JP3311866B2 - Two-stage supercharged engine - Google Patents
Two-stage supercharged engineInfo
- Publication number
- JP3311866B2 JP3311866B2 JP17085994A JP17085994A JP3311866B2 JP 3311866 B2 JP3311866 B2 JP 3311866B2 JP 17085994 A JP17085994 A JP 17085994A JP 17085994 A JP17085994 A JP 17085994A JP 3311866 B2 JP3311866 B2 JP 3311866B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- supercharger
- low
- stage
- engine
- 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.)
- Expired - Fee Related
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
- F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
- F02B37/002—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel the exhaust supply to one of the exhaust drives can be interrupted
-
- 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)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、２段過給エンジンにお
いて、エンジンが低中速で高負荷域で運転する場合の給
気圧力を上昇し、燃焼性能を向上し排気濃度を低下し、
出力の増加を図るものである。BACKGROUND OF THE INVENTION The present invention relates to a two-stage supercharged engine, in which, when the engine is operated at low to medium speeds in a high load range, the supply pressure is increased, the combustion performance is improved, and the exhaust gas concentration is reduced.
This is to increase the output.
【０００２】[0002]
【従来の技術】従来から、２段過給エンジンに関する技
術は公知とされているのである。例えば、実開昭６１−
１６７４２９号公報に記載の技術の如くである。上記実
開昭６１−１６７４２９号公報に記載の２段過給エンジ
ンの技術は、図４において従来技術として開示されてい
るが、次のような不具合があったのである。即ち、上記
従来技術は、低圧段に２個の過給機を有する２段過給エ
ンジンであるが、シーケンス制御による切換を行ってい
ないので、通常に２段過給エンジンと同様の特性しか発
揮できないのである。2. Description of the Related Art Conventionally, a technique related to a two-stage supercharged engine has been known. For example,
This is like the technique described in Japanese Patent No. 167429. The technique of the two-stage supercharged engine described in Japanese Utility Model Laid-Open Publication No. 61-167429 is disclosed as a conventional technique in FIG. 4, but has the following disadvantages. That is, the above prior art is a two-stage supercharged engine having two superchargers in a low-pressure stage. However, since switching by sequence control is not performed, only the same characteristics as those of a two-stage supercharged engine are normally exhibited. You can't.
【０００３】次に図４に記載の従来技術を詳細に説明す
る。該構成におていは、高圧過給機Ｆは１台のみであ
り、低圧過給機がＧとＪと２台が併設されている。故
に、６シリンダのエンジンＥからの排気は、すべて高圧
過給機Ｆのタービン３２に供給される。そして該タービ
ン３２が回転することにより、高圧過給機Ｆのコンプレ
ッサ３１を回転する。前記高圧過給機Ｆのタービン３２
を通過した後の排気ガスは、２方向に分岐されて、２台
が併置された低圧過給機Ｇと低圧過給機Ｊに２分割され
る。そして、該低圧過給機Ｇと低圧過給機Ｊは、同じ条
件でタービン３４と３６が回転し、同じ条件で、コンプ
レッサ３３と３５が回転されるのである。該低圧過給機
Ｇと低圧過給機Ｊにより、給気が低圧圧縮され、次に高
圧過給機Ｆのコンプレッサに供給されて高圧圧縮され
る。該高圧圧縮された給気がアフタークーラ２１を通過
して、エンジンＥの１〜６のシリンダに供給されるので
ある。Next, the prior art shown in FIG. 4 will be described in detail. In this configuration, there is only one high-pressure supercharger F, and two low-pressure superchargers G and J are provided in parallel. Therefore, all the exhaust from the six-cylinder engine E is supplied to the turbine 32 of the high-pressure supercharger F. When the turbine 32 rotates, the compressor 31 of the high-pressure supercharger F rotates. Turbine 32 of high-pressure supercharger F
After passing through the exhaust gas, the exhaust gas is branched in two directions, and is divided into two parts, a low-pressure supercharger G and a low-pressure supercharger J, which are provided side by side. In the low-pressure supercharger G and the low-pressure supercharger J, the turbines 34 and 36 rotate under the same conditions, and the compressors 33 and 35 rotate under the same conditions. By the low-pressure supercharger G and the low-pressure supercharger J, the supply air is compressed at a low pressure, and then supplied to the compressor of the high-pressure supercharger F to be compressed at a high pressure. The high-pressure compressed air passes through the aftercooler 21 and is supplied to the first to sixth cylinders of the engine E.
