JPH0523437Y2 - - Google Patents

Description

【考案の詳細な説明】 〔産業上の利用分野〕 本考案は、舶用二重反転プロペラのプロペラ軸
系における軸受のための潤滑装置に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a lubricating device for a bearing in a propeller shaft system of a counter-rotating marine propeller.

〔従来の技術〕[Conventional technology]

一般に、舶用二重反転プロペラとしては第７図
に示すようなものがあり、前側プロペラ１２′を
後端にそなえた外軸２′が、スタンフレーム１
３′を貫通して配設され、同スタンフレーム１
３′の内周面と外軸２′の外周面との間に介装され
た船尾側固定軸受ブツシユ９′および船首側固定
軸受ブツシユ１０′により支承されている。これ
らの軸受ブツシユ９′，１０′のうち、船尾側固定
軸受ブツシユ９′は静圧軸受として構成され、船
首側固定軸受ブツシユ１０′は通常の船尾管軸受
として構成される。 In general, there is a contra-rotating marine propeller as shown in Fig. 7, in which an outer shaft 2' with a front propeller 12' at the rear end is attached to a stern frame.
3', and the stun frame 1
It is supported by a stern side fixed bearing bush 9' and a bow side fixed bearing bush 10' which are interposed between the inner peripheral surface of the shaft 3' and the outer peripheral surface of the outer shaft 2'. Of these bearing bushes 9', 10', the stern fixed bearing bush 9' is constructed as a hydrostatic bearing, and the bow fixed bearing bush 10' is constructed as a normal stern tube bearing.

また、後側プロペラ１１′を後端にそなえた内
軸１′が、外軸２′内を貫通し同外軸２′と同心的
に配設され、外軸２′の内周面と内軸１′の外周面
との間において船尾側および船首側のそれぞれに
介装された内軸軸受２４′，２４′により支承され
る。これらの内軸軸受２４′，２４′は、それぞれ
外軸２′の内周面に固着される軸受ブツシユ３′
と、この軸受ブツシユ３′と内軸１′の外周面との
間に遊嵌される浮動ブツシユ６′とから動圧型す
べり軸受として構成される。 The inner shaft 1', which has a rear propeller 11' at its rear end, penetrates the outer shaft 2' and is arranged concentrically with the outer shaft 2', and is supported by inner shaft bearings 24', 24' disposed on the stern and bow sides, respectively, between the inner peripheral surface of the outer shaft 2' and the outer peripheral surface of the inner shaft 1'. These inner shaft bearings 24', 24' are supported by bearing bushes 3' fixed to the inner peripheral surface of the outer shaft 2'.
and a floating bushing 6' that is loosely fitted between the bearing bushing 3' and the outer circumferential surface of the inner shaft 1', thereby forming a hydrodynamic type sliding bearing.

そして、内軸１′は図示しない反転装置に連結
されるとともに、外軸２′も２つ割れ中空軸２
３′を介し図示しない反転装置に連結されており、
これらの内軸１′と外軸２′とは、上記反転装置を
介して図示しない主機に接続され、プロペラ１
１′，１２′を互いに反対方向に回転駆動しうるよ
うになつている。 The inner shaft 1' is connected to a reversing device (not shown), and the outer shaft 2' is also split into two hollow shafts 2'.
It is connected to a reversing device (not shown) via 3'.
These inner shaft 1' and outer shaft 2' are connected to the main engine (not shown) via the above-mentioned reversing device, and the propeller 1'
1' and 12' can be rotated in opposite directions.

一方、外軸用シール装置１６′および１８′が、
それぞれ船外および船内におけるスタンフレーム
１３′と外軸２′との間に設けられるとともに、内
軸用シール装置１５′が、船外において、外軸
２′と内軸１′とのすき間を閉塞するように設けら
れており、これらのシール装置１５′，１６′およ
び１８′は、外軸２′、内軸１′およびスタンフレ
ーム１３′それぞれの相対的な軸方向移動を防止
するほか、軸受ブツシユ９′，１０′および内軸軸
受２４′における潤滑油のリークを防止するよう
になつている。 On the other hand, the outer shaft seal devices 16' and 18' are
An inner shaft sealing device 15' is provided between the stern frame 13' and the outer shaft 2' on the outside and inside the ship, respectively, and an inner shaft sealing device 15' closes the gap between the outer shaft 2' and the inner shaft 1' outside the ship. These seal devices 15', 16', and 18' prevent relative axial movement of the outer shaft 2', inner shaft 1', and stan frame 13', and also prevent the bearings from moving in the relative axial direction. This prevents lubricating oil from leaking from the bushes 9', 10' and the inner shaft bearing 24'.

上述のような舶用二重反転プロペラ軸系の軸受
の潤滑装置においては、従来、第７図に示すよう
に、船尾側固定軸受ブツシユ（静圧軸受）９′の
中央部には、同軸受ブツシユ９′の内周面と外軸
２′の外周面との間に高圧の潤滑油を供給すべく、
高圧給油管１９′が接続されるとともに、この高
圧給油管１９′は図示しない高圧油ポンプを介し
図示しない高圧油タンクに接続されている。 In the above-mentioned bearing lubrication device for a marine contra-rotating propeller shaft system, as shown in FIG. In order to supply high pressure lubricating oil between the inner peripheral surface of the shaft 9' and the outer peripheral surface of the outer shaft 2',
A high-pressure oil supply pipe 19' is connected, and this high-pressure oil supply pipe 19' is connected to a high-pressure oil tank (not shown) via a high-pressure oil pump (not shown).

また、外軸用シール装置１６′と船尾側固定軸
受ブツシユ（静圧軸受）９′との間の位置におい
て、スタンフレーム１３′には、低圧油供給管２
０′が開口して接続されている。この低圧油供給
管２０′は、図示しない潤滑油タンクに接続され
る。 Additionally, a low pressure oil supply pipe 2 is attached to the stern frame 13' at a position between the outer shaft sealing device 16' and the stern side fixed bearing bush (static pressure bearing) 9'.
0' is open and connected. This low pressure oil supply pipe 20' is connected to a lubricating oil tank (not shown).

そして、船尾側固定軸受ブツシユ（静圧軸受）
９′に供給され同軸受ブツシユ９′を潤滑した後に
船尾側へ流れる潤滑油と、低圧油供給管２０′か
らシール装置１６′に供給された潤滑油とを、内
軸用シール装置１５′へ導くべく、外軸２′には船
尾側外軸給油穴２１′が形成される一方、上記軸
受ブツシユ９′を潤滑した後に船尾側へ流れ軸受
ブツシユ１０′および外軸用シール装置１８′を経
由した潤滑油を２つ割れ中空軸２３′内へ導くべ
く、外軸２′には船首側外軸給油穴２２′が形成さ
れる。 And the stern side fixed bearing bush (static pressure bearing)
The lubricating oil supplied to the co-bearing bushing 9' and flowing to the stern side after lubricating the co-bearing bushing 9', and the lubricating oil supplied to the sealing device 16' from the low pressure oil supply pipe 20' to the inner shaft sealing device 15'. A stern side outer shaft oil supply hole 21' is formed in the outer shaft 2' in order to guide oil flow to the stern side after lubricating the bearing bush 9' via the bearing bush 10' and the outer shaft sealing device 18'. A bow-side outer shaft oil supply hole 22' is formed in the outer shaft 2' in order to guide the lubricating oil into the hollow shaft 23'.

