JPS5924300B2 - cylinder liner - Google Patents
cylinder linerInfo
- Publication number
- JPS5924300B2 JPS5924300B2 JP51145484A JP14548476A JPS5924300B2 JP S5924300 B2 JPS5924300 B2 JP S5924300B2 JP 51145484 A JP51145484 A JP 51145484A JP 14548476 A JP14548476 A JP 14548476A JP S5924300 B2 JPS5924300 B2 JP S5924300B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder liner
- vibration damping
- crankcase
- damping member
- vibration
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/02—Cylinders; Cylinder heads having cooling means
- F02F1/10—Cylinders; Cylinder heads having cooling means for liquid cooling
- F02F1/12—Preventing corrosion of liquid-swept surfaces
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Compressor (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Description
【発明の詳細な説明】
本発明は、その内面をピストンが往復摺動するシリンダ
ライナの改良に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a cylinder liner on which a piston reciprocates on its inner surface.
一般に往復動内燃機関や往復動式空気圧縮機等。Generally, reciprocating internal combustion engines, reciprocating air compressors, etc.
においては、クランクケースの内部にシリンダライナを
装着し該シリンダライナの内面をピストンが往復摺動す
る様構成されている。The cylinder liner is installed inside the crankcase, and the piston is configured to reciprocate and slide on the inner surface of the cylinder liner.
第1図に往復動内燃機関の1例を示す。FIG. 1 shows an example of a reciprocating internal combustion engine.
同図において1はピストン、2はシリンダライナ、3は
クランクケース、4は連接棒、5はクランク軸、6はオ
イルパン、7は主軸受である。In the figure, 1 is a piston, 2 is a cylinder liner, 3 is a crankcase, 4 is a connecting rod, 5 is a crankshaft, 6 is an oil pan, and 7 is a main bearing.
上記シリンダライナ2はその肩部フランジ2dにて上記
クランクケース3に固着されると共に突起部2b、2C
を該クランクケース3の内面にて支承することによりそ
の軸直角方向の変位を規制せしめている。The cylinder liner 2 is fixed to the crankcase 3 at its shoulder flange 2d, and has protrusions 2b and 2C.
is supported on the inner surface of the crankcase 3, thereby restricting its displacement in the direction perpendicular to the axis.
また上記シリンダライナ2の外面とクランクケース3の
上部(ジャケット部)との間にはシリンダライナ2を冷
却するための冷却液が収容された冷却室8が形成されて
いる。Further, a cooling chamber 8 containing a cooling liquid for cooling the cylinder liner 2 is formed between the outer surface of the cylinder liner 2 and the upper part (jacket portion) of the crankcase 3.
更に上記シリンダライナ2の突起部2 b t 2 c
とクランクケース3の内面との間の嵌合部にて上記冷却
室8内の冷却液のシールを形成している。Furthermore, the protruding portion 2 b t 2 c of the cylinder liner 2
A seal for the coolant in the cooling chamber 8 is formed at the fitting portion between the inner surface of the crankcase 3 and the inner surface of the crankcase 3.
かかる構成を具えた内燃機関においては、シリンダ内に
おける爆発圧力によりピストン1から連接棒4に伝達さ
れる力Fは、シリンダライナ2の軸心方向の力F1とシ
リンダライナ2の軸直角力向の力F2に分解されるが、
該ピストン1がシリンダライナ2内を高速度で往復動す
るため、シリンダライナ2はその内壁面に上記F2によ
る衝撃力を受け、主として軸直角力向に加振される。In an internal combustion engine with such a configuration, the force F transmitted from the piston 1 to the connecting rod 4 due to the explosion pressure within the cylinder is the force F1 in the axial direction of the cylinder liner 2 and the force F1 in the direction perpendicular to the axis of the cylinder liner 2. It is decomposed into force F2,
Since the piston 1 reciprocates within the cylinder liner 2 at a high speed, the cylinder liner 2 receives an impact force from the above F2 on its inner wall surface, and is vibrated mainly in the axis-perpendicular force direction.
