JPS5912128A - Internal combustion engine - Google Patents
Internal combustion engineInfo
- Publication number
- JPS5912128A JPS5912128A JP57120917A JP12091782A JPS5912128A JP S5912128 A JPS5912128 A JP S5912128A JP 57120917 A JP57120917 A JP 57120917A JP 12091782 A JP12091782 A JP 12091782A JP S5912128 A JPS5912128 A JP S5912128A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- recirculation
- engine
- internal combustion
- exhaust
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/16—Control of the pumps by bypassing charging air
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
Description
【発明の詳細な説明】 本発明は排気グーじシ駆動過給機付内燃機関。[Detailed description of the invention] The present invention is an internal combustion engine with an exhaust gas drive supercharger.
即ちターボ過給内燃機関に関する。That is, it relates to a turbocharged internal combustion engine.
近年内燃機関においてターボ過給の普及は著るしく、自
動車用小型内燃機関にも多数採用されている。ターボ過
給内燃機関は回収した排気エネルギで過給をおこなうの
で、最高出力の増加や機関の小型化に大きな効果がある
ものの9回収されたエネルギが過給に必要なエネルギを
上回る場合。Turbocharging has become extremely popular in internal combustion engines in recent years, and has been adopted in many small internal combustion engines for automobiles. Turbocharged internal combustion engines perform supercharging using recovered exhaust energy, which has a significant effect on increasing maximum output and downsizing the engine.9 However, if the recovered energy exceeds the energy required for supercharging.
回収エネルギが効果的に活用されるとはいえない。It cannot be said that the recovered energy is used effectively.
このような排気エネルギを活用するために従来は排気グ
ーにンを過給用と出力用の二段にわけ。In order to utilize such exhaust energy, conventionally the exhaust gas was divided into two stages: one for supercharging and one for output.
出力用ターじシ軸を減速歯車列や緩衝装置を介して機関
の出力軸に結合していた。従って構造は複雑になり又騒
音の発生原因となる欠点があった。The output shaft was connected to the engine's output shaft via a reduction gear train and a shock absorber. Therefore, the structure becomes complicated and there is a drawback that noise is generated.
更に従来のターボ過給内燃機関には応答性が低い欠点も
あった。Furthermore, conventional turbocharged internal combustion engines also have the disadvantage of low responsiveness.
本発明の目的は比較的簡単な手段により排気ターじンに
より回収された排気Iネル千のうち過給に必要とする以
上の部分を有効軸出力として取出すことにあり、同時に
機関の応答性を向上することにある。An object of the present invention is to use relatively simple means to extract a portion of the exhaust gas recovered by the exhaust turbine as effective shaft output in excess of that required for supercharging, and at the same time improve the responsiveness of the engine. It's about improving.
本発明の構成は排気グーじン駆動過給機を設け。The structure of the present invention includes an exhaust gas drive supercharger.
且つ通常の吸気弁排気弁の他に還気弁を設け、圧縮行程
時の始めに該還気弁より新気の一部が前記過給機の低圧
側に還流し得る如くした内燃機関で。In addition, an internal combustion engine is provided with a return valve in addition to a normal intake valve and exhaust valve, so that a part of fresh air can be returned to the low pressure side of the supercharger through the return valve at the beginning of a compression stroke.
この構成をとることにより、過給圧力以上に圧縮された
新気は気筒内において吸気行程の後半に膨張し、又圧縮
行程の始めには膨張した新気の一部が還流し気筒内圧力
を低く保つためrストシを介して動力を発生し、有効軸
出力として取出される。By adopting this configuration, fresh air compressed to more than the boost pressure expands in the cylinder in the latter half of the intake stroke, and at the beginning of the compression stroke, a part of the expanded fresh air returns and lowers the cylinder pressure. In order to keep it low, power is generated through the r-stiff and is taken out as an effective shaft output.
即ち排気ターじンにより回収された排気エネルfは機関
の運転状況に応じ、適当な割合て過給用と有効軸出力用
に分割配分されるものである。よた新気の還流を制御す
ることに上り急速に出力の増減をおこなうことができる
ので応答性は大幅に改善される。That is, the exhaust energy f recovered by the exhaust turbine is divided and distributed to supercharging and effective shaft output at appropriate ratios depending on the operating conditions of the engine. By controlling the recirculation of fresh air, the output can be rapidly increased or decreased, so responsiveness is greatly improved.
図は本発明を気化器付ガソリン機関に実施した例の説明
図てコシジレッ寸1は排気ターじン2によって駆動され
吸気を圧縮する。気筒頭部には排気弁3.吸気弁4の他
に還気弁5を設け、また新気の一部を該還気弁5より]
ンブレッサ1の低圧側に還流する還流管6を設ける。The figure is an explanatory diagram of an example in which the present invention is implemented in a gasoline engine with a carburetor. A compressor 1 is driven by an exhaust turbine 2 to compress intake air. There is an exhaust valve at the head of the cylinder 3. A return air valve 5 is provided in addition to the intake valve 4, and a portion of the fresh air is supplied from the return air valve 5]
A reflux pipe 6 is provided on the low pressure side of the compressor 1 for refluxing.