【０００４】また、図２に記載の従来技術においては、
通常の２段過給エンジンであり、低速と中速で高負荷時
において、給気圧が上昇せず、燃焼性能が悪いのであ
る。図２の従来技術について詳細に説明する。即ち、エ
ンジンＥは６気筒のエンジンを示している。そして、該
１〜６の各シリンダからの排気をまとめて、高圧過給機
Ａを構成するタービン３８に供給し、コンプレッサ３７
を回転している。該タービン３８を通過した後の排気ガ
スは低圧過給機Ｂのタービン４０に供給されて、タービ
ン４０を回転し、コンプレッサ３９を回転すべく構成し
ている。低圧過給機Ｂのコンプレッサ３９により給気を
まず１段過給し、次にインタークーラ２０を通過させ、
該インタークーラ２０を通過させた給気を、高圧過給機
Ａのコンプレッサ３７に供給し、更に高圧化して、アフ
タークーラ２１を通過させて、エンジンＥの１〜６のシ
リンダに供給している。Further, in the prior art shown in FIG.
This is a normal two-stage supercharged engine, and at high speeds at low and medium speeds, the supply pressure does not increase and combustion performance is poor. The prior art of FIG. 2 will be described in detail. That is, the engine E is a six-cylinder engine. Then, the exhaust gas from each of the cylinders 1 to 6 is collectively supplied to the turbine 38 constituting the high-pressure supercharger A, and the compressor 37
Is spinning. The exhaust gas after passing through the turbine 38 is supplied to the turbine 40 of the low-pressure supercharger B to rotate the turbine 40 and rotate the compressor 39. The supply air is first supercharged by the compressor 39 of the low-pressure supercharger B, then passed through the intercooler 20,
The supply air that has passed through the intercooler 20 is supplied to the compressor 37 of the high-pressure supercharger A, further increased in pressure, passed through the aftercooler 21, and supplied to the cylinders 1 to 6 of the engine E. .
【０００５】また図３に記載の従来技術においては、高
圧過給機として２段の過給機を有する２段シーケンシャ
ルエンジンであるが、切換弁８が高温高圧の排気ガスに
直接に触れる為に、切換弁８の耐久性が問題となるとい
う不具合があったのである。図３に記載の従来技術を詳
細に説明する。該従来技術においては、６気筒のエンジ
ンＥの１〜３のシリンダからの排気と、４〜６のシリン
ダの排気を２分している。そして、高圧過給機を２台併
設して、該分割した２群の排気ガスを高圧過給機Ｄと高
圧過給機Ｃに供給している。そして高圧過給機Ｃは使用
する場合と、使用しない場合とに、切換弁８による切換
が可能となっており、該切換弁８が閉鎖されると、４〜
６のシリンダの排気も、１〜３のシリンダの排気と合流
して、高圧過給機Ｄのタービン２８に供給されるべく構
成している。該タービン２８の回転により高圧過給機Ｄ
のコンプレッサ２７が回転される。In the prior art shown in FIG. 3, a two-stage sequential engine having a two-stage supercharger as a high-pressure supercharger is used. In this case, the durability of the switching valve 8 becomes a problem. The prior art shown in FIG. 3 will be described in detail. In the prior art, the exhaust from the cylinders 1 to 3 of the six-cylinder engine E and the exhaust from the cylinders 4 to 6 are divided into two. Then, two high-pressure superchargers are provided side by side, and the divided two groups of exhaust gas are supplied to the high-pressure supercharger D and the high-pressure supercharger C. The high-pressure supercharger C can be switched by the switching valve 8 between when it is used and when it is not used.
The exhaust of the cylinder No. 6 is also configured to be combined with the exhaust of the cylinders No. 1 to No. 3 and supplied to the turbine 28 of the high-pressure supercharger D. By the rotation of the turbine 28, the high-pressure supercharger D
Is rotated.