このようにして誘起されたシリンダライナ2の振動は、
該シリンダライナ2とクランクケース3との接合部2d
、2b、2cを通してクランクケース3やオイルパン6
に伝達される。The vibration of the cylinder liner 2 induced in this way is
Joint portion 2d between the cylinder liner 2 and the crankcase 3
, 2b, 2c to the crankcase 3 and oil pan 6.
transmitted to.
また上記ピストン1とシリンダライナ2との間の衝突エ
ネルギの一部は連接棒4、クランク軸5.主軸受Iを介
して上記クランクケース3やオイルパン6に伝達され、
クランクケース3やオイルパン6の振動の一因となる。Also, part of the collision energy between the piston 1 and the cylinder liner 2 is transferred to the connecting rod 4, the crankshaft 5. is transmitted to the crankcase 3 and oil pan 6 via the main bearing I,
This causes vibrations in the crankcase 3 and oil pan 6.
かかるクランクケース3やオイルパン6の振動は、これ
らの表面から音波として放射され、いわゆる機関騒音の
一因となっていた。Such vibrations of the crankcase 3 and oil pan 6 are radiated as sound waves from their surfaces, contributing to so-called engine noise.
また上記シリンダライナ2の振動により冷却室8内の冷
却液が高周波で加振されてその内部にキャビテーション
を発生し該冷却液に接するシリンダライナ2やクランク
ケース3の表向、ことにシリンダライナ2の表面にキャ
ビテーションエロージョンが発生することが多々あった
。Furthermore, due to the vibration of the cylinder liner 2, the coolant in the cooling chamber 8 is excited with high frequency and cavitation occurs inside the coolant, causing cavitation to occur on the surfaces of the cylinder liner 2 and crankcase 3 that are in contact with the coolant, especially the cylinder liner 2. Cavitation erosion often occurred on the surface.
加えてかかるシリンダライナ2は、熱応力低減の観点か
らその肉厚を比較的薄く構成しているため、シリンダラ
イナ自体の振動減衰能が小さく、従って該シリンダライ
ナ2の振動は殆んど減衰されることなくクランクケース
3やオイルパン6に伝達されざるを得なかった。In addition, since the cylinder liner 2 has a relatively thin wall thickness from the viewpoint of reducing thermal stress, the vibration damping ability of the cylinder liner itself is small, and therefore the vibration of the cylinder liner 2 is hardly damped. It had no choice but to be transmitted to the crankcase 3 and oil pan 6 without any interference.
本発明は、上記の問題点を解消し、シリンダライナの振
動による機関の騒音を低減すると共にその外面における
キャビテーションエロージョンの発生を防止したシリン
ダライナを提供するためになされたものである。The present invention has been made in order to solve the above-mentioned problems and provide a cylinder liner that reduces engine noise caused by vibration of the cylinder liner and prevents cavitation erosion from occurring on its outer surface.
以下第2図ないし第4図を参照して本発明の1実施例に
つき説明する。An embodiment of the present invention will be described below with reference to FIGS. 2 to 4.
11はゴム、プラスチック、ポリエステル等弾性を有し
振動減衰能の大きい物質から成る振動減衰用部材で、シ
リンダライナ本体2aの外周に貼着される。Reference numeral 11 denotes a vibration damping member made of a material having elasticity and high vibration damping ability, such as rubber, plastic, or polyester, and is attached to the outer periphery of the cylinder liner body 2a.
12は、耐蝕性、耐熱性を有する金属から成る金属板で
、上記振動減衰用部材11の外周に該振動減衰用部材1
1をすっぽりと覆う形で以って圧接、巻装され、該振動
減衰用部材11のシリンダライナ本体2aからのはく離
あるいは脱落を防止せしめる。12 is a metal plate made of a metal having corrosion resistance and heat resistance, and the vibration damping member 1 is attached to the outer periphery of the vibration damping member 11.
