JPH0584389B2 - - Google Patents
Info
- Publication number
- JPH0584389B2 JPH0584389B2 JP11815584A JP11815584A JPH0584389B2 JP H0584389 B2 JPH0584389 B2 JP H0584389B2 JP 11815584 A JP11815584 A JP 11815584A JP 11815584 A JP11815584 A JP 11815584A JP H0584389 B2 JPH0584389 B2 JP H0584389B2
- Authority
- JP
- Japan
- Prior art keywords
- gasket
- cylinder
- cylinder block
- cylinder head
- plate
- 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
- 238000007789 sealing Methods 0.000 claims description 9
- 229910052751 metal Inorganic materials 0.000 claims description 7
- 239000002184 metal Substances 0.000 claims description 7
- 238000002485 combustion reaction Methods 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 229910000838 Al alloy Inorganic materials 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 229910001018 Cast iron Inorganic materials 0.000 description 3
- 238000004891 communication Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 238000003780 insertion Methods 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000001771 impaired effect Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 239000010425 asbestos Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 229910052895 riebeckite Inorganic materials 0.000 description 1
- 230000002000 scavenging effect Effects 0.000 description 1
- 238000010008 shearing 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
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
- F16J15/12—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering
- F16J15/121—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering with metal reinforcement
- F16J15/122—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering with metal reinforcement generally parallel to the surfaces
- F16J15/123—Details relating to the edges of the packing
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gasket Seals (AREA)
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明はシリンダブロツクとシリンダヘツドと
の間をシールする金属製のガスケツトに関する。DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a metal gasket for sealing between a cylinder block and a cylinder head.
一般に、エンジンのシリンダブロツクとシリン
ダヘツドとは、第８図ａに示したように、そのシ
リンダブロツク１とシリンダヘツド２との衝合面
にガスケツト３を挟み込み、ボルトで以て結合し
ている。
Generally, the cylinder block and cylinder head of an engine are connected with bolts, with a gasket 3 sandwiched between the abutting surfaces of the cylinder block 1 and cylinder head 2, as shown in FIG. 8a.
ところで、この種のガスケツト３には高い耐熱
性が要求されるが、特に高出力形のエンジンやタ
ーボ過給機付きのエンジンでは、通常のアスベス
ト系のガスケツトに代わつて、例えば２枚のアウ
タプレート４ａ，４ｂ間にインナプレート４ｃを
挟み込んでなる多段重ねのメタルガスケツト３が
用いられている。このメタルガスケツト３のアウ
タプレート４ａ，４ｂには、シリンダ５の周囲を
周方向に連続して取囲む突状部６，６が一体にプ
レス成形されており、このメタルガスケツト３を
シリンダブロツク１とシリンダヘツド２との間で
挟圧すると、上記突状部６，６が弾性的に押し潰
されてシリンダブロツク１とシリンダヘツド２の
衝合面およびインナプレート４ｃに密着し、これ
らの間をシールするようになつている。 By the way, this type of gasket 3 is required to have high heat resistance, but especially in high-output engines or engines with a turbo supercharger, for example, two outer plates are used instead of the usual asbestos-based gasket. A multi-stage metal gasket 3 is used in which an inner plate 4c is sandwiched between 4a and 4b. The outer plates 4a, 4b of the metal gasket 3 are integrally press-molded with protrusions 6, 6 that continuously surround the cylinder 5 in the circumferential direction, and the metal gasket 3 is attached to the cylinder block. When pressed between the cylinder block 1 and the cylinder head 2, the protrusions 6, 6 are elastically crushed and come into close contact with the abutting surfaces of the cylinder block 1 and the cylinder head 2 and the inner plate 4c. It is designed to seal.
一方、シリンダブロツク１やシリンダヘツド２
をアルミ合金製としたエンジンにおいては、シリ
ンダ５の耐摩耗性を高めるため、シリンダ５内に
鋳鉄製のスリーブ７を圧入することが行なわれて
いる。 On the other hand, cylinder block 1 and cylinder head 2
In engines whose cylinders are made of aluminum alloy, a sleeve 7 made of cast iron is press-fitted into the cylinder 5 in order to improve the wear resistance of the cylinder 5.
