JPH081314Y2 - Double inversion shaft power transmission device - Google Patents
Double inversion shaft power transmission deviceInfo
- Publication number
- JPH081314Y2 JPH081314Y2 JP1989086884U JP8688489U JPH081314Y2 JP H081314 Y2 JPH081314 Y2 JP H081314Y2 JP 1989086884 U JP1989086884 U JP 1989086884U JP 8688489 U JP8688489 U JP 8688489U JP H081314 Y2 JPH081314 Y2 JP H081314Y2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- planetary gear
- gear
- propeller
- propeller 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
Landscapes
- Retarders (AREA)
Description
【考案の詳細な説明】 ［産業上の利用分野］ 本考案は、主機の出力軸に連結された内側プロペラ軸
から遊星歯車式動力反転装置を介して外側プロペラ軸に
駆動力を伝達する二重反転軸の動力伝達装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention is a dual structure for transmitting a driving force from an inner propeller shaft connected to an output shaft of a main engine to an outer propeller shaft via a planetary gear type power reversing device. The present invention relates to a power transmission device for an inversion shaft.
［従来の技術］ 船舶に使用される二重反転軸の動力伝達装置は、第５
図に示すように、主機１の出力軸２に中間軸2aを介して
船尾側プロペラ４を駆動する内側プロペラ軸５が連結さ
れている。この内側プロペラ軸５には、これを囲繞して
同心状に太陽歯車８の軸９が設けられている。この太陽
歯車８の軸９は、弾性継手10を介して内側プロペラ軸５
に連結されている。太陽歯車８には一次遊星歯車11が噛
合されている。その一次遊星歯車11には同軸上に二次遊
星歯車12が一体で取り付けられている。二次遊星歯車12
は、一次遊星歯車11に対してその歯数が大きく形成され
る。二次遊星歯車12には、外側プロペラ軸７に取り付け
られた歯車13と噛合する内歯歯車14が噛合されており、
この内歯歯車14を介して、船首側プロペラ６を駆動する
外側プロペラ軸７を、内側プロペラ軸５とほぼ同じ回転
数で反転させるようになっている。[Prior Art] The power transmission device of the counter-rotating shaft used in a ship is the fifth one.
As shown in the figure, an inner propeller shaft 5 for driving a stern side propeller 4 is connected to an output shaft 2 of a main engine 1 via an intermediate shaft 2a. The inner propeller shaft 5 is provided with a shaft 9 of a sun gear 8 concentrically surrounding the inner propeller shaft 5. The shaft 9 of the sun gear 8 is connected to the inner propeller shaft 5 via an elastic joint 10.
It is connected to. A primary planetary gear 11 is meshed with the sun gear 8. The secondary planetary gear 12 is coaxially mounted integrally with the primary planetary gear 11. Secondary planetary gear 12
Has a larger number of teeth than the primary planetary gear 11. An internal gear 14 that meshes with a gear 13 attached to the outer propeller shaft 7 is meshed with the secondary planetary gear 12,
Through this internal gear 14, the outer propeller shaft 7 that drives the bow side propeller 6 is reversed at substantially the same number of revolutions as the inner propeller shaft 5.
［考案が解決しようとする課題］ 第５図に示すように、一般に主機１およびプロペラ4,
6を含む動力伝達系は、主機１における爆発起振力によ
って振動が発生している。この振動は、第６図に示すよ
うに動力伝達系固有の振動数で共振点（ピーク）を持つ
ことになり、特に、動力伝達系に弾性継手10を設けない
場合には、第６図に示すように、主機１の常用回転数付
近において振動トルクがピーク（図中、実線Ｂで示す）
となり、その振動トルクが、平均伝達トルクを大巾に越
えることになる。このため歯車の噛合い部において、振
動トルクによって歯がたたかれる、いわゆるチャタリン
グ現象が発生し、この回転領域での連続使用ができなく
なる。これを避けるために、第５図に示すように、弾性
継手10を設けて上記振動を吸収し、第４図中Ａで示すよ
うに、回転数の低い領域に振動トルクのピークを存在さ
せるようにすると共に、このピーク値を小さい値にする
ことが考えられている。[Problems to be Solved by the Invention] As shown in FIG. 5, in general, the main engine 1 and the propeller 4,
The power transmission system including 6 is vibrating due to the explosion vibration force in the main engine 1. This vibration has a resonance point (peak) at a frequency peculiar to the power transmission system as shown in FIG. 6. Especially, when the elastic joint 10 is not provided in the power transmission system, the vibration is shown in FIG. As shown, the vibration torque peaks near the normal rotation speed of the main engine 1 (shown by the solid line B in the figure).
