JP3402768B2 - Bearing device - Google Patents
Bearing deviceInfo
- Publication number
- JP3402768B2 JP3402768B2 JP18195894A JP18195894A JP3402768B2 JP 3402768 B2 JP3402768 B2 JP 3402768B2 JP 18195894 A JP18195894 A JP 18195894A JP 18195894 A JP18195894 A JP 18195894A JP 3402768 B2 JP3402768 B2 JP 3402768B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- metal
- saddle
- crown
- bearing metal
- 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
Landscapes
- Sliding-Contact Bearings (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
Description
【発明の詳細な説明】
【０００１】
【産業上の利用分野】本発明は舶用大型ディーゼル機関
のクランク軸を軸支するのに好適な軸受装置に関する。
【０００２】
【従来の技術】従来のこの種軸受装置の１例が図２に示
されている。図２において、100 はクランク軸１を軸支
する軸受装置で、下軸受メタル2a、上軸受メタル2b、軸
受サドル3b、軸受冠６等からなる。
【０００３】上記下軸受メタル2a及び上軸受メタル2bは
それぞれ半割り円筒状をなし、鉄系合金からなる裏金２
−１の内面にホワイトメタル等からなる軸受材２−２を
ライニングしてなる。
【０００４】下軸受メタル2aの外面を軸受サドル3bの取
付面に嵌合した後、クランク軸１を下軸受メタル2a上に
載置する。そして、下軸受メタル2aと上軸受メタル2bを
その両端で調整ライナ４を介して互いに突き合わせて位
置決めピン５により位置決めする。次いで上軸受メタル
2bの外面に軸受冠６の取付面を嵌合した後、軸受冠６と
軸受サドル3bをボルト７により締結する。
【０００５】軸受サドル3bの両側はタイボルト支柱3Cを
介して補強プレート3dに結合されている。また、上、下
軸受メタル2b、2aの軸受面、即ち、軸受材２−２の内面
には潤滑油ポンプから送られた潤滑油が供給されて油膜
を形成している。
【０００６】
【発明が解決しようとする課題】軸受装置１００に作用
する荷重はその大きさと作用方向がクランク軸１の回転
に伴って変化する変動荷重である。この変動荷重のうち
鉛直方向に作用する最も大きな荷重は下軸受メタル２ａ
によって支承される。また、上記鉛直方向荷重と同程度
の水平方向荷重が上、下軸メタル２ａ、２ｂの突き合わ
せ面２−３の近傍に伝達され、上、下軸受メタル２ａ、
２ｂによって支承される。更に、荷重が小さいが上記水
平方向荷重と方向が逆の水平方向荷重が他方の突き合わ
せ面２−３近傍の上軸受メタル２ｂに作用する。
【０００７】一方の突き合わせ面２−３の近傍に水平方
向荷重が作用すると、その背後に軸受サドル３ｂと軸受
冠６との合わせ面３−１が位置するため、剛性不連続に
伴う局部変形が生じ、下軸受メタル２ａの突き合わせ面
２−３近傍の軸受材２−２に引張り曲げ応力が作用す
る。
【０００８】また、他方の突き合わせ面２−３近傍の上
軸受メタル2bに作用する水平方向荷重により軸受冠６が
変形し、これが下軸受メタル2aの突き合わせ面２−３近
傍の軸受材２−２に圧縮曲げ応力を与える。即ち、下軸
受メタル2aの突き合わせ面２−３近傍の軸受材２−２に
はクランク軸１が１回転する間に両振りの応力変動が発
生する。
【０００９】これによって、下軸受メタル2aの軸受材２
−２に割れや剥離等が発生し、軸受装置100 の寿命が著
しく低下するという問題があった。
【００１０】
【課題を解決するための手段】本発明は上記課題を解決
するために発明されたものであって、その要旨とすると
ころは、裏金の内面にホワイトメタル等の軸受材をライ
ニングしてなる半割り円筒状の上軸受メタル及び下軸受
メタルを具え、上記下軸受メタルの外面を軸受サドルの
取付面に嵌合するとともに上記上軸受メタルの外面に軸
受冠の取付面を嵌合して上記上軸受メタルと下軸受メタ
ルの両端を互いに突き合わせた状態で上記軸受冠を上記
軸受サドルにボルトにより締結する軸受装置において、
上記軸受冠と軸受サドルとの合わせ面を上記上軸受メタ
ルと下軸受メタルとの突き合わせ面よりも上方に位置さ
せたことを特徴とする軸受装置にある。
【００１１】
【作用】本発明においては、上、下軸受メタルの突き合
わせ面近傍に作用する水平方向荷重はその背後に位置す
る軸受サドルの連続した剛性の高い支持面によって支承
される。
【００１２】
【実施例】本発明の１実施例が図１に示されている。図
１に示されるように、軸受サドル3bと軸受冠６との合わ
せ面３−１は上、下軸受メタル2a、2bの突き合わせ面２
−３よりも上方に距離Ｌだけ偏位せしめられている。偏
位量は水平方向荷重によって上軸受メタル2bの軸受材２
−２の内面に生じる油膜発生域以上が望ましく、水平面
から軸受メタル2a、2bの中心10廻りに角度θ＝10°程度
が好適である。
【００１３】軸受サドル3bの取付面３−３は下軸受メタ
ル2aの外面に沿う形状とされている。また、軸受冠６の
取付面６−１も上軸受メタル2bの外面に沿う形状とされ
ている。そして、軸受冠６はボルト７により軸受サドル
3bに締結されている。他の構成は図２に示す従来のもの
と同様であり、対応する部材には同じ符号が付されてい
る。
【００１４】しかして、ディーゼル機関の運転時におい
て、軸受装置100 に作用する変動荷重のうち大きな水平
方向荷重は上、下軸受メタル2b、2aの一方の突き合わせ
面２−３の近傍に作用する。この突き合わせ面２−３の
近傍の上、下軸受メタル2b、2aの背後には従来のものの
ような合わせ面３−１が無く、軸受サドル3bの連続した
剛性の高い取付面３−３が位置する。
【００１５】これにより水平方向荷重に対する上、下軸
受メタル２ａ、２ｂの変形が減少し、下軸受メタル２ａ
の突き合わせ面２−３近傍の軸受材２−２の剥離や、割
れ等の原因となる引っ張り曲げ応力が発生することはな
い。また、他方の突き合わせ面２−３側の上軸受メタル
２ｂに作用する小さい水平方向荷重も軸受サドル３ｂの
剛性の高い取付け面３−３で支承することとなるため、
上軸受メタル２ｂの軸受材２−２の圧縮曲げ応力の発生