ところがこの場合、シリンダ５が高温となる
と、アルミ合金の熱膨張率の方が鋳鉄の熱膨張率
よりも大きいので、上記第８図ａに示したように
シリンダ５とスリーブ７との間にずれが生じ、シ
リンダ５のシリンダヘツド２側の端部に段差Ｈが
形成されることがある。そうすると、アウタプレ
ート４ｂのシリンダボアＢに臨む開口周辺部が、
シリンダブロツク１とシリンダヘツド２との間で
挟み込まれなくなつて自由状態となるため、爆発
圧力を受けて繰返し振れ動いてしまい、この結
果、アウタプレート４ｂの開口周辺部が疲労し易
くなる。しかも、この疲労に加えて上記シリンダ
ブロツク１の開口端には尖つた角部が形成される
ので、この角部との接触によりアウタプレート４
ｂの開口周辺部には剪断力が作用することにな
り、したがつて、アウタプレート４ｂの開口周辺
部にクラツクが生じたり、第８図ｂに示したよう
に開口周辺部がリング状に分断されてしまう等の
不具合があつた。 However, in this case, when the cylinder 5 becomes high temperature, the coefficient of thermal expansion of aluminum alloy is larger than that of cast iron, so there is a misalignment between the cylinder 5 and the sleeve 7 as shown in Fig. 8a above. This may cause a step H to be formed at the end of the cylinder 5 on the cylinder head 2 side. Then, the peripheral part of the opening of the outer plate 4b facing the cylinder bore B is
Since it is no longer pinched between the cylinder block 1 and the cylinder head 2 and is in a free state, it repeatedly shakes under the explosion pressure, and as a result, the area around the opening of the outer plate 4b becomes easily fatigued. Moreover, in addition to this fatigue, since a sharp corner is formed at the open end of the cylinder block 1, contact with this corner causes the outer plate 4 to
A shearing force will be applied to the area around the opening of the outer plate 4b, and as a result, cracks may occur around the opening of the outer plate 4b, or the area around the opening may be divided into a ring shape as shown in FIG. 8b. There were problems such as being deleted.
なお、この対策として、アウタプレート４ｂの
肉厚を厚くすることが考えられるが、このように
すると肉厚が厚くなつた分、突状部６，６が弾性
変形し難くなるので、開口周辺部の破損は少なく
なるものの、本来のシール機能が損われてしまう
欠点がある。また、その他の対策として、アウタ
プレート４ａ，４ｂおよびインナプレート４ｃ全
ての開口径をシリンダ５の内径と同等にまで大き
くすることも考えられるが、この場合には開口径
が大きくなつた分だけ燃焼室の内容積が増すこと
になるので、圧縮比が変動する等、エンジン性能
に悪影響を及ぼす不具合があり、実用には供し得
ないものであつた。 As a countermeasure for this, it is possible to increase the wall thickness of the outer plate 4b, but if this is done, the protrusions 6, 6 will be less likely to be elastically deformed due to the increased wall thickness. Although this reduces the chance of damage, the disadvantage is that the original sealing function is impaired. In addition, as another countermeasure, it is possible to increase the opening diameters of all the outer plates 4a, 4b and the inner plate 4c to be equal to the inner diameter of the cylinder 5, but in this case, the combustion Since the internal volume of the chamber would increase, there would be problems such as fluctuations in the compression ratio, which would adversely affect engine performance, and it could not be put to practical use.
本発明はこのような事情にもとずいてなされた
もので、シール機能やエンジン性能を何等損なう
ことなく、ガスケツト板のボアに臨む開口周辺部
の破損を防止できるエンジンのシリンダヘツド用
ガスケツトの提供を目的とする。
The present invention has been made based on the above circumstances, and provides a gasket for an engine cylinder head that can prevent damage to the area around the opening facing the bore of the gasket plate without impairing the sealing function or engine performance. With the goal.
