JPH061294A - Bearing structure of contra-rotating propeller device - Google Patents
Bearing structure of contra-rotating propeller deviceInfo
- Publication number
- JPH061294A JPH061294A JP18309692A JP18309692A JPH061294A JP H061294 A JPH061294 A JP H061294A JP 18309692 A JP18309692 A JP 18309692A JP 18309692 A JP18309692 A JP 18309692A JP H061294 A JPH061294 A JP H061294A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- spherical
- shaft
- inner shaft
- reversing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/321—Bearings or seals specially adapted for propeller shafts
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/321—Bearings or seals specially adapted for propeller shafts
- B63H2023/323—Bearings for coaxial propeller shafts, e.g. for driving propellers of the counter-rotative type
Landscapes
- Chemical & Material Sciences (AREA)
- Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、船舶の推進装置として
使用される二重反転プロペラ装置に関し、特にその軸受
部の改良に関する。なお、二重反転プロペラ装置のほか
二重反転軸を用いる装置にも適用可能である。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a contra-rotating propeller device used as a propulsion device of a ship, and more particularly to improvement of a bearing portion thereof. In addition to the contra-rotating propeller device, it is also applicable to a device using a contra-rotating shaft.
【０００２】[0002]
【従来の技術】従来、船舶の推進装置として用いられる
二重反転プロペラ装置の軸系およびその軸受潤滑装置
は、図４に示すように構成されており、船尾部におい
て、前側プロペラ１を回転駆動する管状の外軸３と、同
外軸３の内部に嵌挿され後側プロペラ２を回転駆動する
内軸４とが、船尾管９を貫通し船尾側へ突出してそなえ
られている。そして、これらの内軸４と外軸３とは、図
示しない反転装置および主機に接続され、互いに逆方向
へ回転駆動されるようになっている。2. Description of the Related Art Conventionally, a shaft system of a counter-rotating propeller device used as a propulsion device for ships and its bearing lubrication device are constructed as shown in FIG. 4, and a front propeller 1 is rotationally driven at a stern portion. A tubular outer shaft 3 and an inner shaft 4 that is fitted into the outer shaft 3 and rotates the rear propeller 2 are provided so as to penetrate the stern tube 9 and project toward the stern side. The inner shaft 4 and the outer shaft 3 are connected to a reversing device and a main machine (not shown), and are rotationally driven in opposite directions.
【０００３】符号８は外軸３の内孔内に設置されて内軸
４を支承するすべり軸受を示している。この軸受は内軸
外面と外軸内面の動く方向と逆である（この理由から、
この軸受を以下「反転軸受」と呼ぶ）ため、通常のすべ
り軸受では厚くて安全な潤滑油膜が形成されず、焼付き
や異常摩耗、亀裂などが発生して使えない。そのため、
内軸４の中心部に給油導孔10を形成するとともに、この
給油導孔10に連通する放射状の給油孔11を形成し、給油
導孔10から供給される高圧潤滑油を給油孔11を介して摺
動面すき間に導くようになっている。なお、この場合反
転軸受８を構成する円筒体は、外軸のプロペラボス５の
内孔に圧入され、肉太で剛なプロペラボス５に裏支えさ
れるため、プロペラボス５と同様に剛性が高く、変形に
くい。Reference numeral 8 denotes a slide bearing installed in the inner hole of the outer shaft 3 and supporting the inner shaft 4. This bearing is opposite to the direction of movement of the inner and outer shaft inner surfaces (for this reason,
Since this bearing is hereinafter referred to as "inversion bearing", a normal sliding bearing cannot be used because a thick and safe lubricating oil film is not formed, and seizure, abnormal wear, and cracks occur. for that reason,
A lubrication guide hole 10 is formed in the center of the inner shaft 4, and a radial lubrication hole 11 communicating with the lubrication guide hole 10 is formed. High-pressure lubricating oil supplied from the lubrication guide hole 10 is passed through the lubrication hole 11. It is designed to guide the sliding surface gap. In this case, since the cylindrical body forming the reversing bearing 8 is press-fitted into the inner hole of the propeller boss 5 of the outer shaft and backed by the thick and rigid propeller boss 5, the rigidity is the same as that of the propeller boss 5. High and difficult to deform.
