JPS5835225A - Spark-ignition 2-cycle engine - Google Patents
Spark-ignition 2-cycle engineInfo
- Publication number
- JPS5835225A JPS5835225A JP56133877A JP13387781A JPS5835225A JP S5835225 A JPS5835225 A JP S5835225A JP 56133877 A JP56133877 A JP 56133877A JP 13387781 A JP13387781 A JP 13387781A JP S5835225 A JPS5835225 A JP S5835225A
- Authority
- JP
- Japan
- Prior art keywords
- fresh air
- exhaust
- scavenging
- air
- valve
- 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
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
-
- 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
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- 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
- F02B75/00—Other engines
- F02B75/12—Other methods of operation
- F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
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
【発明の詳細な説明】
本発明は烏渦流、高速燃焼室を有する火花点火式2サイ
クル機関に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a spark-ignition two-stroke engine having a vortex flow and a high-speed combustion chamber.
近年世界的なエネルギー不足などにより原油などの高騰
や代替エネルギー開発が深刻化しており、省エネルギー
化が大きな社会問題になっている。そして、自動車等で
はより熱効率の高いエンジンが要求されるようになって
いる。In recent years, due to global energy shortages, the price of crude oil has skyrocketed, and the development of alternative energy sources has become increasingly serious, making energy conservation a major social issue. In addition, automobiles and the like are increasingly required to have engines with higher thermal efficiency.
一方自動車の排ガスによる公害が社会問題化し、汎用の
4サイクル機関では排ガスを浄化するだめに、一般使用
時には成るべく燃料を薄くして排ガス中の未燃成分を減
らしているのか大勢をしめるようになってきている。On the other hand, pollution caused by automobile exhaust gas has become a social problem, and in order to purify the exhaust gas in general-purpose 4-stroke engines, many people are asking whether the fuel is diluted as much as possible during general use to reduce unburned components in the exhaust gas. It has become to.
このように空燃比を薄くした場合、・火炎伝播速度が遅
′くなる。そこで、吸気時にスワール(回転流)を加え
たり、副燃焼室を設けて副燃焼室からでる噴出流やスキ
ッシュ等で出来るだけ速く撹拌燃焼をさせたり、燃焼室
における火炎伝播距離を知かくするような燃焼室形状を
1失したりして燃費の向上等を図っており、これにより
かなりの効果を上げることに成功している。When the air-fuel ratio is reduced in this way, the flame propagation speed becomes slower. Therefore, it is necessary to add a swirl (rotating flow) during intake, to create a sub-combustion chamber, and use jets and squish from the sub-combustion chamber to stir combustion as quickly as possible, and to increase the distance of flame propagation in the combustion chamber. The aim is to improve fuel efficiency by eliminating the traditional shape of the combustion chamber, and as a result, we have succeeded in achieving considerable results.
ところが、4 +Jイクル機関の場合、ピストン速度が
速いため燃焼工程時間が短かく、点火時期を早めなけれ
ばならず、排気バルブの開き始め時期が早く、(平均で
釣下死点前55°前後が多い)コンロッドの慣性も大き
いなど、4サイクル機関では特有の欠点がある。However, in the case of a 4+J cycle engine, the piston speed is high, so the combustion process time is short, and the ignition timing must be advanced, and the exhaust valve begins to open early (on average, around 55 degrees before bottom dead center). 4-stroke engines have their own drawbacks, such as the high inertia of the connecting rod.
またディーげル機関の場合は燃焼が緩慢なために、ピス
トン往1関の理想である上死点付近で早く燃焼させると
いう点で欠【ノる所がある。Furthermore, since combustion is slow in the case of Diegel engines, there is a deficiency in the ability to burn quickly near top dead center, which is the ideal for piston strokes.
その証明として回転を上げると不完全燃焼を起こすこと
が判明している。As proof of this, it has been found that increasing the speed causes incomplete combustion.
