JPH0663445B2 - Cylinder lubricator - Google Patents
Cylinder lubricatorInfo
- Publication number
- JPH0663445B2 JPH0663445B2 JP20772886A JP20772886A JPH0663445B2 JP H0663445 B2 JPH0663445 B2 JP H0663445B2 JP 20772886 A JP20772886 A JP 20772886A JP 20772886 A JP20772886 A JP 20772886A JP H0663445 B2 JPH0663445 B2 JP H0663445B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- cylinder liner
- lubrication
- cylinder
- engine
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
- F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
Landscapes
- Lubrication Of Internal Combustion Engines (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は内燃機関のシリンダライナとピストンリングの
潤滑に適用されるシリンダ注油装置に関する。TECHNICAL FIELD The present invention relates to a cylinder oiling device applied to lubrication of a cylinder liner and a piston ring of an internal combustion engine.
第５図は従来から用いられている大型低速ディーゼルエ
ンジンのシリンダ注油系を示したもので、01はシリンダ
ライナ、02は冷却水通路孔、03は注油孔、04はピスト
ン、05はピストンリング、06は連接棒、07はクランク
軸、08は軸受、09はクランク歯車、010は注油器、011は
注油導管、012は注油棒をそれぞれ示す。第６図は第５
図に示すライナ注油孔03中心を通るＶ−Ｖ断面を示す。
第６図でa,b,c,d,e,f,gはライナ内周の位置を示したも
ので、a,c,e,gは注油孔03の位置、b,d,f,hは注油孔03の
中間を示し、前者はライナ01の冷却水通路孔02よりライ
ナ01の内面までの距離が最も遠い位置で、後者はその
距離が最も近い位置を示す。FIG. 5 shows a cylinder lubrication system of a large-sized low-speed diesel engine that has been conventionally used. 01 is a cylinder liner, 02 is a cooling water passage hole, 03 is an oil injection hole, 04 is a piston, 05 is a piston ring, 06 is a connecting rod, 07 is a crank shaft, 08 is a bearing, 09 is a crank gear, 010 is an oiling device, 011 is an oiling conduit, and 012 is an oiling rod. FIG. 6 is the fifth
The VV cross section which passes along the center of the liner oiling hole 03 shown in the figure is shown.
In Fig. 6, a, b, c, d, e, f, g show the position of the inner circumference of the liner, a, c, e, g are the positions of the lubrication hole 03, b, d, f, h. Indicates the middle of the oil supply hole 03, the former is the position where the distance from the cooling water passage hole 02 of the liner 01 to the inner surface of the liner 01 is the farthest, and the latter is the position where the distance is the shortest.
注油器010は、エンジンのクランク軸07に取り付けられ
たクランク歯車09により回転され、注油器010内にある
シリンダ油は図示しないプランジャの作動により注油導
管011と注油棒012を介して、シリンダライナ01に設けら
れた注油孔03から吐出される。吐出された油は、シリン
ダライナ01とリング05との潤滑に使用される。The lubricator 010 is rotated by the crank gear 09 attached to the crankshaft 07 of the engine, and the cylinder oil in the lubricator 010 is operated by the plunger (not shown) to operate the cylinder liner 01 and the cylinder liner 012. It is discharged from the oil supply hole 03 provided in the. The discharged oil is used to lubricate the cylinder liner 01 and the ring 05.
なお第５〜６図に示すシリンダライナ01の冷却水用の通
路孔02は、きりで加工されたものでシリンダライナの高
温時の強度が問題とならないように設けられている。The cooling water passage hole 02 of the cylinder liner 01 shown in FIGS. 5 and 6 is machined by cutting and is provided so that the strength of the cylinder liner at high temperature does not matter.
ところが第５〜６図に示すような従来形のシリンダライ
ナ01を使用したときには、シリンダライナ円周方向a,b,
c,d,e,f,gの位置のシリンダライナ内面近傍の温度は第
７図に示す傾向を示している。即ちシリンダライナ内面
温度Ｔ及びシリンダライナ内面の最大温度差ΔＴはエン
ジンの運転条件によって異なるが、シリンダライナ冷却
水通路孔02とシリンダライナ01の内面が最も遠い位置
は最も近い位置に比べ温度が通常30〜40℃高い、この
ようなシリンダライナ01の温度が高い円周部から注油さ
れる場合が多い。However, when the conventional cylinder liner 01 as shown in FIGS. 5 and 6 is used, the cylinder liner circumferential direction a, b,
The temperatures in the vicinity of the inner surface of the cylinder liner at the positions of c, d, e, f and g show the tendency shown in FIG. That is, the temperature T of the inner surface of the cylinder liner and the maximum temperature difference ΔT of the inner surface of the cylinder liner differ depending on the operating conditions of the engine. It is often the case that the temperature of the cylinder liner 01 is higher by 30 to 40 ° C.