【０００６】また、バルブが開いている場合には、４〜
６の排気は高圧過給機Ｃのタービン２６に供給されて、
該タービン２６の回転によりコンプレッサ２５が回転す
べく構成されている。該タービン２６を通過した後の排
気は、タービン２８からの排気と合流して、低圧過給機
Ｅのタービン３０に供給される。該タービン３０の回転
によりコンプレッサ２９が回転する。給気は、コンプレ
ッサ２９によりまず低圧圧縮され、次にコンプレッサ２
９からインタークーラ２０を経て、高圧過給機Ｃのコン
プレッサ２５と、高圧過給機Ｄのコンプレッサ２７の両
方に供給される。しかし、切換弁８が閉鎖されて、高圧
過給機Ｃのタービン２６が回転しない場合には、コンプ
レッサ２５も回転しないので、高圧過給機Ｃは閉鎖され
ていると同じ状態であり、高圧過給機Ｄのコンプレッサ
２７のみを通過して給気が高圧化される。そしてコンプ
レッサ２７により高圧化された給気は、コンプレッサ２
５に逆流しないように配置されたチェックバルブ９を通
過して、アフタークーラ２１に至る。該アフタークーラ
２１からエンジンＥの各１〜６のシリンダに供給され
る。When the valve is open, 4 to
6 is supplied to the turbine 26 of the high-pressure supercharger C,
The compressor 25 is configured to rotate by the rotation of the turbine 26. The exhaust gas having passed through the turbine 26 joins the exhaust gas from the turbine 28 and is supplied to the turbine 30 of the low-pressure supercharger E. The rotation of the turbine 30 causes the compressor 29 to rotate. The supply air is first compressed at a low pressure by the compressor 29 and then the compressor 2
From 9, the air is supplied to both the compressor 25 of the high-pressure supercharger C and the compressor 27 of the high-pressure supercharger D via the intercooler 20. However, when the switching valve 8 is closed and the turbine 26 of the high-pressure supercharger C does not rotate, the compressor 25 does not rotate, so that the high-pressure supercharger C is in the same state as closed, The pressure of the supply air is increased by passing only through the compressor 27 of the supply device D. The supply air pressurized by the compressor 27 is supplied to the compressor 2
5 passes through the check valve 9 arranged so as not to flow back to the aftercooler 21. It is supplied from the aftercooler 21 to each of the cylinders 1 to 6 of the engine E.
【０００７】[0007]
【発明が解決しようとする課題】本発明は上記従来技術
の不具合を解消し、２段過給エンジンにおける、低速と
中速域の高負荷域の給気圧を上昇させて、燃焼性能を向
上し、エンジン出力の増加を図るものである。また、加
速性能の改善をも図るものである。SUMMARY OF THE INVENTION The present invention solves the above-mentioned disadvantages of the prior art and improves the combustion performance by increasing the supply pressure in a high-load region of low speed and medium speed in a two-stage supercharged engine. , To increase the engine output. Further, the acceleration performance is also improved.
【０００８】[0008]
【課題を解決するための手段】本発明の解決しようとす
る課題は以上の如くであり、次に該課題を解決するため
の手段を説明する。低圧段過給機と高圧段過給機の２段
の過給機を有するエンジンにおいて、高圧段過給機Ｈの
タービンスクロールを、エンジンシリンダの排気を２群
に分けたツインスクロール型とし、低圧段過給機には、
容量の異なる２台の過給機を併設し、エンジンの出力に
より小容量過給機Ｌを運転する場合と、大容量過給機Ｍ
を運転する場合と、小容量過給機Ｌと大容量過給機Ｍを
同時に運転する場合とに切換可能としたものである。The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described. In an engine having a two-stage supercharger of a low-pressure stage supercharger and a high-pressure stage supercharger, the turbine scroll of the high-pressure stage turbocharger H is of a twin scroll type in which the exhaust of the engine cylinder is divided into two groups, For the stage turbocharger,
A case where two superchargers having different capacities are provided and a small-capacity supercharger L is operated by the output of the engine,
And a case where the small-capacity supercharger L and the large-capacity supercharger M are simultaneously operated.
