JPH0840370A - Bearing device for counter rotating propeller shaft - Google Patents

Abstract

PURPOSE:To hold down lowering of strength of an inner shaft to the minimum so as to ensure a suitable flow of lubricating oil without the generation of oil film pressure at an unnecessarily high level in the whole interior of a bearing by setting the circumferential positions of oil filling holes with the phases shifted from each other in the sectional position. CONSTITUTION:An oil filling path 12 for receiving lubricating oil from an external lubricating oil supply device is bored extending to the vicinity of the rear end of an inner shaft 2 on the axis of the inner shaft 2. The inner shaft 2 is provided with oil filling holes 13 for guiding lubricating oil supplied by the oil filling path 12 to the bearing surfaces of inner shaft bearings 8, 9 within a range supported on the inner shaft bearings 8, 9. The oil filling holes 13 are formed on two parts in such a manner as to be opposite to each other on one rectilinear diameter in the section right-angled to the axis of the inner shaft 2, and located in such a manner as to be shifted in the circumferential direction with a phase difference between them in the respective sections in plural positions within the range of the inner shaft bearings 8, 9.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は船舶の二重反転プロペラ
軸用軸受装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device for a contra-rotating propeller shaft of a ship.

【０００２】[0002]

【従来の技術】二重反転プロペラ装置は、中空な外軸及
び該外軸の中空空間に該外軸に対し同心に配列した内軸
の二つの推進軸のそれぞれにプロペラを前後して装着
し、各々の軸を逆方向に回転させることによって推進効
率を向上させる省エネルギー装置である。2. Description of the Related Art A counter-rotating propeller device has a propeller mounted in front of and behind each of a hollow outer shaft and two propulsion shafts of an inner shaft concentrically arranged with respect to the outer shaft in a hollow space of the outer shaft. , An energy-saving device that improves propulsion efficiency by rotating each shaft in opposite directions.

【０００３】このような装置を搭載する船舶の軸系にお
いては、従来の単軸の船舶で用いられている軸を支える
軸受の他に、内軸と外軸との間の金属接触を回避するた
めの軸受が必要となる。この内・外軸は、互いに反転す
るために従来用いられている真円すべり軸受を反転軸受
に採用した場合、軸の回転に起因して生じる動圧が発生
しにくいという欠点がある。特に、内・外軸の回転数が
同一、すなわち、反転比が１の場合には、動圧はまった
く発生せず負荷容量は零となる。In a shaft system of a ship equipped with such a device, in addition to a bearing for supporting a shaft used in a conventional single-shaft ship, metal contact between an inner shaft and an outer shaft is avoided. Bearings are required. The inner and outer shafts have a drawback in that, when a perfect circular slide bearing that is conventionally used for reversing each other is adopted as the reversing bearing, dynamic pressure generated due to the rotation of the shaft does not easily occur. In particular, when the rotation speeds of the inner and outer shafts are the same, that is, when the reversal ratio is 1, no dynamic pressure is generated and the load capacity becomes zero.

【０００４】従来、このような問題点を解決する二重反
転プロペラ軸用軸受が特開昭６２−１１０５９５に開示
されている。Conventionally, a counter-rotating propeller shaft bearing that solves such a problem is disclosed in Japanese Patent Laid-Open No. 62-110595.

【０００５】この公知の発明は、内軸を軸芯位置にて中
空として給油路を形成し、内軸軸受面の範囲内において
上記給油路から内軸の外周面へ放射状に貫通する複数本
の給油孔を、内軸の軸線方向の複数位置に配設して潤滑
油の供給を行うことにより低速運転時の金属接触を防止
すると共に軸受後端部の片当たりによる軸受の焼き付き
を防止するものである。According to this known invention, the inner shaft is hollow at the axial center position to form an oil supply passage, and a plurality of radial passages are radially penetrated from the oil supply passage to the outer peripheral surface of the inner shaft within the range of the inner shaft bearing surface. Lubricating holes are provided at multiple positions in the axial direction of the inner shaft to supply lubricating oil to prevent metal contact during low-speed operation and prevent seizure of the bearing due to uneven contact at the rear end of the bearing. Is.

