JPH07208480A - Main bearing for engine - Google Patents
Main bearing for engineInfo
- Publication number
- JPH07208480A JPH07208480A JP2322494A JP2322494A JPH07208480A JP H07208480 A JPH07208480 A JP H07208480A JP 2322494 A JP2322494 A JP 2322494A JP 2322494 A JP2322494 A JP 2322494A JP H07208480 A JPH07208480 A JP H07208480A
- Authority
- JP
- Japan
- Prior art keywords
- main bearing
- metal
- lower metal
- lubricating oil
- load
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
- F16C9/02—Crankshaft bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はエンジンの主軸受に関す
る。FIELD OF THE INVENTION The present invention relates to an engine main bearing.
【０００２】[0002]
【従来の技術】図１に示すディーゼルエンジン１におい
ては、シリンダ爆発力に起因する力は、クランク軸３を
介して主軸受に伝えられる。主軸受は図２に示す如く、
台板サドル５上に下メタル８と上メタル７の２分割形状
で装着され、上メタル７の上部に取付けられた主軸受押
え４を主軸受取付ボルト６を介して台板サドル５に締付
けて固定している。該主軸受において、シリンダ爆発力
等の荷重を主として受ける主軸受下メタル８に対する潤
滑油は、給油口Ａから供給穴Ｂ、主軸受上メタル７の給
油みぞＣをへて、下メタル８の給油みぞＤα，Ｄβに供
給されるが、従来の主軸受の下メタル８の給油みぞ長さ
α，βは、図２に示す如くクランク軸回転中心をとおる
垂直軸Ｙ−Ｙに対し左右対称に設けられている。2. Description of the Related Art In a diesel engine 1 shown in FIG. 1, a force resulting from a cylinder explosive force is transmitted to a main bearing via a crankshaft 3. As shown in Fig. 2, the main bearing is
The main bearing retainer 4 mounted on the base plate saddle 5 in a two-part shape of the lower metal 8 and the upper metal 7 and attached to the upper part of the upper metal 7 is fastened to the base plate saddle 5 via the main bearing mounting bolts 6. It is fixed. In the main bearing, the lubricating oil for the lower metal 8 of the main bearing, which is mainly subjected to a load such as a cylinder explosive force, is fed to the lower metal 8 from the oil supply port A to the supply hole B and the oil supply groove C of the upper metal 7 of the main bearing. Although supplied to the grooves Dα and Dβ, the oil supply groove lengths α and β of the lower metal 8 of the conventional main bearing are provided symmetrically with respect to the vertical axis Y-Y passing through the crankshaft rotation center as shown in FIG. Has been.
【０００３】[0003]
【発明が解決しようとする課題】前記のとおり、従来の
主軸受の下メタルの給油みぞ長さは、図２においてα＝
βとなるように設計されている。ところがエンジン爆発
時主軸受下メタルにかかる荷重は最下部近傍の次に、前
記下メタル表面の潤滑油流れの上流側よりも下流側（図
２では左側）に強くかかる。従って従来構造では前記下
流側の面荷重の最大値は前記上流側のそれより大きくな
るが、荷重のかかる位置に給油みぞＤβが設けられてい
るため、図５でＰ1で示すようにその面荷重の最大値も
大きくなる欠点があった。As described above, the length of the lubrication groove of the lower metal of the conventional main bearing is α =
It is designed to be β. However, when the engine explodes, the load applied to the lower metal of the main bearing is next to the vicinity of the lowermost portion, and is stronger to the downstream side (left side in FIG. 2) than the upstream side of the lubricating oil flow on the surface of the lower metal. Therefore, in the conventional structure, the maximum value of the surface load on the downstream side is larger than that on the upstream side, but since the lubrication groove Dβ is provided at the position where the load is applied, as shown by P 1 in FIG. There was a drawback that the maximum value of the load was also large.
【０００４】本発明の目的は、主軸受下メタルの面荷重
の最大値が図６のように低下し主軸受メタルの耐久性を
延長させることのできるディーゼルエンジンの主軸受を
提供するにある。An object of the present invention is to provide a main bearing of a diesel engine in which the maximum value of the surface load of the metal under the main bearing is reduced as shown in FIG. 6 and the durability of the main bearing metal can be extended.
【０００５】[0005]
【課題を解決するための手段】本発明に係るディーゼル
エンジンの主軸受は、該主軸受下メタルに対し、軸の回
転方向に設けられる給油みぞの円周方向長さを、前記下
メタル表面の潤滑油流れの上流側を長くし、下流側を短
かくしたことを特徴としている。In the main bearing of a diesel engine according to the present invention, the circumferential length of the lubrication groove provided in the rotational direction of the shaft is set to the lower metal surface of the lower metal surface of the main bearing. The feature is that the upstream side of the lubricating oil flow is made longer and the downstream side is made shorter.
