JPH0333457A - Two-layer liner for cylinder - Google Patents
Two-layer liner for cylinderInfo
- Publication number
- JPH0333457A JPH0333457A JP16705189A JP16705189A JPH0333457A JP H0333457 A JPH0333457 A JP H0333457A JP 16705189 A JP16705189 A JP 16705189A JP 16705189 A JP16705189 A JP 16705189A JP H0333457 A JPH0333457 A JP H0333457A
- Authority
- JP
- Japan
- Prior art keywords
- young
- modulus
- ratio
- outer ring
- inner ring
- 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
Landscapes
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、中、大型ディーゼル機関用の2層式シリンダ
ライナに関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a two-layer cylinder liner for medium to large-sized diesel engines.
従来形のディーゼル機関用シリンダライナは耐摩耗性維
持のため鋳鉄一体式のものが用いられ、燃焼のガス圧に
耐えること及び水冷孔(ボアクール)をそなえた厚肉の
単体型が採用されている。Conventional cylinder liners for diesel engines are made of cast iron in order to maintain wear resistance, and are thick-walled single-piece liners that can withstand combustion gas pressure and are equipped with water cooling holes (bore cool). .
第5〜6図は従来形シリンダライナ構造で1′はライナ
本体、3はボアクール孔、5′は受圧部、4′はピスト
ンを示す。Figures 5 and 6 show the structure of a conventional cylinder liner, where 1' is the liner body, 3 is the bore cool hole, 5' is the pressure receiving part, and 4' is the piston.
(発明が解決しようとする課題〕
ところが耐摩耗性の良い鋳鉄を用いた従来形シリンダラ
イナでは、鋳鉄の引張強さが低く高いガス圧を受けるシ
リンダライナでは肉厚とせざるを得ず外径が大きくなる
。さらに肉厚化するとガスの燃焼によるシリンダライナ
の熱応力が大きくなるため、キリ穴状冷却孔(ボアクー
ル孔)を設けて冷却する必要を生じ、開孔によりシリン
ダライナの強度が低下する等の欠点を有している。(Problem to be solved by the invention) However, in conventional cylinder liners made of cast iron, which has good wear resistance, cast iron has low tensile strength and is subject to high gas pressure, so the cylinder liner has to be thick and the outer diameter has to be increased. If the wall becomes thicker, the thermal stress on the cylinder liner due to gas combustion will increase, making it necessary to provide drilled cooling holes (bore cool holes) for cooling, and the openings will reduce the strength of the cylinder liner. It has the following disadvantages.
また特願昭58−72249号では外筒を鋼材としその
内部に鋳鉄を遠心鋳造して内筒を製作する方法が提案さ
れたが外側の鋼材と内筒の鋳鉄との鋳付きが悪いため、
シリンダライナの熱伝導がわるくライナが十分冷却され
ない欠点があった。Furthermore, in Japanese Patent Application No. 58-72249, a method was proposed in which the outer cylinder was made of steel and the inner cylinder was manufactured by centrifugally casting cast iron inside the outer cylinder, but because the casting of the outer steel material and the cast iron of the inner cylinder was poor,
There was a drawback that the liner was not cooled sufficiently due to poor heat conduction of the cylinder liner.
従って従来の一体式ボアクール形鋳鉄シリンダでは設計
上余裕がなく強度限界−杯であり減肉化もなく、出力向
上も難しく機関長の短縮による船舶のコンパクト化は不
可能であった。Therefore, in the conventional integrated bore cool type cast iron cylinder, there is no margin in design, the strength is at its limit, there is no thinning, and it is difficult to increase the output, making it impossible to make the ship more compact by shortening the length of the engine.
本発明の目的は前記従来装置の問題点を解消し、シリン
ダライナの薄肉化と出力向上を図り、機関長の短縮によ
る船のコンパクト化を実現できる2層式シリンダライナ
を提供するにある。SUMMARY OF THE INVENTION An object of the present invention is to provide a two-layer cylinder liner that solves the problems of the conventional apparatus, reduces the thickness of the cylinder liner, increases output, and makes the ship more compact by shortening the length of the engine.
