JPS6327530B2 - - Google Patents
Info
- Publication number
- JPS6327530B2 JPS6327530B2 JP57215325A JP21532582A JPS6327530B2 JP S6327530 B2 JPS6327530 B2 JP S6327530B2 JP 57215325 A JP57215325 A JP 57215325A JP 21532582 A JP21532582 A JP 21532582A JP S6327530 B2 JPS6327530 B2 JP S6327530B2
- Authority
- JP
- Japan
- Prior art keywords
- intake valve
- intake
- valve port
- opened
- port
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000002485 combustion reaction Methods 0.000 claims description 38
- 230000003111 delayed effect Effects 0.000 claims description 4
- 239000000446 fuel Substances 0.000 description 27
- 239000000203 mixture Substances 0.000 description 23
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000003292 diminished effect Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000002000 scavenging effect Effects 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
Classifications
-
- 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
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Description
【発明の詳細な説明】
本発明は、２個の吸気弁口と１個の排気弁口を
燃焼室に開口した３弁式内燃機関に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a three-valve internal combustion engine having two intake valve ports and one exhaust valve port opening into a combustion chamber.
この種内燃機関は、一般に、狭い燃焼室の天井
面において吸気弁口の総合有効面積を充分に大き
く得ることができるので、充填効率を高めること
ができ、しかも１個の吸気弁口の有効面積は比較
的小さいので、これを開閉する吸気弁の小径化を
図つてその慣性重量を軽減し、機関の高速運転時
における動弁機構に対する各吸気弁の追従性を良
好にすることができ、よつて優れた高速出力性能
を発揮し得る利点がある。 In general, this kind of internal combustion engine can increase the total effective area of the intake valve port on the ceiling surface of the narrow combustion chamber, so it is possible to increase the charging efficiency, and the effective area of one intake valve port can be increased. Since this is relatively small, the diameter of the intake valves that open and close it can be reduced to reduce its inertia weight, and the ability of each intake valve to follow the valve mechanism during high-speed engine operation can be improved. It has the advantage of being able to exhibit excellent high-speed output performance.
本発明は、このような形式の機関において、燃
焼室天井面にスワールガイドを相対向する吸気弁
口及び排気弁口間に介入するように突設すること
により、混合気が燃焼室への流入時にスワールを
生起するようにし、その混合気の空燃比の均一化
を図ると共にその燃焼の立上りを促進し、もつて
前述のような利点を助長させると共に燃費の低減
を図ることを目的とする。 In this type of engine, the present invention prevents the air-fuel mixture from flowing into the combustion chamber by protruding a swirl guide from the ceiling surface of the combustion chamber so as to intervene between an intake valve port and an exhaust valve port that face each other. The purpose of this invention is to generate a swirl at times, to equalize the air-fuel ratio of the air-fuel mixture, and to promote the start of combustion, thereby promoting the above-mentioned advantages and reducing fuel consumption.
