery is flat. This is just one example. Other structures can be arbitrarily employed to secure the outer shell internal gear 3. A hole may be formed in the axial direction so that it can be screwed or pinned. In the illustrated example, the anti-rotation convex portion 31 is located away from the center line. The surface on which the torque is applied and the surface on which the anti-rotation protrusion is present are separated. During this time, the outer shell internal gear is twisted. This has the effect of absorbing sudden large shocks. Further, the toothed roller 3 in the outer shell is integrally molded from nylon 68, nylon 6, or polypropylene. It is more flexible than polyacetal and is effective in suppressing vibration and noise. In the example shown in FIG. 3, in order to suppress displacement of the planetary gear 2 in the axial direction, a third convex portion 16 and a fourth convex portion 19 are provided on both sides of the planetary boss portion 9. The sun gear 1 is retracted by the planetary large disk portion 7 of the planetary gear 2. On the opposite side of the sun gear 1, displacement in the axial direction is prohibited by the bulged inner boss portion 22 of the main carrier disk 4a. The sun gear 1 is thus kept in the correct axial position. In this example, the main carrier disk 4a is made larger than the outer small inner cylindrical portion 26 of the outer shell internal gear 3 to prevent the carrier 4 from slipping out from the outer shell internal gear 3 to the left. FIG. 6 is a partial vertical sectional view of a planetary gear device showing another embodiment. The basic structure is the same as the previous example. In order to prevent displacement of the planetary gear 2 in the axial direction, circumferential protrusions 38 and 3 are provided on the back surfaces of the main carrier plate 4a and the sub carrier plate 4b.
7. planetary small disk portion 8 of the planetary gear 2;
The side surface of the planetary large disk portion 7 is the circumferential protrusion 38 of the carrier 4,
37, the planetary gear 2 is kept in the correct position in the axial direction. In addition, in this example, the external shell internal gear has three bolt holes in the axial direction.
8 is punched. The outer shell internal gear 3 is fixed to the casing by passing a bolt here. The sun gear 1 can be made of plastic, sintered alloy, zinc or iron, etc. The planetary gear 2 is made of plastic or sintered alloy. Although it is an oddly shaped gear, it can be made using a mold. The carrier 4 can be made of plastic, aluminum, aluminum alloy, sintered alloy, zinc, iron, etc. The outer shell internal gear 3 can be made of nylon 68, nylon 6 or polypropylene. In the example shown in FIGS. 1 to 6, in order to prevent the sun gear 1 from coming off, the small planetary disk portion 6 is placed closer to the main carrier disk 4a, and the large planetary disk portion 7 is placed closer to the sub-carrier disk 4b. is provided. These relationships may be reversed. If it is reversed, the sun gear 1 can be freely attached and detached even after assembly. Let's talk about dimensions. The radius of the small planetary disk portion 6 of the planetary gear 2 is 0 to 2 modules smaller than the radius of the bottom circle of the planetary gear. The radius of the planetary large disk portion 7 of the planetary gear 2 is 0 to 2 modules larger than the radius of the face tip of the planetary gear. The radius of the outer shell small inner cylindrical portion 26 of the outer shell internal gear 3 is 0 to 2 modules smaller than the tip circle radius of the outer shell internal gear. The radius of the outer shell large inner cylindrical portion 27 of the outer shell internal gear 3 is 0 to 2 modules larger than the root circle radius of the outer shell internal gear surface. Next, I will talk about the assembly process. 1. Place the sub carrier board 4b on the table so that the second convex portion 11 faces upward. Insert the planetary shaft 5 into the planetary shaft fixing hole 16. Insert the planetary gear 2 into the planetary shaft 5 so that the planetary large disk portion 7 is at the bottom. Place the outer shell internal gear 3 so that the outer shell large inner circular part 27 is on the bottom.
Put it on the outside of planetary gear 2. While rotating the sun gear 1 a little, insert it into the center of the planet gear 2. The main carrier board 4a is fitted into the sub carrier board 4b while being aligned. Since the plug portion 12 protrudes from the recess 29, it is pressed and caulked from above.
