JPH1136903A - Engine with exhaust turbosupercharger - Google Patents
Engine with exhaust turbosuperchargerInfo
- Publication number
- JPH1136903A JPH1136903A JP9186798A JP18679897A JPH1136903A JP H1136903 A JPH1136903 A JP H1136903A JP 9186798 A JP9186798 A JP 9186798A JP 18679897 A JP18679897 A JP 18679897A JP H1136903 A JPH1136903 A JP H1136903A
- Authority
- JP
- Japan
- Prior art keywords
- exhaust
- engine
- turbine
- intake
- pressure
- 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.)
- Granted
Links
Classifications
-
- 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
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明はターボ過給機付エン
ジンに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbocharged engine.
【０００２】[0002]
【従来の技術】一般に、ターボ過給機付エンジンではウ
ェストゲート装置を組み合わせて過給圧の過剰上昇を抑
制している。このウェストゲート装置では、過給圧が所
定値以上となったとき、ウェストゲート弁が開き、排ガ
スがタービンをバイパスして流れるようになっている。
こうなるとコンプレッサの回転も抑制されて過給圧が抑
制され、エンジンが保護されるようになる。2. Description of the Related Art Generally, in a turbocharged engine, an excessive increase in supercharging pressure is suppressed by combining a wastegate device. In this wastegate device, when the supercharging pressure becomes equal to or higher than a predetermined value, the wastegate valve opens, and exhaust gas flows by bypassing the turbine.
In this case, the rotation of the compressor is also suppressed, the supercharging pressure is suppressed, and the engine is protected.
【０００３】[0003]
【発明が解決しようとする課題】ところで、ウェストゲ
ート装置では、ウェストゲート弁が開いたときに排ガス
が何等仕事をすることなく捨て去られてしまい、エネル
ギの有効利用が図れないという問題がある。By the way, in the wastegate device, when the wastegate valve is opened, the exhaust gas is discarded without performing any work, and there is a problem that the energy cannot be effectively used.
【０００４】[0004]
【課題を解決するための手段】本発明に係るターボ過給
機付エンジンは、排気行程でタービン上流側に排出され
た排ガスを吸気行程でシリンダ内に逆流させるべく、吸
気行程でリフトする排気弁を設けたものである。SUMMARY OF THE INVENTION An engine with a turbocharger according to the present invention is an exhaust valve that lifts in an intake stroke so that exhaust gas discharged upstream of a turbine in an exhaust stroke flows back into a cylinder in an intake stroke. Is provided.
【０００５】これによれば、吸気行程でタービン上流側
の排ガスがシリンダ内に逆流されるので、タービン上流
側の排ガス圧力、即ち背圧が低減され、タービンの回転
が抑制されるようになる。これにより、ウェストゲート
装置に代わって過給圧の過剰上昇を抑制でき、さらに逆
流された排ガスはピストンを押し下げるのに利用でき
る。According to this, the exhaust gas on the upstream side of the turbine flows back into the cylinder during the intake stroke, so that the exhaust gas pressure on the upstream side of the turbine, that is, the back pressure is reduced, and the rotation of the turbine is suppressed. As a result, an excessive increase in the supercharging pressure can be suppressed in place of the wastegate device, and the exhaust gas that has flowed back can be used to push down the piston.
【０００６】なお、上記排気弁を吸気行程で選択的にリ
フトさせるための切替手段が設けられるのが好ましい。[0006] Preferably, a switching means for selectively lifting the exhaust valve during the intake stroke is provided.