そして上記目的を達成するために本発明は、機
関本体に形成される燃焼室の天井面を略中央部の
稜線から両側に向つて下る二つの天井斜面より構
成し、一方の天井斜面には第１、第２吸気弁によ
り開閉される一対の第１、第２吸気弁口を前記稜
線に沿い並列して開口し、他方の天井斜面には、
前記第１吸気弁口との対向位置で排気弁により開
閉される１個の排気弁口を開口すると共に前記第
２吸気弁口との対向位置で点火栓を配設し、さら
に前記天井面には燃焼室周縁より第１吸気弁口及
び排気弁口間に介入するように延びるスワールガ
イドを突設し、このスワールガイドの前記第１吸
気弁口周縁に沿つた側面を絶壁状に起立した第１
ガイド面に、また前記排気弁口周縁に沿つた側面
を緩やかに傾斜した第２ガイド面にそれぞれ形成
し、前記第１吸気弁の開弁時期よりも前記第２吸
気弁の開弁時期を遅らせたことを特徴とする。 In order to achieve the above object, the present invention consists of a ceiling surface of a combustion chamber formed in an engine body with two ceiling slopes descending from a ridgeline in the approximately central part toward both sides, and one ceiling slope has a slope. 1. A pair of first and second intake valve ports opened and closed by a second intake valve are opened in parallel along the ridgeline, and the other ceiling slope is
One exhaust valve port opened and closed by an exhaust valve is opened at a position opposite to the first intake valve port, and an ignition plug is disposed at a position opposite to the second intake valve port, and further on the ceiling surface. A swirl guide is provided extending from the periphery of the combustion chamber so as to intervene between the first intake valve port and the exhaust valve port, and a swirl guide is provided with a swirl guide that extends in a precipitous manner from the side surface along the periphery of the first intake valve port. 1
A second guide surface is formed on the guide surface and a gently inclined side surface along the circumference of the exhaust valve port, and the opening timing of the second intake valve is delayed from the opening timing of the first intake valve. It is characterized by:
以下、図面により本発明の一実施例について説
明する。図示の内燃機関はクロスフロー型４サイ
クルガソリン機関であつて、その機関本体Ｅは、
シリンダブロツク１と、それの上面にガスケツト
３を介して重合結着されるシリンダヘツド２とを
備え、シリンダブロツク１に形成されたシリンダ
４内にはピストン５が摺合される。シリンダヘツ
ド２の底面には、ピストン５上面に対向する部分
に燃焼室６が凹設され、この燃焼室６の天井面７
は、略中央部の稜線Ｌから両側に向つて下る二つ
の天井斜面７1，７2よりなつている。 An embodiment of the present invention will be described below with reference to the drawings. The illustrated internal combustion engine is a cross-flow type four-cycle gasoline engine, and the engine body E is:
It comprises a cylinder block 1 and a cylinder head 2 which is superimposed and bonded to the upper surface of the cylinder block 1 via a gasket 3. A piston 5 is slidably fitted into a cylinder 4 formed in the cylinder block 1. A combustion chamber 6 is recessed in the bottom surface of the cylinder head 2 at a portion opposite to the top surface of the piston 5, and a ceiling surface 7 of the combustion chamber 6 is provided.
consists of two ceiling slopes 7 1 and 7 2 that descend from a ridgeline L at the approximate center toward both sides.
一方の天井斜面７1には、対をなす第１、第２
吸気弁口９1，９2が稜線Ｌに沿つて並列して開口
され、他方の天井斜面７2には１個の排気弁口１
０が第１吸気弁口９1との対向側に偏位して開口
され、シリンダヘツド２に螺着された点火栓１２
の電極が第２吸気弁口９2との対向側に偏位して
臨まされる。 One ceiling slope 7 1 has a pair of first and second slopes.
Intake valve ports 9 1 and 9 2 are opened in parallel along the ridge line L, and one exhaust valve port 1 is provided on the other ceiling slope 7 2 .
The spark plug 12 is opened with the valve opening deviated to the side opposite to the first intake valve port 91 , and is screwed onto the cylinder head 2.
The electrode is offset to face the side opposite to the second intake valve port 92 .
またさらに天井面７には、スワールガイド８が
燃焼室６の周縁より第１吸気弁口９1及び排気弁
口１０間に介入するように突設される。このスワ
ールガイド８は、第１吸気弁口９1周縁に沿つた
側面を絶壁状に起立した第１ガイド面８ａに形成
され、また排気弁口１０周縁に沿つた側面は比較
的緩かに傾斜した第２ガイド面８ｂに形成され、
さらに底面はシリンダヘツド２底面と同高のスキ
ツシユ面８ｃに形成される。 Further, a swirl guide 8 is provided on the ceiling surface 7 so as to protrude from the periphery of the combustion chamber 6 so as to intervene between the first intake valve port 9 1 and the exhaust valve port 10 . The swirl guide 8 is formed into a first guide surface 8a with a side surface along the circumference of the first intake valve port 91 standing upright in the form of a cliff, and a side surface along the circumference of the exhaust valve port 10 is relatively gently sloped. formed on the second guide surface 8b,
Further, the bottom surface is formed at a skid surface 8c at the same height as the bottom surface of the cylinder head 2.