しかして吸気弁4は吸気行程の終了前に閉じ。Therefore, the intake valve 4 closes before the end of the intake stroke.
還気弁5は圧縮行程の前半に開閉する如くする。The return air valve 5 is opened and closed during the first half of the compression stroke.
その開閉時期の一例をあ一部ると久の通りである吸気弁
閉時期 下死点前 80度
還気弁開時期 下死点前 5度
還気弁閉時期 上死点前 70度
7は還流量を加減する還気制御弁で、軽負荷時には開き
、重負荷になるにつれて閉じ台如くする。An example of the opening/closing timing is as follows: Intake valve closing timing Before bottom dead center 80 degrees Return valve opening timing Before bottom dead center 5 degrees Return valve closing timing Before top dead center 70 degrees 7 This is a return air control valve that adjusts the amount of return air.It opens when the load is light and closes as the load becomes heavier.
なお8は気化器、9は点火栓である。Note that 8 is a carburetor and 9 is a spark plug.
との機関では9例えば過給圧1.7kg / cm に
高過給されたυ「気は吸気弁4かにストン下死点前約8
0度で閉じた後、吸気行程の後半て膨張し1 じストン
を押し下げ動力を発生する。即ち排気■ネル千の一部が
有効軸出力として利用される。For example, in an engine with a high supercharging pressure of 1.7 kg/cm, the air is at about 8 pm before the bottom dead center of the intake valve 4.
After closing at 0 degrees, it expands in the latter half of the intake stroke, pushing down the first stone and generating power. That is, a part of the exhaust gas is used as effective shaft output.
重負荷時においては還気制御弁7が閉じているため吸入
された新気は、還気弁5が圧縮行程の前半で開いても還
流管6を通って還流することはなく、その全部が気筒内
で圧縮される。即ち過給圧1.7kg / cm で吸
入された新気は吸気弁4かにストシ下死点前80度で閉
じた後膨張して動力を発生し、にストンが下死点にきた
ときには約0.3kg/ cm の過給圧になり、以後
過給圧0.3kg / cm2の通常の過給機関と全く
同等に動作する。During heavy loads, the return air control valve 7 is closed, so even if the return air valve 5 opens in the first half of the compression stroke, the fresh air that is taken in does not flow back through the return pipe 6, and all of the fresh air is compressed inside the cylinder. In other words, fresh air sucked in at a supercharging pressure of 1.7 kg/cm passes through the intake valve 4, which closes at 80 degrees before the bottom dead center, then expands and generates power, and when the cylinder reaches the bottom dead center, the The supercharging pressure becomes 0.3 kg/cm2, and from then on it operates exactly the same as a normal supercharging engine with a supercharging pressure of 0.3 kg/cm2.
軽負荷時ないし無負荷時においては還気制御弁7が開き
、新気は圧縮行程の前半では圧縮されずにコニ/プレ9
寸1の低圧側に還流される8例えば新気は過給圧1.2
kg 70m で吸入され(軽負荷時のコ、:/ジレヅ
tJ1の出口圧力は重負荷時のそれよりも低い)吸気弁
4かにストシ下死点前80度で閉じた後膨張して動力を
発生し、じストンが下死点前5度にきたときには大気圧
に等しくなり、還気弁5が開くと還流管6を通って還流
する。以後じストン上死点前70度て還気弁5が閉じる
までは気筒内圧力は]シジレッリ1の入口圧力に等しく
なる。しかしてこの時点で気筒容積はじストンが下死点
にあるときの気筒容積の三分の−であるので気筒内に残
って次に燃焼する混合気の量は従来の機関において絞り
弁が絞られ吸気管圧力が大気圧の三分の−になった場合
に等しく1機関出力も又このような場合に等しい、即ち
本機関においては出力の制御は還気制御弁7によってお
こなわれるので、気化器8の絞り弁はアイ「りンジ調整
のための補助的な動作をするのみであり、このため機関
の絞り損失乃至ボシピシジ損失は大きく低減され、同時
に加速及び減速には気筒内に吸入された新気の還WLを
制御すればよいので応答性は極めて良好になる。When the load is light or no load, the return air control valve 7 opens, and the fresh air is not compressed in the first half of the compression stroke and flows into the Koni/Pure 9.
For example, fresh air that is recirculated to the low pressure side of dimension 1 has a boost pressure of 1.2
kg 70m (when the load is light, the outlet pressure of J1 is lower than that when the load is heavy), and after the intake valve 4 closes at 80 degrees before bottom dead center, it expands and generates power. When the gas is generated and the gas reaches 5 degrees before the bottom dead center, the pressure becomes equal to atmospheric pressure, and when the return valve 5 opens, the gas flows back through the return pipe 6. Thereafter, the cylinder pressure becomes equal to the inlet pressure of Sigillelli 1 until the return valve 5 closes 70 degrees before the top dead center of the cylinder. However, at this point, the cylinder volume is -3/3 of the cylinder volume when the cylinder is at bottom dead center, so the amount of air-fuel mixture that remains in the cylinder and is combusted next is reduced by the throttle valve in a conventional engine. The engine output is also equal to the case where the intake pipe pressure is -3/3 of the atmospheric pressure.In other words, in this engine, the output is controlled by the return air control valve 7, so the carburetor The throttle valve No. 8 performs only an auxiliary operation for adjusting the eye ring, and as a result, the engine's throttle loss or displacement loss is greatly reduced, and at the same time, the new throttle valve sucked into the cylinder is used for acceleration and deceleration. Since it is only necessary to control the air return WL, the response becomes extremely good.