【０００６】[0006]
【作用】主軸受下メタルの設けられる回転方向の給油み
ぞの長さβは面荷重の大きい前記下メタル表面の潤滑油
流れの下流側を短かくしたので、面荷重の最大値も従来
例のＰ1 よりＰ2 と低くすることができ、主軸受メタル
の寿命を延長させることができる。The length β of the oil supply groove in the rotation direction in which the lower metal of the main bearing is provided is short on the downstream side of the lubricating oil flow on the surface of the lower metal having a large surface load. It can be made lower than P 1 by P 2, and the life of the main bearing metal can be extended.
【０００７】[0007]
【実施例】以下図１〜４を参照し、本発明の第１実施例
について説明する。図１に示すディーゼルエンジンでは
シリンダの爆発力がクランク機構を介してクランク軸３
から主軸受２に伝えられる。該第１実施例の主軸受２は
図２に示す従来例のように台板サドル５上に下メタル８
と上メタル７に２分割形状で装着され、上メタル７は上
部から主軸受押え４を主軸受取付ボルト６を介して台板
サドル５に締付けて固定されている。該主軸受におい
て、シリンダ爆発力等の荷重を主として受ける主軸受下
メタル８に対する潤滑油は給油口Ａから供給穴Ｂ、主軸
受上メタル７の給油みぞＣをへて、主軸受下メタル８の
給油みぞＤα，Ｄβに供給されるが、本発明の主軸受下
メタル８では給油みぞの円周方向の長さは、前記下メタ
ル表面の潤滑油流れの上流側をα、下流側をβとすると
α＞βとしている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described below with reference to FIGS. In the diesel engine shown in FIG. 1, the explosive force of the cylinder is transmitted through the crank mechanism to the crankshaft 3
Is transmitted to the main bearing 2. The main bearing 2 of the first embodiment has a lower metal 8 on a base plate saddle 5 as in the conventional example shown in FIG.
The upper metal 7 is fixed to the base plate saddle 5 from above by tightening the main bearing retainer 4 to the base plate saddle 5 via the main bearing mounting bolts 6. In the main bearing, the lubricating oil for the lower metal 8 of the main bearing, which is mainly subjected to a load such as a cylinder explosive force, flows from the oil supply port A to the supply hole B, the oil supply groove C of the upper metal 7 of the main bearing, and the lower metal 8 of the main bearing. It is supplied to the lubrication grooves Dα and Dβ, but in the main bearing lower metal 8 of the present invention, the circumferential length of the lubrication groove is α on the upstream side of the lubricating oil flow on the surface of the lower metal and β on the downstream side. Then, α> β.
【０００８】次に前記実施例の作用について説明する。
上記構成の結果、図３の第１実施例をＥ矢視した立体図
である図４において、Ｇとして示す領域の荷重分担面積
が本発明を採用すると増加するため、軸受としての面荷
重が軽減できる。図６は本発明に係る主軸受面荷重の分
布状況を表したものであるが、給油みぞＤβ2 を短かく
したので荷重のかかる領域から給油みぞＤβ2 がはずれ
ることになり、この部分の面荷重の最大値Ｐ2 は図５に
示す従来例の面荷重の最大値Ｐ1より低減させることが
できる。Next, the operation of the above embodiment will be described.
As a result of the above configuration, in FIG. 4 which is a three-dimensional view of the first embodiment of FIG. 3 as viewed in the direction of arrow E, the load sharing area of the region indicated by G increases when the present invention is adopted, so the surface load as a bearing is reduced it can. FIG. 6 shows the distribution of the main bearing surface load according to the present invention. Since the lubrication groove Dβ 2 is made short, the lubrication groove Dβ 2 is displaced from the area where the load is applied, and the surface of this portion The maximum value P 2 of the load can be made smaller than the maximum value P 1 of the surface load of the conventional example shown in FIG.
【０００９】なお本実施例では主軸受の下メタル８への
潤滑油が上メタル側から供給される場合について説明し
ているが、本発明の効果は台板サドル５側から直接下メ
タル８へ潤滑油が供給される場合のように、その供給通
路が変化した場合でも作用効果が変ることはない。In this embodiment, the case where the lubricating oil is supplied to the lower metal 8 of the main bearing from the upper metal side is explained. However, the effect of the present invention is from the base plate saddle 5 side directly to the lower metal 8. Even when the supply passage is changed as in the case where the lubricating oil is supplied, the action and effect are not changed.
【００１０】[0010]
【発明の効果】本発明に係るエンジンの主軸受は前記の
とおり構成したので、図６に示すように主軸受下メタル
の面荷重が等分布化し、その最大値Ｐ2 が減少するの
で、主軸受メタルの寿命を延長させることができる。Since the main bearing of the engine according to the present invention is constructed as described above, as shown in FIG. 6, the surface load of the metal under the main bearing is evenly distributed, and the maximum value P 2 thereof is reduced. The life of the bearing metal can be extended.
【図１】本発明に係る第１実施例のディーゼルエンジン
の一部断面図。FIG. 1 is a partial sectional view of a diesel engine of a first embodiment according to the present invention.