しかしエンジンが低負荷運転の条件下でシリンダライナ
01の内面で冷却水通路に近い位置即ちb,d,f,h部で
は、温度がかなり低くなり硫酸の凝縮が生じ、この酸を
中和するシリンダ油の供給が不足し、第８図に示すよう
に腐食によるシリンダライナ内面b,d,f,g部の偏摩耗19
が大きくなる。However, when the engine is operating under low load, the cylinder liner
At the positions on the inner surface of 01 near the cooling water passages, that is, at b, d, f, and h, the temperature becomes considerably low and condensation of sulfuric acid occurs, and the supply of cylinder oil that neutralizes this acid is insufficient, causing As shown, uneven wear of cylinder liner inner surfaces b, d, f, g due to corrosion 19
Grows larger.
一方エンジンの高負荷運転の条件下では、シリンダライ
ナの温度が高くなるが、シリンダライナ01の内面で冷却
水通路に遠い位置即ちa,c,e,g部では吐出された高ア
ルカリ成分が折出してアグレシィブ摩耗が著しく増大
し、第９図のようにa,c,e,g部のシリンダライナの偏摩
耗20を生ずる。On the other hand, under the condition of high load operation of the engine, the temperature of the cylinder liner rises, but the discharged high alkaline component is broken at the position distant from the cooling water passage on the inner surface of the cylinder liner 01, that is, at parts a, c, e and g. As a result, the aggressive wear increases remarkably, and as shown in FIG. 9, uneven wear 20 of the cylinder liner at the parts a, c, e, g occurs.
以上のように従来形の注油システムでは運転条件の如何
に拘らず偏摩耗を生じ、かつその値が大きいのでシリン
ダライナの交換寿命が短かくなるという欠点があった。As described above, the conventional lubrication system has a drawback that uneven wear occurs regardless of operating conditions and the value thereof is large, so that the replacement life of the cylinder liner becomes short.
本発明の目的は前記従来装置の問題点を解消し、運転条
件の如何に拘らず著しい偏摩耗と摩耗量の絶対値の増大
を防ぎ、シリンダライナの寿命を大幅に延長することの
できるシリンダ注油装置を提供するにある。It is an object of the present invention to solve the problems of the conventional device, prevent significant uneven wear and increase in absolute value of wear amount regardless of operating conditions, and significantly extend the life of the cylinder liner. To provide the equipment.
本発明は前記問題点を解決するためのもので、次の各項
目を満足するように構成されている。The present invention is intended to solve the above problems and is configured to satisfy the following items.
（１） シリンダライナの上方の横断面内において、シ
リンダライナのきり穴状の冷却水通路とシリンダライナ
内面との距離が最も近い各点と、最も遠い各点にそ
れぞれ複数個の注油孔が設けられていること。(1) In the horizontal cross section above the cylinder liner, multiple points are provided at each point where the distance between the hole-shaped cooling water passage of the cylinder liner and the inner surface of the cylinder liner is closest, and at each point farthest away. Being done.
（２） 上記（１）項の各及び点には相対応する注
油器が設けられ、両者又はどちらか一方がエンジンより
駆動できるようにクラッチを介して注油器の駆動を自由
に選択できること。(2) Corresponding lubricators are provided at the points and points in (1) above, and the driving of the lubricators can be freely selected via a clutch so that both or one of them can be driven by the engine.
（３） 上記（２）項の及び点にはそれぞれ同一油
種又は異った油種が貯えられており、運転条件に応じて
選定された油がライナの注油孔より吐出されること。(3) The same oil type or different oil types are stored in the and points in (2) above, and the oil selected according to the operating conditions is discharged from the oiling hole of the liner.