【０００６】[0006]

【発明が解決しようとする課題】しかし、上述した従来
技術には、次に示す解決すべき問題点がある。However, the above-mentioned prior art has the following problems to be solved.

【０００７】軸の長手方向各断面において放射状に、
軸線方向の複数位置に配設した給油孔は、給油孔の個数
が多いために軸の強度を低下させる。このため、軸径を
太くしなければならない等の処置が必要となる。Radially in each longitudinal section of the shaft,
The oil supply holes arranged at a plurality of positions in the axial direction reduce the strength of the shaft because of the large number of oil supply holes. Therefore, it is necessary to take measures such as increasing the shaft diameter.

【０００８】円周方向、軸方向に給油孔の個数が多い
ため、軸受内全体に不必要に高いレベルの油膜圧力が発
生し、潤滑油流量が大量に必要となる。Since the number of oil supply holes is large in the circumferential direction and the axial direction, an unnecessarily high level of oil film pressure is generated in the entire bearing, and a large amount of lubricating oil flow is required.

【０００９】同一断面において多数の給油孔（実施例
では八個）を放射状に配設しているため、内軸の回転中
に内軸軸受表面に直接潤滑油噴流が衝突する頻度が多
く、内軸軸受表面へのエロージョン発生の危険が高い。Since a large number of oil supply holes (eight in the embodiment) are radially arranged in the same cross section, the lubricating oil jet often collides directly with the inner shaft bearing surface during rotation of the inner shaft. There is a high risk of erosion on the shaft bearing surface.

【００１０】給油孔の個数が多いため加工の工数大で
コスト高となる。Since the number of oil supply holes is large, the number of processing steps is large and the cost is high.

【００１１】本発明は従来かかえていたかかる問題を解
決し、製作が容易で、強度があまり低下せず、潤滑油が
少なくてすみ、そしてエロージョン発生の危険性の低い
船舶の二重反転プロペラ軸用軸受装置を提供することを
目的とする。The present invention solves the above-mentioned problems, is easy to manufacture, does not significantly reduce the strength, requires less lubricating oil, and has a low risk of erosion, and has a low risk of erosion. An object of the present invention is to provide a bearing device for use.

【００１２】[0012]

【課題を解決するための手段】本発明によれば、上記目
的は中空な外軸と該外軸の中空空間内に同心に配された
内軸とを有し、内軸が外軸より後方に突出した部分及び
外軸の後端部分に互いに逆方向に回転するプロペラがそ
れぞれに取りつけられ、外軸には内軸を摺動回転自在に
支持する軸受が設けられ、内軸に軸線方向に延びて形成
された給油路からの潤滑油を上記軸受の接面せる該内軸
の外周面に導く給油孔が該内軸に形成されている二重反
転プロペラ軸用軸受装置において、上記内軸の軸線に直
角な断面にて一つの直径線上で対向する二箇所に設けら
れた給油孔を、上記軸線方向での複数の断面位置に設
け、各断面位置での給油孔の周方向位置が互いに位相を
ずらして設定されていることにより達成される。According to the present invention, the above object has a hollow outer shaft and an inner shaft concentrically arranged in a hollow space of the outer shaft, the inner shaft being rearward of the outer shaft. Propellers that rotate in mutually opposite directions are attached to the protruding portion and the rear end portion of the outer shaft, and the outer shaft is provided with a bearing that slidably and rotatably supports the inner shaft. A bearing device for a counter-rotating propeller shaft, wherein an oil supply hole is formed in the inner shaft for guiding lubricating oil from an extended oil supply passage to the outer peripheral surface of the inner shaft that contacts the bearing. In the cross section perpendicular to the axis line of, the oil supply holes provided at two locations facing each other on one diameter line are provided at a plurality of cross-section positions in the axial direction, and the circumferential positions of the oil supply holes at each cross-section position are different from each other. This is achieved by setting the phases out of phase.