遊星歯車を一体のものとして作ることができる。なぜ一
体化できるかというのは、断面図と第５図を見れば分か
る。遊星ギヤ部８の一方が歯底円より小さい遊星小円板
部６となり他方が歯先円より大きい遊星大円板部７とな
っている。このような形状であるので、二つ割りの金型
で、射出成形により、遊星画車を作ることができる。第
７図、第８図のような遊星歯車は一体に成形出来ない。
一体化できるので、材料コストが低減するし、組み立て
コストも減少する。より安価な遊星歯車装置を提供する
ことができる。
外殻内歯歯車が柔軟な材料であるナイロン６８、ナイロ
ン６またはポリブロビレンで作られるので、過大な圧力
が掛かったときなど、適宜撓み、圧力を好適に緩和する
ことができる。振動、騒音の少ない遊星歯車装置を提供
でき。この点を確かめるために、次のような実験を行っ
た。
ナイロン６Ｂ、ナイロン８、ポリビロピレン、ポリアセ
タールで外殻内歯歯車を成形しその他は同じである遊星
画車装置を作製した。外殻内歯歯車の外径は７５ｍｍで
、歯車のモジュールは０．７５である。外殻内歯歯車の
歯数は７５枚で、減速比は４．８である。太陽画車歯数
は２０枚、遊星歯車画数は２８枚である。太陽歯車は焼
結合金、遊星歯車はボリアセタールである。これを洗濯
機に組込み４ｋｇの洗濯物を入れて実際に洗沼をし、１
ｍ離隔したところで騒音を測定した。試験体の数は１０
である。結果を第１表に示す。
第１表洗沼機に組込んだ遊星歯車装置の騒音測定これら
の結果から、ポリアセタールの場合より約４〜６ホン程
度騒音が低くなっていることが分かる。
半径方向の力は遊星大円板部７と外殻大内円筒部２７と
の間、遊星小円板部６と外殻小内円筒部２６との間で伝
達される。このため歯と歯が強く噛合うということがな
い。遠心力や寸法の不正、不均等な力が加わっても、円
板と円筒部の作用で、円滑な回転をすることができる。Planetary gears can be made as one piece. The reason why they can be integrated can be seen by looking at the cross-sectional view and Figure 5. One of the planetary gear parts 8 is a small planetary disc part 6 smaller than the root circle of the tooth, and the other is a large planetary disc part 7 which is larger than the tip circle. Because of this shape, the planet wheel can be made by injection molding using a two-piece mold. Planetary gears like those shown in FIGS. 7 and 8 cannot be molded in one piece. Integration reduces material costs and assembly costs. A cheaper planetary gear device can be provided. Since the outer shell internal gear is made of a flexible material such as nylon 68, nylon 6, or polypropylene, it can flex appropriately and relieve the pressure appropriately when excessive pressure is applied. We can provide planetary gears with less vibration and noise. In order to confirm this point, we conducted the following experiment. A planetary wheel device was manufactured in which the outer shell internal gear was molded from nylon 6B, nylon 8, polyviropyrene, and polyacetal, and the other aspects were the same. The outer diameter of the outer shell internal gear is 75 mm, and the gear module is 0.75. The number of teeth of the outer shell internal gear is 75, and the reduction ratio is 4.8. The number of teeth on the sun wheel is 20, and the number of strokes on the planetary gear is 28. The sun gear is made of sintered alloy, and the planetary gears are made of boriacetal. I installed this in a washing machine, put 4kg of laundry in it, and actually washed it.
Noise was measured at a distance of m. The number of specimens is 10
It is. The results are shown in Table 1. Table 1: Noise measurement of a planetary gear system installed in a swamp washer. From these results, it is clear that the noise is about 4 to 6 phons lower than in the case of polyacetal. The radial force is transmitted between the large planetary disk portion 7 and the large inner cylindrical portion 27 of the outer shell, and between the small planetary disk portion 6 and the small inner cylindrical portion 26 of the outer shell. For this reason, the teeth do not mesh tightly together. Even if centrifugal force, incorrect dimensions, or uneven forces are applied, the disk and cylindrical portion allow for smooth rotation.