シリンダヘツド２には吸気ポート１３及び排気
ポート１４が形成されており、吸気ポート１３
は、その内端側が第１、第２分岐ポート１３1，
１３2に分れていて前記第１、第２吸気弁口９1，
９2に連なり、その外端はシリンダヘツド２の一
側面に開口し、その開口部には燃料供給装置、例
えば気化器（図示せず）に連なる吸気管１５が連
結される。このようにシリンダヘツド２内で吸気
ポート１３を分岐させれば、吸気管１５の通路構
造を単純化させることができる。また、吸気ポー
ト１３は全体的に燃焼室６周縁の略接線方向を指
向するように形成される。 An intake port 13 and an exhaust port 14 are formed in the cylinder head 2.
The inner end side is the first and second branch ports 13 1 ,
13 2 and the first and second intake valve ports 9 1 ,
9 2 , its outer end opens to one side of the cylinder head 2, and an intake pipe 15 connected to a fuel supply device, such as a carburetor (not shown), is connected to the opening. By branching the intake port 13 within the cylinder head 2 in this manner, the passage structure of the intake pipe 15 can be simplified. Moreover, the intake port 13 is formed so as to be oriented generally in a substantially tangential direction of the periphery of the combustion chamber 6 .
一方、排気ポート１４は内端が前記排気弁口１
０に連なり、その外端はシリンダヘツド２の他側
面に開口し、その開口部に排気管（図示せず）が
連結される。 On the other hand, the inner end of the exhaust port 14 is located at the exhaust valve port 1.
0, its outer end opens to the other side of the cylinder head 2, and an exhaust pipe (not shown) is connected to the opening.
第１、第２吸気弁口９1，９2並びに排気弁口１
０は、シリンダヘツド２に弁ガイド１６1，１６
２，１７を介して摺動自在に支承される第１、第
２吸気弁１８1，１８2並びに排気弁１９によつて
それぞれ開閉されるようになつており、これらの
弁１８1，１８2，１９を開閉作動するための動弁
機構Ｍがシリンダヘツド２の上部に配設される。
動弁機構Ｍは、前記弁１８1，１８2，１９にそれ
ぞれ接続されてこれを閉じ方向に弾発する弁ばね
２０1，２０2，２１と、前記弁１８1，１８2，１
９にロツカアーム２２1，２２2，２３をそれぞれ
介して連動して、前記弁１８1，１８2，１９を各
弁ばね２０1，２０2，２１の弾発力に抗して開き
得る共通のカム軸２４とよりなつており、この動
弁機構Ｍによつて前記弁１８1，１８2，１９には
第４図に示すような開閉タイミングが与えられ
る。 First and second intake valve ports 9 1 , 9 2 and exhaust valve port 1
0 has valve guides 16 1 and 16 in the cylinder head 2.
The first and second intake valves 18 1 , 18 2 and the exhaust valve 19 are slidably supported via valves 2 and 17 to open and close the valves 18 1 and 18 2 , respectively. , 19 is disposed above the cylinder head 2.
The valve mechanism M includes valve springs 20 1 , 20 2 , 21 that are connected to the valves 18 1 , 18 2 , 19 and spring the valves in the closing direction, and valve springs 20 1 , 20 2 , 21 that are connected to the valves 18 1 , 18 2 , 19 and spring the valves 18 1 , 18 2 , 19 in the closing direction.
9 through rocker arms 22 1 , 22 2 , 23, respectively, to open the valves 18 1 , 18 2 , 19 against the elastic force of each valve spring 20 1 , 20 2 , 21. The valve mechanism M provides the valves 18 1 , 18 2 , and 19 with opening and closing timings as shown in FIG. 4.