【０００７】[0007]
【発明の実施の形態】以下、本発明の好適な実施の形態
を添付図面に基づいて詳述する。Preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
【０００８】図１は本発明に係るターボ過給機付エンジ
ンを概略的に示す平面図である。図示するようにシリン
ダ１には吸気ポート２と排気ポート３とが臨ませられ、
これらポート２，３を開閉すべく吸気弁４と排気弁５と
が配設されている。吸気ポート２及び排気ポート３は、
それぞれ吸気通路６及び排気通路７の一部を構成してい
る。吸気通路６及び排気通路７はターボ過給機８で連絡
され、ターボ過給機８のタービン９が排気通路７の途中
に、ターボ過給機８のコンプレッサ１０が吸気通路６の
途中に、それぞれ配設されている。ターボ過給機８はこ
こでは可変容量型のものが使用され、即ち、タービン９
の入口にノズルベーン１１が設けられ、ノズルベーン１
１がタービン入口の通路面積を適宜絞るようになってい
る。ノズルベーン１１の開度制御はECU 等の制御装置１
２によって行われる。即ち、制御装置１２はエンジン回
転数、エンジン負荷等のエンジン運転状態を表す各種デ
ータを常時読み込んでおり、これらの値と予め記憶して
ある開度マップとからアクチェータ１３を最適に動作さ
せ、ノズルベーン１１の開度制御を実行している。FIG. 1 is a plan view schematically showing a turbocharged engine according to the present invention. As shown in the drawing, an intake port 2 and an exhaust port 3 are exposed to the cylinder 1,
An intake valve 4 and an exhaust valve 5 are provided to open and close these ports 2 and 3. The intake port 2 and the exhaust port 3
Each of them constitutes a part of the intake passage 6 and the exhaust passage 7. The intake passage 6 and the exhaust passage 7 are connected by a turbocharger 8. The turbine 9 of the turbocharger 8 is located in the exhaust passage 7, and the compressor 10 of the turbocharger 8 is located in the intake passage 6. It is arranged. Here, a turbocharger 8 of a variable capacity type is used, that is, a turbine 9
A nozzle vane 11 is provided at the inlet of the nozzle vane 1.
1 appropriately reduces the passage area of the turbine inlet. The opening control of the nozzle vane 11 is performed by a control device 1 such as an ECU.
2 is performed. That is, the control device 12 constantly reads various data indicating the engine operation state such as the engine speed and the engine load, and operates the actuator 13 optimally based on these values and the opening degree map stored in advance, thereby controlling the nozzle vane. 11 is performed.
【０００９】ここで特に排気弁５は、図２の破線で示す
ように、通常の排気行程の他、吸気行程でもリフトする
ことができる。つまり排気弁５は２段で開閉を行うこと
となる。そしてここでは吸気行程におけるリフトが、以
下に述べる切替手段により選択的に行われるようになっ
ている。このような切替手段は実開昭61-105705 号等に
よっても周知であるが、ここでは図３に示すような構成
を例示しておく。Here, the exhaust valve 5 can be lifted not only in the normal exhaust stroke but also in the intake stroke as shown by the broken line in FIG. That is, the exhaust valve 5 opens and closes in two stages. Here, the lift in the intake stroke is selectively performed by the switching means described below. Such a switching means is also known from Japanese Utility Model Application Laid-Open No. 105705/1986, but the configuration shown in FIG. 3 is exemplified here.
【００１０】図示する切替手段Ｘにあって、カムシャフ
ト１４には、排気弁５を通常通り排気行程でリフトさせ
るための第１カム１５と、排気弁５を吸気行程でリフト
させるための第２カム１６とが設けられる。これら第１
カム１５と第２カム１６とは、いずれか一方が切替えプ
ッシュロッド１７を押し上げ、ロッカーアーム１８を介
して排気弁５を押し下げる（リフトさせる）ようになっ
ている。即ち、一方のカム１５，１６による押し上げ力
をロッカーアーム１８に伝達するのが切替えプッシュロ
ッド１７である。In the illustrated switching means X, the camshaft 14 has a first cam 15 for lifting the exhaust valve 5 in the exhaust stroke as usual, and a second cam for lifting the exhaust valve 5 in the intake stroke. A cam 16 is provided. These first
One of the cam 15 and the second cam 16 pushes up the switching push rod 17 and pushes down (lifts) the exhaust valve 5 via the rocker arm 18. That is, the switching push rod 17 transmits the push-up force of the cams 15 and 16 to the rocker arm 18.