エンジン負荷に応じた使用注油器と使用シリンダ油種が
第４図の図表に示すように適宜せんたくされ、運転条件
の如何に拘らず著しい偏摩耗と摩耗量の絶対値の増大を
防ぎ、シリンダライナの寿命を大幅に延長させることが
できる。The lubricator used and the cylinder oil type used according to the engine load are appropriately meshed as shown in the chart in Fig. 4 to prevent significant uneven wear and increase in absolute value of wear amount regardless of operating conditions. The life of the liner can be greatly extended.
以下第１〜４図を参照し本発明の一実施例について説明
する。第１図は本発明に係る注油システムの系統図、第
２図は第１図のII−II断面図、第３図は本実施例の注油
法を適用したシリンダライナの摩耗状況図、第４図は本
発明におけるエンジン負荷に対する使用注油器、注油
孔、油種などを示した図表である。An embodiment of the present invention will be described below with reference to FIGS. FIG. 1 is a system diagram of an oiling system according to the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 3 is a wear status diagram of a cylinder liner to which the oiling method of this embodiment is applied. The drawing is a table showing the lubricator used, the lubrication hole, the oil type, etc. for the engine load in the present invention.
第１図において１はシリンダライナ、２は冷却水通路
孔、３はシリンダ注油孔、４はピストン、５はピストン
リング、６は連接棒、７はクランク軸、８は軸受、９は
クランク歯車、10は注油器、11は注油導管、12は注油
棒、13はギヤ軸、14は油圧シリンダ、15はクラッチ、16
は注油器駆動軸、17は注油器駆動ギヤでＡ、B2系列用の
ものが設けられている。In FIG. 1, 1 is a cylinder liner, 2 is a cooling water passage hole, 3 is a cylinder oiling hole, 4 is a piston, 5 is a piston ring, 6 is a connecting rod, 7 is a crankshaft, 8 is a bearing, 9 is a crank gear, 10 is an oiling device, 11 is an oiling conduit, 12 is an oiling rod, 13 is a gear shaft, 14 is a hydraulic cylinder, 15 is a clutch, 16
Is a lubricator drive shaft, and 17 is an lubricator drive gear for A and B2 series.
第２図は第１図のシリンダライナ１の注油孔３の中心線
をとおるII−II断面図を示したもので、a,b,c,d…は注
油孔3Aのグループ、b,d,f,hは注油孔3Bのグループを示
す。前者3Aグループはライナ１内の冷却水通路孔２より
最も遠い位置に配置された注油孔、後車3Bグループは
同じく最も近い位置に配置された注油孔である。FIG. 2 is a sectional view taken along the line II-II of the cylinder liner 1 shown in FIG. 1 taken along the center line of the lubrication hole 3, where a, b, c, d ... Are groups of lubrication holes 3A, b, d, f and h indicate the groups of the lubrication holes 3B. The former 3A group is an oil filling hole located farthest from the cooling water passage hole 2 in the liner 1, and the rear vehicle 3B group is an oil filling hole similarly located at the closest position.
注油孔3Aから出る油は注油器10Aに入れられた油を注油
導管11Aと注油棒12Aとを介してシリンダライナ１の内面
に吐出される。注油器10Aはエンジンのクランク軸７と
注油器駆動用ギヤ17A、ギヤ軸13A、クラッチ15Aを用い
て駆動される。このクラッチ15Aには図示しない油圧回
路と油圧シリンダ14Aとがあり、ギヤ軸13Aと油圧器駆動
軸16Aとが互いに着脱できるようになっている。The oil discharged from the oil-filling hole 3A is discharged to the inner surface of the cylinder liner 1 through the oil-filling conduit 11A and the oil-filling rod 12A. The lubricator 10A is driven by using the crankshaft 7 of the engine, the lubricator drive gear 17A, the gear shaft 13A, and the clutch 15A. The clutch 15A has a hydraulic circuit (not shown) and a hydraulic cylinder 14A, and the gear shaft 13A and the hydraulic device drive shaft 16A can be attached to and detached from each other.
以上と同様に注油孔3Bグループからの油の吐出は注油器
10B内に入れられた油が注油導管11Bと注油棒12Bと介し
て行われる。注油器10Bは注油器駆動用ギヤ17B、ギヤ軸
13B、クラッチ15Bを用いて駆動される。又クラッチ15B
には図示しない油圧回路と、油圧シリンダ14Bとがあ
り、ギヤ軸13Bと注油器駆動軸16Bとが互いに着脱できる
ようになっている。注油器10A,10B内には第４図に示す
ようにエンジンの負荷条件によって、アルカリ価の異な
る油種を供給できるように予め注油器10A,10B内に貯え
られている。なおここで高負荷とはエンジン船用特性で
80％以上、中負荷とは同じく60〜80％、低負荷とは同じ
く60％以下を意味している。Similar to the above, the oil is discharged from the lubrication hole 3B group using the lubricator.
