JP2984221B2 - Bearing lubrication structure for counter-rotating marine propellers - Google Patents
Bearing lubrication structure for counter-rotating marine propellersInfo
- Publication number
- JP2984221B2 JP2984221B2 JP8304940A JP30494096A JP2984221B2 JP 2984221 B2 JP2984221 B2 JP 2984221B2 JP 8304940 A JP8304940 A JP 8304940A JP 30494096 A JP30494096 A JP 30494096A JP 2984221 B2 JP2984221 B2 JP 2984221B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- oil passage
- oil
- propeller
- outer 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 - Fee Related
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)
Description
【0001】[0001]
【発明の属する技術分野】本発明は、舶用二重反転プロ
ペラの軸受に対して円滑に潤滑油を供給し循環させるこ
とのできる軸受潤滑構造に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing lubricating structure capable of smoothly supplying and circulating lubricating oil to a bearing of a contra-rotating marine propeller.
【0002】[0002]
【従来の技術】舶用二重反転プロペラは、二つのプロペ
ラを前後に配置して互いに反転(逆回転)させる点に特
徴のある船舶の推進手段である。図5は、従来の舶用二
重反転プロペラ51について船外の部分を示す縦断面図
であるが、図5(a)に示すとおり、二つのプロペラ53
・52は、中空の外軸70とその内部に通された内軸6
0とに対してそれぞれ取り付けられ、各軸によって互い
に逆向きに回転駆動される。前方にあるプロペラ53の
後流中に含まれる回転エネルギ損失が後方のプロペラ5
2によって回収されるため、推進効率が高く、またキャ
ビテーションや船体振動が少ないという利点がある。2. Description of the Related Art A contra-rotating marine propeller is a propulsion means for a marine vessel characterized in that two propellers are arranged in front of and behind and inverted (reverse rotation) from each other. FIG. 5 is a longitudinal sectional view showing a portion outside the hull of a conventional marine contra-rotating propeller 51. As shown in FIG.
52 is a hollow outer shaft 70 and an inner shaft 6 passed through the inside thereof.
0, and are rotationally driven in opposite directions by each shaft. The rotational energy loss contained in the wake of the propeller 53 in front is reduced by the rear propeller 5.
2 has the advantages of high propulsion efficiency and low cavitation and hull vibration.
【0003】外軸70の内側にて内軸60を支持する軸
受(いわゆる反転軸受)55としては、外部から潤滑油
を圧送することによってすべり面の間に油膜を形成す
る、いわゆる静圧軸受が使用されている。静圧軸受が使
用されるのは、かなりの質量を有する外軸70と内軸6
0とがこの反転軸受55をはさんでほぼ等速度で逆向き
に回転することから、外軸70用の軸受54aなどに用
いられる一般的な動圧型の軸受では安定的な油膜の形成
が困難だからである。図5の例でも、高圧の潤滑油が、
内軸60の内部を通る給油路(往きの油路)82bの中
を送られて軸受55と内軸60との隙間(すなわちすべ
り面の間)に臨む給油口82dから吐出されることによ
り、その面間に強制的に油膜を形成している。すべり面
の間から流れ出た潤滑油は、前方(図の右方)にある戻
し口(図示せず)から回収されてタンク(図示せず)に
戻り、ポンプ等を含む給油源(図示せず)により加圧さ
れて再び上記のすべり面等に給油される、といった経路
で循環使用される。[0003] As a bearing (so-called reversing bearing) 55 for supporting the inner shaft 60 inside the outer shaft 70, there is a so-called hydrostatic bearing in which an oil film is formed between sliding surfaces by supplying lubricating oil from the outside. in use. Hydrostatic bearings are used for the outer shaft 70 and the inner shaft 6 having considerable mass.
0 rotates in the opposite direction at substantially the same speed across the reversing bearing 55, so that it is difficult to form a stable oil film with a general dynamic pressure type bearing used for the bearing 54a for the outer shaft 70 and the like. That's why. Also in the example of FIG. 5, the high-pressure lubricating oil
The oil is sent through an oil supply passage (outgoing oil passage) 82b passing through the inside of the inner shaft 60, and is discharged from an oil supply port 82d facing a gap between the bearing 55 and the inner shaft 60 (that is, between sliding surfaces). An oil film is forcibly formed between the surfaces. The lubricating oil that has flowed out from between the slip surfaces is collected from a return port (not shown) in front (to the right in the figure), returns to a tank (not shown), and is supplied to an oil supply source (not shown) including a pump and the like. ), And the oil is recirculated to the above-mentioned slip surface or the like.
【0004】反転軸受55の後方の位置には、潤滑油を
外部に漏らさずまた外部から水が入るのを防止する目的
で、反転シール73という軸封手段が装備されている。
また反転軸受55には、図5(a)のように後端(つまり
反転シールに面した側)から前端にかけて、外周面上に
図5(b)に示す溝55aが形成されている。溝55a
は、上記のように反転軸受55に供給された潤滑油のう
ち、すべり面の間を船尾側(図5(a)の左方)へ流れた
ものを船首側へ返すための、いわば補助循環油路であ
る。このような油路を設けて潤滑油を前方へ流すことに
より、澱みをなくしてすべての潤滑油を循環させ得るほ
か、反転シール73の前面に過大な圧力がかかるのを防
止でき、また、反転軸受55に安定した軸受性能を維持
させることができる。油路の有無が軸受性能に影響する
のは、もし給油口82dから前方へのみ潤滑油が流れて
後方へは流れないとすると、流れによる圧力損失が不均
一になり、すべり面の間にアンバランスな圧力分布が生
じてしまうからである。なお、そのような油路は従来、
溝55aばかりではなく反転軸受55の肉厚内を通る穴
として形成されることもある。[0004] A shaft sealing means called a reversing seal 73 is provided at a position behind the reversing bearing 55 in order to prevent the lubricating oil from leaking to the outside and to prevent water from entering from outside.
5 (a), a groove 55a shown in FIG. 5 (b) is formed on the outer peripheral surface from the rear end (that is, the side facing the reversal seal) to the front end. Groove 55a
Is a so-called auxiliary circulation for returning the lubricating oil supplied to the reversing bearing 55 flowing toward the stern side (leftward in FIG. 5A) between the slip surfaces to the bow side, as described above. It is an oilway. By providing such an oil passage and allowing the lubricating oil to flow forward, all the lubricating oil can be circulated without stagnation, and excessive pressure can be prevented from being applied to the front surface of the reversing seal 73. The bearing 55 can maintain stable bearing performance. The presence or absence of the oil passage affects the bearing performance if the lubricating oil flows only forward from the oil filler port 82d and does not flow backward, so that the pressure loss due to the flow becomes uneven and the gap between the sliding surfaces This is because a balanced pressure distribution occurs. In addition, such oil passages have conventionally been
It may be formed as a hole that passes through not only the groove 55a but also the thickness of the reversing bearing 55.
【0005】なお、以上のような技術は実公平5−23
437号公報などに記載がある。[0005] The above technology is disclosed in Japanese Utility Model Publication No. 5-23.
No. 437, for example.
【0006】[0006]
【発明が解決しようとする課題】図5などのように、反
転軸受の表面に溝を設けたりその肉厚内に穴をあけたり
することによって補助循環油路を形成することは、強度
に関連する不利を招くほか、製造上も都合がよくない。As shown in FIG. 5 and the like, forming an auxiliary circulation oil passage by forming a groove in the surface of a reversing bearing or making a hole in the thickness thereof is related to strength. In addition to the disadvantages, it is not convenient for manufacturing.
【0007】すなわち、第一には、二重反転プロペラの
うち最も重要な機械要素である反転軸受に対し全長に及
ぶ溝や穴を形成すると、同一の外形寸法をもち溝も穴も
有しない軸受に比べて幾分かは強度が低下する。そこ
で、軸受に必要な強度をもたせるためには、当該軸受を
太くするなど寸法を増大させる必要が生じる。軸受の寸
法が増すと、その外側に配置される外軸をも太くしなけ
ればならないなど、二重反転プロペラを全体的に大きく
することになり、かなりの重量増加とコストアップとを
招いてしまう。That is, first, when grooves or holes are formed over the entire length of a reversing bearing, which is the most important mechanical element of a contra-rotating propeller, a bearing having the same external dimensions and no grooves or holes is formed. The strength is somewhat reduced as compared with. Therefore, in order to provide the necessary strength to the bearing, it is necessary to increase the size of the bearing, for example, by increasing the thickness. When the size of the bearing increases, the size of the contra-rotating propeller must be increased as a whole, for example, the outer shaft disposed outside the bearing must be made thicker, resulting in a considerable increase in weight and cost. .