【０００４】[0004]
【発明が解決しようとする課題】ところで、二重反転プ
ロペラ装置では、上述のとおり前後のプロペラの回転方
向が反対であるため、水流からプロペラが受ける反力・
モーメントも互いに異なる方向を向き、それぞれの軸が
異なる方向に曲がろうとし、外軸３と内軸４とは相互に
傾く。この時、内軸４は外軸３内にある反転軸受８に対
して傾き、反転軸受８の船尾側端部で片当たり接触する
危険性があり、この部分で焼付きや異常摩耗、割れなど
の損傷を起こすという問題点がある。また、一般に、二
重反転プロペラによる省エネ効果は、大型・高出力の船
舶ほど大きくなるとされている。By the way, in the counter-rotating propeller device, since the rotating directions of the front and rear propellers are opposite to each other as described above, the reaction force received by the propeller from the water flow
The moments also point in different directions, the respective axes try to bend in different directions, and the outer shaft 3 and the inner shaft 4 tilt with respect to each other. At this time, the inner shaft 4 tilts with respect to the reversing bearing 8 in the outer shaft 3 and there is a risk of one-sided contact with the stern side end of the reversing bearing 8, and seizure, abnormal wear, cracking, etc. There is a problem of causing damage. In addition, it is generally said that the energy-saving effect of the counter-rotating propeller is greater for larger ships with higher output.
【０００５】一方、大型・高出力の船舶においては、推
進力の増大にともないプロペラ反力・モーメントの大き
さが飛躍的に増大するために、前述の反転軸受と内軸と
の相対傾きも極めて大きくなる。したがって、大型・高
出力の船舶では内外軸間の反転軸受の片当たりが拡大
し、反転軸受の焼付きや異常摩耗などの損傷や、プロペ
ラの回転停止・漂流などの事故の発生する可能性が増大
するという問題点がある。なお、上述のような従来のも
のでも、供給油圧を増大すること等で、わずかな片当た
りならば接触を防止することも不可能ではないが、この
やり方では大きな片当たりには対応できない。On the other hand, in a large-sized and high-powered ship, the magnitude of the propeller reaction force / moment dramatically increases with an increase in propulsion force, so that the relative inclination between the reversing bearing and the inner shaft is extremely large. growing. Therefore, in a large-sized and high-powered ship, the one-sided contact of the reversing bearing between the inner and outer shafts expands, and damage such as seizure and abnormal wear of the reversing bearing, and accidents such as propeller rotation stop and drift may occur. There is a problem of increase. It should be noted that even with the conventional one as described above, it is possible to prevent contact with a slight one-side contact by increasing the supply hydraulic pressure, but this method cannot cope with a large one-side contact.
【０００６】本発明は、上述のような問題点の解決をは
かろうとするもので、反転軸受を外軸に対し球面状の転
接面をそなえた一組みの球面座部材を介して軸方向の傾
動を可能に支持して反転軸受の船尾側端部での片当たり
接触を防止するとともに、球面状の転接面に高圧潤滑油
を導入して上記の傾動がスムーズに行なえるようにし
た、二重反転プロペラ装置の軸受構造を提供することを
目的とする。The present invention is intended to solve the above-mentioned problems, and the reversing bearing is axially arranged through a pair of spherical seat members having a spherical rolling contact surface with respect to the outer shaft. It supports the tilting of the reverse bearing to prevent one-sided contact at the stern side end of the reversing bearing, and introduces high pressure lubricating oil to the spherical rolling contact surface so that the above tilting can be performed smoothly. An object of the present invention is to provide a bearing structure for a counter rotating propeller device.