Therefore, the vibration torque greatly exceeds the average transmission torque. For this reason, in the meshing portion of the gear, a so-called chattering phenomenon occurs, in which the teeth are beaten by the vibration torque, and continuous use in this rotation region becomes impossible. In order to avoid this, as shown in FIG. 5, an elastic joint 10 is provided to absorb the above vibration, and as shown by A in FIG. 4, a peak of the vibration torque exists in a low rotational speed region. In addition to this, it is considered to reduce this peak value.
しかしながら、第５図に示すように、弾性継手10は、
内側プロペラ軸５の回転を太陽歯車８の軸９に伝達する
動力の導入部近傍に設けられているので、大きいトルク
がかかり、その大トルクに耐えるに相当する弾性継手10
を備えなければならない。特に、大馬力の船舶において
は、弾性継手10に巨大なトルクがかかり、このトルクに
対応する弾性継手10を用いると、弾性継手10は巨大な外
形寸法と重量になりその装着が技術的に困難である。However, as shown in FIG. 5, the elastic joint 10
Since it is provided in the vicinity of the introduction part of the power for transmitting the rotation of the inner propeller shaft 5 to the shaft 9 of the sun gear 8, a large torque is applied, and an elastic joint 10 equivalent to withstanding the large torque
Must be equipped. Particularly, in a large horsepower ship, a huge torque is applied to the elastic joint 10, and when the elastic joint 10 corresponding to this torque is used, the elastic joint 10 has a huge outer size and weight, and its mounting is technically difficult. Is.
また、弾性継手10を第５図に示すような箇所に設ける
と、弾性継手10の定期的メンテナンスを行う際、遊星歯
車装置３のハウジングを取り外し、歯車類を取り外しさ
らに船尾側プロペラ４および内側プロペラ軸５を船尾方
向に移動させて弾性継手を取り外さなければならず、そ
の作業が広範囲になる。Further, when the elastic joint 10 is provided at a position as shown in FIG. 5, the housing of the planetary gear unit 3 is removed and the gears are removed when the elastic joint 10 is regularly maintained, and the stern side propeller 4 and the inner propeller are removed. It is necessary to move the shaft 5 in the stern direction to remove the elastic joint, which results in a wide range of work.
本考案は上記問題点を有効に解決すべく創案されたも
ので、その目的は、遊星歯車装置の一次遊星歯車と二次
遊星歯車とを弾性継手で連結することにより、弾性継手
を小容量にしてコンパクト化し、かつ、そのメンテナン
スを容易にする二重反転軸の動力伝達装置を提供するこ
とにある。The present invention was devised to effectively solve the above problems, and its purpose is to reduce the capacity of an elastic joint by connecting the primary planetary gear and the secondary planetary gear of the planetary gear device with the elastic joint. (EN) Provided is a power transmission device of a contra-rotating shaft, which is compact and easy to maintain.
［課題を解決するための手段］ 上記目的を達成するために本考案は、主機の出力軸に
船尾側プロペラを駆動する内側プロペラ軸を連結すると
共に、その内側プロペラ軸と船首側プロペラを駆動する
外側プロペラ軸とを遊星歯車式動力反転装置を介して連
結した二重反転軸の動力伝達装置において、上記内側プ
ロペラ軸に太陽歯車を固定し、該太陽歯車の外周に一次
遊星歯車を噛合し、該一次遊星歯車に主機側に延長され
軸心に沿って挿通孔が形成された一次遊星歯車軸を設
け、他方上記外側プロペラ軸に内歯歯車を一体的に連結
し、該内歯歯車の内周に二次遊星歯車を噛合し、該二次
遊星歯車に主機側に延長された二次遊星歯車軸を設け、
該二次遊星歯車軸を上記一次遊星歯車軸の挿通孔に船尾
側から主機側へ向けて挿通すると共に、主機側に突出し
た一次遊星歯車軸の端部と二次遊星歯車軸の端部との間
に、これらを連結すべく放射状に配置された複数の弾性
片からなる弾性継手を設けて構成したものである。[Means for Solving the Problems] In order to achieve the above object, the present invention connects an inner propeller shaft that drives a stern side propeller to an output shaft of a main engine, and drives the inner propeller shaft and a bow side propeller. In a power transmission device of a double reversal shaft connected to the outer propeller shaft via a planetary gear type power reversal device, the sun gear is fixed to the inner propeller shaft, and the primary planetary gear is meshed with the outer periphery of the sun gear, The primary planetary gear shaft is provided with a primary planetary gear shaft that is extended to the main machine side and has an insertion hole formed along the axial center, and on the other hand, an internal gear is integrally connected to the outer propeller shaft, and the internal gear A secondary planetary gear is meshed with the circumference, and a secondary planetary gear shaft extended to the main machine side is provided on the secondary planetary gear,
The secondary planetary gear shaft is inserted through the insertion hole of the primary planetary gear shaft from the stern side toward the main engine side, and the end portion of the primary planetary gear shaft protruding toward the main engine side and the end portion of the secondary planetary gear shaft are provided. An elastic joint composed of a plurality of elastic pieces radially arranged to connect them is provided between the two.