【0008】第二には、製造過程において反転軸受の軸
長方向に溝や穴を設けるには、旋盤等によってその軸受
の内・外周や端面を加工するのとは別に、フライス盤や
ボール盤にその軸受をセットして新たな加工をしなけれ
ばならない。一般に反転軸受はかなりの大きさと重量を
有するので、機械加工用の装置の間でそれをハンドリン
グし、セットし直したうえで加工するという工程を一つ
増やすことは、無視できない程度に加工コストを引き上
げることになる。[0008] Second, in order to provide grooves and holes in the axial direction of the reversing bearing in the manufacturing process, apart from machining the inner / outer circumference and the end face of the bearing by using a lathe or the like, the milling machine or drilling machine needs to provide the same. The bearing must be set and new machining must be performed. In general, reversing bearings are quite large and heavy, so adding one step of handling, resetting, and machining between machining devices would add considerable machining costs. Will be raised.
【0009】本発明の目的は、舶用二重反転プロペラに
関し、反転軸受の一方の端面に達した潤滑油を戻りの油
路に近い他方の端面側へ送るための補助循環油路を、上
記のような強度上または製造上の不都合を伴わないよう
に形成した潤滑構造を提供することである。An object of the present invention relates to a contra-rotating propeller for a marine vessel, wherein the auxiliary circulation oil passage for sending the lubricating oil which has reached one end face of the reversal bearing to the other end face close to the return oil passage is provided. An object of the present invention is to provide a lubricating structure formed so as not to cause such strength or manufacturing disadvantages.
【0010】[0010]
【課題を解決するための手段】請求項1〜3に記載した
舶用二重反転プロペラの軸受潤滑構造は、図5のような
軸受潤滑構造において、補助循環油路を、図5と違って
軸受(反転軸受)の内部ではなく、その外側(すなわち
外軸、プロペラボスもしくは下記円筒部材)の部材のう
ちに(すなわちそれらに溝や穴を設けて)形成したこと
をまず共通の特徴とする。ここで、図5のような軸受潤
滑構造とは、二重反転プロペラのうち一方のプロペラを
駆動する円筒状の外軸の内側に軸受(軸受金または軸受
ブシュに相当するもの。反転軸受をさす)が一体化さ
れ、他方のプロペラを駆動する内軸がその軸受の内側を
通されて外軸に対し相対回転自在に配置されており、給
油源から軸受・内軸間(つまりすべり面の間)の隙間に
臨む給油口へ通じていてその隙間に潤滑油を送る往きの
油路と、外軸・内軸間の空間に臨む戻し口から給油源
(タンク)へ通じていて潤滑油を戻す戻りの油路とを備
える舶用二重反転プロペラの軸受潤滑構造をいう。ま
た、補助循環油路とは、往きの油路の上記給油口を出た
うえ軸受と内軸との隙間を上記の戻し口から離れる向き
に流れて軸受の一方の端面に達した潤滑油を、軸受の他
方の端面側(つまり上記の戻し口に近い側)へ送るため
の油路をいう。The bearing lubrication structure for a contra-rotating marine propeller according to claims 1 to 3 differs from the bearing lubrication structure shown in FIG. The first common feature is that it is formed not on the inside of the (reversing bearing) but on the outside (that is, the outer shaft, the propeller boss or the cylindrical member described below) (that is, by providing a groove or a hole in them). Here, the bearing lubrication structure as shown in FIG. 5 means that a bearing (equivalent to a bearing metal or a bearing bush; a reversing bearing) is provided inside a cylindrical outer shaft that drives one of the contra-rotating propellers. ) Is integrated, and an inner shaft for driving the other propeller is passed through the inside of the bearing and is disposed so as to be rotatable relative to the outer shaft. ) And returns to the oil supply source (tank) from the oil passage that leads to the oil supply port facing the gap and sends the lubricating oil to the gap, and the return port that faces the space between the outer shaft and the inner shaft to the oil supply source (tank) A bearing lubrication structure for a marine contra-rotating propeller having a return oil passage. In addition, the auxiliary circulation oil passage means the lubricating oil that has flowed out of the oil supply port of the outgoing oil passage, and has flowed through the gap between the bearing and the inner shaft away from the return opening and has reached one end face of the bearing. Refers to an oil passage for feeding to the other end face side of the bearing (that is, the side close to the return port).
【0011】請求項1〜3に共通するこの構造では、給
油源から往きの油路に潤滑油を送ると、その潤滑油は、
まず給油口から軸受・内軸間(つまりすべり面の間)に
供給されて、そのすべり面の間に油膜を形成する。こう
してすべり面に供給された潤滑油の一部は、軸受のうち
上記の戻し口に近い側(図5の例では船首側)の端面か
ら出て外軸・内軸間の空間を流れ、戻し口から戻りの油
路を通って給油源のタンクに戻る。すべり面に供給され
た潤滑油のうち残りのものは、戻し口から離れる向きに
流れて軸受のもう一方(図5の例では船尾側。反転シー
ルのある側)の端面に達するが、その潤滑油は、軸受よ
りも外側の部材に形成された上記の補助循環油路を通っ
て戻し口に近い端面側へ送られ、他の潤滑油とともに外
軸・内軸間の空間および戻りの油路を通ってタンクに戻
る。In this structure common to the first to third aspects, when lubricating oil is sent from an oil supply source to an outgoing oil passage, the lubricating oil is
First, the oil is supplied from the oil supply port to between the bearing and the inner shaft (that is, between the slip surfaces) to form an oil film between the slip surfaces. A part of the lubricating oil thus supplied to the slip surface exits from the end face of the bearing near the return port (the bow side in the example of FIG. 5), flows through the space between the outer shaft and the inner shaft, and returns. Return from the mouth to the oil supply tank through the return oil passage. The rest of the lubricating oil supplied to the sliding surface flows away from the return port and reaches the other end of the bearing (the stern side in FIG. 5; the side with the reversing seal). The oil is sent to the end face side near the return port through the auxiliary circulation oil passage formed in a member outside the bearing, and together with other lubricating oil, the space between the outer shaft and the inner shaft and the return oil passage. And return to the tank.
【0012】このように、すべり面に供給された潤滑油
が、すべり面の間をどちら向きに進んでも澱みなく流れ
ることから、この軸受潤滑構造では、図5に示した従来
の構造と同様に、反転シールの前面に過大な圧力がかか
るのを防止し、かつ、反転軸受に安定した軸受性能を維
持させることが可能になる。潤滑油がスムーズに流れる
と、反転シールの部分にも、また軸受すべり面のうち戻
し口から遠い部分(反転シールに近い部分)にも、流れ
による適切な圧力損失が生じる結果、圧力が部分的に過
大になることが避けられるからである。As described above, since the lubricating oil supplied to the sliding surface flows without stagnation in either direction between the sliding surfaces, this bearing lubricating structure has the same structure as the conventional structure shown in FIG. In addition, it is possible to prevent an excessive pressure from being applied to the front surface of the reversing seal and to maintain stable bearing performance in the reversing bearing. If the lubricating oil flows smoothly, the appropriate pressure loss due to the flow will occur in the reversal seal and also in the part of the bearing slip surface far from the return port (the part close to the reversal seal), resulting in partial pressure reduction. This is because it is possible to avoid being excessively large.
【0013】しかし、従来の軸受潤滑構造とは異なり、
その補助循環油路を軸受の外側の部材のうちに形成して
いるため、この軸受潤滑構造においては、軸受周辺の機
械的強度の確保および軸受の製造に関して有利である。However, unlike the conventional bearing lubrication structure,
Since the auxiliary circulation oil passage is formed in a member outside the bearing, this bearing lubrication structure is advantageous in securing mechanical strength around the bearing and manufacturing the bearing.
【0014】機械的強度を確保しやすいのは、二重反転
プロペラの重要な機械要素である反転軸受そのものに対
しては溝や穴を形成することがないからである。このよ
うな利点があれば、機械的強度や信頼性を補うために軸
受寸法を大きくする必要がないので、その外側に配置さ
れる外軸をも従来(図5)より細くすることができ、し
たがって二重反転プロペラを全体的に小さくすることが
可能である。これによって、二重反転プロペラの重量軽
減とコストダウンの効果があることは言うまでもない。The reason why mechanical strength is easily ensured is that grooves and holes are not formed in the reversing bearing itself, which is an important mechanical element of the contra-rotating propeller. With such advantages, it is not necessary to increase the bearing dimensions to compensate for mechanical strength and reliability, so that the outer shaft disposed outside can be made thinner than in the past (FIG. 5). Therefore, it is possible to make the contra-rotating propeller smaller overall. This obviously has the effect of reducing the weight of the contra-rotating propeller and reducing the cost.
