JPH0417718A - Uni-flow type two cycle internal combustion engine - Google Patents
Uni-flow type two cycle internal combustion engineInfo
- Publication number
- JPH0417718A JPH0417718A JP11763190A JP11763190A JPH0417718A JP H0417718 A JPH0417718 A JP H0417718A JP 11763190 A JP11763190 A JP 11763190A JP 11763190 A JP11763190 A JP 11763190A JP H0417718 A JPH0417718 A JP H0417718A
- Authority
- JP
- Japan
- Prior art keywords
- scavenging
- hole
- air
- exhaust
- cylinder
- 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
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 8
- 230000002000 scavenging effect Effects 0.000 claims abstract description 58
- 238000007664 blowing Methods 0.000 abstract description 4
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000003111 delayed effect Effects 0.000 description 2
- 238000011109 contamination Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process 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
Abstract
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明はユニフロー式2サイクル内燃機関に関する。[Detailed description of the invention] [Industrial application field] The present invention relates to a uniflow two-stroke internal combustion engine.
第5図は従来形の2サイクルユニフロー式掃気機関の掃
排気系を示す。掃気室10内の掃気はライナ20に設け
られた掃気孔11をへてシリンダ21内に流入し、カバ
ー30に設けた排気弁32より排気通路31をへて排出
される。FIG. 5 shows the scavenging and exhaust system of a conventional two-stroke uniflow scavenging engine. Scavenging air in the scavenging chamber 10 flows into the cylinder 21 through the scavenging hole 11 provided in the liner 20, and is discharged through the exhaust passage 31 from the exhaust valve 32 provided in the cover 30.
排気弁32は図示しないカム軸に連設した油圧ポンプの
油圧35により開閉される。The exhaust valve 32 is opened and closed by hydraulic pressure 35 from a hydraulic pump connected to a camshaft (not shown).
ピストン13により開閉される掃気孔11および掃気弁
32のクランク角度に対する開口面積を第6図に示す。FIG. 6 shows the opening area of the scavenging hole 11 and the scavenging valve 32, which are opened and closed by the piston 13, with respect to the crank angle.
クランク角度E1で排気弁32が開きはしめ、Slで掃
気孔11が開きはじめる。The exhaust valve 32 opens and closes at the crank angle E1, and the scavenging hole 11 begins to open at the crank angle S1.
ピストン13の下死点(BCD)後S2で掃気孔11が
閉じ、E2で排気弁32が閉じる。After the bottom dead center (BCD) of the piston 13, the scavenging hole 11 closes at S2, and the exhaust valve 32 closes at E2.
第7図は第6図に対応する掃気孔部および排気弁部の変
動流量を示す。第7図においてクランク角E、で排気弁
32が開きはじめ、排気がシリンダ21から排気111
31へ流出をはしめる。その後S、で掃気孔11が開口
し、掃気室10の掃気がシリンダ21へ流入しはじめる
と、その後は排気の排出と掃気の流入が同時に行われ、
S2で掃気孔11が閉じ掃気が終了した後E2まで排気
の流出が続く。FIG. 7 shows the fluctuating flow rate of the scavenging hole section and the exhaust valve section corresponding to FIG. 6. In FIG. 7, the exhaust valve 32 begins to open at a crank angle E, and the exhaust gas flows from the cylinder 21 to the exhaust 111.
Stop the leak to 31. After that, the scavenging hole 11 opens at S, and the scavenging air in the scavenging chamber 10 begins to flow into the cylinder 21. After that, the exhaust gas is discharged and the scavenging air is inflowed at the same time.
After the scavenging hole 11 closes at S2 and scavenging ends, the exhaust gas continues to flow out until E2.
シリンダ21でのピストン13による圧縮始め時期を遅
らせるため、S2のあとにE2が設定されている。In order to delay the start of compression by the piston 13 in the cylinder 21, E2 is set after S2.