【０００９】[0009]
【作用】次に作用を説明する。本発明によれば、２段過
給エンジンにおいて、低速と中速の高負荷域においても
給気圧（正味平均有効圧）を上昇し、充分な燃焼性能を
得ることができ、また出力性能の向上を図ることが出来
るのである。またエンジンＥの加速性能の向上をも図る
ことが出来るのである。また、従来技術のシーケンシャ
ル技術の如く、エンジンＥからの排気を２段階に構成し
た高圧段過給機に切換えるのではなくて、高圧段過給機
Ｈはツインスクロール型に構成し、６気筒の全てを同じ
ツインスクロール型のタービンに供給すべく構成したの
で、高圧側の切換弁は必要なくなり、該切換弁の耐久性
が問題となることが無くなったのである。また、２群に
分割して２台の高圧段過給機に排気を供給しなくても、
ツインスクロール型であるので、排気の脈動を消すこと
が出来た。Next, the operation will be described. Advantageous Effects of Invention According to the present invention, in a two-stage supercharged engine, the supply pressure (net average effective pressure) can be increased even in a low-speed and medium-speed high load range, sufficient combustion performance can be obtained, and output performance can be improved. Can be achieved. In addition, the acceleration performance of the engine E can be improved. Further, instead of switching the exhaust from the engine E to a two-stage high-pressure supercharger as in the conventional sequential technology, the high-pressure supercharger H is configured as a twin-scroll type, and has a six-cylinder structure. Since all the components are configured to be supplied to the same twin scroll type turbine, the switching valve on the high pressure side is not required, and the durability of the switching valve does not become a problem. Also, without dividing into two groups and supplying exhaust to two high-pressure stage turbochargers,
The twin scroll type eliminated the exhaust pulsation.
【００１０】[0010]
【実施例】次に実施例を説明する。図１は本発明の２段
過給エンジン機構のブロック回路図、図２は従来の通常
の２段過給エンジン機構のブロック回路図、図３は高圧
側に２段の過給機を具備して、切換弁８により切換可能
とした従来の２段過給エンジンのブロック回路図、図４
は低圧側に２段の過給機を具備した従来技術のブロック
回路図、図５は本発明の２段過給エンジンにおいて、低
圧小容量過給機Ｌのみを使用している状態のブロック回
路図、図６は本発明の２段過給エンジンにおいて、低圧
大容量過給機Ｍのみを使用している状態のブロック回路
図、図７は３段切換状態とした本発明の２段過給エンジ
ンの正味平均有効圧の状態を示す作用図、図８は２段切
換状態とした本発明の２段過給エンジンの正味平均有効
圧の状態を示す作用図である。Next, an embodiment will be described. FIG. 1 is a block circuit diagram of a two-stage supercharged engine mechanism of the present invention, FIG. 2 is a block circuit diagram of a conventional ordinary two-stage supercharged engine mechanism, and FIG. 3 is equipped with a two-stage supercharger on the high pressure side. FIG. 4 is a block circuit diagram of a conventional two-stage supercharged engine that can be switched by a switching valve 8.
FIG. 5 is a block diagram of a prior art having a two-stage supercharger on the low-pressure side, and FIG. 5 is a block diagram of the two-stage supercharged engine of the present invention in which only the low-pressure small-capacity supercharger L is used. FIG. 6 and FIG. 6 are block circuit diagrams of the two-stage supercharged engine according to the present invention in which only the low-pressure large-capacity supercharger M is used. FIG. FIG. 8 is an operation diagram showing the state of the net average effective pressure of the engine, and FIG. 8 is an operation diagram showing the state of the net average effective pressure of the two-stage supercharged engine of the present invention in a two-stage switching state.
【００１１】図１，図５・図６において、本発明の２段
過給エンジンの構成を説明する。本発明においては、高
圧段過給機Ｈとして、ツインスクロール型のタービン１
３を使用している。該ツインスクロール型のタービン１
３は、２方向からの排気が、タービンの出口部分で始め
て合流すべく構成しているのである。図１においては、
１〜３のシリンダの排気と、４〜６のシリンダからの排
気は、タービン１３の出口において始めて合流すべく構
成しているので、各シリンダ毎の排気が干渉しあうこと
が少なくなったのである。Referring to FIGS. 1, 5 and 6, the structure of a two-stage supercharged engine according to the present invention will be described. In the present invention, a twin scroll type turbine 1 is used as the high-pressure stage supercharger H.
3 is used. The twin scroll type turbine 1
No. 3 is configured so that the exhaust gas from two directions merges only at the exit portion of the turbine. In FIG.
Since the exhausts of the cylinders 1 to 3 and the exhausts of the cylinders 4 to 6 are configured to join for the first time at the outlet of the turbine 13, the exhaust of each cylinder is less likely to interfere with each other. .
