JPH0532196A - Differectial planetary gearing device for driving double inversive propeller of ship - Google Patents
Differectial planetary gearing device for driving double inversive propeller of shipInfo
- Publication number
- JPH0532196A JPH0532196A JP20893491A JP20893491A JPH0532196A JP H0532196 A JPH0532196 A JP H0532196A JP 20893491 A JP20893491 A JP 20893491A JP 20893491 A JP20893491 A JP 20893491A JP H0532196 A JPH0532196 A JP H0532196A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- shaft
- planetary
- propeller shaft
- propeller
- 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.)
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Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は大型船舶の船尾に搭載す
る二重反転プロペラを駆動させるための舶用二重反転プ
ロペラ駆動用差動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 marine counter-rotating propeller driving differential planetary gear device for driving a counter-rotating propeller mounted on the stern of a large ship.
【０００２】[0002]
【従来の技術】二重反転プロペラ装置は、船舶の推進性
能を向上させるものとして、これまでの一軸の推進装置
に代るものとして用いられるようになって来ている。2. Description of the Related Art A counter-rotating propeller device has come to be used as an alternative to the conventional uniaxial propulsion device for improving the propulsion performance of a ship.
【０００３】二重反転プロペラ装置は、内側プロペラ軸
と外側プロペラ軸を同芯に配して、外側プロペラ軸に前
プロペラを装着すると共に、内側プロペラ軸に後プロペ
ラを装着し、内側プロペラ軸と外側プロペラ軸を互に逆
方向に回転させるようにしてあり、モータからの回転力
で内側プロペラ軸と外側プロペラ軸を逆回転させるよう
にする機構として遊星歯車装置がある。In the counter-rotating propeller device, an inner propeller shaft and an outer propeller shaft are arranged concentrically, a front propeller is mounted on the outer propeller shaft, a rear propeller is mounted on the inner propeller shaft, and a rear propeller is mounted on the inner propeller shaft. There is a planetary gear device as a mechanism for rotating the outer propeller shafts in mutually opposite directions, and rotating the inner propeller shaft and the outer propeller shaft in reverse by rotational force from a motor.
【０００４】従来の遊星歯車装置としては、図６に示す
ものが知られている。すなわち、モータａに連結された
主軸ｂに、太陽歯車ｃを一体的に取り付け、該太陽歯車
ｃの周りに複数個のプラネタリーギヤｄを噛合させ、
又、該複数個のプラネタリーギヤｄには、その外側に配
した内歯歯車ｅを噛合させ、上記各プラネタリーギヤｄ
は、内側プロペラ軸ｇと一体のプラネタリーキャリヤｆ
に各々軸を介して支持させ、内歯歯車ｅは外側プロペラ
軸ｈに一体に連結してなり、モータａにより主軸ｂを介
して太陽歯車ｃが時計方向に回転させられるとき、プラ
ネタリーギヤｄは反時計方向へ回転しながら時計方向へ
公転するので、内歯歯車ｅは反時計方向へ回転させら
れ、プラネタリーギヤｄを支持するプラネタリーキャリ
ヤｆは時計方向へ回転させられる。これにより内側プロ
ペラ軸ｇと外側プロペラ軸ｈとは時計方向、反時計方向
と互に逆方向に回転して、前プロペラｉと後プロペラｊ
は互に逆回転しながら同一方向にスラストを発生するよ
うにしてある。As a conventional planetary gear device, one shown in FIG. 6 is known. That is, the sun gear c is integrally attached to the main shaft b connected to the motor a, and a plurality of planetary gears d are meshed around the sun gear c,
Further, the plurality of planetary gears d are meshed with an internal gear e arranged on the outer side thereof, so that the planetary gears d
Is a planetary carrier f integrated with the inner propeller shaft g.
, The internal gear e is integrally connected to the outer propeller shaft h, and when the sun gear c is rotated clockwise by the motor a via the main shaft b, the planetary gear d Rotates in the clockwise direction while rotating in the counterclockwise direction, the internal gear e is rotated in the counterclockwise direction, and the planetary carrier f that supports the planetary gear d is rotated in the clockwise direction. As a result, the inner propeller shaft g and the outer propeller shaft h rotate in opposite directions, clockwise and counterclockwise, and the front propeller i and the rear propeller j are rotated.
Are designed to generate thrust in the same direction while rotating in opposite directions.
【０００５】[0005]
【発明が解決しようとする課題】ところが、上記従来の
遊星歯車装置は、通常、差動遊星歯車装置と呼ばれ、そ
の機能、特性は、下記(1) 式、(2)式及び(3) 式で規定
されている。However, the above-mentioned conventional planetary gear device is usually called a differential planetary gear device, and its functions and characteristics are as follows (1), (2) and (3). It is specified by the formula.