【0015】製造上有利である理由は、旋盤等によって
軸受の内・外周や端面を機械加工しさえすれば、その軸
受をわざわざフライス盤やボール盤にセットし直して軸
長方向に補助循環油路(溝や穴など)を設ける必要がな
い、という点にある。軸受に形成しない補助循環油路
は、代わりに外軸やプロペラボスなどのどれかに形成す
ることになるが、それらのうち一以上の部材には反転シ
ールの潤滑用油路である溝や孔が形成されるため、補助
循環油路を設ける加工対象部材を適切に選べば、補助循
環油路を形成するためだけの目的で加工対象部材を加工
装置間で運搬しフライス盤やボール盤の適切な位置にセ
ットするという工程を省略できるのである。軸受にして
も、また外軸やプロペラボス等のいずれにしてもかなり
の重量物であるため、そのような工程の一つが省略でき
ると製造コストを相当の幅で低下させることができる。[0015] The reason for the manufacturing advantage is that, as long as the inner / outer circumference and end face of the bearing are machined by a lathe or the like, the bearing is re-set on a milling machine or a drilling machine, and the auxiliary circulation oil passage ( Grooves, holes, etc.). Auxiliary circulating oil passage is not formed in the bearing is will form to any such outer shaft and the propeller boss instead, grooves or holes in one or more members of them is a lubricating oil passage inversion seal Therefore, if the workpiece to be provided with the auxiliary circulation oil passage is appropriately selected, the workpiece is transported between the processing units only for the purpose of forming the auxiliary circulation oil passage, and the appropriate position of the milling machine or drilling machine is selected. The step of setting the value on the first position can be omitted. Since the bearings, the outer shaft, the propeller boss, and the like are quite heavy , any one of such steps can reduce the manufacturing cost to a considerable extent.
【0016】請求項1に記載の軸受潤滑構造は、補助循
環油路を軸受の外側の部材のうちに形成するに関し、と
くにつぎのような構造をとっている点にも特徴がある。
すなわち、プロペラ(のうち一方のもの)のボスを、外
軸のうち軸受を一体化した部分の外周に、閉じた(つま
り閉空間をなす)隙間を介して嵌め入れるとともに、内
外に外軸を貫通して上記の隙間に通じる穴を軸受各端面
の外側の位置(軸受の後端面より船尾側の位置および前
端面より船首側の位置)に設け、それらの穴と上記の隙
間とによって上記の補助循環油路を形成している。閉じ
た隙間を介してプロペラボスを外軸の外周に嵌め入れる
には、たとえば、外軸に形成したフランジ面にプロペラ
ボスの一端面を固定するとともに、外軸に取り付けた環
状部材を同ボスの他方の端面付近に密着して固定するよ
うにすれば容易に実現できる。このような軸受潤滑構造
では、上述の補助循環油路は、軸受のうち前記戻し口か
ら遠い端面の外側位置で外軸を内外に貫通している穴か
ら、上記の隙間に入って軸長方向に通じ、さらに戻し口
に近い軸受端面の外側で外軸を内外に貫通している穴を
通ってその端面(戻し口に近い端面)の側へと続いてい
る。The bearing lubricating structure according to claim 1, the auxiliary循
With respect to forming the ring oil passage in a member outside the bearing,
In particular, it has the following structure.
In other words, the boss of the propeller (one of them) is fitted into the outer periphery of the portion of the outer shaft where the bearing is integrated through a closed (i.e., closed space) gap, and the outer shaft is fitted inside and outside. Holes that penetrate and communicate with the gaps are provided at positions outside the respective end faces of the bearing (positions on the stern side from the rear end face of the bearing and on the bow side from the front end face). An auxiliary circulation oil passage is formed . In order to fit the propeller boss to the outer periphery of the outer shaft through the closed gap, for example, one end surface of the propeller boss is fixed to a flange surface formed on the outer shaft, and an annular member attached to the outer shaft is attached to the boss by the same boss. It can be easily realized if it is fixed close to the other end face. In such a bearing lubrication structure, the above-mentioned auxiliary circulating oil passage enters the above-mentioned gap from the hole passing through the outer shaft inside and outside at a position outside the end face of the bearing far from the return port, and enters the above-mentioned gap in the axial direction. Through the hole passing through the outer shaft in and out of the bearing end face near the return port, and to the end face (end face near the return port).
【0017】請求項1のこの軸受潤滑構造では、上記の
とおり隙間ができるようにプロペラボスの内径と外軸の
該当部分の外径とを定めておけば、その隙間に通じるよ
うに外軸を内外に貫通する短い穴をあけるだけで補助循
環油路ができる。つまり、軸受や外軸、プロペラボスま
たは内軸等のいずれにも、補助循環油路として軸方向に
長い溝や穴をフライス盤やボール盤にて形成する必要が
ないので、製造上とくに有利である。[0017] In this bearing lubricating structure according to claim 1, if set the outer diameter of that portion of the inner diameter and the outer shaft of the propeller boss to allow a gap as described above, the outer shaft so as to communicate the gap An auxiliary circulation oil passage can be created simply by making a short hole that penetrates inside and outside. In other words, there is no need to form a groove or a hole which is long in the axial direction as an auxiliary circulating oil passage in a milling machine or a drilling machine in any of the bearing, the outer shaft, the propeller boss, the inner shaft and the like, which is particularly advantageous in manufacturing.
【0018】なお、この請求項1の構造において軸受周
辺の機械的強度は確保されやすい。補助循環油路を軸受
そのものに設けることはないうえ、隙間を介しながらも
外軸の外周に強固にプロペラボスを取り付けることは強
度を犠牲にすることなく実現でき、また外軸を内外に貫
通する穴も小径で短いものが少数あればよいからであ
る。In the structure of the first aspect, the mechanical strength around the bearing is easily ensured. The auxiliary circulation oil passage is not provided in the bearing itself, and it is possible to firmly attach the propeller boss to the outer periphery of the outer shaft through a gap without sacrificing strength, and penetrate the outer shaft in and out. This is because the holes need only be small in diameter and small in number.
【0019】請求項2の軸受潤滑構造は、補助循環油路
を軸受の外側の部材のうちに形成するに関し、請求項1
の構造とは違って、軸受と外軸との間に他の円筒部材を
配置して軸受および外軸に一体化し、上記の補助循環油
路をその円筒部材の肉厚内を通して形成している−と
いう特徴を有する。ここでいう他の円筒部材としてはた
とえば、外軸・内軸間の空間を半径方向に分割する仕切
り筒であり反転シールの潤滑用油路を形成するための、
いわゆる圧油導入筒の一部を配置することができる。According to a second aspect of the present invention, there is provided a bearing lubrication structure comprising an auxiliary circulation oil passage.
In the outer member of the bearing.
Unlike the above structure , another cylindrical member is disposed between the bearing and the outer shaft to be integrated with the bearing and the outer shaft, and the auxiliary circulation oil passage is formed through the thickness of the cylindrical member. -Has the following characteristics: Examples of the other cylindrical member here include, for example, a partition cylinder that divides a space between an outer shaft and an inner shaft in a radial direction and forms a lubricating oil passage for a reversal seal.
A part of a so-called pressurized oil introduction cylinder can be arranged.
【0020】軸受と外軸との間に一体化する円筒部材
は、外軸や内軸のように動力を伝達する部材ではなく軸
受のように高速度で相対回転するすべり面を有するわけ
でもないので、補助循環油路としての溝や穴をこれに加
工しても強度上の不利はほとんどない。また、動力伝達
をしない同部材は一般的には軽量に構成されるため、こ
れに溝や穴の加工をするのにはあまり手間がかからな
い。つまり、請求項2の軸受潤滑構造においても、軸受
周辺の機械的強度の確保および軸受の製造に関して有利
であるといえる。The cylindrical member integrated between the bearing and the outer shaft is not a member for transmitting power like the outer shaft or the inner shaft, nor does it have a sliding surface that rotates relatively at a high speed like a bearing. Therefore, even if a groove or a hole as an auxiliary circulation oil passage is machined in this, there is almost no disadvantage in strength. In addition, since the member that does not transmit power is generally configured to be light in weight, it does not take much effort to form a groove or a hole in the member. That is, it can be said that the bearing lubrication structure of the second aspect is also advantageous in securing mechanical strength around the bearing and manufacturing the bearing.
【0021】請求項3の軸受潤滑構造は、補助循環油路
を軸受の外側の部材のうちに形成するに関し、請求項1
・2の構造とは違って、上記の補助循環油路を外軸の肉
厚内を通して形成している点にも特徴をもつ。このよう
な構造も、外軸の肉厚内にたとえば反転シールの潤滑用
油路を併せて形成する場合には、製造上の利点をもたら
す。そのような場合、補助循環油路のみの機械加工のた
めに外軸等をボール盤やフライス盤にセットする必要は
ないからである。また、軸受そのものに溝や孔を形成す
るのに比べると、機械的強度の確保は容易である。According to a third aspect of the present invention, there is provided a bearing lubrication structure comprising an auxiliary circulation oil passage.
In the outer member of the bearing.