［作用］ 上記構成によれば、駆動力は主機の出力軸から内側プ
ロペラ軸へ伝達されて船尾側プロペラを回転させる一
方、内側プロペラ軸から遊星歯車式動力反転装置を介し
て外側プロペラ軸へ伝達し、船首側プロペラを反対方向
に回転させる。この動力の伝達の際、遊星歯車式動力装
置に伝達される振動トルクは、弾性継手により吸収され
ると共に、弾性継手は、振動系の共振点（ピーク）を回
転数の低い領域に移行させると共に、そのピーク値を極
めて低くする。したがって、主機の常用回転数領域から
遊星歯車式動力反転装置のチャタリングの発生をなくす
ことができる。また、弾性継手は、一次遊星歯車と二次
遊星歯車とを連結するから、弾性継手に加わるトルク
は、一次および二次遊星歯車の数および太陽歯車との歯
数比によって分散される小さなトルクになる。これによ
り弾性継手は、このトルクに対応させて小さくできコン
パクト化が図れる。また、弾性継手が一次遊星歯車軸と
二次遊星歯車軸との主機側に突出した端部に設けられる
ため、弾性継手のメンテナンスの際には、遊星歯車式動
力反転装置のハウジングの一部を取り外すだけでプロペ
ラ軸を移動することなく弾性継手を取外すことができ、
そのメンテナンス作業がきわめて容易になる。[Operation] According to the above configuration, the driving force is transmitted from the output shaft of the main engine to the inner propeller shaft to rotate the stern side propeller, while the inner propeller shaft is transmitted to the outer propeller shaft via the planetary gear type power reversing device. Then, rotate the bow propeller in the opposite direction. At the time of transmission of this power, the vibration torque transmitted to the planetary gear type power unit is absorbed by the elastic joint, and the elastic joint shifts the resonance point (peak) of the vibration system to a region of low rotational speed. , Make its peak value extremely low. Therefore, the occurrence of chattering in the planetary gear type power reversal device can be eliminated from the normal rotation speed range of the main engine. Further, since the elastic joint connects the primary planetary gear and the secondary planetary gear, the torque applied to the elastic joint is a small torque dispersed by the number of primary and secondary planetary gears and the tooth ratio with the sun gear. Become. As a result, the elastic joint can be made smaller and more compact according to this torque. Further, since the elastic joint is provided at the ends of the primary planetary gear shaft and the secondary planetary gear shaft that protrude toward the main machine side, part of the housing of the planetary gear type power reversing device can be used during maintenance of the elastic joint. You can remove the elastic joint without moving the propeller shaft just by removing it.
The maintenance work becomes extremely easy.
［実施例］ 本考案の一実施例を図面に基づいて説明する。Embodiment An embodiment of the present invention will be described with reference to the drawings.