【０００７】[0007]
【課題を解決するための手段】上述の目的を達成するた
め、本発明の二重反転プロペラ装置の軸受構造は、二重
反転プロペラ装置において、管状の外軸と、同外軸の後
側端部あるいは同後側端部に取付けられたプロペラブッ
シュに形成された内孔に配設される反転軸受と、同反転
軸受に支承された内軸とをそなえ、上記反転軸受が、上
記の外軸の後側端部あるいはプロペラブッシュに形成さ
れた内孔の内周面に、球面状の転接面をそなえた一組み
の球面座部材を介して装着されるとともに、同球面座部
材の上記転接面に潤滑油が供給されるように構成された
ことを特徴としている。In order to achieve the above-mentioned object, a bearing structure of a counter-rotating propeller device according to the present invention has a tubular outer shaft and a rear end of the counter shaft in the counter-rotating propeller device. Part or the reverse shaft bearing provided in the inner hole formed in the propeller bush attached to the rear side end part and the reverse shaft bearing supported by the reverse shaft bearing. The rear end portion or the inner peripheral surface of the inner hole formed in the propeller bush is mounted via a pair of spherical seat members having a spherical rolling contact surface, and the above-mentioned rolling of the spherical seat member is performed. The feature is that the lubricating oil is supplied to the contact surface.
【０００８】[0008]
【作用】上述の本発明の二重反転プロペラ装置の軸受構
造では、プロペラに作用する水流からの反力・モーメン
トの相違に基づく外軸と内軸との相対傾きにより、外軸
等の内孔に配設される反転軸受と内軸とが片当たりする
場合、軸受すき間の互いに接近する部分に周囲よりも高
い油膜圧力が発生し、この油膜圧力の反作用により反転
軸受が球面座部材の球面状の転接面を中心に傾動して、
反転軸受と内軸との相対的傾斜が小さくなる。このと
き、球面座部材の球面状の転接面に潤滑油が供給されて
いて、上記の反転軸受の傾動をスムーズに行なわせる作
用が行なわれる。In the bearing structure of the counter-rotating propeller device according to the present invention described above, the inner shaft of the outer shaft or the like is caused by the relative inclination between the outer shaft and the inner shaft due to the difference in reaction force / moment from the water flow acting on the propeller. When the reversing bearing and the inner shaft are placed against each other, a higher oil film pressure than the surroundings is generated in the parts of the bearing clearance that are close to each other, and the reaction of this oil film pressure causes the reversing bearing to have a spherical shape of the spherical seat member. Tilting around the rolling contact surface of
The relative inclination between the reversing bearing and the inner shaft becomes small. At this time, the lubricating oil is supplied to the spherical rolling contact surface of the spherical seat member, so that the above-mentioned inversion bearing can be smoothly tilted.
【０００９】[0009]
【実施例】以下、図面により本発明の一実施例としての
二重反転プロペラ装置の軸受構造について説明すると、
図１は側断面図、図２は図１のＡ−Ａ矢視断面図、図３
は作用説明用の模式側断面図である。なお、図１〜図３
において、図４と同じ符号はほぼ同一の部材を示してい
る。この実施例の二重反転プロペラ装置にも、前側プロ
ペラ１を回転駆動する管状（中空）の外軸３と、同外軸
３の内部に嵌挿された後側プロペラを回転駆動する内軸
４とが、船尾管９を貫通して船尾側へ突出してそなえら
れている。そしてこれらの内軸４と外軸３とは、図示し
ない反転装置および主機に接続され、互いに逆方向へ回
転駆動されるようになっている。さらに、内軸４を支承
するための円筒状の反転軸受８が外軸３の船尾側軸端部
に取付けられた外軸のプロペラボス５の内孔内に配設さ
れている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The bearing structure of a counter-rotating propeller device according to an embodiment of the present invention will be described below with reference to the drawings.
