JPH0545479B2 - - Google Patents
Info
- Publication number
- JPH0545479B2 JPH0545479B2 JP60250471A JP25047185A JPH0545479B2 JP H0545479 B2 JPH0545479 B2 JP H0545479B2 JP 60250471 A JP60250471 A JP 60250471A JP 25047185 A JP25047185 A JP 25047185A JP H0545479 B2 JPH0545479 B2 JP H0545479B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- shaft
- inner shaft
- propeller
- stern
- 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
- 230000002093 peripheral effect Effects 0.000 claims description 2
- 239000003921 oil Substances 0.000 description 16
- 230000003068 static effect Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001151 other effect Effects 0.000 description 1
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
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は大形船舶の二重反転プロペラ用船尾管
軸受に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a stern tube bearing for a counter-rotating propeller of a large ship.
第６図〜第１０図は、従来の二重反転プロペラ
船尾管軸受の例であり、第６図は、船尾軸受部の
側面図、第７図は、二重反転軸受の断面図、第８
図及び第９図は、二重反転軸受の一従来例及び他
の従来例を示す断面図、第１０図は、内軸と外軸
軸受がプロペラ片持ち支持のため片当りの状態を
示す船尾軸受部の側面図を示す。
6 to 10 show examples of conventional counter-rotating propeller stern tube bearings, FIG. 6 is a side view of the stern bearing, FIG. 7 is a sectional view of the counter-rotating bearing, and FIG.
9 and 9 are cross-sectional views showing one conventional example of counter-rotating bearings and another conventional example, and FIG. 10 is a stern showing a state in which the inner shaft and outer shaft bearings are in one-sided contact due to cantilever support of the propeller. A side view of the bearing section is shown.
従来の二重反転プロペラを有する船舶は、図示
しない原動機（デイーゼルエンジン、蒸気タービ
ン、ガスタービンなど）にて反転装置を介し、先
端に後側プロペラ０１を有する内軸０２と、先端
に前側プロペラ０３を有する外軸０４を逆回転さ
せる船舶の推進方法であり周知のものである。こ
の推進軸を滑らかに駆動させるため、一般に、外
軸０４と船体０５間に前部軸受０６と後部軸受０
７を配し、内軸０２と外軸０４間にも反転前部軸
受０８と反転後部軸受０９を設ける。また、船尾
部の内、外軸間及び外軸、船体間には、船尾軸シ
ール０１０、０１１を設ける。 A conventional ship having a counter-rotating propeller has an inner shaft 02 having a rear propeller 01 at its tip, and a front propeller 03 at its tip, through a reversing device in a prime mover (not shown) (diesel engine, steam turbine, gas turbine, etc.). This is a well-known ship propulsion method in which an outer shaft 04 having a rotation angle is reversely rotated. In order to drive this propulsion shaft smoothly, there is generally a front bearing 06 and a rear bearing 0 between the outer shaft 04 and the hull 05.
7, and an inverted front bearing 08 and an inverted rear bearing 09 are also provided between the inner shaft 02 and the outer shaft 04. Further, stern shaft seals 010 and 011 are provided between the inner and outer shafts of the stern portion, and between the outer shaft and the hull.
外軸０４と船体０５間の軸受は通常の船尾管軸
受で特に技術的困難さはないが、内軸０２と外軸
０４間は逆回転するため軸受を成立させる技術的
な難かしさがある。この理由を次に示す。 The bearing between the outer shaft 04 and the hull 05 is a normal stern tube bearing and there is no particular technical difficulty, but there is a technical difficulty in establishing the bearing between the inner shaft 02 and the outer shaft 04 because it rotates in the opposite direction. . The reason for this is shown below.
第７図は反転する様子を軸方向から見た概略図
を示したものである。外軸０４と軸受０５間は船
体が静止しているため、通常の流体潤滑すべり軸
受が形成できるが、内軸０２と外軸０４間は矢印
で示す回転方向に逆転するため、流体潤滑が困難
となり、ほぼ等速で逆転すると、流体潤滑（軸を
油膜で分離）することができなくなる。 FIG. 7 is a schematic view of the reversal seen from the axial direction. Since the hull is stationary between the outer shaft 04 and the bearing 05, a normal fluid lubrication sliding bearing can be formed, but fluid lubrication is difficult between the inner shaft 02 and the outer shaft 04 because the rotation direction is reversed as shown by the arrow. If the shaft rotates in reverse at almost constant speed, fluid lubrication (separating the shaft with an oil film) will no longer be possible.
これに対処するため、従来は第８図及び第９図
に示すような軸受が提案されている。第８図は内
軸０２と外軸０４の間に浮動ブツシユ０１２を設
け、浮動ブツシユ０１２をほぼ静止させることに
より内軸と浮動ブツシユ間、浮動ブツシユと外軸
間に流体潤滑油膜を形成させる方式である。また
第９図はテーパーランド部を内面に有する外軸０
１３を示したもので、Ａ部がテーパー部で、Ｂ部
が内軸表面と平行のランド部、Ｃ部が全体が逆転
（アスターン）する場合の動圧発生部テーパであ
る。 In order to cope with this problem, bearings as shown in FIGS. 8 and 9 have been proposed. Figure 8 shows a system in which a floating bush 012 is provided between the inner shaft 02 and the outer shaft 04, and by keeping the floating bush 012 almost stationary, a fluid lubricating oil film is formed between the inner shaft and the floating bush and between the floating bush and the outer shaft. It is. In addition, Fig. 9 shows an outer shaft 0 with a tapered land portion on the inner surface.
13, part A is a tapered part, part B is a land part parallel to the inner shaft surface, and part C is a taper of a dynamic pressure generating part when the whole is reversed (astern).
しかしながら従来の軸受は、流体潤滑油膜（動
圧）が容易に生じるが、船舶の運航上の特徴であ
る低速での運転で油膜が薄くなり、軸受面にて金
属接触したり、さらに第１０図に示すようにプロ
ペラの片持支持により軸受０９後端部が片当りし
軸受けが焼付くという欠点を有していた。本発明
は、上上記欠点を解消せんがためのものであり、
プロペラの大形化、推進効率の向上の面から、よ
り低速で運転することが可能であり、また、プロ
ペラは片持ち支持による軸受後端部の片当りに対
し焼付かない軸受を提供することを目的とする。
However, in conventional bearings, a fluid lubricating oil film (dynamic pressure) is easily generated, but the oil film becomes thinner due to low speed operation, which is a characteristic of ship operation, and metal contact may occur on the bearing surface. As shown in Fig. 2, due to the cantilever support of the propeller, the rear end of the bearing 09 hits one side and the bearing seizes. The present invention is intended to solve the above-mentioned drawbacks,
In terms of increasing the size of the propeller and improving propulsion efficiency, it is possible to operate at lower speeds, and the propeller is supported on a cantilever, so it is possible to provide a bearing that does not seize due to uneven contact at the rear end of the bearing. purpose.
このため、本発明の二重反転プロペラ用船尾管
軸受は、後方プロペラを有する内軸と前方プロペ
ラを有する外軸を反転させる二重反転プロペラ用
船尾管軸受において、上記内軸の軸芯を中空とす
ると共に、上記内軸の軸受面の範囲内において内
軸外周面に放射状に貫通するさらに前記給油孔を
内軸長手方向に複数列配設したことを特徴として
いる。
For this reason, the stern tube bearing for a counter-rotating propeller of the present invention is a stern tube bearing for a counter-rotating propeller that reverses the inner shaft having the rear propeller and the outer shaft having the front propeller. In addition, the oil supply hole is characterized in that a plurality of rows of the oil supply holes are arranged in the longitudinal direction of the inner shaft and extend radially through the outer circumferential surface of the inner shaft within the range of the bearing surface of the inner shaft.
上記構成により給油孔の油膜厚さをｈ、給油孔
の出口圧力をp0、内軸中空部油圧をpsとすると、
軸受への流出流量ＱはＱ∝h3poで表わされ、ま
た給油孔を通る流量Ｑ（軸受からの流出流量に等
しい）はＱ∝√−0で示される。
With the above configuration, if the oil film thickness of the oil supply hole is h, the outlet pressure of the oil supply hole is p 0 , and the inner shaft hollow part oil pressure is ps, then
The flow rate Q flowing into the bearing is expressed as Q∝h 3 po, and the flow rate Q through the oil supply hole (equal to the flow rate flowing out of the bearing) is expressed as Q∝√− 0 .
これらの関係より、ｈが大きければp0は小さく
なる。また逆にｈが小さければp0は大きくなる。
よつて、給油孔での軸受部長手方向静圧分布を決
定することにより、内軸の自重を持上げようとす
る静圧力すなわち負荷能力を有することが可能と
なる。 From these relationships, if h is large, p 0 will be small. Conversely, if h is small, p 0 will be large.
Therefore, by determining the static pressure distribution in the longitudinal direction of the bearing at the oil supply hole, it becomes possible to have a static pressure, that is, a load capacity that attempts to lift the weight of the inner shaft.
第１図〜第５図は、本発明の二重反転プロペラ
用船尾管軸受における実施例であり、第１図は、
本発明の第１実施例を示す船尾管軸受の断面図、
第２図ａは、第１図の作用を説明する原理図、第
２図ｂは、第２図ａによる静圧分布図、第３図
は、本発明の第２実施例を示す船尾管軸受の断面
図、第４図は、第１図及び第２図の内軸側面図、
第５図は、第４図の効果を示す説明図である。
1 to 5 show examples of the stern tube bearing for counter-rotating propellers of the present invention, and FIG.
A sectional view of a stern tube bearing showing a first embodiment of the present invention,
Fig. 2a is a principle diagram explaining the action of Fig. 1, Fig. 2b is a static pressure distribution diagram according to Fig. 2a, and Fig. 3 is a stern tube bearing showing a second embodiment of the present invention. 4 is a side view of the inner axis of FIGS. 1 and 2,
FIG. 5 is an explanatory diagram showing the effect of FIG. 4.
第１図において、外軸軸４と外軸受５は従来通
りであるが、内軸２には図示しない油圧源より油
圧を導く内軸外周との同芯穴１９があり放射状に
３個以上設けられた放射状孔２０に通じている。
放射状孔２０の外周部には、オリフイス絞りの機
能を有する***つきねじ２５を締め込み、外周部
は軸外周と同円周になるように仕上げている。第
３図において外軸４と外軸軸受５は実施例１と同
様である。内軸２の油圧同芯穴１９と通じる３個
以上の放射状孔２０として、毛細管絞り機能を有
する孔を設置した方式である。 In FIG. 1, the outer shaft 4 and the outer bearing 5 are the same as before, but the inner shaft 2 has three or more holes 19 radially arranged concentrically with the outer circumference of the inner shaft to guide hydraulic pressure from a hydraulic power source (not shown). radial holes 20.
A small hole screw 25 having an orifice restricting function is screwed into the outer circumference of the radial hole 20, and the outer circumference is finished to have the same circumference as the shaft outer circumference. In FIG. 3, the outer shaft 4 and outer shaft bearing 5 are the same as in the first embodiment. This is a system in which three or more radial holes 20 communicating with the hydraulic concentric hole 19 of the inner shaft 2 are provided with holes having a capillary throttling function.
上記第１及び第２実施例の原理について第２図
ａ及びｂにて説明する。第２図ａより今、多数の
内軸放射状孔２０のうち油膜厚さがｈの放射状孔
２０の周辺部２３を１個考える。放射状孔２０の
出口圧力をp0、同芯穴１９の供給圧をpsとする
と、軸受への流出流量Ｑは次式で示される。 The principles of the first and second embodiments will be explained with reference to FIGS. 2a and 2b. From FIG. 2a, one peripheral portion 23 of the radial hole 20 with an oil film thickness of h among the many inner shaft radial holes 20 will now be considered. When the outlet pressure of the radial hole 20 is p 0 and the supply pressure of the concentric hole 19 is ps, the flow rate Q flowing to the bearing is expressed by the following equation.
Ｑ∝h3po
またオリフイスを通る流量Ｑ（軸受からの流出
流量に等しい）は次式で示される。 Q∝h 3 po Also, the flow rate Q passing through the orifice (equal to the flow rate flowing out from the bearing) is expressed by the following equation.
Ｑ∝√−0
これらの関係より、ｈが大きければp0は小さく
なる。また逆にｈが小さければp0は大きくなる。
よつて、放射状孔２０が多数ある場合の内軸まわ
りの静圧分布は、第２図ｂのように、軸芯まわり
に一様とならない。従つて、内軸の自重２１を持
上げようとする静圧力すなわち負荷能力を有する
ことになる。 Q∝√− 0 From these relationships, if h is large, p 0 will be small. Conversely, if h is small, p 0 will be large.
Therefore, when there are many radial holes 20, the static pressure distribution around the inner axis is not uniform around the axis as shown in FIG. 2b. Therefore, it has a static pressure, that is, a load capacity that attempts to lift the dead weight 21 of the inner shaft.
なお毛細管しぼりの場合もオリフイスと同様な
作用となる。図中、h1及びh2は、油膜の最小及び
最大厚みを示す。 Note that in the case of capillary squeezing, the effect is similar to that of an orifice. In the figure, h 1 and h 2 indicate the minimum and maximum thickness of the oil film.
第４図は第１図及び第３図の側面状態を示して
おり、放射状孔２０が内軸２０長手方向に不等間
隔に配設しており、船尾部分の間隔を小さくして
いる。また、穴の配置は軸受幅（長さ）の範囲内
としている。その作用効果を第５図にて示すと静
圧孔を等間隔に配置すると後端部が最少油膜部と
なり、前方部は大きなすきまとなり前方部の静圧
孔からは無駄油量が多量に消費される。 FIG. 4 shows a side view of FIGS. 1 and 3, in which the radial holes 20 are arranged at uneven intervals in the longitudinal direction of the inner shaft 20, and the intervals at the stern portion are reduced. Additionally, the holes are arranged within the range of the bearing width (length). The effect is shown in Figure 5. If the static pressure holes are arranged at equal intervals, the rear end will have the smallest oil film, and the front part will have a large gap, and a large amount of wasted oil will be consumed from the static pressure holes in the front part. be done.
後端部の片当りの強い側につめて不等間隔で穴
位置を設定すると後端側の浮上りを大きくでき、
かつ必要油量が、等間隔のものに比べてはるかに
少なくすむ。なお、軸の傾きが少ない場合や油量
消費量が問題にならない場合には、等間隔でもよ
い。 By placing the holes on the side where the uneven contact is strong at the rear end and setting the hole positions at uneven intervals, you can increase the floating on the rear end side.
Moreover, the amount of oil required is much smaller than that of the one with equal intervals. Note that if the inclination of the shaft is small or if oil consumption is not a problem, equal intervals may be used.
以上、記述の如く、本発明の二重反転プロペラ
用船尾管軸受を適用することにより、
(1) プロペラの大形化、推進効率の向上の面から
低速運転が可能になる。
As described above, by applying the stern tube bearing for a contra-rotating propeller of the present invention, (1) low-speed operation becomes possible in terms of increasing the size of the propeller and improving propulsion efficiency.
(2) プロペラの片持ち支持による軸受後端部の片
当りによる軸受の焼付けがない。(2) There is no seizure of the bearing due to uneven contact of the rear end of the bearing due to the cantilever support of the propeller.
等の効果がある。There are other effects.
第１図〜第５図は、本発明の二重反転プロペラ
用船尾管軸受における実施例であり、第１図は、
本発明の第１実施例を示す船尾管軸受の断面図、
第２図ａは、第１図の作用を説明する原理図、第
２図ｂは、第２図ａによる静圧分布図、第３図
は、本発明の第２実施例を示す船尾管軸受の断面
図、第４図は、第１図及び第２図の内軸側面図、
第５図は、第４図の効果を示す説明図である。第
６図〜第１０図は、従来の二重反転プロペラ船尾
軸受の例であり、第６図は、船尾軸受部の側面
図、第７図は、二重反転軸受の断面図、第８図及
び第９図は、二重反転軸受の一従来例及び他の従
来例を示す断面図、第１０図は、内軸と外軸軸受
がプロペラ片持ち支持のため片当りの状態を示す
船尾軸受部の側面図を示す。
２……内軸、４……外軸、５……外軸軸受、１
９……同芯穴、２０……放射状孔。
1 to 5 show examples of the stern tube bearing for counter-rotating propellers of the present invention, and FIG.
A sectional view of a stern tube bearing showing a first embodiment of the present invention,
Fig. 2a is a principle diagram explaining the action of Fig. 1, Fig. 2b is a static pressure distribution diagram according to Fig. 2a, and Fig. 3 is a stern tube bearing showing a second embodiment of the present invention. 4 is a side view of the inner axis of FIGS. 1 and 2,
FIG. 5 is an explanatory diagram showing the effect of FIG. 4. Figures 6 to 10 show examples of conventional contra-rotating propeller stern bearings, with Figure 6 being a side view of the stern bearing, Figure 7 being a sectional view of the contra-rotating bearing, and Figure 8 being a cross-sectional view of the contra-rotating bearing. FIG. 9 is a sectional view showing one conventional example of a counter-rotating bearing and another conventional example, and FIG. 10 is a stern bearing showing a state in which the inner shaft and outer shaft bearings are in one-sided contact for cantilever support of the propeller. Figure 2 shows a side view of the section. 2...Inner shaft, 4...Outer shaft, 5...Outer shaft bearing, 1
9... Concentric hole, 20... Radial hole.
Claims (1)
有する外軸を反転させる二重反転プロペラ用船尾
管軸受において、上記内軸の軸芯を中空とすると
共に、上記内軸の軸受面の範囲内において内軸外
周面に放射状に貫通する複数本の給油孔を設け、
さらに、前記給油孔を内軸長手方向に複数列配設
したことを特徴とする二重反転プロペラ用船尾管
軸受。1. In a stern tube bearing for a contra-rotating propeller in which an inner shaft with a rear propeller and an outer shaft with a front propeller are reversed, the axial center of the inner shaft is hollow, and the inner shaft is hollow within the range of the bearing surface of the inner shaft. Multiple oil supply holes are provided radially through the outer peripheral surface of the shaft.