-Unlike the structure of 2, it is also characterized in that the above-mentioned auxiliary circulation oil passage is formed through the thickness of the outer shaft. Such a structure also provides a manufacturing advantage when, for example, the lubricating oil passage of the reversal seal is formed within the thickness of the outer shaft. In such a case, it is not necessary to set an outer shaft or the like on a drilling machine or a milling machine for machining only the auxiliary circulation oil passage. Also, it is easier to secure mechanical strength than forming a groove or a hole in the bearing itself.
【0022】請求項4の軸受潤滑構造は、以上の各特徴
に加え、往きの油路を内軸の内部に形成していて給油口
を内軸の外周面上に設け、戻りの油路については、外軸
の内周面上に戻し口を備え、外軸を内外に貫通して船体
内の固定配管に通じるように形成している、という特徴
をも有する。給油源から出て同じ給油源(のタンク)に
戻るまで潤滑油を円滑に循環させるためには、被潤滑箇
所等に一定向きに潤滑油が流れるよう油路を形成せねば
ならないが、この請求項4のように往きの油路と戻りの
油路とを別の箇所に分けて設けるなら、特別な仕切り部
材を設けなくとも(または最小限の仕切り部材を設ける
だけで)一定向きの流れを形成することができる。ま
た、往きの油路を内軸の内部に形成してその給油口を内
軸の外周面上に設けたので、軸受を半径方向に貫通する
穴をあけなくとも、軸受と内軸との間にあるすべり面に
対して給油することが可能である。軸受に対して半径方
向にも穴をあける必要がない場合、やはり軸受の強度確
保が容易であることは言うまでもない。According to a fourth aspect of the present invention, in addition to the features described above, a forward oil passage is formed inside the inner shaft, an oil supply port is provided on the outer peripheral surface of the inner shaft, and a return oil passage is provided. Is characterized in that a return port is provided on the inner peripheral surface of the outer shaft, and the outer shaft is formed so as to penetrate the outer shaft in and out to communicate with the fixed piping in the hull. Out refueling source in order to smoothly circulate the lubricant oil to return to the same oil supply source (tank) is must be made from the oil passage so that the lubricating oil flows through the constant orientation to the lubricating points and the like, this claim If the outgoing oil passage and the return oil passage are separately provided as in item 4 , the flow in a certain direction can be performed without providing a special partition member (or by providing a minimum partition member). Can be formed. In addition, since the oil passage is formed inside the inner shaft and its oil supply port is provided on the outer peripheral surface of the inner shaft, the hole between the bearing and the inner shaft can be formed without making a hole penetrating the bearing in the radial direction. It is possible to refuel the slip surface at If it is not necessary to make a hole in the bearing in the radial direction, it is needless to say that the strength of the bearing can be easily ensured.
【0023】[0023]
【発明の実施の形態】図1〜図3に本発明の実施につい
て一形態を示す。図1は、図3に示した二重反転プロペ
ラ1のうち船尾側の反転軸受5とその潤滑構造を示す縦
断面図、図2は、やはり図3の二重反転プロペラ1にお
ける船首側の反転軸受6とその潤滑構造を示す縦断面図
である。また、図3は、二重反転プロペラ1などを全体
的に示す概要図である。1 to 3 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional view showing a stern-side reversing bearing 5 and its lubricating structure in the contra-rotating propeller 1 shown in FIG. 3, and FIG. FIG. 3 is a longitudinal sectional view showing a bearing 6 and a lubricating structure thereof. FIG. 3 is a schematic diagram generally showing the contra-rotating propeller 1 and the like.
【0024】図3のように、二重反転プロペラ1におけ
る前後二つのプロペラ3・2は、中空の外軸20および
その内部に通された内軸10に対してそれぞれ取り付け
られており、各軸によって互いに逆向きに回転駆動され
る。外軸20は、船体4を内外に貫通する部分(および
図示しない船首側の部分)において動圧型すべり軸受で
ある船尾管軸受4aによって支持されており、またその
船首側の端部において継手7aを介し中空の駆動軸7に
接続されている。外軸20の内側であって船尾側と船首
側との各部分には、締まり嵌めの結合によって反転軸受
(の軸受ブシュ)5および6がそれぞれ一体化されてお
り、それら軸受5および6の内側に内軸10が相対回転
自在に支持されている。プロペラ3から外軸20にかな
りの荷重が作用することを考慮して、船尾側に配置され
た軸受5の位置は、そのプロペラ3のボス3aの内側と
されている。As shown in FIG. 3, the front and rear propellers 3.2 of the contra-rotating propeller 1 are attached to a hollow outer shaft 20 and an inner shaft 10 passed through the inside thereof, respectively. Are rotated in opposite directions. The outer shaft 20 is supported by a stern tube bearing 4a, which is a dynamic pressure-type slide bearing, at a portion penetrating the hull 4 in and out (and a portion on the bow side not shown), and a joint 7a is provided at an end on the bow side. It is connected to the hollow drive shaft 7 through the intermediary. Reversing bearings (bearing bushes) 5 and 6 are integrated with each other on the inner side of the outer shaft 20 and on the stern side and the bow side by interference fit. The inner shaft 10 is supported so as to be relatively rotatable. Considering that a considerable load acts on the outer shaft 20 from the propeller 3, the position of the bearing 5 arranged on the stern side is set inside the boss 3a of the propeller 3.
【0025】軸受5・6は、軸受面にホワイトメタルを
施した鋳鉄を材料とし、それぞれの内周面と内軸10の
外周面との間をすべり面としたすべり軸受であって、そ
のすべり面の間に外部から潤滑油を圧送することにより
油膜を形成する静圧軸受である。内軸10と外軸20と
は、軸受5・6のうちこのように油膜が形成されたすべ
り面を境にして、互いに逆向きにほぼ等速度で回転する
わけである。船尾側にある軸受5における船尾側端面の
そば、および船首側にある軸受6の船首側端面のそばに
は、すべり面に供給された潤滑油を漏出させないよう、
反転シール23・24がそれぞれ配置されている。Each of the bearings 5 and 6 is a slide bearing made of cast iron having a bearing surface coated with white metal and having a sliding surface between each inner peripheral surface and the outer peripheral surface of the inner shaft 10. This is a hydrostatic bearing that forms an oil film by externally feeding lubricating oil between surfaces. The inner shaft 10 and the outer shaft 20 rotate at substantially the same speed in opposite directions to each other with respect to the sliding surfaces of the bearings 5 and 6 on which the oil film is formed as described above. In order to prevent the lubricating oil supplied to the slip surface from leaking near the stern side end face of the bearing 5 on the stern side and near the bow side end face of the bearing 6 on the bow side.
Inverting seals 23 and 24 are arranged respectively.
【0026】反転軸受5・6の上記すべり面に油膜を形
成するための潤滑油は、図3のように、船体4に搭載さ
れている給油源31から送られて再びそれに戻される循
環経路に沿って供給される。当該経路の概要はつぎのと
おりである。潤滑油はまず、給油源31から送り出され
て往きの油路32を通り、上記のすべり面、すなわち軸
受5・6と内軸10との隙間に供給される。一方の軸受
5におけるすべり面からあふれ出た潤滑油は内軸10・
外軸20間の油路33を船首側(図の右方)へ向かって
流れ、軸受6のすべり面から出た潤滑油は同様の油路3
5を船尾側(図の左方)へ流れたうえ、外軸20を内外
に貫通する戻し口37aに流入し、それより戻りの油路
37に入って給油源31へ戻る。なお、図3のように、
給油源31のうちにはタンク31aと高圧の給油ポンプ
31bとが含まれる。往きの油路32のうちには、固定
された給油配管32aのほか、内軸10の内部において
図示のとおり軸長方向および半径方向にそれぞれ形成さ
れた通孔32b・32c・32e、ならびに各軸受5・
6のすべり面の間に望む給油口32d・32fが含まれ
る。また、戻りの油路37としては、上記の戻し口37
aに環状のスペース37bが続き、さらに船体4内の通
孔37cおよび固定配管37d(空気抜き37eを含
む)が接続されている。As shown in FIG. 3, the lubricating oil for forming an oil film on the sliding surfaces of the reversing bearings 5 and 6 is sent from an oil supply source 31 mounted on the hull 4 and returned to the circulation path again. Supplied along. The outline of the route is as follows. First, the lubricating oil is sent from the oil supply source 31 and passes through the outgoing oil passage 32, and is supplied to the above-mentioned slip surface, that is, the gap between the bearings 5 and 6 and the inner shaft 10. The lubricating oil overflowing from the slip surface of one bearing 5 is
The lubricating oil flowing through the oil passage 33 between the outer shafts 20 toward the bow side (to the right in the figure) and coming out of the slip surface of the bearing 6 is subjected to the same oil passage 3
5 flows to the stern side (left side in the figure), flows into the return port 37a penetrating the outer shaft 20 in and out, enters the return oil passage 37, and returns to the refueling source 31. In addition, as shown in FIG.