【０００６】すなわち、基本歯数比ρは、 ρ＝内歯歯車の歯数（ＺR ）／太陽歯車の歯数（ＺS ）
＝（内歯歯車の半径（ｒR ）／太陽歯車の半径
（ｒS ）） …(1) トルク（Ｑ）については、内歯歯車のトルクをＱR 、太
陽歯車のトルクをＱS 、プラネタリーギヤのトルクをＱ
P とすると、 ＱR ＝−ρ・ＱS 、ＱP ＝（ρ＋１）・ＱS …(2) 回転数（Ｎ）は、内歯歯車の回転数をＮR 、太陽歯車の
回転数をＮS 、プラネタリーギヤの回転数をＮP とする
と、 ＮS ＋ρＮR −（ρ＋１）・ＮP ＝０ …(3) として規定されている。That is, the basic tooth number ratio ρ is ρ = number of teeth of internal gear (Z R ) / number of teeth of sun gear (Z S ).
= (Radius of internal gear (r R ) / radius of sun gear (r S )) (1) As for torque (Q), torque of internal gear is Q R , torque of sun gear is Q S , planetar Q of the torque of Lee gear
When P, Q R = -ρ · Q S, Q P = (ρ + 1) · Q S ... (2) rotational speed (N) is the rotational speed of the internal gear N R, the rotation speed of the sun gear N S, when the rotational speed of the planetary gears and N P, N S + ρN R - (ρ + 1) · N P = 0 ... is defined as (3).
【０００７】従来の装置では、内歯歯車ｅと外側プロペ
ラ軸ｉとが直結であるため、内歯歯車ｅのトルクとプラ
ネタリーギヤｄのトルクが同じになれず、たとえば、太
陽歯車ｃと内歯歯車ｅとの歯数比が１：５とすると、内
歯歯車ｅとプラネタリーギヤｄのトルク比は５：６にな
る。その上、内歯歯車ｅと直結の外側プロペラ軸ｈの回
転数をプラネタリーキャリヤｆと一体の内側プロペラ軸
ｇの回転数に対して任意に変えることもできない。した
がって、今、従来方式のモータａを、たとえば、ディー
ゼル主機関として、図６のシステムを舶用二重反転プロ
ペラの駆動用として使用しても、上記３つの式で機能、
特性が決められるため、二重反転プロペラの最適設計が
できず、高い推進性能が得られない、という問題があ
る。In the conventional device, since the internal gear e and the outer propeller shaft i are directly connected to each other, the torque of the internal gear e and the torque of the planetary gear d cannot be the same. When the ratio of the number of teeth to the gear tooth e is 1: 5, the torque ratio between the internal gear e and the planetary gear d is 5: 6. Moreover, the rotation speed of the outer propeller shaft h directly connected to the internal gear e cannot be arbitrarily changed with respect to the rotation speed of the inner propeller shaft g integrated with the planetary carrier f. Therefore, even if the conventional motor a is used as a diesel main engine and the system of FIG. 6 is used for driving a marine contra-rotating propeller, the functions of the above three formulas are satisfied.
Since the characteristics are determined, there is a problem that the counter-rotating propeller cannot be optimally designed and high propulsion performance cannot be obtained.
【０００８】そこで、本発明は、内側プロペラ軸に直結
するプラネタリーギヤの回転数に対して内歯歯車の回転
数を任意に変えることができるようにして二重反転プロ
ペラの最適設計ができるようにした上で更に歯車を含む
軸系の小直径化が図れるようにした舶用二重反転プロペ
ラ駆動用差動遊星歯車装置を提供しようとするものであ
る。Therefore, according to the present invention, the rotation speed of the internal gear can be arbitrarily changed with respect to the rotation speed of the planetary gear directly connected to the inner propeller shaft, so that the optimum design of the counter-rotating propeller can be performed. Further, it is an object of the present invention to provide a marine counter-rotating propeller-driving differential planetary gear device that can further reduce the diameter of a shaft system including gears.