【００１１】切替えプッシュロッド１７は二股状に構成
され、第２カム１６との接触部に油圧シリンダの如き遊
動機構１９を備えている。遊動機構１９は、プッシュロ
ッド１７に接続されるピストン２０と、ピストン２０を
摺動自在に収容するシリンダボディ２１とから構成され
る。シリンダボディ２１は第２カム１６に摺接する。ピ
ストン２０の上下の室内にはオイルが満たされ、これら
オイルは連絡通路２２を介して往来可能である。連絡通
路２２にはオイルポンプ２３から油圧が選択的に供給さ
れる。即ち、連絡通路２２とオイルポンプ２３とを結ぶ
油圧通路２４に電磁切替弁２５が設けられ、電磁切替弁
２５が前述の制御装置１２で切替制御されることによ
り、油圧が選択的に供給されるようになっている。なお
ポンプ吐出圧はリリーフ弁２６で一定に保持される。The switching push rod 17 has a bifurcated shape, and has a floating mechanism 19 such as a hydraulic cylinder at a contact portion with the second cam 16. The floating mechanism 19 includes a piston 20 connected to the push rod 17 and a cylinder body 21 that slidably accommodates the piston 20. The cylinder body 21 slides on the second cam 16. The upper and lower chambers of the piston 20 are filled with oil, and these oils can flow through the communication passage 22. Oil pressure is selectively supplied to the communication passage 22 from an oil pump 23. That is, an electromagnetic switching valve 25 is provided in a hydraulic passage 24 connecting the communication passage 22 and the oil pump 23, and the electromagnetic switching valve 25 is switched and controlled by the control device 12, so that the hydraulic pressure is selectively supplied. It has become. The pump discharge pressure is kept constant by the relief valve 26.
【００１２】この構成によれば、電磁切替弁２４がOFF
のとき、油圧供給が停止されると共に連絡通路２２と油
圧通路２４とが遮断され、ピストン２０の上下の室内が
連通され、これらの間でオイルが往来可能となる。よっ
てピストン２０はフリーに移動（遊動）できるようにな
り、排気弁５の開閉は専ら第１カム１５によって行われ
る。一方、電磁切替弁２４がONのときには、連絡通路２
２と油圧通路２４とが連通され、ピストン２０の上下の
室内に油圧が供給され、これによってピストン２０がロ
ックされる。こうなるとこんどは第２カム１６が遊動機
構１９を介してプッシュロッド１７を押し上げるように
なり、排気弁５の開閉が専ら第２カム１６によって行わ
れるようになる。According to this configuration, the electromagnetic switching valve 24 is turned off.
At this time, the supply of the hydraulic pressure is stopped, the communication passage 22 and the hydraulic passage 24 are shut off, the upper and lower chambers of the piston 20 are communicated, and oil can flow between them. Therefore, the piston 20 can freely move (float), and the opening and closing of the exhaust valve 5 is exclusively performed by the first cam 15. On the other hand, when the electromagnetic switching valve 24 is ON,
2 and the hydraulic passage 24 are communicated with each other, and hydraulic pressure is supplied to the upper and lower chambers of the piston 20, whereby the piston 20 is locked. In this case, the second cam 16 pushes up the push rod 17 via the floating mechanism 19, so that the opening and closing of the exhaust valve 5 is exclusively performed by the second cam 16.
【００１３】さて、このエンジンではウェストゲート装
置が省略されており、これに代わって過給圧の上昇を抑
制すべく、エンジン高速運転時には以下のように動作す
る。図２に示すように、先ず排気行程で通常通り排気弁
５が１回リフトして排気を行う。次いで排気行程の終り
の上死点（ＴＤＣ）付近で、吸気弁４が排気弁５と僅か
にオーバーラップしてリフトを開始し、吸気を開始す
る。特にこの吸気行程中、排気弁５が再度リフトし、こ
れによってウェストゲート装置と同様の機能を果たすこ
ととなる。即ち、エンジン高速回転時には、排気通路７
のタービン９上流側（入口側）で背圧が高くなっている
が、吸気行程で排気弁５を開くと、その高圧の排ガスが
低圧のシリンダ１内に逆流し、タービン９入口圧が下が
るようになる。これによってタービン９及びコンプレッ
サ１０の回転上昇が抑制され、過給圧の上昇も抑制され
るようになる。一方、この逆流によってシリンダ１内の
ピストンが押し下げられる。Now, in this engine, the wastegate device is omitted. Instead, the following operation is performed during high-speed operation of the engine in order to suppress an increase in the supercharging pressure. As shown in FIG. 2, first, the exhaust valve 5 lifts once and exhausts gas as usual in the exhaust stroke. Next, near the top dead center (TDC) at the end of the exhaust stroke, the intake valve 4 slightly overlaps with the exhaust valve 5 to start the lift and start the intake. In particular, during this intake stroke, the exhaust valve 5 lifts again, thereby performing the same function as the wastegate device. That is, when the engine is rotating at high speed, the exhaust passage 7
When the exhaust valve 5 is opened during the intake stroke, the high-pressure exhaust gas flows back into the low-pressure cylinder 1 and the turbine 9 inlet pressure decreases. become. As a result, an increase in the rotation of the turbine 9 and the compressor 10 is suppressed, and an increase in the supercharging pressure is also suppressed. On the other hand, the piston in the cylinder 1 is pushed down by this backflow.