【００１３】[0013]

【作用】上記構成になる本発明では、内軸の軸線方向に
形成された給油路を通って供給された潤滑油は、内軸の
軸線位置に直角な各断面にて一つの直径線上で対向する
二箇所、そして内軸の軸線方向複数位置の断面に内軸外
周面へ開口して設けられた給油孔により内軸外面と内軸
軸受との摺動面へと供給され、内軸軸受の潤滑を行う。According to the present invention having the above-mentioned structure, the lubricating oil supplied through the oil supply passage formed in the axial direction of the inner shaft is opposed on one diameter line in each cross section perpendicular to the axial position of the inner shaft. It is supplied to the sliding surface between the inner shaft outer surface and the inner shaft bearing by the oil supply holes provided at the two positions, and the cross section at a plurality of positions in the axial direction of the inner shaft, opening to the outer peripheral surface of the inner shaft. Lubricate.

【００１４】上記直径線上で対向する二つの給油孔は、
内軸の軸線方向の複数位置にて位相がずれて設けられて
いるので、軸受全体からみて給油孔の数が少なくとも、
軸受全域に均一かつ十分なる油膜圧力を形成する。The two oil supply holes facing each other on the diameter line are
Since the phases are provided at different positions in the axial direction of the inner shaft, the number of oil supply holes is at least as viewed from the entire bearing,
A uniform and sufficient oil film pressure is formed over the entire bearing.

【００１５】なお、上記給油孔の位相のずれは、９０de
g.，６０deg.，４５deg.等適宜選択して決定することが
できる。The phase shift of the oil supply hole is 90 de
g., 60 deg., 45 deg., etc. can be appropriately selected and determined.

【００１６】[0016]

【実施例】以下、添付図面にもとづき、本発明の実施例
を説明する。Embodiments of the present invention will be described below with reference to the accompanying drawings.

【００１７】図１は本発明の一実施例装置の軸線を含む
面での断面図である。FIG. 1 is a sectional view of an apparatus according to an embodiment of the present invention, taken along a plane including the axis.

【００１８】図において、プロペラ１が後端部（図にて
左端部）に取りつけられた内軸２は、プロペラ３が取り
つけられ、該内軸２とは逆向きに回転する外軸４の中空
空間に収められている。上記外軸４は船体の船尾部５に
設けられた外軸軸受６，７によって回転自在に支持され
ている。そして、内軸２は、外軸４の内径に設けられた
内軸軸受８，９によって回転自在に支持されている。上
記船尾部５と外軸４との間、そして外軸４と内軸２との
間には、それぞれ相対回転を許容するシール１０，１１
が設けられている。In the drawing, a propeller 3 is attached to an inner shaft 2 to which a propeller 1 is attached at a rear end portion (left end in the figure), and a hollow outer shaft 4 which rotates in a direction opposite to the inner shaft 2 is attached. It is contained in space. The outer shaft 4 is rotatably supported by outer shaft bearings 6 and 7 provided on a stern portion 5 of the hull. The inner shaft 2 is rotatably supported by inner shaft bearings 8 and 9 provided on the inner diameter of the outer shaft 4. Between the stern 5 and the outer shaft 4, and between the outer shaft 4 and the inner shaft 2, seals 10 and 11 which permit relative rotation, respectively.
Is provided.