2サイクル機関の場合は4サイクル機関のように独立し
た排気行程を持たないため、その掃気効率が性能に大き
く影響する。In the case of a two-stroke engine, unlike a four-stroke engine, it does not have an independent exhaust stroke, so its scavenging efficiency greatly affects performance.
掃気方法としては大別してループ掃気方式、クロス掃気
方式、それにユニフロ掃気方式があげられ、ループ掃気
方式及びクロス掃気方式では排気孔をシリンダーの比較
的高い位置に設けなければならないところから、ピスト
ン有効行程が短かくなりゃすい欠点がある。、
一方、コニフロ掃気方式には排気がシリンダー頭部の弁
から排出され、新気がシリンダー下部壁の掃気孔から供
給される弁排気型と、また反対にシリンダー頭部の弁か
ら新気が供給され、排気をシリンダ一孔から排出させる
弁操気型があり、弁排気型では高温の排気により弁が加
熱され弁が伽みやJく、また多量の排ガスを頭上弁を通
して排出しなければならないところから、新気容量に比
べ排気容量が大きく大型の弁、またt、L弁数を増やす
必要がある!
この点弁昂気型は排気孔がピストンによっ(開かれるた
め、孔面積が急激に増加し理想的なlJI気噴出が行わ
れ、また頭上弁は新気によ・)(冷却されて加熱の心配
はないのであるが、弁の下部に掃気流の影を生じるので
渦流のため新気、排気の混合を生じ掃気効率を低下させ
る欠点がある。Scavenging methods can be roughly divided into loop scavenging, cross scavenging, and uniflow scavenging. In loop scavenging and cross scavenging, the exhaust hole must be installed at a relatively high position in the cylinder, so the effective stroke of the piston is It has the disadvantage that it tends to become shorter. On the other hand, the Coniflo scavenging system has a valve exhaust type in which exhaust gas is discharged from a valve in the cylinder head and fresh air is supplied through a scavenging hole in the lower wall of the cylinder; There is a valve operated type in which the exhaust gas is discharged from one hole in the cylinder.In the valve exhaust type, the valve is heated by the high temperature exhaust gas, causing the valve to sag, and a large amount of exhaust gas must be discharged through an overhead valve. Therefore, it is necessary to use a large valve with a large exhaust capacity compared to the fresh air capacity, and to increase the number of T and L valves! In this point valve pumping type, the exhaust hole is opened by the piston, so the hole area increases rapidly and ideal lJI air is ejected, and the overhead valve is cooled and heated by fresh air. However, since the shadow of the scavenging air flow is created at the bottom of the valve, there is a drawback that fresh air and exhaust air are mixed due to the vortex flow, reducing the scavenging efficiency.
本発明は−F述のように汎用のエンジンの欠点とりると
ころを改善し、かつ各エンジンの利貞とするところを極
力取り入れた優秀なエンジンを提供しようとするもので
ある。 ・本ブを明のエンジンは基本的には
ユニフロ頭上弁吸−気式の火花点火式2サイクル機関で
ある。The present invention aims to improve the shortcomings of general-purpose engines as described in -F, and to provide an excellent engine that incorporates the advantages of each engine as much as possible.・This engine is basically a spark ignition two-stroke engine with an overhead valve intake system.
コニフロ掃気方式の弁掃気型において弁1・側、の掃気
流の影を生ずる渦のために緒排気が混合するのを頭上吸
撮気弁下部に形設の特殊形状の燃焼室により解消し、ま
た火花点火式とし、4サイクル機関の半分の回転数で・
作動させるものであり、2υイクル機関でありながら各
行程の時間を長く取ることができて効率よく作動させる
ようにし、圧縮比は上死点手前近くで燃料が層状噴射さ
せるため圧縮熱で自発火を起さない程度に^圧縮比と1
にとができ、また回転数が低いことと、排気口孔稙が大
きくとれることによって排気孔の位置が低く設定できる
ために吸掃気効率が−高く、有効行程が最大限に長く設
定でき、更にディーゼル機関と同じく給気を絞らな・い
構成のため部分負荷の低速時においてもトルクが大きく
、乗用車、バス、トラックをはじめ広範囲にわたって使
用できるようにしたものである。In the valve scavenging type of the Coniflo scavenging system, the mixing of the exhaust gas due to the vortices that cause the shadow of the scavenging air flow on the valve 1 side is eliminated by a specially shaped combustion chamber formed at the bottom of the overhead intake air valve. In addition, it is a spark ignition type, and the rotation speed is half that of a 4-cycle engine.
