JPS61210252A - Cylinder head gasket structure - Google Patents
Cylinder head gasket structureInfo
- Publication number
- JPS61210252A JPS61210252A JP5276185A JP5276185A JPS61210252A JP S61210252 A JPS61210252 A JP S61210252A JP 5276185 A JP5276185 A JP 5276185A JP 5276185 A JP5276185 A JP 5276185A JP S61210252 A JPS61210252 A JP S61210252A
- Authority
- JP
- Japan
- Prior art keywords
- liner
- gas pressure
- head gasket
- cylinder head
- pressure receiving
- 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
- 230000002093 peripheral effect Effects 0.000 claims description 2
- 238000005452 bending Methods 0.000 abstract description 4
- 239000007787 solid Substances 0.000 abstract description 2
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general
- F16J10/02—Cylinders designed to receive moving pistons or plungers
- F16J10/04—Running faces; Liners
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Actuator (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は上端部外周にフランジ部を有するライナを採用
した内燃機関のシリンダヘッドガスケット構造に関する
。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a cylinder head gasket structure for an internal combustion engine that employs a liner having a flange portion on the outer periphery of its upper end.
（従来技術）
従来の一例を示す第４図において、１はシリンダブロッ
ク、２はライナ、３はシリンダヘッドである。ライナ２
は上端部外周にフランジ部４を一体に備え、このフラン
ジ部４の下面はガスケット５を介してシリンダブロック
１の上面に支持されている。フランジ部４とライナ本体
２ａとの境界部分、すなわちフランジ部４の首下部には
、ライナ本体２ａ側へ滑かに凹入する環状切欠き部６（
１り首下部）が設けてあり、切欠き部６より下側におい
てライナ本体２ａはシリンダブロック１の内面に挿入さ
れている。ライナ本体２ａの上端のガス圧受圧面８とシ
リンダヘッド３の間には隙間９が設けてあり、ガス圧受
圧面８は段部１０をへてフランジ部上面１１に接続し、
フランジ部上面１１にはへラドガスケット１２を介して
シリンダヘッド３の締付面１３が当接している。隙間９
は燃焼室１４に連通しているため、爆発行程においてガ
ス圧受圧面８には矢印Ａ１で丞すガス圧が作用する。フ
ランジ部上面１１にはヘッドボルト１５の締付力が矢印
Ｂ１のように作用する。Ｃは支点に作用する反力、ｊｌ
はＣ，Ｂ１間の距離、ＬｌはＣ，Ａ１間の距離である。(Prior Art) In FIG. 4 showing a conventional example, 1 is a cylinder block, 2 is a liner, and 3 is a cylinder head. liner 2
is integrally provided with a flange portion 4 on the outer periphery of the upper end portion, and the lower surface of the flange portion 4 is supported on the upper surface of the cylinder block 1 via a gasket 5. At the boundary between the flange portion 4 and the liner body 2a, that is, at the lower part of the neck of the flange portion 4, there is an annular notch 6 (
The liner body 2a is inserted into the inner surface of the cylinder block 1 below the notch 6. A gap 9 is provided between the gas pressure receiving surface 8 at the upper end of the liner body 2a and the cylinder head 3, and the gas pressure receiving surface 8 is connected to the flange portion upper surface 11 via a stepped portion 10.
A tightening surface 13 of the cylinder head 3 is in contact with the upper surface 11 of the flange portion via a helad gasket 12 . Gap 9
is in communication with the combustion chamber 14, so that the gas pressure indicated by the arrow A1 acts on the gas pressure receiving surface 8 during the explosion stroke. The tightening force of the head bolt 15 acts on the upper surface 11 of the flange portion as shown by arrow B1. C is the reaction force acting on the fulcrum, jl
is the distance between C and B1, and Ll is the distance between C and A1.
第４図から明らかなように、フランジ部４には反力Ｃの
作用する支点を中心にＡ１・Ｌ１＋８１・」１のモーメ
ントが時計方向に作用し、これにより切欠き部６が破旧
しやりくなる。即ち爆発力が小さい時は良いが、これが
大きくなると、ヘッドボルト締付力Ｂ１、ガス正荷ｆｉ
Ａ１共に大きくなり、ライナ首下部（切欠き部６）の応
力がきつくなり、強度的に不足する。As is clear from FIG. 4, a moment of A1.L1+81.''1 acts on the flange portion 4 in a clockwise direction around the fulcrum on which the reaction force C acts, and as a result, the notch portion 6 tends to be damaged. Become. In other words, it is good when the explosive force is small, but when it becomes large, the head bolt tightening force B1 and the positive gas load fi
Both A1 and A1 become large, and the stress at the lower part of the liner neck (notch 6) becomes severe, resulting in insufficient strength.
