JP6371942B1 - Engine with three exhaust valves installed in one combustion chamber - Google Patents

Engine with three exhaust valves installed in one combustion chamber Download PDF

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JP6371942B1
JP6371942B1 JP2018038118A JP2018038118A JP6371942B1 JP 6371942 B1 JP6371942 B1 JP 6371942B1 JP 2018038118 A JP2018038118 A JP 2018038118A JP 2018038118 A JP2018038118 A JP 2018038118A JP 6371942 B1 JP6371942 B1 JP 6371942B1
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康仁 矢尾板
康仁 矢尾板
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康仁 矢尾板
康仁 矢尾板
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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
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Abstract

【課題】 火花点火式４サイクルエンジンの耐ノッキング性の向上です。
【解決手段】 シリンダーの内周１に沿って、第１吸気弁の第４底面１２と第１排気弁の第１底面９と第１点火プラグ４と第２排気弁の第２底面１０と第３排気弁の第３底面１１と第２点火プラグ５と第４底面１２が、設置される。第２底面１０の中心と第３底面１１の中心を結ぶ直線から第２底面の半径と第３底面の半径を除外した第２３直線２１の長さが、シリンダー直径の値の１８％を超える値に設定される。第１点火プラグ４と第２３直線２１の間に、第２底面１０が位置する。第２点火プラグ５と第２３直線２１の間に、第３底面１１が位置する。すると、第２３直線２１付近の未燃焼の混合気の温度の上昇が緩和され、耐ノッキング性が向上する。
【選択図】 図２
[PROBLEMS] To improve knocking resistance of a spark ignition type 4-cycle engine.
A first bottom surface of a first intake valve, a first bottom surface of a first exhaust valve, a first spark plug, a second bottom surface of a second exhaust valve, and a second bottom surface are arranged along an inner periphery of the cylinder. A third bottom surface 11, a second spark plug 5, and a fourth bottom surface 12 of the three exhaust valves are installed. The length of the 23rd straight line 21 excluding the radius of the second bottom face and the radius of the third bottom face from the straight line connecting the center of the second bottom face 10 and the center of the third bottom face 11 exceeds 18% of the cylinder diameter value. Set to The second bottom surface 10 is located between the first spark plug 4 and the 23rd straight line 21. The third bottom surface 11 is located between the second spark plug 5 and the 23rd straight line 21. Then, the rise in the temperature of the unburned air-fuel mixture near the 23rd straight line 21 is mitigated, and the knocking resistance is improved.
[Selection] Figure 2

Description

本発明は、火花点火式４サイクルエンジンの耐ノッキング性の向上に関する。 The present invention relates to an improvement in knocking resistance of a spark ignition type 4-cycle engine.

火花点火式４サイクルエンジンの燃焼室の多くは、二つの排気弁と二つの吸気弁を持ち、燃焼室の中心に点火プラグを持つ。上記の二つの排気弁を持つ４弁式燃焼室は、シリンダーの内周に隣接して排気弁が２個設置される。
排気弁は、負荷の増加に応じて高熱化する。排気弁に接して高熱化した混合気は、燃焼速度が増加する。
この為、二つの排気弁を持つ４弁式燃焼室は、過負荷時に、高熱化した排気弁に接した多量の混合気部分が急速に燃焼する事により、ノッキングを誘発させる危険性を持っていた。この為、上記の燃焼室の圧縮比と耐ノッキング性は、制限されていた。 Many of the combustion chambers of a spark ignition type 4-cycle engine have two exhaust valves and two intake valves, and have a spark plug in the center of the combustion chamber. In the four-valve combustion chamber having the two exhaust valves, two exhaust valves are installed adjacent to the inner periphery of the cylinder.
The exhaust valve becomes hot as the load increases. The combustion rate of the air-fuel mixture that has been heated to the exhaust valve increases.
For this reason, a four-valve combustion chamber with two exhaust valves has the risk of causing knocking due to rapid combustion of a large amount of the air-fuel mixture in contact with the heated exhaust valve during overload. It was. For this reason, the compression ratio and the knocking resistance of the combustion chamber are limited.

図１５に示す特許文献１の５弁式燃焼室は、３個の吸気弁と２個の排気弁を持つ。図１５では、吸気弁は符号２３と符号２４と符号２５で示され、排気弁は符号２８で示される。そして、２個の排気弁の底面の直径の大きさは、前記の４弁式燃焼室の排気弁の底面の直径と同じです。従って、上記の構成を持つ５弁式燃焼室の耐ノッキング性は、前記の４弁式燃焼室と同じです。
特許文献２と特許文献３と特許文献４は、３個の排気弁を持つ。
図１６に示す特許文献２の６弁式燃焼室では、１個の点火プラグが燃焼室の中心付近に設置され、３個の排気弁がシリンダーの内周から離れて設置される。
図１７に示すＭａｓｅｒａｔｉの６バルブエンジンと特許文献３のＦＥＲＲＡＲＩのエンジンの６弁式燃焼室は、３個の排気弁がシリンダーの内周に隣接して設置され、燃焼室の中心に１個の点火プラグが設置される。符号１２で示す第１吸気弁の隣の２個の茸弁も吸気弁です。
図１８に示す特許文献４の６弁式燃焼室は、３個の排気弁が一列に連なって設置され、３個の吸気弁が一列に連なって設置され、燃焼室の中心付近に２個の点火プラグが設置される。 The five-valve combustion chamber of Patent Document 1 shown in FIG. 15 has three intake valves and two exhaust valves. In FIG. 15, the intake valves are denoted by reference numerals 23, 24 and 25, and the exhaust valves are denoted by reference numeral 28. The diameter of the bottom surface of the two exhaust valves is the same as the diameter of the bottom surface of the exhaust valve of the 4-valve combustion chamber. Therefore, the five valve combustion chamber with the above configuration has the same knock resistance as the four valve combustion chamber.
Patent Document 2, Patent Document 3 and Patent Document 4 have three exhaust valves.
In the six-valve combustion chamber of Patent Document 2 shown in FIG. 16, one spark plug is installed near the center of the combustion chamber, and three exhaust valves are installed away from the inner periphery of the cylinder.
The 6-valve combustion chamber of the Maserati 6-valve engine shown in FIG. 17 and the Ferrari engine of Patent Document 3 have three exhaust valves installed adjacent to the inner periphery of the cylinder, and one in the center of the combustion chamber. A spark plug is installed. The two soot valves adjacent to the first intake valve indicated by reference numeral 12 are also intake valves.
In the six-valve combustion chamber of Patent Document 4 shown in FIG. 18, three exhaust valves are installed in a row, three intake valves are installed in a row, and two exhaust valves are located near the center of the combustion chamber. A spark plug is installed.

以下の長文の資料であるTales of Cams, Vales, & Combustion chambers http://www.italian.sakura.ne.jp/bad_toys/engine/engine01.htmlの終わりの部分に、ヤマハの７バルブエンジンが紹介されている。この非特許文献の６弁式燃焼室では、４個の小さな吸気弁と３個の排気弁と２個の点火プラグが設置される。３個の排気弁は、一列に連なって設置される。
特願２００６−３２６０３３ （Ｐ２００６−３２６０３３） ４サイクルエンジン ヤマハモ−タ−エンジニアリング株式会社 特願２０１５−２５５５０９ 特許第５９０９３０７号耐ノッキング性を向上させたエンジン 特開平６−０５０１１１ ＪＰＡ−１９９４０５０１１１ シリンダに多数のバルブを具備した特に内燃機関用タイミング機構 ＦＥＲＲＡＲＩ ＳＯＣＩＥＴＡ ＰＥＲ ＡＺＩＯＮＩ 特開平７−１２７４５８ ４サイクルエンジン 川崎重工株式会社 Yamaha's 7-valve engine is introduced at the end of Tales of Cams, Vales, & Combustion chambers http://www.italian.sakura.ne.jp/bad_toys/engine/engine01.html Has been. In the non-patent document 6-valve combustion chamber, four small intake valves, three exhaust valves, and two spark plugs are installed. The three exhaust valves are installed in a row.
Japanese Patent Application No. 2006-326033 (P2006-326033) 4-cycle engine Yamaha Motor Engineering Co., Ltd. Japanese Patent Application No. 2015-255509 Patent No. 5909307 Engine with improved knock resistance JP, Hei 6-050111, JPA-1994050111 A timing mechanism for an internal combustion engine, in particular, provided with a number of valves in a cylinder FERRARI SOCIETA PER AZIONI JP-A-7-127458 4-cycle engine Kawasaki Heavy Industries, Ltd.

本発明の課題は、火花点火式４サイクルエンジンの耐ノッキング性の向上です。 An object of the present invention is to improve the knocking resistance of a spark ignition type 4-cycle engine.