【０００９】[0009]
【課題を解決するための手段】本発明は、上記課題を解
決するために、主機関側の主軸に継手を介して第一太陽
歯車を同芯状に結合すると共に、該第一太陽歯車とその
外側の内歯歯車との間に、両者に互に噛合する複数個の
プラネタリーギヤと、該各プラネタリーギヤを回転自在
に支持するプラネタリーキャリヤとを備え、プラネタリ
ーキャリヤと一体の軸を内側プロペラ軸に、又、内歯歯
車を外側プロペラ軸にそれぞれ接続するようにしてある
舶用二重反転プロペラ駆動用差動遊星歯車装置におい
て、上記内歯歯車と外側プロペラ軸の間に、内歯歯車の
軸上に取り付けた第二太陽歯車と、内歯歯車の軸上に回
転自在に支持し且つ外側プロペラ軸に連結される軸を有
する第三太陽歯車と、上記第二太陽歯車と第三太陽歯車
に別々に噛合し且つケーシングに位置固定された直径の
異なる一対の一体型同芯軸上のプラネタリーギヤとから
なる回転数調整歯車装置を介在させてなる構成とする。SUMMARY OF THE INVENTION In order to solve the above problems, the present invention concentrically couples a first sun gear to a main shaft of a main engine through a joint, and A plurality of planetary gears that mesh with each other and an planetary carrier that rotatably supports each planetary gear are provided between the planetary carrier and an outer internal gear, and a shaft integrated with the planetary carrier. In the differential planetary gear device for driving a contra-rotating propeller for a marine vessel, wherein the internal gear is connected to the inner propeller shaft, and the internal gear is connected to the outer propeller shaft. A second sun gear mounted on the shaft of the toothed gear, a third sun gear having a shaft rotatably supported on the shaft of the internal gear and connected to the outer propeller shaft, the second sun gear and the second sun gear. Separately meshed with the three sun gears and Pacing position fixed by interposing a pair of rotational speed adjusting gear unit consisting of an integrated planetary gears on the concentric axis of different diameters in a structure formed by.
【００１０】[0010]
【作用】主機関からの回転力が第一太陽歯車に伝えられ
ると、プラネタリーギヤは自転しつつ公転して、プラネ
タリーキャリヤと内歯歯車が互に逆方向へ回転するが、
本発明では、内歯歯車の軸と外側プロペラ軸とを直結せ
ずにその間に第二太陽歯車と第三太陽歯車に噛合する同
芯軸上の一体型プラネタリーギヤを位置固定で配置した
構成としてあるので、該同芯軸上一体型の２つのプラネ
タリーギヤの直径比を任意に変えることにより内歯歯車
の回転数に対して第三太陽歯車の回転数を任意に変える
ことができるので、内側プロペラ軸に対して外側プロペ
ラ軸の回転数を最適に選定することができ、二重反転プ
ロペラの最適設計ができる。又、第二、第三太陽歯車と
これに噛合する同芯軸上一体型のプラネタリーギヤは小
直径化が可能であり、小直径化しても上記二重反転プロ
ペラの最適設計から高い推進性能が得られる。[Operation] When the rotational force from the main engine is transmitted to the first sun gear, the planetary gear revolves around its own axis, and the planetary carrier and the internal gear rotate in opposite directions.
In the present invention, the structure in which the integrated planetary gear on the concentric shaft that meshes with the second sun gear and the third sun gear is arranged in a fixed position without directly connecting the shaft of the internal gear and the outer propeller shaft Therefore, by arbitrarily changing the diameter ratio of the two concentric shaft-integrated planetary gears, the rotational speed of the third sun gear can be arbitrarily changed with respect to the rotational speed of the internal gear. The rotation speed of the outer propeller shaft can be optimally selected with respect to the inner propeller shaft, and the contra-rotating propeller can be optimally designed. Also, the planetary gears of the second and third sun gears and the concentric on-shaft planetary gear that meshes with them can be made smaller in diameter, and even if the diameter is made smaller, the optimum design of the above-mentioned counter-rotating propeller will lead to high propulsion performance. Is obtained.
【００１１】[0011]
【実施例】以下、本発明の実施例を図面を参照して説明
する。Embodiments of the present invention will be described below with reference to the drawings.
【００１２】図１乃至図５は本発明の一実施例を示すも
ので、主機関Ｅ側の主軸１に継手２を介して直結する同
芯状の軸３に第一太陽歯車４を設け、上記第一太陽歯車
４とその外側の内歯歯車５との間に、図２にも示すよう
に複数個のプラネタリーギヤ６を周方向に配置して、各
プラネタリーギヤ６を上記第一太陽歯車４と内歯歯車５
にそれぞれ噛合させ、各プラネタリーギヤ６は、一端側
の軸を上記継手２側に支持されるフレーム７に軸受８を
介して回転自在に支持させると共に、他端側の軸を上記
第一太陽歯車４と同芯状の軸１０と一体のプラネタリー
キャリヤ９に軸受８を介して支持させ、且つ上記内歯歯
車５に、上記プラネタリーキャリヤ９と一体の軸１０の
外側に同芯状に配した軸１１を一体的に取り付け、主軸
１の回転で第一太陽歯車４と軸１０と該軸１０上のプラ
ネタリーキャリヤ９とが同一方向へ回転するとき、各プ
ラネタリーギヤ６は反対方向へ自転しながら図３の如く
プラネタリーキャリヤ９により公転し、内歯歯車５は軸
１１と一体に上記プラネタリーキャリヤ９の軸１０とは
逆方向に回転させられるようにしてある。1 to 5 show an embodiment of the present invention, in which a first sun gear 4 is provided on a concentric shaft 3 which is directly connected to a main shaft 1 on a main engine E side through a joint 2. As shown in FIG. 2, a plurality of planetary gears 6 are arranged in the circumferential direction between the first sun gear 4 and the internal gear 5 on the outside thereof, and each planetary gear 6 is connected to the first Sun gear 4 and internal gear 5
Each planetary gear 6 has a shaft on one end side rotatably supported on a frame 7 supported on the joint 2 side via a bearing 8 and a shaft on the other end side on the first sun. A planetary carrier 9 integral with a shaft 10 coaxial with the gear 4 is supported via a bearing 8, and the internal gear 5 is concentrically arranged outside the shaft 10 integral with the planetary carrier 9. When the arranged shafts 11 are integrally mounted, and the first sun gear 4, the shaft 10 and the planetary carrier 9 on the shaft 10 rotate in the same direction by the rotation of the main shaft 1, the planetary gears 6 move in opposite directions. While rotating on its own axis, it revolves around the planetary carrier 9 as shown in FIG. 3, and the internal gear 5 is rotated integrally with the shaft 11 in the opposite direction of the shaft 10 of the planetary carrier 9.