Furthermore, a stern tube bearing for a counter-rotating propeller, characterized in that the oil supply holes are arranged in a plurality of rows in the longitudinal direction of the inner shaft.
Priority Applications (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60250471A JPS62110595A (en) | 1985-11-08 | 1985-11-08 | Stern tube bearing for double reversal propeller |
| KR1019860009164A KR900004060B1 (en) | 1985-11-08 | 1986-10-31 | Stern tube bearing system of contra-rotating propeller |
| EP86115270A EP0221536B1 (en) | 1985-11-08 | 1986-11-04 | Stern tube bearing system of contra-rotating propeller |
| DE8686115270T DE3673603D1 (en) | 1985-11-08 | 1986-11-04 | STEVEL TUBE BEARING ARRANGEMENT FOR CONTINUOUS PROPELLERS. |
| US06/926,623 US4786264A (en) | 1985-11-08 | 1986-11-04 | Stern tube bearing system of contra-rotating propeller |
| ES86115270T ES2000008B3 (en) | 1985-11-08 | 1986-11-04 | SUPPORT SYSTEM FOR THE CODASTE HORN FOR THE CONTRARROTATIVE PROPELLER |
| DE198686115270T DE221536T1 (en) | 1985-11-08 | 1986-11-04 | STEVEL TUBE BEARING ARRANGEMENT FOR CONTINUOUS PROPELLERS. |
| CA000522290A CA1264609A (en) | 1985-11-08 | 1986-11-06 | Stern tube bearing system of contra-rotating propeller |
| NO864464A NO165286C (en) | 1985-11-08 | 1986-11-07 | PROPELL SHELTER STOCK WITH CONTRA-ROTATING PROPELLER. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60250471A JPS62110595A (en) | 1985-11-08 | 1985-11-08 | Stern tube bearing for double reversal propeller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62110595A JPS62110595A (en) | 1987-05-21 |
| JPH0545479B2 true JPH0545479B2 (en) | 1993-07-09 |
Family
ID=17208356
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60250471A Granted JPS62110595A (en) | 1985-11-08 | 1985-11-08 | Stern tube bearing for double reversal propeller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62110595A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996007832A1 (en) * | 1994-09-08 | 1996-03-14 | Kawasaki Jukogyo Kabushiki Kaisha | Reversing bearing device for double reversing propeller |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2190254A (en) * | 1937-03-25 | 1940-02-13 | Caproni Gianni | Coaxial propeller drive |
| US2457999A (en) * | 1946-03-28 | 1949-01-04 | Continental Aviat & Eng Corp | Lubrication means for dual propeller shaft assemblies |
| US2470560A (en) * | 1939-06-13 | 1949-05-17 | Walter S Hoover | Oppositely rotating propellers |
| JPS5149456U (en) * | 1974-10-12 | 1976-04-14 | ||
| JPS521950U (en) * | 1975-06-23 | 1977-01-08 | ||
| JPS61180097A (en) * | 1985-02-01 | 1986-08-12 | Kawasaki Heavy Ind Ltd | Lubricating oil supply structure of double reversal propeller device for marine use |
-
1985
- 1985-11-08 JP JP60250471A patent/JPS62110595A/en active Granted
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2190254A (en) * | 1937-03-25 | 1940-02-13 | Caproni Gianni | Coaxial propeller drive |
| US2470560A (en) * | 1939-06-13 | 1949-05-17 | Walter S Hoover | Oppositely rotating propellers |
| US2457999A (en) * | 1946-03-28 | 1949-01-04 | Continental Aviat & Eng Corp | Lubrication means for dual propeller shaft assemblies |
| JPS5149456U (en) * | 1974-10-12 | 1976-04-14 | ||
| JPS521950U (en) * | 1975-06-23 | 1977-01-08 | ||
| JPS61180097A (en) * | 1985-02-01 | 1986-08-12 | Kawasaki Heavy Ind Ltd | Lubricating oil supply structure of double reversal propeller device for marine use |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996007832A1 (en) * | 1994-09-08 | 1996-03-14 | Kawasaki Jukogyo Kabushiki Kaisha | Reversing bearing device for double reversing propeller |
| EP0803657A4 (en) * | 1994-09-08 | 1999-06-30 | Kawasaki Heavy Ind Ltd | Reversing bearing device for double reversing propeller |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62110595A (en) | 1987-05-21 |
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| LAPS | Cancellation because of no payment of annual fees |