本出願のエンジンは、一つの燃焼室に３個の排気弁が設置される火花点火ピストン式４サイクルエンジンであり、以下の特徴を持つ。
第１から第４までの点は、シリンダーの上端の内周に位置する。前記内周は、仮想水平面に位置する。
前記第１点と前記第２点によって、前記内周は第１円弧と第２円弧に区分される。
前記第３点は、前記第１円弧の中点です。前記第４点は、前記第２円弧の中点です。
第１直線は、前記第１点から第１点火プラグの中心電極を経由してシリンダー中心軸に達する。
第２直線は、前記第２点から第２点火プラグの中心電極を経由して前記シリンダー中心軸に達する。
前記第１円弧に沿って、第１吸気弁の底面である第４底面と第１排気弁の底面である第１底面が設置される。
前記第２円弧に沿って、第２排気弁の底面である第２底面と第３排気弁の底面である第３底面が設置される。
前記第１底面と前記第２底面の両方に隣接して、前記第１点火プラグが位置する。
前記第３底面と前記第４底面の両方に隣接して、前記第２点火プラグが位置する。
以上に、構成要素１が説明された。 The engine of the present application is a spark ignition piston type four-cycle engine in which three exhaust valves are installed in one combustion chamber, and has the following characteristics.
The first to fourth points are located on the inner periphery of the upper end of the cylinder. The inner circumference is located on a virtual horizontal plane.
The inner circumference is divided into a first arc and a second arc by the first point and the second point.
The third point is the midpoint of the first arc. The fourth point is the midpoint of the second arc.
The first straight line reaches the cylinder central axis from the first point via the center electrode of the first spark plug.
The second straight line reaches the cylinder central axis from the second point via the center electrode of the second spark plug.
A fourth bottom surface, which is the bottom surface of the first intake valve, and a first bottom surface, which is the bottom surface of the first exhaust valve, are installed along the first arc.
A second bottom surface that is a bottom surface of the second exhaust valve and a third bottom surface that is a bottom surface of the third exhaust valve are installed along the second arc.
The first spark plug is located adjacent to both the first bottom surface and the second bottom surface.
The second spark plug is located adjacent to both the third bottom surface and the fourth bottom surface.
The component 1 has been described above.

以下に、構成要素２が説明される。
第１直径は、前記シリンダーの直径です。
前記第１底面の直径の値と前記第２底面の直径の値と前記第３底面の直径の値の和が、前記第１直径の値の８３％未満に設定される。 In the following, component 2 is described.
The first diameter is the diameter of the cylinder.
The sum of the value of the diameter of the first bottom surface, the value of the diameter of the second bottom surface, and the value of the diameter of the third bottom surface is set to be less than 83% of the value of the first diameter.

以下に、構成要素３が説明される。
第３仮想垂直面に、前記シリンダー中心軸と前記第３点が位置する。第４仮想垂直面に、前記シリンダー中心軸と前記第４点が位置する。前記第３仮想垂直面と前記第４仮想垂直面は、前記仮想水平面に対して垂直な仮想面です。
第１３直線は、前記第３仮想垂直面と直交する。前記第１３直線は、前記第１底面の中心から前記第３仮想垂直面に至る直線です。
前記第１３直線の長さは、前記第１底面の半径よりも長い値に設定される。
第２３直線は、前記第２底面の中心と前記第３底面の中心を結ぶ直線から前記第２底面の半径と前記第３底面の半径を除外した直線です。
前記第２３直線の長さが、前記第１直径の値の１８％を超える値に設定される。 Below, the component 3 is demonstrated.
The cylinder center axis and the third point are located on the third virtual vertical plane. The cylinder center axis and the fourth point are located on the fourth virtual vertical plane. The third virtual vertical plane and the fourth virtual vertical plane are virtual planes perpendicular to the virtual horizontal plane.
The thirteenth straight line is orthogonal to the third virtual vertical plane. The thirteenth straight line is a straight line extending from the center of the first bottom surface to the third virtual vertical surface.
The length of the thirteenth straight line is set to a value longer than the radius of the first bottom surface.
The 23rd straight line is a straight line obtained by excluding the radius of the second bottom surface and the radius of the third bottom surface from the straight line connecting the center of the second bottom surface and the center of the third bottom surface.
The length of the 23rd straight line is set to a value exceeding 18% of the value of the first diameter.

以下に、作用が説明される。
３個の排気弁の３個の底面に接した混合気部分に火炎が達する前に、２個の点火プラグ付近の既燃焼ガスの膨張によって、３個の底面に接した未燃焼の混合気部分の一部が３個の排気弁の３個の底面から押し出される。すると、押し出された一部の混合気部分が持つ熱量は、３個の排気弁よりも下流側の二つの空間に拡散する。この二つの空間では、未燃焼の混合気部分は、排気弁の底面によって加熱されない。
この二つの空間は、２個の点火プラグから３個の排気弁の３個の底面を経て伝播する火炎の終端部です。そして、一つ目の空間は、第３点付近の上死点時の空間です。二つ目の空間は、第４点付近の上死点時の空間です。
二つの排気弁を持つ従来例の４弁式燃焼室では、排気弁の底面の外周とシリンダー内周との間隔は、排気ガスが通過できる最小限の間隔に設定されている。その為、排気弁よりも下流の火炎伝播経路の長さは、シリンダーの直径である第１直径の値の約４％未満の値に設定されている。排気弁よりも下流の火炎伝播経路は、排気弁の底面の外周からシリンダー内周までの経路です。
これに対して、本願では、第２３直線の長さが、第１直径の値の１８％を超える値に設定されている。そして、第１３直線の長さは、第１底面の半径よりも長い値に設定される。その結果、３個の排気弁よりも下流の火炎伝播経路の長さが、４弁式燃焼室の二つの排気弁の底面より下流の火炎伝播経路の長さよりも、大きく設定される。
すると、燃焼行程の中期までに、３個の排気弁の３個の底面に接した混合気部分の燃焼の大部分が終了する。
すると、二つの排気弁を持つ従来例の燃焼室よりも、燃焼行程の後半の燃焼圧力値の上昇が緩やかになり、ノッキングが発生し難くなる。
その結果、本願発明では、耐ノッキング性が向上する。 The operation will be described below.
The unburned mixture portion in contact with the three bottom surfaces by the expansion of the burned gas near the two spark plugs before the flame reaches the mixture portion in contact with the three bottom surfaces of the three exhaust valves. Are extruded from the three bottom surfaces of the three exhaust valves. Then, the heat quantity of the part of the air-fuel mixture that has been pushed out diffuses into two spaces downstream of the three exhaust valves. In these two spaces, the unburned mixture portion is not heated by the bottom surface of the exhaust valve.
These two spaces are the ends of the flame that propagates from the two spark plugs through the three bottom surfaces of the three exhaust valves. The first space is the space at the top dead center near the third point. The second space is the space at the top dead center near the fourth point.
In the conventional four-valve combustion chamber having two exhaust valves, the interval between the outer periphery of the bottom surface of the exhaust valve and the inner periphery of the cylinder is set to the minimum interval through which the exhaust gas can pass. For this reason, the length of the flame propagation path downstream from the exhaust valve is set to a value less than about 4% of the value of the first diameter, which is the diameter of the cylinder. The flame propagation path downstream from the exhaust valve is the path from the outer periphery of the bottom surface of the exhaust valve to the inner periphery of the cylinder.
On the other hand, in the present application, the length of the 23rd straight line is set to a value exceeding 18% of the value of the first diameter. The length of the thirteenth straight line is set to a value longer than the radius of the first bottom surface. As a result, the length of the flame propagation path downstream of the three exhaust valves is set to be larger than the length of the flame propagation path downstream of the bottom surfaces of the two exhaust valves of the four-valve combustion chamber.
Then, by the middle of the combustion stroke, most of the combustion of the mixture portion in contact with the three bottom surfaces of the three exhaust valves is completed.
Then, the increase in the combustion pressure value in the latter half of the combustion stroke becomes more gradual than in the conventional combustion chamber having two exhaust valves, and knocking is less likely to occur.
As a result, in the present invention, the knocking resistance is improved.

そして、以下の作用が加わる。
第１点火プラグ付近の既燃焼ガスの膨張が、未燃焼の混合気を第１底面から第１円弧の方向に押す。すると、未燃焼の混合気は、第１円弧に斜めに衝突し、第１円弧に沿って第３点の方向に移動する。第２底面から第２円弧の方向に押された未燃焼の混合気は、第２円弧に斜めに衝突し、第２円弧に沿って第４点の方向に移動する。
また、第２点火プラグ付近の既燃焼ガスの膨張によって、第３底面から第２円弧の方向に押された未燃焼の混合気は、第２円弧に斜めに衝突し、第２円弧に沿って第４点の方向に移動する。
この結果、第１円弧または第２円弧に沿って未燃焼の混合気が移動する事によって、直線的に移動する場合よりも、３個の排気弁から火炎伝播経路の終端部までの長さが増加する。 And the following actions are added.
The expansion of the burnt gas near the first spark plug pushes the unburned mixture in the direction of the first arc from the first bottom surface. Then, the unburned air-fuel mixture collides obliquely with the first arc and moves in the direction of the third point along the first arc. The unburned air-fuel mixture pushed from the second bottom surface in the direction of the second arc collides obliquely with the second arc and moves in the direction of the fourth point along the second arc.
Further, the unburned air-fuel mixture pushed in the direction of the second arc from the third bottom surface due to the expansion of the burnt gas in the vicinity of the second spark plug collides obliquely with the second arc and follows the second arc. Move in the direction of the fourth point.
As a result, the unburned mixture moves along the first arc or the second arc, so that the length from the three exhaust valves to the end of the flame propagation path is longer than when moving linearly. To increase.