【００１２】また該ツインスクロール型のタービン１３
が排気で回転すると、コンプレッサ１２が回転する。ま
たタービン１３を通過した排気は、切換弁１８におい
て、２方向に分岐または、低圧大容量過給機Ｍか又は低
圧小容量過給機Ｌの１方のみを使用すべく切換られる。
該切換弁１８の切換は、燃料噴射ポンプＰに設けたセン
サーＳ１と、エンジンＥのフライホイール１０の回転数
を検出するセンサーＳ２により制御されて、回転数が、
低速域か中速域か高速域か、または負荷が大か小か等を
判断して、ＣＰＵ１１が直接に判断して、切換アクチュ
エータ１９に指令信号を出すことにより、自動的に切換
アクチュエータ１９を作動させて、切換弁１８を切換可
能としている。The twin scroll type turbine 13
Is rotated by the exhaust, the compressor 12 rotates. Further, the exhaust gas that has passed through the turbine 13 is branched at the switching valve 18 in two directions or switched to use only one of the low-pressure large-capacity supercharger M or the low-pressure small-capacity supercharger L.
The switching of the switching valve 18 is controlled by a sensor S1 provided on the fuel injection pump P and a sensor S2 for detecting the rotation speed of the flywheel 10 of the engine E.
The CPU 11 directly determines whether the switching actuator 19 is in the low speed range, the middle speed range, the high speed range, or whether the load is large or small, and issues a command signal to the switching actuator 19 to automatically switch the switching actuator 19. By operating, the switching valve 18 can be switched.
【００１３】そして、該切換弁１８により、低圧小容量
過給機Ｌと低圧大容量過給機Ｍの何方かを給気の低圧圧
縮に使用する場合と、どちらも使用する場合とに使い分
けることができる。低圧大容量過給機Ｍはタービン１５
とコンプレッサ１４により構成されており、また、低圧
小容量過給機Ｌはタービン１７とコンプレッサ１６によ
り構成されている。そして、低圧小容量過給機Ｌと低圧
大容量過給機Ｍの間のそれぞれの側に、チェックバルブ
２４・２３が介装されている。該チェックバルブ２４・
２３は、低圧小容量過給機Ｌと低圧大容量過給機Ｍの非
使用側に、低圧給気が逆流しないように構成している。The switching valve 18 is used to selectively use either the low-pressure small-capacity supercharger L or the low-pressure large-capacity supercharger M for low-pressure compression of the air supply, or to use both of them. Can be. The low-pressure large-capacity supercharger M is a turbine 15
The low-pressure small-capacity supercharger L includes a turbine 17 and a compressor 16. Check valves 24 and 23 are provided on each side between the low-pressure small-capacity supercharger L and the low-pressure large-capacity supercharger M. The check valve 24
23 is configured so that the low-pressure air supply does not flow back to the non-use side of the low-pressure small-capacity supercharger L and the low-pressure large-capacity supercharger M.
【００１４】該チェックバルブ２４・２３を押し上げた
低圧圧縮給気は、インタークーラ２０を通過して、高圧
段過給機Ｈのコンプレッサ１２に供給されている。該高
圧段過給機Ｈのコンプレッサ１２において、高圧圧縮さ
れて、アフタークーラ２１からエンジンＥのシリンダの
給気側に供給される。該ＣＰＵ１１における切換アクチ
ュエータ１９を操作する切換の判断は、回転数のみ、ま
たは回転数と燃料噴射ポンプＰのポンプラック目盛りに
より負荷を検出して判断する。The low-pressure compressed air supplied by pushing up the check valves 24 and 23 passes through the intercooler 20 and is supplied to the compressor 12 of the high-pressure stage supercharger H. The compressor 12 of the high-pressure supercharger H is compressed at a high pressure and supplied from the aftercooler 21 to the supply side of the cylinder of the engine E. The determination of the switching operation of the switching actuator 19 in the CPU 11 is made by detecting the load only based on the rotation speed or the rotation speed and the pump rack scale of the fuel injection pump P.