【００１４】こうして従来のウェストゲート装置と異な
り、排ガスの持つ高いエネルギを捨て去ることなく回収
できるため、出力の向上が見込まれ、高過給化も可能と
なる。また逆流をピストンの下降に有効利用でき、ポン
ピングロスの防止により燃費も向上できる。さらに内部
ＥＧＲの効果も十分期待できる。In this way, unlike the conventional wastegate device, the high energy of the exhaust gas can be recovered without being discarded, so that the output can be improved and the supercharging can be achieved. In addition, the reverse flow can be effectively used for lowering the piston, and fuel efficiency can be improved by preventing pumping loss. Further, the effect of the internal EGR can be expected sufficiently.
【００１５】なお、排気弁５の最大リフト量及びリフト
期間は、排気行程のものより吸気行程のものの方が小さ
い。図４は各行程におけるポート内圧力を示すが、図示
するように吸気行程で排ガスの逆流（Ｒ部）が生じてい
ることが分かる。電磁切替弁２４をOFF のまま切り替え
なければ、排気弁５は通常通り排気行程で１回リフトす
るだけである。The maximum lift amount and the lift period of the exhaust valve 5 are smaller in the intake stroke than in the exhaust stroke. FIG. 4 shows the pressure in the port in each stroke. As shown in the figure, it can be seen that the exhaust gas flows backward (R part) in the intake stroke. If the electromagnetic switching valve 24 is not switched OFF, the exhaust valve 5 only lifts once in the exhaust stroke as usual.
【００１６】図５乃至図７は、従来のウェストゲート装
置付きエンジンと、本発明に係るエンジンとの比較を行
うためのグラフである。図５にはエンジン回転数と背圧
との関係が示され、図６にはエンジン回転数と過給圧と
の関係が示される。ＮE0は、従来エンジンにあってはウ
ェストゲート弁の開放を行う切替回転数を、本発明エン
ジンにあっては排気弁５の２回リフトを行う切替回転数
をそれぞれ示す。即ち従来エンジンでは、エンジン回転
数がＮE0より小のときウェストゲート弁が閉、大のとき
開であり、本発明エンジンではエンジン回転数がＮE0よ
り小のとき１回リフト、大のとき２回リフトとなる。な
お、エンジン回転数がＮE0より小のときはターボ過給機
８のコンプレッサ１０がサージラインに入るため、排ガ
スの逆流は行わず１回リフトとしている。FIGS. 5 to 7 are graphs for comparing a conventional engine with a wastegate device with the engine according to the present invention. FIG. 5 shows the relationship between the engine speed and the back pressure, and FIG. 6 shows the relationship between the engine speed and the supercharging pressure. N E0 indicates the switching speed at which the wastegate valve is opened in the conventional engine, and the switching speed at which the exhaust valve 5 is lifted twice in the engine of the present invention. That is, in the conventional engine, a open when the engine speed is N E0 than the small time wastegate valve is closed, a large, single lift when the engine speed is smaller than N E0 in the present invention engine, when a large 2 It becomes a lift. When the engine speed is lower than NE0, the compressor 10 of the turbocharger 8 enters the surge line, so that the exhaust gas does not flow backward and is lifted once.