第１図において、１は主機で、この主機１の出力軸２
には、船尾側プロペラ４を駆動する内側プロペラ軸５が
連結される。また遊星歯車式動力反転装置３は、上記内
側プロペラ軸５を囲繞する外側プロペラ軸７に、上記出
力軸２からの動力を反転させて伝達するようになってい
る。すなわち、内側プロペラ軸５には、この内側プロペ
ラ軸５と一体的に回転する太陽歯車８が取り付けられて
いる。なお、主機出力軸２と内側プロペラ軸５との連結
は上述の構成に限定されるものではなく、主機出力軸２
と内側プロペラ軸５との間に中間軸を設けても構わな
い。第１図及び第２図に示すように太陽歯車８の外周に
は、円周方向に適宜間隔をおいて配列された一次遊星歯
車11が噛合される。これら一次遊星歯車11は、その軸心
上に一次遊星歯車軸17が一体的に設けられており、この
一次遊星歯車軸17の主機１側の端部は、支持枠部材16に
軸受部材16aを介して回転自在に支承されている。一次
遊星歯車11および一次遊星歯車軸17の軸内部には軸挿入
孔17aが形成されており、この軸挿入孔17a内には、軸受
部材17bが一体的に挿入される。軸受部材17b内には二次
遊星歯車軸19が回転自在な状態で挿入されている。各二
次遊星歯車軸19は、その他端部が支持枠部材20に軸受部
材20aを介して回転自在に支承されていると共に、各二
次遊星歯車軸19には、一次遊星歯車11の歯数より大きい
歯数を有する二次遊星歯車12がそれぞれ一体的に設けら
れている。各二次遊星歯車12は、上記内側プロペラ軸５
を囲繞する内歯歯車14に噛合され、内歯歯車14は、上記
外側プロペラ軸７と一体の歯車13に噛合される。なお二
次遊星歯車12の歯数は、外側プロペラ軸７と内側プロペ
ラ軸５とをほぼ同じ回転数で相互に反転させることが可
能な歯数で形成される。In FIG. 1, 1 is a main engine, and an output shaft 2 of this main engine 1
An inner propeller shaft 5 for driving the stern side propeller 4 is connected to the. The planetary gear type power reversing device 3 is adapted to invert and transmit the power from the output shaft 2 to the outer propeller shaft 7 surrounding the inner propeller shaft 5. That is, the sun gear 8 that rotates integrally with the inner propeller shaft 5 is attached to the inner propeller shaft 5. The connection between the main engine output shaft 2 and the inner propeller shaft 5 is not limited to the above-described configuration, and the main engine output shaft 2
An intermediate shaft may be provided between the inner propeller shaft 5 and the inner propeller shaft 5. As shown in FIGS. 1 and 2, the outer periphery of the sun gear 8 is meshed with a primary planetary gear 11 arranged at appropriate intervals in the circumferential direction. A primary planetary gear shaft 17 is integrally provided on the axial center of each of these primary planetary gears 11. The end portion of the primary planetary gear shaft 17 on the main machine 1 side has a support frame member 16 and a bearing member 16a. It is rotatably supported via. A shaft insertion hole 17a is formed inside the shafts of the primary planetary gear 11 and the primary planetary gear shaft 17, and a bearing member 17b is integrally inserted into the shaft insertion hole 17a. A secondary planetary gear shaft 19 is rotatably inserted in the bearing member 17b. The other end of each secondary planetary gear shaft 19 is rotatably supported by the support frame member 20 via the bearing member 20a, and each secondary planetary gear shaft 19 has the number of teeth of the primary planetary gear 11. Secondary planetary gears 12 each having a larger number of teeth are integrally provided. Each secondary planetary gear 12 has an inner propeller shaft 5 as described above.
Is meshed with an internal gear 14 which surrounds the internal gear 14. The internal gear 14 is meshed with a gear 13 which is integral with the outer propeller shaft 7. The number of teeth of the secondary planetary gear 12 is formed so that the outer propeller shaft 7 and the inner propeller shaft 5 can be mutually inverted at substantially the same rotation speed.
ところで、上記各一次遊星歯車軸17と各二次遊星歯車
軸19との間には、これらを相互に連結する弾性継手18が
設けられる。By the way, an elastic joint 18 is provided between each of the primary planetary gear shafts 17 and each of the secondary planetary gear shafts 19 to connect them to each other.
実施例にあって弾性継手18は、第１図、第２図に示す
ように、一次遊星歯車軸17の軸端部にドラム21を設け、
そのドラム21内に、二次遊星歯車軸19の軸端部を挿通
し、二次遊星歯車軸19の外周面とドラム21の内周面との
間に、円周方向に間隔をおいてこれら二次遊星歯車軸19
とドラム21とを連結する板状の弾性片22を設けて構成さ
れる。弾性片22は具体的に、第３図に示すように、二次
遊星歯車軸19の外周面およびドラム21の内周面に、その
軸方向に沿ってそれぞれ形成したスプライン23,24に嵌
合され、対応するスプライン23,24を半径方向に結んで
放射状に設けられる。In the embodiment, the elastic joint 18 is provided with the drum 21 at the shaft end of the primary planetary gear shaft 17, as shown in FIG. 1 and FIG.