【図２】従来の主軸受メタルを示す構成図。FIG. 2 is a configuration diagram showing a conventional main bearing metal.
【図３】本発明の第１実施例に係る主軸受下メタルの断
面図。FIG. 3 is a sectional view of a main bearing lower metal according to the first embodiment of the present invention.
【図４】本発明の第１実施例に係る同主軸受下メタルの
立体図。FIG. 4 is a three-dimensional view of the main bearing lower metal according to the first embodiment of the present invention.
【図５】従来の主軸受下メタルの面荷重分布図。FIG. 5 is a surface load distribution diagram of a conventional metal under a main bearing.
【図６】本発明の第１実施例に係る主軸受下メタルの面
荷重分布図。FIG. 6 is a surface load distribution diagram of a metal under a main bearing according to the first embodiment of the present invention.
１…ディーゼルエンジン、２…主軸受、３…クランク
軸、４…主軸受押え、５…台板サドル、７…主軸受上メ
タル、８…主軸受下メタル、Ｃ…上メタル給油みぞ、Ｄ
α，Ｄβ…下メタル給油みぞ、α…下メタル表面の潤滑
油流れの上流側給油みぞ長さ、β…下メタル表面の潤滑
油流れの下流側給油みぞ長さ、Ｇ…下流側荷重分担部、
Ｐ1 …従来例の面荷重最大値、Ｐ2 …本実施例の面荷重
最大値。1 ... Diesel engine, 2 ... Main bearing, 3 ... Crank shaft, 4 ... Main bearing retainer, 5 ... Bed plate saddle, 7 ... Main bearing upper metal, 8 ... Main bearing lower metal, C ... Upper metal lubrication groove, D
α, Dβ ... Lower metal lubrication groove, α ... Length of upstream lubrication groove of lubricating oil flow on lower metal surface, β ... Length of downstream lubrication groove of lubricating oil flow on lower metal surface, G ... Downstream load sharing section ,
P 1 ... Maximum value of surface load of conventional example, P 2 ... Maximum value of surface load of this embodiment.
Claims (1)
回転方向に設けられる給油みぞの円周方向長さを、前記
下メタル表面の潤滑油流れの上流側を長くし、下流側を
短かくしたことを特徴とするエンジンの主軸受。1. A circumferential length of a lubrication groove provided in a rotation direction of a shaft with respect to a lower metal of a main bearing of an engine is longer on the upstream side of the lubricating oil flow on the lower metal surface and shorter on the downstream side. The main bearing of the engine characterized by this.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2322494A JPH07208480A (en) | 1994-01-25 | 1994-01-25 | Main bearing for engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2322494A JPH07208480A (en) | 1994-01-25 | 1994-01-25 | Main bearing for engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07208480A true JPH07208480A (en) | 1995-08-11 |
Family
ID=12104674
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2322494A Pending JPH07208480A (en) | 1994-01-25 | 1994-01-25 | Main bearing for engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07208480A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2416005A (en) * | 2004-05-14 | 2006-01-11 | Menard Competition Technologie | A bearing with means for increasing lubricant pressure |
| US7194995B2 (en) | 2004-05-14 | 2007-03-27 | Menard Competition Technologies, Ltd. | Bearing |
| WO2010130322A1 (en) * | 2009-05-13 | 2010-11-18 | Bayerische Motoren Werke Aktiengesellschaft | Internal combustion engine |
| US8317401B2 (en) | 2006-10-12 | 2012-11-27 | Toyota Jidosha Kabushiki Kaisha | Slide bearing |
| JP2017110764A (en) * | 2015-12-17 | 2017-06-22 | 大豊工業株式会社 | Slide bearing |
| JP2017110765A (en) * | 2015-12-17 | 2017-06-22 | 大豊工業株式会社 | Slide bearing |
-
1994
- 1994-01-25 JP JP2322494A patent/JPH07208480A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2416005A (en) * | 2004-05-14 | 2006-01-11 | Menard Competition Technologie | A bearing with means for increasing lubricant pressure |
| US7194995B2 (en) | 2004-05-14 | 2007-03-27 | Menard Competition Technologies, Ltd. | Bearing |
| GB2416005B (en) * | 2004-05-14 | 2008-03-05 | Menard Competition Technologie | Bearing |
| US8317401B2 (en) | 2006-10-12 | 2012-11-27 | Toyota Jidosha Kabushiki Kaisha | Slide bearing |
| WO2010130322A1 (en) * | 2009-05-13 | 2010-11-18 | Bayerische Motoren Werke Aktiengesellschaft | Internal combustion engine |
| US8479703B2 (en) | 2009-05-13 | 2013-07-09 | Bayerische Motoren Werke Aktiengesellschaft | Internal combustion engine |
| JP2017110764A (en) * | 2015-12-17 | 2017-06-22 | 大豊工業株式会社 | Slide bearing |
| JP2017110765A (en) * | 2015-12-17 | 2017-06-22 | 大豊工業株式会社 | Slide bearing |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 19990518 |