【００１７】図５から分かるように、本発明エンジンで
は排ガスの逆流があることから、従来エンジンよりＮE0
以上の回転数で背圧が低くなる。そして図６から分かる
ように、本発明エンジンでは従来エンジンよりＮE0以上
の回転数で過給圧を高めることができる。As can be seen from FIG. 5, since the exhaust gas flows backward in the engine of the present invention, N E0
The back pressure decreases at the above rotation speed. As can be seen from FIG. 6, in the engine of the present invention, the supercharging pressure can be increased at a rotational speed of NE0 or more as compared with the conventional engine.
【００１８】さらに図７には、背圧と過給圧とがタービ
ンサイズとの関係で示されている。これから分かるよう
に、タービンサイズが小さいほど背圧及び過給圧は高く
なる。ところでタービンサイズがある程度小さくなる領
域Ａにおいて、従来エンジンの場合だと背圧が高くなっ
てもタービン効率が下がってしまい、過給圧が上がらな
い。しかし、本発明エンジンの場合だと、背圧が下がる
ためにタービン効率が良くなり、過給圧を上げることが
できる。このように本発明エンジンの場合、小さいター
ボ過給機が選定可能となってレスポンス向上等が図れる
と共に、高過給化が可能となって出力を向上できる。FIG. 7 shows the relationship between the back pressure and the supercharging pressure in relation to the turbine size. As can be seen, the smaller the turbine size, the higher the back pressure and boost pressure. By the way, in the region A where the turbine size is reduced to some extent, in the case of the conventional engine, even if the back pressure increases, the turbine efficiency decreases, and the boost pressure does not increase. However, in the case of the engine of the present invention, since the back pressure is reduced, the turbine efficiency is improved, and the supercharging pressure can be increased. As described above, in the case of the engine of the present invention, a small turbocharger can be selected so that the response can be improved, and the output can be improved by increasing the supercharging.
【００１９】図８は、可変容量型ターボ過給機を備えた
従来エンジンと本発明エンジンとにおけるエンジン回転
数とノズルベーン開度との関係を示すグラフである。こ
こでＮE0＝1500(rpm) である。これから分かるように、
本発明エンジンの場合背圧が下がるので、従来エンジン
よりノズルベーン開度を小さくすることができる。即ち
これは、本発明エンジンのターボ過給機が、従来エンジ
ンより小さいサイズのもので済むことを意味する。FIG. 8 is a graph showing the relationship between the engine speed and the nozzle vane opening degree of the conventional engine having the variable displacement turbocharger and the engine of the present invention. Here, N E0 = 1500 (rpm). As you can see,
In the case of the engine of the present invention, since the back pressure is reduced, the opening degree of the nozzle vanes can be made smaller than that of the conventional engine. That is, this means that the turbocharger of the engine of the present invention needs to be smaller in size than the conventional engine.
【００２０】以上、本発明の好適な実施の形態について
説明したが、本発明は他にも様々な実施の形態を採るこ
とが可能である。例えばターボ過給機は可変容量型でな
くてもよいし、切替手段についても他の構成が可能であ
る。ここでは２弁式のエンジンを示したが、当然４弁式
等のエンジンにも適用可能である。エンジン本体につい
てもガソリン、ディーゼル等あらゆる形式のものが採用
できる。Although the preferred embodiments of the present invention have been described above, the present invention can adopt various other embodiments. For example, the turbocharger does not have to be a variable displacement type, and other configurations are possible for the switching means. Although a two-valve engine is shown here, it is naturally applicable to a four-valve engine. The engine body can be of any type, such as gasoline and diesel.
【００２１】[0021]
【発明の効果】本発明は次の如き優れた効果を発揮す
る。The present invention exhibits the following excellent effects.
【００２２】（１） 排ガスの持つエネルギを有効利用
でき、出力向上、燃費向上等を図れる。(1) The energy of the exhaust gas can be effectively used, and the output and the fuel efficiency can be improved.