The shaft end of the secondary planetary gear shaft 19 is inserted into the drum 21, and the outer peripheral surface of the secondary planetary gear shaft 19 and the inner peripheral surface of the drum 21 are circumferentially spaced from each other. Secondary planetary gear shaft 19
And a drum-like elastic piece 22 for connecting the drum 21 to each other. Specifically, as shown in FIG. 3, the elastic piece 22 is fitted to splines 23 and 24 formed on the outer peripheral surface of the secondary planetary gear shaft 19 and the inner peripheral surface of the drum 21, respectively, along the axial direction thereof. The corresponding splines 23 and 24 are radially connected by connecting them in the radial direction.
なお弾性継手18は、上述の構成に限定されるものでな
く上記一次遊星歯車軸17と二次遊星歯車軸19とを連結す
る弾性継手（例えばゴムまたはコイルスプリングを利用
する継手等）であれば構わない。It should be noted that the elastic joint 18 is not limited to the above-described configuration, and may be any elastic joint that connects the primary planetary gear shaft 17 and the secondary planetary gear shaft 19 (for example, a joint that uses rubber or a coil spring). I do not care.
次に、本実施例の作用を説明する。 Next, the operation of this embodiment will be described.
第１図に示すように、先ず、駆動力は主機１の出力軸
２から内側プロペラ軸５へ伝達されて船尾側プロペラ４
を回転させる一方、内側プロペラ軸５から遊星歯車式動
力反転装置３を介して外側プロペラ軸７へ伝達されて船
首側プロペラ６を船尾側プロペラ４とほぼ同じ回転数で
反対方向に回転させる。すなわち、太陽歯車８から一次
遊星歯車11,弾性継手18,二次遊星歯車12,内歯歯車14お
よび歯車13を介して外側プロペラ軸７に駆動力が伝達さ
れる。この動力の伝達の際、軸系および遊星歯車式動力
伝達装置３に発生する捩れ振動は第１図及び第２図に示
す弾性継手18により吸収されて防止されると共に、振動
トルクのピークを、第４図中Ａで示すように、回転数の
低い領域に移し、かつ、そのピーク値を極めて低くす
る。したがって、常用回転域に遊星歯車式動力反転装置
３のチャタリングの発生を防止する。また、弾性継手18
は、一次遊星歯車軸17と二次遊星歯車軸19との連結部に
設けてられるから、弾性継手18に加わるトルクは、一次
および二次遊星歯車11,12の数および太陽歯車８と一次
遊星歯車11の歯数比によって分散され小さなトルクとな
る。したがって、弾性継手18はこのトルクに対応させて
小さくなり、コンパクト化できる。一方、弾性継手18の
メンテナンスの際には、弾性継手18が一次遊星歯車軸17
と二次遊星歯車軸19との主機１側に突出した端部に設け
られるため、遊星歯車式動力反転装置３のハウジングの
一部を取り外し、ドラム21と一次遊星歯車軸17との連結
を解放し、弾性継手18を取り出してメンテナンスができ
る。具体的には、ドラム21を一次遊星歯車軸17から取り
外し、ドラム21内部の板状の弾性片22を点検交換する。
かかる作業は歯車装置を取り外したりプロペラ軸を船尾
方向に移動するような作業がなくきわめて容易になる。As shown in FIG. 1, first, the driving force is transmitted from the output shaft 2 of the main engine 1 to the inner propeller shaft 5, and the stern side propeller 4 is moved.