The oil contained in 10B is supplied through the oil supply conduit 11B and the oil supply rod 12B. Lubricator 10B is lubricator drive gear 17B, gear shaft
It is driven using 13B and clutch 15B. Clutch 15B
Has a hydraulic circuit (not shown) and a hydraulic cylinder 14B, and the gear shaft 13B and the lubricator drive shaft 16B can be attached to and detached from each other. As shown in FIG. 4, the oil injectors 10A and 10B are stored in advance in the oil injectors 10A and 10B so that oil species having different alkali numbers can be supplied depending on engine load conditions. It should be noted that high load here is a characteristic for engine ships
80% or more, medium load means 60 to 80%, and low load means 60% or less.
第４図に示すようにエンジンが低負荷運転のときには、
注油器10Bを使用し注油孔3Bのグループからアルカリ価
の高い油（TBN40以上）が注油され、高負荷運転のとき
には注油器10Aを使用し注油孔3Aのグループからアルカ
リ価の低い油（TBN40以下）が注油され、又中負荷運転
のときには、中油器10A,10Bを使用し注油孔3A及び3Bの
グループから任意のアルカリ価の油が注油される。これ
らのエンジンの負荷運転に応じた油種即ち注油器10A,10
Bの選定は油圧回路とクラッチ15A,15Bの着脱操作により
任意にコントロールされる。As shown in FIG. 4, when the engine is operating at low load,
Oil with a high alkali value (TBN40 or more) is lubricated from the group with lubrication hole 3B using lubricator 10B, and oil with a low alkali value (TBN40 or less from lubrication hole 3A group is used with lubricator 10A during high load operation. ) Is lubricated, and in the case of medium load operation, the medium oil units 10A and 10B are used to lubricate the oil having an arbitrary alkali value from the group of the lubrication holes 3A and 3B. Oil type depending on the load operation of these engines, i.e., lubricators 10A, 10
The selection of B is arbitrarily controlled by the operation of attaching / detaching the hydraulic circuit and the clutches 15A, 15B.
本発明は前記のとおり構成したので、エンジンの低負荷
運転時にはシリンダライナの円周で温度が低く硫酸を凝
縮し易い位置に注油孔を設け、しかも高TBNの油を注
油するので硫酸による腐食摩耗を大幅に低減できる。又
エンジンの高負荷運転時には、シリンダライナの円周で
温度が高い位置からTBNの低い油を吐出させるので、
高温での添加剤の折出によるアグレシィブ摩耗を防止で
きる。中負荷時には腐食とアグレシィブ摩耗はあまり問
題とならないが、シリンダライナ内周で温度の高いとこ
ろと、低いところから微量に注油するので油を有効に利
用でき偏摩耗を減少させることができる。Since the present invention is configured as described above, when the engine is operated under a low load, an oiling hole is provided at a position where the temperature of the cylinder liner is low and the sulfuric acid is easily condensed on the circumference of the cylinder liner. Can be significantly reduced. Also, when the engine is operating under high load, the oil with a low TBN is discharged from the high temperature position on the circumference of the cylinder liner.
It is possible to prevent aggressive wear due to protrusion of the additive at high temperature. Corrosion and aggressive wear do not become a problem at medium load, but a small amount of oil is injected from the high temperature area and low temperature area on the inner circumference of the cylinder liner, so that oil can be effectively used and uneven wear can be reduced.
以上のようにして本発明では従来例にくらべ第３図に示
すように著しい偏摩耗と摩耗量の絶対値の増大を抑制で
き、シリンダライナの寿命を大幅に増大させることがで
きる。As described above, in the present invention, as compared with the conventional example, remarkable uneven wear and increase in absolute value of wear amount can be suppressed as shown in FIG. 3, and the life of the cylinder liner can be greatly extended.