前記従来例では、第7図で掃気孔が閉じるS2から排気
弁が閉じるR2までの間のハツチング部分は、シリンダ
21内にいったん流入した排気のかなりの部分が、排気
弁32を通して流出していることになる。その結果、燃
焼に関与しないシリンダを吹き抜ける掃気部分が増加し
、排気熱の利用率が減少し動力損失を起して機関の熱効
率を低下させる不具合を生じている。In the conventional example, in the hatched portion between S2 where the scavenging hole closes and R2 where the exhaust valve closes in FIG. It turns out. As a result, the amount of scavenging air that blows through cylinders that are not involved in combustion increases, resulting in a decrease in the utilization rate of exhaust heat, resulting in power loss and a problem of lowering the thermal efficiency of the engine.
本発明の目的は前記従来装置の課題を解消し、シリンダ
を吹き抜ける掃気が少なくなり、排気温度が上昇し排気
熱の利用率が向上するユニフロー式2サイクル内燃機関
を提供するにある。SUMMARY OF THE INVENTION An object of the present invention is to provide a uniflow two-stroke internal combustion engine that solves the problems of the conventional apparatus, reduces scavenging air flowing through the cylinder, increases exhaust temperature, and improves exhaust heat utilization.
本発明のユニフロー式2サイクル内燃機関は、ライナの
掃気孔上部に掃気室と連通ずる抽気孔を設け、排気弁の
閉じ終りを早めるとともに抽気孔の閉じ終りを従来の排
気弁の閉じ終りと同じにする。The uniflow type two-stroke internal combustion engine of the present invention has a bleed hole communicating with the scavenging chamber above the scavenging hole of the liner, so that the exhaust valve closes earlier and the bleed hole closes the same as the conventional exhaust valve. Make it.
〔作用〕
排気弁の閉し緋りを早くすることにより、掃気の排気弁
を通じての流出が減り排気温度が上昇し、排気熱の利用
率が向上する。[Operation] By speeding up the closing and closing of the exhaust valve, the outflow of scavenging air through the exhaust valve is reduced, the exhaust gas temperature is increased, and the utilization rate of exhaust heat is improved.
さらに本実施例では排気弁の閉じた後でも抽気孔が開い
ているので、シリンダ内の作動ガスは抽気孔から掃気室
へ抽気され、ピストンによる圧縮始め時期を遅らせるこ
とができる。Furthermore, in this embodiment, since the bleed hole is open even after the exhaust valve is closed, the working gas in the cylinder is bled from the bleed hole to the scavenging chamber, and the timing at which compression by the piston starts can be delayed.
この抽気孔はライナの掃気孔の上方に設けられているた
め、抽気は殆んどシリンダへ、いったん流入した掃気で
あり、抽気の中の残留排気の割合は少なく抽気による掃
気室の汚れは少ない。Since this air bleed hole is provided above the liner's scavenging hole, most of the bleed air is scavenging air that has once flowed into the cylinder, and the proportion of residual exhaust air in the bleed air is small, so there is little contamination of the scavenging air chamber due to bleed air. .
以下第1〜3図を参照し本発明の一実施例について説明
する。An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.
第1図は本発明の全体システム図、第2図は第1図のn
−n断面図、第3図は掃気孔、排気弁、抽気孔の開口面
積図、第4図は掃排気の変動流量図である。Figure 1 is an overall system diagram of the present invention, and Figure 2 is the n of Figure 1.
-n sectional view, FIG. 3 is an opening area diagram of the scavenging hole, exhaust valve, and bleed hole, and FIG. 4 is a fluctuating flow rate diagram for scavenging and exhausting.
本発明ではライナ20の掃気孔11の上部に抽気孔51
を設け、さらに抽気孔51の外側には制御弁52を設け
ている。又掃気孔51は掃気室1゜と連通している。In the present invention, a bleed hole 51 is provided above the scavenging hole 11 of the liner 20.