The vibration damping member 11 is pressed and wrapped so as to completely cover the cylinder liner body 2a, thereby preventing the vibration damping member 11 from peeling off or falling off from the cylinder liner main body 2a.
上記金属板12はそれ自体で振動減衰作用をせしめるた
め、振動減衰能の大きい軟質金属を採用するのが望まし
い。Since the metal plate 12 has a vibration damping effect by itself, it is desirable to use a soft metal with a large vibration damping ability.
更に、上記振動減衰用部材11の厚さはシリンダライナ
本体2a該振動減衰用部材11装着部分の肉厚の1%〜
10%に採るのが望ましい。Further, the thickness of the vibration damping member 11 is 1% to 1% of the wall thickness of the part where the vibration damping member 11 is attached to the cylinder liner main body 2a.
It is desirable to set it at 10%.
上記シリンダライナ2は、第1図に示すように肩部フラ
ンジ2d及び突起部2 b 、2 cを介して内燃機関
のクランクケース3に装着される。As shown in FIG. 1, the cylinder liner 2 is attached to a crankcase 3 of an internal combustion engine via a shoulder flange 2d and projections 2b, 2c.
かかる構成を具えたシリンダライナ2を装着した内燃機
関を運転する際は、前記のようにピストン1の往復摺動
によりシリンダライナ本体2aが主としてその軸直角方
向に加振されるが、該本体2aの外周に貼着された振動
減衰用部材11の変形により該本体2a自体の振幅が減
少せしめられる。When operating an internal combustion engine equipped with a cylinder liner 2 having such a configuration, the cylinder liner main body 2a is mainly vibrated in the direction perpendicular to its axis due to the reciprocating sliding of the piston 1 as described above. The amplitude of the main body 2a itself is reduced by deformation of the vibration damping member 11 attached to the outer periphery of the main body 2a.
更に、該減衰用部材11の上記振動減衰作用により該減
衰用部材11の外周に巻装された金属板12の振動は、
上記のように減衰されたライナ本体2aの振動と同程度
か、またはこれよりも小さくなる。Furthermore, due to the vibration damping effect of the damping member 11, the vibration of the metal plate 12 wound around the outer periphery of the damping member 11 is
The vibration is equal to or smaller than the vibration of the liner body 2a damped as described above.
従ってシリンダライナ2の振動に起因するクランクケー
ス3やオイルパン6の振動が低減されると共に、冷却液
に触れる部分の金属板12の振動は、減衰用部材11を
適用しない場合のライナ本体2の振動よりも、著るしく
低減されるため、冷却液に触れる部分におけるキャビテ
ーションエロージョンの発生が防止される。Therefore, the vibrations of the crankcase 3 and oil pan 6 caused by the vibrations of the cylinder liner 2 are reduced, and the vibrations of the metal plate 12 in the portion that comes into contact with the coolant are reduced, compared to the liner body 2 when the damping member 11 is not applied. Since it is significantly reduced compared to vibration, cavitation erosion is prevented from occurring in the parts that come into contact with the coolant.
また金属板12にて振動減衰用部材11の外周をすっぽ
り覆うことにより、該減衰用部材11のシリンダライナ
本体2aからの脱落を防止し、かつ該金属板12自体の
振動減衰作用により、シリンダライナ2全体の振動が更
に減衰せしめられる。Furthermore, by completely covering the outer periphery of the vibration damping member 11 with the metal plate 12, the damping member 11 is prevented from falling off from the cylinder liner body 2a, and the vibration damping effect of the metal plate 12 itself prevents the cylinder liner from falling off. The vibrations of the entire 2 are further damped.