特許文献１から特許文献４までの文献と本願を比較する。
特許文献１から特許文献４までの特許文献は、本願の構成要素３を持たない。
特許文献１と特許文献３と特許文献４の特許文献では、二つの排気弁を持つ４弁式燃焼室と同様に、排気弁の底面がシリンダーの内周に隣接して位置する。この為、排気弁の底面よりも下流の火炎伝播経路の長さが、シリンダーの直径の値の約４％未満に設定される。この為、これらの特許文献のエンジンでは、点火プラグから排気弁の底面を火炎が通過し終わる時期が燃焼行程の終期になり、燃焼行程後期に排気弁に面した混合気部分が急激に燃焼し、燃焼圧力値が急激に上昇する。
これに対して、本願では、構成要素３によって、排気弁に面した混合気部分の燃焼が終わる時期が、特許文献１と特許文献３と特許文献４よりも早くなる。すると、燃焼圧力値の上昇が制限される。
また、本願では、排気弁の底面から押し出された未燃焼の混合気が、シリンダーの内周に沿って移動する。
これに対して、特許文献１から特許文献４までの特許文献では、排気弁の底面に接した未燃焼の混合気の一部分が、点火プラグ付近の燃焼ガスの膨張によって、排気弁の底面から押し出され、シリンダーの内周に直角に近い角度で衝突し、シリンダーの内周に沿って容易に移動できない。 The patent documents 1 to 4 are compared with the present application.
Patent documents 1 to 4 do not have the component 3 of the present application.
In Patent Document 1, Patent Document 3, and Patent Document 4, the bottom surface of the exhaust valve is located adjacent to the inner periphery of the cylinder, similarly to the four-valve combustion chamber having two exhaust valves. For this reason, the length of the flame propagation path downstream from the bottom surface of the exhaust valve is set to be less than about 4% of the value of the cylinder diameter. For this reason, in the engines of these patent documents, the timing when the flame has passed from the spark plug to the bottom surface of the exhaust valve is the end of the combustion stroke, and the mixture portion facing the exhaust valve burns rapidly in the latter half of the combustion stroke. The combustion pressure value increases rapidly.
On the other hand, in the present application, the time when the combustion of the air-fuel mixture portion facing the exhaust valve is completed by the component 3 is earlier than those of Patent Document 1, Patent Document 3, and Patent Document 4. Then, the increase in the combustion pressure value is limited.
Moreover, in this application, the unburned air-fuel mixture pushed out from the bottom surface of the exhaust valve moves along the inner periphery of the cylinder.
On the other hand, in Patent Documents 1 to 4, a part of the unburned mixture in contact with the bottom surface of the exhaust valve is pushed out from the bottom surface of the exhaust valve due to the expansion of the combustion gas near the spark plug. It collides with the inner circumference of the cylinder at an angle close to a right angle and cannot move easily along the inner circumference of the cylinder.

本発明による効果が説明される。
耐ノッキング性が向上する事によって、本発明は、二つの排気弁を持つ４弁式燃焼室と二つの排気弁を持つ５弁式燃焼室よりも、高圧縮比化が可能になる。高圧縮比化によって、熱効率が向上する。
The effect by this invention is demonstrated.
By improving the knocking resistance, the present invention can achieve a higher compression ratio than a four-valve combustion chamber having two exhaust valves and a five-valve combustion chamber having two exhaust valves. The thermal efficiency is improved by increasing the compression ratio.

全ての実施例のエンジンは、火花点火式４サイクルエンジンであり、３個の排気弁と少なくとも１個の吸気弁を持ち、２個の排気弁を持つ４弁式エンジンではない。
全ての実施例で、全ての吸気弁と全ての排気弁は、燃焼室のシリンダーヘッド側の壁面に設置される。
全ての平面図は、吸気弁と排気弁と点火プラグの位置関係を示す概念図です。吸気弁の円形の底面と排気弁の円形の底面は、吸気弁の軸部と排気弁の軸部が直立する事を示さない。
図１と図２と図３を使って、第１実施例を説明する。
第１実施例のエンジンの一つの燃焼室は、以下の特徴を持つ。
シリンダーヘッドの下面とピストンとの間に、燃焼室の内部空間が位置する。
図１は、カム軸の方向からピストンの方向を透視した時の燃焼室の平面図です。
シリンダーの上端の内周１は、上死点時の燃焼室の内部空間の周辺部に接する。
第１点６と第２点７と第３点１４と第４点１５は、黒く小さな丸で表示され、シリンダーの上端の内周１に位置する。シリンダーの上端の内周１は、仮想水平面に位置する。
第１点６と第２点７によって、シリンダーの上端の内周１は第１円弧と第２円弧に区分される。
第３点１４は、第１円弧の中点です。
第４点１５は、第２円弧の中点です。
第１直線８は、第１点６から第１点火プラグ４の中心電極を経由してシリンダー中心軸に達する。シリンダー中心軸は、中央に位置する黒く小さな丸で示す。
第２直線１６は、第２点７から第２点火プラグ５の中心電極を経由してシリンダー中心軸に達する。第１直線８と第２直線１６は、仮想線です。
第３仮想垂直面１７に、シリンダー中心軸と第３点１４が位置する。
第４仮想垂直面１８に、シリンダー中心軸と第４点１５が位置する。
第３仮想垂直面１７と第４仮想垂直面１８は、シリンダーの上端の内周１が位置する仮想水平面に対して、垂直であり、シリンダー中心軸と平行であり、仮想面です。そして、第３仮想垂直面１７と第４仮想垂直面１８は、図１と図２では直線で示される。 The engine of all the examples is a spark ignition type four-cycle engine, and is not a four-valve engine having three exhaust valves and at least one intake valve and having two exhaust valves.
In all the embodiments, all the intake valves and all the exhaust valves are installed on the wall surface of the combustion chamber on the cylinder head side.
All the plan views are conceptual diagrams showing the positional relationship between the intake valve, exhaust valve, and spark plug. The circular bottom surface of the intake valve and the circular bottom surface of the exhaust valve do not indicate that the shaft portion of the intake valve and the shaft portion of the exhaust valve are upright.
The first embodiment will be described with reference to FIGS. 1, 2, and 3.
One combustion chamber of the engine of the first embodiment has the following characteristics.
An internal space of the combustion chamber is located between the lower surface of the cylinder head and the piston.
Fig. 1 is a plan view of the combustion chamber as seen through the direction of the piston from the direction of the camshaft.
The inner circumference 1 at the upper end of the cylinder is in contact with the peripheral portion of the internal space of the combustion chamber at the top dead center.
The first point 6, the second point 7, the third point 14, and the fourth point 15 are displayed as small black circles and are located on the inner periphery 1 at the upper end of the cylinder. The inner circumference 1 at the upper end of the cylinder is located on the virtual horizontal plane.
By the first point 6 and the second point 7, the inner circumference 1 at the upper end of the cylinder is divided into a first arc and a second arc.
The third point 14 is the midpoint of the first arc.
The fourth point 15 is the midpoint of the second arc.
The first straight line 8 reaches the cylinder central axis from the first point 6 via the central electrode of the first spark plug 4. The cylinder center axis is indicated by a small black circle located in the center.
The second straight line 16 reaches the cylinder central axis from the second point 7 via the center electrode of the second spark plug 5. The first straight line 8 and the second straight line 16 are virtual lines.
The cylinder central axis and the third point 14 are located on the third virtual vertical plane 17.
The cylinder center axis and the fourth point 15 are located on the fourth virtual vertical plane 18.
The third virtual vertical surface 17 and the fourth virtual vertical surface 18 are perpendicular to the virtual horizontal plane on which the inner circumference 1 of the upper end of the cylinder is located, and are parallel to the cylinder center axis. The third virtual vertical surface 17 and the fourth virtual vertical surface 18 are indicated by straight lines in FIGS. 1 and 2.

第１円弧に沿って、第１排気弁の底面である第１底面９と第１吸気弁の底面である第４底面１２が、燃焼室のシリンダーヘッド側の壁面に設置される。
第２円弧に沿って、第２排気弁の底面である第２底面１０と第３排気弁の底面である第３底面１１が、燃焼室のシリンダーヘッド側の壁面に設置される。
第１排気弁の第１底面９に隣接して、第１点火プラグ４が位置する。第２排気弁の第２底面１０に隣接して、第１点火プラグ４が位置する。
第３排気弁の第３底面１１に隣接して、第２点火プラグ５が位置する。第１吸気弁の第４底面１２に隣接して、第２点火プラグ５が位置する。
第１点火プラグ４と第２点火プラグ５は、燃焼室のシリンダーヘッド側の壁面の周辺部に位置する。
第１直径は、シリンダーの直径です。
図３に示す様に、第１実施例では、第１底面９の直径の大きさと第２底面１０の直径の大きさと第３底面１１の直径の大きさは、異なった大きさに設定可能です。
しかし、第１実施例では、第１底面９の直径の値と第２底面１０の直径の値と第３底面１１の直径の値の和が、第１直径の値の８３％未満に設定される。 A first bottom surface 9 that is the bottom surface of the first exhaust valve and a fourth bottom surface 12 that is the bottom surface of the first intake valve are installed along the cylinder head side wall surface of the combustion chamber along the first arc.
A second bottom surface 10 which is the bottom surface of the second exhaust valve and a third bottom surface 11 which is the bottom surface of the third exhaust valve are installed along the cylinder head side wall surface of the combustion chamber along the second arc.
The first spark plug 4 is located adjacent to the first bottom surface 9 of the first exhaust valve. The first spark plug 4 is located adjacent to the second bottom surface 10 of the second exhaust valve.
The second spark plug 5 is located adjacent to the third bottom surface 11 of the third exhaust valve. The second spark plug 5 is located adjacent to the fourth bottom surface 12 of the first intake valve.
The 1st spark plug 4 and the 2nd spark plug 5 are located in the peripheral part of the wall surface by the side of the cylinder head of a combustion chamber.
The first diameter is the cylinder diameter.
As shown in FIG. 3, in the first embodiment, the diameter of the first bottom surface 9, the diameter of the second bottom surface 10, and the diameter of the third bottom surface 11 can be set to different sizes. .
However, in the first embodiment, the sum of the value of the diameter of the first bottom surface 9, the value of the diameter of the second bottom surface 10, and the value of the diameter of the third bottom surface 11 is set to be less than 83% of the value of the first diameter. The