【００１９】上記内軸２の中心軸線上には、図２にも見
られるように、外部の潤滑油供給装置（図示せず）から
潤滑油を受ける給油路１２が該内軸２の後端近くまで延
びて穿設されている。内軸２は、内軸軸受８，９によっ
て支持される範囲内に、上記給油路１２により供給され
る潤滑油を上記内軸軸受８，９の軸受面に導く給油孔１
３が設けられている。該給油孔１３は、内軸２の軸線に
対し直角な断面にて、一つの直径線上で対向するように
二箇所に設けられ、図３，４に見られるように上記内軸
軸受の範囲内での複数位置の各断面でそれぞれ位相差を
もって周方向にずれた位置に設けられている。図示の例
では断面位置Ａ，Ｂ，ＣそしてＤにて、図３，４のごと
く９０deg.ずつずれている。図３は位置Ａ，Ｃそして図
４は位置Ｂ，Ｄにおける内軸２についての断面を示す。
上記位相差は、特にその限定はなく、例えば３０deg.，
４５deg.，６０deg.等とすることもできる。通常、上記
対向する二つの給油孔１３が設けられる断面の位置の数
が多い程、上記位相差をなす角度を小さくすることがで
きる。本実施例では、各給油孔１３の出口部に絞り１４
を設けているが、給油孔の寸法の設定次第では、この絞
り１４は特には必要としない。On the central axis of the inner shaft 2, an oil supply passage 12 for receiving lubricating oil from an external lubricating oil supply device (not shown) is provided at the rear end of the inner shaft 2 as shown in FIG. It is extended to the vicinity and drilled. The inner shaft 2 guides the lubricating oil supplied by the oil supply passage 12 to the bearing surfaces of the inner shaft bearings 8 and 9 within a range supported by the inner shaft bearings 8 and 9.
3 is provided. The oil supply holes 13 are provided at two positions so as to face each other on one diameter line in a cross section perpendicular to the axis of the inner shaft 2, and as shown in FIGS. In each of the cross-sections at a plurality of positions, the positions are shifted in the circumferential direction with a phase difference. In the illustrated example, the cross-sectional positions A, B, C and D are deviated by 90 deg. As shown in FIGS. 3 shows positions A and C, and FIG. 4 shows cross sections about the inner shaft 2 at positions B and D.
The phase difference is not particularly limited, and may be 30 deg.,
It may be 45 deg., 60 deg. Or the like. Generally, the greater the number of positions of the cross section where the two opposing oil supply holes 13 are provided, the smaller the angle forming the phase difference can be. In this embodiment, a throttle 14 is provided at the outlet of each oil supply hole 13.
However, depending on the setting of the size of the oil supply hole, the diaphragm 14 is not particularly necessary.

【００２０】かかる本実施例装置では、内軸２の回転
中、軸受荷重は主として上下方向に対向して位置するこ
ととなった給油孔の領域での油膜圧力によって支えられ
る。In the apparatus of this embodiment, during the rotation of the inner shaft 2, the bearing load is mainly supported by the oil film pressure in the area of the oil supply hole which is positioned so as to face each other in the vertical direction.

【００２１】ここで、本実施例の軸受における油膜圧力
分布について、従来の軸受と比較しつつ説明する。Here, the oil film pressure distribution in the bearing of this embodiment will be described in comparison with the conventional bearing.

【００２２】図５において、横軸は周方向の位置を角度
θ（deg.)で表わし、縦軸は角度θにおける油膜圧力を
表わしたものである。図中、曲線Ｉは本実施例を示し内
軸の各断面に対向する二つの給油孔をもち各断面にてそ
の位置を９０deg.ずつずらしたもの、曲線IIは従来形式
で放射状に八個の給油孔をもち、これを上記曲線Ｉと同
じ数の断面位置に設けたものである。In FIG. 5, the horizontal axis represents the circumferential position by the angle θ (deg.), And the vertical axis represents the oil film pressure at the angle θ. In the figure, a curve I shows the present embodiment and has two oil supply holes facing each cross section of the inner shaft, and the positions thereof are deviated by 90 deg. In each cross section. It has an oil supply hole and is provided at the same number of cross-sectional positions as the curve I.

【００２３】曲線IIの場合、軸受の全周にわたって油膜
圧力が高い。負荷が作用する内軸を支えるために軸受が
発生する負荷容量は、軸受下側（円周方向角度１８０〜
３６０deg.) に発生する圧力と軸受上側（０〜１８０de
g.）に発生する圧力との差に比例する。したがって、軸
受の全周にわたって油膜圧力を高くする必要はなく、逆
にそうすることで潤滑油流量を多くしてしまうという欠
点がある。In the case of curve II, the oil film pressure is high over the entire circumference of the bearing. The load capacity generated by the bearing to support the inner shaft on which the load acts is the lower side of the bearing (circumferential angle 180-
Pressure generated at 360deg. And the upper side of the bearing (0 to 180de
g.) is proportional to the pressure difference. Therefore, it is not necessary to increase the oil film pressure over the entire circumference of the bearing, and conversely, there is a disadvantage that the lubricating oil flow rate is increased.