第１図は本発明の実施例に掛かる遊星歯車装置の一部切
り欠き正面図。
第２図は同じ物の一部切り欠き背面図。
第３図は第１図中の■−■断面図。
第４図は第３図のうち遊星歯車の部分のみの拡大断面図
。
第５図は遊星面車のみの正面図。
第６図は他の実施例を示す遊星歯車近傍のみの断面図。
第７図は従来例にかかる歯先円方式の遊星歯車断面図。
第８図は従来例にかかるピッチ円方式の遊星歯車断面図
。
１●●●−●太陽歯車
２●●拳●●遊星歯車
３●●●●●外殻内歯歯車
４１１●キャリヤ
２ ６ ●
２７拳
２ ８ ●
２ ９ ●
３ ０ φ
発明者FIG. 1 is a partially cutaway front view of a planetary gear device according to an embodiment of the present invention. Figure 2 is a partially cutaway rear view of the same item. FIG. 3 is a sectional view taken along the line ■-■ in FIG. FIG. 4 is an enlarged sectional view of only the planetary gear portion of FIG. 3. Figure 5 is a front view of only the planetary trolley. FIG. 6 is a sectional view of only the vicinity of the planetary gear, showing another embodiment. FIG. 7 is a sectional view of a conventional planetary gear of the tooth tip circle type. FIG. 8 is a sectional view of a pitch circle type planetary gear according to a conventional example. 1●●●−●Sun gear 2●●Fist●●Planetary gear 3●●●●●Outer shell internal gear 411●Carrier 2 6 ● 27 Fist 2 8 ● 2 9 ● 3 0 φ Inventor
Claims (1)
遊星歯車２と、これらに噛合する外殻内歯歯車３と、遊
星歯車２を遊星軸５によって軸支し回転自在に設けられ
たキャリヤ４とよりなる遊星歯車装置に於いて、遊星歯
車２は中央に遊星ギヤ部８、その側方に歯底円より小さ
い遊星小円板部８、反対側に歯先円より大きい遊星大円
板部７を有し、遊星ギヤ部８、遊星小円板部６、遊星大
円板部７は、軸通し穴２１を穿った遊星ボス部９ととも
に一体形成されており、外殻内歯歯車３は、中央に前記
遊星ギヤ部８に噛合する外殻ギヤ部２５、側方に歯先円
より小さい外殻小内円筒部２６、反対側に歯底円より大
きい外殻大内円筒部２７を有し、外殻ギヤ部２５と外殻
小内円筒部２６と外殻大内円筒部２７とはナイロン、ま
たはポリプロピレンにより一体形成されており、遊星小
円板部６は外殻小内円筒部２６に接触転動し、遊星大円
板部７は外殻大内円筒部２７に接触転動する事を特徴と
する一体型非対称遊星歯車装置。 （２）遊星小円板部６の半径は、遊星歯車の歯底円半径
より０〜２モジュール小さく、外殻小内円筒部２６の半
径は外殻内歯歯車の歯先円半径より０〜２モジュール小
さい事を特徴とする請求項１記載の一体型非対称遊星歯
車装置。 （３）遊星大円板部７の半径は、遊星歯車の歯先円半径
より０〜２モジュール大きく、外殻大内円筒部２７の半
径は外殻内歯歯車の歯底円半径より０〜２モジュール大
きい事を特徴とする請求項２記載の一体型非対称遊星歯
車装置。 （４）キャリヤ４は出力軸を結合すべきキャリヤ軸孔１
５を有する主キャリヤ盤４ａと、広い開口を有する副キ
ャリヤ盤４ｂとよりなり、遊星大円板部７及び外殻大内
円筒部２７が副キャリヤ盤４ｂに近い側方に設けられて
いる事を特徴とする請求項３記載の一体型非対称遊星歯
車装置。 （５）キャリヤ４は出力軸を結合すべきキャリヤ軸孔１
５を有する主キャリヤ盤４ａと、広い開口を有する副キ
ャリヤ盤４ｂとよりなり、遊星大円板部７及び外殻大内
円筒部２７が主キャリヤ盤４ａに近い側方に設けられて
いる事を特徴とする請求項３記載の一体型非対称遊星歯
車装置。 （６）主キャリヤ盤４ａは内方に膨出した内ボス部２２
を有し、内ボス部２２は太陽歯車１の軸方向の変位を禁
ずるようにした事を特徴とする請求項４または５に記載
の一体型非対称遊星歯車装置。 （７）外殻内歯歯車３は外周部に平坦な平円筒面３２と
、いくつかの廻り止め突部３１を有し、廻り止め突部３
１は、外殻内歯歯車の中心線から外れた位置に設けられ
ていることを特徴とする請求項６に記載の一体型非対称
遊星歯車装置（８）遊星歯車２がプラスチックまたは焼
結合金であることを特徴とする請求項７に記載の一体型
非対称遊星歯車装置。 （９）主キャリヤ盤４ａ、副キャリヤ盤４ｂが内方に膨
出した第３凸部１８、第４凸部１９を有し、これら凸部
１８、１９に穿った遊星軸止穴１６によって遊星軸５の
両端を固定した事を特徴とする請求項８に記載の一体型
非対称遊星歯車装置。[Scope of Claims] (1) A sun gear 1, an appropriate number of planetary gears 2 that mesh with the sun gear 1, an outer shell internal gear 3 that meshes with these, and the planetary gears 2 are connected by a planetary shaft 5. In a planetary gear device consisting of a carrier 4 that is supported and rotatably provided, the planetary gear 2 has a planetary gear part 8 in the center, a small planetary disk part 8 smaller than the tooth root circle on the side, and a small planetary disk part 8 on the opposite side. The planetary gear part 8, the small planetary disc part 6, and the large planetary disc part 7 are integrally formed with a planetary boss part 9 having a shaft through hole 21. The outer shell internal gear 3 has an outer shell gear part 25 in the center that meshes with the planetary gear part 8, an outer shell small inner cylindrical part 26 smaller than the tooth tip circle on the side, and a tooth root circle on the opposite side. It has a larger outer shell inner cylindrical part 27, and the outer shell gear part 25, the outer shell small inner cylindrical part 26, and the outer shell large inner cylindrical part 27 are integrally formed of nylon or polypropylene. The integrated asymmetric planetary gear device is characterized in that the plate portion 6 rolls in contact with an outer shell small inner cylindrical