直列式の多気筒エンジンの場合は、第３点１４と第４点１５を結ぶ直線とカム軸との角度に関する構成は、以下の２個の構成のいずれか一つの構成が選択できる。
第１の構成では、第１排気弁と第１吸気弁を駆動する第１カム軸の中心軸と第２排気弁と第３排気弁を駆動する第２カム軸の中心軸が、第３点１４と第４点１５を結ぶ直線に仮想的に投影される。その時、２本のカム軸の２本の中心軸の仮想的な投影線が、第３点１４と第４点１５を結ぶ直線に交差する。
第２の構成では、２本のカム軸の２本の中心軸が、第３点１４と第４点１５を結ぶ直線に、仮想的に投影されない。そして、２本の仮想的な投影線が、第３点１４と第４点１５を結ぶ直線に対して、おおよそ平行に設定される。 In the case of an in-line multi-cylinder engine, the configuration relating to the angle between the straight line connecting the third point 14 and the fourth point 15 and the cam shaft can be selected from one of the following two configurations.
In the first configuration, the central axis of the first camshaft that drives the first exhaust valve and the first intake valve and the central axis of the second camshaft that drives the second exhaust valve and the third exhaust valve are the third point. 14 and the fourth point 15 are virtually projected on a straight line. At that time, the virtual projection lines of the two central axes of the two cam shafts intersect the straight line connecting the third point 14 and the fourth point 15.
In the second configuration, the two central axes of the two cam shafts are not virtually projected on a straight line connecting the third point 14 and the fourth point 15. The two virtual projection lines are set to be approximately parallel to the straight line connecting the third point 14 and the fourth point 15.

構成要素３が説明される。
第１直径は、シリンダーの直径です。
第２３直線２１は、第４仮想垂直面１８と直交する。
第２３直線２１は、第２底面１０の中心と第３底面１１の中心を結ぶ直線から第２底面１０の半径と第３底面１１の半径を除外した直線です。第４仮想垂直面１８は、第２３直線２１を分断する。
第２３直線２１の長さが第１直径の値の１８％を超える値に設定される。この設定は、耐ノッキング性の大きさを決める。第２３直線の長さを大きく設定する程、耐ノッキング性が更に向上する。
点線で示す第１３直線２２は、第３仮想垂直面１７と直交する。第３直線２２は、第１底面９の中心から第３仮想垂直面１７に至る直線です。
そして、第１３直線２２の長さは、第１底面９の半径よりも長い値に設定される。
第３仮想垂直面１７と第１底面９の間には、第１３直線２２の一部である第１部分が存在する。第１３直線２２の第１部分は、耐ノッキング性の大きさを決める。
第４点１５付近の領域には、第２底面１０によって加熱された混合気と第３底面１１によって加熱された混合気が流入する。これに対して、第３点１４付近の領域に流入する混合気であるだけでなく排気弁によって加熱された混合気は、第１底面９によって加熱された混合気だけです。この為、第３点１４付近の領域では、第４点１５付近の領域よりも急激な燃焼が発生し難い。 Component 3 is described.
The first diameter is the cylinder diameter.
The 23rd straight line 21 is orthogonal to the fourth virtual vertical plane 18.
The 23rd straight line 21 is a straight line obtained by excluding the radius of the second bottom surface 10 and the radius of the third bottom surface 11 from the straight line connecting the center of the second bottom surface 10 and the center of the third bottom surface 11. The fourth virtual vertical surface 18 divides the 23rd straight line 21.
The length of the 23rd straight line 21 is set to a value exceeding 18% of the value of the first diameter. This setting determines the amount of knock resistance. As the length of the 23rd straight line is set larger, the knocking resistance is further improved.
A thirteenth straight line 22 indicated by a dotted line is orthogonal to the third virtual vertical plane 17. The third straight line 22 is a straight line extending from the center of the first bottom surface 9 to the third virtual vertical surface 17.
The length of the thirteenth straight line 22 is set to a value longer than the radius of the first bottom surface 9.
A first portion that is a part of the thirteenth straight line 22 exists between the third virtual vertical surface 17 and the first bottom surface 9. The first portion of the thirteenth straight line 22 determines the magnitude of knock resistance.
In the region near the fourth point 15, the air-fuel mixture heated by the second bottom surface 10 and the air-fuel mixture heated by the third bottom surface 11 flow. On the other hand, not only the mixture flowing into the region near the third point 14 but also the mixture heated by the exhaust valve is only the mixture heated by the first bottom surface 9. For this reason, in the region near the third point 14, rapid combustion is less likely to occur than in the region near the fourth point 15.

第４底面１２と第１点火プラグ４の間に、第１排気弁の第１底面９が位置する。
第２３直線付近の壁面領域と第１点火プラグ４の間に、第２排気弁の第２底面１０が位置する。
第２３直線付近の壁面領域と第２点火プラグ５の間に、第３排気弁の第３底面１１が位置する。
第１３直線２３の付近の壁面領域と第２３直線付近の壁面領域には、排気弁が設置されない。 A first bottom surface 9 of the first exhaust valve is located between the fourth bottom surface 12 and the first spark plug 4.
Between the wall surface region near the 23rd straight line and the first spark plug 4, the second bottom surface 10 of the second exhaust valve is located.
The third bottom surface 11 of the third exhaust valve is located between the wall surface region near the 23rd straight line and the second spark plug 5.
Exhaust valves are not installed on the wall surface area near the 13th straight line 23 and the wall surface area near the 23rd straight line.

図４と図５と図６と図７使って、第２実施例を説明する。
本出願の一つの燃焼室に設置される吸気弁の数は、１個に限定されない。
第２実施例は、第１実施例に以下の構成を加える。
第２吸気弁が、一つの燃焼室に増設される。また、第３吸気弁も増設可能であり、第４吸気弁も増設可能です。すなわち、一つの燃焼室に、第１吸気弁以外の吸気弁が、少なくとも１個設置される。一つの燃焼室に、第１吸気弁以外の吸気弁が、１個以上の任意の数だけ設置される。
そして、第１吸気弁以外の吸気弁の底面の中心が、少なくとも１個、第７壁面領域に位置する。
第２吸気弁の底面１３が１個設置された場合のエンジンは、５弁式エンジンです。
第７壁面領域は、第６壁面領域から第１底面９と第２底面１０と第３底面１１と第４底面１２を除外した壁面領域です。
第６壁面領域は、シリンダーヘッドの壁面の一部であり、第３点１４と第１底面９の中心と第２底面１０の中心と第４点１５と第３底面１１の中心と第４底面１２の中心と第３点１４を結ぶ６本の点線によって囲まれる六角形の壁面領域です。
図４は、第３点１４の近くに第２吸気弁の底面１３が設置される場合を示す。
図５は、燃焼室の中央部付近に第２吸気弁の底面１３が設置される場合を示す。
図６は、第４点１５の近くに第２吸気弁の底面１３が設置される場合を示す。
第２吸気弁の底面１３と第３吸気弁の底面２３が設置された場合のエンジンは、６弁式エンジンです。６弁式エンジンの一例を図７に示す。図７では、第４点１５に隣接した位置に第２吸気弁の底面１３が設置され、燃焼室の中央部付近の位置に第３吸気弁の底面２３が設置される。
第２吸気弁の底面１３と第３吸気弁の底面２３と第４吸気弁の底面が設置された場合のエンジンは、７弁式エンジンです。
第２実施例は、請求項２に対応する。 The second embodiment will be described with reference to FIGS. 4, 5, 6 and 7.
The number of intake valves installed in one combustion chamber of the present application is not limited to one.
The second embodiment adds the following configuration to the first embodiment.
A second intake valve is added to one combustion chamber. A third intake valve can also be added, and a fourth intake valve can be added. That is, at least one intake valve other than the first intake valve is installed in one combustion chamber. An arbitrary number of intake valves other than the first intake valve are installed in one combustion chamber.
At least one center of the bottom surface of the intake valves other than the first intake valve is located in the seventh wall surface region.
The engine when one bottom face 13 of the second intake valve is installed is a 5-valve engine.
The seventh wall surface area is a wall surface area in which the first bottom surface 9, the second bottom surface 10, the third bottom surface 11, and the fourth bottom surface 12 are excluded from the sixth wall surface region.
The sixth wall surface area is a part of the wall surface of the cylinder head, and the third point 14, the center of the first bottom surface 9, the center of the second bottom surface 10, the fourth point 15, the center of the third bottom surface 11, and the fourth bottom surface. It is a hexagonal wall area surrounded by 6 dotted lines connecting the center of 12 and the third point 14.
FIG. 4 shows a case where the bottom surface 13 of the second intake valve is installed near the third point 14.
FIG. 5 shows a case where the bottom surface 13 of the second intake valve is installed near the center of the combustion chamber.
FIG. 6 shows a case where the bottom surface 13 of the second intake valve is installed near the fourth point 15.
If the bottom surface 13 of the second intake valve and the bottom surface 23 of the third intake valve are installed, the engine is a six-valve engine. An example of a 6-valve engine is shown in FIG. In FIG. 7, the bottom surface 13 of the second intake valve is installed at a position adjacent to the fourth point 15, and the bottom surface 23 of the third intake valve is installed at a position near the center of the combustion chamber.
When the bottom surface 13 of the second intake valve, the bottom surface 23 of the third intake valve, and the bottom surface of the fourth intake valve are installed, the engine is a seven-valve engine.
The second embodiment corresponds to claim 2.