The refueling source 31 includes a tank 31a and a high-pressure refueling pump 31b. In the outgoing oil passage 32, in addition to the fixed oil supply pipe 32a, through holes 32b, 32c, and 32e formed in the inner shaft 10 in the axial and radial directions, respectively, as shown in the drawing, and each bearing. 5.
The desired oil supply ports 32d and 32f are included between the 6 sliding surfaces. The return oil passage 37 includes the return port 37 described above.
a is followed by an annular space 37b, and further connected to a through hole 37c in the hull 4 and a fixed pipe 37d (including an air vent 37e).
【0027】内軸10内の通孔32b・32cを経て給
油口32dから軸受5のすべり面に給油された潤滑油
は、一部がそのすべり面を船首側へ流れて上記の油路3
3から戻し口37aへ至るのに対し、残りの潤滑油はす
べり面を船尾側(戻し口37aから遠い)へ流れて反転
シール23の前面に達する。このように反転シール23
の前面に達した潤滑油についても、戻し口37aへ至る
スムーズな流れが形成されないと圧力が過大になって反
転シール23を傷めたり軸受5の性能を損なったりする
恐れがある。そこで、軸受5のうち船尾側の端部付近
(反転シール23の前面付近)から船首側の端部付近へ
かけて図1のような補助循環油路34を形成し、これら
を含めて軸受5の潤滑構造を構成している。A part of the lubricating oil supplied to the slip surface of the bearing 5 from the oil inlet 32d through the through holes 32b and 32c in the inner shaft 10 partially flows on the slip surface to the bow side, and the above-mentioned oil passage 3
3, while the remaining lubricating oil flows on the slip surface to the stern side (far from the return port 37a) and reaches the front surface of the reversal seal 23. Thus, the reversal seal 23
If the lubricating oil that has reached the front surface of the second member does not form a smooth flow to the return port 37a, the pressure may be excessively high, damaging the reversal seal 23 or impairing the performance of the bearing 5. Therefore, an auxiliary circulation oil passage 34 as shown in FIG. 1 is formed from the vicinity of the end on the stern side (near the front surface of the reversing seal 23) to the vicinity of the end on the bow side of the bearing 5, and includes the bearing 5 Of the lubrication structure.
【0028】補助循環油路34は、軸受5そのものに形
成するのではなく、図1のとおり外軸20とその外側に
形成している。すなわち、軸受5の後端面よりも船尾側
であって反転シール23よりも前方の位置に外軸20を
内外に貫通する穴22aをあけるとともに、軸受5の前
端面より船首側の位置にも同様の穴22cをあけ、ま
た、それらと連通する隙間22bを外軸20の外周面と
プロペラ3のボス3aの内周面との間に設けている。隙
間22bは厚さ数mmとして外軸20の外側全周に形成
し、穴22a・22cは、それぞれ直径を数十mm以下
とし周方向に間隔をおいて数箇所に設けるのがよい。軸
受5のすべり面を船尾側へ流れて反転シール23の前面
へ達した潤滑油は、上記の穴22a・隙間22b・穴2
2cからなる補助循環油路34を船首側へ向かって流れ
ることにより、外軸20・内軸10間の油路33に合流
して戻し口37a(図3)へ至る。このような補助循環
油路34は、軸受5そのものに穴加工等を加えたもので
はないので、軸受5の機械的強度を低下させることがな
い。また、ボス3aの内径と外軸20の外径との間に直
径差を設けるとともに穴22a・22cを何個かあける
だけで容易にその油路34が形成され、しかもその穴2
2a・22cは長さが短く位置の精度も高くする必要が
ないので、軸受5を軸長方向に貫通するように穴をあけ
る場合に比べると加工コストが相当に低減することにな
る。The auxiliary circulation oil passage 34 is not formed in the bearing 5 itself, but is formed outside the outer shaft 20 as shown in FIG. That is, a hole 22a that penetrates the outer shaft 20 inward and outward is formed at a position on the stern side of the rear end face of the bearing 5 and in front of the reversing seal 23, and a similar position is formed on the bow side of the front end face of the bearing 5. And a gap 22b communicating therewith is provided between the outer peripheral surface of the outer shaft 20 and the inner peripheral surface of the boss 3a of the propeller 3. The gap 22b has a thickness of several mm and is formed on the entire outer periphery of the outer shaft 20, and the holes 22a and 22c are preferably provided at several places with a diameter of several tens mm or less and spaced in the circumferential direction. The lubricating oil that has flowed to the stern side of the bearing 5 to the stern side and reached the front surface of the reversing seal 23 is subjected to the above-described hole 22a, gap 22b,
By flowing toward the bow side through the auxiliary circulation oil passage 34 composed of 2c, it joins the oil passage 33 between the outer shaft 20 and the inner shaft 10 to reach the return port 37a (FIG. 3). Since the auxiliary circulation oil passage 34 is not obtained by adding a hole or the like to the bearing 5 itself, the mechanical strength of the bearing 5 is not reduced. In addition, the oil passage 34 is easily formed by providing a diameter difference between the inner diameter of the boss 3a and the outer diameter of the outer shaft 20 and opening a few holes 22a and 22c.
Since the lengths 2a and 22c are short and the positional accuracy does not need to be high, the processing cost is considerably reduced as compared with the case where a hole is formed so as to penetrate the bearing 5 in the axial direction.
【0029】外軸20とプロペラ3のボス3aとの間に
隙間22bを設けるため、前者の外径に比べて後者の内
径を大きくとっているが、それにもかかわらずボス3a
が不安定にならないよう、外軸20に対するボス3aの
取付け部分には特別な構成を採用している。すなわち、
外軸20の一部(軸受5を配置する箇所のすぐ前方)に
フランジ21を形成したうえ、ボス3aの船首側の端面
をそのフランジ21の船尾側の端面に接合してボルト
(図示せず)等により両者を固着したのである。また、
ボス3aの船尾側の端面付近においては、図1のように
ボス3aの内周面と外軸20の端面とに密着するように
シール保持リング23aを取り付けることにより、隙間
22bを潤滑油の外部漏洩がない閉じた空間にしてい
る。In order to provide a gap 22b between the outer shaft 20 and the boss 3a of the propeller 3, the inner diameter of the latter is made larger than the outer diameter of the former.
The boss 3a is attached to the outer shaft 20 with a special structure so that the boss 3a does not become unstable. That is,
A flange 21 is formed on a part of the outer shaft 20 (immediately in front of the place where the bearing 5 is arranged), and a bow-side end face of the boss 3a is joined to a stern-side end face of the flange 21 to form a bolt (not shown). ) And the like were fixed together. Also,
In the vicinity of the end face of the boss 3a on the stern side, as shown in FIG. 1, by attaching a seal holding ring 23a so as to be in close contact with the inner peripheral face of the boss 3a and the end face of the outer shaft 20, the gap 22b is formed outside the lubricating oil. It is a closed space without leakage.
【0030】図3に示す二重反転プロペラ1では、船首
側の反転軸受6においても、すべり面を前記の戻し口3
7aから遠い側へ流れる潤滑油がある。すなわち、内軸
10内の通孔32b・32eおよび給油口32fから軸
受6のすべり面に供給された潤滑油のうち、一部はその
すべり面を船尾側へ流れて油路35から戻し口37aへ
至るものの、残りの潤滑油は、すべり面を船首側(戻し
口37aから遠い方)へ流れて反転シール24の前面に
達する。圧力の過剰な増大を防止して反転シール24を
保護し軸受6に本来の性能を発揮させるためには、前者
の潤滑油と同様に、後者の潤滑油をもスムーズに戻し口
37aへ送る必要がある。そこで、軸受6のうち船首側
の端部付近(反転シール24の後ろ向き面の付近)から
船尾側へかけて図2のように補助循環油路36を形成
し、これらを含めて軸受6の潤滑構造を構成している。In the contra-rotating propeller 1 shown in FIG. 3, the sliding surface of the reversing bearing 6 on the bow side is also adjusted to the return port 3 described above.
There is lubricating oil flowing to the side far from 7a. That is, of the lubricating oil supplied to the slip surface of the bearing 6 from the through holes 32b and 32e in the inner shaft 10 and the oil supply port 32f, a part of the lubricating oil flows on the slip surface toward the stern side and returns from the oil passage 35 to the return port 37a. However, the remaining lubricating oil flows on the slip surface toward the bow (farther from the return port 37a) and reaches the front surface of the reversal seal 24. In order to prevent the pressure from excessively increasing, protect the reversal seal 24, and allow the bearing 6 to exhibit its original performance, it is necessary to smoothly send the latter lubricating oil to the return port 37a as well as the former lubricating oil. There is. Therefore, an auxiliary circulation oil passage 36 is formed from the vicinity of the end of the bearing 6 on the bow side (near the rearward facing surface of the reversing seal 24) to the stern side, as shown in FIG. Make up the structure.