1 is a side sectional view, FIG. 2 is a sectional view taken along the line AA of FIG. 1, and FIG.
[Fig. 4] is a schematic side sectional view for explaining an action. 1 to 3
4, the same reference numerals as those in FIG. 4 indicate almost the same members. Also in the contra-rotating propeller device of this embodiment, a tubular (hollow) outer shaft 3 that rotationally drives the front propeller 1 and an inner shaft 4 that rotationally drives a rear propeller that is fitted inside the outer shaft 3. And pierces the stern tube 9 and projects toward the stern side. The inner shaft 4 and the outer shaft 3 are connected to a reversing device and a main machine (not shown) and are rotationally driven in opposite directions. Further, a cylindrical reversing bearing 8 for supporting the inner shaft 4 is arranged in the inner hole of the propeller boss 5 of the outer shaft attached to the stern side shaft end of the outer shaft 3.
【００１０】すなわち円筒状の反転軸受８の背面（外周
面）には、凸状球面をそなえた球面座部材21が圧入など
の手段で固定され、また、外軸のプロペラボス５の内孔
内周面には上記凸状球面に転接する凹状球面をそなえた
球面座部材22が同じく圧入などの手段で固定されてい
る。そしてこれら一組みの球面座部材21および22の軸方
向の位置決め手段として、反転軸受８およびプロペラボ
ス５の船首側に段付き部23,24が設けられ、さらに船尾
側に固定用のスリーブ25およびリング部材26が設けられ
ている。That is, a spherical seat member 21 having a convex spherical surface is fixed to the back surface (outer peripheral surface) of the cylindrical reversing bearing 8 by means such as press fitting, and also in the inner hole of the propeller boss 5 of the outer shaft. A spherical seat member 22 having a concave spherical surface that is in rolling contact with the convex spherical surface is also fixed to the peripheral surface by means such as press fitting. As a means for axially positioning the pair of spherical seat members 21 and 22, stepped portions 23 and 24 are provided on the bow side of the reversing bearing 8 and the propeller boss 5, and a fixing sleeve 25 and a fixing sleeve 25 are provided on the stern side. A ring member 26 is provided.
【００１１】なお、リング部材26はボルトなどの締め付
け用具により、プロペラボス５に固定されている。これ
らの構造により、一組みの球面座部材21,22の反転軸受
背面部分への取付け・固定の作業を船尾側からすること
が可能となり、作業性のよい実用的な構造になってい
る。内軸４の軸芯部に給油導孔10が形成され、この給油
導孔10に連通する複数の放射状の給油孔11が内軸４に形
成されて、給油導孔10から供給される高圧の潤滑油が反
転軸受８の内周面に供給されるように構成されるほか、
放射孔12が反転軸受８の前側端部の近くに開口するよう
に、設けられている。なお給油孔11にはオリフィス（流
体絞り部材）（図示せず）が設置されている。そして、
この放射孔12の開口部に対向する反転軸受８の内周面上
の位置に、円周溝14が形成され、この円周溝14に連通す
る軸方向の油路15が反転軸受８に形成されている。The ring member 26 is fixed to the propeller boss 5 by a tightening tool such as a bolt. With these structures, the work of attaching and fixing the pair of spherical seat members 21, 22 to the rear surface of the reverse bearing can be performed from the stern side, and the structure is practical and has good workability. An oil supply guide hole 10 is formed in the shaft core portion of the inner shaft 4, and a plurality of radial oil supply holes 11 communicating with the oil supply guide hole 10 are formed in the inner shaft 4 so that the high pressure supplied from the oil supply guide hole 10 is high. In addition to being configured so that the lubricating oil is supplied to the inner peripheral surface of the inversion bearing 8,
The radiation hole 12 is provided so as to open near the front end of the reversing bearing 8. An orifice (fluid throttle member) (not shown) is installed in the oil supply hole 11. And
A circumferential groove 14 is formed at a position on the inner peripheral surface of the reversing bearing 8 facing the opening of the radiation hole 12, and an axial oil passage 15 communicating with the circumferential groove 14 is formed in the reversing bearing 8. Has been done.