【００１５】そして図７と図８に示す如く、作用する。
図７においては、水平軸にエンジン回転数と負荷率を座
標としており、縦軸の座標には、正味平均有効圧を取っ
ている。そして、機関回転数が低く負荷も低い場合に
は、図７の３段切換方式の場合には、ａ域に示す如く、
低圧小容量過給機Ｌと高圧段過給機Ｈを作動させた、図
５の作用状態とする。これにより、低速回転で低負荷の
場合には、充分の正味平均有効圧が得られる曲線域とな
るのである。The operation is performed as shown in FIGS.
In FIG. 7, the horizontal axis represents the engine speed and the load factor as coordinates, and the vertical axis represents the net average effective pressure. Then, when the engine speed is low and the load is low, in the case of the three-stage switching system in FIG.
FIG. 5 shows a state in which the low-pressure small-capacity supercharger L and the high-pressure stage supercharger H are operated. As a result, in the case of low-speed rotation and low load, a curve region in which a sufficient net average effective pressure is obtained is obtained.
【００１６】また機関回転数が上昇し、負荷率が５０％
を越えると、図６に示す如く、低圧大容量過給機Ｍと高
圧段過給機Ｈを作用させた状態としたｂ域の状態とする
のである。これにより、充分の正味平均有効圧を得るこ
とが出来るのである。また、負荷率が８０％を越える
と、低圧小容量過給機Ｌと低圧大容量過給機Ｍと高圧段
過給機Ｈの３者の全てを作用させた図１の作用状態にし
て、ｃ域の如く、充分な正味平均有効圧を得ることが出
来るのである。負荷率の５０％と８０％の点が切換弁１
８の切換点となっている。Further, the engine speed increases and the load factor becomes 50%.
As shown in FIG. 6, the state becomes the state of the region b where the low-pressure large-capacity supercharger M and the high-pressure stage supercharger H are actuated. Thereby, a sufficient net average effective pressure can be obtained. When the load factor exceeds 80%, the low-pressure small-capacity supercharger L, the low-pressure large-capacity supercharger M, and the high-pressure stage supercharger H are all operated, as shown in FIG. As in the region c, a sufficient net average effective pressure can be obtained. Switching valve 1 is at 50% and 80% of load factor
8 switching points.
【００１７】図８の２段切換の場合には、負荷率の切換
点が７０％の点のみとなっている。そして、負荷率が７
０％以下の場合には、ｄ域の如く、低圧小容量過給機Ｌ
と高圧段過給機Ｈを駆動する図５の状態とし、７０％を
越えた場合には、低圧大容量過給機Ｍと高圧段過給機Ｈ
を作用する図６の状態としたｅ域とするのである。この
ようにｄ域と、ｅ域で充分に正味平均有効圧を得ること
が出来るのである。In the case of the two-stage switching shown in FIG. 8, the switching point of the load factor is only 70%. And the load factor is 7
In the case of 0% or less, the low-pressure small-capacity supercharger L as shown in the d region.
And the high-pressure supercharger H is driven as shown in FIG. 5, and if it exceeds 70%, the low-pressure large-capacity supercharger M and the high-pressure supercharger H
Is set to the region e in the state of FIG. Thus, a sufficient net average effective pressure can be obtained in the d region and the e region.
【００１８】[0018]
【発明の効果】本発明は以上の如く構成したので、次の
ような効果を奏するのである。第１に、２段過給エンジ
ンにおいて、低速と中速の高負荷域においても給気圧
（正味平均有効圧）を上昇し、充分な燃焼性能を得るこ
とができ、また出力性能の向上を図ることが出来るので
ある。またエンジンＥの加速性能の向上をも図ることが
出来るのである。第２に、従来技術のシーケンシャル技
術の如く、エンジンＥからの排気を２段階に構成した高
圧段過給機に切換えるのではなくて、高圧段過給機Ｈは
ツインスクロール型に構成し、６気筒の全てを同じツイ
ンスクロール型のタービンに供給すべく構成したので、
高圧側の切換弁は必要なくなり、該切換弁の耐久性が問
題となることが無くなったのである。また、２群に分割
して２台の高圧段過給機に排気を供給しなくても、ツイ
ンスクロール型であるので、排気の脈動を消すことが出
来たのである。As described above, the present invention has the following advantages. First, in a two-stage supercharged engine, the supply pressure (net average effective pressure) is increased even in a low-speed and middle-speed high-load region, so that sufficient combustion performance can be obtained and output performance is improved. You can do it. In addition, the acceleration performance of the engine E can be improved. Second, instead of switching the exhaust from the engine E to a two-stage high-pressure supercharger as in the conventional sequential technology, the high-pressure supercharger H is configured as a twin scroll type, Since all of the cylinders were configured to be supplied to the same twin scroll type turbine,
The switching valve on the high pressure side is no longer necessary, and the durability of the switching valve is no longer a problem. In addition, even if it is not divided into two groups and the exhaust is not supplied to the two high-pressure stage turbochargers, the pulsation of the exhaust can be eliminated because of the twin scroll type.