第１〜４図は本発明に係るもので、第１図は注油システ
ムの系統図、第２図は第１図のII−II断面図、第３図は
本実施例の注油法を適用したシリンダライナの摩耗状況
図、第４図は使用注油器、注油孔、使用シリンダ油種を
示した図表、第５〜９図は従来例で、第５図は第１図応
当図、第６図は第２図応当図、第７図はシリンダライナ
の内面各位置の温度変化線図、第８図は低負荷運転時の
腐食による偏摩耗状況図、第９図は高負荷運転時のアグ
レシィブによる偏摩耗状況図である。 １……シリンダライナ、２……冷却水通路孔、3A,3B…
…注油孔、７……クランク軸、10A,10B……注油器、15
A,15B……クラッチ。1 to 4 relate to the present invention. FIG. 1 is a system diagram of an oiling system, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 3 is an oiling method of this embodiment. Cylinder liner wear status diagram, Fig. 4 is a chart showing lubricator used, lubrication hole, cylinder oil type used, Fig. 5-9 are conventional examples, Fig. 5 is Fig. 1 Corresponding diagram, Fig. 6 Fig. 2 is an ablation diagram, Fig. 7 is a temperature change diagram of each position on the inner surface of the cylinder liner, Fig. 8 is a partial wear state diagram due to corrosion during low load operation, and Fig. 9 is an aggressive state during high load operation. It is a partial wear situation figure. 1 ... Cylinder liner, 2 ... Cooling water passage hole, 3A, 3B ...
… Lubrication hole, 7 …… Crankshaft, 10A, 10B …… Lubricator, 15
A, 15B …… Clutch.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 恒屋 礼二郎 東京都千代田区丸の内２丁目５番１号 三 菱重工業株式会社内 (56)参考文献 特開 昭60−45710（ＪＰ，Ａ) 特開 昭59−128909（ＪＰ，Ａ) 特開 昭58−165515（ＪＰ，Ａ) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Reijiro Tsuneya 2-5-1, Marunouchi, Chiyoda-ku, Tokyo Sanryo Heavy Industries Co., Ltd. (56) References JP-A-60-45710 (JP, A) Kai 59-128909 (JP, A) JP 58-165515 (JP, A)
Claims (1)
路を有する水冷エンジンにおいて、該冷却水通路とシリ
ンダライナ内面との距離が最も近い複数の位置と最も
遠い複数の位置にそれぞれ設けられた注油孔と、これ
らの注油孔にそれぞれ対応し独立して設けられた注油器
と、これらの注油器をエンジンのクランク軸又はカム軸
からクラッチを介して駆動する駆動装置と、前記注油器
内に貯えられた異った油種又は同一油種の潤滑油とを有
してなり、エンジンの負荷条件に応じて選定された該当
潤滑油を該当注油孔より吐出することを特徴とするシリ
ンダ注油装置。1. A water-cooled engine having a cooling water passage in a liner above a cylinder liner, wherein oil is provided at a plurality of positions where the distance between the cooling water passage and the inner surface of the cylinder liner is closest and a plurality of positions where the distance is farthest. Holes, lubricators independently provided corresponding to these lubrication holes, a drive device for driving these lubricators from the crankshaft or camshaft of the engine through a clutch, and a storage device in the lubricator. Cylinder lubrication device, characterized in that different lubrication oils of the same or different oil types are discharged, and the lubrication oil selected according to the load condition of the engine is discharged from the lubrication hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20772886A JPH0663445B2 (en) | 1986-09-05 | 1986-09-05 | Cylinder lubricator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20772886A JPH0663445B2 (en) | 1986-09-05 | 1986-09-05 | Cylinder lubricator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6365109A JPS6365109A (en) | 1988-03-23 |
| JPH0663445B2 true JPH0663445B2 (en) | 1994-08-22 |
Family
ID=16544557
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20772886A Expired - Fee Related JPH0663445B2 (en) | 1986-09-05 | 1986-09-05 | Cylinder lubricator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0663445B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1350929B2 (en) * | 2002-04-04 | 2012-04-11 | Wärtsilä Schweiz AG | Lubrication system for the cylinder of an internal combustion engine and method of lubricating the same |
| JP3806398B2 (en) * | 2002-11-28 | 2006-08-09 | 三菱重工業株式会社 | Cylinder lubrication device |
| CN103628948B (en) * | 2013-12-23 | 2015-11-18 | 北京理工大学 | A kind of free piston IC generator jet lubrication device |
-
1986
- 1986-09-05 JP JP20772886A patent/JPH0663445B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6365109A (en) | 1988-03-23 |
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