【００１２】一方、球面座部材21を内外に貫通する通路
17が設けられていていて、この通路17は反転軸受８に形
成された孔16を介して油路15に連通している。さらに、
円周溝14の内側に隣接して第２の円周溝30が形成され、
この円周溝30は図示しない通路（この通路は反転軸受８
に油路15と干渉しないように形成されている）を介して
反転軸受８の外周面に連通している。On the other hand, a passage that penetrates the spherical seat member 21 in and out.
17 is provided, and this passage 17 communicates with the oil passage 15 through a hole 16 formed in the reversing bearing 8. further,
A second circumferential groove 30 is formed adjacent to the inner side of the circumferential groove 14,
This circumferential groove 30 is a passage (not shown)
Is formed so as not to interfere with the oil passage 15) and communicates with the outer peripheral surface of the reversing bearing 8.
【００１３】図１中の符号13は反転軸受８の内周面と内
軸４の外周面との間に形成されるすき間を示している。
なお固定用スリーブ25と反転軸受８の後部との間の空間
に溜った潤滑油は、反転軸受８に形成された貫通孔（図
示せず）により、反転軸受８の前方側へ排出されるよう
になっている。また、放射孔12を通路17に対向する位置
に設けると、給油孔11の後述の圧力調節差作用を阻害す
るおそれが生じるため、放射孔12は反転軸受８の前端部
付近に開口するように設けられている。Reference numeral 13 in FIG. 1 indicates a gap formed between the inner peripheral surface of the reversing bearing 8 and the outer peripheral surface of the inner shaft 4.
The lubricating oil accumulated in the space between the fixing sleeve 25 and the rear portion of the reversing bearing 8 is discharged to the front side of the reversing bearing 8 through a through hole (not shown) formed in the reversing bearing 8. It has become. Further, if the radiation hole 12 is provided at a position facing the passage 17, there is a risk that the later-described pressure adjustment difference action of the oil supply hole 11 may be hindered, so the radiation hole 12 should be opened near the front end portion of the reversing bearing 8. It is provided.
【００１４】上述の構成により、高圧潤滑油が内軸３の
給油導孔10から軸受部分で放射状の給油孔11を通って内
軸の軸受面に給油される。これと同時に、内軸３の給油
導孔10から供給される潤滑油が、放射孔12を通って一旦
反転軸受８の軸受面のすき間13に導かれ、次いで、反転
軸受８の内周の軸受端近くの円周溝14およびこれと連通
する軸方向の複数個の油路15および孔16を経て反転軸受
８の外周面に導かれ、さらに通路17を経て球面座部材21
の凸球面まで導かれる。With the above structure, the high pressure lubricating oil is supplied from the oil supply guide hole 10 of the inner shaft 3 to the bearing surface of the inner shaft through the radial oil supply holes 11 at the bearing portion. At the same time, the lubricating oil supplied from the oil supply guide hole 10 of the inner shaft 3 is once introduced into the clearance 13 of the bearing surface of the reversing bearing 8 through the radiation hole 12, and then the bearing on the inner circumference of the reversing bearing 8. The spherical seat member 21 is guided to the outer peripheral surface of the reversing bearing 8 through the circumferential groove 14 near the end and a plurality of axial oil passages 15 and holes communicating with this, and further through the passage 17.
It is led to the convex spherical surface of.