portion 26, and the planetary large disk portion 7 contacts and rolls on an outer shell large inner cylindrical portion 27. (2) The radius of the small planetary disk portion 6 is 0 to 2 modules smaller than the root circle radius of the planetary gear, and the radius of the outer shell small inner cylindrical portion 26 is 0 to 2 modules smaller than the tip circle radius of the outer shell internal gear. The integrated asymmetric planetary gear set according to claim 1, characterized in that it is two modules smaller. (3) The radius of the large planetary disk portion 7 is 0 to 2 modules larger than the tip circle radius of the planetary gear, and the radius of the outer shell large inner cylindrical portion 27 is 0 to 2 modules larger than the tooth bottom radius of the outer shell internal gear. 3. The integrated asymmetric planetary gear set according to claim 2, characterized in that it is two modules larger. (4) Carrier 4 is carrier shaft hole 1 to which the output shaft is to be connected
5, and a sub carrier plate 4b having a wide opening, and the planetary large disk part 7 and the outer shell large inner cylindrical part 27 are provided on the side close to the sub carrier plate 4b. The integrated asymmetric planetary gear system according to claim 3, characterized in that: (5) The carrier 4 is the carrier shaft hole 1 to which the output shaft is to be connected.
5, and a sub-carrier plate 4b having a wide opening, and the planetary large disk part 7 and the outer shell large inner cylindrical part 27 are provided on the side near the main carrier plate 4a. The integrated asymmetric planetary gear system according to claim 3, characterized in that: (6) The main carrier plate 4a has an inner boss portion 22 that bulges inward.
6. The integrated asymmetric planetary gear device according to claim 4, wherein the inner boss portion 22 prohibits displacement of the sun gear 1 in the axial direction. (7) The outer shell internal gear 3 has a flat cylindrical surface 32 on the outer periphery and several anti-rotation protrusions 31, and the anti-rotation protrusions 3
7. The integrated asymmetric planetary gear device according to claim 6, wherein the planetary gear 2 is made of plastic or sintered alloy. 8. An integrated asymmetric planetary gear system according to claim 7, characterized in that: (9) The main carrier disk 4a and the sub-carrier disk 4b have a third convex portion 18 and a fourth convex portion 19 that bulge inward, and the planetary shaft is fixed by the planetary shaft fixing hole 16 bored in these convex portions 18 and 19. The integrated asymmetric planetary gear device according to claim 8, characterized in that both ends of the shaft (5) are fixed.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1113924A JPH02292550A (en) | 1989-05-06 | 1989-05-06 | Integral type asymmetrical planetary gear |
| GB8914745A GB2232454B (en) | 1989-05-06 | 1989-06-27 | Planetary gearing assembly |
| AU41001/89A AU617859B2 (en) | 1989-05-06 | 1989-09-01 | Unified asymmetric planetary gear assembly |
| CA000610245A CA1324007C (en) | 1989-05-06 | 1989-09-01 | Unified asymmetric planetary gear assembly |
| SG34194A SG34194G (en) | 1989-05-06 | 1994-03-07 | Planetary gearing assembly |
| HK81694A HK81694A (en) | 1989-05-06 | 1994-08-11 | Planetary gearing assembly |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1113924A JPH02292550A (en) | 1989-05-06 | 1989-05-06 | Integral type asymmetrical planetary gear |
| CA000610245A CA1324007C (en) | 1989-05-06 | 1989-09-01 | Unified asymmetric planetary gear assembly |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02292550A true JPH02292550A (en) | 1990-12-04 |
Family