On the other hand, the inner propeller shaft 5 is transmitted to the outer propeller shaft 7 through the planetary gear type power reversing device 3 to rotate the bow side propeller 6 in the opposite direction at substantially the same speed as the stern side propeller 4. That is, the driving force is transmitted from the sun gear 8 to the outer propeller shaft 7 via the primary planetary gear 11, elastic joint 18, secondary planetary gear 12, internal gear 14 and gear 13. During the transmission of this power, the torsional vibration generated in the shaft system and the planetary gear type power transmission device 3 is absorbed and prevented by the elastic joint 18 shown in FIGS. 1 and 2, and the peak of the vibration torque is As indicated by A in FIG. 4, the region is moved to a region where the rotational speed is low and the peak value is made extremely low. Therefore, the chattering of the planetary gear type power reversing device 3 is prevented from occurring in the normal rotation range. Also, elastic joints 18
Is provided at the connecting portion between the primary planetary gear shaft 17 and the secondary planetary gear shaft 19, the torque applied to the elastic joint 18 depends on the number of the primary and secondary planetary gears 11 and 12 and the sun gear 8 and the primary planetary gears. The torque is dispersed by the gear ratio of the gear 11 and becomes a small torque. Therefore, the elastic joint 18 can be made smaller and smaller in accordance with this torque. On the other hand, when performing maintenance on the elastic joint 18, the elastic joint 18 is
And the secondary planetary gear shaft 19 are provided at the ends projecting to the main machine 1 side, so part of the housing of the planetary gear type power reversing device 3 is removed, and the connection between the drum 21 and the primary planetary gear shaft 17 is released. Then, the elastic joint 18 can be taken out for maintenance. Specifically, the drum 21 is removed from the primary planetary gear shaft 17, and the plate-like elastic piece 22 inside the drum 21 is inspected and replaced.
Such work is extremely easy because there is no work to remove the gear device or move the propeller shaft in the stern direction.
［考案の効果］ 本考案は次のような効果を発揮する。[Effect of Invention] The present invention has the following effects.
捩振動トルクのピークを回転数の低い領域に存在さ
せ、かつ、そのピーク値をきわめて低くすることができ
るので、主機の常用回転数の範囲に歯車装置のチャタリ
ングを発生させないようにできる。また、弾性継手は一
次遊星歯車と二次歯車との間に小さいトルクの系に設け
られるので、小容量にでき、コンパクト化が図れる。ま
た、そのメンテナンスがきわめて容易となる。Since the peak of the torsional vibration torque can be present in a region where the rotation speed is low and the peak value can be made extremely low, chattering of the gear device can be prevented from occurring in the range of the normal rotation speed of the main engine. Further, since the elastic joint is provided in the system of small torque between the primary planetary gear and the secondary gear, the capacity can be reduced and the size can be reduced. In addition, the maintenance becomes extremely easy.
第１図は本考案の実施例を示す概略側面図、第２図は要
部を示す拡大側断面図、第３図は第２図のIII−III線断
面図、第４図は弾性継手を設けた場合の歯車装置の振動
トルクを示す図、第５図は従来例を示す歯車の系統図、
第６図は弾性継手を設けない場合の歯車装置の振動トル
クを示す図である。 図中、１は主機、２は出力軸、３は遊星歯車式動力反転
装置、４は船尾側プロペラ、５は内側プロペラ軸、６は
船首側プロペラ、７は外側プロペラ軸、８は太陽歯車、
11は一次遊星歯車、12は二次遊星歯車、14は内歯歯車、
18は弾性継手、22は弾性片である。FIG. 1 is a schematic side view showing an embodiment of the present invention, FIG. 2 is an enlarged side sectional view showing an essential part, FIG. 3 is a sectional view taken along line III-III of FIG. 2, and FIG. FIG. 5 is a diagram showing the vibration torque of the gear device when it is provided, and FIG.
FIG. 6 is a diagram showing the vibration torque of the gear device when the elastic joint is not provided. In the figure, 1 is a main engine, 2 is an output shaft, 3 is a planetary gear type power reversing device, 4 is a stern side propeller, 5 is an inner propeller shaft, 6 is a bow side propeller, 7 is an outer propeller shaft, 8 is a sun gear,
11 is a primary planetary gear, 12 is a secondary planetary gear, 14 is an internal gear,
Reference numeral 18 is an elastic joint, and 22 is an elastic piece.