【００１５】ここで、二重反転プロペラ装置では、上述
のとおりプロペラに作用する水流からの反力・モーメン
トの相違に基づく外軸３と内軸４との相対傾きにより、
プロペラボス５の内孔に設置される反転軸受８と内軸４
とが片当たりする場合、図３に示すように、軸受すき間
の互いに接近する部分には周囲よりも高い油膜圧力
Ｐ1，Ｐ2が発生する。この油膜圧力の反作用力Ｆは、反
転軸受に対し、内軸の傾きにならわそうとするように作
用する。この実施例の場合反転軸受８の背面を一組みの
球面座部材21,22で揺動可能に支持する構成となってい
るため、上記の作用（力）により、反転軸受８を図３に
おいて反時計方向に回動させることができる。そしてこ
の作動により反転軸受８と内軸４との相対的傾斜が小さ
くなる。Here, in the counter-rotating propeller device, as described above, the relative inclination between the outer shaft 3 and the inner shaft 4 due to the difference in reaction force / moment from the water flow acting on the propeller causes
Inverting bearing 8 and inner shaft 4 installed in the inner hole of propeller boss 5.
In the case where the and the one-side contact occur, as shown in FIG. 3, oil film pressures P 1 and P 2 higher than those in the surroundings are generated in the portions of the bearing clearances that are close to each other. The reaction force F of the oil film pressure acts on the reversing bearing so as to follow the inclination of the inner shaft. In the case of this embodiment, since the back surface of the reversing bearing 8 is swingably supported by the set of spherical seat members 21 and 22, the reversing bearing 8 is reversed in FIG. It can be rotated clockwise. By this operation, the relative inclination between the reversing bearing 8 and the inner shaft 4 becomes small.
【００１６】さらに、一組みの球面座部材21,22の球面
状の転接面に、上述のように、高圧の潤滑油が供給され
るような構成になっているため、球面座部材21,22の球
面状の転接面での摩擦係数を大幅に低減することがで
き、上記の反転軸受の傾動作用をより円滑に行なわせる
ことができる。Further, as described above, since the high-pressure lubricating oil is supplied to the spherical rolling contact surfaces of the pair of spherical seat members 21, 22, the spherical seat members 21, The coefficient of friction at the spherical rolling contact surface of 22 can be significantly reduced, and the tilting operation of the reversing bearing can be performed more smoothly.
【００１７】また、上述の内軸４の傾動の際、給油孔11
にオリフィス（あるいは流体絞り要素）が設置されてお
り、給油孔11の開口部と反転軸受８の内周面との間のす
き間が大きくなろうとするときに、オリフィスがこの部
分の圧力を低下させ、多量の油が流出しないように作用
する。この作用と、逆にすき間が狭くなる側の開口部で
の圧力が高くなる現象とが協同して、反転軸受８内でこ
れに内接されている内軸が偏心して、局部的に接触する
ことを防止する作用が得られる。When the inner shaft 4 is tilted as described above, the oil supply hole 11
When an orifice (or a fluid throttle element) is installed in the valve, the orifice reduces the pressure in this part when the gap between the opening of the oil supply hole 11 and the inner peripheral surface of the reversing bearing 8 is about to increase. , It acts so that a large amount of oil does not flow out. This action and the phenomenon that the pressure increases in the opening on the side where the gap becomes narrower on the contrary, the inner shaft inscribed in the reversing bearing 8 is eccentric and locally contacts. The effect of preventing this is obtained.