なお、第７図中の符号１４′は機関室の後部隔
壁、１７′は船首側の浮動ブツシユ６′の移動を規
制するストツパを示している。 In addition, the reference numeral 14' in FIG. 7 indicates the rear bulkhead of the engine room, and the reference numeral 17' indicates a stopper for restricting the movement of the floating bush 6' on the bow side.

また、２つ割れ中空軸２３′よりも船首側には
潤滑を終えた潤滑油を排出するための図示しない
排出系がそなえられている。 Furthermore, a discharge system (not shown) for discharging lubricating oil after lubrication is provided on the bow side of the two-split hollow shaft 23'.

したがつて、上述のような従来の舶用二重反転
プロペラ用軸受潤滑装置では、図示しない高圧油
タンクおよび潤滑油タンクに貯蔵される潤滑油
が、図示しないポンプ等により送り出され、それ
ぞれ高圧油給油管１９′および低圧油供給管２
０′を介し外軸２′の外周面における船尾側固定軸
受ブツシユ（静圧軸受）９′および外軸用シール
装置１６′に送給される。 Therefore, in the conventional bearing lubrication system for marine counter-rotating propellers as described above, lubricating oil stored in a high-pressure oil tank (not shown) and a lubricating oil tank are pumped out by a pump (not shown), etc. Pipe 19' and low pressure oil supply pipe 2
0' to the stern side fixed bearing bush (static pressure bearing) 9' and the outer shaft sealing device 16' on the outer peripheral surface of the outer shaft 2'.

固定軸受ブツシユ（静圧軸受）９′の潤滑を行
なつた高圧の潤滑油のうち、外軸２′の外周面に
沿つて船首側へ流れたものは、船首側固定軸受ブ
ツシユ１０′および外軸用シール装置１８′を潤滑
した後、船首側外軸給油穴２２′から２つ割れ中
空軸２３′内に導かれる。 Of the high-pressure lubricating oil that lubricates the fixed bearing bushing (static pressure bearing) 9', the oil that flows toward the bow along the outer circumferential surface of the outer shaft 2' is transferred to the bow side fixed bearing bushing 10' and the outer circumferential surface of the outer shaft 2'. After the shaft seal device 18' is lubricated, it is guided into the hollow shaft 23' which is split into two parts from the bow side outer shaft oil supply hole 22'.

一方、上記高圧の潤滑油のうち、外軸２′の外
周面に沿つて船尾側へ流れたものは、低圧油供給
管２０′から供給された低圧の潤滑油と合流し、
外軸用シール装置１６′を潤滑した後、船尾側外
軸給油穴２１′から内軸用シール装置１５′へ導か
れる。 On the other hand, the high pressure lubricating oil that flows along the outer peripheral surface of the outer shaft 2' toward the stern side joins with the low pressure lubricating oil supplied from the low pressure oil supply pipe 20',
After lubricating the outer shaft seal device 16', the lubricant is led to the inner shaft seal device 15' from the stern outer shaft oil supply hole 21'.

そして、このシール装置１５′を潤滑した潤滑
油は、外軸２′の内周面と内軸１′の外周面との間
に沿い船首側に向かつて流れ、内軸軸受２４′，
２４′を潤滑してから、２つ割れ中空軸２３′内に
流入する。 The lubricating oil that has lubricated this sealing device 15' flows toward the bow side between the inner circumferential surface of the outer shaft 2' and the outer circumferential surface of the inner shaft 1', and flows toward the bow side of the inner shaft bearing 24',
After lubricating 24', it flows into the hollow hollow shaft 23'.

２つ割れ中空軸２３′内の潤滑油は、内軸１′の
外周面に沿いさらに船首側へ流れ、図示しない排
出系から潤滑油タンクあるいは高圧油タンクに戻
される。 The lubricating oil in the two-split hollow shaft 23' flows further toward the bow side along the outer peripheral surface of the inner shaft 1', and is returned to the lubricating oil tank or the high-pressure oil tank from a discharge system (not shown).

〔考案が解決しようとする問題点〕[Problem that the invention attempts to solve]

しかしながら、上述のような従来の舶用二重反
転プロペラ用軸受潤滑装置では、構造的に極めて
大きな重量を有する内軸１′および外軸２′がそれ
ぞれ内軸軸受２４′をして互いに反対方向へ高速
回転する。 However, in the conventional bearing lubrication system for marine contra-rotating propellers as described above, the inner shaft 1' and the outer shaft 2', which have extremely large structural weights, are moved in opposite directions by the inner shaft bearings 24'. Rotates at high speed.

このため、動圧型すべり軸受としての内軸軸受
２４′では、その摺動面に潤滑油の油膜が形成さ
れず、内軸軸受２４′の潤滑性能が劣化し、特に
低速回転時の片当たりが問題になる。そして、場
合によつては内軸１′と内軸軸受２４′とが直接接
触を起こして焼き付けを発生することがあるの
で、片当たり性を改善すべく内軸１′の直径をル
ール径以上に大きくする必要が生じ、プロペラ軸
系の配置が困難になるとともに極めて不経済であ
る。 For this reason, in the inner shaft bearing 24' as a hydrodynamic sliding bearing, an oil film of lubricating oil is not formed on the sliding surface of the inner shaft bearing 24', and the lubrication performance of the inner shaft bearing 24' is deteriorated, causing uneven contact especially during low speed rotation. It becomes a problem. In some cases, the inner shaft 1' and the inner shaft bearing 24' may come into direct contact and cause seizure, so in order to improve uneven contact, the diameter of the inner shaft 1' is set to be larger than the rule diameter. This makes it difficult to arrange the propeller shaft system and is extremely uneconomical.

そこで、従来より、内軸と外軸との間に介装さ
れる内軸軸受を静圧軸受として構成し、油膜を確
実に形成し片当たりの発生を防止するようにする
ことが提案されている。 Therefore, it has been proposed to configure the inner shaft bearing interposed between the inner shaft and the outer shaft as a static pressure bearing to reliably form an oil film and prevent uneven contact. There is.

すなわち、第８図（要部横断面図）に示すよう
に、外軸３２′および外軸軸受３３′は従来と同様
であるが、内軸３１′には、図示しない油圧源よ
り高圧油を導く潤滑油通路３０′が形成されてお
り、同潤滑油通路３０′は、内軸３１′に放射状に
形成された複数の穴３４′に連通している。 That is, as shown in FIG. 8 (cross-sectional view of main parts), the outer shaft 32' and the outer shaft bearing 33' are the same as the conventional ones, but the inner shaft 31' is supplied with high pressure oil from a hydraulic source (not shown). A guiding lubricating oil passage 30' is formed, and the lubricating oil passage 30' communicates with a plurality of holes 34' formed radially in the inner shaft 31'.