【００２４】曲線Ｉの場合は、一断面にて対向する二箇
所に給油を限定することで、円周方向の圧力分布を全体
に低く抑え、同一の負荷を支え、かつ潤滑油流量を低く
抑えることができる。（図５の例では曲線IIの場合で必
要な潤滑油流量は、曲線Ｉの場合の約二分の一であ
る。）ただし、二箇所給油一断面だけでは軸の回転位置
（給油孔の円周方向位置）によって負荷容量の変動が大
きいため、内軸の軸線方向に位相をずらして複数配列す
るものである。In the case of the curve I, the oil supply is limited to two locations facing each other in one cross section, so that the pressure distribution in the circumferential direction can be kept low, the same load can be supported, and the lubricating oil flow rate can be kept low. be able to. (In the example of FIG. 5, the flow rate of the lubricating oil required in the case of curve II is about one half that in the case of curve I.) Since the load capacity varies greatly depending on the directional position), a plurality of arrays are arranged with a phase shift in the axial direction of the inner shaft.

【００２５】このように給油孔を配設することで、同一
の負荷容量を保ちながら軸受内に不必要に高いレベルの
油膜圧力を発生させず、潤滑油流量を適正に抑えること
が可能となる。By arranging the oil supply holes in this manner, it is possible to properly suppress the lubricating oil flow rate without generating an unnecessarily high level of oil film pressure in the bearing while maintaining the same load capacity. .

【００２６】本発明では既述のごとく内軸の軸線に直角
な各断面での給油孔の周方向位置をずらして設けるが、
そのずらす角度は図２（そして図３，４）の場合のごと
く９０deg.に限定されず、図６のごとく６０deg.とする
こともできる。図７〜９に示されるごとく、図６におけ
る断面の位置Ｅ，Ｈ（図７）と、位置Ｆ，Ｉ（図８）
と、そして位置Ｇ，Ｊ（図９）とではそれぞれ６０deg.
ずつずれている。なお、図６においては、各給油孔は絞
りのないものとして示したが、絞りを設けてもよい。さ
らに、図１０そして図１１〜１４に示すように４５deg.
ずつずらしてもよい。なお、図１１は図１２における位
置Ｋ，Ｏ、図１２は位置Ｌ，Ｐ、図１３は位置Ｍ，Ｑ、
そして図１４は位置Ｎ，Ｒでの断面を示している。According to the present invention, as described above, the circumferential positions of the oil supply holes in each cross section perpendicular to the axis of the inner shaft are provided so as to be displaced.
The shift angle is not limited to 90 deg. As in the case of FIG. 2 (and FIGS. 3 and 4), but may be 60 deg. As in FIG. As shown in FIGS. 7 to 9, positions E and H (FIG. 7) and positions F and I (FIG. 8) of the cross section in FIG.
And at positions G and J (FIG. 9), 60 deg.
It is deviating from each other. In FIG. 6, each oil supply hole is shown as having no throttle, but a throttle may be provided. Furthermore, as shown in FIG. 10 and FIGS. 11 to 14, 45 deg.
You may shift them one by one. Note that FIG. 11 shows positions K and O in FIG. 12, FIG. 12 shows positions L and P, and FIG. 13 shows positions M and Q.
14 shows a cross section at the positions N and R.

【００２７】本発明では、給油孔にポケットを設け、負
荷容量を増大させることもできる。例えば、図１５及び
図１６，１７のように９０deg.ずつずれて配置された各
給油孔１５の出口部にポケット１６を設けることができ
る。なお、図１６及び図１７は、図１５の位置Ｓ，Ｔに
おける断面をそれぞれ示している。In the present invention, the oil supply hole may be provided with a pocket to increase the load capacity. For example, as shown in FIGS. 15 and 16 and 17, the pockets 16 can be provided at the outlets of the respective oil supply holes 15 which are displaced by 90 degrees. 16 and 17 show cross sections at positions S and T in FIG. 15, respectively.