更に部分負荷時についていえば一度気筒内に吸入され気
1δ1内て加熱された混合気が還流するため燃料の気化
が完全になり、気箇毎及びηイクル毎の空燃比の変動が
非常に少なくなる。このため希薄混合気ても安定した運
転が得られるのて、燃費率を更に向上できる。Furthermore, during partial load, the air-fuel mixture that has been once drawn into the cylinder and heated in the air 1δ1 is recirculated, so the fuel vaporization is complete, and the fluctuations in the air-fuel ratio from one air point to the next and every η cycle are extremely small. Become. Therefore, stable operation can be achieved even with a lean mixture, and the fuel efficiency can be further improved.
また本機関においてはコンラレッη1によって高圧縮さ
れた新気が気筒内で吸入行程の後半で膨張するため、新
気はコンラレッ与1の出口より吸気弁4の開は比較的高
圧高温で供給される。従って]ンジレッリ1の出[1よ
り吸気弁4の間に吸気冷却装圃を設ければ大きな温度差
が得られ効果的に吸気を冷却することを得、これはノッ
+ジグ防止、排気温度(即ちターrシ入ロ温度)の低下
に効果があり、出力増強に奇与するものである。In addition, in this engine, fresh air highly compressed by the Conlaret η1 expands in the latter half of the intake stroke in the cylinder, so fresh air is supplied from the outlet of the Conlaret 1 at a relatively high pressure and high temperature when the intake valve 4 is opened. . Accordingly, according to [1] of Nzirelli 1, if an intake air cooling device is provided between the intake valves 4, a large temperature difference can be obtained and the intake air can be effectively cooled. In other words, it is effective in lowering the turbine input temperature) and has a positive effect on increasing output.
これを要するに本発明は極めて簡単な機構により、排気
エネルfを過給にのみならず有効軸出力にも回収利用し
、且つ機関の応答性を改善したもので1機関の小型軽量
化、燃費と応答性の向上に多大な効果を有するものであ
る。In short, the present invention uses an extremely simple mechanism to recover and use exhaust energy f not only for supercharging but also for effective shaft output, and improves the responsiveness of the engine, thereby reducing the size and weight of a single engine and improving fuel efficiency. This has a great effect on improving responsiveness.
図は本発明の詳細な説明するものて0図中符5う1はコ
ンラレッも 2は排気ターj、7.3は排気弁、4は吸
気弁、5は還気弁、6は還流管、7は還気制御弁、8は
気化器、9ば点火栓。
出願人 松井 功[相]
159−The figures are for detailed explanation of the present invention. 0 Figure 5 is a Conrare. 2 is an exhaust gas, 7.3 is an exhaust valve, 4 is an intake valve, 5 is a return valve, 6 is a return pipe, 7 is a return air control valve, 8 is a carburetor, and 9 is a spark plug. Applicant Isao Matsui [phase] 159-
Claims (1)
気弁の他に還気弁を設け、圧縮行程時の始めに該還気弁
より新気の一部が前記過給機の低圧側に還流し得る如く
した内燃機関6An exhaust turbine drive supercharger is installed, and a return valve is provided in addition to the normal intake valve and exhaust valve, and at the beginning of the compression stroke, part of the fresh air is released from the return valve to the low pressure of the supercharger. Internal combustion engine 6 designed to allow air to flow back to the side
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP57120917A JPS5912128A (en) | 1982-07-12 | 1982-07-12 | Internal combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP57120917A JPS5912128A (en) | 1982-07-12 | 1982-07-12 | Internal combustion engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5912128A true JPS5912128A (en) | 1984-01-21 |
Family
ID=14798184
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP57120917A Pending JPS5912128A (en) | 1982-07-12 | 1982-07-12 | Internal combustion engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5912128A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4852353A (en) * | 1987-01-14 | 1989-08-01 | Ab Volvo | Method and an arrangement for controlling the working cycle of a turbocharged internal combustion engine |
US4916903A (en) * | 1987-01-14 | 1990-04-17 | Ernst Holmer | Method and an arrangement for controlling the working cycle of a turbocharged internal combustion engine |
-
1982
- 1982-07-12 JP JP57120917A patent/JPS5912128A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4852353A (en) * | 1987-01-14 | 1989-08-01 | Ab Volvo | Method and an arrangement for controlling the working cycle of a turbocharged internal combustion engine |
US4916903A (en) * | 1987-01-14 | 1990-04-17 | Ernst Holmer | Method and an arrangement for controlling the working cycle of a turbocharged internal combustion engine |
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