Further, a control valve 52 is provided outside the bleed hole 51. Further, the scavenging hole 51 communicates with the scavenging chamber 1°.
第2図で示すように抽気孔51に対応した制御孔53を
持った制御弁52は、排気弁35と同様に図示しないカ
ム軸により発生される油圧54によって回転され、抽気
孔51を開閉している。As shown in FIG. 2, a control valve 52 having a control hole 53 corresponding to the bleed hole 51 is rotated by a hydraulic pressure 54 generated by a camshaft (not shown) in the same way as the exhaust valve 35, and opens and closes the bleed hole 51. ing.
掃気孔111、排気弁32、抽気孔51の開口面積を示
す第3図において、排気弁32がクランク角E1で開く
と、排気ガスは排気管に流出する。In FIG. 3 showing the opening areas of the scavenging hole 111, the exhaust valve 32, and the bleed hole 51, when the exhaust valve 32 opens at a crank angle E1, exhaust gas flows out into the exhaust pipe.
その後クランク角SIで掃気孔が開くと、掃気室10内
の掃気がシリンダ21内に流入し、シリンダに対し排ガ
スの流出と掃気の流入が同時に起きる。次に排気弁32
と掃気孔11とはほぼ同じクランク角E3と32でそれ
ぞれ閉じる。Thereafter, when the scavenging hole opens at crank angle SI, scavenging air in the scavenging chamber 10 flows into the cylinder 21, and exhaust gas outflow and scavenging air inflow into the cylinder occur simultaneously. Next, the exhaust valve 32
and the scavenging hole 11 are closed at substantially the same crank angles E3 and 32, respectively.
従って従来例のように掃気のシリンダ吹抜けは減少する
。抽気孔51は制御弁52により掃気孔11の閉しる前
にクランク角R2で開きはじめ、排気弁32が閉したあ
とR2で閉じる。このとき各部の流れは第4図に示すと
おりである。Therefore, unlike the conventional example, the scavenging air blowing through the cylinder is reduced. The bleed hole 51 begins to open at crank angle R2 before the scavenging hole 11 is closed by the control valve 52, and closes at R2 after the exhaust valve 32 closes. At this time, the flow of each part is as shown in FIG.
下死点BDC後、掃気孔11、排気弁32が同クランク
角S z、 E *でそれぞれ閉じ、そのあとビ掃気の
一部が開口している抽気孔51より抽気され、掃気室1
0に戻されるので、圧縮はじめが時期がはやくなること
はない。抽気孔51が閉したのちシリンダ21内の圧縮
が開始される。After the bottom dead center BDC, the scavenging hole 11 and the exhaust valve 32 are closed at the same crank angles Sz and E*, respectively, and then a part of the scavenging air is extracted from the open bleed hole 51 and the scavenging air chamber 1
Since the value is returned to 0, the time at which compression begins will not be delayed. After the bleed hole 51 is closed, compression within the cylinder 21 is started.
本発明のユニフロー弐2サイクル内燃機関は前記のとお
り構成され、掃気孔11が閉しるクランク角S2とほぼ
同し時期E3で排気弁32が閉じるので、シリンダ21
を吹き抜ける掃気が少なくなり、排気温度が上昇し排気
熱の利用率が向上する。又抽気孔が掃気孔の上部に設け
られているので、抽気は僅んどシリンダへいったん流入
した掃気である。その結果抽気の中の残留排気の割合が
少なく、抽気による掃気室の汚れは少ない。The uniflow two-stroke internal combustion engine of the present invention is configured as described above, and the exhaust valve 32 closes at approximately the same timing E3 as the crank angle S2 at which the scavenging hole 11 closes, so that the cylinder 21
There is less scavenging air blowing through the exhaust gas, raising the exhaust temperature and improving the utilization rate of exhaust heat. Furthermore, since the bleed air hole is provided above the scavenging hole, the bleed air is only scavenging air that has once flowed into the cylinder. As a result, the proportion of residual exhaust gas in the bleed air is small, and the scavenging chamber is less contaminated by the bleed air.