これらの穴３４′の内軸３１′外周における開口
部には、オリフイス絞りの機能を有する***付き
ねじ３５′が絞め込まれている。 Small hole screws 35' having an orifice restricting function are tightened into the openings of these holes 34' on the outer periphery of the inner shaft 31'.

このような静圧軸受では、図示しない油圧源か
ら潤滑油通路３０′および穴３４′を経由して高圧
の潤滑油が内軸３１′と外軸３２′との間に供給さ
れて、軸受が形成されるとともにその潤滑が行な
われる。 In such a hydrostatic bearing, high-pressure lubricating oil is supplied between the inner shaft 31' and the outer shaft 32' from a hydraulic source (not shown) via the lubricating oil passage 30' and the hole 34', and the bearing is The lubrication takes place as it is formed.

ところで、通常、内軸３１′と外軸３２′とは、
第８図に示すように、たわみにより最下部で接触
する可能性が高いため、この最下部付近に高圧の
潤滑油を確実に供給することが要求される。 By the way, normally, the inner shaft 31' and the outer shaft 32' are
As shown in FIG. 8, there is a high possibility that contact will occur at the lowest part due to deflection, so it is required to reliably supply high-pressure lubricating oil to the vicinity of this lowest part.

したがつて、複数の穴３４′を放射状に形成さ
れているほか、極めて多量の潤滑油を供給するよ
うにしている。 Therefore, a plurality of holes 34' are formed radially, and an extremely large amount of lubricating oil is supplied.

しかしながら、この静圧軸受では、内軸３１′
と外軸３２′との間に供給された多量の潤滑油を
確実に排出する手段が開示されていないため、高
圧の潤滑油によつて内軸用シール装置（第７図の
符号１５′参照）が損傷するといつた不具合を生
じる場合がある。 However, in this hydrostatic bearing, the inner shaft 31'
Since no means is disclosed for reliably discharging a large amount of lubricating oil supplied between ) may be damaged and other problems may occur.

本考案は、上述の問題点の解決をはかろうとす
るもので、内軸軸受を静圧軸受として構成した場
合の潤滑油排出手段を確立し、片当たり等による
焼き付けを確実に防止できるようにして、二重反
転プロペラ軸系における潤滑性能の向上をはかつ
た、舶用二重反転プロペラ用軸受潤滑装置を提供
することを目的とする。 The present invention attempts to solve the above-mentioned problems by establishing a means for discharging lubricating oil when the inner shaft bearing is configured as a static pressure bearing, and thereby reliably preventing seizure due to uneven contact, etc. An object of the present invention is to provide a bearing lubrication device for a counter-rotating marine propeller, which improves the lubrication performance of a counter-rotating propeller shaft system.

〔問題点を解決するための手段〕[Means for solving problems]

このため、本考案の舶用二重反転プロペラ用軸
受潤滑装置は、船尾に設けられた二重反転プロペ
ラ軸系において、管状の外軸と、同外軸の両端部
の内周にそれぞれ装着された軸受ブツシユと同軸
受ブツシユの内周に設けられた軸受メタルとから
なる船首側静圧軸受および船尾側静圧軸受と、こ
れらの静圧軸受により支承される内軸とをそなえ
るとともに、高圧の潤滑油を上記内軸の内部の内
軸内給油通路および同通路から上記軸受メタルの
内側へ向けて開口する給油孔を経由して上記軸受
メタルの内周へ供給する潤滑油供給系と、上記船
首側静圧軸受の前端側および上記船尾側静圧軸受
の後端側でそれぞれ上記給油孔から供給された潤
滑油の漏洩を防止すべく上記の外軸と内軸とのす
き間を閉塞する船首側シール機構および船尾側シ
ール機構と、上記船首側静圧軸受の後端側および
上記船尾側静圧軸受の前端側でこれらの静圧軸受
から上記の外軸と内軸とのすき間を経由した潤滑
油を排出すべく上記外軸の管壁に形成された排油
孔を含む潤滑油排出系とをそなえ、上記の船首側
静圧軸受および船尾側静圧軸受の各軸受メタルの
内側からそれぞれ上記の船首側シール機構および
船尾側シール機構へ向けて流出した潤滑油を上記
潤滑油排出系へ案内すべく、上記の船首側静圧軸
受および船尾側静圧軸受における各軸受ブツシユ
に、同軸受ブツシユの一端から他端へ貫通する潤
滑油案内路が形成されたことを特徴としている。 For this reason, the bearing lubrication device for a counter-rotating marine propeller of the present invention has a bearing lubricating device for a counter-rotating propeller installed at the stern of the ship, which is installed on the tubular outer shaft and on the inner periphery of both ends of the outer shaft. It is equipped with a bow side hydrostatic pressure bearing and a stern side hydrostatic pressure bearing consisting of a bearing bush and a bearing metal provided on the inner circumference of the bearing bush, and an inner shaft supported by these hydrostatic pressure bearings, as well as high-pressure lubrication. a lubricating oil supply system that supplies oil to the inner periphery of the bearing metal via an inner shaft oil supply passage inside the inner shaft and an oil supply hole opening from the passage toward the inside of the bearing metal; On the bow side, the gap between the outer shaft and the inner shaft is closed in order to prevent leakage of the lubricating oil supplied from the oil supply hole on the front end side of the side hydrostatic pressure bearing and the rear end side of the stern side hydrostatic pressure bearing, respectively. Lubrication is provided between the seal mechanism, the stern seal mechanism, the rear end of the bow hydrostatic bearing, and the front end of the stern hydrostatic bearing from these hydrostatic bearings through the gap between the outer shaft and inner shaft. A lubricating oil discharge system including an oil drain hole formed in the pipe wall of the outer shaft is provided to discharge oil, and the lubricating oil discharge system is provided with a lubricating oil discharge system including an oil discharge hole formed in the pipe wall of the outer shaft, and In order to guide the lubricating oil that has leaked toward the bow side seal mechanism and the stern side seal mechanism to the above-mentioned lubricant oil discharge system, a co-bearing bushing is installed in each bearing bush of the above-mentioned bow side hydrostatic pressure bearing and stern side hydrostatic pressure bearing. It is characterized in that a lubricating oil guide path is formed that penetrates from one end to the other end.

〔作用〕[Effect]

上述の本考案の舶用二重反転プロペラ用軸受潤
滑装置では、潤滑油供給系によつて軸受メタルの
内周へ供給された高圧の潤滑油のうち、上記軸受
メタルの内側からシール機構へ向けて流出したも
のは、軸受ブツシユに形成された潤滑油案内路を
通つて潤滑油排出系へ導かれる。 In the bearing lubricating device for a counter-rotating marine propeller of the present invention described above, the high-pressure lubricating oil supplied to the inner circumference of the bearing metal by the lubricating oil supply system is supplied from the inside of the bearing metal toward the sealing mechanism. The spilled material is directed to the lubricant discharge system through a lubricant guide path formed in the bearing bush.