【００１３】本発明は、上記構成において、内歯歯車５
の軸１１を後述する外側プロペラ軸に直結することを止
め、内歯歯車５の軸に対して外側プロペラ軸の回転数が
変えられるようにする回転数調整歯車装置１２を設置す
る。According to the present invention, in the above structure, the internal gear 5 is
A rotation speed adjusting gear unit 12 is installed to stop the direct connection of the shaft 11 to the outer propeller shaft described later and to change the rotation speed of the outer propeller shaft with respect to the shaft of the internal gear 5.
【００１４】詳述すると、上記回転数調整歯車装置１２
は、第二太陽歯車１３と、第三太陽歯車１４と、これら
両太陽歯車１３と１４に別々に噛合できる同芯軸上の一
体型プラネタリーギヤ１５及び１６と、第三太陽歯車１
４の軸１７とからなる。すなわち、内歯歯車５の軸１１
上に第二太陽歯車１３を固定すると共に、第三太陽歯車
１４を第二太陽歯車１３に隣接させてラジアル軸受１８
を介し回転自在に配置し、該第三太陽歯車１４には、上
記内歯歯車５の軸１１と同芯状にして軸１０の外側に配
した軸１７を一体構造とし、且つ上記第二と第三の各太
陽歯車１３と１４には、２つの異なるプラネタリーギヤ
１５と１６を同芯軸上に一体型として図４、図５の如く
複数個配置し、両プラネタリーギヤ１５と１６の軸１９
を、上記プラネタリーギヤ６、内歯歯車５や同軸上のプ
ラネタリーギヤ１５，１６等を覆う大きさを有し且つ船
内の固定据付定盤に固定されるケーシング２０に回転自
在に支持させ、内歯歯車５の回転力が第二太陽歯車１３
を経てプラネタリーギヤ１５に伝えられ、更に、プラネ
タリーギヤ１６を経て第三太陽歯車１４に伝達され、第
三太陽歯車１４がラジアル軸受１８を介して内歯歯車５
の軸１１上で回転できるようにする。More specifically, the rotation speed adjusting gear device 12 is used.
Is a second sun gear 13, a third sun gear 14, integral planetary gears 15 and 16 on concentric shafts that can be separately meshed with both sun gears 13 and 14, and a third sun gear 1.
4 axis 17 and. That is, the shaft 11 of the internal gear 5
The second sun gear 13 is fixed on top of the second sun gear 13 and the third sun gear 14 is adjacent to the second sun gear 13 so that the radial bearing 18
The third sun gear 14 has a shaft 17 arranged concentrically with the shaft 11 of the internal gear 5 and arranged outside the shaft 10 as an integral structure with the second sun gear 14 and In each of the third sun gears 13 and 14, two different planetary gears 15 and 16 are integrally arranged on a concentric shaft as shown in FIG. 4 and FIG. Axis 19
Is rotatably supported by a casing 20 having a size that covers the planetary gears 6, the internal gear 5, the coaxial planetary gears 15, 16 and the like, and is fixed to a fixed installation platen in the ship. The rotational force of the internal gear 5 is the second sun gear 13
Is transmitted to the planetary gear 15 via the planetary gear 16 and further transmitted to the third sun gear 14 via the planetary gear 16, and the third sun gear 14 is transmitted via the radial bearing 18 to the internal gear 5
To be able to rotate on axis 11.
【００１５】上記第三太陽歯車１４の軸１７は、外側プ
ロペラ軸２１に連結した軸２２にスラスト軸受２３を介
して連結し、一方、プラネタリーキャリヤ９と一体の軸
１０は継手２４を介して内側プロペラ軸２５に連結す
る。The shaft 17 of the third sun gear 14 is connected to a shaft 22 connected to the outer propeller shaft 21 via a thrust bearing 23, while the shaft 10 integral with the planetary carrier 9 is connected via a joint 24. It is connected to the inner propeller shaft 25.