【0031】船首側の軸受6についての補助循環油路3
6も、軸受6そのものではなくその外側の部材に形成し
ている。すなわちこの実施形態では、反転シール23・
24への潤滑油供給のための往路・復路を半径方向に区
分して形成するとともに各種センサの信号線を一定位置
に配置することを目的として、図3のように外軸20の
内側に圧油導入筒40を装着しているが、この圧油導入
筒40の端部を軸受6の外側にまで延ばしてそこに厚肉
部40aを形成したうえこれを軸受6および外軸20に
締まり嵌めさせて一体化し、その厚肉部40aの内部に
補助循環油路36を設けている。その補助循環油路36
の詳細は図2に示すとおりである。つまり、厚肉部40
aのうち軸受6の前端面よりも船首側(反転シール24
よりも船尾側)となる箇所に内面から非貫通の穴40b
をあけるとともに、厚肉部40aを軸長方向に貫通して
穴40bと連通する穴40cをあけている。圧油導入筒
40にはまた厚肉部40b以外の箇所で内外に貫通する
穴40dを形成したので、それらの穴40b・40c・
40dによって一連の補助循環油路36を構成したこと
になる。穴40b・40c・40dは、それぞれ直径を
数mm〜数十mmとし圧油導入筒40の周方向に間隔を
おいて数箇所に設ければ十分である。軸受6のすべり面
を船首側へ流れて反転シール24の後ろ向きの面に達し
た潤滑油は、上記の補助循環油路36を船尾側へ向かっ
て流れ、外軸20・内軸10間の油路35に合流して図
3の戻し口37aへ至る。この潤滑油は、船尾側の軸受
5に供給された潤滑油とともに、戻し口37aから戻り
の油路37を通って給油源31のタンク31aへ戻る。Auxiliary circulating oil passage 3 for bearing 6 on bow side
6 is formed not on the bearing 6 itself but on a member outside thereof. That is, in this embodiment, the reversal seal 23
In order to form the outward path and the return path for supplying the lubricating oil to the radial direction 24 in the radial direction and to arrange the signal lines of various sensors at fixed positions, as shown in FIG. The oil introduction cylinder 40 is mounted, but the end of the pressure oil introduction cylinder 40 is extended to the outside of the bearing 6 to form a thick portion 40a, which is tightly fitted to the bearing 6 and the outer shaft 20. The auxiliary circulation oil passage 36 is provided inside the thick portion 40a. The auxiliary circulation oil passage 36
Are as shown in FIG. That is, the thick portion 40
a of the forward end face of the bearing 6 on the bow side (reversal seal 24
Hole 40b that is not penetrated from the inner surface to
And a hole 40c penetrating through the thick portion 40a in the axial direction and communicating with the hole 40b. Holes 40d penetrating inside and outside are formed in the pressure oil introducing cylinder 40 at locations other than the thick portion 40b.
40d constitutes a series of auxiliary circulation oil passages 36. It is sufficient that the holes 40b, 40c, and 40d have diameters of several millimeters to several tens of millimeters, and are provided at several locations at intervals in the circumferential direction of the pressure oil introduction cylinder 40. The lubricating oil flowing on the slip surface of the bearing 6 toward the bow and reaching the rearward surface of the reversing seal 24 flows through the auxiliary circulation oil passage 36 toward the stern side, and the oil between the outer shaft 20 and the inner shaft 10. It joins the road 35 and reaches the return port 37a in FIG. This lubricating oil returns to the tank 31a of the oil supply source 31 through the return oil passage 37 from the return port 37a together with the lubricating oil supplied to the bearing 5 on the stern side.
【0032】図2の補助循環油路36も、軸受6に穴加
工等を施したものではないので機械的強度に関する不利
を招くことがない。また、動力伝達部材ではなく高速度
のすべり面を有してもいない圧油導入筒40に対する穴
あけは、被加工物(この場合は圧油導入筒40)の取り
扱いや加工精度等に関して特に細心の注意を払う必要が
ないので加工が容易である。しかも、圧油導入筒40に
は反転シール23・24への潤滑油供給のための穴(図
示せず)があけられるため、これに上記の穴40b・4
0c・40dをあけるにも特別の準備が不要である。つ
まり、前者の穴加工のためにボール盤等に圧油導入筒4
0がセットされたとき後者の穴(すなわち穴40b・4
0c・40d)をも同時に加工することができ、多少で
も加工の手間を省けることになる。The auxiliary circulating oil passage 36 shown in FIG. 2 does not suffer from disadvantages in mechanical strength because the bearing 6 is not formed by drilling or the like. Drilling of the pressure oil introducing cylinder 40, which is not a power transmission member and does not have a high-speed sliding surface, is particularly meticulous with respect to handling and processing accuracy of a workpiece (in this case, the pressure oil introducing cylinder 40). Processing is easy because no attention is required. In addition, since a hole (not shown) for supplying lubricating oil to the reversing seals 23 and 24 is formed in the pressure oil introducing cylinder 40, the holes 40b and 4 are formed in the holes.
No special preparation is required to open 0c and 40d. In other words, the pressurized oil introducing cylinder 4
When 0 is set, the latter hole (ie, hole 40b.4)
0c and 40d) can also be processed at the same time, and the processing time can be saved to some extent.
【0033】なお、船尾側においても圧油導入筒40の
端部の厚肉部を延ばして外軸20と軸受5との間に固定
したうえ、その厚肉部の内部に補助循環油路としての穴
をあける等の実施形態をとることも可能である。したが
って、図2のような実施形態は、船首側の軸受6のみに
は限らず船尾側の軸受5に対しても採用され得るもので
ある。On the stern side, the thick portion at the end of the pressure oil introducing cylinder 40 is extended to be fixed between the outer shaft 20 and the bearing 5, and an auxiliary circulation oil passage is formed inside the thick portion. It is also possible to take an embodiment such as making a hole. Therefore, the embodiment as shown in FIG. 2 can be adopted not only for the bow-side bearing 6 but also for the stern-side bearing 5.
【0034】つづく図4には、本発明について他の実施
形態を示す。図4(a)は、図3に示した二重反転プロペ
ラ1のうち船尾側の反転軸受5とその潤滑構造に関して
図1以外の形態を示す縦断面図、同(b)は同(a)におけ
るb−b断面図である。図1〜図3の形態と同一の構成
部分には同じ符号を付けている(同じ符号を付けたうえ
以下で説明を省略した部分は、図1〜図3の構成と差異
がない)。FIG. 4 shows another embodiment of the present invention. FIG. 4A is a longitudinal sectional view showing a configuration other than FIG. 1 regarding the stern-side reversing bearing 5 and its lubrication structure in the contra-rotating propeller 1 shown in FIG. 3, and FIG. It is bb sectional drawing in. The same components as those in the embodiments of FIGS. 1 to 3 are denoted by the same reference numerals (portions which are denoted by the same reference numerals and whose description is omitted below do not differ from the configurations of FIGS. 1 to 3).
【0035】内軸10内の通孔32b・32cおよび給
油口32dから軸受5のすべり面に給油された潤滑油の
うち、すべり面を船尾側(図の左方。戻し口から遠い
方)へ流れて反転シール23の前面に達した潤滑油をス
ムーズに戻し口37a(図3)へ流すために、図4の潤
滑構造では、外軸20(鋼製)の肉厚のうちに補助循環
油路38を形成している。すなわち、軸受5の後端面よ
りも船尾側であって反転シール23よりも前方の位置、
および軸受5の前端面より船首側の位置に、外軸20の
内面から厚みの中ほどの部分に達する非貫通の穴22e
・22gをそれぞれあけるとともに、外軸20の厚みの
中ほどに軸長方向に穴22fを形成して穴22e・22
gと連通させ、これら一連の穴22e・22f・22g
を補助循環油路38としている。やはり銅合金製である
軸受5そのものには穴は形成していない。反転シール2
3の前面へ達した潤滑油は、このような補助循環油路3
8を船首側へ向かって流れることにより、外軸20・内
軸10間の油路33に合流して戻し口37a(図3)へ
至ることになる。なお、実際に穴22fを形成するにあ
たっては、外軸20の船尾側端面からボール盤等によっ
てドリル加工をしたのち、同端面にある開口をプラグ等
にて塞ぐ方法をとっている。穴22e・22f・22g
は、いずれも直径を10mm前後として周方向に間隔を
おいた数箇所に設ければよいが、プロペラ3のボス3a
と軸受5との間での外軸20の厚さは比較的厚いため、
このような穴加工に特別の困難はともなわず、また外軸
20において強度上の不利はほとんど発生しない。な
お、このような補助循環油路38は船首側の軸受6の周
辺に形成することも可能である。Of the lubricating oil supplied to the sliding surface of the bearing 5 from the through holes 32b and 32c and the oil supply port 32d in the inner shaft 10, the sliding surface is moved toward the stern side (left side in the figure, far from the return port). In order to smoothly flow the lubricating oil that has flowed and reached the front surface of the reversing seal 23 to the return port 37a (FIG. 3), the lubricating structure of FIG. A path 38 is formed. That is, a position on the stern side of the rear end face of the bearing 5 and in front of the reversal seal 23,
And a non-penetrating hole 22e extending from the inner surface of the outer shaft 20 to a middle thickness portion at a position on the bow side of the front end surface of the bearing 5.