【００２８】ポケットは上記図１５のごとく円形には限
定されない。図１８のごとく、内軸の軸線方向に長く延
びるポケット１７としてもよい。こうすることにより、
油膜圧力の軸線方向分布を所望の形態に改善できる。な
お、図１９，２０は図１８の位置Ｕ，Ｖにおける断面を
それぞれ示す。さらに、周方向に長く延びるポケット１
８としてもよい。その場合は、油膜圧力の周方向分布を
所望の形態に改善できる。なお、図２２，２３は図２１
の位置Ｗ，Ｘにおける断面をそれぞれ示す。The pocket is not limited to the circular shape as shown in FIG. As shown in FIG. 18, the pocket 17 may be elongated in the axial direction of the inner shaft. By doing this,
The distribution of the oil film pressure in the axial direction can be improved to a desired form. 19 and 20 show cross sections at positions U and V in FIG. 18, respectively. Furthermore, a pocket 1 extending in the circumferential direction is long.
It may be eight. In that case, the circumferential distribution of the oil film pressure can be improved to a desired form. 22 and 23 are shown in FIG.
Sections at positions W and X are shown respectively.

【００２９】[0029]

【発明の効果】本発明は、以上のごとく、内軸の軸線方
向の複数の断面位置に給油孔を設けるに際し、給油孔は
各断面では一つの直径線上に対向する二箇所とし、各断
面にて該給油孔の位置を周方向にずらして設けることと
したので、内軸の強度低下を最小限に抑え、軸受内全体
に不必要に高いレベルの油膜圧力を生じることなく適正
な潤滑油流量を確保できる。As described above, according to the present invention, when the lubrication holes are provided at a plurality of cross-section positions in the axial direction of the inner shaft, the lubrication holes are provided at two locations facing each other on one diameter line in each cross-section. Since the positions of the oil supply holes are shifted in the circumferential direction, the decrease in strength of the inner shaft is minimized, and an appropriate lubricating oil flow rate is generated without generating an unnecessarily high level of oil film pressure in the entire bearing. Can be secured.

【００３０】また、給油孔から噴出する潤滑油が直接軸
受メタルに当たる頻度を低下させることで、エロージョ
ン発生の危険を低減できる。さらに、軸に開ける給油孔
の個数減少により軸製作時の加工工数の低減が可能とな
る。Further, by reducing the frequency with which the lubricating oil ejected from the oil supply hole directly contacts the bearing metal, the risk of erosion can be reduced. Furthermore, the number of processing holes when manufacturing the shaft can be reduced by reducing the number of oil supply holes formed in the shaft.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の一実施例装置の断面図である。FIG. 1 is a sectional view of an apparatus according to an embodiment of the present invention.

【図２】図１装置の内軸軸受部分の拡大断面図である。FIG. 2 is an enlarged cross-sectional view of an inner shaft bearing portion of the device shown in FIG.

【図３】図２の内軸のみを示すＡ−Ａ線及びＣ−Ｃ線で
の断面図である。3 is a cross-sectional view taken along line AA and line C-C showing only the inner axis of FIG.

【図４】図２の内軸のみを示すＢ−Ｂ線及びＤ−Ｄ線で
の断面図である。FIG. 4 is a cross-sectional view taken along line BB and line DD showing only the inner axis of FIG.

【図５】図１装置と従来装置の周方向での油膜圧力分布
を示す図である。FIG. 5 is a diagram showing an oil film pressure distribution in the circumferential direction between the device of FIG. 1 and a conventional device.

【図６】本発明の他の実施形態を示す内軸の正面図であ
る。FIG. 6 is a front view of an inner shaft showing another embodiment of the present invention.

【図７】図６のＥ−Ｅ線及びＨ−Ｈ線での断面図であ
る。7 is a cross-sectional view taken along line EE and line HH of FIG.

【図８】図６のＦ−Ｆ線及びＩ−Ｉ線での断面図であ
る。8 is a cross-sectional view taken along line FF and line I-I of FIG.

【図９】図６のＧ−Ｇ線及びＪ−Ｊ線での断面図であ
る。9 is a cross-sectional view taken along the line GG and the line JJ of FIG.

【図１０】本発明のさらに他の実施形態を示す内軸の正
面図である。FIG. 10 is a front view of an inner shaft showing still another embodiment of the present invention.

【図１１】図１０のＫ−Ｋ線及びＯ−Ｏ線での断面図で
ある。11 is a cross-sectional view taken along line KK and line OO of FIG.