ID=25672999
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1113924A Pending JPH02292550A (en) | 1989-05-06 | 1989-05-06 | Integral type asymmetrical planetary gear |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPH02292550A (en) |
| AU (1) | AU617859B2 (en) |
| CA (1) | CA1324007C (en) |
| GB (1) | GB2232454B (en) |
| HK (1) | HK81694A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102588561A (en) * | 2011-01-17 | 2012-07-18 | 日本电产新宝株式会社 | Transmission box body |
| JP2014001816A (en) * | 2012-06-19 | 2014-01-09 | Sumitomo Heavy Ind Ltd | Planetary gear device |
| CN103899501A (en) * | 2009-12-18 | 2014-07-02 | 诺迈士科技有限公司 | Gear box and module, shaft, wind turbine, and assembling method thereof |
| CN107810076A (en) * | 2015-06-24 | 2018-03-16 | 佩朗股份有限公司 | Portable power tool including epicyclic reduction gear |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4421931A1 (en) * | 1994-06-23 | 1996-01-11 | Ford Werke Ag | Planet carrier |
| DE19542779B4 (en) * | 1995-11-16 | 2005-04-14 | Horst Scholz Gmbh & Co. Kg | transmission |
| JP4665516B2 (en) * | 2004-12-28 | 2011-04-06 | トヨタ自動車株式会社 | Planetary gear mechanism and manufacturing method thereof |
| CA2610045A1 (en) * | 2007-11-07 | 2009-05-07 | Marcel Durand | Planetary gear transmission for an engine system |
| EP2402631B1 (en) * | 2010-06-29 | 2014-01-15 | Siemens Aktiengesellschaft | Planetary gear for a main loading direction |
| DE102013205432B4 (en) * | 2013-03-27 | 2023-03-30 | Schaeffler Technologies AG & Co. KG | Planetary gear arrangement with at least two planetary sets arranged axially next to one another |
| EP3812626A1 (en) * | 2019-10-24 | 2021-04-28 | Flender GmbH | Planetary gear, especially multiplanetary gear, for a wind power plant |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6127337A (en) * | 1984-07-19 | 1986-02-06 | Matetsukusu Kk | Asymmetrical planetry gear device |
| JPH0674835B2 (en) * | 1986-03-27 | 1994-09-21 | マテックス株式会社 | Casing mounting structure for planetary gear unit |
-
1989
- 1989-05-06 JP JP1113924A patent/JPH02292550A/en active Pending
- 1989-06-27 GB GB8914745A patent/GB2232454B/en not_active Expired - Lifetime
- 1989-09-01 AU AU41001/89A patent/AU617859B2/en not_active Ceased
- 1989-09-01 CA CA000610245A patent/CA1324007C/en not_active Expired - Fee Related
-
1994
- 1994-08-11 HK HK81694A patent/HK81694A/en not_active IP Right Cessation
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103899501A (en) * | 2009-12-18 | 2014-07-02 | 诺迈士科技有限公司 | Gear box and module, shaft, wind turbine, and assembling method thereof |
| CN102588561A (en) * | 2011-01-17 | 2012-07-18 | 日本电产新宝株式会社 | Transmission box body |
| TWI465656B (en) * | 2011-01-17 | 2014-12-21 | Nidec Shimpo Corp | Transmission case |
| JP2014001816A (en) * | 2012-06-19 | 2014-01-09 | Sumitomo Heavy Ind Ltd | Planetary gear device |
| CN103511559A (en) * | 2012-06-19 | 2014-01-15 | 住友重机械工业株式会社 | Planetary gear device |
| CN107810076A (en) * | 2015-06-24 | 2018-03-16 | 佩朗股份有限公司 | Portable power tool including epicyclic reduction gear |
| JP2018521868A (en) * | 2015-06-24 | 2018-08-09 | ペランク （ソシエテ アノニム）Ｐｅｌｌｅｎｃ （Ｓｏｃｉｅｔｅ Ａｎｏｎｙｍｅ） | Portable power tool having planetary gear reduction device |
| CN107810076B (en) * | 2015-06-24 | 2020-06-12 | 佩朗股份有限公司 | Portable electric tool comprising an epicyclic reduction gear |
Also Published As
| Publication number | Publication date |
|---|---|
| AU4100189A (en) | 1991-03-07 |
| GB2232454B (en) | 1993-10-13 |
| CA1324007C (en) | 1993-11-09 |
| GB2232454A (en) | 1990-12-12 |
| AU617859B2 (en) | 1991-12-05 |
| HK81694A (en) | 1994-08-19 |
| GB8914745D0 (en) | 1989-08-16 |
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