〔実施例〕〔Example〕

以下、図面により本考案に実施例について説明
すると、第１〜５図は本考案の第１実施例として
の舶用二重反転プロペラ用軸受潤滑装置を示すも
ので、第１図はその縦断面図、第２図はその要部
を拡大して示す縦断面図、第３図はその静圧軸受
部の横断面図、第４図はその軸受ブツシユの横断
面図、第５図はその軸受ブツシユの変形例を示す
横断面図であり、第６図は本考案の第２実施例と
しての舶用二重反転プロペラ用軸受潤滑装置を示
す縦断面図である。 Hereinafter, embodiments of the present invention will be explained with reference to the drawings. Figures 1 to 5 show a bearing lubricating device for a counter-rotating marine propeller as a first embodiment of the present invention, and Figure 1 is a longitudinal cross-sectional view thereof. , Fig. 2 is a longitudinal cross-sectional view showing an enlarged view of the main parts, Fig. 3 is a cross-sectional view of the hydrostatic bearing section, Fig. 4 is a cross-sectional view of the bearing bushing, and Fig. 5 is a cross-sectional view of the bearing bushing. FIG. 6 is a cross-sectional view showing a modified example of the present invention, and FIG. 6 is a vertical cross-sectional view showing a bearing lubricating device for a counter-rotating marine propeller as a second embodiment of the present invention.

第１図に示すように、本考案の第１実施例の装
置が適用される舶用二重反転プロペラにおいて
は、前側プロペラ４を後端にそなえた管状の外軸
２が、スタンフレーム１６を貫通して配設され、
同スタンフレーム１６の内周面と外軸２の外周面
との間に介装された船首側外軸軸受１３および船
尾側外軸軸受１４により支承されている。これら
の軸受１３，１４はいずれも通常の船尾管軸受と
して構成される。 As shown in FIG. 1, in a counter-rotating marine propeller to which the device of the first embodiment of the present invention is applied, a tubular outer shaft 2 having a front propeller 4 at its rear end passes through a stern frame 16. is arranged,
It is supported by a bow side outer shaft bearing 13 and a stern side outer shaft bearing 14 interposed between the inner peripheral surface of the stern frame 16 and the outer peripheral surface of the outer shaft 2. Both of these bearings 13 and 14 are configured as normal stern tube bearings.

また、後側プロペラ３を後端にそなえ、内軸内
給油通路２１を有する内軸１が、外軸２内を貫通
し同外軸２と同心的に配設され、外軸２の後端部
内周面と内軸１の外周面との間に介装された船尾
側静圧軸受１５により支承されるとともに、外軸
２の前端部内周面と内軸１の外周面との間に介装
された船首側静圧軸受１２により支承されてい
る。 Further, an inner shaft 1 having a rear propeller 3 at the rear end and having an inner shaft internal oil supply passage 21 passes through the outer shaft 2 and is disposed concentrically with the outer shaft 2, and is arranged at the rear end of the outer shaft 2. It is supported by a stern hydrostatic bearing 15 interposed between the inner circumferential surface of the front end of the outer shaft 2 and the outer circumferential surface of the inner shaft 1. It is supported by a bow-side hydrostatic bearing 12 installed therein.

これらの内軸軸受としての静圧軸受１２，１５
は、いずれも第２〜４図に示すように、外軸２の
内周に装着された軸受ブツシユ１５ｃと、同軸受
ブツシユ１５ｃの内周に設けられた軸受メタル１
５ａとで構成される。 Hydrostatic bearings 12 and 15 as these inner shaft bearings
As shown in FIGS. 2 to 4, the bearing bush 15c is mounted on the inner periphery of the outer shaft 2, and the bearing metal 1 is provided on the inner periphery of the same bearing bush 15c.
5a.

そして、内軸１は図示しない反転装置に連結さ
れるとともに、外軸２も外軸継手６および２つ割
れ中空軸５を介し図示しない反転装置に連結され
ており、これらの内軸１と外軸２とは、上記反転
装置を介して図示しない主機に接続され、プロペ
ラ３，４を互いに反対方向に回転駆動しうるよう
になつている。 The inner shaft 1 is connected to a reversing device (not shown), and the outer shaft 2 is also connected to a reversing device (not shown) via an outer shaft joint 6 and a split hollow shaft 5. The shaft 2 is connected to a main engine (not shown) via the reversing device, and is configured to rotate the propellers 3 and 4 in opposite directions.

一方、外軸用シール装置９および８が、それぞ
れ船外および船内におけるスタンフレーム１６と
外軸２とのすき間を閉塞するように設けられると
ともに、内軸用シール装置としての船尾側シール
機構１０および船首側シール機構７が、それぞ
れ、船外および船内における内軸軸受１２および
１５の軸受ブツシユ１５ｃの一端側で、外軸２と
内軸１とのすき間を閉塞するように設けられてお
り、これらのシール機構７，１０は、外軸２、内
軸１およびスタンフレーム１６それぞれの相対的
な軸方向移動を防止するほか、軸受１２，１５か
らの潤滑油の漏洩を防止するようになつている。 On the other hand, outer shaft sealing devices 9 and 8 are provided to close the gaps between the stern frame 16 and the outer shaft 2 on the outside and inside the boat, respectively, and the stern side sealing mechanism 10 and A bow side seal mechanism 7 is provided at one end side of the bearing bush 15c of the inner shaft bearings 12 and 15 on the outboard and inboard sides, respectively, so as to close the gap between the outer shaft 2 and the inner shaft 1. The seal mechanisms 7 and 10 prevent relative axial movement of the outer shaft 2, inner shaft 1, and stan frame 16, respectively, and also prevent leakage of lubricating oil from the bearings 12 and 15. .

上述のような舶用二重反転プロペラ軸系の軸受
を潤滑するための本考案の第１実施例の装置にお
いては、第１，２図に示すように、内軸１の内部
に形成される内軸内給油通路２１は、その船首側
端部において給油管２０に接続されるとともに、
内軸用軸受１２，１５付近において、内軸１に放
射状に多数形成され軸受メタル１５ａの内周に連
通する給油孔２１ａに接続されていて、給油管２
０から内軸内給油通路２１に流入する潤滑油が、
給油孔２１ａを通り軸受メタル１５ａの内周に至
るように、潤滑油供給系がそなえられる。 In the device of the first embodiment of the present invention for lubricating the bearing of the contra-rotating marine propeller shaft system as described above, as shown in FIGS. The in-shaft oil supply passage 21 is connected to the oil supply pipe 20 at its bow end, and
In the vicinity of the inner shaft bearings 12 and 15, a number of oil supply holes 21a are formed radially on the inner shaft 1 and communicate with the inner periphery of the bearing metal 15a, and the oil supply pipes 2
The lubricating oil flowing into the inner shaft oil supply passage 21 from
A lubricating oil supply system is provided so as to pass through the oil supply hole 21a and reach the inner periphery of the bearing metal 15a.