+taを解決するための手段〕
本発明の2層式シリンダライナは、内輪は耐摩耗性維持
のためヤング率Elの鋳鉄を使用し、外輪はヤング率E
2の高張力鋼材を使用し、外輪と内輪のヤング率比をE
2/E1≧1.5としたことを特徴としている。Means for Solving +ta] The two-layer cylinder liner of the present invention uses cast iron with a Young's modulus of El for the inner ring to maintain wear resistance, and uses cast iron with a Young's modulus of E for the outer ring.
2 high tensile strength steel is used, and the Young's modulus ratio of the outer ring and inner ring is E.
2/E1≧1.5.
以下2層式シリンダライナの内圧(ディーゼル機関では
ガス圧にあたる)による内周方向の応力計算により薄肉
化が可能なことを証明します。この計算式(9)は実施
例で説明するように薄肉円筒と考え内外輪の釣合いから
内外輪の円周方向の応力比を整理して計算したものであ
る。(第3図参照)但しここで El :内輪材のヤン
グ率E2 :外輪材のヤング率
Rml:内輪の平均半径
Rn+2:外輪の平均半径
上記のように内外輪の応力比は内輪と外輪のヤング率の
比E I / E !に左右されることとなり、内輪に
耐摩耗性の良好な鋳鉄を使用しても、鋳鉄のヤング率E
1が小さいので、外輪にヤング率E2が大きい高張力鋼
を使用すれば、内輪に使用される鋳鉄の応力が下げられ
、シリンダライナの薄肉化及び出力向上を図ることがで
きる。Below, we will prove that thinning is possible by calculating the stress in the inner peripheral direction based on the internal pressure (corresponding to gas pressure in diesel engines) of a two-layer cylinder liner. As will be explained in the examples, this calculation formula (9) is calculated by considering a thin-walled cylinder and arranging the stress ratio in the circumferential direction of the inner and outer rings from the balance between the inner and outer rings. (See Figure 3) However, where El: Young's modulus of the inner ring material E2: Young's modulus of the outer ring material Rml: Average radius of the inner ring Rn+2: Average radius of the outer ring As shown above, the stress ratio of the inner and outer rings is the Young's modulus of the inner and outer rings. Rate ratio E I / E ! Even if cast iron with good wear resistance is used for the inner ring, the Young's modulus of cast iron
1 is small, so if high-tensile steel with a large Young's modulus E2 is used for the outer ring, the stress in the cast iron used for the inner ring can be reduced, making it possible to reduce the thickness of the cylinder liner and improve output.
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。An embodiment of the present invention will be described below with reference to FIGS. 1 to 4.
第1図は2層式シリンダライナの横断面図で、lはFC
25鋳鉄製の内輪、2は5CPH鋼製の外輪を示す、第
2図は第1図の縦断面図であり、4はピストンの下死点
位置、5は受圧部を示す。図において内輪1と外輪2と
は旧P(Hot l5ostatic Press i
ng )法により一体的に接合しているので、長時間使
用しても分離することはなく熱伝導率が良好である。Figure 1 is a cross-sectional view of a two-layer cylinder liner, where l is FC.
25 shows an inner ring made of cast iron, 2 shows an outer ring made of 5 CPH steel, FIG. 2 is a longitudinal sectional view of FIG. 1, 4 shows the bottom dead center position of the piston, and 5 shows the pressure receiving part. In the figure, inner ring 1 and outer ring 2 are old P (Hot l5ostatic Press i).
Since they are integrally bonded using the NG method, they do not separate even after long-term use and have good thermal conductivity.
次に2層式シリンダライナとすると内輪の応力が小さく
なり、シリンダライナの薄肉化が可能となる理由につい
て薄肉円筒の式を用いて説明する。Next, the reason why a two-layer cylinder liner reduces the stress in the inner ring and allows the cylinder liner to be made thinner will be explained using the formula for a thin cylinder.
ヤング率が内輪El、外輪E2と異なった2層式シリン
ダライナが内圧Pを受ける場合、内輪l及び外輪2は嵌
合部でそれぞれ同じ値qの内圧及び外圧を受けるものと
する。このとき内輪1及び外輪2の半径方向の変形量u
l+u!はそれぞれ次のようになる。When a two-layer cylinder liner whose Young's modulus is different from that of the inner ring El and the outer ring E2 is subjected to an internal pressure P, the inner ring 1 and the outer ring 2 are each subjected to the same internal pressure and external pressure at the fitting portion q. At this time, the amount of deformation u in the radial direction of the inner ring 1 and outer ring 2
l+u! are as follows:
・・・(1〕
内輪と外輪は隙間なく嵌合しているので半径方向の変位
量が等しいはずであるから
・・・(2)
故に外輪による外圧qは次の値となる。...(1) Since the inner ring and outer ring are fitted without any gap, the amount of displacement in the radial direction should be equal...(2) Therefore, the external pressure q due to the outer ring is the following value.