即ち、排気弁１９に対向する第１吸気弁１８1
の開弁時期に対して点火栓１２に対向する第２吸
気弁１８2の開弁時期は遅らされ、且つ両吸気弁
１８1，１８2の閉弁時期は一致させてある。この
ようにすると、吸気行程において生じる混合気の
スワールが強化され、且各吸気弁口９1，９2から
燃焼室６に作用する吸気の脈動効果が干渉減退す
ることがない。 That is, the first intake valve 18 1 facing the exhaust valve 19
The opening timing of the second intake valve 18 2 facing the spark plug 12 is delayed with respect to the opening timing of the second intake valve 18 2 , and the closing timings of both intake valves 18 1 and 18 2 are made to coincide with each other. In this way, the swirl of the air-fuel mixture that occurs during the intake stroke is strengthened, and the pulsating effect of the intake air acting on the combustion chamber 6 from each of the intake valve ports 9 1 and 9 2 is not interfered with or diminished.
また、排気弁１９と第１、第２吸気弁１８1，
１８2の各開閉タイミング間には、所定の弁重合
期間l1，l2が設けられる。このようにすると、低
速運転時における排気の逆流を最小限に抑えつつ
高速運転時には排気慣性による掃気を効果的に行
うことができ、燃費及び出力の両面の性能向上に
寄与する。 Further, the exhaust valve 19 and the first and second intake valves 18 1 ,
Predetermined valve overlapping periods l 1 and l 2 are provided between each opening/closing timing of 18 2 . In this way, exhaust gas backflow during low-speed operation can be minimized while scavenging can be effectively performed using exhaust inertia during high-speed operation, contributing to improved performance in terms of both fuel efficiency and output.
さらに、両吸気弁１８1，１８2の開弁曲線を略
平行させ、これによつて第２吸気弁１８2の開弁
リフト量を第１吸気弁１８1のそれよりも小さく
してある。これに関連して開弁リフト量の小さい
第２吸気弁１８2の弁ばね２０2は他方の弁ばね２
０1よりばね力を弱く設定される。このようにす
ると、弁ばね２０2のばね力を弱くした分だけカ
ム軸２４の開弁トルクが減少し、動力の内部損失
が少なくなる。 Furthermore, the opening curves of both intake valves 18 1 and 18 2 are made substantially parallel, thereby making the opening lift amount of the second intake valve 18 2 smaller than that of the first intake valve 18 1 . In connection with this, the valve spring 20 2 of the second intake valve 18 2 with a small valve opening lift amount is replaced by the other valve spring 2
0 The spring force is set weaker than 1 . In this way, the valve opening torque of the camshaft 24 is reduced by the amount that the spring force of the valve spring 202 is weakened, and the internal loss of power is reduced.
次にこの実施例の作用を説明する。 Next, the operation of this embodiment will be explained.
機関が運転され、吸気行程が始まると、先ず第
１吸気弁１８1が開くので、第１分岐ポート１３1
を経て第１吸気弁口９1から燃焼室６に流入する
混合気は、第２吸気弁口９2側に指向する第１分
岐ポート１３1と、スワールガイド８の絶壁状の
第１ガイド面８ａとに誘導されて第１図矢印方向
のスワールを起こし、その混合気が緩傾斜の第２
ガイド面８ｂに達すると、それに誘導されて燃焼
室６の下方へスワール方向をそらされるので、ス
ワールは螺旋を描くように進行する。 When the engine is operated and the intake stroke begins, first the first intake valve 18 1 opens, so the first branch port 13 1 opens.
The air-fuel mixture that flows into the combustion chamber 6 from the first intake valve port 9 1 through the first branch port 13 1 directed toward the second intake valve port 9 2 and the cliff-shaped first guide surface of the swirl guide 8 8a, causing a swirl in the direction of the arrow in Figure 1, and the air-fuel mixture flows into the second
When the guide surface 8b is reached, the swirl direction is deflected downward into the combustion chamber 6 by being guided by the guide surface 8b, so that the swirl progresses in a spiral manner.