【図１】本発明の２段過給エンジン機構のブロック回路
図。FIG. 1 is a block circuit diagram of a two-stage supercharged engine mechanism of the present invention.
【図２】従来の通常の２段過給エンジン機構のブロック
回路図。FIG. 2 is a block circuit diagram of a conventional ordinary two-stage supercharged engine mechanism.
【図３】高圧側に２段の過給機を具備して、切換弁８に
より切換可能とした従来の２段過給エンジンのブロック
回路図。FIG. 3 is a block circuit diagram of a conventional two-stage supercharged engine having a two-stage supercharger on the high-pressure side and capable of switching by a switching valve 8.
【図４】低圧側に２段の過給機を具備した従来技術のブ
ロック回路図。FIG. 4 is a block circuit diagram of a related art having a two-stage supercharger on a low pressure side.
【図５】本発明の２段過給エンジンにおいて、低圧小容
量過給機Ｌのみを使用している状態のブロック回路図。FIG. 5 is a block circuit diagram showing a state in which only a low-pressure small-capacity supercharger L is used in the two-stage supercharged engine of the present invention.
【図６】本発明の２段過給エンジンにおいて、低圧大容
量過給機Ｍのみを使用している状態のブロック回路図。FIG. 6 is a block circuit diagram showing a state in which only a low-pressure large-capacity supercharger M is used in the two-stage supercharged engine of the present invention.
【図７】３段切換状態とした本発明の２段過給エンジン
の正味平均有効圧の状態を示す作用図。FIG. 7 is an operation diagram showing a state of a net average effective pressure of the two-stage supercharged engine of the present invention in a three-stage switching state.
【図８】２段切換状態とした本発明の２段過給エンジン
の正味平均有効圧の状態を示す作用図。FIG. 8 is an operation diagram showing a state of a net average effective pressure of the two-stage supercharged engine of the present invention in a two-stage switching state.
Ｈ 高圧段過給機 Ｌ 低圧小容量過給機 Ｍ 低圧大容量過給機 １１ ＣＰＵ １８ 切換弁 １９ 切換アクチュエータ １２，１４，１６ コンプレッサ １３，１５，１７ タービン H High-pressure supercharger L Low-pressure small-capacity supercharger M Low-pressure large-capacity supercharger 11 CPU 18 Switching valve 19 Switching actuator 12, 14, 16 Compressor 13, 15, 17 Turbine
Claims (1)
給機を有するエンジンにおいて、高圧段過給機Ｈのター
ビンスクロールを、エンジンシリンダの排気を２群に分
けたツインスクロール型とし、低圧段過給機には、容量
の異なる２台の過給機を併設し、エンジンの出力により
小容量過給機Ｌを運転する場合と、大容量過給機Ｍを運
転する場合と、小容量過給機Ｌと大容量過給機Ｍを同時
に運転する場合とに切換可能としたことを特徴とする２
段過給エンジン。1. An engine having a two-stage supercharger of a low-pressure stage supercharger and a high-pressure stage supercharger, wherein a turbine scroll of a high-pressure stage supercharger H is divided into two groups in which exhaust of an engine cylinder is divided into two groups. The low-pressure stage supercharger is provided with two superchargers having different capacities, and a small-capacity supercharger L is operated by an engine output and a large-capacity supercharger M is operated. And a case in which the small capacity supercharger L and the large capacity supercharger M are simultaneously operated.
Stage supercharged engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17085994A JP3311866B2 (en) | 1994-07-22 | 1994-07-22 | Two-stage supercharged engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17085994A JP3311866B2 (en) | 1994-07-22 | 1994-07-22 | Two-stage supercharged engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0828287A JPH0828287A (en) | 1996-01-30 |
| JP3311866B2 true JP3311866B2 (en) | 2002-08-05 |
Family
ID=15912645
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17085994A Expired - Fee Related JP3311866B2 (en) | 1994-07-22 | 1994-07-22 | Two-stage supercharged engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3311866B2 (en) |
Cited By (1)
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| CN109339938A (en) * | 2018-12-07 | 2019-02-15 | 哈尔滨工程大学 | Three condition two-stage consecutive pressurization system and its control method |
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|---|---|---|---|---|
| US6055812A (en) * | 1998-12-08 | 2000-05-02 | Detroit Diesel Corporation | System and method for controlling a sequential turbocharging system |
| DE10209002A1 (en) * | 2002-02-28 | 2003-09-11 | Daimler Chrysler Ag | 2-stage charging on the V-engine |
| DE102004009794A1 (en) * | 2004-02-28 | 2005-09-22 | Daimlerchrysler Ag | Internal combustion engine with two exhaust gas turbochargers |
| US7165403B2 (en) * | 2004-07-28 | 2007-01-23 | Ford Global Technologies, Llc | Series/parallel turbochargers and switchable high/low pressure EGR for internal combustion engines |
| DE102004039927A1 (en) * | 2004-08-18 | 2006-02-23 | Daimlerchrysler Ag | Internal combustion engine with an exhaust gas turbocharger and an exhaust gas recirculation device |
| DE102004044819A1 (en) * | 2004-09-16 | 2006-03-23 | Robert Bosch Gmbh | Method for multi-stage supercharging in internal combustion engines |
| DE102004044818A1 (en) | 2004-09-16 | 2006-03-23 | Robert Bosch Gmbh | Compressor bypass valve for multi-stage charging |
| GB2430708B (en) * | 2005-10-03 | 2010-09-22 | Ford Global Tech Llc | Turbo charging in a variable displacement engine |
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| WO2010005805A2 (en) * | 2008-07-07 | 2010-01-14 | Borgwarner Inc. | Multi-stage supercharging device of an internal combustion engine |
| JP5331435B2 (en) | 2008-10-07 | 2013-10-30 | ヤンマー株式会社 | engine |
| DE102008052170B4 (en) | 2008-10-17 | 2023-01-26 | Bayerische Motoren Werke Aktiengesellschaft | Two-stage exhaust gas turbocharging for an internal combustion engine |
| JP5324961B2 (en) | 2009-02-27 | 2013-10-23 | 三菱重工業株式会社 | Internal combustion engine supercharging system |
| DE102009030781A1 (en) * | 2009-06-27 | 2010-12-30 | Bayerische Motoren Werke Aktiengesellschaft | Multi-stage exhaust gas turbocharger for e.g. six-cylinder internal-combustion engine of vehicle, has high pressure turbine designed for ten percent larger exhaust mass flow than that of another high pressure turbine |
| JP5665602B2 (en) * | 2011-02-25 | 2015-02-04 | 三菱重工業株式会社 | Multistage turbocharger structure |
| DE102012020243B4 (en) * | 2012-10-12 | 2020-06-18 | Mtu Friedrichshafen Gmbh | Carrier housing for an exhaust gas turbocharger arrangement, exhaust gas turbocharger arrangement and internal combustion engine |
| US9181867B2 (en) | 2012-10-12 | 2015-11-10 | Mtu Friedrichshafen Gmbh | Carrier housing for a turbocharger arrangement |
| CN103061868A (en) * | 2013-01-31 | 2013-04-24 | 长城汽车股份有限公司 | Three-turbine supercharging mechanism and corresponding turbo-supercharged engine |
| CN105392974B (en) | 2013-06-11 | 2018-05-29 | 洋马株式会社 | Engine |
| JP6168862B2 (en) * | 2013-06-11 | 2017-07-26 | ヤンマー株式会社 | engine |
| DE102015203621A1 (en) * | 2015-03-02 | 2016-09-29 | Bayerische Motoren Werke Aktiengesellschaft | Two-stage turbocharger charging device for an internal combustion engine |
-
1994
- 1994-07-22 JP JP17085994A patent/JP3311866B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109339938A (en) * | 2018-12-07 | 2019-02-15 | 哈尔滨工程大学 | Three condition two-stage consecutive pressurization system and its control method |
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|---|---|
| JPH0828287A (en) | 1996-01-30 |
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