R2m+ ・・・(3) また円筒の円周方向応力をσ。R2m+ ...(3) Also, the stress in the circumferential direction of the cylinder is σ.
とすると、
従って、
2層式シリンダライナの内外輪応力比は(3)式から
(8)式を(7)式に代入して
(9)式より応力比はヤング率の比と平均半径の比で決
まることがわかる。すなわち内輪のヤング率E1が小さ
く外輪のヤング率E2が大きいと内輪の応力σ□が下が
ることになる。Therefore, by substituting equations (3) to (8) into equation (7), the stress ratio of the two-layer cylinder liner is determined by the ratio of Young's modulus and the average radius. It can be seen that it is determined by the ratio. That is, when the Young's modulus E1 of the inner ring is small and the Young's modulus E2 of the outer ring is large, the stress σ□ of the inner ring decreases.
2層式シリンダライナ、で内輪を普通鋳鉄、外輪を高張
力鋼材とする時の内外輪のガス圧による円周方向の応力
比は最終的には(9)式により内外輪のヤング率の比で
決まることがわかる。In a two-layer cylinder liner, when the inner ring is made of ordinary cast iron and the outer ring is made of high-strength steel, the stress ratio in the circumferential direction due to gas pressure in the inner and outer rings is finally determined by the ratio of the Young's modulus of the inner and outer rings using equation (9). It can be seen that it is determined by
全内輪のヤング率をE、 〜10,000kg/閣2、
外輪のヤング率をE z 〜20,000kg/ mm
2と仮定すると、(9)式から内輪の応力σ1.は
となり、ライナが十分径が大きければ半径比の影響は少
くなり、内輪の応力σ、Iは外輪の応力σ。The Young's modulus of the entire inner ring is E, ~10,000kg/Kaku2,
Young's modulus of the outer ring is Ez ~20,000kg/mm
2, the inner ring stress σ1. If the diameter of the liner is sufficiently large, the influence of the radius ratio will be reduced, the stress in the inner ring is σ, and I is the stress in the outer ring.
の略半分に近くなると考えられる。−船釣には内輪の鋳
鉄のヤング率はEl = 8,000 −12,000
kg/mm”、外輪のヤング率はE2=19,000〜
22.000kg/+m++2である。It is thought that it will be close to about half of that. -For boat fishing, the Young's modulus of the cast iron inner ring is El = 8,000 -12,000
kg/mm", Young's modulus of the outer ring is E2 = 19,000 ~
22.000kg/+m++2.
なお全内輪の円周方向応力を従来の単体型ライナの円周
方向応力と等しいと考え、又内外輪円周方向応力の間の
関係式〇〇)を参照すると次の関係式%式%
)
故に2層式シリンダライナの全厚さt。If we assume that the circumferential stress of the entire inner ring is equal to the circumferential stress of a conventional single-piece liner, and refer to the relational expression 〇〇) between the circumferential stress of the inner and outer rings, the following relational expression % formula %) can be obtained. Therefore, the total thickness of the two-layer cylinder liner is t.
は
ライナの径が大きいのでライナの外内輪半径比Rmz/
Ra+、#lとすると
Lz=謝45tζ0.5t ・・・ 06)従って
本発明の2層式シリンダライナでは、ライナ厚さり、は
従来形の一体型ライナの半分とすることができ、又11
1P加工をしているため内外輪が完全に密着しており、
長時間をへても境界面より分離することなく、良好な冷
却性能を保持することができる。Since the diameter of the liner is large, the outer and inner ring radius ratio of the liner is Rmz/
If Ra+, #l, then Lz=X45tζ0.5t... 06) Therefore, in the two-layer cylinder liner of the present invention, the liner thickness can be half that of the conventional integrated liner, and 11
Due to 1P processing, the inner and outer rings are completely in contact,
Good cooling performance can be maintained without separation from the interface even after a long period of time.