【００１６】２６はスラスト軸受２３のケーシング、２
７は内側プロペラ軸２５のスラスト軸受で、内側プロペ
ラ軸２５のスラスト力をスラスト軸受２７で受け、更
に、外側プロペラ軸のスラストとの合力をスラスト軸受
２３で受けるようにしてある。Reference numeral 26 denotes a casing of the thrust bearing 23, 2
Reference numeral 7 is a thrust bearing of the inner propeller shaft 25, and the thrust bearing 27 receives the thrust force of the inner propeller shaft 25, and the thrust bearing 23 receives the resultant force with the thrust of the outer propeller shaft.
【００１７】なお、外側プロペラ軸２１には、図６に示
す如く大径とした前プロペラを取り付け、内側プロペラ
軸２５には図６に示す如く小径とした後プロペラを取り
付ける。A large-diameter front propeller is attached to the outer propeller shaft 21 as shown in FIG. 6, and a small-diameter rear propeller is attached to the inner propeller shaft 25 as shown in FIG.
【００１８】主機関Ｅの回転力は、継手２と直結する軸
３を介して第一太陽歯車４に伝達される。第一太陽歯車
４には複数のプラネタリーギヤ６が噛合していて、各プ
ラネタリーギヤ６は、第一太陽歯車４と同方向に回転す
るプラネタリーキャリヤ９に支持されており、又、各プ
ラネタリーギヤ６は内歯歯車５に噛合していて、第一太
陽歯車４とプラネタリーギヤ６とプラネタリーキャリヤ
９と内歯歯車５とで差動遊星歯車を構成しており、その
機能特性は、前記(1) 式、(2) 式及び(3) 式で規定され
た作動をする。The rotational force of the main engine E is transmitted to the first sun gear 4 via the shaft 3 directly connected to the joint 2. A plurality of planetary gears 6 are meshed with the first sun gear 4, and each planetary gear 6 is supported by a planetary carrier 9 that rotates in the same direction as the first sun gear 4, and The planetary gear 6 meshes with the internal gear 5, and the first sun gear 4, the planetary gear 6, the planetary carrier 9, and the internal gear 5 constitute a differential planetary gear, and its functional characteristics. Operates in accordance with the above equations (1), (2) and (3).
【００１９】本発明では、内歯歯車５の軸１１を外側プ
ロペラ軸２１に直接結合させずに、回転数調整歯車装置
１２を介在させているので、内歯歯車５の回転数と異な
る回転数を外側プロペラ軸２１に伝えることができる。
すなわち、内歯歯車５の軸１１上に第二太陽歯車１３が
あるので、内歯歯車５の回転と同時に第二太陽歯車１３
が同一方向へ回転し、該第二太陽歯車１３に噛合するプ
ラネタリーギヤ１５と、該プラネタリーギヤ１５とは直
径の異なる同芯軸上一体型のプラネタリーギヤ１６とが
一体に回転し、該プラネタリーギヤ１６と噛合する第三
太陽歯車１４が第二太陽歯車１３とは異なる速度で回転
する。図１に示す実施例の如く、プラネタリーギヤ１５
の直径よりもプラネタリーギヤ１６の直径を小さくして
おけば、第三太陽歯車１４を第二太陽歯車１３よりも低
速回転させられるので、内歯歯車５の回転数を下げて外
側プロペラ軸２１側へ伝達させることができ、内歯歯車
５の回転数を、プラネタリーキャリヤ９の回転数と等し
くしたり、下げたりすることができることになる。上記
回転数調整歯車装置１２を構成する第二太陽歯車１３、
第三太陽歯車１４、プラネタリーギヤ１５，１６や、上
記プラネタリーキャリヤ９と一体の軸１０の各回転方向
は、図４、図５に示す矢印方向のとおりであり、第三太
陽歯車１４の回転方向と軸１０の回転方向が逆になり、
軸１０に直結される内側プロペラ軸２５に対して外側プ
ロペラ軸２１が反対に回転させられることになる。In the present invention, since the shaft 11 of the internal gear 5 is not directly coupled to the outer propeller shaft 21 but the rotation speed adjusting gear device 12 is interposed, the rotation speed different from the rotation speed of the internal gear 5. Can be transmitted to the outer propeller shaft 21.
That is, since the second sun gear 13 is on the shaft 11 of the internal gear 5, the second sun gear 13 is rotated at the same time as the rotation of the internal gear 5.