また、外軸２には、船首側外軸軸受１３と外軸
用シール装置８との間付近（すなわち内軸軸受１
２および１５の軸受ブツシユ１５ｃの他端側）に
おいて、同外軸２の内側と外側とを連通し外軸２
と内軸１とのすき間から潤滑油を排出しうる潤滑
油排出系としての排油孔２２が形成される。 In addition, the outer shaft 2 is provided with an inner shaft bearing 1 in the vicinity between the bow side outer shaft bearing 13 and the outer shaft sealing device 8.
2 and 15), the inside and outside of the outer shaft 2 are connected to each other, and the outer shaft 2
An oil drain hole 22 is formed as a lubricant oil discharge system that can drain lubricant oil from the gap between the inner shaft 1 and the inner shaft 1 .

さらに、外軸軸受１３の前後にはそれぞれ排油
管２３，３０が設けられ、これらの排油管２３，
３０は、それぞれサイトグラス２４，２４を介し
高圧油タンク１８および潤滑油タンク３１に接続
されている。 Furthermore, oil drain pipes 23 and 30 are provided before and after the outer shaft bearing 13, respectively.
30 are connected to the high pressure oil tank 18 and the lubricating oil tank 31 via sight glasses 24, 24, respectively.

高圧油タンク１８は、給油管２０に高圧油ポン
プ１９を介して接続されており、潤滑油供給系に
おける内軸内給油通路２１に潤滑油を供給する。 The high-pressure oil tank 18 is connected to the oil supply pipe 20 via the high-pressure oil pump 19, and supplies lubricating oil to the inner shaft oil supply passage 21 in the lubricating oil supply system.

一方、外軸用シール装置９と船尾側外軸軸受１
４との間には、これらのシール装置９および外軸
軸受１４の内周面に潤滑油を供給すべく、給油管
３４が接続されるとともに、この給油管３４は潤
滑油ポンプ３３を介し潤滑油タンク３１に接続さ
れている。 On the other hand, the outer shaft sealing device 9 and the stern outer shaft bearing 1
4, an oil supply pipe 34 is connected to supply lubricating oil to the inner circumferential surface of the seal device 9 and the outer shaft bearing 14, and this oil supply pipe 34 supplies lubrication through a lubricant pump 33. It is connected to the oil tank 31.

なお、高圧油タンク１８には、オーバーフロー
管３２がそなえられ、高圧油タンク１８内の潤滑
油が、所定量以上になると、このオーバーフロー
管３２から潤滑油タンク３１に排出されるように
なつている。 The high-pressure oil tank 18 is provided with an overflow pipe 32, and when the lubricating oil in the high-pressure oil tank 18 exceeds a predetermined amount, it is discharged from the overflow pipe 32 into the lubricating oil tank 31. .

ところで、第３，４図に示すように、内軸用軸
受１２，１５における軸受ブツシユ１５ｃの外周
部には、軸受メタル１５ａの内側から船首側シー
ル機構７あるいは船尾側シール機構１０へ向けて
流出した潤滑油を潤滑油排出系としての排油孔２
２側へ案内するために、潤滑油案内路としての排
油溝１５ｂが複数形成されている。 By the way, as shown in FIGS. 3 and 4, on the outer periphery of the bearing bush 15c of the inner shaft bearings 12 and 15, water flows from the inside of the bearing metal 15a toward the bow side seal mechanism 7 or the stern side seal mechanism 10. Oil drain hole 2 serves as a lubricating oil discharge system for discharging the lubricating oil.
In order to guide the lubricating oil to the second side, a plurality of oil drain grooves 15b are formed as lubricating oil guide paths.

これらの排油溝１５ｂは、軸受ブツシユ１５ｃ
が外軸２への圧入に耐えうるだけの接触面積を有
する一方で、潤滑油の排出を十分に行なえるだけ
の通過面積を持つように、軸受ブツシユ１５ｃの
軸方向に形成される。 These oil drain grooves 15b are connected to the bearing bush 15c.
is formed in the axial direction of the bearing bush 15c so as to have a contact area large enough to withstand press-fitting into the outer shaft 2, and a passage area large enough to sufficiently drain lubricating oil.

なお、潤滑油案内路を、第５図に示すように、
軸受ブツシユ１５ｃの壁部内の排油孔１５ｄとし
て形成してもよい。 Note that the lubricating oil guide path is as shown in Fig. 5.
It may also be formed as an oil drain hole 15d in the wall of the bearing bush 15c.

また、第１図中の符号１１はロープガード、１
７は機関室の後部隔壁、２９は空気抜き管を示し
ている。 In addition, the code 11 in FIG. 1 is a rope guard, 1
7 indicates the rear bulkhead of the engine room, and 29 indicates an air vent pipe.

本考案の第１実施例としての舶用二重反転プロ
ペラ用軸受潤滑装置は上述のごとく構成されてい
るので、高圧油タンク１８に貯蔵される潤滑油
が、高圧油ポンプ１９により加圧されて送り出さ
れ、給油管２０に送給される。 Since the bearing lubricating device for a marine counter-rotating propeller according to the first embodiment of the present invention is constructed as described above, the lubricating oil stored in the high-pressure oil tank 18 is pressurized by the high-pressure oil pump 19 and sent out. The oil is then fed to the oil supply pipe 20.

このようにして、給油管２０に送給された高圧
の潤滑油は、内軸１の内軸内給油通路２１を船首
部から船尾部へ向かつて流れ、多数の給油孔２１
ａから内軸用軸受１２，１５の軸受メタル１５ａ
の内周へ流出し、これらの軸受１２，１５を潤滑
する。 In this way, the high-pressure lubricating oil supplied to the oil supply pipe 20 flows through the inner shaft internal oil supply passage 21 of the inner shaft 1 from the bow to the stern, and flows through the numerous oil supply holes 21.
Bearing metal 15a of inner shaft bearings 12 and 15 from a
and lubricates these bearings 12 and 15.

そして、内軸軸受１２，１５の軸受メタル１５
ａの内周に供給された高圧の潤滑油は、これらの
内軸軸受１２，１５を潤滑した後、各軸受ブツシ
ユ１５ｃの一端側における船首側シール機構７お
よび船尾側シール機構１０へ向けて流出するもの
と、軸受ブツシユ１５ｃの他端側へ流出するもの
とに分かれる。 Then, the bearing metal 15 of the inner shaft bearings 12 and 15
After lubricating these inner shaft bearings 12 and 15, the high-pressure lubricating oil supplied to the inner circumference of the shaft a flows out toward the bow side seal mechanism 7 and the stern side seal mechanism 10 at one end side of each bearing bush 15c. There are two types: one that flows out to the other end of the bearing bush 15c, and one that flows out to the other end of the bearing bush 15c.

ここで、後者の軸受ブツシユ１５ｃの他端側へ
流出した潤滑油は、外軸２と内軸１とのすき間を
通つて、外軸２に形成された排油孔２２から外軸
２の外側へ排出される。 Here, the lubricating oil that has flowed out to the other end side of the latter bearing bush 15c passes through the gap between the outer shaft 2 and the inner shaft 1 and from the oil drain hole 22 formed in the outer shaft 2 to the outside of the outer shaft 2. is discharged to.