本発明の2層式リンダライナは、高張力鋼材よりなる外
輪の内周に鋳鉄製の内輪をはめこみ、外内輪のヤング率
比をE2/E1≧1.5としたため、ライナの厚さを大
幅に薄肉化できることとなり、機関長の短縮による船舶
のコンパクト化が実現可能となる。The two-layer cylinder liner of the present invention has an inner ring made of cast iron fitted into the inner periphery of an outer ring made of high-strength steel, and the Young's modulus ratio of the outer and inner rings is set to E2/E1≧1.5, so the thickness of the liner can be significantly reduced. This makes it possible to reduce the thickness of the ship, making it possible to make the ship more compact by shortening the length of the chief engineer.
第1〜4図は本発明の実施例に係わるもので、第1図は
2層式シリンダライナの横断面図、第2図は同縦断面図
、第3図は内外輪の円周方向応力分布図、第4図は2層
式シリンダライナに内圧pが作用した時の強度計算に関
連した説明図、第5〜6図は従来例で、第5図は第1図
応当図、第6図は第2図応当図である。
■・・・内輪、2・・・外輪、4・・・ピストン、E、
・・・内輪のヤング率、E2・・・外輪のヤング率。
外輪
第
図
第
図
第
図
2層円筒
第4図
第5
図
第6
図Figures 1 to 4 relate to embodiments of the present invention. Figure 1 is a cross-sectional view of a two-layer cylinder liner, Figure 2 is a longitudinal cross-sectional view of the same, and Figure 3 is a stress stress in the circumferential direction of the inner and outer rings. Distribution diagram, Figure 4 is an explanatory diagram related to strength calculation when internal pressure p acts on a two-layer cylinder liner, Figures 5 and 6 are conventional examples, Figure 5 is a diagram corresponding to Figure 1, and Figure 6 is an explanatory diagram related to strength calculation when internal pressure p acts on a two-layer cylinder liner. The figure corresponds to Figure 2. ■...Inner ring, 2...Outer ring, 4...Piston, E,
...Young's modulus of the inner ring, E2...Young's modulus of the outer ring. Outer ring Diagram Diagram Diagram Diagram Double layer cylinder Diagram 4 Diagram 5 Diagram 6
Claims (1)
において、外輪がヤング率E_2の鉄系材料、内輪がヤ
ング率E_1の鋳鉄材料とした時、外輪と内輪のヤング
率の比をE_2/E_1≧1.5としたことを特徴とす
る2層式シリンダライナ。In a two-layer cylinder liner in which an inner ring is fitted to the inner circumference of an outer ring, when the outer ring is made of iron-based material with a Young's modulus of E_2 and the inner ring is made of cast iron with a Young's modulus of E_1, the ratio of the Young's modulus of the outer ring and the inner ring is A two-layer cylinder liner characterized in that E_2/E_1≧1.5.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16705189A JPH0333457A (en) | 1989-06-30 | 1989-06-30 | Two-layer liner for cylinder |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16705189A JPH0333457A (en) | 1989-06-30 | 1989-06-30 | Two-layer liner for cylinder |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0333457A true JPH0333457A (en) | 1991-02-13 |
Family
ID=15842487
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP16705189A Pending JPH0333457A (en) | 1989-06-30 | 1989-06-30 | Two-layer liner for cylinder |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0333457A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012003625A (en) * | 2010-06-18 | 2012-01-05 | Toshiba Corp | Electronic device |
US20140102401A1 (en) * | 2011-05-21 | 2014-04-17 | Mahle International Gmbh | Cylinder liner and structural unit consisting of at least one cylinder liner and a crankcase |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6128740A (en) * | 1984-07-18 | 1986-02-08 | Mitsubishi Heavy Ind Ltd | Cylinder liner of reciprocating engine |
-
1989
- 1989-06-30 JP JP16705189A patent/JPH0333457A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6128740A (en) * | 1984-07-18 | 1986-02-08 | Mitsubishi Heavy Ind Ltd | Cylinder liner of reciprocating engine |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012003625A (en) * | 2010-06-18 | 2012-01-05 | Toshiba Corp | Electronic device |
US20140102401A1 (en) * | 2011-05-21 | 2014-04-17 | Mahle International Gmbh | Cylinder liner and structural unit consisting of at least one cylinder liner and a crankcase |
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