［発明の概要］
すなわち、本発明は上記目的を達成するため、
シリンダブロツクとシリンダヘツドとの間で挾圧
されるガスケツトを、リング状をなす複数枚のガ
スケツト板を同軸状に重ね合わせて構成するに当
り、
上記ガスケツト板のうち、シリンダブロツク側
に位置されたガスケツト板のボアに臨む開口径
を、シリンダの内径と略同一に設定し、このガス
ケツト板の開口径を、他のガスケツト板のボアに
臨む開口径よりも大きく形成したことを特徴とし
ている。[Summary of the invention] That is, in order to achieve the above object, the present invention
When constructing the gasket that is pressed between the cylinder block and the cylinder head by coaxially stacking a plurality of ring-shaped gasket plates, one of the gasket plates is placed on the cylinder block side. The opening diameter of the gasket plate facing the bore is set to be approximately the same as the inner diameter of the cylinder, and the opening diameter of this gasket plate is made larger than the opening diameter of the other gasket plates facing the bore.
以下本発明の一実施例を、２サイクルエンジン
に適用した第１図ないし第７図にもとずいて説明
する。
An embodiment of the present invention will be described below with reference to FIGS. 1 to 7, in which the present invention is applied to a two-stroke engine.
第１図中１１はアルミ合金製のシリンダブロツ
クであり、そのシリンダ１２内には上記アルミ合
金よりも熱膨張率の小さい鋳鉄製のスリーブ１３
（ライナーとも称する）が圧入されている。そし
て、スリーブ１３の内面にはピストン１４によつ
て開閉される吸気孔１５、掃気孔１６，１６およ
び図示しない排気孔が開設されている。シリンダ
ブロツク１１の先端面にはシリンダヘツド１７が
被嵌され、かつボルト１８およびナツト１９を介
して結合されており、このシリンダヘツド１７と
ピストンヘツドとの間に燃焼室２０が形成されて
いるとともに、シリンダブロツク１１とシリンダ
ヘツド１７内には、シリンダ１２および燃焼室２
０の周囲を取囲むウオータジヤケツト２１が形成
されている。なお、シリンダヘツド１７には、ウ
オータジヤケツト２１内を流れる冷却水の流出口
２２が設けられている。 Reference numeral 11 in FIG. 1 is a cylinder block made of aluminum alloy, and inside the cylinder 12 is a sleeve 13 made of cast iron whose coefficient of thermal expansion is smaller than that of the aluminum alloy.
(also called liner) is press-fitted. The inner surface of the sleeve 13 is provided with an intake hole 15, scavenging holes 16, 16, and an exhaust hole (not shown), which are opened and closed by the piston 14. A cylinder head 17 is fitted onto the front end surface of the cylinder block 11 and connected via bolts 18 and nuts 19, and a combustion chamber 20 is formed between the cylinder head 17 and the piston head. , inside the cylinder block 11 and cylinder head 17 are a cylinder 12 and a combustion chamber 2.
A water jacket 21 surrounding the periphery of the water jacket 2 is formed. Incidentally, the cylinder head 17 is provided with an outlet 22 for cooling water flowing inside the water jacket 21.