この対策として従来第５図のように、ガス圧受圧面８の
外径を増し、フランジ部上面１１の内径を増して、ヘッ
ドボルト締付力Ｂ２の作用点を外周側（第５図左方）へ
よせ、ＣＢ２間の距離ｆＪ２を小さくしたものも開発さ
れている。しかしその場合、七−メントＡ２・Ｌ２＋８
２・！Ｊ２の第２項は減少するが、第１項のガス圧荷重
Ａ２が増すため、充分な効果は期待できない。As a conventional countermeasure, as shown in Fig. 5, the outer diameter of the gas pressure receiving surface 8 and the inner diameter of the upper surface 11 of the flange portion were increased, and the point of application of the head bolt tightening force B2 was shifted to the outer circumferential side (left side in Fig. 5). ), and one in which the distance fJ2 between CB2 is reduced has also been developed. However, in that case, 7-ment A2・L2+8
2.! Although the second term of J2 decreases, a sufficient effect cannot be expected because the first term, gas pressure load A2, increases.
（発明の目的）
本発明はヘッドボルトの締付力及び繰返しのガス圧荷重
によるシリンダライナ首下部の応力を低減し、耐久性を
増すことを目的としている。(Objective of the Invention) The object of the present invention is to reduce the stress in the lower part of the cylinder liner neck due to the tightening force of the head bolt and repeated gas pressure loads, and to increase the durability.
（発明の構成）
本発明はライナの上端部外周に下面がシリンダブロック
に支持されるフランジ部を設け、ライナ本体上端のガス
圧受圧面とシリンダヘッドの間に隙間を設け、フランジ
部上面とシリンダヘッドの間にヘッドガスケットを介装
置ノ、フランジ部上面にヘッドガスケットを介してヘッ
ドボルト締付力を及ぼすものにおいて、ライナのガス圧
受圧面の外径をライナ本体の外径より減して作用するガ
ス圧を減し、ヘッドガスケットの内周側路半分をヘッド
ボルト締付力を支持しない可撓性シールで形成してヘッ
ドボルト締付力の作用点を外周側へ寄せたことを特徴と
するシリンダヘッドガスケット構造である。(Structure of the Invention) The present invention provides a flange portion whose lower surface is supported by the cylinder block on the outer periphery of the upper end of the liner, provides a gap between the gas pressure receiving surface at the upper end of the liner body and the cylinder head, and connects the upper surface of the flange portion to the cylinder head. In a device that uses a head gasket between the heads and applies head bolt tightening force to the upper surface of the flange portion through the head gasket, the outer diameter of the gas pressure receiving surface of the liner is made smaller than the outer diameter of the liner body. The head gasket is characterized by reducing gas pressure and forming half of the inner circumferential side path of the head gasket with a flexible seal that does not support the head bolt tightening force, thereby shifting the point of action of the head bolt tightening force to the outer circumferential side. The cylinder head gasket structure is
（実施例）
実施例を示す第１図において第４、第５図中の符号と同
一符号は対応部分である。第１図においてはライナ本体
２ａ上端のガス圧受圧面８の外径Ｄ８（・・・例えば１
８５＃ｌＩ）がライナ本体２ａの外径Ｄ２（・・・例え
ば１９４履）より充分小さくされており、従ってガス圧
受圧面８の面積の減少によりガス圧荷重Ａ３を第４図、
第５図の従来例に比べて大幅に減少させている。又中実
なヘッドガスケット１２の内周部に波形断面の耐熱金属
製可撓性シール１７を一体的に連設している。従って可
撓性シール１７の部分ではヘッドボルト締付力Ｂ３を支
持することはできず、単にガスシール機能を発揮する。(Example) In FIG. 1 showing an example, the same reference numerals as those in FIGS. 4 and 5 indicate corresponding parts. In FIG. 1, the outer diameter D8 (for example, 1
85#lI) is sufficiently smaller than the outer diameter D2 (for example, 194 mm) of the liner main body 2a, and therefore the gas pressure load A3 is reduced by reducing the area of the gas pressure receiving surface 8 as shown in FIG.