Claims (1)
内側プロペラ軸を連結すると共に、その内側プロペラ軸
と船首側プロペラを駆動する外側プロペラ軸とを遊星歯
車式動力反転装置を介して連結した二重反転軸の動力伝
達装置において、上記内側プロペラ軸に太陽歯車を固定
し、該太陽歯車の外周に一次遊星歯車を噛合し、該一次
遊星歯車に主機側に延長され軸心に沿って挿通孔が形成
された一次遊星歯車軸を設け、他方上記外側プロペラ軸
に内歯歯車を一体的に連結し、該内歯歯車の内周に二次
遊星歯車を噛合し、該二次遊星歯車に主機側に延長され
た二次遊星歯車軸を設け、該二次遊星歯車軸を上記一次
遊星歯車軸の挿通孔に船尾側から主機側へ向けて挿通す
ると共に、主機側に突出した一次遊星歯車軸の端部と二
次遊星歯車軸の端部との間に、これらを連結すべく放射
状に配置された複数の弾性片からなる弾性継手を設けた
ことを特徴とする二重反転軸の動力伝達装置。1. An inner propeller shaft for driving a stern side propeller is connected to an output shaft of a main engine, and the inner propeller shaft and an outer propeller shaft for driving a bow side propeller are connected through a planetary gear type power reversing device. In the power transmission device of the counter-rotating shaft, the sun gear is fixed to the inner propeller shaft, the primary planetary gear is meshed with the outer periphery of the sun gear, and the primary planetary gear is extended to the main machine side along the axial center. A primary planetary gear shaft formed with an insertion hole is provided, while an internal gear is integrally connected to the outer propeller shaft, and a secondary planet gear is meshed with the inner periphery of the internal gear to form a secondary planet gear. A secondary planetary gear shaft extended to the main machine side is provided, and the secondary planetary gear shaft is inserted into the insertion hole of the primary planetary gear shaft from the stern side toward the main machine side, and the primary planetary gear protruding toward the main machine side. End of gear shaft and end of secondary planetary gear shaft Power transmission system of counter-rotating shaft, characterized in that a resilient joint comprising a plurality of elastic pieces arranged radially so as to connect them between.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989086884U JPH081314Y2 (en) | 1989-07-26 | 1989-07-26 | Double inversion shaft power transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989086884U JPH081314Y2 (en) | 1989-07-26 | 1989-07-26 | Double inversion shaft power transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0326853U JPH0326853U (en) | 1991-03-19 |
| JPH081314Y2 true JPH081314Y2 (en) | 1996-01-17 |
Family
ID=31636521
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1989086884U Expired - Lifetime JPH081314Y2 (en) | 1989-07-26 | 1989-07-26 | Double inversion shaft power transmission device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH081314Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101304086B1 (en) * | 2012-09-20 | 2013-09-05 | 신중호 | Two axes reversed rotational planet gear reducer |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3147538A1 (en) * | 2015-09-23 | 2017-03-29 | Inovacor Ab | Compound planet gear arrangement and drive train arrangement |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6018094U (en) * | 1983-07-18 | 1985-02-07 | 三菱重工業株式会社 | Contra-rotating propeller device for ships |
-
1989
- 1989-07-26 JP JP1989086884U patent/JPH081314Y2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101304086B1 (en) * | 2012-09-20 | 2013-09-05 | 신중호 | Two axes reversed rotational planet gear reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0326853U (en) | 1991-03-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0727277Y2 (en) | Double inversion shaft power transmission device | |
| RU94021642A (en) | TORQUE TRANSMISSION DEVICE | |
| JPH02234896A (en) | Bearing system for reverse rotation propeller shaft | |
| JPH081314Y2 (en) | Double inversion shaft power transmission device | |
| JPH08166050A (en) | Planetary gear device | |
| EP0375396B1 (en) | Starter motors | |
| JP2020026804A5 (en) | ||
| JPH0243840Y2 (en) | ||
| JP2002213332A (en) | Planetary gear for starter motor | |
| JPS6133457B2 (en) | ||
| JP2831803B2 (en) | Engine balancer device | |
| JPH0518759B2 (en) | ||
| JPS6332441Y2 (en) | ||
| JPH084837A (en) | Crank pulley | |
| JPS6311407Y2 (en) | ||
| JP2730092B2 (en) | Vibration and noise reduction device for vehicle power train | |
| JPH047381Y2 (en) | ||
| JPH0129308Y2 (en) | ||
| SU1240580A1 (en) | Manipulator module | |
| JPS6017557Y2 (en) | Forward/reverse two-speed marine reduction/reversing gear | |
| JPS6311402Y2 (en) | ||
| JPS6120744B2 (en) | ||
| JPH0252134B2 (en) | ||
| JPH0215889Y2 (en) | ||
| JP2554247Y2 (en) | Rotary power transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |