JP5613730B2 - Engine combustion chamber structure - Google Patents
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- JP5613730B2 JP5613730B2 JP2012161825A JP2012161825A JP5613730B2 JP 5613730 B2 JP5613730 B2 JP 5613730B2 JP 2012161825 A JP2012161825 A JP 2012161825A JP 2012161825 A JP2012161825 A JP 2012161825A JP 5613730 B2 JP5613730 B2 JP 5613730B2
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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Description
この発明は、エンジンの燃焼室の構造に関する。 The present invention relates to a structure of a combustion chamber of an engine.
エンジンの燃焼室に関して従来から種々の構造が提案されている。たとえば特許文献１には副燃焼室を有する燃焼室構造が開示されている。 Various structures have been proposed for engine combustion chambers. For example, Patent Document 1 discloses a combustion chamber structure having a sub-combustion chamber.
しかし、前述した従来構造では、副燃焼室での燃焼が主燃焼室の外部で燃焼する外燃機関となってしまう。そのため冷却による損失エネルギーが大きく、熱効率が低いという問題があった。 However, in the above-described conventional structure, the combustion in the auxiliary combustion chamber becomes an external combustion engine that burns outside the main combustion chamber. For this reason, there is a problem that energy loss due to cooling is large and thermal efficiency is low.
本発明は、このような従来の問題点に着目してなされたものであり、高い熱効率を得ることができるエンジンの燃焼室構造を提供することを目的とする。 The present invention has been made paying attention to such a conventional problem, and an object of the present invention is to provide an engine combustion chamber structure capable of obtaining high thermal efficiency.
本発明は以下のような解決手段によって前記課題を解決する。なお、理解を容易にするために本発明の実施形態に対応する符号を付するが、これに限定されるものではない。 The present invention solves the above problems by the following means. In addition, in order to make an understanding easy, although the code | symbol corresponding to embodiment of this invention is attached | subjected, it is not limited to this.
本発明は、混合気を燃焼するエンジンの燃焼室構造であって、前記混合気に着火する点火プラグ(３０)と、エンジンの燃焼室の外周に形成され、燃焼室のスキッシュエリアではない領域に開口し、その開口径のまま筒状に延びて、開口(１１ａ)の反対端を閉塞する底(１１ｃ)を含み、軸線が燃焼室の半径方向に一致して前記点火プラグから伝播する火炎の進行方向と交叉するようにのみ設けられ、火炎の進行波が通過することによって燃焼した開口近傍の混合気の熱膨張による圧力波の跳ね返りによって前記開口からガスを噴出する筒穴部(１１)と、を有する、ことを特徴とする。 The present invention relates to a combustion chamber structure for an engine that burns an air-fuel mixture, and an ignition plug (30) that ignites the air-fuel mixture and an outer periphery of the combustion chamber of the engine that is not a squish area of the combustion chamber. A flame that propagates from the spark plug with an opening , including a bottom (11c ) that extends in a cylindrical shape with the diameter of the opening and closes the opposite end of the opening (11a), and whose axis coincides with the radial direction of the combustion chamber . A cylindrical hole portion (11) which is provided only to cross the traveling direction and ejects gas from the opening by the rebound of the pressure wave due to the thermal expansion of the air-fuel mixture in the vicinity of the opening burned by the passage of the traveling wave of the flame; It is characterized by having.
本発明によれば、着火された混合気の火炎が開口に伝播し通り過ぎると、開口から高速ガスが噴出し燃焼室内の未燃ガスの拡散を促進する。これによって筒内での燃焼速度が速くなり熱効率が高くなる。 According to the present invention, when the flame of the ignited air-fuel mixture passes through the opening, high-speed gas is ejected from the opening and promotes diffusion of unburned gas in the combustion chamber. This increases the combustion rate in the cylinder and increases the thermal efficiency.
以下では図面等を参照して本発明を実施するための最良の形態について説明する。
（第１実施形態）
図１は、本発明によるエンジンの燃焼室構造の第１実施形態を示す図であり、図１(Ａ)は上方から燃焼室を透視した図、図１(Ｂ)は側方から燃焼室を透視した図である。
Hereinafter, the best mode for carrying out the present invention will be described with reference to the drawings.
(First embodiment)
FIG. 1 is a diagram showing a first embodiment of a combustion chamber structure of an engine according to the present invention. FIG. 1 (A) is a perspective view of the combustion chamber from above, and FIG. FIG.
エンジンの燃焼室１０は、本実施形態ではいわゆるペントルーフタイプが例示されている。ペントルーフ稜線には天井点火プラグ３０が設けられる。ペントルーフ稜線を挟んで一方のルーフ(図１では右側のルーフ)には吸気バルブ３１が設けられる。ペントルーフ稜線を挟んで他方のルーフ(図１では左側のルーフ)には排気バルブ３２が設けられる。なおエンジンの当業者においては重力方向とは別に上死点／下死点という表現が使用される。水平対向エンジン等においては、必ずしも上死点が重力方向の上／下死点が重力方向の下になるとは限らないし、また仮にエンジンを倒立した場合には、上死点が重力方向の下／下死点が重力方向の上になるが、本明細書においては、慣習にしたがい、上死点側を上、下死点側を下、とし、燃焼室の上方をルーフと表現する。 The engine combustion chamber 10 is exemplified by a so-called pent roof type in the present embodiment. A ceiling spark plug 30 is provided on the pent roof ridgeline. An intake valve 31 is provided on one roof (the right roof in FIG. 1) across the pent roof ridgeline. An exhaust valve 32 is provided on the other roof (the left roof in FIG. 1) across the pent roof ridge line. Those skilled in the art of engine use the expression top dead center / bottom dead center separately from the direction of gravity. In a horizontally opposed engine or the like, the top dead center is not necessarily above the gravity direction / bottom dead center below the gravity direction. If the engine is inverted, the top dead center is below the gravity direction. Although the bottom dead center is above the gravitational direction, in the present specification, according to convention, the top dead center side is up, the bottom dead center side is down, and the top of the combustion chamber is expressed as a roof.
またエンジンの燃焼室１０の外周にはピストン冠面に平行に４つの筒穴部１１が形成される。筒穴部１１は、着火された混合気の火炎が伝播してくる位置に形成された開口１１ａと、その開口１１ａの反対端を閉塞する底１１ｃと、を含む。筒穴部１１の軸線Ａの方向は、燃焼室１０の半径方向である。このような配置になっているので、筒穴部１１の軸線Ａは、開口１１ａの中心１１ｂと点火部２５とを結んだ直線Ｂと交叉し、直線Ｂに一致しない。また筒穴部１１の直径ｄに対する深さＬの比Ｌ／ｄが６よりも大になるように、筒穴部１１の開口１１ａの穴径(直径)ｄ及び筒穴部１１の深さＬが設定される。たとえば筒穴部１１の開口１１ａの穴径(直径)ｄが１ｍｍであり、深さＬが１０ｍｍである。 Further, four cylindrical hole portions 11 are formed on the outer periphery of the combustion chamber 10 of the engine in parallel with the piston crown surface. The cylindrical hole portion 11 includes an opening 11a formed at a position where the flame of the ignited air-fuel mixture propagates, and a bottom 11c that closes the opposite end of the opening 11a. The direction of the axis A of the cylindrical hole portion 11 is the radial direction of the combustion chamber 10. With this arrangement, the axis A of the cylindrical hole portion 11 intersects with the straight line B connecting the center 11b of the opening 11a and the ignition portion 25 and does not coincide with the straight line B. Further, the hole diameter (diameter) d of the opening 11a of the tube hole 11 and the depth L of the tube hole 11 are set so that the ratio L / d of the depth L to the diameter d of the tube hole 11 is larger than 6. Is set. For example, the hole diameter (diameter) d of the opening 11a of the cylindrical hole portion 11 is 1 mm, and the depth L is 10 mm.
次に本実施形態の作用効果を図２〜図４を参照して説明する。なお図２は本実施形態の作用効果を理解しやすくするための基礎的な燃焼室構造を示す図である。 Next, the effect of this embodiment is demonstrated with reference to FIGS. FIG. 2 is a diagram showing a basic combustion chamber structure for facilitating understanding of the operational effects of the present embodiment.
図２に示した燃焼室１０では、外周にひとつの点火プラグ３０を設けた。図２では、ボア径８０ｍｍの燃焼室１０の左端に、点火プラグ３０を設けた。また燃焼室１０には、着火された混合気の火炎が伝播してくる位置の燃焼室内に開口し、反対端は閉塞する筒穴部１１を形成した。筒穴部１１の大きさは、穴径(直径)ｄが１ｍｍ、深さＬが１０ｍｍである。筒穴部１１の軸線Ａの方向は、燃焼室１０の半径方向である。このような配置になっているので、筒穴部１１の軸線Ａは、開口１１ａの中心１１ｂと点火プラグ３０とを結んだ直線Ｂと交叉し、直線Ｂに一致しない。 In the combustion chamber 10 shown in FIG. 2, one spark plug 30 is provided on the outer periphery. In FIG. 2, the spark plug 30 is provided at the left end of the combustion chamber 10 having a bore diameter of 80 mm. Further, the combustion chamber 10 is formed with a cylindrical hole portion 11 that opens into the combustion chamber at a position where the flame of the ignited air-fuel mixture propagates and closes at the opposite end. The cylinder hole 11 has a hole diameter (diameter) d of 1 mm and a depth L of 10 mm. The direction of the axis A of the cylindrical hole portion 11 is the radial direction of the combustion chamber 10. With this arrangement, the axis A of the tube hole 11 intersects the straight line B connecting the center 11b of the opening 11a and the spark plug 30, and does not coincide with the straight line B.
図３は、図２に示した燃焼室構造による実験結果を示す図であり、火炎の伝播状態を時間ごとに示してある。なお時間の経過につれて図３(Ａ)→図３(Ｌ)と進む。 FIG. 3 is a diagram showing an experimental result by the combustion chamber structure shown in FIG. 2, and shows a flame propagation state for each time. As time passes, the process proceeds from FIG. 3 (A) to FIG. 3 (L).
図３(Ａ)で燃焼室内の混合気が点火プラグ３０によって着火されると、着火点から火炎が急激に進行する。そして図３(Ｆ)で火炎の進行波が筒穴部１１の開口１１ａに到達し、筒穴部１１の開口１１ａを過ぎると、図３(Ｇ)から分かるように筒穴部１１の開口１１ａからガスが噴出する。次の瞬間である図３(Ｈ)を見ると、点火プラグ３０から始まる火炎の進行に比べて、筒穴部１１からのガスの噴出が非常に速いことが分かる。このガスによって燃焼室内の未燃ガスの拡散が促進され未燃ガスの火炎に対する接触面積が拡大する。そのため筒内での燃焼速度が速くなり熱効率を高くする作用効果が得られたのである。 When the air-fuel mixture in the combustion chamber is ignited by the spark plug 30 in FIG. 3A, the flame rapidly advances from the ignition point. Then, in FIG. 3 (F), when the traveling wave of the flame reaches the opening 11a of the cylindrical hole portion 11 and passes through the opening 11a of the cylindrical hole portion 11, the opening 11a of the cylindrical hole portion 11 is understood from FIG. 3 (G). Gas spouts out of. As shown in FIG. 3 (H), which is the next moment, it can be seen that the ejection of gas from the cylindrical hole portion 11 is much faster than the progress of the flame starting from the spark plug 30. This gas promotes the diffusion of the unburned gas in the combustion chamber and increases the contact area of the unburned gas with the flame. Therefore, the combustion speed in the cylinder is increased, and the effect of increasing the thermal efficiency is obtained.
図４は、筒穴部１１から非常に高速のガスが噴出する現象について説明する図である。 FIG. 4 is a diagram for explaining a phenomenon in which very high-speed gas is ejected from the cylindrical hole portion 11.
ガスの噴出現象の生じる理由について本件発明者らは以下のように考察した。 The present inventors considered the reason why the gas ejection phenomenon occurs as follows.
混合気が燃焼室内に存在する状態で点火プラグ３０が点火すると、図４(Ａ)に示すように火炎が進行する。なお火炎の進行波をＷ１〜Ｗ６で示す。そして火炎が筒穴部１１の開口１１ａに到達すると、開口近傍の混合気が燃焼する。混合気は燃焼すると熱膨張する。そして図４(Ｂ)に示すように熱膨張による圧力波が、筒穴部１１に存在する混合気(未燃ガス)を筒穴部１１の底１１ｃのほうへ押し込めるように作用する。すると筒穴部１１の底１１ｃにおいてガス圧力が非常に高圧になる。するとその圧力波の跳ね返りによって、筒穴部１１から非常に高速のガスが噴出することで、ガスの噴出現象が生じると考えられる。 When the spark plug 30 is ignited in a state where the air-fuel mixture exists in the combustion chamber, the flame proceeds as shown in FIG. The traveling wave of the flame is indicated by W1 to W6. When the flame reaches the opening 11a of the tube hole 11, the air-fuel mixture near the opening burns. When the air-fuel mixture burns, it expands thermally. Then, as shown in FIG. 4B, the pressure wave due to thermal expansion acts to push the air-fuel mixture (unburned gas) present in the tube hole portion 11 toward the bottom 11 c of the tube hole portion 11. Then, the gas pressure becomes very high at the bottom 11c of the cylindrical hole portion 11. Then, it is considered that a gas ejection phenomenon occurs when a very high-speed gas is ejected from the cylindrical hole portion 11 due to the rebound of the pressure wave.
なお詳細は省略するが、本件発明者らは、筒穴部１１の穴径ｄを変えても実験した。すると穴径ｄが１〜３ｍｍのときは高速ガスの噴出現象を確認できたが、穴径ｄが５ｍｍのときはガスの噴出現象が弱かった。これは穴径ｄが大きすぎたために、開口近傍で燃焼した混合気による圧力閉じ込め現象が生じにくかったためと考えられる。また穴径ｄが１ｍｍよりも小径であると火炎が筒穴部１１の内部に進行しにくく、この場合もガスの噴出現象が弱かった。したがってガスの噴出現象を得るには、適度な穴径にする必要があるということが本件発明者らによって知見された。 Although details are omitted, the present inventors also experimented even when the hole diameter d of the cylindrical hole portion 11 was changed. When the hole diameter d was 1 to 3 mm, the high-speed gas ejection phenomenon could be confirmed, but when the hole diameter d was 5 mm, the gas ejection phenomenon was weak. This is presumably because the pressure confinement phenomenon due to the air-fuel mixture burned in the vicinity of the opening was difficult to occur because the hole diameter d was too large. Further, when the hole diameter d is smaller than 1 mm, the flame hardly progresses into the cylindrical hole portion 11, and in this case, the gas ejection phenomenon is weak. Accordingly, the present inventors have found that it is necessary to set an appropriate hole diameter in order to obtain the gas ejection phenomenon.
また本件発明者らは、筒穴部１１の深さＬを変えても実験した。すると筒穴部１１の直径ｄに対する深さＬの比Ｌ／ｄが６よりも大であるときは高速ガスの噴出現象を確認できた。これに対して比Ｌ／ｄが６よりも小さいとガスの噴出現象が弱かった。これは深さＬが小さいと筒穴部１１に閉じ込められる圧力が小さいためであると考えられる。したがってガスの噴出現象を得るには、適度な深さＬにする必要があるということが本件発明者らによって知見された。 The inventors also experimented by changing the depth L of the tube hole 11. Then, when the ratio L / d of the depth L to the diameter d of the cylindrical hole portion 11 was larger than 6, the high-speed gas ejection phenomenon could be confirmed. On the other hand, when the ratio L / d was smaller than 6, the gas ejection phenomenon was weak. This is considered to be because when the depth L is small, the pressure confined in the cylindrical hole portion 11 is small. Therefore, the present inventors have found that an appropriate depth L is necessary to obtain the gas ejection phenomenon.
さらに本件発明者らは、筒穴部１１の位置を変えても実験した。すると筒穴部１１の軸線Ａが、開口１１ａの中心１１ｂと点火プラグ３０の飛火部分とを結んだ直線Ｂに一致する位置、たとえば筒穴部１１が点火プラグ３０に対向する位置では、ガスの噴出現象が弱まった。軸線Ａが直線Ｂに一致しては、点火プラグ３０からの進行波と、筒穴部１１からの噴出ガスと、がエネルギをお互いに相殺するためであると考えられる。したがって高速ガスの噴出現象を得るには、筒穴部１１を適切な位置にする必要があるということが本件発明者らによって知見された。 Further, the inventors also experimented even when the position of the cylindrical hole portion 11 was changed. Then, at a position where the axis A of the cylindrical hole portion 11 coincides with a straight line B connecting the center 11b of the opening 11a and the sparking portion of the spark plug 30, for example, at a position where the cylindrical hole portion 11 faces the spark plug 30, The eruption phenomenon has weakened. It is considered that the axis A coincides with the straight line B because the traveling wave from the spark plug 30 and the jet gas from the tube hole portion 11 cancel each other out of energy. Therefore, the present inventors have found that it is necessary to place the cylindrical hole portion 11 in an appropriate position in order to obtain the high-speed gas ejection phenomenon.
上記において燃焼室１０の外周にひとつの点火プラグ３０とひとつの筒穴部１１を設けた場合を例示して説明したが、燃焼室１０の天井に点火プラグ３０を設け、また燃焼室１０の周縁に複数の筒穴部１１を設けても同様の現象が生じる。そこで本実施形態では図１に示したように、燃焼室１０の天井に点火プラグ３０を設け、外周に４つの筒穴部１１を設けたのである。このようにすることで４つの筒穴部１１から高速ガスが噴出する。このガスによって燃焼室内の未燃ガスの拡散作用が促進され未燃ガスの火炎に対する接触面積が拡大する。そのため筒内での燃焼速度が速くなり熱効率を高くできたのである。 In the above description, the case where one ignition plug 30 and one cylinder hole 11 are provided on the outer periphery of the combustion chamber 10 has been described as an example. However, the ignition plug 30 is provided on the ceiling of the combustion chamber 10, and the periphery of the combustion chamber 10 is provided. The same phenomenon occurs even if a plurality of cylindrical hole portions 11 are provided in the case. Therefore, in this embodiment, as shown in FIG. 1, the spark plug 30 is provided on the ceiling of the combustion chamber 10, and the four cylindrical hole portions 11 are provided on the outer periphery. By doing so, high-speed gas is ejected from the four cylindrical hole portions 11. This gas promotes the diffusion action of the unburned gas in the combustion chamber and expands the contact area of the unburned gas with the flame. As a result, the combustion speed in the cylinder was increased and the thermal efficiency was increased.
（第２実施形態）
図５は、本発明によるエンジンの燃焼室構造の第２実施形態を示す図である。
(Second Embodiment)
FIG. 5 is a view showing a second embodiment of the combustion chamber structure of the engine according to the present invention.
第１実施形態においては、筒穴部１１を燃焼室１０の側壁面に形成したが、他の場所に形成してもよい。 In 1st Embodiment, although the cylinder hole part 11 was formed in the side wall surface of the combustion chamber 10, you may form in another place.
たとえば、シリンダヘッドの天井点火プラグ３０の近傍、すなわち天井点火プラグ３０と、吸気バルブ３１や排気バルブ３２と、の間に形成してもよい。点火プラグ３０の近傍であれば火炎進行波が早めに筒穴部１１を通過するので早期に高速ガスが噴出する。これによって燃焼室内の拡散が早期に生じ燃焼が促進されて熱効率が高くなる。また吸気バルブ３１や排気バルブ３２の傘表面に形成してもよい。さらにピストン冠面に形成してもよい。いずれにせよ燃焼室の火炎が伝播してくる位置に形成すればよい。そして筒穴部１１の軸方向が火炎の伝播方向に一致しない向きに形成すればよい。このように構成することで、筒穴部１１から高速ガスが噴出することとなり、筒内での燃焼を促進することができ熱効率を高くできる。 For example, it may be formed near the ceiling spark plug 30 of the cylinder head, that is, between the ceiling spark plug 30 and the intake valve 31 or the exhaust valve 32. If it is in the vicinity of the spark plug 30, the flame traveling wave passes through the cylindrical hole portion 11 early, so that high-speed gas is ejected early. As a result, diffusion in the combustion chamber occurs early, combustion is promoted, and thermal efficiency is increased. Further, it may be formed on the umbrella surface of the intake valve 31 or the exhaust valve 32. Furthermore, you may form in a piston crown surface. In any case, it may be formed at a position where the flame of the combustion chamber propagates. And the axial direction of the cylinder hole part 11 should just be formed in the direction which does not correspond with the propagation direction of a flame. By comprising in this way, high-speed gas will eject from the cylinder hole part 11, combustion in a cylinder can be accelerated | stimulated and thermal efficiency can be made high.
以上説明した実施形態に限定されることなく、その技術的思想の範囲内において種々の変形や変更が可能であり、それらも本発明の技術的範囲に含まれることが明白である。 Without being limited to the embodiments described above, various modifications and changes are possible within the scope of the technical idea, and it is obvious that these are also included in the technical scope of the present invention.
たとえば、筒穴部は上記例示した個数に限らず適宜設定すればよい。図２〜図４を参照して説明したように、ひとつであっても効果を十分得ることができる。 For example, the number of the cylindrical hole portions is not limited to the number exemplified above, and may be set as appropriate. As described with reference to FIGS. 2 to 4, even a single effect can be obtained sufficiently.
また上記説明においては点火プラグを有するエンジンを例示して説明したが、ディーゼルエンジンであってもよい。ディーゼルエンジンであっても圧縮混合気が自着火し、その自着火ポイントから火炎が伝播する。この火炎が伝播してくる位置に開口を形成すればよい。 In the above description, an engine having a spark plug has been described as an example, but a diesel engine may be used. Even in a diesel engine, the compressed air-fuel mixture self-ignites, and the flame propagates from the self-ignition point. An opening may be formed at a position where this flame propagates.
１０ 燃焼室
１１ 筒穴部
１１ａ 開口
１１ｂ 中心
１１ｃ 底
３０ 点火プラグ
DESCRIPTION OF SYMBOLS 10 Combustion chamber 11 Cylinder hole part 11a Opening 11b Center 11c Bottom 30 Spark plug
Claims (6)
前記混合気に着火する点火プラグと、
エンジンの燃焼室の外周に形成され、燃焼室のスキッシュエリアではない領域に開口し、その開口径のまま筒状に延びて、開口の反対端を閉塞する底を含み、軸線が燃焼室の半径方向に一致して前記点火プラグから伝播する火炎の進行方向と交叉するようにのみ設けられ、火炎の進行波が通過することによって燃焼した開口近傍の混合気の熱膨張による圧力波の跳ね返りによって前記開口からガスを噴出する筒穴部と、
を有することを特徴とするエンジンの燃焼室構造。 A combustion chamber structure of an engine that burns an air-fuel mixture,
A spark plug for igniting the mixture;
It is formed on the outer periphery of the combustion chamber of the engine, opens to a region that is not the squish area of the combustion chamber, extends in a cylindrical shape with the opening diameter, and includes a bottom that closes the opposite end of the opening, and the axis is the radius of the combustion chamber It is provided only so as to intersect with the traveling direction of the flame propagating from the spark plug in accordance with the direction, and by the rebound of the pressure wave due to the thermal expansion of the air-fuel mixture near the opening burned by the passage of the traveling wave of the flame A cylindrical hole for ejecting gas from the opening;
An engine combustion chamber structure characterized by comprising:
前記混合気に着火する点火プラグと、
エンジンの燃焼室の外周に形成され、燃焼室のスキッシュエリアではない領域に開口し、その開口径のまま筒状に延びて、開口の反対端を閉塞する底を含み、軸線が燃焼室の半径方向に一致して開口中心と前記点火プラグの点火部とを結んだ直線と交叉するようにのみ設けられ、火炎の進行波が通過することによって燃焼した開口近傍の混合気の熱膨張による圧力波の跳ね返りによって前記開口からガスを噴出する筒穴部と、
を有することを特徴とするエンジンの燃焼室構造。 A combustion chamber structure of an engine that burns an air-fuel mixture,
A spark plug for igniting the mixture;
It is formed on the outer periphery of the combustion chamber of the engine, opens to a region that is not the squish area of the combustion chamber, extends in a cylindrical shape with the opening diameter, and includes a bottom that closes the opposite end of the opening, and the axis is the radius of the combustion chamber Pressure wave due to thermal expansion of the air-fuel mixture near the opening , which is provided only to intersect the straight line connecting the center of the opening and the ignition part of the spark plug, and is combusted by the passage of the traveling wave of the flame. A cylindrical hole portion for ejecting gas from the opening by rebounding ;
An engine combustion chamber structure characterized by comprising:
ことを特徴とする請求項１又は請求項２に記載のエンジンの燃焼室構造。 The spark plug is provided on the combustion chamber roof,
The combustion chamber structure of the engine according to claim 1 or 2, wherein
ことを特徴とする請求項１から請求項３までのいずれか１項に記載のエンジンの燃焼室構造。 The cylindrical hole portion is formed on the inner wall surface of the cylinder block.
The engine combustion chamber structure according to any one of claims 1 to 3, wherein the engine combustion chamber structure is provided.
ことを特徴とする請求項１から請求項４までのいずれか１項に記載のエンジンの燃焼室構造。 The opening diameter of the cylindrical hole is 1 mm or more and 3 mm or less.
The engine combustion chamber structure according to any one of claims 1 to 4 , wherein the engine combustion chamber structure is provided.
ことを特徴とする請求項１から請求項５までのいずれか１項に記載のエンジンの燃焼室構造。 The ratio of the depth to the diameter of the cylindrical hole is greater than 6.
The engine combustion chamber structure according to any one of claims 1 to 5 , wherein the engine combustion chamber structure is provided.
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| JPS5060606A (en) * | 1973-09-29 | 1975-05-24 | ||
| JPS51121606A (en) * | 1975-04-16 | 1976-10-25 | Taisuke Kamei | The combustion in the holes equipped part of the internal combustion e ngine |
| JPS5343105U (en) * | 1976-09-17 | 1978-04-13 | ||
| JPS5362009A (en) * | 1976-11-15 | 1978-06-03 | Toyota Motor Corp | Internal combustion engine with sub-combustion chamber |
| JPS5681122U (en) * | 1979-11-28 | 1981-07-01 | ||
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| JPS57127819U (en) * | 1981-02-03 | 1982-08-09 | ||
| JPH01211612A (en) * | 1988-02-19 | 1989-08-24 | Suzuki Motor Co Ltd | 4-cycle engine with auxiliary combustion chamber |
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