が阻止される。従って、従来の軸受材２−２に作用して
いた両振りの応力変動の発生が阻止されることとなる。
【００１６】
【発明の効果】本発明においては、軸受冠と軸受サドル
との合わせ面を上軸受メタルと下軸受メタルとの突き合
わせ面よりも上方に位置させたので、水平方向荷重の作
用点である上、下軸受メタルの突き合わせ面の外側は軸
受サドルの連続した剛性の高い支持面によって支承され
るため、従来のもののような上、下軸受メタル突き合わ
せ面近傍における軸受メタルの曲げ応力の発生を阻止し
うる。
【００１７】従って、ホワイトメタル等の軸受材の割れ
や裏金からの剥離の発生が防止され、軸受装置の寿命の
延長を実現することができる。これにより軸受装置の信
頼性が向上するとともに軸受装置を小型化できるので機
関全体の軽量コンパクト化に資することが可能となる。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device suitable for supporting a crankshaft of a large marine diesel engine. 2. Description of the Related Art FIG. 2 shows an example of a conventional bearing device of this kind. In FIG. 2, reference numeral 100 denotes a bearing device that supports the crankshaft 1, and includes a lower bearing metal 2a, an upper bearing metal 2b, a bearing saddle 3b, a bearing crown 6, and the like. Each of the lower bearing metal 2a and the upper bearing metal 2b has a half-cylindrical cylindrical shape,
-1, a bearing material 2-2 made of white metal or the like is lined. After fitting the outer surface of the lower bearing metal 2a to the mounting surface of the bearing saddle 3b, the crankshaft 1 is placed on the lower bearing metal 2a. Then, the lower bearing metal 2a and the upper bearing metal 2b are abutted to each other via the adjustment liner 4 at both ends thereof, and are positioned by the positioning pins 5. Then upper bearing metal
After fitting the mounting surface of the bearing crown 6 to the outer surface of 2b, the bearing crown 6 and the bearing saddle 3b are fastened by bolts 7. [0005] Both sides of the bearing saddle 3b are connected to a reinforcing plate 3d through tie bolt posts 3C. Further, the lubricating oil sent from the lubricating oil pump is supplied to the bearing surfaces of the upper and lower bearing metals 2b and 2a, that is, the inner surface of the bearing material 2-2 to form an oil film. [0006] The load acting on the bearing device 100 is a fluctuating load whose magnitude and direction of operation change with the rotation of the crankshaft 1. Among these fluctuating loads, the largest load acting in the vertical direction is the lower bearing metal 2a.
Supported by Also, a horizontal load substantially equal to the vertical load is transmitted to the vicinity of the butting surface 2-3 of the upper and lower shaft metals 2a and 2b, and the upper and lower bearing metals 2a,
2b. Further, a horizontal load having a small load but opposite in direction to the horizontal load acts on the upper bearing metal 2b near the other butting surface 2-3. When a horizontal load is applied in the vicinity of one of the abutting surfaces 2-3, the mating surface 3-1 of the bearing saddle 3b and the bearing crown 6 is located behind the horizontal load, so that local deformation accompanying rigidity discontinuity occurs. Then, a tensile bending stress acts on the bearing material 2-2 near the butting surface 2-3 of the lower bearing metal 2a .
