JPH0245614A - Crank chamber preliminarily pressurized type two cycle engine - Google Patents
Crank chamber preliminarily pressurized type two cycle engineInfo
- Publication number
- JPH0245614A JPH0245614A JP19563088A JP19563088A JPH0245614A JP H0245614 A JPH0245614 A JP H0245614A JP 19563088 A JP19563088 A JP 19563088A JP 19563088 A JP19563088 A JP 19563088A JP H0245614 A JPH0245614 A JP H0245614A
- Authority
- JP
- Japan
- Prior art keywords
- auxiliary
- combustion
- auxiliary scavenging
- port
- air
- 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
- 230000002000 scavenging effect Effects 0.000 claims abstract description 53
- 238000002485 combustion reaction Methods 0.000 claims abstract description 36
- 239000000446 fuel Substances 0.000 claims abstract description 20
- 239000000203 mixture Substances 0.000 abstract description 9
- 230000001788 irregular Effects 0.000 abstract description 8
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000011144 upstream manufacturing 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
- 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
Landscapes
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明はクランク室予圧縮式2行程工/ジンにおける
低負荷運転時の不整燃焼を防止するための装glK関す
るもので、特にシニューレ形の燃焼室において、クラン
ク室内に大気を吸入し、排気口に対向して設けた補助掃
気ポートから燃料を供給するよりにし次ものに関する。[Detailed Description of the Invention] [Field of Industrial Application] This invention relates to a system for preventing irregular combustion during low-load operation in a crank chamber precompression type two-stroke engine/engine, and in particular relates to a ignition system for preventing irregular combustion during low-load operation. In the combustion chamber, atmospheric air is sucked into the crank chamber and fuel is supplied from an auxiliary scavenging port provided opposite to the exhaust port.
従来、排気口と対向するシリンダの内壁部分に既燃ガス
が滞流するのを防止すべく、排気口に対向して開設した
補助掃気ポートを設けること(例えば、実公昭47−3
0643号公報)および掃気の一部が直接排気口から排
出される、いわゆる吹抜は現象を防止するため補助掃気
流に燃料を付加して濃淡2種の空燃比を持つ掃気を作シ
、燃焼室内に2種の混合気層を形成する、いわゆる層状
給気方式が知られている(例えば、実開昭52−170
913号公報)。Conventionally, in order to prevent burnt gas from accumulating on the inner wall portion of the cylinder facing the exhaust port, an auxiliary scavenging port was provided facing the exhaust port (for example,
In order to prevent this phenomenon, fuel is added to the auxiliary scavenging air flow to create scavenging air with two types of rich and light air-fuel ratios, and a part of the scavenging air is directly discharged from the exhaust port. A so-called stratified air supply system in which two types of mixture layers are formed is known (for example, Utility Model Application No. 52-170
Publication No. 913).
しかしながら、低負荷運転時には燃焼室内へ流入する掃
気流量が少ないため掃気が不充分となシやすく、点火栓
近傍の掃気が不充分となって不整燃焼の原因となる他、
新気がピストンの頂面付近に滞留してしまい、ピストン
の上昇行程中に排気口から排出されて燃焼に寄与しない
燃料成分が多く燃料の経済性が低下するなどの不具合が
あった。However, during low-load operation, the flow rate of scavenging air flowing into the combustion chamber is small, so scavenging air tends to be insufficient, and scavenging air near the ignition plug becomes insufficient, causing irregular combustion.
There were problems such as fresh air staying near the top of the piston and being discharged from the exhaust port during the piston's upward stroke, resulting in a large amount of fuel components that did not contribute to combustion, reducing fuel economy.