【００２３】（２） 背圧を下げられ、小サイズのター
ボ過給機が選定可能となる。(2) The back pressure can be reduced, and a small-sized turbocharger can be selected.
【図１】本発明に係るターボ過給機付エンジンを示す概
略平面図である。FIG. 1 is a schematic plan view showing an engine with a turbocharger according to the present invention.
【図２】本発明に係るエンジンのバルブリフト線図であ
る。FIG. 2 is a valve lift diagram of the engine according to the present invention.
【図３】切替手段を示す構成図である。FIG. 3 is a configuration diagram showing a switching unit.
【図４】本発明に係るエンジンのガス流量線図である。FIG. 4 is a gas flow rate diagram of the engine according to the present invention.
【図５】従来エンジンと本発明エンジンとの比較のため
のグラフで、エンジン回転数と背圧との関係を示す。FIG. 5 is a graph for comparison between the conventional engine and the engine of the present invention, showing the relationship between the engine speed and the back pressure.
【図６】従来エンジンと本発明エンジンとの比較のため
のグラフで、エンジン回転数と過給圧との関係を示す。FIG. 6 is a graph for comparison between the conventional engine and the engine of the present invention, showing the relationship between the engine speed and the supercharging pressure.
【図７】従来エンジンと本発明エンジンとの比較のため
のグラフで、タービンサイズと背圧、過給圧との関係を
示す。FIG. 7 is a graph for comparison between the conventional engine and the engine of the present invention, showing the relationship between turbine size, back pressure, and supercharging pressure.
【図８】従来エンジンと本発明エンジンとの比較のため
のグラフで、エンジン回転数とノズルベーン開度との関
係を示す。FIG. 8 is a graph for comparison between the conventional engine and the engine of the present invention, showing the relationship between the engine speed and the nozzle vane opening.
１ シリンダ ５ 排気弁 ９ タービン Ｘ 切替手段 DESCRIPTION OF SYMBOLS 1 Cylinder 5 Exhaust valve 9 Turbine X Switching means
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.6 識別記号 ＦＩ Ｆ０２Ｍ 25/07 Ｆ０２Ｍ 25/07 Ａ ５１０ ５１０Ｂ ５７０ ５７０Ｐ ──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. 6 Identification code FI F02M 25/07 F02M 25/07 A 510 510B 570 570P
Claims (2)
排ガスを吸気行程でシリンダ内に逆流させるべく、吸気
行程でリフトする排気弁を設けたことを特徴とするター
ボ過給機付エンジン。1. An engine with a turbocharger provided with an exhaust valve that lifts in an intake stroke so that exhaust gas discharged upstream of a turbine in an exhaust stroke flows back into a cylinder in an intake stroke.
させるための切替手段が設けられた請求項１記載のター
ボ過給機付エンジン。2. The turbocharged engine according to claim 1, further comprising switching means for selectively lifting said exhaust valve during an intake stroke.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18679897A JP3837847B2 (en) | 1997-07-11 | 1997-07-11 | Turbocharged engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18679897A JP3837847B2 (en) | 1997-07-11 | 1997-07-11 | Turbocharged engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1136903A true JPH1136903A (en) | 1999-02-09 |
| JP3837847B2 JP3837847B2 (en) | 2006-10-25 |
Family
ID=16194778
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18679897A Expired - Fee Related JP3837847B2 (en) | 1997-07-11 | 1997-07-11 | Turbocharged engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3837847B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005291210A (en) * | 2004-03-31 | 2005-10-20 | Inst Fr Petrole | Method of controlling recirculation of exhaust gas of internal combustion supercharged engine and engine using such method |
| JP2013194657A (en) * | 2012-03-21 | 2013-09-30 | Toyota Motor Corp | Drive controller for vehicle |
-
1997
- 1997-07-11 JP JP18679897A patent/JP3837847B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005291210A (en) * | 2004-03-31 | 2005-10-20 | Inst Fr Petrole | Method of controlling recirculation of exhaust gas of internal combustion supercharged engine and engine using such method |
| JP2013194657A (en) * | 2012-03-21 | 2013-09-30 | Toyota Motor Corp | Drive controller for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3837847B2 (en) | 2006-10-25 |
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