You . Further, the bearing crown 6 is deformed by a horizontal load acting on the upper bearing metal 2b in the vicinity of the other butting surface 2-3, and this causes the bearing material 2-2 in the vicinity of the butting surface 2-3 of the lower bearing metal 2a. To compressive bending stress. That is, during the rotation of the crankshaft 1 in the bearing member 2-2 in the vicinity of the butting surface 2-3 of the lower bearing metal 2a, a two-way swing stress variation occurs. Thus, the bearing material 2 of the lower bearing metal 2a is formed.
-2, there was a problem that cracks and peeling occurred, and the life of the bearing device 100 was significantly reduced. SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and the gist of the present invention is that a bearing material such as white metal is lined on the inner surface of a back metal. The upper bearing metal and the lower bearing metal having a half-cylindrical shape, the outer surface of the lower bearing metal is fitted to the mounting surface of the bearing saddle, and the mounting surface of the bearing crown is fitted to the outer surface of the upper bearing metal. In a bearing device for fastening the bearing crown to the bearing saddle with bolts with both ends of the upper bearing metal and the lower bearing metal abutting each other,
A bearing device is characterized in that the mating surface of the bearing crown and the bearing saddle is located above the butting surface of the upper bearing metal and the lower bearing metal. In the present invention, the horizontal load acting near the butting surfaces of the upper and lower bearing metals is supported by the continuous and highly rigid supporting surface of the bearing saddle located behind the horizontal load. FIG. 1 shows one embodiment of the present invention. As shown in FIG. 1, the mating surface 3-1 of the bearing saddle 3b and the bearing crown 6 is the mating surface 2 of the upper and lower bearing metals 2a, 2b.
It is displaced by a distance L above -3. The amount of deviation depends on the horizontal load and the bearing material 2 of the upper bearing metal 2b.
Oil film generation area than is desirable arising on the inner surface of -2 bearing from the horizontal metal 2a, about the angle theta = 10 ° to the center 10 around 2b is preferred. The mounting surface 3-3 of the bearing saddle 3b is formed along the outer surface of the lower bearing metal 2a. In addition, the mounting surface 6-1 of the bearing crown 6 is also formed along the outer surface of the upper bearing metal 2b. The bearing crown 6 is bolted to the bearing saddle.
3b has been signed. Other configurations are the same as those of the conventional one shown in FIG. 2, and corresponding members are denoted by the same reference numerals. Thus, during the operation of the diesel engine, a large horizontal load among the fluctuating loads acting on the bearing device 100 acts on the vicinity of one of the butting surfaces 2-3 of the upper and lower bearing metals 2b and 2a. Above this butting surface 2-3, behind the lower bearing metals 2b and 2a, there is no mating surface 3-1 unlike the conventional one, and the continuous and rigid mounting surface 3-3 of the bearing saddle 3b is located. I do. [0015] Thus on against horizontal load heavy, lower bearing metal 2a, the deformation of the 2b is reduced, the lower bearing metal 2a
Of the bearing member 2-2 in the vicinity of the butting surface 2-3 does not generate a tensile bending stress which causes cracking or the like. Also, a small horizontal load acting on the upper bearing metal 2b on the other butted surface 2-3 side is supported by the highly rigid mounting surface 3-3 of the bearing saddle 3b.
The generation of compressive bending stress of the bearing material 2-2 of the upper bearing metal 2b is prevented. Therefore, the occurrence of the swinging fluctuation of the stress acting on the conventional bearing member 2-2 is prevented. According to the present invention, since the mating surface of the bearing crown and the bearing saddle is located above the butting surface of the upper bearing metal and the lower bearing metal, the point of application of the horizontal load is reduced. Since the outside of the butting surface of the upper and lower bearing metals is supported by the continuous and highly rigid support surface of the bearing saddle, the bending stress of the bearing metal near the butting surface of the upper and lower bearing metals as in the conventional case is reduced. Can be blocked. Accordingly, the occurrence of cracking of the bearing material such as white metal and peeling from the back metal can be prevented, and the life of the bearing device can be extended. As a result, the reliability of the bearing device is improved and the size of the bearing device can be reduced, thereby contributing to a reduction in the weight and size of the entire engine.