また、前者のシール機構７，１０へ流出した潤
滑油は、同シール機構７，１０を潤滑した後、軸
受ブツシユ１５ｃの外周部に形成された排油溝１
５ｂを通つて、軸受ブツシユ１５ｃの他端側へ案
内されるので、この潤滑油も、後者の潤滑油とと
もに排油孔２２から外軸２の外側へ排出されるよ
うになる。 Further, the lubricating oil that has leaked into the former seal mechanisms 7 and 10 lubricates the same seal mechanisms 7 and 10, and then flows into the oil drain groove 1 formed on the outer periphery of the bearing bush 15c.
5b to the other end of the bearing bush 15c, this lubricating oil is also discharged from the oil drain hole 22 to the outside of the outer shaft 2 together with the latter lubricating oil.

なお、軸受ブツシユ１５ｃの一端側から他端側
への排油は両側の圧力差（約0.2〜0.3Kg／cm²）に
より行なわれるため、排出すべき潤滑油量と内軸
用軸受１２，１５の寸法とをもとに、排油溝１５
ｂ（または排油孔１５ｄ）の形状や本数が決定さ
れる。 Note that oil is drained from one end of the bearing bush 15c to the other due to the pressure difference between both sides (approximately 0.2 to 0.3 Kg/cm ² ), so the amount of lubricating oil to be drained and the inner shaft bearings 12, 15 are Based on the dimensions of the oil drain groove 15
The shape and number of the oil drain holes b (or the oil drain holes 15d) are determined.

上述のようにして外軸２と内軸１とのすき間か
ら外軸２の外側に排出された潤滑油は、外軸用シ
ール装置８および外軸軸受１３を潤滑した後、排
油管２３を通じて高圧油タンク１８へ排出され
る。 The lubricating oil discharged to the outside of the outer shaft 2 from the gap between the outer shaft 2 and the inner shaft 1 as described above lubricates the outer shaft sealing device 8 and the outer shaft bearing 13, and then flows to high pressure through the oil drain pipe 23. The oil is discharged to the oil tank 18.

一方、潤滑油タンク３１に貯蔵された潤滑油
は、潤滑油ポンプ３３により加圧されて給油管３
４に送給され、この給油管３４から外軸用シール
装置９および船尾側外軸軸受１４に供給される。 On the other hand, the lubricating oil stored in the lubricating oil tank 31 is pressurized by the lubricating oil pump 33 and
4, and is supplied from this oil supply pipe 34 to the outer shaft sealing device 9 and the stern outer shaft bearing 14.

これらのシール装置９および外軸軸受１４の潤
滑を行なつた潤滑油は、外軸２の外周面に沿つて
船首側へ流れ船首側外軸軸受１３を潤滑した後、
排油管３０から潤滑油タンク３１に排出される。 The lubricating oil that lubricates the seal device 9 and the outer shaft bearing 14 flows toward the bow side along the outer peripheral surface of the outer shaft 2 and lubricates the bow side outer shaft bearing 13, and then
The oil is discharged from the oil drain pipe 30 to the lubricating oil tank 31 .

このように、本考案の第１実施例としての舶用
二重反転プロペラ用軸受潤滑装置によれば、高圧
の潤滑油の排出が確実に行なわれるので、内軸用
軸受１２，１５として静圧軸受を、シール機構
７，１０の損傷を招くことなく採用できるように
なり、内軸用軸受１２，１５において、常に（低
速回転時においても）片当たり角、軸受荷重に関
係なく、油膜を形成することが可能となる。 As described above, according to the bearing lubrication device for marine contra-rotating propellers as the first embodiment of the present invention, high-pressure lubricating oil can be reliably discharged, so that hydrostatic bearings can be used as the inner shaft bearings 12 and 15. can be adopted without causing damage to the seal mechanisms 7 and 10, and an oil film is always formed on the inner shaft bearings 12 and 15 regardless of the one-sided contact angle or bearing load (even during low speed rotation). becomes possible.

したがつて、従来、動圧型すべく軸受を採用し
た場合に問題となつていた、片当たり等による焼
き付けを確実に防止でき、二重反転プロペラの軸
系における潤滑性能が向上する。 Therefore, it is possible to reliably prevent seizure due to uneven contact, etc., which has conventionally been a problem when a dynamic pressure type bearing is adopted, and the lubrication performance of the shaft system of the counter-rotating propeller is improved.

また、内軸１の軸径をルール径以下に抑えるこ
とができるため、二重反転プロペラ軸系全体を、
容易にかつ低コストでコンパクトに構成でき、プ
ロペラ性能の向上にも寄与しうる。 In addition, since the shaft diameter of the inner shaft 1 can be kept below the rule diameter, the entire counter-rotating propeller shaft system can be
It can be easily constructed at low cost and compactly, and can also contribute to improving propeller performance.

次に、本考案の第２実施例としての舶用二重反
転プロペラ用軸受潤滑装置について説明すると、
第６図に示すように、この第２実施例も第１実施
例とほぼ同様に構成されているが、第２実施例で
は、船尾側外軸軸受１４′として静圧軸受が用い
られており、第１実施例において船尾側外軸軸受
（船尾管軸受）１４に潤滑油を送給するためにそ
なえられた潤滑油タンク３１、潤滑油ポンプ３
３、給油管３４等は削除されるとともに、排油管
３０も削除されている。 Next, a bearing lubricating device for a marine counter-rotating propeller as a second embodiment of the present invention will be explained.
As shown in FIG. 6, this second embodiment has almost the same structure as the first embodiment, but in the second embodiment, a hydrostatic bearing is used as the stern outer shaft bearing 14'. , a lubricating oil tank 31 and a lubricating oil pump 3 provided for supplying lubricating oil to the stern outer shaft bearing (stern tube bearing) 14 in the first embodiment.
3. The oil supply pipe 34 and the like have been removed, as well as the oil drain pipe 30.

そして、船尾側外軸軸受（静圧軸受）１４′の
中央部には、同外軸軸受１４′の内周面と外軸２
の外周面との間に高圧の潤滑油を供給すべく、給
油管２６が接続されるとともに、この給油管２６
はオリフイス２５および高圧油ポンプ１９を介し
高圧油タンク１８に接続されている。 At the center of the stern side outer shaft bearing (static pressure bearing) 14', the inner circumferential surface of the outer shaft bearing 14' and the outer shaft 2
An oil supply pipe 26 is connected to supply high-pressure lubricating oil between the outer peripheral surface of the oil supply pipe 26 and
is connected to the high pressure oil tank 18 via an orifice 25 and a high pressure oil pump 19.

また、外軸用シール装置９と船尾側外軸軸受
（静圧軸受）１４′との間の位置において、スタン
フレーム１６には、排油管２７が開口して形成さ
れていて、この排油管２７は流量計２８およびサ
イトグラス２４を介し排油管２３に合流し高圧油
タンク１８に接続される。 Further, an oil drain pipe 27 is formed in the stern frame 16 with an opening at a position between the outer shaft sealing device 9 and the stern outer shaft bearing (static pressure bearing) 14'. flows through a flowmeter 28 and a sight glass 24 into an oil drain pipe 23 and is connected to a high pressure oil tank 18.