ところで、シリンダブロツク１１とシリンダヘ
ツド１７との間には、本発明に係るメタル製のガ
スケツト２３が挟み込まれている。このガスケツ
ト２３は第１図および第４図に示したように、略
リング状をなした３枚のガスケツト板を重ね合わ
せる、つまり２枚の薄肉なアウタプレート２４
ａ，２４ｂ間に、厚肉なインナプレート２５を同
軸的に挟み込んで保持したガスケツト組立体２３
ａを備えている。このガスケツト組立体２３ａの
中央部には、スリーブ１３のボアＢに対応したく
り抜き孔２６が開設されている。そして、アウタ
プレート２４ａ，２４ｂには、スリーブ１３のボ
アＢの周囲を周方向に連続して取囲む突状部２７
ａ，２７ｂが一体にプレス形成されており、これ
ら突状部２７ａ，２７ｂはインナプレート２５側
に向つて所定高さ張出している。したがつて、ア
ウタプレート２４ａ，２４ｂとインナプレート２
５との間には周方向に連続する隙間２８が形成さ
れており、ガスケツト２３の厚み方向に弾性変形
可能となつている。このアウタプレート２４ａ，
２４ｂのうち、シリンダブロツク１１側のアウタ
プレート２４ｂの内径、つまりボアＢに臨む開口
径L1は、その他のアウタプレート２４ａやイン
ナプレート２５の開口径L2，L3よりも大きく形
成され、この開口径Ｌ１はシリンダ１２の内径と
略同等に設定されている。このため、アウタプレ
ート２４ｂの開口内周縁は、シリンダ１２とスリ
ーブ１３との境界部分に位置されて、ボアＢの内
周面よりも径方向外側に引つ込んだ状態に保持さ
れている。 Incidentally, a metal gasket 23 according to the present invention is sandwiched between the cylinder block 11 and the cylinder head 17. As shown in FIGS. 1 and 4, this gasket 23 consists of three substantially ring-shaped gasket plates superimposed, that is, two thin outer plates 24.
A gasket assembly 23 in which a thick inner plate 25 is coaxially held between a and 24b.
It is equipped with a. A hollow hole 26 corresponding to the bore B of the sleeve 13 is formed in the center of the gasket assembly 23a. The outer plates 24a and 24b have a protrusion 27 that continuously surrounds the bore B of the sleeve 13 in the circumferential direction.
a and 27b are integrally press-formed, and these protruding portions 27a and 27b protrude toward the inner plate 25 side by a predetermined height. Therefore, the outer plates 24a, 24b and the inner plate 2
A circumferentially continuous gap 28 is formed between the gasket 23 and the gasket 23, so that the gasket 23 can be elastically deformed in the thickness direction. This outer plate 24a,
24b, the inner diameter of the outer plate 24b on the cylinder block 11 side, that is, the opening diameter L 1 facing the bore B, is formed larger than the opening diameters L 2 and L 3 of the other outer plates 24a and the inner plates 25. The opening diameter L1 is set to be approximately equal to the inner diameter of the cylinder 12. Therefore, the inner circumferential edge of the opening of the outer plate 24b is located at the boundary between the cylinder 12 and the sleeve 13, and is held in a retracted position radially outward from the inner circumferential surface of the bore B.
このようなアウタプレート２４ａ，２４ｂに
は、シリンダブロツク１１とシリンダヘツド１７
内のウオータジヤケツト２１を連通させる複数の
連通孔２９……が周方向に間隔を存して開設され
ているとともに、これら連通孔２９……間に位置
して上記ボルト１９……が挿通される挿通孔３０
……か開設されている。また、アウタプレート２
４ａ，２４ｂには連通孔２９……および挿通孔３
０……の周囲を取囲むようにして、上記隙間２８
を減じる方向に傾斜された斜面部３１ａ，３１ｂ
が形成されており、本実施例の斜面部３１ａ，３
１ｂは、第５図ないし第７図に示したように必要
とするシール性能に応じてその傾斜幅ｌが変化さ
れている。すなわち、上記ウオータジヤケツト２
８に連なる流出口２２が位置する一定の範囲ａ内
では、この流出口２２の存在によつてボルト１８
の締付け力が弱くなり、その分大きなシール性能
を必要とするので、上記斜面部３１ａ，３１ｂは
その傾斜幅ｌが短い急斜面に形成され、シリンダ
ヘツド１７とシリンダブロツク１１との間で挟圧
された際に、大きな弾性力が得られるようになつ
ている。また、逆に挿通孔３０……の周囲のよう
にボルト１８の締付け力が充分に伝えられてそれ
程大きいなシール性能を必要としない部分では、
斜面部３１ａ，３１ｂが緩斜面に形成されてい
る。 The cylinder block 11 and the cylinder head 17 are attached to such outer plates 24a and 24b.
A plurality of communication holes 29 are provided at intervals in the circumferential direction for communicating the water jackets 21 inside, and the bolts 19 are inserted between the communication holes 29. insertion hole 30
...or has been established. Also, outer plate 2
4a, 24b have communication holes 29... and insertion holes 3.
The gap 28 is arranged so as to surround the periphery of 0...
Slope portions 31a, 31b inclined in a direction that reduces
are formed, and the slope portions 31a, 3 of this embodiment
As shown in FIGS. 5 to 7, the slope width l of 1b is varied depending on the required sealing performance. That is, the water jacket 2
Within a certain range a where the outlet 22 connected to the bolt 18 is located, the presence of the outlet 22 causes the bolt 18
Since the tightening force of the cylinder head 17 and the cylinder block 11 becomes weaker and a greater sealing performance is required accordingly, the slope portions 31a and 31b are formed into steep slopes with a short slope width l, and are pressed between the cylinder head 17 and the cylinder block 11. It is designed to provide a large amount of elastic force when Conversely, in areas where the tightening force of the bolt 18 is sufficiently transmitted and does not require such a large sealing performance, such as around the insertion hole 30...
The slope portions 31a and 31b are formed into gentle slopes.
このような構成によれば、アウタプレート２４
ｂのボアＢに臨む開口径Ｌ１を、シリンダ１２の
内径と略同等に設定し、このアウタプレート２４
ｂの開口内周縁部をシリンダ１２とスリーブ１３
との境界部分に位置させたので、シリンダ１２と
スリーブ１３との熱膨張率の相違により、シリン
ダ１２のヘツド側に段差Ｈが生じた場合でも、ア
ウタプレート２４ｂの開口周辺部が上記段差Ｈ部
分に張出することはなく、このためガスケツト１
３は常にシリンダブロツク１１とシリンダヘツド
１７との間に挟持された状態に保たれる。したが
つて、アウタプレート２４ｂの開口周辺部が繰返
し振り動かされることもないから、この開口周辺
部の疲労による破損を未然に防止することができ
る。 According to such a configuration, the outer plate 24
The opening diameter L1 facing the bore B of b is set to be approximately equal to the inner diameter of the cylinder 12, and this outer plate 24
The inner peripheral edge of the opening of b is connected to the cylinder 12 and the sleeve 13.
Since the outer plate 24b is located at the boundary between the cylinder 12 and the sleeve 13, even if a step H occurs on the head side of the cylinder 12 due to a difference in thermal expansion coefficient between the cylinder 12 and the sleeve 13, the peripheral part of the opening of the outer plate 24b will be located at the step H. Therefore, gasket 1
3 is always held between the cylinder block 11 and the cylinder head 17. Therefore, since the area around the opening of the outer plate 24b is not repeatedly shaken, damage to the area around the opening due to fatigue can be prevented.
しかも、アウタプレート２４ｂの肉厚を厚くす
る必要もないので、突状部２７ａ，２７ｂのばね
効果、つまりシリンダブロツク１１，シリンダヘ
ツド１７およびインナプレート２５に対する密着
性が損われることもなく、本体のシール機能を長
期に亙つて持続させることができる。それととも
に、ヘツド側のアウタプレート２４ａやインナプ
レート２５の開口周縁は、ボアＢに臨んでいるか
ら、燃焼室２０の容積変化を極めて少なく抑える
ことができ、エンジン性能に悪影響を及ぼすこと
もない等の利点がある。 Moreover, since there is no need to increase the thickness of the outer plate 24b, the spring effect of the protrusions 27a and 27b, that is, the adhesion to the cylinder block 11, cylinder head 17, and inner plate 25, is not impaired, and the main body The sealing function can be maintained for a long period of time. At the same time, since the opening edges of the outer plate 24a and the inner plate 25 on the head side face the bore B, changes in the volume of the combustion chamber 20 can be kept to an extremely small level, and there will be no negative impact on engine performance. There are advantages.