Rotate in the same direction, and the planetary gear 15 that meshes with the second sun gear 13 and the planetary gear 16 of a concentric shaft integral type having a different diameter from the planetary gear 15 rotate integrally, The third sun gear 14 meshing with the planetary gear 16 rotates at a speed different from that of the second sun gear 13. As in the embodiment shown in FIG. 1, the planetary gear 15
If the diameter of the planetary gear 16 is made smaller than the diameter of the third sun gear 14, the third sun gear 14 can be rotated at a lower speed than the second sun gear 13, so that the rotation speed of the internal gear 5 is reduced and the outer propeller shaft 21 is rotated. The rotation speed of the internal gear 5 can be made equal to or lower than the rotation speed of the planetary carrier 9. A second sun gear 13, which constitutes the rotation speed adjusting gear device 12,
The rotation directions of the third sun gear 14, the planetary gears 15 and 16, and the shaft 10 integrated with the planetary carrier 9 are as shown by the arrows in FIGS. The rotation direction and the rotation direction of the shaft 10 are reversed,
The outer propeller shaft 21 is rotated in the opposite direction with respect to the inner propeller shaft 25 directly connected to the shaft 10.
【００２０】上記において、第二太陽歯車１３の回転数
（Ｎ13）とトルク（Ｑ13）の関係（Ｎ13・Ｑ13）と第三
太陽歯車１４の回転数（Ｎ14）とトルク（Ｑ14）の関係
（Ｎ14・Ｑ14）は、プラネタリーギヤ１５と１６を介し
て等しい関係（Ｎ13・Ｑ13＝Ｎ14・Ｑ14）にあるので、
上記プラネタリーギヤ１５と１６の直径比を適当に選ぶ
ことにより内側プロペラ軸２５に直結される軸１０の回
転数とトルクの関係に対して上記第三太陽歯車１４の回
転数とトルクの関係（Ｎ14・Ｑ14）を最適に選定するこ
とができ、二重反転プロペラの最適設計が可能となる。
又、第一太陽歯車４の部分の差動遊星歯車と同様に、第
二、第三太陽歯車１３，１４の部分の差動遊星歯車は、
差動遊星歯車の原理で回転するので、歯車装置の小直径
比を図ることができ、しかも、回転数調整歯車装置１２
を構成する第二太陽歯車１３と、一体型同芯軸上のプラ
ネタリーギヤ１５，１６と、第三太陽歯車１４とにより
内歯歯車５の回転数を変えて出力できるようにして外側
プロペラ軸２１の回転数とトルクを内側プロペラ軸２５
のそれに見合うように設計できるので、小直径化されて
いても、充分な二重反転プロペラ性能を出すことができ
る。[0020] In the above, the rotational speed of the second sun gear 13 (N 13) and torque (Q 13) of the relationship (N 13 · Q 13) and the rotational speed of the third sun gear 14 (N 14) and torque (Q 14 relationship) (N 14 · Q 14), since a relationship equal through the planetary gear 15 and 16 (N 13 · Q 13 = N 14 · Q 14),
By appropriately selecting the diameter ratio of the planetary gears 15 and 16, the relationship between the rotational speed and the torque of the shaft 10 directly connected to the inner propeller shaft 25 and the relationship between the rotational speed and the torque of the third sun gear 14 ( N 14 · Q 14 ) can be optimally selected, and the optimal design of the contra-rotating propeller is possible.
Similarly to the differential planetary gears of the first sun gear 4, the differential planetary gears of the second and third sun gears 13 and 14 are
Since it rotates on the principle of the differential planetary gear, it is possible to achieve a small diameter ratio of the gear device, and further, the rotation speed adjusting gear device 12
The second sun gear 13, the planetary gears 15 and 16 on the integral concentric shaft, and the third sun gear 14 are configured to change the rotational speed of the internal gear 5 and output the outer propeller shaft. 21 rotation speed and torque to the inner propeller shaft 25
Since it can be designed to meet that requirement, sufficient counter-rotating propeller performance can be achieved even if the diameter is reduced.
【００２１】外側プロペラ軸２１と内側プロペラ軸２５
の回転により前プロペラと後プロペラが反転させられる
が、後プロペラのスラストはスラスト軸受２７を介して
外側プロペラ軸２１へ伝達され、前プロペラのスラスト
とともにスラスト軸受２３で受けられる。更に、該スラ
スト軸受２３で受けた全プロペラのスラストは、ケーシ
ング２６及び２０を介して船体の据付定盤で受けられ
る。Outer propeller shaft 21 and inner propeller shaft 25
Although the front propeller and the rear propeller are reversed by the rotation of, the thrust of the rear propeller is transmitted to the outer propeller shaft 21 via the thrust bearing 27, and is received by the thrust bearing 23 together with the thrust of the front propeller. Further, the thrust of all propellers received by the thrust bearing 23 is received by the installation surface plate of the hull via the casings 26 and 20.