22g, and a hole 22f is formed in the axial direction in the middle of the thickness of the outer shaft 20 to form a hole 22e.
g, and a series of these holes 22e, 22f, 22g
Is an auxiliary circulation oil passage 38. No holes are formed in the bearing 5 itself, which is also made of a copper alloy. Inverted seal 2
The lubricating oil reaching the front of the auxiliary circulation oil passage 3
8 flows toward the bow side and joins the oil passage 33 between the outer shaft 20 and the inner shaft 10 to reach the return port 37a (FIG. 3). To actually form the hole 22f, a method is used in which drilling is performed from the stern side end surface of the outer shaft 20 with a drilling machine and the like, and the opening on the end surface is closed with a plug or the like. Holes 22e / 22f / 22g
May be provided at several places circumferentially spaced with a diameter of about 10 mm, but the boss 3a of the propeller 3
Since the thickness of the outer shaft 20 between the bearing and the bearing 5 is relatively thick,
There is no particular difficulty in drilling such holes, and almost no disadvantage in strength occurs in the outer shaft 20. Note that such an auxiliary circulation oil passage 38 can be formed around the bearing 6 on the bow side.
【0036】[0036]
【発明の効果】請求項1〜3にそれぞれ記載した舶用二
重反転プロペラの軸受潤滑構造は、補助循環油路、つま
り反転軸受のすべり面に供給された潤滑油のうち戻し口
から遠い側へ流れたものを戻し口の側へ戻すための油路
を、反転軸受の内部以外の部材のうちに形成して軸受そ
のものには形成しないものであるため、軸受周辺の機械
的強度の確保および軸受の製造に関して利点をもたら
す。機械的強度を確保しやすい点は、軸受寸法を小さく
し、したがってその外側の外軸をも細くして二重反転プ
ロペラを全体的に小さくすることを可能にする。またそ
の点は、二重反転プロペラの重量を軽減し、コストを低
減することにもつながる。製造上有利であるのは、補助
循環油路の形成のみの目的でわざわざ軸受をボール盤等
にセットし直す必要がないことによるが、この点も、二
重反転プロペラの製造コストを低減する効果に通じる。The bearing lubricating structure for a contra-rotating marine propeller according to any one of claims 1 to 3 has an auxiliary circulating oil passage, that is, the lubricating oil supplied to the sliding surface of the reversing bearing, which is farther from the return port. An oil passage for returning the flowed material to the return port side is formed in a member other than the inside of the reversing bearing and is not formed in the bearing itself, so that mechanical strength around the bearing is secured and the bearing is secured. Provides advantages with respect to the manufacture of The point that it is easy to ensure mechanical strength makes it possible to reduce the size of the bearing, and thus also make the outer shaft outside thereof smaller, so that the contra-rotating propeller can be made smaller overall. This also leads to a reduction in the weight of the contra-rotating propeller and a reduction in cost. The advantage in manufacturing is that it is not necessary to reset the bearing to a drilling machine etc. only for the purpose of forming the auxiliary circulation oil passage, but this point also has the effect of reducing the manufacturing cost of the contra-rotating propeller. Lead.
【0037】請求項1に記載の軸受潤滑構造は、プロペ
ラボスと外軸との間に閉じた隙間を設けること等によっ
て補助循環油路を形成したものであり、軸受や外軸、プ
ロペラボスまたは内軸等のいずれにも長い溝や穴を形成
することを要しないため、製造上とくに有利である。The bearing lubricating structure according to claim 1 is obtained by forming the auxiliary circulation oil path, such as by providing a closed gap between the propeller boss and the outer shaft, bearings and the outer shaft, the propeller boss or Since it is not necessary to form a long groove or hole in any of the inner shaft and the like, it is particularly advantageous in manufacturing.
【0038】請求項2の軸受潤滑構造は、軸受と外軸と
の間に他の円筒部材を配置してこれに補助循環油路を形
成するものであり、やはり軸受周辺の機械的強度の確保
および軸受の製造に関して有利である。円筒部材として
いわゆる圧油導入筒を利用する場合には、補助循環油路
としての穴などをとくに形成しやすい。In the bearing lubricating structure according to the second aspect , another cylindrical member is disposed between the bearing and the outer shaft to form an auxiliary circulation oil passage therein, which also ensures mechanical strength around the bearing. And the manufacture of bearings. When a so-called pressure oil introduction cylinder is used as the cylindrical member, a hole or the like as an auxiliary circulation oil passage is particularly easily formed.
【0039】請求項3の軸受潤滑構造は、補助循環油路
を外軸の肉厚内を通して形成するため、たとえば外軸の
肉厚内に反転シールの潤滑用油路を併せて形成する場合
などに製造上の利点をもたらす。軸受そのものには溝や
孔を形成しないので、やはり機械的強度の確保が容易で
ある。In the bearing lubrication structure of the third aspect , the auxiliary circulation oil passage is formed through the thickness of the outer shaft. For example, when the lubrication oil passage of the reversing seal is formed within the thickness of the outer shaft, etc. Provides manufacturing advantages. Since no grooves or holes are formed in the bearing itself, it is easy to secure mechanical strength.
【0040】請求項4の軸受潤滑構造は、さらに、往き
の油路を内軸の内部に形成し戻りの油路を外軸の内外貫
通口として形成するなどの構成を有するため、潤滑油に
一定向きの流れを形成しやすい。また、軸受を半径方向
に貫通する穴をあけなくともすべり面へ給油を実現でき
るので、軸受の強度確保が一層容易である。The bearing lubricating structure according to claim 4 further has a structure in which the outgoing oil passage is formed inside the inner shaft and the return oil passage is formed as the inner and outer through holes of the outer shaft. It is easy to form a flow in a certain direction. Further, since lubrication can be achieved on the sliding surface without making a hole penetrating the bearing in the radial direction, it is easier to secure the strength of the bearing.
【図1】本発明の実施についての一形態を示す図であ
り、図3に示した二重反転プロペラ1のうち船尾側の反
転軸受5とその潤滑構造を示す縦断面図である。FIG. 1 is a view showing an embodiment of the present invention, and is a longitudinal sectional view showing a stern-side reversing bearing 5 and a lubricating structure thereof in a contra-rotating propeller 1 shown in FIG.
【図2】図3の二重反転プロペラ1における船首側の反
転軸受6とその潤滑構造を示す縦断面図である。FIG. 2 is a longitudinal sectional view showing a reversing bearing 6 on the bow side of the contra-rotating propeller 1 of FIG. 3 and a lubricating structure thereof.
【図3】二重反転プロペラ1などを全体的に示す概要図
である。FIG. 3 is a schematic diagram generally showing a contra-rotating propeller 1 and the like.
【図4】本発明について他の実施形態を示すもので、図
4(a)は、図3に示した二重反転プロペラ1のうち船尾
側の反転軸受5とその潤滑構造に関して図1以外の形態
を示す縦断面図、同(b)は同(a)におけるb−b断面図
である。FIG. 4 shows another embodiment of the present invention. FIG. 4 (a) shows a stern-side reversing bearing 5 of the contra-rotating propeller 1 shown in FIG. FIG. 4B is a longitudinal sectional view showing the configuration, and FIG. 4B is a bb sectional view in FIG.
【図5】図5(a)は、従来の軸受潤滑構造を含む舶用二
重反転プロペラ51について船外部分を示す縦断面図、
また同(b)は、同(a)におけるb−b断面図である。FIG. 5 (a) is a longitudinal sectional view showing an outboard part of a contra-rotating marine propeller 51 including a conventional bearing lubrication structure,
(B) is a cross-sectional view taken along line bb in (a).