Although it is a 2υ cycle engine, each stroke can take a long time to operate efficiently, and the compression ratio is near the top dead center, where the fuel is injected in layers, so the heat of compression causes spontaneous ignition. ^ Compression ratio and 1 to the extent that it does not cause
In addition, due to the low rotational speed and the large exhaust hole, the position of the exhaust hole can be set low, resulting in high suction and scavenging efficiency, and the effective stroke can be set as long as possible. Like a diesel engine, it does not throttle the air supply, so it has a large torque even at low speeds under partial load, making it suitable for use in a wide range of applications, including passenger cars, buses, and trucks.
以下、本発明の実施例を図面について説明する。Embodiments of the present invention will be described below with reference to the drawings.
1はシリンダー、2はピストン、3はシリンダーヘッド
のスキッシュ部で、このスキッシュ部3の上の部分には
吸Ill気弁4が設けられる。1 is a cylinder, 2 is a piston, 3 is a squish portion of the cylinder head, and an intake valve 4 is provided above the squish portion 3.
吸帰気弁4は通常スプリングにより弁座5に圧着され、
吸顛気管6から膨張室8に進入する暖缶1気を制御?l
φ。7は吸操気弁4と膨張室8間に形成した特殊碗型の
燃焼室兼渦流形成室−ぐ、その壁面全体が円弧面で開口
が若干絞り形状で細長形にできている。9はこの燃焼室
兼渦流形IIA至7に通じて設けた燃料供給通路で、こ
の通路9内に燃料噴射弁10とその下部に点火プラグ1
1を装着する。12はシリンダー下部壁に設けた排気孔
で1排気管13に連通している。The intake/return valve 4 is normally pressed onto the valve seat 5 by a spring.
Controlling the warm canister air entering the expansion chamber 8 from the suction trachea 6? l
φ. Reference numeral 7 denotes a special bowl-shaped combustion chamber/vortex forming chamber formed between the intake air valve 4 and the expansion chamber 8, the entire wall surface of which is an arcuate surface, and the opening is slightly constricted and elongated. Reference numeral 9 denotes a fuel supply passage connected to this combustion chamber/vortex type IIA to 7. Inside this passage 9, there is a fuel injection valve 10 and a spark plug 1 below it.
Attach 1. 12 is an exhaust hole provided in the lower wall of the cylinder and communicates with 1 exhaust pipe 13.
本発明は上記の如く構成したものであり、次に作用を説
明する。The present invention is constructed as described above, and its operation will be explained next.
本発明は火花点火式4サイクル機関の半分の速1& C
作動させるものであり、第4図に示づ行程図に基づいて
、その圧縮行程から説明するーと、圧縮行程の接期に燃
料噴射弁10を開いて燃料噛躬が行われる。ここで燃料
は通路9を介して先ず燃焼室兼渦流形成室7に噴出し層
状になって膨張室8に向う。燃料噴射弁10が閉じ燃料
噴射直後の上死点手前で点火プラグ11により火花点火
がなされτ高圧縮及び高渦流やスキッシュ等で急速層状
燃焼となる。そしてピストン2が下降し、シリンダー下
部壁の排気孔12が開かれると排気は一気にシリンダー
外に排出されることになりその後、少し頭上吸掃気弁4
が燃焼室兼渦流形成室7の半分程の位置まで開かれ、燃
焼室兼渦流形成室7において渦流をともなった掃気新気
入替が排気孔12が閉じるまで行われ、排気口12が閉
じて後、若干の過給を行い吸掃気弁4を閉じ圧縮行程へ
移り、前記同様のサイクルを繰り返す。The present invention is a spark ignition type 4-cycle engine with half speed 1&C.
Based on the stroke diagram shown in FIG. 4, the compression stroke will be explained. The fuel injection valve 10 is opened during the engagement phase of the compression stroke to inject fuel. Here, the fuel is first injected into the combustion chamber/vortex forming chamber 7 through the passage 9, and then flows into the expansion chamber 8 in the form of a layer. Immediately after the fuel injection valve 10 is closed and the fuel is injected, a spark is ignited by the spark plug 11 just before top dead center, resulting in rapid stratified combustion due to high compression τ and high vortex flow, squish, etc. Then, when the piston 2 descends and the exhaust hole 12 in the lower cylinder wall is opened, the exhaust gas is discharged out of the cylinder at once.
is opened to about half of the combustion chamber/vortex forming chamber 7, scavenging fresh air is exchanged with a vortex in the combustion chamber/vortex forming chamber 7 until the exhaust port 12 is closed, and after the exhaust port 12 is closed, Then, a slight supercharging is performed, the intake air valve 4 is closed, the engine moves to the compression stroke, and the same cycle as described above is repeated.
以上のように本発明は、シリンダーヘッドの部分に特殊
碗型の燃焼室兼渦流形成室を設け゛C1掃気新気入替時
に当該燃焼室兼渦流形成室で新気の積極的渦流を生起し
て掃気作用をなすようにしたから、新気排気の混合が少
なく、また燃料噴射及び点火すこの燃焼室兼渦流形成室
に対して行われ急速層状燃焼を実現して理想的燃焼とす
るものであり、熱効率が高く、しかも給気を絞らない構
成のため、部分負荷の低速時においてもトルクが大きく
、また高温高圧縮比であるため、多種類の燃料が使用可
能であり、更に回転数が低くピストンコンロッドの慣性
による機械的損失も少ない等の優れた効果を秦する。As described above, the present invention provides a special bowl-shaped combustion chamber/vortex forming chamber in the cylinder head part, and actively generates a vortex of fresh air in the combustion chamber/vortex forming chamber when C1 scavenging fresh air is replaced. Since it has a scavenging effect, there is less mixing of fresh air exhaust, and it also performs rapid stratified combustion in the combustion chamber and vortex forming chamber of the fuel injection and ignition shaft, resulting in ideal combustion. , has high thermal efficiency, and has a configuration that does not restrict supply air, so it has large torque even at low speeds under partial load, and because of its high temperature and high compression ratio, it can use a variety of fuels and has a low rotational speed. It has excellent effects such as less mechanical loss due to the inertia of the piston connecting rod.
図面は本発明の実施例を示し、第1図はシリンダーの縦
断面図、第2図はシリンダーヘツ、ド部正面図、第3図
はシリンダーヘッド部斜視図、第4゛図は行程線図であ
る。
1・・・シリンダー、 2・・・ピストン、3・
・・スキッシュ部、 4・・・吸掃気弁、5・・・
弁座、 6・・・吸帰気管、7・・・燃焼
室兼渦流形成室、8・・・膨張室、9・・・燃料供給通
路、 10・・・燃料噴射弁、11・・・点火プラグ
、 12・・・排気孔、13・・・排気管。
特許出願人代理人氏名
係20!1
体3(!1
$1図
手続補正書(自発)
昭和56年lO月 5 日
許庁長官島田春樹 殿
事件の表示 昭和56 年 特 許 願第183877
号発明の名称 火花点火式2サイクル機関補正をす
る者事件との関係 特 許 出願人、 代 理
人 〒050
補正指令 の日付 昭和 年 月 日補正ノ対象
明細書中発明の詳細な説明の欄手続補正書は却
昭和57年 2[19
特許庁長官島田春樹 殿
1、事件の表示 昭和56年 特 許 願第f3887
2、発明の名称 火花点火式2サイクル機関3、補正
をする者事件との関係 特 許 出願人4、 代
理 人 〒650
7・ 補正)内容 別紙の通シ補正します。The drawings show an embodiment of the present invention, and FIG. 1 is a vertical cross-sectional view of a cylinder, FIG. 2 is a front view of the cylinder head and end, FIG. 3 is a perspective view of the cylinder head, and FIG. 4 is a stroke diagram. It is. 1...Cylinder, 2...Piston, 3.
...Squish part, 4...Suction and scavenging valve, 5...
Valve seat, 6... Intake air pipe, 7... Combustion chamber/vortex forming chamber, 8... Expansion chamber, 9... Fuel supply passage, 10... Fuel injection valve, 11... Ignition Plug, 12...Exhaust hole, 13...Exhaust pipe. Patent Applicant Agent Name Section 20!1 Body 3 (!1 $1 Figure Procedure Amendment (Spontaneous) October 5th, 1980 Indication of the case of Mr. Haruki Shimada, Commissioner of the Japan Patent Office 1983 Patent Application No. 183877
Title of the invention Relationship to the case of person who amends a spark-ignition two-stroke engine Patent applicant, agent
Person 〒050 Date of amendment order Showa year Month Date Subject of amendment Detailed explanation of the invention in the specification Procedural amendment rejected 1982 2 [19 Haruki Shimada, Commissioner of the Patent Office 1, Indication of the case 1988 Special Permission No. f3887
2. Title of the invention Spark-ignition two-cycle engine 3. Relationship with the case of the person making the amendment Patent Applicant 4, Representative
Mr. 〒650 7. Amendment) Contents I will revise the attached document.
Claims (1)
において、燃料噴射弁とその下部に点火プラグを装着し
、頭上吸気弁下部に膨張室に連通ずる特殊碗型渦流形成
室を形設し、吸帰気時に回転渦流を発生させることを特
徴とづる火花点火式2サイクル機関。In the UNIFLO asymmetrical scavenging type overhead scavenging air valve type two-stroke engine, a fuel injection valve and a spark plug are installed below it, and a special bowl-shaped swirl forming chamber that communicates with the expansion chamber is formed at the bottom of the overhead intake valve. A spark-ignition two-stroke engine that generates a rotating vortex when the engine is activated.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP56133877A JPS5835225A (en) | 1981-08-26 | 1981-08-26 | Spark-ignition 2-cycle engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP56133877A JPS5835225A (en) | 1981-08-26 | 1981-08-26 | Spark-ignition 2-cycle engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5835225A true JPS5835225A (en) | 1983-03-01 |
Family
ID=15115159
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP56133877A Pending JPS5835225A (en) | 1981-08-26 | 1981-08-26 | Spark-ignition 2-cycle engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5835225A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6388717A (en) * | 1986-10-01 | 1988-04-19 | メトロ電装株式会社 | Time lag switch |
US4881513A (en) * | 1987-11-19 | 1989-11-21 | Tohatsu Corporation | Two-cycle internal combustion engine |
JPH0566226U (en) * | 1992-02-12 | 1993-09-03 | ダイハツ工業株式会社 | 2-cycle engine |
-
1981
- 1981-08-26 JP JP56133877A patent/JPS5835225A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6388717A (en) * | 1986-10-01 | 1988-04-19 | メトロ電装株式会社 | Time lag switch |
US4881513A (en) * | 1987-11-19 | 1989-11-21 | Tohatsu Corporation | Two-cycle internal combustion engine |
JPH0566226U (en) * | 1992-02-12 | 1993-09-03 | ダイハツ工業株式会社 | 2-cycle engine |
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