次いで第２吸気弁１８2が開くと、第２分岐ポ
ート１３2を経て第２吸気弁口９2から燃焼室６に
流入する混合気は、点火栓１２側に指向する第２
分岐ポート１３2に誘導されて同じく第１図矢印
方向のスワールを起こし、先に第１吸気弁口９1
から流入した混合気に合流しながらそのスワール
を強化する。これによつて燃焼室６における混合
気の空燃比は均一化される。 Next, when the second intake valve 18 2 opens, the air-fuel mixture flowing into the combustion chamber 6 from the second intake valve port 9 2 via the second branch port 13 2 flows into the second intake valve 18 2 directed toward the spark plug 12 side.
It is guided to the branch port 13 2 and similarly causes a swirl in the direction of the arrow in FIG. 1, and first the first intake valve port 9 1
The swirl is strengthened as it joins the air-fuel mixture flowing in from the air. As a result, the air-fuel ratio of the air-fuel mixture in the combustion chamber 6 is made uniform.
機関の圧縮行程では、スワールガイド８はピス
トン５の上面と協働して燃焼室６内の混合気にス
キツシユを与えるので、圧縮比を高めると共に混
合気の流動を強化することにも寄与する。 During the compression stroke of the engine, the swirl guide 8 cooperates with the upper surface of the piston 5 to give a squish to the air-fuel mixture in the combustion chamber 6, which contributes to increasing the compression ratio and strengthening the flow of the air-fuel mixture.
圧縮行程の終了近くで点火栓１２が作動され、
その火花放電により混合気に着火されるが、混合
気流は、前述のように第１吸気弁口９1、第２吸
気弁口９2、点火栓１２、排気弁口１０の順の方
向にスワール方向をとつているので、点火栓１２
で着火された直後、既に排気熱の影響より高温状
態となつている排気弁１９の周辺を通過すること
になり、その周辺で燃焼の立上りが促進される。 Near the end of the compression stroke, the spark plug 12 is activated,
The air-fuel mixture is ignited by the spark discharge, and the air-fuel mixture swirls in the order of the first intake valve port 9 1 , the second intake valve port 9 2 , the ignition plug 12 , and the exhaust valve port 10 as described above. Since the direction is taken, the spark plug 12
Immediately after being ignited, the fuel passes through the vicinity of the exhaust valve 19, which is already in a high temperature state due to the influence of exhaust heat, and the rise of combustion is promoted in that vicinity.
以上のように本発明によれば、燃焼室の天井面
を略中央部の稜線から両側に向つて下る二つの天
井斜面より構成し、一方の天井斜面には第１、第
２吸気弁により開閉される一対の第１、第２吸気
弁口を前記稜線に沿い並列して開口し、他方の天
井斜面には、前記第１吸気弁口との対向位置で排
気弁により開閉される１個の排気弁口を開口する
と共に前記第２吸気弁口との対向位置で点火栓を
配設したので、３つの弁口に干渉されずに点火栓
電極を燃焼室天井面中心部へ近接させて配置する
ことができ、従つて燃焼室の各方面への火焔伝播
距離を概ね等しくできて混合気の急速燃焼を図る
ことができる。 As described above, according to the present invention, the ceiling surface of the combustion chamber is composed of two ceiling slopes descending from a ridgeline in the approximately central portion toward both sides, and one ceiling slope is provided with valves that can be opened and closed by first and second intake valves. A pair of first and second intake valve ports are opened in parallel along the ridgeline, and a pair of first and second intake valve ports are opened in parallel along the ridgeline, and a pair of first and second intake valve ports are opened and closed by an exhaust valve at a position opposite to the first intake valve port on the other ceiling slope. Since the exhaust valve port is opened and the spark plug is placed opposite the second intake valve port, the spark plug electrode is placed close to the center of the ceiling surface of the combustion chamber without being interfered with by the three valve ports. Therefore, the flame propagation distance in each direction of the combustion chamber can be made approximately equal, and rapid combustion of the air-fuel mixture can be achieved.
また前記天井面には燃焼室周縁より第１吸気弁
口及び排気弁口間に介入するように延びるスワー
ルガイドを突設し、このスワールガイドの前記第
１吸気弁口周縁に沿つた側面を絶壁状に起立した
第１ガイド面に、また前記排気弁口周縁に沿つた
側面を緩やかに傾斜した第２ガイド面にそれぞれ
形成したので、吸気行程中、第１吸気弁の開弁に
より第１吸気弁口より燃焼室に流入した混合気は
スワールガイドの絶壁状第１ガイド面に誘導案内
されて、第２吸気弁口及び点火栓の各近傍を通過
して排気弁口に向かうスワールを生起し、一方、
第２吸気弁の開弁により第２吸気弁口より燃焼室
に流入した混合気は、前記スワールガイドによら
なくても点火栓の近傍を通過して排気弁口に向か
うスワールとなつて、上記第１吸気弁口からのス
ワール混合気と合流し、以上の結果、上記スワー
ル混合気はその空燃比の均一化が図られると共
に、着火直後に高温の排気弁周辺を通過すること
を余儀なくされて、その燃焼の立上りが促進さ
れ、その結果燃焼時間が短縮してアンチノツキン
グ性が向上し、また全体として燃焼が著しく改善
され、燃費の低減と出力性能の向上を達成するこ
とができる。 Further, a swirl guide extending from the periphery of the combustion chamber so as to intervene between the first intake valve port and the exhaust valve port is provided on the ceiling surface, and a side surface of the swirl guide along the periphery of the first intake valve port is formed into a cliff. Since the first guide surface stands upright in the form of a first guide surface, and the second guide surface is formed with a gently inclined side surface along the circumference of the exhaust valve port, during the intake stroke, when the first intake valve is opened, the first intake valve is opened. The air-fuel mixture that has flowed into the combustion chamber from the valve port is guided by the precipitous first guide surface of the swirl guide, passing through the vicinity of the second intake valve port and the spark plug to generate a swirl toward the exhaust valve port. ,on the other hand,
When the second intake valve is opened, the air-fuel mixture that flows into the combustion chamber from the second intake valve port passes through the vicinity of the ignition plug without using the swirl guide and swirls toward the exhaust valve port. The swirl mixture from the first intake valve port merges with the air-fuel mixture, and as a result, the air-fuel ratio of the swirl mixture is made uniform, and immediately after ignition, the swirl mixture is forced to pass around the high-temperature exhaust valve. , the start-up of combustion is promoted, and as a result, the combustion time is shortened and anti-knocking properties are improved, and overall combustion is significantly improved, reducing fuel consumption and improving output performance.
また特に前記第１吸気弁の開弁時期よりも前記
第２吸気弁の開弁時期を遅らせたので、吸気行程
開始当初の、第１吸気弁のみが先行して開弁した
状態では、第２吸気弁の開弁による絞り効果によ
り特に高速で第１吸気弁口から燃焼室に流入する
混合気をスワールガイドの絶壁状第１ガイド面に
勢いよく当てて、該第１ガイド面による誘導案内
作用を効果的に発揮させることができ、これによ
り第１吸気弁口からの高速流入混合気が強力なス
ワール流を生じ、一方、遅れて開弁する第２吸気
弁からの流入混合気は、その流速が比較的低くて
も、その流入方向が点火栓を略指向する関係上、
前記スワールガイドによることなく強力なスワー
ル流を生じ、従つて上記両スワール流の合流によ
つて全体として極めて強力なスワール流が得ら
れ、前述のスワール混合気による諸効果を一層確
実に発揮することができる。 In particular, since the opening timing of the second intake valve is delayed compared to the opening timing of the first intake valve, when only the first intake valve opens in advance at the beginning of the intake stroke, the second intake valve opens earlier than the first intake valve. Due to the throttling effect caused by opening the intake valve, the air-fuel mixture flowing into the combustion chamber from the first intake valve port at a particularly high speed is forcefully applied to the precipitous first guide surface of the swirl guide, and the first guide surface acts as a guiding guide. As a result, the high-speed inflowing air-fuel mixture from the first intake valve port produces a strong swirl flow, while the inflowing air-fuel mixture from the second intake valve, which opens later, generates a strong swirl flow. Even if the flow velocity is relatively low, the inflow direction is generally directed towards the ignition plug, so
A strong swirl flow is generated without using the swirl guide, and an extremely strong swirl flow is obtained as a whole by the merging of the two swirl flows, and the various effects of the swirl mixture described above are more reliably exhibited. Can be done.
図面は本発明の一実施例を示すもので、第１図
はシリンダヘツドの底面図、第１Ａ図及び第１Ｂ
図は第１図のＡ−Ａ及びＢ−Ｂ線断面図、第２図
及び第３図は第１図の−及び−線にそれ
ぞれ沿つた内燃機関の縦断面図、第４図はこの機
関の吸、排気弁の開閉タイミング図である。
Ｌ……稜線、Ｍ……動弁機構、２……シリンダ
ヘツド、４……シリンダ、５……ピストン、６…
…燃焼室、７……天井面、７1，７2……天井斜
面、８……スワールガイド、８ａ……第１ガイド
面、８ｂ……第２ガイド面、９1，９2……第１、
第２吸気弁口、１０……排気弁口、１２……点火
栓、１８1，１８2……第１、第２吸気弁、１９…
…排気弁。
The drawings show one embodiment of the present invention, and FIG. 1 is a bottom view of the cylinder head, FIG. 1A and FIG. 1B.
The figures are sectional views taken along lines A-A and B-B in Fig. 1, Figs. 2 and 3 are longitudinal sectional views of the internal combustion engine taken along lines - and -, respectively, in Fig. 1, and Fig. 4 is a longitudinal sectional view of the engine taken along lines - and - in Fig. 1, respectively. FIG. 3 is a timing chart of opening and closing of intake and exhaust valves. L...Ridge line, M...Valve mechanism, 2...Cylinder head, 4...Cylinder, 5...Piston, 6...
... Combustion chamber, 7 ... Ceiling surface, 7 1 , 7 2 ... Ceiling slope, 8 ... Swirl guide, 8a ... First guide surface, 8b ... Second guide surface, 9 1 , 9 2 ... Third guide surface 1,
Second intake valve port, 10... Exhaust valve port, 12... Spark plug, 18 1 , 18 2 ... First and second intake valves, 19...
...exhaust valve.
Claims (1)
略中央部の稜線Ｌから両側に向つて下る二つの天
井斜面７1，７2より構成し、一方の天井斜面７1
には第１、第２吸気弁１８1，１８2により開閉さ
れる一対の第１、第２吸気弁口９1，９2を前記稜
線Ｌに沿い並列して開口し、他方の天井斜面７2
には、前記第１吸気弁口９1との対向位置で排気
弁１９により開閉される１個の排気弁口１０を開
口すると共に前記第２吸気弁口９2との対向位置
で点火栓１２を配設し、さらに前記天井面７には
燃焼室６周縁より第１吸気弁口９1及び排気弁口
１０間に介入するように延びるスワールガイド８
を突設し、このスワールガイド８の前記第１吸気
弁口９1周縁に沿つた側面を絶壁状に起立した第
１ガイド面８ａに、また前記排気弁口１０周縁に
沿つた側面を緩やかに傾斜した第２ガイド面８ｂ
にそれぞれ形成し、前記第１吸気弁１８1の開弁
時期よりも前記第２吸気弁１８2の開弁時期を遅
らせた、３弁式内燃機関。 ２ 特許請求の範囲第１項記載のものにおいて、
前記第１、第２吸気弁口９1，９2は、前記機関本
体の一側面に開口する１本の吸気ポート１３の途
中から分けられた第１、第２分岐ポート１３1，
１３2にそれぞれ連なる、３弁式内燃機関。[Scope of Claims] 1. The ceiling surface 7 of the combustion chamber 6 formed in the engine body is composed of two ceiling slopes 7 1 and 7 2 that descend from the ridge line L at the approximate center toward both sides, and one ceiling slope 7 1
A pair of first and second intake valve ports 9 1 and 9 2 opened and closed by the first and second intake valves 18 1 and 18 2 are opened in parallel along the ridge line L, and the other ceiling slope 7 is opened. 2
, one exhaust valve port 10 opened and closed by an exhaust valve 19 is opened at a position opposite to the first intake valve port 9 1 , and an ignition plug 12 is opened at a position opposite to the second intake valve port 9 2 . Further, a swirl guide 8 is provided on the ceiling surface 7 and extends from the periphery of the combustion chamber 6 so as to intervene between the first intake valve port 91 and the exhaust valve port 10.
A side surface along the circumference of the first intake valve port 91 of the swirl guide 8 is formed into a first guide surface 8a that stands up in a precipitous manner, and a side surface along the circumference of the exhaust valve port 10 is formed into a gentle slope. Slanted second guide surface 8b
A three-valve internal combustion engine, wherein the opening timing of the second intake valve 18 2 is delayed from the opening timing of the first intake valve 18 1 . 2. In what is stated in claim 1,
The first and second intake valve ports 9 1 and 9 2 are first and second branch ports 13 1 , which are separated from the middle of one intake port 13 that opens on one side of the engine body.
13 3-valve internal combustion engine, each connected to 2 .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57215325A JPS59105926A (en) | 1982-12-08 | 1982-12-08 | Three valve type internal-combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57215325A JPS59105926A (en) | 1982-12-08 | 1982-12-08 | Three valve type internal-combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59105926A JPS59105926A (en) | 1984-06-19 |
| JPS6327530B2 true JPS6327530B2 (en) | 1988-06-03 |
Family
ID=16670427
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57215325A Granted JPS59105926A (en) | 1982-12-08 | 1982-12-08 | Three valve type internal-combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59105926A (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3584936D1 (en) * | 1984-10-17 | 1992-01-30 | Nissan Motor | INLET CHANNEL SYSTEM FOR AN INTERNAL COMBUSTION ENGINE WITH SEVERAL INLET VALVES PER COMBUSTION ROOM. |
| JPS61232327A (en) * | 1985-04-05 | 1986-10-16 | Mazda Motor Corp | Three valve type combustion chamber structure |
| JPS62113827A (en) * | 1985-11-13 | 1987-05-25 | Mazda Motor Corp | Structure of combustion chamber for engine |
| JPH077544Y2 (en) * | 1986-03-05 | 1995-02-22 | マツダ株式会社 | Engine combustion chamber structure |
| JPS6436919A (en) * | 1987-07-31 | 1989-02-07 | Mazda Motor | Supercharged engine |
| JP6115197B2 (en) * | 2013-03-08 | 2017-04-19 | スズキ株式会社 | Combustion chamber structure of internal combustion engine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5548104U (en) * | 1978-09-22 | 1980-03-29 | ||
| JPS5644418A (en) * | 1979-09-20 | 1981-04-23 | Honda Motor Co Ltd | Device for improving combustion of mixture in four-cycle internal combustion engine |
-
1982
- 1982-12-08 JP JP57215325A patent/JPS59105926A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5548104U (en) * | 1978-09-22 | 1980-03-29 | ||
| JPS5644418A (en) * | 1979-09-20 | 1981-04-23 | Honda Motor Co Ltd | Device for improving combustion of mixture in four-cycle internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59105926A (en) | 1984-06-19 |
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