以上述べたように、本発明に係るシリンダライナは、外
周向にゴム、プラスチック等の高い振動減衰能を有する
非金属材料から成る振動減衰用部材を貼着し、更にその
外周を金属板で覆ったので該振動減衰用部材の減衰作用
及び振動減衰用部材と金−属板とを組合せたことによる
附加減衰作用によりシリンダライナ自体の振動が減衰さ
れ、従って該シリンダライナの振動に起因するクランク
ケースやオイルパンの振動が著るしく低減される。As described above, the cylinder liner according to the present invention has a vibration damping member made of a non-metallic material such as rubber or plastic having a high vibration damping ability affixed to the outer periphery, and the outer periphery is further covered with a metal plate. Therefore, the vibration of the cylinder liner itself is damped by the damping effect of the vibration damping member and the additional damping effect of the combination of the vibration damping member and the metal plate, and therefore, the vibration of the cylinder liner itself is damped. and oil pan vibrations are significantly reduced.
このため、クランクケースやオイルパンの振動による騒
音を低減することができる。Therefore, noise caused by vibrations of the crankcase and oil pan can be reduced.
更にシリンダライナの外周向を冷却液にて冷却する機関
においては、シリンダライナの振動に起因するキャビテ
ーションエロージョンの発生を未然に防止することがで
きる。Furthermore, in an engine in which the outer periphery of the cylinder liner is cooled with a cooling liquid, cavitation erosion caused by vibration of the cylinder liner can be prevented from occurring.
第1図はシリンダライナを装着した往復動内燃機関の1
例を示す図でクランク軸心線に直角方向の断面図、第2
図ないし第4図は本発明の1実施例を示し、第2図はシ
リンダライナの軸心線に沿う断面図、第3図は第2図の
B部を拡大したる図、第4図は第2図のA−A緋に沿う
断面図である。
1・・・・・・ピストン、2・・・・・・シリンダライ
ナ、2a・・・・・・シリンダライナ本体、3・・・・
・・クランクケース、4・・・・・・連接棒、5・・・
・・・クランク軸、6・・・・・・オイルパン、7・・
・・・・主軸受、8・・・・・・冷却室、11・・・・
・・振動減衰用部材、12・・・−・・金属板。Figure 1 shows a reciprocating internal combustion engine equipped with a cylinder liner.
This is a cross-sectional view in the direction perpendicular to the crankshaft center line, the second
4 to 4 show one embodiment of the present invention, FIG. 2 is a cross-sectional view along the axis of the cylinder liner, FIG. 3 is an enlarged view of section B in FIG. 2, and FIG. FIG. 3 is a sectional view taken along line A-A in FIG. 2; 1...Piston, 2...Cylinder liner, 2a...Cylinder liner body, 3...
...Crankcase, 4...Connecting rod, 5...
...Crankshaft, 6...Oil pan, 7...
...Main bearing, 8...Cooling chamber, 11...
...Vibration damping member, 12...--Metal plate.
Claims (1)
高い振動減衰能を有する非金属材料から成る振動減衰用
部材を貼着し、更に該振動減衰用部材の外周に金属板を
巻装したことを特徴とするシリンダライナ。1. A vibration damping member made of a non-metallic material with high vibration damping ability such as rubber or plastic is attached to the outer peripheral surface of the cylinder liner, and a metal plate is further wrapped around the outer periphery of the vibration damping member. cylinder liner.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP51145484A JPS5924300B2 (en) | 1976-12-03 | 1976-12-03 | cylinder liner |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP51145484A JPS5924300B2 (en) | 1976-12-03 | 1976-12-03 | cylinder liner |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5370256A JPS5370256A (en) | 1978-06-22 |
JPS5924300B2 true JPS5924300B2 (en) | 1984-06-08 |
Family
ID=15386315
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP51145484A Expired JPS5924300B2 (en) | 1976-12-03 | 1976-12-03 | cylinder liner |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5924300B2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5844253A (en) * | 1981-09-10 | 1983-03-15 | Hamada Eng Kk | Wet liner and manufacturing method thereof |
JPH0310362Y2 (en) * | 1985-06-28 | 1991-03-14 |
-
1976
- 1976-12-03 JP JP51145484A patent/JPS5924300B2/en not_active Expired
Also Published As
Publication number | Publication date |
---|---|
JPS5370256A (en) | 1978-06-22 |
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