第1〜4図は本発明に係わるもので、第1図は第1実施
例の要部断面図、第2図は第1図のn−■断面図、第3
図は掃気孔、排気弁、抽気孔の開口面積図、
第4図は掃排気の変動流量図、第5〜
0・・・掃気室、
1・・・掃気孔、
3・・・ピストン、
20・・・ライナ、
1・・・シリンダ、
0・・・シリンダ
ヘッド・
2・・・排気弁、
1・・・抽気孔、
2・・・制
御卸弁。
第
図
第
図
第
図
第
図
第
図
第
図
第
図1 to 4 are related to the present invention. FIG. 1 is a sectional view of the main part of the first embodiment, FIG. 2 is a sectional view taken along the line n-■ in FIG.
The figure shows the opening area of the scavenging hole, exhaust valve, and bleed hole. Figure 4 shows the fluctuating flow rate of scavenging and exhaust. ...Liner, 1...Cylinder, 0...Cylinder head, 2...Exhaust valve, 1...Bleed hole, 2...Control outlet valve. fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig fig.
Claims (1)
掃気孔より上部に掃気室と連通する抽気孔を設けるとと
もに、該抽気孔外周に開閉制御弁を設けたことを特徴と
するユニフロー式2サイクル内燃機関。A two-stroke uniflow internal combustion engine, characterized in that a bleed hole communicating with a scavenging chamber is provided above the scavenging hole of a liner, and an opening/closing control valve is provided around the periphery of the bleed hole.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11763190A JPH0417718A (en) | 1990-05-09 | 1990-05-09 | Uni-flow type two cycle internal combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11763190A JPH0417718A (en) | 1990-05-09 | 1990-05-09 | Uni-flow type two cycle internal combustion engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0417718A true JPH0417718A (en) | 1992-01-22 |
Family
ID=14716499
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP11763190A Pending JPH0417718A (en) | 1990-05-09 | 1990-05-09 | Uni-flow type two cycle internal combustion engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0417718A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006022734A (en) * | 2004-07-08 | 2006-01-26 | Mitsubishi Heavy Ind Ltd | Internal combustion engine equipped with scavenging control valve device |
JP2009115099A (en) * | 2003-04-21 | 2009-05-28 | Mitsubishi Heavy Ind Ltd | Internal combustion engine equipped with scavenging control valve device |
JP2016035216A (en) * | 2014-08-01 | 2016-03-17 | 本田技研工業株式会社 | Uniflow two-stroke engine |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6125912A (en) * | 1984-07-17 | 1986-02-05 | Mitsubishi Heavy Ind Ltd | Axial flow scavenging type 2-cycle engine |
-
1990
- 1990-05-09 JP JP11763190A patent/JPH0417718A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6125912A (en) * | 1984-07-17 | 1986-02-05 | Mitsubishi Heavy Ind Ltd | Axial flow scavenging type 2-cycle engine |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009115099A (en) * | 2003-04-21 | 2009-05-28 | Mitsubishi Heavy Ind Ltd | Internal combustion engine equipped with scavenging control valve device |
JP4625526B2 (en) * | 2003-04-21 | 2011-02-02 | 三菱重工業株式会社 | Internal combustion engine equipped with scavenging control device |
JP2006022734A (en) * | 2004-07-08 | 2006-01-26 | Mitsubishi Heavy Ind Ltd | Internal combustion engine equipped with scavenging control valve device |
JP2016035216A (en) * | 2014-08-01 | 2016-03-17 | 本田技研工業株式会社 | Uniflow two-stroke engine |
US9938890B2 (en) | 2014-08-01 | 2018-04-10 | Honda Motor Co., Ltd. | Uniflow two-stroke engine |
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