なお、本発明に係るエンジンは、２サイクルエ
ンジンに限らず４サイクルエンジンであつても良
いとともに、冷却方式も水冷に制約されず、空冷
であつても何等差し支えない。 Note that the engine according to the present invention is not limited to a 2-stroke engine, but may be a 4-stroke engine, and the cooling method is not limited to water cooling, and air cooling may also be used.
また、ガスケツト板の積層枚数も３枚に限定さ
れるものではなく、例えば５枚あるいは７枚であ
つても良い。 Further, the number of stacked gasket plates is not limited to three, but may be five or seven, for example.
以上詳述した本発明によれば、シリンダブロツ
ク側に位置されたガスケツト板のボアに臨む開口
径を、シリンダの内径と略同一に設定し、このガ
スケツト板の開口径を、他のガスケツト板のボア
に臨む開口径よりも大きく形成したので、シリン
ダとスリーブとの熱膨張率の相違によりシリンダ
のヘツド側に段差が生じた場合でも、ガスケツト
板の開口周辺部が上記段差部分に張出すこともな
く、このためガスケツトは常にシリンダブロツク
とシリンダヘツドとの間に挟持された状態に保た
れる。したがつて、ガスケツト板の開口周辺部が
繰返し振り動かされることもないから、疲労によ
る破損を未然に防止することができる。しかもこ
の構成によれば、ガスケツト板の肉厚を厚くした
り全てのガスケツト板の開口径を大きくする必要
もないので、突状部のばね効果、つまりシリンダ
ブロツク、シリンダヘツドおよび中間のガスケツ
ト板に対する密着性が損われることもなく、従来
のシール機能を長期に亙つて持続させることがで
きるとともに、燃焼室の容積変化に伴う圧縮比の
変動を極力少なく抑えることができ、エンジン性
能に悪影響を及ぼすこともない等の利点がある。
According to the present invention described in detail above, the opening diameter facing the bore of the gasket plate located on the cylinder block side is set to be approximately the same as the inner diameter of the cylinder, and the opening diameter of this gasket plate is set to be the same as that of the other gasket plates. Since the diameter of the opening facing the bore is larger than that of the opening, even if a step occurs on the head side of the cylinder due to the difference in thermal expansion coefficient between the cylinder and the sleeve, the area around the opening of the gasket plate will not overhang the step. Therefore, the gasket is always held between the cylinder block and the cylinder head. Therefore, since the area around the opening of the gasket plate is not repeatedly shaken, damage due to fatigue can be prevented. Moreover, according to this configuration, there is no need to increase the thickness of the gasket plate or to increase the opening diameter of all gasket plates, so the spring effect of the protrusion, that is, the spring effect on the cylinder block, cylinder head, and intermediate gasket plate, is The conventional sealing function can be maintained for a long period of time without loss of adhesion, and fluctuations in the compression ratio due to changes in combustion chamber volume can be minimized, which has no negative impact on engine performance. There are advantages such as no problems.
第１図ないし第７図は本発明の一実施例を示
し、第１図は第２図中部の拡大断面図、第２図
は２サイクルエンジンの断面図、第３図はガスケ
ツトの平面図、第４図は第３図中−線に沿う
断面図、第５図は第３図中−線に沿う断面
図、第６図は第３図中−線に沿う断面図、第
７図は第３図中−線に沿う断面図、第８図ａ
およびｂはそれぞれ本発明の技術的背景を示す断
面図である。
１１……シリンダブロツク、１２……シリン
ダ、１３……スリーブ、１７……シリンダヘツ
ド、２３……ガスケツト、２３ａ……ガスケツト
組立体、２４ａ，２４ｂ，２５……ガスケツト板
（アウタプレート、インナプレート）、２７ａ，２
７ｂ……突状部、Ｂ……ボア。
1 to 7 show one embodiment of the present invention, FIG. 1 is an enlarged sectional view of the middle part of FIG. 2, FIG. 2 is a sectional view of a two-cycle engine, and FIG. 3 is a plan view of a gasket. 4 is a sectional view taken along the line - in FIG. 3, FIG. 5 is a sectional view taken along the line - in FIG. 3, FIG. 6 is a sectional view taken along the line - in FIG. Figure 3 - cross-sectional view along the line, Figure 8a
and b are cross-sectional views showing the technical background of the present invention, respectively. 11... Cylinder block, 12... Cylinder, 13... Sleeve, 17... Cylinder head, 23... Gasket, 23a... Gasket assembly, 24a, 24b, 25... Gasket plate (outer plate, inner plate) , 27a, 2
7b... protrusion, B... bore.