This is significantly reduced compared to the conventional example shown in FIG. Further, a flexible seal 17 made of heat-resistant metal and having a corrugated cross section is integrally connected to the inner peripheral portion of the solid head gasket 12. Therefore, the flexible seal 17 cannot support the head bolt tightening force B3, and merely functions as a gas seal.
この結果、ヘッドガスケット１２はフランジ部上面１１
の外周側に当接してヘッドボルト締付力Ｂ３を支持する
ことになり、締付力Ｉう３の作用点はフランジ部４の外
周側に近寄り、０８３間の距離ｊ１３はＯ又は僅少値に
なる。フランジ部支点を中心とするモーメントの合計は
、Ａ３・Ｌ３＋８３・１３となり、Ａ３が僅少なため第
２項は無視しつる程度に小さくなり、Ｌ３は多少増加す
るがＡ３が減少するため第１項も大幅に減少し、モーメ
ントの合計値は従来より大幅に減少する。これにより首
下切欠き部６に作用する応力が減少する。As a result, the head gasket 12 is attached to the flange portion upper surface 11.
The point of action of the tightening force I3 approaches the outer circumference of the flange portion 4, and the distance j13 between 083 becomes O or a small value. Become. The total moment about the fulcrum of the flange part is A3・L3+83・13, and since A3 is small, the second term is ignored and becomes small enough to be ignored. L3 increases somewhat, but A3 decreases, so the first term is also significantly reduced, and the total moment value is significantly reduced compared to before. This reduces the stress acting on the under-neck notch 6.
（発明の効果）
以上説明したように本発明においては、ライナ２のガス
圧受圧面８の外径（Ｄ８）をライナ本体２ａの外径（Ｄ
２）より減して作用するガス圧Ａ３を減し、ヘッドガス
ケットの内径側路半分をヘッドボルト締付力＋３３を支
持しない可撓性シール１７で形成してヘッドボルト締付
力Ｂ３の作用点を外周側へよせだので、ヘッドボルトの
締付力Ｂ３による曲げモーメント及びガス圧Ａ３による
曲げモーメントを両方共減少させ、ライナ首下部（切欠
き部６）に掛る曲げモーメントを減し、ライナ首下部の
破損を効果的に防止しうる利点がある。(Effects of the Invention) As explained above, in the present invention, the outer diameter (D8) of the gas pressure receiving surface 8 of the liner 2 is the outer diameter (D8) of the liner body 2a.
2) The acting gas pressure A3 is further reduced, and half of the inner diameter side passage of the head gasket is formed with a flexible seal 17 that does not support the head bolt tightening force +33, thereby reducing the acting point of the head bolt tightening force B3. Because it leans toward the outer circumference, both the bending moment due to the head bolt tightening force B3 and the bending moment due to the gas pressure A3 are reduced, the bending moment applied to the lower part of the liner neck (notch 6) is reduced, and the liner neck This has the advantage of effectively preventing damage to the lower part.
（別の実施例）
第３図のへラドガスフット１２は内周部に横開きＵ形断
面の可撓性シール１８を一体に有する。(Another Embodiment) The helad gas foot 12 shown in FIG. 3 has a flexible seal 18 with a laterally open U-shaped cross section integrally formed on its inner circumference.
この可撓性シール１８もヘッドボルト締付力を伝達ｉ！
ヂ、単にシール部材の役割を果す。ヘッドガスケット１
２と可撓性シール１７．１８は一体に結合した方が、組
付け、取扱い性の面で好ましい。This flexible seal 18 also transmits the head bolt tightening force i!
It simply serves as a sealing member. head gasket 1
2 and the flexible seals 17, 18 are preferably combined together in terms of ease of assembly and handling.