【００１８】さらに、放射孔12を通って給油された高圧
潤滑油は、一旦反転軸受８と内軸４とのすき間13に導か
れ、反転軸受８の内周面の軸受端近くの円滑溝14内で全
円周にわたり高圧が展開されるが、これよりやや軸受内
部側に設けられたもう一つの円周溝30を図示しない孔で
軸受外周面と連絡させることにより、周囲圧程度に減圧
する作用が行なわれる。（これは、円周溝14に展開され
る高圧が、放射状の給油孔11により軸受面に展開される
正式の油膜圧力分布に大きく影響しないようにするため
である。）なお、一組みの球面座部材21,22の球面状の
転接面に高圧潤滑油を導く手段として、上述の実施例の
ほか、外軸３の内孔面にパイプを敷設し、このパイプに
より外軸３側の球面座部材22を介して高圧潤滑油を供給
するようにしてもよい。Further, the high-pressure lubricating oil supplied through the radial holes 12 is once introduced into the clearance 13 between the reversing bearing 8 and the inner shaft 4, and the smooth groove 14 near the bearing end on the inner peripheral surface of the reversing bearing 8 is provided. High pressure is developed over the entire circumference inside, but the pressure is reduced to about ambient pressure by connecting another circumferential groove 30 slightly inside the bearing with the outer peripheral surface of the bearing through a hole (not shown). The action takes place. (This is to prevent the high pressure developed in the circumferential groove 14 from significantly affecting the formal oil film pressure distribution developed on the bearing surface by the radial oil supply holes 11.) Note that a set of spherical surfaces is provided. As a means for guiding the high-pressure lubricating oil to the spherical rolling contact surfaces of the seat members 21, 22, a pipe is laid on the inner hole surface of the outer shaft 3 in addition to the above-mentioned embodiment, and the pipe is used to form a spherical surface on the outer shaft 3 side. The high-pressure lubricating oil may be supplied via the seat member 22.
【００１９】[0019]
【発明の効果】以上詳述したように、本発明の二重反転
プロペラ装置の軸受構造によれば、次のような効果ない
し利点が得られる。 (1) 反転軸受に対する内軸の傾きが軽減され、片当たり
による軸受の焼付き、異常摩耗、割れなどの損傷の発生
を回避することができ、推進プロペラの回転不能や船舶
の漂流などの事故の発生を防ぐことができる。 (2) 大型・大出力船に対する二重反転プロペラの装備を
実現することができ、大幅な省エネ効果を得ることがで
きる。As described above in detail, according to the bearing structure of the counter-rotating propeller device of the present invention, the following effects and advantages can be obtained. (1) The inclination of the inner shaft with respect to the reversing bearing is reduced, and it is possible to avoid the occurrence of damage such as seizure, abnormal wear, and cracking of the bearing due to one-sided contact. Can be prevented. (2) It is possible to equip a large-scale / high-power ship with a counter-rotating propeller, and to obtain a significant energy saving effect.
【図１】本発明の一実施例としての二重反転プロペラ装
置の軸受構造を示す側断面図。FIG. 1 is a side sectional view showing a bearing structure of a counter-rotating propeller device according to an embodiment of the present invention.
【図２】図１のＡ−Ａ矢視断面図。FIG. 2 is a sectional view taken along the line AA of FIG.
【図３】同作用説明用の模式側断面図。FIG. 3 is a schematic side sectional view for explaining the same action.
【図４】従来の二重反転プロペラ装置の側断面図。FIG. 4 is a side sectional view of a conventional counter-rotating propeller device.