第３実施例を説明する。
第３実施例は、第１実施例と第２実施例に以下の構成を加える。
第１排気弁９と第２排気弁１０と第３排気弁１１の３個の底面の直径の値の和が第１直径の値の７３．５％に設定される場合は、第１から第３までの排気弁の底面の面積の和は、前記の４弁式燃焼室の２個の排気弁の底面の面積の和と等しくなる。
これに対して、第３実施例では、第１底面９と第２底面１０と第３底面１１の３個の底面の直径の値の和が、前記第１直径の値の７３％未満の値に設定される。
すると、３個の排気弁の３個の底面の面積の和が、前記の４弁式燃焼室の２個の排気弁の底面の面積の和よりも、小さくなる。すると、３個の排気弁の底面に接して加熱される混合気部分の面積と排気弁の底面に接する混合気の量が減少し、耐ノッキング性が増加する。
第１角度は、水平方向の角度であり、第２直線１６がシリンダー中心軸を中心にして第４底面１２を経由して第１直線８の位置まで回転した角度です。
第１角度が１２０度未満の値に設定される時に、第１底面９の直径を小さく設定する必要がある。すると、第２底面１０の直径の値と第３底面１１の直径の値が、大きくなる。すると、第４点１５付近の空間で急激な燃焼の発生の危険が高まる。
また、第１角度が２３０度を超える値に設定される時に、第２底面１０と第３底面１１の２つの直径の値は、非常に小さく設定する必要がある。すると、第１底面９の直径の値を大きく設定する必要が生まれる。すると、第１底面９の直径の値が、大きくなる。すると、第３点１４付近の空間で急激な燃焼の発生の危険が高まる。
これに対して、第３実施例では、第１角度が１２０度から２３０度までの範囲内に設定される。
そして、第２３直線の長さを第１直径の値の２４％を超える値に設定する事によって、第１と第２の実施例よりも、第３実施例の耐ノッキング性が増加する。 A third embodiment will be described.
In the third embodiment, the following configuration is added to the first embodiment and the second embodiment.
When the sum of the diameter values of the three bottom surfaces of the first exhaust valve 9, the second exhaust valve 10, and the third exhaust valve 11 is set to 73.5% of the first diameter value, the first to second The sum of the areas of the bottom surfaces of the exhaust valves up to 3 is equal to the sum of the areas of the bottom surfaces of the two exhaust valves of the four-valve combustion chamber.
In contrast, in the third embodiment, the sum of the diameter values of the three bottom surfaces of the first bottom surface 9, the second bottom surface 10, and the third bottom surface 11 is less than 73% of the first diameter value. Set to
Then, the sum of the areas of the three bottom surfaces of the three exhaust valves is smaller than the sum of the areas of the bottom surfaces of the two exhaust valves of the four-valve combustion chamber. Then, the area of the air-fuel mixture part heated in contact with the bottom surfaces of the three exhaust valves and the amount of the air-fuel mixture in contact with the bottom surfaces of the exhaust valves are reduced, and the knocking resistance is increased.
The first angle is an angle in the horizontal direction, and is an angle obtained by rotating the second straight line 16 about the cylinder central axis through the fourth bottom surface 12 to the position of the first straight line 8.
When the first angle is set to a value less than 120 degrees, the diameter of the first bottom surface 9 needs to be set small. Then, the value of the diameter of the second bottom surface 10 and the value of the diameter of the third bottom surface 11 are increased. This increases the risk of sudden combustion occurring in the space near the fourth point 15.
Further, when the first angle is set to a value exceeding 230 degrees, the values of the two diameters of the second bottom surface 10 and the third bottom surface 11 need to be set very small. Then, it becomes necessary to set a large value for the diameter of the first bottom surface 9. Then, the value of the diameter of the first bottom surface 9 increases. This increases the risk of sudden combustion occurring in the space near the third point 14.
In contrast, in the third embodiment, the first angle is set within a range from 120 degrees to 230 degrees.
And by setting the length of the 23rd straight line to a value exceeding 24% of the value of the first diameter, the knocking resistance of the third embodiment is increased as compared with the first and second embodiments.

図８を使って、第４実施例を説明する。
第１点火プラグ４の中心電極が第１２直線２０よりもシリンダー中心軸側に位置する場合は、第１底面９と第２底面１０よりも下流の混合気の内のシリンダー内周に近い部分の混合気が、第２円弧または第１円弧に沿って移動し難くなり、シリンダー内周１に沿って混合気が流れる作用が制限される。
第４実施例は、上記の問題を解決する。
第４実施例は、第１から第３までの実施例に以下の構成を加える。
第１２直線２０は、第１点火プラグ４の中心電極と十字線で示すシリンダー中心軸の間に位置する。
そして、第３４直線１９は、第２点火プラグ５の中心電極とシリンダー中心軸の間に位置する。
点線で示す第１２直線２０は、第１底面９の中心と第２底面１０の中心を結ぶ直線から第１底面９の半径と第２底面１０の半径を削除した直線です。
また、点線で示す３４直線１９は、第３底面１１の中心と第４底面１２の中心を結ぶ直線から第３底面１１の半径と第４底面１２の半径を削除した直線です。
これによって、３個の排気弁よりも下流の混合気のほとんど全部が、第２円弧に沿って第４点１５の付近の燃焼室空間に移動し、第１円弧に沿って第３点１４の付近の燃焼室空間に移動する。従って、前記の作用の制限が解消する。 A fourth embodiment will be described with reference to FIG.
When the center electrode of the first spark plug 4 is located on the cylinder center axis side with respect to the twelfth straight line 20, the portion of the air-fuel mixture downstream of the first bottom surface 9 and the second bottom surface 10 is close to the inner periphery of the cylinder. The air-fuel mixture becomes difficult to move along the second arc or the first arc, and the action of the air-fuel mixture flowing along the cylinder inner periphery 1 is limited.
The fourth embodiment solves the above problem.
The fourth embodiment adds the following configuration to the first to third embodiments.
The twelfth straight line 20 is located between the center electrode of the first spark plug 4 and the cylinder center axis indicated by a cross line.
The 34th straight line 19 is located between the center electrode of the second spark plug 5 and the cylinder center axis.
A twelfth straight line 20 indicated by a dotted line is a straight line obtained by deleting the radius of the first bottom surface 9 and the radius of the second bottom surface 10 from the straight line connecting the center of the first bottom surface 9 and the center of the second bottom surface 10.
A 34 straight line 19 indicated by a dotted line is a straight line obtained by deleting the radius of the third bottom surface 11 and the radius of the fourth bottom surface 12 from the straight line connecting the center of the third bottom surface 11 and the center of the fourth bottom surface 12.
As a result, almost all of the air-fuel mixture downstream from the three exhaust valves moves along the second arc to the combustion chamber space near the fourth point 15, and reaches the third point 14 along the first arc. Move to the nearby combustion chamber space. Therefore, the limitation of the above action is eliminated.