第１図は本発明によるヘッドガスケット構造を示す縦断
面図、第２図は第１図中の部分拡大図、第３図は別の実
施例を示すための第２図に対応する図面、第４図は従来
構造を承り縦断面部分図、第５図は従来の改良案を示す
縦断面図である。１・・・シリンダブ【１ツク、２・・
・ライナ、３・・・シリンダヘッド、４・・・フランジ
部、８・・・ガス正量圧面、９・・・隙間、１２・・・
ヘッドガスケット、１７・・・可撓性シール、Ａ３・・
・ガス圧、Ｂ３・・・ヘッドボルト締付力、Ｄ２・・・
ライナ本体外径、Ｄ８・・・ガス斤量圧面外径
特許出願人 ヤンマーディーゼル株式会社代理人
弁理士 大食忠孝（１″−づ二１
一′−二（FIG. 1 is a longitudinal sectional view showing a head gasket structure according to the present invention, FIG. 2 is a partially enlarged view of FIG. 1, FIG. 3 is a drawing corresponding to FIG. 2 for showing another embodiment, and FIG. FIG. 4 is a partial vertical cross-sectional view of the conventional structure, and FIG. 5 is a vertical cross-sectional view showing an improved conventional structure. 1...Cylinder tab [1 tsuk, 2...
・Liner, 3... Cylinder head, 4... Flange part, 8... Gas positive pressure surface, 9... Gap, 12...
Head gasket, 17...Flexible seal, A3...
・Gas pressure, B3...Head bolt tightening force, D2...
Liner body outer diameter, D8...Gas weight pressure surface outer diameter Patent applicant Yanmar Diesel Co., Ltd. Agent
Patent attorney Tadataka Oshiki (1″-zu21 1′-2)
Claims (5)
支持されるフランジ部を設け、ライナ本体上端のガス圧
受圧面とシリンダヘッドの間に隙間を設け、フランジ部
上面とシリンダヘッドの間にヘッドガスケットを介装し
、フランジ部上面にヘッドガスケットを介してヘッドボ
ルト締付力を及ぼすものにおいて、ライナのガス圧受圧
面の外径をライナ本体の外径より減して作用するガス圧
を減し、ヘッドガスケットの内周側路半分をヘッドボル
ト締付力を支持しない可撓性シールで形成してヘッドボ
ルト締付力の作用点を外周側へ寄せたことを特徴とする
シリンダヘッドガスケット構造。(1) A flange portion whose lower surface is supported by the cylinder block is provided on the outer periphery of the upper end of the liner, a gap is provided between the gas pressure receiving surface at the upper end of the liner body and the cylinder head, and a gap is provided between the upper surface of the flange portion and the cylinder head. In the case where a gasket is installed and the head bolt tightening force is applied to the upper surface of the flange part through the head gasket, the outer diameter of the gas pressure receiving surface of the liner is made smaller than the outer diameter of the liner body to reduce the acting gas pressure. A cylinder head gasket structure characterized in that half of the inner circumferential side path of the head gasket is formed with a flexible seal that does not support the head bolt tightening force, so that the point of action of the head bolt tightening force is moved toward the outer circumferential side. .
り階段状に低くされている特許請求の範囲第１項記載の
シリンダヘッドガスケット構造。(2) The cylinder head gasket structure according to claim 1, wherein the upper surface of the liner flange portion is stepped lower than the gas pressure receiving surface of the liner.
切欠きが設けてある特許請求の範囲第１項記載のシリン
ダヘッドガスケット構造。(3) The cylinder head gasket structure according to claim 1, wherein an R-shaped notch is provided between the lower surface of the flange and the outer peripheral surface of the liner body.
の範囲第１項記載のシリンダヘッドガスケット構造。(4) The cylinder head gasket structure according to claim 1, wherein the flexible seal has a laterally opening U-shaped cross section.
第１項記載のシリンダヘッドガスケット構造。(5) The cylinder head gasket structure according to claim 1, wherein the flexible seal has a corrugated cross section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5276185A JPS61210252A (en) | 1985-03-15 | 1985-03-15 | Cylinder head gasket structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5276185A JPS61210252A (en) | 1985-03-15 | 1985-03-15 | Cylinder head gasket structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61210252A true JPS61210252A (en) | 1986-09-18 |
Family
ID=12923859
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5276185A Pending JPS61210252A (en) | 1985-03-15 | 1985-03-15 | Cylinder head gasket structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61210252A (en) |
-
1985
- 1985-03-15 JP JP5276185A patent/JPS61210252A/en active Pending
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