上述の構成により、この第２実施例において
は、内軸軸受１２，１５における潤滑は第１実施
例と全く同様に行なわれる一方、高圧油タンク１
８から高圧油ポンプ１９により加圧され給油管２
６に送給された高圧の潤滑油のうちの一部は、外
軸軸受（静圧軸受）１４′の潤滑を行なつた後、
外軸２の外周面に沿つて船首側へ流れ、船首側外
軸軸受１３を潤滑してから、排油管２３から高圧
油タンク１８に排出される。また、上記高圧の潤
滑油のうち、外軸２の外周面に沿つて船尾側へ流
れたものは、外軸用シール装置９を潤滑した後、
排油管２７から高圧油タンク１８へ排出される。 With the above-mentioned configuration, in the second embodiment, lubrication of the inner shaft bearings 12 and 15 is performed in exactly the same manner as in the first embodiment, while the high-pressure oil tank 1
8 is pressurized by a high-pressure oil pump 19 and fed into the oil supply pipe 2
A part of the high pressure lubricating oil fed to the outer shaft bearing (hydrostatic bearing) 14' is lubricated and then discharged.
The high-pressure lubricating oil flows along the outer peripheral surface of the outer shaft 2 toward the bow side, lubricates the bow-side outer shaft bearing 13, and is then discharged from the oil drain pipe 23 to the high-pressure oil tank 18. The high-pressure lubricating oil that flows along the outer peripheral surface of the outer shaft 2 toward the stern side lubricates the outer shaft seal device 9, and then
The oil is discharged from the oil drain pipe 27 to the high-pressure oil tank 18 .

このようにして、本考案の第２実施例でも、第
１実施例と同様の作用効果が得られるのである。 In this way, the second embodiment of the present invention can provide the same effects as the first embodiment.

〔考案の効果〕[Effect of idea]

以上詳述したように、本考案の舶用二重反転プ
ロペラ用軸受潤滑装置によれば、船尾に設けられ
た二重反転プロペラ軸系において、管状の外軸
と、同外軸の両端部の内周にそれぞれ装着された
軸受ブツシユと同軸受ブツシユの内周に設けられ
た軸受メタルとからなる船首側静圧軸受および船
尾側静圧軸受と、これらの静圧軸受により支承さ
れる内軸とをそなえるとともに、高圧の潤滑油を
上記内軸の内部の内軸内給油通路および同通路か
ら上記軸受メタルの内側へ向けて開口する給油孔
を経由して上記軸受メタルの内周へ供給する潤滑
油供給系と、上記船首側静圧軸受の前端側および
上記船尾側静圧軸受の後端側でそれぞれ上記給油
孔から供給された潤滑油の漏洩を防止すべく上記
の外軸と内軸とのすき間を閉塞する船首側シール
機構および船尾側シール機構と、上記船首側静圧
軸受の後端側および上記船尾側静圧軸受の前端側
でこられの静圧軸受から上記の外軸と内軸とのす
き間を経由した潤滑油を排出すべく上記外軸の管
壁に形成された排油孔を含む潤滑油排出系とをそ
なえ、上記の船首側静圧軸受および船尾側静圧軸
受の各軸受メタルの内側からそれぞれ上記の船首
側シール機構および船尾側シール機構へ向けて流
出した潤滑油を上記潤滑油排出系へ案内すべく、
上記の船首側静圧軸受および船尾側静圧軸受にお
ける各軸受ブツシユに、同軸受ブツシユの一端か
ら他端へ貫通する潤滑油案内路が形成されるとい
う簡素な構成で、高圧の潤滑油を外軸と内軸との
すき間から確実に排出できるので、静圧用軸受
を、シール機構の損傷を招くことなく採用でき、
片当たり等による焼き付けが防止されて、二重反
転プロペラ軸系における潤滑性能が大幅に向上す
るのである。また、静圧軸受の採用により、内軸
の軸径をルール径以下に抑えることができるた
め、二重反転プロペラ軸系全体を、容易にかつ低
コストでコンパクトに構成できるようになり、プ
ロペラ性能が大幅に向上する利点もある。 As described in detail above, according to the bearing lubrication device for a counter-rotating marine propeller of the present invention, in the counter-rotating propeller shaft system installed at the stern, a tubular outer shaft and an inner wall at both ends of the outer shaft are provided. A bow side hydrostatic pressure bearing and a stern side hydrostatic pressure bearing, each consisting of a bearing bush attached to the periphery and a bearing metal provided on the inner periphery of the same bearing bush, and an inner shaft supported by these hydrostatic pressure bearings. At the same time, high-pressure lubricating oil is supplied to the inner periphery of the bearing metal via an inner shaft oil supply passage inside the inner shaft and an oil supply hole opening from the same passage toward the inside of the bearing metal. The supply system is connected to the outer shaft and the inner shaft to prevent leakage of the lubricating oil supplied from the oil supply hole at the front end of the bow hydrostatic bearing and the rear end of the stern hydrostatic bearing, respectively. A bow side seal mechanism and a stern side seal mechanism that close the gap, and a rear end side of the bow side hydrostatic pressure bearing and a front end side of the above stern side hydrostatic pressure bearing are connected to the outer shaft and the inner shaft from these hydrostatic pressure bearings. and a lubricating oil discharge system including an oil drain hole formed in the tube wall of the outer shaft to discharge the lubricating oil that has passed through the gap between the bow side hydrostatic bearing and the stern side hydrostatic bearing. In order to guide the lubricating oil flowing out from the inside of the bearing metal toward the bow side seal mechanism and the stern side seal mechanism, respectively, to the above lubricant oil discharge system,
A simple structure in which a lubricating oil guide path is formed in each bearing bush of the above-mentioned bow side hydrostatic bearing and stern side hydrostatic bearing from one end of the bearing bush to the other, allowing high pressure lubricating oil to be removed. Since the air can be reliably discharged from the gap between the shaft and the inner shaft, static pressure bearings can be used without damaging the seal mechanism.
Seizure caused by uneven contact is prevented, and the lubrication performance of the counter-rotating propeller shaft system is greatly improved. In addition, by using hydrostatic bearings, the diameter of the inner shaft can be kept below the rule diameter, making it possible to construct the entire contra-rotating propeller shaft system easily, at low cost, and compactly, resulting in improved propeller performance. There is also the advantage of significantly improving

【図面の簡単な説明】[Brief explanation of the drawing]