図９と図１０と図１１を使って、第５実施例を説明する。
図９は、第１実施例に第５実施例の構成を加えた平面図です。図１０は、第２実施例に第５実施例の構成を加えた平面図です。図１１は、第１実施例に第５実施例の構成を加えた断面図であり、上死点時前５０度の図です。
第５実施例は、第１から第４までの実施例に以下の構成を加える。
第４円弧は、シリンダーの上端の内周１の一部分です。第４円弧は、第２円弧の一部です。第４円弧は、第４点１５を中点とする円弧です。
第４弧の長さは、点線で示す第２３直線２１の長さの１５０％です。
第４４壁面領域２４は、シリンダーヘッドの壁面部分です。第４４壁面領域２４は、第２３直線２１と第４円弧の間に位置する。
ピストン２の上面の一部である第４０壁面領域２５は、上死点時に、第４４壁面領域２４に対面する。第４０壁面領域２５は、ピストン２の上面の凸部です。
上死点時の第２スキッシュエリア空間は、第４４壁面領域２４と上死点時の第４０壁面領域２５の間に形成される。
図１１に示す様に、第４４壁面領域２４の垂直断面の形と上死点時の第４０壁面領域２５の垂直断面の形は、おおよそ平行です。
なお、第４４壁面領域２４と第４０壁面領域２５は、平面に限定されない。第４４壁面領域２４の面が突出した形に形成される時は、第４０壁面領域２５の面は凹んだ形に形成される。第４４壁面領域２４が凹んだ形に形成される時は、第４０壁面領域２５は突出した形に形成される。
第２スキッシュエリア空間の上死点時のシリンダー中心軸と平行な方向の長さが、ピストン２のストローク量の４％未満に設定される。 A fifth embodiment will be described with reference to FIGS. 9, 10 and 11. FIG.
FIG. 9 is a plan view in which the configuration of the fifth embodiment is added to the first embodiment. FIG. 10 is a plan view in which the configuration of the fifth embodiment is added to the second embodiment. FIG. 11 is a cross-sectional view in which the configuration of the fifth embodiment is added to the first embodiment, and is a view at 50 degrees before the top dead center.
The fifth embodiment adds the following configuration to the first to fourth embodiments.
The fourth arc is a part of the inner circumference 1 at the upper end of the cylinder. The fourth arc is a part of the second arc. The fourth arc is an arc with the fourth point 15 as the midpoint.
The length of the 4th arc is 150% of the length of the 23rd straight line 21 shown by the dotted line.
The 44th wall surface area 24 is a wall surface portion of the cylinder head. The 44th wall surface region 24 is located between the 23rd straight line 21 and the fourth arc.
The 40th wall surface area 25 which is a part of the upper surface of the piston 2 faces the 44th wall surface area 24 at the top dead center. The 40th wall region 25 is a convex portion on the upper surface of the piston 2.
The second squish area space at the top dead center is formed between the 44th wall surface area 24 and the 40th wall surface area 25 at the top dead center.
As shown in FIG. 11, the shape of the vertical cross section of the 44th wall surface region 24 and the shape of the vertical cross section of the 40th wall surface region 25 at the top dead center are approximately parallel.
In addition, the 44th wall surface area | region 24 and the 40th wall surface area | region 25 are not limited to a plane. When the surface of the forty-fourth wall surface region 24 is formed in a protruding shape, the surface of the forty-fourth wall surface region 25 is formed in a recessed shape. When the 44th wall surface region 24 is formed in a recessed shape, the 40th wall surface region 25 is formed in a protruding shape.
The length in the direction parallel to the cylinder central axis at the top dead center of the second squish area space is set to be less than 4% of the stroke amount of the piston 2.

図１２と図１３と図１４を使って、第６実施例を説明する。
図１２は、第１実施例に第６実施例の構成を加えた平面図です。図１３は、第２実施例に第６実施例の構成を加えた平面図です。図１４は、第１実施例に第６実施例の構成を加えた断面図です。
第６実施例は、第１から第４までの実施例に以下の構成を加える。
第１４直線２８は、第１底面９の中心と第４底面１２の中心を結ぶ直線から第１底面９の半径と第４底面１２の半径を削除した直線です。
第３円弧は、第１円弧の一部です。第３円弧は、第３点１４を中点とする円弧です。第３弧の長さは、第１４直線２８の長さの１５０％です。
第３３壁面領域２６は、シリンダーヘッドの壁面部分です。第３３壁面領域２６は、第１４直線２８と第３円弧の間に位置する。
ピストン２の上面の一部である第３０壁面領域２７は、上死点時に、第３３壁面領域２６に対面する。
上死点時の第１スキッシュエリア空間は、第３３壁面領域２６と上死点時の第３０壁面領域２７の間に形成される。
図１４に示す様に、第３３壁面領域２６の垂直断面の形と上死点時の第３０壁面領域２７の垂直断面の形は、おおよそ平行です。
なお、第３３壁面領域２６と第３０壁面領域２７は、平面に限定されない。この事は、第５実施例と同様です。
第１スキッシュエリア空間の上死点時のシリンダー中心軸と平行な方向の長さが、ピストン２のストローク量の４％未満に設定される。 A sixth embodiment will be described with reference to FIGS. 12, 13, and 14.
FIG. 12 is a plan view in which the configuration of the sixth embodiment is added to the first embodiment. FIG. 13 is a plan view in which the configuration of the sixth embodiment is added to the second embodiment. FIG. 14 is a sectional view in which the configuration of the sixth embodiment is added to the first embodiment.
In the sixth embodiment, the following configuration is added to the first to fourth embodiments.
The fourteenth straight line 28 is a straight line obtained by deleting the radius of the first bottom surface 9 and the radius of the fourth bottom surface 12 from the straight line connecting the center of the first bottom surface 9 and the center of the fourth bottom surface 12.
The third arc is a part of the first arc. The third arc is an arc with the third point 14 as the midpoint. The length of the third arc is 150% of the length of the 14th straight line 28.
The 33rd wall surface area 26 is a wall surface portion of the cylinder head. The thirty-third wall region 26 is located between the fourteenth straight line 28 and the third arc.
The 30th wall surface region 27 which is a part of the upper surface of the piston 2 faces the 33rd wall surface region 26 at the top dead center.
The first squish area space at the top dead center is formed between the 33rd wall surface area 26 and the 30th wall surface area 27 at the top dead center.
As shown in FIG. 14, the shape of the vertical cross section of the 33rd wall surface region 26 and the shape of the vertical cross section of the 30th wall surface region 27 at the top dead center are approximately parallel.
In addition, the 33rd wall surface area | region 26 and the 30th wall surface area | region 27 are not limited to a plane. This is the same as the fifth embodiment.
The length in the direction parallel to the cylinder central axis at the top dead center of the first squish area space is set to be less than 4% of the stroke amount of the piston 2.

第５実施例と第６実施例の作用を説明する。
第１点火プラグ付近の既燃焼ガスの膨張によって、第１底面９から第３点付近の空間に未燃焼の混合気が押され、第２底面１０から第４点付近の空間に未燃焼の混合気が押される。そして、第２点火プラグ付近の既燃焼ガスの膨張によって、第３底面１１から第４点付近の空間に未燃焼の混合気が押される。
高負荷時の燃焼行程期間に、ピストン２は全ストローク量の約０．６％下降する。
圧縮上死点時の第３点付近の空間と第４点付近の空間の２つの空間のシリンダー中心軸と平行な方向の長さがピストンのストロークの４％の時、圧縮比１３の燃焼室の前記の２つの空間は、燃焼行程中に、容積が約１６％増加する。前記の２つの空間のシリンダー中心軸と平行な方向の長さが２．５％に設定される時は、容積が約２８％増加する。
すると、３個の排気弁の底面から押された未燃焼の混合気が、圧縮上死点時の前記の２つの空間に侵入する。前記の２つの空間の容積の増加に対して、燃焼室の平均的な高さの空間部分の燃焼行程中の容積の増加は、約８％です。
すると、第３点付近の空間と第４点付近の空間の混合気部分の膨張によって、温度の低下要因が増し、排気弁から２つの空間に流れ込んだ混合気部分の燃焼速度も制限され、燃焼行程の後半の燃焼圧力値の上昇が制限される。
従って、耐ノッキング性が向上する。
The operation of the fifth and sixth embodiments will be described.
Due to the expansion of the burnt gas in the vicinity of the first spark plug, the unburned mixture is pushed from the first bottom surface 9 to the space near the third point, and the unburned mixture from the second bottom surface 10 to the space near the fourth point. I feel depressed. The unburned air-fuel mixture is pushed from the third bottom surface 11 to the space near the fourth point by the expansion of the burnt gas near the second spark plug.
During the combustion stroke period at high load, the piston 2 descends by about 0.6% of the total stroke amount.
Combustion chamber with a compression ratio of 13 when the length in the direction parallel to the cylinder central axis of the space near the third point and the space near the fourth point at the time of compression top dead center is 4% of the piston stroke. These two spaces increase in volume by about 16% during the combustion stroke. When the length of the two spaces in the direction parallel to the cylinder central axis is set to 2.5%, the volume increases by about 28%.
Then, the unburned air-fuel mixture pushed from the bottom surfaces of the three exhaust valves enters the two spaces at the time of compression top dead center. Compared to the increase in volume of the two spaces mentioned above, the increase in volume during the combustion stroke of the space part of the average height of the combustion chamber is about 8%.
Then, the expansion of the air-fuel mixture in the space near the third point and the space near the fourth point increases the temperature reduction factor, and the combustion speed of the air-fuel mixture flowing into the two spaces from the exhaust valve is also limited. The increase in the combustion pressure value in the second half of the stroke is limited.
Therefore, the knocking resistance is improved.

第１実施例の平面図。The top view of 1st Example. 第１実施例の平面図。The top view of 1st Example. 第１実施例の平面図。The top view of 1st Example. 第２吸気弁を増設する第２実施例の平面図。The top view of 2nd Example which adds a 2nd intake valve. 第２吸気弁を増設する第２実施例の平面図。The top view of 2nd Example which adds a 2nd intake valve. 第２吸気弁を増設する第２実施例の平面図。The top view of 2nd Example which adds a 2nd intake valve. 第２吸気弁と第３吸気弁を増設する第２実施例の平面図。The top view of 2nd Example which adds a 2nd intake valve and a 3rd intake valve. 第４実施例の平面図。The top view of 4th Example. 第５実施例の平面図。The top view of 5th Example. 第５実施例の平面図Plan view of the fifth embodiment 第５実施例の断面図。Sectional drawing of 5th Example. 第６実施例の平面図。The top view of 6th Example. 第６実施例の平面図。The top view of 6th Example. 第６実施例の断面図。Sectional drawing of 6th Example. 従来の技術である特許文献１の５弁式燃焼室の平面図。The top view of the 5-valve combustion chamber of patent document 1 which is a prior art. 特許文献２の図１に相当する従来の技術の図。The figure of the prior art corresponded to FIG. 従来の技術であるＭａｓｅｒａｔｉの６バルブエンジンの燃焼室の平面図。The top view of the combustion chamber of Maserati's 6-valve engine which is a conventional technique. 従来の技術である特許文献４の燃焼室の平面図。The top view of the combustion chamber of patent document 4 which is a prior art.

１・・・シリンダーの上端の内周
２・・・ピストン
３・・・燃焼室
４・・・第１点火プラグ
５・・・第２点火プラグ
６・・・第１点
７・・・第２点
８・・・第１直線
９・・・第１排気弁の底面である第１底面
１０・・・第２排気弁の底面である第２底面
１１・・・第３排気弁の底面である第３底面
１２・・・第１吸気弁の底面である第４底面
１３・・・第２吸気弁の底面
１４・・・第３点
１５・・・第４点
１６・・・第２直線
１７・・・第３仮想垂直面
１８・・・第４仮想垂直面
１９・・・第３４直線
２０・・・第１２直線
２１・・・第２３直線
２２・・・第１３直線
２３・・・第３吸気弁の底面
２４・・・第４４壁面領域
２５・・・ピストン上面の一部である第４０壁面領域
２６・・・第３３壁面領域
２７・・・ピストン上面の一部である第３０壁面領域
２８・・・第１４直線
1 ... Inner circumference of upper end of cylinder 2 ... Piston
3 ... Combustion chamber
4 ... 1st spark plug 5 ... 2nd spark plug 6 ... 1st point 7 ... 2nd point 8 ... 1st straight line
9... First bottom surface 10 that is the bottom surface of the first exhaust valve... Second bottom surface 11 that is the bottom surface of the second exhaust valve... Third surface 12 that is the bottom surface of the third exhaust valve. 4th bottom surface 13 which is the bottom surface of 1 intake valve ... Bottom surface of 2nd intake valve
14 ... Third point
15 ... 4th point 16 ... 2nd straight line 17 ... 3rd virtual vertical surface 18 ... 4th virtual vertical surface 19 ... 34th straight line 20 ... 12th straight line
21 ... 23rd straight line 22 ... 13th straight line
23 ... Bottom surface of the third intake valve 24 ... 44th wall surface area
25... 40th wall surface region 26 that is a part of the piston upper surface 26... 33th wall surface region 27.

Claims (6)

４サイクル火花点火式エンジンの一つの燃焼室において、
第１から第４までの点はシリンダーの上端の内周に位置し、前記内周は仮想水平面に位置し、
前記第１点と前記第２点によって前記内周は第１円弧と第２円弧に区分され、
前記第３点は前記第１円弧の中点であり、前記第４点は前記第２円弧の中点であり、
第１直線は前記第１点から第１点火プラグの中心電極を経由してシリンダー中心軸に達し、
第２直線は前記第２点から第２点火プラグの中心電極を経由して前記シリンダー中心軸に達し、
前記第１円弧に沿って第１吸気弁の底面である第４底面と第１排気弁の底面である第１底面が設置され、
前記第２円弧に沿って第２排気弁の底面である第２底面と第３排気弁の底面である第３底面が設置され、
前記第１底面と前記第２底面の両方に隣接して前記第１点火プラグが位置し、
前記第３底面と前記第４底面の両方に隣接して前記第２点火プラグが位置し、
第１直径は前記シリンダーの直径であり、
前記第１底面の直径の値と前記第２底面の直径の値と前記第３底面の直径の値の和が前記第１直径の値の８３％未満に設定され、
第３仮想垂直面に前記シリンダー中心軸と前記第３点が位置し、第４仮想垂直面に前記シリンダー中心軸と前記第４点が位置し、前記第３仮想垂直面と前記第４仮想垂直面は前記仮想水平面に対して垂直な仮想面であり、
第１３直線は前記第３仮想垂直面と直交し、前記第１３直線は前記第１底面の中心から前記第３仮想垂直面に至る直線であり、
前記第１３直線の長さは前記第１底面の半径よりも長い値に設定され、
第２３直線は前記第２底面の中心と前記第３底面の中心を結ぶ直線から前記第２底面の半径と前記第３底面の半径を除外した直線であり、
前記第２３直線の長さが前記第１直径の値の１８％を超える値に設定される事を特徴とする１つの燃焼室に３個の排気弁が設置されるエンジン。 In one combustion chamber of a 4-cycle spark ignition engine,
The first to fourth points are located on the inner circumference of the upper end of the cylinder, the inner circumference is located on a virtual horizontal plane,
The inner circumference is divided into a first arc and a second arc by the first point and the second point,
The third point is a midpoint of the first arc, and the fourth point is a midpoint of the second arc;
The first straight line reaches the cylinder central axis from the first point via the center electrode of the first spark plug,
The second straight line reaches the cylinder center axis from the second point via the center electrode of the second spark plug,
A fourth bottom surface that is a bottom surface of the first intake valve and a first bottom surface that is a bottom surface of the first exhaust valve are installed along the first arc.
A second bottom surface that is a bottom surface of the second exhaust valve and a third bottom surface that is a bottom surface of the third exhaust valve are installed along the second arc,
The first spark plug is located adjacent to both the first bottom surface and the second bottom surface;
The second spark plug is located adjacent to both the third bottom surface and the fourth bottom surface;
The first diameter is the diameter of the cylinder,
The sum of the value of the diameter of the first bottom surface, the value of the diameter of the second bottom surface and the value of the diameter of the third bottom surface is set to be less than 83% of the value of the first diameter;
The cylinder central axis and the third point are located on a third virtual vertical plane, the cylinder central axis and the fourth point are located on a fourth virtual vertical plane, and the third virtual vertical plane and the fourth virtual vertical are The plane is a virtual plane perpendicular to the virtual horizontal plane,
The thirteenth straight line is orthogonal to the third virtual vertical plane, the thirteenth straight line is a straight line from the center of the first bottom surface to the third virtual vertical plane,
The length of the thirteenth straight line is set to a value longer than the radius of the first bottom surface,
The 23rd straight line is a straight line obtained by excluding the radius of the second bottom surface and the radius of the third bottom surface from a straight line connecting the center of the second bottom surface and the center of the third bottom surface,
The engine in which three exhaust valves are installed in one combustion chamber, wherein the length of the 23rd straight line is set to a value exceeding 18% of the value of the first diameter. ４サイクル火花点火式エンジンの一つの燃焼室において、
第１から第４までの点はシリンダーの上端の内周に位置し、前記内周は仮想水平面に位置し、
前記第１点と前記第２点によって前記内周は第１円弧と第２円弧に区分され、
前記第３点は前記第１円弧の中点であり、前記第４点は前記第２円弧の中点であり、
第１直線は前記第１点から第１点火プラグの中心電極を経由してシリンダー中心軸に達し、
第２直線は前記第２点から第２点火プラグの中心電極を経由して前記シリンダー中心軸に達し、
前記第１円弧に沿って第１吸気弁の底面である第４底面と第１排気弁の底面である第１底面が設置され、
前記第２円弧に沿って第２排気弁の底面である第２底面と第３排気弁の底面である第３底面が設置され、
前記第１底面と前記第２底面の両方に隣接して前記第１点火プラグが位置し、
前記第３底面と前記第４底面の両方に隣接して前記第２点火プラグが位置し、
第１直径は前記シリンダーの直径であり、
前記第１底面の直径の値と前記第２底面の直径の値と前記第３底面の直径の値の和が前記第１直径の値の８３％未満に設定され、
第３仮想垂直面に前記シリンダー中心軸と前記第３点が位置し、第４仮想垂直面に前記シリンダー中心軸と前記第４点が位置し、前記第３仮想垂直面と前記第４仮想垂直面は前記仮想水平面に対して垂直な仮想面であり、
第１３直線は前記第３仮想垂直面と直交し、前記第１３直線は前記第１底面の中心から前記第３仮想垂直面に至る直線であり、
前記第１３直線の長さは前記第１底面の半径よりも長い値に設定され、
第２３直線は前記第２底面の中心と前記第３底面の中心を結ぶ直線から前記第２底面の半径と前記第３底面の半径を除外した直線であり、
前記第２３直線の長さが前記第１直径の値の１８％を超える値に設定され、
第６壁面領域は前記第３点と前記第１底面の中心と前記第２底面の中心と前記第４点と前記第３底面の中心と前記第４底面の中心と前記第３点を結ぶ６本の直線によって囲まれる六角形の壁面領域であり、
第７壁面領域は前記第６壁面領域から前記第１底面と前記第２底面と前記第３底面と前記第４底面を除外した壁面領域であり、
前記第１吸気弁以外の吸気弁が少なくとも１個増設され、
前記第１吸気弁以外の前記吸気弁の底面の中心が前記第７壁面領域に位置する事を特徴とする一つの燃焼室に３個の排気弁が設置されるエンジン。 In one combustion chamber of a 4-cycle spark ignition engine,
The first to fourth points are located on the inner circumference of the upper end of the cylinder, the inner circumference is located on a virtual horizontal plane,
The inner circumference is divided into a first arc and a second arc by the first point and the second point,
The third point is a midpoint of the first arc, and the fourth point is a midpoint of the second arc;
The first straight line reaches the cylinder central axis from the first point via the center electrode of the first spark plug,
The second straight line reaches the cylinder center axis from the second point via the center electrode of the second spark plug,
A fourth bottom surface that is a bottom surface of the first intake valve and a first bottom surface that is a bottom surface of the first exhaust valve are installed along the first arc.
A second bottom surface that is a bottom surface of the second exhaust valve and a third bottom surface that is a bottom surface of the third exhaust valve are installed along the second arc,
The first spark plug is located adjacent to both the first bottom surface and the second bottom surface;
The second spark plug is located adjacent to both the third bottom surface and the fourth bottom surface;
The first diameter is the diameter of the cylinder,
The sum of the value of the diameter of the first bottom surface, the value of the diameter of the second bottom surface and the value of the diameter of the third bottom surface is set to be less than 83% of the value of the first diameter;
The cylinder central axis and the third point are located on a third virtual vertical plane, the cylinder central axis and the fourth point are located on a fourth virtual vertical plane, and the third virtual vertical plane and the fourth virtual vertical are The plane is a virtual plane perpendicular to the virtual horizontal plane,
The thirteenth straight line is orthogonal to the third virtual vertical plane, the thirteenth straight line is a straight line from the center of the first bottom surface to the third virtual vertical plane,
The length of the thirteenth straight line is set to a value longer than the radius of the first bottom surface,
The 23rd straight line is a straight line obtained by excluding the radius of the second bottom surface and the radius of the third bottom surface from a straight line connecting the center of the second bottom surface and the center of the third bottom surface,
The length of the 23rd straight line is set to a value exceeding 18% of the value of the first diameter;
The sixth wall surface region connects the third point, the center of the first bottom surface, the center of the second bottom surface, the fourth point, the center of the third bottom surface, the center of the fourth bottom surface, and the third point 6. A hexagonal wall area surrounded by straight lines of books,
The seventh wall surface region is a wall surface region excluding the first bottom surface, the second bottom surface, the third bottom surface, and the fourth bottom surface from the sixth wall surface region,
At least one intake valve other than the first intake valve is added,
An engine in which three exhaust valves are installed in one combustion chamber, wherein the center of the bottom surface of the intake valve other than the first intake valve is located in the seventh wall surface region. 前記第１底面の直径の値と前記第２底面の直径の値と前記第３底面の直径の値の和が前記第１直径の値の７３％未満に設定され、
第１角度は前記第２直線が前記シリンダー中心軸を中心にして前記第４底面を経由して前記第１直線の位置まで回転した角度であり、
前記第１角度が１２０度から２３０度までの範囲内に設定され、
前記第２３直線の長さが前記第１直径の値の２４％を超える値に設定される事を特徴とする前記請求項１と前記請求項２のいずれか一つの前記請求項に記載された１つの燃焼室に３個の排気弁が設置されるエンジン。 The sum of the value of the diameter of the first bottom surface, the value of the diameter of the second bottom surface and the value of the diameter of the third bottom surface is set to be less than 73% of the value of the first diameter;
The first angle is an angle obtained by rotating the second straight line about the cylinder central axis through the fourth bottom surface to the position of the first straight line,
The first angle is set within a range of 120 degrees to 230 degrees;
The length of the 23rd straight line is set to a value that exceeds 24% of the value of the first diameter, According to any one of the claims 1 and 2, An engine with three exhaust valves installed in one combustion chamber. 第１２直線は前記第１底面の中心と前記第２底面の中心を結ぶ直線から前記第１底面の半径と前記第２底面の半径を削除した直線であり、
第３４直線は前記第３底面の中心と前記第４底面の中心を結ぶ直線から前記第３底面の半径と前記第４底面の半径を削除した直線であり、
前記第１２直線は前記第１点火プラグの前記中心電極と前記シリンダー中心軸の間に位置し、
前記第３４直線は前記第２点火プラグの前記中心電極と前記シリンダー中心軸の間に位置する事を特徴とする前記請求項１から前記請求項３までのいずれか一つの前記請求項に記載された１つの燃焼室に３個の排気弁が設置されるエンジン。 The twelfth straight line is a straight line obtained by deleting the radius of the first bottom surface and the radius of the second bottom surface from a straight line connecting the center of the first bottom surface and the center of the second bottom surface,
The 34th straight line is a straight line obtained by deleting the radius of the third bottom surface and the radius of the fourth bottom surface from the straight line connecting the center of the third bottom surface and the center of the fourth bottom surface,
The twelfth straight line is located between the center electrode of the first spark plug and the cylinder central axis,
The 34th straight line is located between the center electrode of the second spark plug and the center axis of the cylinder, according to any one of claims 1 to 3. An engine with three exhaust valves installed in a single combustion chamber. 第４円弧は前記内周の一部分であり、前記第４円弧は前記第４点を中点とする円弧であり、前記第４弧の長さは前記第２３直線の長さの１５０％であり、
第４４壁面領域はシリンダーヘッドの壁面の一部であり、第４４壁面領域は前記第２３直線と前記第４円弧の間に位置し、
ピストンの上面の一部である第４０壁面領域は上死点時に前記第４４壁面領域に対面し、
前記第４４壁面領域の垂直断面の形と上死点時の前記第４０壁面領域の垂直断面の形はおおよそ平行であり、
第２スキッシュエリア空間は前記第４４壁面領域と上死点時の前記第４０壁面領域の間に形成され、
前記第２スキッシュエリア空間の上死点時のシリンダー中心軸と平行な方向の長さが前記ピストンのストローク量の４％未満に設定される事を特徴とする前記請求項１から前記請求項４までのいずれか一つの前記請求項に記載された１つの燃焼室に３個の排気弁が設置されるエンジン。 The fourth arc is a part of the inner circumference, the fourth arc is an arc centered on the fourth point, and the length of the fourth arc is 150% of the length of the twenty-third straight line. ,
The 44th wall surface region is a part of the wall surface of the cylinder head, the 44th wall surface region is located between the 23rd straight line and the fourth arc,
The 40th wall surface area which is a part of the upper surface of the piston faces the 44th wall surface area at the top dead center,
The shape of the vertical cross section of the 44th wall surface region and the shape of the vertical cross section of the 40th wall surface region at the top dead center are approximately parallel,
The second squish area space is formed between the 44th wall surface area and the 40th wall surface area at the top dead center,
The length in the direction parallel to the cylinder central axis at the time of top dead center of the second squish area space is set to be less than 4% of the stroke amount of the piston. An engine in which three exhaust valves are installed in one combustion chamber according to any one of the preceding claims. 第１４直線は前記第１底面の中心と前記第４底面の中心を結ぶ直線から前記第１底面の半径と前記第４底面の半径を削除した直線であり、
第３円弧は前記内周の一部分であり、前記第３円弧は前記第３点を中点とする円弧であり、前記第３弧の長さは前記第１４直線の長さの１５０％であり、
第３３壁面領域はシリンダーヘッドの壁面の一部であり、前記第３３壁面領域は前記第１４直線と前記第３円弧の間に位置し、
ピストンの上面の一部である第３０壁面領域は上死点時に前記第３３壁面領域に対面し、
前記第３３壁面領域の垂直断面の形と上死点時の前記第３０壁面領域の垂直断面の形はおおよそ平行であり、
第１スキッシュエリア空間は前記第３３壁面領域と上死点時の前記第３０壁面領域の間に形成され、
前記第１スキッシュエリア空間の上死点時のシリンダー中心軸と平行な方向の長さが前記ピストンのストローク量の４％未満に設定される事を特徴とする前記請求項１から前記請求項４までのいずれか一つの前記請求項に記載された１つの燃焼室に３個の排気弁が設置されるエンジン。
The fourteenth straight line is a straight line obtained by deleting the radius of the first bottom surface and the radius of the fourth bottom surface from a straight line connecting the center of the first bottom surface and the center of the fourth bottom surface,
The third arc is a part of the inner circumference, the third arc is an arc centered on the third point, and the length of the third arc is 150% of the length of the fourteenth straight line. ,
The 33rd wall surface area is a part of the wall surface of the cylinder head, and the 33rd wall surface area is located between the 14th straight line and the 3rd arc,
The 30th wall surface region that is a part of the upper surface of the piston faces the 33rd wall surface region at the top dead center,
The shape of the vertical cross section of the 33rd wall surface region and the shape of the vertical cross section of the 30th wall surface region at the top dead center are approximately parallel,
The first squish area space is formed between the 33rd wall surface area and the 30th wall surface area at the top dead center,
The length in the direction parallel to the cylinder central axis at the top dead center of the first squish area space is set to be less than 4% of the stroke amount of the piston. An engine in which three exhaust valves are installed in one combustion chamber according to any one of the preceding claims.
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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006083765A (en) * 2004-09-16 2006-03-30 Toyota Motor Corp Spark ignition internal combustion engine
JP2014043782A (en) * 2012-08-24 2014-03-13 Mazda Motor Corp Combustion chamber structure of engine
JP2017031828A (en) * 2015-07-29 2017-02-09 マツダ株式会社 Combustion chamber structure of engine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006083765A (en) * 2004-09-16 2006-03-30 Toyota Motor Corp Spark ignition internal combustion engine
JP2014043782A (en) * 2012-08-24 2014-03-13 Mazda Motor Corp Combustion chamber structure of engine
JP2017031828A (en) * 2015-07-29 2017-02-09 マツダ株式会社 Combustion chamber structure of engine

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