【図面の簡単な説明】
【図１】本発明の実施例に係わる大型ディーゼル機関用
軸受装置の部分的縦断面図である。
【図２】従来の軸受装置の部分的縦断面図である。
【符号の説明】
100 軸受装置
１ クランク軸
2a 下軸受メタル
2b 上軸受メタル
２−１ 裏金
２−２ 軸受材
２−３ 突き合わせ面
3b 軸受サドル
３−１ 合わせ面
３−３ 取付面
６ 軸受冠
６−１ 取付面BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial longitudinal sectional view of a bearing device for a large diesel engine according to an embodiment of the present invention. FIG. 2 is a partial longitudinal sectional view of a conventional bearing device. [Description of Signs] 100 Bearing device 1 Crankshaft 2a Lower bearing metal 2b Upper bearing metal 2-1 Back metal 2-2 Bearing material 2-3 Butt surface 3b Bearing saddle 3-1 Fitting surface 3-3 Mounting surface 6 Bearing crown 6 -1 Mounting surface
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F16C 3/00 - 9/06 F16C 17/00 - 17/26 F16C 33/00 - 33/28 F16C 35/00 - 43/08 ──────────────────────────────────────────────────の Continued on the front page (58) Field surveyed (Int. Cl. 7 , DB name) F16C 3/00-9/06 F16C 17/00-17/26 F16C 33/00-33/28 F16C 35 / 00-43/08
Claims (1)
をライニングしてなる半割り円筒状の上軸受メタル及び
下軸受メタルを具え、上記下軸受メタルの外面を軸受サ
ドルの取付面に嵌合するとともに上記上軸受メタルの外
面に軸受冠の取付面を嵌合して上記上軸受メタルと下軸
受メタルの両端を互いに突き合わせた状態で上記軸受冠
を上記軸受サドルにボルトにより締結する軸受装置にお
いて、 上記軸受冠と軸受サドルとの合わせ面を上記上軸受メタ
ルと下軸受メタルとの突き合わせ面よりも上方に位置さ
せたことを特徴とする軸受装置。(57) [Claims] [Claim 1] A half-split cylindrical upper bearing metal and a lower bearing metal obtained by lining a bearing material such as white metal on an inner surface of a back metal, and an outer surface of the lower bearing metal. The bearing crown is fitted to the mounting surface of the bearing saddle and the mounting surface of the bearing crown is fitted to the outer surface of the upper bearing metal so that both ends of the upper bearing metal and the lower bearing metal abut against each other. A bearing device to be fastened to a saddle by bolts, wherein a mating surface between the bearing crown and the bearing saddle is positioned higher than an abutting surface between the upper bearing metal and the lower bearing metal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18195894A JP3402768B2 (en) | 1994-07-12 | 1994-07-12 | Bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18195894A JP3402768B2 (en) | 1994-07-12 | 1994-07-12 | Bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0828581A JPH0828581A (en) | 1996-02-02 |
| JP3402768B2 true JP3402768B2 (en) | 2003-05-06 |
Family
ID=16109850
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18195894A Expired - Fee Related JP3402768B2 (en) | 1994-07-12 | 1994-07-12 | Bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3402768B2 (en) |
-
1994
- 1994-07-12 JP JP18195894A patent/JP3402768B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0828581A (en) | 1996-02-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPS6320847Y2 (en) | ||
| JP2977901B2 (en) | Crosshead type two-stroke internal combustion engine | |
| JP3939788B2 (en) | Crankshaft bearing device for internal combustion engine | |
| JP3402768B2 (en) | Bearing device | |
| JP3455644B2 (en) | Pile foundation structure | |
| CN113825904A (en) | Structural joint for an offshore structure, method for assembling such an offshore frame structure and use of such a structural joint | |
| JP3416367B2 (en) | Slide bearing device | |
| AU775271B2 (en) | Racing engine having trimetal bearings with a thick overlay for high speed and/or high load applications | |
| JPH0446087Y2 (en) | ||
| CN1692064A (en) | Belt conveyor frame and method for manufacturing the same | |
| JP3071547B2 (en) | Engine structure | |
| JP3495479B2 (en) | Plain bearings for internal combustion engines | |
| JPH0561232U (en) | Steel column base structure | |
| JPS61291298A (en) | Supporter for reciprocating internal combustion engine | |
| JP3460296B2 (en) | Connecting rod | |
| JP2002098132A (en) | Link | |
| JP3021293B2 (en) | Plain bearing mounting structure | |
| JPS63111266A (en) | Cylinder block structure of engine | |
| JP3506247B2 (en) | Internal combustion engine | |
| JPH0650166A (en) | Mounting structure of exhaust gas turbine supercharger hunting plate | |
| US20100024679A1 (en) | Locomotive car body flexible joint | |
| JPH0219565Y2 (en) | ||
| JP3696251B2 (en) | Device for transmitting thrust | |
| JPH11166395A (en) | Shield tunnel lining body | |
| JPH0131600Y2 (en) |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20030121 |
|
| LAPS | Cancellation because of no payment of annual fees |