Claims (1)
が小さい他の金属製のスリーブを挿入してなるシ
リンダブロツクと、このシリンダブロツクに連結
されたシリンダヘツドとの間に、リング状をなす
複数枚の金属製ガスケツト板を同軸状に重ね合わ
せてなるガスケツト組立体を介装し、 このガスケツト組立体の少なくとも両外側のガ
スケツト板には、上記スリーブのボアの周囲を周
方向に連続して取囲む突状部を一体に設け、 この突状部を上記シリンダブロツクとシリンダ
ヘツドとの間で挾圧して弾性変形させることによ
り、シリンダブロツクとシリンダヘツドとの間を
シールするようにしたガスケツトにおいて、 上記ガスケツト板のうち、シリンダブロツク側
に位置されたガスケツト板のボアに臨む開口径
を、上記シリンダの内径と略同一に設定し、 このガスケツト板の開口径を、他のガスケツト
板のボアに臨む開口径よりも大きく形成したこと
を特徴とするエンジンのシリンダヘツド用ガスケ
ツト。[Scope of Claims] 1. A ring is provided between a cylinder block formed by inserting a sleeve made of another metal with a coefficient of thermal expansion smaller than that of the cylinder into the cylinder, and a cylinder head connected to this cylinder block. A gasket assembly is interposed in which a plurality of metal gasket plates having a shape are coaxially stacked, and at least the outer gasket plates on both sides of the gasket assembly are provided with a circumferential groove around the bore of the sleeve. A continuous surrounding protrusion is integrally provided, and this protrusion is pressed between the cylinder block and the cylinder head to elastically deform it, thereby sealing the gap between the cylinder block and the cylinder head. In the gasket, the opening diameter of the gasket plate facing the bore of the gasket plate located on the cylinder block side is set to be approximately the same as the inner diameter of the cylinder, and the opening diameter of this gasket plate is set to be the same as that of the other gasket plate. A gasket for an engine cylinder head, characterized in that the opening diameter is larger than the opening diameter facing the bore of the engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11815584A JPS60261960A (en) | 1984-06-11 | 1984-06-11 | Gasket for engine cylinder head |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11815584A JPS60261960A (en) | 1984-06-11 | 1984-06-11 | Gasket for engine cylinder head |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60261960A JPS60261960A (en) | 1985-12-25 |
| JPH0584389B2 true JPH0584389B2 (en) | 1993-12-01 |
Family
ID=14729454
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11815584A Granted JPS60261960A (en) | 1984-06-11 | 1984-06-11 | Gasket for engine cylinder head |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60261960A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8887537B2 (en) | 2002-12-27 | 2014-11-18 | Lg Electronics Inc. | Drum-type washing machine |
| US8887538B2 (en) | 2004-07-20 | 2014-11-18 | Lg Electronics Inc. | Drum-type washing machine and bearing housing structure thereof |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5277434A (en) * | 1992-09-11 | 1994-01-11 | Dana Corporation | Multiple layer cylinder head gasket |
-
1984
- 1984-06-11 JP JP11815584A patent/JPS60261960A/en active Granted
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8887537B2 (en) | 2002-12-27 | 2014-11-18 | Lg Electronics Inc. | Drum-type washing machine |
| US8887538B2 (en) | 2004-07-20 | 2014-11-18 | Lg Electronics Inc. | Drum-type washing machine and bearing housing structure thereof |
| US8931312B2 (en) | 2004-07-20 | 2015-01-13 | Lg Electronics Inc. | Drum-type washing machine and bearing housing structure thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60261960A (en) | 1985-12-25 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |