JPH10325325A - Combustion chamber for spark ignition type engine - Google Patents
Combustion chamber for spark ignition type engineInfo
- Publication number
- JPH10325325A JPH10325325A JP13631397A JP13631397A JPH10325325A JP H10325325 A JPH10325325 A JP H10325325A JP 13631397 A JP13631397 A JP 13631397A JP 13631397 A JP13631397 A JP 13631397A JP H10325325 A JPH10325325 A JP H10325325A
- Authority
- JP
- Japan
- Prior art keywords
- cavity
- outer peripheral
- recess
- intake valve
- squish
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/26—Pistons having combustion chamber in piston head
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B1/00—Engines characterised by fuel-air mixture compression
- F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
- F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、火花点火式エンジ
ンの燃焼室に関する。The present invention relates to a combustion chamber of a spark ignition type engine.
【０００２】[0002]
【従来の技術】火花点火式エンジンの燃焼室の従来技術
として図４に示すものがある。これは、本発明と同様、
図４（Ａ）・（Ｂ）に示すように、ピストン頂面１０１
の中央部にキャビティ１０２を形成し、ピストン頂面１
０１の外周部にスキッシュ面１０３と吸気弁侵入用凹部
１０４とを形成し、吸気弁侵入用凹部１０４とキャビテ
ィ１０２とを連通させてある。2. Description of the Related Art FIG. 4 shows a prior art of a combustion chamber of a spark ignition type engine. This is similar to the present invention.
As shown in FIGS. 4A and 4B, the piston top surface 101
A cavity 102 is formed at the center of the piston top surface 1.
A squish surface 103 and an intake valve intrusion concave portion 104 are formed in the outer peripheral portion of 01, and the intake valve intrusion concave portion 104 and the cavity 102 are communicated.
【０００３】この従来技術では、図４（Ｂ）・（Ｄ）に
示すように、吸気弁侵入用凹部１０４は、吸気弁１１２
の弁頭１３２とスキッシュ面１０３との衝突を回避する
ことのみを目的とするため、その内底面１０５は浅い位
置でスキッシュ面１０３と平行に形成してある。In this prior art, as shown in FIGS. 4B and 4D, the intake valve intrusion recess 104 is
In order to avoid collision between the valve head 132 and the squish surface 103 only, the inner bottom surface 105 is formed at a shallow position and parallel to the squish surface 103.
【０００４】[0004]
【発明が解決しようとする課題】上記従来技術には次の
問題がある。上記従来技術では、図４（Ｂ）・（Ｄ）に
示すように、吸気弁侵入用凹部１０４の内底面１０５は
浅い位置でスキッシュ面１０３と平行に形成してあるた
め、吸気弁侵入用凹部１０４の内部容積は小さい。この
ため、図４（Ａ）・（Ｂ）に示すように、適性な圧縮比
を確保するためには、キャビティ１０２の内部容積を大
きくしておく必要があり、キャビティ１０２の内径を大
きく設定してある。このようにすると、図４（Ｃ）に示
すように、スキッシュ面１０３の幅が狭くなり、スキッ
シュ流１１３が弱くなるので、撹拌不足により、混合気
の濃度が不均一になり、燃焼効率が低下して、高出力が
得られない。The above prior art has the following problems. In the above prior art, as shown in FIGS. 4B and 4D, the inner bottom surface 105 of the intake valve intrusion recess 104 is formed at a shallow position and parallel to the squish surface 103, so that the intake valve intrusion recess 104 is formed. The internal volume of 104 is small. Therefore, as shown in FIGS. 4A and 4B, in order to secure an appropriate compression ratio, it is necessary to increase the internal volume of the cavity 102, and set the inner diameter of the cavity 102 to be large. It is. By doing so, as shown in FIG. 4C, the width of the squish surface 103 is reduced and the squish flow 113 is weakened, so that the concentration of the air-fuel mixture becomes non-uniform due to insufficient stirring and the combustion efficiency is reduced. As a result, high output cannot be obtained.
【０００５】上記従来技術では、撹拌不足によりキャビ
ティ１０２内の混合気に過濃部分と希薄部分とが形成さ
れる。混合気に過濃部分が形成されると、ここで燃焼温
度が局部的に高まるため、ＮＯXの発生量が多くなる。
また、混合気に希薄部分が形成されると、これが点火プ
ラグ１０９に接することにより、失火が起こりやすくな
るため、点火プラグ１０９の要求電圧が高まり、点火プ
ラグ１０９の寿命が短くなるとともに、電力消費量も多
くなる。[0005] In the above prior art, an air-fuel mixture in the cavity 102 is formed with an excessively rich portion and a lean portion due to insufficient stirring. When the rich portion is formed in the air-fuel mixture, the combustion temperature is locally increased here, so that the amount of generated NO X increases.
Further, if a lean portion is formed in the air-fuel mixture, it comes into contact with the spark plug 109 and misfire easily occurs. Therefore, the required voltage of the spark plug 109 increases, the life of the spark plug 109 is shortened, and power consumption is reduced. The amount also increases.
【０００６】上記従来技術では、図４（Ｂ）・（Ｄ）に
示すように、吸気弁侵入用凹部１０４の内底面１０５は
浅い位置でスキッシュ面１０３と平行に形成してあるた
め、図４（Ｄ）に示すように、キャビティ１０２内で発
生した火炎１１４は吸気弁侵入用凹部１０４には侵入し
にくい。ガスエンジンの場合、吸気弁侵入用凹部１０４
の内底面１０５には、吸気弁口１１５から吸気とともに
吸入されたブローバイガス中のオイルミスト等が付着
し、これが炭化物１１６となって膠着するが、上記のよ
うに、キャビティ１０２内で発生した火炎１１４が吸気
弁侵入用凹部１０４に侵入しにくいため、膠着した炭化
物１１６は火炎１１４によって焼却されることなく、堆
積により成長する。この炭化物１１６はある程度の大き
さに成長すると、ヒートポンイトとなり、過早着火が起
こり、燃焼効率が低くなる。In the above prior art, as shown in FIGS. 4B and 4D, the inner bottom surface 105 of the intake valve intrusion recess 104 is formed at a shallow position in parallel with the squish surface 103. As shown in (D), the flame 114 generated in the cavity 102 does not easily enter the intake valve entry concave portion 104. In the case of a gas engine, the intake valve intrusion recess 104
Oil mist and the like in the blow-by gas sucked together with the intake air from the intake valve port 115 adheres to the inner bottom surface 105 of the inner surface 105, and this adheres to the carbide 116. As described above, the flame generated in the cavity 102 Since it is difficult for the 114 to enter the intake valve entry concave portion 104, the adhered carbide 116 grows by deposition without being burned by the flame 114. When this carbide 116 grows to a certain size, it becomes a heat ponto, premature ignition occurs, and the combustion efficiency decreases.
【０００７】上記従来技術では、図４（Ｂ）・（Ｄ）に
示すように、吸気弁侵入用凹部１０４の内底面１０５は
浅い位置にあり、図４（Ｄ）に示すように、この内底面
１０５で炭化物１１６が堆積により成長するので、成長
した炭化物１１６に吸気弁１１２の弁頭１３２が衝突
し、吸気弁１１２や動弁装置が損傷するおそれがある。In the above prior art, as shown in FIGS. 4B and 4D, the inner bottom surface 105 of the intake valve intrusion recess 104 is at a shallow position, and as shown in FIG. Since the carbide 116 grows on the bottom surface 105 by deposition, the valve head 132 of the intake valve 112 collides with the grown carbide 116, and the intake valve 112 and the valve train may be damaged.
【０００８】各発明の課題は次の通りである。第１発明
の課題は、次の点にある。スキッシュ面の幅を広くし
て、スキッシュ流を強化すること。キャビティ内で発生
した火炎が吸気弁侵入用凹部にスムーズに侵入できるよ
うにすること。第２発明の課題は、第１発明の課題に加
え、次の点にある。キャビティ内の混合気をスムーズに
点火プラグに案内できるようにすること。第３発明の課
題は、第１発明の課題または第２発明の課題に加え、次
の点にある。キャビティ内の燃焼済みガスをスムーズに
排気弁口に案内できるようにすること。The objects of each invention are as follows. The object of the first invention is as follows. Widening the squish surface to enhance the squish flow. The flame generated in the cavity must be able to smoothly enter the intake valve entry recess. The object of the second invention is as follows in addition to the object of the first invention. The mixture in the cavity must be smoothly guided to the spark plug. The object of the third invention is as follows in addition to the object of the first invention or the object of the second invention. To enable the burned gas in the cavity to be smoothly guided to the exhaust port.
【０００９】[0009]
（第１発明）第１発明は、図１（Ａ）・（Ｂ）または図
３（Ａ）・（Ｂ）に示すように、ピストン頂面１の中央
部にキャビィティ２を形成し、ピストン頂面１の外周部
にスキッシュ面３と吸気弁侵入用凹部４とを形成し、吸
気弁侵入用凹部４とキャビティ２とを連通させた、火花
点火式エンジンの燃焼室において、次のようにしたこと
を特徴とする。すなわち、図１（Ｄ）または図３（Ｄ）
に示すように、吸気弁侵入用凹部４の内面５を、キャビ
ティ２の内底面６の外周縁部からスキッシュ面３の外周
縁部に向かう傾斜面または凹状の湾曲面としたことを特
徴とする。(First Invention) In the first invention, a cavity 2 is formed in the center of a piston top surface 1 as shown in FIGS. In the combustion chamber of a spark ignition type engine in which a squish surface 3 and an intake valve intrusion concave portion 4 are formed on the outer peripheral portion of the surface 1 and the intake valve intrusion concave portion 4 and the cavity 2 are communicated with each other, the following is performed. It is characterized by the following. That is, FIG. 1 (D) or FIG. 3 (D)
As shown in (1), the inner surface 5 of the intake valve intrusion concave portion 4 is characterized in that it is an inclined surface or a concave curved surface extending from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 to the outer peripheral edge of the squish surface 3. .
【００１０】（第２発明）第２発明は、図１（Ａ）・
（Ｂ）または図３（Ａ）・（Ｂ）に示すように、第１発
明において、ピストン頂面１の外周部に点火プラグ用凹
部７を形成し、図１（Ｅ）または図３（Ｅ）に示すよう
に、点火プラグ用凹部７の内面８を、キャビティ２の内
底面６の外周縁部からスキッシュ面３の外周縁部に向か
う傾斜面または凹状の湾曲面とし、点火プラグ用凹部７
を点火プラグ９に臨ませたことを特徴とする。(Second Invention) A second invention is shown in FIG.
As shown in FIG. 3 (B) or FIGS. 3 (A) and 3 (B), in the first invention, a recess 7 for an ignition plug is formed on the outer peripheral portion of the piston top surface 1, and FIG. 1 (E) or FIG. ), The inner surface 8 of the recess 7 for the spark plug is an inclined surface or a concave curved surface extending from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 toward the outer peripheral edge of the squish surface 3.
Facing the spark plug 9.
【００１１】（第３発明）第３発明は、図１（Ａ）・
（Ｂ）または図３（Ａ）・（Ｂ）に示すように、第１発
明または第２発明において、ピストン頂面１の外周部に
排気バルブ侵入用凹部１０を形成し、図１（Ｆ）または
図３（Ｆ）に示すように、排気弁侵入用凹部１０の内面
１１を、キャビティ２の内底面６の外周縁部からスキッ
シュ面３の外周縁部に向かう傾斜面または凹状の湾曲面
としたことを特徴とする。(Third invention) A third invention is shown in FIG.
As shown in FIG. 3 (B) or FIGS. 3 (A) and 3 (B), in the first invention or the second invention, an exhaust valve intrusion recess 10 is formed in the outer peripheral portion of the piston top surface 1, and FIG. Alternatively, as shown in FIG. 3 (F), the inner surface 11 of the exhaust valve intrusion recess 10 is formed by forming an inclined surface or a concave curved surface from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 to the outer peripheral edge of the squish surface 3. It is characterized by having done.
【００１２】[0012]
（第１発明）第１発明は、次の作用効果を奏する。第１
発明では、図１（Ｄ）または図３（Ｄ）に示すように、
吸気弁侵入用凹部４の内面５を、キャビティ２の内底面
６の外周縁部からスキッシュ面３の外周縁部に向かう傾
斜面または凹状の湾曲面としたので、吸気弁侵入用凹部
４の内部容積は大きくなる。このため、適性な圧縮比を
確保するためには、図１（Ａ）・（Ｂ）または図３
（Ａ）・（Ｂ）に示すように、キャビティ２の内部容積
を小さくしておく必要があり、キャビティ２の内径を小
さく設定できる。このようにすると、図１（Ｃ）または
図３（Ｃ）に示すように、スキッシュ面３の幅が広くな
り、スキッシュ流１３が強くなるので、十分な撹拌によ
り混合気の濃度が均一化され、燃焼効率が高くなり、高
出力が得られる。(First Invention) The first invention has the following effects. First
In the invention, as shown in FIG. 1 (D) or FIG. 3 (D),
Since the inner surface 5 of the intake valve intrusion recess 4 is an inclined surface or a concave curved surface from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 to the outer peripheral edge of the squish surface 3, the inside of the intake valve intrusion recess 4 is formed. The volume increases. For this reason, in order to secure an appropriate compression ratio, it is necessary to use FIG.
As shown in (A) and (B), the internal volume of the cavity 2 needs to be small, and the inner diameter of the cavity 2 can be set small. By doing so, as shown in FIG. 1C or FIG. 3C, the width of the squish surface 3 is increased and the squish flow 13 is strengthened, so that the concentration of the air-fuel mixture is made uniform by sufficient stirring. As a result, the combustion efficiency is increased and a high output is obtained.
【００１３】第１発明では、キャビティ２内の混合気は
十分に撹拌されるため、過濃部分や希薄部分が形成され
にくい。このため、混合気の過濃部分によって生じてい
た燃焼温度の局部的な高まりが防止され、ＮＯXの発生
量が少なくなる。また、混合気の希薄部分によって生じ
ていた失火が防止され、点火プラグ９の要求電圧が低く
なり、点火プラグ９の寿命を延長できるとともに、電力
消費量も少なくできる。In the first invention, the air-fuel mixture in the cavity 2 is sufficiently stirred, so that an excessively concentrated portion or a lean portion is not easily formed. For this reason, a local increase in the combustion temperature caused by the rich portion of the air-fuel mixture is prevented, and the amount of generated NO X is reduced. Further, misfire caused by the lean portion of the air-fuel mixture is prevented, the required voltage of the spark plug 9 is reduced, the life of the spark plug 9 can be extended, and the power consumption can be reduced.
【００１４】第１発明では、キャビティ２内を伝播する
火炎は、吸気弁侵入用凹部４の入口で絞られるため、吸
気弁侵入用凹部４への火炎伝播が遅れるため、燃焼速度
が遅くなり、燃焼温度が低くなるので、ＮＯXの発生量
が少なくなる。In the first aspect, the flame propagating in the cavity 2 is throttled at the entrance of the intake valve intrusion concave portion 4, so that the flame propagation to the intake valve intrusion concave portion 4 is delayed, so that the combustion speed is reduced. Since the combustion temperature is lowered, the amount of generated NO X is reduced.
【００１５】第１発明では、図１（Ｄ）または図３
（Ｄ）に示すように、吸気弁侵入用凹部４の内面５を、
キャビティ２の内底面６の外周縁部からスキッシュ面３
の外周縁部に向かう傾斜面または凹状の湾曲面としたの
で、キャビティ２内で発生した火炎１４が吸気弁侵入用
凹部４にスムーズに侵入する。ガスエンジンの場合、吸
気弁侵入用凹部４の内面５には、吸気弁口１５から吸気
とともに吸入されたブローバイガス中のオイルミスト等
が付着し、これが炭化物１６となって膠着するが、上記
のように、キャビティ２内で発生した火炎１４が吸気弁
侵入用凹部４にスムーズに侵入するので、膠着した炭化
物１６は火炎１４によって焼却され、堆積による成長が
妨げられる。このため、成長した炭化物１６によるヒー
トポンイトの発生が抑制され、過早着火が起こりにく
く、燃焼効率が高まる。In the first invention, FIG. 1D or FIG.
As shown in (D), the inner surface 5 of the intake valve intrusion recess 4 is
From the outer peripheral edge of the inner bottom surface 6 of the cavity 2 to the squish surface 3
As a result, the flame 14 generated in the cavity 2 smoothly enters the intake valve entry recess 4. In the case of a gas engine, oil mist or the like in the blow-by gas sucked together with the intake air from the intake valve port 15 adheres to the inner surface 5 of the intake valve indentation concave portion 4, which becomes a carbide 16 and sticks. As described above, since the flame 14 generated in the cavity 2 smoothly enters the intake valve intrusion concave portion 4, the adhered carbide 16 is incinerated by the flame 14 and growth due to deposition is hindered. For this reason, the generation of heat ponto by the grown carbide 16 is suppressed, premature ignition is unlikely to occur, and the combustion efficiency is increased.
【００１６】第１発明では、図１（Ｄ）または図３
（Ｄ）に示すように、吸気弁侵入用凹部４の内面５での
炭化物１６の成長が妨げられるうえ、吸気弁侵入用凹部
４がキャビティ２の内底面６に向かって深まっているた
め、炭化物１６への吸気弁１２の弁頭３２の衝突が起こ
りにくく、吸気弁１２や動弁装置が損傷するおそれが少
ない。In the first invention, FIG. 1 (D) or FIG.
As shown in (D), the growth of carbides 16 on the inner surface 5 of the intake valve intrusion recess 4 is prevented, and the carbides 16 are deepened toward the inner bottom surface 6 of the cavity 2 because the intake valve intrusion recess 4 is deepened toward the inner bottom surface 6 of the cavity 2. The collision of the valve head 32 of the intake valve 12 with the intake valve 16 hardly occurs, and the intake valve 12 and the valve train are less likely to be damaged.
【００１７】（第２発明）第２発明は、第１発明の作用
効果に加え、次の作用効果を奏する。第２発明では、図
１（Ｅ）または図３（Ｅ）に示すように、点火プラグ用
凹部７の内面８を、キャビティ２の内底面６の外周縁部
からスキッシュ面３の外周縁部に向かう傾斜面または凹
状の湾曲面とし、点火プラグ用凹部７を点火プラグ９に
臨ませたので、キャビティ２内で均一化された適性濃度
の混合気１７がスキッシュ流１３に押され、点火プラグ
用凹部７の内面８に沿って点火プラグ９に案内される。
このため、点火プラグ９の周囲に燃焼済みの残留ガスや
希薄な混合気があっても、これらが適性濃度の混合気１
７と入れ替わるので、失火が起こりにくく、点火プラグ
９の要求電圧が低くなり、点火プラグ９の寿命を延長で
きるとともに、電力消費量も少なくできる。(Second Invention) The second invention has the following functions and effects in addition to the functions and effects of the first invention. In the second invention, as shown in FIG. 1 (E) or FIG. 3 (E), the inner surface 8 of the spark plug recess 7 is moved from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 to the outer peripheral edge of the squish surface 3. Since the spark plug recess 7 faces the ignition plug 9, the mixture 17 having an appropriate concentration uniformized in the cavity 2 is pushed by the squish flow 13, and the spark plug recess 7 faces the ignition plug 9. It is guided to the spark plug 9 along the inner surface 8 of the recess 7.
For this reason, even if there is a burned residual gas or a lean mixture around the ignition plug 9, these are mixed with an appropriate concentration of the mixture 1
7, the misfire does not easily occur, the required voltage of the spark plug 9 is reduced, the life of the spark plug 9 can be extended, and the power consumption can be reduced.
【００１８】第３発明は、第１発明または第２発明の作
用効果に加え、次の作用効果を奏する。第３発明では、
図１（Ｆ）または図３（Ｆ）に示すように、排気弁侵入
用凹部１０の内面１１を、キャビティ２の内底面６の外
周縁部からスキッシュ面３の外周縁部に向かう傾斜面ま
たは凹状の湾曲面としたので、キャビティ２内の燃焼済
みガス１８が排気弁侵入用凹部１０の内面１１に沿って
排気弁口１９にスムーズに案内され、排気効率が高ま
り、燃焼効率が高まる。The third invention has the following functions and effects in addition to the functions and effects of the first or second invention. In the third invention,
As shown in FIG. 1 (F) or FIG. 3 (F), the inner surface 11 of the exhaust valve intrusion concave portion 10 is inclined from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 toward the outer peripheral edge of the squish surface 3. Because of the concave curved surface, the burned gas 18 in the cavity 2 is smoothly guided to the exhaust valve port 19 along the inner surface 11 of the exhaust valve intrusion concave portion 10, and the exhaust efficiency is increased, and the combustion efficiency is increased.
【００１９】第３発明では、図１（Ｆ）または図３
（Ｆ）に示すように、キャビティ２内を伝播する火炎
は、排気弁侵入用凹部１０の入口で絞られるため、排気
弁侵入用凹部１０への火炎伝播が遅れるため、燃焼速度
が遅くなり、燃焼温度が低くなるので、ＮＯXの発生量
が少なくなる。In the third invention, FIG. 1 (F) or FIG.
As shown in (F), the flame propagating in the cavity 2 is throttled at the entrance of the exhaust valve intrusion concave portion 10, so that the flame propagation to the exhaust valve intrusion concave portion 10 is delayed, so that the combustion speed becomes slow. Since the combustion temperature is lowered, the amount of generated NO X is reduced.
【００２０】[0020]
【発明の実施の形態】本発明の実施の形態を図面に基づ
いて説明する。図１と図２は本発明の第１実施形態を説
明する図である。このエンジンはガスヒートポンプまた
はコージェネレーション等に用いる多気筒ガスエンジン
である。Embodiments of the present invention will be described with reference to the drawings. FIG. 1 and FIG. 2 are diagrams illustrating a first embodiment of the present invention. This engine is a multi-cylinder gas engine used for a gas heat pump or cogeneration.
【００２１】このエンジンの構成は次の通りである。図
２（Ｂ）に示すように、シリンダブロック２０の各シリ
ンダ２１にピストン２２を内嵌し、シリンダブロック２
０の上部にシリンダヘッド２３を組み付けている。図２
（Ａ）に示すように、シリンダヘッド２３には吸気弁口
１５と排気弁口１９と点火プラグ差し込み口２４とを形
成し、吸気弁口１５と排気弁口１９から吸気ポート２５
と排気ポート２６とを左右逆向きに導出してある。The configuration of this engine is as follows. As shown in FIG. 2 (B), a piston 22 is fitted in each cylinder 21 of the cylinder block 20, and the cylinder block 2
The cylinder head 23 is attached to the upper part of the cylinder head 23. FIG.
As shown in (A), an intake valve port 15, an exhaust valve port 19, and a spark plug insertion port 24 are formed in the cylinder head 23, and the intake port 25 and the exhaust port
And the exhaust port 26 are led out in opposite directions.
【００２２】図２（Ａ）に示すように、シリンダ中心軸
線２７と平行な向きに見て、弁口寄り吸気ポート部分２
８は、シリンダ内周面２９の接線方向に沿って真っすぐ
に形成してある。吸気弁口１５の内径は排気弁口１９の
内径よりも大きく形成してある。吸気弁口１５には吸気
弁１２を着座させ、排気弁口１９には排気弁３１を着座
させている。図１（Ｅ）に示すように、点火プラグ差し
込み口２４には点火プラグ９を挿入してある。As shown in FIG. 2A, when viewed in a direction parallel to the cylinder center axis 27, the intake port portion 2 near the valve opening
8 is formed straight along the tangential direction of the cylinder inner peripheral surface 29. The inside diameter of the intake valve port 15 is formed larger than the inside diameter of the exhaust valve port 19. The intake valve 12 is seated on the intake valve port 15, and the exhaust valve 31 is seated on the exhaust valve port 19. As shown in FIG. 1 (E), the spark plug 9 is inserted into the spark plug insertion port 24.
【００２３】ピストン２２の構成は次の通りである。図
１（Ａ）・（Ｂ）に示すように、ピストン頂面１の中央
部にキャビィティ２を形成し、ピストン頂面１の外周部
にスキッシュ面３と吸気弁侵入用凹部４とを形成し、吸
気弁侵入用凹部４とキャビティ２とを連通させている。
図２（Ｂ）に示すように、キャビティ２はバブタブ型で
ある。吸気弁侵入用凹部４は、ピストン２２が上死点に
至った時に、開弁状態の吸気弁１２の弁頭３２を侵入さ
せ、吸気弁１２の弁頭３２とスキッシュ面３との衝突を
避けるためのものである。The structure of the piston 22 is as follows. As shown in FIGS. 1A and 1B, a cavity 2 is formed at the center of the piston top surface 1, and a squish surface 3 and an intake valve intrusion recess 4 are formed at the outer periphery of the piston top surface 1. In addition, the intake valve intrusion concave portion 4 communicates with the cavity 2.
As shown in FIG. 2B, the cavity 2 is a bubble tab type. The intake valve intrusion recess 4 allows the valve head 32 of the intake valve 12 in the opened state to enter when the piston 22 reaches the top dead center, thereby avoiding collision between the valve head 32 of the intake valve 12 and the squish surface 3. It is for.
【００２４】この実施形態では、図１（Ｄ）に示すよう
に、吸気弁侵入用凹部４の内面５を、キャビティ２の内
底面６の外周縁部からスキッシュ面３の外周縁部に向か
う傾斜面としている。このような構成によれば、吸気弁
侵入用凹部４の内部容積は大きくなる。このため、適性
な圧縮比を確保するためには、図１（Ａ）・（Ｂ）に示
すように、キャビティ２の内部容積を小さくしておく必
要があり、キャビティ２の内径を小さく設定できる。こ
のようにすると、図１（Ｃ）に示すように、スキッシュ
面３の幅が広くなり、スキッシュ流１３が強くなるの
で、十分な撹拌により混合気の濃度が均一化される。In this embodiment, as shown in FIG. 1D, the inner surface 5 of the intake valve intrusion recess 4 is inclined from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 toward the outer peripheral edge of the squish surface 3. With the face. According to such a configuration, the internal volume of the intake valve intrusion recess 4 becomes large. Therefore, in order to secure an appropriate compression ratio, it is necessary to reduce the internal volume of the cavity 2 as shown in FIGS. 1A and 1B, and the inner diameter of the cavity 2 can be set small. . By doing so, as shown in FIG. 1C, the width of the squish surface 3 is widened and the squish flow 13 is strengthened, so that the concentration of the air-fuel mixture is made uniform by sufficient stirring.
【００２５】この実施形態では、図１（Ａ）・（Ｂ）に
示すように、ピストン頂面１の外周部に点火プラグ用凹
部７を形成し、図１（Ｅ）に示すように、点火プラグ用
凹部７の内面８を、キャビティ２の内底面６の外周縁部
からスキッシュ面３の外周縁部に向かう傾斜面とし、点
火プラグ用凹部７を点火プラグ９に臨ませている。この
ような構成によれば、キャビティ２内で均一化された適
性濃度の混合気１７がスキッシュ流１３に押され、点火
プラグ用凹部７の内面８に沿って点火プラグ９に案内さ
れる。In this embodiment, as shown in FIGS. 1 (A) and 1 (B), a spark plug recess 7 is formed on the outer periphery of the piston top surface 1 and, as shown in FIG. The inner surface 8 of the concave portion 7 for the plug is an inclined surface extending from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 toward the outer peripheral edge of the squish surface 3, and the concave portion 7 for the ignition plug faces the ignition plug 9. According to such a configuration, the air-fuel mixture 17 having an appropriate concentration uniformized in the cavity 2 is pushed by the squish flow 13 and guided to the spark plug 9 along the inner surface 8 of the spark plug recess 7.
【００２６】この実施形態では、図１（Ａ）・（Ｂ）に
示すように、ピストン頂面１の外周部に排気弁侵入用凹
部１０を形成し、図１（Ｆ）に示すように、排気弁侵入
用凹部１０の内面１１を、キャビティ２の内底面６の外
周縁部からスキッシュ面３の外周縁部に向かう傾斜面と
している。このような構成によれば、キャビティ２内の
燃焼済みガス１８が排気弁侵入用凹部１０の内面１１に
沿って排気弁口１９にスムーズに案内される。排気弁侵
入用凹部１０は、ピストン２２が上死点に至った時に、
開弁状態の排気弁３１の弁頭３３を侵入させ、排気弁３
１の弁頭３３とピストン２２との衝突を避けるためのも
のである。In this embodiment, as shown in FIGS. 1A and 1B, an exhaust valve intrusion recess 10 is formed on the outer periphery of the piston top surface 1, and as shown in FIG. The inner surface 11 of the exhaust valve intrusion recess 10 is an inclined surface extending from the outer peripheral edge of the inner bottom surface 6 of the cavity 2 to the outer peripheral edge of the squish surface 3. According to such a configuration, the burned gas 18 in the cavity 2 is smoothly guided to the exhaust valve port 19 along the inner surface 11 of the exhaust valve entry recess 10. When the piston 22 reaches the top dead center, the exhaust valve intrusion recess 10
The valve head 33 of the exhaust valve 31 in the open state is made to enter, and the exhaust valve 3
This is for avoiding collision between the first valve head 33 and the piston 22.
【００２７】この実施形態では、図１（Ａ）に示すよう
に、シリンダ中心軸線２７と平行な向きに見て、吸気弁
１２の弁頭３２は吸気弁侵入用凹部４とキャビティ２と
に跨がるように配置し、排気弁３１の弁頭３３は排気弁
侵入用凹部１０とキャビティ２とに跨がるように配置
し、点火プラグ９の電極３４は点火プラグ用凹部７とキ
ャビティ２に跨がるように配置してある。In this embodiment, as shown in FIG. 1A, when viewed in a direction parallel to the cylinder center axis 27, the valve head 32 of the intake valve 12 straddles the intake valve intrusion recess 4 and the cavity 2. The valve head 33 of the exhaust valve 31 is disposed so as to straddle the exhaust valve entry recess 10 and the cavity 2, and the electrode 34 of the ignition plug 9 is connected to the ignition plug recess 7 and the cavity 2. It is arranged to straddle.
【００２８】図３に示す第２実施形態では、図３（Ｄ）
〜（Ｆ）に示すように、吸気弁侵入用凹部４の内面５と
点火プラグ用凹部７の内面８と排気弁侵入用凹部１０の
内面１１を、いずれも、キャビティ２の内底面６の外周
縁部からスキッシュ面３の外周縁部に向かう凹状の湾曲
面とした。他の構成は、第１実施形態と同じである、図
３中、第１実施形態と同一の要素には、同一の符号を付
しておく。この第２実施形態のものでも、第１実施形態
のものと同様の機能が得られる。In the second embodiment shown in FIG. 3, FIG.
As shown in (F), the inner surface 5 of the concave portion 4 for the intake valve entry, the inner surface 8 of the concave portion 7 for the spark plug, and the inner surface 11 of the concave portion 10 for the exhaust valve entry are all located outside the inner bottom surface 6 of the cavity 2. A concave curved surface extending from the peripheral edge toward the outer peripheral edge of the squish surface 3 was used. Other configurations are the same as those of the first embodiment. In FIG. 3, the same elements as those of the first embodiment are denoted by the same reference numerals. In the second embodiment, the same function as in the first embodiment can be obtained.
【図１】第１実施形態に係るエンジンの燃焼室を説明す
る図で、図１（Ａ）はシリンダの横断平面図、図１
（Ｂ）はピストンの斜視図、図１（Ｃ）は図１（Ａ）の
Ｃ−Ｃ線断面図、図１（Ｄ）は図１（Ａ）のＤ−Ｄ線断
面図、図１（Ｅ）は図１（Ａ）のＥ−Ｅ線断面図、図１
（Ｆ）は図１（Ａ）のＦ−Ｆ線断面図である。FIG. 1 is a view for explaining a combustion chamber of an engine according to a first embodiment. FIG. 1 (A) is a cross-sectional plan view of a cylinder, and FIG.
1B is a perspective view of the piston, FIG. 1C is a cross-sectional view taken along line CC of FIG. 1A, FIG. 1D is a cross-sectional view taken along line DD of FIG. E) is a sectional view taken along line EE of FIG.
(F) is a sectional view taken along line FF of FIG.
【図２】第１実施形態に係るエンジンの燃焼室を説明す
る図で、図２（Ａ）はシリンダヘッドの縦断平面図、図
２（Ｂ）は図２（Ａ）のＢ−Ｂ線断面図である。FIG. 2 is a view for explaining a combustion chamber of the engine according to the first embodiment. FIG. 2 (A) is a vertical cross-sectional view of a cylinder head, and FIG. 2 (B) is a cross section taken along line BB of FIG. 2 (A). FIG.
【図３】第２実施形態に係るエンジンの燃焼室を説明す
る図で、図３（Ａ）はシリンダの横断平面図、図３
（Ｂ）はピストンの斜視図、図３（Ｃ）は図３（Ａ）の
Ｃ−Ｃ線断面図、図３（Ｄ）は図３（Ａ）のＤ−Ｄ線断
面図、図３（Ｅ）は図３（Ａ）のＥ−Ｅ線断面図、図３
（Ｆ）は図３（Ａ）のＦ−Ｆ線断面図である。FIG. 3 is a view for explaining a combustion chamber of an engine according to a second embodiment, and FIG. 3 (A) is a cross-sectional plan view of a cylinder;
3 (B) is a perspective view of the piston, FIG. 3 (C) is a cross-sectional view taken along line CC of FIG. 3 (A), FIG. 3 (D) is a cross-sectional view taken along line DD of FIG. FIG. 3E is a sectional view taken along line EE of FIG.
FIG. 3F is a sectional view taken along line FF of FIG.
【図４】従来技術に係るエンジンの燃焼室を説明する図
で、図４（Ａ）はシリンダの横断平面図、図４（Ｂ）は
ピストンの斜視図、図４（Ｃ）は図４（Ａ）のＣ−Ｃ線
断面図、図４（Ｄ）は図４（Ａ）のＤ−Ｄ線断面図であ
る。4A and 4B are views for explaining a combustion chamber of an engine according to a conventional technique. FIG. 4A is a cross-sectional plan view of a cylinder, FIG. 4B is a perspective view of a piston, and FIG. 4A is a cross-sectional view taken along line CC, and FIG. 4D is a cross-sectional view taken along line DD in FIG.
１…ピストン頂面、２…キャビティ、３…スキッシュ
面、４…吸気弁侵入用凹部、５…内面、６…内底面、７
…点火プラグ用凹部、８…内面、９…点火プラグ、１０
…排気弁侵入用凹部、１１…内面。DESCRIPTION OF SYMBOLS 1 ... Piston top surface, 2 ... Cavity, 3 ... Squish surface, 4 ... Intake valve entry recess, 5 ... Inner surface, 6 ... Inner bottom surface, 7
... recess for spark plug, 8 ... inner surface, 9 ... spark plug, 10
... recesses for exhaust valve entry, 11 ... inner surface.
Claims (3)
ィ(２)を形成し、ピストン頂面(１)の外周部にスキッシ
ュ面(３)と吸気弁侵入用凹部(４)とを形成し、吸気弁侵
入用凹部(４)とキャビティ(２)とを連通させた、火花点
火式エンジンの燃焼室において、 吸気弁侵入用凹部(４)の内面(５)を、キャビティ(２)の
内底面(６)の外周縁部からスキッシュ面(３)の外周縁部
に向かう傾斜面または凹状の湾曲面とした、ことを特徴
とする火花点火式エンジンの燃焼室。Cavity (2) is formed at the center of piston top surface (1), and squish surface (3) and intake valve indentation recess (4) are formed at the outer periphery of piston top surface (1). Then, in the combustion chamber of the spark ignition type engine in which the intake valve intrusion recess (4) communicates with the cavity (2), the inner surface (5) of the intake valve intrusion recess (4) is connected to the cavity (2). A combustion chamber of a spark ignition type engine, wherein the combustion chamber has an inclined surface or a concave curved surface extending from an outer peripheral edge of an inner bottom surface (6) to an outer peripheral edge of a squish surface (3).
の燃焼室において、 ピストン頂面(１)の外周部に点火プラグ用凹部(７)を形
成し、点火プラグ用凹部(７)の内面(８)を、キャビティ
(２)の内底面(６)の外周縁部からスキッシュ面(３)の外
周縁部に向かう傾斜面または凹状の湾曲面とし、点火プ
ラグ用凹部(７)を点火プラグ(９)に臨ませた、ことを特
徴とする火花点火式エンジンの燃焼室。2. A combustion chamber of a spark ignition type engine according to claim 1, wherein a recess (7) for a spark plug is formed on an outer peripheral portion of a piston top surface (1), and an inner surface of the recess (7) for a spark plug. (8) with the cavity
(2) An inclined surface or a concave curved surface extending from the outer peripheral edge of the inner bottom surface (6) to the outer peripheral edge of the squish surface (3), and the ignition plug recess (7) faces the ignition plug (9). A combustion chamber for a spark ignition engine.
点火式エンジンの燃焼室において、 ピストン頂面(１)の外周部に排気弁侵入用凹部(１０)を
形成し、排気弁侵入用凹部(１０)の内面(１１)を、キャ
ビティ(２)の内底面(６)の外周縁部からスキッシュ面
(３)の外周縁部に向かう傾斜面または凹状の湾曲面とし
た、ことを特徴とする火花点火式エンジンの燃焼室。3. A combustion chamber of a spark ignition engine according to claim 1, wherein an exhaust valve indentation recess (10) is formed in an outer peripheral portion of the piston top surface (1). The inner surface (11) of the recess (10) is squished from the outer peripheral edge of the inner bottom surface (6) of the cavity (2).
(3) A combustion chamber of a spark ignition type engine, wherein the inclined surface is directed toward an outer peripheral portion or a concave curved surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13631397A JPH10325325A (en) | 1997-05-27 | 1997-05-27 | Combustion chamber for spark ignition type engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13631397A JPH10325325A (en) | 1997-05-27 | 1997-05-27 | Combustion chamber for spark ignition type engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10325325A true JPH10325325A (en) | 1998-12-08 |
Family
ID=15172291
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13631397A Pending JPH10325325A (en) | 1997-05-27 | 1997-05-27 | Combustion chamber for spark ignition type engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10325325A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014043777A (en) * | 2012-08-24 | 2014-03-13 | Mazda Motor Corp | Combustion chamber structure of engine |
| JP2014043782A (en) * | 2012-08-24 | 2014-03-13 | Mazda Motor Corp | Combustion chamber structure of engine |
| CN104428507A (en) * | 2012-04-13 | 2015-03-18 | 卡特彼勒能源方案有限公司 | Piston of an internal combustion engine |
| WO2022016403A1 (en) * | 2020-07-22 | 2022-01-27 | 宁波吉利罗佑发动机零部件有限公司 | Engine combustion system, gasoline engine for hybrid vehicle, and vehicle |
-
1997
- 1997-05-27 JP JP13631397A patent/JPH10325325A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104428507A (en) * | 2012-04-13 | 2015-03-18 | 卡特彼勒能源方案有限公司 | Piston of an internal combustion engine |
| JP2014043777A (en) * | 2012-08-24 | 2014-03-13 | Mazda Motor Corp | Combustion chamber structure of engine |
| JP2014043782A (en) * | 2012-08-24 | 2014-03-13 | Mazda Motor Corp | Combustion chamber structure of engine |
| WO2022016403A1 (en) * | 2020-07-22 | 2022-01-27 | 宁波吉利罗佑发动机零部件有限公司 | Engine combustion system, gasoline engine for hybrid vehicle, and vehicle |
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