第１〜５図は本考案の第１実施例としての舶用
二重反転プロペラ用軸受潤滑装置を示すもので、
第１図はその縦断面図、第２図はその要部を拡大
して示す縦断面図、第３図はその静圧軸受部の横
断面図、第４図はその軸受ブツシユの横断面図、
第５図はその軸受ブツシユの変形例を示す横断面
図であり、第６図は本考案の第２実施例としての
舶用二重反転プロペラ用軸受潤滑装置を示す縦断
面図であり、第７図は動圧型すべり軸受による従
来の舶用二重反転プロペラ用軸受潤滑装置を示す
縦断面図であり、第８図は静圧軸受による従来の
舶用二重反転プロペラ用軸受潤滑装置の要部を示
す横断面図である。 １……内軸、２……外軸、３……後側プロペ
ラ、４……前側プロペラ、５……２つ割れ中空
軸、６……外軸継手、７……船首側シール機構、
８，９……外軸用シール装置、１０……船尾側シ
ール機構、１１……ロープガード、１２……船首
側静圧軸受、１３……船首側外軸軸受（船尾管軸
受）、１４……船尾側外軸軸受（船尾管軸受）、１
４′……船尾側外軸軸受（静圧軸受）、１５……船
尾側静圧軸受、１５ａ……軸受メタル、１５ｂ…
…潤滑油案内路としての排油溝、１５ｃ……軸受
ブツシユ、１５ｄ……潤滑油案内路としての排油
孔、１６……スタンフレーム、１７……機関室の
後部隔壁、１８……高圧油タンク、１９……高圧
油ポンプ、２０……給油管、２１……内軸内給油
通路、２１ａ……給油孔、２２……潤滑油排出系
としての排油孔、２３……排油管、２４……サイ
トグラス、２５……オリフイス、２６……給油
管、２７……排油管、２８……流量計、２９……
空気抜き管、３０……排油管、３１……潤滑油タ
ンク、３２……オーバーフロー管、３３……潤滑
油ポンプ、３４……給油管。 1 to 5 show a bearing lubricating device for a contra-rotating marine propeller as a first embodiment of the present invention.
Figure 1 is a vertical cross-sectional view of the same, Figure 2 is a vertical cross-sectional view showing an enlarged view of the main parts, Figure 3 is a cross-sectional view of the hydrostatic bearing section, and Figure 4 is a cross-sectional view of the bearing bushing. ,
FIG. 5 is a cross-sectional view showing a modified example of the bearing bushing, FIG. 6 is a longitudinal cross-sectional view showing a bearing lubricating device for a counter-rotating marine propeller as a second embodiment of the present invention, and FIG. The figure is a longitudinal cross-sectional view showing a conventional bearing lubrication system for marine counter-rotating propellers using hydrodynamic sliding bearings, and Figure 8 shows the main parts of a conventional bearing lubrication system for marine contra-rotating propellers using hydrostatic pressure bearings. FIG. 1... Inner shaft, 2... Outer shaft, 3... Rear propeller, 4... Front propeller, 5... Hollow shaft split in two, 6... Outer shaft joint, 7... Bow side seal mechanism,
8, 9... Seal device for outer shaft, 10... Stern side seal mechanism, 11... Rope guard, 12... Bow side static pressure bearing, 13... Bow side outer shaft bearing (stern tube bearing), 14... ...Stern side outer shaft bearing (stern tube bearing), 1
4'...Stern side outer shaft bearing (static pressure bearing), 15...Stern side static pressure bearing, 15a...Bearing metal, 15b...
...Oil drain groove as a lubricating oil guide path, 15c... Bearing bush, 15d... Oil drain hole as a lubricating oil guide path, 16... Stan frame, 17... Rear bulkhead of engine room, 18... High pressure oil Tank, 19... High pressure oil pump, 20... Oil supply pipe, 21... Oil supply passage in the inner shaft, 21a... Oil supply hole, 22... Oil drain hole as a lubricating oil discharge system, 23... Oil drain pipe, 24 ... Sight glass, 25 ... Orifice, 26 ... Oil supply pipe, 27 ... Oil drain pipe, 28 ... Flowmeter, 29 ...
Air vent pipe, 30... oil drain pipe, 31... lubricating oil tank, 32... overflow pipe, 33... lubricating oil pump, 34... oil supply pipe.

Claims (1)

【実用新案登録請求の範囲】[Scope of utility model registration request] 船尾に設けられた二重反転プロペラ軸系におい
て、管状の外軸と、同外軸の両端部の内周にそれ
ぞれ装着された軸受ブツシユと同軸受ブツシユの
内周に設けられた軸受メタルとからなる船首側静
圧軸受および船尾側静圧軸受と、これらの静圧軸
受により支承される内軸とをそなえるとともに、
高圧の潤滑油を上記内軸の内部の内軸内給油通路
および同通路から上記軸受メタルの内側へ向けて
開口する給油孔を経由して上記軸受メタルの内周
へ供給する潤滑油供給系と、上記船首側静圧軸受
の前端側および上記船尾側静圧軸受の後端側でそ
れぞれ上記給油孔から供給された潤滑油の漏洩を
防止すべく上記の外軸と内軸とのすき間を閉塞す
る船首側シール機構および船尾側シール機構と、
上記船首側静圧軸受の後端側および上記船尾側静
圧軸受の前端側でこれらの静圧軸受から上記の外
軸と内軸とのすき間を経由した潤滑油を排出すべ
く上記外軸の管壁に形成された排油孔を含む潤滑
油排出系とをそなえ、上記の船首側静圧軸受およ
び船尾側静圧軸受の各軸受メタルの内側からそれ
ぞれ上記の船首側シール機構および船尾側シール
機構へ向けて流出した潤滑油を上記潤滑油排出系
へ案内すべく、上記の船首側静圧軸受および船尾
側静圧軸受における各軸受ブツシユに、同軸受ブ
ツシユの一端から他端へ貫通する潤滑油案内路が
形成されたことを特徴とする、舶用二重反転プロ
ペラ用軸受潤滑装置。 In the contra-rotating propeller shaft system installed at the stern, the shaft is made up of a tubular outer shaft, bearing bushes attached to the inner periphery of both ends of the outer shaft, and bearing metal provided on the inner periphery of the same bearing bushes. It is equipped with a bow side hydrostatic pressure bearing and a stern side hydrostatic pressure bearing, and an inner shaft supported by these hydrostatic pressure bearings.
A lubricating oil supply system that supplies high-pressure lubricating oil to the inner periphery of the bearing metal via an inner shaft oil supply passage inside the inner shaft and an oil supply hole opening from the same passage toward the inside of the bearing metal. , close the gap between the outer shaft and the inner shaft to prevent leakage of the lubricating oil supplied from the oil supply hole at the front end of the bow hydrostatic bearing and the rear end of the stern hydrostatic bearing, respectively. a bow side seal mechanism and a stern side seal mechanism,
In order to drain the lubricating oil that has passed through the gap between the outer shaft and the inner shaft from the hydrostatic bearings at the rear end of the bow hydrostatic bearing and the front end of the stern hydrostatic bearing, The bow side seal mechanism and the stern side seal are installed from the inside of each bearing metal of the bow side hydrostatic bearing and the stern side hydrostatic bearing, respectively. In order to guide the lubricating oil that has flowed out toward the mechanism to the lubricating oil discharge system, a lubricant is installed in each of the bearing bushes of the bow side hydrostatic bearing and the stern side hydrostatic bearing, which penetrates from one end of the bearing bush to the other end. A bearing lubricating device for a counter-rotating marine propeller, characterized in that an oil guide path is formed.