１ 前側プロペラ ２ 後側プロペラ ３ 外軸 ４ 内軸 ５ プロペラボス ８ 反転軸受 ９ 船尾管 10 給油導孔 11 給油孔 12 放射孔 13 すき間 14,30 円周溝 15 油路 16 孔 17 通路 21,22 球面座部材 23,24 段部 25 スリーブ 26 リング部材 1 Front Propeller 2 Rear Propeller 3 Outer Shaft 4 Inner Shaft 5 Propeller Boss 8 Reverse Bearing 9 Stern Tube 10 Lubrication Guide Hole 11 Lubrication Hole 12 Radiation Hole 13 Clearance 14,30 Circumferential Groove 15 Oil Passage 16 Hole 17 Passage 21,22 Spherical seat member 23, 24 Step 25 Sleeve 26 Ring member
───────────────────────────────────────────────────── フロントページの続き (72)発明者 牧野 武朗 長崎市深堀町５丁目717番１号 三菱重工 業株式会社長崎研究所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takero Makino 5-717-1, Fukahori-cho, Nagasaki City Mitsubishi Heavy Industries, Ltd. Nagasaki Research Institute
Claims (1)
外軸と、同外軸の後側端部あるいは同後側端部に取付け
られたプロペラブッシュに形成された内孔に配設される
反転軸受と、同反転軸受に支承された内軸とをそなえ、
上記反転軸受が、上記の外軸の後側端部あるいはプロペ
ラブッシュに形成された内孔の内周面に、球面状の転接
面をそなえた一組みの球面座部材を介して装着されると
ともに、同球面座部材の上記転接面に潤滑油が供給され
るように構成されたことを特徴とする、二重反転プロペ
ラ装置の軸受構造。1. A counter-rotating propeller device in which a tubular outer shaft and an inner hole formed in a rear end portion of the outer shaft or a propeller bush attached to the rear end portion of the outer shaft are disposed. A bearing and an inner shaft supported by the reversing bearing,
The reversing bearing is mounted on a rear end portion of the outer shaft or an inner peripheral surface of an inner hole formed in a propeller bush via a pair of spherical seat members having a spherical rolling contact surface. At the same time, the bearing structure of the counter-rotating propeller device is characterized in that lubricating oil is supplied to the rolling contact surface of the spherical seat member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4183096A JP3004475B2 (en) | 1992-06-17 | 1992-06-17 | Bearing structure of contra-rotating propeller device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4183096A JP3004475B2 (en) | 1992-06-17 | 1992-06-17 | Bearing structure of contra-rotating propeller device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH061294A true JPH061294A (en) | 1994-01-11 |
| JP3004475B2 JP3004475B2 (en) | 2000-01-31 |
Family
ID=16129698
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4183096A Expired - Fee Related JP3004475B2 (en) | 1992-06-17 | 1992-06-17 | Bearing structure of contra-rotating propeller device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3004475B2 (en) |
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| KR101360750B1 (en) * | 2012-03-30 | 2014-02-11 | 삼성중공업 주식회사 | Propulsion apparatus for ship, install method of the propulsion apparatus, and ship having the propulsion apparatus |
| KR101380661B1 (en) * | 2011-06-07 | 2014-04-04 | 삼성중공업 주식회사 | Propulsion apparatus for ship and ship having the same |
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| KR101444340B1 (en) * | 2012-03-30 | 2014-09-26 | 삼성중공업 주식회사 | Propulsion apparatus for ship, and ship having the same |
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-
1992
- 1992-06-17 JP JP4183096A patent/JP3004475B2/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101380661B1 (en) * | 2011-06-07 | 2014-04-04 | 삼성중공업 주식회사 | Propulsion apparatus for ship and ship having the same |
| KR101324967B1 (en) * | 2011-06-16 | 2013-11-05 | 삼성중공업 주식회사 | Propulsion apparatus for ship, and ship having the same |
| KR101360750B1 (en) * | 2012-03-30 | 2014-02-11 | 삼성중공업 주식회사 | Propulsion apparatus for ship, install method of the propulsion apparatus, and ship having the propulsion apparatus |
| KR101390831B1 (en) * | 2012-03-30 | 2014-05-12 | 삼성중공업 주식회사 | Propulsion apparatus for ship, install method of the propulsion apparatus, and ship having the propulsion apparatus |
| KR101444340B1 (en) * | 2012-03-30 | 2014-09-26 | 삼성중공업 주식회사 | Propulsion apparatus for ship, and ship having the same |
| KR101444328B1 (en) * | 2012-04-27 | 2014-09-26 | 삼성중공업 주식회사 | Propulsion apparatus for ship, and ship having the same |
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| KR101422477B1 (en) * | 2012-05-10 | 2014-07-23 | 삼성중공업 주식회사 | Coupling structure of propulsion apparatus for ship stern, install method of the propulsion apparatus, and ship having the propulsion apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3004475B2 (en) | 2000-01-31 |
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