1 二重反転プロペラ 2・3 プロペラ 3a ボス 5・6 軸受(反転軸受) 10 内軸 20 外軸 31 給油源 32 往きの油路 32d・32f 給油口 34・36・38 補助循環油路 37 戻りの油路 37a 戻し口 40 圧油導入筒(円筒部材) DESCRIPTION OF SYMBOLS 1 Contra-rotating propeller 2.3 Propeller 3a Boss 5.6 Bearing (reversing bearing) 10 Inner shaft 20 Outer shaft 31 Oil supply source 32 Outgoing oil passage 32d / 32f Oil supply port 34/36/38 Auxiliary circulation oil passage 37 Return Oil passage 37a Return port 40 Pressure oil introduction cylinder (cylindrical member)
フロントページの続き (56)参考文献 特開 平8−74851(JP,A) 特開 平6−107285(JP,A) 特開 平9−48397(JP,A) 特開 平7−69292(JP,A) 実開 平3−72099(JP,U) 実公 平5−23437(JP,Y2) (58)調査した分野(Int.Cl.6,DB名) B63H 23/36 B63H 5/10 Continuation of the front page (56) References JP-A-8-74851 (JP, A) JP-A-6-107285 (JP, A) JP-A-9-48397 (JP, A) JP-A-7-69292 (JP, A) , A) Japanese Utility Model Hei 3-72099 (JP, U) Japanese Utility Model Hei 5-23437 (JP, Y2) (58) Field surveyed (Int. Cl. 6 , DB name) B63H 23/36 B63H 5/10
Claims (4)
を駆動する円筒状の外軸の内側に軸受が一体化され、他
方のプロペラを駆動する内軸がその軸受の内側を通され
て外軸に対し相対回転自在に配置されており、 給油源から軸受・内軸間の隙間に臨む給油口へ通じてい
てその隙間に潤滑油を送る往きの油路と、外軸・内軸間
の空間に臨む戻し口から給油源へ通じていて潤滑油を戻
す戻りの油路を備える舶用二重反転プロペラの軸受潤滑
構造であって、 往きの油路の上記給油口を出たうえ軸受と内軸との隙間
を上記の戻し口から離れる向きに流れて軸受の一方の端
面に達した潤滑油を、軸受の他方の端面側へ送るための
補助循環油路が、軸受の内部に形成されることなく、そ
の外側の部材のうちに形成されていること、すなわち、 プロペラのボスが、外軸のうち軸受を一体化した部分の
外周に、閉じた隙間を介して嵌め入れられるとともに、
内外に外軸を貫通して上記の隙間に通じる穴が軸受の各
端面より外側の位置に設けられ、それらの穴と上記の隙
間とによって上記の補助循環油路が形成されていること
を特徴とする舶用二重反転プロペラの軸受潤滑構造。A bearing is integrated inside a cylindrical outer shaft that drives one of the contra-rotating propellers, and an inner shaft that drives the other propeller is passed through the inside of the bearing to form an outer shaft. And a space between the outer and inner shafts, which leads from the oil supply to the oil supply port facing the gap between the bearing and the inner shaft and sends lubricating oil to the gap. A reverse lubrication structure for a marine contra-rotating propeller provided with a return oil passage that returns lubricating oil from a return port facing the oil supply source, and the bearing and the inner shaft exit the oil supply port of the forward oil path. An auxiliary circulation oil passage is formed inside the bearing for sending the lubricating oil flowing through the gap away from the return port to the one end face of the bearing to the other end face side of the bearing. without that it is formed within the outer member, i.e., the propeller Scan is the integral part of the bearing of the outer shaft
While being fitted to the outer circumference via a closed gap,
Holes that penetrate the outer shaft inside and outside and communicate with the above clearances
It is provided at a position outside the end face, and
A bearing lubrication structure for a contra-rotating marine propeller, wherein the auxiliary circulation oil passage is formed by the gap.
を駆動する円筒状の外軸の内側に軸受が一体化され、他
方のプロペラを駆動する内軸がその軸受の内側を通され
て外軸に対し相対回転自在に配置されており、 給油源から軸受・内軸間の隙間に臨む給油口へ通じてい
てその隙間に潤滑油を送る往きの油路と、外軸・内軸間
の空間に臨む戻し口から給油源へ通じていて潤滑油を戻
す戻りの油路を備える舶用二重反転プロペラの軸受潤滑
構造であって 、 往きの油路の上記給油口を出たうえ軸受と内軸との隙間
を上記の戻し口から離れる向きに流れて軸受の一方の端
面に達した潤滑油を、軸受の他方の端面側へ送るための
補助循環油路が、軸受の内部に形成されることなく、そ
の外側の部材のうちに形成されていること、すなわち、 軸受と外軸との間に他の円筒部材が配置されて軸受およ
び外軸に一体化され、上記の補助循環油路がその円筒部
材の肉厚内を通して形成されていること を特徴とする 舶
用二重反転プロペラの軸受潤滑構造。2. A propeller of one of contra-rotating propellers.
The bearing is integrated inside the cylindrical outer shaft that drives the
The inner shaft driving the other propeller is threaded inside its bearing
It is arranged so as to be rotatable relative to the outer shaft, and communicates from the oil supply source to the oil supply port facing the gap between the bearing and the inner shaft.
Between the outer oil passage and the inner shaft
Return the lubricating oil to the oil supply through the return port facing the space
Bearing lubrication of marine contra-rotating propeller with return oil passage
A structure, a clearance between the bearing and the inner shaft after leaving the filler opening of the oil passage of the forward
Flows away from the return port at one end of the bearing
To send the lubricating oil that has reached the surface to the other end of the bearing.
The auxiliary circulating oil passage is not formed inside the bearing,
That is, the other cylindrical member is disposed between the bearing and the outer shaft so that the bearing and the
And the above-mentioned auxiliary circulating oil passage is
Bearing lubricating structure of a marine contra-rotating propeller, characterized in that it is formed through the thickness of the wood.
を駆動する円筒状の外軸の内側に軸受が一体化され、他
方のプロペラを駆動する内軸がその軸受の内側を通され
て外軸に対し相対回転自在に配置されており、 給油源から軸受・内軸間の隙間に臨む給油口へ通じてい
てその隙間に潤滑油を送る往きの油路と、外軸・内軸間
の空間に臨む戻し口から給油源へ通じていて潤滑油を戻
す戻りの油路を備える舶用二重反転プロペラの軸受潤滑
構造であって 、 往きの油路の上記給油口を出たうえ軸受と内軸との隙間
を上記の戻し口から離れる向きに流れて軸受の一方の端
面に達した潤滑油を、軸受の他方の端面側へ送るための
補助循環油路が、軸受の内部に形成されることなく、そ
の外側の部材のうちに形成されていること、すなわち、 上記の補助循環油路が、外軸の肉厚内を通して形成され
ていること を特徴とする 舶用二重反転プロペラの軸受潤
滑構造。3. A propeller of one of contra-rotating propellers.
The bearing is integrated inside the cylindrical outer shaft that drives the
The inner shaft driving the other propeller is threaded inside its bearing
It is arranged so as to be rotatable relative to the outer shaft, and communicates from the oil supply source to the oil supply port facing the gap between the bearing and the inner shaft.
Between the outer oil passage and the inner shaft
Return the lubricating oil to the oil supply through the return port facing the space
Bearing lubrication of marine contra-rotating propeller with return oil passage
A structure, a clearance between the bearing and the inner shaft after leaving the filler opening of the oil passage of the forward
Flows away from the return port at one end of the bearing
To send the lubricating oil that has reached the surface to the other end of the bearing.
The auxiliary circulating oil passage is not formed inside the bearing,
That is, the auxiliary circulation oil passage is formed through the thickness of the outer shaft.
Bearing lubricating structure of a marine contra-rotating propeller, characterized in that is.
て給油口を内軸の外周面上に備え、戻りの油路が、外軸
の内周面上に戻し口を備え、外軸を内外に貫通して船体
内の固定配管に通じるよう形成されていることを特徴と
する請求項1〜3のいずれかに記載の舶用二重反転プロ
ペラの軸受潤滑構造。4. The outgoing oil passage is formed inside the inner shaft.
Oil supply port on the outer peripheral surface of the inner shaft, and the return oil passage is
A return port is provided on the inner peripheral surface of the
It is formed so as to communicate with the fixed piping inside
The bearing lubrication structure for a contra-rotating marine propeller according to any one of claims 1 to 3 .
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP8304940A JP2984221B2 (en) | 1996-11-15 | 1996-11-15 | Bearing lubrication structure for counter-rotating marine propellers |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP8304940A JP2984221B2 (en) | 1996-11-15 | 1996-11-15 | Bearing lubrication structure for counter-rotating marine propellers |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH10147292A JPH10147292A (en) | 1998-06-02 |
JP2984221B2 true JP2984221B2 (en) | 1999-11-29 |
Family
ID=17939156
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP8304940A Expired - Fee Related JP2984221B2 (en) | 1996-11-15 | 1996-11-15 | Bearing lubrication structure for counter-rotating marine propellers |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2984221B2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2024121137A (en) * | 2023-02-27 | 2024-09-06 | 日本シップヤード株式会社 | Fueling device for marine contra-rotating propeller device and marine contra-rotating propeller device |
-
1996
- 1996-11-15 JP JP8304940A patent/JP2984221B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH10147292A (en) | 1998-06-02 |
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