この発明は上記した不具合を排除し、燃料の経済性に優
れ、かつ低速運転時の不整燃焼のない2行程エンジンを
得ることを目的とするもので、クランク室内を流入弁と
絞り弁とを介して大気中に開口させ、シリンダの内壁に
排気口とその排気口の両側に隣接して主掃気通路および
排気口と対向した壁面に比較的小面積の補助掃気ポート
とを開設したものにおいて、この補助掃気ポートに連な
る補助掃気道路に補助絞り弁と燃料供給装置とを備え、
その補助掃気ポートをシリンダヘッドの燃焼室をなす凹
面に設けた燃焼凹部へ指向させ、かつ前記補助掃気通路
に補助掃気を一旦貯留させるための貯留手段を設けたも
のである。The purpose of this invention is to eliminate the above-mentioned problems, provide a two-stroke engine with excellent fuel economy, and without irregular combustion during low-speed operation. The exhaust port is opened to the atmosphere on the inner wall of the cylinder, and an auxiliary scavenging port with a relatively small area is provided on the main scavenging passage adjacent to both sides of the exhaust port and on the wall facing the exhaust port. The auxiliary scavenging road connected to the auxiliary scavenging port is equipped with an auxiliary throttle valve and a fuel supply device,
The auxiliary scavenging port is directed to a combustion recess provided in a concave surface forming a combustion chamber of the cylinder head, and a storage means is provided for temporarily storing auxiliary scavenging air in the auxiliary scavenging passage.
〔作用〕
ピストンの上昇行程中にクランク室内へ吸入された大気
は、その下降行程中に主掃気口から燃焼室内へ圧送され
る。他方、ピストンの上昇によるり−)/り室内の圧力
降下は貯留手段たる膨張室に波及し、気化器を経て混合
気が流入し貯留される。[Operation] Atmospheric air sucked into the crank chamber during the upward stroke of the piston is forced into the combustion chamber through the main scavenging air port during the downward stroke. On the other hand, the pressure drop in the chamber caused by the rise of the piston spreads to the expansion chamber, which is a storage means, and the air-fuel mixture flows through the carburetor and is stored.
ピストンが下降するとクランク室内の圧力が上昇し、そ
れが膨張室へ波及してそこに貯留されている混合気を補
助掃気口から点火栓近傍の燃焼室内へ細い高速気流とし
て噴出し、圧縮行程の終期に点火栓の近傍に混合気層を
形成する。When the piston descends, the pressure in the crank chamber increases, which spreads to the expansion chamber and blows out the air-fuel mixture stored there from the auxiliary scavenging port into the combustion chamber near the spark plug as a thin, high-speed air stream, which accelerates the compression stroke. At the end of the process, a mixture layer is formed near the ignition plug.
以下、図示の実施例によってこの発明を説明すると、図
中、1はクランク室予圧縮式2行程エンジンを示し、2
はそのクランク室である。3は燃焼室であり、燃焼室3
はシリンダ4、シリンダヘッド5およびピストン6によ
って形成されている。The present invention will be explained below with reference to the illustrated embodiments. In the figure, 1 indicates a two-stroke engine with precompression in the crank chamber;
is its crank chamber. 3 is a combustion chamber; combustion chamber 3
is formed by a cylinder 4, a cylinder head 5 and a piston 6.
燃焼室3をなすシリンダヘッド5の凹面は全体として浅
い半球状をなし、その一部に後述する排気口13側に偏
してやや深い半球形の燃焼凹部3aが形成され、その中
央部に点火栓7の電極を臨ませである。The concave surface of the cylinder head 5 forming the combustion chamber 3 has a shallow hemispherical shape as a whole, and a slightly deeper hemispherical combustion recess 3a is formed in a part thereof toward the exhaust port 13 side, which will be described later, and the ignition plug is located in the center of the concave surface. 7 electrodes are facing.
8は吸気通路であシ、クランク室内への気流のみを許容
する流入弁たる逆止弁9と吸気流量を調節する手動の主
絞夛弁10とが設けられている。Reference numeral 8 denotes an intake passage, which is provided with a check valve 9, which is an inflow valve that only allows airflow into the crank chamber, and a manual main throttle valve 10, which adjusts the intake flow rate.
なお、この実施例では吸気通路8に気化器その他の燃料
供給装置が設けてないが、後述する補助掃気よシも希薄
な混合気を生成する燃料供給装置を設けることもある。In this embodiment, a carburetor or other fuel supply device is not provided in the intake passage 8, but a fuel supply device that generates a lean air-fuel mixture may also be provided for auxiliary scavenging, which will be described later.
また、前記流入弁はこの逆止弁9に限られず、ピストン
6のスカート部によって開閉される、いわゆるピストン
弁であってもよいのは勿論である。11はクランク室2
内とシリンダ4内とを接続する主掃気通路であり、主掃
気口12.12に通じている。13は排気通路14に連
なる排気口であシ、左右対称に設けられた主掃気口12
0間に開設される。以上の構成は従来公知のものとtミ
は同様である。Furthermore, the inflow valve is not limited to the check valve 9, and may of course be a so-called piston valve that is opened and closed by the skirt portion of the piston 6. 11 is crank chamber 2
This is a main scavenging passage that connects the inside of the cylinder 4 with the inside of the cylinder 4, and communicates with the main scavenging air port 12.12. Reference numeral 13 denotes an exhaust port connected to the exhaust passage 14, and main scavenging air ports 12 are provided symmetrically.
It will be opened between 0 and 0. The above configuration is essentially the same as a conventionally known configuration.
この発明において、シリンダ4の内壁には排気口13に
対向した壁面に比較的小面積の補助掃気ポート21が開
設されており、これに接続される補助掃気通路22には
一部を膨大させて貯留手段たる膨張室23が形成され、
その上流側に位置して燃料供給装置たる気化器24が設
けられている。In this invention, an auxiliary scavenging port 21 with a relatively small area is provided on the inner wall of the cylinder 4 facing the exhaust port 13, and an auxiliary scavenging passage 22 connected to this port is partially enlarged. An expansion chamber 23 serving as a storage means is formed,
A carburetor 24 serving as a fuel supply device is provided upstream thereof.
24mは気化器に付設された補助絞り弁である。なお、
燃料供給装置は気化器に代えて電子式燃料噴射装置とし
てもよい仁とは勿論であシ、この場合(も補助絞り弁2
4&は主掃気と補助掃気の流量比を制御するため必要と
される。すなわち、絞り弁241は前記主絞り弁10と
連動して動作し、第3図で示すように、エンジン負荷の
低い領域では補助掃気流の割合を増し、高い領域では減
じるように構成されている。24m is an auxiliary throttle valve attached to the carburetor. In addition,
It is of course possible to use an electronic fuel injection device instead of the carburetor as the fuel supply device;
4& is required to control the flow rate ratio of main scavenging air and auxiliary scavenging air. That is, the throttle valve 241 operates in conjunction with the main throttle valve 10, and, as shown in FIG. 3, is configured to increase the proportion of the auxiliary scavenging air flow in low engine load regions and decrease it in high engine load regions. .
この実施例で膨張室23は補助掃気を一旦蓄えるもので
、縦長の円筒状に形成され、その下部に気化器24が接
続されると共に、上部には作用通路25を介してクラン
ク室2が接続され、クランク室2内の圧力が波及するよ
うKなっている。In this embodiment, the expansion chamber 23 temporarily stores auxiliary scavenging air, and is formed into a vertically elongated cylindrical shape.A carburetor 24 is connected to the lower part of the expansion chamber 23, and the crank chamber 2 is connected to the upper part through a working passage 25. K is set so that the pressure inside the crank chamber 2 spreads.
なお、この例では作用通路25を膨張室23の上部へ接
線状に接続し、気化器24を通して導入される補助掃気
流と混合しないようにしであるが、図中、二点鎖線で示
すようにダイアフラム26で仕切れば一層確実となる。In this example, the working passage 25 is connected tangentially to the upper part of the expansion chamber 23 so as not to mix with the auxiliary scavenging air flow introduced through the carburetor 24. If it is partitioned by a diaphragm 26, it will be even more reliable.
補助掃気ポート21は概ね点火栓7を指向して開設され
ておシ、前記燃焼凹部3aへ向けて比較的高速の細い気
流として供給される。なお、燃焼凹部3aはこの実施例
で示すように、シリンダ4孔の中心よシやや排気口13
側へ偏倚して設けられ、その平面図における直径はシリ
ンダ直径のおよそ半分に設定しである。The auxiliary scavenging air port 21 is opened generally facing the spark plug 7, and is supplied as a relatively high-speed thin air stream toward the combustion recess 3a. As shown in this embodiment, the combustion recess 3a is located at the center of the cylinder 4 hole and at the exhaust port 13.
It is provided offset to the side, and its diameter in plan view is set to approximately half the cylinder diameter.
次にこのエンジンの動作を説明する。エンジンが低負荷
域で運転されるとき、すなわち主絞り弁10の開度が低
いときには、ピストン6の上昇行程中にクランク室2内
へ少量の新気が吸入される。Next, the operation of this engine will be explained. When the engine is operated in a low load range, that is, when the opening degree of the main throttle valve 10 is low, a small amount of fresh air is sucked into the crank chamber 2 during the upward stroke of the piston 6.
一方、補助掃気通路22に設けた補助絞り弁24mは比
較的大きい開度に保たれ、補助掃気通路22へ比較的多
量の新気が導入される。On the other hand, the auxiliary throttle valve 24m provided in the auxiliary scavenging passage 22 is kept at a relatively large opening, and a relatively large amount of fresh air is introduced into the auxiliary scavenging passage 22.
ピストン6が下降し主掃気口12.12が開くと、クラ
ンク室内の新気は燃焼室内へ流入し既燃ガスを排気口1
3から押し出すが、その流量が少ないため主掃気流は一
般的に弱く、大部分はピストン60表面付近に滞留し燃
焼室上部に滞留する既燃ガスを掃気するには十分でない
。When the piston 6 descends and the main scavenging port 12.12 opens, fresh air in the crank chamber flows into the combustion chamber and burnt gas is transferred to the exhaust port 1.
However, since the flow rate is small, the main scavenging airflow is generally weak, and most of it remains near the surface of the piston 60 and is not sufficient to scavenge the burned gas that remains in the upper part of the combustion chamber.
他方、補助掃気流は主掃気に比して流量が多く主掃気や
既燃ガスの層を突き破って点火栓7近傍の燃焼凹部3a
へ噴出し、引き続く圧縮行程の終期に点火栓近傍に混合
気層を形成する。よって、点火栓7による点火が行われ
ると燃焼当初に良好な燃焼が得られるため、燃焼が全体
として安定し不整燃焼を防止できる。On the other hand, the auxiliary scavenging air flow has a larger flow rate than the main scavenging air and breaks through the main scavenging air and the layer of burnt gas to reach the combustion recess 3a near the spark plug 7.
At the end of the subsequent compression stroke, a mixture layer is formed near the spark plug. Therefore, when ignition is performed by the spark plug 7, good combustion is obtained at the beginning of combustion, so that combustion is stabilized as a whole and irregular combustion can be prevented.
この発明は以上のように、補助掃気ポート21から燃料
供給装置24によって生成された混合気がシリンダヘッ
ド5に形成された燃焼凹部31へ向けて高速で噴出し、
主掃気によって形成される空気層や残存する既燃ガスの
層を一気に突き破って点火栓7に達するので、燃焼室頂
部で拡散することなく、燃焼凹部3a内に可燃混合気層
を形成する。As described above, the present invention jets the air-fuel mixture generated by the fuel supply device 24 from the auxiliary scavenging port 21 at high speed toward the combustion recess 31 formed in the cylinder head 5,
Since the main scavenging air breaks through the air layer formed by the main scavenging air and the remaining burnt gas layer and reaches the ignition plug 7, a combustible mixture layer is formed in the combustion recess 3a without being diffused at the top of the combustion chamber.
よって、引き続く点火行程において、点火栓7に生じ九
電弧は既燃ガスによって阻害されることなく、新気に火
炎を生じさせるので不整燃焼が減じ、エンジンの運転を
円滑にすると共に、燃料の吹き抜けを防止できエンジン
の効率を高め得る効果がある。Therefore, in the subsequent ignition stroke, the arc generated in the ignition plug 7 is not inhibited by burnt gas and generates a flame in fresh air, which reduces irregular combustion, smoothes engine operation, and prevents fuel from blowing out. This has the effect of preventing this and increasing engine efficiency.
図面はこの発明の一実施例を示すもので、第1図はエン
ジンの断面図、第2図はその■−■断面図、第3図は絞
り弁の開弁特性図である。
3& ・・・・燃焼凹部、21・・・・補助掃気ポート
、23・・争・膨張室。
第1図
特詐出願人 ヤマハ発動機株式会社The drawings show an embodiment of the present invention; FIG. 1 is a cross-sectional view of the engine, FIG. 2 is a cross-sectional view taken along line 1--2, and FIG. 3 is a diagram showing opening characteristics of a throttle valve. 3 &... Combustion recess, 21... Auxiliary scavenging port, 23... War/expansion chamber. Figure 1 Special fraud applicant Yamaha Motor Co., Ltd.
Claims (1)
させ、シリンダの内壁に排気口とその排気口の両側に隣
接して主掃気通路および排気口と対向した壁面に比較的
小面積の補助掃気ポートとを開設したものにおいて、こ
の補助掃気ポートに連なる補助掃気通路に補助絞り弁と
燃料供給装置とを備え、補助掃気ポートをシリンダヘッ
ドの燃焼室をなす凹面に設けた燃焼凹部へ指向させ、か
つ前記補助掃気通路に補助掃気を一旦貯留させるための
貯留手段を設けてなるクランク室予圧縮式2行程エンジ
ン。The inside of the crank chamber is opened to the atmosphere through an inflow valve and a throttle valve, and an exhaust port is provided on the inner wall of the cylinder, and a relatively small area is provided on the main scavenging passage adjacent to both sides of the exhaust port and on the wall facing the exhaust port. In the case where an auxiliary scavenging air port is opened, an auxiliary scavenging air passage connected to the auxiliary scavenging air port is equipped with an auxiliary throttle valve and a fuel supply device, and the auxiliary scavenging air port is directed to a combustion recess provided in a concave surface forming a combustion chamber of the cylinder head. A two-stroke engine with a crank chamber precompression type, further comprising a storage means for temporarily storing auxiliary scavenging air in the auxiliary scavenging passage.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19563088A JPH0245614A (en) | 1988-08-05 | 1988-08-05 | Crank chamber preliminarily pressurized type two cycle engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19563088A JPH0245614A (en) | 1988-08-05 | 1988-08-05 | Crank chamber preliminarily pressurized type two cycle engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0245614A true JPH0245614A (en) | 1990-02-15 |
Family
ID=16344361
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP19563088A Pending JPH0245614A (en) | 1988-08-05 | 1988-08-05 | Crank chamber preliminarily pressurized type two cycle engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0245614A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2745849A1 (en) * | 1996-03-08 | 1997-09-12 | Honda Motor Co Ltd | Precompression two=stroke IC-engine for motor vehicle |
-
1988
- 1988-08-05 JP JP19563088A patent/JPH0245614A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2745849A1 (en) * | 1996-03-08 | 1997-09-12 | Honda Motor Co Ltd | Precompression two=stroke IC-engine for motor vehicle |
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