【図１２】図１０のＬ−Ｌ線及びＰ−Ｐ線での断面図で
ある。12 is a cross-sectional view taken along line LL and line PP of FIG.

【図１３】図１０のＭ−Ｍ線及びＱ−Ｑ線での断面図で
ある。13 is a cross-sectional view taken along line MM and QQ of FIG.

【図１４】図１０のＮ−Ｎ線及びＲ−Ｒ線での断面図で
ある。14 is a cross-sectional view taken along line NN and line RR of FIG.

【図１５】本発明のさらに他の実施形態を示す内軸の一
部破断正面図である。FIG. 15 is a partially cutaway front view of an inner shaft showing still another embodiment of the present invention.

【図１６】図１５のＳ−Ｓ線での断面図である。16 is a cross-sectional view taken along the line SS of FIG.

【図１７】図１５のＴ−Ｔ線での断面図である。17 is a cross-sectional view taken along the line TT of FIG.

【図１８】本発明のさらに他の実施形態を示す内軸の正
面図である。FIG. 18 is a front view of an inner shaft showing still another embodiment of the present invention.

【図１９】図１８のＵ−Ｕ線での断面図である。19 is a cross-sectional view taken along the line U-U of FIG.

【図２０】図１８のＶ−Ｖ線での断面図である。20 is a cross-sectional view taken along the line VV of FIG.

【図２１】本発明のさらに他の実施形態を示す内軸の正
面図である。FIG. 21 is a front view of an inner shaft showing still another embodiment of the present invention.

【図２２】図２１のＷ−Ｗ線での断面図である。22 is a cross-sectional view taken along the line WW of FIG.

【図２３】図２１のＸ−Ｘ線での断面図である。23 is a cross-sectional view taken along line XX of FIG.

【符号の説明】[Explanation of symbols]

１ プロペラ ２ 内軸 ３ プロペラ ４ 外軸 ８，９ 軸受 １２ 給油路 １３ 給油孔 1 Propeller 2 Inner shaft 3 Propeller 4 Outer shaft 8,9 Bearing 12 Oil supply passage 13 Oil supply hole

───────────────────────────────────────────────────── フロントページの続き (72)発明者 慶林坊 智 東京都千代田区丸の内一丁目１番２号 日 本鋼管株式会社内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Satoshi Keirinbo, 1-2-1, Marunouchi, Chiyoda-ku, Tokyo Nihon Steel Pipe Co., Ltd.

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】 中空な外軸と該外軸の中空空間内に同心
に配された内軸とを有し、内軸が外軸より後方に突出し
た部分及び外軸の後端部分に互いに逆方向に回転するプ
ロペラがそれぞれに取りつけられ、外軸には内軸を摺動
回転自在に支持する軸受が設けられ、内軸に軸線方向に
延びて形成された給油路からの潤滑油を上記軸受の接面
せる該内軸の外周面に導く給油孔が該内軸に形成されて
いる二重反転プロペラ軸用軸受装置において、上記内軸
の軸線に直角な断面にて一つの直径線上で対向する二箇
所に設けられた給油孔を、上記軸線方向での複数の断面
位置に設け、各断面位置での給油孔の周方向位置が互い
に位相をずらして設定されていることとを特徴とする二
重反転プロペラ軸用軸受装置。1. A hollow outer shaft and an inner shaft concentrically arranged in a hollow space of the outer shaft, wherein the inner shaft is protruded rearward from the outer shaft and the rear end portion of the outer shaft is mutually opposed. Propellers rotating in opposite directions are attached to the respective shafts, bearings for slidably rotating the inner shaft are provided on the outer shaft, and lubricating oil from the oil supply passage formed in the inner shaft extending in the axial direction is used as the above. In a bearing device for a counter-rotating propeller shaft, in which an oil supply hole that leads to the outer peripheral surface of the inner shaft to be brought into contact with the bearing is formed in the inner shaft, in a cross section perpendicular to the axis of the inner shaft, on one diameter line The oil supply holes provided at two opposite locations are provided at a plurality of cross-section positions in the axial direction, and the circumferential positions of the oil supply holes at each cross-section position are set to be out of phase with each other. Bearing device for counter rotating propeller shaft.