【００２２】[0022]
【発明の効果】以上述べた如く、本発明の舶用二重反転
プロペラ駆動用差動遊星歯車装置によれば、主機関から
の回転力を内側プロペラ軸側へ直接伝えるプラネタリー
キャリヤの回転数に対して、これとは逆方向へ回転する
内歯歯車の回転数を、等しくしたり、あるいは下げたり
して外側プロペラ軸側へ伝えるための回転数調整歯車装
置を備え、該回転数調整歯車装置は、内歯歯車の軸上に
取り付けた第二太陽歯車と、該第二太陽歯車と噛合する
プラネタリーギヤと、該プラネタリーギヤとは直径を異
にし且つ同芯軸上に一体型としたプラネタリーギヤと、
該プラネタリーギヤと噛合し且つ外側プロペラ軸に連結
される軸を有する第三太陽歯車とからなる構成としてあ
るので、従来は内歯歯車の回転数が外側プロペラ軸の回
転数となって、外側プロペラ軸の回転数を内側プロペラ
軸の回転数に対して変えることができなかったことを、
本発明では第二及び第三の各太陽歯車に噛合する一体型
同芯軸上の２つのプラネタリーギヤの直径比を適当に選
ぶことにより内側プロペラ軸の回転数に対して外側プロ
ペラ軸の回転数を等しくしたり、下げたりして二重反転
プロペラの最適回転数に選定することができ、二重反転
プロペラを最適条件で駆動できて高い推進性能が得ら
れ、しかも、内歯歯車の軸と外側プロペラ軸の間に介在
させた太陽歯車やプラネタリーギヤは小直径比が可能で
あり、小直径化しても外側プロペラ軸に回転力を伝達で
きて二重反転プロペラの性能を出すことができ、コンテ
ナ船等の如き細長船型の船尾に大馬力の二重反転プロペ
ラ駆動用の差動歯車装置の搭載が容易となる、等の優れ
た効果を奏し得る。As described above, according to the marine counter-rotating propeller driving differential planetary gear device of the present invention, the rotational speed of the planetary carrier for directly transmitting the rotational force from the main engine to the inner propeller shaft side can be achieved. On the other hand, a rotation speed adjusting gear device for equalizing or lowering the rotation speed of the internal gear that rotates in the opposite direction to this and transmitting it to the outer propeller shaft side is provided. Is a second sun gear mounted on the shaft of the internal gear, a planetary gear that meshes with the second sun gear, and the planetary gear has a different diameter and is integrated on a concentric shaft. Planetary gear,
Since the third sun gear has a shaft that meshes with the planetary gear and is connected to the outer propeller shaft, conventionally, the rotation speed of the internal gear becomes the rotation speed of the outer propeller shaft, It was not possible to change the rotation speed of the propeller shaft with respect to the rotation speed of the inner propeller shaft.
In the present invention, by appropriately selecting the diameter ratio of the two planetary gears on the integral concentric shaft that meshes with the second and third sun gears, the rotation of the outer propeller shaft relative to the rotation speed of the inner propeller shaft can be changed. The number of rotations of the counter-rotating propeller can be selected by equalizing or lowering the number, and the counter-rotating propeller can be driven under optimum conditions to achieve high propulsion performance. The sun gear and planetary gear interposed between the outer propeller shaft and the outer propeller shaft can have a small diameter ratio, and even if the diameter is reduced, the rotational force can be transmitted to the outer propeller shaft and the performance of the counter-rotating propeller can be achieved. Therefore, it is possible to achieve an excellent effect such that a differential gear device for driving a large horsepower counter-rotating propeller can be easily mounted on a stern of a slender ship such as a container ship.
【図１】本発明の舶用二重反転プロペラ駆動用差動遊星
歯車装置の一実施例を示す断面図である。FIG. 1 is a sectional view showing an embodiment of a marine counter-rotating propeller driving differential planetary gear device of the present invention.
【図２】図１のＡ−Ａ矢視図である。FIG. 2 is a view on arrow AA of FIG.
【図３】図１のＢ−Ｂ矢視図である。FIG. 3 is a view taken along the line BB of FIG.
【図４】図１のＣ−Ｃ矢視図である。FIG. 4 is a view taken along the line C-C in FIG.
【図５】図１のＤ−Ｄ矢視図である。5 is a view taken along the line DD of FIG.
【図６】従来の差動遊星歯車装置の概略図である。FIG. 6 is a schematic view of a conventional differential planetary gear device.
４ 第一太陽歯車 ５ 内歯歯車 ６ プラネタリーギヤ ９ プラネタリーキャリヤ １０ 軸 １１ 内歯歯車の軸 １２ 回転数調整歯車装置 １３ 第二太陽歯車 １４ 第三太陽歯車 １５，１６ プラネタリーギヤ １７ 第三太陽歯車の軸 ２０ ケーシング ２１ 外側プロペラ軸 ２５ 内側プロペラ軸 Ｅ 主機関 4 First Sun Gear 5 Internal Gear 6 Planetary Gear 9 Planetary Carrier 10 Shaft 11 Shaft of Internal Gear 12 Rotation Speed Adjustment Gear Device 13 Second Sun Gear 14 Third Sun Gear 15, 16 Planetary Gear 17 Third Sun gear shaft 20 Casing 21 Outer propeller shaft 25 Inner propeller shaft E Main engine
Claims (1)
歯車と、該第一太陽歯車に噛合するプラネタリーギヤ
と、各プラネタリーギヤに噛合して第一太陽歯車とは逆
方向に回転する内歯歯車と、各プラネタリーギヤを回転
自在に支持し第一太陽歯車と同方向に回転するプラネタ
リーキャリヤとを備え、プラネタリーキャリヤと一体の
軸を内側プロペラ軸に、又、内歯歯車を外側プロペラ軸
にそれぞれ接続するようにしてある舶用二重反転プロペ
ラ駆動用差動遊星歯車装置において、上記内歯歯車と外
側プロペラ軸の間に、内歯歯車の軸上に取り付けた第二
太陽歯車と、内歯歯車の軸上に回転自在に支持し且つ外
側プロペラ軸に連結される軸を有する第三太陽歯車と、
上記第二太陽歯車と第三太陽歯車に別々に噛合し且つケ
ーシングに位置固定された直径の異なる一対の一体型同
芯軸上のプラネタリーギヤとからなる回転数調整歯車装
置を介在させてなることを特徴とする舶用二重反転プロ
ペラ駆動用差動遊星歯車装置。Claim: What is claimed is: 1. A first sun gear that rotates with a rotational force from a main engine, a planetary gear that meshes with the first sun gear, and a first sun that meshes with each planetary gear. An internal gear that rotates in the opposite direction to the gear and a planetary carrier that rotatably supports each planetary gear and that rotates in the same direction as the first sun gear are provided, and the shaft integral with the planetary carrier has an inner propeller. In the differential planetary gear device for driving a marine counter-rotating propeller, which is configured to connect the internal gear to the shaft and the external gear to the external propeller shaft, between the internal gear and the external propeller shaft, the internal gear A second sun gear mounted on the shaft, a third sun gear having a shaft rotatably supported on the shaft of the internal gear and connected to the outer propeller shaft,
The second sun gear and the third sun gear are separately meshed with each other, and a rotation speed adjusting gear device consisting of a pair of planetary gears on a concentric shaft with a different diameter fixed in position in the casing is interposed. A differential planetary gear device for marine counter-rotating propeller drive, which is characterized in that
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP03208934A JP3079670B2 (en) | 1991-07-26 | 1991-07-26 | Differential planetary gear system for marine contra-rotating propeller drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP03208934A JP3079670B2 (en) | 1991-07-26 | 1991-07-26 | Differential planetary gear system for marine contra-rotating propeller drive |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0532196A true JPH0532196A (en) | 1993-02-09 |
| JP3079670B2 JP3079670B2 (en) | 2000-08-21 |
Family
ID=16564555
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP03208934A Expired - Lifetime JP3079670B2 (en) | 1991-07-26 | 1991-07-26 | Differential planetary gear system for marine contra-rotating propeller drive |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3079670B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008094359A (en) * | 2006-10-16 | 2008-04-24 | Oshima Shipbuilding Co Ltd | Hatch device |
| JP2008545583A (en) * | 2005-06-09 | 2008-12-18 | ショッテル ゲゼルシャフトミットベシュレンクターハフトゥング | Ship propulsion unit and ship propulsion method |
| US9452815B2 (en) | 2013-03-15 | 2016-09-27 | Michigan Marine Propulsion Systems, LLC | Contra-rotating propulsor for marine propulsion |
| WO2018225369A1 (en) * | 2017-06-05 | 2018-12-13 | 新潟原動機株式会社 | Ship propulsion device |
-
1991
- 1991-07-26 JP JP03208934A patent/JP3079670B2/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008545583A (en) * | 2005-06-09 | 2008-12-18 | ショッテル ゲゼルシャフトミットベシュレンクターハフトゥング | Ship propulsion unit and ship propulsion method |
| JP2008094359A (en) * | 2006-10-16 | 2008-04-24 | Oshima Shipbuilding Co Ltd | Hatch device |
| US9452815B2 (en) | 2013-03-15 | 2016-09-27 | Michigan Marine Propulsion Systems, LLC | Contra-rotating propulsor for marine propulsion |
| US10392089B2 (en) | 2013-03-15 | 2019-08-27 | Michigan Marine Propulsion Systems, LLC | Contra-rotating propulsor for marine propulsion |
| WO2018225369A1 (en) * | 2017-06-05 | 2018-12-13 | 新潟原動機株式会社 | Ship propulsion device |
| JP2018203059A (en) * | 2017-06-05 | 2018-12-27 | 新潟原動機株式会社 | Ship propulsion device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3079670B2 (en) | 2000-08-21 |
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